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EP0190013A2 - Variable capacity compressor - Google Patents

Variable capacity compressor

Info

Publication number
EP0190013A2
EP0190013A2 EP19860300455 EP86300455A EP0190013A2 EP 0190013 A2 EP0190013 A2 EP 0190013A2 EP 19860300455 EP19860300455 EP 19860300455 EP 86300455 A EP86300455 A EP 86300455A EP 0190013 A2 EP0190013 A2 EP 0190013A2
Authority
EP
Grant status
Application
Patent type
Prior art keywords
plate
inclined
chamber
angle
surface
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Withdrawn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
EP19860300455
Other languages
German (de)
French (fr)
Other versions
EP0190013A3 (en )
Inventor
Kiyoshi Terauchi
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.)
Sanden Holdings Corp
Original Assignee
Sanden Holdings Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0873Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878Pistons
    • F04B27/0886Piston shoes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/1809Controlled pressure
    • F04B2027/1813Crankcase pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/1822Valve-controlled fluid connection
    • F04B2027/1831Valve-controlled fluid connection between crankcase and suction chamber
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804Controlled by crankcase pressure
    • F04B2027/184Valve controlling parameter
    • F04B2027/1859Suction pressure

Abstract

A variable capacity compressor (40) has an inclined plate (10) which is rotated by a rotor (8) attached to a drive shaft (4). The rotary motion is converted by a pair of shoes (19) which make sliding contact with both faces of the plate (10) into reciprocating motion of a piston (21) so that fluid may be pumped from a suction chamber (27) into a discharge chamber (28). The shoes (19) have spherically curved surfaces which allow the plate (10) to pivot relatively to the piston (21) and which are arranged to be coincident with the surface of a notional common sphere of radius (R) so as to prevent pivoting of the plate (10) from causing a gap to appear between the plate (10) and the shoes (19). A bellows (34) is used to control the pressure in a chamber (1a) so that changes of pressure are used to cause the plate (10) to pivot about a pin (11) and thereby alter the stroke of the piston (21).

Description

  • [0001]
    The invention relates to an inclined plate type compressor suitable for use in a refrigerator, and more particularly to one having variable capacity.
  • [0002]
    In known compressors which compress fluid by converting the rotary motion of an inclined plate into the reciprocating, motion of pistons, the swept volumes are altered by changing the stroke length of the pistons, which are connected to the inclined plate, by varying the angle of inclination of the inclined plate.
  • [0003]
    The inclined plate comprises a cam rotor and a swash plate. The angle of the cam rotor, which is connected to a rotary shaft, can be varied and, since the swash plate moves with the motion of the cam rotor, the angle of inclination of the swash plate varies with the change in angle of the cam rotor. The pistons are connected to the swash plate via connecting rods and their stroke length varies with the variations in the angle of inclination of the swash plate. In this manner, the total swept volume of the compressor is altered.
  • [0004]
    However, the construction of the swash plate and cam rotor supports and the bearings needed to permit variations in the cam rotor angle is complicated, and a rotation prevention mechanism has to be provided in order to prevent rotation of the swash plate.
  • [0005]
    Furthermore, since the rotation prevention mechanism in a variable capacity compressor must function even when the angle of inclination of the plate is being varied, it cannot use the bevel gear construction used in fixed capacity compressors. Instead, it has comprised a slide rod which projects radially from the outer edge of the swash plate and engages a guide groove formed axially in the crank case. Rotation of the swash plate is prevented by sliding motion of the slide rod in the guide groove. However, durability is a problem because of the rubbing that occurs. Also, since the sliding friction changes in response to the range of movement of the swash plate, the angular velocity, which should be transfered to the swash plate, is not uniform during variations of the angle of inclination and hence vibration is produced.
  • [0006]
    In accordance with the present invention, a variable capacity compressor comprises a housing having a chamber; a drive shaft supported rotatably in the housing; an inclined plate coupled to the drive shaft; a plurality of pistons arranged to be driven reciprocably by rotation of the inclined plate, each piston being connected to the inclined plate by a connecting means which abuts slidably against both faces of the inclined plate; a hinge mechanism for coupling the inclined plate to the drive shaft and for permitting the angle of inclination of the inclined plate to be varied within a predetermined range; and a means for controlling the pressure in the chamber, the arrangement of the hinge mechanism being such that variations in the chamber pressure force the mechanism to move and vary the angle of inclination of the inclined plate, and wherein each connecting means comprises a pair of sliding shoes, each shoe being mounted in a respective holding portion of the respective piston and having a first surface in sliding contact with the respective face of the inclined plate and a second, spherically curved, surface in sliding abutment with a complementary surface on the respective holding portion, the second surfaces of the two shoes being coincident with the surface of a common notional sphere.
  • [0007]
    The invention will now be described by way of example with reference to the accompanying drawings, in which;-
    • Figure 1 is a sectional side view of a variable capacity compressor in accordance with the invention showing the inclined plate at its largest angle of inclination;
    • Figure 2: is a sectional side view similar to that of Figure 1, but showing the inclined plate at its smallest angle of inclination;
    • Figure 3(a) is a sectional side view of a conventional mechanism for coupling a piston and an inclined plate.
    • Figure 3(b) is a sectional side view of the conventional coupling mechanism of Figure 3(a) illustrating the situation in which a gap appears between the inclined plate and a pair of sliding shoes when the angle of inclination of the inclined plate is reduced; and,
    • Figure 4 is a sectional side view of a coupling mechanism in accordance with the invention.
    • Figure 1 shows an example of a variable capacity compressor 40 which has a casing 1 covered at one end by a front housing 3 and at the other end by a valve plate 24 and a cylinder head 26. A cylinder block 2 is mounted inside the other end of the casing 1 and has a cylinder bore 2a. A hole 3a is formed in the centre of the front housing 3 to allow a drive shaft 4 to pass through. A radial bearing 5 is disposed in hole 3a to support rotatably the drive shaft 4.
  • [0008]
    A sleeve 3b extends.from the outer wall of the front housing 3 and surrounds the drive shaft 4. A mechanical seal 7 is positioned in a seal chamber 6 formed between the outer surface of the drive shaft 4 and the inner wall of the sleeve 3b. A chamber la is formed between the inner wall of the front housing 3 and an end surface of the cylinder block 2. A rotor 8 is mounted on the drive shaft 4 in the chamber la, and has an ear-shaped portion 8a which is formed in the ear-shape by an end of the rotor 8 being bent towards the drive shaft 4. An elongate hole 8b is formed in the ear-shaped portion 8a.
  • [0009]
    A spherical surface bush 9 is disposed on the drive shaft 4 at a distance along from the rotor 8 so that the spherical surface bush 9 can slide along the drive shaft 4. A disk-shaped inclined plate 10 is pivotably mounted on the spherical surface bush 9 and is attached to an ear-shaped portion 10a located adjacent to the ear-shaped portion 8a and having a hole 10b in alignment with the elongate hole 8b, a pin 11 being inserted through both the elongate hole 8b and the hole 10b with the pin 11 being able to slide within the elongate hole 8b. A hinge mechanism which couples the inclined plate 10 to the drive shaft 4 thus comprises the following components: the elongate hole 8b in the ear-shaped portion 8a of the rotor 8, the hole 10b in the portion 10a and the pin 11. A spring 12 is mounted over the drive shaft 4 and biases apart the rotor 8 and the bush 9. A pair of thrust races 13 are formed on the inner wall of the front housing 3 and the opposing surface of the rotor 8 with a thrust needle bearing 14 placed therebetween.
  • [0010]
    The other end of the drive shaft 4 is supported rotatably by a radial needle bearing 15 mounted in the cylinder block 2 and is restrained axially by a thrust needle bearing 16 and a plate 17 held in position by an adjusting screw 18.
  • [0011]
    Sliding shoes 19 each having a flat surface and a spherically curved surface are disposed on each side of the inclined plate 10 with the flat surfaces in contact with the plate 10 so that it can slide between them. As shown in Figure 1, the pair of shoes 19 are positioned so that their spherically curved surfaces form part of the surface of a common sphere having a radius of curvature of R. The centre of the sphere defined by the curved surfaces is located in a plane halfway between the two faces of the inclined plate 10, i.e. at the middle of the thickness of the inclined plate 10. A piston rod 20 has a forked structure on one of its ends which is used to hold together the sliding shoes 19 and the inclined plate 10. A piston 21 is disposed on, or as in this case forms an integral extension of, the other end of the piston rod 20, and is mounted slidably in the cylinder bore 2a. A number of such piston rods/pistons and pairs of sliding shoes are located in the compressor.
  • [0012]
    A suction hole 22 and a discharge hole 23 are formed in the valve plate 24. One side of the valve plate 24 abuts the cylinder block 2 through a gasket 25; and the other side abuts the cylinder head 26 through a gasket 29. A partition 26a divides the cylinder head 26 into a suction chamber 27 and a discharge chamber 28. The casing 1 is closed by the valve plate 24 and the cylinder head 26 which are attached to the top of the cylinder block 2. A suction port 27a allows flow into the suction chamber 27, and a discharge port 28a allows flow out of the discharge chamber 28.
  • [0013]
    A duct 30 formed mainly in the cylinder block 2 connects the suction chamber 27 with the chamber la and comprises a hole 30a which penetrates the valve plate 24 and the gaskets 25 and 29 and a chamber 30b formed in the cylinder block 2 itself and within which a bellows 34 is positioned.
  • [0014]
    A coupling 31, which has a hole 31a and a valve seat 31b, is located in the chamber 30b at the end adjacent to the chamber la. An 0-ring 32 is inserted between the coupling 31 and the cylinder block 2 to prevent leakage of fluid gas. A pedestal 33, which has holes 33a on two sides of its top, is fixed in the chamber 30b and the bellows 34, which has a needle 34a on its top end, is mounted on the surface of the pedestal 33 and contains gas at a certain pressure. When the top end of the needle 34a is inserted into the hole 31a, a seal is formed between the needle 34a and the valve seat 31b of the coupling 31.
  • [0015]
    The operation of the above-described compressor when used in a refrigeration circuit will now be explained with reference to Figures 1 and 2.
  • [0016]
    When rotary motion from a drive source rotates the drive shaft 4, the inclined plate plate 10 is also rotated since it is connected to the shaft 4 through the rotor 8 and the hinge portion. However, the rotary motion is not transmitted to the piston rod 20 because the sliding shoes 19 allow the inclined plate 10 to slide between their flat surfaces. Thus, the rotary motion of the inclined plate 10 is converted only into reciprocating motion of the piston 21 (i.e. motion towards the left and right in these figures). This reciprocating motion causes the fluid to be sucked through the suction hole 22, compressed in the cylinder bore 2a and discharged into the discharge chamber 28 through the discharge hole 23.
  • [0017]
    The swept volume of the compressor is changed in the following manner. When the load on the refrigeration system rises above its "substantially off-load" capacity (compressor as in Figure 2), the suction pressure of the refrigerant increases, thereby increasing the pressure in the suction chamber 27. Accordingly, the pressure in the chamber 30b, which is connected to the suction chamber 27, also increases.
  • [0018]
    The gas in the bellows 34 is at a pressure which is a little higher than the suction pressure produced when the load is within the capabilities of the "substantially off-load" system. Therefore, the rise in suction pressure causes the bellows 34 to contract and the free end to move towards the right as shown in Figure 1. The needle 34a moves away from valve seat 31b and this opens the hole 31a. The suction chamber 27 is now connected to the chamber la and, since the gas which leaks from the cylinder chambers 2a into the chamber la during the compression strokes is now able to return to the suction chamber 27, the pressure in the chamber la reduces to a value almost equal to the pressure in the suction chamber 27.
  • [0019]
    The pistons, which are equiangularly spaced around the plate 10, experience reactive forces from the gas being compressed during the compression strokes and this produces a moment M1 tending to cause clockwise rotation of the portion 10a (as viewed in Figures 1 and 2) about the pin 11. An anticlockwise moment M2 is produced by the compression of the coil spring 12; and an anticlockwise moment M3 is produced by any pressure difference between the chamber la and the suction chamber 27 acting across the pistons. Thus, when the aperture 31a is open and no pressure difference exists between the chamber la and the suction chamber 27, only the moment M2 is opposing the moment M1, The spring rate of the coil spring 12 is chosen to result in Ml being greater than M2, and therefore the inclined plate 10 moves towards the rotor 8 and is rotated about the pin 11 of the hinge coupling mechanism with pin 11 being pushed to the radially outer end of the elongate hole 8b (i.e. the compressor becomes as shown in Figure 1). In this way, the slant angle of the inclined plate 10 is set to its maximum, thereby maximizing the stroke length of the pistons 21 and causing the compressor to bring the refrigeration system up to its "on-load" capacity.
  • [0020]
    When the load on the system decreases, the compressor runs at high speed and the swept volume of the compressor is now too large. The pressure in the suction chamber 27 decreases and the bellows 34 move to close the hole 31a with its needle 34a, i.e. the bellows is as shown in Figure 2. The pressure in the chamber la gradually rises as gas leaks from the cylinder chambers into the chamber la through the gaps between the pistons 21 and the cylinder block 2 during the compression strokes. As the pressure rises, a pressure difference between the chamber la and the suction chamber 27 appears, thereby generating an increasing moment M3. This moment M3 is opposed to the moment M1 so that, at some point, the combined magnitude of moments M2 and M3 exceeds the moment M1. When this occurs, a net moment in the anticlockwise direction about pin 11 appears and rotates the inclined plate 10 so that the slant angle of the inclined plate 10 decreases. The slant angle continues to decrease until the pin 11 contacts the radially inner end of the elongate hole 8b (i.e. the compressor returns to being as shown in Figure 2). This decrease in slant angle reduces the stroke of the pistons 21 in the cylinders 2a and hence the swept volume of the compressor. Since it is undesirable to stop completely movement of the pistons, as this would result in the flow of refrigerant gas and lubricating oil also stopping, some movement of the pistons should be maintained to continue lubrication of the compressor. For this reason, the length of the elongate hole 8b is chosen such that the minimum swept volume is between 20 and 30 percent of the maximum swept volume.
  • [0021]
    Figure 3(a) shows a conventional coupling mechanism for a piston and an inclined plate. The sliding shoes 19' are half spheres having a radius B and are located on respective sides of an inclined plate 10' of thickness t, the distance A between the furthest extremities of the shoes being defined by the following formula (1). Where a is the angle between the axis of the shaft 4' and the bisection plane D' of the inclined plate 10', i.e. a is the angle of inclination of the inclined plate 10'.
  • [0022]
    As has been described previously, the angle of inclination of the inclined plate is varied and, therefore, the distance A defined in the formula (1) varies in accordance with the variations of the angle a. The distance A between the furthest extremities of the shoes is equal to the distance C between the holding portions 35' of the piston rod 20' when the inclined plate is as shown in Figure 3(a). However, the distance C is fixed and this results in a gap being produced between the sliding shoes 19' and the inclined plate 10' when the angle is reduced (see Figure 3(b)), thereby disturbing the smooth motion of the piston 21'.
  • [0023]
    This contrasts with the sliding shoes 19 shown in Figure 4, which are in accordance with the present invention. They each have a spherically curved surface in addition to a flat surface which abuts against the inclined plate 10. The extent of each spherically curved surface is such that when the shoes 19 are located on either side of the inclined plate 10, these surfaces are coincident with the surface of an imaginary common sphere of radius R centered at a point on the bisection plane D of the inclined plate 10. This ensures that the distance between the extremities of the shoes is not dependent upon the angle of inclination of the inclined plane. Thus, no gap is ever produced between the shoes 19 and the inclined plate 10, and this results in smooth operation of the piston 21 irrespective of its swept volume.

Claims (3)

1. A variable capacity compressor (40) comprising a housing (1,2,3,24,26) having a chamber (la); a drive shaft (4) supported rotatably in the housing (1,2,3,24,26); an inclined plate (10) coupled to the drive shaft (4); a plurality of pistons (21) arranged to be driven reciprocably by rotation of the inclined plate (10), each piston (21) being connected to the inclined plate (10) by a connecting means (19) which abuts slidably against both faces of the inclined plate (10); a hinge mechanism (8,8a,8b,10a,10b,ll) for coupling the inclined plate (10) to the drive shaft (4) and for permitting the angle of inclination of the inclined plate (10) to be varied within a predetermined range; and a means (34) for controlling the pressure in the chamber (la), the arrangement of the hinge mechanism (8,8a,8b,10a,10b,11) being such that variations in the chamber pressure force the mechanism to move and vary the angle of inclination of the inclined plate (10), and wherein each connecting means (19) comprises a pair of sliding shoes (19), each shoe (19) being mounted in a respective holding portion (35) of the respective piston (21) and having a first surface in sliding contact with the respective face of the inclined plate (10) and a second, spherically curved, surface in sliding abutment with a complementary surface on the respective holding portion (35), the second surfaces of the two shoes (19) being coincident with the surface of a common notional sphere.
2. A compressor (40) according to claim 1, wherein the controlling means (34) is a bellows (34).
3. A compressor (40) according to claim 1 or claim 2, wherein the notional sphere has its centre located halfway between the two faces of the inclined plate (10).
EP19860300455 1985-01-25 1986-01-23 Variable capacity compressor Withdrawn EP0190013A3 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP10992/85 1985-01-25
JP1099285A JPS641668B2 (en) 1985-01-25 1985-01-25

Publications (2)

Publication Number Publication Date
EP0190013A2 true true EP0190013A2 (en) 1986-08-06
EP0190013A3 true EP0190013A3 (en) 1987-06-03

Family

ID=11765641

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860300455 Withdrawn EP0190013A3 (en) 1985-01-25 1986-01-23 Variable capacity compressor

Country Status (4)

Country Link
EP (1) EP0190013A3 (en)
JP (1) JPS641668B2 (en)
KR (1) KR920007053B1 (en)
CN (1) CN86101051A (en)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0256793A1 (en) * 1986-08-07 1988-02-24 Sanden Corporation Slant plate type compressor with variable displacement mechanism
EP0259760A2 (en) * 1986-09-02 1988-03-16 Nippondenso Co., Ltd. Variable displacement swash-plate type compressor
US4747753A (en) * 1986-08-08 1988-05-31 Sanden Corporation Slant plate type compressor with variable displacement mechanism
EP0282190A1 (en) * 1987-02-19 1988-09-14 Sanden Corporation Wobble plate compressor
EP0283963A2 (en) * 1987-03-24 1988-09-28 Sanden Corporation Wobble plate type compressor with variable displacement mechanism
US4842488A (en) * 1986-07-08 1989-06-27 Sanden Corporation Slant plate type compressor with variable displacement mechanism
EP0334634A1 (en) * 1988-03-23 1989-09-27 Sanden Corporation Slant plate type compressor
US4874295A (en) * 1987-03-24 1989-10-17 Sanden Corporation Slant plate type compressor with variable displacement mechanism
US4882909A (en) * 1987-09-22 1989-11-28 Sanden Corporation Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism
US5027612A (en) * 1987-09-22 1991-07-02 Sanden Corporation Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism
WO1992017705A1 (en) * 1991-03-30 1992-10-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism
US5168716A (en) * 1987-09-22 1992-12-08 Sanden Corporation Refrigeration system having a compressor with an internally and externally controlled variable displacement mechanism
US5189886A (en) * 1987-09-22 1993-03-02 Sanden Corporation Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism
FR2759425A1 (en) * 1997-02-10 1998-08-14 Toyoda Automatic Loom Works type compressor with variable capacity
FR2767359A1 (en) * 1997-08-01 1999-02-19 Ntn Toyo Bearing Co Ltd Pad for type compressor beater plate and device skate
US6336392B1 (en) 1998-11-11 2002-01-08 Sanden Corporation Compressor which can be easily and efficiently assembled by facilitating adjustment of an axial clearance of a shaft

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JP2530707Y2 (en) * 1989-09-16 1997-03-26 株式会社豊田自動織機製作所 Coil spring mounting structure of a variable displacement compressor
JP2573362Y2 (en) * 1990-09-04 1998-05-28 株式会社豊田自動織機製作所 Piston guide structure in the variable capacity swash plate type compressor
JP2979687B2 (en) * 1991-03-26 1999-11-15 株式会社豊田自動織機製作所 Variable displacement swash plate type compressor
DE69635266T2 (en) 1995-11-24 2006-05-18 Calsonic Kansei Corp. Swash plate compressor
JP2007002717A (en) * 2005-06-23 2007-01-11 Japan Servo Co Ltd Series rotor type tube pump
CN103629081A (en) * 2013-05-23 2014-03-12 浙江三田汽车空调压缩机有限公司 Device and method for adjusting automobile air conditioner compressor exhaust volume with pressure difference

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US3746475A (en) * 1971-02-03 1973-07-17 Gen Motors Corp Double-acting swashplate compressor
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US2545929A (en) * 1949-03-31 1951-03-20 Acrotorque Co Pump
US3746475A (en) * 1971-02-03 1973-07-17 Gen Motors Corp Double-acting swashplate compressor
DE2704729A1 (en) * 1976-02-06 1977-08-11 Borg Warner compressor

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4842488A (en) * 1986-07-08 1989-06-27 Sanden Corporation Slant plate type compressor with variable displacement mechanism
EP0256793A1 (en) * 1986-08-07 1988-02-24 Sanden Corporation Slant plate type compressor with variable displacement mechanism
US4747753A (en) * 1986-08-08 1988-05-31 Sanden Corporation Slant plate type compressor with variable displacement mechanism
EP0513871A3 (en) * 1986-09-02 1993-08-11 Nippondenso Co., Ltd. Variable displacement swash-plate type compressor
EP0259760A2 (en) * 1986-09-02 1988-03-16 Nippondenso Co., Ltd. Variable displacement swash-plate type compressor
EP0259760A3 (en) * 1986-09-02 1990-05-16 Nippondenso Co., Ltd. Variable displacement swash-plate type compressor
EP0513871A2 (en) * 1986-09-02 1992-11-19 Nippondenso Co., Ltd. Variable displacement swash-plate type compressor
EP0282190A1 (en) * 1987-02-19 1988-09-14 Sanden Corporation Wobble plate compressor
EP0283963A3 (en) * 1987-03-24 1989-08-02 Sanden Corporation wobble plate type compressor with variable displacement mechanism
US4874295A (en) * 1987-03-24 1989-10-17 Sanden Corporation Slant plate type compressor with variable displacement mechanism
EP0283963A2 (en) * 1987-03-24 1988-09-28 Sanden Corporation Wobble plate type compressor with variable displacement mechanism
US4882909A (en) * 1987-09-22 1989-11-28 Sanden Corporation Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism
US5027612A (en) * 1987-09-22 1991-07-02 Sanden Corporation Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism
US5189886A (en) * 1987-09-22 1993-03-02 Sanden Corporation Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism
US5168716A (en) * 1987-09-22 1992-12-08 Sanden Corporation Refrigeration system having a compressor with an internally and externally controlled variable displacement mechanism
US5025636A (en) * 1987-09-22 1991-06-25 Sanden Corporation Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism
EP0334634A1 (en) * 1988-03-23 1989-09-27 Sanden Corporation Slant plate type compressor
WO1992017705A1 (en) * 1991-03-30 1992-10-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism
US5336056A (en) * 1991-03-30 1994-08-09 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism
USRE35878E (en) * 1991-03-30 1998-08-25 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism
FR2759425A1 (en) * 1997-02-10 1998-08-14 Toyoda Automatic Loom Works type compressor with variable capacity
FR2767359A1 (en) * 1997-08-01 1999-02-19 Ntn Toyo Bearing Co Ltd Pad for type compressor beater plate and device skate
US6336392B1 (en) 1998-11-11 2002-01-08 Sanden Corporation Compressor which can be easily and efficiently assembled by facilitating adjustment of an axial clearance of a shaft

Also Published As

Publication number Publication date Type
CN86101051A (en) 1986-07-23 application
KR920007053B1 (en) 1992-08-24 grant
JPS61171886A (en) 1986-08-02 application
JPS641668B2 (en) 1989-01-12 grant
EP0190013A3 (en) 1987-06-03 application
JP1520505C (en) grant
JP1001668B (en) grant

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