US20060039798A1 - Control valve for variable displacement compressor - Google Patents

Control valve for variable displacement compressor Download PDF

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Publication number
US20060039798A1
US20060039798A1 US11/205,064 US20506405A US2006039798A1 US 20060039798 A1 US20060039798 A1 US 20060039798A1 US 20506405 A US20506405 A US 20506405A US 2006039798 A1 US2006039798 A1 US 2006039798A1
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United States
Prior art keywords
pressure
discharge
valve
crank
receiving
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Abandoned
Application number
US11/205,064
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English (en)
Inventor
Ryosuke Yoshihiro
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TGK Co Ltd
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TGK Co Ltd
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
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Assigned to TGK CO., LTD. reassignment TGK CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YOSHIHIRO, RYOSUKE
Publication of US20060039798A1 publication Critical patent/US20060039798A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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 control valve for a variable displacement compressor, and more particularly to a control valve for a variable displacement compressor, for controlling a discharge capacity of refrigerant discharged from a variable displacement compressor for an automotive air conditioner.
  • a compressor used in a refrigeration cycle of an automotive air conditioner is driven by an engine whose rotational speed varies depending on a traveling condition of the vehicle, and hence incapable of performing rotational speed control.
  • a variable displacement compressor capable of changing the discharge capacity of refrigerant is generally employed so as to obtain an adequate refrigerating capacity without being constrained by the rotational speed of the engine.
  • a swash plate is disposed within a crankcase formed gastight, such that the inclination angle thereof can be changed, and driven by the rotational motion of a rotational shaft, for performing wobbling motion, and pistons caused to perform reciprocating motion in a direction parallel to the rotational shaft by the wobbling motion of the swash plate draw refrigerant from a suction chamber into associated cylinders, compress the refrigerant, and then discharge the compressed refrigerant into a discharge chamber.
  • the inclination angle of the swash plate can be varied by changing the pressure in the crankcase, whereby the stroke of the pistons is changed for changing the discharge capacity of the refrigerant.
  • the control valve for a variable displacement compressor provides control to change the pressure in the crankcase.
  • control valve for variably controlling the discharge capacity of the compressor decompresses part of refrigerant discharged at discharge pressure Pd from the discharge chamber to introduce the decompressed refrigerant into the crankcase, and controls pressure Pc in the crankcase (crank pressure) through control of the amount of the refrigerant thus introduced.
  • the control of the amount of the introduced refrigerant is realized by supplying external electric current to a solenoid provided in the control valve for control of actuation of a valve element in the control valve, specifically, by a method based on suction pressure Ps in the suction chamber, for example.
  • control valve senses the suction pressure Ps, and controls the flow rate of refrigerant introduced at discharge pressure Pd from the discharge chamber into the crankcase such that the suction pressure Ps is maintained at a predetermined level.
  • the value of suction pressure Ps at which the variable displacement operation is to be started can be freely set according to the amount of electric current supplied to the solenoid.
  • the Pd ⁇ Ps differential pressure control performs the control based on the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps (hereinafter this control is referred to as “the Pd ⁇ Ps differential pressure control”).
  • the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps is sensed and the flow rate of refrigerant introduced at the discharge pressure Pd from the discharge chamber into the crankcase is controlled such that the differential pressure (Pd ⁇ Ps) is maintained at a predetermined level.
  • the control valve for the control method is configured such that an effective pressure-receiving area of an intermediate, which comprises e.g.
  • a valve element and a piston rod, for receiving the discharge pressure Pd, and an effective pressure-receiving area of the intermediate for receiving the suction pressure Ps, are made equal to each other such that the crank pressure Pc applied to the intermediate is cancelled.
  • a valve section of the control valve performs an opening/closing operation by the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps, irrespective of the crank pressure Pc (see e.g. Japanese Unexamined Patent Publication (Kokai) No. 2003-328936 (Paragraph numbers [0040] to [0045], FIG. 3 )).
  • the discharge pressure Pd and the suction pressure Ps are directly received by the valve element for sensing the differential pressure therebetween, and hence it is possible to dispense with the above-mentioned flexible member.
  • the discharge pressure Pd is directly sensed, it is possible to reflect a change in pressure of the variable displacement compressor as it is, and hence realize displacement control with excellent response.
  • the Pd ⁇ Ps differential pressure control should be performed according to the value of electric current supplied to the solenoid, irrespective of the crank pressure Pc, such that the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps is maintained at a predetermined level.
  • the crank pressure Pc is increased by increasing the differential pressure (Pd ⁇ Ps), and conversely the differential pressure (Pd ⁇ Ps) as well is varied to some extent in a manner affected by a variation in the crank pressure Pc, etc. More specifically, as the crank pressure Pc increases, the differential pressure (Pd ⁇ Ps) increases with a slight slope, for example.
  • the phenomenon may not be ideal when considering only the characteristics of the control valve, this is not always true when considering matching between the Pd ⁇ Ps differential pressure control and control of the variable displacement compressor. More specifically, when the differential pressure (Pd ⁇ Ps) instantaneously rises to a fixed value in response to a change in the value of electric current supplied to the solenoid, the valve section is instantaneously opened, which enhances the response of the swash plate of the variable displacement compressor, but nevertheless hunting or overshooting is sometimes caused in the displacement control. This makes it difficult to perform the displacement control with stability. On the other hand, when the differential pressure (Pd ⁇ Ps) is slow in rising, the response of the swash plate is degraded.
  • the value of the differential pressure (Pd ⁇ Ps) to be controlled varies with the value of the crank pressure Pc. This sometimes leads to hysteresis of the displacement control, and hence is not preferable for control of the variable displacement compressor. Therefore, it is considered preferable to cause the differential pressure (Pd ⁇ Ps) to rise with a proper response (slope) according the value of electric current. For example, when the swash plate of the variable displacement compressor is difficult to move, it is required to increase the response to improve motion of the swash plate, whereas when the swash plate is excessively easy-to move, it is required to lower the response to stabilize motion of the swash plate.
  • the degree (slope) of influence of the crank pressure Pc on a change in the differential pressure (Pd ⁇ Ps) has conventionally been adjusted e.g. by changing the characteristic of a spring for urging the valve element in the moving direction thereof or changing the attractive force characteristic of the solenoid according to characteristics required of the control valve.
  • the characteristic of the spring or the attractive force characteristic of the solenoid is changed as described above, the differential pressure characteristics, i.e. the relationship between the value of electric current supplied to the solenoid and the differential pressure (Pd ⁇ Ps) can also be changed, which makes it difficult to perform a total tuning operation.
  • the present invention has been made in view of these problems, and an object thereof is to provide a control valve for a variable displacement compressor, based on a Pd ⁇ Ps differential pressure control method, which is capable of setting characteristics concerning the degree of influence of crank pressure on a change in the differential pressure between discharge pressure and suction pressure, to desired characteristics with ease.
  • the present invention provides a control valve for a variable displacement compressor, the control valve being mounted in the variable displacement compressor, for controlling pressure in a crankcase of the compressor to thereby vary a discharge capacity of refrigerant, comprising a body that has a discharge pressure port for introducing discharge pressure of the compressor, a crank pressure port for delivering crank pressure generated in the control valve to the crankcase, and a suction pressure port for introducing suction pressure, the discharge pressure port, the crank pressure port, and the suction pressure port being sequentially arranged from one end of the body, a valve element that is moved to and away from a valve seat provided between the discharge pressure port and the crank pressure port, for reducing the discharge pressure introduced from the discharge pressure port by a restriction passage formed between the valve element and the valve seat to generate the crank pressure, a shaft that supports the valve element in a valve-opening or valve-closing direction and is capable of operating in unison with the valve element, and a solenoid that is connected to an end of the body, opposite to the discharge
  • a plunger capable of being made integral with the valve element via the shaft the plunger need not necessarily be directly connected to the shaft, but it may be connected to the shaft via an interposed object formed separately from the shaft.
  • FIG. 1 is a cross-sectional view showing the arrangement of a control valve for a variable displacement compressor, according to an embodiment of the present invention.
  • FIG. 2 is a fragmentary expanded cross-sectional view of an upper portion of the FIG. 1 control valve.
  • FIG. 3A to 3 C are diagrams useful in explaining differential pressure ⁇ crank pressure characteristics of the control valve for a variable displacement compressor.
  • FIG. 1 is a cross-sectional view showing the arrangement of a control valve for a variable displacement compressor, according to the present embodiment
  • FIG. 2 is a fragmentary expanded cross-sectional view of an upper part of the FIG. 1 control valve.
  • the control valve introduces part of refrigerant discharged from a variable displacement compressor, not shown, and allows the introduced refrigerant to flow into a crankcase while controlling the flow rate thereof.
  • the control valve is formed by integrally assembling a valve-forming section 1 containing a valve section for adjusting the flow rate of refrigerant, and a solenoid 2 for controlling the valve lift of the valve section.
  • the valve-forming section 1 has a stepped hollow cylindrical upper body 3 having an open upper end defining therein a discharge pressure port 4 which communicates with a discharge chamber of the compressor, for receiving discharge pressure Pd, and a strainer 5 capped on the upper body 3 in a manner covering the open upper end of the upper body 3 .
  • the discharge pressure port 4 communicates with a crank pressure port 6 opening in a side of a central portion of the upper body 3 .
  • the crank pressure port 6 communicates with the crankcase of the compressor, for delivering controlled pressure (crank pressure) Pc to the crankcase.
  • a suction pressure port 7 opens in a side of a lower portion of the upper body 3 , for communication with a suction chamber of the compressor for introducing suction pressure Ps, and a refrigerant passage connected to the suction pressure port 7 changes its direction downward inside the upper body 3 to open in a lower end face of the upper body 3 .
  • crankcase-communicating chamber 8 Formed between the discharge pressure port 4 and the crank pressure port 6 in the upper portion of the upper body 3 is a crankcase-communicating chamber 8 that is filled with the crank pressure Pc.
  • a guide hole 9 In the center of the lower portion of the upper body 3 is formed a guide hole 9 which axially extends therethrough for having a shaft, referred to hereinafter, inserted therein to guide the same.
  • the guide hole 9 communicates with the crankcase-communicating chamber 8 via an opening at an upper end thereof.
  • a valve seat-forming member 10 having a stepped hollow cylindrical shape is disposed in a manner inserted into the crankcase-communicating chamber 8 .
  • the valve seat-forming member 10 has the outer periphery of an upper end thereof press-fitted in the open upper end of the upper body 3 , and a lower portion of the valve seat-forming member 10 extends downward through the crankcase-communicating chamber 8 with a diameter reduced by a step.
  • This reduced diameter portion has a root portion formed with communication holes 11 for communication between the inside and the outside of the valve seat-forming member 10 .
  • the valve seat-forming member 10 has an intermediate portion of an inner part thereof formed with a valve hole 12 such that a space on the discharge chamber side and a space on the crankcase side communicate with each other, and the rim of an opening of the valve hole 12 on the crankcase side forms a valve seat 13 .
  • a valve element 14 is disposed in a lower opening of the valve seat-forming member 10 in a manner movable axially back and forth.
  • the valve element 14 comprises a holder 15 that is slidable along an inner wall of the valve seat-forming member 10 , and a ball 16 that is press-fitted in a central portion of the upper end of the holder 15 .
  • the holder 15 has the outer periphery of an upper portion thereof reduced in diameter, and a spring 17 is fitted on the reduced-diameter portion. The spring 17 is interposed between the valve seat-forming member 10 and the holder 15 , for urging the ball 16 in a direction away from the valve seat 13 .
  • the holder 15 has a side formed with communication holes 15 a for communication between the inside and the outside of the holder 15 .
  • the ball 16 operates in unison with the holder 15 such that it can be seated on the valve seat 13 .
  • the discharge pressure Pd introduced from the discharge pressure port 4 is decompressed by passing through a restriction flow passage between the ball 16 and the valve seat 13 , whereby the crank pressure Pc is generated.
  • a shaft 18 is inserted into the guide hole 9 of the upper body 3 in a manner movable axially back and forth.
  • the shaft 18 has one end extending though the holder 15 to abut the ball 16 , and the other end extending downward from the upper body 3 .
  • the valve element 14 acts based on the principle of a balancing toy. As a result, a lateral motion of the valve element 14 is suppressed, and hence the valve element 14 is capable of axially moving back and forth in a stable state in which lateral load is reduced. Further, since the lateral load on the valve element 14 generated upon axial movement of the valve element 14 is reduced, hysteresis is decreased in the opening and closing characteristics of the control valve and the lateral displacement of the valve element 14 is suppressed. As a result, complete closing of the valve element 14 can be expected.
  • the upper body 3 has an upper open end of a lower body 19 joined to a bottom portion thereof by caulking, and a core 20 of the solenoid 2 is screwed onto a lower end of the upper body 3 .
  • the core 20 has a central hole 21 axially formed therethrough, and an upper portion of the core 20 is formed with communication holes 22 extending from the outer periphery to communicate with the central hole 21 , and communication holes 23 that open in an upper end of the core 20 , with one ends of the communication holes 23 communicating with a refrigerant passage connected to the suction pressure port 7 and the other ends of the same communicating with the communication hole 22 . With this configuration, the suction pressure Ps is received by an end of the shaft 18 .
  • a sleeve 24 is disposed inside the lower body 19 .
  • a stopper 25 in the form of a lid is fitted in a lower opening of the sleeve 24 , as viewed in FIG. 1 , and an annular bearing member 26 is press-fitted in the inner periphery of the stopper 25 .
  • the core 20 screwed onto the upper body 3 and a plunger 27 are arranged in the sleeve 24 .
  • the plunger 27 is rigidly fixed to a shaft 28 that has one end extending through the core 20 into an opening in the lower end of the upper body 3 to be supported thereat, and the other end supported by the bearing member 26 . Movement of the plunger 27 toward the shaft 18 is restricted by a stop ring 29 fitted on the shaft 28 .
  • a spring 30 is interposed between the core 20 and the plunger 27 , and a spring 31 between the plunger 27 and the bearing member 26 .
  • a yoke 32 Arranged along the outer periphery of the sleeve 24 are a yoke 32 , a solenoid coil 33 , and a casing 34 surrounding the yoke 32 and the solenoid coil 33 , which constitute the solenoid 2 together with the core 20 and the plunger 27 .
  • a handle 36 having a harness 35 inserted therethrough is fitted in the bottom of the casing 34 to close the lower end of the solenoid 2 .
  • control valve for a variable displacement compressor will be described in association with the operation of the variable displacement compressor.
  • the discharge pressure Pd of refrigerant introduced from the discharge chamber acts on the ball 16 from above, as viewed in FIG. 1 .
  • the suction pressure Ps introduced from the suction chamber into the central opening 21 via the suction pressure port 7 and the communication holes 23 and 22 acts on the shaft 18 in abutment with the ball 16 , from below, as viewed in FIG. 1 , via a clearance between the upper body 3 and the shaft 28 .
  • the effective pressure-receiving area of the ball 16 for receiving the discharge pressure Pd and the effective pressure-receiving area of the shaft 18 for receiving the suction pressure Ps become equal to each other. Therefore, the crank pressure Pc applied to an intermediate formed by making the valve element 14 and the shaft 18 integral with each other is cancelled, and the ball 16 for control of the flow rate of refrigerant flowing from the discharge chamber into the crankcase forms a differential pressure valve that operates by sensing the differential pressure between the discharge pressure Pd and the suction pressure Ps. In the present embodiment, however, the difference between the above-mentioned effective pressure-receiving areas is adjusted e.g.
  • the plunger 27 is attracted by the core 20 according to the magnitude of the control current, which generates a force for moving the plunger 27 upward, as viewed in FIG. 1 , by a predetermined amount.
  • This force serves as a set value of the control valve that operates as the differential pressure valve. Therefore, the control valve senses the differential pressure between the discharge pressure Pd and the suction pressure Ps, and controls the flow rate of refrigerant flowing from the discharge chamber into the crankcase such that the differential pressure is held at a value corresponding to the set value set by the solenoid 2 .
  • control valve is configured such that desired differential pressure ⁇ crank pressure characteristics can be obtained by adjusting the difference between the effective pressure-receiving area A on the discharge pressure side of the intermediate formed by making the valve element 14 and the shaft 18 integral with each other, and the effective pressure-receiving area B on the suction pressure side of the intermediate, as shown in FIG. 2 .
  • the effective pressure-receiving area A on the discharge pressure side can be adjusted by adjusting the diameter of the valve hole 12
  • the effective pressure-receiving area B on the suction pressure side can be adjusted by adjusting the diameter of the shaft 18 (i.e. the diameter of the guide hole 9 ).
  • FIG. 3A to 3 C are diagrams useful in explaining the differential pressure ⁇ crank pressure characteristics of the control valve, wherein FIG. 3A represents the case where the effective pressure-receiving area A and the effective pressure-receiving area B are equal to each other, FIG. 3B the case where the effective pressure-receiving area A is smaller than the effective pressure-receiving area B, and FIG. 3C the case where the effective pressure-receiving area A is larger than the effective pressure-receiving area B.
  • the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps is slightly changed under the influence of the crank pressure Pc even when the value of electric current supplied to the solenoid is fixed.
  • the differential pressure (Pd ⁇ Ps) varies with the magnitude of the value (Isol) of electric current supplied to the solenoid 2 .
  • the effective pressure-receiving area A on the discharge pressure side and the effective pressure-receiving area B on the suction pressure side are equal to each other, so that originally, the crank pressure Pc should be cancelled and the differential pressure (Pd ⁇ Ps) should assume a predetermined value, irrespective of the crank pressure Pc, but actually, it is difficult to completely eliminate the influence of the crank pressure Pc, and there appears a slight slope in the characteristics, as shown in FIG. 3A .
  • the control valve is only required to be configured such that the effective pressure-receiving area A becomes smaller than the effective pressure-receiving area B.
  • the control valve is only required to be configured such that the effective pressure-receiving area A becomes larger than the effective pressure-receiving area B.
  • the difference between the effective pressure-receiving area A on the discharge pressure side of the intermediate formed by making the -valve element 14 and the shaft 18 integral with each other and the effective pressure-receiving area B on the suction pressure side of the intermediate is adjusted as required.
  • Changes in the effective pressure-receiving areas have almost no influence on the electric current ⁇ differential pressure characteristics, i.e. the relationship between the value of electric current supplied to the solenoid 2 and the differential pressure between the discharge pressure Pd and the suction pressure Ps, and hence it is possible to realize the changes in the effective pressure-receiving areas with ease.
  • desired differential pressure ⁇ crank pressure characteristics (characteristics concerning the degree of influence of the crank pressure on a change in the differential pressure between the discharge pressure and the suction pressure) can be obtained by adjusting the difference between the effective pressure-receiving area on the discharge pressure side of the intermediate formed by making the valve element and the shaft integral with each other, and the effective pressure-receiving area on the suction pressure side of the intermediate. Since the changes in the effective pressure-receiving areas have almost no influence on the electric current ⁇ differential pressure characteristics, i.e. the relationship between the value of electric current supplied to the solenoid and the differential pressure between the discharge pressure and the suction pressure, it is possible to obtain desired differential pressure ⁇ crank pressure characteristics with ease.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US11/205,064 2004-08-19 2005-08-17 Control valve for variable displacement compressor Abandoned US20060039798A1 (en)

Applications Claiming Priority (2)

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JP2004239161A JP2006057506A (ja) 2004-08-19 2004-08-19 可変容量圧縮機用制御弁
JP2004-239161 2004-08-19

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US20060039798A1 true US20060039798A1 (en) 2006-02-23

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US (1) US20060039798A1 (zh)
EP (1) EP1628017A3 (zh)
JP (1) JP2006057506A (zh)
KR (1) KR20060050534A (zh)
CN (1) CN100436813C (zh)

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US20080041080A1 (en) * 2006-08-21 2008-02-21 Yoshinori Inoue Structure for sensing refrigerant flow rate in a compressor
US20080110188A1 (en) * 2006-11-15 2008-05-15 Yoshinori Inoue Structure for sensing refrigerant flow rate in a compressor

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JP5149580B2 (ja) * 2007-09-26 2013-02-20 サンデン株式会社 可変容量圧縮機のための容量制御弁、容量制御システム及び可変容量圧縮機
JP6340661B2 (ja) 2014-02-27 2018-06-13 株式会社テージーケー 可変容量圧縮機用制御弁
JP2016020682A (ja) * 2014-06-19 2016-02-04 株式会社テージーケー 可変容量圧縮機用制御弁
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
JP2016014334A (ja) 2014-07-01 2016-01-28 株式会社テージーケー 可変容量圧縮機用制御弁
JP6528108B2 (ja) 2014-07-18 2019-06-12 株式会社テージーケー 可変容量圧縮機用制御弁
DE102014116214B3 (de) * 2014-11-06 2016-02-04 Eto Magnetic Gmbh Proportionalventil, Klimakompressoranordnung sowie Betriebsverfahren
EP3059445B1 (en) 2015-02-23 2020-06-24 TGK CO., Ltd. Electromagnetic control valve of a variable displacement compressor

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US20040074245A1 (en) * 2002-10-18 2004-04-22 Tgk Co., Ltd. Capacity control valve for variable displacement compressor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080041080A1 (en) * 2006-08-21 2008-02-21 Yoshinori Inoue Structure for sensing refrigerant flow rate in a compressor
US8186172B2 (en) * 2006-08-21 2012-05-29 Kabushiki Kaisha Toyota Jidoshokki Structure for sensing refrigerant flow rate in a compressor
US20080110188A1 (en) * 2006-11-15 2008-05-15 Yoshinori Inoue Structure for sensing refrigerant flow rate in a compressor

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EP1628017A2 (en) 2006-02-22
CN100436813C (zh) 2008-11-26
JP2006057506A (ja) 2006-03-02
KR20060050534A (ko) 2006-05-19
EP1628017A3 (en) 2006-11-02
CN1737370A (zh) 2006-02-22

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