CN1616824A - Variable displacement compressor - Google Patents
Variable displacement compressor Download PDFInfo
- Publication number
- CN1616824A CN1616824A CNA2004101023219A CN200410102321A CN1616824A CN 1616824 A CN1616824 A CN 1616824A CN A2004101023219 A CNA2004101023219 A CN A2004101023219A CN 200410102321 A CN200410102321 A CN 200410102321A CN 1616824 A CN1616824 A CN 1616824A
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- Prior art keywords
- cam
- live axle
- compressor
- supporting element
- direction protrusion
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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
- F04B27/1072—Pivot mechanisms
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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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
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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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0891—Component parts, e.g. sealings; Manufacturing or assembly thereof casings, housings
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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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving means
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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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- 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
- F04B27/1081—Casings, housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2250/00—Geometry
- F05B2250/10—Geometry two-dimensional
- F05B2250/19—Geometry two-dimensional machined; miscellaneous
- F05B2250/192—Geometry two-dimensional machined; miscellaneous beveled
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/40—Transmission of power
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/50—Kinematic linkage, i.e. transmission of position
- F05B2260/506—Kinematic linkage, i.e. transmission of position using cams or eccentrics
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The present invention relates to a variable displacement compressor(10)including a hinge mechanism(19)that is easily machined. The hinge mechanism is arranged in the compressor between the lug plate(17)and the cam plate(18). The hinge mechanism includes a support(20)formed on the cam plate. A spherical projection(23)extends from the support in a direction rearward with respect to the direction a drive shaft(16)rotates. A roller(22)extends from the support in a direction forward with respect to the direction the drive shaft rotates. A first cam(24)is formed on the lug plate surrounding and guiding the spherical portion. A second cam(25)is formed on the lug plate. The second cam includes a cam surface that contacts and guides the roller.
Description
Technical field
The present invention relates to a kind of compressor, relate in particular to the variable displacement compressor in a kind of refrigeration cycle that is used in air conditioner for vehicles.
Background technique
The variable displacement compressor of use in refrigeration cycle comprises having the cylinder-bore and the housing of supporting driving shaft rotatably.Live axle supports swash plate in the tiltable mode.The lug dish is fixed on the live axle to rotate with the live axle one.Articulated mechanism is arranged between lug dish and the swash plate.Piston to-and-fro motion in each cylinder-bore.Piston is connected on the periphery of swash plate.When live axle rotates, this rotation is passed to swash plate by lug dish and articulated mechanism.This makes reciprocating motion of the pistons and compress refrigerant gas in the respective cylinder hole.And articulated mechanism guiding swash plate also changes the stroke of the tilt angle of swash plate with the change piston.Change the discharge capacity of variable displacement compressor by this way.
Day patent publication No. of the present disclosure is the example that the patent of 2001-289159 has been described the articulated mechanism of a kind of use in variable displacement compressor.As shown in Figure 1, swash plate 101 has towards the end face 101a of lug dish 102 (thrust flange).Connecting pin 103 is arranged on the end face 101a.Spherical protuberances 103a and 103b from the opposition side of connecting pin 103 to outstanding.Lug dish 102 has the end face 102c towards swash plate 101.Be used to guide the guiding groove 102a of spherical protuberances 103a and be used to guide the guiding groove 102b of spherical protuberances 103b to be arranged near the end face 102c.When changing the tilt angle of swash plate 101, guiding groove 102a and the spherical protuberances 103a of 102b guiding connecting pin 103 and the motion of 103b.
Lug dish 102 is gone up rotation in the direction (sense of rotation R) of arrow R shown in Figure 1.More particularly, when observing lug dish 102 away from the sidepiece of end face 102c, lug dish 102 is rotated in a clockwise direction.The guiding groove 102a that is positioned at connecting pin 103 fronts on sense of rotation R does not pass to swash plate 101 with moment from lug dish 102a.On the contrary, another guiding groove 102b passes to swash plate 101 with moment from lug dish 102.Therefore, guiding groove 102b must long enough and enough deeply to hold and to guide spherical protuberances 103b.And the inwall of guiding groove 102b must contact spherical protuberances 103b power passed to spherical protuberances 103b on sense of rotation R.More particularly, the inwall of guiding groove 102b must be with respect to the back side contacts of sense of rotation R from spherical protuberances 103b.
The guiding groove 102a that does not pass torque to swash plate 101 then needn't do not only dark but also longly.And contacting and not requiring between the inwall of guiding groove 102a and the spherical protuberances 103a is used for moment is passed to swash plate 101 from lug dish 102, the tilt angle of swash plate 101 and be used to receive the compression reaction force that is applied on swash plate 101 and the piston.
Yet, require more numerous and diverse processing to form dark and long groove, that is, and guiding groove 102a and 102b.Therefore, the processing request of articulated mechanism for example shown in Figure 1 is more.
The guiding groove 102a that does not pass torque to swash plate 101 has the wall that is positioned at spherical protuberances 103a front on sense of rotation R.And the distance between spherical protuberances 103a and the spherical protuberances 103b is little.Distance between guiding groove 102a and the guiding groove 102b is also little.Therefore, the support by 101 pairs of lug dishes 102 of swash plate is not enough.
Acted on the swash plate 101 with the eccentric manner shown in the arrow X by the compression reaction force that piston produced, arrow X represents the carrying center of reaction force.This can make swash plate 101 direction that swash plate 101 tilts when being different from the change discharge capacity tilt.In this case, spherical protuberances 103a and 103b are to be different from designed mode contact guidance groove 102a and the inwall of 102b.This can increase the inwall of guiding groove 102a and 102b and the slip resistance between corresponding spherical protuberances 103a and the 103b, and weakens the controllability of the discharge capacity of variable displacement compressor.
Summary of the invention
The invention provides a kind of variable displacement compressor with articulated mechanism of easy processing.
An aspect of of the present present invention is a kind of compressor, and this compressor passes to lobe plate with the rotation of live axle from the lug dish, and the to-and-fro motion of lobe plate when rotation driven plunger is with pressurized gas, and the tilt angle that changes lobe plate is to change discharge capacity.This compressor comprises the articulated mechanism that is arranged between lug dish and the swash plate.Articulated mechanism comprises the supporting element that is formed on the cam disk.First direction protrusion extends from supporting element on the backward directions of the direction of rotating with respect to live axle.Second direction protrusion forwards extends upward the direction of rotating with respect to live axle.Be formed on first cam guidance, first direction protrusion on the lug dish in mode around first direction protrusion.Second cam is formed on the lug dish and comprises the camming surface that is used to contact and guide second direction protrusion.
Another aspect of the present invention is a kind of compressor, and this compressor comprises: housing, be formed on the cylinder-bore in the housing and be supported on live axle on the housing in rotatable mode.The lug dish is connected in live axle to rotate with the live axle one.Cam disk supports with tiltable mode driven shaft.Cam disk has towards the first surface of lug dish.The lug dish has towards the second surface of the first surface of cam disk.Piston has end and the to-and-fro motion in cylinder-bore that is connected in cam disk.Articulated mechanism is arranged between lug dish and the cam disk.Articulated mechanism comprises the supporting element that is formed on the first surface.First direction protrusion extends from supporting element on the backward directions of the direction of rotating with respect to live axle.Second direction protrusion forwards upwards extends from supporting element the direction of rotating with respect to live axle.Be formed on first cam guidance, first direction protrusion on the second surface in mode around first direction protrusion.Second cam is formed on the second surface and comprises the camming surface that is used to contact and guide second direction protrusion.
Another aspect of the present invention is a kind of compressor, and this compressor comprises: housing, be formed on the cylinder-bore in the housing and be supported on live axle on the housing in rotatable mode.The lug dish is connected in live axle to rotate with the live axle one.Cam disk supports with tiltable mode driven shaft.Cam disk has towards the first surface of lug dish.The lug dish has towards the second surface of the first surface of cam disk.Has the piston to-and-fro motion in cylinder-bore that is connected to the end on the cam disk.Articulated mechanism is arranged between lug dish and the cam disk.Articulated mechanism has the supporting element that is formed on the first surface and comprises jack.Pin inserts in the jack and has spherical part and rotatable roller.Spherical part extends from supporting element on the backward directions of the direction of rotating with respect to live axle.Roller forwards upwards extends from supporting element the direction of rotating with respect to live axle.First cam be formed on the second surface and comprise around and the guiding spherical part groove.Second cam is formed on the second surface and comprises the camming surface that is used to contact and guide roller.
By following description and in conjunction with the accompanying drawing that shows principle of the present invention by example, other aspects of the present invention and beneficial effect will be conspicuous.
Description of drawings
Referring to following description of the preferred embodiment of the present invention and accompanying drawing, can understand the present invention and purpose and beneficial effect more thoroughly, accompanying drawing is as follows:
Fig. 1 is the cross sectional view of the articulated mechanism of expression variable displacement compressor of the prior art;
Fig. 2 is the cross sectional view according to the variable displacement compressor of first preferred embodiment of the invention;
Fig. 3 is the planimetric map of the articulated mechanism of the compressor in the presentation graphs 2;
Fig. 4 is the side view of the articulated mechanism of presentation graphs 3;
Fig. 5 is the planimetric map of expression articulated mechanism of another preferred embodiment according to the present invention;
Fig. 6 is the planimetric map of expression articulated mechanism of another preferred embodiment according to the present invention;
Fig. 7 is the planimetric map of expression articulated mechanism of another preferred embodiment according to the present invention.
Embodiment
In the accompanying drawings, similar reference character is used for representing the similar component of whole accompanying drawings.
The variable displacement compressor 10 of the preferred embodiments of the present invention is described now with reference to accompanying drawing 2 to 4.In a preferred embodiment, compressor 10 is used in the refrigeration cycle of vehicle air conditioning.
Fig. 2 is the cross sectional view of compressor 10.Left side shown in Figure 2 is referred to as the front side of compressor 10, the right side is referred to as the rear side of compressor 10.As shown in Figure 2, compressor 10 has housing 10a, housing 10a comprises cylinder block 11, be fixed in cylinder block 11 front end front case 12 and be fixed in the rear case 14 of the rear end of cylinder block 11 by valve plate 13.
Crank chamber 15 is limited among the housing 10a and between cylinder block 11 and front case 12.The live axle 16 that runs through crank chamber 15 is supported between cylinder block 11 and the front case 12 in rotatable mode.Live axle 16 is connected in the motor (not shown) as the vehicle traction source.Live axle 16 rotates by engine-driving and on the direction shown in the arrow R.
Dish type lug dish (lug plate) 17 is fixed in crank chamber 15 on the live axle 16 to rotate with live axle 16 one.Crank chamber 15 has held the swash plate 18 of cam disk effect.Axis hole 18a runs through the core of swash plate 18, and live axle 16 inserts among this axis hole 18a.Articulated mechanism 19 is arranged between lug dish 17 and the swash plate 18.Swash plate 18 is connected in lug dish 17 by articulated mechanism 19 and supports at axis hole 18a place driven shaft 16.Swash plate 18 rotates synchronously with lug dish 17 and live axle 16.In addition, when swash plate 18 during in the axial direction along live axle 16 rotation, swash plate 18 tilts with respect to live axle 16.
A plurality of uniformly-spaced cylinder-bore 27 (only illustrating one among Fig. 2) run through cylinder block 11 around the axle T of live axle 16.Single head pison 28 to-and-fro motion in each cylinder-bore 27.The open front in piston 28 closed cylinder holes 27.The after-opening in the front end closed cylinder hole 27 of valve plate 13.Compression chamber 29 is limited in the cylinder-bore 27.The volume of compression chamber 29 changes according to the to-and-fro motion of piston 28.
Piston 28 is connected in the periphery of swash plate 18 by a pair of piston shoes 30.Air aspiration cavity 31 and exhaust cavity 40 are limited between valve plate 13 and the rear case 14.Valve plate 13 comprises intakeport 32 and the Aspirating valves 33 between each compression chamber 29 and air aspiration cavity 31.In addition, valve plate 13 comprises relief opening 34 and the outlet valve 35 between each compression chamber 29 and exhaust cavity 40.
When each piston 28 when the dead center position moves to its lower dead point position from it, refrigerant gas (being carbon dioxide in a preferred embodiment) is inhaled into the corresponding compression chamber 29 by corresponding intakeport 32 and Aspirating valves 33 from air aspiration cavity 31.When piston 28 when upper dead center position moves on to lower dead point position, the refrigerant gas in the compression chamber 29 is compressed into and reaches predetermined pressure and be discharged in the exhaust cavity 40 by respective vent ports 34 and outlet valve 35.
Discharge passage 36, gas delivery channels 37 and control valve 38 are arranged among the housing 10a of compressor 10.Discharge passage 36 connecting crank chambeies 15 and air aspiration cavity 31.Gas delivery channels 37 connects exhaust cavity 40 and crank chamber 15.Known in the prior art control valve 38 is arranged in the gas delivery channels 37.
Control is transported to the high pressure gas amount in the crank chamber 15 by gas delivery channels 37 and is discharged from the opening degree that balance between the gas flow in crank chamber 15 is come adjusting control valve 38 by discharge passage 36.This has just determined the interior pressure in crank chamber 15.When the interior pressure in crank chamber 15 changed, the difference between the interior pressure in crank chamber 15 and the interior pressure of compression chamber 29 also changed.This has changed the tilt angle (swash plate 18 is with respect to the angle on plane perpendicular to the axle T of live axle 16) of swash plate 18.By this way, the discharge capacity of the stroke of piston 28 or compressor 10 is conditioned.
For example, the tilt angle that reduces to have increased swash plate 18 of the interior pressure in crank chamber 15.The discharge capacity that this has increased the stroke of piston 28 and has increased compressor 10.On the contrary, the increase of the interior pressure in crank chamber 15 has reduced the tilt angle of swash plate 18.Thereby the discharge capacity that this has reduced the stroke of piston 28 and has reduced compressor 10.
Now articulated mechanism 19 will be discussed.
Shown in Fig. 2 to 4, swash plate 18 has the end face 18b towards lug dish 17.Supporting element 20 is 17 outstanding from end face 18b towards the lug dish.Certain part of supporting element 20 contiguous swash plates 18, this part moves on to upper dead center position with each piston 28.This part of swash plate 18 is referred to as upper dead center corresponding position P.Midplane S is limited to the central authorities of supporting element 20, and the end of supporting element 20 is divided into two halves in equal size in this centre.Midplane S is positioned at and is parallel on the plane of (this plane comprises the axle T and the upper dead center corresponding position P of live axle 16), a plane.Midplane S is offset from upper dead center corresponding position P on the sense of rotation R of live axle 16.
Jack 20a runs through supporting element 20 on the direction perpendicular to midplane S.Connecting pin 21 press-fits and is fixed among the jack 20a of supporting element 20.Connecting pin 21 comprises first end section 21a (right-hand member as shown in Figure 2) and the second end section 21b (left end as shown in Figure 2) that extends from supporting element 20.Second end section 21b is positioned at the front of first end section 21a on sense of rotation R.In other words, first end section 21a extends from supporting element 20 on the backward directions of the direction of rotating with respect to live axle 16.In addition, second end section 21b is forwards upwards extending from supporting element 20 with respect to the direction of live axle 16 rotations.
The second end section 21b of connecting pin 21 is with rotatable mode support cylinder shape roller 22 (second direction protrusion).Stop ring 26 (retainer) is connected in second end section 21b and comes off from connecting pin 21 to prevent roller 22.The spherical protuberances 23 that plays the first direction protrusion effect is integral with first end section 21a.
The upper dead center corresponding position P of swash plate 18 is between roller 22 and spherical protuberances 23.Roller 22 (specifically, be positioned at the plane M1 on the exterior edge face of roller 22) and upper dead center corresponding position P between distance greater than the distance between spherical protuberances 23 (more particularly, comprise the center of spherical protuberances 23 and be parallel to the plane M2 of the planar S of supporting element 20) and the upper dead center corresponding position P.The minimum range of spherical protuberances 23 and supporting element 20 is greater than the minimum range between roller 22 and the supporting element 20.
When moment when lug dish 17 passes to swash plate 18, the internal surface 24a of first cam 24 puts on power on the spherical protuberances 23.The compression reaction force that is produced by compressed refrigerant gas passes to swash plate 18 with the eccentric manner shown in the arrow X from piston 28, and arrow X represents the load center of reaction force.The camming surface 25a of second cam 25 is by this compression reaction force of roller 22 main receptions.
In order to increase the discharge capacity of compressor 10, change the tilt angle of swash plate 18.Under state like this, roller 22 moves away from live axle 16 along the camming surface 25a of second cam 25, and spherical protuberances 23 moves away from live axle 16 along the camming surface 24a of first cam 24.In order to reduce the discharge capacity of compressor 10, change the tilt angle of swash plate 18.Under state like this, roller 22 moves towards live axle 16 along the camming surface 25a of second cam 25, and spherical protuberances 23 moves towards live axle 16 along the internal surface 24a of first cam 24.First and second cams 24 and 25 guide swash plate 18 by this way.
Compressor 10 in the preferred embodiment has following advantage.
(1) second cam 25 of articulated mechanism 19 with respect to sense of rotation R towards anterior opening.In other words, moment not groove and do not have the inwall that contacts roller 22 at sense of rotation R from second cam 25 that lug dish 17 passes to swash plate 18.Therefore, numerous and diverse processing of dark groove is necessary a position or at first cam, 24 places only.Therefore, simplified the processing of articulated mechanism 19.Thereby this has reduced the manufacture cost of compressor 10.
And the camming surface 25a of second cam 25 is not surrounded by any wall portion.Thereby the shaped design of camming surface 25a is simple relatively.Therefore, design the side (for example, arc shaped surface or planar combination) of camming surface 25a easily, thereby when even the tilt angle of swash plate 18 changes, the dead volume of compression chamber 29 (promptly, when piston 28 is positioned at upper dead center position, the gap between each piston 28 and the valve plate 13) the maintenance constant.
In addition, because do not have wall portion around camming surface 25a, the second end section 21b of connecting pin 21 is outstanding from roller 22.So just can connect stop ring 26 comes off from the second end section to prevent roller 22.After being installed in roller 22 on the 21b of second end section, stop ring 26 is connected on the second end section 21b of connecting pin 21.By this way, roller 22 easily is installed on the connecting pin 21.
(2) on second cam 25, only camming surface 25a is towards roller 22.In other words, except camming surface 25a, second cam 25 does not have any wall portion towards roller 22.Therefore, make the distance between roller 22 and the upper dead center corresponding position P reach maximum.In other words, distance between roller 22 (plane M1) and the spherical protuberances 23 (plane M2) and the distance between first cam 24 and second cam 25.Thereby lug dish 17 stably supports swash plate 18.Therefore, even compression reaction force X passes to swash plate 18 with eccentric manner from piston 28, suppressed swash plate 18 and tilted being different from the direction that swash plate tilts with the direction that changes discharge capacity.In addition, the slip resistance of articulated mechanism reduces, and has improved the controllability of the discharge capacity of compressor 10.
(3) connecting pin 21 is with rotatable mode support rollers 22.Therefore, roller 22 moves smoothly along the camming surface 25a of second cam 25.This has just improved the controllability of the discharge capacity of compressor 10.
(4) the roller 22 contiguous supporting elements 20 of reception reaction force X.Thereby this has reduced to be produced and imposed on from roller 22 by compression reaction force the pressure of connecting pin 21.Therefore, improved the durability of connecting pin 21.The load that imposes on spherical protuberances 23 during transmission of torque is little.Therefore, it is little to impose on the pressure of connecting pin 21 during transmission of torque.So,, also can not influence the durability of connecting pin 21 even spherical protuberances 23 is separated with supporting element 20.
(5) carbon dioxide is used as the refrigeration agent of vehicle air conditioning.Verified by experience: big when acting on the compression reaction force X ratio use freon refrigerant on the swash plate 18 when using carbon dioxide coolant.Proved also that by experience compression reaction force X acts on the periphery of swash plate 18.
In a preferred embodiment, roller 22 separates with upper dead center corresponding position P.And, distance between roller 22 (plane M1) and the spherical protuberances 23 (plane M2) and the distance between first cam 24 and second cam 25.Therefore, in the compressor 10 of compression arbon dioxide refrigerant gas, articulated mechanism 19 and lug dish 17 receive the compression reaction force that acts on the swash plate 18 with optimal way.In addition, prevented that swash plate 18 from tilting being different from the direction that swash plate 18 tilts with the direction that changes discharge capacity.Thereby compressor 10 is applicable to the compression arbon dioxide refrigerant gas.
Under the situation that does not break away from essence of the present invention or scope, the present invention can be embodied in many other special shapes, and this is tangible for a person skilled in the art.Particularly, will be appreciated that the present invention can imbody form below.
As shown in Figure 5, the roller 22 of articulated mechanism 19 is spherical.In this case, camming surface 25a curves inwardly corresponding to spherical roller 22.Aduncate camming surface 25a is than the groove that the internal surface 24a by first cam 24 forms shallow (more particularly, the arc that is formed by the cross section of camming surface 25a is shorter than semi-circle).Therefore, as described in the advantage (1) of above-mentioned preferred embodiment, can easily process articulated mechanism 19.
Referring to Fig. 6, saved the spherical protuberances 23 of articulated mechanism 19.In this case, the first end section 21a of connecting pin 21 plays first direction protrusion.First cam 24 comprises prolongation pilot hole 24b, and the first end section 21a of connecting pin 21 inserts among this prolongation pilot hole 24b.First cam 24 directly contacts supporting element 20 so that moment is passed to swash plate 18 from lug dish 17.
Can know from Fig. 3 and to find out that the diameter of the spherical protuberances 23 of connecting pin 21 is greater than the diameter of the jack 20a of supporting element 20.But as shown in Figure 7, the diameter of spherical protuberances 23 is less than the diameter of jack 20a.This makes the connecting pin 21 that comprises spherical protuberances 23 to be formed by the cutting of single pole material.Because spherical protuberances 23 and connecting pin 21 are integrally formed, the number of parts that forms articulated mechanism 19 reduces.
Its diameter inserts among the jack 20a less than the spherical protuberances 23 of jack 20a.More particularly, when connecting pin 21 was connected with swash plate 18, connecting pin 21 inserted the jack 20a of supporting element 20 from first end section 21a.In the embodiment of Fig. 7, flange 21c is integrally formed to prevent that roller 22 from coming off at edge and the connecting pin 21 of second end section 21b.Therefore, do not need the stop ring 26 (referring to Fig. 3) that separates with connecting pin 21.This has reduced the number of parts that forms articulated mechanism 19.
The camming surface 25a of second cam 25 can be outwardly-bent towards roller 22.
The spherical protuberances 23 of connecting pin 21 is supported in rotatable mode.When the tilt angle of swash plate 18 changed, spherical protuberances 23 moved along the internal surface of first cam 24.That is, first direction protrusion can be a roller.
In the embodiment of Fig. 2 to 7, roller 22 is used as second direction protrusion of articulated mechanism 19.But second direction protrusion can be fixed on the supporting element so that it does not rotate.
The supporting element 20 of articulated mechanism 19 (specifically, midplane S) can form with upper dead center corresponding position P and be in line.
Distance between roller 22 and the supporting element 20 and spherical protuberances 23 can equate with distance between the supporting element 20.
In the embodiment of Fig. 2 to 7, the present invention applies in the variable swash plate capacity compressors 10.But the present invention can apply in the Wobble plate compressor with variable displacement.
In a preferred embodiment, carbon dioxide is used as the refrigeration agent of vehicle air conditioning.But, also can use chlorofluoromethane refrigerant.In other words, the present invention also can apply in the compressor with variable displacement that fluorine Lyons is refrigerant gas.
These examples of the present invention and embodiment are illustrative and nonrestrictive, and the present invention is not limited to details given herein, but can change in the equivalent of claims and scope.
Claims (16)
1. a compressor (10), this compressor passes to cam disk (18) with the rotation of live axle (16) from lug dish (17), along with the cam disk rotation makes piston (28) to-and-fro motion with pressurized gas, and the tilt angle of change cam disk is to change discharge capacity, this compressor comprises the articulated mechanism (19) that is arranged between lug dish and the cam disk, and this compressor is characterised in that:
This articulated mechanism comprises: be formed on the supporting element (20) on the cam disk; First direction protrusion (23) that on the backward directions of the direction of rotating, extends from this supporting element with respect to live axle; Second direction protrusion (22) that forwards upwards extends in the direction of rotating from this supporting element with respect to live axle; Be formed on first cam (24) on the lug dish in the mode around this first direction protrusion, it is used to guide this first direction protrusion; With second cam (25) that is formed on the lug dish, it comprises the camming surface that is used to contact and guide second direction protrusion.
2. compressor according to claim 1 is characterized in that this second cam comprises the front portion relative with the sense of rotation of live axle, and this front portion is in the sense of rotation upper shed of live axle.
3. compressor according to claim 1 and 2, wherein, piston moves to upper dead center position, and cam disk comprises the part (P) between first direction protrusion and second direction protrusion, this part is used for the upper dead center position place that driven plunger moves on to piston, it is characterized in that:
Distance between second projection and this part is greater than the distance between first direction protrusion and this part.
4. compressor according to claim 1 and 2 is characterized in that this articulated mechanism also comprises the pin part (21b) from the supporting element extension that edge and live axle intersect, and second direction protrusion comprises the roller that is supported by this pin part in rotatable mode.
5. compressor according to claim 4, it is characterized in that this supporting element comprises jack (20a), and this articulated mechanism comprises the pin (21) in the jack that inserts supporting element, this pin has the second end section that limits first end section this first direction protrusion, that have head (21a) and limit this pin part, wherein, the diameter of this spherical part is less than the diameter of jack.
6. compressor according to claim 5 is characterized in that this spherical part and pin are integrally formed.
7. compressor according to claim 5 is characterized in that this pin comprises the retainer integrally formed with the second end section, is used to prevent that roller from coming off from pin.
8. compressor according to claim 4 is characterized in that this pin part extends out from roller.
9. compressor according to claim 1 and 2 is characterized in that distance between this second direction protrusion and the supporting element is less than the distance between first direction protrusion and the supporting element.
10. compressor according to claim 1 and 2 is characterized in that this compressor compresses is used for the carbon dioxide refrigeration gas of air conditioner.
11. compressor according to claim 1 and 2 is characterized in that this first cam comprises the groove that is used to guide first targeting part.
12. compressor according to claim 1 and 2 is characterized in that this first cam comprises the elongated pore that is used to guide first direction protrusion.
13. compressor according to claim 1 and 2 is characterized in that this first direction protrusion extends from supporting element from second direction protrusion backward with respect to the sense of rotation of live axle.
14. a compressor (10), this compressor comprises:
Housing (10a); Be formed on the cylinder-bore (27) in the housing; Be supported on live axle (16) in the housing in rotatable mode; Be connected in live axle with the lug dish (17) of live axle one rotation; With the cam disk (18) that tiltable mode driven shaft supports, this cam disk has towards the first surface of lug dish (18b), and this lug dish has the second surface (17a) towards the first surface of cam disk; Has the end that is connected in cam disk and pistons reciprocating (28) in cylinder-bore; And be arranged at articulated mechanism (19) between lug dish and the cam disk, this compressor is characterised in that:
This articulated mechanism comprises: be formed on the supporting element (20) on the first surface; First direction protrusion (23) that on the backward directions of the direction of rotating, extends from supporting element with respect to live axle; Second direction protrusion (22) that forwards upwards extends in the direction of rotating from supporting element with respect to live axle; Be formed on first cam (24) on the second surface in the mode around first direction protrusion, it is used to guide first direction protrusion; Be formed on the second surface and comprise second cam (25) of camming surface, this camming surface is used for contact and guides second direction protrusion.
15. a compressor (10), this compressor comprises:
Housing (10a); Be formed on the cylinder-bore (27) in the housing; Be supported on live axle (16) in the housing in rotatable mode; Be connected in live axle with the lug dish (17) of live axle one rotation; With the cam disk (18) that tiltable mode driven shaft supports, this cam disk has towards the first surface of lug dish (18b), and the lug dish has towards the second surface of the first surface of cam disk (17a); Has the end that is connected in cam disk and pistons reciprocating (28) in cylinder-bore; And be arranged at articulated mechanism (19) between lug dish and the cam disk, this compressor is characterised in that:
This articulated mechanism comprises: be formed on the first surface and comprise the supporting element (20) of jack (20a); Insert in this jack and have spherical part (23) and the pin (21) of rotatable roller (22), this spherical part extends from supporting element on the backward directions of the direction of rotating with respect to running shaft, this roller forwards upwards extends from supporting element the direction of rotating with respect to live axle, be formed on the second surface and comprise first cam (24) of groove, this groove around and guide spherical part; Be formed on second surface on and comprise second cam (25) that is used to contact and guide the camming surface of roller.
16. compressor according to claim 15, to such an extent as to it is characterized in that this groove and the camming surface live axle that tilts is just far away more from them the closer to their second surfaces.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003386004 | 2003-11-14 | ||
| JP386004/03 | 2003-11-14 | ||
| JP386004/2003 | 2003-11-14 | ||
| JP14766/04 | 2004-01-22 | ||
| JP14766/2004 | 2004-01-22 | ||
| JP2004014766A JP4103806B2 (en) | 2003-11-14 | 2004-01-22 | Variable capacity compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1616824A true CN1616824A (en) | 2005-05-18 |
| CN100373048C CN100373048C (en) | 2008-03-05 |
Family
ID=34436996
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004101023219A Expired - Fee Related CN100373048C (en) | 2003-11-14 | 2004-11-12 | Variable displacement compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20050147504A1 (en) |
| EP (1) | EP1531266B1 (en) |
| JP (1) | JP4103806B2 (en) |
| KR (1) | KR100614023B1 (en) |
| CN (1) | CN100373048C (en) |
| DE (1) | DE602004005943T2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4103806B2 (en) | 2003-11-14 | 2008-06-18 | 株式会社豊田自動織機 | Variable capacity compressor |
| KR102038507B1 (en) * | 2018-09-14 | 2019-10-30 | 에스트라오토모티브시스템 주식회사 | Hinge mechanism for variable swash plate type compressor and variable swash plate type compressor including the same |
Family Cites Families (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60175783A (en) * | 1984-02-21 | 1985-09-09 | Sanden Corp | Variable capacity swash plate compressor |
| JPS6282283A (en) * | 1985-10-02 | 1987-04-15 | Toyoda Autom Loom Works Ltd | Swaying swash plate type compressor |
| JPS63149319U (en) * | 1987-03-24 | 1988-09-30 | ||
| KR970003251B1 (en) * | 1992-08-21 | 1997-03-15 | 가부시끼가이샤 도요다 지도쇽끼 세이사꾸쇼 | Variable capacity type swash plate compressor |
| JP3125952B2 (en) * | 1993-04-08 | 2001-01-22 | 株式会社豊田自動織機製作所 | Variable capacity swash plate compressor |
| DE19616961C2 (en) * | 1996-04-27 | 2002-11-07 | Daimler Chrysler Ag | Reciprocating piston machine with swash plate gear |
| EP0855505B1 (en) * | 1997-01-24 | 2004-03-31 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement compressor |
| JP3826473B2 (en) | 1997-02-28 | 2006-09-27 | 株式会社豊田自動織機 | Variable capacity compressor |
| JP4007637B2 (en) * | 1997-03-31 | 2007-11-14 | サンデン株式会社 | Variable capacity compressor |
| JP3880159B2 (en) * | 1997-10-21 | 2007-02-14 | カルソニックカンセイ株式会社 | Swash plate type variable capacity compressor |
| JPH11201032A (en) * | 1998-01-13 | 1999-07-27 | Toyota Autom Loom Works Ltd | Variable displacement type compressor |
| JPH11264371A (en) | 1998-03-18 | 1999-09-28 | Toyota Autom Loom Works Ltd | Variable displacement compressor |
| US6139283A (en) * | 1998-11-10 | 2000-10-31 | Visteon Global Technologies, Inc. | Variable capacity swash plate type compressor |
| KR100318772B1 (en) * | 1999-12-16 | 2001-12-28 | 신영주 | Variable capacity swash plate type compressor |
| JP2001289159A (en) * | 2000-04-03 | 2001-10-19 | Zexel Valeo Climate Control Corp | Variable displacement swash plate compressor |
| JP2001304108A (en) * | 2000-04-20 | 2001-10-31 | Toyota Industries Corp | Compressor |
| KR100661358B1 (en) * | 2000-11-20 | 2006-12-27 | 한라공조주식회사 | Structure for hinge connecting rotor and swash plate of a variable displacement swash plate type compressor |
| KR100661359B1 (en) * | 2000-11-20 | 2006-12-27 | 한라공조주식회사 | Structure for hinge connecting rotor and swash plate of a variabie displacement swash plate type cpmpressor |
| JP3891099B2 (en) * | 2001-11-12 | 2007-03-07 | 株式会社豊田自動織機 | Piston compressor |
| US6860188B2 (en) * | 2003-06-20 | 2005-03-01 | Visteon Global Technologies, Inc. | Variable displacement compressor hinge mechanism |
| JP4103806B2 (en) | 2003-11-14 | 2008-06-18 | 株式会社豊田自動織機 | Variable capacity compressor |
-
2004
- 2004-01-22 JP JP2004014766A patent/JP4103806B2/en not_active Expired - Fee Related
- 2004-11-11 KR KR1020040091816A patent/KR100614023B1/en not_active IP Right Cessation
- 2004-11-11 US US10/987,758 patent/US20050147504A1/en not_active Abandoned
- 2004-11-11 DE DE602004005943T patent/DE602004005943T2/en not_active Expired - Fee Related
- 2004-11-11 EP EP04026808A patent/EP1531266B1/en active Active
- 2004-11-12 CN CNB2004101023219A patent/CN100373048C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| EP1531266A3 (en) | 2006-01-11 |
| JP2005163772A (en) | 2005-06-23 |
| KR20050046569A (en) | 2005-05-18 |
| JP4103806B2 (en) | 2008-06-18 |
| KR100614023B1 (en) | 2006-08-22 |
| EP1531266B1 (en) | 2007-04-18 |
| CN100373048C (en) | 2008-03-05 |
| DE602004005943T2 (en) | 2008-01-17 |
| EP1531266A2 (en) | 2005-05-18 |
| US20050147504A1 (en) | 2005-07-07 |
| DE602004005943D1 (en) | 2007-05-31 |
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