EP1712791A2 - Compresseur à plateau en biais - Google Patents

Compresseur à plateau en biais Download PDF

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Publication number
EP1712791A2
EP1712791A2 EP06112256A EP06112256A EP1712791A2 EP 1712791 A2 EP1712791 A2 EP 1712791A2 EP 06112256 A EP06112256 A EP 06112256A EP 06112256 A EP06112256 A EP 06112256A EP 1712791 A2 EP1712791 A2 EP 1712791A2
Authority
EP
European Patent Office
Prior art keywords
rotary shaft
oil
plate assembly
pressure region
supply passage
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Withdrawn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
EP06112256A
Other languages
German (de)
English (en)
Inventor
Yoshinori Inoue
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 EP1712791A2 publication Critical patent/EP1712791A2/fr
Withdrawn legal-status Critical Current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
    • 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
    • A—HUMAN NECESSITIES
    • A46—BRUSHWARE
    • A46B—BRUSHES
    • A46B15/00—Other brushes; Brushes with additional arrangements
    • A46B15/0055—Brushes combined with other articles normally separate from the brushing process, e.g. combs, razors, mirrors
    • A46B15/0075—Brushes with an additional massage device
    • A—HUMAN NECESSITIES
    • A46—BRUSHWARE
    • A46B—BRUSHES
    • A46B9/00—Arrangements of the bristles in the brush body
    • A46B9/06—Arrangement of mixed bristles or tufts of bristles, e.g. wire, fibre, rubber
    • 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
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members
    • A—HUMAN NECESSITIES
    • A46—BRUSHWARE
    • A46B—BRUSHES
    • A46B2200/00—Brushes characterized by their functions, uses or applications
    • A46B2200/10—For human or animal care
    • A46B2200/1066—Toothbrush for cleaning the teeth or dentures

Definitions

  • the present invention relates to a piston type compressor having an oil separator for separating lubricating oil from discharged refrigerant gas.
  • a piston type compressor for a vehicle air conditioner lubricating oil in the form of mist is mixed with refrigerant gas for flowing therewith within the compressor thereby to lubricate inner parts of the compressor.
  • the oil is contained in the discharged refrigerant gas.
  • an oil separator is provided in a discharge-pressure region within the compressor for separating oil from the refrigerant gas. This is because the oil flowing with the refrigerant gas into the external refrigerant circuit tends to adhere to an inner wall surface of a heat exchanger in the external refrigerant circuit thereby to deteriorate the heat exchanging efficiency of the heat exchanger.
  • a typical piston type compressor having an oil separator is disclosed, for example, in Japanese Patent Application Publication No. 2004-218601 .
  • the piston type compressor has such a structure in which oil separated from refrigerant gas by the oil separator returns into the compressor (specifically, returns into a compression chamber) in order to keep efficient lubrication of inner parts of the compressor.
  • the oil separator and the interior of the compressor are in communication through an oil return passage.
  • the oil return passage connects the oil separator with the compression chamber, so that there is a pressure differential between the oil separator and the compression chamber when the oil return passage connects the compression chamber that has just completed the suction stroke (namely, a suction-pressure region) with the oil separator (namely, a discharge-pressure region).
  • the oil return passage should be formed with an extremely small cross-sectional area or the oil return passage should have a throttle portion therein to provide a throttle function in the oil return passage, thereby preventing the refrigerant gas from flowing back.
  • the present invention is directed to a piston type compressor that prevents the leakage of refrigerant gas from a discharge-pressure region to a suction-pressure region of the compressor and effectively returns lubricating oil to the suction-pressure region of the compressor.
  • a piston type compressor comprises a housing, a rotary shaft supported by the housing, a cam mounted on the rotary shaft.
  • the housing is formed with a cylinder bore in which a piston is accommodated and a cam chamber in which the cam is accommodated.
  • the housing is further provided with a discharge-pressure region and a suction-pressure region therein.
  • the compressor further comprises an oil separator provided in the discharge-pressure region and an oil reservoir for storing lubricating oil from the oil separator.
  • the rotary shaft is provided with a regulating means for regulating the axial movement of the rotary shaft and for forming a clearance between the regulating means and the valve plate assembly.
  • the clearance is communicated with the oil reservoir through a communication hole formed in the valve plate assembly so that the clearance functions as a throttle in an oil return passage extending from the oil separator to the inside of the compressor.
  • the rotary shaft may be provided with a rotary valve.
  • a supply passage as a suction passage is formed in the rotary valve and in communication with the cam chamber in which a suction port is provided to be connected to an evaporator in an external refrigerant circuit.
  • the piston type compressor 10 includes a front housing 12 and a rear housing 13 connected to the rear end of the front housing 12.
  • a cylinder block 11 is fixedly connected inside the front housing 12.
  • a valve plate assembly 14 is interposed between the cylinder block 11 and the rear housing 13.
  • the cylinder block 11, the rear housing 13 and the valve plate assembly 14 are fastened together by a plurality of bolts B (only one bolt B shown in FIG. 1).
  • the front housing 12 and the rear housing 13 cooperate to form the housing assembly of the compressor 10.
  • the housing assembly has a discharge chamber 18 formed between the rear housing 13 and the valve plate assembly 14 on the radially outer side in the rear housing 13.
  • the rear housing 13 is provided with an oil separator S for separating lubricating oil contained in refrigerant gas.
  • the oil separator S is in fluid communication with the discharge chamber 18 through a communication port 18a. Hence, the oil separator S is located in a discharge-pressure region of the compressor 10.
  • the oil separator S includes an oil separation chamber 44 and an oil separation cylinder 45 accommodated in the oil separation chamber 44.
  • the oil separation chamber 44 is in communication with the discharge chamber 18 through the communication port 18a.
  • the communication port 18a is opened to the oil separation chamber 44 at a position which faces the outer peripheral surface of the oil separation cylinder 45.
  • the oil separator S has a discharge hole 35 formed therein for allowing refrigerant gas from which lubricating oil has been separated to be discharged out from the compressor 10.
  • the discharge chamber 18 is in communication with an external refrigerant circuit 26 through the discharge hole 35.
  • the external refrigerant circuit 26 includes a condenser 27 for removing heat from refrigerant gas, an expansion valve 28 and an evaporator 29 for transferring ambient heat in vehicle compartment to refrigerant gas.
  • the discharge hole 35 is in communication with the condenser 27.
  • An oil reservoir T is formed at the center of the rear housing 13 between the rear housing 13 and the valve plate assembly 14.
  • the oil reservoir T and the oil separation chamber 44 of the oil separator S are in communication through an oil passage 32, through which lubricating oil separated from refrigerant gas in the oil separator S is carried into the oil reservoir T for storage therein.
  • the oil reservoir T is in communication with a shaft hole 20, or the like, at the center of the cylinder block 11 through a communication hole 46 formed in the valve plate assembly 14, so that the lubricating oil stored in the oil reservoir T flows back toward the cylinder block 11 through the communication hole 46.
  • the valve plate assembly 14 has discharge ports 14a and discharge valves 14b formed therein in association with the discharge chamber 18.
  • the discharge valves 14b are operable to open and close the respective discharge ports 14a.
  • the discharge chamber 18, the oil separation chamber 44, the discharge hole 35, the oil reservoir T and the compression chamber 34 in discharge stroke form the discharge-pressure region of the compressor 10.
  • a rotary shaft 19 is rotatably supported in the crank chamber 17 by the cylinder block 11 and the front housing 12.
  • the rotary shaft 19 is inserted at one end thereof into the shaft hole 20 formed in the cylinder block 11 and at the other end thereof into a shaft hole 21 formed in the front housing 12.
  • the shaft hole 20 is located in alignment with the oil reservoir T through the valve plate assembly 14, and the communication hole 46 adjacent to the cylinder block 11 is opened to the shaft hole 20.
  • the rotary shaft 19 is supported at its front side by the front housing 12 through a radial bearing 22 placed in the shaft hole 21.
  • the rotary shaft 19 is directly supported at its rear side by the cylinder block 11 through a peripheral sealing surface 20a formed on the inner peripheral surface of the shaft hole 20.
  • the communication hole 46 adjacent to the cylinder block 11 is opened to the rear end of the rotary shaft 19.
  • the radial bearing 22 and the peripheral sealing surface 20a of the shaft hole 20 receive radial loads on the front and rear sides of the rotary shaft 19, respectively.
  • a shaft seal 23 of a lip seal type is interposed between the front housing 12 and the rotary shaft 19.
  • a swash plate 24 which serves as a cam is secured on the rotary shaft 19 within the crank chamber 17.
  • the swash plate 24 has at its boss portion 24a an inserting hole 24b which is formed along the axis of the swash plate 24 (that is, along the axis L of the rotary shaft 19), and the rotary shaft 19 is press-fitted in the inserting hole 24b.
  • the crank chamber 17 is in communication with the evaporator 29 in the external refrigerant circuit 26 through a suction hole 25 formed in the front housing 12.
  • Refrigerant gas which is discharged into the discharge chamber 18 and the lubricating oil separated therefrom at the oil separator S, flows into the condenser 27 in the external refrigerant circuit 26 through a discharge hole 35 adjacent to the oil separator S.
  • refrigerant gas flows into the crank chamber 17 through the suction hole 25.
  • the shaft seal 23 prevents the leakage of refrigerant gas through a clearance between the peripheral surface of the rotary shaft 19 and the front housing 12.
  • a thrust bearing 30 is interposed between the front housing 12 and the boss portion 24a of the swash plate 24 for receiving an axial load (or thrust load) of the rotary shaft 19.
  • a plurality of cylinder bores 11a (five cylinder bores in this embodiment but only one being shown in FIG. 1) are formed in the cylinder block 11 around the rotary shaft 19.
  • Each of the cylinder bores 11a is closed by the valve plate assembly 14 and accommodates therein a reciprocally slidable single-headed piston 31.
  • Each piston 31 slidably engages with the periphery of the swash plate 24 through a pair of shoes 33a, 33b.
  • the rotation of the swash plate 24 with the rotary shaft 19 is converted into the reciprocal movement of the pistons 31 in the cylinder bore 11 a through the shoes 33a, 33b.
  • the pistons 31 are operatively associated with the rotation of the rotary shaft 19 through the swash plate 24 secured to the rotary shaft 19.
  • the pistons 31 and the valve plate assembly 14 define compression chambers 34 in the respective cylinder bores 11 a.
  • the shaft hole 20 of the cylinder block 11 surrounded by the cylinder bores 11a serves also as a valve chamber.
  • the shaft hole 20 and the compression chambers 34 (cylinder bores 11a) are in communication with each other through respective suction ports 36 formed in the cylinder block 11.
  • Each suction port 36 has an inlet 36a opened at the peripheral sealing surface 20a of the shaft hole 20 and an outlet 36b opened at the inner peripheral surface of the cylinder bore 11 a.
  • the rotary shaft 19 is rotatably received at the rear end thereof (or the side thereof adjacent to the valve plate assembly 14) in the shaft hole 20.
  • the rotary shaft 19 has a supply passage 41 extending axially from the thrust bearing 30 to the rear end of the rotary shaft 19.
  • An introducing hole 42 extends through the boss portion 24a of the swash plate 24 and the rotary shaft 19 for fluid communication between the supply passage 41 and the crank chamber 17. That is, the introducing hole 42 permits refrigerant gas in the crank chamber 17 to flow into the supply passage 41.
  • An introducing port 43 is formed in the rotary shaft 19 adjacent to the valve plate assembly 14 for communication with the supply passage 41.
  • the introducing port 43 has an inlet 43a which is opened at the inner peripheral surface of the rotary shaft 19 and an outlet 43b which is opened at the outer peripheral surface of the rotary shaft 19.
  • the outlet 43b of the introducing port 43 communicates intermittently with the inlet 36a of the suction port 36.
  • the supply passage 41, the introducing hole 42 and the introducing port 43 in the rotary shaft 19 are provided to introduce refrigerant gas from the crank chamber 17 into the compression chamber 34.
  • the rear portion of the rotary shaft 19 which is surrounded by the peripheral sealing surface 20a of the shaft hole 20 functions as a rotary valve 50 formed integrally with the rotary shaft 19 adjacent to the valve plate assembly 14.
  • the crank chamber 17, the shaft hole 20, the supply passage 41 and the compression chamber 34 in suction stroke form a suction-pressure region of the compressor 10.
  • the rotary valve 50 has an opening at its rear end.
  • a closure cap 51 which serves a closure means, is fitted to the rear end of the rotary valve 50 at a position that is closer to the valve plate assembly 14 than the introducing port 43.
  • This closure cap 51 includes a cylindrical and hollow cap portion 52 and a flange portion 53.
  • the flange portion 53 extends radially from the rear end periphery of the cap portion 52.
  • the flange portion 53 extends all around the cap portion 52.
  • the closure cap 51 is fitted in the rotary valve 50 by the portion 52 press-fitted into the supply passage 41.
  • the closure cap 51 is rotatable with the rotary valve 50. With the cap portion 52 fitted in the supply passage 41, the flange portion 53 covers the entire end face of the rotary valve 50 (or the rotary shaft 19).
  • the length of the cap portion 52 in the axial direction of the closure cap 51 is slightly shorter than the distance from the rear end of the rotary valve 50 to the introducing port 43. In other words, the introducing port 43 is not closed by the cap portion 52.
  • the diameter of the cap portion 52 is slightly greater than the inner diameter of the rotary valve 50 (that is, the inner diameter of the rotary shaft 19 or the diameter of the supply passage 41).
  • the cap portion 52 closes the supply passage 41 and is pressed against the peripheral surface of the supply passage 41 (or the inner peripheral surface of the rotary shaft 19) thereby to form a sealing surface 55.
  • the cap portion 52 seals to prevent the leakage of refrigerant gas through the rear end of the rotary valve 50 from the supply passage 41.
  • a clearance CL is formed between the valve plate assembly 14 and the end face 53a of the flange portion 53 adjacent to the valve plate assembly, as shown in FIG. 2. This clearance CL is provided to prevent sliding contact between the closure cap 51 and the valve plate assembly 14 during operation of the piston type compressor 10.
  • the closure cap 51 also functions as a regulating means for regulating the axial sliding movement of the rotary shaft 19 to a specified amount.
  • the rotary shaft 19 is movable slightly in its axial direction though this axial sliding movement of the rotary shaft 19 in forward direction is so regulated that the boss portion 24a of the swash plate 24 contacts with the thrust bearing 30.
  • the compressor 10 is stopped (e.g. when a clutch for transmitting power from a drive source to the rotary shaft 19 is just disengaged)
  • the compression reaction force that acts on the pistons 31 from the compression chambers 34 is decreased rapidly, so that the rotary shaft 19 tends to slide axially rearward.
  • such axial sliding movement of the rotary shaft 19 in a rearward direction is regulated by the end face 53a of the flange portion 53 of the closure cap 51 to be brought into contact with the valve plate assembly 14.
  • the clearance CL between the end face 53a and the valve plate assembly 14 may be adjusted.
  • the clearance CL should preferably be as small as possible to prevent the leakage of refrigerant gas.
  • the clearance CL is formed with a cross-sectional area smaller than the communication hole 46.
  • the communication hole 46 is formed in the valve plate assembly 14 for providing communication between the oil reservoir T and the clearance CL. That is, the communication hole 46 is opened at one end thereof to the oil reservoir T and at the other end to the clearance CL.
  • the clearance CL is in communication with the communication hole 46 and has a smaller cross-sectional area than the communication hole 46, so that it functions as a throttle to prevent the refrigerant gas from flowing back from the oil separator S through the oil passage 32, the oil reservoir T and the communication hole 46.
  • the end face 53a of the flange portion 53 and the inner surface 52a of the cap portion 52 cooperate to form a surface receiving back pressure from the oil reservoir T.
  • refrigerant gas discharged from the compression chamber 34 into the discharge chamber 18 then flows into the oil separator S through the communication port 18a.
  • Refrigerant gas introduced into the oil separation chamber 44 in the oil separator S is whirled in the space between the inner peripheral surface of the oil separation chamber 44 and the outer peripheral surface of the oil separations cylinder 45, and the lubricating oil contained in the refrigerant gas is separated therefrom under the influence of centrifugal force.
  • Refrigerant gas the lubricating oil is separated therefrom flows into the oil separation cylinder 45 through the bottom opening thereof and then flows out to the external refrigerant circuit 26 (specifically, to the condenser 27) through the discharge hole 35 formed at the top of the oil separation cylinder 45.
  • lubricating oil separated from refrigerant gas in the oil separation chamber 44 is conveyed to the oil reservoir T through the oil passage 32. Furthermore, lubricating oil stored in the oil reservoir T is supplied to the shaft hole 20 through the communication hole 46. In other words, lubricating oil separated from refrigerant gas returns to the shaft hole 20 from the oil separator S.
  • the oil separator S and the shaft hole 20 are in communication through the oil passage 32, the oil reservoir T and the communication hole 46.
  • the communication hole 46 communicates with the clearance CL, which functions as a throttle for the oil return passage extending from the oil separator S to the inner side of the compressor 10. Therefore, high-pressure refrigerant gas in the oil separator S is prevented from leaking in large amount into the low-pressure shaft hole 20 which forms a part of a suction-pressure region of the compressor 10.
  • the closure cap 51 which rotates integrally with the rotary valve 50 prevents the clearance CL from being clogged with foreign matters, thereby maintaining the clearance CL for constant communication between the hole 46 and the shaft hole 20. Accordingly, there will not occur a trouble that the clearance CL clogs thereby to block the flow of lubricating oil returning from the oil separator S to the shaft hole 20.
  • lubricating oil returned to the shaft hole 20 through the clearance CL is supplied between the outer peripheral surface 50a of the rotary valve 50 and the peripheral sealing surface 20a and further supplied into the crank chamber 17 along the rotary shaft 19. As a result, lubricating oil circulates in the compressor 10, thus ensuring lubrication of its parts.
  • the swash plate 24 secured to the rotary shaft 19 is also urged forward in the axial direction of the rotary shaft 19, and its front surface of the boss portion 24a is entirely pressed against the thrust bearing 30. Urging the swash plate 24 against the thrust bearing 30 prevents the swash plate 24 from being inclined by compression reaction force via the pistons 31, otherwise the front face of the swash plate boss portion 24a would be inclined by the reaction force with respect to the thrust bearing 30, perpendicular to the axis of the rotary shaft 19. This ensures the entire circumferential contact between the front surface of the swash plate boss portion 24a and the thrust bearing 30, and prevents their partial contact.
  • the present invention is not limited to the above-described embodiment but it may be modified into various alternative embodiments as exemplified below.
  • the cap portion 52 is not limited to a hollow structure, but it may be of solid provided that the cap portion 52 press-fitted in a position closes the supply passage 41.
  • the closure cap 51 may be formed only by the cap portion 52 without the flange portion 53.
  • the present invention is also applicable to a piston type compressor equipped with a cam having a shape other than that of the swash plate 24.
  • the oil separator S is not limited to a centrifugal separator, but it may be, for example, an inertial separator for separating lubricating oil from refrigerant gas by allowing the refrigerant gas to collide against a wall surface.
  • a filter may be provided in the oil reservoir T.
  • a cylindrical valve body having a bottom at one end may be fitted in the inserting hole 24b of the swash plate 24 for forming the rotary valve 50.
  • the bottom of the valve body closes the supply passage 41, and the clearance CL is formed between the bottom and the valve plate assembly 14.
  • the bottom of the valve body may serve as a closure means, a pressure receiving surface and a regulating means.
  • a piston type compressor comprises a housing, a rotary shaft supported by the housing, a cam mounted on the rotary shaft.
  • the housing includes a discharge-pressure region and a suction-pressure region.
  • the compressor further comprises an oil separator provided in the discharge-pressure region and an oil reservoir for storing lubricating oil from the oil separator.
  • the rotary shaft has a regulating means for regulating the axial movement of the rotary shaft and for forming a clearance between the regulating means and the valve plate assembly. The clearance is communicated with the oil reservoir through a communication hole formed in the valve plate assembly so that the clearance functions as a throttle in an oil return passage extending from the oil separator to the inside of the compressor.
  • a supply passage is formed in the rotary valve and in communication with the cam chamber in which a suction port is provided.

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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)
EP06112256A 2005-04-06 2006-04-05 Compresseur à plateau en biais Withdrawn EP1712791A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005110238A JP2006291751A (ja) 2005-04-06 2005-04-06 ピストン式圧縮機

Publications (1)

Publication Number Publication Date
EP1712791A2 true EP1712791A2 (fr) 2006-10-18

Family

ID=36228763

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06112256A Withdrawn EP1712791A2 (fr) 2005-04-06 2006-04-05 Compresseur à plateau en biais

Country Status (6)

Country Link
US (1) US20060228229A1 (fr)
EP (1) EP1712791A2 (fr)
JP (1) JP2006291751A (fr)
KR (1) KR100675547B1 (fr)
CN (1) CN1844665A (fr)
BR (1) BRPI0601341A (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100754106B1 (ko) * 2003-11-28 2007-08-31 텍스틸마 악티엔게젤샤프트 직물 기계, 특히 셰딩 장치에 대한 실 제어 장치
JP4513684B2 (ja) * 2005-07-27 2010-07-28 株式会社豊田自動織機 両頭ピストン式圧縮機
JP4758728B2 (ja) * 2005-10-25 2011-08-31 サンデン株式会社 往復動型流体機械
KR101037177B1 (ko) * 2007-06-01 2011-05-26 한라공조주식회사 사판식 압축기
JP2010209680A (ja) * 2007-08-16 2010-09-24 Sanden Corp 開放型ピストン式圧縮機
JP5045555B2 (ja) * 2008-05-29 2012-10-10 株式会社豊田自動織機 両頭ピストン型斜板式圧縮機
CN101718267B (zh) * 2009-04-30 2011-09-14 上海加冷松芝汽车空调股份有限公司 含有油气分离结构的压缩机
JP5741554B2 (ja) * 2012-11-02 2015-07-01 株式会社豊田自動織機 ピストン型圧縮機
KR101567235B1 (ko) 2014-08-20 2015-11-06 한국남부발전 주식회사 증기터빈 설비의 윤활유 탱크용 차폐시스템
CN105863989A (zh) * 2016-05-27 2016-08-17 李晓峰 单向斜盘式压缩机

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2743682B2 (ja) * 1992-02-20 1998-04-22 株式会社豊田自動織機製作所 ピストン型圧縮機におけるシール構造
US5765996A (en) * 1994-04-08 1998-06-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Vibration preventing structure in swash plate type compressor
JP3747533B2 (ja) 1996-10-23 2006-02-22 株式会社豊田自動織機 カム式圧縮機
JPH11182431A (ja) 1997-12-24 1999-07-06 Toyota Autom Loom Works Ltd 圧縮機
JP2001165049A (ja) * 1999-12-08 2001-06-19 Toyota Autom Loom Works Ltd 往復式圧縮機
JP2002031043A (ja) * 2000-07-14 2002-01-31 Toyota Industries Corp 圧縮機
JP4399994B2 (ja) * 2000-11-17 2010-01-20 株式会社豊田自動織機 容量可変型圧縮機
JP2003184738A (ja) 2001-12-17 2003-07-03 Sanden Corp 斜板式圧縮機
US7014428B2 (en) * 2002-12-23 2006-03-21 Visteon Global Technologies, Inc. Controls for variable displacement compressor

Also Published As

Publication number Publication date
CN1844665A (zh) 2006-10-11
JP2006291751A (ja) 2006-10-26
KR100675547B1 (ko) 2007-01-30
KR20060107284A (ko) 2006-10-13
BRPI0601341A (pt) 2006-12-05
US20060228229A1 (en) 2006-10-12

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