EP0809026A1 - Compresseur - Google Patents

Compresseur Download PDF

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Publication number
EP0809026A1
EP0809026A1 EP97100207A EP97100207A EP0809026A1 EP 0809026 A1 EP0809026 A1 EP 0809026A1 EP 97100207 A EP97100207 A EP 97100207A EP 97100207 A EP97100207 A EP 97100207A EP 0809026 A1 EP0809026 A1 EP 0809026A1
Authority
EP
European Patent Office
Prior art keywords
swash plate
arrangement
spring
compressor according
piston
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
EP97100207A
Other languages
German (de)
English (en)
Other versions
EP0809026B1 (fr
Inventor
Harry Stentoft-Nissen
Stig Helmer. Jorgensen
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
Danfoss AS
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 Danfoss AS filed Critical Danfoss AS
Priority to US08/859,992 priority Critical patent/US5894782A/en
Publication of EP0809026A1 publication Critical patent/EP0809026A1/fr
Application granted granted Critical
Publication of EP0809026B1 publication Critical patent/EP0809026B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the invention relates to a compressor with at least one piston movable in a cylinder, a drive shaft and a swash plate arrangement between the piston and the drive shaft, which has a swash plate with a variable angle of inclination, and with a spring arrangement which acts on the swash plate arrangement in the direction of minimal displacement.
  • Compressors of this type are used, for example, in motor vehicle air conditioning systems.
  • attempts have been made in recent years to replace the environmentally harmful refrigerants used to date.
  • refrigerants will escape in the event of an accident and escape into the environment.
  • CO 2 carbon dioxide
  • relatively high pressures are required with this refrigerant. Accordingly, the force to be applied by the spring must be correspondingly large.
  • the invention has for its object to be able to operate a compressor even at higher pressures.
  • the spring arrangement is preferably arranged adjacent to a wall which surrounds an interior of the compressor.
  • the space available within the compressor is thus optimally used. It is not necessary to enlarge the diameter of the compressor. Nevertheless, it becomes possible to arrange the spring arrangement radially relatively far outwards.
  • the spring arrangement is preferably arranged essentially on the same radius as the piston. This counteracts the force exerted by the piston where it arises. The piston and force application location of the spring arrangement are then essentially on the same axial line.
  • the spring arrangement is advantageously clamped between the swash plate arrangement and a rotatably mounted base plate.
  • the large diameter of the spring arrangement can thus also be maintained on the side facing away from the swash plate arrangement.
  • the spring can thus be accommodated overall in an at least approximately cylindrical space without it having to taper in any way for support purposes.
  • the spring arrangement is arranged radially outside an adjustment mechanism for the angle of inclination of the swash plate. This also ensures that the forces of the spring arrangement act approximately where the counter forces of the piston or pistons arise. In addition, this ensures that the spring arrangement and the adjustment mechanism do not interfere with one another. Radially within the spring arrangement, there is sufficient space to accommodate the adjustment mechanism.
  • the swash plate arrangement preferably has a pressure plate against which the spring arrangement rests. This provides a relatively large area which is able to absorb the forces of the spring arrangement and to pass them on to the swash plate arrangement.
  • the adjustment mechanism is passed through an opening in the pressure plate. This ensures that the compressor does not need a greater overall height, even though the pressure plate is used.
  • the pressure plate and the adjustment mechanism can then be nested, so to speak. Despite the presence of the adjustment mechanism, the pressure plate can be acted upon where this is desired. There are no restrictions with regard to the arrangement of the adjustment mechanism by the spring arrangement.
  • the pressure plate advantageously has a neck which surrounds the drive shaft and which bears against a bearing arrangement of the swash plate which is axially displaceable on the drive shaft.
  • This neck ie a circumferential projection axially protruding from the pressure plate, secures on the one hand, a relatively good axial guidance of the pressure plate on the drive shaft. This prevents the pressure plate from tilting in relation to the drive shaft.
  • this provides a simple way of transmitting the forces from the spring arrangement via the pressure plate to the swash plate arrangement.
  • the swash plate arrangement preferably has a swash plate that is rotatable both with respect to the swash plate and with respect to the piston.
  • the swashplate will then rotate, somewhere between the speed of the drive shaft at which the swashplate rotates and zero, which corresponds to the "speed" of the pistons.
  • the speed of the swashplate will automatically adjust itself so that the smallest amount of energy is required. In other words, the losses are kept as small as possible.
  • the swash plate can act radially relatively far outward, so that the pistons are loaded essentially purely axially. This ensures that the pistons in the cylinders are not loaded on one side, which reduces wear.
  • the swash plate is advantageously supported radially within or in the region of the adjustment mechanism in relation to the swash plate. It is thereby achieved that the pressure forces of the pistons are more or less transmitted directly to the pressure plate.
  • the spring arrangement has a spring arranged coaxially around the drive shaft.
  • the spring then surrounds the drive shaft, possibly at a distance. This is a very simple option, especially with regard to assembly.
  • the spring has a non-uniform pressure distribution in the circumferential direction and an anti-rotation and positioning device is provided which fixes the area with the highest pressure in the area of the top dead center of the swash plate.
  • an anti-rotation and positioning device is provided which fixes the area with the highest pressure in the area of the top dead center of the swash plate.
  • the area with the highest counterforce can be positioned slightly before the top dead center of the swash plate. If the direction of rotation is not exactly known or a change in the direction of rotation is expected, this area can also be fixed exactly at the top dead center. This is sufficient to be able to absorb the loads in the vicinity of top dead center.
  • the spring arrangement has a plurality of individual springs which are arranged in a strip at a predetermined distance around the drive shaft.
  • the desired spring force amplification can also be achieved on the one hand with such individual springs.
  • the force on the swash plate arrangement then results from the sum of the forces of the individual springs.
  • the load can also be compensated for where it arises, namely more or less on the same axial line on which the pistons are arranged.
  • the individual springs have different spring constants. This takes into account the fact that, as stated above, an uneven force distribution acts on the swash plate arrangement in the circumferential direction. The counterforce is greatest where the piston is close to its top dead center. It is therefore sufficient to use the correspondingly strong springs there. The remaining springs can then be weaker. Basically, they only serve to stabilize the swash plate arrangement, that is, they are intended to prevent indefinite tipping.
  • At least one single spring is preferably arranged at a predetermined angle before the top dead center of the swash plate. As stated above, this is the point where the highest load is expected. If the machine is to be operated in both directions of rotation, two single springs are expediently used.
  • a compressor 1 (FIG. 1) has a drive shaft 2. It is therefore also known as a shaft-operated compressor.
  • the drive shaft 2 is guided through a shaft bushing 3 into a housing which consists of a front part 26, a middle part 27 and a rear part 28.
  • the housing parts 26, 27, 28 are connected to one another in the axial direction by known means, for example threaded bolts 29.
  • a piston 9 which can be moved back and forth in the axial direction.
  • the piston 9 or the piston 9 is driven by a swash plate arrangement 30.
  • the swash plate arrangement 30 has a swash plate 5 which is rotatably mounted on a swash plate 4.
  • needle bearings 6 or other friction-reducing bearings are provided between the swash plate 5 and the swash plate 4.
  • the swash plate 5 in turn is connected to the piston 9 via slide bearings 7.
  • the sliding bearings 7 have hemispherical sliding shoes 8 which are front and rear, i.e. rest axially on both sides of the swashplate.
  • the sliding shoes 8 are received in correspondingly negatively formed bearing shells 31, which in turn are fastened in the piston 9.
  • the swash plate 5 can rotate freely in relation to the piston 9 through the slide bearing 7.
  • the radial orientation of the swash plate 5 relative to the piston 9 can also change. This means, for example, that the swash plate 5 acts radially further outwards or further inwards with respect to the piston 9 when the inclination of the swash plate 4 changes. In the position of the swash plate 4 shown, the swash plate is located radially relatively far outwards. When the angle between the swash plate 4 and the drive shaft 2 increases, the swash plate 5 retracts correspondingly further radially inwards with its sliding surface. It is thereby achieved that the piston 9 can always be subjected to a force which acts essentially parallel to its direction of movement.
  • the cylinder 10 has a suction valve opening 11 through which a coolant can be sucked in.
  • a pressure valve opening 12 is also provided, via which compressed refrigerant can be output from the cylinder.
  • the pressure valve opening 12 can be closed by a valve element 32.
  • Corresponding valves for the suction valve opening 11 are not shown here, but are available if required.
  • a base plate 16 is rotatably connected to the drive shaft 2. With the base plate 16, an articulated arm 13 is rotatably connected. When the base plate 16 rotates, the articulated arm 13 is therefore taken along.
  • the swash plate 4 is connected to the articulated arm 13 at a pivot point 14, i.e. it can be pivoted about this pivot point 14.
  • the articulated arm 13 is in turn connected to the base plate 16 via a pivot point 15.
  • a flange 25 is arranged on the base plate 16 and connected to it in a rotationally fixed manner.
  • a pressure plate 18 is arranged displaceably in the axial direction.
  • a compression spring 17 is arranged and clamped between the pressure plate 18 and the flange 25. The compression spring 17 presses the pressure plate 18 forward, ie to the left in the figure, and thus also pushes the swash plate 4 in this direction. Since the swash plate 4 is connected to the base plate 16 via the articulated arm 13, this causes the swash plate to assume a slight inclination, so that the piston 9 performs a correspondingly small stroke.
  • the swash plate 4 is not only pivotable about its pivot point, it also rotates about a pivot point 19 of a guide arrangement 20 which, together with the pressure plate 18, can be displaced on the drive shaft 2 in the axial direction.
  • the pressure plate 18 has a through opening 35 through which the articulated arm 13 is guided.
  • the compression spring 17 has a relatively large diameter, i.e. it coaxially surrounds the drive shaft 2 and can additionally also comprise the articulated arm 13 on the outside. This makes it possible to pressurize the pressure plate 18 relatively far outwards without the function of the articulated arm 13 being impaired by the compression spring 17. This has a correspondingly favorable effect on the dimensioning of the compression spring 17 and the size of the compressor 1.
  • the compression spring 17 coaxially surrounds the shaft 2. It engages on the pressure plate 18 relatively far out, namely in the area of its radial edge. Thus the compression spring 18 practically has the largest diameter that is possible. It is adjacent to the wall of the housing interior 33, which is formed here by the central part 27. Of course, a certain distance is maintained because the compression spring 18 rotates together with the drive shaft 2.
  • the compression spring 17 virtually forms a wooden cylinder.
  • the cylinder wall is located on the same circumferential line on which the pistons 9 are also arranged.
  • the pressure plate 18 has a neck 36 with which it is mounted on the drive shaft 2.
  • the neck 36 surrounds the drive shaft and ensures that the pressure plate 18 is oriented perpendicular to the drive shaft even in the event of a possibly one-sided load 2 maintains.
  • the neck 36 of the pressure plate 18 acts against the guide arrangement 20 for the swash plate 4.
  • the compression spring 17 Due to its design as a helical spring, which is flattened on its two end faces, the compression spring 17 has a non-uniform pressure distribution in the circumferential direction. This results, among other things, from the fact that the end windings 37, 38 of the compression spring 17 have a decreasing strength.
  • the compression spring 17 is now aligned and held relative to the pressure plate 18, for example by a pin 39, that the angular region with the greatest force is below the top dead center of the swash plate 4.
  • the top dead center is the point at which the piston 9 assumes its greatest deflection and the cylinder 10 its smallest volume. Shortly before this operating position, the gas volume enclosed in the cylinder 10 exerts the greatest back pressure on the piston and thus also on the compression spring 17.
  • the piston 9 is provided on its outer surface with a groove 21.
  • a pin 22 protrudes into the groove 21 and is formed, for example, by the end of a screw 23 which has been screwed in radially from the outside through the central part 27 of the housing. Together with the groove 21, the pin 22 forms an anti-rotation device for the piston 9.
  • the piston 9 is pulled out to a certain extent into a housing interior 33 during its back and forth movement. It is almost inevitable that a small amount of, in particular, gaseous refrigerant escapes or leaks into the housing interior 33. This constant inflow of refrigerant leads to an increase in the pressure in the interior 33 of the housing.
  • an opening 24 is provided which is connected to a valve 34 shown schematically. With the help of the valve 34, the pressure in the interior of the housing can be reduced.
  • the other side of the valve can be connected to the suction valve opening 11, for example, so that the pressure in the housing interior 33 can be reduced to a maximum of the suction pressure of the compressor.
  • the inclined position of the swash plate 4 and thus the delivery capacity of the compressor 1 can now be controlled. If the pressure in the housing interior 33 is the same or almost the same as the pressure at the pressure valve opening, then both ends of the piston 9 are almost in equilibrium. In this case, only slight reaction forces act on the swash plate 4, so that the compression spring 17 moves the swash plate 4 into the position shown in the figure. If, on the other hand, the pressure in the housing interior 33 is reduced, higher forces act against the spring 17, so that the inclination of the swash plate 4 is increased.
  • the drive shaft 2 When the drive shaft 2 is rotated, it rotates the base plate 16.
  • the base plate 16 takes the swash plate 4 with it via the articulated arm 13.
  • the swash plate 5 is made to wobble so that the piston 9 is reciprocated.
  • the swash plate 4 is more or less inclined by the corresponding reaction forces.
  • the position of the swash plate 5 relative to the slide bearing 7 also changes, i.e. the slide bearing 7 between the swash plate 5 and the piston 9 is located radially more or less outside on the swash plate. A position arises where the least forces occur.
  • the swash plate 5 can continue to rotate freely with respect to the piston 9. You can also rotate freely with respect to the swash plate 4, so that a speed of rotation of the swash plate 5 will be set at which the frictional forces are lowest. In this way it is possible for the compressor 1 to operate with a relatively high degree of efficiency and a relatively small amount of wear.
  • the forces on the piston 9 are limited almost exclusively to the axial direction, so that tilting of the piston 9 relative to the cylinder 10 is avoided. As a result, the wear remains small and the tightness of the compressor 1 is correspondingly high.
  • Fig. 2 shows a drive shaft 2 with a swash plate arrangement, in which only the design of the spring arrangement has changed.
  • the other parts correspond to those of Fig. 1. They are therefore provided with the same reference numerals.
  • three individual springs 41, 42, 43 are now provided, which are also designed as compression springs and are arranged between the flange 25 and the pressure plate 18.
  • the compression springs 41-43 are also arranged so that they are as wide as possible engage radially on the outside, ie in the area of the edge of the pressure plate 18.
  • the springs 41-43 are arranged on a circle. While this is advantageous, it is not mandatory.
  • the springs also form an isosceles triangle, the base of which is delimited by the springs 41, 42. This configuration is also advantageous, but not mandatory.
  • the spring 43 has a weaker spring constant than the other two springs 41, 42, which are arranged adjacent to the articulated arm 13.
  • the articulated arm 13 is located at the point where the swash plate 4 has its top dead center.
  • the springs 41, 42 are at a predetermined angle before and after this top dead center, i.e. exactly at the point where the gas compressed in the cylinder 10 develops its greatest resistance before it can escape from the cylinder 10. Basically, only one of the two springs 41, 42 would be necessary.
  • the other of the two springs 42, 41 is provided so that the compressor can be operated in both directions of rotation.
  • the third spring 43 basically serves only for stabilization in order to prevent the pressure plate 18 from tipping over.
  • a greater spring force can also be generated with the three individual springs than with the known individual spring which is arranged around the drive shaft 2. Regardless of whether the spring assembly is formed by a compression spring 17 which surrounds the drive shaft 2 with the largest possible radius, or whether it is formed by individual springs 41-43, you can operate a compressor at high pressure without the Size must be increased significantly.
  • FIG. 3 shows a third embodiment of a compressor, which essentially corresponds to that of FIG. 1.
  • the pistons 9 ' are driven in the present case via piston rods 50 which are connected to the swash plate 5 via a ball joint 51.
  • the ball joint 51 only allows a pivoting movement of the piston rod 50 relative to the swash plate 5. No other movement is possible.
  • the swash plate 5 can therefore neither move in the circumferential direction nor in the radial direction relative to the ball joint 51. Accordingly, the speed difference between the stationary pistons 9 'and the rotating shaft 2 must be completely absorbed by the bearings 6 between the swash plate 4 and the swash plate 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP97100207A 1996-05-24 1997-01-09 Compresseur Expired - Lifetime EP0809026B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US08/859,992 US5894782A (en) 1996-05-24 1997-05-21 Compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19621174A DE19621174A1 (de) 1996-05-24 1996-05-24 Kompressor, insbesondere für Fahrzeug-Klimaanlagen
DE19621174 1996-05-24

Publications (2)

Publication Number Publication Date
EP0809026A1 true EP0809026A1 (fr) 1997-11-26
EP0809026B1 EP0809026B1 (fr) 2001-07-18

Family

ID=7795356

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97100207A Expired - Lifetime EP0809026B1 (fr) 1996-05-24 1997-01-09 Compresseur

Country Status (8)

Country Link
US (1) US5826490A (fr)
EP (1) EP0809026B1 (fr)
AT (1) ATE203306T1 (fr)
DE (2) DE19621174A1 (fr)
DK (1) DK0809026T3 (fr)
FR (1) FR2749045B1 (fr)
GB (1) GB2313416B (fr)
PT (1) PT809026E (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19947677B4 (de) 1999-10-04 2005-09-22 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter
DE19954570A1 (de) * 1999-11-12 2001-08-02 Zexel Valeo Compressor Europe Axialkolbenverdichter
DE19960284A1 (de) * 1999-12-14 2001-08-02 Zexel Valeo Compressor Europe Axialgleitringdichtung, insbesondere für einen Verdichter einer Fahrzeug-Klimaanlage
DE10058447C1 (de) * 2000-11-24 2002-01-17 Zexel Valeo Compressor Europe Axialkolbenverdichter für Fahrzeugklimaanlagen
EP1249604A1 (fr) 2001-04-11 2002-10-16 Zexel Valeo Climate Control Corporation Piston pour compresseur à plateau en biais
JP2003028057A (ja) 2001-07-13 2003-01-29 Toyota Industries Corp 可変容量型圧縮機における絞り構造
DE10135726A1 (de) * 2001-07-21 2003-02-06 Volkswagen Ag Taumelscheibenkompressor
EP1281864A1 (fr) 2001-08-03 2003-02-05 Zexel Valeo Climate Control Corporation Agencement de plateau oscillant pour un compresseur
EP1329634B1 (fr) 2002-01-17 2008-11-19 Zexel Valeo Climate Control Corporation Compresseur à plateau en biais ou à plateau oscillant
DE10229152A1 (de) * 2002-06-28 2004-01-29 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter für Fahrzeugklimaanlagen mit Kolben in Compound-Bauweise
DE10250649A1 (de) * 2002-10-30 2004-05-13 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter, insbesondere CO2-Verdichter für Kraftfahrzeugklimaanlagen
US6860188B2 (en) * 2003-06-20 2005-03-01 Visteon Global Technologies, Inc. Variable displacement compressor hinge mechanism
US7234385B2 (en) * 2004-07-21 2007-06-26 Parker-Hannifin Corporation Return to neutral mechanism for hydraulic pump
DE102004056929B4 (de) * 2004-11-25 2014-11-27 Schaeffler Technologies Gmbh & Co. Kg Verfahren zur Herstellung einer Lagereinheit

Citations (5)

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US4174191A (en) * 1978-01-18 1979-11-13 Borg-Warner Corporation Variable capacity compressor
US4178136A (en) * 1978-06-02 1979-12-11 General Motors Corporation Guide shoe members for wobble plate compressor
US4526516A (en) * 1983-02-17 1985-07-02 Diesel Kiki Co., Ltd. Variable capacity wobble plate compressor capable of controlling angularity of wobble plate with high responsiveness
EP0292288A1 (fr) * 1987-05-19 1988-11-23 Sanden Corporation Compresseur à déplacement variable avec membre incliné prétendu
US5387091A (en) 1992-08-21 1995-02-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity type swash plate compressor

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JPS59221480A (ja) * 1983-05-31 1984-12-13 Showa Seiki Kogyo Kk 往復形オイルフリ−・ガス圧縮機
JPS6371501A (ja) * 1986-09-12 1988-03-31 Ckd Corp アキシヤル式エアモ−タ
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JPH04109481U (ja) * 1991-03-08 1992-09-22 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
DE4211695C2 (de) * 1991-04-08 1996-11-14 Zexel Corp Taumelscheibenverdichter
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JP2572690Y2 (ja) * 1992-09-02 1998-05-25 サンデン株式会社 斜板式圧縮機のピストン回転防止機構
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Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4174191A (en) * 1978-01-18 1979-11-13 Borg-Warner Corporation Variable capacity compressor
US4178136A (en) * 1978-06-02 1979-12-11 General Motors Corporation Guide shoe members for wobble plate compressor
US4526516A (en) * 1983-02-17 1985-07-02 Diesel Kiki Co., Ltd. Variable capacity wobble plate compressor capable of controlling angularity of wobble plate with high responsiveness
EP0292288A1 (fr) * 1987-05-19 1988-11-23 Sanden Corporation Compresseur à déplacement variable avec membre incliné prétendu
US5387091A (en) 1992-08-21 1995-02-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity type swash plate compressor

Also Published As

Publication number Publication date
PT809026E (pt) 2001-10-31
GB2313416B (en) 2000-02-09
FR2749045B1 (fr) 2001-01-05
DE59704059D1 (de) 2001-08-23
DK0809026T3 (da) 2001-11-19
GB2313416A (en) 1997-11-26
US5826490A (en) 1998-10-27
DE19621174A1 (de) 1997-11-27
GB9710499D0 (en) 1997-07-16
FR2749045A1 (fr) 1997-11-28
EP0809026B1 (fr) 2001-07-18
ATE203306T1 (de) 2001-08-15

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