EP1835177A2 - Verstellungsregelventil eines verstellbaren Verdichters - Google Patents

Verstellungsregelventil eines verstellbaren Verdichters Download PDF

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Publication number
EP1835177A2
EP1835177A2 EP07104137A EP07104137A EP1835177A2 EP 1835177 A2 EP1835177 A2 EP 1835177A2 EP 07104137 A EP07104137 A EP 07104137A EP 07104137 A EP07104137 A EP 07104137A EP 1835177 A2 EP1835177 A2 EP 1835177A2
Authority
EP
European Patent Office
Prior art keywords
passage
pressure
valve
chamber
valve body
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.)
Withdrawn
Application number
EP07104137A
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English (en)
French (fr)
Inventor
Satoshi Umemura
Masahiro Kawaguchi
Masaki Ota
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.)
Toyota Industries Corp
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Toyota Industries 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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1835177A2 publication Critical patent/EP1835177A2/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • 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

Definitions

  • the present invention relates to a displacement control valve of a variable displacement compressor that controls displacement through adjustment of pressure in a pressure control chamber by supplying refrigerant from a discharge pressure zone to the control pressure chamber through a supply passage and drawing the refrigerant from the control pressure chamber to a suction pressure zone through a discharge passage.
  • the inclination angle of the swash plate is controlled to become smaller as the pressure in the control pressure chamber becomes higher and become greater as the pressure in the control pressure chamber becomes lower.
  • the stroke of pistons connected to the swash plate becomes smaller, thus decreasing the displacement.
  • the stroke of the pistons becomes greater, increasing the displacement.
  • Japanese Laid-Open Patent Publication No. 2003-322086 describes a displacement control valve that adjusts the flow rate of the refrigerant supplied from a discharge pressure zone to a control chamber and the flow rate of the refrigerant discharged from the control chamber to a suction pressure zone.
  • the control chamber of this technique corresponds to a control pressure chamber described herein.
  • the displacement control valve described in Japanese Laid-Open Patent Publication No. 2003-322086 includes a pressure sensing device, an electromagnetic solenoid, and a valve body operated by the electromagnetic solenoid.
  • a detection communication passage, or an open passage communicating with a suction pressure zone, is provided in the valve body.
  • the pressure in the open passage, or suction pressure acts on an engagement portion joined with a bellows of the pressure sensing device.
  • a displacement chamber is defined around the bellows and communicates with the control chamber through a second communication passage.
  • the displacement chamber is connectable to a first communication passage, or a discharge pressure zone, through a valve hole selectively opened and closed by the valve body.
  • the bellows is extended and contracted by control pressure, or the discharge pressure, supplied through the first communication passage and the valve hole or the pressure in a control chamber supplied through a second communication passage.
  • suction pressure of refrigerant flowing from the detection communication passage and the control pressure of the refrigerant flowing from the first communication passage, or the discharge pressure act on the valve body to control the pressure in the control chamber.
  • the refrigerant is supplied to the control chamber in a compressed and high-pressure state. Therefore, as the amount of the refrigerant drawing from the control chamber to the suction pressure zone becomes greater, the operation efficiency of the variable displacement compressor becomes lower. Accordingly, to improve the operation efficiency of the variable displacement compressor, it is desired that the drawing passage that discharges the refrigerant from the control chamber to the suction pressure zone should have a minimum cross-sectional area.
  • variable displacement compressor If the variable displacement compressor is held in a deactivated state for a long time, the refrigerant liquefies and accumulates in the control chamber, or a control pressure chamber. If the variable displacement compressor has a discharge passage with a small cross-sectional area provided externally from the displacement control valve and is activated in the state that the refrigerant liquefies and accumulates in the control chamber, the refrigerant retained in the control chamber in the liquefied state cannot be rapidly drawn to the suction pressure zone. The liquefied refrigerant in the control pressure chamber thus evaporates and excessively increases the pressure in the control pressure chamber. As a result, excessive time is consumed for sufficiently raising the displacement after the compressor is started.
  • a displacement control valve of a variable displacement compressor draws refrigerant from a suction pressure zone and discharges the refrigerant to a discharge pressure zone, and controls displacement according to a pressure in a control pressure chamber.
  • the displacement control valve includes an electromagnetic solenoid, a drive force transmitting body, a pressure sensing portion, an internal passage, an external passage, and first, second, and third valve bodies.
  • the drive force transmitting body is movable along a movement axis, and receives, from the electromagnetic solenoid, a drive force in a drive direction along the movement axis.
  • the pressure sensing portion has a pressure sensing chamber that communicates with the suction pressure zone and a pressure sensing body that receives a pressure in the pressure sensing chamber.
  • the pressure sensing body is urged in the drive direction by the pressure in the pressure sensing chamber.
  • the position of the pressure sensing body in a direction along the movement axis is regulated in accordance with the pressure in the pressure ' sensing chamber.
  • the internal passage is provided in the drive force transmitting body to be connectable to the pressure sensing chamber.
  • the external passage is provided about the drive force transmitting body to be connected to the control pressure chamber.
  • the first valve body is provided at the drive force transmitting body, and adjusts a cross-sectional area of a passage between the external passage and the internal passage.
  • the second valve body is contactable with and separable from the pressure sensing body.
  • the second valve body adjusts a cross-sectional area of a passage between the internal passage and the pressure sensing chamber.
  • the third valve body is provided at the drive force transmitting body, and adjusts a cross-sectional area of a passage between the external passage and the discharge pressure zone.
  • the drive force transmitting body is switched among first, second, and third arrangement states by the electromagnetic solenoid. With the drive force transmitting body at the first arrangement state, the third valve body is at an open position when the first valve body is at a closed position. With the drive force transmitting body at the second arrangement state, the first valve body is at an open position when the third valve body is at a closed position. With the drive force transmitting body at the third arrangement state, both of the first and third valve bodies are at the open position.
  • variable displacement compressor has the displacement control valve described above and a bleed passage.
  • the bleed passage connects the control pressure chamber and the suction pressure zone to each other.
  • a front housing member 12 is joined with the front end of a cylinder block 11.
  • a rear housing member 13 is joined with the rear end of the cylinder block 11 through a valve plate 14, valve flap plates 15, 16, and a retainer plate 17.
  • the cylinder block 11, the front housing member 12, and the rear housing member 13 form the housing of a clutchless type variable displacement compressor 10.
  • a control pressure chamber 121 is defined by the front housing member 12 and the cylinder block 11.
  • a rotary shaft 18 is supported by the front housing member 12 and the cylinder block 11 through radial bearings 19, 20 in such a manner that the rotary shaft 18 rotates about the axis of the rotary shaft 18.
  • the rotary shaft 18 projects from the control pressure chamber 121 to the exterior and rotates when driven by a vehicle engine E, which is an external drive source.
  • a rotation support 21 is secured to the rotary shaft 18 and a swash plate 22 is supported by the rotary shaft 18. In this state, the swash plate 22 is allowed to move and incline along the axial direction of the rotary shaft 18.
  • a couple of guide pins 23, which are fixed to the swash plate 22, are provided in the swash plate 22.
  • the guide pins 23 are movably received in guide bores 211, which are defined in the rotation support 21.
  • the swash plate 22 is allowed to incline with respect to the axis of the rotary shaft 18 and rotate integrally with the rotary shaft 18 through cooperation of the guide bores 211 and the guide pins 23.
  • the swash plate 22 is tilted by the sliding of the guide pins 23 in the guide bores 211 and the sliding of the swash plate 22 on the rotary shaft 18.
  • the inclination angle of the swash plate 22 increases.
  • the inclination angle of the swash plate 22 is at a maximum inclination position.
  • the swash plate 22 is inclined at a maximum inclination angle.
  • the swash plate 22 is inclined at a minimum inclination angle.
  • the minimum inclination angle of the swash plate 22 is set to a value slightly greater than zero degrees.
  • a plurality of cylinder bores 111 are defined in the cylinder block 11. Each bore 111 receives one of a plurality of pistons 24. Rotation of the swash plate 22 is converted to reciprocation of each of the pistons 24 in the axial direction of the rotary shaft 18 through a shoe 25. The pistons 24 reciprocate in the corresponding cylinder bores 111.
  • a suction chamber 131 and a discharge chamber 132 are defined in the rear housing member 13.
  • the control pressure chamber 121 communicates with the suction chamber 131 through a bleed passage 72.
  • Suction ports 141 extend through the valve plate 14, the valve flap plate 16, and the retainer plate 17.
  • Discharge ports 142 extend through the valve plate 14 and the valve flap plate 15.
  • Suction valve flaps 151 are formed in the valve flap plate 15 and discharge valve flaps 161 are formed in the valve flap plate 16.
  • the refrigerant flows from the suction chamber 131, or a suction pressure zone, to the cylinder bore 111 through the suction port 141 while flexing the suction valve flap 151.
  • the piston 24 moves from the bottom dead center to the top dead center (moves from the left to the right as viewed in Fig. 1)
  • the gaseous refrigerant is discharged from the cylinder bore 111 to the discharge chamber 132, or a discharge pressure zone, through the discharge port 142 while flexing the discharge valve flap 161.
  • the opening degree of the discharge valve flap 161 is regulated through contact between the discharge valve flap 161 and a retainer 171 provided on the retainer plate 17.
  • a suction passage 26 that introduces the refrigerant into the suction chamber 131 and a discharge passage 27 that discharges the refrigerant from the discharge chamber 132 are connected together by an external refrigerant circuit 28.
  • the external refrigerant circuit 28 includes a heat exchanger 29 that radiates heat from the refrigerant, an expansion valve 30, and a heat exchanger 31 that transmits the ambient heat to the refrigerant.
  • the expansion valve 30 controls the flow rate of the refrigerant supplied to the heat exchanger 31 in correspondence with variation of the temperature of the refrigerant at an outlet of the heat exchanger 31.
  • a check valve 32 is provided in the discharge passage 27.
  • the check valve 32 has a cylindrical valve housing 33, a cylindrical valve body 34, a cylindrical spring seat 35, and a compression spring 36.
  • the valve body 34 is slidably received in the valve housing 33.
  • the spring seat 35 is fixed in the valve housing 33.
  • the compression spring 36 is arranged between the spring seat 35 and the valve body 34.
  • a valve hole 331 is defined in an end wall of the valve housing 33.
  • the valve body 34 is movable between a seated position and an open position. When located at the seated position, the valve body 34 contacts the end wall of the valve housing 33 and closes the valve hole 331. When located at the open position, the valve body 34 is separated from the end wall of the valve housing 33 and opens the valve hole 331.
  • the compression spring 36 urges the valve body 34 toward the seated position at which the valve hole 331 is closed.
  • An outlet port 332 is defined in the circumferential wall of the valve housing 33.
  • An electromagnetic type displacement control valve 37 is incorporated in the rear housing member 13.
  • a fixed iron core 39 of an electromagnetic solenoid 38 of the displacement control valve 37 attracts a movable iron core 41 in correspondence with excitement by a current supply to a coil 40.
  • An urging spring 42 is provided between the fixed iron core 39 and the movable iron core 41.
  • the movable iron core 41 is urged by the urging force of the urging spring 42 to separate from the fixed iron core 39.
  • the electromagnetic solenoid 38 is subjected to current supply control (in the illustrated embodiment, duty ratio control) by a control computer C (shown in Fig. 1).
  • a drive rod 43 is secured to the movable iron core 41.
  • a partition wall 45 is fixed to a cylindrical housing 44 of the displacement control valve 37.
  • the partition wall 45 divides the interior of the housing 44 to a chamber 46 and a pressure sensing chamber 47.
  • a valve assembly 48 is provided in the chamber 46.
  • a pressure sensing mechanism 49 is arranged in the pressure sensing chamber 47.
  • the chamber 46 communicates with the control pressure chamber 121 through a passage 65.
  • the pressure sensing chamber 47 communicates with the suction chamber 131 through a passage 66.
  • a valve seat plate 54 is fixed in the housing 44 to close the chamber 46.
  • a distal portion of the drive rod 43 extends through the valve seat plate 54 and projects into the chamber 46.
  • a lid 59 is fixed in the housing 44 to close the pressure sensing chamber 47.
  • the valve assembly 48 has a shaft body 50 extending through the partition wall 45 and a cylindrical body 51 fixed to the shaft body 50 in the chamber 46.
  • a shaft passage 501 is defined in the shaft body 50 and extends in the movement direction of the drive rod 43.
  • the distal portion of the drive rod 43 is secured to the shaft body 50 and extends along the shaft passage 501.
  • the drive rod 43 and the valve assembly 48 form a drive force transmitting body 61, which is driven by the electromagnetic force generated by the electromagnetic solenoid 38.
  • the direction in which the drive force transmitting body 61 is driven that is, the direction in which the drive force transmitting body 61 is urged or moved by electromagnetic force of the electromagnetic solenoid 38, will hereafter be referred to as a drive direction of the drive force transmitting body 61.
  • the drive direction is directed from the chamber 46 toward the pressure sensing chamber 47.
  • the drive direction agrees with the direction of drive force that is applied to the electromagnetic solenoid 38 by the drive force transmitting body 61.
  • the drive force transmitting body 61 is movable along a movement axis in the drive direction and a direction opposite to the drive direction.
  • a valve hole 52 is defined in the partition wall 45 and extends in the movement direction of the drive rod 43.
  • the shaft body 50 is received in the valve hole 52 movably along the movement direction of the drive rod 43.
  • a distal portion of the shaft body 50 projects into the pressure sensing chamber 47, thus allowing communication between the shaft passage 501 and the pressure sensing chamber 47.
  • a communication port 502 is defined in the circumferential surface of the shaft body 50 in the cylindrical body 51 and communicates with the shaft passage 501.
  • the shaft passage 501 communicates with the interior of the cylindrical body 51 through the communication port 502.
  • the shaft passage 501 and the communication port 502 form an internal passage that is defined in the drive force transmitting body 61 in such a manner as to communicate with the pressure sensing chamber 47.
  • the chamber 46 is an external passage provided externally from the drive force transmitting body 61 in such a manner as to communicate with the control pressure chamber 121.
  • the cylindrical body 51 which is fixed to the shaft body 50, is urged by the urging force of the urging spring 53 in a direction opposite to.the acting direction of the electromagnetic force produced by the electromagnetic solenoid 38.
  • a valve body 62 capable of contacting and separating from a seat surface 541 of the valve seat plate 54 is provided at an end of the cylindrical body 51 corresponding to the electromagnetic solenoid 38.
  • the valve body 62 will be referred to as a first valve body 62.
  • the first valve body 62 When the first valve body 62 is arranged at a closed position at which the first valve body 62 contacts the seat surface 541, the communication between the shaft passage 501 and the chamber 46 is blocked. In other words, the first valve body 62 is arranged in the drive force transmitting body 61 to adjust the cross-sectional area of a passage extending between the external passage and the internal passage.
  • the pressure sensing mechanism 49 has a bellows 55, a plate-like pressure receiving body 56 joined with the bellows 55, and urging springs 57, 58.
  • the urging spring 57 urges the pressure receiving body 56 toward the shaft body 50.
  • the urging spring 58 urges the pressure receiving body 56 separately from the shaft body 50.
  • a chamber 60 defined in the bellows 55 is under vacuum.
  • the chamber 60 accommodates a stopper 591 extending from the lid 59 and a stopper 561 extending from the pressure receiving body 56.
  • the stoppers 591, 561 are capable of contacting and separating from each other.
  • the stoppers 591, 561 determine the minimum length of the bellows 55, which extends and contracts.
  • the pressure sensing mechanism 49, the pressure sensing chamber 47, and the chamber 60 form a pressure sensing portion.
  • the pressure receiving body 56 of the pressure sensing mechanism 49 is urged by the pressure in the pressure sensing chamber 47 in the direction in which the drive force transmitting body 61 is driven.
  • the position of the pressure receiving body 56 in the movement direction of the drive force transmitting body 61 is regulated in correspondence with the pressure in the pressure sensing chamber 47.
  • the bellows 55 and the pressure receiving body 56 form a pressure sensing body the position of which in the movement direction of the drive force transmitting body 61 is regulated in correspondence with the pressure in the pressure sensing chamber 47.
  • a valve body 63 capable of contacting and separating from the pressure receiving body 56 is formed in the distal portion of the shaft body 50.
  • the valve body 63 will be referred to as a second valve body 63.
  • the second valve body 63 is capable of contacting and separating from the pressure receiving body 56 and provided in the drive force transmitting body 61 to adjust the cross-sectional area of a passage between the internal passage and the pressure sensing chamber 47.
  • the pressure receiving area of the pressure sensing body in the drive direction of the drive force transmitting body 61, or the pressure receiving area for receiving the pressure in the pressure sensing chamber 47, is greater than the closed area S (see Fig. 4) of the second valve body 63.
  • the closed area S becomes equal to the pressure receiving area of the pressure receiving body 56 for receiving the pressure in the shaft passage 501.
  • a third valve body 64 is formed in the circumferential surface of the shaft body 50 in the chamber 46.
  • the third valve body 64 contacts and separates from a seat surface 451 of the partition wall 45.
  • An annular groove 503 is defined in the circumferential surface of the shaft body 50 between the third valve body 64 and the second valve body 63.
  • the annular groove 503 communicates with the valve hole 52 and with the discharge chamber 132 through a passage 67.
  • the annular groove 503 is a groove passage communicating with the discharge chamber 132 (the discharge pressure zone) and the valve hole 52 at a position between the second valve body 63 and the third valve body 64.
  • the third valve body 64 When the third valve body 64 is located at a closed position contacting the seat surface 451, the communication between the annular groove 503 and the chamber 46 is blocked.
  • the third valve body 64 is provided in the drive force transmitting body 61 to adjust the cross-sectional area of a passage extending between the external passage and the discharge chamber 132.
  • the passage 67, the annular groove 503, the chamber 46, and the passage 65 form a supply passage by which the refrigerant is supplied from the discharge chamber 132 to the control pressure chamber 121.
  • the passage 65, the chamber 46, the communication port 502, the shaft passage 501, the pressure sensing chamber 47, and the passage 66 form a drawing passage by which the refrigerant is discharged from the control pressure chamber 121 to the suction chamber 131.
  • the control computer C which executes the current supply control (duty ratio control) to the electromagnetic solenoid 38 of the displacement control valve 37, permits the current supply to the electromagnetic solenoid 38 when an air conditioner switch 68 is turned on. When the air conditioner switch 68 is turned off, the control computer C stops the current supply.
  • the control computer C receives signals from a compartment temperature setting device 69 and a compartment temperature detection device 70. When the air conditioner switch 68 is held in a turned-on state, the control computer C controls the current supplied to the electromagnetic solenoid 38 in correspondence with the difference between a target temperature set through the compartment temperature setting device 69 and a detected temperature provided by the compartment temperature detection device 70. In the illustrated embodiment, the control computer C adjusts the duty ratio of the current supplied to the electromagnetic solenoid 38 in correspondence with the difference between the target temperature set through the compartment temperature setting device 69 and the detected temperature provided by the compartment temperature detection device 70.
  • variable displacement compressor operates with minimum displacement, or the current supply to the electromagnetic solenoid 38 is stopped (the duty ration is 0%), with the vehicle engine E running, the first valve body 62 is urged by the urging forces of the urging springs 53, 42 to reach the closed position at which the first valve body 62 contacts the seat surface 541, with reference to Fig. 4. In this state, the third valve body 64 is located at the open position spaced from the seat surface 451.
  • the operational state of the variable displacement compressor with the minimum. displacement will be referred to as a minimum displacement operational state.
  • the drive force transmitting body 61 when the first valve body 62 is at the closed position, the drive force transmitting body 61 is held in a first arrangement state in which the third valve body 64 is located at the open position when the first valve body 62 is at the closed position.
  • the drive force transmitting body 61 is maintained in the first arrangement state, the refrigerant is sent from the discharge chamber 132 to the control pressure chamber 121. In this state, as indicated by the chain lines of Fig. 1, the inclination angle of the swash plate 22 becomes minimized.
  • variable displacement compressor 10 When the variable displacement compressor 10 is started by turning on the air conditioner switch 68, the duty ratio of the current supplied to the electromagnetic solenoid 38 is controlled to become 100%. This control state is continued for a predetermined time (for example, several minutes) after the variable displacement compressor 10 is started.
  • the third valve body 64 is located at the closed position at which the third valve body 64 contacts the seat surface 451 against the urging forces of the urging springs 53, 42.
  • the first valve body 62 is arranged at the open position spaced from the seat surface 541.
  • the drive force transmitting body 61 is held in a second arrangement state in which the third valve body 64 is held at the closed position and the first valve body 62 is located at the open position.
  • the refrigerant flows from the control pressure chamber 121 to the suction chamber 131 through the chamber 46, the shaft passage 501, and the pressure sensing chamber 47.
  • the refrigerant does not flow from the discharge chamber 132 to the control pressure chamber 121. This decreases the pressure in the control pressure chamber 121, or control pressure.
  • the inclination angle of the swash plate 22 switches from the minimum value to the maximum value.
  • liquid refrigerant may retain in the control pressure chamber 121.
  • the liquid refrigerant is rapidly drained from the control pressure chamber 121 to the suction chamber 131 through the drawing passage. This prevents foaming of the liquid refrigerant from hampering restoration of the inclination angle of the swash plate 22 from the minimum inclination angle to the maximum inclination angle.
  • the swash plate 22 is allowed to quickly incline from the minimum inclination angle to the maximum inclination angle.
  • the discharge pressure gradually rises.
  • the pressure upstream from the check valve 32 in the discharge passage 27 thus exceeds the sum of the pressure downstream from the check valve 32 and the urging force of the compression spring 36.
  • the valve hole 331 opens to send the refrigerant from the discharge chamber 132 to the external refrigerant circuit 28. That is, circulation of the refrigerant in the external refrigerant circuit 28 is brought about, thus reducing thermal load.
  • Fig. 3 illustrates an example of such control in a state of 0 ⁇ (duty ratio) ⁇ 100%.
  • the first valve body 62 is arranged at the open position spaced from the seat surface 541 and the third valve body 64 is located at the open position spaced from the seat surface 451.
  • the drive force transmitting body 61 is held in a third arrangement state in which the first and third valve bodies 62, 64 are held at the respective open positions, the refrigerant flows from the discharge chamber 132 to the control pressure chamber 121 through the chamber 46.
  • the pressure receiving body 56 contacts and spaces from the second valve body 63 in correspondence with variation of the pressure in the pressure sensing chamber 47, or the suction pressure. In this manner, the suction pressure is controlled to become a target suction pressure that is set in accordance with the duty ratio of the current supplied to the electromagnetic solenoid 38.
  • the pressure receiving body 56 and the second valve body 63 are not constantly held in a separated state.
  • the amount of the refrigerant drawn from the control pressure chamber 121 to the suction chamber 131 thus does not increase excessively.
  • the operation efficiency of the variable displacement compressor 10 in variable displacement control is thus prevented from lowering.
  • the illustrated embodiment has the following advantages.
  • the pressure sensing chamber 47 which forms the pressure sensing portion of the present invention, communicates with the suction chamber 131, or the suction pressure zone. Therefore, even if the control pressure rapidly rises, the stoppers 561, 591 provided in the bellows 55 are prevented from striking each other, and the pressure sensing device is prevented from being damaged. Also, durability of the bellows 55 may be improved due to suppressed vibration of the bellows 55.
  • a third valve body 64A, a first valve body 62, and a second valve body 63 may be arranged sequentially in this order from the side corresponding to the electromagnetic solenoid 38 to the side corresponding to the pressure sensing portion.
  • a chamber 71 accommodating the third valve body 64A communicates with a discharge chamber 132.
  • a valve hole 543 is defined in a valve seat plate 54 in such a manner as to communicate with a chamber 46.
  • the third valve body 64A contacts and separates from a seat surface 542 of the valve seat plate 54, thus permitting and blocking communication between the chamber 71 and the valve hole 543.
  • the bleed passage 72 may be omitted.
  • the drawing passage is the sole passage to connect the control pressure chamber 121 and the suction chamber 131.
  • a pressure sensing portion provided with a pressure sensing body having a diaphragm may be used.
  • a pressure sensing portion using a piston type movable wall as a pressure sensing body may be employed.
  • a displacement control valve includes an electromagnetic solenoid and a drive force transmitting body.
  • a pressure sensing chamber communicates with a suction chamber and a pressure sensing body is located in the pressure sensing chamber.
  • An internal passage is provided in the transmitting body and an external passage is provided about the transmitting body.
  • the first to third valve bodies are provided at the transmitting body.
  • the first valve body adjusts a cross-sectional area of a passage between the external passage and the internal passage.
  • the second valve body adjusts a cross-sectional area of a passage between the internal passage and the pressure sensing chamber.
  • the third valve body adjusts a cross-sectional area of a passage between the external passage and a discharge chamber.
  • the transmitting body is switched among first, second, and third arrangement states by the electromagnetic solenoid.
  • the third valve body is at an open position when the first valve body is at a closed position.
  • the first valve body is at an open position when the third valve body is at a closed position.
  • both of the first and third valve bodies are at the open position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Magnetically Actuated Valves (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP07104137A 2006-03-15 2007-03-14 Verstellungsregelventil eines verstellbaren Verdichters Withdrawn EP1835177A2 (de)

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WO2021241477A1 (ja) * 2020-05-25 2021-12-02 イーグル工業株式会社 容量制御弁
WO2021241478A1 (ja) * 2020-05-25 2021-12-02 イーグル工業株式会社 容量制御弁
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