EP1479907B1 - Umgehungsvorrichtung in einem Kompressor variabler Verdrängung - Google Patents

Umgehungsvorrichtung in einem Kompressor variabler Verdrängung Download PDF

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Publication number
EP1479907B1
EP1479907B1 EP04011301A EP04011301A EP1479907B1 EP 1479907 B1 EP1479907 B1 EP 1479907B1 EP 04011301 A EP04011301 A EP 04011301A EP 04011301 A EP04011301 A EP 04011301A EP 1479907 B1 EP1479907 B1 EP 1479907B1
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EP
European Patent Office
Prior art keywords
valve
pressure
pressure region
valve body
passage
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.)
Expired - Fee Related
Application number
EP04011301A
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English (en)
French (fr)
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EP1479907A3 (de
EP1479907A2 (de
Inventor
Yuji Hashimoto
Satoshi Umemura
Masakazu Murase
Tatsuya Koide
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Toyota Industries Corp
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Toyota Industries Corp
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Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1479907A2 publication Critical patent/EP1479907A2/de
Publication of EP1479907A3 publication Critical patent/EP1479907A3/de
Application granted granted Critical
Publication of EP1479907B1 publication Critical patent/EP1479907B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B27/14—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

Definitions

  • the present invention relates to a variable displacement compressor.
  • a variable displacement compressor for use in an air conditioner as disclosed in document JP-A-2000111177
  • pressure in a drive chamber for accommodating a swash plate is controlled by an electromagnetic control valve.
  • the control valve is operable to open and close a supply passage interconnecting a discharge chamber, which forms a part of discharge pressure region of the compressor, with the drive chamber.
  • refrigerant in the discharge chamber flows into the drive chamber, so that pressure in the drive chamber increases and the inclination angle of the swash plate is reduced, thereby to reduce the displacement of the compressor.
  • the control valve closes the supply passage the refrigerant flowing from the discharge chamber into the drive chamber is blocked, so that the pressure in the drive chamber reduces and the inclination angle of the swash plate is increased, thereby to increase the displacement of the compressor.
  • variable displacement compressor a by-pass device is provided for releasing the refrigerant in the discharge pressure region when the discharge pressure is built up excessively.
  • the discharge pressure region and the drive chamber are in communication with each other through a by-pass passage and a by-pass valve is provided in the by-pass passage.
  • the spring force of a spring is applied to a valve body through a differential pressure actuating member and a connector bar.
  • the valve body is urged by the spring force of the spring toward a valve seat.
  • the discharge pressure in the discharge pressure region opposes the suction pressure in a suction pressure region through the differential pressure actuating member.
  • the by-pass valve maintains a closed state where the valve body sits on the valve seat.
  • the refrigerant gas in the discharge pressure region does not flow into the drive chamber through the by-pass passage.
  • the valve body is moved away from the valve seat and the by-pass valve is held in an opened state, accordingly.
  • the refrigerant in the discharge pressure chamber flows into the drive chamber through the by-pass passage.
  • a seal ring need be interposed between the circumferential wall of a partitioned chamber for accommodating the differential pressure actuating member and the peripheral edge portion of the differential pressure actuating member.
  • Lubricating oil is contained in a refrigerant circuit of the air conditioner, and the seal ring is swelled by the lubricating oil.
  • the seal ring may be foamed due to fluctuating pressure of the refrigerant.
  • pressure of the refrigerant becomes relatively high and, therefore, the seal ring tends to be easily foamed.
  • a variable displacement compressor comprising the feature summarized in the preamble of claim 1 is known from document JP-A-62 247 186 .
  • the control valve of this known variable displacement compressor opens the supply passage, refrigerant flows from the discharge chamber through the supply passage into the crank chamber, so that the pressure in the crank chamber increases and the inclination angle of a swash plate is reduced, thereby reducing the displacement of the compressor.
  • the control valve closes the supply passage, flow of refrigerant from the discharge chamber into the crank chamber is blocked and refrigerant is released from the crank chamber through the bleed passage to the suction chamber.
  • the pressure in the crank chamber reduces and the inclination angle of the swash plate is increased, thereby increasing the displacement of the compressor.
  • the compressor according to document JP-A-62 247 186 is usually used in an air conditioner. Under certain operating conditions, an excessively high discharge pressure is temporarily built up in the discharge chamber. This excessively high discharge pressure should be avoided.
  • Document EP-A-1 033 490 discloses a variable displacement compressor comprising a control valve including a deformable separator in the form of a bellows.
  • variable displacement compressor defined in claim 1.
  • variable displacement compressor 10 A first preferred embodiment of a variable displacement compressor 10 according to the present invention will now be described with reference to FIGS. 1 through 5 .
  • the variable displacement compressor 10 includes a cylinder block 11, a front housing 12 and a rear housing 13.
  • the front housing 12 is connected to the front end of the cylinder block 10.
  • the rear housing 13 is connected to the rear end of the cylinder block 11 through a valve port plate 14, valve forming plates 15, 16 and a retainer plate 17.
  • the cylinder block 11, the front housing 12 and the rear housing 13 cooperate to form a complete housing of the variable displacement compressor 10.
  • a crank chamber 121 is defined by the front housing 12 and the cylinder block 11.
  • a rotary shaft 18 is rotatably supported by the front housing 12 and the cylinder block 11 through radial bearings 25, 26. The front end portion of the rotary shaft 18 protrudes outside the crank chamber 121 and is coupled to a vehicle engine or an external power source E through a pulley (not shown) and a belt (not shown) so as to receive driving force.
  • a rotor 19 is fixedly connected to the rotary shaft 18, while a swash plate 20 is supported on the rotary shaft 18 in such a manner that the swash plate 20 is slidable in the axial direction of the rotary shaft 18 and inclinable relative to the rotary shaft 18.
  • connecting elements 21, 22 are fixedly connected to the swash plate 20.
  • Guide pins 23, 24 are fixedly connected to the respective connecting elements 21, 22.
  • a pair of guide holes 191, 192 is formed in the rotor 19. The heads of the guide pins 23, 24 are slidably fitted in the respective guide holes 191, 192.
  • the swash plate 20 is slidable in the axial direction of the rotary shaft 18 and rotatable integrally with the rotary shaft 18 because of the linkage between the guide holes 191, 192 and their corresponding guide pins 23, 24.
  • the swash plate 20 is guided for inclination and sliding movement by the linkage between the guide holes 191, 192 and the guide pins 23, 24, and a slidable support of the rotary shaft 18.
  • the maximum inclination angle of the swash plate 20 is regulated in such a manner that the swash plate 20 contacts with the rotor 19.
  • the swash plate 20 indicated by the solid line in FIG. 1 is positioned at the maximum inclination angle.
  • the inclination angle of the swash plate 20 reduces.
  • the swash plate 20 indicated by the chain line in FIG. 1 is positioned at the minimum inclination angle.
  • a plurality of cylinder bores 111 is formed in the cylinder block 11 for accommodating slidable pistons 28.
  • the rotation of the swash plate 20 is converted to the reciprocation of the pistons 28 through a pair of shoes 29 in a manner well known in the art, so that the pistons 28 reciprocate in the respective cylinder bores 111.
  • a suction chamber 131 and a discharge chamber 132 are defined in the rear housing 13.
  • Suction ports 141 and discharge ports 142 are formed in the valve port plate 14 and the valve forming plates 15, 16.
  • Suction valves 151 are formed in the valve forming plate 15, and discharge valves 161 are formed in the valve forming plate 16, respectively.
  • Gaseous refrigerant in the suction chamber 131 which forms a part of suction pressure region, flows into the cylinder bore 111 through the suction port 141 by pushing away the suction valve 151 as the piston 28 moves in its suction stroke (from right to left as seen in FIG. 1 ).
  • the gaseous refrigerant compressed in the cylinder bore 111 is discharged into the discharge chamber 132, which forms a part of a discharge pressure region, through the discharge port 142 while pushing away the discharge valve 161 as the piston 28 moves in discharge stroke (from left to right in FIG. 1 ).
  • the opening degree of the discharge valve 161 is regulated by a retainer 171 formed in the retainer plate 17 with which the discharge valve 161 is brought into contact.
  • carbon dioxide is employed as the refrigerant.
  • a thrust bearing 30 is interposed between the rotor 19 and the front housing 12.
  • the thrust bearing 30 receives reactive force of discharge pressure that acts on the rotor 19 through the cylinder bores 111, the pistons 28, the shoes 29, the swash plate 20, the connecting elements 21, 22 and the guide pins 23, 24.
  • the rear housing 13 forms a suction passage 31 through which refrigerant gas is introduced into the suction chamber 131 and a discharge passage 32 through which refrigerant gas in the discharge chamber 132 is discharged out of the compressor 10.
  • the suction passage 31 and the discharge passage 32 are in communication by an external refrigerant circuit 33.
  • the external refrigerant circuit 33 includes a heat exchanger 34 for removing heat from the refrigerant, an expansion valve 35, and a heat exchanger 36 for transferring ambient heat to the refrigerant.
  • the expansion valve 35 is a thermally automatic expansion valve which is operable to control the flow of refrigerant in response to variation in gas temperature on the outlet side of the heat exchanger 36.
  • the rear housing 13 incorporates a by-pass valve 27 disposed in a by-pass passage 37 which extends from the discharge passage 32 to the crank chamber 121.
  • the by-pass valve 27 includes a cylindrical housing 38, a cylindrical valve seat 39, a diaphragm 40 disposed so as to be movable into contact with or away from the valve seat 39, a spring seat 41 screwed in the cylindrical housing 38 and a return spring 42 interposed between the spring seat 41 and the diaphragm 40 to serve as an urging means.
  • the elastically deformable diaphragm 40 has a peripheral portion which is held by and between the housing 38 and the valve seat 39.
  • the valve seat 39 forms a valve hole 391 in the end wall thereof and an outlet 392 at a part of the inner peripheral wall thereof.
  • the valve hole 391 and the outlet 392 communicate with an internal passage 393 of the cylindrical valve seat 39.
  • the valve hole 391, the internal passage 393 and the outlet 392 form a part of the by-pass passage 37.
  • the diaphragm 40 is formed at the central portion thereof with a semi-spherical convex portion 401 bulged toward the internal passage 393.
  • the convex portion 401 is selectively located at the closed position where the convex portion 401 is placed in contact with the valve seat 39, thereby to close the valve hole 391 and at the opened position where the convex portion 401 is placed away from the valve seat 39, thereby to open the valve hole 391.
  • the return spring 42 accommodated in a space inside the housing 38 hereinafter, a back pressure chamber 381 acts on the diaphragm 40 such that the convex portion 401 of the diaphragm 40 is urged from the opened position to the closed position.
  • the housing 38 and the valve seat 39 hold fluid-tightly therebetween the peripheral portion of the diaphragm 40 to shut off fluid communication between the internal passage 393 and the back pressure chamber 381 so that the refrigerant gas in the internal passage 393 which forms a part of the by-pass passage 37 does not flow into the back pressure chamber 381 through the peripheral portion of the diaphragm 40.
  • the diaphragm 40 serves as an elastically deformable separator for separating the back pressure chamber 381 from the by-pass passage 37 without sliding.
  • the convex portion 401 which is a part of the diaphragm 40 serves as a valve body for opening and closing the valve hole 391 which forms a part of the by-pass passage 37.
  • the diaphragm 40 contacts with the valve seat 39 without any substantial deformation. In other words, the diaphragm 40 is pressed against the valve seat 39 by the atmospheric pressure applied to the diaphragm 40 from the back pressure chamber 381 and the spring force of the return spring 42.
  • the discharge chamber 132 and the crank chamber 121 are in communication through a supply passage 43. Also, the crank chamber 121 and the suction chamber 131 communicate with each other through a bleed passage 44. The refrigerant in the crank chamber 121 flows to the suction chamber 131 through the bleed passage 44.
  • An electromagnetic control valve 45 is provided in the supply passage 43.
  • the control valve 45 receives energization/de-energization control of a controller C.
  • the controller C is activated by turning on air conditioner switch 46 and connected to a temperature setting device 47 for setting a desired target compartment temperature and an actual temperature detector 48 for detecting the current compartment temperature.
  • the controller C is operable to energize or de-energize the control valve 45 based on the information of the target temperature set by the temperature setting device 47 and the current temperature detected by the actual temperature detector 48.
  • the control valve 45 In the de-energized state, the control valve 45 is closed, thereby to block the flow of refrigerant from the discharge chamber 132 to the crank chamber 121 through the supply passage 43. Since the refrigerant in the crank chamber 121 flows to the suction chamber 131 through the bleed passage 44, the pressure in the crank chamber 121 reduces. Accordingly, the inclination angle of the swash plate 20 increases to increase the displacement of the compressor 10.
  • the control valve 45 is opened, thereby to allow the flow of refrigerant from the discharge chamber 132 to the crank chamber 121 through the supply passage 43. Accordingly, the pressure in the crank chamber 121 increases, so that the inclination angle of the swash plate 20 is reduced, thereby to reduce the displacement of the compressor 10.
  • FIG. 6 A second preferred embodiment of the present invention will now be described with reference to FIG. 6 .
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment.
  • valve 27A of the second preferred embodiment in a state where the convex portion 401 of the diaphragm 40 closes the valve hole 391, pressure in the valve hole 391 is substantially equivalent to the pressure in the crank chamber 121 (the crank pressure).
  • An inlet 394 is formed in the circumferential wall of the valve seat 39 and communicates with the discharge passage 32. The inlet 394, the internal passage 393 and the valve hole 391 form a part of the by-pass passage 37.
  • the pressure in the crank chamber 121 (the crank pressure) is only applied from the side of the valve hole 391 to the central portion of the diaphragm 40.
  • the pressure in the discharge pressure region is applied to the peripheral portion of the diaphragm 40.
  • FIG. 7 A third preferred embodiment of the present invention will now be described with reference to FIG. 7 .
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment.
  • a ball-shaped valve body 49 is connected to a diaphragm 40B for opening and closing the valve hole 391.
  • the valve body 49 receives the spring force of the return spring 42 through the diaphragm 40B.
  • the return spring 42 urges the valve body 49 in the direction to close the valve hole 391.
  • FIGS. 8A and 8B A fourth preferred embodiment of the present invention will now be described with reference to FIGS. 8A and 8B .
  • the same reference numerals denote the substantially identical components to those of the first preferred embodiment.
  • the by-pass valve 27C includes a cylindrical housing 51 which is screwed into a cylindrical support cylinder 50 which is in turn secured to the rear housing 13.
  • the by-pass valve 27C further includes a support seat 52 secured in the cylinder of the housing 51 and a bellows 53 connected to the support seat 52.
  • a valve body 54 is secured to the outer surface of an end portion 531 of the bellows 53.
  • the bellows 53 accommodates a guide rod 55 and a return spring as an urging means 56.
  • the return spring 56 is interposed between the support seat 52 and a head 551 of the guide rod 55.
  • a vent 521 is formed in the support seat 52, and the guide rod 55 is inserted into the vent 521.
  • Another vent 511 is formed in the end wall of the housing 51 for communication with a region (a back pressure chamber 532) in the bellows 53 through the vent 521.
  • a valve seat 57 is screwed into the cylinder of the housing 51.
  • a valve hole 571 is formed in the valve seat 57 for communication with the discharge passage 32 through the inside of the support cylinder 50.
  • An outlet 58 is formed through the circumferential wall of the support cylinder 50 and the circumferential wall of the housing 51. The outlet 58 and the valve hole 571 communicate with an internal passage 512 in the cylinder of the housing 51.
  • the valve hole 571, the internal passage 512 and the outlet 58 form part of the by-pass passage 37.
  • the valve hole 571 is opened and closed by the valve body 54. That is, the valve body 54 opens and closes the by-pass passage 37.
  • the bellows 53 and the valve body 54 separate the internal passage 512 from the back pressure chamber 532 so that the refrigerant in the internal passage 512 which is a part of the by-pass passage does not flow into the back pressure chamber 532.
  • the bellows 53 and the valve body 54 serve as an elastically deformable separator for separating the back pressure chamber 532 from the by-pass passage 37 without sliding.
  • the valve body 54 is pressed against the valve seat 57 by the atmospheric pressure applied from the back pressure chamber 381 to the end portion 531 of the bellows 53 and the spring force of the return spring 56.
  • the inside of the valve hole 571 communicates with the discharge passage 32, so that the inside of the valve hole 571 then forms a part of the discharge pressure region.
  • the inside of the internal passage 512 communicates with the crank chamber 121 through the outlet 58, so that the pressure in the inside of the internal passage 512 is substantially equivalent to the pressure in the crank chamber 121 (the crank pressure).
  • the back pressure chamber 532 communicates with the atmospheric region through the vents 521, 511. Accordingly, the back pressure chamber 532 is a part of the atmospheric region, so that the spring force of the return spring 56 and the atmospheric pressure act as the pressure applied from the back pressure chamber or the back pressure region 532 to the end portion 531 of the bellows 53. That is, the spring force of the return spring 56 and the atmospheric pressure act in opposition to the pressure in the internal passage 512 and pressure in the valve hole 571 (the discharge pressure) through the bellows 53.
  • the sum of the total discharge pressure in the valve hole 57 applied to the valve body 54 in the direction in which the valve body 54 is separated from the valve seat 57 and the total crank pressure in the internal passage 512 both applied to the valve body 54 in the direction in which the valve body 54 is moved away from the valve seat 57 is referred to as F1.
  • the total atmospheric pressure in the back pressure chamber 532 applied to the valve body 54 in the direction in which the valve body 54 is urged toward the valve body 57 and the pressure resulting from the spring force of the return spring 56 is referred to as F2.
  • F1 is lower than F2
  • the valve body 54 is held at the closed position, as shown in FIG. 8A . In this position, the by-pass passage 37 is closed, so that the refrigerant in the discharge passage 32 does not flow into the crank chamber 121 through the by-pass passage 37.
  • a fifth preferred embodiment of the present invention will now be described with reference to FIG. 9 .
  • the same reference numerals denote the substantially identical components to those of the fourth preferred embodiment.
  • a valve seat 57D is integrally formed with a cylindrical housing 51 D.
  • the valve hole 571 is formed in the valve seat 57D.
  • the support seat 52 is slidably fitted in the cylinder of the housing 51 D.
  • a screw body 59 is screwed into the cylinder of the housing 51 D.
  • the support seat 52 is pressed to contact with the screw body 59 by the spring force of the return spring 56.
  • a vent 591 is formed in the screw body 59.
  • the back pressure chamber 532 in the bellows 53 communicates with the atmospheric region through the vents 521, 591.
  • the length of the return spring 56 in the direction in which it expands and contracts may be varied.
  • the housing 51 D and the screw body 59 which are screwed relative to each other serve as the urging force adjustor for adjusting the spring force of the return spring as an urging means 56.
  • the spring force of the return spring 56 is appropriately adjusted merely by changing the position of the screw body 59 relative to the housing 51 D.
  • the position to screw the screw body 59 may be changed, for example, in such a manner that the vent 591 partially forms a square hole and the valve seat 57 is rotated by utilizing the wrench that fits the square hole.

Claims (11)

  1. Verdichter mit variabler Verdrängung zum Verdichten eines gasartigen Kältemittels mit
    einer Kurbelkammer (121),
    einer Saugdruckregion (131),
    einer Abgabedruckregion (32, 132),
    einem Zufuhrdurchgang (43), der die Abgabedruckregion (32, 132) mit der Kurbelkammer (121) verbindet,
    einem in dem Zufuhrdurchgang (43) vorgesehenen Steuerventil (45) zum Steuern der Kältemittelströmung von der Abgabedruckregion (32, 132) durch den Zufuhrdurchgang (43) zu der Kurbelkammer (121), und
    einem Ablassdurchgang (44), der die Kurbelkammer (121) mit der Saugdruckregion (131) verbindet, zum Ausströmen des Kältemittels von der Kurbelkammer (121) zu der Saugdruckregion (131),
    wobei die Verdrängung des Verdichters (10) durch Einstellen des Drucks in der Kurbelkammer (121) mittels des Steuerventils (45) gesteuert wird,
    gekennzeichnet durch
    einen Umgehungsdurchgang (37), der die Abgabedruckregion (32, 132) mit der Kurbelkammer (121) verbindet, zum Ausströmen von Kältemittel von der Abgabedruckregion (32, 132) zu der Kurbelkammer (121), und
    ein Umgehungsventil (27; 27A; 27B; 27C; 27D), das in dem Umgehungsdurchgang (37) angeordnet ist,
    wobei das Umgehungsventil (27; 27A; 27B; 27C; 27D) einen in dem Umgehungsdurchgang (37) angeordneten Ventilkörper (49; 54; 401) zum Öffnen und Schließen des Umgehungsdurchgangs (37), einen Ventilsitz (39; 57; 57D) und eine verformbare Trenneinrichtung (40; 40B; 53) hat, die eine Gegendruckregion (381; 532) von dem Umgehungsdurchgang (37) ohne Gleitbewegung trennt, und
    wobei der Ventilkörper (49; 54; 401) von einer Seite einer geöffneten Position in Richtung einer Seite einer geschlossenen Position gedrängt wird, der Ventilkörper (49; 54; 401) von dem Ventilsitz (39; 57; 57D) in der geöffneten Position beabstandet ist, der Ventilkörper (49; 54; 401) durch einen Druck, der von der Gegendruckregion (381; 532) auf die Trenneinrichtung (40; 40b; 53) aufgebracht wird, den Ventilsitz (39; 57; 57D) berührt, und der Ventilkörper (49; 54; 401) durch Verformen der Trenneinrichtung (40; 40B; 53) von der geschlossenen Position zu der geöffneten Position bewegt wird.
  2. Verdichter nach Anspruch 1, wobei die verformbare Trenneinrichtung (40; 40B; 53) so festgelegt ist, dass sie bricht, wenn sich die Druckdifferenz zwischen der Abgabedruckregion (32; 132) und der Gegendruckregion (381; 532) auf ein nicht normales Niveau erhöht.
  3. Verdichter nach Anspruch 1 oder 2, wobei die Gegendruckregion (381; 532) ein Teil einer Atmosphärenregion ist.
  4. Verdichter nach einem der Ansprüche 1 bis 3, gekennzeichnet durch eine Drängeinrichtung (42; 56) zum elastischen Drängen der verformbaren Trenneinrichtung (40; 40B; 53) von der Seite der Gegendruckregion (381; 532), um den Ventilkörper (49; 54; 401) von der Seite der geöffneten Position zu der Seite der geschlossenen Position zu drängen, und durch eine Drängkrafteinstellvorrichtung (41; 52, 57; 52, 59) zum Einstellen der Drängkraft der Drängeinrichtung (42; 56).
  5. Verdichter nach Anspruch 4, wobei die Drängeinrichtung (42; 56) eine Feder ist und die Drängkrafteinstellvorrichtung ein Schraubenbauteil ist, das als ein Federsitz (41) für die Feder dient, wobei eine Position, an der das Schraubenbauteil verschraubt ist, verändert wird, um die Federkraft der Feder zu verändern.
  6. Verdichter nach einem der Ansprüche 1 bis 5, wobei die verformbare Trenneinrichtung (40; 40B) eine Membran ist.
  7. Verdichter nach Anspruch 6, wobei die Membran einen konvexen Abschnitt als den Ventilkörper (401) zum Öffnen und Schließen eines Ventillochs (391) hat.
  8. Verdichter nach Anspruch 6, wobei der Ventilkörper (49) eine Ballform bildet, und der Ventilkörper (49) mit der Membran verbunden ist.
  9. Verdichter nach einem der Ansprüche 1 bis 5, wobei die verformbare Trenneinrichtung (53) ein Balg ist.
  10. Verdichter nach einem der Ansprüche 1 bis 9, wobei der Druck in der Abgabedruckregion (32, 132) auf einen zentralen Abschnitt des Ventilkörpers (49; 54; 401) aufgebracht wird, und der Druck in der Kurbelkammer (121) auf den Umfangsabschnitt des Ventilkörpers (49; 54; 401) aufgebracht wird.
  11. Verdichter nach einem der Ansprüche 1 bis 10, wobei sich die verformbare Trenneinrichtung (40; 40B, 53) elastisch verformt, um den Ventilkörper (49; 54; 401) von der geschlossenen Position zu der geöffneten Position zu bewegen.
EP04011301A 2003-05-14 2004-05-12 Umgehungsvorrichtung in einem Kompressor variabler Verdrängung Expired - Fee Related EP1479907B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003136407A JP2004340007A (ja) 2003-05-14 2003-05-14 可変容量型圧縮機におけるバイパス装置
JP2003136407 2003-05-14

Publications (3)

Publication Number Publication Date
EP1479907A2 EP1479907A2 (de) 2004-11-24
EP1479907A3 EP1479907A3 (de) 2005-09-14
EP1479907B1 true EP1479907B1 (de) 2008-02-27

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US (1) US20040228738A1 (de)
EP (1) EP1479907B1 (de)
JP (1) JP2004340007A (de)
DE (1) DE602004012022T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20230006288A (ko) 2021-07-02 2023-01-10 에스트라오토모티브시스템 주식회사 크랭크실의 압력을 조절하기 위한 압력 조절 밸브, 및 이를 포함하는 가변형 사판식 압축기

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005007849A1 (de) * 2005-01-25 2006-08-17 Valeco Compressor Europe Gmbh Axialkolbenverdichter
KR100631140B1 (ko) * 2005-04-25 2006-10-02 양해숙 실린더형 공기압축기의 흡배기밸브
DE102005031511A1 (de) * 2005-07-06 2007-01-11 Daimlerchrysler Ag Steuerungsventil für einen Kältemittelverdichter und Kältemittelverdichter
JP4656044B2 (ja) * 2006-11-10 2011-03-23 株式会社豊田自動織機 圧縮機の吸入絞り弁
JP5025294B2 (ja) * 2007-03-14 2012-09-12 サンデン株式会社 制御弁及び制御弁を備える可変容量圧縮機
JP5133647B2 (ja) * 2007-10-05 2013-01-30 カヤバ工業株式会社 ベーンポンプ
DE102012006907A1 (de) * 2012-04-05 2013-10-10 Gea Bock Gmbh Verdichter

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4583373A (en) * 1984-02-14 1986-04-22 Dunham-Bush, Inc. Constant evaporator pressure slide valve modulator for screw compressor refrigeration system
JPS60171989U (ja) * 1984-04-25 1985-11-14 株式会社ボッシュオートモーティブ　システム カ−ク−ラ用ベ−ン型圧縮機
JPH0631614B2 (ja) * 1986-04-17 1994-04-27 株式会社豊田自動織機製作所 可変容量圧縮機
EP0498552B1 (de) * 1991-01-28 1994-08-31 Sanden Corporation Schiefscheibenverdichter mit einer Vorrichtung zur Hubveränderung
JPH06200875A (ja) * 1993-01-08 1994-07-19 Toyota Autom Loom Works Ltd 揺動斜板式可変容量圧縮機
US5598870A (en) * 1994-11-01 1997-02-04 Toyoda Gosei Co., Ltd. Fuel tank device for vehicle having float valve and diaphragm valve
JP2000111177A (ja) * 1998-10-05 2000-04-18 Toyota Autom Loom Works Ltd 空調装置
WO2000020808A1 (fr) * 1998-10-08 2000-04-13 Zexel Valeo Climate Control Corporation Cycle frigorifique
JP2000249051A (ja) * 1999-03-01 2000-09-12 Toyota Autom Loom Works Ltd 容量可変型斜板式圧縮機の制御弁

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20230006288A (ko) 2021-07-02 2023-01-10 에스트라오토모티브시스템 주식회사 크랭크실의 압력을 조절하기 위한 압력 조절 밸브, 및 이를 포함하는 가변형 사판식 압축기

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US20040228738A1 (en) 2004-11-18
DE602004012022T2 (de) 2009-02-26
EP1479907A3 (de) 2005-09-14
JP2004340007A (ja) 2004-12-02
DE602004012022D1 (de) 2008-04-10
EP1479907A2 (de) 2004-11-24

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