CN86101051A - Capacity variable type compressor - Google Patents

Capacity variable type compressor Download PDF

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Publication number
CN86101051A
CN86101051A CN198686101051A CN86101051A CN86101051A CN 86101051 A CN86101051 A CN 86101051A CN 198686101051 A CN198686101051 A CN 198686101051A CN 86101051 A CN86101051 A CN 86101051A CN 86101051 A CN86101051 A CN 86101051A
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CN
China
Prior art keywords
wobbler
piston
compressor
variable type
type compressor
Prior art date
Application number
CN198686101051A
Other languages
Chinese (zh)
Inventor
寺内清
Original Assignee
三电有限公司
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
Priority to JP60010992A priority Critical patent/JPS641668B2/ja
Application filed by 三电有限公司 filed Critical 三电有限公司
Priority to JPP10,992/60 priority
Publication of CN86101051A publication Critical patent/CN86101051A/en
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=11765641&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=CN86101051(A) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.

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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 specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-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
    • 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 specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-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
    • F04B27/0873Component 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 specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-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
    • F04B27/14Control
    • 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 specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-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
    • F04B27/14Control
    • 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 specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-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
    • F04B27/14Control
    • 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 specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-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
    • F04B27/14Control
    • 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

The present invention relates to a kind of capacity variable type compressor, this compressor comprises that one is used to connect the bindiny mechanism of wobbler and piston.This bindiny mechanism comprises a pair of piston shoes, and the outer spherical surface of these piston shoes is one the sphere in the public center of circle to be arranged, and the center of circle of sphere is arranged on the face of described wobbler.

Description

Capacity variable type compressor
The invention relates to a kind of swash-plate-type compressor that is used for refrigeration plants such as refrigerator.Capacity variable type compressor particularly.
The compressor that a kind of prior art is arranged, this compressor is to come compressed liquid with the to-and-fro motion that rotatablely moving of wobbler is become piston, the compressor of this prior art also utilizes the stroking distance that changes piston from changing its compression volume, in this compressor, the mode that its piston can change with the wobbler tilt angle is connected on this wobbler.
The wobbler of the above capacity variable type compressor comprises an eccentric rotor and a baffle plate.The angle of the eccentric rotor that is connected with running shaft can change.Baffle plate moves along with the rotation of eccentric rotor, and its angle changes along with the variation at eccentric rotor angle of inclination.Piston is connected on the plate washer by connecting rod, and its stroke changes along with the variation at plate washer tilt angle.Thereby can change the compression volume of compressor by this way.
Yet, in this compressor, the supporting structure of plate washer and eccentric rotor and to change the bearing structure of eccentric rotor angle complicated.And, also need an anti-rotation mechanism in case the rotation of stop plate.
In addition, when the plate washer tilt angle varied, the anti-rotation mechanism in the capacity variable type compressor also must work, and during transfiguration, the anti-rotation mechanism in the compressor can not use such as the helical gear structure of using in the constant volume compressor.Therefore, the anti-rotation mechanism in the capacity variable type compressor comprises a slide bar that garden week radially extends outside plate washer and an axial channel that is positioned at crankcase.The slip that utilization is arranged in the guide groove slide bar prevents the rotation of plate washer.Yet because the wearing and tearing in the anti-rotation mechanism, its life-span is a problem, also have, because the variation of the force of sliding friction that produces along with the variation of plate washer range of movement makes when the plate washer tilt angle varied, the angular velocity that should be delivered on the plate washer is inhomogeneous, and produces vibrations.
The objective of the invention is to provide a kind of simple in structure, capacity variable type compressor that reliability is high with anti-rotation mechanism.
The present invention relates to a kind of capacity variable type compressor.This compressor has a cavity volume, comprises a crankcase in the cavity volume, and live axle is rotatably supported in the cavity volume, and wobbler is connected on the live axle.By the rotation of wobbler several pistons is moved reciprocatingly.Piston is connected on the wobbler by a bindiny mechanism, makes the periphery slip of bindiny mechanism along wobbler.Wobbler is connected on the live axle by a hinge mechanism, with this tilt angle of wobbler is changed within the limits prescribed.Pressure in the crankcase comprises that by a control mechanism control connection mechanism a pair of piston shoes and one are used for the retained part on the piston of being positioned at of clamping piston shoes.Each piston shoes has the first surface and the reverse ball surface, garden that regard to the wobbler interarea.Ball surface, garden is limited by the garden week outer surface in concentric garden.
Other purpose of the present invention, characteristics and aspect can be understood by the embodiment who describes in detail with reference to the accompanying drawings.
Fig. 1 is the sectional view according to variable volume compressor of the present invention, in this case, and the tilt angle maximum of wobbler;
Fig. 2 is the sectional view according to variable volume compressor of the present invention, in this case, and the tilt angle minimum of wobbler;
Fig. 3 (a) is the sectional view of piston and the existing bindiny mechanism of wobbler.
Fig. 3 (b) is the sectional view of the existing bindiny mechanism of explanation, shows among the figure, in this state, because the tilt angle varied of wobbler makes to produce the gap between wobbler and the piston shoes;
Fig. 4 is the view according to the bindiny mechanism between piston of the present invention and the wobbler.
With reference to Fig. 1, it represents the embodiment according to capacity variable type compressor of the present invention.Compressor 40 comprises: a cup 3; A valve plates 24; A cylinder baffle 1, this cylinder baffle one end links to each other with the end face of cup 3, and the other end links to each other with the end face of valve plates 24; With a cylinder head 26, this cylinder head links to each other with the other end of valve plates 24.A cylinder block 2 constitutes the end of cylinder baffle 1 and has cylinder chamber 2a.Be formed centrally a through hole 3a that can put in live axle 4 in cup 3, a radial bearing 5 places through hole 3a to be used for rotatably support live axle 4.
An axle sleeve 3b outwards stretches from the through hole 3a outer end of cup 3, be centered around live axle 4 around.The closed chamber 6 that places the inwall by the outer surface of live axle 4 and axle sleeve 3b to constitute under mechanical seal ring.A crankcase 1a is made of the inwall of cup 3 and the end face of cylinder block 2.A rotor 8 is contained on the end of the live axle 4 that is arranged in crankcase 1a.Rotor 8 has an ear shape part 8a, and this ear shape partly is the ear shape that an end of rotor 8 is shaped towards live axle 4.On ear shape part 8a, be formed with slotted hole 8b.
A spherical bushing 9 is contained on the live axle 4 apart from rotor 8 one segment distances, so that make spherical bushing 9 to slide on live axle 4.A garden plate-like wobbler 10 places on the spherical bushing 9 slidably.Ear shape part 10a places on the end surfaces of wobbler 10 towards the ear shape part 8a of rotor 8, and hole, a garden 10b who aims at slotted hole 8b on the ear shape part 8a is being arranged on this ear shape part 10a.Pin 11 passes from slotted hole 8b and hole, garden 10b and makes pin 11 to slide in slotted hole 8b.Therefore, the hinge mechanism that wobbler 10 is connected on the live axle 4 comprises these assemblies: be positioned at slotted hole 8b, hole, garden 10b and pin 11 on the ear shape part 8a of rotor 8.12 on spring is held on the outer surface of live axle 4 and both offset with rotor 8 and spherical bushing 9.A pair of thrust bearing seat ring 13 places on the inner wall surface of cup 3 and towards the surface of rotor 8.A needle roller thrust bearing 14 places between the bearing race 13.
The other end of live axle 4 is rotatably mounted by the radial needle bearing 15 that is arranged in cylinder block 2.In addition, the other parts of live axle 4 under the adjusting of adjusting screw 18 with respect to axial needle bearing 16 and leaf spring 17 by rotatably mounted.
Piston shoes 19 are placed on each interarea of the wobbler between the sliding surface of each piston shoes 19.Piston shoes 19 have spherical, the curve opposite surfaces.The interarea of wobbler 10 peripheries slides along the sliding surface of piston shoes 19.As shown in Figure 1, a pair of piston shoes 19 are this forms, and promptly its positive camber forms and has the sphere that radius is approximately R.Being centered close on the plane of dividing wobbler 10 equally of sphere, the center that is to say sphere are the centers of wobbler 10 thickness.The piston rod 20 that one one end has prong blocks the piston shoes between it and the wobbler 10.A piston 21 is placed on the other end of (or integrally extending to) piston rod 20, and is slidably received among the cylinder chamber 2a.Several this piston rods and paired piston shoes are set in compressor.
Be formed with the exhaust port that is used to import the suction port 22 of liquid and is used for drain on valve plates 24, a side of valve plates 24 is connected with cylinder block 2 by packing ring 25; The opposite side of valve plates 24 is connected with cylinder head 26 by packing ring 29.The next door 26a of cylinder head 26 is separated into cylinder head 26 suction chamber 27 and discharges chamber 28.Cylinder baffle 1 is by valve plates 24 that is connected in cylinder block 2 tops and cylinder head 26 cappings.Suction passage 27a is used for to suction chamber 27 input medias; Discharge route 28a is used for discharging medium from discharging chamber 28.Form a through hole 30 that is used to be communicated with crankcase 1a and suction chamber 27 in the cylinder block 2.Path 30 comprises: a through hole 30a who runs through valve plates 24, and packing ring 25 and 29, and the port hole 30b of bellows 34 is equipped with in inside.
Pipe coupling joint 31 with through hole 31a and valve base 31b faces crankcase 1a and is placed in the through hole 30b.Between pipe coupling joint 31 and cylinder block 2, embed an O-RunddichtringO 32 in case the fluid stopping body leaks.The base 33 that has through hole 33a in the both sides, top is fixed among the through hole 30b.The bellows 34 that the end has a thimble 34a is placed on the surface of base 33 and is filled with the gas of certain pressure in bellows 34.When the top of thimble 34a was inserted among the through hole 31a, through hole 31a was just sealed by the valve base 31b of thimble 34a and pipe coupling joint 31.
See figures.1.and.2, represented the above-mentioned operational situation that is used for the compressor of cooling cycle system among the figure.
When the rotatory force rotating driveshaft by driving source input, this rotatory force partly passes to wobbler 10 by rotor 8 and hinge, and wobbler 10 is rotated.Yet this rotational motion is not delivered on the piston rod 20, and when wobbler 10 rotated, the interarea of wobbler 10 slided on a pair of sliding surface of facing of piston shoes 19, and piston rod 20 is exactly to be connected to by this way on the piston shoes 19.That is to say the not motion of the above-below direction in these figure of piston 21.Therefore, the rotatory force of wobbler 10 has become the motion of piston 21 to-and-fro motion of left and right directions motion in these figure.Because the to-and-fro motion of piston 21, compress thereby the liquid that sucks from suction port 22 is pressed into the cylinder chamber 2a, and by tap hole 23, liquid is discharged to discharge in the chamber 28 goes.
Can change the compression volume of compressor with following method.In air-conditioning system, when air conditioning load was higher than the load of predetermined temperature, then refrigeration capacity was just inadequate, and it is higher that the incoming pressure of refrigeration will become, and made the pressure in the input chamber 27 become very high.Therefore, with the input port hole 30b that is communicated with of chamber 27 in pressure also will become very high.
The gas that is arranged in the bellows 34 of port hole 30b seals by this way, that is: in refrigeration system, the gas in the bellows 34 is a bit higher than the incoming pressure corresponding to predetermined temperature slightly.Therefore, when air conditioning load was higher than the load of predetermined temperature, bellows 34 was towards as shown in Figure 1 right-hand contraction, and thimble 34a removes from valve base 31b, opens through hole 31a with this.Like this, suction chamber 27 just has been communicated with crankcase 1a.Because the gas that leaks into crankcase 1a owing to the work of compressor is got back to suction chamber 27, then the pressure among the crankcase 1a becomes almost and to equate with pressure in the suction chamber 27.
In this case, when carrying out the compression cycle process, by being in the corresponding wobbler 10 equal angles pressurized air reaction force acts that piston action produced spaced apart on wobbler 10, and act on thus on the above-mentioned hinge part.Owing to the reaction force that acts on the piston 21 produces moment M 1, this moment M 1Act on its clockwise direction is rotated.Because the rebounding force that helical spring 12 produces produces moment M 2; Also owing to the pressure difference between crankcase 1a and the suction chamber 27 has produced moment M 3Therefore, when through hole 31a opens, make in crankcase 1a and the suction chamber 27 not have pressure difference, thereby have only moment M 1Resistant function moment M 2So, if be provided with helical spring 12 to such an extent that make moment M 1Greater than M 2, wobbler 10 just moves and pushes to around the pin turning handle pin 11 of hinge bindiny mechanism the upper end portion of elongated hole 8b to rotor 8 so.At this moment, the relative vertical surface in the tilt angle of wobbler 10 is maximum.Thereby the piston 21 that causes being among the cylinder 2a that is equivalent to the normal refrigerating volume of compressor has maximum stroke.
When air conditioning load is low, and compressor operation speed is very high, and it is very big that the compression volume of compressor will become.Therefore, the pressure in the suction chamber 27 will reduce, and bellows 34 moves to left and makes thimble 34a close through hole 31a.This state as shown in Figure 2.In this case, because gas leakage, the pressure of crankcase 1a increases gradually, produce a pressure difference, in compression stroke, the leakage of this gas is to leak to crankcase 1a from cylinder chamber by the slit between piston and the cylinder, and collects among the crankcase 1a.In the process that pressure raises in crankcase 1a, produce moment 3 and its increasing amount increasing amount corresponding to pressure among the crankcase 1a.Moment M 3React on moment M 1, therefore in some aspects, moment M 2With moment M 3Total amount surpass moment M 1When this happens, produce in the hinge bindiny mechanism around pin 11 counterclockwise the moment loadings of effect on wobbler 10, make wobbler 10 reduce with respect to the angle of inclination of vertical plane.The tilt angle continues to reduce till pin 11 and slotted hole 8b underpart offset.Because the tilt angle reduces, the stroke of piston will reduce and the capacity of compressor reduces gradually among the cylinder 2a.Because if the complete stop motion of piston, then flowing of refrigerant gas and lubricant oil also can stop (motion of piston can be kept compressor and lubricate with keeping), do not stop fully so do not wish the motion of piston.
The length that is in the slotted hole 8b of hinge part determines by this way according to the compressor compresses capacity, promptly the minimal compression capacity of compressor should be its maximum compression capacity 35 20 percent to percent between.
With reference to Fig. 3 (a), it has represented the bindiny mechanism of existing piston and wobbler.The hemisphere piston shoes 19 that have radius and be B are placed on two sides of wobbler 10, and the thickness of wobbler is t, and the distance A between two piston shoes, 19 spheres is determined by following formula (1):
A=2B+tx 1/(cosα) (1)
α represents the angle between vertical axis and wobbler 10 medial axis.
Just as described above, because the tilt angle varied of wobbler 10, the interhemispheric distance represented by formula (1) also changes along with the tilt angle of wobbler 10.Yet, both made the retained part 35 of distance A between the two hemispheres and piston rod 20 ' between the equal in length of distance C, shown in Fig. 3 a, because interhemispheric distance A changes along with the tilt angle of wobbler 10, and on the other hand, retained part 35 ' between distance C constant, therefore, shown in Fig. 3 (b), between piston shoes 19 and wobbler 10, produce the gap, make the piston 21 can not smooth sliding.
In addition, as shown in Figure 4, each piston shoes 19 according to the present invention has and the opposite garden sphere of sliding surface of facing wobbler 10.A pair of piston shoes 19 are settled by this way round the principal plane of wobbler 10, the outer spherical surface that is piston shoes is that the garden sphere of R limits by radius substantially, and the centre of sphere is arranged in a bit the going up of face D of wobbler 10, and (this face D is divided equally into two equal parts to wobbler 10 between the principal plane outside two of wobbler 10.Two interhemispheric distance A do not change along with the tilt angle of wobbler 10, but keep equating.Therefore, can not produce the gap between piston shoes 19 and wobbler 10, piston 21 is always worked reposefully.
The present invention is described in detail in conjunction with optimum implementation, but this is some examples, the present invention is not limited to this.Understand easily, all engineers and technicians that are familiar with this technical field all can conceive range content in the present invention and change places and carry out various changes and improvements.

Claims (3)

1, a kind of capacity variable type compressor is characterized in that it comprises, the cavity volume with crankcase, a live axle that can be rotated to support in the cavity volume; A wobbler that is connected on the described live axle; Reciprocating several pistons under described wobbler drives; One is connected to bindiny mechanism on the described wobbler to described piston, and described bindiny mechanism is slided along the periphery of described wobbler; One is connected to hinge on the described live axle to described wobbler, and the angle of inclination of described wobbler can be changed in predetermined scope; Also be useful on the control gear of pressure in the described bent case of control; Described bindiny mechanism comprises: a pair of piston shoes and the retained part that is used on the described piston of being positioned at of the described piston shoes of clamping, each piston shoes all has first plane and the opposed surface in the face of described wobbler interarea, and the opposed surface of described piston shoes is formed by the outer spherical surface with a public garden heart.
2, according to the capacity variable type compressor of claim 1, wherein said control gear is a bellows.
3, according to the capacity variable type compressor of claim 1, the wherein said public garden heart is arranged on the face of described wobbler.
CN198686101051A 1985-01-25 1986-01-20 Capacity variable type compressor CN86101051A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP60010992A JPS641668B2 (en) 1985-01-25 1985-01-25
JPP10,992/60 1986-01-25

Publications (1)

Publication Number Publication Date
CN86101051A true CN86101051A (en) 1986-07-23

Family

ID=11765641

Family Applications (1)

Application Number Title Priority Date Filing Date
CN198686101051A CN86101051A (en) 1985-01-25 1986-01-20 Capacity variable type compressor

Country Status (8)

Country Link
EP (1) EP0190013A3 (en)
JP (1) JPS641668B2 (en)
KR (1) KR920007053B1 (en)
CN (1) CN86101051A (en)
AU (1) AU5267986A (en)
BR (1) BR8600296A (en)
IN (1) IN165951B (en)
MX (1) MX168487B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
CN107605702A (en) * 2017-10-30 2018-01-19 华中科技大学 A kind of compression mechanism of compressor

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JPH0312674B2 (en) * 1986-07-08 1991-02-20 Sanden Corp
JPH0610468B2 (en) * 1986-08-07 1994-02-09 サンデン株式会社 Variable capacity compressor
JPS6341677A (en) * 1986-08-08 1988-02-22 Sanden Corp Variable capacity compressor
BR8704487A (en) * 1986-09-02 1988-04-19 Nippon Denso Co VARIABLE DISPLACEMENT OSCILLATING PLATE TYPE COMPRESSOR
JPH0231235B2 (en) * 1987-02-19 1990-07-12 Sanden Corp
JPH0649918Y2 (en) * 1987-03-24 1994-12-14 サンデン株式会社 Variable capacity compressor
JPS63149319U (en) * 1987-03-24 1988-09-30
JPH0231799B2 (en) * 1987-07-24 1990-07-16 Sanden Corp
JPH0313433B2 (en) * 1987-09-22 1991-02-22 Sanden Corp
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
JPH0341101Y2 (en) * 1988-03-23 1991-08-29
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 for variable capacity 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 for variable displacement swash plate compressor
JP2979687B2 (en) * 1991-03-26 1999-11-15 株式会社豊田自動織機製作所 Variable capacity swash plate compressor
JP2626292B2 (en) * 1991-03-30 1997-07-02 株式会社豊田自動織機製作所 Variable capacity swash plate compressor
EP0780572B1 (en) 1995-11-24 2005-10-12 Calsonic Kansei Corporation Swash-plate type compressor
JPH10220347A (en) 1997-02-10 1998-08-18 Toyota Autom Loom Works Ltd Variable capacity compressor
US6024010A (en) * 1997-08-01 2000-02-15 Ntn Corporation Shoe for swash plate type compressor and shoe assembly
JP2000205127A (en) 1998-11-11 2000-07-25 Sanden Corp Compressor
JP2007002717A (en) * 2005-06-23 2007-01-11 Japan Servo Co Ltd Series rotor type tube pump
CN108150479A (en) * 2016-12-05 2018-06-12 江苏汉力士液压制造有限公司 It is split type to wave

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US3746475A (en) * 1971-02-03 1973-07-17 Gen Motors Corp Double-acting swashplate compressor
US4073603A (en) * 1976-02-06 1978-02-14 Borg-Warner Corporation Variable displacement compressor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
CN107605702A (en) * 2017-10-30 2018-01-19 华中科技大学 A kind of compression mechanism of compressor
CN107605702B (en) * 2017-10-30 2019-01-29 华中科技大学 A kind of compression mechanism of compressor

Also Published As

Publication number Publication date
EP0190013A2 (en) 1986-08-06
KR920007053B1 (en) 1992-08-24
KR860005980A (en) 1986-08-16
IN165951B (en) 1990-02-17
JPS61171886A (en) 1986-08-02
BR8600296A (en) 1986-10-07
MX168487B (en) 1993-05-27
EP0190013A3 (en) 1987-06-03
AU5267986A (en) 1986-07-31
JPS641668B2 (en) 1989-01-12

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