[go: up one dir, main page]

WO2009116485A1 - Soupape de commande de cylindrée pour compresseur à cylindrée variable et compresseur à cylindrée variable de type alternatif - Google Patents

Soupape de commande de cylindrée pour compresseur à cylindrée variable et compresseur à cylindrée variable de type alternatif Download PDF

Info

Publication number
WO2009116485A1
WO2009116485A1 PCT/JP2009/055020 JP2009055020W WO2009116485A1 WO 2009116485 A1 WO2009116485 A1 WO 2009116485A1 JP 2009055020 W JP2009055020 W JP 2009055020W WO 2009116485 A1 WO2009116485 A1 WO 2009116485A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
valve body
chamber
control valve
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.)
Ceased
Application number
PCT/JP2009/055020
Other languages
English (en)
Japanese (ja)
Inventor
田口幸彦
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of WO2009116485A1 publication Critical patent/WO2009116485A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1854—External parameters
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a capacity control valve and a reciprocating variable capacity compressor for a variable capacity compressor applied to an air conditioning system.
  • a swash plate type variable capacity compressor includes a housing, and inside the housing is a discharge pressure region (discharge chamber), a suction pressure region (suction chamber), A crank chamber and a cylinder bore are defined.
  • a swash plate is tiltably connected to a drive shaft extending in the crank chamber, and a conversion mechanism including the swash plate converts the rotation of the drive shaft into a reciprocating motion of a piston disposed in the cylinder bore.
  • the reciprocating motion of the piston performs the steps of sucking the working fluid from the suction chamber into the cylinder bore, compressing the sucked working fluid, and discharging the compressed working fluid into the discharge chamber.
  • the stroke length of the piston that is, the discharge capacity of the compressor is variable by changing the crank chamber pressure (crank pressure Pc) as the control pressure.
  • crank pressure Pc crank pressure
  • a capacity control valve is accommodated in the housing.
  • the capacity control valve is disposed in an air supply passage that communicates the discharge chamber and the crank chamber, and a throttle is disposed in an extraction passage that communicates the crank chamber and the suction chamber.
  • the capacity control valve disclosed in Patent Document 1 has an operating rod, and the operating rod has a valve body portion and a guide rod portion. It is considered that the pressure of the discharge chamber (discharge pressure Pd) acts on the inner portion of the end face of the valve body, and the crank pressure Pc acts on the outer portion thereof. It is considered that the pressure of the suction chamber (suction pressure Ps) acts on the end surface of the guide rod portion, and the discharge pressure Pd and the suction pressure Ps act on the operating rod in directions opposite to each other.
  • discharge pressure Pd discharge pressure
  • suction pressure Ps suction pressure
  • the energization amount to the capacity control valve is changed using the Pd-Ps differential pressure as a control target, and the discharge capacity is changed accordingly. For example, in this air conditioner, if the Pd-Ps differential pressure is to be reduced, the discharge capacity is increased to operate the Pd-Ps differential pressure close to a predetermined value.
  • the throttle is a pressure reducing part, and it is reasonable to think that there is a pressure gradient from the inside (discharge pressure side) to the outside (crank pressure side) of the seal width, and because the fluid flows, the valve body On the other hand, dynamic pressure may act in the valve opening direction. Considering this, it is unlikely that the area where the discharge pressure Pd acts is SG and the area where the crank pressure Pc acts is SF-SG.
  • the valve hole diameter of the capacity control valve of the variable capacity compressor is, for example, in the range of 2 mm to 3.5 mm when R134a is a refrigerant, and is 0.4 mm to, for example, when carbon dioxide is a refrigerant.
  • the valve hole area is very small.
  • a slight difference in pressure receiving area greatly affects the control characteristics of the Pd-Ps differential pressure, as can be seen from the equations (6) to (8). .
  • this effect becomes significant in a region where the Pd-Ps differential pressure is large.
  • the flat end surface of the valve body portion is in contact with the valve seat, and the shape of the contact portion between the valve body portion and the valve seat is an annular shape. It is thought that. For this reason, it is reasonable to consider that the crank pressure Pc does not act on the valve body in a state where the valve body closes the valve hole. In other words, in this capacity control valve, the force acting on the valve body portion is different between when the valve hole is closed and when the valve hole is open, with respect to the operating characteristics of the valve body portion when opening from the closed state. The operating characteristics of the valve body after opening are deviated. Such a deviation in the operating characteristics of the valve body is not preferable because it causes variation in capacity control.
  • the present invention has been made on the basis of the above-described circumstances, and the purpose thereof is a variable in which the pressure receiving area where the valve body receives pressure through the valve hole is suppressed from changing with the opening / closing operation, and the accuracy of capacity control is improved.
  • a capacity control valve of a capacity compressor and a reciprocating variable capacity compressor provided with the capacity control valve.
  • the displacement control valve of the variable displacement compressor is a variable displacement inserted in an air supply passage connecting the discharge pressure region of the reciprocating variable displacement compressor and the crank chamber.
  • a pressure sensing chamber communicating with the suction pressure region of the reciprocating variable displacement compressor
  • a valve chamber communicating with the crank chamber via a part of the air supply passage
  • the air supply passage A valve hole that communicates with the discharge pressure region through the remaining portion and opens into the valve chamber
  • a valve housing that has an insertion hole that extends between the valve chamber and the pressure sensing chamber, and provided in the valve housing
  • a valve seat that surrounds the opening of the valve hole
  • a cylindrical outer peripheral surface disposed in the valve chamber, and the outer periphery One end portion having a sealing region that can be brought into contact with the valve seat in a state close to a line contact, and slidably supported
  • the distance (seal width) between the inner edge and the outer edge of the seal region is about 0.05 mm to 0.3 mm, depending on the outer diameter of the valve body.
  • the contact area between the seal area and the valve seat is small.
  • the valve body and the valve seat are formed such that a distance between the valve body and the valve seat increases as it goes radially inward from a seal region of the valve body. 2).
  • the valve seat has a flat surface, and the valve body has a recess radially inward of the seal region.
  • the outer diameter of the one end portion of the valve body is larger than the outer diameter of the sliding portion.
  • a reciprocating variable displacement compressor comprising the displacement control valve of the variable displacement compressor according to any one of claims 1 to 4. 5).
  • the reciprocating variable displacement compressor is used for compressing carbon dioxide as a refrigerant.
  • the capacity control valve of the variable capacity compressor of the present invention since the valve body comes into contact with the valve seat in a state close to line contact, the area (pressure receiving area) of the valve body that receives the discharge pressure through the valve hole is clearly defined. Is done. Further, in the valve body, since the seal region is located on the edge side of the cylindrical outer peripheral surface, the valve body is hardly affected by dynamic pressure in the valve opening direction when the valve is opened. Therefore, in this capacity control valve, the operating characteristics of the valve body when it is changed from the closed state to the open state and the operating characteristics of the valve body when it is in the open state are expressed with high accuracy by the same characteristic equation. Can do.
  • the pressure receiving area that receives the discharge pressure through the valve hole in the valve body is substantially defined by the outer diameter or the cross-sectional area of the end of the cylindrical outer peripheral surface, that is, one end of the valve body.
  • the area to receive is defined by the outer diameter or cross-sectional area of the sliding part. Since the one end part and the sliding part of the valve body are integrated to form the same component (valve body), the area adjustment between the area receiving the discharge pressure and the area receiving the suction pressure is It is carried out with high accuracy during body manufacturing. As a result, in the variable capacity compressor to which the capacity control valve is applied, the discharge capacity can be controlled with high accuracy (claim 1).
  • the pressure receiving area is clearly defined by increasing the distance between the valve body and the valve seat as it goes radially inward from the seal region.
  • the area where the valve body receives pressure through the valve hole is reliably suppressed from changing between the closed state and the open state, and the discharge capacity is reliably ensured in the variable capacity compressor to which the capacity control valve is applied. It is controlled with high accuracy (claim 2).
  • the valve seat is a flat surface, even if the valve body is misaligned with respect to the valve seat, the valve hole is reliably closed by the valve body. As a result, undesired valve leakage is prevented with this capacity control valve.
  • the area receiving the discharge pressure and the area receiving the suction pressure are determined by the dimensions of the one end part and the sliding part of the valve body, the area difference between the area receiving the discharge pressure and the area receiving the suction pressure is adjusted with high accuracy. . And by making one end part larger diameter than a sliding part, it adjusts so that the area which a valve body receives crank pressure in a valve closing direction may increase with high precision. As a result, the crank pressure increasing speed is controlled to decrease with high accuracy, and the discharge capacity is stably controlled.
  • variable capacity compressor the stroke length defined by the minimum inclination angle of the swash plate element can be set very small, and the variable range of the discharge capacity is wide. If the capacity control valve described above is applied to a reciprocating variable capacity compressor, the discharge capacity can be controlled with high accuracy over the entire variable range.
  • the inner diameter of a valve hole of a displacement control valve is designed to be small. Therefore, in the reciprocating variable displacement compressor, even if the inner diameter of the valve hole is small, the valve body contacts the valve seat in a state close to a line contact, so that the discharge capacity is controlled with high accuracy (claim) Item 6).
  • FIG. 2 is an enlarged view of region III in FIG.
  • FIG. 3 is an enlarged view of region IV in FIG. 3 and a diagram showing a relationship between a pressure receiving area and a cross-sectional area
  • FIG. 3 is a graph showing the relationship between the control current supplied to the capacity control valve and the Pd ⁇ Ps differential pressure as the operating characteristics of the valve body in the refrigeration cycle of FIG.
  • an enlarged view corresponding to the region IV in FIG. In the capacity control valve of the second embodiment, an enlarged view corresponding to the region IV in FIG.
  • an enlarged view corresponding to the region IV in FIG. It is a graph for demonstrating the operating characteristic of the valve body in the other discharge capacity
  • FIG. 1 shows a refrigeration cycle 10 of a vehicle air conditioning system
  • the refrigeration cycle 10 includes a circulation path 12 through which a refrigerant as a working fluid circulates.
  • the compressor 100, the radiator (condenser or gas cooler) 14, the expander 16, and the evaporator 18 are sequentially inserted in the flow direction of the refrigerant, and when the compressor 100 is activated, the compressor 100
  • the refrigerant circulates through the circulation path 12 in accordance with the discharge capacity of the refrigerant. That is, the compressor 100 performs a series of processes including a refrigerant suction process, a suction refrigerant compression process, and a compressed refrigerant discharge process.
  • the radiator 14 has a function of cooling the refrigerant discharged from the compressor 100, and the cooled refrigerant is expanded by passing through the expander 16.
  • the expanded refrigerant is vaporized in the evaporator 18, and the vaporized refrigerant is sucked into the compressor 100.
  • the evaporator 18 also constitutes a part of the air circuit of the vehicle air conditioning system, and the air flow passing through the evaporator 18 is cooled by taking heat of vaporization by the refrigerant in the evaporator 18.
  • the compressor 100 is a variable capacity compressor, for example, a swash plate type clutchless compressor.
  • the compressor 100 includes a cylinder block 101, and the cylinder block 101 is formed with a plurality of cylinder bores 101a.
  • a front housing 102 is connected to one end of the cylinder block 101, and a rear housing (cylinder head) 104 is connected to the other end of the cylinder block 101 via a valve plate 103.
  • the cylinder block 101 and the front housing 102 define a crank chamber 105, and a drive shaft 106 extends longitudinally through the crank chamber 105.
  • the drive shaft 106 passes through an annular swash plate 107 disposed in the crank chamber 105, and the swash plate 107 is hinged to a rotor 108 fixed to the drive shaft 106 via a connecting portion 109. Accordingly, the swash plate 107 can tilt while moving along the drive shaft 106.
  • a portion of the drive shaft 106 extending between the rotor 108 and the swash plate 107 is provided with a coil spring 110 that urges the swash plate 107 toward the minimum inclination angle.
  • a coil spring 111 that urges the swash plate 107 toward the maximum inclination angle is attached to a portion of the drive shaft 106 that extends between the swash plate 107 and the cylinder block 101.
  • the drive shaft 106 penetrates through a boss portion 102a protruding outside the front housing 102, and is connected to a pulley 112 as a power transmission device at the outer end of the drive shaft 106.
  • the pulley 112 is rotatably supported by a boss portion 102a via a ball bearing 113, and a belt 115 is wound around a pulley of an engine 114 as an external drive source.
  • a shaft seal device 116 is disposed inside the boss portion 102a to block the inside and the outside of the front housing 102 from each other.
  • the drive shaft 106 is rotatably supported by bearings 117, 118, 119, and 120 in the radial direction and the thrust direction. Power from the engine 114 is transmitted to the pulley 112, and can rotate in synchronization with the rotation of the pulley 112.
  • a piston 130 is disposed in the cylinder bore 101a, and a tail portion protruding into the crank chamber 105 is formed integrally with the piston 130.
  • a pair of shoes 132 is disposed in a recess 130a formed in the tail portion, and the shoes 132 are in sliding contact with the outer peripheral portion of the swash plate 107 so as to be sandwiched therebetween. Therefore, the piston 130 and the swash plate 107 are interlocked with each other via the shoe 132, and the piston 130 reciprocates in the cylinder bore 101a by the rotation of the drive shaft 106.
  • a suction chamber 140 and a discharge chamber 142 are defined in the rear housing 104, and the suction chamber 140 can communicate with the cylinder bore 101 a through a suction hole 103 a provided in the valve plate 103.
  • the discharge chamber 142 communicates with the cylinder bore 101a through a discharge hole 103b provided in the valve plate 103.
  • the suction hole 103a and the discharge hole 103b are opened and closed by a suction valve and a discharge valve (not shown), respectively.
  • a muffler 150 is provided outside the cylinder block 101, and the muffler casing 152 is joined to a muffler base 101b formed integrally with the cylinder block 101 via a seal member (not shown).
  • the muffler casing 152 and the muffler base 101b define a muffler space 154, and the muffler space 154 communicates with the discharge chamber 142 via a discharge passage 156 that passes through the rear housing 104, the valve plate 103, and the muffler base 101b.
  • a discharge port 152a is formed in the muffler casing 152, and a check valve 200 is disposed in the muffler space 154 so as to block between the discharge passage 156 and the discharge port 152a.
  • the check valve 200 opens and closes according to the pressure difference between the pressure on the discharge passage 156 side and the pressure on the muffler space 154 side, and closes when the pressure difference is smaller than a predetermined value ⁇ Pset, and the pressure difference is When it is larger than the predetermined value ⁇ Pset, the opening operation is performed.
  • the discharge chamber 142 can communicate with the forward portion of the circulation path 12 via the discharge passage 156, the muffler space 154, and the discharge port 152a, and the muffler space 154 is interrupted by the check valve 200.
  • the suction chamber 140 communicates with the return path portion of the circulation path 12 via a suction port 104 a formed in the rear housing 104.
  • the rear housing 104 accommodates a capacity control valve (electromagnetic control valve) 300 of the variable capacity compressor of the first embodiment of the present invention, and the capacity control valve 300 is inserted in the air supply passage 160.
  • the air supply passage 160 extends from the rear housing 104 to the cylinder block 101 through the valve plate 103 so as to communicate between the discharge chamber 142 and the crank chamber 105.
  • the suction chamber 140 communicates with the crank chamber 105 via the extraction passage 162.
  • the extraction passage 162 includes a clearance between the drive shaft 106 and the bearings 119 and 120, a space 164, and a fixed orifice 103 c formed in the valve plate 103.
  • the suction chamber 140 is connected to the capacity control valve 300 independently of the air supply passage 160 through a pressure sensitive passage 166 formed in the rear housing 104. More specifically, the capacity control valve 300 includes a valve unit and a solenoid unit that opens and closes the valve unit.
  • the valve unit has a cylindrical valve housing 301, and an inlet port (valve hole 301 a) is formed at one end of the valve housing 301.
  • the valve hole 301 a communicates with the discharge chamber 142 via the upstream portion of the air supply passage 160 and opens to the valve chamber 303 defined inside the valve housing 301.
  • the valve chamber 303 has an outlet port 301b that passes through the valve housing 301 in the radial direction, and the valve chamber 303 communicates with the crank chamber 105 via the outlet port 301b and the downstream portion of the air supply passage 160. . Further, one end of an insertion hole 304 is opened in the valve chamber 303 on the opposite side to the valve hole 301a, and the insertion hole 304 extends on the axis of the valve housing 301, like the valve hole 301a. The other end of the insertion hole 304 opens to the pressure sensing chamber 305, and a pressure sensing port 301 c that penetrates the valve housing 301 in the radial direction opens to the pressure sensing chamber 305. Therefore, the pressure sensing chamber 305 communicates with the suction chamber 140 through the pressure sensing port 301 c and the pressure sensing path 166.
  • a valve body 306 is disposed in the valve housing 301. As shown in FIG. 3 in an enlarged manner, the valve body 306 has a cylindrical main body portion 306 a, and the main body portion 306 a extends from the valve chamber 303 to the pressure sensitive chamber 305 through the insertion hole 304. The main body 306a is slidably supported by the insertion hole 304.
  • the valve body 306 has a shaft portion 306 b that is integral with and coaxially connected to the main body portion 306 a, and the shaft portion 306 b is located in the pressure-sensitive chamber 305.
  • a head 306c having a larger diameter than that of the shaft portion 306b is integrally formed at the end of the shaft portion 306b opposite to the main body portion 306a.
  • An open spring 307 made of a conical coil spring is disposed between the end wall of the pressure sensing chamber 305 where the insertion hole 304 is opened and the head portion 306c, and the open spring 307 is separated from the valve hole 301a (valve open).
  • the valve body 306 is biased in the direction).
  • the solenoid unit has a cylindrical solenoid housing 310, and the solenoid housing 310 is coaxially connected to the other end of the valve housing 301 by press fitting.
  • the open end of the solenoid housing 310 is closed by an end cap 312, and a cylindrical coil (solenoid coil) 316 covered with a resin member 314 is accommodated in the solenoid housing 310.
  • a concentric cylindrical fixed core 318 is accommodated in the solenoid housing 310, and the fixed core 318 extends from the valve housing 301 toward the end cap 312 to the center of the coil 316.
  • the end cap 312 side of the fixed core 318 is surrounded by a cylindrical member 320, and the cylindrical member 320 has a closed end on the end cap 312 side.
  • a support member 322 is disposed in close contact with the closed end of the cylindrical member 320, and a cylindrical movable core 324 is accommodated between the fixed core 318 and the support member 322.
  • a movable core housing space 325 is defined.
  • the fixed core 318 has a central hole 318 a, and one end of the central hole 318 a opens into the movable core housing space 325.
  • a solenoid rod 326 is inserted into the center hole 318a, and the solenoid rod 326 protrudes from both ends of the fixed core 318.
  • a cylindrical movable core 324 is integrally fixed to a portion of the solenoid rod 326 that vertically cuts through the movable core housing space 325. The solenoid rod 326 reaches the support member 322, and the end of the solenoid rod 326 on the support member 322 side is slidably supported by the cylindrical bottomed hole of the support member 322.
  • the movable core 324, the fixed core 318, the solenoid housing 310, and the end cap 312 are made of a magnetic material and constitute a magnetic circuit.
  • the cylindrical member 320 is made of a nonmagnetic stainless steel material.
  • a compression coil spring 328 is disposed between the movable core 324 and the support member 322, and the compression coil spring 328 biases the movable core 324 in a direction away from the support member 322 (valve closing direction). However, a predetermined gap is secured between the movable core 324 and the fixed core 318.
  • the outer diameter of the movable core 324 is smaller than the inner diameter of the cylindrical member 320, and a gap is secured between the movable core 324 and the cylindrical member 320.
  • the other end of the central hole 318a opens into the pressure sensitive chamber 305, and referring to FIG. 3 again, the inner diameter of the central hole 318a is reduced at the protruding end of the fixed core 318 protruding into the pressure sensitive chamber side 305. ing.
  • the end of the solenoid rod 326 on the pressure sensitive chamber 305 side is slidably supported by the protruding end of the fixed core 318, that is, the reduced diameter portion of the central hole 318a.
  • the end of the solenoid rod 326 protruding into the pressure sensing chamber 305 is in contact with the head 306 c of the valve body 306.
  • a communication hole 330 is formed at the base of the protruding end of the fixed core 318, and the pressure sensing chamber 305 communicates with the movable core housing space 325 through the communication hole 330 and the central hole 318a. Therefore, the pressure of the suction chamber 140, that is, the suction pressure Ps acts in the valve closing direction on the back side of the valve body 306, that is, the pressure sensing chamber 305 side, via the solenoid rod 326.
  • a control device 400 provided outside the compressor 100 is connected to the coil 316 (see FIG. 2), and when the control current I is supplied from the control device 400 to the coil 316, the solenoid unit generates an electromagnetic force F. (I) is generated.
  • the electromagnetic force F (I) of the solenoid unit attracts the movable core 324 toward the fixed core 318 and acts on the valve body 306 in the valve closing direction via the solenoid rod 326.
  • FIG. 4 shows the region IV in FIG. 3 in an enlarged manner, and the end surface of the main body 306a can close the valve hole 301a by contacting the wall surface of the valve chamber 303 in which the valve hole 301a is opened. . That is, the wall surface of the valve chamber 303 in which the valve hole 301a is opened functions as a flat valve seat 338.
  • the cross-sectional area Sr of the main body 306a is larger than the opening area Sd of the valve hole 301a (Sr> Sd), and a shallow dish-shaped recess 340 is opened in the center on the end surface of the main body 306a.
  • the recess 340 is formed by a curved surface portion 342 that is continuous with the opening edge of the recess 340 and a flat portion 344 that is continuous with the inside of the curved surface portion 342.
  • the flat portion 344 forms the bottom of the recess 340 and is parallel to the valve seat 338.
  • the opening area Sc of the recess 340 in the end surface of the main body 306a is substantially equal to or slightly smaller than the transverse area Sr of the main body 306a. For this reason, a flat annular seal region 346 surrounding the recess 340 is defined on the end surface of the main body 306a.
  • the seal region 346 includes an edge of the cylindrical outer peripheral surface.
  • the opening area Sc of the recess 340 is larger than the opening area (transverse area) Sd of the valve hole 301a.
  • the diameter of the inner peripheral edge of the seal region 346 is larger than the diameter of the opening edge of the valve hole 301a, and the seal region 346 contacts the valve seat 338 radially outward from the opening edge of the valve hole 301a by a predetermined distance. Touch.
  • the end surface of the main body portion 306a of the valve body 306 faces the valve hole 301a, and the end surface of the main body portion 306a faces the pressure of the discharge chamber 142 in the valve opening direction, that is, the discharge pressure Pd. Act.
  • valve body 306 The other end of the valve body 306, that is, the head 306c is located in the pressure sensing chamber 305, and the pressure of the suction chamber 140, that is, the suction pressure Ps acts in the valve closing direction on the other end of the valve body 306. . Therefore, the valve body 306 also functions as a pressure-sensitive member that operates in response to the pressure difference between the discharge pressure Pd and the suction pressure Ps.
  • the valve body 306 slides to transmit the pressure of the pressure sensing chamber 305, that is, the pressure of the suction chamber 140 and the electromagnetic force F (I) of the solenoid unit to the one end having the seal region 346.
  • the pressure receiving area (Sv1) of the valve body 306 through which the discharge pressure Pd acts in the valve opening direction through the valve hole 301a is larger than the inner peripheral edge of the seal region 346.
  • the area inside the direction, that is, the opening area Sc of the recess 340 is equal.
  • the pressure receiving area of the valve body 306 on which the suction pressure Ps acts is equal to the transverse area Sr of the main body 306 a supported by the insertion hole 304.
  • the main body portion 306a is formed so that the pressure receiving area Sv1 and the cross sectional area Sr are substantially equal, whereby the valve body 306 has a pressure in the valve chamber 303 in the opening / closing direction, that is, a pressure in the crank chamber 105. (Crank pressure Pc) substantially does not act.
  • the distance between the outer edge of the seal region 346 and the inner edge of the seal region 346 is set in a range of 0.05 mm or more and 0.3 mm or less, and the seal region 346 has a valve body 306 that closes the valve hole 301a. When in contact with the valve seat 338, the valve seat 338 comes into contact with the valve seat 338 in a state close to line contact.
  • the force acting on the valve body 306 includes the discharge pressure Pd, the suction pressure Ps, the electromagnetic force F (I) of the coil 316, the biasing force f1 of the release spring 307, and the biasing force f2 of the compression coil spring 328. It is. Among these, the discharge pressure Pd and the biasing force f1 of the release spring 307 are in the valve opening direction, and the other suction pressure Ps, the electromagnetic force F (I) of the solenoid unit and the biasing force f2 of the compression coil spring 328 are in the valve opening direction. Acts in the opposite valve closing direction.
  • the pressure difference (Pd ⁇ Ps differential pressure) between the discharge pressure Pd and the suction pressure Ps can be adjusted by the electromagnetic force F (I) of the solenoid unit, that is, the control current I supplied to the coil 316. It shows that there is.
  • the electromagnetic force F (I) acts on the valve body 306 in the valve closing direction, and by increasing the control current I, as shown in FIG. 5, the Pd-Ps differential pressure can be increased.
  • the control device 400 sets a target differential pressure ⁇ P or a control current I corresponding to the target differential pressure ⁇ P based on various external information provided from external information detection means (not shown) of the vehicle air conditioning system, A control current I is supplied to the displacement control valve 300 so that the Pd-Ps differential pressure approaches the target differential pressure ⁇ P. Corresponding to the control current I, the valve opening degree of the capacity control valve 300 is adjusted, whereby the discharge capacity of the compressor 100 is feedback-controlled.
  • the biasing force f1 of the release spring 307 is set larger than the biasing force f2 of the compression coil spring 328 (f1> f2), when the control current I is zero, the biasing force f1 of the release spring 307 causes the valve to The hole 301a is opened. Thereby, the refrigerant is supplied from the discharge chamber 142 to the crank chamber 105, the inclination angle of the swash plate 107 is minimized, and the discharge capacity is minimized.
  • the region where the main body 306a of the valve body 306 contacts the valve seat 338 is the seal region 346 due to the formation of the recess 340.
  • the recess 340 is formed such that the distance between the valve body 306 and the valve seat 338 increases from the seal region 346 toward the inside in the radial direction, thereby clearly defining the pressure receiving area Sv1. Since the seal width or area of the seal region 346 is set to be very small, the area where the discharge pressure Pd acts on the main body 306a when the seal region 346 is separated from the valve seat 338 is the seal region 346. It is almost the same as the pressure receiving area Sv1 in contact with the valve seat 338, and can be regarded as substantially equal to the pressure receiving area Sv1.
  • the operating characteristics of the valve body 306 when the valve body 306 is in contact with the valve seat 338 and the operating characteristics of the valve body 306 when the valve body 306 is separated from the valve seat 338 are as follows: Exactly follow the above characteristic formulas (1) to (3). Furthermore, since the seal region 346 is on the edge of the cylindrical outer peripheral surface of the main body portion 306a and is set to be minute, the valve body 306 is not easily affected by dynamic pressure in the valve opening direction. Further, the area for receiving the discharge pressure Pd (pressure receiving area Sv1) is substantially defined by the edge of the cylindrical outer peripheral surface, that is, the dimension of the main body 306a of the valve body 306, and the area for receiving the suction pressure Ps is the axis of the valve body 306.
  • the capacity control valve 300 Since it is defined by the dimensions of the portion 306b, it is easy to adjust these areas equally. As a result, according to the capacity control valve 300, if the control current I determined based on the characteristic equation (3) is supplied to the coil 316, the Pd-Ps differential pressure approaches the target differential pressure ⁇ P with certainty, and the discharge The accuracy of capacity control is improved. In particular, in a region where the difference between the discharge pressure Pd and the suction pressure Ps is large, the capacity control valve 300 contributes to improving the accuracy of the discharge capacity control.
  • FIG. 6 shows an enlarged part of the capacity control valve according to the second embodiment.
  • the capacity control valve according to the second embodiment has the same configuration as the capacity control valve 300 except for the shape of the valve body 350.
  • the valve body 350 includes a sliding portion 306d in which a portion corresponding to the main body portion 306a of the valve body 306 in the capacity control valve 300 is slidably supported by the insertion hole 304, and a cylinder having a larger diameter than the sliding portion 306d. And a large-diameter end (one end) 306e having a shape.
  • the diameter of the sliding portion 306d is the same as the diameter of the main body portion 306a, and the end surface of the large-diameter end portion 306e can contact the valve seat 338.
  • a recess 360 is formed on the end surface of the large-diameter end 306e, and the recess 360 is also constituted by a curved surface portion 362 and a flat portion 364. Accordingly, an annular seal region 366 is also formed on the end surface of the large-diameter end portion 306e, and the seal region 366 includes the edge of the cylindrical outer peripheral surface of the large-diameter end portion 306e.
  • the opening area of the recess 360 is larger than the opening area of the valve hole 301a, and the inner peripheral edge of the seal region 366 is spaced radially outward from the opening edge of the valve hole 301a by a predetermined distance.
  • the opening area of the recess 360 is set larger than the cross-sectional area Sr of the sliding portion 306d.
  • the end surface of the large diameter end portion 306e of the valve body 350 faces the valve hole 301a, and the discharge pressure Pd acts on the end surface of the large diameter end portion 306e in the valve opening direction.
  • the suction pressure Ps acts on the opposite side of the valve body 350 from the large diameter end 306e. Therefore, the valve body 350 also functions as a pressure-sensitive member that operates in response to the Pd ⁇ Ps differential pressure.
  • the pressure receiving area (Sv2) of the valve body 350 where the discharge pressure Pd acts in the valve opening direction is the area inside the inner peripheral edge of the seal region 366, that is, the depression 360 Equal to the opening area. Further, the pressure receiving area of the valve body 350 on which the suction pressure Ps acts in the valve closing direction is equal to the transverse area Sr of the sliding portion 306 d supported by the insertion hole 304.
  • the opening area of the recess 360 that is, the pressure receiving area Sv2
  • the cross sectional area Sr of the sliding portion 306d Sv2> Sr
  • the crank pressure Pc acts in the valve closing direction on the area of the large-diameter end 306e corresponding to Sv2-Sr. Accordingly, the force acting on the valve body 350 is expressed by the following characteristic equations (4) to (7).
  • the characteristic equation (5) is obtained.
  • the characteristic equation (7) indicates that the pressure difference between the discharge pressure Pd and the suction pressure Ps (Pd ⁇ Ps differential pressure) is the electromagnetic force F (I) of the solenoid unit, that is, even in the capacity control valve of the second embodiment. This shows that adjustment is possible with the control current I supplied to the coil 316.
  • the difference from the capacity control valve 300 is that the crank pressure Pc acts on the valve body 350 in the valve closing direction.
  • the valve body 350 when the valve body 350 is separated from the valve seat 338 when the valve is opened and the refrigerant flows into the crank chamber 105 and the crank pressure Pc rapidly increases, the force acting on the valve body 350 in the valve closing direction increases. For this reason, excessive separation of the valve body 350 from the valve seat 338 is suppressed. Further, the rising speed of the crank pressure Pc can be adjusted by adjusting the difference between the pressure receiving area Sv2 and the cross sectional area Sr of the sliding portion 306d. As a result, in the variable capacity compressor 100 to which the capacity control valve of the second embodiment is applied, the discharge capacity control becomes stable.
  • the snap ring may be attached to the shaft portion 306b as a spring seat without providing the head portion 306c in the valve body 350 in consideration of its assembly. .
  • the present invention is not limited to the first and second embodiments described above, and various modifications are possible.
  • the first embodiment and the second embodiment by forming the recesses 340 and 360 in the end surfaces of the valve bodies 306 and 350, the end edges of the cylindrical outer peripheral surface are formed at one end portions of the valve bodies 306 and 350.
  • the seal regions 346 and 366 that are included and can contact the valve seat 338 in a state close to line contact are formed, but the shapes of the valve body and the valve seat are not particularly limited.
  • FIG. 7 shows an enlarged part of the capacity control valve according to the third embodiment, and this capacity control valve has a valve body 370 instead of the valve body 350.
  • the valve body 370 is not formed with a recess in the large-diameter end portion 306e, and accordingly, the valve seat 372 is not a flat seat but a female taper shape. That is, the valve seat 372 is configured by a female tapered surface that is continuous with the opening end of the valve hole 301 a, and the opening area of the valve seat 372 gradually increases as the valve chamber 303 is approached. For this reason, when the valve is closed, the outer peripheral edge of the end surface of the large-diameter end portion 306e comes into contact with the valve seat 372 as a seal region 376 in a state close to line contact.
  • the valve bodies 306 and 350 have seal regions 346 and 366 having a minute area.
  • the seal regions 346 and 366 are set to be smaller and are closer to line contact.
  • the difference (seal width) between the radius of the outer peripheral edge of the seal regions 346 and 366 and the radius of the inner peripheral edge of the seal regions 346 and 366 is preferably in the range of 0.05 mm or more and 0.2 mm or less. .
  • the recesses 340, 360 of the valve bodies 306, 350 have curved surface portions 342, 362, and the valve bodies 306, 350 and the valve seat 338 or the valve hole as they approach the radial center.
  • the dent may have a right-angled corner instead of the curved surface.
  • the dent preferably has a curved surface as in the first and second embodiments.
  • valve bodies 306 and 350 and the solenoid rod 326 are separate bodies, but may be integrated.
  • the compression coil spring 328 may be omitted.
  • the valve bodies 306 and 350 are always urged in the valve opening direction only by the opening spring 307, but the valve bodies 306, 350 are combined by combining two or more springs. 350 may be constantly urged in the valve opening direction.
  • a diaphragm may be used in order to apply the discharge pressure Pd, the suction pressure Ps or the electromagnetic force F (I) to the valve bodies 306, 350.
  • the head portion 306c of the valve body 306 is brought into contact with the outer surface of the bellows closed end.
  • a portion on the tip side of the solenoid rod 326 is inserted inside the bellows through the opening end of the bellows, and the tip of the solenoid rod 326 is brought into contact with the inner surface of the closed end of the bellows.
  • the solenoid rod 326 enables the valve body 306 to be biased by the electromagnetic force F (I).
  • the pressure inside the bellows is made equal to the suction pressure Ps, and the suction pressure Ps is applied to the valve body 306 via the bellows.
  • the movable core 324 is not in contact with the cylindrical member 320, but by sliding the outer peripheral surface of the movable core 324 on the inner peripheral surface of the cylindrical member 320, the cylindrical member The movable core 324 may be supported by 320.
  • the control device 400 sets the control current I corresponding to the target differential pressure ⁇ P, and the control current I is supplied to the capacity control valve 300 so that the Pd ⁇ Ps differential pressure approaches the target differential pressure ⁇ P.
  • the control method executed by the control device 400 is not limited to this.
  • the characteristic equation (3) is modified, the following characteristic equation (8) is obtained.
  • the target suction pressure Ps is set as the target value of the suction pressure Ps. If Pss is determined in advance and information on the changing discharge pressure Pd is known, the electromagnetic force F (I) to be generated, that is, the control current I can be calculated.
  • the valve bodies 306 and 350 operate so that the suction pressure Ps approaches the target suction pressure Pss, and the crank pressure Pc is adjusted. That is, the discharge capacity is controlled so that the suction pressure Ps approaches the target suction pressure Pss.
  • the discharge capacity control method of adjusting the control current I so that the Pd ⁇ Ps differential pressure approaches the target differential pressure ⁇ P is a control method of the discharge capacity can be adopted such that the control current I is adjusted based on the discharge pressure Pd and the target suction pressure Pss so that the suction pressure Ps approaches the target suction pressure Pss. In the latter case, it is necessary to provide detection means for detecting the discharge pressure Pd in the vehicle air conditioning system.
  • the compressor 100 is a reciprocating swash plate variable displacement compressor, but may be a reciprocating oscillating plate variable displacement compressor.
  • the oscillating plate type variable capacity compressor has an element for oscillating the oscillating plate, and the swash plate 107 and these elements are collectively referred to as a swash plate element.
  • the compressor 100 may be driven by an electric motor.
  • the stroke length defined by the minimum inclination angle of the swash plate element can be set very small, and the variable range of the discharge capacity is wide.
  • the discharge capacity is controlled with high accuracy over the entire variable range.
  • the fixed orifice 103c is arranged as a throttle element in the extraction passage 162 in order to regulate the flow rate of the extraction passage 162 and increase the crank pressure Pc.
  • a throttle with variable flow rate may be used, and a valve may be arranged to adjust the valve opening.
  • the refrigerant is not limited to R134a or carbon dioxide, and other new refrigerants may be used. That is, the capacity control valve 300 of the first embodiment and the capacity control valve of the second embodiment can be applied to a conventional air conditioning system. Finally, the capacity control valve of the variable capacity compressor according to the present invention is applicable to air conditioning systems in general, such as indoor air conditioning systems other than vehicle air conditioning systems.

Landscapes

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

Abstract

La présente invention concerne une soupape de commande de cylindrée montée dans un parcours d'alimentation en air pour interconnecter une région de pression de décharge et une chambre de manivelle d'un compresseur à cylindrée variable de type alternatif. La soupape de commande de cylindrée est munie d'un élément de soupape (306) et l'extrémité de l'élément de soupape (306) qui est montée dans une chambre de soupape (303) comprend une région d'étanchéité (346). La région d'étanchéité (346) comprend une surface périphérique extérieure tubulaire circulaire et un bord de la surface périphérique extérieure et peut entrer en contact avec un siège de soupape (338) selon un contact sensiblement linéaire. Une section coulissante de l'élément de soupape (306) est supportée de manière coulissante dans un trou d'insertion (304) et transmet la pression dans une chambre de détection de pression et une force électromagnétique à une extrémité de l'élément de soupape (306).
PCT/JP2009/055020 2008-03-17 2009-03-16 Soupape de commande de cylindrée pour compresseur à cylindrée variable et compresseur à cylindrée variable de type alternatif Ceased WO2009116485A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-067643 2008-03-17
JP2008067643A JP2009221965A (ja) 2008-03-17 2008-03-17 可変容量圧縮機の容量制御弁及び往復動型可変容量圧縮機

Publications (1)

Publication Number Publication Date
WO2009116485A1 true WO2009116485A1 (fr) 2009-09-24

Family

ID=41090888

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/055020 Ceased WO2009116485A1 (fr) 2008-03-17 2009-03-16 Soupape de commande de cylindrée pour compresseur à cylindrée variable et compresseur à cylindrée variable de type alternatif

Country Status (2)

Country Link
JP (1) JP2009221965A (fr)
WO (1) WO2009116485A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6281048B2 (ja) * 2014-04-22 2018-02-21 株式会社テージーケー 可変容量圧縮機用制御弁
CN116137884A (zh) 2020-08-03 2023-05-19 伊格尔工业股份有限公司 阀
JP7673071B2 (ja) 2020-08-04 2025-05-08 イーグル工業株式会社 弁
EP4194774A4 (fr) 2020-08-04 2024-08-28 Eagle Industry Co., Ltd. Soupape de détente
JP7600243B2 (ja) 2020-08-04 2024-12-16 イーグル工業株式会社 弁
JP7625357B2 (ja) 2020-08-24 2025-02-03 イーグル工業株式会社 弁
EP4219994A4 (fr) 2020-09-28 2024-10-02 Eagle Industry Co., Ltd. Vanne
US12359729B2 (en) 2020-10-01 2025-07-15 Eagle Industry Co., Ltd. Valve
WO2022071092A1 (fr) 2020-10-01 2022-04-07 イーグル工業株式会社 Soupape de commande de fluide
EP4265949B1 (fr) 2020-12-17 2025-11-19 Eagle Industry Co., Ltd. Soupape
CN117098943A (zh) 2021-03-29 2023-11-21 伊格尔工业股份有限公司 阀
CN117355694A (zh) 2021-05-31 2024-01-05 伊格尔工业股份有限公司 流体控制阀
EP4397891A4 (fr) 2021-09-02 2025-08-13 Eagle Ind Co Ltd Soupape de commande de fluide

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003254246A (ja) * 2002-02-27 2003-09-10 Eagle Ind Co Ltd 容量制御弁
JP2006342718A (ja) * 2005-06-08 2006-12-21 Toyota Industries Corp 容量可変型圧縮機の容量制御弁
JP2007051568A (ja) * 2005-08-17 2007-03-01 Tgk Co Ltd 可変容量圧縮機用制御弁
JP2007315189A (ja) * 2006-05-23 2007-12-06 Sanden Corp 可変容量圧縮機の容量制御弁
WO2008010404A1 (fr) * 2006-07-19 2008-01-24 Sanden Corporation valve de commande de capacité de compresseur à capacité variable

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003254246A (ja) * 2002-02-27 2003-09-10 Eagle Ind Co Ltd 容量制御弁
JP2006342718A (ja) * 2005-06-08 2006-12-21 Toyota Industries Corp 容量可変型圧縮機の容量制御弁
JP2007051568A (ja) * 2005-08-17 2007-03-01 Tgk Co Ltd 可変容量圧縮機用制御弁
JP2007315189A (ja) * 2006-05-23 2007-12-06 Sanden Corp 可変容量圧縮機の容量制御弁
WO2008010404A1 (fr) * 2006-07-19 2008-01-24 Sanden Corporation valve de commande de capacité de compresseur à capacité variable

Also Published As

Publication number Publication date
JP2009221965A (ja) 2009-10-01

Similar Documents

Publication Publication Date Title
WO2009116485A1 (fr) Soupape de commande de cylindrée pour compresseur à cylindrée variable et compresseur à cylindrée variable de type alternatif
JP5235569B2 (ja) 容量制御弁、可変容量圧縮機及び可変容量圧縮機の容量制御システム
EP2182213B1 (fr) Compresseur de type à déplacement variable doté d'un mécanisme de contrôle du déplacement
US9518568B2 (en) Swash plate type variable displacement compressor
EP0953766A2 (fr) Soupape de contrÔle
JP2009057855A (ja) 可変容量圧縮機
CN100402847C (zh) 变容式压缩机的控制阀
US6783332B2 (en) Control valve of variable displacement compressor with pressure sensing member
WO2009145163A1 (fr) Système de contrôle de déplacement pour compresseur à déplacement variable
JP5118430B2 (ja) 容量制御弁及びこれを用いた可変容量圧縮機
US20170211561A1 (en) Variable displacement swash plate type compressor
JP5064918B2 (ja) 可変容量圧縮機の容量制御システム
JP5430401B2 (ja) 可変容量圧縮機
US10815980B2 (en) Variable displacement swash plate type compressor
JP5180695B2 (ja) 可変容量圧縮機の容量制御システム
JP5053740B2 (ja) 可変容量圧縮機の容量制御弁
JP5260906B2 (ja) 可変容量圧縮機の容量制御弁
US20160252084A1 (en) Variable displacement swash plate type compressor
US11015587B2 (en) Piston compressor
JP5091757B2 (ja) 可変容量圧縮機の容量制御システム
JP5202170B2 (ja) ベローズ組立体、可変容量圧縮機の容量制御弁、及び、可変容量圧縮機
WO2019058827A1 (fr) Compresseur
JP2003343433A (ja) 可変容量型圧縮機の制御弁
JP2008281323A (ja) 冷凍サイクルおよび可変容量圧縮機
JP2016169698A (ja) 可変容量型斜板式圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09722053

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 09722053

Country of ref document: EP

Kind code of ref document: A1