WO2016047600A1 - Compresseur - Google Patents

Compresseur Download PDF

Info

Publication number
WO2016047600A1
WO2016047600A1 PCT/JP2015/076702 JP2015076702W WO2016047600A1 WO 2016047600 A1 WO2016047600 A1 WO 2016047600A1 JP 2015076702 W JP2015076702 W JP 2015076702W WO 2016047600 A1 WO2016047600 A1 WO 2016047600A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
shaft
seal space
drive shaft
crank chamber
Prior art date
Application number
PCT/JP2015/076702
Other languages
English (en)
Japanese (ja)
Inventor
勝孝 宇根
Original Assignee
株式会社ヴァレオジャパン
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 株式会社ヴァレオジャパン filed Critical 株式会社ヴァレオジャパン
Priority to EP15844821.7A priority Critical patent/EP3199810A4/fr
Priority to CN201580051405.0A priority patent/CN106715905A/zh
Publication of WO2016047600A1 publication Critical patent/WO2016047600A1/fr

Links

Images

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
    • F04B39/02—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
    • 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
    • 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
    • F04B27/1081—Casings, housings
    • 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
    • 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

Definitions

  • the present invention relates to a compressor used for an air conditioner for a vehicle, and the like, and relates to a compressor having an improved path structure of lubricating oil provided around a drive shaft and supplied to a shaft sealing member that seals between a housing and a housing. .
  • a drive shaft that passes through the crank chamber and is rotatably supported by the housing, and is arranged in the crank chamber and rotates in synchronization with the rotation of the drive shaft, and is rotatably supported on the inner wall surface of the housing via a thrust bearing.
  • a radial bearing that receives the drive shaft and a shaft seal member that prevents fluid leakage in the crank chamber are arranged, and in particular, the sliding contact portion between the drive shaft and the shaft seal member requires good lubrication to prevent seizure. Has been.
  • a lubricating oil introduction groove for introducing the lubricating oil of the crank chamber is provided on the bearing surface of the thrust bearing on the inner wall surface of the housing, and the lubricating oil introduced through the lubricating oil introduction groove is provided as a shaft seal member.
  • the sealed space is communicated with the crank chamber via a lubricating oil passage provided in the housing, and is communicated with the crank chamber via a gap between the flat portion provided on the drive shaft and the slide bearing.
  • a configuration in which the lubricating oil in the crank chamber is introduced into the seal space and the lubricating oil in the seal space is returned to the crank chamber via the other is considered (see Patent Document 2).
  • the lubricating oil is returned to the crank chamber through the gap between the flat portion and the slide bearing.
  • the gap between the flat portion and the sliding bearing is not fixed at a predetermined position (because it rotates with the rotation of the drive shaft), more lubricant than necessary is accumulated in the lower portion of the seal space.
  • the temperature of the shaft seal member rises, and there is a concern that the lubricating oil leaks due to a decrease in the shaft seal function.
  • an oil supply passage for supplying oil from the inner wall surface of the housing located above the drive shaft to the seal space formed around the drive shaft is provided between the radial bearing and the shaft seal member.
  • an oil discharge passage that has one end communicating with the seal space and the other end communicating with the crank chamber is positive for the shaft seal member and the radial bearing.
  • an oil discharge passage for discharging the oil in the seal space to the crank chamber is provided between the bearing surface that receives the radial bearing and the radial bearing.
  • the oil discharge amount is relatively larger than the introduction amount, the oil is not sufficiently retained in the seal space, and the sliding contact portion between the drive shaft and the shaft seal member is seized. There are concerns about inconvenience.
  • the present invention has been made in view of the above points, and maintains an appropriate amount of oil in the seal space to avoid oil shortage and ensure good lubrication, and also provides lubricating oil supplied to the shaft seal member.
  • the main object is to provide a compressor capable of suppressing the deterioration of the shaft seal function (oil leakage) due to the temperature rise of the shaft seal member by promoting the replacement.
  • a compressor includes a housing that defines a crank chamber, and is rotatably supported by the housing through a radial bearing that passes through the crank chamber.
  • a drive shaft protruding from the housing; a shaft sealing member disposed on one end side of the radial bearing of the drive shaft; sealing the space between the drive shaft and the housing;
  • An oil supply passage that communicates with the crank chamber, the other end communicates with a seal space formed between the radial bearing and the shaft seal member, one end communicates with the seal space, and the other end communicates with the crank chamber.
  • An oil discharge passage that communicates with the oil discharge passage, and the inflow port that opens into the seal space of the oil discharge passage is the lowest in contact with the shaft seal member of the drive shaft And upper and than location, and is characterized in that it is open in the lower position than or horizontal plane the same position passing through the axis of the drive shaft.
  • the housing is inclined and mounted about the axis of the drive shaft.
  • the inlet opening to the seal space of the oil discharge passage on the basis of the installation state May be open at a position above the lowest position in contact with the shaft seal member of the drive shaft and below the horizontal position including the axis of the drive shaft.
  • the inlet opening to the seal space of the oil discharge passage is opened above the lowest position in contact with the shaft seal member of the drive shaft, the liquid level of the oil in the seal space is the oil discharge passage. Even if the oil is not discharged from the seal space and less oil is introduced from the oil supply passage, the contact position between the drive shaft and the shaft seal member is immersed in the accumulated oil, and lubrication of the sliding part The shortage can be avoided.
  • the oil accumulated in the seal space reaches the inlet of the oil discharge passage, excess oil is discharged to the crank chamber through the oil discharge passage, so there is no inconvenience of the oil in the seal space and the oil is replaced. It is possible to avoid the temperature rise of the shaft seal member.
  • the seal space is defined by being surrounded by the radial bearing, the shaft seal member, the inner surface of the housing, and the peripheral surface of the drive shaft, and the housing that defines the seal space.
  • the inner surface has a conical surface whose inner diameter increases toward the shaft seal member. According to such a configuration, the oil guided to the seal space via the oil supply passage is easily guided to the shaft sealing member by the gravity along the inclined surface at the lower part of the conical surface, and the volume of the seal space is also increased. It is possible to further suppress the stagnation of oil without increasing the oil more than necessary.
  • the other end of the oil supply passage is preferably connected to the seal space at the conical surface.
  • the other end of the oil supply passage is preferably opened at a position where the introduced oil does not directly hit the shaft seal member. If the oil flowing from the oil supply passage into the shaft sealing member directly hits the shaft sealing member, the shaft sealing member may be deformed due to many years of use, and the sealing function may be impaired. The deformation of the shaft seal member can be suppressed, and the life of the shaft seal member can be extended.
  • one end of the oil supply passage communicates with the crank chamber, the other end communicates with the seal space formed between the radial bearing and the shaft seal member, and one end of the seal space.
  • the inflow opening that opens to the seal space of the oil discharge passage is the lowest in contact with the shaft seal member of the drive shaft Since it opens above the position and is positioned at the lower side of the horizontal plane that includes the axis of the drive shaft, the oil in the seal space is maintained at an appropriate amount to prevent oil shortage.
  • the inner surface of the housing defining the seal space has a conical surface whose inner diameter increases toward the shaft seal member, so that oil guided to the seal space via the oil supply passage is below the conical surface by gravity. It becomes easy to be guided to the shaft seal member along the inclined surface, and by making the peripheral surface of the seal space a conical surface, the volume of the seal space is not increased more than necessary, and it is possible to suppress oil stagnation. .
  • FIG. 1B is a cross-sectional view of a compressor according to an embodiment of the present invention.
  • 2A is an enlarged cross-sectional view of a part of the front head of the compressor of FIG. 1B
  • FIG. 2B is a cross-sectional view taken along line AA in FIG.
  • FIG. 4B is a cross-sectional view taken along line BB in FIG.
  • FIG. 3 is a diagram for explaining the flow of oil to the seal space and the oil storage state.
  • FIG. 3A is a cross-sectional view in which a part of the front head of the compressor in FIG. 1 is enlarged, and FIG. It is sectional drawing cut
  • FIG. 4 is an enlarged cross-sectional view of a part of the front head of the compressor showing another example of the oil discharge passage.
  • FIG. 5 is an enlarged cross-sectional view of a part of the front head of the compressor showing still another example of the oil discharge passage.
  • FIG. 1 shows a variable capacity swash plate compressor used in a refrigeration cycle as an example of a compressor.
  • This compressor includes a cylinder block 1, a rear head 3 assembled on the rear side (right side in the figure) of the cylinder block 1 via a valve plate 2, and a front side (left side in the figure) of the cylinder block 1. And a front head 4 assembled so as to be closed.
  • the front head 4, the cylinder block 1, the valve plate 2, and the rear head 3 are fastened in the axial direction by fastening bolts 5 and constitute a housing for the entire compressor.
  • a crankshaft 6 provided by the front head 4 and the cylinder block 1 accommodates a drive shaft 7 having one end protruding from the front head 4.
  • a drive pulley (not shown) connected to the engine of the vehicle via a belt is fixed to a portion of the drive shaft 7 protruding from the front head 4.
  • one end side of the drive shaft 7 is hermetically sealed with the front head 4 via a shaft sealing member 10 provided between the drive shaft 7 and the refrigerant leakage along the drive shaft 7 is prevented.
  • One end side of the drive shaft 7 is rotatably supported by a radial bearing 11 accommodated on the crank chamber side of the shaft seal member 10 of the front head 4, and the other end side of the drive shaft 7 is supported by the cylinder block 1. Is rotatably supported by a radial bearing 12 housed in the housing.
  • the cylinder block 1 is formed with a support hole 13 in which the radial bearing 12 is accommodated, and a plurality of cylinder bores 15 arranged at equal intervals on a circumference around the support hole 13.
  • a single-head piston 16 is inserted into the cylinder bore 15 so as to be slidable back and forth.
  • the one-head piston 16 is formed by joining a head portion 16a inserted into the cylinder bore 15 and an engaging portion 16b protruding into the crank chamber 6 in the axial direction.
  • a thrust flange 17 that rotates integrally with the drive shaft 7 is fixed to the drive shaft 7 in the crank chamber 6.
  • the thrust flange 17 is rotatably supported via a thrust bearing 18 on an inner wall surface 4 a of the front head 4 formed substantially perpendicular to the drive shaft 7.
  • the thrust flange 17 constitutes a power transmission member, and the thrust flange 17 is connected to a swash plate 20 via a link mechanism 19.
  • the swash plate 20 is attached so as to be able to tilt around a hinge ball 21 slidably provided on the drive shaft 7, and is integrated with the rotation of the thrust flange 17 via the link mechanism 19. It is designed to rotate. And the engaging part 16b of the single-headed piston 16 is moored to the peripheral part of the swash plate 20 via a pair of shoes 22 arranged at the front and back.
  • Reference numeral 24 denotes a suction hole formed in the valve plate 2 that communicates the suction chamber 25 formed in the rear head 3 and the compression chamber 23 via a suction valve (not shown), and 26 denotes a hole formed in the rear head 3. This is a discharge hole formed in the valve plate 2 that communicates the discharge chamber 27 and the compression chamber 23 via a discharge valve (not shown).
  • Reference numeral 28 denotes a pressure control valve that controls the communication state between the discharge chamber 27 and the crank chamber 6 and adjusts the crank chamber pressure to adjust the tilt angle of the swash plate 20.
  • the shaft seal member 10 and the radial bearing 11 are disposed with an interval in the axial direction, and a shaft seal is provided between the inner surface of the front head 4 and the peripheral surface of the drive shaft 7.
  • An annular seal space 30 defined by the member 10 and the radial bearing 11 is formed. That is, the seal space 30 is defined by being surrounded by the radial bearing 11, the shaft sealing member 10, the inner surface of the boss portion 41 of the front head 4, and the peripheral surface of the drive shaft 7. Then, the inner surface of the boss portion 41 of the front head 4 that defines the seal space 30 is formed by a conical surface 30a having an inner diameter gradually increasing from the radial bearing 11 toward the shaft seal member 10 and a cylindrical surface 30b continuous therewith. ing.
  • the front head 4 also has a bearing surface for receiving the thrust bearing 18 on the inner wall surface 4a located above the drive shaft 7, more specifically, the thrust bearing 18 is held by the needle roller 18a and this as shown.
  • a guide groove 31 that guides the lubricating oil is extended downward to a portion of the front head 4 that receives the thrust trace 18b.
  • the guide groove 31 and the seal space 30 are connected by an oil supply passage 32 formed in the front head 4 at a predetermined angle with respect to the axis of the drive shaft 7.
  • the lubricating oil introduced into the guide groove 31 is supplied to the seal space 30.
  • the oil supply passage 32 is opened immediately below the guide groove 31 so as to receive the lubricant that descends through the guide groove 31, and most of the lubricant that descends through the guide groove 31. Can be introduced.
  • the other end of the oil supply passage 32 is connected to the seal space 30 only by the conical surface 30a, and is opened at a position where the introduced oil does not directly hit the shaft seal member 10. That is, the conical surface 30a is not located at a position overlapping the shaft seal member 10 in the axial direction, but is formed to be shifted to a portion closer to the radial bearing 11 by a predetermined dimension than the shaft seal member 10, and the formation position of this conical surface is determined.
  • the introduction position of the oil supplied from the oil supply passage 32 to the seal space is set to a predetermined position closer to the radial bearing side than the shaft seal member 10.
  • the angle formed by the conical surface 30a and the axis of the drive shaft 7 is set to about 25 degrees, and the angle formed by the oil supply passage 32 and the axis of the drive shaft 7 is set to 30 to 35 degrees. Therefore, the angle formed between the conical surface 30a and the oil supply passage 32 is set to 55 to 60 degrees.
  • the oil supply passage 32 is connected to the seal space 30 only at the conical surface 30a, when drilling the oil supply passage 32, a drill is performed from the inside to the outside of the conical surface 30a of the seal space 30. Even in the case of drilling, it is possible to increase the incident angle of the drill with respect to the conical surface 30a of the oil supply passage 32, and it is possible to reduce inconvenience that burrs are generated at the peripheral edge of the drill.
  • the front head 4 is further formed with an oil discharge passage 34 having one end communicating with the seal space 30 and the other end communicating with the crank chamber 6.
  • the oil discharge passage 34 is formed substantially parallel to the drive shaft 7, and a part or all of the inflow port 34 a (one end of the oil discharge passage 34) that opens into the seal space 30 is on the conical surface 30 a. And is above the lowest position in contact with the shaft sealing member of the drive shaft 7 and on a horizontal plane including the axis O of the drive shaft 7 or below the horizontal plane. Is opened (a range indicated by ⁇ in FIG. 2B).
  • the other end of the oil discharge passage 34 is open to the inner wall surface 4a of the front head 4 on the inner side (drive shaft side) of the thrust bearing 18, and the lubricating oil that has flowed out of the oil discharge passage 34 is removed from the thrust bearing 18. Is returned to the crank chamber 6.
  • the oil discharge passage 34 is above the lowest position in contact with the shaft seal member 10 of the drive shaft 7 and on the horizontal plane including the axis O of the drive shaft 7 or below this. Since the conical surface 30a is open at a position where the oil level in the seal space 30 does not reach the shaft seal member 10, the oil in the seal space 30 is not discharged. Further, after the oil level accumulated in the seal space 30 reaches the shaft seal member 10, the oil in the seal space 30 passes through the oil discharge passage 34 as shown in FIG. Therefore, only the minimum necessary amount of oil is stored in the seal space 30, and the replacement of the lubricating oil supplied to the shaft seal member 10 can be promoted. Therefore, it becomes possible to prevent sludge from agitating and sliding heat generation of the oil retained in the seal space 30 and oil leakage from the shaft seal member 10 due to the sludge, thereby extending the life of the shaft seal member 10. It becomes.
  • the temperature during high-speed intermittent operation is 157 ° C.
  • the minimum discharge capacity is high-speed continuous.
  • the temperature during operation was 157 ° C.
  • the temperature during high-speed intermittent operation was 148 ° C.
  • the temperature during minimum discharge capacity high-speed continuous operation was 136 ° C.
  • the oil discharge passage 34 is formed in parallel with the drive shaft 7. However, as shown in FIG. 4, the oil discharge passage 34 is inclined with respect to the drive shaft 7. It may be formed and communicated with the crank chamber 6 at a position below the opening end of the seal space 30. Even in such a configuration, the opening end of the oil discharge passage 34 to the crank chamber 6 is at an opening position where the lubricating oil flowing out from the oil discharge passage 34 passes through the gap of the thrust bearing 18 and returns to the crank chamber 6. Good. In such a configuration, surplus oil in the seal space 30 is guided to the crank chamber 6 through the oil discharge passage 34 by the action of gravity in addition to the back pressure, so that the oil level in the seal space 30 can be easily managed. It will be a thing.
  • each of the oil discharge passages 34-1 and 34-2 is located above the lowest position at which the inlet opening to the seal space 30 contacts the shaft seal member 10 of the drive shaft 7, In addition, it is necessary that the horizontal axis including the axis O of the drive shaft 7 is placed at the same position as the horizontal plane (open in this example, the inlet of one oil discharge passage 34-1 is driven).
  • the inlet of the other oil discharge passage 34-2 is above the lowest position in contact with the shaft seal member 10 of the drive shaft 7, and And is open at a position below the horizontal plane including the axis of the drive shaft 7).
  • the oil discharge passages 34-1 and 34-2 may be parallel to the drive shaft 7 or may be inclined so that the crank chamber side faces downward.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Sealing Devices (AREA)
  • Sealing Of Bearings (AREA)

Abstract

Le problème décrit par l'invention est de produire un compresseur qui empêche les manques d'huile et maintient une lubrification appropriée grâce au maintien d'une quantité appropriée d'huile dans un espace d'étanchéité, ce qui favorise le remplacement d'huile de lubrification apportée à un élément d'étanchéité d'arbre, et ce qui permet ainsi de réduire au minimum les baisses de performance d'étanchéité d'arbre (fuite d'huile) causées par des hausses de la température de l'élément d'étanchéité d'arbre. La solution selon l'invention porte sur un compresseur dans lequel est formé un logement : un passage d'alimentation en huile 32 dont une extrémité est reliée à une chambre de vilebrequin 6 et l'autre extrémité est reliée à un espace d'étanchéité 30 formé entre un palier radial 11 et un élément d'étanchéité d'arbre 10; et un passage de rejet d'huile 34 dont une extrémité est reliée à l'espace d'étanchéité 30 et l'autre extrémité est reliée à la chambre de vilebrequin 6. L'entrée 34a du passage de rejet d'huile 34 s'ouvre dans l'espace d'étanchéité dans une position qui est au-dessus d'une position la plus basse dans laquelle un arbre d'entraînement 7 est en contact avec l'élément d'étanchéité d'arbre 10 et dans la même position ou inférieure à un plan horizontal contenant le centre axial O de l'arbre d'entraînement 7.
PCT/JP2015/076702 2014-09-24 2015-09-18 Compresseur WO2016047600A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP15844821.7A EP3199810A4 (fr) 2014-09-24 2015-09-18 Compresseur
CN201580051405.0A CN106715905A (zh) 2014-09-24 2015-09-18 压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-193228 2014-09-24
JP2014193228A JP6498405B2 (ja) 2014-09-24 2014-09-24 圧縮機

Publications (1)

Publication Number Publication Date
WO2016047600A1 true WO2016047600A1 (fr) 2016-03-31

Family

ID=55581127

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/076702 WO2016047600A1 (fr) 2014-09-24 2015-09-18 Compresseur

Country Status (4)

Country Link
EP (1) EP3199810A4 (fr)
JP (1) JP6498405B2 (fr)
CN (1) CN106715905A (fr)
WO (1) WO2016047600A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3450754A4 (fr) * 2016-08-09 2019-04-10 Mitsubishi Heavy Industries Thermal Systems, Ltd. Compresseur de réfrigérant de type ouvert

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7213700B2 (ja) * 2019-01-29 2023-01-27 サンデン株式会社 圧縮機
JP7213709B2 (ja) * 2019-02-06 2023-01-27 サンデン株式会社 圧縮機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4292539B2 (ja) * 2003-07-02 2009-07-08 株式会社ヴァレオサーマルシステムズ 圧縮機
JP2009209682A (ja) * 2008-02-05 2009-09-17 Toyota Industries Corp 斜板式圧縮機
JP2010013962A (ja) * 2008-07-02 2010-01-21 Calsonic Kansei Corp 気体圧縮機

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945765A (en) * 1974-04-15 1976-03-23 Sankyo Electric Co., Ltd. Refrigerant compressor
US4236878A (en) * 1978-09-29 1980-12-02 Sankyo Electric Company Limited Lubrication system for compressor unit
JPH08284835A (ja) * 1995-04-18 1996-10-29 Toyota Autom Loom Works Ltd 片頭ピストン圧縮機
JP3567346B2 (ja) * 1995-04-18 2004-09-22 株式会社ゼクセルヴァレオクライメートコントロール 圧縮機
JP2002310067A (ja) * 2001-04-10 2002-10-23 Toyota Industries Corp 圧縮機
JP2005194932A (ja) * 2004-01-07 2005-07-21 Zexel Valeo Climate Control Corp 可変容量型圧縮機
JP4425289B2 (ja) * 2007-03-30 2010-03-03 株式会社デンソー ピストン型圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4292539B2 (ja) * 2003-07-02 2009-07-08 株式会社ヴァレオサーマルシステムズ 圧縮機
JP2009209682A (ja) * 2008-02-05 2009-09-17 Toyota Industries Corp 斜板式圧縮機
JP2010013962A (ja) * 2008-07-02 2010-01-21 Calsonic Kansei Corp 気体圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3199810A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3450754A4 (fr) * 2016-08-09 2019-04-10 Mitsubishi Heavy Industries Thermal Systems, Ltd. Compresseur de réfrigérant de type ouvert

Also Published As

Publication number Publication date
CN106715905A (zh) 2017-05-24
JP2016065459A (ja) 2016-04-28
EP3199810A4 (fr) 2018-04-25
JP6498405B2 (ja) 2019-04-10
EP3199810A1 (fr) 2017-08-02

Similar Documents

Publication Publication Date Title
CN103807166B (zh) 涡旋压缩机
JP2006307700A (ja) 圧縮機
CN107630814B (zh) 涡旋压缩机、节流结构及空调器
WO2016047600A1 (fr) Compresseur
JPH08284835A (ja) 片頭ピストン圧縮機
JP2013072365A (ja) 圧縮機
JP4292539B2 (ja) 圧縮機
US9512830B2 (en) Reciprocating compressor
JP2007127118A (ja) ピストン型圧縮機
WO2018207724A1 (fr) Compresseur
JP2009062820A (ja) 密閉形ロータリ圧縮機
JP6280783B2 (ja) 水圧回転機
US6523455B1 (en) Compressor having an oil collection groove
EP3795833B1 (fr) Compresseur à spirale et véhicule doté de celui-ci
JP2010101202A (ja) 可変容量型圧縮機
US20130101443A1 (en) Variable Capacity Compressor
CN214944832U (zh) 曲轴组件、变频压缩机及制冷设备
CN220151501U (zh) 一种用于摇摆式压缩机的压力平衡装置和摇摆式压缩机
JP2009062954A (ja) 密閉型圧縮機
JP2020165425A (ja) 可変容量斜板式圧縮機
JP2015227632A (ja) 圧縮機
WO2009128228A1 (fr) Structure de distribution d'agent lubrifiant pour compresseur
CA2787527A1 (fr) Machines a fluide
JP6961438B2 (ja) 開放型圧縮機
JP2003293953A (ja) レシプロ式密閉型電動圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15844821

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

REEP Request for entry into the european phase

Ref document number: 2015844821

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2015844821

Country of ref document: EP