US20060039799A1 - Control valve for variable displacement compressor - Google Patents

Control valve for variable displacement compressor Download PDF

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Publication number
US20060039799A1
US20060039799A1 US11/205,119 US20511905A US2006039799A1 US 20060039799 A1 US20060039799 A1 US 20060039799A1 US 20511905 A US20511905 A US 20511905A US 2006039799 A1 US2006039799 A1 US 2006039799A1
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Prior art keywords
pressure
valve
sensing
control valve
discharge
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Abandoned
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US11/205,119
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English (en)
Inventor
Hisatoshi Hirota
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TGK Co Ltd
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TGK Co Ltd
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Publication of US20060039799A1 publication Critical patent/US20060039799A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • 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
    • 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
    • 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
    • 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
    • F04B2027/184—Valve controlling parameter
    • F04B2027/185—Discharge 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
    • F04B2027/184—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, which is mounted on a variable displacement compressor as a component of a refrigeration cycle of an automotive air conditioner, for control of the discharge capacity of the compressor by the differential pressure between discharge pressure and suction pressure.
  • a compressor used in the refrigeration cycle of an automotive air conditioner, for compressing refrigerant uses an engine as a drive source, and hence is incapable of performing rotational speed control.
  • a variable displacement compressor capable of varying the compression capacity of refrigerant is employed so as to obtain an adequate cooling capacity without being constrained by the rotational speed of the engine.
  • a wobble plate fitted on a shaft driven by the engine for rotation has compression pistons connected thereto, and by varying the inclination angle of the wobble plate, the stroke of the pistons is varied to vary the discharge amount of refrigerant.
  • the inclination angle of the wobble plate is continuously changed by introducing part of compressed refrigerant into a hermetically closed crankcase, and causing a change in the pressure of the introduced refrigerant, thereby changing the balance of pressures acting on the opposite sides of each piston.
  • a control valve for a variable displacement compressor is known (see e.g. Japanese Unexamined Patent Publication (Kokai) No. 2001-132650 (Paragraph numbers [0043] to [0045], FIG. 4)) which is disposed between a discharge chamber and a crankcase of the compressor, or between the crankcase and a suction chamber of the compressor, for adjusting pressure in the crankcase by changing the flow rate of refrigerant introduced from the discharge chamber into the crankcase, or changing the flow rate of refrigerant delivered from the crankcase to the suction chamber.
  • the control valve described in Japanese Unexamined Patent Publication (Kokai) No. 2001-132650 is configured such that it has a valve section disposed in a refrigerant passage between the discharge chamber and the crankcase of the compressor when it is mounted in the compressor, and a path is formed along which refrigerant flows from the discharge chamber to the suction chamber of the compressor via an orifice provided between the crankcase and the suction chamber.
  • the control valve has the valve section which comprises a valve element that receives discharge pressure Pd in the valve-opening direction, and a piston rod that is integrally formed with the valve element on a rear side of the valve element and has approximately the same diameter as that of a valve hole, and is configured such that an end face of the piston rod receives suction pressure Ps and the load of a solenoid for setting the discharge capacity of the compressor by an external signal, in the valve-closing direction.
  • the discharge pressure Pd and the suction pressure Ps are received by the opposite ends of the valve element and piston rod, both having the same effective pressure-receiving area, and hence the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps causes the valve element to perform an opening/closing operation to thereby control the flow rate of refrigerant flowing from the discharge chamber into the crankcase.
  • control valve controls the flow rate of refrigerant being introduced into the crankcase such that the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps is held at a predetermined value.
  • the predetermined value of the differential pressure can be set from outside by a value of electric current supplied to the solenoid.
  • the control valve for the variable displacement compressor that operates based on the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and the suction pressure Ps
  • the pressure Pc in the crankcase is adjusted after the differential pressure (Pd ⁇ Ps) is changed due to the change in the discharge capacity of the compressor. Therefore, when the engine is in a transient period in which the rotational speed of the engine has rapidly changed, the discharge capacity of the compressor can be temporarily largely changed due to low responsiveness of the compressor. This inconvenience can be eliminated by improving the sensitivity of the control valve.
  • control valve for the variable displacement compressor which operates based on the differential pressure (Pd ⁇ Ps)
  • Pd ⁇ Ps differential pressure
  • the control valve for the variable displacement compressor which operates based on the differential pressure (Pd ⁇ Ps)
  • Pd ⁇ Ps differential pressure
  • the present invention has been made in view of the problem, and an object thereof is to provide a control valve for a variable displacement compressor, which is capable of promptly restoring the compressor to a predetermined discharge capacity even when the rotational speed of an engine has rapidly changed.
  • the present invention provides a control valve for a variable displacement compressor, which is configured to sense differential pressure between discharge pressure in a discharge chamber of the compressor and suction pressure in a suction chamber of the compressor, and control a flow rate of refrigerant allowed to flow from the discharge chamber into a crankcase to thereby change a discharge capacity of the refrigerant, comprising a pressure-sensing section that senses a change in pressure caused by a rapid change in a rotational speed of the compressor and accelerates a motion of a valve section in a valve-opening/closing direction performed in response to the change in pressure.
  • FIG. 1 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a first embodiment of the present invention.
  • FIG. 2 is a diagram useful in explaining operation of the control valve, in the case where the rotational speed of the compressor is rapidly increased.
  • FIG. 3 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a second embodiment of the present invention.
  • FIG. 4 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a third embodiment of the present invention.
  • FIG. 5 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a fourth embodiment of the present invention.
  • FIG. 6 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a fifth embodiment of the present invention.
  • FIG. 7 is a central longitudinal cross-sectional view showing a configuration of a control valve for a variable displacement compressor, according to a sixth embodiment of the present invention.
  • FIG. 8 is an enlarged fragmentary central longitudinal cross-sectional view showing details of essential parts of a control valve for a variable displacement compressor, according to a seventh embodiment of the present invention.
  • FIG. 9 is an enlarged fragmentary central longitudinal cross-sectional view showing details of essential parts of a control valve for a variable displacement compressor, according to an eighth embodiment of the present invention.
  • FIG. 10 is an enlarged fragmentary central longitudinal cross-sectional view of the control valve according to the eighth embodiment in an operative state in which the discharge pressure of the compressor has rapidly decreased.
  • FIG. 11 is an enlarged fragmentary central longitudinal cross-sectional view showing a control valve for a variable displacement compressor, according to a ninth embodiment of the present invention, in states in which the discharge pressure has rapidly increased and in which the discharge pressure has rapidly decreased.
  • FIG. 12 is an enlarged fragmentary central longitudinal cross-sectional view showing details of essential parts of a control valve for a variable displacement compressor, according to a tenth embodiment of the present invention.
  • FIG. 1 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a first embodiment of the present invention.
  • the control valve 11 comprises a pressure-sensing section 12 that senses a rapid change in discharge pressure Pd, a valve section 13 that senses the differential pressure (Pd ⁇ Ps) between the discharge pressure Pd and suction pressure Ps to control the flow rate of refrigerant allowed to flow from a discharge chamber into a crankcase, and a solenoid 14 that is capable of setting a predetermined value to which the differential pressure (Pd ⁇ Ps) is to be controlled by the control valve, from outside, these sections being arranged on the same axis.
  • the pressure-sensing section 12 and the valve section 13 have a first body 15 , and a second body 16 into which the first body 15 is press-fitted.
  • the first body 15 has a cylinder 17 that has an open upper end, as viewed in FIG. 1 , and the open end defines a high-pressure port 18 communicating with the discharge chamber when the control valve 11 is mounted in the variable displacement compressor.
  • a pressure-sensing piston 19 is disposed within the cylinder 17 in a manner movable axially back and forth, and the pressure-sensing piston 19 is urged downward, as viewed in FIG. 1 , by a spring 21 disposed between the pressure-sensing piston 19 and a stopper 20 fixed to an upper end of the first body 15 .
  • the cylinder 17 has a hole formed in the center of a bottom thereof, and a hollow cylindrical valve seat-forming member 22 is press-fitted in the hole.
  • the valve seat-forming member 22 has an upper part thereof inserted into a cylinder formed in an center of a lower end the pressure-sensing piston 19 , as viewed in FIG. 1 , in a recessed manner, thereby defining a pressure-adjusting chamber 23 having an annular space, together with the first body 15 and the pressure-sensing piston 19 .
  • the pressure-sensing piston 19 is formed with a through hole which communicates between the cylinder formed in the pressure-sensing piston 19 in a recessed manner and the high-pressure port 18 , whereby the high-pressure port 18 communicates with a passage axially extending through the valve seat-forming member 22 , i.e. a valve hole, via the through hole of the pressure-sensing piston 19 . Further, the pressure-sensing piston 19 has one end of a shaft 24 fixed thereto, the shaft 24 extending through the valve hole defined by the valve seat-forming member 22 .
  • the valve seat-forming member 22 has a lower end, as viewed in FIG. 1 , which forms a valve seat, and a valve element 25 is disposed in a manner opposed to the valve seat such that the valve element 25 can open and close the valve hole.
  • the valve element 25 is formed integrally with a piston rod 26 , and the piston rod 26 is held by the second body 16 in a manner movable axially back and forth.
  • the piston rod 26 is formed such that it has an outer diameter equal to the inner diameter of the valve hole of the valve seat-forming member 22 .
  • the valve element 25 is in abutment with the other end of the shaft 24 which is disposed within the valve hole of the valve seat-forming member 22 and urged downward by the spring 21 , as viewed in FIG. 1 .
  • valve element 25 is disposed communicates with a medium-pressure port 28 for supplying pressure Pc to the crankcase of the compressor when the control valve 11 is mounted in the compressor, and a space where the spring 27 is disposed communicates with a low-pressure port 29 for receiving the suction pressure Ps from a suction chamber.
  • the second body 16 has a hole formed in the center of a lower part thereof, as viewed in FIG. 1 .
  • the rim of an opening of a bottomed sleeve 30 is tightly connected to the hole.
  • the bottomed sleeve 30 has a core 31 and a plunger 32 of the solenoid 14 arranged therein.
  • the core 31 is fixed to the hole of the second body 16 and the bottomed sleeve 30 by press-fitting.
  • the plunger 32 is axially slidably disposed in the bottomed sleeve 30 , and fixed to one end of a shaft 33 disposed in a manner axially extending through the core 31 .
  • the plunger 32 is urged toward the core 31 by a spring 34 such that the other end of the shaft 33 is brought into abutment with a lower end face of the piston rod 26 , as viewed in FIG. 1 .
  • a coil 35 Disposed around the outer periphery of the bottomed sleeve 30 is a coil 35 , and a harness 36 for supplying electric current to the coil 35 is led to the outside of the solenoid 14 .
  • the spring 27 urging the piston rod 26 of the valve section 13 toward the solenoid 14 is set to have a larger spring load than that of the spring 34 urging the shaft 33 of the solenoid 14 toward the valve section 13 . Therefore, when the solenoid 14 is not energized, the valve element 25 of the valve section 13 is away from the valve seat-forming member 22 , and hence the valve section 13 is held in the fully open state. At this time, high-pressure refrigerant at the discharge pressure Pd, which has been introduced from the discharge chamber of the compressor to the high-pressure port 18 , passes through the valve section 13 in the fully open state, and flows from the medium-pressure port 28 into the crankcase. This makes the pressure Pc in the crankcase close to the discharge pressure Pd, whereby the compressor is caused to operate with the minimum discharge capacity.
  • the valve element 25 is stopped at a valve lift position where the loads of the springs 21 and 27 urging the valve element 25 in the valve-opening direction, the load of the solenoid 14 urging the valve element 25 in the valve-closing direction, the discharge pressure Pd which the valve element 25 receives in the valve-opening direction, and the suction pressure Ps which the valve element 25 receives in the valve-closing direction are balanced.
  • the pressure-sensing section 12 is insensitive, and performs the same operation as that of the conventional control valve for a variable displacement compressor.
  • a description will be given of operation of the control valve 11 in the case where the rotational speed of the compressor is rapidly changed by a rapid change in the rotational speed of the engine as in the case where the automotive vehicle has been rapidly accelerated or decelerated.
  • FIG. 2 is a diagram useful in explaining operation of the control valve for a variable displacement compressor, in the case where the rotational speed of the compressor is rapidly increased.
  • the valve lift is increased due to a rise in the discharge pressure Pd and a drop in the suction pressure Ps, and as a result, the control valve 11 tends to increase the pressure Pc in the crankcase, as indicated by broken lines in FIG. 2 .
  • the pressure-sensing section 12 receives the discharge pressure Pd, which has rapidly increased, at the pressure-sensing piston 19 having a larger pressure-receiving area than that of the valve element 25 .
  • the valve lift is increased more promptly, so that the control valve 11 causes the pressure Pc in the crankcase to increase more promptly.
  • the rapidly increased discharge pressure Pd is promptly introduced into the pressure-adjusting chamber 23 via the clearance between the cylinder 17 and the pressure-sensing piston 19 and the clearance between the pressure-sensing piston 19 and the valve seat-forming member 22 , whereby the differential pressure (Pd ⁇ Pd(av)) becomes equal to zero.
  • the function of the pressure-sensing section 12 has been lost.
  • the pressure-sensing section 12 has the function of a derivative element for sensing a rapid increase in the discharge pressure Pd, and temporarily accelerating the motion of the valve section 13 in the valve-opening direction. This enables the control valve 11 to promptly restore the compressor to the predetermined discharge capacity.
  • the control valve 11 operates similarly when the rotational speed of the compressor is rapidly decreased. More specifically, when the rotational speed of the compressor is rapidly decreased, the differential pressure (Pd(av) ⁇ Pd) acting on the pressure-sensing section 12 causes the pressure-sensing piston 19 to move away from the valve section 13 , and hence the urging force of the spring 21 urging the valve element 25 in the valve-opening direction via the pressure-sensing piston 19 and the shaft 24 is weakened, which causes the valve element 25 to move in the valve-closing direction. After all, when the rotational speed of the compressor is rapidly decreased as well, the control valve 11 operates in a quite an opposite way compared with the case of the rotational speed of the compressor being rapidly increased.
  • FIG. 3 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a second embodiment.
  • component elements having functions identical or equivalent to those of the component elements shown in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the shaft 24 of the pressure-sensing section 12 , the valve element 25 of the valve section 13 , and the piston rod 26 are formed integrally with each other, and the spring 21 urging the pressure-sensing piston 19 toward the valve section 13 is eliminated. That is, in the pressure-sensing section 12 and the valve section 13 of this control valve 11 a, the shaft 24 , the valve element 25 , and the piston rod 26 are formed integrally with each other, and the shaft 24 is fixed to the pressure-sensing piston 19 .
  • the control valve 11 a is capable of directly exerting influence of the pressure-sensing section 12 on the valve section 13 in both the cases where the rotational speed of the compressor has rapidly increased and where the same has rapidly decreased. That is, when the rotational speed of the compressor is rapidly increased, the control valve 11 a operates in quite the same way as the control valve 11 according to the first embodiment, but when the rotational speed of the compressor is rapidly decreased, the pressure-sensing piston 19 of the pressure-sensing section 12 is capable of directly actuating the shaft 24 , the valve element 25 , and the piston rod 26 which are integrally formed with each other, in the direction of closing the valve section 13 . Therefore, the control valve 11 a is suitable when the valve-opening characteristic is desired to be made symmetric between when the rotational speed of the compressor is rapidly increased and when the same is rapidly decreased.
  • FIG. 4 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a third embodiment of the present invention.
  • component elements having functions identical or equivalent to those of the component elements shown in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • control valve 11 b in the control valve 11 b according to the third embodiment, comprises flow rate-adjusting means for adjusting the amount of leakage of refrigerant flowing into or out of the pressure-adjusting chamber 23 , at a location between the cylinder 17 of the pressure-sensing section 12 and the pressure-sensing piston 19 and between the pressure-sensing piston 19 and the valve seat-forming member 22 .
  • the pressure-sensing piston 19 and the valve seat-forming member 22 have outer peripheries thereof formed with grooves, respectively, and sealing members 37 and 38 , such as piston rings, are disposed in the respective grooves.
  • the sealing members 37 and 38 have the shape of a C-shaped ring which is circumferentially partially cut out, and is made of a material low in sliding resistance, such as polytetrafluoroethylene.
  • the sealing members 37 and 38 are arranged between the cylinder 17 and the pressure-sensing piston 19 and between the pressure-sensing piston 19 and the valve seat-forming member 22 , and the circumferential length of each of cut-off portions of the members 37 and 38 are adjusted, whereby the flow rate of refrigerant flowing from the high-pressure port 18 into the pressure-adjusting chamber 23 or the flow rate of refrigerant flowing out from the pressure-adjusting chamber 23 to the high-pressure port 18 can be adjusted. This makes it possible to adjust the rise and fall characteristics of the valve lift.
  • FIG. 5 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a fourth embodiment of the present invention.
  • component elements having functions identical or equivalent to those of the component elements shown in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • control valve 11 c As is distinct from the control valves 11 , 11 a, and 11 b according to the first to third embodiments which are configured to sense a rapid change in the discharge pressure Pd for control of the valve lift of the valve section 13 , the control valve 11 c according to the fourth embodiment is configured to sense a rapid change in pressure Pc supplied to the crankcase for control of the valve lift of the valve section 13 .
  • the pressure-sensing section 12 is disposed between the valve section 13 and the solenoid 14 , and the pressure-sensing piston 19 that receives the pressure Pc is fixed to the piston rod 26 integrally formed with the valve element 25 .
  • the pressure-adjusting chamber 23 having an annular shape, which is defined by the first body 15 having the cylinder 17 formed in an end face thereof toward the valve section 13 , and the pressure-sensing piston 19 , there is disposed a spring 39 for urging the piston rod 26 in the valve-opening direction via the pressure-sensing piston 19 against the discharge pressure Pd.
  • the pressure-sensing piston 19 of the pressure-sensing section 12 has a sufficiently larger pressure-receiving area than that of the valve element 25 , a force is generated which causes the pressure-sensing piston 19 to further move in a direction away from the valve section 13 , and the force causes the piston rod 26 fixed to the pressure-sensing piston 19 to act in the valve-opening direction. Therefore, the force of the pressure-sensing piston 19 acting in the valve-opening direction is additionally applied to the valve element 25 , and thereby causes the valve lift to promptly increase, and hence the discharge pressure Pd and the pressure Pc in the crankcase to sharply increase.
  • FIG. 6 is a central longitudinal cross-sectional view schematically showing a control valve for a variable displacement compressor, according to a fifth embodiment of the present invention.
  • component elements having functions identical or equivalent to those of the component elements shown in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • control valves 11 , 11 a, and 11 b according to the first to third embodiments which are configured to sense a rapid change in the discharge pressure Pd for control of the valve lift of the valve section 13
  • control valve 11 c according to the fourth embodiment which is configured to sense a rapid change in pressure Pc supplied to the crankcase for control of the valve lift of the valve section 13
  • control valve 11 d according to the fifth embodiment is configured to sense a rapid change in suction pressure Ps for control of the valve lift of the valve section 13 .
  • the cylinder 17 is formed in an end face, toward the solenoid 14 , of the first body 15 holding the piston rod 26 , and in the cylinder 17 , there is disposed the pressure-sensing piston 19 which is fixed to the piston rod 26 integrally formed with the valve element 25 . Then, in the pressure-adjusting chamber 23 having an annular shape, there is disposed a spring 27 urging the piston rod 26 in the valve-opening direction via the pressure-sensing piston 19 .
  • the force of the pressure-sensing piston 19 acting in the valve-opening direction is additionally applied to the valve element 25 , and thereby causes the valve lift to promptly increase, and hence the pressure Pc in the crankcase to sharply increase, to thereby promptly cause the discharge capacity of the compressor to change in the decreasing direction.
  • the pressure in the pressure-adjusting chamber 23 becomes equal to the suction pressure Ps
  • the discharge pressure Pd, the pressure Pc in the crankcase, the suction pressure Ps, and the valve lift promptly returns to their original states.
  • the control valve 11 c operates promptly, similarly to the above, to thereby make it possible to promptly restore the compressor to the predetermined discharge capacity.
  • FIG. 7 is a central longitudinal cross-sectional view showing a configuration of a control valve for a variable displacement compressor, according to a sixth embodiment of the present invention.
  • component elements having functions identical or equivalent to those of the component elements shown in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the pressure-sensing section 12 senses rapid changes in the discharge pressure Pd in an increasing direction and a decreasing direction for control of the valve lift of the valve section 13
  • the pressure-sensing section 12 sensitively senses a rapid change in the discharge pressure Pd in the increasing direction but insensitively senses a rapid change in the discharge pressure Pd in the decreasing direction for control of the valve lift of the valve section 13 , and a main passage for high-pressure refrigerant does not extend through the pressure-sensing section 12 .
  • the pressure-sensing piston 19 as a component of the pressure-sensing section 12 is provided with a check valve mechanism for switching sensitivity between when a rapid change occurs in the discharge pressure Pd in the increasing direction and when a rapid change occurs in the same in the decreasing direction.
  • the check valve mechanism is formed by forming a passage with a stepped portion in the pressure-sensing piston 19 for communication between the high-pressure port 18 and the pressure-adjusting chamber 23 , and disposing a ball-shaped valve element 40 in a large-diameter passage toward the high-pressure port 18 .
  • the pressure-sensing piston 19 is urged by a leaf spring 42 engaged with the open end of the cylinder-forming member 41 which is formed integrally with the valve seat-forming member 22 in a manner accommodating the pressure-sensing piston 19 , such that the pressure-sensing piston 19 is brought into contact with the shaft 24 that transmits the motion of the pressure-sensing section 12 to the valve element 25 of the valve section 13 .
  • the leaf spring 42 also servers to prevent the valve element 40 of the check valve mechanism from being removed from a large-diameter passage in which it is disposed.
  • the shaft 24 is held by the cylinder-forming member 41 with a predetermined clearance therefrom, in a manner movable axially back and forth.
  • valve hole of the valve seat-forming member 22 directly opens into the high-pressure port 18 .
  • first body 15 has a strainer 43 attached thereto such that the strainer 43 covers the high-pressure port 18 including the pressure-sensing section 12 .
  • the check valve mechanism provided in the pressure-sensing piston 19 is opened by the differential pressure between the rapidly-lowered discharge pressure Pd and pressure in the pressure-adjusting chamber 23 , so that the pressure-sensing piston 19 becomes only little sensitive to a change in the rapidly-lowered discharge pressure Pd.
  • the control valve 11 e has asymmetric valve-opening characteristics that it has a high sensitivity to a rapid change in the discharge pressure Pd in the increasing direction, whereas it has a low sensitivity to a rapid change in the discharge pressure Pd in the decreasing direction. Therefore, e.g.
  • FIG. 8 is an enlarged fragmentary central longitudinal cross-sectional view showing details of essential parts of a control valve for a variable displacement compressor, according to a seventh embodiment of the present invention.
  • component elements identical to those shown in FIG. 7 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the check valve mechanism of the pressure-sensing section 12 is formed using a ball-shaped valve
  • the check valve mechanism of the pressure-sensing section 12 is formed using a poppet valve.
  • the check valve mechanism provided in the pressure-sensing section 12 is formed by disposing a valve element 40 a in the form of a mushroom in a large-diameter passage toward the high-pressure port 18 , which is formed in the pressure-sensing piston 19 such that the passage communicates between the high-pressure port 18 and the pressure-adjusting chamber 23 , and urging the valve element 40 a in the valve-closing direction using a spring 44 which is low in load.
  • the operation of the control valve 11 f including the pressure-sensing section 12 constructed as above, is the same as the operation of the control valve 11 e according to the sixth embodiment.
  • FIG. 9 is an enlarged fragmentary central longitudinal cross-sectional view showing details of essential parts of a control valve for a variable displacement compressor, according to an eighth embodiment of the present invention.
  • FIG. 10 is an enlarged fragmentary central longitudinal cross-sectional view of the control valve according to the eighth embodiment in an operative state in which the discharge pressure of the compressor has rapidly decreased.
  • component elements identical to those shown in FIG. 8 are designated by identical reference numerals, and detailed description thereof is omitted.
  • control valve 11 f As is distinct from the control valve 11 f according to the seventh embodiment in which the check valve mechanism of the pressure-sensing section 12 is formed using a poppet valve, in the control valve 11 g according to the eighth embodiment, the check valve mechanism is formed using a reed valve.
  • the check valve mechanism provided in the pressure-sensing section 12 has a through hole formed through the pressure-sensing piston 19 such that the through hole communicates between the high-pressure port 18 and the pressure-adjusting chamber 23 , and a valve element 40 b is provided such that the valve element 40 b opens and closes the through hole at an end face of the pressure-sensing piston 19 toward the high-pressure port 18 .
  • the valve element 40 b comprises a film-like part which is capable of easily bending in response to the differential pressure between discharge pressure Pd in the high-pressure port 18 and pressure in the pressure-adjusting chamber 23 , and a base part fixed to the pressure-sensing piston 19 , which are integrally formed of rubber or a flexible resin.
  • the valve element 40 b has the base portion thereof fitted in a fixing through hole formed through the pressure-sensing piston 19 , and a portion of the film-like part close to the base part is retained by the leaf spring 42 , whereby the valve element 40 b is fixed to the pressure-sensing piston 19 .
  • the check valve mechanism of the pressure-sensing section 12 is closed as shown in FIG. 9 .
  • the check valve mechanism of the pressure-sensing section 12 is opened by the differential pressure between the discharge pressure Pd and the pressure in the pressure-adjusting chamber 23 , as shown in FIG. 10 .
  • FIG. 11 is an enlarged fragmentary central longitudinal cross-sectional view showing a control valve for a variable displacement compressor, according to a ninth embodiment of the present invention, in states in which the discharge pressure has rapidly increased and in which the discharge pressure has rapidly decreased.
  • component elements identical to those shown in FIGS. 9 and 10 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the control valve 11 h according to the ninth embodiment is distinguished from the control valve 11 g according to the eighth embodiment, in that the check valve mechanism formed using a reed valve is differently configured.
  • the check valve mechanism provided in the pressure-sensing section 12 has a valve hole formed by a gap formed around the outer periphery of the pressure-sensing piston 19 , and a valve element 40 c disposed such that the valve element 40 c blocks the valve hole from an end toward the high-pressure port 18 , with a central portion of the valve element 40 c being held by the leaf spring 42 and the pressure-sensing piston 19 in a sandwiched manner.
  • the valve element 40 c may be formed by a circular film made of rubber or a flexible resin.
  • valve element 40 c of the check valve mechanism When the rotational speed of the compressor is gently being changed, and when the rotational speed of the compressor is rapidly increased to increase the discharge pressure Pd, the valve element 40 c of the check valve mechanism is brought into intimate contact with upper end faces of the pressure-sensing piston 19 and the cylinder in a manner extending over a gap around the outer periphery of the pressure-sensing piston 19 to close the check valve mechanism, as shown in the left half of FIG. 11 .
  • the valve element 40 c of the check valve mechanism is bent upward due to the differential pressure between the discharge pressure Pd and the pressure in the pressure-adjusting chamber 23 , to open the check valve mechanism, as shown in the right half of FIG. 11 .
  • FIG. 12 is an enlarged fragmentary central longitudinal cross-sectional view showing details of essential parts of a control valve for a variable displacement compressor, according to a tenth embodiment of the present invention.
  • component elements identical to those shown in FIG. 11 are designated by identical reference numerals, and detailed description thereof is omitted.
  • control valve 11 i includes a sensitivity-switching mechanism which is capable of switching sensitivity between when the discharge pressure Pd rapidly increases and when the same rapidly decreases.
  • the sensitivity-switching mechanism provided in the pressure-sensing section 12 switches ease of flow of refrigerant flowing into or out of the pressure-adjusting chamber 23
  • the outer peripheral shape of the pressure-sensing piston 19 is formed into a tapered shape in which the outer diameter of the pressure-sensing piston 19 progressively decreases from the side toward the high-pressure port 18 to the pressure-adjusting chamber 23 . Therefore, a gap between the outer periphery of the pressure-sensing piston 19 and the body 15 provides a narrowest restriction at an upper end of the gap, as viewed in FIG. 12 , and is progressively increased in passage cross-sectional area from the restriction to the pressure-adjusting chamber 23 .
  • the pressure-sensing section 12 has a characteristic that insofar as the differential pressure between pressure in the high-pressure port 18 and pressure in the pressure-adjusting chamber 23 is the same, the flow rate of refrigerant is smaller when refrigerant having entered the high-pressure port 18 passes through a restriction after being suddenly restricted in flow than when refrigerant in the pressure-adjusting chamber 23 passes through the restriction after being progressively restricted in flow.
  • a force which the pressure-sensing piston 19 exerts on the valve element 25 of the valve section 13 in the valve-opening direction when the discharge pressure Pd has rapidly increased can be made larger than a force which the pressure-sensing piston 19 exerts on the valve element 25 of the valve section 13 in the valve-closing direction when the discharge pressure Pd has rapidly decreased.
  • the control valve for a variable displacement compressor is configured such that when the compressor undergoes a rapid change in the rotational speed thereof, the pressure-sensing section senses a change in pressure caused by the rapid change in the rotational speed of the compressor and accelerates the motion of the valve section in the valve-opening/closing direction performed in response to the change in pressure.
  • This is advantageous in that the sensitivity of the control valve can be enhanced only when the compressor undergoes a rapid change in the rotational speed thereof.

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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)
US11/205,119 2004-08-19 2005-08-17 Control valve for variable displacement compressor Abandoned US20060039799A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2004-239162 2004-08-19
JP2004239162 2004-08-19
JP2004-289520 2004-10-01
JP2004289520A JP2006083837A (ja) 2004-08-19 2004-10-01 可変容量圧縮機用制御弁

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US11/205,119 Abandoned US20060039799A1 (en) 2004-08-19 2005-08-17 Control valve for variable displacement compressor

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US (1) US20060039799A1 (de)
EP (1) EP1630418B1 (de)
JP (1) JP2006083837A (de)
KR (1) KR20060050535A (de)
DE (1) DE602005002899T2 (de)

Cited By (2)

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US20090246041A1 (en) * 2006-07-19 2009-10-01 Sanden Corporation Displacement control valve of a variable displacement compressor
US20130001450A1 (en) * 2011-01-07 2013-01-03 Tgk Co., Ltd., A Japanese Corporation Control valve for variable displacement compressor

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US9885508B2 (en) 2011-12-28 2018-02-06 Carrier Corporation Discharge pressure calculation from torque in an HVAC system
KR20200013358A (ko) 2018-07-30 2020-02-07 조방훈 비트 제조방법

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Also Published As

Publication number Publication date
DE602005002899D1 (de) 2007-11-29
DE602005002899T2 (de) 2008-02-21
EP1630418A1 (de) 2006-03-01
JP2006083837A (ja) 2006-03-30
EP1630418B1 (de) 2007-10-17
KR20060050535A (ko) 2006-05-19

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