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Excellent and friendly host, great apartment, very well equipped, at superb location, great experience overall
Teddy was very welcoming and greeted us very early as our flight arrived very early, this was much appreciated. The unit is as pictured and is very clean. It is in a perfect location, so close to everything. There is a list which is great for luggage and I would recommend Teddy as a host to anyone wanting a clean, convenient and centrally located apartment in Munich
The apartment was exactly as expected, and exactly what we needed. Being so close to Marinplatz, was well as the Viktualienmarkt, was great. Teddy is a great host and is dry knowledgable and responsive. He contacted us early, and gave us great directions on how to get to the apartment.
We stayed here for 3 nights in November and have not traveled to Germany before. We were greeted by Teddy upon our arrival and he was immediately friendly and helpful. The unit is very close to all of the main sights which you can walk to easily. There are taxis directly out the front of the unit block and the short taxi ride to the Hauptbahnhof will cost you about 10€. The beds are comfortable and the unit has everything you could need. I would definitely recommend staying here!
The reservation was canceled 69 days before arrival. This is an automated posting.
The apartment was exactly as described and very clean. An added bonus was the use of the giant i-mac, very helpful for finding your way around Munich. Although Teddy was not there in person his colleague Klaus was there and waiting and Teddy called me for a personal welcome. The location of the apartment is fantastic, couldn't be more central, and right in the heart of everything.
Would give this a 10/10 rating!
Appartement wie beschrieben; ausgezeichnete Lage im Zentrum; sehr, sehr sauber; freundlicher Empfang durch Teddy Lakis und seine Helfer; gerne wieder einmal - auch länger!
We were not able to meet Teddy personally due to timing conflict but he called us up a few times to address our questions and make sure we were comfortable. The lift was not available during our stay (Teddy had already informed us) however, he had a nice young man help us with our luggage. The apartment is the "BEST" in the area! Marienplatz, Viktualienmrkt, taxis, trams, city tour buses, HbF were all within steps! We would definitely stay here again!
Everything was as expected. Teddy took great care to communicate with us. We would consider staying there again. Great location! The elevator was out, but Teddy warned us in advance and made concessions. He was very reasonable. Overall, the apartment was very clean.
Teddy's apartment is great. A big apartment with two very comfortable beds, a large couch and other great features like a big TV, desktop computer, great internet and a printer. The apartment's balcony was great to have a coffee in the morning. For us it was the perfect apartment to visit Oktoberfest.
The location is just a few steps away from a very good food market, Haufbrauhaus, Augustiner, Paulaner restaurant and other very good restaurants and pubs. It was also very easy to take the subway, tran and S-bahn to Oktoberfest, Dachau and other sightseens. There is a beautiful square near Teddy's apartment called Marienplatz. A must for all visitors. As soon as you arrive, Teddy and Klaus will be waiting for you, so don't worry. The location is also very safe.
One of my long term friends. Nearly since 30 Years.
I trust him allways never fail !
Teddy ist einer meiner Freunde die ich seit fast 30 Jahren kenne und vertraue.
Ein sehr netter Mensch den ich seit einigen Jahren kennen darf. 100% vertrauenswürdig und weiterzuempfehlen. Ein toller AIRbnb'ler


text:
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subset: commoncrawl


text:
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Matthew J. Kleiman, Jenifer K. Lamie, and Maria-Vittoria "Giugi" Carminati are the coauthors of The Laws of Spaceflight: A Guidebook for New Space Lawyers, which will be published by the ABA this summer.
Adapted from The Laws of Spaceflight: A Guidebook For New Space Lawyers
From Earth, outer space seems like an endless expanse. It can be hard to believe that we need to worry about contaminating the outer space environment. Many people once held similar views about the oceans, yet we now know that human activity can have a very detrimental impact on the marine environment. The same is true for outer space. While outer space is vast, the usable regions of outer space are relatively small. Certain regions are already becoming overcrowded. Space operations can also have a detrimental impact on terrestrial environments, both on Earth and on other planetary bodies.
This excerpt discusses the environmental impact of human activities in outer space and the laws, regulations, and standards that attempt to mitigate environmental harm. Specifically, it focuses on the problem of orbital space debris.
Earth orbit is crowded. The US government currently tracks about 22,000 manmade objects in Earth orbit. However, it is estimated that more than 500,000 man-made objects larger than a centimeter, and millions of objects smaller than a centimeter, are currently circling Earth.1 Of these objects, only about 1,000 are operational spacecraft. The rest are dead satellites, discarded equipment, spent rocket boosters, fragments from collisions and explosions, paint chips, and other by-products of human space activities, collectively known as space debris. Space debris in low orbits will eventually succumb to atmospheric drag and reenter Earth's atmosphere. Most will burn up, but some fragments will survive reentry and strike the ground. Debris in higher orbits will remain in space for hundreds or thousands of years, or even forever.
Space debris was first recognized as a serious problem in the late 1970s and early 1980s.2 However, several events in recent years have significantly increased the amount of debris in orbit. In 2007, the Chinese government used a dead Chinese weather satellite, Fengyun-1C, as a target for the test of an antisatellite missile system. As of 2011, 3,135 pieces of debris from the Fengyun-1C satellite have been catalogued in LEO, and NASA's Orbital Debris Program Office estimates that more than 150,000 pieces of debris larger than one centimeter in diameter were generated by this impact.3 In 2009, a satellite operated by Iridium Communications, Inc., was destroyed in a collision with a defunct Russian military satellite, the first major collision between an operational satellite and space debris. The Iridium collision generated about 1,000 pieces of debris larger than 10 centimeters, and many more smaller pieces.4 Experts fear that if the amount of debris in orbit reaches a critical mass, a few major debris-creating episodes (whether intentional or accidental) could set off a sequence of ever more frequent collisions—a kind of chain reaction that would expand until, within decades, certain regions of Earth orbit would be rendered virtually unusable. This "collisional cascading" is known as the Kessler Syndrome, named after NASA scientist Donald Kessler, who first proposed this possibility in 1978.5 Some studies indicate that Earth orbit is already unstable at certain altitudes, in the sense that absent debris mitigation efforts, a collisional cascade could already be inevitable.6
Efforts to address the space debris problem fall into three categories: (1) debris tracking, (2) growth mitigation, and (3) removal.
In order for operational spacecraft to avoid space debris, their operators must have comprehensive knowledge of the population of space objects, particularly of any objects that might cross their orbital paths. Knowledge of the space environment is referred to as space situational awareness (SSA). SSA is obtained through space surveillance, which is the detection, correlation, characterization, and orbit determination of space objects. The US Department of Defense's Space Surveillance Network (SSN) maintains the "world's most capable space surveillance network, consisting of ground-based radars, optical telescopes, and satellites."7 The SSN is capable of tracking objects as small as five centimeters in diameter in low Earth orbit and about one meter in diameter in geosynchronous orbit.8 The United States makes much of this data publicly available through the SSA Sharing Program, which is administered by the US Strategic Command and is available at http://www.space-track.org.
In addition to the SSA Sharing Program, several non-US government organizations also provide SSA tracking data. The European Space Agency is developing its own SAA capability under the European SSA Preparatory Programme.9 In 2009, the three largest commercial satellite companies, Intelsat, Inmarsat, and SES, formed the non-profit Space Data Association (http://www.space-data.org/sda) to share SSA data. The Center for Space Standards and Innovation (CSSI) also provides SSA services. CSSI operates the satellite tracking website, CelesTrak (http://celestrak.com), which redistributes two-line element sets and information from the space-track.org website, supplemented with its own data and analysis. CSSI also offers a service called Satellite Orbital Conjunction Reports Assessing Threatening Encounters in Space (SOCRATES) (http://celestrak.com/SOCRATES). SOCRATES provides information on pending orbital conjunctions during the coming week. Finally, the International Scientific Optical Network (ISON) (http://www.isonteam.com) describes itself as a "scientific project" initiated by the Keldysh Institute of Applied Mathematics of the Russian Academy of Sciences in 2001. ISON receives its data from 25 optical telescopes located at 18 observation facilities.10
Debris mitigation efforts first began in the early 1980s. One early solution implemented by McDonnell Douglas, for example, was to modify its Delta booster so that it did not explode in orbit after completing its mission.11 In 1995, NASA became the first space agency to issue comprehensive orbital debris mitigation guidelines.12 Two years later, an interagency working group led by NASA and the Department of Defense developed Orbital Debris Mitigation Standard Practices for all US government satellites and launch vehicles. Other countries and organizations, including Japan, France, Russia, and the European Space Agency (ESA), have followed suit with their own orbital debris mitigation guidelines.
In 2002, the Inter-Agency Space Debris Coordination Committee (IADC), which is comprised of the space agencies of 11 countries and ESA, adopted a set of guidelines designed to mitigate the growth of the orbital debris population. In 2007, after a multiyear effort, the United Nations' Committee on the Peaceful Uses of Outer Space (COPUOS) developed and adopted a consensus set of space debris mitigation guidelines similar to the IADC guidelines, which were subsequently endorsed by the full U.N. General Assembly.13 The COPUOS guidelines include seven recommendations:
In addition to the COPUOS and national orbital debris mitigation guidelines, there have been several efforts to develop more comprehensive "rules of the road" for outer space operations. In December 2008, the European Union proposed a draft Code of Conduct for Outer Space Activities, which would require, among other things, that participating States "refrain from intentional destruction of any on-orbit space object or other harmful activities which may generate long-lived space debris," and "adopt, in accordance with their national legislative process, the appropriate policies and procedures in order to implement" the COPUOS debris mitigation guidelines.15 Although initially responding favorably to this effort, the United States announced in January 2012 that it would not support the European Code of Conduct because the US government found it to be "too restrictive."16 Instead, US Secretary of State Hillary Rodham Clinton announced that the United States would "join with the European Union and other nations to develop an International Code of Conduct for Outer Space Activities" that "will help maintain the long-term sustainability, safety, stability, and security of space by establishing guidelines for the responsible use of space" and "reverse the troubling trends that are damaging our space environment."17
There are generally two forms of debris removal: self-removal and external removal. Self-removal is where, at the end of its useful life, a spacecraft either removes itself from orbit by entering into a decaying orbit that will reenter the atmosphere in a reasonable timeframe (the U.S. Standard Practices require that this be done within 25 years of the end of the satellite's mission), or moves itself into a graveyard orbit out of the way of other spacecraft. Technologies are currently being developed as alternatives to using valuable propellant to deorbit spacecraft, such as electrodynamic tethers and sail-like attachments that would be installed on a spacecraft prior to launch and, when deployed at the end of the spacecraft's useful life, would create drag that would eventually deorbit the spacecraft.18
Spacecraft in high-Earth orbits cannot realistically carry enough extra propellant to move into atmosphere dispersal orbits at the end of their missions. The International Telecommunications Union therefore requires that States ensure that geostationary satellites are transferred to a "supersynchronous graveyard orbit" that does not intersect with the geosynchronous orbit (GSO) at the end of their useful life.19 In the United States, this requirement has been implemented in Section 25.283(a) of the Federal Communication Commission's rules for satellite operations, which provides that "a space station authorized to operate in the geostationary satellite orbit under this part shall be relocated, at the end of its useful life, barring catastrophic failure of satellite components, to an orbit with a perigee with an altitude of no less than: 36,021 km [22,382 miles]."20 Unfortunately, spacecraft operators do not always comply with this requirement. In 2009, for example, only 11 of 21 satellites in GSO that reached their end of life were disposed of in proper graveyard orbits.21
While self-removal is the preferred mechanism for removing debris from orbit, this is not possible for the thousands of pieces of debris currently in orbit without any built-in means of self-removal. Proposed mechanisms for external removal of debris from orbit include, for example, building spacecraft to rendezvous with and capture debris and ground-based "laser brooms" to sweep debris from orbit.
There are two problems with currently proposed external removal mechanisms. First, none of the proposed mechanisms are economically feasible with today's technology. Second, since the Outer Space Treaty provides that launching States retain ownership, jurisdiction, and control of their space objects and there is no law of salvage for outer space similar to the law of salvage under maritime law, one State cannot remove another State's nonfunctionary spacecraft from orbit without permission. States would likely be willing to consent to the removal of their debris in most cases, but obtaining consent for each item of debris would be time-consuming and inefficient, the origin of many items of debris cannot be determined with certainty, and States would be less willing to allow another State to interact with debris that may contain national security secrets, such as derelict reconnaissance satellites. Accordingly, many technological solutions to the space debris problem would need to be accompanied by an international legal framework authorizing the removal efforts. u
1. National Aeronautics and Space Administration, Frequently Asked Questions: Orbital Debris, http://www.nasa.gov/news/debris_faq.html.
2. Jim Schefter, The Growing Peril of Space Debris, Popular Science (July 1982).
3. CelesTrak.com, Chinese ASAT Test (updated May 20, 2011), http://celestrak.com/events/asat.asp; National Aeronautics and Space Administration, Fengyun-1C Debris: One Year Later, 12 Orbital Debris Q. News 1, 3 (2008), available at http://www.orbitaldebris.jsc.nasa.gov/newsletter/pdfs/ODQNv12i1.pdf.
4. Veronika Oleksyn, What a Mess! Experts Ponder Space Junk Problem, USA Today, Feb. 19, 2009, available at http://www.usatoday.com/tech/science/space/2009-02-19-space-junk_N.htm; Philip Hattis, The Growing Menace of Orbital Debris, Livebetter eMagazine, Jan. 2012, http://www.centerforabetterlife.com/eng/magazine/article_detail.lasso?id=265.
5. Donald J. Kessler & Burton G. Cour-Palais, Collision Frequency of Artificial Satellites: The Creation of a Debris Belt, 83 J. of Geophysical Res. 2637–46 (1978).
6. Donald J. Kessler et al., The Kessler Syndrome: Implications to Future Space Operations, 33rd Annual AAS Guidance and Control Conference, Paper AAS 10-016 (Feb. 2010), available at http://webpages.charter.net/dkessler/files/Kessler%20 Syndrome-AAS%20Paper.pdf; Donald J. Kessler & Phillip D. Anz-Meador, Critical Number of Spacecraft in Low Earth Orbit: Using Fragmentation Data to Evaluate the Stability of the Orbital Debris Environment, Third European Conference on Space Debris (Mar. 2001), available at http://webpages.charter.net/dkessler/files/CriticalNumberofSpacecraftinLow.pdf.
7. James D. Randleman & Robert E. Ryals, Spacecraft Operator Duty of Care, AIAA Space 2011 Conference & Exposition 3 (2011).
8. National Aeronautics and Space Administration, Space Debris and Human Spacecraft, http://www.nasa.gov/mission_pages/station/news/orbital_debris.html.
9. European Space Agency, Space Situational Awareness, http://www.esa.int/esaMI/SSA.
10. Tiffany Chow, Space Situational Awareness Sharing Program: An SWF Issue Brief, The Secure World Foundation (Sept. 22, 2011), http://swfound.org/media/3584/ssa_sharing_program_issue_brief_nov2011.pdf.
11. Jim Schefter, The Growing Peril of Space Debris, Popular Science (July 1982).
12. NASA Orbital Debris Program Office, Orbital Debris Mitigation, http://orbitaldebris.jsc.nasa.gov/mitigate/mitigation.html.
13. G.A. Res. 62/217, International Cooperation in the Peaceful Uses of Outer Space, U.N. GAOR, 62nd Sess. U.N. Doc. A/RES/62/217, at ¶26 (Dec. 22, 2007).
14. United National Office for Outer Space Affairs, Space Debris Mitigation Guidelines of the Committee on the Peaceful Uses of Outer Space, Official Records of the General Assembly, 62nd Sess., Supp. No. 20 (A/62/20), paras. 117 and 118 and annex., available at http://orbitaldebris.jsc.nasa. gov/library/Space%20Debris%20Mitigation%20Guidelines_COPUOS.pdf.
15. Council of the European Union, Draft Code of Conduct for Outer Space Activities, at art. II, § 5 (2008), available at http://www.eu2008.fr/webdav/site/PFUE/shared/import/1209_CAGRE_ resultats/Code%20of%20Conduct%20for%20outer%20space%20activities_EN.pdf.
16. Marcus Weisberger, U.S. Won't Accept EU Code of Conduct for Space, Space News, Jan. 12, 2012 (quoting U.S. Undersecretary of State for Arms Control and International Security Ellen Tauscher), http://www.spacenews.com/policy/120112-wont-adopt-code-conduct-space.html.
17. Press Release, U.S. Secretary of State Hillary Rodham Clinton, International Code of Conduct for Outer Space Activities (Jan. 17, 2012), http://www.state.gov/secretary/rm/2012/01/180969.htm.
18. See, e.g., Bill Christensen, The Terminator Tether Aims to Clean Up Low Earth Orbit, Space.com, Nov. 17, 2004, http://www.space.com/537-terminator-tether-aims-clean-earth-orbit.html (tethers); Jonathan Amos, How Satellites Could "Sail" Home, BBC News.com, May 3, 2009, http://news.bbc.co.uk/2/hi/science/nature/8029899.stm (sails).
19. Francis Lyall & Paul B. Larsen, Space Law: A Treatise 246 (Ashgate, 2009) (citing International Telecommunications Union Radiocommunication Sector Recommendation S.1003-1 (01/04), "Environmental Protection of the Geostationary Orbit").
20. 47 C.F.R. § 25.283(a).
21. European Space Agency, Classification of Geosynchronous Objects (Feb. 2010), at 126, available at http://lfvn.astronomer.ru/files/COGO-issue12.pdf.


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Two Michigan sites escape drought's worst
By KEVIN WALKER
Michigan Correspondent
CHARLOTTE, Mich. — Two corn seed test sites in the lower midsection of Michigan's Lower Peninsula showed once again the state escaped the worst of last summer's severe and extreme drought that plagued much of the country's heartland.
The tests were conducted by the Farmer's Independent Research of Seed Technologies (F.I.R.S.T.), which is based in Illinois. One test was done at the farm of Jim and Dennis Orr in Eaton County, in Charlotte, located approximately 20 miles southwest of Lansing.
The other was done at the farm of Tony Igl of Ingham County, in Mason, which is about 20 miles southeast of Lansing.
F.I.R.S.T. Site Manager Rich Schleuning said drought and abnormally dry conditions at the test site at Charlotte hurt the corn crop some, but "we were anticipating something worse."
The top-yielding brand at the Charlotte site was NuTech variety 5N-001 with a yield of 152.8 bushels an acre, gross income per acre of $1,086, moisture of 26.7 percent and a plant stand of 26,800.
Taking second place was Channel 197-67VT3P, with a yield of 150.1 bushels, income of $1,065, moisture of 27.2 percent and a stand of 27,500. Coming in third was AgriGold A6252VT3Pro, with a yield of 146.5 bushels, gross income of $1,040, moisture of 27 percent and a stand of 28,800.
In his report Schleuning also noted a timely shower in July followed by more rain in August rejuvenated the grain and resulted in good quality at harvest.
At the Mason site, Schleuning said a late planting date caused by excessive early rains and moisture turned out to be fortunate, given the later abnormally dry conditions. He noted the corn pollination window ended up missing the worst of the summer heat.
At Mason, the top spot was taken by G2 Genetics 5X-0004, with a yield of 165.1 bushels an acre, gross income of $1,179 an acre, moisture of 25.4 percent and a stand of 30,200. Taking second place was Steyer 10604-3000GT, with yield of 163.2 bushels, income of $1,152, moisture of 28.6 percent and a stand of 32,200.
In third place, Great Lakes variety 4727STXRIB yielded 156.6 bushels and a gross income of $1,132 an acre, with moisture of 21.8 percent and a stand of 30,200.
More test results are available online at www.firstseedtests.com
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Bath edge it at the death
ESPN Staff
September 1, 2012
Bath's Olly Barkley goes for the posts
© Getty Images
A late Olly Barkley penalty was enough to give Bath a narrow 24-23 win over Worcester at Sixways on Saturday.
Bath had not led until the 65th minute but even when home lock James Percival responded by crashing over for the only try of the game soon after, it was the accuracy of Barkley that proved decisive. By contrast Andy Goode spurned a couple of kicks late on, including failing to convert Percival's 69th-minute score, which proved crucial when his opposite number landed the winning blow with the final kick of the game.
Worcester had raced out to a 12-0 with Goode initially solid with the boot as he slotted a 40-metre penalty in just the second minute. Minutes later Bath offended in the ruck area and again the outside half was on target, this time from 35 metres.
The Warriors continued to dominate play and when Matt Banahan was penalised for not rolling away at a ruck, Goode converted his third penalty to give his side a 9-0 lead after only 10 minutes. Worse was to follow for Banahan and Bath. The centre was yellow carded for a deliberate knock on and again Goode made no mistake with his penalty kick.
Banahan was soon joined in the sin-bin by rival captains, Stuart Hooper and Dean Schofield, who were yellow carded by young referee, Luke Pearce, after a substantial melee involving most of the forwards. However, the Warriors failed to take advantage of their numerical superiority.
Barkley reduced the arrears with the first of his eight penalties and Banahan then returned with no damage done to his side's chances. Goode should have restored Worcester's 12-point advantage but the outside half fired wide with a 30-metre drop-kick attempt.
Another error from the Warriors saw Josh Drauniniu fail to collect an up-and-under and another penalty was conceded for offside which Barkley kicked from 45 metres. A simple penalty from Goode after 32 minutes made it 15-6 to the Warriors and they should have extended that lead when they blew the best try scoring opportunity of the half. Goode, David Lemi and Josh Matavesi combined brilliantly in a sweeping 70-metre move but Lemi's scoring pass to Goode was ruled forward.
Bath scored the first points of the second half when Barkley was successful with a 45-metre penalty and the lead was soon down to three points with another simple goal from the outside half. A handling error from Lemi and a powerful run from Banahan exerted more pressure on the Warriors defence and they conceded another penalty at the ruck area to allow Barkley to tie up the scores.
Bath were now the dominant side with Banahan becoming increasingly influential with his driving runs in midfield and they looked the more likely winners as the game entered the final quarter. Barkley gave Bath the lead for the first time in the match with a 35-metre penalty after 65 minutes.
Stung by the reverse Worcester immediately brought on three replacements and it soon paid dividends when Percival drove over from close range but Goode's conversion rebounded back of a post which proved costly as Barkley was successful with his longest penalty of the game to give Bath a one-point lead with six minutes remaining.
Back came the Warriors to secure two penalties in the Bath 22, Goode surprisingly missed the first but kept his nerve to kick the second. But with the last kick of the match Barkley made no mistake with his eighth penalty and with it an away victory.
And Bath coach Toby Booth admitted his side were lucky to come away with the win. "We had no ball at all in the first half and Andy Goode's monster right boot kept pegging us back and we couldn't get out of our half," Booth said. "We showed great resilience to get back into the game and nick it at the end.
"At half-time we knew we had to adjust and it was a complete reversal of the first 20 minutes."
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Spoiled Onions: Exposing Malicious Tor Exit Relays 65
from the just-tell-me-I'll-pass-on-the-message dept.
We've improved Slashdot's video section; now you can view our video interviews, product close-ups and site visits with all the usual Slashdot options to comment, share, etc. No more walled garden! It's a work in progress -- we hope you'll check it out (Learn more about the recent updates).
"New information" being this isn't 25 of 1,000 nodes.
its 25 of some unknown number of nodes, of which 1,000 are active at any one time.
And as I tried to point out last tiime (and am greatful for the opportunity to reiterate)
exit nodes only account for 100Mbps of tors 3Gbps average traffic (most of the traffic being to hidden services which never go near an exit node)
So if anything this is testament to the security of tor.network.
I guess much of the fear comes from the silkroad take down, but that was foiled by the good old postal service and human error, not the technology itself.
Not to mention we have seen several cases in the past couple of years of users having their computer equipment confiscated for running TOR exit nodes by grabbing them for CP distribution, who is to say that when they get their PC back it doesn't have a little "extra hardware" to keep an eye on TOR users?
But you should be able to test without risking lives, have those using the exit nodes go to a "political website" that has an address that nobody would come up with by accident and see if that site after using supposedly "good" nodes suddenly has a jump in activity.
How is that any different from running a free wifi service? Note that most of the illegal material is on Tor hidden services so would never leave your exit node at all, and all censorship on your connection remains in place for everyone using it.
After any salary raise, you will have less money at the end of the month than you did before.


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A machine tool having an automatic tool changer for interchanging cutting tools between the machine spindle and a tool storage wheel. The shanks of the tools are fitted in special "pot-type" holders which support the tools in assigned positions on the storage wheel. A shuttle extracts a selected tool and its holder from the storage wheel and transports them to an interchange position adjacent the machine spindle. At the interchange position a newly selected tool is extracted from its holder and is inserted into the spindle while the previously used tool is inserted into the holder in which the newly selected tool was delivered to the interchange position. The old tool is then returned in this holder to its assigned position on the storage wheel.
1. A tool changing mechanism for a machine tool having a drive spindle carried by a movable spindle head and adapted to receive the shank of a tool, said mechanism including:
a tool storage member mounted independently of the machine tool,
a plurality of tool holders releasably secured to said tool storage member and each operable to support a tool by engagement with the shank thereof,
said tool storage member being indexable to present tool holders and their tools successively to a tool removal position,
means for unlatching a tool holder in said tool removal position,
a shuttle frame mounted in a fixed position with respect to said machine tool and independently of the machine spindle head and extending between said tool removal position and an interchange position,
a shuttle linearly movable on said shuttle frame to engage a tool holder in said tool removal position and transfer such tool holder and its tool to said interchange position, and
an interchange mechanism mounted on the machine tool and operable to engage a tool supported by a tool holder in the interchange position, remove such tool from its tool holder and insert such tool in the machine tool spindle.
2. The structure set forth in claim 1 in which said interchange mechanism is provided with two opposite tool gripping portions operable simultaneously to grip tools in said spindle and in the tool holder in said interchange position and interchange said tools.
3. The structure set forth in claim 1 in which said tool storage member has a plurality of slots formed in spaced locations about the outer periphery thereof, said shuttle having a portion movable through a slot in said tool removal position for removing a tool from said position.
4. The structure set forth in claim 1 in which said tool holders project beyond a peripheral surface of said tool storage member and in which said shuttle engages a tool holder in said tool removal position by straight line movement from the side thereof opposite from said interchange position.
5. The structure set forth in claim 1 in which said shuttle is driven by a hydraulic motor into engagement with a tool holder in said tool removal position and in which said shuttle stalls against a tool holder in said tool removal position until the tool holder in said position is unlatched.
6. The structure set forth in claim 1 in which said tool storage member is mounted on a free standing storage member frame and in which said shuttle frame is mounted on said tool storage member frame.
7. The structure set forth in claim 1 in which said tool holders are provided with flanges having at least one aperture operable to receive a pin on said shuttle and a socket for receiving the shank of a tool to be used in the machine tool, said socket being open at its rear end for reception of a projection on said shuttle.
8. The structure set forth in claim 7 in which said tool holders are provided with barrel portions defining said socket, said barrel portions having a groove on the outer periphery thereof operable to receive a latch on said shuttle.
9. The structure set forth in claim 1 including a latch carried by said shuttle for latching a tool holder in the tool removal position to said shuttle and means for effecting the simultaneous engagement of said shuttle latch and unlatching of the tool holder in said tool removal position from said tool storage member.
10. The structure set forth in claim 9 in which said shuttle latch is spring biased to a closed position and means adjacent the tool removal position for unlatching said shuttle latch when said shuttle is in engagement with a tool holder in the tool removal position.
11. The structure set forth in claim 1 in which the linear movement of said shuttle is parallel to the axis of the machine tool spindle.
12. The structure set forth in claim 1 in which said tool holders are latched to said tool storage members in coded locations on said tool storage member.
13. The structure set forth in claim 12 in which some of said tool storage locations are variably spaced with respect to the remainder of said tool storage locations.
14. The structure set forth in claim 1 including means for stopping said shuttle in a ready position intermediate said tool removal and said interchange positions whereby a tool holder and tool removed from said storage member may be held at said ready position until the completion of a preceding machining operation.
15. The structure set forth in claim 1 in which said tool holders are provided with apertures receiving projections on said shuttle upon the linear movement of said shuttle into engagement with a tool holder in said tool removal position.
16. The structure set forth in claim 1 including a tool storage frame on which said tool storage member is rotatably mounted, said shuttle frame being supported entirely on said tool storage frame.
A variety of machine tools have been introduced in recent years which embody the concept of "automatic tool changing". Such machines function automatically (or semi-automatically) under numerical controls and employ a tool storage device in which all of the metal cutting tools to be used on a given workpiece are stored. The tools perform milling, drilling, boring, tapping, reaming and various other metal cutting functions. All of such tools have a shank which is received within the socket of a drive spindle of the machine. Many automatic tool changing machines incorporate some type of tool handling mechanism by which the tool is extracted from a tool storage device and is inserted in the machine spindle. In other machines the entire storage device is moved to position a desired new tool in alignment with the machine spindle and the spindle itself extracts the desired tool from the tool storage member. Many machines have required the use of expensive tools having special flanges or the like which are gripped by a tool handling mechanism or have means for receiving coding rings or the like by which the tool can be identified in the tool storage device. Many tool changing mechanisms have either been extremely bulky and/or expensive in construction or have lacked adequate tool storage capacity. The tool changer of the present invention solves the basic tool handling and identification problems at a minimum cost and without compromising the performance of the machine or imposing undue limitations on the number or types of tools which can be used.
The tool handler of the present invention is characterized by the use of interchangeable toolholders which support the tools by their shanks both in the tool storage member and during their movement between the storage member and an "interchange position" adjacent the machine tool spindle. The toolholders are extremely simple in design and they are completely interchangeable, the toolholder which is used to bring a new tool to the spindle being used to return an old or previously used tool to the tool storage device. The toolholders are releasably latched in coded positions on a storage wheel and neither the toolholders nor the tools are coded themselves. The tools which are used with the tool changer are of a type previously in common used by a large number of machine tool users. Still other tools can be used with the tool changer of the present invention with minimal machining or alteration thereof.
The tool changer of the present invention is extremely compact in size for the number of tools which it accommodates and may be utilized without impairing the accuracy of the machine tool itself inasmuch as the entire weight ot the tool storage mechanism and the shuttle assembly (by which the tool is transported from the tool storage mechanism to a position adjacent the spindle) is supported independently of the machine tool itself. The tool changer mechanism of the present invention is also extremely rapid in operation, simple in design, easy to program and highly convenient to use. The tool changer may be constructed and sold at a reasonable cost compared to other commercially available tool changers and is both rugged and reliable in performance, the various parts of the tool changer being made to fairly loose dimensional tolerances. The tool changer is of such a design as to minimize or substantially eliminate any danger of dropping a tool during its movement between the tool storage member and the work spindle. The toolholders in which the tools are transported protects the shank of the tools from damage or the buildup of dust or grease which might impair the accuracy of the machining function.
FIG. 1 is a perspective view of a horizontal boring, milling and drilling machine having a tool changer which is constructed in accordance with the present invention and which includes a tool storage device, a shuttle assembly and an interchange mechanism;
FIG. 2 is an enlarged side elevational view of the shuttle assembly portion of the tool changer of FIG. 1;
FIG. 3 is an enlarged sectional view of the structure illustrated in FIG. 2, taken along the line 3--3 thereof;
FIG. 4 is an enlarged rear elevational view, with parts broken away, of the tool storage device and shuttle assembly portions of the tool changer of FIG. 1;
FIG. 5 is an enlarged sectional view of the structure illustrated in FIG. 4, taken along the line 5--5 thereof;
FIG. 6 is an enlarged sectional view of the structure illustrated in FIG. 4, taken generally along the line 6--6 thereof;
FIG. 7, is an enlarged view, with parts broken away, of a portion of the structure illustrated in FIG. 4;
FIG. 8 is an enlarged front elevational view of a portion of the tool changer illustrated in FIG. 1;
FIG. 9 is an enlarged sectional view of the structure illustrated in FIG. 6, taken along the line 9--9 thereof;
FIG. 10 is a sectional view of the structure illustrated in FIG. 9, taken along the line 10--10 thereof;
FIG. 11 is a perspective view of the tool holder shown in FIGS. 9 and 10;
FIG. 12 is an enlarged vertical sectional view of the interchange arm assembly portion of the tool changer illustrated in FIG. 1;
FIG. 13 is an enlarged front elevational view of a portion of the structure illustrated in FIG. 12;
FIG. 14 is an enlarged sectional view of the structure illustrated in FIG. 12, taken along the line 14--14 thereof;
FIGS. 15 and 16 are diagrams schematically illustrating the operation of the various hydraulically operated parts of the tool changer illustrated in the preceding views.
Referring now to FIG. 1, a horizontal boring, milling and drilling machine is illustrated at 10. The machine 10 employs a customary bed 12, a vertical column 14 and a saddle 16 mounted on the bed 12 for horizontal rectilinear movement. A table 18 is mounted on the saddle 16 for horizontal movement perpendicular to the direction of movement of the saddle 16. A rotary worktable 20 is shown mounted on the table 18. A conventional spindle head 22 is mounted on the column 14 for vertical movement thereon and carries a rotary drive spindle 24. A pendant control panel is illustrated at 26 where it is conveniently reached by the machine operator. The panel 26 is wired to a numerical control console 28. The console 28 is of the conventional tape programmed type and directs the functioning of the machine 10 and its tool changer subject to the input of certain manual controls from the panel 26. A tool storage device is illustrated at 30 for the storage of a plurality of cutting tools to be used on the machine 10. Tools are transported from the tool storage device 30 to an "interchange" position adjacent the spindle 24 by a horizontal shuttle assembly 34. Tools are interchanged between the shuttle assembly 34 and the spindle 24 by an interchange mechanism 32.
The tool storage device 30 is illustrated in FIG. 1 as containing a large number of cutting tools 36 of diverse type. The shuttle assembly 34 includes a fixed shuttle frame 38 which is mounted on and projects horizontally from a fixed frame 40 of the tool storage device 30. The frame 40 is a free standing, floor mounted structure and neither the frame 38 nor the frame 40 are connected to the machine 10.
Fixed to the frame 40 is a stub axle 44, which supports a tool storage wheel or member 42 for rotation about a fixed axis through bearings 46 and a hub 48. Fastened to the back of the wheel 42 is a large external spur gear 50 which is engaged by a driving pinion 52 (FIG. 4). The pinion 52 is driven by an electric motor 54 through a belt 56, a speed reducer 58 and a shaft 60. Thus, the motor 54 is effective to rotate the wheel 42 about the axis of the stub axle 44.
Rotation of the wheel 42 produces a corresponding rotation of a rod 64 positioned coaxially thereof within a hollow interior of the axle 44. The rod 64 has a non-cylindrical end portion 66 fitted in a similarly shaped opening of a plate 68 fastened to the end of the hub 48. Keyed to the end of the rod 64 opposite from its portion 66 are a plurality of spaced parallel cam plates 70 disposed in operative relationship to a like number of switches 72 and designed to individually actuate the switches 72 through balls 74. The cam plates 70 are mounted within a cam housing 78 while the switches 72 are mounted within a switch housing 76. The cam plates 70 are designed to actuate their switches 72 in accordance with the angular position of the wheel 42. By the selective shaping of the cam plates 70, the switches 72 will produce a different electrical signal for each of a plurality of selected angular positions of the wheel 42. This electrical signal is transmitted to the control console 28 for the purpose of controlling the energization of the electric motor 54 as will be hereinafter described.
Mounted on the rear side of the wheel 42 are a plurality of cylindrical abutments 80 disposed in a spaced circular arrangement. Also mounted on the rear surface of the wheel 42 is a mounting plate 82 supporting an hydraulic cylinder 84 which is designed to actuate an end 86 of a bell crank-shaped lever 88. The lever 88 is pivoted about a pivot 90 and has an end 92 opposite from the end 86 which is designed to engage any one of the abutments 80. The lever end 86 is held against a rod cap 96 of the cylinder 84 by a spring biased pin 94 which also operates a limit switch 98.
The abutments 80 correspond in number and location to a plurality of key-hole shaped tool storage slots 102 cut into the outer periphery 100 of the wheel 42. Each of the slots 102 is designed to receive a pot shaped toolholder 104. Each of the toolholders 104 is of identical configuration and has a barrel portion 106 closely fitted in a slot 102. Each barrel 106 has an annular groove 108 formed in its outer periphery adjacent its rear end. The forward end of each holder 104 is formed with a radially extending flange 110 abutable with a front face 112 of the wheel 42. The flange has a single hole 114 extending through it at the radially inner side thereof which is designed to receive a pin 116 projecting from the front face 112 of the wheel. The pins 116 correspond in number and location to the slots 102. The flange 110 is further provided with a pair of outer through holes 118 which cooperate with the shuttle asembly 34 as will be hereinafter described. Each holder 104 has a tapered socket 120 designed to receive the shank 122 of a tool 36. The tapered socket 120 has a straight cylindrical bore portion 124 adjacent its rear end which is open to the rear end of the holder. A detent 126 is mounted in the holder and is biased by a spring 128 into the bottom of a notch 130 formed in the tool shank 122. The entire tool shank 122 is identical in shape to the shape of the tool illustrated in U.S. Pat. No. 2,816,770, including the notch 130. Tools having this shank configuration are in common use and thus the tool changer mechanism of the present invention will be seen to work with currently available tooling and does not require tooling of a new type.
The wheel 42 is rotationally indexed by the motor 54 to present toolholders 104 successively to what may be termed a "tool removal position". The tool removal position has a coordinate relationship with the shuttle assembly 34 and a toolholder 104 in this position is designed to be extracted from the wheel 42 by the shuttle assembly 34. When the control console 28 produces a signal directing the wheel 42 to present the tool in a particular slot 102 to the tool removal position, the wheel 42 is driven in rotation until this angular position of the wheel is sensed by the switches 72. Actually, the switches 72 will produce the desired signal when the selected slot 102 is just slightly past the tool removal position. In response to the signal produced by the switches 72, the hydraulic cylinder 84 is actuated to withdraw its rod cap 96 and permit the spring biased pin 94 to move the lever end 92 into circular alignment with the abutments 80. When the limit switch 98 senses that the lever end 92 has been so extended, the motor 54 is reversed to cause the lever end 92 to abut one of the abutments 80. At that point the wheel 42 will have been angularly positioned to position the desired tool 36 and its toolholder 104 in the tool removal position.
Mounted on the wheel 42 is a separate latch mechanism 132 for each slot 102. Each latch mechanism 132 incorporates a latch tongue 134 which projects into the groove 108 of the toolholder 104 in its associated slot 102. The latch tongue 134 is inclined to apply a rearward camming force to the toolholder 104 which will hold the tool-holder flange 110 against the front face 112 of the wheel 42. The latch tongue 134 is designed to be held in either a latching position as illustrated in the drawings or a radially inward unlatched position by means of a detent 135.
Mounted on the tool storage frame 40 adjacent the rear of the wheel 42 is an unlatching mechanism which includes an hydraulic cylinder 136 having a slotted fitting 138 mounted on the actuating rod thereof. The fitting 138 has a slot 140 through which pass a plurality of pins 142, each pin 142 being mounted on one of the latch tongues 134. A pair of limit switches 144 and 146 sense whether the fitting is in a radially outward or a radially inward position. The fitting 138 is designed to be held in a normally radially outward position so that the pins 142 will pass freely through the slot 140 when the latch tongues 134 are in their latched or radially outward position. However, when the wheel 42 is indexed to present a selected slot 102 to the tool removal position, the latch pin 142 for that slot will lie within the slot 140. When the cylinder 136 is then actuated to draw the fitting 138 inwardly that particular latch mechanism 132 will be unlatched and the toolholder 104 which is positioned in the associated slot 102 will be released from the wheel 42 and freed for horizontal travel with the shuttle assembly 34 as will be hereinafter described.
The second of the three major subassemblies of the tool changer comprises the shuttle assembly 34, including its frame 38. Mounted on the frame 38 for horizontal rectilinear movement is a shuttle 150 which rides on a pair of vertically spaced parallel ways in the form of horizontal bars 152. The bars 152 are supported by brackets 154 in such a manner that the shuttle 150 may embrace more than 180� of the periphery of the bars 152. Movement of the shuttle 150 is accomplished by a chain 156 which has its opposite ends connected thereto and is guided by a pair of idler sprockets 158. The chain 156 is driven by a drive sprocket 160 mounted on a drive shaft 162 which is journaled in a bearing housing 164. The drive shaft 162 is driven by an hydraulic motor 166.
The forward end of the shuttle assembly 34 is enclosed within a sheet metal casing 168 to protect the shuttle 150 in its forward position. A collar 170 is mounted on the upper one of the bars 152 at the forward end thereof while a collar 172 is fastened to the lower bar 152 adjacent the rear end thereof. The collars 170 and 172 are designed to limit the forward and rearward travel of the shuttle 150.
The shuttle 150 will be seen to carry a pair of forwardly projecting pins 174 which can be viewed in FIG. 10 as projecting through the outer holes 118 of the toolholder 104. A projection 176 of larger diameter than the pins 174 is mounted on a depending flange 178 of the shuttle 150 in such a position as to enter the bore 124 at the rear end of the toolholder 104.
Looking at FIG. 6, the shuttle 150 will be seen to carry a latch 180 which is integral with a reciprocal block 182. A bore 184 extends transversely through the shuttle 150 in a position slightly offset from but communicating with a tapered opening 186 in the block 182. The latch 180 is normally biased to a latching position illustrated in FIG. 6 by means of a spring 188 seated against a threaded plug 190 fitted in the shuttle 150. The latch 180 is designed to enter the annular groove 108 of the toolholder 104 for securing the toolholder to the shuttle 150. In this latched position the flange 110 of the toolholder 104 will engage a flat front face 191 of the shuttle 150, the pins 174 will be fitted within the holes 118 of the toolholder 104 in the tool removal position and the projection 176 will be disposed within the bore 124 of the toolholder. The latch 180 is retracted by an actuating device which includes an hydraulic cylinder 192 fixed to the frame 38 and a latch actuating pin 194 connected to the piston of the hydraulic cylinder 192. The pin 194 is designed to enter the bore 184 and then wedge its way into the opening 186. The front end of the pin 194 is tapered and cooperates with the opening 186 to cam or bias the latch 180 so that it moves out of the toolholder groove 108.
The shuttle 150 is designed to come to rest in four specific positions on the way bars 152. The movement of the shuttle 150 to these positions is either controlled or monitored by six different limit switches 196, 198, 200, 202, 204 and 206. The four positions of the shuttle are (a) a fully retracted position at which it actuates limit switch 206, (b) a tool removal position at which it actuates limit switch 204, (c) a "ready" position at which it actuates limit switch 200 and (d) a fully advanced or "interchange" position at which it actuates the limit switch 196. Positions a, b and c are shown by broken line representations of the lower portion of the shuttle 150 in FIG. 2. The limit switch 198 is utilized to energize a solenoid actuated valve 208 as the shuttle 150 approaches the advanced or interchange position. When the limit switch 198 is actuated, fluid which powers the hydraulic motor 166 will be directed in a more restricted path through a fluid control device 210 to slow down its rate of flow and thus slow down the speed of the shuttle. This prevents the shuttle from being abruptly stopped for a purpose which will be hereinafter explained. A similar function is performed by limit switch 202 as the shuttle 150 approaches the "ready" position.
FIGS. 12, 13 and 14 show the various parts of the interchange mechanism 32 which is used to interchange tools between the "interchange position" and the machine spindle 24. The interchange mechanism 32 is mounted on the spindle head 22 and includes a support or bracket 212 secured to the spindle head. A long hollow shaft 216 is supported on the support 212 through bearings 214 for both reciprocation and rotation. Mounted on the outer side of the support 212 is an hydraulic cylinder 218 which is connected by a piston rod 220 to a floating housing 222. The floating housing 222 is held against rotation by the piston rod 220 and an anti-rotation rod 224 which slides in a bearing 225 of the hub 212. However, the housing 222 is movable axially of the shaft 216 under the power of the hydraulic cylinder 218. The support 212, housing 222 and related parts are enclosed by a cover 254. The forward and retracted positions of the floating housing 222 are monitored by limit switches 226 and 228 which are actuated by the rod 224.
Supported within the floating housing 222 are bearings 230 which permit the housing 222 to be carried by the shaft 216 without rotating with the shaft 216. An hydraulic motor 232 is carried by the housing 222 and, through a pinion 234, rotates a spur gear 236 keyed to the shaft 216. Fastened to the spur gear 236 is a cam plate 238 which works cooperatively with a retractable stop 240. The stop 240 is mounted on the piston 242 of an hydraulic cylinder 244 so as to be selectively movable in and out of either one of a pair of notches 246 formed in the outer periphery 248 of the cam plate 238. When the stop 240 is positioned in one of the notches 246 it will engage a shoulder 250 disposed at one end of that notch when the shaft 216 is rotated in one direction and it will engage a shoulder 252 disposed at the opposite end of the notch 246 when the shaft 216 is rotated in the opposite direction.
Disposed within the hollow interior of the shaft 216 is a push rod 256 which carries a piston 257. The piston 257 lies in a cylinder bore 258, formed within the hollow interior of the shaft 216. The push rod 256 carries a wedge 260 at its outer end which is inserted between a pair of rollers 262. One of the rollers 262 is carried by each of a pair of parallel arms 264 which are positioned for opposite reciprocal movement within a housing 268 fixed to the outer end of the shaft 216. The arms 264 have cooperating jaws 266 at their opposite ends. The jaw 266 at one end of each arm 264 carries a single pin 276, while a pair of pins 274 are formed on the jaw 266 at the other end thereof. The single pin 276 of one arm 266 faces the pins 274 of the other arm so as to grip therebetween the flange 278 of a tool 36. The configuration of both the tool gripping jaws 266 and the tool flange 278 is identical to that shown in may prior U.S. Pat. No. 3,449,823. The jaws 266 are normally biased toward closed positions by springs 270 which operate against abutments 272 fixed to the housing 268. The space between the pins 276 and 274 is enlarged and the two sets of jaws 266 are forced to open positions by the insertion of the wedge 260 between the rollers 262. By this means the pins 274 and 276 may be positioned on opposite sides of a tool flange 278 and the jaws 266 thereafter closed to insert the pins 274 and 276 into the corresponding holes formed in the flange 278.
Understanding the operation of the tool changer of the present invention is facilitated by reference to FIGS. 15 and 16, which illustrate the operation of the various hydraulically powered components of the system. All movements of the tool changer are powered hydraulically except for the rotation of the tool storage member 42 which is driven by the electric motor 54.
The tool changing function is initiated by rotation of the tool storage member 42 to search for the tool in a selected tool storage slot 102. When the switches 72 produce an electrical signal indicative of the positioning of the selected slot 102 in the tool removal position (actually, just past the tool removal position) a solenoid operated valve 282 is energized and the direction of rotation of the motor 54 is simultaneously reversed. By this means the end 92 of the lever 88 will engage one of the abutments 80 and the tool 36 and toolholder 104 in the selected tool storage slot 102 will be positioned in the tool removal position. During this movement of the member 42, the shuttle 150 is in its fully retracted position where it will actuate the limit switch 206. The movement of the lever 88 is sensed by the limit switch 98 and this signal is utilized to operate the hydraulic motor 166 and produce a slight (about two inch) forward movement of the shuttle 150 into the tool removal position. The shuttle 150 is stopped in this position by abutment of its front face 191 with the toolholder flange 110. The motor 166 stalls with the shuttle 150 in this position. This shuttle movement causes the upper pins 174 of the shuttle to enter the outer openings 118 of the toolholder 104 in the tool removal position and the shuttle projection 176 will enter the rear of the bore 124 of that toolholder.
The arrival of the shuttle 150 in the tool removal position is sensed by the limit switch 204 whereupon a solenoid operated valve 284 is energized to deliver hydraulic fluid to the hydraulic cylinder 192 and the hydraulic cylinder 136. By this means the pin 194, which was previously in a forwardly projected position, is withdrawn from the hole 186 to permit the latch 180 to enter the toolholder groove 108 under the influence of its spring 188. The shuttle 150 is thereby latched to the toolholder 104 in the tool removal position. The delivery of hydraulic fluid to the cylinder 136 causes that cylinder to draw its fitting 138 downwardly to remove the latch 134 from the groove 108 of said toolholder. The toolholder in the tool removal position is thereby unlatched from the tool storage member 42 and the shuttle 150 is freed for continued forward movement by the hydraulic motor 166. This forward movement continues until the shuttle 150 actuates a limit switch 202 at which time the speed of the motor 54 is substantially reduced until the shuttle hits a limit switch 200 at which point the operation of the hydraulic motor 166 is stopped. The selected tool 36 is now in the "ready" position. The purpose of the slowing down of the shuttle 150 prior to completely stopping it in the "ready" position is to prevent possible dislodgement of the tool 36 from the toolholder 104. By very suddenly stopping the movement of the toolholder 104 the high inertia of the tool 36 might cause it to pop out of the toolholder socket 120 against the force of the detent spring 128. By first slowing down the shuttle 150 and then stopping it, this possible accidental loss of the tool 36 from the toolholder 104 in this manner is averted.
A newly selected tool 36 and its toolholder 104 remain in the "ready" position while the preceding machining operation is in progress. During this time the interchange arms 264 are positioned in a vertical attitude with the shaft 216 fully retracted. When that machining operation is completed, the spindle 24 is fully retracted and is angularly oriented to a preset position. The angular and axial positioning of a machine tool spindle is well known in the art and no special means for accomplishing this function is illustrated herein. The spindle head 22 is then indexed on the column 14 to a preset height so that the interchange mechanism 32 (which is positioned on the spindle head) will register with a tool 36 presented to it by the shuttle 150. Before actual interchange of the old and new tools, it may also be necessary to move the machine table 18 away from the spindle. Such a movement, however, must be programmed into the machine and is only done when using very long tools which might interfere with a work-piece on the table.
The final movement of the tool changer prior to the actual "interchange" function is the forward movement of the shuttle 150 from the "ready" position into an "interchange" position. This is accomplished by the operation of the valve 280 (FIG. 15) to deliver hydraulic fluid to the motor 166 in a forward direction. This will drive the chain 156 to move the shuttle 150 forwardly until it actuates the limit switch 198. The operation of the limit switch 198 will actuate the valve 208 to cause the hydraulic fluid flowing to the motor 166 to be delivered through the low speed orifices of a restrictor mechanism 210. The movement of the shuttle 150 is thus slowed down until its stalls against the collar 170 and actuates limit switch 196. The new tool 36 is now in the interchange position and is ready to be interchanged with a previously used tool in the machine spindle 24.
The solenoid 296 now is actuated to angularly index the interchange arms 264 45� so that the jaws 266 of the interchange arms will be poised over the flanges 110 of the tools 36 in the spindle 24 and in the interchange position. As the interchange arms approach the 45� position, a limit switch 300 is actuated to operate a solenoid valve 292 which will alter the flow of fluid flowing to the hydraulic motor 232 so that is flows through the low speed orifices of a restrictor mechanism 294. The arrival of the interchange arms 264 in the 45� tool changing position is sensed by limit switches 298 and 302. The jaws 266 of the interchange arms are then closed to grip the tools 36 in the spindle 24 and in the interchange position. The tool in the spindle 24 is then released from the spindle by a conventional drawbolt (not shown) which is customarily used to hold a tool in a machine spindle. The interchange shaft 216 is then moved axially outwardly to move the old tool out of the spindle and to extract the new tool from its toolholder 104. When the tool 36 is pulled out of its toolholder 104, the spring loaded detent 126 simply snaps out of the tool recess 130. The full forward extension of the interchange arms 264 is sensed by the limit switch 228, which causes the interchange arms to rotate 180�. This is accomplished by withdrawing the abutment member 240 through energization of the solenoid 288 and reversing the direction of energization of the hydraulic motor 232 by actuation of the solenoid 296. When the interchange arms approach the 180� reversed position, this is sensed by one of the limit switches 298, 302, to actuate the solenoid valve 288 and re-extend the abutment member 240. The cam plate shoulder 250 or 252 will engage the abutment 240 and the hydraulic motor 232 will stall to hold the parts in this position at which the new tool will be aligned with the spindle 24 and the old tool will be aligned with the toolholder 104 in the interchange position. The interchange mechanism shaft 216 is then retracted to insert the new tool in the spindle and the old tool in the toolholder 104 in the interchange position. This function is, of course, accomplished by operation of the valve 286 to deliver hydraulic fluid to the cylinder 218 in such a direction as to retract its piston. The jaws 266 are then reopened and the arms 264 angularly indexed 45� to a vertical or parked position.
During the use of the interchange arms 264, the shuttle 150 remains stalled against the collar 170 in the forward position holding the toolholder 104 which was used to deliver the new tool to the interchange position. That same toolholder 104 is now used to receive the old or previously used tool from the spindle 24 and will remain with that old tool in the tool storage member 42 until that tool is next called upon to perform a machining operation.
During the prevously described tool interchanging function it is to be noted that the tool storage member 42 remains with an open or unoccupied slots 102 for both the old and the new tools. While the open slot for the new tool is initially in the "tool removal" position, the tool storage member is now indexed to present the slot 102 for the old tool to "tool removal" position.
The valve 280 is now actuated to reversely drive the hydraulic motor 166 and thereby retract the shuttle 150. During such retraction the shuttle 150 passes through the "ready" position until the flange 110 of the toolholder 104 on the shuttle 150 abuts the front face 112 of the tool storage member 42. At this point the hydraulic motor 166 simply stalls with the shuttle in that position. The arrival of the shuttle 150 at the tool storage member 42 is sensed by the limit switch 204 to actuate the valve 284. When this is done the pin 194 is moved forwardly into the block 182 to retract the shuttle latch 180. Simultaneously, the hydraulic cylinder 136 is operated to extend its fitting 130 and engage the latch 134 in the tool removal position to the toolholder 104 which is now in that position. When this is accomplished the shuttle 150 is no longer held to the member 42 and it may continue its rearward movement an additional two inches to a fully retracted position at which it abuts the collar 172 and the hydraulic motor 166 stalls with the shuttle in this position. The tool storage member 42 may then be angularly indexed by the electric motor 54 to search for a tool 36 which is to be used in the next machining function. Thus, the cycle is repeated to extract a still additional tool from the member 42 and bring it to the "ready" position while the previously selected tool completes its machining function.
It should be mentioned that the tool storage slots 102 are not necessarily equally spaced about the wheel periphery 100. In practice it has been found desirable to space most of the slots only far enough apart to accommodate most of the tools. Only a small minority of the tools used in almost all machining operation have a very large radial dimension. Therefore only a small number of the slots 102 are spaced widely apart to accommodate such large diameter tools. It is only necessary to space the abutments 80 and shape the cam plates 70 in accordance with the location of the slots 102 and this may be done to suit whatever slot locations are desired.
It should also be noted that the tool changer of the present invention uses one less toolholder 104 than there are slots 102. There must always be a completely empty slot 102 for the tool which is in the spindle 24. That tool is returned to its slot 102 in the toolholder for the next tool which is to be used and this function would be prevented by the presence of an empty toolholder in its slot.
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Welcome Music Lovers! Listen to The Great Voices of the 20th Century. Live and Studio Recordings, Arias, Choruses and Duets. Alternately, you can listen to complete operas at TUNEIN RADIO :The Opera House Visit our website at www.opera-thegreatvoices.com
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Navajo Nation Chapters Information
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Thanks to all the chapters that attended the Navajochapters.org Website Training in Farmington at San Juan College. It was a successful training and we hope to continue to help you improve your websites.The next website training has been scheduled for April 15th, 2015 at Navajo Dept. of Transportation Senator Pinto Conference Room 307. Registration will open on April 1st, 2015.
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27 March 2015
From the section Africa
Thousands of people in Sierra Leone have died of Ebola
The authorities in Sierra Leone are enforcing a three-day
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But they also challenged the President to
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This is one of the worse case of cheating, coming from a breastfeeding mum is highly unbearable. This nursing mum in the scene was a
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Sequel to "Nowadays"
Features: Funke Akindele, Queen Nwokoye, Nse Ekpe Etim, Pince Eke, Clem Ohameze, Emmanuel France,Joyce Kalu, Nuella Njubuigbo


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Item: 142366 Model: 34715B5000
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(France 1756 – )
Vase [one of pair]
- Location
- 18th c European porcelain
- Further information
The vase shape was introduced before 1756. A slightly more elaborate version introduced in 1757 was known as a 'vase Marmet'. It is unusual to find a pair of vases made one of soft-paste, the other of hard-paste porcelain. The production of such a pair would have presented considerable difficulties, the soft- and hard-paste workshops being kept entirely separate.
- Year
- 1777
- Media
- Ceramic
- Medium
- soft-paste porcelain
- Dimensions
- 18.9 x 15.0 x 11.5 cm
- Credit
- On loan from Kenneth Reed
- Accession number
Art Set
Add this work to your own Art Set.
Art Set


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Photo : Entrada de Quintas del Pacifico
A picture of 'Entrada de Quintas del Pacifico', this photo is taken in the destination of Puerto Caimito in the province of Panama in the country of Panama. You can click on the image below to see a higher resolution version of this picture, or on the links below that to see more photos by this photographer. You can also add your pictures to this gallery via the links below, or you can click here to see more photos of Puerto Caimito, Panama.This picture is displayed according to Panaramio Copyright Policies.
Photographer : MichaelAngelo [02 May 2010]
Photos provided by Panoramio are under the copyright of their owners


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piping size okay?
My pool company is installing 2.5 inch piping on the suction of the spa and 2 skimmers. The rest looks like 2 inch except for a few pipes coming out of the sides which are 1.5 inch. With this pool set up, does that sound okay?
Pool: 35x19 depth=3ft-5ft water surface=537 sqft
Spa: 5x9
Weeping wall with 4 spillways
Gunite slide/fall combo
No other water features
Equipment:All Pentair
variable speed for pool and spa
2 hp WF for slide water fall
1.5 hp WF for gunite slide and weeping wall
1.5 hp blower
400K heater
500 cartridge filter
Suction cleaner
thanks for the help,
Big pipes make it easier for the flow of water to happen without meeting resistance. The slower the water moves, the better.
Big pipes are more important on the suction side.
I am assuming there is a booster powered pool sweep also, even though it's not been mentioned. These are always 1-1/2 inch piping.
When in circulation mode, the water is usually moving slower. As such, the 2" and 1.5" plumbing is usually fine. Eyeball return fittings, if used are usually smaller, either 3/4" or 1" in size.
The 2.5" suction on the spa generally allows for water to move faster and thus, provide added pressure. I am assuming you have 8 jets and not 6.
You mentioned two WFs. Both are attached to the slide?
Alas, pipe size gets reduced at the pump to two inches and all the equipment such as the filter, heater, salt cell are 2" also.
While 3" pipes certainly reduce the flow's friction and thus, the head loss induced traveling from the pad to the pool, the fact that the motor speed is normally run slower makes the 2.5 suction lines and 2" returns palatable. The XF style version, once it makes it's arrival, will make this an entirely moot issue as it will have the larger pipe size connections.
Hopefully all the other gear will get pipe size upgrades too. I normally hate scuttlebutt but I hear one of the main measures the commercial guys use to differentiate from the residential gear is pipe size. The way I see it, if Zodiac/Jandy can sort it out, so will Pentair.
Pool designs, hydraulically speaking, are becoming more green when it comes to energy usage and this is the way of the future. Slower moving water takes less energy and bigger pipes helps this immensely.


text: by Kristina Gill FACEBOOK TWITTER PINTEREST Katja December 25th, 2011 I love the green sweater. Where did you get it from? LEAVE A COMMENT Design*Sponge reserves the right to restrict comments that do not contribute constructively to the conversation at hand, contain profanity, personal attacks or seek to promote a personal or unrelated business.


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Beauty, Rachel! Terrific work!
Love this. xox
Wonderful scenery that refreshes the old poem words in my mind. When the night is coming… It might be the title of this shot. The work is beautiful. :)
wow… this is the stuff dreams are made of!
Life is beautiful!
Beautiful – love it. Michelle
This is gorgeous – you have a great portfolio Rachel. Looks like you live in a beautiful part of the world :)


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Kampung Tok Senik Resort Langkawi
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Mighty Nature- Borneo / tropikalne lasy Borneo
... Along the way he pointed out plants for headache and toothache relief, stomach problems, insect bites, hear strengthening and even one which helps with red eyes. Truly the jungle can provide everything one needs- from food to cleaning products as long as you know what is what. It's sad to watch this knowledge quickly disappearing. Jeśli lubisz przygodę, spartańskie warunki i spędzanie czasu na łonie przyrody- Borneo powinno znaleźć się ...
How Langkawi stole my heart
... easy to get carried away there and as a result there's always lots of left overs to take home. Cenang was a different story. The main street is filled with fancy restaurants, taxis, motorbike rentals, tour operators and some of the big American franchises such as McDonalds, KFC and Starbucks. The same types of food, clothes and souvenirs as those we saw in Kuah Town cost at least 4 times as much in Cenang. Furthermore, the whole vibe and energy in Cenang was ...
Langkawi-Day 51
... and headed back to the hotel. On the way, we found the mall that we stopped at to get money from on our first day at Langkawi. We decided to have a looked inside to see if they had a supermarket. They did but it wasn't the best. On the way back, around the corner from our hotel, the night market looked as if it had just started. We gave the scooter back, after Eiry ha a quick go, and headed over to the market. The market ...
Aaarrgh.... it's a Pirate Wedding
... had their fill of food, it was time to cut the cake and I managed to get the staff to take a picture of all the pirates and wenches with the happy couple which was nice.
So the evening continued with much hilarity and a great time was had by all, ending up on Joe's boat in the marina until the wee small hours! So congratulations Joe and Anita, may you have a long and happy life together filled with love, fun, and great times. I love you both x
Been having too much fun to blog..!!
... a bucket of 5 beers..!!! I lost the room key and had to retrace our steps all way back along beach thinking we would lose our 50 ringgit deposit for sure(£10) but as we got back to bar we where first at drinking all them beers it was in sand under seat I had been sitting at lucky or what..!! We had one the best Indian meals with a sizzling choc brownie and amazing ice-cream. Went to beach where Jen got burnt..!! :-( We had another amazing meal ...


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Rifleman's Range Bag
The US PALM Rifleman's Range Bag in A-TACS AU Camo is the ultimate range companion. Whether taking a trip to the range for a quick zero or competing in a local shooting match, the RRB can do it all.
Featuring a massive main compartment, there is enough room for several pistols, ammo, and range gear. Exterior pockets for your ear pro, M4/AK or pistol mags, cleaning kit, pens/pencils, spent brass, and even a loop field for your favorite US PALM Morale patches. The main carry handles are built around the entire bag, so heavy ammo loads are no problem for the RRB. Dual zippers provide easy access to the main compartment with one pull. A removable shoulder strap with pad is also included.
With the addition of the RRB Insert (Sold separately), you can keep the interior organized. The removable padded insert has two (2) zippered pistol pockets and two (2) movable dividers to organize your gear. Reinforced carry handles allows you to carry all your ammo with you, without having to bring the main bag along.
The Rifleman's Range Bag is constructed of 500d A-TACS AU Camo Cordura nylon, and utilizes USA made hardware and materials. Completely Made in the USA, and Berry Compliant. For more information on dealers or to purchase, visit www.uspalm.com.
Rifleman's Range Bag Insert
The US PALM Rifleman's Range Bag Insert in A-TACS AU Camo is the perfect upgrade to your US PALM Rifleman's Range Bag (RRB). Stored in the large main compartment of the RRB, this insert allows you to further organize your gear with two (2) zippered pistol pockets and two (2) movable dividers. The reinforced carry handles allow the RRB Insert to handle the load of two pistols and all of your magazines and ammo.
While the RRB Insert is designed to pair with the RRB, it's adjustable design and reinforced construction make it a competent range bag on its own. For more information, dealer info or to purchase, visit www.uspalm.com.
34 inch Rifle Case
The US PALM Rifle Case in A-TACS AU Camo is designed to fit rifles and carbines 34″ inches and smaller, one interior wall includes three row by six column MOLLE webbing at both ends for a wide variety of accessory pouches. The other wall has a pair of repositionable hook and loop straps for securing your rifle in place.
By designing the case's zippers to go further around the perimeter, the US PALM Rifle Case opens up to become a completely flat surface, allowing you use it as a quick access shooting mat, or even to clean or repair your rifle in the field.
Included with the Rifle Case is a padded removable shoulder strap, and the exterior has a large patch of loop material for patches or name tapes. Made of 500D A-TACS AU Camo Cordura. For more information, dealer info or to purchase, visit www.uspalm.com


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Converting-machinery manufacturer Nordmeccanica Group will host a special "Focus on Innovation" open house and technical conference June 2, 2015, at its new expanded facilities in Hauppauge, NY (Long Island).
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Michelman is pleased to announce the hiring of Bill Magee, as Group Director, Printing & Packaging. The Printing & Packaging Group is one of three Michelman global Strategic Business Groups that were formed in January of 2015 as the company improved and streamlined its or...
The Assn. of International Metallizers, Coaters and Laminators (AIMCAL) and the Society of Plastics Engineers (SPE), Bethel, CT, will once again collaborate on a fall technical conference. The joint event combines AIMCAL's Web Coating & Handling Conference USA (WCHC) with SPE's F...
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