EP1228314A1 - Compresseur a piston axial - Google Patents

Compresseur a piston axial

Info

Publication number
EP1228314A1
EP1228314A1 EP00981247A EP00981247A EP1228314A1 EP 1228314 A1 EP1228314 A1 EP 1228314A1 EP 00981247 A EP00981247 A EP 00981247A EP 00981247 A EP00981247 A EP 00981247A EP 1228314 A1 EP1228314 A1 EP 1228314A1
Authority
EP
European Patent Office
Prior art keywords
lubricant
axial piston
piston compressor
bearing
housing
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.)
Granted
Application number
EP00981247A
Other languages
German (de)
English (en)
Other versions
EP1228314B1 (fr
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
Priority to EP03015448A priority Critical patent/EP1371847A1/fr
Publication of EP1228314A1 publication Critical patent/EP1228314A1/fr
Application granted granted Critical
Publication of EP1228314B1 publication Critical patent/EP1228314B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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, in particular for a vehicle air conditioning system, with a housing in the interior of which at least one bearing is arranged, an outlet line for the compressed refrigerant and with lubricant which is present in the interior of the housing.
  • Such an axial piston compressor is known for example from DE 196 21 174 AI. It is used as a compressor for that
  • Refrigerant of a vehicle air conditioning system is used and serves to draw in the refrigerant from a heat exchanger, in which it evaporates while absorbing heat at low pressure, and to compress it to a higher pressure, in which the refrigerant liquefies and / or cools in a further heat exchanger, giving off heat becomes.
  • Such compressors are known in a wide variety of designs; axial piston compressors that work with a swash plate have prevailed for various reasons.
  • the axial movement of the pistons is generated by a swash plate, the tilt angle of which can be controlled relative to the drive shaft.
  • the pistons are connected to the swash plate in a tensile and compressive manner; since the cylinders in which the pistons are slidable are stationary while the swash plate is driven, as a coupling mechanism between the swash plate and the piston either sliding blocks with plain bearings are provided, which are attached to the pistons, or a swash plate with piston rods, which are attached to the pistons in plain bearings.
  • pistons are connected directly to the swash plate, two hemispherical bearings are formed on each piston, in which the two sliding blocks are arranged so that they engage on one and the other side of the swash plate on a tread.
  • a swash plate is used, it is rotatably mounted relative to the swash plate, so that only the inclined position of the swash plate is transmitted to the swash plate, but not its rotational movement.
  • the piston rods are supported on the swash plate as well as on the pistons by a ball joint.
  • the object of the invention is therefore to ensure reliable pressure oil lubrication of the bearings in an axial piston compressor of the type mentioned at the outset, without the need for a separate oil pump, lubrication still being achieved should, which goes beyond the lubrication of the bearing points by the lubricant mist inside the housing.
  • 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 which can supply the necessary lubricant to the bearing points in the interior of the housing.
  • this lubricant circuit is based on a return of the proportion of the lubricant which inevitably leaves the axial piston compressor together with the compressed refrigerant, and on the use of the pressure difference between the compressor side and the interior of the housing of the axial piston compressor. Due to this high pressure difference between the compressor side and the interior of the housing, there is a very high lubricant throughput without having to do so separately
  • the lubricant separator provided according to the invention represents a comparatively simple component which does not entail high costs.
  • a suitable throttling within the lubricant pressure circuit thus formed provides the necessary resistance against the lubricant flowing too quickly out of the separator. Such throttling occurs automatically, for example, when a plain bearing is supplied; the narrow bearing gap limits the lubricant flow. If, on the other hand, a rolling bearing is lubricated, a cover plate may have to be used in order to appropriately limit the discharge cross-section.
  • the construction according to the invention is thus characterized in that the last bearing to be supplied is also supplied with lubricant under high pressure, ie compression pressure.
  • the bearings themselves represent throttling points on the low-pressure side, ie are either sealed off on the low-pressure side or, because of their construction - this applies in particular to plain bearings - an extremely efficient throttle on the low-pressure side.
  • the oil pressure is at the bearing or bearing gap.
  • the bearings are connected in series with regard to their lubricating oil supply and are designed so that even the last bearing to be supplied is supplied with oil under almost unchanged high pressure. It is only because of this construction that it is possible to replace an oil pump with a high-pressure oil separator without replacing it, without the supply of oil to the bearings suffering from high pressure.
  • the plain bearings with "narrow gaps" are preferably initially supplied with oil, since plain bearings represent efficient throttle points towards the low pressure side due to the design. If, due to the design, rolling or needle bearings have to be supplied first, they should be sealed to the low pressure side.
  • the essence of the present invention is to be understood that the lubricant is conveyed from the lubricant separator to the lubricant channel solely on the basis of the pressure difference between the compression pressure of the refrigerant and the internal pressure of the housing, and is supplied to the bearings under the appropriate pressure. This means that all bearings are supplied with lubricant under high pressure without the need for a separate oil pump.
  • the lubricant separator is arranged on the pressure side of the circuit, either between the compressor and a pressure-side heat exchanger or between the pressure-side heat exchanger and an expansion valve.
  • the supply line is provided with a controllable valve. With this valve, the supply line can be closed during the standstill of the axial piston compressor, so that the high pressure present on the compressor side
  • the controllable valve could also be dispensed with. If the compressor stops only for a short time, there is still no pressure equalization between the pressure side of the compressor and the low pressure side. Thus, the compressor must work against a high pressure when restarted; however, lubricants are also immediately available. On the other hand, the compressor must first build up pressure after a long standstill, which has led to pressure equalization so that lubricant that is not directly under pressure is also supplied; it does not initially work under high load, so that full lubrication is not immediately necessary. The lubrication also improves with increasing compressor load.
  • the controllable valve could be replaced by a throttle point if it is ensured that the pressure equalization occurs primarily at other points in the circuit when the compressor is at a standstill, for example by a separate valve.
  • a throttling line could also be used, in which the necessary throttling is brought about by the various pressure losses in the lubricant supply, in particular by channels in the compressor.
  • An overflow line is preferably provided, which leads from the lubricant separator to the interior of the housing. In this way, excess lubricant that accumulates in the collecting space can be removed if necessary.
  • a controllable valve can be provided in the overflow line, which valve is opened depending on, for example, a level sensor in the collecting space.
  • the 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 the lubricant returned to the bearings, which was warmed by the refrigerant during the compression stroke, is returned to its initial temperature.
  • a drive shaft is provided, which is provided with an axial distribution bore.
  • An axial distribution hole in the drive shaft enables To reach almost all important bearing points inside the housing of the axial piston compressor with particularly little effort.
  • the outlay here is significantly less than in the case of a solution in which the corresponding lubricant channels to all bearing points are formed in the housing of the compressor.
  • the distribution bore preferably opens at an end face of the drive shaft arranged in the interior of the housing, that is to say the end face which lies opposite the drive end of the drive shaft.
  • a swash plate which is arranged displaceably on the drive shaft by means of a slide bearing, a branch bore being provided in the drive shaft in the region of the slide bearing and connecting the slide bearing to the distribution bore.
  • the plain bearing is very difficult to lubricate due to the lubricant mist inside the housing; the branch hole makes it possible to supply the required amount of lubricant to the plain bearing. The amount supplied can be determined by the cross section of the branch hole.
  • a supply bore is formed in the swash plate, which is supplied with lubricant through the slide bearing, wherein sliding blocks act on the swash plate and are supplied with lubricant by means of the supply bore of the swash plate.
  • the sliding blocks which only perform a slightly oscillating movement and are therefore also difficult to lubricate due to the lubricant mist, are specifically supplied with lubricant under pressure.
  • the drive shaft is supported by at least one assembly comprising a radial bearing and an axial bearing, this assembly being supplied with lubricant by a branch bore from the drive shaft, and the lubricant first flowing through the radial bearing and then through the axial bearing.
  • the series connection of the bearings used with regard to the lubricant flow enables both bearings to be lubricated with comparatively little effort. Since the radial bearing is the most endangered in terms of service life due to the available installation space and the resulting bearing size, this bearing is first supplied with lubricant; the lubricant flow emerging from the radial bearing is then led to the axial bearing.
  • the supply of the bearings can, as is preferably provided, be adjusted by means of sealing disks which form a defined leakage gap.
  • C0 2 is used as the refrigerant.
  • an air conditioning system with the refrigerant C0 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 about 5 bar and the compression pressure is about 20 bar.
  • Figure 1 is a schematic sectional view of an axial piston compressor according to a first embodiment of the invention.
  • Axial piston compressor according to a second embodiment of the invention.
  • Axial piston compressor according to a third embodiment of the invention.
  • an axial piston compressor according to a first embodiment is shown schematically. It contains a drive shaft 10 which is mounted in a housing 12. With the drive shaft 10, a swash plate 14 is rotatably connected between a position in which they are approximately perpendicular to Longitudinal axis of the drive shaft 10 extends, and a maximum tilted position can be pivoted, which is shown in Figure 1.
  • the position that the swash plate 14 assumes during operation is a function of the difference between the suction pressure of the compressor and the pressure in
  • a swash plate 20 is rotatably mounted on the swash plate by means of radial and axial roller bearings 22, 24.
  • a plurality of ball joints 26 engage, by means of which a piston 28 is tension and pressure-resistant with the
  • Each piston 28 is displaceable in a cylinder 30, the central axis of which runs parallel to the longitudinal axis of the drive shaft 10. Only two pistons are shown in the drawing; in fact, the compressor can contain up to seven pistons.
  • each piston 28 reciprocates in the corresponding cylinder 30.
  • This movement can be used to compress a refrigerant, for example C0 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.
  • the lubricant present in the collecting space 40 is under the pressure of the refrigerant.
  • a compressor line 39 for the compressed refrigerant leads from the separation space 38 to a heat exchanger.
  • any common separation principle can be used to implement the lubricant circuit.
  • a supply line 42 which is provided with a controllable valve 44, is connected to the collecting space 40 at the lowest point.
  • the feed line 42 leads to a supply channel 46 in the housing 12, which opens at a radial bearing 48 for the drive shaft 10.
  • An overflow line 43 which is provided with a valve 45, is connected to the separating space 38. By opening the valve 45, it is possible to return an excess volume of the separated lubricant contained in the collecting space 40 into the housing.
  • the drive shaft 10 is provided with an axially extending distribution bore 50 which is connected to the radial bearing 48 via a radially extending supply bore 52.
  • the drive shaft 10 is further provided with two radially extending branch bores 54, one of which is assigned to a slide bearing 56, by means of which the swash plate is mounted on the drive shaft 10, and the other is assigned to a radial bearing 58, which together with an axial bearing 60 inside the housing 12 arranged, opposite to the drive side of the drive shaft 10 supports.
  • valve 44 of the supply line 42 is open, this flows in the
  • Collection chamber 40 contains lubricant due to the difference between the pressure in the separating chamber 38 and the interior of the housing 12 through the supply line 42 to the supply channel 46. From there it flows via the radial bearing 48 and the supply bore 52 into the distribution bore 50 of the drive shaft 10. From this it can reach the various bearing points in the interior of the housing via the branch bores 54.
  • the plain bearing 56 is lubricated, as is the assembly of the radial bearing 58 and the axial bearing 60.
  • the radial bearing 58 is designed such that the lubricant provided is guided to the axial bearing after flowing through the radial bearing.
  • the radial bearing can be integrated into the housing in such a way that a housing shoulder forms a narrow gap together with the rotating drive shaft, which gap is only so much
  • Lubricant can escape so that an acceptable lubricant pressure can be guaranteed for the "series connection" of the bearings.
  • the return of the lubricant supplied to the interior of the housing to the lubricant separator is ensured in that there is always a lubricant mist in the interior of the housing due to the rotating components of the axial piston compressor. This is also reflected on the inner wall of the cylinder 30, from where it passes through the compressed refrigerant back into the lubricant separator.
  • FIG. 1 An axial piston compressor according to a second embodiment is shown schematically in FIG.
  • the same reference numerals are used here, so that reference can be made to the above explanations.
  • the lubricant is supplied axially to the distribution bore 50 in the drive shaft 10, specifically at the right end of the drive shaft with respect to FIG.
  • a sealing element 62 is provided on the front side of the drive shaft 10, which, owing to the small amount there
  • Circumferential speed can be carried out with small dimensions.
  • Branch bore 54 is provided so that this bearing is reliably supplied with lubricant.
  • the lubricant flows from this bearing to an axial bearing 64, which supports the holder 18.
  • the lubricant is again supplied radially here, but this time in the area of the radial bearing 58. From there it can flow to the slide bearing 56 and the radial bearing 48 via the distribution bore 50.
  • a supply bore 66 is provided in both the swash plate 14 and the swash plate 20 in the third embodiment.
  • the lubricant provided can thus pass through the branch bore 54 through the slide bearing 56, through the radial bearing 22 and the swash plate 20 to the ball joints 26 and supply them with lubricant, in particular the articulated stones arranged in the ball joints.
  • Cylinder race formed a lubricant pocket, which is supplied with lubricant through a suitable channel.
  • the narrow gap between the cylinder and piston ensures the necessary throttling of the lubricant throughput.

Landscapes

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

Abstract

La présente invention concerne un compresseur à piston axial destiné à un agent de refroidissement, en particulier à un système de climatisation de véhicule. Ledit compresseur comprend un boîtier (12) dont l'intérieur comprend au moins un palier (22, 24, 26, 48, 56, 58, 60, 64), un conduite de sortie (34) destinée à l'agent de refroidissement comprimé, ainsi qu'un lubrifiant se trouvant à l'intérieur du boîtier (12). L'objet de l'invention est l'amélioration de la lubrification. Pour cela, au moins un canal de lubrifiant se trouve dans le boîtier, ledit canal servant à approvisionner le palier en lubrifiant, et l'intérieur du boîtier comporte également un séparateur de lubrifiant (36) relié à la conduite de sortie (34) d'agent de refroidissement et comprenant un espace d'accumulation (40) destiné au lubrifiant séparé de l'agent de refroidissement comprimé, ainsi qu'une conduite d'amenée (42) reliant l'espace d'accumulation au canal de lubrifiant (46), le lubrifiant étant acheminé seul du séparateur de lubrifiant au canal de lubrifiant, en raison de la différence de pression existant entre la pression de compression du lubrifiant et la pression interne du boîtier.
EP00981247A 1999-11-12 2000-11-10 Compresseur a piston axial Expired - Lifetime EP1228314B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03015448A EP1371847A1 (fr) 1999-11-12 2000-11-10 Compresseur à piston axial

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19954570 1999-11-12
DE19954570A DE19954570A1 (de) 1999-11-12 1999-11-12 Axialkolbenverdichter
PCT/EP2000/011135 WO2001036823A1 (fr) 1999-11-12 2000-11-10 Compresseur a piston axial

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP03015448A Division EP1371847A1 (fr) 1999-11-12 2000-11-10 Compresseur à piston axial

Publications (2)

Publication Number Publication Date
EP1228314A1 true EP1228314A1 (fr) 2002-08-07
EP1228314B1 EP1228314B1 (fr) 2004-02-11

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 Before (1)

Application Number Title Priority Date Filing Date
EP03015448A Withdrawn EP1371847A1 (fr) 1999-11-12 2000-11-10 Compresseur à 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

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPH08326655A (ja) * 1995-06-05 1996-12-10 Calsonic Corp 斜板式コンプレッサ
JP3282457B2 (ja) * 1995-08-21 2002-05-13 株式会社豊田自動織機 片頭ピストン型圧縮機
JPH0972277A (ja) * 1995-09-04 1997-03-18 Toyota Autom Loom Works Ltd 可変容量圧縮機
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
JPH11125176A (ja) * 1997-10-21 1999-05-11 Calsonic Corp 斜板式可変容量圧縮機
JP3851971B2 (ja) * 1998-02-24 2006-11-29 株式会社デンソー Ｃｏ２用圧縮機
JPH11264371A (ja) * 1998-03-18 1999-09-28 Toyota Autom Loom Works Ltd 可変容量型圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0136823A1 *

Also Published As

Publication number Publication date
WO2001036823A1 (fr) 2001-05-25
AU1856401A (en) 2001-05-30
JP2003515036A (ja) 2003-04-22
EP1371847A1 (fr) 2003-12-17
US6910406B1 (en) 2005-06-28
DE50005274D1 (de) 2004-03-18
DE19954570A1 (de) 2001-08-02
EP1228314B1 (fr) 2004-02-11

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