WO2010041775A1 - Compresseur à capacité variable - Google Patents

Compresseur à capacité variable Download PDF

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Publication number
WO2010041775A1
WO2010041775A1 PCT/JP2009/067964 JP2009067964W WO2010041775A1 WO 2010041775 A1 WO2010041775 A1 WO 2010041775A1 JP 2009067964 W JP2009067964 W JP 2009067964W WO 2010041775 A1 WO2010041775 A1 WO 2010041775A1
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WO
WIPO (PCT)
Prior art keywords
pressure
chamber
valve
valve body
crank chamber
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PCT/JP2009/067964
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English (en)
Japanese (ja)
Inventor
幸彦 田口
Original Assignee
サンデン株式会社
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Filing date
Publication date
Application filed by サンデン株式会社 filed Critical サンデン株式会社
Priority to DE112009002441T priority Critical patent/DE112009002441T5/de
Priority to US13/123,043 priority patent/US20110194951A1/en
Publication of WO2010041775A1 publication Critical patent/WO2010041775A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure

Definitions

  • the present invention relates to a variable capacity compressor, and more particularly to a variable capacity compressor suitable for use in a refrigeration circuit of a vehicle air conditioner.
  • a capacity control valve that opens and closes a supply passage that communicates between the discharge chamber and the crank chamber by sensing suction pressure; and a throttle that is disposed in a bleed passage that communicates between the crank chamber and the suction chamber.
  • a variable capacity compressor is known in which the pressure in the crank chamber is changed by adjusting the opening, and the stroke of the reciprocating motion of the piston is adjusted to compress the refrigerant sucked into the cylinder bore from the suction chamber and discharge it into the discharge chamber (for example, Patent Document 1).
  • Such a variable capacity compressor is provided, for example, in a refrigeration circuit of a vehicle air conditioner and is used as a refrigerant compressor.
  • a small amount of the refrigerant gas throttled by the throttle through the extraction passage is extracted from the crank chamber, and the refrigerant gas in the discharge chamber is introduced into the crank chamber controlled by adjusting the opening of the capacity control valve.
  • the pressure is controlled to the target pressure, whereby the stroke of the piston is adjusted via the tilt angle control of the swash plate element, and the discharge capacity of the compressor is controlled to the target capacity.
  • the valve body of the capacity control valve opens and closes the air supply passage in response to the displacement of the pressure-sensitive member (for example, a diaphragm) that senses the suction pressure, but the discharge pressure is high. Since the amount of discharge gas introduced into the crank chamber is greatly different even when the discharge pressure is low, the throttle placed in the bleed passage that connects the crank chamber and the suction chamber is fixed at a fixed opening. In some cases, the pressure increase sensitivity of the crank chamber pressure (that is, the change amount of the crank chamber pressure with respect to the change amount of the suction pressure) also greatly changes.
  • the pressure-sensitive member for example, a diaphragm
  • an object of the present invention is to provide a variable displacement compressor including a displacement control valve that can easily adjust the pressure increase sensitivity of the crank chamber pressure to an optimum sensitivity.
  • a variable capacity compressor includes a housing in which a discharge chamber, a suction chamber, a crank chamber, and a cylinder bore are defined, a piston inserted into the cylinder bore, and the housing
  • the discharge shaft and the crank chamber are communicated with each other, a drive shaft rotatably supported therein, a motion conversion mechanism including a variable swash plate element that converts the rotation of the drive shaft into a reciprocating motion of the piston, and the discharge chamber.
  • a capacity control valve that opens and closes the air supply passage; and a throttle element disposed in a bleed passage that connects the crank chamber and the suction chamber, and changes the pressure in the crank chamber by adjusting the opening of the capacity control valve.
  • the capacity control valve includes a valve chamber that communicates with the discharge chamber, a valve hole that communicates with the valve chamber at one end, and a valve hole that communicates with the crank chamber at the other end.
  • a valve seat that faces the valve chamber and is formed around the valve hole; a valve body that is disposed in the valve chamber and that opens and closes the valve hole by contacting and separating from the valve seat; and the suction chamber
  • a pressure sensing chamber communicating with the pressure sensing member, a pressure sensing member disposed in the pressure sensing chamber and displaced in response to the pressure in the suction chamber, one end connected to the pressure sensing member, and the other end to the valve hole side
  • a pressure-sensitive rod connected to the valve body and driving the valve body in response to displacement of the pressure-sensitive member, and the pressure in the crank chamber is applied to the valve body from the valve hole side.
  • the crank chamber pressure By setting the chamber pressure larger than the pressure receiving area Sv, the crank chamber pressure always acts in the direction of closing the valve body.
  • the state in which the crank chamber pressure always acts in the direction in which the valve body is closed does not basically change even if the discharge pressure changes, so the crank chamber pressure increase sensitivity (that is, the crank chamber pressure relative to the amount of change in the suction pressure)
  • the crank chamber pressure increase sensitivity that is, the crank chamber pressure relative to the amount of change in the suction pressure
  • variable capacity compressor In practice, it is possible to satisfy the above Sr> Sv simply by changing the pressure receiving area of the crank chamber pressure of the pressure sensitive rod without changing other parts. It becomes possible to adjust the pressure increase sensitivity of the chamber pressure, and it is possible to stabilize the opening / closing state of the valve body and obtain a stable discharge capacity control state.
  • the pressure in the discharge chamber acts on the valve body in a direction to close the valve body, and the pressure receiving area where the pressure-sensitive member receives the pressure in the suction chamber is Sb.
  • Sr, Sv, and Sb may be set so as to satisfy Sb + Sv> 2Sr.
  • the suction pressure control accuracy can be improved particularly in the case of a capacity control valve structure in which the pressure in the discharge chamber acts in the direction of closing the valve body.
  • the capacity control valve further includes a pressure chamber communicating with the suction chamber, and one end of the valve body abuts and separates from the valve seat and the valve hole And the other end of the valve body is disposed in the pressure chamber so that the pressure in the suction chamber acts in a direction to close the valve body, and the pressure sensing member receives the pressure in the suction chamber.
  • Sr, Sv, Sp and Sb may be set so as to satisfy Sb + Sp + Sv> 2Sr.
  • Sr, Sv, Sp and Sb may be set so as to satisfy Sb + Sp + Sv> 2Sr.
  • Sp and Sv are set so that Sp> Sv is satisfied.
  • the throttle element arranged in the extraction passage can be a throttle element whose opening degree can be adjusted.
  • the present invention is particularly effective when the opening degree is a fixed orifice. That is, in the present invention, by applying the structure according to the present invention, it is possible to easily adjust the pressure increase sensitivity of the crank chamber pressure only by the capacity control valve, so that the crank chamber and the suction chamber communicate with each other.
  • the throttle element is an orifice having a fixed opening, it is possible to suppress the fluctuation in the pressure increase sensitivity of the crank chamber pressure particularly when the discharge gas introduction amount fluctuates greatly.
  • variable capacity compressor can be applied to any variable capacity compressor in which the stroke of the reciprocating motion of the piston is adjusted by changing the pressure of the crank chamber by adjusting the opening of the capacity control valve.
  • it is suitable for a compressor provided in a refrigeration circuit of a vehicle air conditioner, and can suppress the hunting phenomenon of the valve body of the capacity control valve, so that the operation of the valve body can be stabilized. The occurrence of temperature fluctuations in the room can be prevented. Further, since it is possible to suppress the torque fluctuation of the compressor, it is possible to prevent the engine control from being adversely affected particularly when the compressor drive source is an engine.
  • the relationship between the pressure receiving area Sr of the crank chamber pressure of the pressure sensing rod in the capacity control valve and the pressure receiving area Sv of the crank chamber pressure of the valve body is set to Sr> Sv. It is possible to easily adjust the pressure increase sensitivity of the crank chamber pressure, and it is possible to stably perform target capacity control while suppressing the occurrence of the hunting phenomenon of the valve body. In particular, it is possible to easily adjust the pressure increase sensitivity of the crank chamber pressure by simply changing the pressure receiving area of the crank chamber pressure of the pressure sensing rod, and the valve body opening / closing operation is stabilized to obtain a stable discharge capacity control state. be able to.
  • the suction pressure control accuracy can be improved.
  • the suction pressure control accuracy can be improved.
  • the throttle element arranged in the extraction passage that connects the crank chamber and the suction chamber is an orifice whose opening is fixed.
  • the present invention is particularly effective.
  • FIG. 3 is a relationship diagram between a suction pressure and a crank chamber pressure showing an operation at each condition of the capacity control valve of FIG. 2.
  • FIG. 3 is a relationship diagram between discharge pressure and suction pressure showing an example of control characteristics of the capacity control valve of FIG. 2.
  • FIG. 6 is a relationship diagram between a current of an electromagnetic coil and a control suction pressure showing an example of control characteristics by the capacity control valve of FIG. 5.
  • FIG. 1 to 4 are a longitudinal sectional view of a variable capacity compressor according to a first embodiment of the present invention, a longitudinal sectional view of a capacity control valve used in the variable capacity compressor, and an operation explanatory view thereof.
  • the variable capacity compressor 100 includes a cylinder block 101 having a plurality of cylinder bores 101a, a front housing 102 provided at one end of the cylinder block 101, and a rear provided via a valve plate 103 at the other end of the cylinder block 101.
  • the housing 104 is provided, and these constitute the housing referred to in the present invention.
  • a drive shaft 106 is provided across the crank chamber 105 defined by the cylinder block 101 and the front housing 102, and a swash plate 107 is disposed around the center thereof.
  • the swash plate 107 is coupled to the rotor 108 fixed to the drive shaft 106 via a connecting portion 109, and the inclination angle can be changed along the drive shaft 106.
  • a coil spring 110 is mounted between the rotor 108 and the swash plate 107 to urge the swash plate 107 toward the minimum inclination side, and the swash plate 107 is disposed on the opposite side of the swash plate 107.
  • a coil spring 111 that biases the tilt angle toward the increasing direction is mounted.
  • One end of the drive shaft 106 extends through the boss portion 102a protruding to the outside of the front housing 102 and extends to the outside, and is connected to an electromagnetic clutch (not shown).
  • a shaft seal device 112 is inserted between the drive shaft 106 and the boss portion 102a to block the inside and outside of the compressor.
  • the drive shaft 106 is supported by bearings 113, 114, 115, and 116 in the radial direction and the thrust direction, and power from an external drive source (for example, a vehicle engine) is transmitted through an electromagnetic clutch so as to be rotatable. .
  • a piston 117 is inserted into the cylinder bore 101a so as to be able to reciprocate.
  • the periphery of the outer periphery of the swash plate 107 is accommodated in a recess 117a at one end inside the piston 117.
  • the piston 117 and the swash plate 107 are configured to interlock with each other via a pair of shoes 118 that are in sliding contact. Therefore, the rotation of the drive shaft 106 enables the piston 117 to reciprocate within the cylinder bore 101a, and these series of members constitute the motion conversion mechanism referred to in the present invention.
  • a suction chamber 119 and a discharge chamber 120 are defined in the rear housing 104.
  • the suction chamber 119 is connected to the cylinder bore 101a through a communication hole 103a (suction hole) provided in the valve plate 103 and a suction valve (not shown).
  • the discharge chamber 120 communicates with the cylinder bore 101a via a discharge valve (not shown) and a communication hole 103b (discharge hole) provided in the valve plate 103.
  • the suction chamber 119 is connected to the air conditioner system side via the suction port 104a, and the discharge chamber 120 is connected to the air conditioner system side via the discharge port 104b.
  • the rear housing 104 is provided with a capacity control valve 200.
  • the capacity control valve 200 adjusts the opening of an air supply passage 121 (121a, 121b) that communicates the discharge chamber 120 and the crank chamber 105, and controls the amount of discharge gas introduced into the crank chamber 105.
  • the refrigerant in the crank chamber 105 is sucked into the suction chamber through a bleed passage through a clearance between the outer periphery of the drive shaft 106 and the bearings 115 and 116, a space 122 and a fixed orifice 103c formed in the valve plate 103 with a fixed opening. It flows to 119. Therefore, the discharge capacity can be controlled by adjusting the discharge gas introduction amount into the crank chamber 105 by the capacity control valve 200 and changing the pressure in the crank chamber 105.
  • Capacity control valve structure (Fig. 2) As shown in FIG.
  • the capacity control valve 200 includes a valve housing 210, a valve body 220, a pressure sensitive rod 230, a bellows assembly 240 as a pressure sensitive member, a spring 250, and a spring guide 260. And sealing members 270, 271 and 272.
  • the valve housing 210 includes a member 210a that accommodates the bellows assembly 240 and a member 210b in which the pressure sensitive rod 230 is slidably supported and the valve body 220 is disposed.
  • the member 210b is press-fitted and fixed to the member 210a. ing.
  • the member 210a and the member 210b define a pressure sensitive chamber 211, and the pressure sensitive chamber 211 communicates with the suction chamber 119 via the communication hole 212 and the communication passage 123 (FIG. 1).
  • a valve chamber 213 is formed in the member 210b, and one of the valve chambers 213 communicates with the discharge chamber 120 via a communication hole 261 and an air supply passage 121a formed in the spring guide 260, and the other of the valve chambers 213 is a valve
  • the crank chamber 105 communicates with the hole 214, the communication hole 215, and the air supply passage 121b.
  • a valve body 220 is disposed in the valve chamber 213, and the valve body 220 contacts and separates from a valve seat 216 formed around the valve hole 214 to open and close the valve hole 214.
  • One end of the spring 250 abuts on the valve body 220 and the other end abuts on the spring guide 260, and the valve body 220 is urged in the valve closing direction by the urging force of the spring 250.
  • the spring guide 260 is press-fitted and fixed to the peripheral wall of the valve chamber 213.
  • An insertion hole 217 that slidably supports the pressure-sensitive rod 230 is formed in the member 210b, and a gap between the outer periphery of the pressure-sensitive rod 230 and the insertion hole 217 is set to a minimum, and the pressure-sensitive chamber 211 and the valve hole 214 Is almost airtight.
  • the bellows assembly 240 is positioned on the bellows 241, the end member 242 that closes both ends of the bellows 241, the guide member 243 that receives one end of the pressure-sensitive rod 230, and the member 210a.
  • a compression coil spring 245 that is arranged inside the bellows 241 and biases the bellows assembly 240 in the extending direction.
  • the inside of the bellows assembly 240 is maintained in a substantially vacuum state.
  • the bellows assembly 240 is disposed in the pressure-sensitive chamber 211, and a positioning member 244 is fitted and fixed in a positioning hole 218 formed in the member 210a.
  • the guide member 243 receives one end of the pressure-sensitive rod 230, and the other end of the pressure-sensitive rod 230 contacts the valve body 220 from the valve hole 214 side, so that the valve body 220 corresponds to the expansion and contraction of the bellows assembly 240. Opens and closes the valve hole 214.
  • the seal member 270 ensures airtightness between the atmosphere side and the region where the pressure of the suction chamber 119 acts, and the seal member 271 is formed between the region where the pressure of the suction chamber 119 acts and the region where the pressure of the crank chamber 105 acts. Further, the seal member 272 ensures airtightness between the region where the crank chamber 105 pressure acts and the region where the discharge chamber 120 pressure acts.
  • the valve body 220 has a pressure in the discharge chamber 120 in the valve closing direction (hereinafter referred to as discharge pressure Pd) and a pressure in the crank chamber 105 in the valve opening direction (hereinafter referred to as crank chamber pressure Pc).
  • the crank chamber pressure Pc acts in the valve closing direction on the pressure sensitive rod 230, and the pressure of the suction chamber 119 (hereinafter referred to as the suction pressure Ps) acts in the valve opening direction.
  • the suction pressure Ps acts on the bellows assembly 240 in the valve closing direction.
  • the pressure receiving area Sv of the crank chamber pressure Pc acting on the valve body 220 is substantially equal to the cross-sectional area of the valve hole 214.
  • the pressure receiving area Sr of the crank chamber pressure Pc acting on the pressure sensing rod 230 is a cross-sectional area of the pressure sensing rod 230 in a region supported by the insertion hole 217, and is set to Sr> Sv.
  • the crank chamber pressure Pc always acts in the direction in which the valve body 220 is closed. If the pressure receiving area (effective area) of the suction pressure Ps acting in the expansion / contraction direction of the bellows assembly 240 is Sb, the biasing force of the spring 250 is fs, and the biasing force of the bellows assembly 240 is Fb, it acts on the valve body 220.
  • the force can be expressed by the following formula [Expression 1] (including Formula (1) and Formula (2)).
  • the coefficient (Sb ⁇ Sr) / (Sr ⁇ Sv) of Ps is the sensitivity of Pc change to Ps change.
  • the sensitivity of the crank chamber pressure Pc when the suction pressure Ps changes depending on the magnitude of (Sb ⁇ Sr) / (Sr ⁇ Sv). Changes. Since Sb, Sv, and Sr are the pressure receiving areas of the respective pressures, the sensitivity of the crank chamber pressure Pc when the suction pressure Ps changes can be adjusted by adjusting the pressure receiving areas.
  • the suction pressure Ps can be accurately controlled by setting Sb, Sr, and Sv so as to satisfy (Sb ⁇ Sr) / (Sr ⁇ Sv)> 1, that is, Sb + Sv> 2Sr.
  • Sr> Sv the crank chamber pressure Pc acts in the direction of closing the valve body 220, and as a result, as shown in [Equation 1], the sensitivity of the crank chamber pressure Pc when the suction pressure Ps changes is shown.
  • Pd constant.
  • Equation (3) shows the suction pressure control characteristic of the displacement control valve 200, and as shown in FIG. 4, the suction pressure Ps to be controlled is slightly reduced and corrected when the discharge pressure Pd increases.
  • the refrigerant pressure is balanced. For example, if the outside air temperature is high, the suction pressure Ps is significantly higher than the expression (3).
  • the bellows assembly 240 is contracted by the force of the suction pressure Ps, whereby the valve body 220 closes the valve hole 214.
  • the discharge gas is not introduced into the crank chamber 105, so that the refrigerant gas (blow-by gas) in the crank chamber 105 flows into the suction chamber 119 via the extraction passage, and the crank chamber pressure is increased.
  • Pc becomes equal to the suction pressure Ps.
  • the inclination angle of the swash plate 107 increases and the piston stroke is maintained at the maximum.
  • the bellows assembly 240 expands.
  • the degree of increase in the crank chamber pressure Pc that is, the amount of change in the crank chamber pressure Pc relative to the amount of change in the suction pressure Ps is appropriately adjusted by setting Sb, Sr, and Sv (Sb + Sv> 2Sr).
  • Sb, Sr, and Sv Sb + Sv> 2Sr.
  • the bellows assembly 240 extends again to push up the valve body 220, the amount of discharge gas introduced into the crank chamber 105 is increased, and the crank chamber pressure Pc is increased.
  • the tilt angle of the swash plate 107 is reduced and the piston stroke is reduced.
  • the piston stroke is controlled so that the suction pressure Ps approaches the suction pressure control characteristic of the above formula (3).
  • FIG. 5 shows a capacity control valve 300 in the second embodiment of the present invention.
  • the second embodiment basically differs from the first embodiment described above in that the discharge pressure Pd acts in the direction of closing the valve body in the capacity control valve 200 of FIG. 2, but the capacity control of FIG.
  • the valve 300 has a structure in which the suction pressure Ps acts in the direction in which the valve body is closed, and the discharge pressure Pd does not act on the valve body.
  • the valve 300 is a capacity control valve by a so-called external control system in which electromagnetic force is applied to the valve body. That is.
  • Capacity control valve structure Referring to FIG.
  • the capacity control valve 300 is disposed in a pressure sensing chamber 302 formed in the valve housing 301, receives the suction pressure through the communication hole 301a and the communication path 123, and evacuates the inside to be a spring.
  • a bellows assembly 303 that functions as a pressure-sensitive member, a pressure-sensitive rod 304 that has one end abutting against the bellows assembly 303 and is slidably supported by the valve housing 301, and the pressure-sensitive rod 304
  • a valve body 304a that is integrally formed and that has the other end slidably supported by the support hole 305a of the fixed core 305 and that is disposed in the valve chamber 306 and opens and closes the valve hole 301b according to the expansion and contraction of the bellows assembly 303.
  • the solenoid rod 3 has one end abutting against the other end surface of the valve body 304a and the other end fixed to the fixed core 305 and a movable core 307 disposed opposite to the fixed core 305 with a predetermined gap.
  • a spring 309 that presses the movable core 307 in the valve closing direction, an outer peripheral portion of the movable core 307 slidably supported, and a non-magnetic sleeve 311 that is fixed to the solenoid case 310 by inserting the fixed core 305.
  • the coil 312 is disposed outside the sleeve 311 and inside the solenoid case 310 and generates electromagnetic force.
  • the solenoid includes a fixed core 305, a movable core 307, a solenoid rod 308, a sleeve 311, a solenoid case 310, and an electromagnetic coil 312. Further, the end of the bellows assembly 303 opposite to the pressure-sensitive rod 304 is supported by a bellows guide 313, and the bellows guide 313 is slidably supported by the pressure setting member 314. Further, between the pressure setting member 314 and the bellows guide 313, a forced opening spring 315 that presses the bellows assembly 303 in the valve opening direction is disposed. The pressure setting member 314 is press-fitted and fixed to the valve housing 301 so that the capacity control valve 300 is set to a predetermined pressure.
  • the valve chamber 306 communicates with the discharge chamber 120 through the communication hole 301c.
  • the valve hole 301b communicates with the crank chamber 105 through a communication hole 301d. Therefore, the communication hole 301 c, the valve chamber 306, the valve hole 301 b, and the communication hole 301 d constitute a part of the air supply passage 121.
  • the space inside the sleeve 311 in which the movable core 307, the solenoid rod 308, and the surface on the other end side of the valve body 304a are disposed communicates with the pressure sensitive chamber 302 through the communication hole 301e.
  • the crank chamber pressure Pc acts on the surface on one end side (valve hole 301b side) of the valve body 304a, and the suction pressure Ps acts on the surface on the other end side of the valve body 304a. Since the sectional area Sp of the valve body 304a supported by the support hole 305a is set to be slightly larger than the sectional area Sv of the valve hole 301b, the force of the discharge pressure Pd in the valve chamber 306 in the valve opening direction of the valve body 304a. Is acting slightly. Further, the cross-sectional area Sr of the pressure-sensitive rod 304 is set larger than the cross-sectional area Sv of the valve hole 301b, and the crank chamber pressure Pc acts in the direction of closing the valve body.
  • the force acting on the valve body 304a of the capacity control valve 300 can be expressed by the following formula [Expression 3] (including Formula (4) and Formula (5)).
  • the meanings represented by the symbols in Equation 3 are as follows.
  • Sp pressure receiving area of the suction pressure acting on the valve body
  • Sr crank chamber pressure acting on the pressure sensing rod
  • Pressure receiving area Sb pressure receiving area (effective area) of suction pressure acting in the expansion / contraction direction of the bellows
  • fs1 biasing force of the spring 309
  • fs2 biasing force of the spring 315
  • Fb biasing force F (I) of the bellows assembly 303: electromagnetic force of the solenoid
  • Pc is a linear function of Ps
  • Pc decreases as Ps increases, and conversely increases as Ps decreases, and its inclination is
  • the coefficient (Sb + Sp ⁇ Sr) / (Sr ⁇ Sv) of Ps is the sensitivity of Pc change to Ps change. Since Sb, Sv, Sp, and Sr are the pressure receiving areas of the respective pressures, the sensitivity of the crank chamber pressure Pc when the suction pressure Ps changes can be adjusted by adjusting the pressure receiving areas.
  • Sp is set slightly larger than Sv. For example, if the opening degree of the valve body 304a increases and the crank chamber pressure Pc increases, the discharge capacity decreases, but the discharge pressure Pd decreases as the discharge capacity decreases. If Sp> Sv is set so that the discharge pressure Pd acts in the valve opening direction, the force in the valve opening direction due to the discharge pressure Pd acting on the valve body 304a decreases when the discharge capacity decreases. There is an effect of suppressing excessive opening of the valve body 304a, which contributes to stabilization of the open / closed state of the valve body 304a.
  • the capacity control valve shown in FIG. 2 is a mechanical control valve, but may be an externally controlled capacity control valve in which a solenoid is added thereto to apply an electromagnetic force to the valve body.
  • the present invention can be used for a variable displacement compressor driven by a swing plate type variable displacement compressor or a motor, and can be used for either a variable displacement compressor equipped with an electromagnetic clutch or a clutchless compressor. .
  • the throttle element of the bleed passage in addition to the above-mentioned orifice with a fixed opening, it is also possible to employ a variable flow rate throttle or a structure in which opening and closing is controlled by a valve body. Furthermore, the present invention can also be applied to a variable capacity compressor that uses a new refrigerant (for example, a refrigerant that has been recently announced to prevent global warming) instead of the current R134a.
  • a new refrigerant for example, a refrigerant that has been recently announced to prevent global warming
  • the present invention can be applied to any variable capacity compressor in which the stroke of the piston is adjusted by changing the pressure in the crank chamber by adjusting the opening of the capacity control valve, and particularly in a refrigeration circuit of a vehicle air conditioner. It is suitable for the variable capacity compressor provided.

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

Abstract

L’invention concerne un compresseur à capacité variable doté d'une soupape de régulation de capacité capable de régler facilement à un niveau optimal la sensibilité à une augmentation de la pression dans un carter. L’invention concerne un compresseur à capacité variable configuré de sorte que la course d’un piston soit modifiée en réglant la pression dans un carter, la pression dans le carter étant modifiée en réglant le degré d’ouverture d’une soupape de régulation de capacité pour ouvrir et fermer un circuit permettant l’interconnexion d’une chambre d’évacuation et d’un carter, la soupape de régulation de capacité étant dotée d'une chambre de soupape communiquant avec la chambre d'évacuation, d'un orifice de soupape, d'un élément de soupape permettant d'ouvrir et de fermer l'orifice de soupape, d’une chambre de détection de pression communiquant avec une chambre d'aspiration, d’un élément de détection de pression disposé dans la chambre de détection de pression, et d’une tige de détection de pression comprenant une extrémité reliée à l’élément de détection de pression et l'autre extrémité reliée à l’élément de soupape et entraînant l'élément de soupape en réponse au déplacement de l'élément de détection de pression. La pression dans le carter agit sur l'élément de soupape depuis le côté de l'orifice de soupape dans la direction d’ouverture de l’élément de soupape, et agit sur la tige de détection de pression depuis le côté de l’orifice de soupape dans la direction de fermeture de l’élément de soupape. La zone (Sr) de la tige de détection de pression qui reçoit la pression dans le carter est conçue de manière à être plus importante que la zone (Sv) de l’élément de soupape qui reçoit la pression dans le carter.
PCT/JP2009/067964 2008-10-09 2009-10-09 Compresseur à capacité variable WO2010041775A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112009002441T DE112009002441T5 (de) 2008-10-09 2009-10-09 Verdichter mit variabler Verdrängung
US13/123,043 US20110194951A1 (en) 2008-10-09 2009-10-09 Variable Displacement Compressor

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JP2008262768A JP5142212B2 (ja) 2008-10-09 2008-10-09 可変容量圧縮機
JP2008-262768 2008-10-09

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WO2010041775A1 true WO2010041775A1 (fr) 2010-04-15

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JP (1) JP5142212B2 (fr)
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WO (1) WO2010041775A1 (fr)

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CN112762874A (zh) * 2021-01-26 2021-05-07 中广核核电运营有限公司 一种波纹管膨胀节位移测量方法

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JP6340501B2 (ja) * 2014-06-19 2018-06-13 株式会社テージーケー 可変容量圧縮機用制御弁

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JPS63190579U (fr) * 1987-05-27 1988-12-08
JP2007064028A (ja) * 2005-08-29 2007-03-15 Sanden Corp 可変容量圧縮機
JP2007107538A (ja) * 2007-01-26 2007-04-26 Sanden Corp 可変容量圧縮機
JP2008202480A (ja) * 2007-02-19 2008-09-04 Sanden Corp 可変容量圧縮機の容量制御弁

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