EP0283963B1 - wobble plate type compressor with variable displacement mechanism - Google Patents
wobble plate type compressor with variable displacement mechanism Download PDFInfo
- Publication number
- EP0283963B1 EP0283963B1 EP88104389A EP88104389A EP0283963B1 EP 0283963 B1 EP0283963 B1 EP 0283963B1 EP 88104389 A EP88104389 A EP 88104389A EP 88104389 A EP88104389 A EP 88104389A EP 0283963 B1 EP0283963 B1 EP 0283963B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- compressor
- plate
- central bore
- cylinder block
- 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.)
- Expired - Lifetime
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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
- F04B25/00—Multi-stage pumps
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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
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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
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
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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
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
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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
- F04B2027/184—Valve controlling parameter
- F04B2027/1845—Crankcase pressure
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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
- F04B2027/184—Valve controlling parameter
- F04B2027/1859—Suction pressure
Definitions
- the present invention relates to a refrigerant compressor, and more particularly, to a wobble plate type piston compressor for an air conditioning system in which the compressor includes a mechanism for adjusting the capacity of the compressor.
- thermal control is accomplished by intermittent operation of the compressor in response to a signal from a thermostat located in the room being cooled.
- the refrigerant capacity of the air conditioning system generally need not be very large in order to handle supplementary cooling due to further temperature changes in the room or for keeping the room at the desired temperature.
- the most common technique for controlling the output of the compressor is by intermittent operation of the compressor.
- intermittent operation of the compressor results in intermittent application of a relatively large load to the driving mechanism of the compressor in order to drive the compressor.
- the compressor In automobile air conditioning compressors, the compressor is driven by the engine of the automobile through an electromagnetic clutch. These automobile air conditioning compressors face the same intermittent load problems described above once the passenger compartment reaches a desired temperature. Control of the compressor normally is accomplished by intermittent operation of the compressor through the electromagnetic clutch which couples the automobile engine to the compressor. Thus, the relatively large load which is required to drive the compressor is intermittently applied to the automobile engine.
- passageway 391 through cylinder block 101 tends to decrease the mechanical strength and structural integrity of cylinder block 101.
- the mechanical strength and structural integrity of the cylinder block in a wobble plate type compressor is of considerable importance due to the high pressures which are present inside the cylinder block during operation of the compressor.
- the diameter of the cylinder block 101 must be enlarged, further adding to manufacturing cost, weight and overall size of the compressor.
- a refrigerant compressor is provided as indicated in claim 1.
- One embodiment of this invention is providing a refrigerator compressor wherein the central bore connects a part of the communicating path with a female thread portion for an adjusting screw which adjusts the axial location of the compressor drive shaft.
- Figure 1 is a vertical cross-sectional view of a refrigerant compressor according to one embodiment of this invention.
- Figure 2 is a cross-sectional view taken substantially along line A-A of Figure 1.
- Figure 3 is a vertical cross-sectional view of a refrigerant compressor according to a second embodiment of this invention.
- Figure 4 is a vertical cross-sectional view of a refrigerant compressor according to a third embodiment of this invention.
- Figure 5 is a vertical cross-sectional view of a refrigerant compressor according to a fourth embodiment of this invention.
- Figure 6 is a vertical cross-sectional view of a refrigerant compressor according to a fifth embodiment of this invention.
- Figure 7 is a cross-section view taken along line A-A of Figure 1 according to a sixth embodiment of this invention.
- Figure 8 is a vertical cross-sectional view of a prior art refrigerant compressor.
- the compressor 1 includes a closed cylindrical housing assembly 10 formed by a cylinder block 101, a crank chamber 13 within the cylinder block 101, a front end plate 11 and a rear end plate 25.
- the front end plate 11 is mounted on the left end portion of the crank chamber 13, as shown in Figure 1, by a plurality of bolts (not shown).
- the rear end plate 25 and a valve plate 24 are mounted on cylinder block 101 by a plurality of bolts (not shown).
- An opening 111 is formed in front end plate 11 for receiving drive shaft 12.
- Drive shaft 12 is rotatably supported by front end plate 11 through a bearing 20 which is disposed within opening 111.
- the inner end portion of drive shaft 12 is also rotatably supported by cylinder block 101 through a bearing 23 which is disposed within a central bore 102.
- Central bore 102 is a cavity formed in the center portion of cylinder block 101.
- a thrust needle bearing 22a is disposed between the inner end surface of front end plate 11 and the adjacent axial end surface of a cam rotor (input drive rotor) 14.
- Cam rotor 14 is fixed on drive shaft 12 by a pin member 15 which penetrates cam rotor 14 and drive shaft 12.
- Cam rotor 14 is provided with an arm 141 having slot 142.
- a slant plate 16 has an opening 161 through which passes drive shaft 12.
- An axial annular projection 162 extends from the circumference of opening 161 in the front end surface of slant plate 16.
- Slant plate 16 includes an arm 163 having a pin 21 which is inserted in slot 142.
- Cam rotor 14 and slant plate 16 are joined by the hinged joint of pin 21 and slot 142. The pin 21 is able to slide within slot 142 so that the angular position of slant plate 16 can be changed with respect to the longitudinal axis of drive shaft 12.
- a wobble plate 17 is rotatably mounted on slant plate 16.
- the rotation of wobble plate 17 is prevented by a fork-shaped slider 172 which is attached to the outer peripheral end of wobble plate 17 and is slidably mounted on a sliding rail 173 held between front end plate 11 and cylinder block 101.
- wobble plate 17 wobbles in a non-rotating manner in spite of the rotation of cam rotor 14.
- Cylinder block 101 has a plurality of annularly arranged cylinder chambers 32 in which respective pistons 33 slide. All pistons 33 are connected to wobble plate 17 by a corresponding plurality of connecting rods 34. A ball 34a at one end of rod 34 is received in a socket 331 of pistons 33 and ball 34b at the other end of rod 34 is received in a socket 171 of wobble plate 17. It should be understood that, although only one such ball socket connection is shown in the drawing, there are a plurality of sockets arranged peripherally around wobble plate 17 to receive the balls of various rods, and that each piston 33 is formed with a socket for receiving the other ball of rods 34.
- Rear end plate 25 is shaped to define suction chamber 35 and a discharge chamber 36.
- the axial position of drive shaft 12 can be adjusted by an adjusting screw 27 into a threaded portion 41 of central bore 102. That is to say, the axial clearance between cam rotor 14 and front end plate 11 through bearing 22a can be adjusted by adjusting screw 27.
- Central bore 102 is partitioned into a front chamber 102a and a rear chamber 102b by adjusting screw 27.
- Front chamber 102a communicates with crank chamber 13.
- a plurality of axial grooves 42 are formed at inner peripheral threaded portion 41 of central bore 102 to communicate between front chamber 102a and rear chamber 102b of central bore 102.
- a groove 43 is formed at the front end surface of cylinder block 101 facing gasket 37. Groove 43 extends radially from rear chamber 102b of central bore 102 to a pressure sensitive chamber 44 which is formed in the cylinder block 101. Therefore the crank chamber 13 communicates with pressure sensitive chamber 44 through grooves 42 and groove 43. A hole 45 is formed through gasket 37, valve plate 24 and gasket 38 to connect pressure sensitive chamber 44 and suction chamber 35.
- a bellows valve device 46 is fixed to one surface of pressure sensitive chamber 44 with a valve 461 arranged to close off hole 45 in response to the pressure within pressure sensitive chamber 44. The operation of bellows valve device 46 is as follows: The pressure within crank chamber 13 is communicated to pressure sensitive chamber 44 through grooves 42 and 43.
- the pressure within pressure sensitive chamber 44 is the same as the pressure within crank chamber 13.
- the bellows of the bellows valve device 46 expands causing valve 461 to close hole 45. Therefore when the compressor is not being driven, the pressure within crank chamber 13 is balanced pressure, valve 461 of the bellows valve device 46 closes the hole 45.
- the bellows of bellows valve device 46 is compressed causing valve 461 to open hole 45.
- drive shaft 12 is rotated by the engine of the vehicle through an electromagnetic clutch.
- Cam rotor 14 is rotated together with drive shaft 12 to cause a non-rotating wobbling motion of wobble plate 17.
- Rotating motion of wobble plate 17 is prevented by fork-shaped slider 172 which is attached to the outer peripheral end of wobble plate 17 and is slidably mounted on sliding rail 173 held between front end plate 11 and cylinder block 101.
- a wobble plate 17 moves, pistons 33 reciprocate out of phase in their respective cylinders 32.
- the refrigerant gas which is introduced into suction chamber 35 from a fluid inlet port 35a, is taken into each cylinder 32 and compressed.
- the compressed refrigerant is discharged to discharge chamber 36 from each cylinder 32 through discharge port 24b, and therefrom into an external fluid circuit, for example, a cooling circuit, through a fluid outlet port 36b.
- crank chamber 13 At the beginning of compressor operation, hole 45 is closed by valve 461 of the bellows valve device 46 because the pressure within crank chamber 13 is low. As the compressor operates, the pressure within crank chamber 13 gradually rises to create a small pressure difference between crank chamber 13 and suction chamber 35. This pressure difference occurs because blow-by gas, which leaks from the cylinder chambers to crank chamber 13 through a gap between pistons 33 and cylinders 32 during the compression stroke, is contained in crank chamber 13.
- pistons 33 The movement of pistons 33 is hindered by the pressure difference between crank chamber 13 and suction chamber 35, i.e., as the pressure in the crank chamber approaches the mid-pressure of the compressed gas in the cylinder chambers during the suction stroke, movement of the pistons is hindered because the slant angle of slant plate 16 gradually decreases until it approaches zero, i.e., slant plate 16 would be perpendicular to the drive shaft 12. As the slant angle of slant plate 16 decreases, the stroke of pistons 33 in the cylinders 32 is reduced and the capacity of the compressor gradually decreases.
- crank chamber 13 When the pressure of crank chamber 13 and pressure sensitive chamber 44 rises over the predetermined pressure, the bellows of bellows valve device 46 is sufficiently compressed and valve 461 of bellows valve device 46 opens hole 45. Simultaneously, crank chamber 13 communicates with suction chamber 35 through a central bore 102 via grooves 42 and groove 43 formed at the front end surface of cylinder block 101, pressure sensitive chamber 44 and hole 45. Accordingly, the pressure of crank chamber 13 falls to the pressure of suction chamber 35. In this condition, wobble plate 17 usually is urged toward slant plate 16 during the compression stroke of the pistons 33 so that slant plate 16 moves toward rotor 14.
- the bellows valve device 46 is disposed in pressure sensitive chamber 44 formed in the cylinder block 101. Bellows valve device 46 also may be disposed in suction chamber 35 as shown in Figure 3. In the embodiment shown in Figure 3, the opening and closing of hole 45 are accordingly controlled by the change of pressure in suction chamber 35.
- annular shim 51 is disposed between adjusting screw 27 screwed into the threaded portion 41 of central bore 102 and the inner end of the drive shaft 12. Shim 51 prevents friction which would otherwise occur by the contact of rotating drive shaft 12 with adjusting screw 27.
- An annular thrust bearing 61 may also be used in place of shim 51 as shown in Figure 5.
- a refrigerant compressor 1 is shown in accordance with a further embodiment of the present invention.
- an electromagnetic valve 40 is disposed in suction chamber 35 in place of bellows valve device 46 which is shown in Figure 3.
- an adjusting screw 271 is shown in accordance with another embodiment of the present invention.
- a plurality of axial grooves 421 are formed at an outer peripheral surface of adjusting screw 271 to communicate the front chamber 102a and rear chamber 102b of central bore 102.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Description
- The present invention relates to a refrigerant compressor, and more particularly, to a wobble plate type piston compressor for an air conditioning system in which the compressor includes a mechanism for adjusting the capacity of the compressor.
- Generally, in air conditioning apparatus, thermal control is accomplished by intermittent operation of the compressor in response to a signal from a thermostat located in the room being cooled. Once the temperature in the room has been lowered to a desired temperature, the refrigerant capacity of the air conditioning system generally need not be very large in order to handle supplementary cooling due to further temperature changes in the room or for keeping the room at the desired temperature. Accordingly, after the room has cooled down to the desired temperature, the most common technique for controlling the output of the compressor is by intermittent operation of the compressor. However, intermittent operation of the compressor results in intermittent application of a relatively large load to the driving mechanism of the compressor in order to drive the compressor.
- In automobile air conditioning compressors, the compressor is driven by the engine of the automobile through an electromagnetic clutch. These automobile air conditioning compressors face the same intermittent load problems described above once the passenger compartment reaches a desired temperature. Control of the compressor normally is accomplished by intermittent operation of the compressor through the electromagnetic clutch which couples the automobile engine to the compressor. Thus, the relatively large load which is required to drive the compressor is intermittently applied to the automobile engine.
- Furthermore, since the compressor of an automobile air conditioner is driven by the engine of the automobile, the rotation frequency of the drive mechanism changes from moment to moment, which causes the refrigerant capacity to change in proportion to the rotation frequency of the engine. Since the capacity of the evaporator and condenser of the air conditioner does not change when the compressor is driven at high rotation speed, the compressor performs useless work. To avoid performing useless work, prior art automobile air conditioning compressors often are controlled by intermittent operation of the magnetic clutch. Again, this results in a large load being intermittently applied to the automobile engine.
- Recently, it was recognized that it is desirable to provide a wobble plate type piston compressor with a displacement or capacity adjusting mechanism to control the compression ratio in response to demand. In a wobble plate type piston compressor, control of the compression ratio can be accomplished by changing the slant angle of the sloping surface of the slant plate in response to operation of the valve control mechanism as disclosed in US-A- 4,586,874 Referring to Figure 8, this application discloses a mechanism for controlling the compression ratio of the compressor which includes a
passageway 391 formed betweensuction chamber 35 andcrank chamber 13. Thispassageway 391 is formed by drilling a hole throughcylinder block 101 andvalve plate 24. The machining operation required to form thepassageway 391 adds to the manufacturing cost of the compressor. Furthermore, the formation ofpassageway 391 throughcylinder block 101 tends to decrease the mechanical strength and structural integrity ofcylinder block 101. The mechanical strength and structural integrity of the cylinder block in a wobble plate type compressor is of considerable importance due to the high pressures which are present inside the cylinder block during operation of the compressor. Thus, in order to maintain the requisite strength and integrity, the diameter of thecylinder block 101 must be enlarged, further adding to manufacturing cost, weight and overall size of the compressor. - In order to overcome the above noted deficiencies of wobble plate type compressors known in the prior art, a refrigerant compressor is provided as indicated in
claim 1. - One embodiment of this invention is providing a refrigerator compressor wherein the central bore connects a part of the communicating path with a female thread portion for an adjusting screw which adjusts the axial location of the compressor drive shaft.
- An axially penetrating hole in the cylinder block is not anymore necessary.
- Further objects, features and other aspects of this invention will be understood from the following detailed description of the preferred embodiment of this invention with reference to the annexed drawings.
- Figure 1 is a vertical cross-sectional view of a refrigerant compressor according to one embodiment of this invention.
- Figure 2 is a cross-sectional view taken substantially along line A-A of Figure 1.
- Figure 3 is a vertical cross-sectional view of a refrigerant compressor according to a second embodiment of this invention.
- Figure 4 is a vertical cross-sectional view of a refrigerant compressor according to a third embodiment of this invention.
- Figure 5 is a vertical cross-sectional view of a refrigerant compressor according to a fourth embodiment of this invention.
- Figure 6 is a vertical cross-sectional view of a refrigerant compressor according to a fifth embodiment of this invention.
- Figure 7 is a cross-section view taken along line A-A of Figure 1 according to a sixth embodiment of this invention.
- Figure 8 is a vertical cross-sectional view of a prior art refrigerant compressor.
- Referring to the Figure 1, a
refrigerant compressor 1 in accordance with one embodiment of the present invention is shown. Thecompressor 1 includes a closedcylindrical housing assembly 10 formed by acylinder block 101, acrank chamber 13 within thecylinder block 101, a front end plate 11 and arear end plate 25. - The front end plate 11 is mounted on the left end portion of the
crank chamber 13, as shown in Figure 1, by a plurality of bolts (not shown). Therear end plate 25 and avalve plate 24 are mounted oncylinder block 101 by a plurality of bolts (not shown). An opening 111 is formed in front end plate 11 for receivingdrive shaft 12. -
Drive shaft 12 is rotatably supported by front end plate 11 through abearing 20 which is disposed within opening 111. The inner end portion ofdrive shaft 12 is also rotatably supported bycylinder block 101 through abearing 23 which is disposed within acentral bore 102.Central bore 102 is a cavity formed in the center portion ofcylinder block 101. A thrust needle bearing 22a is disposed between the inner end surface of front end plate 11 and the adjacent axial end surface of a cam rotor (input drive rotor) 14. -
Cam rotor 14 is fixed ondrive shaft 12 by apin member 15 which penetratescam rotor 14 anddrive shaft 12.Cam rotor 14 is provided with anarm 141 havingslot 142. Aslant plate 16 has an opening 161 through which passesdrive shaft 12. An axialannular projection 162 extends from the circumference of opening 161 in the front end surface ofslant plate 16.Slant plate 16 includes anarm 163 having apin 21 which is inserted inslot 142.Cam rotor 14 andslant plate 16 are joined by the hinged joint ofpin 21 andslot 142. Thepin 21 is able to slide withinslot 142 so that the angular position ofslant plate 16 can be changed with respect to the longitudinal axis ofdrive shaft 12. - A
wobble plate 17 is rotatably mounted onslant plate 16. The rotation ofwobble plate 17 is prevented by a fork-shaped slider 172 which is attached to the outer peripheral end ofwobble plate 17 and is slidably mounted on a slidingrail 173 held between front end plate 11 andcylinder block 101. In order to slideslider 172 on the slidingrail 173,wobble plate 17 wobbles in a non-rotating manner in spite of the rotation ofcam rotor 14. -
Cylinder block 101 has a plurality of annularly arrangedcylinder chambers 32 in whichrespective pistons 33 slide. Allpistons 33 are connected towobble plate 17 by a corresponding plurality of connectingrods 34. Aball 34a at one end ofrod 34 is received in a socket 331 ofpistons 33 and ball 34b at the other end ofrod 34 is received in asocket 171 ofwobble plate 17. It should be understood that, although only one such ball socket connection is shown in the drawing, there are a plurality of sockets arranged peripherally aroundwobble plate 17 to receive the balls of various rods, and that eachpiston 33 is formed with a socket for receiving the other ball ofrods 34. -
Rear end plate 25 is shaped to definesuction chamber 35 and adischarge chamber 36.Valve plate 24, which is fastened to the end ofcylinder block 101 by screws (not shown) together withrear end plate 25, is provided with a plurality ofvalved suction ports 24a connected betweensuction chamber 35 and therespective cylinders 32, and a plurality of valve discharge ports 24b connected betweendischarge chamber 36 and therespective cylinders 32. Suitable reed valves forsuction port 24a and discharge port 24b are described in U.S. Patent No. 4,011,029 issued to Shimizu.Gaskets cylinder block 101 and the inner surface ofvalve plate 24, and the outer surface ofvalve plate 24 andrear end plate 25, to seal the mating surfaces of the cylinder block, the valve plate and the rear end plate. - Referring to Figure 2 in addition to Figure 1, the axial position of
drive shaft 12 can be adjusted by an adjustingscrew 27 into a threadedportion 41 ofcentral bore 102. That is to say, the axial clearance betweencam rotor 14 and front end plate 11 through bearing 22a can be adjusted by adjustingscrew 27.Central bore 102 is partitioned into a front chamber 102a and a rear chamber 102b by adjustingscrew 27. Front chamber 102a communicates withcrank chamber 13. A plurality ofaxial grooves 42 are formed at inner peripheral threadedportion 41 ofcentral bore 102 to communicate between front chamber 102a and rear chamber 102b ofcentral bore 102. - A
groove 43 is formed at the front end surface ofcylinder block 101 facinggasket 37.Groove 43 extends radially from rear chamber 102b ofcentral bore 102 to a pressuresensitive chamber 44 which is formed in thecylinder block 101. Therefore thecrank chamber 13 communicates with pressuresensitive chamber 44 throughgrooves 42 andgroove 43. Ahole 45 is formed throughgasket 37,valve plate 24 andgasket 38 to connect pressuresensitive chamber 44 andsuction chamber 35. A bellowsvalve device 46 is fixed to one surface of pressuresensitive chamber 44 with avalve 461 arranged to close offhole 45 in response to the pressure within pressuresensitive chamber 44. The operation ofbellows valve device 46 is as follows: The pressure within crankchamber 13 is communicated to pressuresensitive chamber 44 throughgrooves sensitive chamber 44 is the same as the pressure within crankchamber 13. When the pressure within crankchamber 13 and pressuresensitive chamber 44 are below a predetermined pressure, the bellows of thebellows valve device 46 expands causingvalve 461 to closehole 45. Therefore when the compressor is not being driven, the pressure within crankchamber 13 is balanced pressure,valve 461 of thebellows valve device 46 closes thehole 45. When the pressure within crankchamber 13 and pressuresensitive chamber 44 is above a predetermined pressure, the bellows ofbellows valve device 46 is compressed causingvalve 461 to openhole 45. - In operation of the compressor, drive
shaft 12 is rotated by the engine of the vehicle through an electromagnetic clutch.Cam rotor 14 is rotated together withdrive shaft 12 to cause a non-rotating wobbling motion ofwobble plate 17. Rotating motion ofwobble plate 17 is prevented by fork-shapedslider 172 which is attached to the outer peripheral end ofwobble plate 17 and is slidably mounted on slidingrail 173 held between front end plate 11 andcylinder block 101. Awobble plate 17 moves,pistons 33 reciprocate out of phase in theirrespective cylinders 32. Upon reciprocation ofpistons 33, the refrigerant gas, which is introduced intosuction chamber 35 from afluid inlet port 35a, is taken into eachcylinder 32 and compressed. The compressed refrigerant is discharged to dischargechamber 36 from eachcylinder 32 through discharge port 24b, and therefrom into an external fluid circuit, for example, a cooling circuit, through afluid outlet port 36b. - At the beginning of compressor operation,
hole 45 is closed byvalve 461 of thebellows valve device 46 because the pressure within crankchamber 13 is low. As the compressor operates, the pressure within crankchamber 13 gradually rises to create a small pressure difference between crankchamber 13 andsuction chamber 35. This pressure difference occurs because blow-by gas, which leaks from the cylinder chambers to crankchamber 13 through a gap betweenpistons 33 andcylinders 32 during the compression stroke, is contained incrank chamber 13. The movement ofpistons 33 is hindered by the pressure difference between crankchamber 13 andsuction chamber 35, i.e., as the pressure in the crank chamber approaches the mid-pressure of the compressed gas in the cylinder chambers during the suction stroke, movement of the pistons is hindered because the slant angle ofslant plate 16 gradually decreases until it approaches zero, i.e.,slant plate 16 would be perpendicular to thedrive shaft 12. As the slant angle ofslant plate 16 decreases, the stroke ofpistons 33 in thecylinders 32 is reduced and the capacity of the compressor gradually decreases. - When the pressure of
crank chamber 13 and pressuresensitive chamber 44 rises over the predetermined pressure, the bellows ofbellows valve device 46 is sufficiently compressed andvalve 461 ofbellows valve device 46 openshole 45. Simultaneously, crankchamber 13 communicates withsuction chamber 35 through acentral bore 102 viagrooves 42 andgroove 43 formed at the front end surface ofcylinder block 101, pressuresensitive chamber 44 andhole 45. Accordingly, the pressure ofcrank chamber 13 falls to the pressure ofsuction chamber 35. In this condition,wobble plate 17 usually is urged towardslant plate 16 during the compression stroke of thepistons 33 so thatslant plate 16 moves towardrotor 14. Thus, the slant angle ofslant plate 16 is maximized relative to a vertical plane through the hinged joint ofpin 21 andslot 142. This results in the maximum stroke ofpistons 33 withincylinders 32 which corresponds to the normal refrigerant capacity of the compressor. However, the falling pressure ofcrank chamber 13 causesvalve 461 of bellows valve device to closehole 45. Thus the compressor is placed in a reduced compression stage again. Thus, in accordance with the above mentioned stages, full and reduced displacement of compressor is achieved. - In this embodiment, the
bellows valve device 46 is disposed in pressuresensitive chamber 44 formed in thecylinder block 101.Bellows valve device 46 also may be disposed insuction chamber 35 as shown in Figure 3. In the embodiment shown in Figure 3, the opening and closing ofhole 45 are accordingly controlled by the change of pressure insuction chamber 35. - Referring to Figure 4, a
refrigerant compressor 1 in accordance with another embodiment of the present invention is shown. In this embodiment, anannular shim 51 is disposed between adjustingscrew 27 screwed into the threadedportion 41 ofcentral bore 102 and the inner end of thedrive shaft 12.Shim 51 prevents friction which would otherwise occur by the contact of rotatingdrive shaft 12 with adjustingscrew 27. An annular thrust bearing 61 may also be used in place ofshim 51 as shown in Figure 5. - Referring to Figure 6, a
refrigerant compressor 1 is shown in accordance with a further embodiment of the present invention. In this embodiment, an electromagnetic valve 40 is disposed insuction chamber 35 in place ofbellows valve device 46 which is shown in Figure 3. - Referring to Figure 7, an adjusting
screw 271 is shown in accordance with another embodiment of the present invention. In this embodiment, a plurality of axial grooves 421 are formed at an outer peripheral surface of adjustingscrew 271 to communicate the front chamber 102a and rear chamber 102b ofcentral bore 102.
Claims (9)
- A compressor (1) including a compressor housing (10) having a cylinder block (101) provided with a plurality of cylinders (32) and a crank chamber (13) within said cylinder block (101), a piston (33) slidably fitted within each of said cylinders (32) and reciprocated by a drive mechanism including a wobble plate (17), an input drive rotor (14) and a drive shaft (12) connected to said input drive rotor (14) to drive said input drive rotor (14), an adjustable slant plate (16) with a sloping surface being connected to said input drive rotor (14) at an adjustable slant angle in close proximity to said wobble plate (17), a front end plate (11) on said compressor housing (10) including a bearing (20) for rotatably supporting said drive shaft (12),a rear end plate (25) and a valve plate (24) being disposed on the opposite end of said compressor housing (10) said rear end plate (25) having a suction chamber (35) and a discharge chamber (36), a central bore (102) formed at said cylinder block (101) wherein said drive shaft (12) being supported rotatably, an adjusting screw (17) being screwed into said central bore (102) to adjust axial location of said drive shaft (12) and dividing said central bore (102) into a front chamber (102a) and a rear chamber (102b), a communicating path communicating from said crank chamber (13) to said suction chamber (35), a valve control means (46) controlling the opening and closing of said communicating path, the angle of the sloping surface of said adjustable slant angle being able to be changed in response to the change of pressure in said crank chamber (13), said change in pressure being achieved by said valve control means (46) controlling the opening and closing of said communicating path, the stroke of said pistons (33) within said cylinders (32) being able to be changed by adjusting the slant angle of said adjustable slant plate (16), characterized by said communicating path being formed by a first hole or groove (42, 421) located at said central bore (102) and connecting said front chamber (102a) to said rear chamber (102b) of said central bore (102);
a groove (43) formed at an end surface of said cylinder block (101) facing said valve plate (24) and connecting said rear chamber (102b) of said central bore (102) to a second hole (45) formed at said valve plate (24) to connect one end of said groove (43) to said suction chamber (35). - The refrigerant compressor (1) of claim 1, characterized in that said valve control means (46) is disposed in a chamber (44) formed in said cylinder block (101) and is connected to one end of said groove (43) and said second hole (45).
- The refrigerant compressor (1) of claim 1, characterized in that said valve control means (46) is disposed in said suction chamber (35).
- The refrigerant compressor (1) of one of claims 1 to 3, characterized in that said valve control means (46) is a bellows valve (46) which senses the pressure of said crank chamber (13) or of said suction chamber (35).
- The refrigerant compressor (1) of one of claims 1 to 3, characterized in that said valve control means (46) is an electromagnetic valve (40).
- The refrigerant compressor (1) of one of claims 1 to 5, characterized in that said first hole or groove (42) is formed at an inner peripheral surface of said central bore (102).
- The refrigerant compressor (1) of one of claims 1 to 5, characterized in that said first hole (421) is formed at an outer peripheral surface of said adjusting screw (27).
- The refrigerant compressor (1) of one of claims 1 to 7, characterized in that an annular shim (51) is disposed between said adjusting screw (27) and an inner end of said drive shaft (12).
- The refrigerant compressor (1) of one of claims 1 to 7, characterized in that an annular thrust bearing (61) is disposed between said adjusting screw (27) and an inner end of said drive shaft (12).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP42022/87U | 1987-03-24 | ||
JP1987042022U JPH0649918Y2 (en) | 1987-03-24 | 1987-03-24 | Variable capacity compressor |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0283963A2 EP0283963A2 (en) | 1988-09-28 |
EP0283963A3 EP0283963A3 (en) | 1989-08-02 |
EP0283963B1 true EP0283963B1 (en) | 1991-07-31 |
Family
ID=12624541
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP88104389A Expired - Lifetime EP0283963B1 (en) | 1987-03-24 | 1988-03-18 | wobble plate type compressor with variable displacement mechanism |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0283963B1 (en) |
JP (1) | JPH0649918Y2 (en) |
KR (1) | KR960012113B1 (en) |
AU (1) | AU606139B2 (en) |
DE (1) | DE3863949D1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01142276A (en) * | 1987-11-27 | 1989-06-05 | Sanden Corp | Variable displacement swash-plate type compressor |
JPH1162823A (en) * | 1997-08-08 | 1999-03-05 | Sanden Corp | Variable displacement compressor |
JPH1182300A (en) * | 1997-09-05 | 1999-03-26 | Sanden Corp | Variable delivery compressor |
JP2003028057A (en) * | 2001-07-13 | 2003-01-29 | Toyota Industries Corp | Throttle structure of variable displacement type compressor |
PL396589A1 (en) | 2011-10-10 | 2013-04-15 | Janusz Marcin Ejma | Machine with a tool manipulator, especially precision tool manipulator |
CN116557256A (en) * | 2023-07-10 | 2023-08-08 | 耐力股份有限公司 | Oil-free air compressor for vehicle |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60135680A (en) * | 1983-12-23 | 1985-07-19 | Sanden Corp | Oscillation type compressor |
JPH0637874B2 (en) * | 1984-12-28 | 1994-05-18 | 株式会社豊田自動織機製作所 | Variable capacity compressor |
JPS61171886A (en) * | 1985-01-25 | 1986-08-02 | Sanden Corp | Volume variable oblique plate type compressor |
JPS61215468A (en) * | 1985-03-20 | 1986-09-25 | Toyoda Autom Loom Works Ltd | Variable capacity compressor |
-
1987
- 1987-03-24 JP JP1987042022U patent/JPH0649918Y2/en not_active Expired - Lifetime
-
1988
- 1988-03-18 DE DE8888104389T patent/DE3863949D1/en not_active Expired - Lifetime
- 1988-03-18 EP EP88104389A patent/EP0283963B1/en not_active Expired - Lifetime
- 1988-03-23 AU AU13397/88A patent/AU606139B2/en not_active Ceased
- 1988-03-24 KR KR1019880003165A patent/KR960012113B1/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
KR960012113B1 (en) | 1996-09-12 |
JPH0649918Y2 (en) | 1994-12-14 |
DE3863949D1 (en) | 1991-09-05 |
AU606139B2 (en) | 1991-01-31 |
EP0283963A2 (en) | 1988-09-28 |
JPS63150090U (en) | 1988-10-03 |
EP0283963A3 (en) | 1989-08-02 |
KR880011469A (en) | 1988-10-28 |
AU1339788A (en) | 1988-09-22 |
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