US20050287014A1 - Displacement control valve for variable displacement compressor - Google Patents
Displacement control valve for variable displacement compressor Download PDFInfo
- Publication number
- US20050287014A1 US20050287014A1 US11/167,708 US16770805A US2005287014A1 US 20050287014 A1 US20050287014 A1 US 20050287014A1 US 16770805 A US16770805 A US 16770805A US 2005287014 A1 US2005287014 A1 US 2005287014A1
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- United States
- Prior art keywords
- valve
- valve hole
- valve body
- hole
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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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
- 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
Landscapes
- 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)
- Magnetically Actuated Valves (AREA)
Abstract
A displacement control valve for a variable displacement compressor includes a first valve hole forming a part of a supply passage and a second valve hole forming a part of a discharge passage. Displacement of a reciprocating body is transmitted to each of first and second valve bodies so that each valve body opens or closes the corresponding valve hole. When the reciprocating body is within a predetermined displacement range, a double closing state occurs, in which the first valve body closes the first valve hole and the second valve hole closes the second valve hole. When the reciprocating body is out of the displacement range, a single closing state occurs. Therefore, the control valve prevents the first valve hole from opening concurrently with the second valve hole.
Description
- The present invention relates to a displacement control valve employed for a variable displacement compressor, which valve supplies refrigerant from a discharge pressure zone to a control pressure chamber and discharges refrigerant from the control pressure chamber to a suction pressure zone, thereby controlling the pressure in the control pressure chamber, and changing the displacement of the compressor, accordingly.
- In a variable displacement compressor having a control pressure chamber for accommodating a tiltable swash plate, the inclination angle of the swash plate is reduced as the pressure in the control pressure chamber is increased, and increased as the control chamber pressure is reduced. When the inclination angle of the swash plate is reduced, the stroke of pistons is reduced, which decreases the displacement. When the inclination angle of the swash plate is increased, the piston stroke is increased, which increases the displacement.
- Japanese Laid-Open Patent Publication No. 2000-249050 discloses a displacement control valve having a first valve body and a second valve body. The first valve body selectively opens and closes a supply passage for supplying refrigerant from a discharge pressure zone to a crank chamber (control pressure chamber). The second valve body selectively opens and closes a discharge passage for discharging refrigerant from the crank chamber to a suction pressure zone. The displacement control valve includes a single solenoid and a pressure sensing member senses suction pressure and actuates the first valve body. The solenoid includes a plunger. The pressure sensing member is coupled to a first rod, which is fixed to the plunger. The first valve body receives urging force from the pressure sensing member in a direction opening a first valve hole, which is a part of the supply passage. The second valve body receives discharge pressure in a direction closing a second valve hole, which is a part of the discharge passage. A second rod is fixed to the first valve body. When the first valve body moves from a position for opening the first valve hole toward a position for closing the first valve hole, the second rod is moved in a direction to move the second valve body from a position closer to a position for closing the second valve hole toward a position for opening the second valve hole. The first valve hole is formed in a movable valve seat. The first valve body, the movable valve seat, and the second rod are movable with the first valve hole closed.
- The displacement control valve is configured such that a state in which the first valve body is in the position for opening the first valve hole does not concurrently occurs with a state in which the second valve body is in the position for opening the second valve hole (refer to
FIG. 4 of the above mentioned publication). That is, when the second valve body opens the second valve hole, the first valve body closes the first valve hole, and when the first valve body opens the first valve hole, the second valve body closes the second valve hole. A configuration in which the first valve hole and the second valve hole are not simultaneously opened, the suction pressure is stabilized at a target suction pressure when the electromagnetic force of the solenoid is adjusted to correspond to the target suction pressure. That is, the target suction pressure is set accurately. - In the displacement control valve disclosed in the above mentioned publication, when the first valve body closes the first valve hole, the second valve body opens the second valve hole, and when the second valve body closes the second valve hole, the first valve body opens the first valve hole. That is, a state in which the first valve body is located in the position for closing the first valve hole and the second valve body is located in the position for closing the second valve hole occurs only when the second rod is at a specific position (a position of the second rod when the first valve body contacts the movable valve seat, and the movable valve seat contacts a valve seat defining portion). However, due to dimensional errors and assembly errors of the components of the displacement control valve, it is difficult to configure the valve such that, only when the second rod is at the specific position, the first valve body closes the first valve hole and the second valve body closes the second valve hole. That is, it is possible that the first and second valve open simultaneously. When opening simultaneously, the first and second valve holes increase the flow rate of refrigerant that wastefully flows from the discharge pressure zone to the suction pressure zone through the control pressure chamber. This reduces the efficiency of the compressor.
- Accordingly, it is an objective of the present invention to provide a displacement control valve for a variable displacement compressor, which valve prevents a valve hole that is a part of a supply passage from opening concurrently with a valve hole that is a part of a discharge passage.
- To achieve the above-mentioned objective, the present invention provides a displacement control valve for a variable displacement compressor. The compressor has a discharge pressure zone exposed to the pressure of refrigerant that has been compressed by the compressor; a suction pressure zone exposed to the pressure of refrigerant that is drawn into the compressor; a control pressure chamber; a supply passage that connects the discharge pressure zone to the control pressure chamber; and a discharge passage that connects the suction pressure zone to the control pressure chamber. The control valve adjusts the pressure of the control pressure chamber by supplying refrigerant in the discharge pressure zone to the control pressure chamber through the supply passage and discharging refrigerant in the control pressure chamber to the suction pressure zone through the discharge passage, thereby controlling the displacement of the compressor. The control valve includes a first valve hole forming a part of the supply passage; a first valve body that selectively opens and closes the first valve hole; a second valve hole forming a part of the discharge passage; a second valve body that selectively opens and closes the second valve hole; and a reciprocating body that is capable of being displaced and reciprocated. Displacement of the reciprocating body is transmitted to each of the first and second valve bodies so that each valve body opens or closes the corresponding valve hole. When the reciprocating body is within a predetermined displacement range, a double closing state occurs, in which the first valve body closes the first valve hole and the second valve hole closes the second valve hole. When the reciprocating body is out of the displacement range, a single closing state occurs, in which only one of the first valve body and the second valve body closes the corresponding one of the valve holes.
- Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
- The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
-
FIG. 1 is a side cross-sectional view illustrating an entire compressor according a first embodiment of the present invention; -
FIG. 2 (a) is a cross-sectional view illustrating a displacement control valve incorporated in the compressor shown inFIG. 1 ; - FIGS. 2(b) and 2(c) arc enlarged partial cross-sectional views of the control valve shown in
FIG. 2 (a); - FIGS. 3(a) to 3(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 2 (a); -
FIG. 4 (a) is a cross-sectional view illustrating a displacement control valve according to a second embodiment of the present invention; -
FIG. 4 (b) is an enlarged partial cross-sectional view of the control valve shown inFIG. 4 (a); -
FIG. 5 (a) is a cross-sectional view illustrating a displacement control valve according to a third embodiment; - FIGS. 5(b) and 5(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 5 (a); - FIGS. 6(a) to 6(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 5 (a); -
FIG. 7 is an enlarged partial cross-sectional view illustrating a control valve according to a fourth embodiment; - FIGS. 8(a) and 8(b) are enlarged partial cross-sectional views illustrating a control valve according to a fifth embodiment;
-
FIG. 9 (a) is a cross-sectional view illustrating a displacement control valve according to a sixth embodiment; - FIGS. 9(b) and 9(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 9 (a); - FIGS. 10(a) to 10(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 9 (a); -
FIG. 11 (a) is a cross-sectional view illustrating a displacement control valve according to a seventh embodiment; -
FIG. 11 (b) is an enlarged partial cross-sectional view ofFIG. 11 (a); -
FIG. 12 (a) is a cross-sectional view illustrating a displacement control valve according to an eighth embodiment; - FIGS. 12(b) and 12(c) are enlarged partial cross-sectional views of
FIG. 12 (a); - FIGS. 13(a) to 13(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 12 (a); -
FIG. 14 (a) is a cross-sectional view illustrating a displacement control valve according to a ninth embodiment; -
FIG. 14 (b) is an enlarged partial cross-sectional view ofFIG. 14 (a); -
FIG. 15 (a) is a cross-sectional view illustrating a displacement control valve according to a tenth embodiment; -
FIG. 15 (b) is an enlarged partial cross-sectional view ofFIG. 15 (a); -
FIG. 16 (a) is a cross-sectional view illustrating a displacement control valve according to an eleventh embodiment; - FIGS. 16(b) and 16(c) are enlarged partial cross-sectional views of
FIG. 16 (a); - FIGS. 17(a), 17(b), and 17(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 16 (a); -
FIG. 18 (a) is a cross-sectional view illustrating a displacement control valve according to a twelfth embodiment; -
FIG. 18 (b) is an enlarged partial cross-sectional view ofFIG. 18 (a); -
FIG. 19 (a) is a cross-sectional view illustrating a displacement control valve according to a thirteenth embodiment; - FIGS. 19(b) and 19(c) are enlarged partial cross-sectional views of
FIG. 19 (a); - FIGS. 20(a), 20(b), and 20(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 19 (a); -
FIG. 21 is an enlarged cross-sectional view illustrating a fourteenth embodiment; -
FIG. 22 (a) is a cross-sectional view illustrating a displacement control valve according to a fifteenth embodiment; -
FIG. 22 (b) is an enlarged partial cross-sectional view ofFIG. 22 (a); -
FIG. 23 is an enlarged partial cross-sectional view illustrating a control valve according to another embodiment; -
FIG. 24 is an enlarged partial cross-sectional view illustrating a control valve according to another embodiment; -
FIG. 25 is an enlarged partial cross-sectional view illustrating a control valve according to another embodiment; -
FIG. 26 is an enlarged partial cross-sectional view illustrating a control valve according to another embodiment; -
FIG. 27 (a) is a cross-sectional view illustrating a displacement control valve according to a sixteenth embodiment; - FIGS. 27(b) and 27(c) are enlarged partial cross-sectional views of
FIG. 27 (a); -
FIG. 27 (d) is a graph showing the spring characteristics of first and second urging springs; - FIGS. 28(a), 28(b), and 28(c) are enlarged partial cross-sectional views of the control valve shown in
FIG. 27 (a); -
FIG. 29 (a) is a cross-sectional view illustrating a displacement control valve according to a seventeenth embodiment; - FIGS. 29(b) and 29(c) are enlarged partial cross-sectional views of
FIG. 29 (a); -
FIG. 30 (a) is a cross-sectional view illustrating a displacement control valve according to an eighteenth embodiment; - FIGS. 30(b) and 30(c) are enlarged partial cross-sectional views of
FIG. 30 (a); -
FIG. 31 (a) is a cross-sectional view illustrating a displacement control valve according to a nineteenth embodiment; - FIGS. 31(b) and 31(c) are enlarged partial cross-sectional views of
FIG. 31 (a); -
FIG. 32 is a diagram for explaining the relationship of pressure loads acting on thetransmission rod 45 ofFIG. 21 (a); -
FIG. 33 (a) is an enlarged partial cross-sectional view illustrating a twentieth embodiment; and -
FIG. 33 (b) is a diagram for explaining the relationship of pressure loads acting on thetransmission rod 45 ofFIG. 33 (a). - A first embodiment of the present invention will now be described with reference to FIGS. 1 to 3(c).
- As shown in
FIG. 1 , afront housing member 12 is secured to the front end of acylinder block 11. Arear housing member 13 is secured to the rear end of thecylinder block 11 with avalve plate 14,valve flap plates 15, 16, and a retainer plate 17 arranged in between. Thecylinder block 11, thefront housing member 12, and therear housing member 13 form a housing of thecompressor 10. - The
front housing member 12 and thecylinder block 11 define acontrol pressure chamber 121. Thefront housing member 12 and thecylinder block 11 rotatably support arotary shaft 18 withradial bearings 19, 20. Therotary shaft 18 projects from thecontrol pressure chamber 121 to the outside, and receives power from a vehicle engine E, which is an external power source, through an electromagnetic clutch (not shown). - A rotary support 21 is fixed to the
rotary shaft 18, and aswash plate 22 is supported on therotary shaft 18. Theswash plate 22 is permitted to incline with respect to and slide along therotary shaft 18. A pair of guide holes 211 are formed in the rotary support 21, and a pair of guide pins 23 are formed on theswash plate 22. The guide pins 23 are slidably fitted in the guide holes 211. The engagement of the guide pins 23 with the guide holes 211 allows theswash plate 22 to be tiltable with respect to therotary shaft 18 and rotatable together with therotary shaft 18. The guide holes 211 slidably guide the guide pins 23, and therotary shaft 18 slidably supports theswash plate 22. These actions permit theswash plate 22 to be inclined. - When the center of the
swash plate 22 moves toward the rotary support 21, the inclination of theswash plate 22 increases. When contacting theswash plate 22, the rotary support 21 determines the maximum inclination of theswash plate 22. When in a position indicated by solid lines inFIG. 1 , theswash plate 22 is at the maximum inclination position. When in a position indicated by chain lines, theswash plate 22 is at the minimum inclination position. The minimum inclination angle of theswash plate 22 is slightly greater than zero degrees. - Cylinder bores 111 extend through the
cylinder block 11. Each cylinder bore 111 accommodates apiston 24. The rotation of theswash plate 22 is converted to reciprocation of thepistons 24 by means ofshoes 25. Thus, eachpiston 24 reciprocates in the corresponding cylinder bore 111. - A
suction chamber 131 and adischarge chamber 132 are defined in therear housing member 13. Suction ports 141 are formed in avalve plate 14 and avalve flap plate 16.Discharge ports 142 are formed in thevalve plate 14 and a valve flap plate 15. Suction valve flaps 151 are formed on the valve flap plate 15, and discharge valve flaps 161 are formed on thevalve flap plate 16. As eachpiston 24 moves from the top dead center to the bottom dead center (from the right side to the left side inFIG. 1 ), refrigerant in thesuction chamber 131, which is a suction pressure zone, is drawn into the associated cylinder bore 111 through the corresponding suction port 141 while flexing thesuction valve flap 151. When eachpiston 24 moves front the bottom dead center to the top dead center (from the left side to the right side inFIG. 1 ), gaseous refrigerant in the corresponding cylinder bore 111 is discharged to thedischarge chamber 132, which is a discharge pressure zone, through thecorresponding discharge port 142 while flexing thedischarge valve flap 161. The retainer plate 17 includes retainers 171, which correspond to thedischarge valves 161. Each retainer 171 restricts the opening degree of the correspondingdischarge valve flap 161. - A
suction passage 26 for guiding refrigerant into thesuction chamber 131 and adischarge passage 27 for discharging refrigerant from thedischarge chamber 132 are connected to each other by an externalrefrigerant circuit 28. Aheat exchanger 29 for drawing heat from refrigerant, anexpansion valve 30, and aheat exchanger 31 for transferring the ambient heat to refrigerant are located on the externalrefrigerant circuit 28. Theexpansion valve 30 is an automatic thermal expansion valve that controls the flow rate of refrigerant in accordance with fluctuations of gas temperature at the outlet of theheat exchanger 31. Aconstriction 281 is provided in a part of the external refrigerant circuit (hereinafter referred to ascircuit sections discharge passage 27 and upstream of theheat exchanger 29. Thecircuit section 28A is located upstream of theconstriction 281, and thecircuit section 28B is located downstream of theconstriction 281. - An electromagnetic
displacement control valve 32 is installed in therear housing member 13. - As shown in
FIG. 2 (a), thedisplacement control valve 32 includes asolenoid 41. A fixediron core 42 of thesolenoid 41 attracts amovable iron core 44 based on excitation by current supplied to acoil 43. Thesolenoid 41 is subjected to current supply control (duty ratio control in this embodiment) executed by a control computer C (seeFIG. 1 ). Atransmission rod 45 is fixed to themovable iron core 14. - A
valve housing 33, which forms thedisplacement control valve 32, has a valvehole forming wall 34 and avalve seat 35. Afirst valve hole 36 is formed in the valvehole forming wall 34, and asecond valve hole 37 is formed in thevalve seat 35. That is, the valve housing 33 (specifically, the valve hole forming wall 34) functions as a first valve hole forming member. Thevalve seat 35 functions as a second valve hole forming member. Thesecond valve hole 37 opens on theseating face 351. Achamber 46 is defined between thevalve seat 35 and the fixediron core 42. Thetransmission rod 45 extends through thechamber 46 and thesecond valve hole 37. Aspring seat 55 is located in thechamber 46 and attached to thetransmission rod 45. An urgingspring 56 is located between thespring seat 55 and thevalve seat 35. Thetransmission rod 45 is urged by the force of the urgingspring 56 in a direction moving themovable iron core 44 away from the fixediron core 42. Thechamber 46 communicates with thesuction chamber 131 through apassage 57. - As shown in
FIG. 2 (b), a sharedchamber 38 is defined between the valvehole forming wall 34 and the valve seat 35 (between thefirst valve hole 36 and the second valve hole 37). The sharedchamber 38 is connected to thefirst valve hole 36 and thesecond valve hole 37. The sharedchamber 38 communicates with thecontrol pressure chamber 121 through apassage 58. - A
first valve body 39 is integrally formed with (fixed to) thetransmission rod 45. That is, thefirst valve body 39 functions as a fixed valve body that is fixed to thetransmission rod 45 functioning as a reciprocating body. Thefirst valve body 39 includes acylindrical portion 391 and atapered portion 392. The diameter of the taperedportion 392 is reduced in a direction from thesecond valve hole 37 to thefirst valve hole 36. - A
second valve body 40 is accommodated in the sharedchamber 38. Thesecond valve body 40 functions as a sliding valve body that is slidably fitted around thetransmission rod 45. Thecylindrical portion 391 of thefirst valve body 39 is configured to enter and close thefirst valve hole 36, while thesecond valve body 40 is configured to contact aseating face 351 of thevalve seat 35 and close thesecond valve hole 37. Thesecond valve body 40 has avalve closing face 403 that contacts theseating face 351 to close the correspondingsecond valve hole 37. - A
compression spring 47 is located between an opposingface 341 of the valvehole forming wall 34 and thesecond valve body 40. Thecompression spring 47 urges thesecond valve body 40 toward a closing position at which thesecond valve body 40 closes the second valve hole 37 (a position where thesecond valve body 40 contacts theseating face 351 of the valve seat 35). Astep 451 is formed on thetransmission rod 45. Thesecond valve body 40 selectively contacts thestep 451. Specifically, thestep 451 can contact thevalve closing face 403 of thesecond valve body 40. Thesecond valve body 40 is urged toward thestep 451 by the force of thecompression spring 47. - A distance H1 (see
FIG. 2 (b)) between thestep 451 and aboundary 393 between thecylindrical portion 391 of thefirst valve body 39 and the taperedportion 392 is greater than a distance K1 (seeFIG. 2 (b)) between anopen end 361 of thefirst valve hole 36 and theseating face 351. Theboundary 393 functions as a first initial contact portion, or a portion of thefirst valve body 39 that initially contacts the circumferential surface of thefirst valve hole 36 when thefirst valve body 39 switches the correspondingfirst valve hole 36 from the open state to the closed state. Theopen end 361 of thefirst valve hole 36 functions as a second initial contact portion, which is a portion of the circumferential surface of thefirst valve hole 36 that initially contacts theboundary 393 when thefirst valve hole 36 is switched from the open state to the closed state. - As shown in
FIG. 2 (a),pressure sensing chambers displacement control valve 32 by abellows 50. A stationary end of thebellows 50 is coupled to anend wall 51 forming thevalve housing 33. A movable end of thebellows 50 is coupled to amovable body 52, which functions as a movable portion. Anend face 452 of thetransmission rod 45 always contacts themovable body 52. - The
pressure sensing chamber 48 communicates with thesection 28A of the externalrefrigerant circuit 28, which is upstream of theconstriction 281, through apassage 53A, while thepressure sensing chamber 49 communicates with thesection 28B of the externalrefrigerant circuit 28, which is downstream of theconstriction 281, through apassage 53B. That is, the interior of thepressure sensing chamber 48 is exposed to the pressure of thecircuit section 28A, which is upstream of theconstriction 281, while the interior of thepressure sensing chamber 49 is exposed to the pressure of thecircuit section 28B, which is downstream of theconstriction 281 and upstream of theheat exchanger 29. The pressure in thepressure sensing chamber 48 and the pressure in thepressure sensing chamber 49 oppose each other with thebellows 50 in between. - The
pressure sensing chambers bellows 50 form apressure sensing mender 54 that senses the pressure difference between the pressure of thecircuit section 28A, which is upstream of theconstriction 281, and the pressure of thecircuit section 28B, which is downstream of theconstriction 281 and upstream of theheat exchanger 29. When refrigerant is flowing through thecircuit sections circuit section 28A, which is upstream of theconstriction 281, is higher than the pressure of thecircuit section 28B, which is downstream of theconstriction 281 and upstream of theheat exchanger 29. When the flow rate of refrigerant in thecircuit sections constriction 281 is increased. When the flow rate of refrigerant in thecircuit sections constriction 281 is reduced. When the pressure difference between the sections upstream and downstream of theconstriction 281 is increased, the pressure difference between thepressure sensing chambers constriction 281 is reduced, the pressure difference between thepressure sensing chambers pressure sensing chambers movable body 52 and thetransmission rod 45 in a direction from thefirst valve hole 36 to thesecond valve hole 37. - The control computer C shown in
FIG. 1 executes the current supply control (duty ratio control) for thesolenoid 41 of thedisplacement control valve 32. When an air-conditioner switch 59 is ON, the control computer C supplies current to thesolenoid 41. When the air-conditioner switch 59 is OFF, the control computer C steps supplying the current. The control computer C is connected to a compartmenttemperature setting device 60 and acompartment temperature detector 61. When the air-conditioner switch 59 is ON, the control computer C controls current supplied to thesolenoid 41 based on the difference between a target compartment temperature set by the compartmenttemperature setting device 60 and the temperature detected by thecompartment temperature detector 61. - FIGS. 1, 2(a), and 2(b) show a state in which the air-
conditioner switch 59 is ON, and the current control (duty ratio control) is being executed based on the difference between a target temperature set by manipulating the compartmenttemperature setting device 60 and the temperature detected by thecompartment temperature detector 61. In FIGS. 1, 2(a), and 2(b), the duty ratio is set to 100% in the control of current to thesolenoid 41. In this state, themovable iron core 44 is closest to the fixediron core 42. Thestep 451 of thetransmission rod 45 contacts thesecond valve body 40, and thesecond valve body 40 is at an opening position separated from theseating face 351 of thevalve seat 35. Since thesecond valve hole 37 is open, refrigerant in the sharedchamber 38 flows to thechamber 46 through thesecond valve hole 37. That is, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. On the other hand, thecylindrical portion 391 of thefirst valve body 39 is in thefirst valve hole 36 so that thefirst valve hole 36 is closed. Since thefirst valve hole 36 is closed, refrigerant in thepressure sensing chamber 49 does not flow into the sharedchamber 38 through thefirst valve hole 36. Also, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown in FIGS. 1, 2(a), and 2(b), thedisplacement control valve 32 does not allow refrigerant in thecircuit section 28B (discharge pressure zone) to flow into thecontrol pressure chamber 121, while allowing refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. Therefore, the pressure in thecontrol pressure chamber 121 is reduced, and the inclination angle of theswash plate 22 is maximized. Accordingly, thevariable displacement compressor 10 operates at the maximum displacement. - FIGS. 2(c), 3(a), and 3(b) show a state in which the air-
conditioner switch 59 is ON, and the current control (duty ratio control) is being executed based on the difference between a target temperature set by manipulating the compartmenttemperature setting device 60 and the temperature detected by thecompartment temperature detector 61. - In the state of
FIG. 2 (c), although less than 100%, the duty ratio control is being executed at a relatively high duty ratio. In this state, thestep 451 of thetransmission rod 45 contacts thesecond valve body 40, and thesecond valve body 40 is at an opening position separated from theseating face 351 of thevalve seat 35. Since thesecond valve hole 37 is open, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. On the other hand, thecylindrical portion 391 of thefirst valve body 39 is in thefirst valve hole 36 so that thefirst valve hole 36 is closed. Since thefirst valve hole 36 is closed, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown in FIG. 2(c), thedisplacement control valve 32 does not allow refrigerant in thecircuit section 28B (discharge pressure zone) to flow into thecontrol pressure chamber 121, while allowing refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - The opening degree of the
second valve hole 37 in the state ofFIG. 2 (c) is less than that in the state ofFIG. 2 (b). In the state ofFIG. 2 (c), an intermediate displacement operation is performed in which the inclination angle of theswash plate 22 is less than the maximum inclination angle. - In the state of
FIG. 3 (a), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 2 (c). In the illustrated state, thestep 451 of thetransmission rod 45 contacts thesecond valve body 40, and thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36). Thesecond valve body 40 is in a position where it contacts theseating face 351 of the valve seat 35 (a position where thesecond valve body 40 closes the second valve hole 37). That is, thesecond valve hole 37 is closed by thesecond valve body 40. - In the state of
FIG. 3 (b), the duty ratio control is being executed at a duty ratio that is less than that of the stale shown inFIG. 3 (a). In the illustrated state, thestep 451 of thetransmission rod 45 is separated from thesecond valve body 40, and thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36). Thesecond valve body 40 is in a position where it contacts theseating face 351 of the valve seat 35 (a position where thesecond valve body 40 closes the second valve hole 37). That is, thesecond valve hole 37 is closed by thesecond valve body 40. - In either of the states shown in FIGS. 3(a) and 3(b), the
first valve body 39 is in a position where it closes thefirst valve hole 36, and thesecond valve body 40 is in a position where it closes thesecond valve hole 37. As the electromagnetic force of thesolenoid 41 is reduced from the state ofFIG. 3 (a) (a state in which theend face 452 of thetransmission rod 45 is in a position W1), theend face 452 of thetransmission rod 45 is moved from the position W1 toward thefirst valve hole 36, and thestep 451 is separated from thesecond valve body 40. As the electromagnetic force of thesolenoid 41 is increased from the state ofFIG. 3 (b) (a state in which theend face 452 of thetransmission rod 45 is in a position W2), theend face 452 of thetransmission rod 45 is moved from the position W2 toward the position W1, and thestep 451 approaches thesecond valve body 40. If theend face 452 of thetransmission rod 45 is in a displacement range [W1, W2] from the position W1 to the position W2, thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36), and thesecond valve body 40 is in the position where it contacts theseating face 351 of the valve seat 35 (a position where thesecond valve body 40 closes the second valve hole 37). - The displacement range [W1, W2] is a predetermined range of a double closing state of the
transmission rod 45, in which thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. When thetransmission rod 45, which is a reciprocating body, is in the predetermined displacement range [W1, W2], the double closing state occurs, in which thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. This state is obtained because the distance H1 between thestep 451 and theboundary 393 is greater than the distance K1 between theopen end 361 and theseating face 351. That is, to ensure that a the predetermined displacement range [W1, W2] be created, the distance H1 between the displacement transmission portion (the step 451) and the first initial contact portion (theboundary 393 of the first valve body 39) is different from the distance K1 between the second initial contact portion (theopen end 361 of the first valve hole 36) and theseating face 351. - In FIGS. 3(a) and 3(b), since the
second valve hole 37 is closed, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone) On the other hand, since thefirst valve hole 36 is closed, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown in FIGS. 3(a) and 3(b), thedisplacement control valve 32 does not allow refrigerant in thecircuit section 28B (discharge pressure zone) to flow into thecontrol pressure chamber 121. Thedisplacement control valve 32 also does not allow refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - If the duty ratio is further reduced from the state of
FIG. 3 (b), the state shown inFIG. 3 (c) is obtained (including a case where the duty ratio is zero). In this state, this control is executed when thevariable displacement compressor 10 is operated at a small displacement or when the speed of the vehicle engine E is abruptly increased while the air-conditioner switch 59 is ON. - The
step 451 of thetransmission rod 45 is separated from thesecond valve body 40, and thesecond valve body 40 is in the position where it contacts theseating face 351 of the valve seat 35 (the position where it closes the second valve hole 37). Since thesecond valve hole 37 is closed, refrigerant in the sharedchamber 38 does riot flow out to thechamber 46 through thesecond valve hole 37. That is, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. On the other hand, thecylindrical portion 391 of thefirst valve body 39 is out of thefirst valve hole 36 so that thefirst valve hole 36 is open. Since thefirst valve hole 36 is open, refrigerant in thepressure sensing chamber 49 flows into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, thedisplacement control valve 32 allows refrigerant in thecircuit section 28B (discharge pressure zone) to flow into thecontrol pressure chamber 121, while preventing refrigerant in thecontrol pressure chamber 121 from flowing out to thesuction chamber 131. Therefore, the pressure in thecontrol pressure chamber 121 is high, and the inclination angle of theswash plate 22 is minimized. Accordingly, thevariable displacement compressor 10 operates at the minimum displacement. - In the state of
FIG. 3 (c), thetransmission rod 45 is out of the predetermined displacement range [W1, W2], thefirst valve body 39 opens thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. In the state of FIGS. 2(b) and 2(c), thetransmission rod 45 is out of the predetermined displacement range [W1, W2], thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 40 opens thesecond valve hole 37. That is, when thetransmission rod 45 is out of the predetermined displacement range [W1, W2], one of the state in which thefirst valve body 39 closes thefirst valve hole 36, and the state in which thesecond valve body 40 closes thesecond valve hole 37 occurs. In other words, when thetransmission rod 45 is out of the displacement range ([W1, W2]), a single closing state occurs, in which only one of thefirst valve body 39 and thesecond valve body 40 closes the corresponding one of the valve holes 36, 37. - In the state of
FIG. 2 (c) or the state of FIGS. 3(a) and 3(b), if the rotation speed of thevariable displacement compressor 10 is increased, the flow rate of refrigerant through thecircuit sections circuit section 28A and the refrigerant pressure in thecircuit section 28B. Thepressure sensing member 54 moves thetransmission rod 45 in a direction from thefirst valve hole 36 to thesecond valve hole 37 based on the increase in the pressure difference. When thecylindrical portion 391 of thefirst valve body 39 is out of thefirst valve hole 36, thefirst valve hole 36 is open. When thefirst valve hole 36 is open, refrigerant in thepressure sensing chamber 49 flows into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. This increases the pressure in thecontrol pressure chamber 121, thereby reducing the inclination angle of theswash plate 22. Accordingly, the compressor displacement is reduced. - In the state of FIGS. 3(a) to 3(c), if the rotation, speed of the
variable displacement compressor 10 is reduced, the flow rate of refrigerant through thecircuit sections circuit section 28A and the refrigerant pressure in thecircuit section 28B. This moves thetransmission rod 45 in a direction from thesecond valve hole 37 to thefirst valve hole 36. When thestep 451 of thetransmission rod 45 contacts thesecond valve body 40, and thesecond valve body 40 is separated from theseating face 351 of thevalve seat 35, thesecond valve hole 37 is open. When thesecond valve hole 37 is open, refrigerant in thecontrol pressure chamber 121 flows out to thesuction chamber 131 through thepassage 58, the sharedchamber 38, thesecond valve hole 37, and thepassage 57. This reduces the pressure in thecontrol pressure chamber 121, thereby increasing the inclination angle of theswash plate 22. Accordingly, the compressor displacement is increased. - The opening degree of the
first valve hole 36 is determined by the balance of the electromagnetic force produced by thesolenoid 41, the force of the urgingspring 56, and the force of thepressure sensing member 54. The opening degree of thesecond valve hole 37 is determined by the balance of the electromagnetic force produced by thesolenoid 41, the force of the urgingspring 56, the force of thecompression spring 47, and the force of thepressure sensing member 54. Together with thepassage 53B, thepressure sensing chamber 49, the sharedchamber 38, and thepassage 58, thefirst valve hole 36 forms a supply passage for supplying refrigerant of thecircuit section 28B (discharge pressure zone) to thecontrol pressure chamber 121. Together with thepassage 58, the sharedchamber 38, thechamber 46, and thepassage 57, thesecond valve hole 37 forms a discharge passage for discharging refrigerant of thecontrol pressure chamber 121 to the suction chamber 131 (suction pressure zone). - The
displacement control valve 32 is a control valve of a valve opening degree changing type, which changes the electromagnetic force (duty ratio), thereby continuously varying the flow passage areas of thefirst valve hole 36 and thesecond valve hole 37. The air-conditioner switch 59, the compartmenttemperature setting device 60, thecompartment temperature detector 61, and the control computer C form an electromagnetic force changing unit for changing the electromagnetic force in thedisplacement control valve 32. - In this embodiment, carbon dioxide is used as refrigerant.
- The first embodiment provides the following advantages.
- (1-1) When the
transmission rod 45 is moved from the outside of the predetermined displacement range [W1, W2] into the displacement range [W1, W2], the state is shifted from a state in which one of the first and second valve holes 36, 37 is closed (single closing state) to a state in which both of the first and second valve holes 36, 37 are closed (double closing state). The displacement range [W1, W2] is the difference between the distance H1 between thestep 451 and theboundary 393 and the distance K1 between theopen end 361 and theseating face 351, and is expressed by (H1−K1)>0. Since the displacement range [W1, W2] has a width, the displacement range [W1, W2] is reliably secured even if there are dimensional errors and assembly errors of the components of thedisplacement control valve 32. That is, when the state is being shifted from a state in which thefirst valve hole 36 is open and thesecond valve hole 37 is closed and a state in which thesecond valve hole 37 is open and thefirst valve hole 36 is closed, both of the first and second valve holes 36, 37 are closed. In other words, thefirst valve hole 36 and thesecond valve hole 37 are not open at the same time. - (1-2) When the
second valve body 40 is in the position where it closes the second valve hole 37 (a specific position where it contacts theseating face 351 of the valve seat 35), thesecond valve body 40 is moveable relative to thetransmission rod 45 in a direction opposite to the direction from thefirst valve hole 36 to thesecond valve hole 37. If thetransmission rod 45 is moved in a direction from thefirst valve hole 36 to thesecond valve hole 37 when thesecond valve body 40 is at the closing position for closing thesecond valve hole 37, the distance between theboundary 393 of thefirst valve body 39 and theseating face 351 is changed (shortened). That is, the distance between thefirst valve body 39 and thesecond valve body 40 is changed according to the displacement of thetransmission rod 45. This configuration, in which the distance is changeable, permits thesecond valve body 40 to be located at the closing position for closing the second valve hole 37 (specific position) when thetransmission rod 45 is in the predetermined displacement range [W1, W2]. This configuration, in which the distance is changeable, is suitable for realizing the double closing state, in which thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37 when thetransmission rod 45 is in the predetermined displacement range [W1, W2]. - When the
transmission rod 45 is outside of the displacement range [W1, W2], and thestep 451 of thetransmission rod 45 is not contacting thesecond valve body 40, thesecond valve body 40 closes thesecond valve hole 37 by means of the force of thecompression spring 47. Thestep 451, which functions as a displacement transmission portion for separating thesecond valve body 40 from the closing position for closing thesecond valve hole 37, and a distance changing mechanism having thecompression spring 47, which functions as an urging member for causing thesecond valve body 40 to contact thevalve seat 35, are suitable as means for changing the distance between thefirst valve body 39 and thesecond valve body 40 according to the position of thetransmission rod 45. When thesecond valve body 40 closes thesecond valve hole 37 at a specific position, the distance changing mechanism permits thetransmission rod 45 to be displaced relative to thesecond valve body 40 at the specific position. - (1-3) When the
transmission rod 45 is in the predetermined displacement range [W1, W2], thefirst valve body 39 is in thefirst valve hole 36 to close thefirst valve hole 36. The configuration in which thefirst valve body 39 fixed to thetransmission rod 45 is caused to enter and close thefirst valve hole 36 is a simplified configuration for closing thefirst valve hole 36 when thetransmission rod 45 is in the predetermined displacement range [W1, W2]. - (1-4) If the flow passage area of the
first valve hole 36, which is a part of the supply passage, is finely changed, the compressor displacement can be finely controlled. Thefirst valve body 39 has the taperedportion 392, which is selectively inserted Into thefirst valve hole 36. The taperedportion 392 is a favorable structure for finely changing the flow passage area of thefirst valve hole 36 according to the position of thefirst valve body 39 when thefirst valve body 39 is in thefirst valve hole 36. The taperedportion 392 is advantageous for permitting thecylindrical portion 391 outside of thefirst valve hole 36 to smoothly enter thefirst valve hole 36. - (1-5) The greater the pressure difference between the pressure in the discharge pressure zone and the pressure in the
control pressure chamber 121, and the greater the pressure difference between the pressure in thecontrol pressure chamber 121 and the pressure in the suction pressure zone, the more likely refrigerant flows out from the discharge pressure zone to the suction pressure zone through the supply passage, thecontrol pressure chamber 121, and the discharge passage. When refrigerant flows from the discharge pressure zone to thecontrol pressure chamber 121 through the supply passage, and flows to the suction pressure zone from thecontrol pressure chamber 121 through the discharge passage, the flow of refrigerant is wasteful and reduces the efficiency of the compressor. The greater the flow rate of refrigerant that flows from the discharge pressure zone to the suction pressure zone through thecontrol pressure chamber 121, the more reduced the compressor efficiency becomes. - The refrigerant pressure in a case where carbon dioxide is used as the refrigerant is significantly higher than the refrigerant pressure in a case where chlorofluorocarbon gas is used as refrigerant. That is, the pressure difference between the pressure in the discharge pressure zone and the pressure in the
control pressure chamber 121, and the pressure difference between the pressure in thecontrol pressure chamber 121 and the pressure in the suction pressure zone (the suction chamber 131) are significantly greater in a case where carbon dioxide is used as the refrigerant than in a case where chlorofluorocarbon gas is used as the refrigerant. Therefore, in a case where carbon dioxide is used as the refrigerant, wasteful flow of refrigerant from the discharge pressure zone to the suction pressure zone through thecontrol pressure chamber 121 affects the compressor efficiency by a great degree. - In this embodiment, the
first valve hole 36 and thesecond valve hole 37 are not open at the same time. This prevents carbon dioxide, which is used as refrigerant, from wastefully flowing from the discharge pressure zone to the suction pressure zone through thecontrol pressure chamber 121. That is, thedisplacement control valve 32, which does not open thefirst valve hole 36 and thesecond valve hole 37 at the same time, is suitable as a displacement control valve used in thevariable displacement compressor 10, which uses carbon dioxide as the refrigerant. - (1-6) Since the
first valve body 39 is integrated with thetransmission rod 45, the number of the components is reduced, and the valve mechanism is simplified. - A second embodiment will now be described with reference to FIGS. 4(a) and 4(b). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c).
- A
first chamber 63 and asecond chamber 64 are defined by aseparation member 62 between the valvehole forming wall 34 and thevalve seat 35. Thefirst chamber 63 is connected to thefirst valve hole 36, and thesecond chamber 64 is connected to thesecond valve hole 37. Thefirst chamber 63 communicates with thecontrol pressure chamber 121 through apassage 65, and thesecond chamber 64 communicates with thecontrol pressure chamber 121 through apassage 66. Thecompression spring 47 is located between theseparation member 62 and thesecond valve body 40 and urges thesecond valve body 40 in a direction from thefirst valve hole 36 to thesecond valve hole 37. The distance H1 between thestep 451 and theboundary 393 is greater than the distance K1 between theopen end 361 and theseating face 351 of thevalve seat 35. - When the
cylindrical portion 391 of thefirst valve body 39 is out of thefirst valve hole 36, refrigerant in thepressure sensing chamber 49 flows into thecontrol pressure chamber 121 through thefirst valve hole 36, thefirst chamber 63, and thepassage 65. When thesecond valve body 40 is separated from theseating face 351, refrigerant in thecontrol pressure chamber 121 flows out to thesuction chamber 131 through thepassage 66, thesecond chamber 64, thesecond valve hole 37, thechamber 46, and thepassage 57. When thetransmission rod 45 is in the predetermined displacement range [W1, W2], thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. - The second embodiment has the same advantages as the advantages (1-1) to (1-6) of the first embodiment.
- A third embodiment will now be described with reference to FIGS. 5(a) to 6(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c).
- As shown in FIGS. 5(a) and 5(b), a
first valve body 67 is accommodated in the sharedchamber 38 between avalve seat 69 and a valvehole forming plate 70. Thefirst valve body 67 is slidably fitted around a slidingportion 453 formed on thetransmission rod 45. Thefirst valve body 67 has avalve closing face 673 that contacts theseating face 691 of thevalve seat 69 to close the correspondingfirst valve hole 36. - A
second valve body 68 is integrally formed with (fixed to) thetransmission rod 45. Thesecond valve body 68 includes acylindrical portion 681 and atapered portion 682. The diameter of the taperedportion 682 is reduced in a direction from thefirst valve hole 36 to thesecond valve hole 37. Thecylindrical portion 681 of thesecond valve body 68 is configured to enter and close thesecond valve hole 37, while thefirst valve body 67 is configured to contact aseating face 691 of thevalve seat 69 and close thefirst valve hole 36. - A
compression spring 71 is located between the valvehole forming plate 70 and thefirst valve body 67. Thecompression spring 71 urges thefirst valve body 67 toward a closing position at which thefirst valve body 67 closes the first valve hole 36 (a position where thefirst valve body 67 contacts theseating face 691 of the valve seat 69). - An
auxiliary rod 72 is attached to themovable body 52 of thepressure sensing member 54 at acoupling face 722. Anend face 723 of theauxiliary rod 72 always contacts anend face 454 of thetransmission rod 45. The diameter of theend face 721 of theauxiliary rod 72, which forms a reciprocating body with thetransmission rod 45, is greater than the diameter of theend face 454 of the slidingportion 453. Theend face 721 of theauxiliary rod 72 selectively contacts thefirst valve body 67. Thevalve body 67 is urged toward theend face 721 by the force of thecompression spring 71. - A distance H2 (see
FIG. 5 (b)) between theend face 721 and aboundary 683 between thecylindrical portion 681 of thesecond valve body 68 and the taperedportion 682 is greater than a distance K2 (seeFIG. 5 (b)) between anopen end 371 of thesecond valve hole 37 and theseating face 691. - In FIGS. 5(a), and 5(b), the duty ratio is set to 100% in the control of current to the
solenoid 41. Theend face 721 of theauxiliary rod 72 is farthest from thefirst valve hole 36, and thesecond valve body 68 is located at an opening position away from thesecond valve hole 37. Since thesecond valve hole 37 is open, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. On the other hand, thefirst valve body 67 contacts the sealingface 691 of thevalve seat 69 so that thefirst valve hole 36 is closed. Since thefirst valve hole 36 is closed, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown in FIGS. 5(a) and 5(b), thedisplacement control valve 32 does not allow refrigerant in thecircuit section 28A (discharge pressure zone) to flow into thecontrol pressure chamber 121. Thedisplacement control valve 32 also allows refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. Therefore, the pressure in thecontrol pressure chamber 121 is reduced, and the inclination angle of theswash plate 22 is maximized. Accordingly, thevariable displacement compressor 10 operates at the maximum displacement. - In the state of
FIG. 5 (c), although less than 100%, the duty ratio control is being executed at a relatively high duty ratio. In this state, the taperedportion 682 of thesecond valve body 68 is in thesecond valve hole 37, while theboundary 683 is not in thesecond valve hole 37. That is, thesecond valve body 68 is at the opening position, where it opens thesecond valve hole 37. Since thesecond valve hole 37 is open, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. On the other hand, thefirst valve body 67 contacts theseating face 691 so that thefirst valve hole 36 is closed. Since thefirst valve hole 36 is closed, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown inFIG. 5 (c), thedisplacement control valve 32 does not allow refrigerant in thecircuit section 28B (discharge pressure zone) to flow into thecontrol pressure chamber 121, while allowing refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - The opening degree of the
second valve hole 37 in the state ofFIG. 5 (c) is less than that in the state ofFIG. 5 (b). In the state ofFIG. 5 (c), an intermediate displacement operation is performed in which the inclination angle of theswash plate 22 is less than the maximum inclination angle. - In the state of
FIG. 6 (a), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 5 (c). In the illustrated state, theend face 721 of theauxiliary rod 72 is separated from thefirst valve body 67, and thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the second valve hole 37). Thefirst valve body 67 is in a position where it contacts theseating face 691 of the valve seat 69 (a position where thefirst valve body 67 closes the first valve hole 36). That is, thefirst valve hole 36 is closed by thefirst valve body 67. - In the state of
FIG. 6 (b), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 6 (a). In the illustrated state, theend face 721 of theauxiliary rod 72 contacts thefirst valve body 67, and thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the first valve hole 36). Thesecond valve hole 37 is closed by thesecond valve body 68. Thefirst valve body 67 is in a position where it contacts theseating face 691 of the valve seat 69 (a position where thefirst valve body 67 closes the first valve hole 36). That is, thefirst valve hole 36 is closed by thefirst valve body 67. - As the electromagnetic force of the
solenoid 41 is reduced from the state ofFIG. 6 (a) (a state in which thecoupling face 722 of theauxiliary rod 72 is located in a position W1 relative to the movable body 52), theend face 721 of theauxiliary rod 72 approaches thefirst valve body 67. As the electromagnetic force of thesolenoid 41 is increased from the state ofFIG. 6 (b) (a state in which thecoupling face 722 is in the position W2), theend face 721 of theauxiliary rod 72 is moved from the position W2 toward the position W1. If thecoupling face 722 of theauxiliary rod 72 is in a displacement range [W1, W2] from the position W1 to the position W2, thefirst valve body 67 is in a position where it contacts theseating face 691 of the valve seat 69 (closing position for closing the first valve hole 36), and thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the second valve hole 37). - The displacement range [W1, W2] is a predetermined range of a double closing state of the
transmission rod 45, in which thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. When thetransmission rod 45, which is a reciprocating body, is in the predetermined displacement range [W1, W2], the double closing state occurs, in which thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. This state is obtained because the distance 112 between theend face 721 and theboundary 683 is greater than the distance K2 between theseating face 691 and theopen end 371. - If the duty ratio is further reduced from the state of
FIG. 6 (b), the state shown inFIG. 6 (c) is obtained (including a case where the duty ratio is zero). Theend face 721 of theauxiliary rod 72 contacts thefirst valve body 67, and thefirst valve body 67 is separated from theseating face 691. That is, thefirst valve hole 36 is open. Since thefirst valve hole 36 is open, refrigerant in thepressure sensing chamber 49 flows into thecontrol pressure chamber 121 through tiefirst valve hole 36, the sharedchamber 38, and thepassage 58. On the other hand, thecylindrical portion 681 of thesecond valve body 68 is in thesecond valve hole 37 so that thesecond valve hole 37 is closed. Since thesecond valve hole 37 is closed, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. That is, thedisplacement control valve 32 allows refrigerant in thecircuit section 28B (discharge pressure zone) to flow into thecontrol pressure chamber 121, while preventing refrigerant in thecontrol pressure chamber 121 from flowing out to thesuction chamber 131. Therefore, the pressure in thecontrol pressure chamber 121 is high, and the inclination angle of theswash plate 22 is minimized. Accordingly, thevariable displacement compressor 10 operates at the minimum displacement. - In the state of
FIG. 6 (c), thetransmission rod 45 is out of the predetermined displacement range [W1, W2], thefirst valve body 67 opens thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. In the state of FIGS. 5(b) and 5(c), thetransmission rod 45 is out of the predetermined displacement range [W1, W2], thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 68 opens thesecond valve hole 37. That is, when thetransmission rod 45 is out of the predetermined displacement range [W1, W2], one of the state in which thefirst valve body 67 closes thefirst valve hole 36, and the state in which thesecond valve body 68 closes thesecond valve hole 37 occurs. - The third embodiment has the same advantages as the advantages (1-1) and (1-5) of the first embodiment. Further, the third embodiment provides the following advantages.
- (3-1) The distance between the
first valve body 67 and thesecond valve body 68 is changed according to the displacement of thetransmission rod 45. This configuration, in which the distance is changeable, permits thefirst valve body 67 to be located at the closing position for closing the first valve hole 36 (specific position) when thetransmission rod 45 is in the predetermined displacement range [W1, W2]. This configuration, in which the distance is changeable, is suitable for realizing the double closing state, in which thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37 when thetransmission rod 45 is in the predetermined displacement range [W1, W2]. - When the
transmission rod 45 is outside of the displacement range [W1, W2], and theend face 721 of theauxiliary rod 72 is not contacting thefirst valve body 67, thefirst valve body 67 closes thefirst valve hole 36 by means of the force of thecompression spring 71. Theend face 721 for separating thefirst valve body 67 from the closing position for closing thefirst valve hole 36, and a distance changing mechanism having thecompression spring 71 for causing thefirst valve body 67 to contact thevalve seat 69, are suitable as means for changing the distance between thefirst valve body 67 and thesecond valve body 68 according to the position of thetransmission rod 45. - (3-2) When the
transmission rod 45 is in the predetermined displacement range [W1, W2], thesecond valve body 68 is in thesecond valve hole 37 to close thesecond valve hole 37. The configuration in which thesecond valve body 68 fixed to thetransmission rod 45 is caused to enter and close thesecond valve hole 37 is a simplified configuration for closing thesecond valve hole 37 when thetransmission rod 45 is in the predetermined displacement range [W1, W2]. - (3-3) If the flow passage area of the
second valve hole 37, which is a part of the discharge passage, is finely changed, the compressor displacement can be finely controlled. Thesecond valve body 68 has the taperedportion 682, which is selectively inserted into thesecond valve hole 37. The taperedportion 682 is a favorable structure for finely changing the flow passage area of thesecond valve hole 37 according to the position of thesecond valve body 68 when thesecond valve body 68 is in thesecond valve chamber 37. The taperedportion 682 is advantageous for permitting thecylindrical portion 681 outside of thesecond valve hole 37 to smoothly enter thesecond valve hole 37. - (3-4) Since the
second valve body 68 is integrated with thetransmission rod 45, the number of the components is reduced, and the valve mechanism is simplified. - A fourth embodiment will now be described with reference to
FIG. 7 . Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the second embodiment shown in FIGS. 4(a) and 4(b) and the third embodiment shown in FIGS. 5(a) to 6(c). - A
first chamber 74 and asecond chamber 75 are defined by aseparation member 73 between thevalve seat 69 and the valvehole forming plate 70. Thefirst chamber 74 is connected to thefirst valve hole 36, and thesecond chamber 75 is connected to thesecond valve hole 37. Thefirst chamber 74 communicates with thecontrol pressure chamber 121 through apassage 65, and thesecond chamber 75 communicates with thecontrol pressure chamber 121 through apassage 66. Thecompression spring 76 is located between theseparation member 73 and thefirst valve body 67 and urges thefirst valve body 67 in a direction from thesecond valve hole 37 to thefirst valve hole 36. The distance H2 between theend face 721 and theboundary 683 is greater than the distance K2 between theseating face 691 and theopen end 371. - When the
first valve body 67 does not contact theseating face 691, refrigerant in thepressure sensing chamber 49 flows into thecontrol pressure chamber 121 through thefirst valve hole 36, thefirst chamber 74, and thepassage 65. When thecylindrical portion 681 of thesecond valve body 68 is out of thesecond valve hole 37, refrigerant in thecontrol pressure chamber 121 flows out to thesuction chamber 131 through thepassage 66, thesecond chamber 75, thesecond valve hole 37, thechamber 46, and thepassage 57. When thetransmission rod 45 is in the predetermined displacement range [W1, W2], thefirst valve body 67 closes thefirst valve hole 36, and tiesecond valve body 68 closes thesecond valve hole 37. - The fourth embodiment thus provides the same advantages as the third embodiment.
- A fifth embodiment will now be described with reference to FIGS. 8(a) and 8(b). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c) and the third embodiment shown in FIGS. 5(a) to 6(c).
- In the fifth embodiment, the
first valve body 39 of the first embodiment and thesecond valve body 68 of the third embodiment are used together. That is, thefirst valve body 39 and thesecond valve body 68 are both integrally formed with (fixed to) thetransmission rod 45. That is, both of thefirst valve body 39 and thesecond valve body 68 are fixed valve bodies that are fixed to thetransmission rod 45. A distance H3 between theboundary 393 of thefirst valve body 39 and theboundary 683 of thesecond valve body 68 is greater than a distance K3 between theopen end 361 of thefirst valve hole 36 and theopen end 371 of thesecond valve hole 37. - When the
transmission rod 45 is in the predetermined displacement range [W1, W2], a double closing state occurs, in which thefirst valve body 39 is in thefirst valve hole 36 and closes thefirst valve hole 36, and thesecond valve body 68 is in thesecond valve hole 37 and closes thesecond valve hole 37. In other words, in the double closing state, thefirst valve body 39 enters thefirst valve hole 36 to close thefirst valve hole 36. When thetransmission rod 45 is in the predetermined displacement range [W1, W2], thevalve bodies transmission rod 45 are in positions closing the valve holes 36, 37. When thetransmission rod 45 is moved from the inside of the predetermined displacement range [W1, W2] to the outside of the displacement range [W1, W2], one of thevalve bodies - The fifth embodiment has the same advantages as hie advantages (1-1), (1-3) to (1-6) of the first embodiment, and the advantages (3-2) to (3-4) of the third embodiment.
- A sixth embodiment will now be described with reference to FIGS. 9(a), 9(b), 9(c), 10(b), and 10(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c).
- As shown in
FIG. 9 (a), adisplacement control valve 32A includes asolenoid 41A. A fixediron core 42A of thesolenoid 41 attracts amovable iron core 44A based on excitation by current supplied to acoil 43A. An urgingspring 80 is located between the fixediron core 42A and themovable iron core 44A. The urgingspring 80 urges themovable iron core 44A in a direction away from the fixediron core 42A. Atransmission rod 45A is fixed to themovable iron core 44A. - The
pressure sensing chamber 48 communicates with asection 28B of the externalrefrigerant circuit 28, which is downstream of theconstriction 281, through apassage 53B, while thepressure sensing chamber 49 communicates with asection 28A of the externalrefrigerant circuit 28, which is upstream of theconstriction 281, through apassage 53A. That is, thepressure sensing chamber 48 is exposed to the pressure in thecircuit section 28B, and thepressure sensing chamber 49 is exposed the pressure of thecircuit section 28A. The pressure in thepressure sensing chamber 48 and the pressure in thepressure sensing chamber 49 oppose each other with thebellows 50 in between. - The
pressure sensing chambers bellows 50 form apressure sensing member 54A that senses the pressure difference between the pressure of thecircuit section 28A, which is upstream of theconstriction 281, and the pressure of thecircuit section 28B, which is downstream of theconstriction 281 and upstream of theheat exchanger 29. - A
valve housing 33A, which forms thedisplacement control valve 32A, has a valvehole forming portion 77. Afirst valve hole 36A, a sharedpassage 78, and asecond valve hole 37A are formed in the valvehole forming portion 77. Thefirst valve hole 36A and thesecond valve hole 37A communicate with each other through the sharedpassage 78. The sharedpassage 78 communicates with thecontrol pressure chamber 121 through thepassage 58. Anaccommodation chamber 79 is defined between the valvehole forming portion 77 and themovable iron core 44A. Thoaccommodation chamber 79 communicates with thesuction chamber 131 through apassage 57. Thetransmission rod 45A extends through theaccommodation chamber 79, thesecond valve hole 37A, the sharedpassage 78, and thefirst valve hole 36A, and projects into thepressure sensing chamber 49. Thetransmissions rod 45A is attached to themovable body 52 at anend face 455. - When the flow rate of refrigerant in the
circuit sections constriction 281 is increased. When the flow rate of refrigerant in thecircuit sections constriction 281 is reduced. When the pressure difference between the sections upstream and downstream of theconstriction 281 is increased, the pressure difference between thepressure sensing chambers constriction 281 is reduced, the pressure difference between thepressure sensing chambers pressure sensing chambers movable body 52 in a direction from thesecond valve hole 37A to thefirst valve hole 36A. - As shown in
FIG. 9 (b), thefirst valve body 39A includes acylindrical portion 394 and atapered portion 395. The diameter of the taperedportion 395 is increased in a direction from thesecond valve hole 37A to thefirst valve hole 36A. - A
second valve body 40A is accommodated in theaccommodation chamber 79. Thesecond valve body 40A is slidably filled around thetransmission rod 45A. Thecylindrical portion 394 of thefirst valve body 39A is configured to enter and close thefirst valve hole 36A, while thesecond valve body 40A is configured to contact aseating face 771 of the valvehole forming portion 77 and close thesecond valve hole 37A. - A
compression spring 82 is located between aspring seat 81 and thesecond valve body 40A. Thecompression spring 82 urges thesecond valve body 40A toward a closing position at which thesecond valve body 40A closes thesecond valve hole 37A (a position where thesecond valve body 40A contacts the seating face 771). Astep 456 is formed on thetransmission rod 45A. Thesecond valve body 40A selectively contacts thestep 456. Thesecond valve body 40A is urged toward thestep 456 by the force of thecompression spring 82. - A distance H4 (see
FIG. 9 (b)) between thestep 456 and aboundary 396 between thecylindrical portion 394 of thefirst valve body 39A and theboundary 396 is less than a distance K4 (seeFIG. 9 (b)) between anopen end 362 of thefirst valve hole 36A and theseating face 771. - In FIGS. 9(a) and 9(b), the duty ratio is set to 100% in the control of current to the
solenoid 41A. In this state, themovable iron core 44A is closest to the fixediron core 42A. Thestep 456 of thetransmission rod 45A contacts thesecond valve body 40A, and thesecond valve body 40A is at an opening position separated from theseating face 771. Since thesecond valve hole 37A is open, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedpassage 78, thesecond valve hole 37A, theaccommodation chamber 79, and thepassage 57. On the other hand, thecylindrical portion 394 of thefirst valve body 39A is in thefirst valve hole 36A so that thefirst valve hole 36A is closed. Since thefirst valve hole 36A is closed, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36A, the sharedpassage 78, and thepassage 58. Therefore, the pressure in thecontrol pressure chamber 121 is reduced, and the inclination angle of theswash plate 22 is maximized. Accordingly, the variable displacement compressor 10 (seeFIG. 1 ) operates at the maximum displacement. - In the state of
FIG. 9 (c), although less than 100%, the duty ratio control is being executed at a relatively high duty ratio. In this state, thestep 456 of thetransmission rod 45A contacts thesecond valve body 40A, and thesecond valve body 40A is at an opening position separated from theseating face 771. Since thesecond valve hole 37A is open, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedpassage 78, thesecond valve hole 37A, theaccommodation chamber 79, and thepassage 57. On the other hand, thecylindrical portion 394 of thefirst valve body 39A is in thefirst valve hole 36A so that thefirst valve hole 36A is closed. Since thefirst valve hole 36A is closed, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36A, the sharedpassage 78, and thepassage 58. - The opening degree of the
second valve hole 37A in the state ofFIG. 9 (c) is less than that in the state ofFIG. 9 (b). In the state ofFIG. 9 (c), an intermediate displacement operation is performed in which the inclination angle of theswash plate 22 is less than the maximum inclination angle. - In the state of
FIG. 10 (a), the duty ratio control is being executed at a duty ratio that is less than that of the slate shown inFIG. 9 (c). In the illustrated state, thestep 456 of thetransmission rod 45A contacts thesecond valve body 40A, and thecylindrical portion 394 of thefirst valve body 39A is in thefirst valve hole 36A (theboundary 396 is in thefirst valve hole 36A). Thesecond valve body 40A is in a position where it contacts the seating face 771 (a position where thesecond valve body 40A closes thesecond valve hole 37A). That is, thesecond valve hole 37A is closed by thesecond valve body 40A. - In the state of
FIG. 10 (b), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 10 (a). In the illustrated state, thestep 456 of thetransmission rod 45A is separated from thesecond valve body 40A, and thecylindrical portion 394 of thefirst valve body 39A is in thefirst valve hole 36A (theboundary 396 is in thefirst valve hole 36A). Thesecond valve body 40A is in a position where it contacts the seating face 771 (a position where thesecond valve body 40A closes thesecond valve hole 37A). That is, thesecond valve hole 37A is closed by thesecond valve body 40A. - In either of the states shown in FIGS. 10(a) and 10(b), the
cylindrical portion 394 of thefirst valve body 39A is in thefirst valve hole 36A, and thesecond valve body 40A is in a postilion where it closes thesecond valve hole 37A. As the electromagnetic force of thesolenoid 41A is reduced from the state ofFIG. 10 (a) (a stale in which theend face 455 of thetransmission rod 45A is in a position W3), theend face 455 of thetransmission rod 45 is moved away from thefirst valve hole 36A, so that thestep 456 is separated from thesecond valve body 40A. As the electromagnetic force of thesolenoid 41A is increased from the state ofFIG. 10 (b) (a state in which theend face 455 of thetransmission rod 45A is in a position W4), theend face 455 of thetransmission rod 45A is moved from the position W4 toward the position W3, and thestep 456 approaches thesecond valve body 40A. - The displacement range [W3, W4] is a predetermined range of a double closing state of the
transmission rod 45A, in which thefirst valve body 39A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A. When thetransmission rod 45A, which is a reciprocating body, is in the predetermined displacement range [W3, W4], the double closing state occurs, in which thefirst valve body 39A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A. This state is obtained because the distance H4 between thestep 456 and theboundary 396 is less than the distance K4 between theopen end 362 of thefirst valve hole 36A and theseating face 771. - In FIGS. 10(a) and 10(b), since the
second valve hole 37A is closed, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone). On the other hand, since thefirst valve hole 36A is closed, refrigerant in thepressure sensing chamber 49 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36A, the sharedpassage 78, and thepassage 58. That is, in the state shown in FIGS. 10(a) and 10(b), thedisplacement control valve 32A does not allow refrigerant in thecircuit section 28A (discharge pressure zone) to flow into thecontrol pressure chamber 121. Thedisplacement control valve 32A also does not allow refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - If the duty ratio is further reduced from the state of
FIG. 10 (b), the state shown inFIG. 10 (c) is obtained (including a case where the duty ratio is zero). - The
step 456 of thetransmission rod 45A is separated from thesecond valve body 40A, and thesecond valve body 40A is in the position where it contacts the seating face 771 (the closing position for closing thesecond valve hole 37A). Since thesecond valve hole 37A is closed, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedpassage 78, thesecond valve hole 37A, theaccommodation chamber 79, and thepassage 57. On the other hand, thecylindrical portion 394 of thefirst valve body 39A is out of thefirst valve hole 36A so that thefirst valve hole 36A is open. Since thefirst valve hole 36A is open, refrigerant in thepressure sensing chamber 49 flows into thecontrol pressure chamber 121 through thefirst valve hole 36A, the sharedpassage 78, and thepassage 58. Therefore, the pressure in thecontrol pressure chamber 121 is high, and the inclination angle of theswash plate 22 is minimized. Accordingly, thevariable displacement compressor 10 operates at the minimum displacement. - In the state of
FIG. 9 (c) or the state of FIGS. 10(a) and 10(b), if the rotation speed of thevariable displacement compressor 10 is increased, the flow rate of refrigerant through thecircuit sections circuit section 28A and the refrigerant pressure in thecircuit section 28B. Thepressure sensing member 54A moves thetransmission rod 45A in a direction from thesecond valve hole 37A to thefirst valve hole 36A based on the increase in the pressure difference. When thecylindrical portion 394 of thefirst valve body 39A is out of thefirst valve hole 36A, thefirst valve hole 36A is open. When thefirst valve hole 36A is open, refrigerant in thepressure sensing chamber 49, flows into thecontrol pressure chamber 121 through thefirst valve hole 36A, the sharedpassage 78, and thepassage 58. This increases the pressure in thecontrol pressure chamber 121, thereby reducing the inclination angle of theswash plate 22. Accordingly, the compressor displacement is reduced. - In the state of FIGS. 10(a), 10(b), and 10(c), if the rotation speed of the
variable displacement compressor 1 is reduced, the flow rate of refrigerant through thecircuit sections circuit section 28A and the refrigerant pressure in thecircuit section 28B. This moves thetransmission rod 45A in a direction from thefirst valve hole 36A to thesecond valve hole 37A. When thestep 456 of thetransmission rod 45A contacts thesecond valve body 40A, and thesecond valve body 40A is separated from theseating face 771, thesecond valve hole 37A is open. When thesecond valve hole 37A is open, refrigerant in thecontrol pressure chamber 121 flows out to thesuction chamber 131 through thepassage 58, the sharedpassage 78, thesecond valve hole 37A, and thepassage 57 This reduces the pressure in thecontrol pressure chamber 121, thereby increasing the inclination angle of theswash plate 22. Accordingly, the compressor displacement is increased. - The opening degree of the
first valve hole 36A is determined by the balance of the electromagnetic force produced by thesolenoid 41A, the force of the urgingspring 80, and the force of thepressure sensing member 54A. The opening degree of thesecond valve hole 37A is determined by the balance of the electromagnetic force produced by thesolenoid 41A, the force of the urgingspring 80, the force of thecompression spring 82, and the force of thepressure sensing member 54A. Together with thepassage 53A, thepressure sensing chamber 49, the sharedpassage 78, and thepassage 58, thefirst valve hole 36A forms a supply passage for supplying refrigerant of thecircuit section 28A (discharge pressure zone) to thecontrol pressure chamber 121. Together with thepassage 58, the sharedpassage 78, theaccommodation chamber 79, and thepassage 57, thesecond valve hole 37A forms a discharge passage for discharging refrigerant of thecontrol pressure chamber 121 to the suction chamber 131 (suction pressure zone). - The
displacement control valve 32A is a control valve of a valve opening degree changing type, which changes the electromagnetic force (duty ratio), thereby continuously varying the flow passage areas of thefirst valve hole 36A and thesecond valve hole 37A. - The sixth embodiment has the same advantages as the advantages (1-1) and (1-5) of the first embodiment. Further, the sixth embodiment provides the following advantages.
- (6-1) The distance between the
first valve body 39A and thesecond valve body 40A is changed according to the displacement of thetransmission rod 45A. This configuration, in which the distance is changeable, permits thesecond valve body 40A to be located at the closing position for closing thesecond valve hole 37A (specific position) when thetransmission rod 45A is in the predetermined displacement range [W3, W4]. This configuration, in which the distance is changeable, is suitable for realizing the double closing state, in which thefirst valve body 39A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A when thetransmission rod 45A is in the predetermined displacement range [W3, W4]. - When the
transmission rod 45A is outside of the displacement range [W3, W4], and thestep 456 is not contacting thesecond valve body 40A, thesecond valve body 40A closes thesecond valve hole 37A by means of the force of thecompression spring 82. Thestep 456 for separating thesecond valve body 40A from the closing position for closing thesecond valve hole 37A, and a distance changing mechanism having thecompression spring 82 for causing thesecond valve body 40A to contact theseating face 771, are suitable as means for changing the distance between thefirst valve body 39A and thesecond valve body 40A according to the position of thetransmission rod 45A. - (6-2) When the
transmission rod 45A is in the predetermined displacement range [W3, W4], thefirst valve body 39A is in thefirst valve hole 36A to close thefirst valve hole 36A. The configuration in which thefirst valve body 39A fixed to thetransmission rod 45A is caused to enter and close thefirst valve hole 36A is a simplified configuration for closing thefirst valve hole 36A when thetransmission rod 45A is in the predetermined displacement range [W3, W4]. - (6-3) If the flow passage area of the
first valve hole 36A, which is a part of the supply passage, is finely changed, the compressor displacement can be finely controlled. Thefirst valve body 39A has the taperedportion 395, which is selectively inserted into thefirst valve hole 36A. The taperedportion 395 is a favorable structure for finely changing the flow passage area of thefirst valve hole 36A according to the position of thefirst valve body 39A when thefirst valve body 39A is in thefirst valve hole 36A. The taperedportion 395 is advantageous for permitting thecylindrical portion 394 outside of thefirst valve hole 36A to smoothly enter thefirst valve hole 36A. - (6-4) Since the
first valve body 39A is integrated with thetransmission rod 45A, the number of the components is reduced, and the valve mechanism is simplified. - A seventh embodiment will now be described with reference to FIGS. 11(a) and 11(b). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the sixth embodiment shown in
FIGS. 9 and 10 . - The
first valve hole 36A and thesecond valve hole 37A are separated from each other by aseparation portion 83, which is a separation member, formed on the circumference of thetransmission rod 45A. Thefirst valve hole 36A communicates with thecontrol pressure chamber 121 through apassage 65, and thesecond valve hole 37A communicates with, thecontrol pressure chamber 121 through apassage 66. The distance H4 between thestep 456 and theboundary 396 is less than the distance K4 between theopen end 362 of thefirst valve hole 36A and theseating face 771. - When the
cylindrical portion 394 of thefirst valve body 39A is out of thefirst valve hole 36A, refrigerant in thepressure sensing chamber 49 flows into thecontrol pressure chamber 121 through thefirst valve hole 36A and thepassage 65. When thesecond valve body 40A is separated from theseating face 771, refrigerant in thecontrol pressure chamber 121 flows out to thesuction chamber 131 through thepassage 66, thesecond valve hole 37A, theaccommodation chamber 79, and thepassage 57. When thetransmission rod 45A is in the predetermined displacement range [W3, W4] (seeFIG. 10 (b)), thefirst valve body 39A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A. - The seventh embodiment thus provides the same advantages as the sixth embodiment.
- An eighth embodiment will now be described with reference to FIGS. 12(a), 12(b), 12(c), 13(a), 13(b), and 13(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the sixth embodiment shown in
FIGS. 9 and 10 . - As shown in
FIG. 12 (a), afirst valve body 67A is accommodated in thepressure sensing chamber 49. Thefirst valve body 67A is slidably fitted around thetransmission rod 45A. Astep 457 is formed on thetransmission rod 45A. Thefirst valve body 67A selectively contacts thestep 457. - A
second valve body 68A is integrally formed with (fixed to) thetransmission rod 45A. Thesecond valve body 68A includes acylindrical portion 684 and atapered portion 685. The diameter of the taperedportion 685 is increased in a direction from thefirst valve hole 36A to thesecond valve hole 37A. Thecylindrical portion 684 of thesecond valve body 68A is configured to enter and close thesecond valve hole 37A, while thefirst valve body 67A is configured to contact aseating face 772 of the valvehole forming portion 77 and close thefirst valve hole 36A. - A
compression spring 84 is located between theend wall 51 and thefirst valve body 67A. Thecompression spring 84 urges thefirst valve body 67A toward a closing position at which thefirst valve body 67A closes thefirst valve hole 36A (a position where thefirst valve body 67A contacts the seating face 772). Thefirst valve body 67A is urged toward thestep 457 by the force of thecompression spring 84. - A distance H5 (see
FIG. 12 (b)) between thestep 457 and aboundary 686 between thecylindrical portion 684 of thesecond valve body 68A and the taperedportion 685 is less than a distance K5 (seeFIG. 12 (b)) between anopen end 372 of thesecond valve hole 37A and theseating face 772. - In FIGS. 12(a) and 12(b), the duty ratio is set to 100% in the control of current to the
solenoid 41A. In this state, thestep 457 of thetransmission rod 45A is separated from thefirst valve body 67A, and thefirst valve body 67A contacts theseating face 772. That is, thefirst valve hole 36A is closed. On the other hand, thecylindrical portion 684 of thesecond valve body 68A is out of thesecond valve hole 37A so that tiesecond valve hole 37A is open. Therefore, the pressure in thecontrol pressure chamber 121 is reduced, and the inclination angle of the swash plate 22 (seeFIG. 1 ) is maximized. Accordingly, the variable displacement compressor 10 (seeFIG. 1 ) operates at the maximum displacement. - In the state of
FIG. 12 (c), although less than 100%, the duty ratio control is being executed at a relatively high duty ratio. In this state, thestep 457 of thetransmission rod 45A is separated from thefirst valve body 67A, and thefirst valve hole 36A is closed by thefirst valve body 67A. On the other hand, thecylindrical portion 684 of thesecond valve body 68A is out of thesecond valve hole 37A so that thesecond valve hole 37A is open. The opening degree of thesecond valve hole 37A in the state ofFIG. 12 (c) is less than that in the state ofFIG. 12 (b). In the state ofFIG. 12 (c), an intermediate displacement operation is performed in which the inclination angle of theswash plate 22 is less than the maximum inclination angle. - In the state of
FIG. 13 (a), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 12 (c). In the illustrated state, thestep 457 of thetransmission rod 45A is separated from thefirst valve body 67A, and thecylindrical portion 684 of thesecond valve body 68A is in thesecond valve hole 37A (theboundary 686 is in thesecond valve hole 37A). Thefirst valve body 67A is in a position where it contacts the seating face 772 (a closing position for thefirst valve hole 36A). That is, thefirst valve hole 36A is closed by thefirst valve body 67A. - In the state of
FIG. 13 (b), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 13 (a). In the illustrated state, thestep 457 of thetransmission rod 45A contacts thefirst valve body 67A, and thecylindrical portion 684 of thesecond valve body 68A is in thesecond valve hole 37A (theboundary 686 is in thesecond valve hole 37A). Thefirst valve body 67A is in a position where it contacts the seating face 772 (a closing position for closing thefirst valve hole 36A). That is, thefirst valve hole 36A is closed by thefirst valve body 67A. - In either of the states shown in FIGS. 13(a) and 13(b), the
cylindrical portion 684 of thesecond valve body 68A is in thesecond valve hole 37A, and thefirst valve body 67A is in a closing position for closing thefirst valve hole 36A. As the electromagnetic force of thesolenoid 41A is reduced from the state ofFIG. 13 (a) (a state in which theend face 455 of thetransmission rod 45A is in a position W3), theend face 455 of the transmission rod: 45A is moved away from thefirst valve hole 36A, so that thestep 457 approaches thefirst valve body 67A. As the electromagnetic force of thesolenoid 41A is increased from the state ofFIG. 13 (b) (a state in which theend face 455 of thetransmission rod 45A is in a position W4), theend face 455 of thetransmission rod 45A is moved from the position W4 toward the position W3, and thestep 457 is separated from thefirst valve body 67A. - The displacement range [W3, W4] is a predetermined range of a double closing state of the
transmission rod 45A, in which thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 68A closes thesecond valve hole 37A. When thetransmission rod 45A, which is a reciprocating body, is in the predetermined displacement range [W3, W4], the double closing state occurs, in which thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 68A closes thesecond valve hole 37A. This state is obtained because the distance H5 between thestep 457 and theboundary 686 is less than the distance K5 between theseating face 772 and theopen end 372 of thesecond valve hole 37A. - It the duty ratio is further reduced from the state of
FIG. 13 (b), the state shown inFIG. 13 (c) is obtained (including a case where the duty ratio is zero). Thestep 457 of thetransmission rod 45A contacts thefirst valve body 67A, and thefirst valve body 67A is in the position where it is separated from the seating face 772 (the position opening thefirst valve hole 36A). On the other hand, thecylindrical portion 684 of thesecond valve body 68A is in thesecond valve hole 37A so that thesecond valve hole 37A is closed. Therefore, the pressure in thecontrol pressure chamber 121 is high, and the inclination angle of theswash plate 22 is minimized. Accordingly, thevariable displacement compressor 10 operates at the minimum displacement. - The opening degree of the
first valve hole 36A is determined by the balance of the electromagnetic force produced by thesolenoid 41A, the force of the urgingspring 80, the force of thecompression spring 84, and the force of thepressure sensing member 54A. The opening degree of thesecond valve hole 37A is determined by the balance of the electromagnetic force produced by thesolenoid 41A, the force of the urgingspring 80, and the force of thepressure sensing member 54A. - The eighth embodiment has the same advantages as the advantages (1-1) and (1-5) of the first embodiment. Further, the eighth embodiment provides the following advantages.
- (8-1) The distance between the
first valve body 67A and thesecond valve body 68A is changed according to the displacement of thetransmission rod 45A. This configuration, in which the distance is changeable, permits thefirst valve body 67A to be located at the closing position for closing thefirst valve hole 36A (specific position) when thetransmission rod 45A is in the predetermined displacement range [W3, W4]. This configuration, in which the distance is changeable, is suitable for realizing the double closing state, in which thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 68A closes thesecond valve hole 37A when thetransmission rod 45A is in the predetermined displacement range [W3, W4]. - When the
transmission rod 45A is outside of the displacement range [W3, W4], and thestep 457 is not contacting thefirst valve body 67A, thefirst valve body 67A closes thefirst valve hole 36A by means of the force of thecompression spring 84. Thestep 457 for separating thefirst valve body 67A from the closing position for closing thefirst valve hole 36A, and a distance changing mechanism having thecompression spring 84 for causing thefirst valve body 67A to contact theseating face 772, are suitable as means for changing the distance between thefirst valve body 67A and thesecond valve body 68A according to the position of thetransmission rod 45A. - (8-2) When the
transmission rod 45A is in the predetermined displacement range [W3, W4], thesecond valve body 68A is in thesecond valve hole 37A to close thesecond valve hole 37A. The configuration in which thesecond valve body 68A fixed to thetransmission rod 45A is caused to enter and close tiesecond valve hole 37A is a simplified configuration for closing thesecond valve hole 37A when thetransmission rod 45A is in the predetermined displacement range [W3, W4]. - (8-3) If the flow passage area of the
second valve hole 37A, which is a part of the discharge passage, is finely changed, the compressor displacement can be finely controlled. Thesecond valve body 68A has the taperedportion 685, which is selectively inserted into thesecond valve hole 37A. The taperedportion 685 is a favorable structure for finely changing the flow passage area of thesecond valve hole 37A according to the position of thesecond valve body 68A when thesecond valve body 37A is in thesecond valve hole 37A. The taperedportion 685 is advantageous for permitting thecylindrical portion 684 outside of thesecond valve hole 37A to smoothly enter thesecond valve hole 37A. - (8-4) Since the
second valve body 68A is integrated with thetransmission rod 45A, the number of the components is reduced, and the valve mechanism is simplified. - A ninth embodiment will now be described with reference to
FIG. 14 . Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the eighth embodiment shown inFIGS. 12 and 13 . - The
first valve hole 36A and thesecond valve hole 37A are separated from each other by aseparation portion 83 formed on the circumference of thetransmission rod 45A. Thefirst valve hole 36A communicates with thecontrol pressure chamber 121 through apassage 65, and thesecond valve hole 37A communicates with thecontrol pressure chamber 121 through apassage 66. The distance H5 between thestep 457 and theboundary 686 is less than the distance K5 between theseating face 772 and theopen end 372 of thesecond valve hole 37A. When thetransmission rod 45A is in the predetermined displacement range [W3, W4] (seeFIG. 12 (b)), thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 68A closes thesecond valve hole 37A. - The ninth embodiment thus provides the same advantages as the eighth embodiment.
- A tenth embodiment will now be described with reference to FIGS. 15(a) and 15(b). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the sixth embodiment shown in
FIGS. 9 and 10 and the eighth embodiment shown inFIGS. 12 and 13 . - In the tenth embodiment, the
first valve body 39A of the sixth embodiment and thesecond valve body 68A of the eighth embodiment are used together. That is, thefirst valve body 39A and thesecond valve body 68A are both integrally formed with (fixed to) thetransmission rod 45A. A distance H6 between theboundary 396 of thefirst valve body 39A and theboundary 686 of thesecond valve body 68A is less than a distance K6 between theopen end 362 of thefirst valve hole 36A and theopen end 372 of thesecond valve hole 37A. - When the
transmission rod 45A is in the predetermined displacement range [W3, W4], a double closing state occurs, in which thefirst valve body 39A is in thefirst valve hole 36A and closes thefirst valve hole 36A, and thesecond valve body 68A is in thesecond valve hole 37A and closes thesecond valve hole 37A. When thetransmission rod 45A is in the predetermined displacement range [W3, W4], thevalve bodies transmission rod 45 are in positions closing the valve holes 36A, 37A. When thetransmission rod 45A is moved from the inside of the predetermined displacement range [W3, W4] to the outside of the displacement range [W3, W4], one of thevalve bodies - The tenth embodiment has the same advantages as the advantages (1-1) and (1-5) of the first embodiment, advantages (6-1) to (6-4) of the sixth embodiment, and the advantages (8-1) to (8-4) of the eighth embodiment.
- An eleventh embodiment will now be described with reference to FIGS. 16(a), 16(b), 16(c), 17(a), 17(b), and 17(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c) and the third embodiment shown in FIGS. 5(a) to 6(c).
- As shown in
FIG. 16 (a), a pair ofvalve seats valve housing 33 that forms part of adisplacement control valve 32. Afirst valve hole 36 is formed in thevalve seat 85, and asecond valve hole 37 is formed in thevalve seat 35. Thetransmission rod 45 extends through thechamber 46 and thesecond valve hole 37. - A shared
chamber 38 is defined between thevalve seat 85 and the valve seat 35 (between thefirst valve hole 36 and the second valve hole 37). Afirst valve body 67 and asecond valve body 40 are accommodated in the sharedchamber 38. Thefirst valve body 67 and thesecond valve body 40 are slidably fitted around thetransmission rod 45. Thefirst valve body 67 is configured to contact thevalve seat 85 and close thefirst valve hole 36, while thesecond valve body 40 is configured to contact thevalve seat 35 and close thesecond valve hole 37. - An
auxiliary rod 87 is attached to themovable body 52 of thepressure sensing member 54 at acoupling face 872. Anend face 871 of theauxiliary rod 87 always contacts anend face 452 of thetransmission rod 45. The diameter of theend face 871 of theauxiliary rod 87, which forms a reciprocating body with thetransmission rod 45, is greater than the diameter of theend face 452 of thetransmission rod 45. Theend face 871, which functions as a first displacement transmission portion, selectively contacts thefirst valve body 67. The end face 871 contacts thesecond valve body 40 to transmit displacement of thetransmission rod 45, thereby moving thesecond valve body 40, which functions as a sliding valve body, from the closing position to the opening position. - A
compression spring 99 is located between thefirst valve body 67 and thevalve seat 35, and acompression spring 86 is located between thefirst valve body 67 and thesecond valve body 40. Thecompression spring 99 urges thefirst valve body 67 toward a closing position at which thefirst valve body 67 closes the first valve hole 36 (a position where thefirst valve body 67 contacts the valve seat 85). Thecompression spring 86 urges thefirst valve body 67 toward a closing position at which thefirst valve body 67 closes the first valve hole 36 (a position where thefirst valve body 67 contacts the valve seat 85). Thecompression spring 86 also urges thesecond valve body 40 toward a closing position at which thesecond valve body 40 closes the second valve hole 37 (a position where thesecond valve body 67 contacts the valve seat 35). Thefirst valve body 67 is urged toward theend face 871 by the force of thecompression spring 99. Thesecond valve body 40 is urged toward thestep 451, which functions as a second displacement transmission portion, by the force of thecompression spring 86. Thecompression spring 99 functions as a first urging member that urges thefirst valve body 67 toward a position at which thefirst valve body 67 contacts theend face 871. Thecompression spring 86 functions as a second urging member that urges thesecond valve body 40 toward a position at which thesecond valve body 40 contacts thestep 451. - The
displacement control valve 32 has aseating face 851 in which thefirst valve hole 36 opens and aseating face 351 in which thesecond valve hole 37 opens. A distance K7 between theseating face 851 of thevalve seat 85 and theseating face 351 of thevalve seat 35 is less than a distance H7 (shown inFIG. 16 (b)) between theend face 871 and thestep 451. That is, to ensure that the predetermined displacement range [W1, W2] be created, the distance K7 between the seating faces 851, 351 is different from the distance H7 between the first displacement transmission portion (end face 871) and the second displacement transmission portion (the step 451). - In FIGS. 16(a) and 16(b), the duty ratio is set to 100% in the control of current to the
solenoid 41. In this state, theend face 871 is separated from thefirst valve body 67, and thestep 451 contacts thesecond valve body 40. That is, thefirst valve hole 36 is open, and thesecond valve hole 37 is closed. Therefore, the pressure in thecontrol pressure chamber 121 is reduced, and the inclination angle of the swash plate 22 (seeFIG. 1 ) is maximized. Accordingly, the variable displacement compressor 10 (seeFIG. 1 ) operates at the maximum displacement. - In the state of
FIG. 16 (c), although less than 100%, the duty ratio control is being executed at a relatively high duty ratio. Theend face 871 is separated from thefirst valve body 67, and thefirst valve body 67 contacts theseating face 851. Thestep 451 contacts thesecond valve body 40, and thesecond valve body 40 is separated from theseating face 351. That is, thefirst valve hole 36 is closed, and thesecond valve hole 37 is open. The opening degree of thesecond valve hole 37 in the state ofFIG. 16 (c) is less than that in the state ofFIG. 16 (b). In the state ofFIG. 16 (c), an intermediate displacement operation is performed in which the inclination angle of theswash plate 22 is less than the maximum inclination angle. - In the state of
FIG. 17 (a), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 16 (c). In the illustrated state, theend face 871 is separated from thefirst valve body 67, and thestep 451 contacts thesecond valve body 40. Thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. - In the state of
FIG. 17 (b), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 17 (a). In the illustrated state, theend face 871 contacts thefirst valve body 67, and thestep 451 is separated from thesecond valve body 40. Thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. - As the electromagnetic force of the
solenoid 41 is reduced from the state ofFIG. 17 (a) (a state in which thecoupling face 872 of theauxiliary rod 87 is in a position W5), theend face 871 of theauxiliary rod 87 approaches thefirst valve body 67, and thestep 451 is separated from thesecond valve body 40. As the electromagnetic force of thesolenoid 41 is increased from the state ofFIG. 17 (b) (a state in which thecoupling face 872 of theauxiliary rod 87 is in a position W6), theend face 871 of theauxiliary rod 87 is separated from thefirst valve body 67, and thestep 451 approaches thesecond valve body 40. - The displacement range [W5, W6] is a predetermined range of a double closing state of the
transmission rod 45, in which thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. When thetransmission rod 45, which is a reciprocating body, is in the predetermined displacement range [W5, W6], the double closing state occurs, in which thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. This state is obtained because the distance H7 between theend face 871 and thestep 451 is greater than the distance K7 between theseating face 851 and theseating face 351. - If the duty ratio is further reduced from the state of
FIG. 17 (b), the state shown inFIG. 17 (c) is obtained (including a case where the duty ratio is zero). - The end face 871 contacts the
first valve body 67, and thefirst valve body 67 is in the position where it is separated from the seating face 851 (the position opening the first valve hole 36). On the other hand, thestep 451 is separated from thesecond valve body 40 so that thesecond valve hole 37 is closed. Therefore, the pressure in thecontrol pressure chamber 121 is high, and the inclination angle of theswash plate 22 is minimized. Accordingly, thevariable displacement compressor 10 operates at the minimum displacement. - The eleventh embodiment has the same advantages as the advantages (1-1) and (1-5) of the first embodiment. Further, the eleventh embodiment provides the following advantage.
- (11-1) The distance between the
first valve body 67 and thesecond valve body 40 is changed according to the displacement of thetransmission rod 45. This configuration, in which the distance is changeable, permits a state to be realized, in which thefirst valve body 67 is at a closing position (specific position) for closing thefirst valve hole 36, and thesecond valve body 40 is at a closing position (specific position) for closing thesecond valve hole 37 when thetransmission rod 45 is in the predetermined displacement range [W5, W6]. This configuration, in which the distance is changeable, is suitable for realizing the double closing state, in which thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37 when thetransmission rod 45 is in the predetermined displacement range [W5, W6]. - When the
transmission rod 45 is outside of the displacement range [W5, W6], and theend face 871 of theauxiliary rod 87 is not contacting thefirst valve body 67, thefirst valve body 67 closes thefirst valve hole 36 by means of the force of thecompression spring 99. When thetransmission rod 45 is outside of the displacement range [W5, W6], and thestep 451 is not contacting thesecond valve body 40, thesecond valve body 40 closes thesecond valve hole 37 by means of the force of thecompression spring 86. Theend face 871 for separating thefirst valve body 67 from the closing position for closing thefirst valve hole 36, thestep 451 for separating thesecond valve body 40 from the closing position for closing thesecond valve hole 37, and a distance changing mechanism having the compression springs 86, 99 are suitable as means for changing the distance between thefirst valve body 67 and thesecond valve body 40 according to the position of thetransmission rod 45. - A twelfth embodiment will now be described with reference to FIGS. 18(a) and 18(b). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the eleventh embodiment shown in
FIGS. 16 and 17 . - A
first chamber 88 and asecond chamber 64 are defined by aseparation member 62 between thevalve seat 85 and thevalve seat 35. Thefirst chamber 88 is connected to thefirst valve hole 36, and thesecond chamber 64 is connected to thesecond valve hole 37. Thefirst chamber 88 communicates with thecontrol pressure chamber 121 through apassage 65, and thesecond chamber 64 communicates with thecontrol pressure chamber 121 through apassage 66. Acompression spring 71 located between thevalve seat 85 and theseparation member 62 urges thefirst valve body 67 toward thevalve seat 85. Acompression spring 47 located between theseparation member 62 and thesecond valve body 40 urges thesecond valve body 40 toward thevalve seat 35. A distance H7 between theend face 871 and thestep 451 is greater than a distance K7 between theseating face 851 and theseating face 351. When thetransmission rod 45 is in the predetermined displacement range [W5, W6], thefirst valve body 67 closes thefirst valve hole 36, and thesecond valve body 40 closes thesecond valve hole 37. - The twelfth embodiment has the same advantages as the advantages (1-1) and (1-4) of the first embodiment. Further, the twelfth embodiment provides the following advantage.
- (12-1) When the
transmission rod 45 is outside of the displacement range [W5, W6], and theend face 871 of theauxiliary rod 87 is not contacting thefirst valve body 67, thefirst valve body 67 closes thefirst valve hole 36 by means of tie force of thecompression spring 71. When thetransmission rod 45 is outside of the displacement range [W5, W6], and thestep 451 is not contacting thesecond valve body 40, thesecond valve body 40 closes thesecond valve hole 37 by means of the force of thecompression spring 47. Theend face 871 for separating thefirst valve body 67 from the closing position for closing thefirst valve hole 36, thestep 451 for separating thesecond valve body 40 from the closing position for closing thesecond valve hole 37, and a distance changing mechanism having the compression springs 71, 47 are suitable as means for changing the distance between thefirst valve body 67 and thesecond valve body 40 according to the position of thetransmission rod 45. When thefirst valve body 67 closes thefirst valve hole 36 at a specific position, the distance changing mechanism permits thetransmission rod 45 to be displaced relative to thefirst valve body 67 at the specific position. When thesecond valve body 40 closes thesecond valve hole 37 at a specific position, the distance changing mechanism permits thetransmission rod 45 to be displaced relative to thesecond valve body 40 at the specific position. - A thirteenth embodiment will now be described with reference to FIGS. 19(a), 19(b), 19(c), 20(a), 20(b), and 20(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the sixth embodiment shown in
FIGS. 9 and 10 and the eighth embodiment shown inFIGS. 12 and 13 . - As shown in FIGS. 19(a) and 19(b), a
first valve body 67A is accommodated in thepressure sensing chamber 49. Thefirst valve body 67A is slidably fitted around thetransmission rod 45A. Thefirst valve body 67A is configured to contact theseating face 772 formed on the valvehole forming portion 77 to close thefirst valve hole 36A. Astep 457 is formed on thetransmission rod 45A. Thefirst valve body 67A selectively contacts thestep 457. Asecond valve body 40A is accommodated in theaccommodation chamber 79. Thesecond valve body 40A is slidably fitted around thetransmission rod 45A. Thesecond valve body 40A is configured to contact theseating face 771 formed on the valvehole forming portion 77 to close thesecond valve hole 37A. - A
compression spring 84 is located between theend wall 51 and thefirst valve body 67A. Thecompression spring 84 urges thefirst valve body 67A toward a closing position at which thefirst valve body 67A closes thefirst valve hole 36A (a position where thefirst valve body 67A contacts the seating face 772). Thefirst valve body 67A is urged toward thestep 457 by the force of thecompression spring 84, which functions as a first urging member. - A
compression spring 82 is located between aspring seat 81 and thesecond valve body 40A. Thecompression spring 82, which functions as a second urging member, urges thesecond valve body 40A toward a closing position at which thesecond valve body 40A closes thesecond valve hole 37A (a position where thesecond valve body 40A contacts the seating face 771). Astep 456 is formed on thetransmission rod 45A. Thesecond valve body 40A selectively contacts thestep 456. Thesecond valve body 40A is urged toward thestep 456 by the force of thecompression spring 82. - A distance H8 (shown in
FIG. 19 (b)) between thestep 457 and thestep 456 is less than a distance K8 (shown inFIG. 19 (b)) between theseating face 772 and theseating face 771. - In FIGS. 19(a) and 19(b), the duty ratio is set to 100% in the control of current to the
solenoid 41A. In this state, thestep 457 is separated front thefirst valve body 67A, and thestep 456 contacts thesecond valve body 40A. That is, thefirst valve hole 36A is closed, and thesecond valve hole 37A is open. Therefore, the pressure in thecontrol pressure chamber 121 is reduced, and the inclination angle of the swash plate 22 (seeFIG. 1 ) is maximized. Accordingly, the variable displacement compressor 10 (seeFIG. 1 ) operates at the maximum displacement. - In the state of
FIG. 19 (c), although less than 100%, the duty ratio control is being executed at a relatively high duty ratio. Thestep 457 is separated from thefirst valve body 67A, and thestep 456 contacts thesecond valve body 40A. That is, thefirst valve hole 36A is closed, and thesecond valve hole 37A is open. The opening degree of thesecond valve hole 37 in the state ofFIG. 19 (c) is less than that in the state ofFIG. 19 (b). in the state ofFIG. 19 (c), an intermediate displacement operation is performed in which the inclination angle of theswash plate 22 is less than the maximum inclination angle. - In the state of
FIG. 20 (a), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 19 (c). In the illustrated state, thestep 457 is separated from thefirst valve body 67A, and thestep 456 contacts thesecond valve body 40A. Thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A. - In the state of
FIG. 20 (b), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 20 (a). In the illustrated state, thestep 457 contacts thefirst valve body 67A, and thestep 456 is separated from thesecond valve body 40A. Thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A. - As the electromagnetic force of the
solenoid 41A is reduced from the state ofFIG. 20 (a) (a state in which theend face 455 of thetransmission rod 45A is in a position W7), thestep 457 approaches thefirst valve body 67A, and thestep 456 is separated from thesecond valve body 40A. As the electromagnetic force of thesolenoid 41A is increased from the state ofFIG. 20 (b) (a state in which theend face 455 of thetransmission rod 45A is in a position W8), thestep 457 is separated from thefirst valve body 67A, and thestep 456 approaches thesecond valve body 40A. - The displacement range [W7, W8] is a predetermined range of a double closing state of the
transmission rod 45A, in which thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 68A closes thesecond valve hole 37A. When thetransmission rod 45A, which is a reciprocating body, is in the predetermined displacement range [W7, W8], the double closing state occurs, in which thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A. This state is obtained because the distance H8 between thestep 457 and thestep 456 is less than the distance K8 between theseating face 772 and theseating face 771. - If the duty ratio is further reduced from the state of
FIG. 20 (b), the state shown inFIG. 20 (c) is obtained (including a case where the duty ratio is zero). Thestep 457 contacts thefirst valve body 67A, and thefirst valve body 67A is in the position where it is separated from the seating face 772 (the position opening thefirst valve hole 36A). Thestep 456 is separated from thesecond valve body 40A so that thesecond valve hole 37A is closed. Therefore, the pressure in thecontrol pressure chamber 121 is high, and the inclination angle of theswash plate 22 is minimized. Accordingly, thevariable displacement compressor 10 operates at the minimum displacement. - The thirteenth embodiment has the same advantages as the advantages (1-1) and (1-5) of the first embodiment. Further, the thirteenth embodiment provides the following advantage.
- (13-1) When the
transmission rod 45A is outside of the displacement range [W7, W8], and thestep 457 is not contacting thefirst valve body 67A, thefirst valve body 67A closes thefirst valve hole 36A by means of the force of thecompression spring 84. When thetransmission rod 45A is outside of the displacement range [W7, W8], and thestep 456 is not contacting thesecond valve body 40A, thesecond valve body 40A closes thesecond valve hole 37A by means of the force of thecompression spring 82. Thestep 457 for separating thefirst valve body 67A from the closing position for closing thefirst valve hole 36A, thestep 456 for separating thesecond valve body 40A from the closing position for closing thesecond valve hole 37A, and a distance changing mechanism having the compression springs 84, 82 are suitable as means for changing the distance between thefirst valve body 67A and thesecond valve body 40A according to the position of thetransmission rod 45A. - A fourteenth embodiment will now be described with reference to
FIG. 21 . Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the thirteenth embodiment shown inFIGS. 19 and 20 . - The
first valve hole 36A and thesecond valve hole 37A are separated from each other by aseparation portion 83 formed on the circumference of thetransmission rod 45A. Thefirst valve hole 36A communicates with thecontrol pressure chamber 121 through apassage 65, and thesecond valve hole 37A communicates with thecontrol pressure chamber 121 through apassage 66. A distance H8 between thestep 457 and thestep 456 is less than a distance K8 between theseating face 772 and theseating face 771. - When the
transmission rod 45A is in the predetermined displacement range [W7, W8], thefirst valve body 67A closes thefirst valve hole 36A, and thesecond valve body 40A closes thesecond valve hole 37A. - The fourteenth embodiment thus provides the same advantages as the thirteenth embodiment.
- A fifteenth embodiment will now be described with reference to FIGS. 22(a) and 22(b). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the eleventh embodiment shown in
FIGS. 16 and 17 and the thirteenth embodiment shown inFIGS. 19 and 20 . - A
first valve body 89 and asecond valve body 90 are accommodated in a sharedchamber 38 of adisplacement control valve 32B. Thefirst valve body 89 and thesecond valve body 90 are slidably fitted around atransmission rod 45B. Thefirst valve body 89 is configured to contact avalve seat 91 and close afirst valve hole 92, while thesecond valve body 90 is configured to contact avalve seat 93 and close asecond valve hole 94. Thefirst valve body 89 has avalve closing face 893, and thevalve body 90 has avalve closing face 903. - A
compression spring 95 is located between thefirst valve body 89 and thesecond valve body 90. Thecompression spring 95 urges thefirst valve body 89 toward a closing position at which thefirst valve body 89 closes the first valve hole 92 (a position where thefirst valve body 89 contacts the valve seat 91). Thecompression spring 86 also urges thesecond valve body 90 toward a closing position at which thesecond valve body 90 closes the second valve hole 94 (a postilion where thesecond valve body 90 contacts the valve seat 93). - The
auxiliary rod 87 extends through thevalve seat 93 and projects into thesecond valve hole 94. Theend face 871 of theauxiliary rod 87 always contacts anend face 452 of thetransmission rod 45B. - A distance K9 between a
seating face 911 of thevalve seat 91 and aseating face 931 of thevalve seat 93 is less than a distance H9 between theend face 871 of theauxiliary rod 87 and thestep 451. - The shared
chamber 38 communicates with thecontrol pressure chamber 121 through apassage 58. Thechamber 46 communicates with thecircuit section 28B through thepassage 97. Thechamber 46 communicates with aback pressure space 98 between themovable iron core 44A and the fixediron core 42A through apassage 441. A diameter D1 of a portion of thetransmission rod 45B that is in thechamber 46 and a diameter D2 of theauxiliary rod 87 is substantially equal to each other (D1=D2). - When the
coupling face 872 of theauxiliary rod 87 is in a predetermined displacement range [W9, W10], the double closing state occurs, in which thefirst valve body 89 closes thefirst valve hole 92, and thesecond valve body 90 closes thesecond valve hole 94. This state is obtained because the distance H9 between theseating face 911 of thevalve seat 91 and theseating face 931 of thevalve seat 93 is less than the distance H9 between theend face 871 of theauxiliary rod 87 and thestep 451. When thecoupling face 872 of theauxiliary rod 87 is out of the displacement range [W9, W10], and thesecond valve hole 94 is open, refrigerant in thecontrol pressure chamber 121 flows out to thesuction chamber 131 through thepassage 58, the sharedchamber 38, thesecond valve hole 94, and thepassage 96. When thecoupling face 872 of theauxiliary rod 87 is out of the displacement range [W9, W10], and thefirst valve hole 92 is open, refrigerant in thecircuit section 28B flows into thecontrol pressure chamber 121 through thepassage 97, thechamber 46, thefirst valve hole 92, the sharedchamber 38, and thepassage 58. - The fifteenth embodiment has the same advantages as the advantages (1-1) and (1-5) of the first embodiment, and the advantage (11-1) of the eleventh embodiment.
- A load F1 acts on the
transmission rod 45B by the pressure of refrigerant in theback pressure space 98, which is a first discharge pressure chamber, and a load F2 acts on theauxiliary rod 87 by the pressure of refrigerant in thepressure sensing chamber 48, which is a second discharge pressure chamber. The loads F1, F2 act against each other through thetransmission rod 45B in between. In other words, thetransmission rod 45 has a first end (the lower end of the rod 45) that extends through thefirst valve hole 92 and receives the pressure of the first discharge pressure chamber (the back pressure space 98), and a second end (the upper end of the rod 45) that extends through thesecond valve hole 94 and receives the pressure of the second discharge pressure chamber (the pressure sensing chamber 48). The pressure of the first discharge pressure chamber (the back pressure space 90) acts against the pressure of the second discharge pressure chamber (the pressure sensing chamber 48) through thetransmission rod 45. The pressure in thepressure sensing chamber 48 and in theback pressure space 98 is the same as the pressure in thecircuit section 28B. Since the diameter D1 of a portion of thetransmission rod 45B that is in thechamber 46 and the diameter D2 of theauxiliary rod 87 is substantially equal to each other, the loads F1 and F2 cancel each other. This configuration, in which the loads cancel each other, is effective for preventing the accuracy of the position control of thetransmission rod 45B from deteriorating due to fluctuations of the discharge pressure. That is, the configuration effectively prevents deterioration of the control accuracy of the opening degrees of thefirst valve hole 92 and thesecond valve hole 94. Thevariable displacement compressor 10 uses carbon dioxide, the pressure of which can be significantly higher than that of chlorofluorocarbon gas. The configuration, which permits the loads to cancel each other, is suitable for compressors like thecompressor 10, which use carbon dioxide. - A sixteenth embodiment will now be described with reference to FIGS. 27(a), 27(b), 27(c), 27(b), 28(a), 28(b), and 28(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c), the third embodiment shown in FIGS. 5(a) to 6(c), and the fifth embodiment shown in
FIG. 8 . - As shown in
FIG. 27 (a), a dischargepressure introducing chamber 103 is defined in thevalve housing 33. The dischargepressure introducing chamber 103 communicates with asection 28C of the externalrefrigerant circuit 28 between thedischarge chamber 132 and theheat exchanger 29 through apassage 53C. Aspring seat 101 and afirst urging spring 102 are accommodated in the dischargepressure introducing chamber 103. Thefirst urging spring 102 is located between thespring seat 101 and theend wall 51. Theend face 452 of thetransmission rod 45 contacts thespring seat 101. Thefirst urging spring 102 urges thetransmission rod 45, which has thefirst valve body 39 and thesecond valve body 68, in a direction from thefirst valve hole 36 to thesecond valve hole 37. Thetransmission rod 45 is urged in a direction from thefirst valve hole 36 to thesecond valve hole 37 by the urging spring 56 (hereinafter, referred to as a second urging spring 56). - The
chamber 46 communicates with aspace 104 between themovable iron core 44 and the fixediron core 42 through apassage 421. Thechamber 46 communicates with aback pressure space 98A at the back of themovable iron core 44 through thepassages - The pressure in the discharge
pressure introducing chamber 103 is equal to the pressure in thecircuit section 28C (discharge pressure). The pressure in thespace 104 and the pressure in theback pressure space 98A correspond to the pressure in the suction chamber 131 (suction pressure). Thechamber 46, thespace 104, and theback pressure space 98A form a suction pressure introducing chamber of a pressure zone that corresponds to the suction pressure. The dischargepressure introducing chamber 103 and the suction pressure introducing chamber are arranged with the first and second valve holes 36, 37 in between. One end of thetransmission rod 45 extends through thefirst valve hole 36 and receives the pressure in the dischargepressure introducing chamber 103. The other end of thetransmission rod 45 extends through thesecond valve hole 37 and receives the pressure in the suction pressure introducing chamber. - A diameter D3 of the
cylindrical portion 391 of thefirst valve body 39 is equal to a diameter D4 of thecylindrical portion 681 of the second valve body 68 (D3=D4). That is, the diameter of thefirst valve hole 36 is equal to the diameter of thesecond valve hole 37. Thetransmission rod 45 receives a load F3 in a direction from thesecond valve hole 37 to thefirst valve hole 36 due to the suction pressure. The load F3 is obtained by multiplying the cross-sectional area of the first andsecond valve bodies transmission rod 45 also receives a load F4 in a direction from thefirst valve hole 36 to thesecond valve hole 37 due to the discharge pressure in the dischargepressure introducing chamber 103. The load F4 is obtained by multiplying the cross-sectional area of the first andsecond valve bodies transmission rod 45 by the suction pressure in a direction from thesecond valve hole 37 to thefirst valve hole 36, and the load F4, which is applied to thetransmission rod 45 by the refrigerant pressure in the dischargepressure introducing chamber 103 in a direction from thefirst valve hole 36 to thesecond valve hole 37, oppose each other with thetransmission rod 45 in between. Therefore, thetransmission rod 45 is urged in a direction from thefirst valve hole 36 to thesecond valve hole 37 by the load difference (F4−F3). That is, the load difference (F4−F3) acts against the electromagnetic force of thesolenoid 41. - The opening degrees of the first and second valve holes 36, 37 are determined by the balance of the electromagnetic force produced by the
solenoid 41, the force of thefirst urging spring 102, the force of thesecond urging spring 56, and the force of the load difference (F4−F3). When the difference between the discharge pressure and the suction pressure is increased, the load difference (F4−F3) is increased, accordingly. When the difference between the discharge pressure and the suction pressure is reduced, the load difference (F4−F3) is reduced, accordingly. When the load difference (F4−F3) is increased, thetransmission rod 45 is displaced in a direction from thefirst valve hole 36 to thesecond valve hole 37. When the load difference (F4−F3) is reduced, thetransmission rod 45 is displaced in a direction from thesecond valve hole 37 to thefirst valve hole 36. - In FIGS. 27(a) and 27(b), the duty ratio is set to 100% in the control of current to the
solenoid 41. Thecylindrical portion 391 of thefirst valve body 39 is in thefirst valve hole 36 so that thefirst valve hole 36 is closed. Since thefirst valve hole 36 is closed, refrigerant in the dischargepressure introducing chamber 103 does not flow into the sharedchamber 38 through thefirst valve hole 36. Also, refrigerant in the dischargepressure introducing chamber 103 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. On the other hand, thecylindrical portion 681 of thesecond valve body 68 is out of thesecond valve hole 37 so that thesecond valve hole 37 is open. Since thesecond valve hole 37 is open, refrigerant in the sharedchamber 38 flows out to thesuction chamber 131 through thesecond valve hole 37, thechamber 46, and thepassage 57. That is, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. - That is, in the state shown in FIGS. 27(a) and 27(b), a
displacement control valve 32C does not allow refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121, while permitting refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. Therefore, the pressure in thecontrol pressure chamber 121 is reduced, and the inclination angle of the swash plate 22 (seeFIG. 1 ) is maximized. Accordingly, the variable displacement compressor 10 (seeFIG. 1 ) operates at the maximum displacement. - In the state of
FIG. 27 (c), although less than 100%, the duty ratio control is being executed at a relatively high duty ratio. In this state, thefirst valve hole 36 is closed, and thesecond valve hole 37 is open. That is, thedisplacement control valve 32C allows refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121. Thecontrol valve 32C also allows refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. The opening degree of thesecond valve hole 37 in the state ofFIG. 27 (c) is less than that in the state ofFIG. 27 (b). In the state ofFIG. 27 (c), an intermediate displacement operation is performed in which the inclination angle of theswash plate 22 is less than the maximum inclination angle. - In the state of
FIG. 28 (a), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 27 (c). In the state ofFIG. 28 (b), the duty ratio control is being executed at a duty ratio that is less than that of the state shown inFIG. 28 (a). In either of the states shown in FIGS. 28(a) and 28(b), thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36), and thefirst valve hole 36 is closed by thefirst valve body 39. Also, thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the second valve hole 37), and thesecond valve hole 37 is closed by thesecond valve body 68. - In either of the states shown in FIGS. 28(a) and 28(b), the
first valve body 39 is in a position where it closes thefirst valve hole 36, and thesecond valve body 68 is in a position where it closes thesecond valve hole 37. If theend face 452 of thetransmission rod 45 is in a displacement range [W1, W2] from the position W1 to the position W2, thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36), and thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the second valve hole 37). - The displacement range [W1, W2] is a predetermined range of a double closing slate of the
transmission rod 45, in which thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. When thetransmission rod 45, which is a reciprocating body, is in the predetermined displacement range [W1, W2], the double closing state occurs, in which thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. This state is obtained because a distance H3 between theboundary 683 and theboundary 393 is greater than a distance K3 between theopen end 361 and theopen end 371. That is, to ensure that the predetermined displacement range [W1, W2] be created, the distance H3 between the first initial contact portions (theboundaries 683, 393) is different from the distance K3 between the second initial contact portions (the open ends 361, 371). - In FIGS. 28(a) and 28(b), since the
second valve hole 37 is closed, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone). Also, since thefirst valve hole 36 is closed, refrigerant in the dischargepressure introducing chamber 103 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown in FIGS. 28(a) and 28(b), thedisplacement control valve 32C does not allow refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121. Thedisplacement control valve 32C also does not allow refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - If the duty ratio is further reduced from the state of
FIG. 28 (b), the state shown inFIG. 28 (c) is obtained (including a case where the duty ratio is zero). in this state, this control is executed when thevariable displacement compressor 10 is operated at a small displacement or when the speed of the vehicle engine E is abruptly increased while the air-conditioner switch 59 is ON. - The
cylindrical portion 681 of thesecond valve body 68 is in thesecond valve hole 37 so that thesecond valve hole 37 is closed. Therefore, refrigerant in the sharedchamber 38 does not flow out to thechamber 46 through thesecond valve hole 37. That is, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. On the other hand, thecylindrical portion 391 of thefirst valve body 39 is out of thefirst valve hole 36 so that thefirst valve hole 36 is open. Since thefirst valve hole 36 is open, refrigerant in the dischargepressure introducing chamber 103 flows into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, thedisplacement control valve 32C allows refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121, while preventing refrigerant in thecontrol pressure chamber 121 from flowing out to thesuction chamber 131. Therefore, the pressure in thecontrol pressure chamber 121 is high, and the inclination angle of theswash plate 22 is minimized. Accordingly, thevariable displacement compressor 10 operates at the minimum displacement. - In the state of
FIG. 28 (c), thetransmission rod 45 is out of the predetermined displacement range [W1, W2], thefirst valve body 39 opens thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. In the state of FIGS. 27(b) and 27(c), thetransmission rod 45 is out of the predetermined displacement range [W1, W2], thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 68 opens thesecond valve hole 37. That is, when thetransmission rod 45 is out of the predetermined displacement range [W1, W2], one of the state in which thefirst valve body 39 closes thefirst valve hole 36, and the state in which thesecond valve body 68 closes thesecond valve hole 37 occurs. - In the state of
FIG. 27 (c) or the state of FIGS. 28(a) and 28(b), if the difference between the discharge pressure and the suction pressure increases, thetransmission rod 45 is displaced in a direction from thefirst valve hole 36 to thesecond valve hole 37 due to an increase in the load difference (F4−F3). When thecylindrical portion 391 of thefirst valve body 39 is out of thefirst valve hole 36, thefirst valve hole 36 is open. When thefirst valve hole 36 is open, refrigerant in the dischargepressure introducing chamber 103 flows into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. This increases the pressure in thecontrol pressure chamber 121, thereby reducing the inclination angle of theswash plate 22. Accordingly, the compressor displacement is reduced. - In the state of FIGS. 28(a), 28(b), and 28(c), if the difference between the discharge pressure and the suction pressure is reduced, the
transmission rod 45 is displaced in a direction from thesecond valve hole 37 to thefirst valve hole 36 due to a decrease in the load difference (F4−F3). When thecylindrical portion 681 of thesecond valve body 68 is out of thesecond valve hole 37, thesecond valve hole 37 is open. When thesecond valve hole 37 is open, refrigerant in thecontrol pressure chamber 121 flows out to thesuction chamber 131 through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. This reduces the pressure in thecontrol pressure chamber 121, thereby increasing the inclination angle of theswash plate 22. Accordingly, the compressor displacement is increased. - In addition to the same advantages as the fifth embodiment, the sixteenth embodiment provides the following advantages.
- (16-1) In the
displacement control valve 32C, the pressure in the dischargepressure introducing chamber 103 and the pressure in the suction pressure introducing chamber oppose each other with thetransmission rod 45, which functions as a reciprocating body, in between. Thedisplacement control valve 32C thus configured only controls the pressure difference between the discharge pressure and the suction pressure. That is, thedisplacement control valve 32C is controlled such that the difference between the discharge pressure and the suction pressure is balanced with the electromagnetic force of thesolenoid 41. Since thedisplacement control valve 32C does not use thepressure sensing member 54 having thebellows 50 as in the first embodiment, thedisplacement control valve 32C of the present embodiment has a simpler construction than thedisplacement control valve 32 having thepressure sensing member 54. - (16-2) The spring characteristics of the
first urging spring 102 and thesecond urging spring 56 are set, for example, as indicated by lines E1, E2 in the graph ofFIG. 27 (d). A horizontal axis L represents the distance between the fixediron core 42 and themovable iron core 44, and the vertical axis represents force. To represents the maximum distance between the fixediron core 42 and themovable iron core 44. Line E1 represents the spring characteristics of thefirst urging spring 102, and line E2 represents the spring characteristics or thesecond urging spring 56. Curve G represents the electromagnetic force of thesolenoid 41. - If the
second urging spring 56 is not used, the spring characteristics of thefirst urging spring 102 need to be changed to that indicated by chain line E3. However, such spring characteristics would result in too strong a spring force. In such a case, thesolenoid 41 needs to be configured to produce a greater force, or the size of thesolenoid 41 needs to be increased. The combination of thefirst urging spring 102 and thesecond urging spring 56 is favorable for reliably controlling the opening degrees of the first and second valve holes 36, 37, while eliminating the necessity for increasing the size of thesolenoid 41. - (16-3) The diameter D3 of the
cylindrical portion 391 of thefirst valve body 39 is equal to the diameter D4 of thecylindrical portion 681 of the second valve body 68 (D3=D4). That is, the diameter of thefirst valve hole 36 is equal to the diameter of thesecond valve hole 37. - If the diameter D3 of the
cylindrical portion 391 of thefirst valve body 39 is less than the diameter D4 of thecylindrical portion 681 of thesecond valve body 68, thetransmission rod 45 is urged in a direction from thefirst valve hole 36 to thesecond valve hole 37 by the pressure in the shared chamber 38 (control pressure introducing chamber), which corresponds to the control pressure. In contrast, if the diameter D3 of thecylindrical portion 391 of thefirst valve body 39 is greater than the diameter D4 of thecylindrical portion 681 of thesecond valve body 68, thetransmission rod 45 is urged in a direction from thesecond valve hole 37 to thefirst valve hole 36 by the pressure in the sharedchamber 38, which corresponds to the control pressure. That is, the opening degree control of the first and second valve holes 36, 37 is affected by the pressure in the shared chamber 38 (corresponding to the control pressure). As a result, the opening degrees of the first and second valve holes 36, 37 are not reliably controlled. - The present embodiment, in which the diameter D3 of the
cylindrical portion 391 of thefirst valve body 39 is equal to the diameter D4 of thecylindrical portion 681 of thesecond valve body 68, avoids problems in the opening degree control of the first and second valve holes 36, 37 ascribable to the pressure in the shared chamber 38 (corresponding to the control pressure). - A seventeenth embodiment will now be described with reference to FIGS. 29(a), 29(b), and 29(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c) and the sixteenth embodiment shown in
FIGS. 27 and 28 . - A
flange 458 is integrally formed with a circumferential surface of thetransmission rod 45 in the shared chamber 3B. Arecess 401 is formed in asecond valve body 40B. Theflange 458 is inserted into therecess 401. Oneend face 459 of theflange 458 selectively contacts abottom 402 of therecess 401. The bottom 402 functions as a displacement receiving face that can contact theend face 459. The bottom 402 is separated from thevalve closing face 403 with respect to the direction of displacement of thetransmission rod 45. The open end of therecess 401 forms thevalve closing face 403. A diameter of therecess 401 is equal to a diameter D5 of thesecond valve hole 37, and the diameter D5 of thesecond valve hole 37 is greater than a diameter D6 of thefirst valve hole 36. - In the state of
FIG. 29 (a), theend face 459 of theflange 458 contacts the bottom 402, and thesecond valve body 40B is at an opening position separated from theseating face 351 of thevalve seat 35. Since thesecond valve hole 37 is open, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. On the other hand, thecylindrical portion 391 of thefirst valve body 39 is in thefirst valve hole 36 so that thefirst valve hole 36 is closed. Since thefirst valve hole 36 is closed, refrigerant in the dischargepressure introducing chamber 103 does not flow into the sharedchamber 38 through thefirst valve hole 36. Also, refrigerant in the dischargepressure introducing chamber 103 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown inFIG. 29 (a), adisplacement control valve 32C does not allow refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121, while permitting refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - In the state of
FIG. 29 (b), theend face 459 of theflange 458 contacts the bottom 402. Thesecond valve body 40B is in a position where it contacts theseating face 351 of thevalve seat 35. That is, thesecond valve hole 37 is closed by thesecond valve body 40B. Thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36). - In the state of
FIG. 29 (c), theend face 459 of theflange 458 is separated frown the bottom 402. Thesecond valve body 40B is in a position where it contacts theseating face 351 of the valve scat 35 (a position where thesecond valve body 40B closes the second valve hole 37). That is, thesecond valve hole 37 is closed by thesecond valve body 40B. Thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36). - In either of the states shown in FIGS. 29(b) and 29(c), the
first valve body 39 is in a position where it closes thefirst valve hole 36, and thesecond valve body 40B is in a position where it closes thesecond valve hole 37. As the electromagnetic force of thesolenoid 41 is reduced from the state ofFIG. 29 (b) (a state in which theend face 452 of thetransmission rod 45 is in a position W1), theend face 452 of thetransmission rod 45 is moved from the position W1 toward thefirst valve hole 36, and theend face 459 is separated from the bottom 402. As the electromagnetic force of thesolenoid 41 is increased from the state ofFIG. 29 (c) (a state in which theend face 452 of thetransmission rod 45 is in a position W2), theend face 452 of thetransmission rod 45 is moved from the position W2 toward the position W1, and theend face 459 approaches the bottom 402. If theend face 452 of thetransmission rod 45 is in a displacement range [W1, W2] from the position W1 to the position W2, thecylindrical portion 391 of thefirst valve body 39 is in the first valve hole 36 (theboundary 393 is in the first valve hole 36), and thesecond valve body 40B is in the position where it contacts theseating face 351 of the valve seat 35 (a position where thesecond valve body 40B closes the second valve hole 37). - The displacement range [W1, W2] is a predetermined range of a double closing state of the
transmission rod 45, in which thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 40B closes thesecond valve hole 37. When thetransmission rod 45, which is a reciprocating body, is in the predetermined displacement range [W1, W2], the double closing state occurs, in which thefirst valve body 39 closes thefirst valve hole 36, and thesecond valve body 40B closes thesecond valve hole 37. This state is obtained because the sum of a distance H11 between theend face 459 and theboundary 393 and a depth H12 of the recess 401 (H11+H12=H1) is greater than the distance H11 between theopen end 361 and theseating face 351. That is, to ensure that the predetermined displacement range [W1, W2] be created, the sum (H11+H12=H1) of the distance H11 between the displacement transmission portion (the end face 459) and the first initial contact portion (theboundary 393 of the first valve body 39) and the distance (the depth H12 of the recess 401) between thevalve closing face 403 of thesecond valve body 40B and the displacement receiving face (thebottom 402 of the recess 401) is different from the distance K1 between the second initial contact portion (theopen end 361 of the first valve hole 36) and theseating face 351 of thesecond valve hole 37. - In FIGS. 29(b) and 29(c), since the
second valve hole 37 is closed, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone). Also, since thefirst valve hole 36 is closed, refrigerant in the dischargepressure introducing chamber 103 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. That is, in the state shown in FIGS. 29(b) and 29(c), thedisplacement control valve 32C does not allow refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121. Thedisplacement control valve 32C also does not allow refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - The seventeenth embodiment has the same advantages as the advantages (16-1) and (16-2) of the sixteenth embodiment.
- The configuration in which the
flange 458 is inserted into therecess 401 contributes to increase in a flow passage area of the second valve hole 37 (the cross-sectional area obtained by subtracting the cross-sectional area Π(D7/2)2 of thetransmission rod 45 in thesecond valve hole 37 from the cross-sectional area Π(D5/2)2 of thesecond valve hole 37, or Π((D5/2)2−Π(D7/2)2). D7 represents the diameter of thetransmission rod 45 in thesecond valve hole 37. - When assembling the
displacement control valve 32C, thetransmission rod 45 is inserted from thesecond valve hole 37 to pass through thesecond valve hole 37, thesecond valve body 40B, and thefirst valve hole 36. If the diameter D5 of thesecond valve hole 37 is too large, the sealing effectiveness between thesecond valve body 40B and theseating face 351 is degraded. Therefore, the diameter D5 of thesecond valve hole 37 is minimized while permitting theflange 458 to pass therethrough. In this case, if the diameter D7 of the transmission rod 4 b in thesecond valve hole 37 is equal to that of theflange 458, the flow passage area of thesecond valve hole 37 is significantly reduced. This hinders flow of refrigerant out to thesuction chamber 131 from thecontrol pressure chamber 121. This hinders a reliable control for varying the flow passage area. - The configuration, in which the
flange 458 is inserted into therecess 401, permits a sufficient flow passage area of thesecond valve 37 to be obtained, and is thus effective for a reliable control for varying the flow passage area. - An eighteenth embodiment will now be described with reference to FIGS. 30(a), 30(b), and 30(c). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the third embodiment shown in FIGS. 5(a) to 6(c) and the sixteenth embodiment shown in
FIGS. 27 and 28 . - A
recess 671 is formed in afirst valve body 67B, and anauxiliary rod 72 is inserted into therecess 671. Anend face 723 of theauxiliary rod 72 selectively contacts abottom 672 of therecess 671. - In the state of
FIG. 30 (a), theend face 723 of theauxiliary rod 72 is separated from the bottom 672. Thefirst valve body 67B contacts theseating face 691 of thevalve seat 69 so that thefirst valve hole 36 is closed. Since thefirst valve hole 36 is closed, refrigerant in the dischargepressure introducing chamber 103 does not flow into the sharedchamber 38 through thefirst valve hole 36. Also, refrigerant in the dischargepressure introducing chamber 103 does not flow into thecontrol pressure chamber 121 through thefirst valve hole 36, the sharedchamber 38, and thepassage 58. On the other hand, thecylindrical portion 681 of thesecond valve body 68 is out of thesecond valve hole 37 so that thesecond valve hole 37 is open. Since thesecond valve hole 37 is open, refrigerant in thecontrol pressure chamber 121 flows out to the suction chamber 131 (suction pressure zone) through thepassage 58, the sharedchamber 38, thesecond valve hole 37, thechamber 46, and thepassage 57. That is, in the state shown inFIG. 30 (a), adisplacement control valve 32C does not allow refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121, while permitting refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - In the state of
FIG. 30 (b), theend face 723 of theauxiliary rod 12 is separated from the bottom 672. Thefirst valve body 67B is in a position where it contacts theseating face 691 of thevalve seat 69. That is, thefirst valve hole 36 is closed by thefirst valve body 67B. Thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the second valve hole 37), and thesecond valve hole 37 is closed by thesecond valve body 68. - In the state of
FIG. 30 (c), theend face 723 of theauxiliary rod 72 contacts the bottom 672. Thefirst valve body 67B contacts the sealingface 691 of thevalve seat 69 so that thefirst valve hole 36 is closed. Thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the second valve hole 37), and thesecond valve hole 37 is closed by thesecond valve body 68. - In either of the states shown in FIGS. 30(b) and 30(c), the
first valve body 67B is in a position where it closes thefirst valve hole 36, and thesecond valve body 68 is in a position where it closes thesecond valve hole 37. As the electromagnetic force of thesolenoid 41 is reduced from the state ofFIG. 30 (b) (a state in which thecoupling face 722 of theauxiliary rod 72 is in a position W1), thecoupling face 722 is moved from the position W1 toward thefirst valve hole 36, and theend face 723 approaches the bottom 672. As the electromagnetic force of thesolenoid 41 is increased from the state ofFIG. 30 (c) (a state in which thecoupling face 722 of theauxiliary rod 72 is in a position W2), thecoupling face 722 is moved from the position W2 toward the position W1, and theend face 723 is separated from the bottom 672. If thecoupling face 722 of theauxiliary rod 72 is in a displacement range [W1, W2] from the position W1 to the position W2, thecylindrical portion 681 of thesecond valve body 68 is in the second valve hole 37 (theboundary 683 is in the second valve hole 37), and thefirst valve body 67B is in the position where it contacts theseating face 691 of the valve seat 69 (a position where thefirst valve body 67B closes the first valve hole 36). - The displacement range [W1, W2] is a predetermined range of a double closing state of the
transmission rod 45 and theauxiliary rod 72, in which thefirst valve body 67B closes thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. When thetransmission rod 45 and theauxiliary rod 72, which are reciprocating bodies, are in the predetermined displacement range [W1, W2], the double closing state occurs, in which thefirst valve body 67B closes thefirst valve hole 36, and thesecond valve body 68 closes thesecond valve hole 37. This state is obtained because the sum of a distance H21 between theend face 723 and theboundary 683 and a depth H22 of the recess 671 (H21+H22=H2) is greater than the distance K2 between theopen end 371 and theseating face 691. - In FIGS. 30(b) and 30(c), since the
second valve hole 37 is closed, refrigerant in thecontrol pressure chamber 121 does not flow out to the suction chamber 131 (suction pressure zone) Also, since thefirst valve hole 36 is closed, refrigerant in the dischargepressure introducing chamber 103 does not flow into thecontrol pressure chamber 121. That is, in the state shown in FIGS. 30(b) and 30(c), thedisplacement control valve 32C does not allow refrigerant in thecircuit section 28C (discharge pressure zone) to flow into thecontrol pressure chamber 121. Thedisplacement control valve 32C also does not allow refrigerant in thecontrol pressure chamber 121 to flow out to thesuction chamber 131. - The eighteenth embodiment has the same advantages as the advantages (16-1) and (16-2) of the sixteenth embodiment.
- A nineteenth embodiment will now be described with reference to FIGS. 31(a), 31(b), 31(c), and 32. Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the first embodiment shown in FIGS. 1 to 3(c) and the sixteenth embodiment shown in
FIGS. 27 and 28 . - A
first valve body 39 and asecond valve body 68B are formed on atransmission rod 45. Thesecond valve body 68B includes acylindrical portion 681 and atapered portion 682. The diameter of the taperedportion 682 is reduced in a direction from thefirst valve hole 36 to thesecond valve hole 37. Thecylindrical portion 681 of thesecond valve body 68B can enter the second valve hole 37 (theboundary 683 is in the second valve hole 37), thereby closing thesecond valve hole 37. - A diameter D4 of the
cylindrical portion 681 of thesecond valve body 68B is greater than a diameter D3 of thecylindrical portion 391 of thefirst valve body 39. That is, the diameter of thesecond valve hole 37 is greater than the diameter of thefirst valve hole 36. Since the diameter of thefirst valve hole 36 is substantially equal to the diameter D3 of thecylindrical portion 391 of thefirst valve body 39, the diameter of thefirst valve hole 36 is assumed to be the diameter D3. Likewise, since the diameter of thesecond valve hole 37 is substantially equal to the diameter D4 of thecylindrical portion 681 of thesecond valve body 68B, the diameter of thesecond valve hole 37 is assumed to be the diameter D4. - The
second valve hole 37 is connected to thesuction chamber 131 through a throughhole 105 and acommunication passage 106 communicating with the throughhole 105. Thetransmission rod 45, which is a reciprocating body, extends through the throughhole 105. The sharedchamber 38 and thechamber 46 communicate with each other through apassage 107. - The
chamber 46 communicates with aspace 104 between themovable iron core 44 and the fixediron core 42 through apassage 421. Thechamber 46 communicates with aback pressure space 98A at the back of themovable iron core 44 through thepassages space 104 and theback pressure space 98A is similar to the pressure in the shared chamber 38 (corresponding to the control pressure). The sharedchamber 38 is a first control pressure introducing zone that is defined between thefirst valve hole 36 and thesecond valve hole 31. Thechamber 46, thespace 104, and the back pressure space 90A is a second control pressure introducing zone that is defined to connect the shared chamber 38 (first control pressure introducing zone) with thesecond valve hole 37. - The
transmission rod 45 extends through the throughhole 105 such that thechamber 46, which is part of the second control pressure introducing zone, is shut off from thecommunication passage 106 when thesecond valve hole 37 is closed. - The
transmission rod 45 receives a load F5 directed in a direction from thefirst valve hole 36 to thesecond valve hole 3/ due to the pressure in the first control pressure zone (shared chamber 38). The load F5 is obtained by multiplying the pressure in the first control pressure zone by the difference between cross-sectional area of thefirst valve hole 36 and the cross-sectional area of thesecond valve hole 37. Thetransmission rod 45 also receives a load F6 in a direction from thesecond valve hole 37 to thefirst valve hole 36 due to the pressure in the second control pressure introducing zone. The load F6 is obtained by multiplying the cross-sectional area of thesecond hole 37 by the pressure in the second control pressure introducing zone. That is, the load F5, which is applied to thetransmission rod 45 in a direction from thefirst valve hole 36 to thesecond valve hole 37, and the load F6, which is applied to thetransmission rod 45 in a direction from thesecond valve hole 37 to thefirst valve hole 36, oppose each other with thetransmission rod 45 in between. Therefore, the load F5, which is applied to thetransmission rod 45 in a direction from thefirst valve hole 36 to thesecond valve hole 37, is cancelled. A load that is resulted from the pressures in the first and second control pressure introducing zones and actually influences thetransmission rod 45 is a load (F6−F5) that is applied to thetransmission rod 45 in a direction from thesecond valve hole 37 to thefirst valve hole 36. - Pressure loads acting on the
transmission rod 45 will now be described with reference toFIG. 32 . - S1 in
FIG. 32 represents a pressure receiving area of thebellows 50 and themovable body 52 with respect to the displacement direction of thetransmission rod 45. Specifically, S1 represents the area of thebellows 50 and themovable body 52 that receives the pressure in thepressure sensing chamber 48. S2 represents the cross-sectional area of thefirst valve hole 36. The cross-sectional area S2 is expressed by a formula Π(D3/2)2. S3 represents the a cross-sectional area of thesecond valve hole 37. The cross-sectional area S3 is expressed by a formula Π(D4/2)2. S4 represents the cross-sectional area of the throughhole 105. In this embodiment, the diameter D5 of the throughhole 105 and the diameter D4 of thesecond valve hole 37 are equal to each other. The cross-sectional area S4 of the throughhole 105 is expressed by formulae having the same value, or Π(D5/2)2=Π(D4/2)2=S3. - When the pressure in the
pressure sensing chamber 48, the pressure in the pressure sensing chamber, the control pressure, and the suction pressure are represented by PdH, PdL, Pc, and Ps, the pressure load acting on thetransmission rod 45 is expressed by the formula (1).
T=S1×(PdH−PdL)+S2×(Pdt−Pc)+S3×(Pc−Ps)−S4×(Pc−Ps) (1) - The formula (1) indicates that the influence of the control pressure Pc manifests itself as the difference (PdL Pc) between the discharge pressure Pd and the control pressure Pc, and the difference (Pc−Ps) between the control pressure Pc and the suction pressure Ps. The above mentioned load (F6−F5) is expressed by a formula (S3×Pc−S4×Pc).
- The
transmission rod 45 receives a load in a direction from thefirst valve hole 36 to thesecond valve hole 37 due to the pressure in the pressure sensing chamber 48 (discharge pressure PdH). The load is obtained by multiplying the cross-sectional area of thefirst valve hole 36 and the discharge pressure PdH. This load acts against the load (F6−F5) and cancel the load (F6−F5) to a considerable degree by appropriately setting the diameter of thefirst valve hole 36. - In a case where the
passage 107 is riot formed (that is if thechamber 46 is not connected to the shared chamber 38), if the pressure in thechamber 46 is equal to the atmospheric pressure, it is difficult to cancel the load F5, which acts on thetransmission rod 45 and is in a direction from thefirst valve hole 36 to thesecond valve hole 37. That is, the opening degree control of the first and second valve holes 36, 37 is affected by the pressure in the shared chamber 38 (corresponding to the control pressure). As a result, the opening degrees of the first and second valve holes 36, 37 are not reliably controlled. In the illustrated example, thetransmission rod 45 can pass a desired position when moving in a direction from thefirst valve hole 36 to thesecond valve hole 37. - The present embodiment, in which the load F5, which acts on the
transmission rod 45 in a direction from thefirst valve hole 36 to thesecond valve hole 37 is cancelled, avoids problems in the opening degree control of the first and second valve holes 36, 37 ascribable to the pressure in the shared chamber 38 (corresponding to the control pressure). - In this embodiment, since S3=S4, the formula (1) can be changed to the formula (2).
T=S1×(PdH−PdL)+S2×(Pdt−Pc) (2) - The formula (2) indicates that the influence of the control pressure Pc manifests itself as the difference (PdL−Pc) between the discharge pressure ed and the control pressure Pc. That is, in the configuration where the cross-sectional area S4 of the through
hole 105 is equal to the cross-sectional area S3 of tiesecond valve hole 37, the difference between the control pressure Pc and the suction pressure Ps does not manifest itself as a pressure load acting on the transmission rod 45 (reciprocating body). Since the control pressure Pc is approximate to the suction pressure Ps, a change to (fluctuation of) the control pressure Pc made by thedisplacement control valve 32C affects the difference (Pc−PS). On the contrary, since the pressure PdL is greatly different from the control pressure Pc, fluctuations of the control pressure Pc do not fluctuate the difference (PdL−Pc) by a great degree. Therefore, the configuration in which the difference (Pc−Ps) is cancelled, is favorable for reliably controlling the opening degrees of thefirst valve hole 36 and thesecond valve hole 37. - When the
cylindrical portion 391 of thefirst valve body 39 is not in thefirst valve hole 36, the flow passage area of thefirst valve hole 36 is equal to or less than the cross-sectional area [Π((D4/2)2−Π(D8/2)2)], which is obtained by subtracting the cross-sectional area Π(D8/2)2 of a small diameter portion 45d 1 of thetransmission rod 45 from the cross-sectional area Π(D3/2)2 of thefirst valve hole 36. D8 is the diameter of the small diameter portion 45d 1. Even If the flow passage area of thefirst valve hole 36 is small (that is, even if the diameter D3 of thefirst valve hole 36 is small), a flow of refrigerant from thepressure sensing chamber 49 to thecontrol pressure chamber 121 is not hindered. - When the
cylindrical portion 681 of thesecond valve body 68 is not in thesecond valve hole 37, the flow passage area of thesecond valve hole 37 is equal to or less than the cross-sectional area [Π((D4/2)2−Π(D9/2)2)], which is obtained by subtracting the cross-sectional area Π(D9/2)2 of a middle diameter portion 45d 2 of thetransmission rod 45 from the cross-sectional area Π(D4/2)2 of thesecond valve hole 37. D9 is the diameter of the middle diameter portion 45d 2. If the flow passage area of the second valve hole 37 (that is, the diameter D4 of the second valve hole 37) is as small as the flow passage area of the first valve hole 36 (that is, the diameter D3 of the first valve hole 36), flow of refrigerant from thecontrol pressure chamber 121 to thesuction chamber 131 is hindered. This hinders a reliable control for varying the flow passage area. - The configuration, in which the diameter of the
second valve hole 37 is greater than the diameter of thefirst valve hole 36, permits a sufficient flow passage area of thesecond valve 37, and is thus effective for a reliable control for varying the flow passage area. - A twentieth embodiment will now be described with reference to FIGS. 33(a) and 33(b). Like or the same reference numerals are given to those components that are like or the same as the corresponding components of the nineteenth embodiment shown in FIGS. 31 to 32.
- As shown in
FIG. 33 (a), the twentieth embodiment is the same as the nineteenth embodiment except that a diameter D10 of thesecond valve hole 37 is different from a diameter D11 of the throughhole 105. S2 shown inFIG. 33 (b) represents the cross-sectional area of thefirst valve hole 36. The cross-sectional area S2 is expressed by a formula Π(D3/2)2. S5 represents the a cross-sectional area of thesecond valve hole 37. The cross-sectional area S5 is expressed by a formula Π(D10/2)2. S6 represents the cross-sectional area of the throughhole 105. The cross-sectional area S4 of the throughhole 105 is expressed by a formula Π(D11/2)2. In this embodiment, the equation S6−S5−S2 is satisfied. - In this embodiment, since the equation S6=S5−S2 is satisfied, the formula (1) can be changed to the formula (3).
T=S1×(PdH−PdL)+S2×(Pdt−Ps) (3) - The formula (3) indicates that the influence of the control pressure Pc does not manifest itself as a pressure load acting on the transmission rod 45 (reciprocating body). That is, in the configuration where the difference between the cross-sectional area S5 of the
second valve hole 37 and the cross-sectional area S6 of the throughhole 105 is equal to the cross-sectional area S2 of thefirst valve hole 36 does not permit the control pressure Pc to manifest itself as a pressure load acting on thetransmission rod 45. Thedisplacement control valve 32C is configured to control the control pressure Pc, thereby controlling the displacement of thevariable displacement compressor 10. Therefore, the configuration in which the control pressure Pc is cancelled so that the control pressure Pc does not affect a pressure load T is more favorable for reliably controlling the opening degrees of thefirst valve hole 36 and thesecond valve hole 37 than the nineteenth embodiment. - The invention may be embodied in the following forms.
- (1) In the first embodiment, the tapered
portion 392 of thefirst valve body 39 may be omitted, and atapered portion 363 may he formed in thefirst valve hole 36 as shown inFIG. 23 . That is, the opening of thefirst valve hole 36, which corresponds to thefirst valve body 39 functioning as a fixed valve body, may widen toward thefirst valve body 39. The taperedportion 363, which is a groove in the first valve hole, 36 has a similar function as the taperedportion 392 in the first embodiment. In this case, anupper end 365 of the taperedportion 363 of thefirst valve hole 36 functions as a second initial contact portion, which is a portion of the circumferential surface of thefirst valve hole 36 that initially contacts theboundary 393 when thefirst valve hole 36 is switched from the open state to the closed state. That is, to ensure that the predetermined displacement range [W1, W2] be created, the distance H1 between the displacement transmission portion (the step 451) and the first initial contact portion (theboundary 393 of the first valve body 39) is different from the distance K1 between the second initial contact portion (theupper end 365 of the tapered portion 363) and theseating face 351. - (2) In the third embodiment, the tapered
portion 682 of thesecond valve body 68 may be omitted, and atapered portion 373 may be formed in thesecond valve hole 37 as shown inFIG. 24 . The taperedportion 373 in thesecond valve hole 37 has a similar function as the taperedportion 682 in the third embodiment. In this case, alower end 375 of the taperedportion 373 of thesecond valve hole 37 functions as a second initial contact portion, which is a portion of the circumferential surface of thesecond valve hole 37 that initially contacts theboundary 683 when thesecond valve hole 37 is switched from the open state to the closed state. - (3) In the sixth embodiment, the tapered
portion 395 of thefirst valve body 39A may be omitted, and a tapered portion 364 may be formed in thefirst valve hole 36A as shown inFIG. 25 . The tapered portion 364 in thefirst valve hole 36A has a similar function as the taperedportion 395 in the sixth embodiment. - (4) In the eighth embodiment, the tapered
portion 685 of thesecond valve body 68A may be omitted, and atapered portion 374 may ho formed in thesecond valve hole 37A as shown inFIG. 26 . The taperedportion 374 in thesecond valve hole 37A has a similar function as the taperedportion 685 in the eighth embodiment. - (5) A displacement control valve of a variable electromagnetic force type may be used, which has a pressure sensing member that senses a pressure difference between two positions in a suction pressure zone.
- (6) The present invention may be applied to a clutchless type variable displacement compressor. In such a variable displacement compressor, circulation of refrigerant is stopped in an external refrigerant circuit when the inclination angle of a swash plate is the minimum.
- (7) In the seventeenth and eighteenth embodiments, the
first valve body 67B and thesecond valve body 40B may be used as first and second valve bodies. - (8) In the nineteenth and twentieth embodiments, the
first valve body 67B may be used as a first valve body. - (9) In the nineteenth and twentieth embodiments, the
second valve body 40B may be used as a second valve body. - The present examples and embodiments are to be considered as illustrative and not restrictive and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.
Claims (28)
1. A displacement control valve for a variable displacement compressor, the compressor having: a discharge pressure zone exposed to the pressure of refrigerant that has been compressed by the compressor; a suction pressure zone exposed to the pressure of refrigerant that is drawn into the compressor; a control pressure chamber; a supply passage that connects the discharge pressure zone to the control pressure chamber; and a discharge passage that connects the suction pressure zone to the control pressure chamber, wherein the control valve adjusts the pressure of the control pressure chamber by supplying refrigerant in the discharge pressure zone to the control pressure chamber through the supply passage and discharging refrigerant in the control pressure chamber to the suction pressure zone through the discharge passage, thereby controlling the displacement of the compressor, wherein the control valve comprises:
a first valve hole forming a part of the supply passage;
a first valve body that selectively opens and closes the first valve hole;
a second valve hole forming a part of the discharge passage;
a second valve body that selectively opens and closes the second valve hole; and
a reciprocating body that is capable of being displaced and reciprocated, wherein displacement of the reciprocating body is transmitted to each of the first and second valve bodies so that each valve body opens or closes the corresponding valve hole, wherein, when the reciprocating body is within a predetermined displacement range, a double closing state occurs, in which the first valve body closes the first valve hole and the second valve hole closes the second valve hole,
wherein, when the reciprocating body is out of the displacement range, a single closing state occurs, in which only one of the first valve body and the second valve body closes the corresponding one of the valve holes.
2. The control valve according to claim 1 , further comprising:
a distance changing mechanism that changes the distance between the first valve body and the second valve body according to the position of the reciprocating body when the reciprocating body is displaced, thereby causing the double closing state or the single closing state to occur, and wherein, when at least one of the first and second valve bodies is at a specific position and closes the corresponding valve hole, the distance changing mechanism permits the reciprocating body to be displaced relative to the valve body at the specific position.
3. The control valve according to claim 2 , wherein only one of the first and second valve bodies is a fixed valve body that is fixed to the reciprocating body, and wherein, when the reciprocating body is in the predetermined displacement range, the fixed valve body enters the valve hole that corresponds to the fixed valve body to close the valve hole.
4. The control valve according to claim 3 , wherein the fixed valve body includes a tapered portion that enters and exits the corresponding valve hole.
5. The control valve according to claim 3 , wherein an opening of the valve hole that corresponds to the fixed valve body widens toward the fixed valve body.
6. The control valve according to claim 3 ,
wherein one of the first and second valve bodies that is not the fixed valve body is a sliding valve body that is slidably fitted to the reciprocating body, wherein the sliding valve body is capable of being moved between a closing position for closing the corresponding valve hole and an opening position for opening the valve hole,
wherein the reciprocating body includes a displacement transmission portion that contacts the sliding valve body to transmit displacement of the reciprocating body to the sliding valve body, thereby moving the sliding valve body from the closing position to the opening position, and
wherein the distance changing mechanism includes the displacement transmission portion and an urging member for urging the sliding valve body toward the displacement transmission portion.
7. The control valve according to claim 6 , further comprising a seating face in which a valve hole that corresponds to the sliding valve body opens,
wherein the sliding valve body has a valve closing face that contacts the seating face to close the corresponding valve hole, the displacement transmission portion being capable of contacting the valve closing face,
wherein the fixed valve body has a first initial contact portion, and the circumferential surface of the valve hole that corresponds to the fixed valve body has a second initial contact portion, wherein, when the fixed valve body switches the corresponding valve hole from an open state to a closed state, the first initial contact portion initially contacts the circumferential surface of the corresponding valve hole, and the second initial contact portion initially contacts the first initial contact portion, and
wherein, to ensure that a predetermined displacement range be created, the distance between the displacement transmission portion and the first initial contact portion is different from the distance between the second initial contact portion and the seating face.
8. The control valve according to claim 6 , further comprising a seating face in which a valve hole that corresponds to the sliding valve body opens,
wherein the sliding valve body has a valve closing face that contacts the corresponding seating face to close the corresponding valve hole, and a displacement receiving face that is capable of contacting the displacement transmission portion, the valve closing face and the displacement receiving face being separated from each other with respect to a direction of displacement of the reciprocating body,
wherein the fixed valve body has a first initial contact portion, and the circumferential surface of the valve hole that corresponds to the fixed valve body has a second initial contact portion, wherein, when the fixed valve body switches the corresponding valve hole from an open state to a closed state, the first initial contact portion initially contacts the circumferential surface of the corresponding valve hole, and the second initial contact portion initially contacts the first initial contact portion, and
wherein, to ensure that a predetermined displacement range be created, the sum of the distance between the displacement transmission portion and the first initial contact portion and the distance between the valve closing face and the displacement receiving face is different from the distance between the second initial contact portion and the seating face.
9. The control valve according to claim 8 , wherein the sliding valve body has a recess, a hole through which the reciprocating body extends being formed in a bottom of the recess, and wherein an open end of the recess forms the valve closing face, and the bottom of the recess forms the displacement receiving face.
10. The control valve according to claim 2 , wherein the first valve body and the second valve body are slidably fitted to the reciprocating body, and
wherein the reciprocating body includes;
a first displacement transmission portion that contacts the first valve body to transmit displacement of the reciprocating body to the first valve body, thereby moving the first valve body from the closing position to the opening position, and
a second displacement transmission portion that contacts the second valve body to transmit displacement of the reciprocating body to the second valve body, thereby moving the second valve body from the closing position to the opening position,
wherein the distance changing mechanism includes the first displacement transmission portion, the second displacement transmission portion, a first urging member for urging the first valve body toward the first displacement transmission portion, and a second urging member for urging the second valve body toward the second displacement transmission portion.
11. The control valve according to claim 10 , further comprising a seating face in which the first valve hole opens and a seating face in which the second valve hole opens,
wherein, to ensure that a predetermined displacement range be created, the distance between the seating faces is different from the distance between the first displacement transmission portion and the second displacement transmission portion.
12. The control valve according to claim 1 , wherein the first valve body and the second valve body are fixed to the reciprocating body, and
wherein, when the reciprocating body is in the predetermined displacement range, the first valve body enters the first valve hole to close the first valve body, and the second valve body enters the second valve hole to close the second valve hole.
13. The control valve according to claim 12 ,
wherein the first and second valve bodies each have a first initial contact portion, and the circumferential surface of each valve hole has a second initial contact portion, wherein, when one of the first and second valve bodies switches the corresponding valve hole from an open state to a closed state, the first initial contact portion of the one of the first and second valve bodies initially contacts the circumferential surface of the valve hole, and the second initial contact portion of the valve hole initially contacts the first initial contact portion, and
wherein, to ensure that a predetermined displacement range be created, the distance between the first initial contact portions is different from the distance between the second initial contact portions.
14. The control valve according to claim 12 , wherein the first and second valve bodies each have a tapered portion, and where each tapered portion enters and exits the corresponding valve hole.
15. The control valve according to claim 14 , wherein, to ensure that a predetermined displacement range be created, the distance between proximal ends of the tapered portions is different from the distance between open ends of the first and second valve holes.
16. The control valve according to claim 1 ,
wherein a shared chamber is defined between the first valve hole and the second valve hole, the first valve hole and the second valve hole opening to the shared chamber,
wherein the shared chamber communicates with the control pressure chamber, the first valve hole communicates with the discharge pressure zone, and the second valve hole communicates with tie suction pressure zone, and
wherein, when the first valve body opens the first valve hole, the shared chamber communicates with the discharge pressure zone through the first valve hole, and, when the second valve body opens the second valve hole, the shared chamber communicates with the suction pressure zone through the second valve hole.
17. The control valve according to claim 1 ,
wherein the first valve hole is connected to the second valve hole, the reciprocating body extending through the first valve hole and the second valve hole,
wherein the reciprocation body has a separation portion that separates the second valve hole from the first valve hole,
wherein the control pressure chamber is connected to the discharge pressure zone through the first valve hole, and is connected to the suction pressure zone through the second valve hole, and
wherein, when the first valve body opens the first valve hole, the control pressure chamber communicates with the discharge pressure zone through the first valve hole, and, when the second valve body opens the second valve hole, the control pressure chamber communicates with the suction pressure zone through the second valve hole.
18. The control valve according to claim 16 , further comprising:
a first discharge pressure chamber and a second discharge pressure chamber, which are arranged with the first and second valve holes in between,
wherein the reciprocating body has a first end that extends through the first valve hole and receives the pressure of the first discharge pressure chamber, and a second end that extends through the second valve hole and receives the pressure of the second discharge pressure chamber, and
wherein the pressure of the first discharge pressure chamber acts against the pressure of the second discharge pressure chamber through the reciprocating body.
19. The control valve according to claim 16 , further comprising:
a discharge pressure introducing chamber that is exposed to the pressure of the discharge pressure zone; and
a suction pressure introducing chamber that is exposed to the pressure of the suction pressure zone,
wherein the first valve hole and the second valve hole are arranged between the discharge pressure introducing chamber and the suction pressure introducing chamber,
wherein the reciprocating body has a first end that extends through the first valve hole and receives the pressure of the discharge pressure introducing chamber, and a second end that extends through the second valve hole and receives the pressure of the suction pressure introducing chamber, and
wherein the pressure of the suction pressure introducing chamber acts against the pressure of the discharge pressure introducing chamber through the reciprocating body.
20. The control valve according to claim 19 , further comprising:
a solenoid for urging the reciprocating body from the second valve hole toward the first valve hole; and
a first urging spring and a second urging spring that urge the reciprocating body from the first valve hole toward the second valve hole.
21. The control valve according to claim 1 , further comprising:
a control pressure introducing chamber that is exposed to the pressure of the control pressure chamber, wherein the control pressure introducing chamber is defined between the first valve hole and the second valve hole, the control pressure introducing chamber connecting the first valve hole and the second valve hole to each other,
wherein the diameter of the first valve hole is the same as the diameter of the second valve hole.
22. The control valve according to claim 1 , further comprising:
a first control pressure introducing zone and a second control pressure introducing zone that are exposed to the pressure of the control pressure chamber,
wherein the first control pressure introducing zone is defined between the first valve hole and the second valve hole,
wherein the first valve hole opens to the first control pressure introducing zone,
wherein the second valve hole opens to the first control pressure introducing zone and the second control pressure introducing zone,
wherein the first control pressure introducing zone is connected to the second control pressure introducing zone,
wherein the pressure of the first control pressure introducing zone acts against the pressure of the second control pressure introducing zone through the reciprocating body, and
wherein the diameter of the first valve hole is different from the diameter of the second valve hole.
23. The control valve according to claim 22 , wherein the diameter of the second valve hole is greater than tie diameter of the first valve hole.
24. The control valve according to claim 22 ,
wherein the second valve hole opens to the suction pressure zone through a through hole that permits the reciprocating body to extend therethrough and a communication passage that communicates with the through hole, and
wherein, closing the second valve hole, the reciprocating body disconnects the second control pressure introducing zone from the communication passage.
25. The control valve according to claim 24 , wherein the cross-sectional area of the through hole is the same as the cross-sectional area of the second valve hole.
26. The control valve according to claim 24 , wherein the cross-sectional area of the second valve hole is greater than the cross-sectional area of the first valve hole, and
wherein the cross-sectional area of the through hole is the same as the value obtained by subtracting the cross-sectional area of the first valve hole from the cross-sectional area of the second valve hole.
27. The control valve according to claim 1 , further comprising a solenoid for actuating the reciprocating body.
28. The control valve according to claim 1 , further comprising:
a pressure sensing member that detects a pressure difference between two points in the discharge pressure zone or a pressure difference between two points in the suction pressure zone, wherein the pressure sensing member displaces the reciprocating body by using the pressure difference.
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
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JP2004190005 | 2004-06-28 | ||
JP2004-190005 | 2004-06-28 | ||
JP2004-253450 | 2004-08-31 | ||
JP2004253450 | 2004-08-31 | ||
JP2004-291724 | 2004-10-04 | ||
JP2004291724A JP2006097665A (en) | 2004-06-28 | 2004-10-04 | Capacity control valve in variable displacement compressor |
Publications (1)
Publication Number | Publication Date |
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US20050287014A1 true US20050287014A1 (en) | 2005-12-29 |
Family
ID=34937617
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/167,708 Abandoned US20050287014A1 (en) | 2004-06-28 | 2005-06-27 | Displacement control valve for variable displacement compressor |
Country Status (4)
Country | Link |
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US (1) | US20050287014A1 (en) |
EP (1) | EP1612420B1 (en) |
JP (1) | JP2006097665A (en) |
DE (1) | DE602005016046D1 (en) |
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2005
- 2005-06-22 DE DE602005016046T patent/DE602005016046D1/en active Active
- 2005-06-22 EP EP05013509A patent/EP1612420B1/en not_active Expired - Fee Related
- 2005-06-27 US US11/167,708 patent/US20050287014A1/en not_active Abandoned
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Cited By (37)
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US7273356B2 (en) * | 2003-03-28 | 2007-09-25 | Sanden Corporation | Control valve device for variable capacity type swash plate compressor |
US20040191077A1 (en) * | 2003-03-28 | 2004-09-30 | Yoshihiro Ochiai | Control valve device for variable capacity type swash plate compressor |
US20060039799A1 (en) * | 2004-08-19 | 2006-02-23 | Tgk Co., Ltd. | Control valve for variable displacement compressor |
US20070012057A1 (en) * | 2004-12-24 | 2007-01-18 | Satoshi Umemura | Displacement control mechanism for variable displacement compressor |
US7523620B2 (en) | 2004-12-24 | 2009-04-28 | Kabushiki Kaisha Toyota Jidoshokki | Displacement control mechanism for variable displacement compressor |
EP1835176A3 (en) * | 2006-03-15 | 2008-09-10 | Delphi Technologies, Inc. | Two-set point pilot piston control valve |
US20070217923A1 (en) * | 2006-03-15 | 2007-09-20 | Warren Matthew R | Two set-point pilot piston control valve |
US7611335B2 (en) * | 2006-03-15 | 2009-11-03 | Delphi Technologies, Inc. | Two set-point pilot piston control valve |
EP1835176A2 (en) | 2006-03-15 | 2007-09-19 | Delphi Technologies, Inc. | Two-set point pilot piston control valve |
US20160053755A1 (en) * | 2013-03-22 | 2016-02-25 | Sanden Holdings Corporation | Control Valve And Variable Capacity Compressor Provided With Said Control Valve |
US20150044067A1 (en) * | 2013-08-08 | 2015-02-12 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate type compressor |
US20150044065A1 (en) * | 2013-08-08 | 2015-02-12 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate type compressor |
US9581150B2 (en) * | 2013-08-08 | 2017-02-28 | Kabushiki Kaisha Toshiba Jidoshokki | Variable displacement swash plate type compressor |
US20150104334A1 (en) * | 2013-10-10 | 2015-04-16 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate compressor |
US9518568B2 (en) * | 2014-01-30 | 2016-12-13 | Kabushiki Kaisha Toyota Jidoshokki | Swash plate type variable displacement compressor |
US20150211502A1 (en) * | 2014-01-30 | 2015-07-30 | Kabushiki Kaisha Toyota Jidoshokki | Swash plate type variable displacement compressor |
US20150219082A1 (en) * | 2014-02-03 | 2015-08-06 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement type swash plate compressor |
US9631612B2 (en) * | 2014-02-03 | 2017-04-25 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement type swash plate compressor |
US20150275874A1 (en) * | 2014-03-25 | 2015-10-01 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement type swash plate compressor |
US9506459B2 (en) * | 2014-03-25 | 2016-11-29 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate type compressor |
US20150275875A1 (en) * | 2014-03-25 | 2015-10-01 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate type compressor |
CN111656011A (en) * | 2018-01-31 | 2020-09-11 | 三电汽车部件株式会社 | Capacity control valve for variable capacity compressor |
US20210363980A1 (en) * | 2018-07-12 | 2021-11-25 | Eagle Industry Co., Ltd. | Capacity control valve |
US11555489B2 (en) | 2018-07-12 | 2023-01-17 | Eagle Industry Co., Ltd. | Capacity control valve |
US11536257B2 (en) | 2018-07-12 | 2022-12-27 | Eagle Industry Co., Ltd. | Capacity control valve |
US11480166B2 (en) * | 2018-07-13 | 2022-10-25 | Eagle Industry Co., Ltd. | Capacity control valve |
US11473683B2 (en) | 2018-08-08 | 2022-10-18 | Eagle Industry Co., Ltd. | Capacity control valve |
US11873805B2 (en) | 2018-08-08 | 2024-01-16 | Eagle Industry Co., Ltd. | Capacity control valve |
US11473684B2 (en) | 2018-12-04 | 2022-10-18 | Eagle Industry Co., Ltd. | Capacity control valve |
US11598437B2 (en) | 2019-03-01 | 2023-03-07 | Eagle Industry Co., Ltd. | Capacity control valve |
US20220154838A1 (en) * | 2019-04-03 | 2022-05-19 | Eagle Industry Co., Ltd. | Capacity control valve |
US11754194B2 (en) * | 2019-04-03 | 2023-09-12 | Eagle Industry Co., Ltd. | Capacity control valve |
US11821540B2 (en) | 2019-04-03 | 2023-11-21 | Eagle Industry Co., Ltd. | Capacity control valve |
US11841090B2 (en) | 2019-04-03 | 2023-12-12 | Eagle Industry Co., Ltd. | Capacity control valve |
US11927275B2 (en) | 2019-04-03 | 2024-03-12 | Eagle Industry Co., Ltd. | Capacity control valve |
EP3961075A4 (en) * | 2019-04-24 | 2023-01-04 | Eagle Industry Co., Ltd. | Capacity control valve |
EP4242504A3 (en) * | 2019-04-24 | 2023-11-15 | Eagle Industry Co., Ltd. | Capacity control valve |
Also Published As
Publication number | Publication date |
---|---|
EP1612420A3 (en) | 2006-11-22 |
EP1612420A2 (en) | 2006-01-04 |
EP1612420B1 (en) | 2009-08-19 |
DE602005016046D1 (en) | 2009-10-01 |
JP2006097665A (en) | 2006-04-13 |
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Legal Events
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AS | Assignment |
Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:UMEMURA, SATOSHI;KAWAGUCHI, MASAHIRO;OTA, MASAKI;AND OTHERS;REEL/FRAME:016742/0566 Effective date: 20050623 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |