WO2018132591A1 - Fluid compressor - Google Patents
Fluid compressor Download PDFInfo
- Publication number
- WO2018132591A1 WO2018132591A1 PCT/US2018/013349 US2018013349W WO2018132591A1 WO 2018132591 A1 WO2018132591 A1 WO 2018132591A1 US 2018013349 W US2018013349 W US 2018013349W WO 2018132591 A1 WO2018132591 A1 WO 2018132591A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- set forth
- compression chamber
- fluid compressor
- fluid
- compressor
- Prior art date
Links
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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
-
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B27/0404—Details, component parts specially adapted for such pumps
- F04B27/0409—Pistons
-
- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/0276—Lubrication characterised by the compressor type the pump being of the reciprocating piston type, e.g. oscillating, free-piston compressors
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0284—Constructional details, e.g. reservoirs in the casing
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
Definitions
- This application relates to various improvements in structures for fluid compressors.
- Refrigerant compressors are utilized to compress a refrigerant for use in a refrigerant cycle.
- the present invention seeks to address these deficiencies.
- a fluid compressor in one embodiment, includes a housing; a compression chamber within the housing; a motor, a shaft that is rotated by the motor, and a piston assembly including at least two pistons directly connected to each other without any piston rods.
- the piston assembly performs a reciprocating motion when acted on by the shaft such that the at least two pistons move within the compression chamber to compress a fluid.
- Figure 1 is a schematic view of a compressor in accordance with one embodiment of the present invention.
- Figure 2 is a side and cross-sectional view of the shaft and piston assembly shown in Figure 1;
- Figure 3 is a top view of an embodiment with 4 pistons that simultaneously proceed through their compression cycles;
- Figure 4 is an embodiment of a piston assembly for a 4 piston fluid compressor that does not simultaneously compress
- Figure 5 is a cross-section through an assembly of a horizontal embodiment of the present invention.
- Figure 6 is a cross-section through a compression chamber of an alternative embodiment of the present invention.
- Figure 7 is a close up cross-sectional view of the connection between the stator laminates and the housing of one embodiment of the present invention.
- a fluid compressor 20 is illustrated in Figure I having a suction tube 22 providing a suction refrigerant into a suction chamber 24.
- a motor 26 is mounted within a housing, and drives a rotary shaft 28.
- Rotary shaft 28 causes a piston assembly 30 to reciprocate a pair of attached pistons 35 through the connection of yoke 29 and an eccentric pin 31.
- the pistons 35 arc directly connected to piston assembly 30.
- Conventional compressors may attach the pistons to connecting rods which requires more labor and maintenance. The present invention eliminates these problems.
- Suction plenums 32 lead the refrigerant from suction chamber 24 through inlet valves 33 and into compression chambers 36, defined by a crankcase or housing 34.
- Discharge valve assemblies 38 are placed at an opposite end of each compression chamber 36 from the inlet valves 33.
- the refrigerant passes outwardly through the discharge valves 38 into a discharge chamber 40, and then through a discharge tube 42.
- This dramatic separation of the suction discharge gas flow from the intake gas flow results in less heat pickup in the intake suction stream. This results in more dense gas into compression chamber, which allows compressor 20 to provide more capacity out of a smaller mechanism.
- the separation of the discharge valve 38 from the inlet valve 33 maximizes the discharge volumetric geometry, allowing reduced pressure drops and improved fluid flow. This can be accomplished whether the gas is brought in through a valve on a face of the piston or through a valve in the bore (a side of the compression chamber) that is exposed when the piston retreats during the suction stroke.
- Figure 6 shows a compression chamber with an inlet valve 33 on a lower side surface of the compression chamber. When the piston 35 retreats for a suction stroke, the valve 33 is exposed to the compression chamber. This again allows a maximizing of the distance between the intake and discharge valves, maximizing the discharge volumetric geometry.
- the size of the discharge valve can be made significantly larger.
- a larger discharge valve doesn't need to open as much to allow the compressed fluid out of the compression chamber. This improves valve timing and reduces backflow into compression chamber, further improving performance.
- the disclosed configuration also eliminates the need for any discharge mufflers, internal high pressure exhaust tubes, mechanical mounting springs or mounts, cylinder heads, and valve plates. The elimination of all of these parts also reduces manufacturing costs and maintenance. In particular, the volume in housing 34 of the discharge chamber of compressor 20 becomes a discharge muffler chamber. This eliminates the need for a separate part for a discharge muffler.
- Figure 2 also shows high pressure relief valve 85. This valve is designed to vent the high pressure from the discharge side if that pressure exceeds a critical value. This prevents catastrophic failure of the compressor housing.
- Figure 2 also shows seal point 90, onto which an o-ring (not shown) is mounted. This seal prevents high pressure compressed fluid from leaking back into the intake side.
- the present invention includes far fewer possible leakage paths.
- the present invention can perform at much higher compression ratios than a scroll compressor, such as greater than a 10: 1 compression ratio.
- a scroll compressor such as greater than a 10: 1 compression ratio.
- Compressor 20 also includes lower bearing 70 and upper bearing 80. These bearings allow for a smaller sized motor, which results in greater efficiently and lower cost.
- FIG. 1 motor 26 is in direct contact with the inner surface of housing 21. This allows heat generated by motor 26 to more efficiently escape the compressor 20.
- Figure 7 shows a close up of the contact between the motor laminate layers 52 and the housing 21. (Although the housing has a circular cross-section, the housing is shown in this view as having straight sides due to the small scale.)
- Each stator laminate layer 52 has a thickness of approximately 0.020 in.
- Each stator laminate layer 52 may then line up with a corresponding heat dissipation fin 23 on an outer surface of housing 21 to promote heat transfer from the laminate layer 52, through housing 21, and out corresponding fin 23.
- Fin 23 is shown with a triangular cross-section, but any shape or configuration suitable for heat dissipation is possible. These modifications are within the scope of the invention as claimed.
- this direct connection to the outer housing means that the compressor can be deployed in varying configurations, such as standing up or on its side.
- Figure 5 shows a horizontal configuration of the present invention. The only changes needed to place the compressor horizontally is the feet need to be moved to support the compressor. Also, the compressor 20 is not completely horizontal, but at approximately 5-10 degrees from horizontal to ensure oil 60 can continue to be drawn into the bottom of lower bearing 70.
- the outer housing is cylindrical.
- conventional compressor housings have an oval horizontal cross-section.
- the cylindrical outer housing of the present invention has several advantages. First, the circular cross- section is stronger, and thus higher pressure operation is possible, allowing higher compression ratios and higher performance. Further, the cylindrical shape creates a smaller oil sump volume 60 that must be filled with oil. Reducing the amount of oil needed saves costs throughout the lifetime of the compressor. Additionally, oval cross-sections may vibrate during operation of the compressor. This creates added noise that is not generated by the circular cross-section.
- Figure 3 shows an alternative embodiment which include 4 pistons 135, each of which proceed through the compression cycle simultaneously.
- Springs 137 are located in the compression chambers at an outer end to push the pistons 13S back when cam 139 moves to remove the force on piston 135.
- Cam 139 rotates on shaft 128, which is turned by a motor as in the first embodiment.
- either or both of the modifications may be used within the scope of the invention as claimed.
- 'Chat is, 2 piston unsynchronized, 4 piston unsynchronized, 2 piston synchronized, and 4 piston synchronized are ail within the scope of the invention as claimed.
- Figure 5 shows a piston assembly for a 4 piston unsynchronized configuration.
- This piston assembly includes a connection portion 30A that extends above the piston surfaces to allow for a perpendicular piston assembly to reciprocate below the portion 30A as the shaft rotates.
- 4 pistons can run in an unsynchronized manner to compress fluid.
Abstract
A fluid compressor includes a housing; a compression chamber within the housing; a motor; a shaft that is rotated by the motor; and a piston assembly including at least two pistons directly connected to each other without any connecting rods. The piston assembly performs a reciprocating motion when acted on by the shaft such that the at least two pistons move within the compression chamber to compress a fluid.
Description
FLUID COMPRESSOR
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application claims priority to U.S. Patent Application No. 15/868,355, filed January 11, 2018, which claims priority under 35 U.S.C. §119(e) to U.S. Application No. 62/445.218, filed January 11, 2017. Each of these applications is incorporated by reference herein in its entirety.
BACKGROUND OF THE INVENTION
[0002] This application relates to various improvements in structures for fluid compressors.
[0003] Refrigerant compressors are utilized to compress a refrigerant for use in a refrigerant cycle.
[0004] In two known types of refrigerant compressors, significant drawbacks exist that reduce performance and increase cost. First, in conventional reciprocating compressors, a pair of pistons are driven to reciprocate within compression chambers by a motor. Fluid enters through an entry passage in each compression chamber and exits through a discharge passage. These passages are generally in a same surface of the compression chamber, in a surface opposite the face of the piston. This close proximity between the entry and discharge passages allows heat from the discharge passage to travel to the suction entry passage, heating up the fluid entering the chamber. This causes the fluid to expand, which reduces the amount of fluid entering the chamber for each stroke of the piston. Thus, the capacity of the compressor is reduced, and performance is reduced.
[0005] Second, in conventional scroll compressors, there are many places throughout the travel path of the fluid that can leak, especially at higher pressures. Accordingly, scroll compressors cannot provide high pressure operation or compression ratios. For example, compression ratios of over 7: 1 are very problematic for scroll compressors, likely leading to leaks as well as higher friction levels within the compression passages and reduced performance.
[0006] The present invention seeks to address these deficiencies.
SUMMARY OF THE INVENTION
[0007] In one embodiment of the present invention, a fluid compressor includes a housing; a compression chamber within the housing; a motor, a shaft that is rotated by the motor, and a piston assembly including at least two pistons directly connected to each other without any piston rods. The piston assembly performs a reciprocating motion when acted on by the shaft such that the at least two pistons move within the compression chamber to compress a fluid.
[0008] These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
BRIEF DESCRIPTION OF THE DRAWINGS
[0009] Figure 1 is a schematic view of a compressor in accordance with one embodiment of the present invention;
[0010] Figure 2 is a side and cross-sectional view of the shaft and piston assembly shown in Figure 1;
[0011] Figure 3 is a top view of an embodiment with 4 pistons that simultaneously proceed through their compression cycles;
[0012] Figure 4 is an embodiment of a piston assembly for a 4 piston fluid compressor that does not simultaneously compress;
[0013] Figure 5 is a cross-section through an assembly of a horizontal embodiment of the present invention;
[0014] Figure 6 is a cross-section through a compression chamber of an alternative embodiment of the present invention; and
[0015] Figure 7 is a close up cross-sectional view of the connection between the stator laminates and the housing of one embodiment of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0016] A fluid compressor 20 is illustrated in Figure I having a suction tube 22 providing a suction refrigerant into a suction chamber 24. A motor 26 is mounted within a housing, and drives a rotary shaft 28. Rotary shaft 28 causes a piston assembly 30 to reciprocate a pair of attached pistons 35 through the connection of yoke 29 and an eccentric pin 31. Thus, the pistons 35 arc directly connected to piston assembly 30. Conventional compressors may attach the pistons to connecting rods which requires more labor and maintenance. The present invention eliminates these problems.
[0017] Suction plenums 32 lead the refrigerant from suction chamber 24 through inlet valves 33 and into compression chambers 36, defined by a crankcase or housing 34. Discharge valve assemblies 38 are placed at an opposite end of each compression chamber 36 from the inlet valves 33. The refrigerant passes outwardly through the discharge valves 38
into a discharge chamber 40, and then through a discharge tube 42. This dramatic separation of the suction discharge gas flow from the intake gas flow results in less heat pickup in the intake suction stream. This results in more dense gas into compression chamber, which allows compressor 20 to provide more capacity out of a smaller mechanism.
[0018] Further, the separation of the discharge valve 38 from the inlet valve 33 maximizes the discharge volumetric geometry, allowing reduced pressure drops and improved fluid flow. This can be accomplished whether the gas is brought in through a valve on a face of the piston or through a valve in the bore (a side of the compression chamber) that is exposed when the piston retreats during the suction stroke. For example, Figure 6 shows a compression chamber with an inlet valve 33 on a lower side surface of the compression chamber. When the piston 35 retreats for a suction stroke, the valve 33 is exposed to the compression chamber. This again allows a maximizing of the distance between the intake and discharge valves, maximizing the discharge volumetric geometry.
[0019] By maximizing the discharge volumetric geometry, the size of the discharge valve can be made significantly larger. A larger discharge valve doesn't need to open as much to allow the compressed fluid out of the compression chamber. This improves valve timing and reduces backflow into compression chamber, further improving performance.
[0020] The disclosed configuration also eliminates the need for any discharge mufflers, internal high pressure exhaust tubes, mechanical mounting springs or mounts, cylinder heads, and valve plates. The elimination of all of these parts also reduces manufacturing costs and maintenance. In particular, the volume in housing 34 of the
discharge chamber of compressor 20 becomes a discharge muffler chamber. This eliminates the need for a separate part for a discharge muffler.
[0021] Figure 2 also shows high pressure relief valve 85. This valve is designed to vent the high pressure from the discharge side if that pressure exceeds a critical value. This prevents catastrophic failure of the compressor housing. Figure 2 also shows seal point 90, onto which an o-ring (not shown) is mounted. This seal prevents high pressure compressed fluid from leaking back into the intake side.
[0022] In comparison to a scroll compressor, the present invention includes far fewer possible leakage paths. Thus, the present invention can perform at much higher compression ratios than a scroll compressor, such as greater than a 10: 1 compression ratio. Thus allows for usage in such applications as medium and low temperature refrigeration, high ambient temperature air conditioning, and more severe heat pump conditions.
[0023] Compressor 20 also includes lower bearing 70 and upper bearing 80. These bearings allow for a smaller sized motor, which results in greater efficiently and lower cost.
[0024] As shown in Figure 1, motor 26 is in direct contact with the inner surface of housing 21. This allows heat generated by motor 26 to more efficiently escape the compressor 20. For example, Figure 7 shows a close up of the contact between the motor laminate layers 52 and the housing 21. (Although the housing has a circular cross-section, the housing is shown in this view as having straight sides due to the small scale.) Each stator laminate layer 52 has a thickness of approximately 0.020 in. Each stator laminate layer 52 may then line up with a corresponding heat dissipation fin 23 on an outer surface of housing 21 to promote heat transfer from the laminate layer 52, through housing 21, and out
corresponding fin 23. Fin 23 is shown with a triangular cross-section, but any shape or configuration suitable for heat dissipation is possible. These modifications are within the scope of the invention as claimed.
[0025] Moreover, this direct connection to the outer housing means that the compressor can be deployed in varying configurations, such as standing up or on its side. Figure 5 shows a horizontal configuration of the present invention. The only changes needed to place the compressor horizontally is the feet need to be moved to support the compressor. Also, the compressor 20 is not completely horizontal, but at approximately 5-10 degrees from horizontal to ensure oil 60 can continue to be drawn into the bottom of lower bearing 70.
[0026] Further, as shown in Figure 1, the outer housing is cylindrical. In contrast, conventional compressor housings have an oval horizontal cross-section. The cylindrical outer housing of the present invention has several advantages. First, the circular cross- section is stronger, and thus higher pressure operation is possible, allowing higher compression ratios and higher performance. Further, the cylindrical shape creates a smaller oil sump volume 60 that must be filled with oil. Reducing the amount of oil needed saves costs throughout the lifetime of the compressor. Additionally, oval cross-sections may vibrate during operation of the compressor. This creates added noise that is not generated by the circular cross-section.
[0027] Figure 3 shows an alternative embodiment which include 4 pistons 135, each of which proceed through the compression cycle simultaneously. Springs 137 are located in the compression chambers at an outer end to push the pistons 13S back when cam 139 moves to remove the force on piston 135. Cam 139 rotates on shaft 128, which is turned by a motor as in the first embodiment. Thus, the forces on the pistons that could cause
vibrations in fact cancel out to eliminate bearing toad and perfectly balance the mechanism. This reduces noise, vibration, and power usage. Further, either or both of the modifications may be used within the scope of the invention as claimed. 'Chat is, 2 piston unsynchronized, 4 piston unsynchronized, 2 piston synchronized, and 4 piston synchronized are ail within the scope of the invention as claimed.
[0028] In this regard, Figure 5 shows a piston assembly for a 4 piston unsynchronized configuration. This piston assembly includes a connection portion 30A that extends above the piston surfaces to allow for a perpendicular piston assembly to reciprocate below the portion 30A as the shaft rotates. Thus, 4 pistons can run in an unsynchronized manner to compress fluid.
[0029] A worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.
Claims
1. A fluid compressor comprising:
a housing;
a compression chamber within the housing;
a motor;
a shaft that is rotated by the motor, and
a piston assembly including at least two pistons directly connected to each other without any connecting rods, the piston assembly performing a reciprocating motion when acted on by the shaft such that the at least two pistons move within the compression chamber to compress a fluid.
2. The fluid compressor as set forth in claim 1, wherein the piston assembly includes 2 pistons.
3. The fluid compressor as set forth in claim 1, wherein the piston assembly includes 4 pistons.
4. The fluid compressor as set forth in claim 3, wherein each of the 4 pistons moves through a compression cycle simultaneously.
5. The fluid compressor as set forth in claim 1, wherein the motor is fixed directly to an inner surface of the outer housing.
6. The fluid compressor as set forth in claim 1, wherein fluid enters the compression chamber through a first surface of the compression chamber and exits the compression chamber through a second surface of the compression chamber that is an opposite surface from the first surface.
7. The fluid compressor as set forth in claim 6, wherein the first surface is a surface of the at least one piston.
8. The fluid compressor as set forth in claim 1, wherein fluid enters the compression chamber through a first surface of the compression chamber and exits the compression chamber through a second surface of the compression chamber that different from the first surface.
9. The fluid compressor as set forth in claim 8, wherein the first surface is a bottom surface of the compression chamber.
10. The fluid compressor as set forth in claim 1 , further comprising:
a plurality of heat dissipation fins on an outer surface of the housing.
11. The fluid compressor as set forth in claim 10, wherein each of the plurality of heat dissipation fins corresponds to a layer of stator laminate of the motor within the housing.
12. The fluid compressor as set forth in claim 1, wherein a discharge volume muffles noise created within the compressor.
13. The fluid compressor as set forth in claim 1 , further comprising:
an oil sump within a lower bearing that supports the shaft.
14. The fluid compressor as set forth in claim 13, wherein the oil sump has a slanted surface having an angle of approximately 2S-3S degrees with a horizontal.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201762445218P | 2017-01-11 | 2017-01-11 | |
US62/445,218 | 2017-01-11 | ||
US15/868,355 | 2018-01-11 | ||
US15/868,355 US20180195503A1 (en) | 2017-01-11 | 2018-01-11 | Fluid compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2018132591A1 true WO2018132591A1 (en) | 2018-07-19 |
Family
ID=62782838
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2018/013349 WO2018132591A1 (en) | 2017-01-11 | 2018-01-11 | Fluid compressor |
Country Status (2)
Country | Link |
---|---|
US (1) | US20180195503A1 (en) |
WO (1) | WO2018132591A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7226194B2 (en) | 2019-08-30 | 2023-02-21 | 株式会社豊田自動織機 | electric compressor |
CN117307440B (en) * | 2023-11-29 | 2024-01-30 | 沈阳海龟医疗科技有限公司 | Frequency conversion level middle oil-free vacuum compressor |
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US3784331A (en) * | 1972-05-18 | 1974-01-08 | Gen Motors Corp | Radial compressor with two-piece cylinder housing and shell |
US4352640A (en) * | 1979-02-24 | 1982-10-05 | Honda Giken Kogyo Kabushiki Kaisha | Fluid compressor |
US4373876A (en) * | 1980-03-21 | 1983-02-15 | Musashi Seimitsu Kogyo Kabushiki Kaisha | Double-acting piston compressor |
US4400144A (en) * | 1981-10-03 | 1983-08-23 | Trw, Inc. | Air compressor |
US4486157A (en) * | 1981-12-16 | 1984-12-04 | Nissan Motor Company, Limited | Reciprocating compressor |
US4492127A (en) * | 1982-10-29 | 1985-01-08 | Carrier Corporation | Motor-compressor unit |
US4834632A (en) * | 1988-01-25 | 1989-05-30 | Tecumseh Products Company | Compressor valve system |
US6139295A (en) * | 1998-06-22 | 2000-10-31 | Tecumseh Products Company | Bearing lubrication system for a scroll compressor |
US20060177336A1 (en) * | 2005-02-04 | 2006-08-10 | Lg Electronics Inc. | Dual-piston valve for orbiting vane compressors |
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US1130349A (en) * | 1912-05-11 | 1915-03-02 | Templeton Mfg Company | Steam-trap. |
US1747457A (en) * | 1927-02-07 | 1930-02-18 | Rhoda S Dunlap | Compressor |
US2130349A (en) * | 1932-09-30 | 1938-09-20 | Gen Motors Corp | Motor-compressor unit for refrigeration |
US2323068A (en) * | 1941-03-29 | 1943-06-29 | Maniscalco Pictro | Compressor |
US2417197A (en) * | 1943-08-21 | 1947-03-11 | Westinghouse Air Brake Co | Air compressor apparatus |
US3800675A (en) * | 1972-04-17 | 1974-04-02 | Gen Motors Corp | Unitary piston-suction valve assembly |
US4072210A (en) * | 1976-01-19 | 1978-02-07 | Chien Chao C | Compressor |
US5476371A (en) * | 1994-06-08 | 1995-12-19 | Tecumseh Products Company | Compressor suction valve of toroidal shape with a radial finger |
DE19501220A1 (en) * | 1995-01-17 | 1996-07-18 | Knorr Bremse Systeme | compressor |
US7258086B2 (en) * | 2005-02-24 | 2007-08-21 | John William Fitzgerald | Four-cylinder, four-cycle, free piston, premixed charge compression ignition, internal combustion reciprocating piston engine with a variable piston stroke |
WO2017015456A1 (en) * | 2015-07-22 | 2017-01-26 | Trane International Inc. | Compressor bearing housing drain |
US10215166B2 (en) * | 2016-12-29 | 2019-02-26 | Stuart H. Bassine | Medical air compressor |
-
2018
- 2018-01-11 US US15/868,355 patent/US20180195503A1/en not_active Abandoned
- 2018-01-11 WO PCT/US2018/013349 patent/WO2018132591A1/en active Application Filing
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3784331A (en) * | 1972-05-18 | 1974-01-08 | Gen Motors Corp | Radial compressor with two-piece cylinder housing and shell |
US4352640A (en) * | 1979-02-24 | 1982-10-05 | Honda Giken Kogyo Kabushiki Kaisha | Fluid compressor |
US4373876A (en) * | 1980-03-21 | 1983-02-15 | Musashi Seimitsu Kogyo Kabushiki Kaisha | Double-acting piston compressor |
US4400144A (en) * | 1981-10-03 | 1983-08-23 | Trw, Inc. | Air compressor |
US4486157A (en) * | 1981-12-16 | 1984-12-04 | Nissan Motor Company, Limited | Reciprocating compressor |
US4492127A (en) * | 1982-10-29 | 1985-01-08 | Carrier Corporation | Motor-compressor unit |
US4834632A (en) * | 1988-01-25 | 1989-05-30 | Tecumseh Products Company | Compressor valve system |
US6139295A (en) * | 1998-06-22 | 2000-10-31 | Tecumseh Products Company | Bearing lubrication system for a scroll compressor |
US20060177336A1 (en) * | 2005-02-04 | 2006-08-10 | Lg Electronics Inc. | Dual-piston valve for orbiting vane compressors |
Also Published As
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US20180195503A1 (en) | 2018-07-12 |
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