US20070258831A1 - Single stage to two stage compressor - Google Patents
Single stage to two stage compressor Download PDFInfo
- Publication number
- US20070258831A1 US20070258831A1 US11/381,859 US38185906A US2007258831A1 US 20070258831 A1 US20070258831 A1 US 20070258831A1 US 38185906 A US38185906 A US 38185906A US 2007258831 A1 US2007258831 A1 US 2007258831A1
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- US
- United States
- Prior art keywords
- compressor
- chamber
- major
- minor
- cam
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/007—Installations or systems with two or more pumps or pump cylinders, wherein the flow-path through the stages can be changed, e.g. from series to parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/005—Multi-stage pumps with two cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/02—Multi-stage pumps of stepped piston type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B5/00—Machines or pumps with differential-surface pistons
- F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
Definitions
- Multi-stage compressors act to compress air in a first chamber forcing it to a smaller second chamber and subsequently to an outlet.
- the piston in the smaller chamber is compressing already compressed air. This allows the compressor to achieve higher pressures.
- such operation is volumetrically inefficient at lower pressures.
- the present invention is premised on the realization that the efficiency of a compressor can be improved by switching from a single stage compressor having major and minor compression chambers to a two stage or dual stage compressor.
- the output from the larger major chamber is switched between either an outlet such as to a holding tank or to the intake of the smaller minor chamber which is in turn connected to an outlet and subsequently the holding tank.
- This allows for initial operation of the compressor in a single stage mode wherein the outputs from both the major and minor compression chambers are directed to a holding tank.
- the output from the major chamber is directed to the intake to the minor chamber, thus switching to a two stage compressor and allowing for greater pressures.
- the present invention is described with respect to a three-lobed cam-operated dual-piston compressor which provides many advantages for the present invention.
- other compressor designs with more than one compression chamber will function in the present invention.
- a three lobed cam-operated dual piston compressor is shown in U.S. patent application Ser. No. 11/235,884, entitled ROTARY TO RECIPROCAL POWER TRANSFER DEVICE, filed on Sept. 25, 2005, the disclosure of which is hereby incorporated by reference.
- FIG. 1 is an elevational view of the present invention
- FIG. 2A is a cross sectional view of the present invention in a single stage mode with the pistons in a first stroke position;
- FIG. 2B is a cross sectional view of the present invention in a single stage mode with the pistons in a second stroke position;
- FIG. 3A is a cross sectional view of the present invention in a dual stage mode with the pistons in a first stroke position;
- FIG. 3B is a cross sectional view of the present invention in a two-stage mode with the pistons in a second stroke position.
- FIG. 4 is an exploded perspective view of the follower of the present invention, partially broken away.
- the compressor 10 includes an exterior housing 18 .
- Housing 18 includes a circular peripheral wall 24 and two side walls 26 and 28 .
- First and second cylindrical mounts 20 and 22 located on peripheral wall 24 , support the first and second compressor chambers 14 and 16 .
- a shaft 30 extends through walls 26 and 28 and is fixed to cam 12 . The cam 12 , when rotated by shaft 30 , moves a follower 34 which, in turn, causes reciprocation of first and second pistons 36 and 38 .
- Cam 12 rotates within the follower 34 which includes a body portion 48 (see FIG. 4 ) formed from first and second spaced body members 50 and 52 on either side of cam 12 .
- the first and second members 50 and 52 each include slots 54 , 56 aligned with a central axis 58 of device 10 .
- the follower 34 has dogleg portions 55 and 57 , which are oppositely offset from central axis 58 .
- the follower 34 further includes first and second head portions 60 and 62 which hold the body members 50 and 52 together on either side of cam 12 .
- First and second rollers 64 and 66 are mounted to head portions 60 and 62 . Also fixed to head portions 60 and 62 are first and second rods 68 and 70 which, in turn, attach to the first and second pistons 36 and 38 , respectively.
- the dogleg portions 55 and 57 and follower 34 are directed toward the driving surface of the cam 12 , and opposite the direction of arrows 46 .
- first head portion 60 is resiliently mounted to the first and second members 50 and 52 of the follower body, whereas second head portion 62 is fixedly attached to first and second members 50 and 52 .
- the first head portion 60 includes a top surface 72 and first and second legs 74 and 76 .
- the first roller 64 is attached to the first head 60 by a pin 78 which extends through first and second legs 74 and 76 .
- the head portion 60 is mounted to first and second members 50 and 52 with four hex screws 80 which run through axially stepped bores 82 .
- Shaft 84 of screws 80 extend through a resilient member which, as shown, is a series of Belleville washers 86 and a sleeve 88 and fastens to members 50 and 52 of the follower body 48 .
- the Belleville washers rest on a shoulder 90 secured by head 91 of screw 80 .
- Any suitable resilient member such as a spring or the like, can be used in place of the Belleville washer.
- the second head 62 can be a mirror image of first head 60 , or, as shown, is simply a C-shaped cap with legs 92 and 93 attached with screws 81 to the members 50 and 52 of follower body 48 .
- the rods 68 and 70 are bolted to heads 60 and 62 at one end 61 and are attached to cylinders 36 and 38 at the opposite end.
- Compression chambers 14 and 16 are cylindrical which house pistons 36 and 38 .
- Rods 68 and 70 extend into chambers portion 14 and 16 through bushings 94 , 95 and oil seals 96 , 97 in circular plates 98 , 99 of discs 100 , 101 .
- Chambers 14 and 16 fit within discs 100 , 101 forming sealed cylindrical chambers.
- Compression chamber 14 includes major and minor (by volume) compression chambers 125 and 126 separated by piston 36 .
- compression chamber 16 includes major and minor compression chambers 127 and 128 separated by piston 38 .
- Compression chambers 14 and 16 also include intakes 104 , 105 , 106 , and 107 , and exhausts 108 , 109 , 110 and 111 leading to and from the respective major and minor compression chambers. Each of these intakes and exhausts utilizes flap valves 112 to allow air or gas in or out of the respective chambers.
- exhaust output lines 108 and 109 lead from the minor compression chambers 128 and 126 directly to a holding tank 113 . These could lead to any output connected to the compressor. Further, intakes 106 and 107 lead from the ambient environment (or any source of low pressure gas) to the major compression chambers 125 and 127 . Exhaust line 110 leads from major compression chamber 125 to valve 114 , and exhaust line 111 leads from major compression chamber 127 to valve 116 .
- the valve 114 and 116 can direct intake air for intake 104 and 105 respectively, either from the exhaust lines 110 and 111 or from the ambient intakes 118 and 120 .
- the exhaust from lines 110 and 111 are directed through lines 122 and 124 to the holding tank 113 .
- Valves 114 and 116 are in turn controlled by a pressure sensor (not shown) located in the holding tank 113 . The pressure sensor will enable pre-set pressure switching of valves 114 and 116 .
- the shaft 30 will rotate, causing the cam 12 to rotate.
- the action of the cam 12 against rollers 64 and 66 causes the follower 34 to move in the direction of arrow 102 as shown in FIG. 2A and, subsequently, in the direction of arrow 103 shown in FIG. 2B .
- This will in turn cause the rods 68 and 70 and associated cylinders 36 and 38 to move in the direction of arrow 102 and, subsequently, 103 .
- the piston 38 will be in an extended position as shown in FIG. 2A with piston 36 in a retracted position.
- gas from chamber 125 will be directed through exhaust 111 through line 124 to holding tank 113 .
- Gas will be drawn into chamber 126 from intake line 120 into line 105 .
- gas will be drawn through intake 106 into chamber 127 .
- Gas in chamber 128 will be forced through exhaust 108 directly to holding tank 113 .
- gas in chamber 125 is forced through exhaust 110 to holding tank 113 .
- Gas will be drawn in through intake 107 to fill chamber 127 .
- gas will be directed from intake 118 through line 104 into chamber 126 , and gas from chamber 128 will be forced through line 111 through valve 116 and line 124 to the holding tank 113 .
- valves 114 and 116 switch to the positions shown in FIGS. 3A and 3B .
- FIG. 3A With the pistons 36 and 38 moving in the direction of arrow 102 , the compressed air from major chamber 127 will be driven through exhaust 111 through valve 116 to intake line 105 and into minor chamber 128 .
- Piston 36 will draw gas into chamber 125 through intake 106 and direct gas from minor chamber 126 through exhaust line 108 to holding tank 113 .
- the compressor 10 pumps the largest volume of gas with output from all four chambers 125 , 126 , 127 , 128 directed to the holding tank to fill the holding tank 113 with gas as rapidly as possible.
- the valves 114 and 116 will be switched to the position shown in FIGS. 3A and 3B , which will allow gas at a higher pressure and lower volume to be forced into holding tank 113 .
- the chambers 126 and 128 are smaller than chambers 125 and 127 , the air introduced in this mode into chambers 126 and 128 will be compressed, as opposed to ambient pressure, which will then be again compressed further when forced into the holding tank. This allows for higher pressure operation.
- this pump Due to the design of this pump, only two valves are required, switching from one mode to a second mode. Further, these valves operate automatically in response to a preset pressure.
- both pistons 36 and 38 will be compressing gas regardless of the direction of movement of the pistons 36 and 38 .
- the oil seals 96 , 97 must also provide the compression seals for the minor chambers in addition to preventing oil in the housing 18 from entering the cylinders 14 , 16 . This allows the compressor cylinders 14 , 16 to operate without oil. This eliminates the need for any type of oil removal equipment downstream from the compressor in applications where the presence of oil cannot be tolerated.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
A compressor includes a cylinder having major and minor compression chambers. The major compression chamber includes an ambient intake and an outlet which can be directed either to the intake of the minor chamber or directly to a holding tank. The outlet from the minor chamber is likewise directed to the gas storage tank. In a preferred embodiment, the compressor includes two cylinders each with a major and minor chamber operated by a three-lobed cam. The compressor switches from single stage to dual stage operation with valves operable in response to attaining a preset gas pressure in the holding tank or output.
Description
- Multi-stage compressors act to compress air in a first chamber forcing it to a smaller second chamber and subsequently to an outlet. Thus, the piston in the smaller chamber is compressing already compressed air. This allows the compressor to achieve higher pressures. However, such operation is volumetrically inefficient at lower pressures.
- The present invention is premised on the realization that the efficiency of a compressor can be improved by switching from a single stage compressor having major and minor compression chambers to a two stage or dual stage compressor. The output from the larger major chamber is switched between either an outlet such as to a holding tank or to the intake of the smaller minor chamber which is in turn connected to an outlet and subsequently the holding tank. This allows for initial operation of the compressor in a single stage mode wherein the outputs from both the major and minor compression chambers are directed to a holding tank. When a predetermined pressure is achieved, the output from the major chamber is directed to the intake to the minor chamber, thus switching to a two stage compressor and allowing for greater pressures.
- This maximizes the efficiency of the compressor allowing it to maximize volumetric output initially and, subsequently, maximize pressure output.
- The present invention is described with respect to a three-lobed cam-operated dual-piston compressor which provides many advantages for the present invention. However, other compressor designs with more than one compression chamber will function in the present invention. A three lobed cam-operated dual piston compressor is shown in U.S. patent application Ser. No. 11/235,884, entitled ROTARY TO RECIPROCAL POWER TRANSFER DEVICE, filed on Sept. 25, 2005, the disclosure of which is hereby incorporated by reference.
-
FIG. 1 is an elevational view of the present invention; -
FIG. 2A is a cross sectional view of the present invention in a single stage mode with the pistons in a first stroke position; -
FIG. 2B is a cross sectional view of the present invention in a single stage mode with the pistons in a second stroke position; -
FIG. 3A is a cross sectional view of the present invention in a dual stage mode with the pistons in a first stroke position; -
FIG. 3B is a cross sectional view of the present invention in a two-stage mode with the pistons in a second stroke position. -
FIG. 4 is an exploded perspective view of the follower of the present invention, partially broken away. - As shown, the
compressor 10 includes anexterior housing 18.Housing 18 includes a circularperipheral wall 24 and twoside walls cylindrical mounts peripheral wall 24, support the first andsecond compressor chambers shaft 30 extends throughwalls cam 12. Thecam 12, when rotated byshaft 30, moves afollower 34 which, in turn, causes reciprocation of first andsecond pistons -
Cam 12 rotates within thefollower 34 which includes a body portion 48 (seeFIG. 4 ) formed from first and second spacedbody members cam 12. The first andsecond members slots central axis 58 ofdevice 10. Thefollower 34 hasdogleg portions central axis 58. Thefollower 34 further includes first andsecond head portions 60 and 62 which hold thebody members cam 12. First andsecond rollers head portions 60 and 62. Also fixed tohead portions 60 and 62 are first andsecond rods second pistons - The
dogleg portions follower 34 are directed toward the driving surface of thecam 12, and opposite the direction of arrows 46. - As shown in
FIG. 4 ,first head portion 60 is resiliently mounted to the first andsecond members second members - The
first head portion 60 includes atop surface 72 and first andsecond legs first roller 64 is attached to thefirst head 60 by apin 78 which extends through first andsecond legs head portion 60 is mounted to first andsecond members hex screws 80 which run through axially steppedbores 82. Shaft 84 ofscrews 80 extend through a resilient member which, as shown, is a series of Bellevillewashers 86 and asleeve 88 and fastens tomembers follower body 48. The Belleville washers rest on ashoulder 90 secured byhead 91 ofscrew 80. Any suitable resilient member, such as a spring or the like, can be used in place of the Belleville washer. - The second head 62 can be a mirror image of
first head 60, or, as shown, is simply a C-shaped cap withlegs 92 and 93 attached withscrews 81 to themembers follower body 48. Therods heads 60 and 62 at oneend 61 and are attached tocylinders -
Compression chambers house pistons Rods chambers portion bushings oil seals circular plates discs Chambers discs -
Compression chamber 14 includes major and minor (by volume)compression chambers piston 36. Likewise,compression chamber 16 includes major andminor compression chambers piston 38.Compression chambers intakes exhausts flap valves 112 to allow air or gas in or out of the respective chambers. - The
exhaust output lines minor compression chambers holding tank 113. These could lead to any output connected to the compressor. Further,intakes major compression chambers Exhaust line 110 leads frommajor compression chamber 125 tovalve 114, andexhaust line 111 leads frommajor compression chamber 127 tovalve 116. - As shown in
FIGS. 2A, 2B , 3A and 3B, thevalve intake exhaust lines ambient intakes inlets ambient intakes lines lines holding tank 113.Valves holding tank 113. The pressure sensor will enable pre-set pressure switching ofvalves - In operation, the
shaft 30 will rotate, causing thecam 12 to rotate. The action of thecam 12 againstrollers follower 34 to move in the direction ofarrow 102 as shown inFIG. 2A and, subsequently, in the direction ofarrow 103 shown inFIG. 2B . This will in turn cause therods cylinders arrow 102 and, subsequently, 103. In the single stage operation, as shown inFIG. 2A , with the follower fully extended in the direction ofarrow 102 thepiston 38 will be in an extended position as shown inFIG. 2A withpiston 36 in a retracted position. As these pistons move, gas fromchamber 125 will be directed throughexhaust 111 throughline 124 to holdingtank 113. Gas will be drawn intochamber 126 fromintake line 120 intoline 105. Likewise, as thecylinder 36 moves in the direction ofarrow 102, gas will be drawn throughintake 106 intochamber 127. Gas inchamber 128 will be forced throughexhaust 108 directly to holdingtank 113. - As
pistons arrow 103, the gas inchamber 125 is forced throughexhaust 110 to holdingtank 113. Gas will be drawn in throughintake 107 to fillchamber 127. Likewise, gas will be directed fromintake 118 throughline 104 intochamber 126, and gas fromchamber 128 will be forced throughline 111 throughvalve 116 andline 124 to theholding tank 113. - If a pre-determined pressure is sensed in the holding tank or output lines,
valves FIGS. 3A and 3B . As shown inFIG. 3A , with thepistons arrow 102, the compressed air frommajor chamber 127 will be driven throughexhaust 111 throughvalve 116 tointake line 105 and intominor chamber 128.Piston 36 will draw gas intochamber 125 throughintake 106 and direct gas fromminor chamber 126 throughexhaust line 108 to holdingtank 113. When the pistons move in the direction ofarrow 103, gas will be drawn in throughintake 107 intomajor chamber 127 and the gas inminor chamber 128, which previously was directed fromchamber 127, will go directly to holdingtank 113 throughline 109.Piston 36, in turn, will force compressed gas frommajor chamber 125 throughexhaust line 110 andvalve 114 throughintake line 104 intominor chamber 126. Thus, in this embodiment, the gas initially is taken into major, or larger,chambers chambers tank 113. - In the first mode of operation, the
compressor 10 pumps the largest volume of gas with output from all fourchambers holding tank 113 with gas as rapidly as possible. Once the tank reaches a pre-determined pressure, thevalves FIGS. 3A and 3B , which will allow gas at a higher pressure and lower volume to be forced into holdingtank 113. Because thechambers chambers chambers - Due to the design of this pump, only two valves are required, switching from one mode to a second mode. Further, these valves operate automatically in response to a preset pressure.
- Because the compressor is set up for operation in both directions of piston movement, both
pistons pistons - In this design, the oil seals 96,97 must also provide the compression seals for the minor chambers in addition to preventing oil in the
housing 18 from entering thecylinders compressor cylinders - This has been a description of the present invention along with the preferred method of practicing the present invention. However, the invention itself should only be defined by the appended claims, WHEREIN
Claims (8)
1. A compressor having a major compression chamber and a minor compression chamber, and a piston operable in said compressor and dividing said major and minor chambers
an inlet into said major chamber;
an inlet into said minor chamber;
an outlet from said major chamber;
an outlet from said minor chamber leading to a compressed gas storage container;
a valve configured to connect said outlet from said major chamber to alternately said inlet to said minor chamber and said compressed gas storage container.
2. The compressor claimed in claim 1 wherein said valve is actuated by a preset output pressure.
3. The compressor claimed in claim 2 wherein said major and minor chambers are in a cylinder divided by said piston.
4. The compressor claimed in claim 1 including first and second cylinders having first and second major and first and second minor chambers and a second valve, said second valve configured to connect said outlet from said second major chamber to alternately said inlet to said second minor chamber or said compressed gas storage container.
5. The compressor claimed in claim 4 wherein said compressor is a rotary cam operated compressor.
6. The compressor claimed in claim 5 comprising a multi-lobed rotating cam;
a follower having two bearing surfaces riding on said cam, said follower movable back and forth along a first axis;
said follower having first and second ends fixed to said first and second pistons, said first and second ends being oppositely offset from said first axis wherein said pistons are movable on second and third axes which are offset and parallel to said first axis.
7. The compressor claimed in claim 6 wherein said follower includes a central body portion with first and second oppositely extended doglegs.
8. The compressor claimed in claim 6 wherein said cam is a three-lobed cam.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/381,859 US20070258831A1 (en) | 2006-05-05 | 2006-05-05 | Single stage to two stage compressor |
PCT/US2007/067585 WO2007130850A2 (en) | 2006-05-05 | 2007-04-27 | Single stage to two stage compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/381,859 US20070258831A1 (en) | 2006-05-05 | 2006-05-05 | Single stage to two stage compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070258831A1 true US20070258831A1 (en) | 2007-11-08 |
Family
ID=38661335
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/381,859 Abandoned US20070258831A1 (en) | 2006-05-05 | 2006-05-05 | Single stage to two stage compressor |
Country Status (2)
Country | Link |
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US (1) | US20070258831A1 (en) |
WO (1) | WO2007130850A2 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110044130A1 (en) * | 2009-08-21 | 2011-02-24 | Oeystein Traetten | Seismic sensor holder and method |
US20110044128A1 (en) * | 2009-08-21 | 2011-02-24 | Eskild Storteig | Marine Seismic Streamer with Increased Skin Stiffness |
WO2013106810A1 (en) * | 2012-01-12 | 2013-07-18 | Bassine Stuart H | Compressor for pressurized fluid output |
US10215166B2 (en) | 2016-12-29 | 2019-02-26 | Stuart H. Bassine | Medical air compressor |
US10584696B2 (en) * | 2015-05-12 | 2020-03-10 | Fugro-Improv Pty Ltd | Subsea multipiston pump module and subsea multistage pump |
CN112855491A (en) * | 2020-12-28 | 2021-05-28 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, refrigerator and control method |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102011084666A1 (en) | 2011-02-11 | 2012-08-16 | Continental Teves Ag & Co. Ohg | Compressor circuit for a pneumatic control device of a vehicle |
CN108131271B (en) * | 2015-12-01 | 2019-08-27 | 唐山亨通科技有限公司 | The fluid energy pumping system of solar energy tracking energy supply |
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US1810688A (en) * | 1928-11-10 | 1931-06-16 | Charles A Toce | Triple cam internal combustion motor |
US5577390A (en) * | 1994-11-14 | 1996-11-26 | Carrier Corporation | Compressor for single or multi-stage operation |
US5915297A (en) * | 1995-12-11 | 1999-06-29 | Valmet Corporation | Apparatus for preventing vibrations of a roll set |
US6068448A (en) * | 1996-12-09 | 2000-05-30 | Sugino Machine Limited | Pressure hydraulic pump having first and second synchronously driven reciprocating pistons with a pressure control structure |
US6394762B1 (en) * | 1999-08-11 | 2002-05-28 | Delphi Technologies, Inc. | Fuel pump |
US7074020B2 (en) * | 2003-08-15 | 2006-07-11 | Cott Technologies, Inc. | Sanitary pump and sanitary valve |
US7475627B2 (en) * | 2005-09-27 | 2009-01-13 | Ragain Air Compressors, Inc. | Rotary to reciprocal power transfer device |
Family Cites Families (1)
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JP3564516B2 (en) * | 1996-09-04 | 2004-09-15 | アイシン精機株式会社 | Reciprocating pump that generates fluid pressure for machine operation |
-
2006
- 2006-05-05 US US11/381,859 patent/US20070258831A1/en not_active Abandoned
-
2007
- 2007-04-27 WO PCT/US2007/067585 patent/WO2007130850A2/en active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1810688A (en) * | 1928-11-10 | 1931-06-16 | Charles A Toce | Triple cam internal combustion motor |
US5577390A (en) * | 1994-11-14 | 1996-11-26 | Carrier Corporation | Compressor for single or multi-stage operation |
US5915297A (en) * | 1995-12-11 | 1999-06-29 | Valmet Corporation | Apparatus for preventing vibrations of a roll set |
US6068448A (en) * | 1996-12-09 | 2000-05-30 | Sugino Machine Limited | Pressure hydraulic pump having first and second synchronously driven reciprocating pistons with a pressure control structure |
US6394762B1 (en) * | 1999-08-11 | 2002-05-28 | Delphi Technologies, Inc. | Fuel pump |
US7074020B2 (en) * | 2003-08-15 | 2006-07-11 | Cott Technologies, Inc. | Sanitary pump and sanitary valve |
US7475627B2 (en) * | 2005-09-27 | 2009-01-13 | Ragain Air Compressors, Inc. | Rotary to reciprocal power transfer device |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9001617B2 (en) | 2009-08-21 | 2015-04-07 | Westerngeco L.L.C. | Marine seismic streamer with increased skin stiffness |
US20110044128A1 (en) * | 2009-08-21 | 2011-02-24 | Eskild Storteig | Marine Seismic Streamer with Increased Skin Stiffness |
US20110044129A1 (en) * | 2009-08-21 | 2011-02-24 | Oeystein Traetten | Apparatus and method for decoupling a seismic sensor from its surroundings |
US20110044130A1 (en) * | 2009-08-21 | 2011-02-24 | Oeystein Traetten | Seismic sensor holder and method |
US8588026B2 (en) | 2009-08-21 | 2013-11-19 | Westerngeco L.L.C. | Apparatus and method for decoupling a seismic sensor from its surroundings |
US8593906B2 (en) | 2009-08-21 | 2013-11-26 | Westerngeco L.L.C. | Seismic sensor holder and method |
WO2013106810A1 (en) * | 2012-01-12 | 2013-07-18 | Bassine Stuart H | Compressor for pressurized fluid output |
EP2802779A4 (en) * | 2012-01-12 | 2015-12-02 | Stuart H Bassine | Compressor for pressurized fluid output |
KR101882701B1 (en) * | 2012-01-12 | 2018-08-24 | 스튜어트 에이치. 바자인 | Compressor for pressurized fluid output |
US11187220B2 (en) | 2012-01-12 | 2021-11-30 | Stuart H. Bassine | Compressor for pressurized fluid output |
US10584696B2 (en) * | 2015-05-12 | 2020-03-10 | Fugro-Improv Pty Ltd | Subsea multipiston pump module and subsea multistage pump |
US10215166B2 (en) | 2016-12-29 | 2019-02-26 | Stuart H. Bassine | Medical air compressor |
CN112855491A (en) * | 2020-12-28 | 2021-05-28 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, refrigerator and control method |
Also Published As
Publication number | Publication date |
---|---|
WO2007130850A3 (en) | 2008-07-31 |
WO2007130850A2 (en) | 2007-11-15 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: RAGAIN AIR COMPRESSORS, INC., TENNESSEE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:IRICK, DAVID KIM;REEL/FRAME:017580/0814 Effective date: 20060418 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |