EP1371847A1 - Compresseur à piston axial - Google Patents

Compresseur à piston axial Download PDF

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Publication number
EP1371847A1
EP1371847A1 EP03015448A EP03015448A EP1371847A1 EP 1371847 A1 EP1371847 A1 EP 1371847A1 EP 03015448 A EP03015448 A EP 03015448A EP 03015448 A EP03015448 A EP 03015448A EP 1371847 A1 EP1371847 A1 EP 1371847A1
Authority
EP
European Patent Office
Prior art keywords
lubricant
drive shaft
swash plate
axial piston
swashplate
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Withdrawn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
EP03015448A
Other languages
German (de)
English (en)
Inventor
Otfried Schwarzkopf
Ullrich Hesse
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.)
Valeo Compressor Europe GmbH
Original Assignee
Zexel Valeo Compressor Europe GmbH
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 Zexel Valeo Compressor Europe GmbH filed Critical Zexel Valeo Compressor Europe GmbH
Publication of EP1371847A1 publication Critical patent/EP1371847A1/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Withdrawn legal-status Critical Current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
    • F04B27/1054—Actuating elements
    • 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

Definitions

  • the invention relates to an axial piston compressor for a Refrigerant, especially for a vehicle air conditioning system, with a an engine chamber delimiting housing, a cylinder block with cylinders for the reciprocating reception of Piston, the piston being driven by an inside of the Engine chamber arranged and with a rotary drive Drive shaft rotatably connected oblique and / or Swashplate mechanism takes place.
  • Such an axial piston compressor is, for example, from the DE 196 21 174 A1 known. It is used as a compressor for that Refrigerant used and used in a vehicle air conditioning system to the refrigerant from a heat exchanger in which it evaporated while absorbing heat at low pressure and compress to a higher pressure at which the Refrigerant in another heat exchanger, giving off heat is liquefied and / or cooled.
  • Such compressors come in a wide variety of designs known; have different reasons Axial piston compressors with a swash plate work. With this design, the axial movement of the pistons generated by a swashplate, the tilt angle relative to Drive shaft can be controlled. With the swashplate the pistons are connected in a tensile and compressive manner; because the cylinders, in which the pistons are slidable are stationary while the swashplate is driven as a coupling mechanism between the swash plate and the pistons either sliding blocks with plain bearings attached to the pistons, or a swashplate with piston rods that are in plain bearings are attached to the piston.
  • each piston hemispherical bearing formed in which the two Sliding blocks are arranged so that they are on one and the other attack the other side of the swash plate on a tread.
  • a swashplate it is rotatably mounted relative to the swash plate, so that on the Swashplate only the inclined position of the swashplate is transmitted, but not their rotational movement.
  • the Piston rods are on the swash plate as well as on the Piston supported by a ball joint.
  • An oil circuit with a pump for lubricating the component of the Axial piston compressor is for axial piston compressors that are in Motor vehicles is not possible. For one thing, would the axial piston compressor by the lubricant pump may considerably more expensive. Furthermore, it leads to performance losses, with an axial piston compressor for vehicle air conditioning, that have a rather low performance are more important than with a high performance axial piston compressor .. After all, a pump that would take the lubricant out of a Oil sump would have to suck in, together with this oil sump lead to significantly larger construction volumes. For all of these reasons is the lubrication inside the housing instead of through an oil circuit with a pump through an oil mist generated there achieved.
  • the object of the invention is therefore in one Axial piston compressor of the type mentioned at the beginning the simplest means of reliable pressure oil lubrication To ensure bearings without a separate oil pump is required, but lubrication is still achieved that is supposed to be qualitative through the lubrication of the bearings the lubricant mist inside the housing goes.
  • An axial piston compressor of the type mentioned with the Features of the characterizing part of claim 1 offers the advantage that a pressure lubricant circuit is formed, the the bearings in the interior of the housing the necessary Can supply lubricants.
  • This lubricant circuit is based Put simply, a reduction in the share of the Lubricant that is inevitable along with the compressed Refrigerant leaves the axial piston compressor, as well as on the Use of the pressure difference between the compressor side and the interior of the housing of the axial piston compressor. by virtue of this high pressure difference between the compressor side and the The interior of the housing is very high Lubricant throughput without the need for separate drive energy or even a pump would have to be provided.
  • the Lubricant separator provided according to the invention adjusts comparatively simple component that does not have high costs entails.
  • a suitable throttling for the necessary resistance to one rapid drainage of the lubricant from the separator.
  • a such throttling occurs automatically, for example, when a plain bearing is supplied; the narrow bearing gap limits the Lubricant flow.
  • a roller bearing is lubricated may have to a cover plate can be used to the Limit the discharge cross-section appropriately.
  • the construction according to the invention is thus characterized that the last warehouse to be supplied with Lubricant is supplied under high pressure, i.e. Compression pressure.
  • high pressure i.e. Compression pressure.
  • the oil pressure is at the bearing or bearing gap.
  • the Bearings are in line for their lubricating oil supply switched and just designed so that the last too supplying bearings under almost unchanged high pressure with oil is supplied. It is only because of this construction that it is possible an oil pump without replacement by a high pressure side Oil separator to replace without underneath the supply of the Bearing with oil suffers from high pressure.
  • the lubricant separator is on the pressure side of the Circuit arranged, either between the Compressor and a pressure side heat exchanger or between the pressure side heat exchanger and an expansion valve.
  • the supply line with a controllable valve is provided.
  • the supply line can when the axial piston compressor is at a standstill, so that the existing high pressure on the compressor Lubricant present in the collecting chamber is not in the housing Axial piston compressor can push in, causing the Eventually the collecting room would be emptied. In this case none when starting up the axial piston compressor Lubricant available. If, however, the valve with Commissioning of the axial piston compressor is opened Sufficient lubrication immediately by the in Lubricant collection containers available.
  • the controllable valve can also be dispensed with. If the lubricant drains from the reservoir due to the internal resistances and throttling points of the system a sufficient resistance could be opposed the controllable valve can also be dispensed with. If the The compressor only comes to a standstill for a short time no pressure equalization between the pressure side of the compressor and the low pressure side. Thus, the compressor must Restarting against high pressure; it stands but also immediately available lubricants. against that the compressor after a long standstill leading to a Pressure equalization has resulted, so that not immediately below Lubricant under pressure is supplied, only pressure build up; so he doesn’t work under heavy loads at first, so that not even a complete lubrication is required. With increasing load of the compressor then the lubrication also improves.
  • controllable valve could be replaced by a Throttle point are replaced if it is guaranteed that the Pressure equalization when the compressor stops first Line happens over other points of the cycle for example through a separate valve.
  • Throttle line can be used by the various pressure drops in the lubricant supply, especially through channels in the compressor, the required Throttling is brought about.
  • An overflow line is preferably provided, which runs from Lubricant separator leads to the interior of the housing. On this way excess lubricant that is in the Collecting room accumulates, if necessary, removed. Therefor a controllable valve can be provided in the overflow line be depending on, for example, a Level sensor in the collecting room is opened.
  • lubricant separator is integrated in the housing. This leads to a particularly compact design.
  • the lubricant separator is separated from the housing and the supply line acts as a lubricant cooler. This ensures that that too Lubricant returned to the bearings, from the Refrigerant was warmed up during the compression stroke is returned to its initial temperature.
  • a drive shaft provided that is provided with an axial distribution bore.
  • An axial distribution hole in the drive shaft enables almost all important ones with particularly little effort Bearing points inside the housing of the axial piston compressor to reach. The effort is significantly less than with a solution in which in the housing of the compressor appropriate lubricant channels to all bearings are trained.
  • the distribution bore preferably opens into one in the interior of the housing arranged end face of the drive shaft, that is the end face, which is the drive end of the drive shaft opposite.
  • a swash plate provided by means of a plain bearing on the drive shaft is arranged displaceably, in the region of the plain bearing a branch hole is provided in the drive shaft, the connects the plain bearing to the distribution hole.
  • the plain bearing is due to the existing in the interior of the housing Lubricant mist is very difficult to lubricate; the Branch hole allows the slide bearing to the required Amount of lubricant. The amount supplied can be determined by the cross section of the branch hole.
  • the drive shaft by at least one assembly consisting of a radial bearing and a thrust bearing stored, this assembly through a branch hole from the drive shaft is supplied with lubricant and the Lubricant first through the radial bearing and then through that Thrust bearing flows.
  • the series connection of the bearings used allows both bearings in terms of lubricant flow to lubricate with comparatively little effort. There due to the available space and the resulting bearing size the radial bearing in terms of Life is most at risk, this bearing is included first Lubricant supplies; the one leaving the radial bearing Lubricant flow is then led to the thrust bearing.
  • the Supply of the bearings can be done as this is preferred is intended to be adjusted by sealing washers form a defined leakage gap.
  • CO 2 is used as the refrigerant.
  • an air conditioning system with the refrigerant CO 2 works at a much higher pressure level than an air conditioning system with a conventional refrigerant.
  • the suction pressure for the refrigerant R134a is approximately 5 bar and the compression pressure is approximately 20 bar.
  • Figure 1 is an axial piston compressor according to a first embodiment shown. It contains one Drive shaft 10, which is mounted in a housing 12. With the Drive shaft 10 is non-rotatably connected to a swash plate 14, between a position in which they are approximately perpendicular to the Longitudinal axis of the drive shaft 10 extends, and a maximum tilted position can be pivoted in Figure 1 is shown.
  • the position of the swash plate 14 in operation takes place depending on the difference between the suction pressure of the compressor and the pressure in the Interior of the housing 12 and the bias of a spring 16, which the swash plate on the drive shaft 10 can move, the swashplate on a holder 18 supports, so that it is in a shift on the Drive shaft is pivoted.
  • a swash plate 20 can be rotated on the swash plate by means of radial and axial roller bearings 22, 24 mounted. At the Swash plate 20 attack several ball joints 26 by means of which each have a piston 28 tensile and pressure resistant with the Swash plate 20 is connected. Each piston 28 is in one Cylinder 30 slidable, the central axis parallel to Longitudinal axis of the drive shaft 10 runs. In the drawing are only two pistons shown; actually the compressor can be up to seven pistons included.
  • each piston 28 reciprocates in the corresponding cylinder 30.
  • This movement can be used to compress a refrigerant, for example CO 2 .
  • the refrigerant is sucked up from an inlet line 32 under evaporation pressure or suction pressure and conveyed into an outlet line 34 while standing under condensation pressure or evaporation pressure.
  • the refrigerant takes up small amounts of a lubricant that is present in the interior of the housing and is also present on the inner wall of the cylinders 30.
  • the outlet line 34 opens into a lubricant separator 36.
  • This has a separation space 38, in which the Lubricants at a reduction in Flow rate of the present as compressed gas Refrigerant is separated by gravity, as well as a Collection space 40 for the separated lubricant. That in Collection space 40 existing lubricant is under pressure of the refrigerant.
  • Supply line 42 connected to a controllable Valve 44 is provided.
  • the feed line 42 leads to one Supply channel 46 in the housing 12, which is connected to a radial bearing 48 for the drive shaft 10 opens.
  • an overflow line 43 connected to a valve 45 is provided. By opening the valve 45, it is possible to excess volume of the contained in the collecting space 40, deposited lubricant in the housing.
  • the drive shaft 10 is axially extending Distribution bore 50 provided which is radial extending supply bore 52 with the radial bearing 48 connected is.
  • the drive shaft 10 is also with two radially extending branch holes 54 are provided, of which one is assigned to a plain bearing 56, by means of which the Swash plate is mounted on the drive shaft 10, and the another is assigned to a radial bearing 58, which together with an axial bearing 60 in the interior of the housing 12 arranged to the drive side of the drive shaft 10 opposite end camps.
  • the radial bearing can be integrated into the housing be that a paragraph of the housing together with the rotating Drive shaft forms a narrow gap that only so much Lubricant can escape that for the "series connection" an acceptable lubricant pressure throughout the bearings can be guaranteed.
  • Figure 2 is an axial piston compressor according to shown a second embodiment.
  • Reference numerals are used, so that on the above explanations can be referred.
  • the second Embodiment the lubricant of the distribution bore 50 in the Drive shaft 10 axially fed, namely on the Figure 2 right end of the drive shaft.
  • a sealing element 62 on the end face of the drive shaft 10 provided that due to the low there Circumferential speed can be carried out with small dimensions can.
  • FIG a third embodiment An axial piston compressor according to FIG a third embodiment shown. Again, for known components used the same reference numerals as in the first embodiment, so that on the above explanations is referred.
  • the third embodiment differs from the first Embodiment a supply bore 66 in both the Swash plate 14 and the swash plate 20 are provided.
  • the lubricant provided can over the Branch bore 54 through the slide bearing 56 through which Radial bearing 22 and the swash plate 20 to the ball joints 26 get and this, especially those in the ball joints arranged articulated stones, with lubricant.
  • the pistons 28 in the cylinders 30 To supply pressure oil in the area of the friction pairing there, which can be seen as a plain bearing, a better one Ensure lubricating film.
  • the Cylinder career formed a lubricant pocket that with Lubricant is supplied through a suitable channel. The narrow gap between cylinder and piston ensures that required throttling of the lubricant throughput.

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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)
EP03015448A 1999-11-12 2000-11-10 Compresseur à piston axial Withdrawn EP1371847A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19954570A DE19954570A1 (de) 1999-11-12 1999-11-12 Axialkolbenverdichter
DE19954570 1999-11-12
EP00981247A EP1228314B1 (fr) 1999-11-12 2000-11-10 Compresseur a piston axial

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP00981247A Division EP1228314B1 (fr) 1999-11-12 2000-11-10 Compresseur a piston axial

Publications (1)

Publication Number Publication Date
EP1371847A1 true EP1371847A1 (fr) 2003-12-17

Family

ID=7928880

Family Applications (2)

Application Number Title Priority Date Filing Date
EP03015448A Withdrawn EP1371847A1 (fr) 1999-11-12 2000-11-10 Compresseur à piston axial
EP00981247A Expired - Lifetime EP1228314B1 (fr) 1999-11-12 2000-11-10 Compresseur a piston axial

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP00981247A Expired - Lifetime EP1228314B1 (fr) 1999-11-12 2000-11-10 Compresseur a piston axial

Country Status (6)

Country Link
US (1) US6910406B1 (fr)
EP (2) EP1371847A1 (fr)
JP (1) JP2003515036A (fr)
AU (1) AU1856401A (fr)
DE (2) DE19954570A1 (fr)
WO (1) WO2001036823A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10214045B4 (de) * 2002-03-28 2015-07-16 Volkswagen Ag R 744-Kompressor für eine Fahrzeug-Klimaanlage
JP4013754B2 (ja) * 2002-12-18 2007-11-28 株式会社豊田自動織機 車両用空調装置
US7181926B2 (en) 2005-05-23 2007-02-27 Visteon Global Technologies, Inc. Oil separator and muffler structure
US7520210B2 (en) 2006-09-27 2009-04-21 Visteon Global Technologies, Inc. Oil separator for a fluid displacement apparatus
JP2008115768A (ja) * 2006-11-06 2008-05-22 Sanden Corp 圧縮機のオイル戻し構造
JP5140402B2 (ja) * 2007-12-06 2013-02-06 カルソニックカンセイ株式会社 斜板式コンプレッサ
WO2018179190A1 (fr) * 2017-03-29 2018-10-04 株式会社日立産機システム Compresseur de gaz du type à alimentation en liquide
NO20211589A1 (en) * 2021-12-23 2023-06-26 Heaten As A working fluid extraction system for a displacement machine and a method of operating the system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0748936A1 (fr) * 1995-06-05 1996-12-18 Calsonic Corporation Compresseur à plateau en biais à compression variable
FR2738301A1 (fr) * 1995-09-04 1997-03-07 Toyoda Automatic Loom Works Compresseur a cylindree variable
US5842834A (en) * 1995-08-21 1998-12-01 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor employing single-headed pistons
EP0911523A2 (fr) * 1997-10-21 1999-04-28 Calsonic Corporation Plateau entre plateau-came et arbre d'entraínement
DE19907492A1 (de) * 1998-02-24 1999-08-26 Denso Corp CO¶2¶-Kompressor
DE19911635A1 (de) * 1998-03-18 1999-10-14 Toyoda Automatic Loom Works Verdichter mit veränderlichem Verdrängungsvolumen

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JPS5395730A (en) * 1977-02-01 1978-08-22 Toshiba Corp Golf training machine
US4283997A (en) * 1978-08-22 1981-08-18 Sankyo Electric Company Limited Refrigerant compressors
JPS6196188A (ja) * 1984-10-17 1986-05-14 Taiho Kogyo Co Ltd 斜板式コンプレツサ
JP2641479B2 (ja) * 1988-03-11 1997-08-13 株式会社デンソー 可変容量式斜板型圧縮機
JPH01267374A (ja) * 1988-04-15 1989-10-25 Hitachi Ltd 斜板式可変容量型圧縮機
JPH04166685A (ja) * 1990-10-31 1992-06-12 Toshiba Corp 密閉型圧縮機の油冷却装置
JPH06249146A (ja) * 1993-02-19 1994-09-06 Toyota Autom Loom Works Ltd 斜板式圧縮機
JP3417067B2 (ja) 1994-07-29 2003-06-16 株式会社豊田自動織機 可変容量型圧縮機
JPH08284835A (ja) 1995-04-18 1996-10-29 Toyota Autom Loom Works Ltd 片頭ピストン圧縮機
DE19621174A1 (de) * 1996-05-24 1997-11-27 Danfoss As Kompressor, insbesondere für Fahrzeug-Klimaanlagen
JPH09324758A (ja) * 1996-06-06 1997-12-16 Toyota Autom Loom Works Ltd カムプレート式圧縮機
JP3608299B2 (ja) * 1996-07-09 2005-01-05 株式会社豊田自動織機 両頭ピストン式圧縮機
JPH10281060A (ja) * 1996-12-10 1998-10-20 Toyota Autom Loom Works Ltd 可変容量圧縮機
JPH10196540A (ja) * 1997-01-10 1998-07-31 Toyota Autom Loom Works Ltd 圧縮機
JPH10311277A (ja) * 1997-05-13 1998-11-24 Zexel Corp 冷媒圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0748936A1 (fr) * 1995-06-05 1996-12-18 Calsonic Corporation Compresseur à plateau en biais à compression variable
US5842834A (en) * 1995-08-21 1998-12-01 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor employing single-headed pistons
FR2738301A1 (fr) * 1995-09-04 1997-03-07 Toyoda Automatic Loom Works Compresseur a cylindree variable
EP0911523A2 (fr) * 1997-10-21 1999-04-28 Calsonic Corporation Plateau entre plateau-came et arbre d'entraínement
DE19907492A1 (de) * 1998-02-24 1999-08-26 Denso Corp CO¶2¶-Kompressor
DE19911635A1 (de) * 1998-03-18 1999-10-14 Toyoda Automatic Loom Works Verdichter mit veränderlichem Verdrängungsvolumen

Also Published As

Publication number Publication date
EP1228314B1 (fr) 2004-02-11
DE19954570A1 (de) 2001-08-02
WO2001036823A1 (fr) 2001-05-25
DE50005274D1 (de) 2004-03-18
EP1228314A1 (fr) 2002-08-07
AU1856401A (en) 2001-05-30
JP2003515036A (ja) 2003-04-22
US6910406B1 (en) 2005-06-28

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