EP1930591A2 - Kompressor mit einem Mechanismus zur Trennung und Wiedergewinnung von Schmieröl - Google Patents

Kompressor mit einem Mechanismus zur Trennung und Wiedergewinnung von Schmieröl Download PDF

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Publication number
EP1930591A2
EP1930591A2 EP07121736A EP07121736A EP1930591A2 EP 1930591 A2 EP1930591 A2 EP 1930591A2 EP 07121736 A EP07121736 A EP 07121736A EP 07121736 A EP07121736 A EP 07121736A EP 1930591 A2 EP1930591 A2 EP 1930591A2
Authority
EP
European Patent Office
Prior art keywords
oil
chamber
compressor
pressure sensing
spool
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.)
Withdrawn
Application number
EP07121736A
Other languages
English (en)
French (fr)
Inventor
Yoshinori Inoue
Hiroyuki Nakaima
Akinobu Kanai
Naoki Koeda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1930591A2 publication Critical patent/EP1930591A2/de
Withdrawn legal-status Critical Current

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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
    • 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
    • F04B39/16—Filtration; Moisture separation
    • 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
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/109—Lubrication
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves

Definitions

  • the present invention relates to a compressor used in an air conditioner for a vehicle, and more specifically to a compressor having a mechanism for separating lubrication oil from compressed refrigerant gas and recovering the lubrication oil.
  • lubrication oil is mixed in the form of mist in refrigerant gas and lubricates movable sliding parts.
  • the lubrication oil mixed in the refrigerant gas flows out of the compressor together with the refrigerant gas and circulates in the external refrigerant circuit, the oil adheres to an inner wall of an evaporator and the like, and deteriorates the heat exchange efficiency.
  • an oil separator is formed outside a compressor and is located in the high-pressure piping connecting the compressor to a condenser.
  • the separated lubrication oil is recovered into the compressor through an oil recovery passage.
  • the oil separator outside of the compressor is utilized, however, the construction of the whole refrigerant circuit becomes congested with equipments and additional piping. Furthermore, the oil recovery passage is elongated and has a small diameter so that problems such as clogging may occur. Therefore, an oil separator formed inside a compressor has been offered recently.
  • the lubrication oil is separated in the oil separation mechanism and is supplied from the oil separation mechanism to a low pressure region through an oil supply passage.
  • the compressor is stopped, all the stored oil flows out to the low pressure region through the oil supply passage. Therefore, when the compressor restarts, highly-pressurized refrigerant gas may flow reversely through the oil supply passage, and the lubrication oil stored in the low pressure region may be compressed in liquid state.
  • Unexamined Japanese Patent Publication No. 05-240158 discloses a compressor which includes an oil separation chamber, a primary oil storage chamber, a main oil storage chamber, an oil recovery hole, and a valve means.
  • the oil separation chamber is formed in a high pressure region inside the compressor.
  • the primary oil storage chamber for recovering lubrication oil is located below the oil separation chamber.
  • the main oil storage chamber is connected to the primary oil storage chamber via a hole.
  • the hole extends upward from a bottom portion of the primary oil storage chamber to the main oil storage chamber.
  • the lubrication oil in the primary oil storage chamber flows upward through the hole and drops downward in the main storage chamber.
  • the oil recovery hole is opened in a valve seat surface formed at the bottom of the main oil storage chamber and connects the main oil storage chamber to the low pressure region inside the compressor.
  • the valve means adjusts the flow rate of the lubrication oil to be recovered in accordance with the pressure differential between the high pressure region and the low pressure region.
  • the valve means adjusts the flow rate of the lubrication oil to be gradually decreased.
  • the valve means ensures an optimal amount of the lubrication oil based on the balance between the amount of the separated lubrication oil and the required amount of the lubrication oil to be recovered.
  • the move of the separated lubrication oil between the primary oil storage chamber and the main oil storagae chamber is stopped at the time when the pressure differential is balanced to the force due to the weight of the lubrication oil which is in the hole.
  • the optimal amount of the lubrication oil is stored in the primary oil storage chamber.
  • the opening degree of the oil recovery hole is fully opened and the amount of the separated lubrication oil is small in comparison to the amount of the recovered lubrication oil. Accordingly, all the stored oil flows out to the low pressure region.
  • the refrigerant gas may flow reversely and the lubrication oil may be compressed in liquid state.
  • the structure of the valve means is complicated, thereby needs many assembling processes and accuracy in manufacturing.
  • a compressor has an outlet, a discharge passage, an oil separation mechanism, an oil supply passage, and a valve mechanism.
  • the outlet discharges refrigerant gas out from the compressor.
  • the discharge passage is connected to the outlet, and the refrigerant gas is discharged through the discharge passage and the outlet from the compressor.
  • the oil separation mechanism separates lubrication oil from the refrigerant gas.
  • the oil supply passage supplies the separated lubrication oil into an oil recovery region.
  • the valve mechanism is formed in the oil supply passage and includes a valve chamber, a spool and an urging member. The spool separates the valve chamber into a first pressure sensing chamber and a second pressure sensing chamber.
  • the amount of the lubrication oil supplied to the oil recovery region is adjusted in such a manner that as the pressure differential between the first pressure sensing chamber and the second pressure sensing chamber increases, the spool slides in the valve chamber and the opening degree of the oil supply passage increases to the maximum and then decreases, and that when the compressor is stopped, the opening degree of the oil supply passage is minimized by the urging force of the urging member.
  • variable displacement swash plate compressor 10 (hereinafter referred to as a "compressor") according to the present invention will now be described with reference to FIGS. 1 through 5 .
  • the compressor 10 includes a cylinder block 11, a front housing 12 and a rear housing 14.
  • the left-hand side of the compressor 10 corresponds to the front side and the right-hand side of the compressor 10 corresponds to the rear side as viewed in Fig. 1 .
  • the front housing 12 is connected to the front end of the cylinder block 11.
  • the rear housing 14 is connected to the rear end of the cylinder block 11 through a valve port plate assembly 13.
  • the cylinder block 11, the front housing 12 and the rear housing 14 cooperate to form a housing of the compressor 10.
  • a crank chamber 15 is defined by the cylinder block 11 and the front housing 12.
  • a drive shaft 16 is rotatably disposed in the crank chamber 15. The front end portion of the drive shaft 16 protrudes from the crank chamber 15 and is coupled to a vehicle engine (not shown) to receive driving force so that the drive shaft 16 is rotated.
  • a lug plate 17 is disposed in the crank chamber 15 and fixed to the drive shaft 16 for rotation therewith.
  • a swash plate 18 is disposed in the crank chamber 15.
  • the swash plate 18 is supported by the drive shaft 16 so as to be slidable in the axial direction of the drive shaft 16 and also inclinable relative to the axis of the drive shaft 16.
  • the swash plate 18 is connected to the lug plate 17 via a hinge mechanism 19.
  • the hinge mechanism 19 is provided between the lug plate 17 and the swash plate 18. Through the hinge mechanism 19 the swash plate 18 is synchronously rotatable with the lug plate 17 and the drive shaft 16 and inclinable relative to the axial direction of the drive shaft 16 with sliding on the drive shaft 16.
  • the inclination angle of the swash plate 18 is adjusted by a control valve 20.
  • a plurality of cylinder bores 21 are formed in the cylinder block 11 for accommodating a reciprocable single-headed piston 22 respectively.
  • a compression chamber 23 is defined by the piston 22 and the valve port plate assembly 13.
  • Each piston 22 is engaged with the outer periphery of the swash plate 18 through a pair of shoes 24.
  • the rotation of the swash plate 18 in accordance with the rotation of the drive shaft 16 is converted to the reciprocation of the pistons 22 through the pair of shoes 24 so that each piston 22 reciprocates in the respective cylinder bore 21.
  • a suction chamber 25 is defined in the rear housing 14 at the center thereof, and a discharge chamber 26 is defined around the suction chamber 25 in the rear housing 14.
  • Suction ports 27 and suction valves 28 are formed in the valve port plate assembly 13.
  • Discharge ports 29 and discharge valves 30 are formed in the valve port plate assembly 13.
  • Refrigerant gas in the suction chamber 25 is introduced into the compression chamber 23 through the respective suction port 27 by pushing away the respective suction valve 28 as the piston 22 moves from its top dead center position to its bottom dead center position.
  • the refrigerant gas is compressed in the compression chamber 23 to a predetermined pressure level, and is discharged into the discharge chamber 26 through the discharge port 29 while pushing away the discharge valve 30 as the piston 28 moves from its bottom dead center position to its top dead center position.
  • the rear housing 14 has an inlet 31 and an outlet 32.
  • the inlet 31 is connected to an external refrigerant circuit (not shown) and the refrigerant gas is introduced into the suction chamber 25 through the inlet 31.
  • the outlet 32 is connected to the external refrigerant circuit.
  • a discharge passage 33 is formed to connect the outlet 32 and the discharge chamber 26.
  • the refrigerant gas in the discharge chamber 26 is discharged out from the compressor 10 through the discharge passage 33 and the outlet 32.
  • An oil separation mechanism is formed in the discharge passage 33.
  • the oil separation mechanism includes an oil separation chamber 34 and an oil separation cylinder 35.
  • the oil separation chamber 34 is formed with a cylindrical shape with a bottom surface at the rear end thereof.
  • the oil separation cylinder 35 is received in the oil separation chamber 34.
  • a valve mechanism is integrally formed with the oil separation mechanism. As shown in FIG. 1 , the valve mechanism is formed adjacent to the oil separation mechanism so that the front end of the oil separation mechanism is shared by the rear end of the valve mechanism.
  • the valve mechanism includes a valve chamber 36, a spool 38, and a spring 39 as an urging member.
  • the valve chamber 36 is formed in the rear housing 14 and has a cylindrical shape with a bottom surface. The diameter of the valve chamber 36 is greater than that of the oil separation chamber 34.
  • the spool 38 separates the valve chamber 36 into a first pressure sensing chamber S1 and a second pressure sensing chamber S2.
  • the first pressure sensing chamber S1 is in communication with the discharge chamber 26 and the discharge passage 33 as a high pressure region through the oil separation chamber 34.
  • the second pressure sensing chamber S2 is in communication with the suction chamber 25 as a low pressure region through a pressure introduction passage 37.
  • the spring 39 is disposed in the second pressure sensing chamber S2 and urges the spool 38 in the direction toward the rear end of the valve mechanism, or toward the oil separation mechanism.
  • an oil introduction hole 40 is formed so as to face a circumferential surface of the valve chamber 36.
  • An oil passage 41 supplies the lubrication oil to the suction chamber 25, and is formed in such a manner that one end of the oil passage 41 opens to the suction chamber 25 and the other end of the oil passage 41 opens to the circumferential surface of the valve chamber 36.
  • an oil supply passage includes the oil separation chamber 34, the valve chamber 36, the oil introduction hole 40, and the oil passage 41.
  • the valve mechanism is formed in the oil supply passage to adjust the opening degree of the oil supply passage.
  • the compressor 10 of the first embodiment As the drive shaft 16 is rotated, the swash plate 18 is rotated therewith and the piston 22 engaged with the swash plate 18 reciprocates in the cylinder bore 21, accordingly.
  • the piston 22 As the piston 22 reciprocates, the refrigerant gas is introduced into the compression chamber 23 from the suction chamber 25, and is compressed in the compression chamber 23, and then discharged to the discharge chamber 26.
  • the highly-pressurized refrigerant gas is introduced into the oil separation chamber 34 from the discharge chamber 26 through the discharge passage 33.
  • the refrigerant gas introduced into the oil separation chamber 34 flows through the opening of the oil separation cylinder 35 to the inside of the oil separation cylinder 35 while swirling along the inner cylindrical wall of the oil separation chamber 34.
  • the refrigerant gas is sent to the external refrigerant circuit (not shown) through the outlet 32.
  • the oil mixed in the refrigerant gas is separated from the refrigerant gas by the centrifugal force generated by the swirling flow.
  • the opening degree of the oil supply passage is minimum.
  • pressure differential is generated between the pressure in the first pressure sensing chamber S1 which acts on the rear side of the spool 38 and the pressure in the second pressure sensing chamber S2 which acts on the front side of the spool 38.
  • the pressure in the first pressure sensing chamber S1 is based on the refrigerant gas introduced from the discharge chamber 26 through the discharge passage 33.
  • the pressure in the second pressure sensing chamber S2 is based on the refrigerant gas introduced from the suction chamber 25 through the pressure introduction passage 37.
  • the pressure differential between the first pressure sensing chamber S1 and the second pressure sensing chamber S2 that is, the pressure differential which acts on the spool 38, overcomes the urging force of the spring 39, and the spool 38 slides frontward, or in the direction away from the oil separation mechanism to some extent in such a manner that the volume of the second pressure sensing chamber S2 is decreased and the oil introduction hole 40 begins to overlap with the opening end of the oil passage 41.
  • the opening degree of the oil supply passage increases to the maximum.
  • the oil separation chamber 34 is in communication with the oil passage 41 through the oil introduction hole 40.
  • the lubrication oil separated in the oil separation chamber 34 is temporarily stored in the oil separation chamber 34, and introduced into the oil passage 41 through the oil introduction hole 40. Then the lubrication oil is recovered to the suction chamber 25.
  • the pressure differential which acts on the spool 38 increases, the amount of the lubrication oil supplied to the suction chamber 25 increases until the opening degree of the oil supply passage increases to the maximum. Then, the spool 38 slides further, and the oil introduction hole 40 begins to pass through the opening end of the oil passage 41.
  • the opening degree of the oil supply passage becomes decreasing. As a result, small amount of the lubrication oil is recovered to such an extent that the lubrication oil in the oil separation chamber 34 does not flow out completely. Thereby, the circulation of lubrication oil in the compressor 10 is maintained.
  • the pressure in the first pressure sensing chamber S1 decreases to substantially the same level as the pressure in the second pressure sensing chamber S2.
  • the urging force of the spring 39 overcomes the pressure differential which acts on the spool 38 so that the spool 38 is pushed rearward, or in the direction toward the oil separation mechanism to make contact with the rear end surface of the first pressure sensing chamber S1.
  • the opening end of the oil passage 41 is closed by the spool 38, and the communication between the valve chamber 36 and the oil passage 41 is shut. In other words, the opening degree of the oil supply passage is minimized by the urging force of the spring 39.
  • the oil separation chamber 34 and the valve chamber 36 are integrally formed.
  • the oil separation chamber 34 and the valve chamber 36 may be formed separately and an oil storage chamber 45 is formed therebetween, as shown in FIG. 12 .
  • the separated lubrication oil may be supplied to the second pressure sensing chamber S2, instead of supplying to the first pressure chamber S1.
  • the oil introduction hole 40 may be formed in the side of the second pressure sensing chamber S2 so as to face the second pressure sensing chamber S2.
  • the oil passage 41 may be formed in the side of the first pressure sensing chamber S1 so as to face the first pessure sensing chamber S1.
  • the spring 39 is disposed in the valve chamber 36 to urge the spool 38 in the direction toward the end surface of the valve chamber 36.
  • the spool 38 and an end surface of the valve chamber 36 may be connected by a bellows.
  • the bellows may be disposed in the first pressure sensing chamber S1, and not in the second pressure sensing chamber S2.
  • the oil passage 41 is connected to the suction chamber 25 as an oil recovery region where the separated lubrication oil is supplied.
  • the oil passage 41 may be connected to the crank chamber 15.
  • a compressor has a discharge passage, an oil separation mechanism, an oil supply passage, and a valve mechanism.
  • the oil supply passage supplies the separated lubrication oil into an oil recovery region.
  • the valve mechanism is formed in the oil supply passage and includes a valve chamber, a spool and an urging member. The spool separates the valve chamber into a first pressure sensing chamber and a second pressure sensing chamber.
  • the amount of the lubrication oil supplied to the oil recovery region is adjusted in such a manner that as the pressure differential between the first and the second pressure sensing chambers increases, the spool slides in the valve chamber and the opening degree of the oil supply passage increases to the maximum and then decreases, and that when the compressor is stopped, the opening degree of the oil supply passage is minimized by the urging force of the urging member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP07121736A 2006-11-29 2007-11-28 Kompressor mit einem Mechanismus zur Trennung und Wiedergewinnung von Schmieröl Withdrawn EP1930591A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006322384A JP2008133810A (ja) 2006-11-29 2006-11-29 圧縮機

Publications (1)

Publication Number Publication Date
EP1930591A2 true EP1930591A2 (de) 2008-06-11

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Family Applications (1)

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EP07121736A Withdrawn EP1930591A2 (de) 2006-11-29 2007-11-28 Kompressor mit einem Mechanismus zur Trennung und Wiedergewinnung von Schmieröl

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US (1) US20080120991A1 (de)
EP (1) EP1930591A2 (de)
JP (1) JP2008133810A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104024638A (zh) * 2011-12-16 2014-09-03 法雷奥日本株式会社 压缩机
CN104271011A (zh) * 2012-02-09 2015-01-07 库里格绿山股份有限公司 具有膨胀室的液体输送箱
CN104271011B (zh) * 2012-02-09 2016-11-30 库里格绿山股份有限公司 具有膨胀室的液体输送箱

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8128737B2 (en) * 2008-01-07 2012-03-06 Lummus Technology Inc. Absorbing PAHs from gas streams
JP2010285898A (ja) * 2009-06-10 2010-12-24 Valeo Thermal Systems Japan Corp 可変容量型圧縮機
JP5413851B2 (ja) * 2010-12-24 2014-02-12 サンデン株式会社 冷媒圧縮機

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4487562A (en) * 1981-03-23 1984-12-11 Nippon Soken, Inc. Rotary vane type compressor
US5577894A (en) * 1993-11-05 1996-11-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type variable displacement compressor
JPH09324758A (ja) * 1996-06-06 1997-12-16 Toyota Autom Loom Works Ltd カムプレート式圧縮機
US6019350A (en) * 1997-03-05 2000-02-01 Gelbfish; Gary A. Hand held control device and associated method
US5979168A (en) * 1997-07-15 1999-11-09 American Standard Inc. Single-source gas actuation for screw compressor slide valve assembly
JP2000080983A (ja) * 1998-07-09 2000-03-21 Toyota Autom Loom Works Ltd 圧縮機
JP2000346241A (ja) * 1999-06-07 2000-12-15 Toyota Autom Loom Works Ltd 逆止弁
JP3864673B2 (ja) * 2000-06-27 2007-01-10 株式会社豊田自動織機 圧縮機
US6467287B2 (en) * 2000-08-15 2002-10-22 Thermo King Corporation Valve arrangement for a compressor
JP3726759B2 (ja) * 2002-02-18 2005-12-14 株式会社豊田自動織機 容量可変型圧縮機の制御装置
JP4211477B2 (ja) * 2003-05-08 2009-01-21 株式会社豊田自動織機 冷媒圧縮機のオイル分離構造

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104024638A (zh) * 2011-12-16 2014-09-03 法雷奥日本株式会社 压缩机
CN104271011A (zh) * 2012-02-09 2015-01-07 库里格绿山股份有限公司 具有膨胀室的液体输送箱
CN104271011B (zh) * 2012-02-09 2016-11-30 库里格绿山股份有限公司 具有膨胀室的液体输送箱

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Publication number Publication date
US20080120991A1 (en) 2008-05-29
JP2008133810A (ja) 2008-06-12

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