US20050254961A1 - Control valve for variable displacement compressor - Google Patents

Control valve for variable displacement compressor Download PDF

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Publication number
US20050254961A1
US20050254961A1 US11/187,441 US18744105A US2005254961A1 US 20050254961 A1 US20050254961 A1 US 20050254961A1 US 18744105 A US18744105 A US 18744105A US 2005254961 A1 US2005254961 A1 US 2005254961A1
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US
United States
Prior art keywords
valve
crankcase
flow rate
control valve
pressure
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.)
Abandoned
Application number
US11/187,441
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English (en)
Inventor
Yuji Kawamura
Kazutaka Kowada
Kazuhiro Irie
Shunji Muta
Yoshie Sato
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.)
Valeo Thermal Systems Japan Corp
Original Assignee
Zexel Valeo Climate Control 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 Zexel Valeo Climate Control Corp filed Critical Zexel Valeo Climate Control Corp
Assigned to ZEXEL VALEO CLIMATE CONTROL CORPORATION reassignment ZEXEL VALEO CLIMATE CONTROL CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IRIE, KAZUHIRO, SATO, YOSHIE, KAWAMURA, YUJI, KOWADA, KAZUTAKA, MUTA, SHUNJI
Publication of US20050254961A1 publication Critical patent/US20050254961A1/en
Assigned to VALEO THERMAL SYSTEMS JAPAN CORPORATION reassignment VALEO THERMAL SYSTEMS JAPAN CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: ZEXEL VALEO CLIMATE CONTROL CORPORATION
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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery 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
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction 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 used in a refrigeration cycle of an automotive air conditioner.
  • a swash plate variable displacement compressor capable of changing the discharge amount of refrigerant is generally used in an automotive air conditioner.
  • a swash plate disposed within a crankcase such that the inclination angle thereof can be changed is driven by the rotation of a rotating shaft, for performing wobbling motion, and the wobbling motion causes a plurality of pistons to perform reciprocating motion in a direction parallel to the rotating shaft, whereby refrigerant is drawn, compressed, and then discharged.
  • the inclination angle of the swash plate is varied by changing the pressure in the crankcase, whereby the stroke of the pistons is changed for changing the discharge amount of the refrigerant.
  • control valve is disposed in a refrigerant passage communicating between a discharge chamber and a crankcase, and controls the flow rate of refrigerant introduced at discharge pressure Pd from the discharge chamber into the crankcase, to thereby control pressure Pc within the crankcase.
  • the refrigerant introduced into the crankcase is drawn into the suction chamber via a fixed orifice.
  • suction pressure Ps in the suction chamber is sensed e.g. by a pressure-sensing member, such as a diaphragm, and the flow rate of the refrigerant introduced into the crankcase is controlled such that the suction pressure Ps is maintained at a constant level.
  • variable displacement compressors using these two types of control valves, the fixed orifice having an invariable flow passage area is interposed in the passage from the discharge chamber to the crankcase or the passage from the crankcase to the suction chamber in series with the passage. Consequently, in the variable displacement compressor using one of the above-described control valves, increased amount of refrigerant circulates therein, which inevitably causes degradation of compression efficiency.
  • control valve having two valves disposed, respectively, in the refrigerant passage communicating between the discharge chamber and the crankcase and the refrigerant passage communicating between the crankcase and the suction chamber, such that the two valves operate in a manner interlocked with each other, so as to simultaneously control the flow rate of the refrigerant introduced into the crankcase and the flow rate of the refrigerant drawn from the crankcase (e.g. in Japanese Unexamined Patent Publication (Kokai) NO. S58-158382, FIG. 3 ).
  • control valve provides control such that when the flow rate of refrigerant in one of the refrigerant passage communicating between the discharge chamber and the crankcase and the refrigerant passage communicating between the crankcase and the suction chamber is increased, the flow rate of refrigerant in the other is reduced.
  • a control valve having two valves disposed, respectively, in the refrigerant passage communicating between the discharge chamber and the crankcase and the refrigerant passage communicating between the crankcase and the suction chamber, such that the two valves operate in a manner interlocked with each other to hold one of the refrigerant passages in a closed state when the other passage is open in a controlled state (e.g. in Japanese Unexamined Patent Publication (Kokai) No. S64-41680, FIG. 2 ).
  • this control valve when the flow rate of refrigerant in one of the refrigerant passages is being controlled, the other refrigerant passage is closed, so that refrigerant circulating in the variable displacement compressor can be further reduced.
  • the present invention has been made in view of the above points, and an object thereof is to provide a control valve for a variable displacement compressor, which is capable of reducing the amount of refrigerant circulating within the compressor to thereby improve compression efficiency, while ensuring stable controllability.
  • the present invention provides a control valve for a variable displacement compressor, which is capable of controlling pressure in a crankcase to thereby change a discharge amount of refrigerant, comprising a first valve that is disposed between a discharge chamber and the crankcase of the compressor, for controlling a flow rate of refrigerant flowing from the discharge chamber to the crankcase, a second valve that is disposed between the crankcase and a suction chamber of the compressor, for controlling a flow rate of refrigerant flowing from the crankcase to the suction chamber to a predetermined minimum rate when the first valve is controlling the flow rate of the refrigerant flowing from the discharge chamber to the crankcase, and for controlling the flow rate of the refrigerant flowing from the crankcase to the suction chamber when the first valve is fully closed or nearly fully closed, and a pressure-sensing section that senses suction pressure in the suction chamber, for changing a lift amount of the first valve and a lift amount of the second valve.
  • FIG. 1 is a conceptual view showing the arrangement of a control valve for a variable displacement compressor, according to the present invention.
  • FIG. 2 is an enlarged fragmentary view useful in explaining the control valve set to a first opening/closing timing.
  • FIG. 3 is a diagram showing characteristics of the control valve set to the first opening/closing timing.
  • FIG. 4 is an enlarged fragmentary view useful in explaining the control valve set to a second opening/closing timing.
  • FIG. 5 is a diagram showing characteristics of the control valve set to the second opening/closing timing.
  • FIG. 6 is an enlarged fragmentary view useful in explaining the control valve set to a third opening/closing timing.
  • FIG. 7 is a diagram showing characteristics of the control valve set to the third opening/closing timing.
  • FIG. 8 is an enlarged fragmentary view useful in explaining a control valve in which a fixed orifice is formed in each of an inlet side and an outlet side.
  • FIG. 9 is a diagram showing characteristics of the control valve set to a fourth opening/closing timing.
  • FIG. 10 is a conceptual view showing a control valve in which a fixed orifice is formed in each of an inlet side and an outlet side.
  • FIG. 11 is a diagram showing characteristics of the control valve set to a fifth opening/closing timing.
  • FIG. 12 is a conceptual view showing the arrangement of a mechanical control valve for a variable displacement compressor.
  • FIG. 13 is a conceptual view showing the arrangement of a mechanical control valve for a variable displacement compressor.
  • FIG. 14 is a conceptual view showing the arrangement of a control valve for a variable displacement compressor, in which the fixed orifice function of a second valve is provided independently.
  • FIG. 1 is a conceptual view showing the arrangement of a control valve for a variable displacement compressor, according to the present invention.
  • the control valve for a variable displacement compressor has a ball valve 11 forming a first valve, a spool valve 12 forming a second valve, a diaphragm 13 forming a pressure-sensing section, and a solenoid 14 forming a pressure-setting section, which are arranged in the mentioned order.
  • the ball valve 11 introduces refrigerant discharged at discharge pressure Pd from a discharge chamber of the variable displacement compressor, and controls the flow rate of the introduced refrigerant to supply the refrigerant at pressure Pc 1 to a crankcase.
  • the spool valve 12 introduces refrigerant delivered at pressure Pc 2 from the crankcase, and controls the flow rate of the introduced refrigerant to supply the pressure to a suction chamber of the compressor in a manner interlocked with operation of the ball valve 11 .
  • the diaphragm 13 receives suction pressure Ps from the suction chamber, and when the suction pressure becomes lower than a predetermined suction pressure setting point, the diaphragm 13 displaces the ball valve 11 and the spool valve 12 to increase pressure in the crankcase.
  • the suction pressure of an air conditioner is controlled to a level in the vicinity of the predetermined suction pressure setting point.
  • the solenoid 14 applies urging load to the diaphragm 13 to set the suction pressure setting point.
  • the urging load is set according to the value of an electric current externally supplied.
  • the spool valve 12 comprises a valve seat 15 and a valve element 16 removably inserted into a valve hole. Between the valve seat 15 and the valve element 16 , there is formed a predetermined clearance 17 .
  • This clearance 17 forms a fixed orifice with an invariable flow passage area between the crankcase and the suction chamber when the valve element 16 is inserted into the valve hole.
  • the clearance 17 is determined depending on the stability of the swash plate of the compressor.
  • the valve element 16 is integrally formed with a shaft 18 for driving the ball valve 11 .
  • the valve element 16 and the shaft 18 are joined to each other by a joining part 19 having a frustoconical shape with a taper in cross section.
  • the spool valve 12 can be freely modified according to characteristics, such as hunting, controllability, and stability, of the variable displacement compressor such that the spool valve 12 has a different opening/closing timing from that of the ball valve 11 interlocking with operation of the spool valve 12 .
  • the change in the opening/closing timing of the spool valve 12 can be easily achieved by changing the distance between an end of the valve element 16 as a boundary to the joining part 19 and a forward end of the shaft 18 in contact with a valve element 20 of the ball valve 11 to thereby axially shift a position where the end of the valve element 16 is held in a fully-closed state of the ball valve 11 .
  • the valve element 20 moves in a valve-opening direction, and the maximum valve lift of the ball valve 11 is limited by abutment of a stepped part 21 of the shaft 18 against a stepped part 22 of a body.
  • FIG. 2 is an enlarged fragmentary view useful in explaining the control valve set to a first opening/closing timing
  • FIG. 3 is a diagram showing characteristics of the control valve set to the first opening/closing timing.
  • the first opening/closing timing is set such that the opening/closing timing of the ball valve 11 and that of the spool valve 12 coincide with each other, and more specifically such that when the ball valve 11 is fully closed, the end of the valve element 16 of the spool valve 12 is aligned with a solenoid-side open end face of the valve seat 15 .
  • the characteristics exhibited by the control valve when the valve element 16 of the spool valve 12 is axially moved are as shown in FIG. 3 .
  • the abscissa represents a stroke of the shaft 18
  • the origin represents a state where the stepped part 21 of the shaft 18 is in abutment with the stepped part 22 of the body and at a position closest to the ball valve side (or a deenergized state of the solenoid).
  • the ordinate in FIG. 3 represents the opening area of the ball valve 11 and that of the spool valve 12 .
  • a line indicated by Pd-Pc represents changes in the opening area of the ball valve 11
  • a line indicated by Pc-Ps represents changes in the opening area of the spool valve 12 .
  • the spool valve 12 In the first opening/closing timing, as long as the ball valve 11 is open, the spool valve 12 has an opening area corresponding to the clearance 17 , and operates as the fixed orifice.
  • the shaft 18 moves toward the solenoid 14 and reaches a position s 1 , the valve element 20 of the ball valve 11 is seated to fully close the ball valve 11 .
  • the shaft 18 further moves toward the solenoid 14 , the forward end of the shaft 18 moves away from the valve element 20 of the ball valve 11 , whereby the ball valve 11 is held in its fully-closed state, and the spool valve 12 starts opening from the state operating as the fixed orifice to increase its opening area in accordance with increase in the stroke of the shaft 18 .
  • FIG. 4 is an enlarged fragmentary view useful in explaining the control valve set to a second opening/closing timing
  • FIG. 5 is a diagram showing characteristics of the control valve set to the second opening/closing timing.
  • the second opening/closing timing is set such that the opening timing of the spool valve 12 is retarded with respect to the closing timing of the ball valve 11 , and hence in the second opening/closing timing, when the ball valve 11 is fully closed, the spool valve 12 is still in its closed state (fixed orifice state).
  • the distance between the ball valve-side end of the valve element 16 and the forward end of the shaft in contact with the valve element 20 of the ball valve 11 is made shorter by a distance “a” than in the first opening/closing timing such that when the ball valve 11 is closed, the ball valve-side end of the valve element 16 of the spool valve 12 is positioned within the valve hole.
  • FIG. 6 is an enlarged fragmentary view useful in explaining the control valve set to a third opening/closing timing
  • FIG. 7 is a diagram showing characteristics of the control valve set to the third opening/closing timing.
  • the third opening/closing timing is configured such that the opening timing of the spool valve 12 is advanced with respect to the closing timing of the ball valve 11 .
  • the distance between the ball valve-side end of the valve element 16 and the forward end of the shaft in contact with the valve element 20 of the ball valve 11 is made longer by a distance “b” than in the first opening/closing timing whereby when the ball valve 11 is closed, the ball valve-side end of the valve element 16 of the spool valve 12 is positioned closer to the solenoid 14 than the valve seat 15 .
  • FIG. 8 is an enlarged fragmentary view useful in explaining a control valve in which a fixed orifice is formed in each of an inlet side and an outlet side
  • FIG. 9 is a diagram showing characteristics of the control valve set to a fourth opening/closing timing. It should be noted that component elements in FIG. 8 identical to those in FIG. 1 are designated by identical reference numerals.
  • This control valve is configured such that the fixed orifices are formed on the respective inlet and outlet sides of the crankcase.
  • the forward end of the shaft 18 in contact with the valve element 20 of the ball valve 11 is formed into a spool shape, and a clearance 24 is formed between the outer periphery of a contact end part 23 of the shaft 18 and the inner wall of the valve hole.
  • the clearance 24 is formed within the valve hole to form a fixed orifice with an invariable flow passage area between a compression chamber and the crankcase.
  • the fixed orifice is provided for stably maintaining the flow rate of refrigerant introduced from the discharge chamber into the crankcase in a region where refrigerant is introduced into the crankcase by blowby gas, and the flow rate of refrigerant discharged from the crankcase is controlled by the spool valve 12 .
  • the distance between the rear end (diameter reduction start position) of the contact end part 23 and the seated position of the valve element 20 is set to a distance “c”.
  • the distance “d” between the end of the valve element 16 of the spool valve 12 and a valve closing start position of the spool valve 12 is set such that it becomes equal in value to the distance “c” when the ball valve 11 is fully closed with the valve element 20 thereof held in contact with the contact end part 23 .
  • the control valve set as above has the following characteristics: As shown in FIG. 9 , first, when the solenoid is not energized, the stepped part 21 of the shaft 18 is in contact with the stepped part 22 of the body, and hence the ball valve 11 is in its fully-open state, and the spool valve 12 is in the fixed orifice state.
  • the ball valve 11 turns from the fully-open state in the direction of reducing its opening area, whereas the spool valve 12 maintains its fixed orifice state. Then, when the shaft moves to a position s 1 , the rear end of the contact end part 23 reaches the seated position of the valve element 20 , and the spool valve 12 reaches a valve opening start position at which it starts to get out of the fixed orifice state. When the shaft 18 further moves from the position s 1 , the rear end of the contact end part 23 enters the valve hole, whereby the ball valve 11 enters its fixed orifice state, and the spool valve 12 changes from its fixed orifice state in the direction of increasing its opening area.
  • the fixed orifice state of the ball valve 11 is maintained until the opening area of the ball valve 11 becomes smaller than that of the fixed orifice, and finally the ball valve 11 is seated to be fully closed.
  • the distance “c” and the distance “d” are set to the same value, the distance “d” may be increased or decreased according to the characteristics of the variable displacement compressor to thereby easily change the opening/closing timing of the spool valve 12 .
  • FIG. 10 is a conceptual view showing the arrangement of a control valve in which a fixed orifice is formed in each of the inlet side and the outlet side
  • FIG. 11 is a diagram showing characteristics of the control valve set to a fifth opening/closing timing. It should be noted that component elements in FIG. 10 identical to those in FIG. 1 are designated by identical reference numerals.
  • a valve disposed between the compressor and the crankcase and a valve disposed between the crankcase and the suction chamber are implemented by respective spool valves 11 a and 12 .
  • the valve element 16 of the spool valve 12 , the shaft 18 , and a valve element 20 a of the spool valve 11 a are integrally formed with each other.
  • the valve element 20 a is smaller in diameter than the shaft 18 supported by the body, and the clearance 24 is formed between the valve element 20 a and the inner wall of the valve hole. Further, a portion between the valve element 20 a and the shaft 18 is reduced in diameter to have a spool shape.
  • the distance between the rear end (diameter reduction start position) of the valve element 20 a and a valve closing start position where the valve element 20 a enters the valve hole is set such that it becomes equal to a distance “e” when the spool valve 12 is in a valve closing start position.
  • the control valve set as above has the following characteristics: As shown in FIG. 11 , first, when the solenoid is not energized, the stepped part 21 of the shaft 18 is in contact with the stepped part 22 of the body, and hence the spool valve 11 a is in its fully-open state, and the spool valve 12 is fully closed and in its fixed orifice state.
  • the rear end of the valve element 20 a of the spool valve 11 a approaches the valve hole and changes from its fully-open state in the direction of reducing its opening area, whereas the spool valve 12 maintains its fixed orifice state. Then, when the shaft 18 moves to a position s 1 , the spool valve 11 a reaches the valve closing start position, and the spool valve 12 reaches a valve opening start position at which it starts to get out of its fixed orifice state.
  • valve element 20 a When the shaft 18 further moves from the position s 1 , the valve element 20 a enters the valve hole, whereby the spool valve 11 a enters its fixed orifice state, and the spool valve 12 changes from its fixed orifice state in the direction of increasing its opening area.
  • the electric control valves which use, as means for setting the suction pressure Ps in the suction chamber, the solenoid that enables a set point (pressure control point) thereof to be freely set by external electric control current.
  • mechanical control valves will be describe in which the suction pressure Ps is set to a fixed value.
  • FIG. 12 is a conceptual view showing the arrangement of a mechanical control valve for a variable displacement compressor. It should be noted that component elements in FIG. 12 identical to those in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • This control valve has the ball valve 11 forming the first valve, the spool valve 12 forming the second valve, the diaphragm 13 forming the pressure-sensing section, and a spring 25 forming a pressure-setting section, which are arranged in the mentioned order.
  • This control valve is also configured such that as long as the ball valve 11 is variably controlling its opening area, the spool valve 12 functions as a fixed orifice, and when the ball valve 11 is in its fully-closed state, the spool valve 12 variably controls its opening area.
  • the opening/closing timing of the spool valve 12 is set to one of the above described first to third opening/closing timings in accordance with the characteristics of the variable displacement compressor.
  • the diaphragm 13 has a disk 26 provided on a spring-side surface thereof, and the spring 25 urges the diaphragm 13 toward the spool valve 12 via the disk 26 .
  • the spring 25 is adjusted to have a spring load corresponding to a predetermined suction pressure control point. Therefore, when the suction pressure Ps received from the suction chamber becomes lower than the suction pressure control point, the diaphragm 13 urges the ball valve 11 and the spool valve 12 such that the pressure in the crankcase is increased, whereby the control valve controls the displacement of the variable displacement compressor to thereby control suction pressure in the air conditioner to a level in the vicinity of the predetermined suction pressure control point.
  • control valve can also be configured as a control valve set to the fourth opening/closing timing, by forming the contact end part 23 at the end of the shaft 18 to form the fixed orifice shown in FIG. 8 and thereby forming the fixed orifices on the respective refrigerant inlet and outlet sides of the crankcase.
  • FIG. 13 is a conceptual view showing the arrangement of a mechanical control valve for a variable displacement compressor. It should be noted that component elements in FIG. 13 identical to those in FIGS. 1 and 10 are designated by identical reference numerals, and detailed description thereof is omitted.
  • This control valve has the spool valve 11 a forming the first valve, the spool valve 12 forming the second valve, the diaphragm 13 forming the pressure-sensing section, and the spring 25 forming the pressure-setting section, which are arranged in the mentioned order.
  • the spool valve 11 a is identical in construction to that shown in FIG. 10 . Therefore, the present control valve has the characteristic of the fifth opening/closing timing shown in FIG. 11 .
  • the suction pressure Ps is received from the suction chamber to change the lift amount of each of the spool valves 11 a and 12 , and the pressure in the crankcase is controlled such that the suction pressure Ps is held constant as a consequence.
  • FIG. 14 is a conceptual view showing the arrangement of a control valve for a variable displacement compressor, in which the fixed orifice function of the second valve is provided independently. It should be noted that component elements in FIG. 14 identical to those in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the present control valve is distinguished from the control valve shown in FIG. 1 , in which the clearance 17 formed between the valve element 16 of the spool valve 12 and the inner wall of the valve hole provides the fixed orifice function, in that a fixed orifice 27 having an opening area equivalent to that formed by the clearance 17 is formed in the body.
  • the clearance 17 formed between the valve element 16 of the spool valve 12 and the inner wall of the valve hole is minimized.
  • refrigerant passage between the crankcase and the suction chamber is narrowed by the spool valve 12 , refrigerant is caused to flow through the fixed orifice 27 larger in diameter, and prevented from flowing through the clearance 17 which is small. This provides an advantageous effect that a change in the flow rate of refrigerant due to deposition of sludge contained in the refrigerant can be reduced.
  • the clearance 17 between the valve element 16 of the spool valve 12 and the inner wall of the valve hole is e.g. 0.1 mm
  • the fixed orifice 27 having an opening area equivalent to the clearance 17 is a through hole with a diameter of 1 mm
  • sludge deposited on the valve element 16 or the inner wall of the valve hole, or on the inner wall of the fixed orifice 27 has grown e.g. to a thickness of 0.1 mm
  • the clearance 17 is almost clogged with the sludge
  • the diameter of the fixed orifice 27 is reduced only to 0.8 mm, which makes smaller the change in the flow rate of refrigerant due to deposition of sludge.
  • refrigerant since refrigerant mainly flows through the fixed orifice 27 which is easier for refrigerant to flow through, the amount of refrigerant flowing through the narrow clearance 17 is small, which makes it difficult for sludge to deposit.
  • control valve is configured to comprise the first valve for controlling the flow rate of refrigerant flowing from the discharge chamber to the crankcase, the second valve for controlling the flow rate of refrigerant flowing from the crankcase to the suction chamber, the pressure-sensing section for sensing suction pressure, and the pressure-setting section for setting the suction pressure, wherein the second valve starts flow rate control after the first valve is fully closed or nearly fully closed, and the first valve starts flow rate control after the valve lift of the second valve is minimum or nearly minimum.
  • the first and second valves are both open simultaneously during switching of control between the first valve and the second valve, which makes it possible to minimize the flow rate of refrigerant flowing from the discharge chamber to the crankcase and further from the crankcase to the suction chamber, i.e. the flow rate of refrigerant circulating within the variable displacement compressor without contributing to a refrigerating operation, to thereby improve the efficiency of the compressor.
  • the second valve is equipped with the fixed orifice function for reducing the flow rate of refrigerant flowing from the crankcase to the suction chamber to a predetermined minimum flow rate, it is possible to stably adjust the pressure in the crankcase to thereby provide excellent controllability.

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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)
US11/187,441 2003-01-22 2005-07-20 Control valve for variable displacement compressor Abandoned US20050254961A1 (en)

Applications Claiming Priority (3)

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JP2003013890 2003-01-22
JP2003-013890 2003-01-22
PCT/JP2004/000505 WO2004065789A1 (ja) 2003-01-22 2004-01-21 可変容量圧縮機の制御弁

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US (1) US20050254961A1 (ja)
EP (1) EP1589223B1 (ja)
JP (1) JP4547332B2 (ja)
KR (1) KR100984214B1 (ja)
CN (1) CN100396916C (ja)
WO (1) WO2004065789A1 (ja)

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US20060039799A1 (en) * 2004-08-19 2006-02-23 Tgk Co., Ltd. Control valve for variable displacement compressor
US20100068074A1 (en) * 2006-11-30 2010-03-18 Calsonic Kansei Corporation Control valve for variable displacement compressor
CN101985926A (zh) * 2010-10-22 2011-03-16 四川金科环保科技有限公司 液压活塞式压缩机排气量无级调节方法
WO2011075300A2 (en) * 2009-12-18 2011-06-23 Cameron International Corporation A bi-directional valve with cavity pressure relief
US20110214564A1 (en) * 2010-03-08 2011-09-08 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor
US20160123321A1 (en) * 2014-11-05 2016-05-05 Delphi Technologies, Inc. Variable displacement compressor with an oil check vlave
US20170356430A1 (en) * 2016-06-13 2017-12-14 Tgk Co., Ltd. Control valve for variable displacement compressor
US9903362B2 (en) 2013-07-04 2018-02-27 Tgk Co., Ltd. Control valve for a variable displacement compressor
US11401922B2 (en) 2017-03-28 2022-08-02 Eagle Industry Co., Ltd. Displacement control valve
US11536389B2 (en) 2017-08-28 2022-12-27 Eagle Industry Co., Ltd. Electromagnetic valve

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JP4456906B2 (ja) * 2004-03-25 2010-04-28 株式会社不二工機 可変容量型圧縮機用の制御弁
JP2013144957A (ja) * 2012-01-16 2013-07-25 Japan Climate Systems Corp 可変容量圧縮機
JP6500186B2 (ja) * 2016-02-25 2019-04-17 株式会社テージーケー 可変容量圧縮機用制御弁
JP6500185B2 (ja) * 2016-02-25 2019-04-17 株式会社テージーケー 可変容量圧縮機用制御弁
US10690125B2 (en) * 2016-03-17 2020-06-23 Eagle Industry Co., Ltd. Displacement control valve
JP6714274B2 (ja) * 2016-06-13 2020-06-24 株式会社テージーケー 可変容量圧縮機用制御弁
KR102051661B1 (ko) * 2017-05-30 2019-12-04 한온시스템 주식회사 컨트롤 밸브 및 가변 용량식 압축기
JP6910871B2 (ja) * 2017-07-14 2021-07-28 サンデン・オートモーティブコンポーネント株式会社 可変容量圧縮機
KR20190092234A (ko) * 2018-01-29 2019-08-07 한온시스템 주식회사 압축기의 제어장치, 그에 사용되는 전자식 제어밸브 및 그를 포함한 전동 압축기
EP3835576B1 (en) * 2018-08-08 2024-03-27 Eagle Industry Co., Ltd. Capacity control valve
CN110469497A (zh) * 2019-08-14 2019-11-19 珠海格力节能环保制冷技术研究中心有限公司 压缩机及具有其的制冷设备

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US20060039799A1 (en) * 2004-08-19 2006-02-23 Tgk Co., Ltd. Control valve for variable displacement compressor
US20100068074A1 (en) * 2006-11-30 2010-03-18 Calsonic Kansei Corporation Control valve for variable displacement compressor
WO2011075300A3 (en) * 2009-12-18 2011-11-17 Cameron International Corporation A bi-directional valve with cavity pressure relief
WO2011075300A2 (en) * 2009-12-18 2011-06-23 Cameron International Corporation A bi-directional valve with cavity pressure relief
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US20110214564A1 (en) * 2010-03-08 2011-09-08 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor
CN101985926A (zh) * 2010-10-22 2011-03-16 四川金科环保科技有限公司 液压活塞式压缩机排气量无级调节方法
US9903362B2 (en) 2013-07-04 2018-02-27 Tgk Co., Ltd. Control valve for a variable displacement compressor
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US20170356430A1 (en) * 2016-06-13 2017-12-14 Tgk Co., Ltd. Control valve for variable displacement compressor
CN107489791A (zh) * 2016-06-13 2017-12-19 株式会社Tgk 可变容量压缩机用控制阀
US20180135610A1 (en) * 2016-06-13 2018-05-17 Tgk Co., Ltd. Control valve for variable displacement compressor
US10760559B2 (en) * 2016-06-13 2020-09-01 Tgk Co., Ltd. Control valve for variable displacement compressor
US10883480B2 (en) * 2016-06-13 2021-01-05 Tgk Co., Ltd. Control valve for variable displacement compressor
US11401922B2 (en) 2017-03-28 2022-08-02 Eagle Industry Co., Ltd. Displacement control valve
US11536389B2 (en) 2017-08-28 2022-12-27 Eagle Industry Co., Ltd. Electromagnetic valve

Also Published As

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JPWO2004065789A1 (ja) 2006-05-18
JP4547332B2 (ja) 2010-09-22
CN100396916C (zh) 2008-06-25
EP1589223A4 (en) 2011-03-16
KR20050094868A (ko) 2005-09-28
CN1738971A (zh) 2006-02-22
KR100984214B1 (ko) 2010-09-28
EP1589223A1 (en) 2005-10-26
EP1589223B1 (en) 2019-04-24
WO2004065789A1 (ja) 2004-08-05

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