EP1701036A1 - Variable displacement swash plate compressor - Google Patents
Variable displacement swash plate compressor Download PDFInfo
- Publication number
- EP1701036A1 EP1701036A1 EP06004335A EP06004335A EP1701036A1 EP 1701036 A1 EP1701036 A1 EP 1701036A1 EP 06004335 A EP06004335 A EP 06004335A EP 06004335 A EP06004335 A EP 06004335A EP 1701036 A1 EP1701036 A1 EP 1701036A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- swash plate
- rotating shaft
- inclination
- cap
- cylindrical body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
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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
- F04B27/10—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 having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/028—Earthquake withstanding shelters
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/14—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate against other dangerous influences, e.g. tornadoes, floods
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/16—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate against adverse conditions, e.g. extreme climate, pests
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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
- F04B27/10—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 having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1063—Actuating-element bearing means or driving-axis bearing means
Definitions
- the present invention relates to a variable displacement swash plate compressor.
- Japanese Patent Laid-Open Publication No. 2000-002180 teaches a variable displacement swash plate compressor comprising a rotating shaft, a swash plate fitted on the rotating shaft to engage the rotating shaft slidably and to be variable in inclination relative to the rotating shaft, thereby rotating synchronously with the rotating shaft, a first spring for forcing the swash plate in the direction decreasing the inclination, and a second spring for forcing the swash plate inclined to near the minimum inclination in the direction increasing the inclination.
- variable displacement swash plate compressor When the variable displacement swash plate compressor is operated with the swash plate inclined to near the minimum inclination, the load acting on the compressor becomes nearly zero. As a result, the biasing forces of the first spring and the second spring become the primary forces acting on the swash plate, the inclination of the swash plate becomes liable to increase and decrease repeatedly with a short period near the minimum inclination owing to the telescopic motions of the two springs, and the swash plate becomes liable to move unstably. The unstable movement of the swash plate causes wear and fatigue of the elements of the compressor.
- An object of the present invention is to provide a variable displacement swash plate compressor comprising a rotating shaft, a swash plate fitted on the rotating shaft to engage the rotating shaft slidably and to be variable in inclination relative to the rotating shaft, thereby rotating synchronously with the rotating shaft, a first spring for forcing the swash plate in the direction decreasing the inclination, and a second spring for forcing the swash plate inclined to near the minimum inclination in the direction increasing the inclination, wherein short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination is prevented.
- a variable displacement swash plate compressor comprising a rotating shaft, a swash plate fitted on the rotating shaft to engage the rotating shaft slidably and to be variable in inclination relative to the rotating shaft, thereby rotating synchronously with the rotating shaft, a first spring for forcing the swash plate in the direction decreasing the inclination of the swash plate, a second spring for forcing the swash plate inclined to near the minimum inclination in the direction increasing the inclination of the swash plate, and a damper for countering the short period variation of the inclination of the swash plate inclined to near the minimum inclination.
- the damper counters the short period variation of the inclination of the swash plate inclined to near the minimum inclination to prevent the short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination.
- the damper forms a case for accommodating the second spring.
- the compressor becomes smaller than that wherein the damper is disposed independent of the second spring.
- the second spring fits on the rotating shaft
- the damper comprises a cylindrical body provided with an annular bottom wall opposing the swash plate and slidably fitting on the rotating shaft and a circumferential sidewall, and a cap slidably fitting in the open end of the cylindrical body and fitting on the rotating shaft, the second spring abuts the bottom wall of the cylindrical body at the end adjacent to the swash plate and abuts the cap at the end distanced from the swash plate, and the cap is prevented from moving in the direction away from the swash plate.
- the damper provided with the aforementioned simple structure can prevent the short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination.
- a snap ring fixed to the rotating shaft prevents the cap from moving in the direction away from the swash plate.
- the cap is press fitted on the rotating shaft to be prevented from moving in the direction away from the swash plate.
- the cap can be prevented from moving in the direction away from the swash plate by snap ring fixed to the rotating shaft or by press fitting on the rotating shaft.
- the cylindrical body or the cap is provided with a pore.
- the damping force of the damper against the short periodical increase and decrease of the inclination of the swash plate can be adjusted by adjusting the size of the pore formed in the cylindrical body or the cap.
- the circumferential sidewall of the cylindrical body is provided with a pore elongated in the longitudinal direction of the cylindrical body, the elongated pore can overlap the cap, and the opening area of the elongated pore decreases as the inclination of the swash plate decreases.
- the opening area of the elongated pore becomes minimum to maximize the damping force against the short periodical increase and decrease of the inclination of the swash plate, thereby effectively preventing the short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination.
- the cylindrical body is provided with a projection for abutting the end face of the cap distanced from the bottom wall of the cylindrical body at the open end.
- the projection prevents the cylindrical body from leaving the cap.
- variable displacement swash plate compressor in accordance with the first preferred embodiment of the present invention will be described.
- a variable displacement swash plate compressor A is provided with a rotating shaft 10, a rotor 11 fixed to the rotating shaft 10, and a swash plate 12 fitted on the rotating shaft 10 to engage the rotating shaft 10 slidably and to be variable in inclination relative to the rotating shaft 10.
- the swash plate 12 is connected to the rotor 11 through a linkage 13 to be variable in inclination relative to the driving shaft 10, thereby rotating synchronously with the rotating shaft 10.
- a first spring 14 is disposed between the rotor 11 and the swash plate 12 and fits on the rotating shaft 10 to force the swash plate 12 in the direction decreasing the inclination of the swash plate 12.
- a second spring 15 fits on the rotating shaft 10 to force the swash plate 12 in the direction increasing the inclination of the swash plate 12.
- the first spring 14 and the second spring 15 are disposed to face opposite surfaces of the swash plate 12.
- a plurality of pistons 17 engage the swash plate 12 through a plurality of pairs of shoes 16 that slidably engage the outer peripheral portion of the swash plate 12.
- the pistons 17 are inserted into cylinder bores 18a formed in a cylinder block 18.
- the plurality of pairs of shoes 16, the pistons 17 and the cylinder bores 18a are distanced from each other in the circumferential direction.
- the rotor 11, the swash plate 12, the linkage 13, the shoes 16 and the pistons 17 form a compressing mechanism driven by the rotating shaft 10.
- a cylindrical front housing 20 provided with a bottom wall forms a crank chamber 19 for accommodating the rotating shaft 10, the rotor 11 and the swash plate 12.
- the fore end portion of the rotating shaft 10 passes through the bottom wall of the front housing 20 to extend out of the front housing 20.
- a seal member 21 is disposed in the annular space between the bottom wall of the front housing 20 and the rotating shaft 10.
- a rotating force is transferred from a power source not shown in the figures to the fore end portion of the rotating shaft 10.
- a cylinder head 22 is installed to form an inlet chamber 22a and an outlet chamber 22b.
- a valve plate 23 is disposed between the cylinder block 18 and the cylinder head 22.
- the valve plate 23 is provided with inlet holes 23a and outlet holes 23b communicating with the cylinder bores 18a.
- Inlet valves 24 and outlet valves 25 are fitted to the valve plate 23.
- the front housing 20, the cylinder block 18, the valve plate 23 and the cylinder head 22 are assembled as a unitary body by a plurality of through bolts 26 circumferentially distanced from each other.
- the rotating shaft 10 is rotatably supported by radial bearings 27 and 28 disposed in the front housing 20 and the cylinder block 18.
- the rotor 11 is rotatably supported by a thrust bearing 29 disposed in the front housing 20.
- a damper 30 is disposed to accommodate the second spring 15.
- the damper 30 comprises a cylindrical body 31 provided with an annular bottom wall 31a opposing the swash plate 12 and slidably fitting on the rotating shaft 10 and a circumferential sidewall 31b, and a cap 32 slidably fitting in the cylindrical body 31 and slidably fitting on the rotating shaft 10.
- the second spring 15 abuts the bottom wall 31a of the cylindrical body 31 at the end adjacent to the swash plate 12 and abuts the cap 32 at the end distanced from the swash plate 12.
- the cap 32 is restricted from moving in the direction away from the swash plate 12 by a snap ring 33 fixed to the rotating shaft 10.
- the cylindrical body 31 is provided with projections 31c at the open end.
- the projections 31c can abut the end face of the cap 32 distanced from the bottom wall 31a of the cylindrical body 31.
- variable displacement swash plate compressor A The operation of the variable displacement swash plate compressor A is as follows. Rotating force is transferred to the rotating shaft 10 from the external power source not shown in the figures, and rotation of the rotating shaft 10 is transferred to the swash plate 12 through the rotor 11 and the linkage 13. The rotation of the swash plate 12 causes reciprocal movement of the peripheral portion of the swash plate 12 in the longitudinal direction of the rotating shaft 10. The reciprocal movement of the peripheral portion of the swash plate 12 is transferred to the pistons 17 through the shoes 16, and the pistons 17 move reciprocally in the cylinder bores 18a. Refrigerant gas enters into the inlet chamber 22a from an external refrigerant circuit through an inlet port formed in the cylinder head 22.
- the refrigerant gas is sucked into the cylinder bores 18a through the inlet holes 23a and the inlet valves 24 to be pressurized in the cylinder bores 18a.
- the pressurized refrigerant gas in the cylinder bores 18a discharges into the outlet chamber 22b through the outlet holes 23b and the outlet valves 25, and then discharges from the outlet chamber 22b into the external refrigerant circuit through an outlet port formed in the cylinder head 22.
- a displacement control valve not shown in the figures controls the introduction of the pressurized refrigerant gas in the outlet chamber 22b into the crank chamber 19 to control the internal pressure in the crank chamber 19 and the inclination of the swash plate 12, thereby controlling displacement of the variable displacement compressor A.
- the first spring 14 extends to force the swash plate 12 toward the cylinder block 18.
- the swash plate 12 moves toward the cylinder block 18 and the inclination of the swash plate 12 decreases.
- the swash plate 12 abuts the bottom wall 31a of the damper 30.
- the swash plate 12 further moves toward the cylinder block 18 and forces the cylindrical body 31 toward the cap 32.
- the cylindrical body 31 slides toward the cap 32 and contracts the second spring 15 that abuts the cap 32 prevented from moving in the direction away from the swash plate 12 by the snap ring 33 and is prevented from rigid body movement.
- the second spring 15 extends to force the swash plate 12 toward the front housing 20.
- the projections 31c prevent the cylindrical body 31 from leaving the cap 32.
- variable displacement swash plate compressor A When the variable displacement swash plate compressor A is operated with the swash plate 12 inclined to near the minimum inclination, the load acting on the compressor A becomes nearly zero. As a result, the biasing forces of the first spring 14 and the second spring 15 become the primary forces acting on the swash plate 12. Therefore, generally speaking, the inclination of the swash plate 12 becomes liable to increase and decrease repeatedly with a short period near the minimum inclination owing to the telescopic motions of the springs 14 and 15, and the swash plate 12 becomes liable to move unstably. The unstable movement of the swash plate 12 causes wear and fatigue of the elements of the compressor A.
- the swash plate 12 abuts the bottom wall 31a of the damper 30 when the inclination of the swash plate decreases to near the minimum inclination.
- the swash plate 12 repeats the increase and decrease near the minimum inclination, and the swash plate 12 repeats reciprocally the movement toward the cylinder block 18 and the movement toward the front housing 20, while abutting the bottom wall 31a of the damper 30, the cylindrical body 31 repeats reciprocally the movement toward the cap 32 and the movement away from the cap 32 under the biasing force of the second spring 15.
- the space enclosed by the rotating shaft 10, the cylindrical body 31 and the cap 32 is filled with the refrigerant gas and lubrication oil.
- the resistance force prevents the short period discharging of the refrigerant gas and the lubrication oil from the aforementioned space and the short period sucking of the refrigerant gas and the lubrication oil into the aforementioned space, the short period reciprocal movement of the cylindrical body 31 and the swash plate 12, the short period increase and decrease of the inclination of the swash plate 12, and the unstable movement of the swash plate 12.
- the damper 30 forms a case for accommodating the second spring 15. Therefore, the compressor A becomes smaller than that wherein the damper 30 is disposed independent of the second spring 15.
- the damper 30 can be provided with the aforementioned simple structure to prevent the short period increase and decrease of the inclination of the swash plate 12 inclined to near the minimum inclination.
- the cap 32 can be press fitted on the rotating shaft 10.
- the cap 32 is prevented from moving in the direction away from the swash plate 12.
- the snap spring 33 can be removed and the number of elements decreases.
- the bottom wall 31a of the cylindrical body 31 can be provided with small pores 31d as shown in Figures 4(a) and 4(b).
- the circumferential sidewall 31b of the cylindrical body 31 can be provided with small pores 31e as shown in Figures 4(c) and 4(d).
- the resistance force against the flow of the refrigerant gas and the lubricating oil through the small pores 31d and 31e can be adjusted and the damping force of the damper 30 against the short period increase and decrease of the inclination of the swash plate 12 inclined to near the minimum inclination can be adjusted by adjusting the opening areas of the small pores 31d and 31e.
- the small pores 31e can be elongated in the longitudinal direction of the cylindrical body 31 to form elongated pores 31e' as shown in Figure 4(c).
- the elongated pores 31e' can overlap the cap 32 and the opening areas thereof decrease as the inclination of the swash plate decreases.
- the opening areas of the elongated pores 31e' become minimum to maximize the damping force against the short period increase and decrease of the inclination of the swash plate 12, thereby effectively preventing the short period increase and decrease of the inclination of the swash plate 12 inclined to near the minimum inclination.
- the cap 32 can be provided with small pores 31f as shown in Figures 4(a).
- the resistance force against the flow of the refrigerant gas and the lubricating oil through the small pores 31f can be adjusted and the damping force of the damper 30 against the short period increase and decrease of the inclination of the swash plate 12 inclined to near the minimum inclination can be adjusted by adjusting the opening area of the pore small pores 31f.
Abstract
Description
- The present invention relates to a variable displacement swash plate compressor.
-
Japanese Patent Laid-Open Publication No. 2000-002180 - When the variable displacement swash plate compressor is operated with the swash plate inclined to near the minimum inclination, the load acting on the compressor becomes nearly zero. As a result, the biasing forces of the first spring and the second spring become the primary forces acting on the swash plate, the inclination of the swash plate becomes liable to increase and decrease repeatedly with a short period near the minimum inclination owing to the telescopic motions of the two springs, and the swash plate becomes liable to move unstably. The unstable movement of the swash plate causes wear and fatigue of the elements of the compressor.
- An object of the present invention is to provide a variable displacement swash plate compressor comprising a rotating shaft, a swash plate fitted on the rotating shaft to engage the rotating shaft slidably and to be variable in inclination relative to the rotating shaft, thereby rotating synchronously with the rotating shaft, a first spring for forcing the swash plate in the direction decreasing the inclination, and a second spring for forcing the swash plate inclined to near the minimum inclination in the direction increasing the inclination, wherein short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination is prevented.
- In accordance with the present invention, there is provided a variable displacement swash plate compressor comprising a rotating shaft, a swash plate fitted on the rotating shaft to engage the rotating shaft slidably and to be variable in inclination relative to the rotating shaft, thereby rotating synchronously with the rotating shaft, a first spring for forcing the swash plate in the direction decreasing the inclination of the swash plate, a second spring for forcing the swash plate inclined to near the minimum inclination in the direction increasing the inclination of the swash plate, and a damper for countering the short period variation of the inclination of the swash plate inclined to near the minimum inclination.
- In the variable displacement swash plate compressor of the present invention, the damper counters the short period variation of the inclination of the swash plate inclined to near the minimum inclination to prevent the short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination.
- In a preferred embodiment of the present invention, the damper forms a case for accommodating the second spring.
- When the damper forms a case for accommodating the second spring, the compressor becomes smaller than that wherein the damper is disposed independent of the second spring.
- In another preferred embodiment of the present invention, the second spring fits on the rotating shaft, the damper comprises a cylindrical body provided with an annular bottom wall opposing the swash plate and slidably fitting on the rotating shaft and a circumferential sidewall, and a cap slidably fitting in the open end of the cylindrical body and fitting on the rotating shaft, the second spring abuts the bottom wall of the cylindrical body at the end adjacent to the swash plate and abuts the cap at the end distanced from the swash plate, and the cap is prevented from moving in the direction away from the swash plate.
- When the second spring fits on the rotating shaft, the damper provided with the aforementioned simple structure can prevent the short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination.
- In another preferred embodiment of the present invention, a snap ring fixed to the rotating shaft prevents the cap from moving in the direction away from the swash plate.
- In another preferred embodiment of the present invention, the cap is press fitted on the rotating shaft to be prevented from moving in the direction away from the swash plate.
- The cap can be prevented from moving in the direction away from the swash plate by snap ring fixed to the rotating shaft or by press fitting on the rotating shaft.
- In another preferred embodiment of the present invention, the cylindrical body or the cap is provided with a pore.
- The damping force of the damper against the short periodical increase and decrease of the inclination of the swash plate can be adjusted by adjusting the size of the pore formed in the cylindrical body or the cap.
- In another preferred embodiment of the present invention, the circumferential sidewall of the cylindrical body is provided with a pore elongated in the longitudinal direction of the cylindrical body, the elongated pore can overlap the cap, and the opening area of the elongated pore decreases as the inclination of the swash plate decreases.
- When the inclination of the swash plate becomes minimum, the opening area of the elongated pore becomes minimum to maximize the damping force against the short periodical increase and decrease of the inclination of the swash plate, thereby effectively preventing the short periodical increase and decrease of the inclination of the swash plate inclined to near the minimum inclination.
- In another preferred embodiment of the present invention, the cylindrical body is provided with a projection for abutting the end face of the cap distanced from the bottom wall of the cylindrical body at the open end.
- The projection prevents the cylindrical body from leaving the cap.
- In the drawings:
- Figure 1 is a sectional view of a variable displacement swash plate compressor in accordance with the first preferred embodiment of the present invention.
- Figure 2 is an enlarged sectional view of the damper of the variable displacement swash plate compressor in accordance with the first preferred embodiment of the present invention.
- Figure 3 is an enlarged sectional view of the damper of a variable displacement swash plate compressor in accordance with the second preferred embodiment of the present invention.
- Figure 4 is a set of structural views of the damper of a variable displacement swash plate compressor in accordance with the third preferred embodiment of the present invention. Figures 4(a) and 4(c) are enlarged sectional views, and Figures 4(b) and 4(d) are perspective views.
- A variable displacement swash plate compressor in accordance with the first preferred embodiment of the present invention will be described.
- As shown in Figure 1, a variable displacement swash plate compressor A is provided with a
rotating shaft 10, a rotor 11 fixed to the rotatingshaft 10, and aswash plate 12 fitted on the rotatingshaft 10 to engage the rotatingshaft 10 slidably and to be variable in inclination relative to the rotatingshaft 10. Theswash plate 12 is connected to the rotor 11 through alinkage 13 to be variable in inclination relative to thedriving shaft 10, thereby rotating synchronously with the rotatingshaft 10. - A
first spring 14 is disposed between the rotor 11 and theswash plate 12 and fits on the rotatingshaft 10 to force theswash plate 12 in the direction decreasing the inclination of theswash plate 12. Asecond spring 15 fits on the rotatingshaft 10 to force theswash plate 12 in the direction increasing the inclination of theswash plate 12. Thefirst spring 14 and thesecond spring 15 are disposed to face opposite surfaces of theswash plate 12. - A plurality of
pistons 17 engage theswash plate 12 through a plurality of pairs ofshoes 16 that slidably engage the outer peripheral portion of theswash plate 12. Thepistons 17 are inserted intocylinder bores 18a formed in acylinder block 18. - The plurality of pairs of
shoes 16, thepistons 17 and thecylinder bores 18a are distanced from each other in the circumferential direction. - The rotor 11, the
swash plate 12, thelinkage 13, theshoes 16 and thepistons 17 form a compressing mechanism driven by the rotatingshaft 10. - A cylindrical
front housing 20 provided with a bottom wall forms acrank chamber 19 for accommodating the rotatingshaft 10, the rotor 11 and theswash plate 12. The fore end portion of the rotatingshaft 10 passes through the bottom wall of thefront housing 20 to extend out of thefront housing 20. - A
seal member 21 is disposed in the annular space between the bottom wall of thefront housing 20 and the rotatingshaft 10. - A rotating force is transferred from a power source not shown in the figures to the fore end portion of the rotating
shaft 10. - A
cylinder head 22 is installed to form aninlet chamber 22a and anoutlet chamber 22b. - A
valve plate 23 is disposed between thecylinder block 18 and thecylinder head 22. Thevalve plate 23 is provided withinlet holes 23a andoutlet holes 23b communicating with thecylinder bores 18a.Inlet valves 24 andoutlet valves 25 are fitted to thevalve plate 23. - The
front housing 20, thecylinder block 18, thevalve plate 23 and thecylinder head 22 are assembled as a unitary body by a plurality of throughbolts 26 circumferentially distanced from each other. - The rotating
shaft 10 is rotatably supported byradial bearings front housing 20 and thecylinder block 18. The rotor 11 is rotatably supported by a thrust bearing 29 disposed in thefront housing 20. - A
damper 30 is disposed to accommodate thesecond spring 15. - As shown in Figure 2, the
damper 30 comprises acylindrical body 31 provided with anannular bottom wall 31a opposing theswash plate 12 and slidably fitting on the rotatingshaft 10 and acircumferential sidewall 31b, and acap 32 slidably fitting in thecylindrical body 31 and slidably fitting on the rotatingshaft 10. Thesecond spring 15 abuts thebottom wall 31a of thecylindrical body 31 at the end adjacent to theswash plate 12 and abuts thecap 32 at the end distanced from theswash plate 12. Thecap 32 is restricted from moving in the direction away from theswash plate 12 by asnap ring 33 fixed to the rotatingshaft 10. - The
cylindrical body 31 is provided withprojections 31c at the open end. Theprojections 31c can abut the end face of thecap 32 distanced from thebottom wall 31a of thecylindrical body 31. - The operation of the variable displacement swash plate compressor A is as follows. Rotating force is transferred to the rotating
shaft 10 from the external power source not shown in the figures, and rotation of the rotatingshaft 10 is transferred to theswash plate 12 through the rotor 11 and thelinkage 13. The rotation of theswash plate 12 causes reciprocal movement of the peripheral portion of theswash plate 12 in the longitudinal direction of therotating shaft 10. The reciprocal movement of the peripheral portion of theswash plate 12 is transferred to thepistons 17 through theshoes 16, and thepistons 17 move reciprocally in thecylinder bores 18a. Refrigerant gas enters into theinlet chamber 22a from an external refrigerant circuit through an inlet port formed in thecylinder head 22. The refrigerant gas is sucked into thecylinder bores 18a through theinlet holes 23a and theinlet valves 24 to be pressurized in thecylinder bores 18a. The pressurized refrigerant gas in thecylinder bores 18a discharges into theoutlet chamber 22b through theoutlet holes 23b and theoutlet valves 25, and then discharges from theoutlet chamber 22b into the external refrigerant circuit through an outlet port formed in thecylinder head 22. - A displacement control valve not shown in the figures controls the introduction of the pressurized refrigerant gas in the
outlet chamber 22b into thecrank chamber 19 to control the internal pressure in thecrank chamber 19 and the inclination of theswash plate 12, thereby controlling displacement of the variable displacement compressor A. - When the inclination of the
swash plate 12 decreases, thefirst spring 14 extends to force theswash plate 12 toward thecylinder block 18. Theswash plate 12 moves toward thecylinder block 18 and the inclination of theswash plate 12 decreases. When the inclination of theswash plate 12 decreases to a predetermined angle near the minimum inclination angle, theswash plate 12 abuts thebottom wall 31a of thedamper 30. When the inclination of theswash plate 12 further decreases, theswash plate 12 further moves toward thecylinder block 18 and forces thecylindrical body 31 toward thecap 32. Thecylindrical body 31 slides toward thecap 32 and contracts thesecond spring 15 that abuts thecap 32 prevented from moving in the direction away from theswash plate 12 by thesnap ring 33 and is prevented from rigid body movement. - When the inclination of the
swash plate 12 increases, thesecond spring 15 extends to force theswash plate 12 toward thefront housing 20. Theprojections 31c prevent thecylindrical body 31 from leaving thecap 32. - When the variable displacement swash plate compressor A is operated with the
swash plate 12 inclined to near the minimum inclination, the load acting on the compressor A becomes nearly zero. As a result, the biasing forces of thefirst spring 14 and thesecond spring 15 become the primary forces acting on theswash plate 12. Therefore, generally speaking, the inclination of theswash plate 12 becomes liable to increase and decrease repeatedly with a short period near the minimum inclination owing to the telescopic motions of thesprings swash plate 12 becomes liable to move unstably. The unstable movement of theswash plate 12 causes wear and fatigue of the elements of the compressor A. - However, in the variable displacement swash plate compressor A, the
swash plate 12 abuts thebottom wall 31a of thedamper 30 when the inclination of the swash plate decreases to near the minimum inclination. When the inclination of theswash plate 12 repeats the increase and decrease near the minimum inclination, and theswash plate 12 repeats reciprocally the movement toward thecylinder block 18 and the movement toward thefront housing 20, while abutting thebottom wall 31a of thedamper 30, thecylindrical body 31 repeats reciprocally the movement toward thecap 32 and the movement away from thecap 32 under the biasing force of thesecond spring 15. The space enclosed by the rotatingshaft 10, thecylindrical body 31 and thecap 32 is filled with the refrigerant gas and lubrication oil. When thecylindrical body 31 repeats reciprocally the movement toward thecap 32 and the movement away from thecap 32, discharging of the refrigerant gas and the lubrication oil from the aforementioned space and sucking of the refrigerant gas and the lubrication oil into the aforementioned space are repeated reciprocally through the clearances formed in the slidable abutments between therotating shaft 10 and thebottom wall 31a of thecylindrical body 31, the rotatingshaft 10 and thecap 32, and thecap 32 and thecircumferential wall 31b of thecylindrical body 31. When the refrigerant gas and the lubrication oil are discharged from and sucked into the aforementioned space through the aforementioned clearances formed in the slidable abutments, resistance force proportional to the flow velocity of the refrigerant gas and the lubrication oil is generated due to the viscosities of the refrigerant gas and the lubrication oil. The resistance force prevents the short period discharging of the refrigerant gas and the lubrication oil from the aforementioned space and the short period sucking of the refrigerant gas and the lubrication oil into the aforementioned space, the short period reciprocal movement of thecylindrical body 31 and theswash plate 12, the short period increase and decrease of the inclination of theswash plate 12, and the unstable movement of theswash plate 12. - The
damper 30 forms a case for accommodating thesecond spring 15. Therefore, the compressor A becomes smaller than that wherein thedamper 30 is disposed independent of thesecond spring 15. - When the
second spring 15 fits on therotating shaft 10, thedamper 30 can be provided with the aforementioned simple structure to prevent the short period increase and decrease of the inclination of theswash plate 12 inclined to near the minimum inclination. - As shown in Figure 3, the
cap 32 can be press fitted on therotating shaft 10. Thecap 32 is prevented from moving in the direction away from theswash plate 12. Thus, thesnap spring 33 can be removed and the number of elements decreases. - The
bottom wall 31a of thecylindrical body 31 can be provided withsmall pores 31d as shown in Figures 4(a) and 4(b). Thecircumferential sidewall 31b of thecylindrical body 31 can be provided withsmall pores 31e as shown in Figures 4(c) and 4(d). - The resistance force against the flow of the refrigerant gas and the lubricating oil through the
small pores damper 30 against the short period increase and decrease of the inclination of theswash plate 12 inclined to near the minimum inclination can be adjusted by adjusting the opening areas of thesmall pores - The
small pores 31e can be elongated in the longitudinal direction of thecylindrical body 31 to formelongated pores 31e' as shown in Figure 4(c). The elongated pores 31e' can overlap thecap 32 and the opening areas thereof decrease as the inclination of the swash plate decreases. When the inclination of theswash plate 12 becomes minimum, the opening areas of theelongated pores 31e' become minimum to maximize the damping force against the short period increase and decrease of the inclination of theswash plate 12, thereby effectively preventing the short period increase and decrease of the inclination of theswash plate 12 inclined to near the minimum inclination. - The
cap 32 can be provided withsmall pores 31f as shown in Figures 4(a). The resistance force against the flow of the refrigerant gas and the lubricating oil through thesmall pores 31f can be adjusted and the damping force of thedamper 30 against the short period increase and decrease of the inclination of theswash plate 12 inclined to near the minimum inclination can be adjusted by adjusting the opening area of the poresmall pores 31f. - While the present invention has been described with reference to preferred embodiments, one of ordinary skill in the art will recognize that modifications and improvements may be made while remaining within the spirit and scope of the present invention. The scope of the invention is determined solely by the attached claims.
Claims (8)
- A variable displacement swash plate compressor comprising a rotating shaft, a swash plate fitted on the rotating shaft to engage the rotating shaft slidably and to be variable in inclination relative to the rotating shaft, thereby rotating synchronously with the rotating shaft, a first spring for forcing the swash plate in the direction decreasing the inclination of the swash plate, a second spring for forcing the swash plate inclined to near the minimum inclination in the direction increasing the inclination of the swash plate, and a damper for countering the short period variation of the inclination of the swash plate inclined to near the minimum inclination.
- A variable displacement swash plate compressor of claim 1, wherein the damper forms a case for accommodating the second spring.
- A variable displacement swash plate compressor of claim 1 or 2, wherein the second spring fits on the rotating shaft, the damper comprises a cylindrical body provided with an annular bottom wall opposing the swash plate and slidably fitting on the rotating shaft and a circumferential sidewall, and a cap slidably fitting in the open end of the cylindrical body and fitting on the rotating shaft, the second spring abuts the bottom wall of the cylindrical body at the end adjacent to the swash plate and abuts the cap at the end distanced from the swash plate, and the cap is prevented from moving in the direction away from the swash plate.
- A variable displacement swash plate compressor of claim 3, wherein a snap ring fixed to the rotating shaft prevents the cap from moving in the direction away from the swash plate.
- A variable displacement swash plate compressor of claim 3, wherein the cap is press fitted on the rotating shaft to be prevented from moving in the direction away from the swash plate.
- A variable displacement swash plate compressor of any one of claims 3 to 5, wherein the cylindrical body or the cap is provided with a pore.
- A variable displacement swash plate compressor of any one of claims 3 to 5, wherein the circumferential sidewall of the cylindrical body is provided with a pore elongated in the longitudinal direction of the cylindrical body, and wherein the elongated pore can overlap the cap and the opening area of the elongated pore decreases as the inclination of the swash plate decreases.
- A variable displacement swash plate compressor of any one of claims 3 to 7, wherein the cylindrical body is provided with a projection for abutting the end face of the cap distanced from the bottom wall of the cylindrical body at the open end.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005068572A JP2006250057A (en) | 2005-03-11 | 2005-03-11 | Variable displacement swash plate type compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1701036A1 true EP1701036A1 (en) | 2006-09-13 |
Family
ID=36123441
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06004335A Withdrawn EP1701036A1 (en) | 2005-03-11 | 2006-03-03 | Variable displacement swash plate compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20060204369A1 (en) |
EP (1) | EP1701036A1 (en) |
JP (1) | JP2006250057A (en) |
KR (1) | KR100770236B1 (en) |
CN (1) | CN100425832C (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008119319A2 (en) * | 2007-03-29 | 2008-10-09 | Ixetic Mac Gmbh | Air conditioning compressor |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100986942B1 (en) * | 2008-08-12 | 2010-10-12 | 주식회사 두원전자 | Variable displacement swash plate compressor |
Citations (5)
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JP2000002180A (en) | 1998-04-13 | 2000-01-07 | Toyota Autom Loom Works Ltd | Variable capacity type swash plate compressor, cooling circuit for air-conditioning, and capacity control valve |
EP1146228A2 (en) * | 2000-04-11 | 2001-10-17 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressors |
JP2002357179A (en) * | 2001-05-31 | 2002-12-13 | Toyota Industries Corp | Variable displacement compressor |
EP1281867A2 (en) * | 2001-08-02 | 2003-02-05 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement compressor and method of inhibiting noise for the same |
EP1281866A2 (en) * | 2001-07-31 | 2003-02-05 | Kabushiki Kaisha Toyota Jidoshokki | Vibration damping mechanism for piston type compressor |
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JPH0633769B2 (en) * | 1988-04-20 | 1994-05-02 | 本田技研工業株式会社 | Capacity setting device at start-up in variable capacity compressor |
JP2682290B2 (en) * | 1991-09-09 | 1997-11-26 | 株式会社豊田自動織機製作所 | Piston type compressor |
JPH08326655A (en) * | 1995-06-05 | 1996-12-10 | Calsonic Corp | Swash plate compressor |
JP3582284B2 (en) * | 1997-03-13 | 2004-10-27 | 株式会社豊田自動織機 | Refrigeration circuit and compressor |
JPH10266952A (en) * | 1997-03-25 | 1998-10-06 | Zexel Corp | Variable displacement type swash plate compressor |
JP2000064957A (en) * | 1998-08-17 | 2000-03-03 | Toyota Autom Loom Works Ltd | Variable displacement swash prate compressor and extraction side control valve |
BR0007085A (en) * | 1999-08-20 | 2001-07-10 | Toyoda Jidoshokki Seisakucho K | Variable capacity oscillating plate compressor |
-
2005
- 2005-03-11 JP JP2005068572A patent/JP2006250057A/en active Pending
-
2006
- 2006-03-03 EP EP06004335A patent/EP1701036A1/en not_active Withdrawn
- 2006-03-10 CN CNB2006100673045A patent/CN100425832C/en not_active Expired - Fee Related
- 2006-03-10 KR KR1020060022557A patent/KR100770236B1/en not_active IP Right Cessation
- 2006-03-13 US US11/373,260 patent/US20060204369A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000002180A (en) | 1998-04-13 | 2000-01-07 | Toyota Autom Loom Works Ltd | Variable capacity type swash plate compressor, cooling circuit for air-conditioning, and capacity control valve |
EP1146228A2 (en) * | 2000-04-11 | 2001-10-17 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressors |
JP2002357179A (en) * | 2001-05-31 | 2002-12-13 | Toyota Industries Corp | Variable displacement compressor |
EP1281866A2 (en) * | 2001-07-31 | 2003-02-05 | Kabushiki Kaisha Toyota Jidoshokki | Vibration damping mechanism for piston type compressor |
EP1281867A2 (en) * | 2001-08-02 | 2003-02-05 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement compressor and method of inhibiting noise for the same |
Non-Patent Citations (1)
Title |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008119319A2 (en) * | 2007-03-29 | 2008-10-09 | Ixetic Mac Gmbh | Air conditioning compressor |
WO2008119319A3 (en) * | 2007-03-29 | 2008-11-27 | Ixetic Mac Gmbh | Air conditioning compressor |
CN101631955B (en) * | 2007-03-29 | 2012-04-25 | 艾克塞蒂克马克有限公司 | Air conditioning compressor |
US8353680B2 (en) | 2007-03-29 | 2013-01-15 | Ixetic Mac Gmbh | Air conditioning compressor |
Also Published As
Publication number | Publication date |
---|---|
JP2006250057A (en) | 2006-09-21 |
KR20060099453A (en) | 2006-09-19 |
CN1831331A (en) | 2006-09-13 |
CN100425832C (en) | 2008-10-15 |
KR100770236B1 (en) | 2007-10-26 |
US20060204369A1 (en) | 2006-09-14 |
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