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Slate is a metamorphic rock that forms from mudstone or shale. Its colour is determined by the amount of iron it contains. Our slate wall tiles are offered in three colour choices, grey, black and a multicolour of brown, gold and blue tones. Slate has excellent non-slip qualities making it a perfect choice for wet rooms where they can be used seamlessly on floors and walls. Rich in natural texture, slate wall tiles create stunning feature walls, especially when cut to different sizes to create a brick bond effect.
Request or download one of our beautiful brochures to browse at your leisure.Request a brochure


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Kingston DataTraveler Elite DTE30/16GB USB Flash Drive - 16GB, USB 3.0, 30MB/s Write Speed, Plug & PlayItem#: K24-9976 | Model#: DTE30/16GB
Currently Out Of Stock!
Additional Resources
Kingston DataTraveler Elite 16GB USB Flash Drive Product Details
Product Type: USB flash drive
Storage Capacity: 16 GB
Enclosure Color: Black, white, graphite
Compatibility: Non-specific
Read Rate: Up to 70 MB/s
Write Rate: Up to 30 MB/s
Interface Type: USB 3.0
Features: Sliding lid
Software / System Requirements
OS Required: Linux 2.6.x or later, Microsoft Windows Vista SP2, Apple MacOS X 10.5.x or later, Microsoft Windows Vista SP1, Microsoft Windows XP SP3, Microsoft Windows 7 SP1
Manufacturer Warranty
Service & Support: Limited warranty - 5 years
Dimensions & Weight
Width: 2.7 in
Depth: 0.9 in
Height: 0.4 in
Environmental Parameters
Min Operating Temperature: 32 °F
Max Operating Temperature: 140 °F
Additional Resources: Product Manuals
Recommended Items
Manufactured by: Kingston
Warranty provided by: Kingston
UPC No: 740617200126
Mfg Part No: DTE30/16GB
Box Size:
( Length:4, Width:3, Depth:1)
Shipping Weight: 0.2500 pound(s)
Dimensional Weight: 1pounds
What is Dimensional weight?
Click here for full warranty and support information
- Kingston logos are registered trademarks of Kingston. All others trademarks and copyrights mentioned herein are the property of their respective owners.

subset: commoncrawl


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- Reliable Tub Resurfacing in Round Rock, TX
- Experienced Round Rock Tub Resurfacing Professionals
- Free Estimates on Tub Resurfacing in Round Rock
Tub Resurfacing in Round Rock, TX
Tub resurfacing Round Rock, TX services can erase all of the scratches, scuffs, and other superficial imperfections from your bathtub so that it looks great again. If you want to improve the way your bathtub looks, it is extremely important that you hire professionals to provide you with these services as soon as possible. One of the best things about paying to get your tub resurfaced is that doing so will cost a lot less than buying a whole new bathtub.
Avg Costs for Tub Resurfacing
Min Cost
Max Cost
Avg Cost
$291.32 - $397.41
Find the Best Quality Tub Resurfacing - Round Rock, TX
Those who are planning on remodeling their bathroom will certainly want to spend time looking into Round Rock tub resurfacing services. Tub resurfacing services in Round Rock, TX can make all the difference when it comes to making your bathtub look like new, and you will definitely need to hire professionals for the job. Over time all bathtubs get scratched and scuffed, but you can restore the aesthetics of yours by taking advantage of these services. When you pay for these services you will be able to get exactly what you need to guarantee that your tub looks much better as a whole. If you are tired of looking at your scratched and scuffed up bathtub, Round Rock tub resurfacing services will provide you with what you need.
Tub Resurfacing Companies
Hernandez, Ruben V
14100 Hytop Dr
Pflugerville, TX 78660
Bear Repair & Remodeling
760 Bent Wood Place Round
Round Rock, TX 78665
Harrington Glass
1003 S Industrial Blvd
Round Rock, TX 78681
Acme Roofing and Remodeling Co.
2401 W Whitestone Blvd
Cedar Park, TX 78613
Glass Commerical & Residential-Morris Glass
3575 Rocking J Rd
Round Rock, TX 78664
R.J.'s Construction
107 Desert Highlands Trl.
Round Rock, TX 78664


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In Dogs
life span?
I took in a small male dog in that my daughter had gotten for my grandson and I have no idea what breed he is.How can I find out his breed? I think he may be from the miniature terrier group.
Teeth cleaning
has anyone had their senior dogs teeth cleaned and had problems with eating afterward? Our dog seems to have pain when eating even after a week after the cleaning. This does not seem normal.
1 Comments
Our sweet Maddie
she has a red bump
hi my name is lavonna i have a dog a she has a red small bump on her paw what can that be or what is it i dont have money to go to a vet please help me
entropion in dog
can a dog who has had surgery for entropion be shown in conformation according to AKC rules
2 Comments
In Cats
sleepy cats
why some kittens like sleeping most time? my little cats look lazy...sometimes I do not know if they wanted to sleep or something else as in this video? help me pleasehttps://www.youtube.com/watch?v=RgbOjzn-qrA
my pet cat
I almost lost my cat tonight.My cooking gas ran out at night,and I couldn't get it refilled immediately. Due to the fact that I always fed my cat with cooked food, I opted for the closest alternative, and then fed it grilled meat. At first,it ate without any problems(as usual) After about 30 minutes when I was already immersed in my study,a heard a loud and strange sound from a corner of the house. On rushing down, there was my cat,struggling to survive. Its eyes were already dilated and it looked as if struggling to breath. I tried to see if I could eject something from its mouth, only to be bitten by it unconsciously. I was so upset and confused as to what next to do while I watched life fading out of my lovely companion(only the two of us live together) out of desperation. I hit it twice on the chest,then tried forcing some water down its throat and to my greatest surprise,it appreared to work, so I continued. By this time,it had already passed out stool. I almost lost hope ,but I didn't relent. Am so happy my cat is back to life.
Hey, does anyone have a kitten that fetches crisp packets? They have to be made up in a triangle and he will play fetch like a dog does with a ball.. it is the strangest funniest thing I have ever seen a kitten do. Does anyone else have cats/kittens that do similar things? Ollie also enjoys playing with long bits of plastic (supervised) but will play for hours and purr all day long with it. Never needing to buy toys for our kitten haha ! Would love to hear other stories similar ??
dogs are my favorite
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PIU's Fall 2017 Semester classes begin on August 28, 2017. Here are some important events to be aware of as you prepare to attend PIU this Fall. Please call 671-734-1812 for further information about any of these events. Or, email: [email protected] New Student Orientation – Wednesday, August 23......... more »
June July 17 Newsletter......... more »
Pacific Islands University is pleased to announce the appointment of Dorothy Houde as the University's Liberal Studies Chair. Dot is a graduate of State University of New York with a BA in Spanish and a MS in Teaching English to Speakers of Other Languages (TESOL). She is well qualified to lead PIU in providing quality......... more »
Click here for more information......... more »
On behalf of the PIU Board of Trustees, we are pleased to announce the appointment of Rev. Howard Merrell as Interim President of the Pacific Islands University, effective March 10. This decision was approved at the Annual Board Meeting on March 7-9, 2017. Rev. Merrel has taken over as Interim President after replacing......... more »
February 2017 Newsletter......... more »
Souls in Our Care Connecting Counseling and Pastoring February 2-4 at the PIU Campus Ministry Equipping Conference 2017 Information ......... more »
September 2016 Newsletter......... more »
Pacific Islands University held 2016 Graduation activities on Friday and Saturday, April 29 and 30. The Baccalaureate Service was held on Friday, April 29 at the Onnuri Church in Mangilao. The Graduation Ceremony was held on Saturday, April 30 at the Abundant Life Church in Dededo. The 2016 graduates included......... more »
Pacific Islands University held, "A Celebration of Micronesia," a fundraising dinner on Monday, March 7 at 6:00 PM at Puntan Dos Amantes (Two Lovers' Point). Please scroll to the bottom of the page to see pictures from the event. The event was a significant one for PIU. First, it honors the founding of PIU as ......... more »
Monday, January 24, 2016 at 2:30 PM Tuesday, January 25, 2016, is Pacific Islands University's Prayer Chapel and conclusion to our Day of Prayer. The Day of Prayer began at Noon today with a time of prayer led by Dr David L. Owen, President of PIU, in the Pavilion at the center of campus with everyone in......... more »
If you have questions, feel free to contact Joshua Combs at 734-1812 or by email at [email protected] ......... more »
Pacific Islands University, a fully accredited university located in Guam, begins Spring semester classes, at the Guam campus, January 11, 2016. Both on-site and online classes will be offered at PIU-Palau. Spring classes at PIU-Palau meet Monday-Thusrsday from5:00-6:30pm, beginning January 18. New Testament Surv......... more »
Pacific Islands University's 2015 Ministry Equipping Conference, Practical Trinitarian Theology, Was held October 1-3 at the Guam Reef Hotel. We were blessed with the presence of Dr. C. Baxter Kruger, lead the presentations and discussions. In addition, PIU Bible Study faculty taught and lead workshops. Resourc......... more »


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Maker's Halloween Large Cloche Birdcage-Black
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Additional Information
Striking and appealing, the Maker's Halloween Large Cloche Birdcage-Black is perfect to enliven your table decor this Halloween. This cloche birdcage has a tiny bat embellishment on the top for added spooky flair. You can display it as is, or place faux bats, ravens, pumpkins or other Halloween accents inside for a creepy look.
- Brand: Maker's Halloween
- Theme: Bat
- Dimensions: 8 x 8 x 14 inches (L x W x H)
- Handling Code:
Standard Delivery
You can usually expect delivery within 6-10 business days from your order date (business days are Monday-Friday, excluding Holidays). You'll receive an email with tracking information when your order is shipped. Please allow up to 5 business days to receive your tracking information.
Some items sent directly from our suppliers may take longer, and will ship separate from the remainder of your order.
Please note that Singer sewing machines cannot be shipped to Guam, Puerto Rico or the U.S. Virgin Islands or to military bases overseas.
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For more details & pricing. See our Full Shipping Policy >
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4 Milk St, Blackstone, Massachusetts
4 Milk St, Blackstone, Massachusetts 01504 - This gently sloping and wooded 4 acre lot is located on one of the few scenic roads in Blackstone, offering lots of space and privacy. This is an approved buildable lot which has been cut out of a larger parcel. The availability of single buildable lots of this caliber do not come along often. Do not miss this opportunity. Frontage is on the gravel portion of the lot. There is a marker noting the lot number approximately mid way along the frontage. Seller has completed the perc testing. A septic design is currently being developed - the lot will be conveyed with an approved septic design. Seller will work with buyer to build a home on the lot if requested - bring your plans or choose from some he has available.
Listing Courtesy of Lioce Properties, Inc.
"Karen's positive energy and enthusiasm lead me to list with her. Her knowledge of the area and community were key assets, that enabled her to find a buyer quickly for the home. She was always available to answer questions and guide me through the selling process. She held my hand throughout the entire process if there was a bump in the road, her can do attitude found a solution and kept things moving forward. She went above and beyond for me, and I am so grateful to her."


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Kitchenaid Kxu2836yss Range Hood Reviews and Complaints
Clear all filters (1 of 1 reviews match)
Nothing they can do for me, have to hire an electrician because they can't take the time to disclose you need to have it professionally installed. Home Depot who I bought it from doesn't list anything on their site either. If you can't be honest and upfront stop scamming consumers. Trust me KitchenAid...Read more
Kitchenaid Kxu2836yss Range Hood


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Peru: Ultimate Inca Trail
Day 1: Cusco Tour On arrival in Cusco airport please proceed to the baggage hall. At the exit to the building your guide will be waiting for you with a sign at the barrier outside the arrivals gate…. Read More
Costa Rica – Ultimate Adventure
For this fantastic activity packed Costa Rican ultimate adventure we explore the central and north-eastern part of Costa Rica, taking in the canals and rainforest in the Tortugero Sarapiqui – an adventurers dream, explore the cloud and paramo forest then you have the opportunity to relax at the 2 pools of hot springs in Chirripo Cloud Forest, snorkeling in the turquoise water and explore the capital city of Costa Rica.
Madagascar – Trekking and Kayaking in the Masoala Peninsula
On this trip we explore this natural paradise, kayaking the forested coastline and to deserted tropical islands, into pristine mangroves and shady rivers overhung by primary rainforest; snorkeling the coral reefs; swimming in warm tropical sea and crystal clear streams; beachcombing and exploring the rainforest for the unique wildlife.
Madagascar – Mountains & Rivers – Pic Boby to the Sea
This is an unforgettable trek through this mysterious land. Long series of adventures from the dry western side of the island to the moist eastern tropical rain forests while summiting Madagascar's second highest mountain in the country at… Read More
Nicaragua Explorer
Explore colonial cities, soaking up the history and atmosphere; peek into the rim of active volcanoes & walk through the rain forest; and swim through Somoto Canyon. This trip provides for an unforgettable holiday in one of Central America´s most diverse, friendly and beautiful countries.
Luxury Colombia – A Country of Contrasts
This expedition takes travellers through the most contrasting destinations in Colombia: Bogota's cosmopolitan restaurants and neighbourhoods, the Coffee Region's verdant hills and lush nature, Cartagena's streets lined with colourful colonial mansions, and the Rosario Islands' turquoise waters.
Arctic Adventure – Spitsbergen on Tracks
A trip of a lifetime that will be etched in your memories in years to come. We'll use snowmobiles to access the interior of the island, take you across frozen fjords, through steep sided gorges, glaciers and vast mountain ranges. A great way to experience Svalbard!
Costa Rica Family Holiday Multi-Activity Adventure
A fantastic action packed adventure, exploring the rainforests on foot, by horseback, cablecar, boat and raft. We check out volcano's, sea kayak on the pacific coast and get the chance to see the amazing rainforest fauna and flora…. Read More
South West Madagascar Nature Holiday – Land of the Lemurs
It's known as the Land of the Lemurs! Explore the wonders of Southern Madagascar on this nature guided trip of a lifetime, whilst taking in the most diverse environments at a comfortable pace. We will visit some of the best national parks, sites and arboretums & of course some off the beaten track places along the way. You'll be accompanied by a naturalist guide to ensure you have the best chance of witnessing as well as learning about all of the wonderfully unique flora and fauna of Madagascar. The south west is filled with adventure, iconic Madagascan animals, fabulous wildlife watching opportunities, outstanding landscapes, an abundance of culture and gorgeous hidden beaches lining the Indian Ocean; all waiting to be explored, encountered and cherished.
Borneo Wildlife and Rainforest Holiday
This Borneo holiday focusses on the wildlife, rainforests and beaches of the Sabah region of Borneo, one of the best areas for seeing the great variety of Borneo's fauna and flora. The jungles are literally millions of years old and teeming with wildlife, from the smallest insects and amphibians to orangutans, gibbons, monkeys, pygmy elephants and exotic birds.


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Arielle Castillo
Celebrate Hump Day With Roofless Records at the American Legion, April 14
Thursday, April 1, 2010 at 3 p.m.
For those of us sadly toiling, at least occasionally, in a cubicle, Wednesday is a shining beacon -- if you can just grasp onto your sanity until this day, everything will be okay. Actually, chances are, if you're part of the crew that frequents the shows at the American Legion, you may not have the most demanding 9-to-5, but shit, who are we to judge? It's as good a reason as any to toast life with cheap drinks and some live rock and roll.
Wednesday, April 14 marks a hump day celebration put on by Roofless Records, a one-man operation that just seems to gain more and more steam lately with an increased number of releases and shows around the Biscayne corridor. And this one features some out-of-towners, the Baltimore threesome Yukon. B-more is a growing epicenter of a scrappy movement of d.i.y. rock, and Yukon's sound is, as expected, kind of lo-fi. Where it differs from many of the typical garagey offerings at the Legion shows, though, is in a certain progressive heaviness, with an arty, space-filling sound that hovers around the lightest edges of stoner rock.
Co-headliners Cop City/Chill Pillars are semi-local, hailing from Lake Worth, and play a considerably louder, more roughed-up sound, something akin old school punk rock lovingly retrieved from a dumpster. Miami-based support for this show comes from the experimental, heavy-ish semi-supergroup Beings, and the comparatively hushed, psychedelic trio Raja Khan.
Hump Day by Roofless Records. With Yukon, Cop City/Chill Pillars, Beings, and Raja Khan. 9 p.m. Wednesday, April 14. The American Legion, 6445 NE 7th Ave., Miami. Admission is $5; age 21 and up; rooflessrex.com
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New regulations put professionals at the forefront of business
In spite of a turbulent decade for the accountancy and auditing professions, the vice-president of the Association of Certified Chartered Accountants (ACCA) says lessons have been learned and the industry is responding responsibly.
Professor Barry Cooper says accounting scandals involving Enron, which subsequently led to the collapse of accounting firm Arthur Andersen, and the recent global financial crisis, had resulted in new regulations and put the accounting profession at the forefront of business processes.
He says accountants now have a more defined role in setting standards and maintaining good corporate governance. In addition to technical skills, accountants' involvement in a business has become much broader to include strategic decision-making, ethics standards and risk management.
"Accountants need to be aware of new business models and be part of the wider management process. It is no longer only the CEO and senior management team that make strategic decisions; they are involving their accountants to look at the financial risks involved in transactions that could pose a financial risk or a possible threat to reputation."
Cooper says the ACCA welcomes the focus placed on professional values, ethics, and governance. "The ACCA syllabus has ethics at the heart of its qualification, but you cannot teach ethics. You can sensitise students to ethical issues and give them a mould to work with," says Cooper, who is a professor of accounting at Deakin University, Australia.
With Asian economies booming and companies moving to the region, the demand for accountants and the opportunities for accountants to move into senior management positions continue to grow.
Cooper says qualified Asian accountants with overseas experience are in a prime position to provide services to European and United States firms expanding into Asia. "The unique benefits and characteristics of having an Asian background coupled with an understanding of Asian and Western business cultures is a valuable asset to any business that migrates to this part of the world," says Cooper, head of Polytechnic University's accountancy department from 1987 to 1991.
Cooper says Asian accountants should also prepare themselves for the growing global acceptance of International Financial Reporting Standards (IFRS). But the region's accountants still need to be aware of local variations in the IFRS.
This will be particularly important where accountants are involved with cross-border transactions and companies operating in multiple jurisdictions. Third-party disclosure rules used among mainland state-owned enterprises is another area that Hong Kong accountants working for mainland firms could master, Cooper adds.


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Chesson thrills home fans at New Egypt. NEW EGYPT, NJ (July 29)-- P.J. Chesson couldn't have written a better script for his first Pennzoil World of Outlaws Series "A" Feature victory. The 23-year-old driver from Far Hills, NJ, started on the ...
Chesson thrills home fans at New Egypt.
NEW EGYPT, NJ (July 29)-- P.J. Chesson couldn't have written a better script for his first Pennzoil World of Outlaws Series "A" Feature victory. The 23-year-old driver from Far Hills, NJ, started on the pole and led all 30 laps to the delight of his home fans Monday at New Egypt Speedway.
"This is great!" Chesson yelled to the partisan crowd after turning doughnuts and climbing the fence on the front straightaway. "This is New Jersey. This is my home. These are my fans. We own this place! My guys-- Matt Anderson and Scott Vogelsong-- work really hard and they gave me a great car tonight. When the car's as good as it was tonight, it's pretty easy to drive-- even I can win a race. I'm just glad to get a win here with my family here, and all of my friends. It doesn't get any better. Now we'll go to Eldora and try to win another Big One."
Chesson, the seventh-fastest qualifier, finished third in the First Heat Race and earned the right to start the main event on the pole by winning the First O'Reilly Auto Parts Dash. He drove his family's #76 Automotive Service Centers Eagle into the lead as the green flag fell in the "A" Feature.
Tim Shaffer steered the #83 Beef Packers Eagle around fast-qualifier Craig Dollansky in the high groove between turns one and two for third place as Chesson raced away from the field during the second lap.
Donny Schatz, who won the Pennzoil World of Outlaws Series' inaugural race at New Egypt last July 30th, started inside the seventh row. The 1997 Kevin Gobrecht Rookie of the Year drove his #15 Parker Stores J&J past Second Heat Race winner Fred Rahmer for 10th place in the high groove in turn one early in the fourth lap.
Chesson was 2.3 seconds ahead of Second O'Reilly Auto Parts Dash winner Daryn Pittman when he entered lapped traffic during the sixth lap. The defending World of Outlaws Gumout Series champion closed to within .5 seconds of the leader within five laps, only to have Chesson burst through traffic and open a 3.5-second advantage midway through the race.
Schatz won a front-straightaway drag race with Danny Wood for ninth place early in the 18th lap.
Pittman was only .3 seconds behind Chesson when Jason Hagenbuch and Randy West crashed in the third corner late in lap 22.
Mark Kinser, who suffered a blown engine during the qualifying session, started at the rear of the field and raced past nine cars in the first 17 laps. He drove the #5M Mopar Maxim into the low groove between turns three and four to pass Wood for 12th place late in lap 25.
Chesson was 1.8 seconds ahead of Pittman when he caught the back-markers with four laps remaining. A daring move between Hagenbuch and Trevor Lewis in the fourth corner the next time around gave Chesson a 2.2-second lead. Chesson, who won the Preliminary Feature during the Duel in Dakotas at Red River Valley Speedway July 5th, took the checkered flag with 1.8 seconds to spare. He is the 14th driver to win a Pennzoil World of Outlaws Series main event this year.
Shaffer finished in third place, ahead of Dollansky, Randy Hannagan, Brad Furr, Johnny Herrera, Pennzoil World of Outlaws Series point standings leader Steve Kinser, Schatz and Rahmer.
Dollansky set quick time for the fifth time this season, circling the slightly-banked, 4/10-mile oval in 16.359 seconds, an average speed of 88.025 M.P.H.
Herrera drove the #20 J.D. Byrider Eagle for the injured Danny Lasoski for the second straight race.


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Umzi Motors Ltd
- Telephone:
- 020 80339292 | 07441 906952
- 330-332 Eastern Avenue, ILFORD, ESSEX, IG4 5AA
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Key factsPrint summary
HPI CLEAR, FULL LEATHER HEATED SEATS, FULL PANORAMIC SUNROOF, FULL SERVICE HISTORY FROM NISSAN MAIN DEALER, VERY WELL LOOKED AFTER, FIRST TO SEE WILL BUY-- WE HAVE MORE IN STOCK, SIMILAR QASHQAIS. ++++ IT COMES WITH THE TOW-BAR, WHICH IS REMOVABLE. Black, CALL US FOR FURTHER DETAILS , WARRANTY AVAILABLE T/C APPLIED , 5 DAYS DRIVE AWAY INSURANCE , ALL MAJOR CARDS & CREDIT CARDS ACCEPTED , PART EXCHANGE WELCOME , FINANCE AVAILABLE, , Contact: 07498192255, £4,670
This car comes with
Panoramatic Glass Roof, Sunroof Electric, Parking Aid (Rear), Cruise Control, Climate Control, Seats Heated (Driver/Passenger), Upholstery Leather, Electric Windows (Front/Rear), Alarm, Telephone Equipment, In Car Entertainment (Radio/CD Autochanger), Alloy Wheels
- 201707107244423
- 2007
- 07
- £4,670
- 467
- 116,398
- Cars
- xJIZlzc0o/w=
Vehicle summary
|Body style
|Engine size
|1997 cc
|Fuel type
|Number of doors
|Number of seats
|Gearbox type
|Continuously Variable Transmission
|CO2 emissions
|192 g/km
|Insurance group
|Standard manufacturer's warranty (miles)
|60000 miles
|Standard manufacturer's warranty (years)
|3 years
|Standard paintwork guarantee
|3 years
Performance & economy
|Fuel consumption (urban)
|27.2 mpg
|Fuel consumption (extra urban)
|43.5 mpg
|Fuel consumption (combined)
|35.3 mpg
|0 - 60 mph
|10.7 seconds
|Top speed
|118 mph
|Engine power
|139 bhp
|Engine torque
|144.57 lbs/ft
|1615 mm
|Height inclusive of roof rails
|No details available
|4315 mm
|2630 mm
|1780 mm
|Width including mirrors
|No details available
|Fuel tank capacity
|65 litres
|Minimum kerb weight
|1378 kg
|Interior features
|Exterior features
|Seats Heated (Driver/Passenger)
|Sunroof Electric
|Climate Control
|Windscreen Wiper
|Roof Rails
|In Car Entertainment (Radio/CD Autochanger)
|Panoramatic Glass Roof
|Upholstery Leather
|Spare Wheel (Space Saver)
|Electric Windows (Front/Rear)
|Headlamp Wash
|Seat Height Adjustment
|Mirrors External
|Cruise Control
|Alloy Wheels
|Adjustable Steering Column/Wheel
|Trip Computer
|Telephone Equipment
|Seat Lumbar Support
|Head Restraints
|Seat - ISOFIX Anchorage Point
|Air Bag Passenger
|Third Brake Light
|Air Bag Side
|Anti-Lock Brakes
|Air Bag Driver
|Power-Assisted Steering
|Central Door Locking
|Parking Aid (Rear)
|Centre Rear Seat Belt
|Electronic Stability Programme
|Front Fog Lights
|Traction Control System
Please note
This includes MPG figures which are calculated under European Standards, in test conditions, and will vary under normal driving conditions. The information displayed above describes the typical specification of the most recent model of this vehicle. It is not the exact specification for the actual vehicle being offered for sale which may vary. Specifications for older models may also vary. Please contact us prior to purchase to confirm the exact specification of this vehicle.
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American City Life and Rural Life Essay
American City Life and Rural Life
Was life in an American city better or worse than life on the farm for the average American? " Substantiate your answer with facts/examples. (Ch. 18) Does it really make a difference where you live? Is there any change in people's lives if they live in the city or the country? With no pun intended, this is a chicken and egg question – do urban and rural residents choose where they want to live based on their lifestyle preferences or do lifestyles change because of the environment? The word Rural" is defined by population density which means how many people are there in a given square mile.
Urban areas are defined by the "census blocks" that have a population density of at least 1,000 people per square mile. The life in a city and on a farm has its own pros and cons. Even though my life is in the city (suburban) area, I prefer to live life on a farm. There are different aesthetic experiences between city and farm life. Even the prepositions show the difference-The farmer lives "ON" a farm and the urban friend lives "IN" a city. The cities attracted people from the countryside looking for higher wages and cultural enlightenment (Brinkley p496).
In addition, life in an American City was visualized as an escape for many citizens, an escape from what they considered "The Boredom of Rural Life" (p. 502). Also, the city was preferred because people can experience the new forms of entertainment, amenities and cultural experiences unavailable in rural areas. People moved to cities because new forms of transportation made it easier for them to get there. (pg 503) but this also was a cause for increased crowding in the cities. The unemployment rate is also much higher than in the city.
Some differences between city and farm life: First of all, countryside is not polluted,so you can breath there fresh air. Besides, the road traffic is much lesser compared to cities, thus you can enjoy silence in the country. You can also relax and go for a nice walk in the forest or in the meadows. What is more important, is that the country people can grow their own fruit and vegetables which are healthier than those you can buy in the greengrocer's in the city. Another advantage of country life is it is safer than life in a metropolis.
In small towns or villages, crime rate is usually very low and people need to be afraid of having their house broken into or of being attacked and robbed in the street. In addition, it seems that in the country the relationship between people are more genuine as people are more friendly and open there. On the other hand, divorce rates in rural areas are generally lower, in part because couples don't move around as much. While incomes tend to be lower in rural counties, the cost of living is also proportionally lower.
As they become older, people are tired with the hectic and stressful city life and often decide to move outside the city. All things considering, it is obvious that both country and city life have their advantages and disadvantages. Some people find city life more exciting and appealing than small towns but others prefer beauty and tranquility of the countryside, but a lot of people prefer city life because it is much easier. The choice whether to live in a city or country side depends on every person's character and preferences.
Subject: City,
University/College: University of California
Type of paper: Thesis/Dissertation Chapter
Date: 9 January 2017
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Bleacher Report
France vs. Portugal: Score, Report and Reaction from International Friendly
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France continued their preparations for the hosting of Euro 2016 with a 2-1 win over Portugal in Paris on Saturday. Les Bleus coach Didier Deschamps will have to make do with friendlies due to his side qualifying automatically as hosts. But this was …
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The Apt complex went through some major exterior renovations earlier this year and some random loose ends continue to be addressed. This Apt complex was swarming with construction workers of dubious character and beady eyes… sorry but I do not like strangers, especially those hanging outside my bedroom window singing Mexican folk music while painting the window trim. The creep factor is high!
My point is that every day when I leave for work I require the Hubby to lock the door behind me "so the Mexican's don't rape you". Yes, of course I mean it as a joke, but living in an Apt complex is a lot different than living in a single family home (where I never locked a door in my life). Too many strangers, too close for comfort. Stay outta my personal space. Yes, I am a Northerner and my Northern Attitude is not conducive to Southern hospitality…or Apt living obviously.
This morning as I am getting ready for work, wearing a robe and making a cup of tea, the door bell rings…Hubby and I look at each other…"you answer it…no you answer it". What the hell? Isn't he supposed to be the tough man protecting his household and wife from strangers at the door at 8:30 a.m.? Humpf.
I peek out the eye hole and I can see a woman wearing what looks like scrubs. I open the door…Turns out there are 4 women outside the door. They ask me if the décor/wicker chairs/etc. displayed outside my Apt. door belongs to me.
Now I'm thinking they are going to tell me to clear my stuff out as (for the third time in 6 months) this Apt. complex has changed management companies and they don't like it.
Turns out, the ladies are from a cleaning agency that services the Corporate Housing Apt across the hall (random Asian men live there from time-to-time). They love my décor choices and want to know where I find my eclectic crappy-craps, especially the etched slate plaque that reads: "Please don't piss off the fairies".
OK ladies, once again the Southern charm factor has softened my hard northern skepticism. Albeit early, thank you for your kind words and making me feel good about my crappy-craps.
Before I leave for work, I turn to Hubby and state the following: "lock the door behind me so the cleaning ladies don't come in here and capture a new husband".
He replied, "Well, at least the place will be clean."


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|Publication number
|Publication type
|Application number
|Publication date
|Apr 10, 1990
|Filing date
|Oct 3, 1988
|Priority date
|Apr 25, 1986
|Fee status
|Publication number
|James B. Lammers
|Original Assignee
|Campbell Hausfeld/Scott Fetzer Company
|Export Citation
|BiBTeX, EndNote, RefMan
|Patent Citations (16), Referenced by (12), Classifications (14), Legal Events (4)
|External Links: USPTO, USPTO Assignment, Espacenet
This is a division of application Ser. No. 856,645, filed Apr. 25, 1986, now U.S. Pat. No. 4,801,250.
The efficiency and reliability of an air compressor are generally functions of a number of factors, primarily having to do with the way air is moved, and its temperature controlled, throughout the process.
This invention relates to air compressors and more particularly to improvements in the valving, intake manifolds, crankshafts and to cooling of air in air compressors, which improve efficiency and reliability and which reduce operating noise.
A typical, industrial quality air compressor may currently be of the two-stage type wherein air is first compressed in one cylinder, then transferred to another cylinder from where it is moved to a receiver. Such cylinders may be oriented in a "V" configuration, and driven by a belt driven pulley, for example, at a speed of about 900 to 1000 rpm.
In the past, such compressors have used, among other arrangements, valve plates disposed between the cylinder and cylinder head to provide appropriate intake and exhaust valving for that cylinder. While various types of valves have been used in connection with such plates, it is common to find reed valves mounted thereon. Such reed valves are generally a flexible reed of metal, fixed at one end to the valve plate or associated cylinder head for closing appropriate ports in the head or valve plate as air is compressed from or drawn into the cylinder.
In another known reed valve configuration, a reed valve lies freely over a port in a valve plate and a curved valve stop surface in the head lies above the reed to stop it when air blows through the port. In these devices, the head is separated from the valve plate by a gasket and the ends of the reed valve are prone to chew away at the gasket, work their way into the gap between head and plate, and become pinched. Further compressor operation flexes the reed around its "pinch point" and between the head and plate, and the reed can prematurely fail, severely reducing compressor reliability. Another disadvantage of this construction is that fluttering valve ends can cut grooves in the head stop surfaces. The reed can work itself into these wear grooves and find itself then locked in the wear zone it has cut out, in an open position spaced away from its associated port.
In another type of known device, a reed is positioned over a raised port in a valve plate, and an integral, concave stop bar is disposed on the valve plate over the reed. The stop bar, at its ends, captures the flexible reed over the raised port and may or may not touch the reed when it is closed. Air pressure in the port flexes the reed open. Such stop bar configuration, because of its shape, is difficult and expensive to use where it must be hardened. It also requires separate fasteners which lead to assembly difficulties.
Moreover, it is believed that compressors of the type noted, i.e., two-stage, twin-cylinder compressors of about 5 horsepower, for example, are generally run at about 900-1000 rpm, or less, by a belt and pulley drive, for example, and produces about 16.5 cfm at 175 psi. It is desirable, however, to provide a compressor of much more compact and lighter construction, while retaining a similar output. While it may be possible to retain such similar output in a smaller compressor operating at higher speeds, it has been found that valve structures such as the reed valves mentioned above, which function sufficiently at lesser speeds, cannot handle such higher speeds. When run at higher speeds, such valves produce less efficient results, fail prematurely, or both. Thus, the selection of a valve structure for a compressor having an increased output is considerably complicated by the inherent disadvantages of the prior structures noted above, or by their inability to efficiently handle increased operating speeds, or both.
It has accordingly been one objective of this invention to provide an improved reed valve for an air compressor.
A further objective of the invention has been to provide an improved valve plate and valves for use with an expansible chamber and head.
A further objective has been to provide an efficient, long-lasting reed valve for a compact, twin cylinder, two-stage air compressor operating at about 1725 rpm and producing about 16.5 cfm at about 175 psi.
One consideration in the manufacture of piston type air compressors is the construction of the crankshaft, which must be dynamically balanced, and the simultaneous desirability of using a one-piece piston connecting rod.
In order to most optimally dynamically balance a crankshaft used in a V-twin compressor, it is generally necessary to provide a crankshaft with counterweights at each end thereof. This necessitates, however, the use of two-piece connecting rods since it is generally not possible to slip such a double weighted crankshaft through a one-piece connecting rod for assembly. Use of a two-piece connecting rod increases the possibility of a loose screw or other part in the crankcase, failure of the connecting rods, or both. This can severely reduce reliability.
Accordingly, it has been a further objective of the invention to provide an improved crankshaft for a compressor, which can be dynamically balanced with counterweights at both ends, yet can be used with one-piece piston connecting rods.
Where it is desired to provide a direct drive compressor, the coupling between the motor drive shaft and the compressor crankshaft can be the source of several problems. In one configuration, as an example of one problem, the motor drive shaft is screwed into the crankshaft. Through time and many operational cycles, the drive shaft and crankshaft interact to produce "fretting" corrosion. This makes it extremely difficult to separate the two parts for maintenance or parts replacement.
Accordingly, it has been one objective of the invention to provide an improved crankshaft and for preventing fretting or corrosion between the crankshaft and a motor drive shaft.
Moreover, where a cooling fan is to be used in conjunction with the compressor, means to mount and drive the fan must also be considered.
In a typical belt driven compressor, a driven pulley serves dual purpose. It provides a speed reducer, its spokes operate as a cooling fan. Where a direct drive motor and compressor configuration is to be utilized, in lieu of a belt drive and fan pulley, the compressor crankshaft can also be used to drive a cooling fan.
In this regard, it has been a further objective of the invention to provide an improved cooling fan drive for a direct drive compressor.
It has been a further objective of the invention to provide an improved cooling fan drive in a direct drive air compressor together with an improved compressor crankshaft.
It has been a still further objective of the invention to provide an improved direct drive compressor crankshaft for preventing fretting or corrosion between the crankshaft and a drive shaft, which can be dynamically balanced by means of counterweights on opposite sides of a one-piece piston connecting rod and which provides an improved direct drive fan or cooling fan.
When a fan is used with a compressor for cooling, it is desirable to maximize its cooling efficiency. Air directing shrouds have been used for this purpose. It has been, however, a further objective of this invention to provide an improved fan shroud and compressor wherein cooling air is even more efficiently handled.
Air compressors frequently utilize intake manifolds for the purpose of both filtering air or for muffling the noise generated by the compressor. The combination of elements to provide both appropriate filtering and desirable muffling performance is frequently elusive.
Accordingly, it has been a further objective to provide an improved intake manifold for both filtering incoming air to be compressed and for muffling compressor noise.
To these ends a preferred embodiment of the invention includes an improved valve and valve plate for use between the cylinder and cylinder head of a compressor. The valve plate is provided with at least one free-floating reed valve therein. The new reed valve is not held, pinched or biased into any particular position, but is free to float between a closed position over an exhaust port, for example, in the plate, and an open position where portions of its end areas engage respective hardened and radiused keeper bars lying transversely over the reed. There is more vertical space between the keeper bars at the floor of the reed valve recess on the valve plate than the reed is thick, thereby providing its free-floating condition.
Since the keeper bars are relatively small and constitute parts which are not an integral part of the head, the valve plate or any restrictor plate, they can be easily hardened and thus eliminate the necessity and expense of hardening the much larger head or valve plate, for example.
The keeper bars lie in recesses which are shallower than the thickness of the bars. Thus, the bars extend above the surface of the valve plate. The head is provided with keeper bar engaging surfaces and a concave reed stop surface contoured to receive the opening reed, and grooved to permit air to cross over the reed to the exhaust port from the head.
An elongated silicone seal is disposed preferably in a groove extending peripherally around the head and seals against the valve plate, when the head is assembled to the valve plate, once the keeper bar engaging surfaces engage the keeper bar. These surfaces are in the same general plane as other head surfaces mating with the valve plate and may not touch, except at the points where the head bolts are located. Nevertheless, the seal effectively seals the head and valve plate together once the head engages the keeper bars.
On the intake side, the valve plate is provided with an intake valve recess receiving a free-floating reed valve similar to that of the exhaust side. This intake valve is similarly captured, in a free-floating condition, by hardened and radiused keeper bars lying in channels and transversely spaced over the reed.
A restrictor plate recess is also provided in the intake side, and a ported restrictor plate is disposed therein for securing the keeper bars over the intake reed and serving as a reed stop. The restrictor plate has a portion extending beyond the open cylinder bore below it so as to itself be held in place by surfaces surrounding the cylinder at its upper end.
As in the exhaust side, the intake reed keeper bars are thicker than their receiving channels are deep. The restrictor plate has surfaces engaging these bars before the restrictor plate bottoms out in its recess. The engagement of the restrictor plate by the upper cylinder surfaces thus retains the keeper bars in proper position, capturing the intake reed in its recess in operative relationship with an intake port in the valve plate.
An elongated silicone seal is disposed in a groove in the intake side of the valve plate. This seal engages surfaces on the upper end of the cylinder and seals the valve plate and cylinder when the plate is assembled thereover and the restrictor plate is bottomed on the keeper bars.
The valve plate and valves so described are capable of operating at high speed cycles of, for example, 1725 compressions per minute. The free-floating valves are not pinched, and not required to flex along a fixed "hinge line," but rather free float and provide a lengthy service life even at the noted high speed operation. The valves are very easy to replace, and there are no rivets or screws to remove, or to fall into the cylinder.
In another aspect of the invention, an improved compressor crankshaft is cored or hollowed out, and has an integral counterweight provided at a driven end thereof. For direct drive, the crankshaft drive end is bored out and threaded to receive the drive shaft of a motor. According to a preferred embodiment of the invention, the bore of the drive end of the crankshaft extends through said crankshaft to the hollowed out area. This area is opened, through large portals in the crankshaft within the crankcase, and oil from the crankcase is transmitted to the internal threaded area connecting the crankshaft with the drive shaft. This lubricates the threaded drive connection and prevents fretting or corrosion.
The cored crankshaft is preferably provided with an integral counterweight on its driven end, but no integral counterweight on the other end. This other end can easily be slipped into a one-piece piston connecting rod. A removable counterweight is disposed on this same other end, after connecting rod assembly. Thus, the crankshaft can be balanced through the use of counterweights on two ends, yet still accommodates a one-piece connecting rod.
A fan is mounted on the drive axis provided by the end of the crankshaft to which the removable balance counterweight is mounted. According to the invention, a fan drive pin extends from the removable counterweight at a position radially spaced from the drive axis and engages the fan to drive it as the crankshaft and counterweight rotate. This provides a positive fan drive through the nevertheless removable counterweight.
In another aspect of the invention, a shroud is provided to direct air into and from the fan over the cylinders and cylinder heads in a V-shaped configuration. Deflectors are provided in conjunction with air exhaust ports mounted in shroud projections of a V-shaped shroud backplate to direct cooling air over the heads and cylinders.
An intercooler provides a compressed air passage leading from one cylinder to the other, i.e., from the first to the second stage. The intercooler is in a wound or spiral configuration and is disposed behind the shroud backplate. An orifice is disposed in the backplate, between the cylinder cooling exhausts, and is in register with the intercooler to direct cooling air over it and cool the first stage air as it moves into the second stage.
In still another aspect of the invention, an intake manifold comprises a chamber defined by a shroud and a backing plate. The chamber is divided into two portions by two sets of ribs extending from the backing plate to the shroud. The sets of ribs define between them a slot for receiving a foam type air filter. Opposed walls mounted on elongated edges of the ribs close off the chamber portions from each other, excepting an air passageway between the forward wall edges spaced from, but near, the shroud side of the chamber.
A plurality of open air inlet tubes extend into a first chamber portion from said shroud to a position spaced from but proximate to the backing plate. An air outlet port is disposed in the second chamber portion for conducting filtered air to the first stage of the compressor. The combination of the tubes and the chamber portions serve to efficiently muffle compressor noise.
These and other objectives and advantages will become readily apparent from the following written description of the invention and from the drawings in which:
FIG. 1 is a top plan view of a V-twin, two-stage, air compressor according to a preferred embodiment of the invention;
FIG. 2 is a cross-sectional view taken along lines 2--2 of FIG. 1;
FIG. 2A is a partial enlarged view of the cylinder top, valve plate, and head as shown in the upper right portion of FIG. 2;
FIG. 3 is a cross-sectional view taken along lines 3--3 of FIG. 2;
FIG. 4 is a cross-sectional view of the cooling fan shroud taken along lines 4--4 of FIG. 3;
FIG. 5 is a cross-sectional view of the intake manifold taken along lines 5--5 of FIG. 2;
FIG. 6 is a cross-sectional view of the valve plate, intake valve, keeper bars and restrictor plate taken along lines 6--6 of FIG. 2A;
FIG. 7 is a cross-sectional view taken along lines 7--7 of FIG. 6;
FIG. 7A is a cross-sectional view taken along lines 7A--7A of FIG. 6;
FIG. 8 is a cross-sectional view of the valve plate, exhaust valve and head taken along lines 8--8 of FIG. 2A;
FIG. 9 is a cross-sectional view taken along lines 9--9 of FIG. 8;
FIG. 10 is a cross-sectional view taken along lines 10--10 of FIG. 2A, looking down onto the valve plate;
FIG. 11 is a cross-sectional view taken along lines 11--11 of FIG. 2A, looking up onto the valve plate, but without the restrictor plate thereon;
FIG. 11A is a view looking up onto the restrictor plate, omitted for clarity, from FIG. 11;
FIG. 12 is a cross-sectional view taken along lines 12--12 of FIG. 2, looking down onto the valve plate of the cylinder on the left side of FIG. 2;
FIG. 13 is a cross-sectional view taken along lines 13--13 of FIG. 2, looking up onto the valve plate noted in FIG. 12, except with the restrictor plate omitted for clarify;
FIG. 13A is a view looking up into the restrictor plate, omitted for clarity, from FIG. 13; and
FIG. 14 is a diagrammatic illustration of a modified valve construction according to the invention.
Turning now to the drawings, there is shown in FIG. 1 thereof a compressor 10 according to a preferred embodiment of the invention. Compressor 10 includes a drive motor 11, a crankcase 12, two cylinders 13 and 14 mounted on the crankcase 12, and a cooling fan shroud 15.
According to a preferred embodiment of the invention, and without limitation, compressor 10 is preferably a two-stage air compressor wherein cylinder 13 is a first stage for compressing air from ambient pressure a first elevated pressure and cylinder 14 comprises a second stage for compressing compressed air at the first elevated pressure from the first cylinder 13 to a second and higher pressure. Compressed air from cylinder 13 is transmitted to cylinder 14 for further compression via an intercooler 16. Each of the cylinders 13 and 14 is provided with a respective head 17 and 18.
It will be appreciated that the cylinders 13 and 14 are disposed on the crankcase 12 in a V-shaped configuration, the compressor being commonly referred to then as a V-twin compressor. Also, it will be noted that the motor 11 is preferably directly coupled to the compressor so that the compressor is referred to as a direct drive compressor.
As shown in FIG. 2, each of the cylinders 13 and 14 is provided with a respective piston 19 and 20 mounted for reciprocation within the cylinders about a crankshaft 21. A one-piece connecting rod 22 connects piston 19 to the crankshaft 21, while a somewhat similar one-piece connecting rod 23 connects piston 20 to the crankshaft 21. Each of the cylinders and pistons define respective expansible chambers 24 and 25.
It is to be appreciated that the compressor as shown in FIGS. 1 and 2 comprises preferably an industrial quality, V-twin, direct drive compressor, wherein the motor 11 is of any suitable size, and preferably constitutes a 4-pole, 60 cycle motor of about 5 horsepower, and producing an operating rotation of about 1725 rpm, such that each expansion chamber 24 and 25 undergoes about 1725 compression cycles per minute. While compressors of other parameters and characteristics are also contemplated within the scope of this invention, a preferred two-stage compressor has a low pressure or first stage cylinder 13 and piston 19, providing a cylinder bore of about 3.25" diameter and a piston stroke of about 2.63". The high pressure or second stage cylinder 14 and piston 20 provide a bore of about 1.71" diameter and a stroke of about 2.63". When such compressor is run at 1725 cpm, it produces compressed air in a volume of about 16.5 cfm at 175 psi. Features of the invention may be used in other types of compressors, both single and two-stage, direct drive and belt-driven and of varying power, output and speed.
It should also be appreciated at this point that the normal desired speed of a motor 11, such as a 4-pole motor at 60 cycles is about 1725 rpm. The capacity of the compressor to operate at this speed (and thereby retaining an output of about 16.25 cfm at about 175 psi) eliminates the need for a bulky and weighty speed reducing device. This is a substantial advantage provided by this invention.
Chamber 24 is further defined by a valve plate 26, while the expansible chamber 25, associated with cylinder 14 and piston 20, is further defined by a valve plate 27. With the exception of size, and of the particular port size and configuration in the valve plates, the respective valve plates and heads associated with each of the cylinders 13 and 14 are essentially similar.
It will be further noted that the head 17 includes a first intake port 30 for receiving ambient air from an intake manifold 31. Head 17 further includes an exhaust port 32 for connecting the exhaust from the expansible chamber 24 to the intercooler 16. Head 18 includes an intake port 33 for receiving compressed air from the intercooler 16, and a further exhaust port 34 for transmitting further compressed air from expansible chamber 25 to an outlet duct 35.
As shown in FIG. 1, the intercooler 16 comprises a wound conduit 36 having cooling fins 37 thereon for the purpose of cooling air transmitted through the intercooler 16. Intercooler 16 is in a general spiral configuration as shown in FIGS. 1 and 2, providing an extended path between the compressor stages defined by the expansible chamber 24 and 25, respectively.
For the purpose of clarity and illustration, the valve plate 26 (associated with the cylinder 13), together with the top surfaces of the cylinder and the lower surfaces of the associated head 17 have been shown in an enlarged form in FIG. 2A. Valve plate 26 will now be described.
Valve plate 26 comprises an essentially flat piece of preferably metallic material having holes, such as holes 38 (FIG. 10), disposed therein for receiving elongated fasteners which secure the head, the valve plate and the cylinder together. As also shown in FIG. 10, plate 26 includes two intake ports 40 and 41 and an exhaust port 42.
Turning now to FIG. 8, there is provided in the upper or exhaust side of valve plate 26 a first recess 45. Disposed in the recess 45 is a free-floating, flexible reed valve comprising an exhaust valve 46. Transverse recesses or channels 47 and 48 (see also FIG. 10) are cut into the exhaust side of the valve plate in a position where they extend across the reed valve receiving first recess 45. Thus, the second and third recesses 47 and 48 are centrally discontinuous, with only their ends being defined by respective relieved portions in each side of the first recess 45 for receiving the ends of hardened keeper bars 49 and 50.
Each of the keeper bars 49 and 50 has a respective corner 51, 52 which is radiused and provides a smooth surface for engagement by the free-floating reed exhaust valve 46. The keeper bars 49 and 50 each have lower surfaces 53 and 54 which extend over the reed valve 46 in such a way that the reed valve, when moved in an upward direction as seen in FIG. 8, can engage the surfaces 53 and 54. Moreover, it will be appreciated that the keeper bars are separate from the head, valve plate or restrictor plate and require no fasteners to retain them in position. It will also be appreciated that the floor of the recess 45 at its ends can be relieved to provide a free flex area for the ends of the reed therein.
It will further be appreciated that the respective recesses 47 and 48 have a predetermined depth which is slightly less than the thickness of the hardened keeper bars 49 and 50. In this regard and as shown in FIG. 8, the keeper bars 49 and 50 extend slightly above the exhaust side 55 of the valve plate 56. In addition, it will be further appreciated that the lower surfaces 53 and 54 of the respective keeper bars 49 and 50 do not normally engage the free-floating reed valve 46 when the reed valve is in a position to cover the exhaust port 42, as shown in FIG. 8. Accordingly, there is a gap between the lower surfaces 53 and 54 of the respective keeper bars 49 and 50 and the reed valve 46 when the reed valve is in its closed position.
When exhaust air is urged upwardly through the exhaust port 42, the reed valve is lifted off that port. End portions 56 and 57 of the reed valve engage the keeper bars 49 and 50 and the radiused edges 51 and 52. Further upward motion of the exhaust air urges the reed valve 46 into contact with a reed stop surface 58 disposed on the head 17.
Reed stop surface 58 is traversed by a plurality of grooves 59 for the purpose of permitting exhaust air to move from one side of the reed valve to the other. For example, and returning momentarily to FIG. 2A, it will be appreciated that exhaust air is moved through port 42 to lift the reed valve 46 from the port. Utilization of the grooves 59 permits air on either side of the reed valve to move through the grooves and out the exhaust side to the exhaust port 32 (FIG. 2). It has been found that grooves 59 prevent torsional twisting or deformation which may otherwise be generated in the flexible reed 46 if there were no air passages over the reed.
Furthermore, it will be appreciated that the surfaces 58 are concave with respect to the head. If the reed is moved off the port 42, it tends to rest in a curved configuration, with the end portions 56 and 57 engaging the smooth radiused corners 51 and 52 of the respective keeper bars 49 and 50.
An elongated, round, silicone seal 60 is formed in a circle and is disposed in a circular seal recess or groove 61 in the head 17. The seal 60 engages peripheral surfaces of the valve plate 26 to seal the head 17 to the valve plate. Likewise, an elongated, round, silicone seal 62 is provided in a straight groove 63 to separate an intake chamber 64 in the head from an exhaust chamber 65 in the head.
Moreover, it will be further appreciated that the thickness of the keeper bars 49 and 50 prevent the head from fully engaging the valve plate 26. More particularly, the head includes keeper bar engaging surfaces 66 and 67, respectively. These keeper bar engaging surfaces are in the same general plane as the remaining peripheral surface areas of the head which would otherwise normally contact and mate with the valve plate 26. Accordingly, when the head is tightened down onto the cylinder and over the valve plate, it will be appreciated that the seals 61 and 62 are operative to form a seal against the valve plate surface prior to the time at which the head actually contacts the valve plate. Thus, the head is seated or bottomed out on the keeper bars 49 and 50. Use of a convention "sheet" type gasket is not believed suitable since such gasket may not compress sufficiently to provide an adequate seal when the head bottoms out on the thick keeper bars.
The valve plate 26 also includes an intake or compression side 70. A fourth recess 71 is disposed in the compression side 70 of the valve plate 26 for receiving therein a free-floating, flexible reed intake valve 72 therein. Similarly to the keeper bar recesses 47 and 48, relieved areas are disposed in the valve plate adjacent the fourth free-floating valve recess. These areas define keeper bar channels or recesses 73 and 74, having hardened radiused keeper bars 75 and 76 disposed therein and transversely over the free-floating flexible reed 72. The thickness of the keeper bars 75 and 76 is slightly greater than the depth of the relieved portions or recesses 73 and 74 in the valve plate such that the keeper bars 75 and 76 extend slightly above the floor 77 of a seventh recess, referred to as a restrictor plate recess 78. A restrictor plate 79 is disposed in the recess 78 and rests on keeper bars 75 and 76, slightly above the floor 77 of the recess 78.
When compression is present on the compression side 70 of the plate 26, the flexible reed valve 72 is urged against the intake ports 40 and 41 to close those ports. This position of the reed 72 is shown in both FIGS. 6 and 7. In this position, it will be noted that there is a gap between the surfaces of the keeper bars 75 and 76 and the flexible reed 72. When the piston 19 begins to retract away from the valve plate 26, the reed 72 is opened away from the ports 40 and 41 such that the reed engages the keeper bars 75 and 76 and can further flex away from the ports 40 and 41 into engagement with the restrictor plate 79. The keeper bars 75 and 76, similarly to the keeper bars 49 and 50, have interior rounded corners for engaging the flexible reed valve to prevent undue wear at the end portions of the reed.
Valve plate 26 is provided with a peripheral groove 80 receiving an elongated, round, silicone seal 81 for engaging upper surfaces 82 and 83 of the cylinder 13 (see FIG. 2A). It will also be appreciated from FIG. 2A and from FIG. 6 that since the restrictor plate is bottomed out on the keeper bars 75 and 76, the thickness of the restrictor plate causes it to project slightly outwardly of the compression side 70 of the plate 26. At least portions of the outer periphery of the restrictor plate 79 extend outwardly of the cylinder bore 84 of the cylinder 13 (FIGS. 2 and 11). This relationship is perhaps best seen in FIG. 11. Accordingly, it will be appreciated that as the valve plate 26 is assembled to the cylinder 13, the restrictor plate 79 has peripheral portions which lie on the surfaces 82 and 83 of the cylinder 13, at least at the corners of the restrictor plate, for example. Accordingly, due to the previously mentioned relationship between the thickness of the keeper bars and the thickness of the restrictor plate, the valve plate is supported over the cylinder 13 by means of engagement of the restrictor plate on the surfaces 82 and 83 of the cylinder 13. The outer edges of the valve plate 26, as shown in FIG. 2A, do not necessarily engage the surfaces of the upstanding cylinder 13. The seal 81 is, however, sufficient to provide effective sealing between the valve plate and the cylinder 13, even though the valve plate may be slightly spaced away from the cylinder 13 by the engagement of the restrictor plate therebetween.
The restrictor plate 79 is provided preferably with four intake ports 86-89 and two exhaust ports 90 and 91. As best seen in FIGS. 2A and 11A, the intake ports 86, 87 and 88, 89 are disposed respectively on opposite sides of the intake valve receiving recess 71. Accordingly, when the reed 79 lifts off the intake ports 40, 41 of the valve plate 26, intake air can be drawn from the intake chamber 64 and the head 17 on either side of the reed 72 through the ports 86, 87 on one side of the reed and the ports 88, 89 on the other side of the reed. This prevents torsional twisting of the flexible reed and extends its useful life.
On the compression stroke of the piston 19, compressed air is forced outwardly through the exhaust ports 90, 91 in the restrictor plate through the exhaust port 42 in the valve plate 26 and past the free-floating exhaust reed 46 into the exhaust chamber 65 of the head 17. Thereafter, that compressed air is exhausted through the port 32 and into the intercooler 16.
Turning now to FIGS. 12, 13 and 13A, the valve plate 27 is associated with the second-stage cylinder 14 to control the valving of compressed air through the second stage. In this connection, compressed air from the expansible chamber 24 of the first stage has been moved through the intercooler 16, where the air is cooled, into an intake port 33 and into the intake chamber 95 of the head 18. From there, the compressed air moves into the expansible chamber 25 and is compressed into the exhaust chamber 96 of the head 18. The finally compressed air is exhausted from chamber 96 through the port 34 and the conduit for fitting 35.
The valve plate 27 and its free-floating intake and exhaust reed valves are constructed similarly to the valve plate 26 and its associated reed valves, with only two significant exceptions. The valve plate 27 is slightly smaller than the valve plate 26, and the restrictor plate 105, associated with the valve plate 27, has ports of different configuration than those shown with respect to the restrictor plate 79. For this reason, the detail of the relationship between the various free-floating reeds, the respective keeper bars, and the restrictor plate of the valve plate 27 are essentially the same as those shown for the valve plate 26 in FIGS. 2A and 6-10, and will not be repeated in similar additional figures.
The elements of valve plate 27 are primarily shown in FIGS. 12-13A. Valve plate 27 includes an exhaust side 99 facing the intake and exhaust chambers 95 and 96 of the head 18. An intake or compression side of the plate 27 faces the expansible chamber 25 defined in part by the cylinder 14 of the second compressor stage. The valve plate 27 includes an intake port 100, communicating with intake chamber 95 and a free-floating valve 101 constituting a flexible intake reed valve. The reed is movably captured between respective keeper bars 102 and 103, and is held at its ends in relieved areas extending from a recess cut into the compression side of the valve plate 27 for receiving the intake valve 101. The keeper bars 102 and 103 are slightly thicker than their receiving recesses and extend above the floor of a recess 104 for receiving a restrictor plate 105 (FIGS. 13 and 13A). The restrictor plate bottoms out on the keeper bars 102 and 103 and is of such a thickness as to extend slightly below the compression or intake side of the valve plate 27. In this regard, when the valve plate 27 is mounted on the cylinder 14, the restrictor plate engages upper surfaces of the cylinder 14 to hold the valve plate spaced slightly away from the cylinder. Nevertheless, peripheral seals similar to those as described with respect to valve plate 26 serve to seal the valve plate against the top of the cylinder, and chambers 95 and 96 from each other.
The valve plate 27 also includes a recess 106 for receiving a free-floating exhaust valve 107. Keeper bars 108 and 109 are disposed in relieved areas on either side of the recess 106, forming a discontinuous recess for each keeper bar. The thickness of the keeper bars is slightly greater than the recesses so that upper surfaces of the keeper bars extend above the exhaust side 99 of the valve plate 27. Moreover, there is a gap between the lower surfaces of the keeper bars 108 and 109. Reed 107 can float between the bottom of its recess and the bottom surfaces of its respective keeper bars, similarly to the same construction of plate 26, and similarly to the free-floating action of the reed intake valve 101 in its recess. An exhaust port 110 is provided in valve plate 27 through which finally compressed air is exhausted against the reed 107.
The restrictor plate 105 is perhaps best seen in FIG. 13A where it can be seen that the restrictor plate has two intake ports 112, 113, and three exhaust ports 114, 115 and 116. Accordingly, when the intake reed is drawn inwardly by the descending piston 20, air is pulled around the reed on both sides thereof through the respective ports 112 and 113. This prevents torsional twisting and undue wear and fatigue on the reed material.
The head 18 is provided with a reed valve stop surface 111 (FIG. 2) for engaging and holding the exhaust reed 107 as it is moved upwardly when compressed air is exhausted. The reed valve stop surface in head 18 is grooved, similarly to the stop surface in the head 17 for the first stage cylinder, in order to transmit air over the reed and prevent its deformation from air movement at the opposite reed edges from ports 114, 115 on one hand and port 116 on the other.
It will be appreciated that the restrictor plate 105 has peripheral edge surfaces which seat on the upper surfaces of the cylinder 14, thereby securing the keeper bars 102 and 103 in their proper position to maintain the intake valve in its proper condition. The head 18 also has keeper bar engaging surfaces for engaging the keeper bars 108 and 109 for freely capturing the exhaust valve reed 107 when the head, valve plate and cylinder are assembled.
Similarly to the first stage, the head 18, valve plate 27 and cylinder 14 do not contact each other, but rather are slightly spaced with the respective seals between the head and the valve plate on the one hand, and the valve plate and the cylinder on the other, forming effective seals. Accordingly, the head is bottomed out on the keeper bars in the valve plate, and if not tilted or slightly deformed is slightly spaced from the valve plate, while the valve plate is bottomed out by virtue of the relationship between the restrictor plate 105 and the keeper bars 102 and 103, the restrictor plate resting on the upper surfaces of the cylinder 14.
The particular construction of the valve plates and valves as described provide valving which has a number of advantages. First, the valves are capable of operation at high compressor speeds such as, for example, 1725 cpm. The keeper bars are hardened and are radiused so there is no defined flex line across the reeds and no undue wear placed on the free-floating reeds. The ends of the reed valves are not prone to cutting wear grooves in any surface, such as may lock the reed valve in an open or inoperable condition.
Returning now to FIGS. 2 and 3, it will be further appreciated that the compressor is provided with an improved crankshaft for accomplishing several benefits. First, it will be noted in FIG. 3 that the crankshaft has a hollowed out or cored area 120. This hollowed out or cored area is open to the crankcase through large portals or openings such as shown at 121 and 122. Accordingly, oil in the crankcase 12 easily works its way into the cored center of the crankshaft 21. The crankshaft 21 is provided with an integral balance counterweight 123 thereon disposed at a driven end of the crankshaft. The driven end 124 of the crankshaft is provided with a bore 125 which is internally threaded at 126. The other driving end 127 of the crankshaft is not provided with any integral counterweight and thus the crankshaft 21 has an end 127 which is easily slipped through one-piece connecting rods 22 and 23, as shown in FIG. 3, for assembly. It is unnecessary to provide a composite connecting rod which may require other fasteners and could be subject to inadvertent separation during a compressor operation.
A motor 11 is connected by appropriate fastener means, such as bolts 129, to the crankcase 12. Motor 11 is provided with a rotatable drive shaft 130 having threads 131 on the end thereof for mating with the threads 126 in the driven end 124 of the crankshaft 21. A bearing 132 is disposed at the end 124 of the crankshaft outwardly of the counterweight 123. A second bearing 133 is disposed in the crankcase for mounting the other end of crankshaft 121 outwardly of the piston bearing surface which supports the connecting rods 22 and 23, and on the other side thereof from the counterweight 123.
It will be appreciated that the bore 125 in the crankshaft 21 extends completely through the driven end 124 of the crankshaft and into the cored or hollowed-out area 120. Accordingly, the threaded area 126 of the bore is open to internal area of the crankshaft and is in communication with any oil present therein. During operation, this oil tends to work its way into the threaded area and prevents fretting or corrosion between the material of the crankshaft 21 and threads 126, and the drive shaft 130 and its threads 131. Accordingly, the drive shaft 130 can be easily unthreaded from the crankshaft 21 for maintenance or for replacement of other parts. Moreover, it will be appreciated that the crankshaft 21 is also provided with lubricating ports 134 for the purpose of lubricating the outer crankshaft surfaces in the area of its connection to the one-piece connecting rods 22 and 23, thereby further promoting lubrication of the unit.
In order to provide for a sufficient dynamic balancing of the crankshaft 21, there is provided on the other end 127 a removable balance counterweight 135 (FIG. 3). This counterweight is of sufficient shape and angular disposition with respect to the crankshaft 21 as to provide for a sufficient dynamic balancing as the compressor is operated.
Moreover, it will be appreciated that the compressor 10 also includes a cooling fan 140 of the squirrel-cage type. This fan is secured to the crankshaft 21 at end 127 by means of an appropriate fastener 141 for rotation about a drive axis 142. In order to drive the fan, a drive pin 143 is extended from the counterweight 135 toward the fan 140 so as to engage a rear surface 144 of the fan in a driving relationship radially spaced from the drive axis 142.
Accordingly, the crankshaft 21 includes a cored area in conjunction with an integral counterweight and a drive shaft receiving bore whereby that bore is lubricated to prevent fretting and corrosion. The crankshaft is also adapted for utilization with one-piece piston connecting rods and is provided with a removable counterweight balance on an opposite end from the drive thereof, which counterweight is provided with drive means for driving the compressor cooling fan.
In conjunction with the fan, the compressor 10 is provided with a shroud 15 for the purpose of efficiently directing air from the fan over both the cylinders' respective heads and the intercooler between the compressor stages defined by the cylinders. This shroud is perhaps best seen in FIGS. 1-4 and reference with respect to the shroud will be primarily had with respect to FIGS. 3 and 4. FIG. 4 shows the shroud 15 with a back plate 150 thereof being partially broken away to show the internal area of the shroud adjacent the fan.
The shroud includes a scroll vane 151 for the purpose of receiving air, drawn through the center of the fan and expelled at the fan periphery, and for directing that air up into a cooling air chamber defined by the shroud body and the back plate 150. The shroud comprises two projections 152 and 153 disposed in a V-shaped configuration in register with the V-shaped configuration of the cylinders 13 and 14 as shown in FIG. 2. The backing plate 150 is also provided with projections 154 and 155 corresponding to the projections 152 and 153 of the shroud. Cooling air exhaust ports 156 and 157 are disposed in the backing plate as best shown in FIG. 4. As shown by the arrows in FIG. 4, air is generated by the fan in a clockwise direction and up into the shroud chamber between the shroud body and the backplate 150. From there, the air is exhausted to the ports 156 and 157 toward the respective cylinders immediately therebehind.
In order to further cool the cylinders, deflectors 158 and 159 are provided on the backplate adjacent the respective ports 156 and 157. These direct air from the ports over the respective cylinders and heads. In addition, a third cool air exhaust port 160 is provided in the back plate 150 in general register with intercooler 16, extending between the two cylinders of the compressor. Upon operation of the fan, cooling air is thus also blown from the shroud and fan over the intercooler 16, thereby further cooling air which has been compressed and is moving for introduction into the second stage.
Turning now to FIGS. 2 and 5, it will be appreciated that the invention in another aspect includes an improved intake manifold 31. Intake manifold 31 is defined by a shroud 165 and a backing plate 166 defining an intake manifold chamber having an overall volume of about 50.08 cubic inches. Backing plate 166 is provided with two sets of ribs 167 and 168. The ribs in each of the sets have inwardly facing edges 169 and 170 defining therebetween a slot 171 for receiving a foam type or other suitable air filter 172. Walls 173 and 174 extend from the backing plate along the upper opposite edges of the respective sets of ribs to forward wall edges 175 and 176, respectively. The forward edges 175 and 176 of the walls 173 and 174 define between them, and the shroud 165, an air passageway 177 for the purpose of passing air from a first chamber 178 through the filter 172 to a second chamber 179 where the air can be exhausted from the manifold 31 through an exhaust port 180 into the intake chamber 64 of the head 17 (see FIG. 2A). Chambers 178 and 179 comprise portions of the overall intake manifold chamber noted above, together with a center chamber defined between the walls 173, 174. Chamber 178 has a volume of about 12.97 cubic inches. Chamber 179 has a volume of about 14.55 cubic inches. The remaining chamber between the walls 173, 174 has a volume of about 22.56 cubic inches.
Returning now to FIGS. 2 and 5, it will be appreciated that the shroud 165 is provided with a plurality of intake tubes 181 having air intake passageways 182 therethrough. Passageways 182 are about 0.312" in diameter, providing a cross-sectional flow are of about 0.0765 square inches. The tubes are about 2.188" long terminating at 183 within the first chamber 178.
Air inleted from the tubes expands into the first chamber 178 and then moves toward the air passageway 177, the filter 172 and chamber 179. The shroud is held onto the backing plate by means of elongated fastener 184, and the entire unit is secured to the head 17 by means of the fasteners 185.
The relationship of the various elements of the intake manifold to the elements of the specific preferred compressor described herein is such that the noise generated by the compressor is substantially muffled by the intake manifold. Of course, the intake manifold also serves to filter air by means of the air filter 172 which extends entirely across the manifold from the backing plate 166 to the shroud 165, as shown in FIG. 2.
It will also be appreciated that other similar manifolds of varying sizes can be used with compressors of other characteristics to provide both filtering and efficient sound muffling.
Accordingly, the invention provides, in a number of varied aspects, an improved compressor capable of operating at relatively high speed cycles of about 1725 cpm without undue valve wear and without losing efficiency due to valve operation. The capability of running the compressor at 1725 rpm, provided by the improved valve structure herein, also means that the compressor is run at the same design rpm of the drive motor 11, thereby eliminating any need for bulky and heavy speed reduction devices such as belt-driven pulleys. This further facilitates a more compact and lightweight compressor. At the same time, the invention provides an improved crankshaft which serves to prevent fretting and corrosion between the direct drive coupling of the drive motor to the crankshaft, and at the same time is suitable for use with one-piece piston connecting rods while providing means, in the form of a removable counterweight, for dynamic balancing of the crankshaft. The removable counterweight is also utilized in order to drive the compressor cooling fan and a shroud and backing plate serve to direct cooling air over each stage of the compressor as well as the intercooler therebetween. An improved intake manifold provides for both sound muffling and air filtering for air as it enters the first stage of the compressor.
It should be appreciated that the keeper bars and free-floating reed can be disposed within the head, the valve plate or the restrictor plate while still obtaining the advantage of the free-floating reed and of the separate keeper bars to provide an easily hardened and smooth surface for engagement of the opening reed.
It should also be appreciated that the invention with respect to the free-floating valve structure can be modified to provide an advantage in a fixed-end reed valve construction. In the past, the non-fixed end of a fixed reed valve was susceptible to impact or wear damage. The velocity of the reed flexure of such past valves led to fatigue and premature failure. According to the invention, the free end of a single fixed-end reed valve could be freely captured between its closed port position and an overlying keeper bar spaced therefrom (as described herein). As such a modified valve opens, its free end engages the keeper bar and slightly slides under it as the entire reed bows outwardly into a curved valve open configuration. This would eliminate the wear and impact damage caused by the free, but uncaptured, end of a fixed-end reed and would also reduce velocity and the fatiguing flexure of the reed both at its fixed end and throughout the whole reed, thereby prolonging its life. Such a construction is shown diagrammatically in FIG. 14.
These and other embodiments and alterations thereof will be readily appreciated by those of ordinary skill in the art without departing from the scope of this invention, and applicant intends to be bound only by the claims appended hereto.
|Cited Patent
|Filing date
|Publication date
|Dec 31, 1921
|Mar 3, 1925
|Worthington Pump & Mach Corp
|Automatic plate valve
|Mar 31, 1925
|Nov 9, 1926
|Mar 31, 1930
|Mar 31, 1931
|Joseph Klimek
|Feather valve for gas compressors
|Sep 27, 1929
|Sep 11, 1934
|Maytag Co
|Gasoline engine starter
|Aug 8, 1936
|Nov 8, 1938
|Kellogg Compressor And Mfg Cor
|Refrigerating apparatus
|Jun 17, 1939
|May 27, 1941
|Westinghouse Electric & Mfg Co
|Fluid translating apparatus
|Dec 20, 1940
|Sep 1, 1942
|Paul S Mantonya
|Refrigerating apparatus
|Feb 26, 1947
|Aug 7, 1951
|Specialties Dev Corp
|Dec 3, 1954
|Aug 11, 1959
|Oct 6, 1960
|May 16, 1961
|Worthington Corp
|Valve service for compressors
|Nov 2, 1960
|Feb 6, 1962
|James R Head
|Dispenser for disinfectant and the like
|Jan 7, 1957
|Jul 24, 1962
|Atlas Copco Ab
|Welded sheet metal casings
|Oct 10, 1966
|Sep 10, 1968
|Danfos As
|Piston-type compressor particularly for small refrigerating units
|Dec 19, 1986
|Jan 31, 1989
|Wankel Gmbh
|Cooling system for a rotary piston internal combustion engine
|May 24, 1988
|May 16, 1989
|Wankel Gmbh
|Lubrication system for a rotary-piston internal combustion engine
|Jun 21, 1988
|May 30, 1989
|Diesel Kiki Co., Ltd.
|Sliding-vane rotary compressor for bearing lubrication
|Citing Patent
|Filing date
|Publication date
|Apr 2, 1992
|Sep 6, 1994
|Devilbiss Air Power Company
|Eccentric crank assembly for a reciprocating piston air compressor
|Feb 23, 1996
|Jun 30, 1998
|Millipore Investment Holdings Limited
|Fluid dispensing system having independently operated pumps
|May 8, 1997
|May 9, 2000
|Reliance Electric Industrial Company
|Speed reducer apparatus having auxiliary seal assembly
|Aug 8, 1997
|Aug 1, 2000
|Black & Decker Inc.
|Compressor mechanism for a portable battery operated inflator
|Feb 16, 1999
|Oct 24, 2000
|Tecumseh Products Company
|Detachably affixed counterweight and method of assembly
|Feb 20, 2002
|Dec 23, 2003
|Hans-Georg G. Pressel
|Compressor apparatus
|Jan 6, 2010
|Apr 30, 2013
|Hitachi Industrial Equipment Systems Co., Ltd.
|Reciprocative compressor
|Jan 6, 2010
|Dec 2, 2010
|Hitachi Industrial Equipment Systems Co., Ltd.
|Reciprocative Compressor
|Dec 15, 2015
|Mar 16, 2016
|Direct connection type oilless air compressor
|Aug 16, 2002
|Nov 17, 2004
|Continental Aktiengesellschaft
|Air supply unit for a vehicle
|May 7, 2015
|Nov 12, 2015
|Westinghouse Air Brake Technologies Corporation
|Compressor cooled by a temperature controlled fan
|Aug 27, 2015
|Mar 24, 2016
|Knorr-Bremse Systeme f�r Schienenfahrzeuge GmbH
|Multi-stage piston compressor having an outer cooling air conduction system
|U.S. Classification
|417/265, 74/603, 416/19, 416/144, 417/271
|International Classification
|Cooperative Classification
|European Classification
|Sep 27, 1993
|Fee payment
Year of fee payment: 4
|Feb 13, 1998
|Maintenance fee reminder mailed
|Apr 12, 1998
|Lapse for failure to pay maintenance fees
|Jun 23, 1998
|Expired due to failure to pay maintenance fee
Effective date: 19980415


text:
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text:
We will continue with the playback of the Announcer/Spokesperson assignment.
You homework for Wednesday is an Extra Credit assignment. Please refer to page 19 of your workbook for the assignment. This is worth 1 point. Some of you already need the extra credit. All of you need the practice.
Extra Credit Assignment: Practice Your Delivery
"Think about the most important things you look for in a place to call home."
Start your recorder and read the sentence above three times in a row. Each time you say the sentence, bring out more meaning. Don't stop and think about it between each read. Let your brain work its magic. This is an important skill to have in the voiceover business because you will frequently be asked to do ABC reads or "groups of 3." You need to be able to provide the producer with options within the tone and general pace you have established.
As you play back what you have just recorded, listen carefully to see what kind of team you and your brain made. Here are some things you might be hearing.
- You may not hear much difference at all. Is that the case for you? If so, try the exercise again. This time see right through the words deep into the meaning of the words. Did you hear a difference in the delivery?
- You may hear that certain words are said a bit more strongly than others. What words popped out at you? This may vary with each of the three reads – and probably should!
- If a different word is stressed each time, does the stress sound natural or forced?
- Did the pacing of the words vary? By that I mean, did you insert pauses in the delivery, or did you stretch out certain words?
- Do you like the delivery of one of the reads more than the others? If so, can you figure out why it sounds better?
- Did the meaning or intent of the words become clearer as you moved from the first read to the third?