EP1630418A1 - Soupape de contrôle pour un compresseur à capacité variable - Google Patents

Soupape de contrôle pour un compresseur à capacité variable Download PDF

Info

Publication number
EP1630418A1
EP1630418A1 EP05016774A EP05016774A EP1630418A1 EP 1630418 A1 EP1630418 A1 EP 1630418A1 EP 05016774 A EP05016774 A EP 05016774A EP 05016774 A EP05016774 A EP 05016774A EP 1630418 A1 EP1630418 A1 EP 1630418A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
discharge
sensing
sensing piston
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.)
Granted
Application number
EP05016774A
Other languages
German (de)
English (en)
Other versions
EP1630418B1 (fr
Inventor
Hisatoshi Hirota
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.)
TGK Co Ltd
Original Assignee
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
Publication date
Application filed by TGK Co Ltd filed Critical TGK Co Ltd
Publication of EP1630418A1 publication Critical patent/EP1630418A1/fr
Application granted granted Critical
Publication of EP1630418B1 publication Critical patent/EP1630418B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • 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 invention relates to a control valve according to the preamble part of claim 1. More particularly, such a control valve equipped with a variable displacement compressor may be used in a refrigeration cycle of an automotive air conditioner.
  • a wobble plate type variable displacement compressor in the refrigeration cycle of an automotive air conditioner is driven by an engine and is adapted to independently vary the refrigerant compression capacity so as to obtain an adequate cooling capacity without being constrained by the rotational speed of the engine.
  • Pistons are connected to a wobble plate on a shaft driven by the engine.
  • the stroke of the pistons is varied to vary the refrigerant discharge amount.
  • the inclination angle is continuously changed by introducing part of compressed refrigerant into a hermetically closed crankcase, thereby changing the balance of pressures acting on the opposite sides of each piston.
  • a known variable displacement compressor control valve known from JP-2001 132650 A, Fig. 1, corresponding to EP1 098 091 A is disposed either between the discharge chamber and the crankcase, or between the crankcase and a suction chamber.
  • the control valve adjusts the controlled pressure in the crankcase by changing the flow either between the discharge chamber and the crankcase, or between the crankcase and the suction chamber.
  • a valve section is disposed in a refrigerant passage between the discharge chamber and the crankcase.
  • a refrigerant path having an orifice is provided between the suction chamber and the crankcase.
  • a valve element receives discharge pressure Pd in valve-opening direction.
  • a piston rod integrally formed on a rear side of the valve element has approximately the same diameter as the valve seat.
  • An end face of the piston rod receives in valve-closing direction the suction pressure Ps and the load of a solenoid for setting the discharge capacity of the compressor by an external signal.
  • the discharge pressure Pd and the suction pressure Ps load the opposite ends of the valve element and the piston rod on the same effective pressure-receiving areas.
  • the differential pressure (Pd - Ps) causes the valve element to perform a valve opening/closing operation to control the flow rate between the discharge chamber and the crankcase.
  • the pressure-sensing section When only a gradual pressure change is caused by a gentle change of the rotational speed of the engine and the compressor, the pressure-sensing section remains insensitive to the occurring gradual pressure change. The same operation is performed as in the conventional compressor. However, whenever a significant pressure change is caused by a rapid change of the rotational speed of the engine and the compressor, the pressure-sensing section will respond to the pressure change by accelerating the valve motion in valve-opening and/or closing direction, which motion is initiated by the pressure change. The variable displacement compressor promptly starts changing the discharge capacity to thereby promptly restore a predetermined discharge capacity. The pressure sensing section then operates as a pressure change compensating the valve section servo-drive.
  • the pressure-sensing section responds to the pressure change caused by the rapid speed change and accelerates the motion of the valve section in the valve-opening and/or closing direction.
  • the motion per se is performed in response to the pressure change.
  • the response sensitivity of the control valve hence is enhanced only temporarily when the compressor rotational speed changes rapidly.
  • the control valve 11 in Fig. 1 comprises a pressure-sensing section 12 for particularly responding to a rapid change in discharge pressure Pd, a valve section 13 for responding to the value of the differential pressure (Pd - Ps) between the discharge pressure Pd and the suction pressure Ps to control the flow rate between the discharge chamber and the crankcase of a variable displacement compressor (not shown), and a solenoid 14 for setting a predetermined value of the differential pressure (Pd - Ps) which value is to be controlled by the control valve 11.
  • These sections are arranged on the same axis.
  • the pressure-sensing section 12 and the valve section 13 are contained in a first body 15 and in a second body 16 into which the first body 15 is press-fitted.
  • the first body 15 defines a cylinder 17.
  • the open upper cylinder end defines a high-pressure port 18 communicating with the discharge chamber.
  • a pressure-sensing piston 19 is axially movably disposed within the cylinder 17 and is urged in valve opening direction by a spring 21 backed up by a stopper 20.
  • a hollow cylindrical valve seat-forming member 22 is press-fitted into a central hole in the cylinder bottom.
  • valve seat-forming member 22 An upper part of the valve seat-forming member 22 is inserted into a cylinder formed in the centre of the lower end of the pressure-sensing piston 19 such that an annular pressure-adjusting chamber 23 is defined by the first body 15 and the pressure-sensing piston 19.
  • a through hole of the pressure-sensing piston 19 connects the cylinder in the pressure-sensing piston 19 and the high-pressure port 18.
  • the high-pressure port 18 communicates via the through hole of the pressure-sensing piston 19 with an axial passage or valve hole extending through the valve seat-forming member 22.
  • One end of a shaft 24 is fixed to the pressure-sensing piston 19. The shaft 24 extends further through the valve hole in the valve seat-forming member 22.
  • a lower end of the valve seat-forming member 22 forms a valve seat 22a.
  • a valve element 25 is axially movably disposed opposed to the valve seat 22a.
  • the valve element 25 is integral with a piston rod 26.
  • the piston rod 26 is axially movably guided by the second body 16 and has an outer diameter which is equal to the inner diameter of the valve hole.
  • the valve element 25 abuts at the other end of the shaft.
  • the piston rod 26 is urged by a spring 27 in valve opening direction.
  • a space containing the valve element 25 communicates with a medium-pressure port 28 supplying controlled pressure Pc to the crankcase.
  • a space containing the spring 27 communicates with a low-pressure port 29 receiving the suction pressure Ps.
  • a hole is formed in the centre of a lower part of the second body 16.
  • the rim of an opening of a bottomed sleeve 30 is tightly connected to the hole.
  • the bottomed sleeve 30 contains a fixed core 31 and an axially movable plunger 32 of the solenoid 14.
  • 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 fixed to one end of a shaft 33 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 abuts at a lower end face of the piston rod 26. 1.
  • a coil 35 surrounds the bottomed sleeve 30.
  • a harness 36 for supplying electric current to the coil 35 leads to the outside of the solenoid 14.
  • the force of the spring 27 is set larger than the force of the spring 34.
  • the solenoid 14 When the solenoid 14 is de-energized, the valve element 25 is kept away from the valve seat 22a. The valve section 13 is in the fully open state. Discharge pressure Pd at the high-pressure port 18 passes through the valve section 13. Refrigerant flows from the medium-pressure port 28 into the crankcase. The pressure Pc is brought close to the discharge pressure Pd.
  • the compressor operates with minimum discharge capacity.
  • the value of electric current supplied to the solenoid 14 is a maximum as well.
  • the plunger 32 is attracted with maximum attractive force by the core 31.
  • the piston rod 26 is pushed by the shaft 33 in valve-closing direction against the force of the spring 27.
  • the valve element 25 is seated on the valve seat 22a to place the valve section 13 in the fully closed state.
  • the discharge pressure Pd is blocked at the high-pressure port 18 by the closed valve section 13.
  • the pressure Pc is brought close to the suction pressure Ps.
  • the compressor operates with maximum discharge capacity.
  • valve element 25 When the value of the electric current is set to a predetermined value, the valve element 25 is stopped at a valve lift position where the loads of the springs 21 and 27 in valve-opening direction, the solenoid load in valve-closing direction, the force generated by the discharge pressure Pd on the valve element 25 in valve-opening direction, and the force of the suction pressure Ps in valve-closing direction are balanced.
  • the control valve 11 will operate differently when the compressor rotational speed is rapidly changed by a rapid change in the engine rotational speed, e.g. when the automotive vehicle has been rapidly accelerated or decelerated.
  • the compressor first steadily runs at e.g. 800 rpm, before the rotational speed has been rapidly increased to 2000 rpm.
  • the valve lift increases due to a rise of the discharge pressure Pd and a drop of the suction pressure Ps.
  • 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.
  • pressure Pd(av) which is an average pressure derived from the discharge pressure Pd before it has rapidly increased, is maintained.
  • the differential pressure (Pd - Pd(av)) generates a force on the pressure-sensing piston 19 in a direction toward the valve section 13. This force is applied by the shaft 24 to the valve element 25, and hence in addition to the rapidly increased discharge pressure Pd, the differential pressure (Pd - Pd(av)) of the pressure-sensing section 12 is additionally applied to the valve element 25. As a result, as indicated by solid lines in Fig. 2, 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, until the differential pressure (Pd - Pd(av)) becomes zero.
  • the function of the pressure-sensing section 12 is nullified.
  • the pressure-sensing section 12 only has the function of a derivative element for sensing a rapid increase in the discharge pressure Pd, and for temporarily accelerating the motion of the valve section 13 e.g. in valve-opening direction only. This enables the control valve 11 to promptly restore the compressor to the predetermined discharge capacity.
  • the control valve 11 operates similarly but inversely when the compressor rotational speed is rapidly decreased. Then, the differential pressure (Pd(av) - Pd) moves the pressure-sensing piston 19 away from the valve section 13. The urging force of the spring 21 in valve-opening direction via the pressure-sensing piston 19 and the shaft 24 is weakened, which causes the valve element 25 to move in valve-closing direction.
  • any pressure rises or pressure drops are transmitted into or out of the pressure-adjusting chamber 23 in retarded fashion in order to generate a boosting effect on the valve section, but only when the pressure drops or pressure rises originate from rapid compressor speed changes.
  • This effect is caused by flow restricting means in the flow path into or out of the pressure-adjusting chamber 23.
  • the shaft 24 sometimes even may separate from the valve element 25, depending on the setting of the spring 21.
  • the speed of the motion of the valve element 25 in valve-closing direction is slower, so that the valve-opening characteristic of the control valve becomes asymmetric such that the valve opens differently between when the compressor rotational speed is rapidly increased or rapidly decreased.
  • the compressor rotational speed is rapidly increased, if the discharge capacity of the compressor is not promptly decreased, the compressor load applied to the engine becomes more significant for the engine, whereas in the opposite case, even if the compressor discharge capacity is not promptly increased, the compressor load applied to the engine only decreases the vehicle speed, and hence there is no problem even if the valve opening characteristic is asymmetric as mentioned.
  • the pressure-sensing section 12 of the control valve 11a directly exerts influence on the valve section 13 in both cases (compressor rotational speed has rapidly increased or has rapidly decreased).
  • the control valve 11a operates like the control valve 11 of Fig. 1, but when the compressor rotational speed is rapidly decreased, the pressure-sensing piston 19 directly actuates the shaft 24, the valve element 25, and the piston rod 26 in valve closing direction.
  • This control valve 11a is suitable when a symmetric valve-opening characteristic is desired between when the rotational speed of the compressor is rapidly increased and when it is rapidly decreased.
  • the control valve 11b in Fig. 4 (third embodiment) comprises flow rate-adjusting means 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 for adjusting an amount of refrigerant leakage flowing into or out of the pressure-adjusting chamber 23,.
  • Grooves in the peripheries of the pressure-sensing piston 19 and of the valve seat-forming member 22 contain sealing members 37 and 38, such as piston rings.
  • Each of the sealing members 37 and 38 has the shape of a C-shaped ring which is circumferentially partially cut out, and is made of a material having low sliding resistance, such as polytetrafluoroethylene.
  • each cut-off portion of the members 37 and 38 is adjusted to determine the refrigerant flow rate in both directions between the high-pressure port 18 and the pressure-adjusting chamber 23. This setting adjusts the rise and fall characteristics of the valve lift.
  • the control valve 11c in Fig. 5 (fourth embodiment) response to a rapid change of the controlled pressure Pc for controlling the valve lift of the valve section 13.
  • the pressure-sensing section 12 is disposed between the valve section 13 and the solenoid 14.
  • 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 annular pressure-adjusting chamber 23 is defined by the first body cylinder 17 and the pressure-sensing piston 19.
  • a spring 39 urges the piston rod 26 via the pressure-sensing piston 19 in valve-opening direction and against the discharge pressure Pd.
  • the force of the pressure-sensing piston 19 acting in 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.
  • the pressure in the pressure-adjusting chamber 23 becomes equal to the pressure Pc
  • 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 11c operates promptly, similarly to the above, to thereby make it possible to promptly restore the compressor to the predetermined discharge capacity.
  • the control valve 11c of Fig. 6 responds to a rapid change of the suction pressure Ps for controlling the valve lift of the valve section 13.
  • the cylinder 17 of the first body 15 in this case is formed in an end facing toward the solenoid 14.
  • the first body 15 guides the piston rod 26.
  • the pressure-sensing piston 19 which is fixed to the piston rod 26 integrally formed with the valve element 25 is disposed in the cylinder 17.
  • a spring 27 urging the piston rod 26 in valve-opening direction via the pressure-sensing piston 19 is arranged in the annular pressure-adjusting chamber.
  • the force in valve-opening direction is additionally applied to the valve element 25, and 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 to change in 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 return to their original states.
  • the control valve 11c operates promptly, similarly to the above, to promptly restore the compressor to the predetermined discharge capacity.
  • the pressure-sensing section 12 sensitively responds to a rapidly increasing change of the discharge pressure Pd but insensitively responds to a rapidly decreasing change of the discharge pressure Pd.
  • a main passage for high-pressure refrigerant in this case does not extend through the pressure-sensing section 12.
  • the pressure-sensing piston 19 is equipped with a check valve mechanism for switching sensitivity between when a rapidly increasing change of the discharge pressure Pd occurs and when a rapidly decreasing change occurs.
  • the check valve mechanism comprises 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.
  • a ball-shaped valve element 40 is arranged in a large-diameter passage extending toward the high-pressure port 18.
  • the pressure-sensing piston 19 is urged by a leaf spring 42 engaged with the open end of a cylinder-forming member 41 which is integral with the valve seat-forming member 22.
  • the cylinder-forming member 41 accommodates the pressure-sensing piston 19, such that the pressure-sensing piston 19 is in contact with the shaft 24.
  • the leaf spring 42 also serves to prevent that the valve element 40 may fall out.
  • the shaft 24 extends axially movably through the cylinder-forming member 41 with a predetermined clearance.
  • the valve hole of the valve seat-forming member 22 directly opens into the high-pressure port 18.
  • the first body 15 carries a strainer 43 covering the high-pressure port 18 and the pressure-sensing section 12.
  • the check valve mechanism in the pressure-sensing piston 19 When the discharge pressure Pd rapidly increases, the check valve mechanism in the pressure-sensing piston 19 is closed.
  • the pressure-sensing piston 19 having a larger pressure-receiving area than the valve element 25 senses the change of the discharge pressure Pd which has rapidly increased, and causes the valve section 13 to rapidly operate in valve-opening direction, thereby causing the pressure Pc in the crankcase to rise more promptly such that the discharge capacity is promptly controlled in decreasing direction.
  • 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 the pressure in the pressure-adjusting chamber 23, so that the pressure-sensing piston 19 becomes only little sensitive to the change of the rapidly-lowered discharge pressure Pd.
  • the control valve 11e has asymmetric valve-opening characteristics, i.e. high responsiveness to a rapidly increasing change of the discharge pressure Pd, but low responsiveness to a rapidly decreasing change of the discharge pressure Pd. Therefore, e.g.
  • a valve element 40a in the form of a mushroom is arranged in a large-diameter passage in the pressure-sensing piston 19 extending toward the high-pressure port 18.
  • the passage connects the high-pressure port 18 and the pressure-adjusting chamber 23.
  • a spring 44 which has low spring force urges the valve element 40a in valve-closing direction.
  • the check valve mechanism in the control valve 11g of Figs 9 and 10 (eighth embodiment) is designed as a reed valve.
  • the check valve mechanism comprises 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.
  • a valve element 40b is movably arranged such that it opens and closes the through hole at the end of the pressure-sensing piston 19 facing toward the high-pressure port 18.
  • the valve element 40b comprises a film-like part which is easily bent in response to the differential pressure between the discharge pressure Pd and the pressure in the pressure-adjusting chamber 23, and a base part fixed to the pressure-sensing piston 19. Both parts are integrally formed of rubber or a flexible resin.
  • the base part is fitted in a fixing through hole formed through the pressure-sensing piston 19. A portion of the film-like part close to the base part is retained by the leaf spring 42 securing the valve element 40b to the pressure-sensing piston 19.
  • the control valve 11h in Fig. 11 has a check valve mechanism with a differently configured a reed valve.
  • a valve hole is formed by a gap between the outer periphery of the pressure-sensing piston 19 and the inner wall of the cylinder forming part 41 of the member 22.
  • a valve element 40c can block the valve hole at the side of the high-pressure port 18.
  • a central portion of the valve element 40c is sandwiched between the leaf spring 42 and the pressure-sensing piston 19.
  • the valve element 40c may be formed by a circular film made of rubber or a flexible resin.
  • valve element 40c When the compressor rotational speed changes gently only and also when the compressor rotational speed rapidly increases to increase the discharge pressure Pd, the valve element 40c is brought into intimate contact with upper end faces of the pressure-sensing piston 19 and the cylinder forming part 41 to close the valve hole (left half of Fig. 11).
  • the valve element 40c When the compressor rotational speed is rapidly decreased to rapidly decrease the discharge pressure Pd, the valve element 40c is bent upward in an outer edge portion due to the differential pressure between the discharge pressure Pd and the pressure in the pressure-adjusting chamber 23, to clear the valve hole (right half of Fig. 11).
  • the control valve 11i in Fig. 12 includes a sensitivity-switching mechanism for switching the sensitivity or the responsiveness between when the discharge pressure Pd rapidly increases and when it rapidly decreases.
  • the sensitivity-switching mechanism switches ease of a refrigerant flow into or out of the pressure-adjusting chamber 23.
  • the outer periphery of the pressure-sensing piston 19 is tapered such that the outer diameter progressively decreases from the side of the high-pressure port 18 to the side of the pressure-adjusting chamber 23.
  • a gap between the outer periphery of the pressure-sensing piston 19 and the cylinder wall of the cylinder forming part 41 has the narrowest restriction at an upper end of the gap. From there, the gap progressively increases in passage cross-sectional area into 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 the pressure in the pressure-adjusting chamber 23 is the same, the flow rate 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. For the same value of the differential pressure the flow rate into the chamber 23 will be smaller than the flow rate out of the chamber 23.
  • the force of the pressure-sensing piston 19 on the valve element 25 in valve-opening direction when the discharge pressure Pd has rapidly increased can be larger than the force of the pressure-sensing piston 19 on the valve element 25 in valve-closing direction when the discharge pressure Pd has rapidly decreased.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP05016774A 2004-08-19 2005-08-02 Soupape de contrôle pour un compresseur à capacité variable Expired - Fee Related EP1630418B1 (fr)

Applications Claiming Priority (2)

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

Publications (2)

Publication Number Publication Date
EP1630418A1 true EP1630418A1 (fr) 2006-03-01
EP1630418B1 EP1630418B1 (fr) 2007-10-17

Family

ID=35447475

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05016774A Expired - Fee Related EP1630418B1 (fr) 2004-08-19 2005-08-02 Soupape de contrôle pour un compresseur à capacité variable

Country Status (5)

Country Link
US (1) US20060039799A1 (fr)
EP (1) EP1630418B1 (fr)
JP (1) JP2006083837A (fr)
KR (1) KR20060050535A (fr)
DE (1) DE602005002899T2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9885508B2 (en) 2011-12-28 2018-02-06 Carrier Corporation Discharge pressure calculation from torque in an HVAC system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4695032B2 (ja) * 2006-07-19 2011-06-08 サンデン株式会社 可変容量圧縮機の容量制御弁
JP5699259B2 (ja) * 2011-01-07 2015-04-08 株式会社テージーケー 可変容量圧縮機用制御弁
KR20200013358A (ko) 2018-07-30 2020-02-07 조방훈 비트 제조방법

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5071321A (en) * 1989-10-02 1991-12-10 General Motors Corporation Variable displacement refrigerant compressor passive destroker
EP0935107A2 (fr) * 1998-02-06 1999-08-11 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Procédé et dispositif pour régler un compresseur à refoulement variable
EP1098091A2 (fr) 1999-11-05 2001-05-09 TGK Co., Ltd. Régulation du débit d'un compresseur dans un circuit de réfrigération
EP1103721A2 (fr) * 1999-11-25 2001-05-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Dispositif de climatisation et soupape de régulation pour un compresseur à capacité variable

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2672881A (en) * 1950-12-18 1954-03-23 A V Roe Canada Ltd Pressure regulating valve
US2949096A (en) * 1957-09-13 1960-08-16 Gen Dynamics Corp Pneumatic actuator
US3559535A (en) * 1969-01-21 1971-02-02 Patrick W Conolly Hydraulic cylinder with cushioned stroke
JP2567947B2 (ja) * 1989-06-16 1996-12-25 株式会社豊田自動織機製作所 可変容量圧縮機
US5035440A (en) * 1989-08-09 1991-07-30 Chappell International, Inc. Pump
US5129635A (en) * 1990-06-21 1992-07-14 Power Components, Inc. Gas spring with c-shaped seal
JP2588365Y2 (ja) * 1992-06-23 1999-01-06 株式会社ユニシアジェックス 圧力制御弁
JPH08159056A (ja) * 1994-11-30 1996-06-18 Matsushita Electric Ind Co Ltd スクロール圧縮機
US6062497A (en) * 1996-01-19 2000-05-16 Caterpillar Inc. Fuel injector nozzle assembly with improved needle check valve stop mechanism
JP3797055B2 (ja) * 2000-02-07 2006-07-12 株式会社豊田自動織機 可変容量型圧縮機の制御装置
JP3735512B2 (ja) * 2000-05-10 2006-01-18 株式会社豊田自動織機 容量可変型圧縮機の制御弁
JPWO2002101237A1 (ja) * 2001-06-06 2004-09-30 株式会社テージーケー 可変容量圧縮機
JP2004278511A (ja) * 2002-10-23 2004-10-07 Tgk Co Ltd 可変容量圧縮機用制御弁
JP4547332B2 (ja) * 2003-01-22 2010-09-22 株式会社ヴァレオサーマルシステムズ 可変容量圧縮機の制御弁
JP2004251159A (ja) * 2003-02-19 2004-09-09 Sanden Corp 可変容量斜板式圧縮機の制御弁
US6953056B1 (en) * 2003-02-26 2005-10-11 Chrisp Lynn E Metering valve assembly
JP2004293497A (ja) * 2003-03-28 2004-10-21 Tgk Co Ltd 可変容量圧縮機の制御弁
JP4118181B2 (ja) * 2003-03-28 2008-07-16 サンデン株式会社 可変容量斜板式圧縮機の制御弁
JP2006097665A (ja) * 2004-06-28 2006-04-13 Toyota Industries Corp 可変容量型圧縮機における容量制御弁
JP2006029144A (ja) * 2004-07-13 2006-02-02 Sanden Corp 可変容量斜板式圧縮機の容量制御弁

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5071321A (en) * 1989-10-02 1991-12-10 General Motors Corporation Variable displacement refrigerant compressor passive destroker
EP0935107A2 (fr) * 1998-02-06 1999-08-11 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Procédé et dispositif pour régler un compresseur à refoulement variable
EP1098091A2 (fr) 1999-11-05 2001-05-09 TGK Co., Ltd. Régulation du débit d'un compresseur dans un circuit de réfrigération
JP2001132650A (ja) 1999-11-05 2001-05-18 Tgk Co Ltd 冷凍サイクルの圧縮容量制御装置
EP1103721A2 (fr) * 1999-11-25 2001-05-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Dispositif de climatisation et soupape de régulation pour un compresseur à capacité variable

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9885508B2 (en) 2011-12-28 2018-02-06 Carrier Corporation Discharge pressure calculation from torque in an HVAC system
US10619903B2 (en) 2011-12-28 2020-04-14 Carrier Corporation Discharge pressure calculation from torque in an HVAC system

Also Published As

Publication number Publication date
KR20060050535A (ko) 2006-05-19
DE602005002899D1 (de) 2007-11-29
JP2006083837A (ja) 2006-03-30
EP1630418B1 (fr) 2007-10-17
DE602005002899T2 (de) 2008-02-21
US20060039799A1 (en) 2006-02-23

Similar Documents

Publication Publication Date Title
CN110192052B (zh) 容量控制阀
EP1574710B1 (fr) Soupape de contrôle pour un compresseur à capacité variable
EP1605161A2 (fr) Soupape de contrôle pour un compresseur à capacité variable
EP1561948A2 (fr) Soupape de contrôle pour un compresseur à capacité variable
EP1281868B1 (fr) Soupape de contrôle de capacité
JP7139076B2 (ja) 容量制御弁
EP1602828A2 (fr) Soupape de contrôle pour un compresseur à capacité variable
US6302656B1 (en) Solenoid controlled valve and variable displacement compressor
EP1024285A2 (fr) Soupape de contrôle pour compresseur à capacité variable
US20040086391A1 (en) Control valve for variable displacement compressor
KR20060050534A (ko) 가변 용량 압축기용 제어 밸브
EP1512871A1 (fr) Soupape de contrôle pour un compresseur à capacité variable
US7437881B2 (en) Control valve for variable displacement compressor
US20060045758A1 (en) Control valve for variable displacement compressor
EP1630418B1 (fr) Soupape de contrôle pour un compresseur à capacité variable
EP0907021B1 (fr) Soupape de contrôle de déplacement pour utilisation dans un compresseur à capacité variable
KR102634942B1 (ko) 용량 제어 밸브
JP2000320464A (ja) 容量可変型圧縮機用制御弁
EP1808601A2 (fr) Soupape de contrôle pour un compresseur à capacité variable
EP0908624A2 (fr) Soupape de contrÔle de déplacement pour utilisation dans un compresseur à capacité variable
US6036450A (en) Variable capacity vane compressor
CN100436815C (zh) 用于可变容积式压缩机的控制阀
JP7051238B2 (ja) 容量制御弁
KR20220066410A (ko) 용량 제어 밸브

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20060707

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HIROTA, HISATOSHI

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: TGK CO., LTD.

AKX Designation fees paid

Designated state(s): DE FR

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR

REF Corresponds to:

Ref document number: 602005002899

Country of ref document: DE

Date of ref document: 20071129

Kind code of ref document: P

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20080718

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080822

Year of fee payment: 4

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20080926

Year of fee payment: 4

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090831

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100302