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Patent US5649959 - Assembly for sealing a puncture in a vessel - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign inPatentsA bioabsorbable assembly for sealing an incision or puncture in the body of the patient including a first member which is positioned generally along the wall of the blood vessel, duct, body cavity or lumen of the patient and a gelatinous material which is injected into the incision or puncture around...http://www.google.com/patents/US5649959?utm_source=gb-gplus-sharePatent US5649959 - Assembly for sealing a puncture in a vesselAdvanced Patent SearchPublication numberUS5649959 APublication typeGrantApplication numberUS 08/389,839Publication dateJul 22, 1997Filing dateFeb 10, 1995Priority dateFeb 10, 1995Fee statusPaidAlso published asCA2187545A1, CA2187545C, EP0755226A1, EP0755226A4, WO1996024290A1Publication number08389839, 389839, US 5649959 A, US 5649959A, US-A-5649959, US5649959 A, US5649959AInventorsPeter Henry Hannam, Richard Dale AllisonOriginal AssigneeSherwood Medical CompanyExport CitationBiBTeX, EndNote, RefManPatent Citations (68), Referenced by (652), Classifications (14), Legal Events (4) External Links: USPTO, USPTO Assignment, EspacenetAssembly for sealing a puncture in a vessel
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methods of use* Cited by examinerClassifications U.S. Classification606/213, 606/214, 604/93.01, 604/43, 604/257, 604/181International ClassificationA61B17/00, A61B17/12Cooperative ClassificationA61B2017/0065, A61B2017/00659, A61B2017/00637, A61B17/0057, A61B17/00491European ClassificationA61B17/00PLegal EventsDateCodeEventDescriptionMay 22, 1995ASAssignmentOwner name: SHERWOOD MEDICAL COMPANY, MISSOURIFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SHERWOOD MEDICAL INDUSTRIES, LTD.;REEL/FRAME:007512/0205Effective date: 19950511Owner name: SHERWOOD MEDICAL COMPANY, MISSOURIFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:ALLISON, RICHARD D.;REEL/FRAME:007512/0212Effective date: 19950519Owner name: SHERWOOD MEDICAL INDUSTRIES, LTD., ENGLANDFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HANNAM, PETER HENRY;REEL/FRAME:007512/0215Effective date: 19950502Jan 8, 2001FPAYFee paymentYear of fee payment: 4Jan 13, 2005FPAYFee paymentYear of fee payment: 8Jan 22, 2009FPAYFee paymentYear of fee payment: 12RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services


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Patent US4520767 - Low flow cooling system and apparatus - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign in<nobr>Advanced Patent Search</nobr>PatentsThe disclosure illustrates a cooling system for a turbocharged diesel engine having an aftercooler and an oil cooler. The cooling system is defined by two flow loops, one for the engine and the other for cooling purposes. An engine driven pump circulates a coolant through the engine block and cylinder...http://www.google.com/patents/US4520767?utm_source=gb-gplus-sharePatent US4520767 - Low flow cooling system and apparatusAdvanced Patent SearchPublication numberUS4520767 APublication typeGrantApplication numberUS 06/533,099Publication dateJun 4, 1985Filing dateSep 16, 1983Priority dateSep 16, 1983Fee statusPaidAlso published asDE3433370A1, DE3433370C2Publication number06533099, 533099, US 4520767 A, US 4520767A, US-A-4520767, US4520767 A, US4520767AInventorsLeslie A. Roettgen, Beth A. Webber, Robert M. Brooks, Robert J. LaymanOriginal AssigneeCummins Engine CompanyExport CitationBiBTeX, EndNote, RefManPatent Citations (12), Referenced by (38), Classifications (29), Legal Events (7) External Links: USPTO, USPTO Assignment, EspacenetLow flow cooling system and apparatusUS 4520767 AAbstract The disclosure illustrates a cooling system for a turbocharged diesel engine having an aftercooler and an oil cooler. The cooling system is defined by two flow loops, one for the engine and the other for cooling purposes. An engine driven pump circulates a coolant through the engine block and cylinder heads. The pump also circulates coolant through the cooling loop which includes the engine oil cooler immediately upstream of a radiator and bypass line. The aftercooler is downstream of the radiator and bypass line. Placement of the oil cooler ahead of the radiator and bypass line produces a higher temperature potential which permits a reduction in radiator size in addition to other benefits. A flow control logic system embodied in a dual thermostat arrangement ahead of the radiator and bypass line minimizes mixing of bypass flow with radiator flow and reduces radiator flow rates to permit low aftercooler temperatures that hithertofore have not been achievable.
5. A logic control system for an internal combustion engine having a cooling system including a combination of a heat exchanger and a bypass passage in parallel connection, an aftercooler serially connected to the combination and disposed immediately downstream thereof and pumping means for circulating a heat exchange medium through said cooling system, said logic control system comprising:temperature sensing means for sensing the temperature of the heat exchange medium at one or more locations in the cooling system; bypass logic control means for effecting control of the flow of heat exchange medium through said bypass passage whereby maximum flow through the bypass passage is effected when the temperature sensed by said temperature sensing means at a first predetermined location in the cooling system is equal to or below a first setpoint temperature, and whereby no flow through the bypass passage is effected when the temperature sensed by said temperature sensing means at the first location is equal to or greater than a second setpoint temperature greater than said first setpoint temperature; cooling logic control means for effecting control of the flow of heat exchange medium through the heat exchanger whereby no flow through the heat exchanger is effected when the temperature sensed by said temperature sensing means at a second predetermined location is equal to or below a third setpoint temperature, and whereby maximum flow through the heat exchanger is effected when the temperature sensed by said temperature sensing means at the second location is equal to or greater than a fourth setpoint temperature greater than said third setpoint temperature; and wherein said third setpoint temperature is independent of said first setpoint temperature and said fourth setpoint temperature is independent of said second setpoint temperature. 6. The logic control system set forth in claim 5 wherein said first location is the same as said second location.
10. The logic control system set forth in claim 9 wherein said dual valve thermostat comprises:a housing defining upper and lower bypass control chambers and upper and lower cooling control chambers; a bypass control valve engaging said upper and lower bypass control chambers, said bypass control valve selectively allowing communication between said upper and lower bypass control chambers only when the temperature of the heat exchange medium in the lower bypass control chamber is less than the second setpoint temperature; and a cooling control valve engaging said upper and lower cooling control chambers, said cooling control valve selectively allowing communication between said upper and lower cooling control chambers only when the temperature of the heat exchange medium in the lower cooling control chamber is greater than the third setpoint temperature. 11. The logic control system system set forth in claim 10 wherein said bypass control valve permits maximum communication between said upper and lower bypass control chambers when the temperature of the heat exchange medium in the lower bypass control chamber is less than the first setpoint temperature, and said cooling control valve permits maximum communication between said upper and lower cooling control chambers when the temperature of the heat exchange medium in the lower cooling control chamber is greater than the fourth setpoint temperature.
14. A dual valve thermostat for an internal combustion engine having a cooling system including a combination of a heat exchanger and a bypass passage in parallel connection and pumping means for circulating a heat exchange medium through said cooling system, said dual valve thermostat comprising:a housing defining upper and lower bypass control chambers and upper and lower cooling control chambers; a bypass control valve engaging said upper and lower bypass control chambers, said bypass control valve allowing maximum communication between said upper and lower bypass control chambers when the temperature of the heat exchange medium in said lower bypass chamber is less than a first setpoint temperature, and selectively allowing communication between said upper and lower bypass control chambers only when the temperature of the heat exchange fluid is less than a second setpoint temperature; and a cooling control valve engaging said upper and lower cooling control chambers, said cooling control valve selectively allowing communication between said upper and lower cooling control chambers only when the temperature of the heat exchange medium in said lower cooling control chamber is greater than a third setpoint temperature, and allowing maximum communication between said upper and lower cooling control chambers when the temperature of the heat exchanger medium in said lower cooling chamber is greater than a fourth setpoint temperature. Description
FIGS. 9, 10, and 11 are graphs showing the intake manifold temperature for a diesel engine versus the percent load on the engine for an engine equipped with conventional control logic and for an engine equipped with the logic control system of the present invention at ambient air temperatures of 35� F., 60� F., and 85� F., respectively.
The cooling loop 70 is shown in FIG. 3 while the system is operating in a full cooling or first mode. In the full cooling mode the oil cooler 10, the heat exchanger or radiator 30, and the aftercooler 20 are hydraulically coupled. The logic control system causes the coolant discharged from the oil cooler 10 to be directed through only the radiator 30 of the combination C and from radiator 30 to aftercooler 20. The full cooling mode is dictated in this embodiment by the temperature of the coolant at the outlet 14 of the oil cooler 10 as sensed by the temperature sensing means of the logic control system. In this particular embodiment, the temperature sensing means are included in the dual valve thermostat 50. When the sensed temperature exceeds a first setpoint temperature, typically in the range of 190� to 195� F., the bypass valve section 52 of the thermostat 50 is in a seated or closed position and the coolant is directed by cooling valve section 54 of the thermostat 50, which is in an open position, to the radiator inlet 32. See FIG. 6. After the coolant circulates through the radiator 30, its temperature is significantly decreased and it is discharged to the aftercooler inlet 22. In this mode the temperature potential of the coolant to the aftercooler 20 is maximized, promoting efficient operation of the diesel engine 1.
An important advantage of the cooling system described in FIG. 3 is the presence of oil cooler 10 in the cooling loop 70 directly upstream of the radiator 30. The oil cooler 10 can typically operate at temperatures significantly higher than can be tolerated by the engine block 2 or cylinder liners 4. Accordingly, it contributes additional heat to the coolant which raises the coolant's temperature above the temperature at which it would otherwise enter the radiator 30. This increase in temperature improves the temperature potential across the radiator 30 which in turn permits the use of a smaller or more cost effective radiator 30 and associated fan assembly. For example, it has been calculated for the cooling system shown in FIG. 3 that when the oil cooler 10 is not in circuit the temperature of the coolant to the radiator 30 is about 204� F. for a given engine heat rejection load. For the same heat rejection load, however, placing the oil cooler 10 in circuit as shown in FIG. 3 increases the temperature of the coolant to the radiator 30 to about 214� F. This temperature increase gives the engine designer the option of reducing the radiator frontal area by 25%, of reducing the number of fins-per-inch on the airside of the radiator core by 25%, or of utilizing a reduction in air horsepower (power consumed by the radiator fan) of 47%.
The system of FIG. 3 operates in a full bypass or second mode when the temperature of the coolant discharged from the outlet 14 of the oil cooler 10 is sensed by the dual valve thermostat 50 as being equal to or below a second setpoint temperature, typically in the range of 140� to 145� F. In this circumstance, which typically occurs during engine start-up, cooling valve section 54 is seated or closed, blocking all flow of coolant to the radiator 30, whereas bypass valve section 52 is simultaneously in an open condition thus directing the coolant directly to the inlet 22 of aftercooler 20. Thus, it will be observed during the second mode that oil cooler 10 is fluidly in series with the bypass pipe section 35 and the aftercooler 20, and that radiator 30 is completely bypassed. This permits the engine charge air to be heated during start-up which significantly improves the combustion efficiency during the start-up period, and also helps reduce noxious emissions.
FIG. 8 is a graphical illustration of one flow profile attainable by the logic control system of the present invention. The graph compares cooling loop flow, measured at the aftercooler inlet 22 in gallons per minute, versus the temperature sensed by the dual valve thermostat 50 in degrees fahrenheit. For this particular embodiment it can be seen that the flow in the cooling loop 70 is relatively constant until the bypass valve section 52 begins to seat or close at approximately 140� to 145� F. (the first setpoint temperature). At approximately 175� F. (the third setpoint temperature) the cooling valve section 54 begins to open and between 175� to 185� F. the flow through the aftercooler is a combination of the flows passing the sections of cooling control valve 54 and bypass control valve 52. At 185� F. (the second setpoint temperature) the heating control valve section 52 is completely closed preventing the flow of coolant through the bypass passage 35. The cooling valve section reaches a full open position at approximately 190� to 195� F. (the fourth setpoint temperature), at which point a constant flow rate through the cooling loop is achieved. In general, it is preferable for a diesel engine having a cooling system of a type generally described above to employ a flow profile in which the ratio of the difference between the second setpoint temperature and the first setpoint temperature to the difference between the fourth setpoint temperature and the first setpoint temperature is in the range of about 0.1 to about 0.5.
FIGS. 9, 10, and 11 illustrate at least one of the benefits of this invention. A comparison is made of the intake manifold temperature for a diesel engine having the logic control system of the present invention to the intake manifold temperature of a diesel engine having prior art flow control logic of substantial and continued bypass flow during modulation of the flows for various ambient temperatures and various loadings of the engine. As shown, significantly more cooling of the air charged to the cylinders is achieved when the present invention is utilized. Thus, in FIG. 9, for example, at 50% load and 35� F. ambient temperature, the intake manifold temperature of a diesel engine with a conventional flow control logic is approximately 155� F. whereas in a diesel engine utilizing the present invention, the intake manifold temperature is approximately 80� F. It will readily be appreciated by those of ordinary skill in the art that this illustrates a substantial improvement in engine performance characteristics, including fuel savings and lower emissions.
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NEMINNEAPOLFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CUMMINGS ENGINE COMPANY, INC. /AR;REEL/FRAME:013868/0374Sep 30, 1996FPAYFee paymentYear of fee payment: 12Sep 30, 1992FPAYFee paymentYear of fee payment: 8Feb 15, 1989SULPSurcharge for late paymentFeb 15, 1989FPAYFee paymentYear of fee payment: 4Jan 3, 1989REMIMaintenance fee reminder mailedSep 16, 1983ASAssignmentOwner name: CUMMINS ENGINE COMPANY INC COLUMBUS IN A IN CORPFree format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:ROETTGEN, LESLIE A.;WEBBER, BETH A.;BROOKS, ROBERT M.;AND OTHERS;REEL/FRAME:004182/0467Effective date: 19830916RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services©2012 Google

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Frost & Sullivan: Record Production of Commercial Aircraft Spawns a Huge Market for Sensors -- LONDON, Aug. 19, 2014 /PRNewswire/ --
LONDON, Aug. 19, 2014 /PRNewswire/ -- In 2013, for the third year in a row, the annual global production of commercial aircraft crossed 1,000 aircraft per year. In the next 20 years, the aerospace industry is expected to have an additional 34,000 commercial aircraft. The frenzied activity in this industry is expected to ripple into the sensor market. Sensor manufacturers have been developing technologically superior sensors to keep pace with airlines, which are updating their fleets with new fuel-efficient aircraft in order to stay competitive.
Analysis of Sensor Market in the Global Aerospace Industry is part of the Sensors & Instrumentation (http://www.sensors.frost.com) Growth Partnership Service program. Frost & Sullivan's related studies include: Sensors Market in Shale Gas Industry, Global Wireless Sensor Networks Market, Sensors in Test and Measurement, and Strategic Analysis of the World Optical and Image Sensors Market. All studies included in subscriptions provide detailed market opportunities and industry trends evaluated following extensive interviews with market participants.
Analysis of Sensor Market in the Global Aerospace IndustryMA34-32
Contact:Julia NikishkinaCorporate Communications – EuropeP: +7 (499) 213 0156E: julia.nikishkina@frost.com LinkedIn: Future of Measurement and Instrumentation Twitter: @FS_Automation
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