CN1081235A - The oblique tray type compressor that variable displacement mechanism is arranged - Google Patents
The oblique tray type compressor that variable displacement mechanism is arranged Download PDFInfo
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- CN1081235A CN1081235A CN 92109295 CN92109295A CN1081235A CN 1081235 A CN1081235 A CN 1081235A CN 92109295 CN92109295 CN 92109295 CN 92109295 A CN92109295 A CN 92109295A CN 1081235 A CN1081235 A CN 1081235A
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Abstract
The present invention relates to a kind of Wobble plate type refrigerant agent compressor, for example the swing-plate type coolant compressor with capacity regulating mechanism.Capacity regulating mechanism comprises a control valve unit and a valve member, and control valve unit has the bellows of the extending/contraction of a response crankshaft cavity pressure, and valve member is contained in an end of bellows, is communicated with the opening and closing of the path of crankshaft cavity and induction chamber in order to direct control.Bellows has first effective pressure of response crankshaft cavity pressure to bear cross-section area, valve member has second effective pressure of response induction chamber pressure to bear cross-section area, second effective pressure of valve member bears that cross-section area approximates or bear 80% of cross-section area greater than first effective pressure of bellows, cause volume controlled stage induction chamber pressure range obviously to reduce, thereby can control the air conditioning in the passenger carriage of vehicle effectively in press operation.
Description
The present invention relates to a kind of coolant compressor, relate in particular to a kind of Wobble plate type refrigerant agent compressor, for example be used for the swing-plate type coolant compressor with variable displacement mechanism of vehicle air conditioner.
The swing-plate type coolant compressor with variable displacement mechanism that is shown among Fig. 1 was done in the Patent right U.S. Patent No. 4,960,367 of Terauchi to describe authorizing.For convenience of description, the left side of figure is referred to as front end or front portion, and the right side of figure is referred to as the rear end.
With bearing 61 and 62 balance 60 is rotatably installed on the swash plate 50, fork-shaped slide block 63 is installed in the outer periphery end of balance 60, and is slidably mounted on the slide rail 64 that is between front end-plate 23 and the cylinder block 21.Fork-shaped slide block 63 can prevent that balance 60 from rotating, and when cam turntable 40 rotations, balance 60 is done pitching movement along slide rail 64.Cylinder block 21 has the cylinder 70 that distributes around some edges, and piston 71 is reciprocating in cylinder.Each piston 71 links to each other with balance 60 by its corresponding connecting rod 72.
Referring now to Fig. 2, valve control device 19' has a cup-shaped housing member 191 that limits valve chamber 192 within it." O " type circle 19a is contained between the internal surface of the outer surface of housing member 191 and through hole 210, in order to the fitting surface of seal casinghousing spare 191 and cylinder block 21.At the closed end of housing member 191 (Fig. 1,2 the left side) some hole 19b are arranged, so that make the pressure of valve chamber 192 the same with the pressure of crankshaft cavity by the slit 31a that exists between bearing 31 and the cylinder block 21.Control valve unit 193 is contained in the valve chamber 192, and this control valve unit has the bellows 193a of energy longitudinal tensile strain and contraction and is contained in the valve member 193b of bellows 193a rear end.Bellows 193a can vertically shrink and extend according to pressure in the crankshaft cavity.Bellows 193a is made by elastic material, for example makes with phosphor bronze, and the effective pressure of this bellows is born and used area A below the cross-section area
1Expression.Valve member 193b is generally hemisphere, and it is contained in the rear end of bellows 193a.The overhanging element 193c that is contained in bellows 193a front end is inserted among the axial convex 19c at housing member 191 closed end centers.Biasing spring 193d longitudinally is fitted in the interior space of bellows 193a.The F that makes a concerted effort of the restoring force of bellows 193a and biasing spring 193d promotes the right side of valve member 193b(towards Fig. 1 and Fig. 2 continuously backward).
The center that the cylindrical member 194 that contains valve seat 194a inserts valve board assembly 200, this valve board assembly comprises valve plate 25, pad 27 and 28, suction reed valve 271 and exhaust reed valve 281.Valve seat 194a forms at the front end of cylindrical member 194, and is inserted into the opening end of housing member 191.The rear end of the cylindrical member 194 in the exhaust chamber 251 is screwed in nut 100 on the cylindrical member 194, and cylindrical member 194 just is fixed on the valve board assembly 200 with valve guard sheet 253 like this.The tapered opening 194b that holds valve member 193b is arranged on valve seat 194a, and this opening communicates with the axial cylinder 194c that forms in the cylindrical member 194.Therefore, the boundary between tapered opening 194b and cylinder 194c has just constituted ring edge 194d.
When bellows 193a longitudinally extended certain-length, common hemisphere valve member 193b just withstood tapered opening 194b, has so just formed circular Line of contact 193e between them.Circle Line of contact 193e is divided into anterior 193f and rear portion 193g with valve member 193b, the propagation of pressure in the induction chamber 241 is given the outer surface at valve member rear portion by the following radial hole that will describe 151, passage 152 and hole 153.The effective pressure of valve member 193b rear portion 193g is born the cross-section area area A
2Expression, it is about the effective pressure of bellows 193a and bears cross-sectional area A
150%.
Be contained in the rear end that the catch bar 195 among the cylinder 194c slightly stretches out cylinder 194c slidably, catch bar links to each other with valve member 193b by biasing spring 196, and the valve member 193b of control valve unit 193 passed to power reposefully by this spring from catch bar 195.Catch bar 195 has one and its all-in-one-piece annular flange 195a, and this flange radially extends from the outer surface of catch bar 195 front ends.Circular flange 195a is arranged in tapered opening 194b, and this annular flange can make catch bar 195 avoid moving too backwards by contacting with ring edge 194d." O " RunddichtringO 197 is installed around catch bar 195, so that the fitting surface of sealed cylindrical 194c and catch bar 195, thereby bleed in the gap of refrigerant gas between cylinder 194c and bar 195 that prevents exhaust chamber 251 among the tapered opening 194b.Threaded cup shell 103 on the inner circumference sidewall is installed in the rearward end of cylindrical member 194, falls down from the rear end of cylindrical member 194 to prevent " O " type circle 197.
On valve seat 194a, have radial hole 151, so that the passage of opening on tapered opening 194b and the cylinder block 21 152 communicates.The passage 152 that contains the 152a that has living space communicates with induction chamber 241 by the hole 153 of opening on the valve board assembly 200.The path 150 that crankshaft cavity 22 and induction chamber 241 are connected comprises gap 31a, hole 210, hole 19b, valve chamber 192, tapered opening 194b, radial hole 151, passage 152 and hole 153.Therefore, the opening and closing of path 150 are by the contraction and the elongation control of control valve unit 193.The contraction of control valve unit is relevant with the crankshaft cavity internal pressure with elongation.
During compressor 10 runnings, vehicle motor drives live axle 26 rotations by magnetic clutch 300.Cam turntable 40 and swash plate 50 are with live axle 26 one rotation.The rotation of swash plate causes that balance 60 does pitching movement.The pitching movement of balance 60 impels all pistons 71 reciprocating in its cylinder 70 separately.When piston 71 to-and-fro motion, the refrigerant gas that enters induction chamber 241 by inlet 241a flows in each cylinder 70 through intakeport 242, and refrigerant gas is compressed then.Refrigerant gas after the compression is discharged in the exhaust chamber 251 by relief opening 252 from each cylinder 70, flows into the refrigerating circuit by outlet 251a from exhaust chamber again.
The swept volume of regulating compressor 10 according to the variation of the variation of vaporizer heat load or compressor rotary speed makes the pressure in the induction chamber 241 keep constant.Save the swept volume of compressor by the adjustable angle that changes the swash plate 50 relevant with pressure in the crankshaft cavity.The pressure increase causes that the tilt angle of swash plate 50 and balance 60 reduces in the crankshaft cavity, so just reduced the swept volume of compressor.Pressure in the crankshaft cavity reduces the tilt angle that causes swash plate 50 and balance 60 and increases, so just increased the swept volume of compressor.
As U.S. Patent No. 4,960,367 described like that, the effect of valve control device 19 is that the swept volume by following method control compressor makes the outlet pressure of vaporizer keep constant.Catch bar 195 pushes away valve member 193b towards the direction that bellows 193a and bias spring 19b are shunk.The mobile pressure that depends in the exhaust chamber 251 of catch bar 195, and the pressure increase in the exhaust chamber 251 makes bar 195 move towards bellows 193a, bellows 193a is further shunk, move at the control point that its result changes compressor capacity, thereby keep the outlet pressure of vaporizer constant.That is to say that what valve control device 19 utilized is basic this fact that is directly proportional with inspiratory flow rate of exhaust pressure of compressor.Because catch bar 195 directly moves according to the variation of exhaust pressure, and it has a pressure that directly acts on control valve unit 193, so directly move according to the variation of exhaust pressure at the control point that control valve unit 193 is worked.
Also to describe in detail below the concrete working condition of valve control device 19.For the description of the work that makes valve control device 19 for simplicity, the back is omitted the above-mentioned effect of valve control device 19 and is not said.
Referring now to Fig. 3 and 4, particularly with reference to Fig. 4, when compressor was out of service, the pressure P s of induction chamber and the pressure P c of crankshaft cavity were in state of equilibrium, i.e. Ps=Pc, this pressure greater than the pressure P of the operation point of control valve unit 193 '
1This just makes bellows 193a shrink, so that valve assembly 193b makes between induction chamber 241 and the valve chamber 192 through tapered opening 194b, and radial hole 151, passage 152 and hole 153 communicate, and therefore make between crankshaft cavity 22 and the induction chamber 241 to communicate.
At compressor when to be in the time period shown in Figure 4 " a " be running state in the cooling stage, the runnability of compressor is as follows: when compressor starts is moved, keep between crankshaft cavity 22 and the induction chamber 241 being communicated with, therefore satisfy equation Pc=Ps, this straight line " li " as shown in Figure 3, until induction chamber pressure P s drop to control valve unit 193 the operation point pressure P '
1Till.When the pressure P s of induction chamber drop to control valve unit 193 the operation point pressure P '
1The time, because bellows 193a elongation, valve member 193b contacts with the internal surface of tapered opening 194b.If the pressure P s of induction chamber drop to the operation point pressure P that is lower than control valve unit 193 '
1The time, valve member 193b is according to following equation repeated open and close tapered opening 194b:
F＝（A
1-A
2）Pc+A
2·Ps （1）
Herein: F is making a concerted effort of bellows 193a and biasing spring 193d restoring force, A
1Be that bellows 193a effective pressure is born cross-section area, A
2Be that valve member 193b rear portion 193g effective pressure is born cross-section area, Ps is the pressure in the induction chamber 241, and Pc is the pressure in the crankshaft cavity 22.Below can converting to, top equation (1) finds the solution the equation of Pc:
Pc＝A
2·Ps/（A
2-A
1）+F/（A
1-A
2） （2）
The pressure P c that equation (2) illustrates crankshaft cavity changes with the variation of the pressure P s of induction chamber.In addition, in the prior art, A
2=0.5A
1So, use 0.5A
1Replaced A
2After, equation (2) can further change into following equation:
Pc＝-Ps+2F/A
1（3）
Equation (3) is represented with the straight line " m' " of Fig. 3.So the pressure P s of induction chamber descends inversely with the increase of crankshaft cavity pressure P c, when induction chamber pressure P s be lower than control valve unit 193 the operation point pressure P '
1The time their become 1 to 1 relation, the oblique position of swash plate 50 remains on the position of maximum inclination angle at this moment.Yet as shown in Figure 4, in case the pressure P s of induction chamber reaches setting pressure P'
5Pressure (pressure reduction when this pressure between crankshaft cavity 22 and the induction chamber 241 is maximum △ Pmax) time, the angle of inclination of swash plate 50 changes to the angle littler than allowable angle of inclination.So the capacity of compressor changes to the capability value littler than maximum value.
The working condition of compressor was shown in time period " b " among Fig. 4 when the heat load on the vaporizer reduced gradually.The a certain angle that crankshaft cavity pressure P c increases gradually as long as the oblique position of swash plate 50 remains on that the pressure P s that makes induction chamber reduces gradually just satisfies equation (3).Yet, in case induction chamber pressure P s reaches setting pressure P'
5The time, the oblique position of swash plate 50 just becomes another angle littler than first angle from this angle.So the compressor displacement value changes to another value littler than first value from a value.When compressor capacity changed to smaller value because of the tilt angle of swash plate 50 becomes smaller angle, because the new compressor capacity that reduces is not enough to the heat load of compensating evaporator, the pressure P s of induction chamber increased sharply.But, reach setting pressure P' at the pressure P s of induction chamber
4(pressure reduction under this pressure between crankshaft cavity 22 and the induction chamber 241 is △ Pmin) quick the increasing of induction chamber pressure P s before reaches peak value.After this, induction chamber pressure P s is reduced gradually and a certain angle that crankshaft cavity pressure P c increases gradually, just satisfy equation (3) as long as the oblique position of swash plate 50 is kept.When the heat load of vaporizer reduces in time gradually, repeat above-mentioned running.
In addition, the heat load on vaporizer in time (by the expression of time period " C " of Fig. 4) compressor is other operation conditions when increasing gradually.Induction chamber pressure P s is increased gradually and a certain angle that crankshaft cavity pressure P c reduces gradually as long as the oblique position of swash plate 50 remains on, just satisfy equation (3).But, in case induction chamber pressure P s reaches setting pressure P'
4The time, the oblique position of swash plate 50 just changes to another angle bigger than first angle from this angle.So compressor capacity just changes to another value bigger than first value from a value.When compressor capacity became higher value because of the tilt angle of swash plate 50 changes to than wide-angle, because of the compressor capacity that increases newly is enough to the heat load of compensating evaporator, induction chamber pressure P s reduced rapidly.But the rapid minimizing of induction chamber pressure P s is to reach setting pressure P' at induction chamber pressure P s
SFinished in the past.After this, induction chamber pressure P s is increased gradually and a certain angle that crankshaft cavity pressure P c reduces gradually, just satisfy equation (3) as long as the oblique position of swash plate 50 remains on.When the heat load of vaporizer increases in time gradually, repeat above-mentioned running.
Therefore, at the volume controlled working stage that comprises time period shown in Figure 4 " b " and " C ", the excursion of induction chamber pressure P s is △ P'
S=P'
4-P'
5, and the excursion of crankshaft cavity pressure P c is △ P'
C=P'
2-P'
3In addition, because induction chamber pressure P s descends inversely according to the increase with crankshaft cavity pressure P c of 1 to 1 relation, so the excursion △ P' of induction chamber pressure
SEqual the excursion △ P' of crankshaft cavity pressure
CSo induction chamber pressure is at the excursion △ in volume controlled stage P'
SCan not ignore.Therefore, when existing compressor was used for vehicle air conditioner, the variation of temperature scope of leaving the cool air of vaporizer was not very little, thereby the air conditioning in the passenger compartment of vehicle in fact can not get effective control.
Therefore, the object of the present invention is to provide a kind of Wobble plate type refrigerant agent compressor with capacity control mechanism, above-mentioned control mechanism can make the induction chamber pressure range enough little at the volume controlled working stage.
In order to achieve the above object, Wobble plate type refrigerant agent compressor provided by the invention comprises a compressor housing with front end-plate and end plate.Crankshaft cavity and cylinder block place housing, and some cylinders are arranged in the cylinder block.The piston that a cunning is joined all is housed in each cylinder, and piston drives reciprocating by driving mechanism.Above-mentioned driving mechanism comprises live axle, linking to each other with all pistons with the driving rotating disk of the continuous also rotation of live axle and this rotating disk makes rotatablely moving of rotating disk be transformed into the reciprocating bindiny mechanism of piston.Between surface of an assembly of this bindiny mechanism and the plane tilt angle is arranged perpendicular to drive axis.The above-mentioned tilt angle of assembly can be regulated, so that change the stroke of reciprocating piston, thus the ability to work or the capacity of change compressor.Induction chamber and exhaust chamber are surrounded by end plate.Article one, path makes the fluid communication between crankshaft cavity and the induction chamber.An angle controller is housed in the compressor, and this control gear can be according to the angle of inclination of variation in pressure control connection mechanism assembly in the crankshaft cavity.
The present invention also provides a valve control device, this valve control device contain one can longitudinal tensile strain according to pressure in the crankshaft cavity and the bellows of contraction and one be contained in bellows one end in order to open and close the valve member of above-mentioned path.Bellows has first effective pressure of a response crankshaft cavity pressure to bear cross-section area.A valve seat that holds valve member is arranged in the path.When valve member enters in the valve seat, just formed the separatrix of this valve member on the outer surface of valve member.This separatrix is divided into first portion and second portion to valve member, when valve member enters in the valve seat, and the pressure of the outer surface of first portion response induction chamber, second portion is exactly the part that valve member is left except that first portion.The first portion of this valve member has second effective pressure of response induction chamber pressure and bears cross-section area.Second effective pressure is born cross-section area be designed to equal at least first effective pressure and bear 80% of cross-section area, thereby make the minimum of putting forward at press volume controlled working stage induction chamber pressure that is changed to.
Fig. 1 is the vertical longitudinal sectional drawing of traditional swing-plate type coolant compressor with variable displacement mechanism;
Fig. 2 is the amplification profile of valve control device shown in Figure 1;
Fig. 3 is the crankshaft cavity of expression swing-plate type coolant compressor shown in Figure 1 and the graph of relation between the pressure in the induction chamber;
Fig. 4 is expression swing-plate type coolant compressor institute's elapsed time shown in Figure 1 and the graph of relation between the pressure in crankshaft cavity and the induction chamber;
Fig. 5 is for having the amplification view of the valve control device that is equipped with in the swing-plate type coolant compressor of variable displacement mechanism according to an embodiment of the invention;
Fig. 6 is the graph of relation between the pressure of the crankshaft cavity of swing-plate type coolant compressor shown in Figure 5 and induction chamber;
Fig. 7 is swing-plate type coolant compressor institute's elapsed time shown in Figure 5 and the graph of relation between the pressure in crankshaft cavity and the induction chamber.
Fig. 5 has represented the structure of the valve control device of being installed 19 according to an embodiment of the invention in having the swing-plate type coolant compressor of variable displacement mechanism.In the figure, identical label is in order to identical parts among expression and Fig. 1 and 2.In addition, in order to narrate conveniently, the left side of figure is referred to as front end or front portion, and the right side of figure is referred to as the rear end.
Referring to Fig. 5, valve control device 19 comprises the control valve unit 293 and the valve member 293b who is contained in bellows 193a rear end that contain the bellows 193a of energy longitudinal tensile strain and contraction.Bellows 193a is according to the pressure longitudinal tensile strain and the contraction of crankshaft cavity.Bellows 193a is for example made by phosphor bronze by elastic material, and the effective pressure of this bellows is born and used area A below the cross-section area
1Expression.Valve member 293b is common truncated cone shape, and it is fixed on the rear end of bellows 193a.The overhanging element 193c that is fixed on bellows 193a front end is inserted among the axial convex 19c in housing member 191 closed end center portions.Biasing spring 193d longitudinally is fitted in the interior space of bellows 193a.The restoring force of bellows 193a and biasing spring 193d make a concerted effort F constantly with valve member 293b to pusher (towards the right of Fig. 5).
When bellows 193a was elongated to a certain longitudinal length, truncated cone shape valve member 293b just entered among the tapered opening 194b usually, has formed circular Line of contact 293e like this between them.Circular Line of contact 293e is divided into anterior 293f and rear portion 293g to valve member 293b, can respond the pressure of induction chamber 241 by the outer surface at radial hole 151, passage 152 and 153 rear portions, hole.The effective pressure of the rear portion 293g of valve member 293b is born and is used area A below the cross-section area
2Expression, this area is about the effective pressure of bellows 193a and bears cross-sectional area A
180%.
Referring to Fig. 6 and Fig. 7, especially as shown in Figure 7, when compressor was out of service, the pressure P s of induction chamber and the pressure P c of crankshaft cavity were in state of equilibrium, i.e. Pc=Ps, and this pressure is greater than the operation point pressure P of control valve unit 293
1This just makes bellows 193a shrink, so that valve assembly 293b makes between induction chamber 241 and the valve chamber 192 and communicate through tapered opening 194b, radial hole 151, passage 152 and hole 153, therefore makes between crankshaft cavity 22 and the induction chamber 241 to communicate.
At compressor when to be in the time period shown in Figure 7 " a " be running state in the cooling stage, compressor moves as follows: when compressor starts is moved, keep between crankshaft cavity 22 and the induction chamber 241 being communicated with, therefore satisfy equation Pc=Ps, this straight line " li " as shown in Figure 6 is until induction chamber pressure P s drops to the operation point pressure P of control valve unit 293
1Till.Drop to the operation point pressure P of control valve unit 293 as induction chamber pressure P s
1The time, valve member 293b contacts with the internal surface of tapered opening 194b owing to the elongation of bellows 193a.If induction chamber pressure P s drops to the operation point pressure P that is lower than control valve unit 293
1The time, valve member 293b opens and closes tapered opening 194b repeatedly according to following equation:
F＝（A
1-A
2）·Pc+A
2·Ps （1）
Wherein F be bellows 193a and biasing spring 193d restoring force make a concerted effort A
1The effective pressure that is bellows 193a is born cross-section area, A
2The effective pressure that is valve member 293b rear portion 293g is born cross-section area, and Ps is the pressure in the induction chamber 241, and Pc is the pressure in the crankshaft cavity 22.Below can converting to, top equation (1) finds the solution the equation of Pc:
Pc＝A
2·Ps/（A
2-A
1）+F/（A
1-A
2） （2）
The pressure P c that equation (2) shows crankshaft cavity changes with the variation of the pressure P s of induction chamber.In addition, in this valve control device, A
2Equal 0.8A
1So, use 0.8A
1Replaced A
2After, equation (2) can further convert following equation to:
Pc＝-4Ps+5F/A
1（4）
Equation (4) is represented with the straight line " m " among Fig. 6.So, be lower than the operation point pressure P of control valve unit 293 as induction chamber pressure P s
1The time, induction chamber pressure P s is along with the increase of the crankshaft cavity pressure P c proportionate relationship with 1: 4 reduces inversely.The oblique position of swash plate 50 remains on the position of maximum inclination angle at this moment.Yet as shown in Figure 7, in case the pressure P s of induction chamber reaches the 3rd setting pressure P
5When (pressure reduction when this pressure between crankshaft cavity 22 and the induction chamber 241 becomes maximum △ Pmax), then the tilt angle of swash plate 50 changes to the angle littler than allowable angle of inclination, so the capacity of compressor changes to the capability value littler than maximum value.
The working condition of compressor was shown in time period " b " among Fig. 7 when the heat load on the vaporizer reduced gradually.As long as the oblique position of swash plate 50 remains on and induction chamber pressure P s reduced gradually and crankshaft cavity pressure P c increases sharply, just can satisfy equation (4).Yet, in case induction chamber pressure P s reaches setting pressure P
5The time, the oblique position of swash plate 50 just becomes another angle littler than first angle from this angle.Thereby compressor capacity changes to another value littler than first value from this value.When compressor capacity changed to smaller value because of the tilt angle of swash plate 50 becomes smaller angle, because the off-capacity of the new compressor that reduces is with the heat load of compensating evaporator, induction chamber pressure P s increased sharply.But s reaches setting pressure P in the induction chamber pressure P
4(at setting pressure P
4The time pressure reduction between crankshaft cavity 22 and the air aspiration cavity 241 become △ Pmin) before induction chamber pressure P s increase fast and reach maximum.After this, induction chamber pressure P s is reduced gradually and a certain angle that crankshaft cavity pressure P c increases sharply, just can satisfy equation (4) as long as the oblique position of swash plate 50 maintains.When the heat load of vaporizer reduces in time gradually, repeat above-mentioned running.
In addition, (represent by the time period " c " of Fig. 7 during this period) in the compressor operating operating mode when heat load on vaporizer progressively increases in time, as long as the oblique position of swash plate 50 remains on induction chamber pressure P s is increased gradually, and a certain angle that crankshaft cavity pressure P c reduces rapidly just satisfies equation (4).But, in case induction chamber pressure P s reaches setting pressure P
4The time, the oblique position of swash plate 50 just changes to another angle bigger than first angle from this angle.Thereby compressor capacity just changes to another value bigger than first value from a value.When compressor capacity became higher value because of the tilt angle of swash plate 50 changes to than wide-angle, because of compressor capacity increases the heat load that is enough to compensating evaporator again, induction chamber pressure P s reduced rapidly.But the rapid minimizing of induction chamber pressure P s is to reach setting pressure P at induction chamber pressure P s
5Finished in the past.After this, as long as the oblique position of swash plate 50 remains on and induction chamber pressure P s increased gradually and crankshaft cavity pressure P c reduces rapidly, just satisfy equation (4).When the heat load of vaporizer progressively increases in time, repeat above-mentioned running.
Therefore, at the volume controlled working stage that comprises time period shown in Figure 7 " b " and " c ", in the compressor of preferred embodiment, the excursion of induction chamber pressure P s is △ Ps=P
4-P
5, and the excursion of crankshaft cavity pressure P c is △ Pc=P
2-P
3In addition, because induction chamber pressure P s according to 1: 4 ratio with the increase of crankshaft cavity pressure P c underground the falling that be inversely proportional to, so the excursion △ Ps of induction chamber pressure is 1/4th of crankshaft cavity pressure range △ Pc.For example, the laboratory data after conventional compressor and compressor of the present invention compared shows: in the volume controlled stage, the excursion of induction chamber pressure from 0.26 to 0.1kgf/cm
2G.So in compressor of the present invention, in the volume controlled stage, the excursion of induction chamber pressure is more much smaller than conventional compressor significantly.Therefore, when compressor of the present invention was used for vehicle air conditioner, the range of temperature of leaving the cool air of vaporizer can be omitted and be disregarded, thereby can control the air conditioning in the Vehicular occupant compartment effectively.
In conjunction with the preferred embodiments the present invention has been done detailed description above.But this embodiment only is as an example, and the present invention is not limited to this.Should expect that those of ordinary skill in the art can carry out other conversion and change at an easy rate in the scope of the design that does not exceed claim qualification of the present invention.
Claims (5)
1, a kind of Wobble plate type refrigerant agent compressor, it comprises a compressor housing with cylinder block, cylinder block has some cylinders, be contained in described cylinder block one end and crankshaft cavity is trapped among front end-plate in the described cylinder block, slidably be contained in ordinatedly in described each cylinder and and drive reciprocating piston by driving mechanism, this driving mechanism comprises the rotating disk that links to each other with live axle, one has adjustable swash plate that inclined surface links to each other with rotating disk, this swash plate and can regulate perpendicular to the tilt angle between the plane of described drive axis, connection set in service links to each other described swash plate with piston, make described live axle, rotatablely moving of rotating disk and swash plate is transformed into the to-and-fro motion of described piston in cylinder, above-mentioned angle of inclination changes with the variation in pressure in the crankshaft cavity, thereby change the capacity of compressor, end plate is contained in the other end relative with front end-plate on the described cylinder block, end plate defines induction chamber and the exhaust chamber that is positioned at wherein, there is a path that described induction chamber is connected with crankshaft cavity, open or close described path by control valve device, the bellows that described control valve device has an elongation according to pressure in the crankshaft cavity and longitudinally or shrinks, and a valve member that is contained in described bellows one end arranged, in order to open and close described path, described bellows has first effective pressure of the pressure in the described crankshaft cavity of response to bear cross-section area, a valve seat is arranged on the described path, in order to hold described valve member, when valve member enters in the valve seat, this valve member has a separatrix of determining on this valve member outer surface, this separatrix is divided into first portion and second portion to valve member, when described valve member enters in the described valve seat, first of valve member partly has the outer surface of a response induction chamber pressure, the first portion of described valve member has second effective pressure of the described induction chamber pressure of response to bear cross-section area, and this second effective pressure bears that cross-section area approximates or bear 80% of cross-section area greater than described first effective pressure.
2, a kind of adjustable Wobble plate type refrigerant agent compressor comprises:
Compressor housing with some cylinders, an induction chamber, an exhaust chamber and a sealing crankshaft cavity;
The sliding piston that is contained in described each cylinder with joining;
The driving mechanism that comprises a rotating disk;
An adjustable swash plate, the inclined surface adjustable ground of this swash plate links to each other with described rotating disk, and the tilt angle of swash plate is adjustable, and this tilt angle changes with the variation in pressure in the described crankshaft cavity, thereby changes the capacity of described compressor;
In service with described swash plate and the connection set that described piston links to each other, it is reciprocating in cylinder to make rotatablely moving of described rotating disk and swash plate change piston into;
Article one, be arranged in the path that described induction chamber is connected with crankshaft cavity of compressor housing;
Control the control valve device that described path opens or closes, this control valve device comprises that first effective pressure with response crankshaft cavity pressure bears the bellows of cross-section area and one and be contained in bellows one end in order to open and close the valve member of described path, one valve seat is arranged on the described path, in order to hold valve member, when valve member enters in the valve seat, this valve member has a velamen to determine separatrix on the outer surface of valve member, this separatrix is divided into first portion and second portion to described valve member, when described valve member enters in the valve seat, just there is the outer surface of a response induction chamber pressure in described first portion, the first portion of described valve member has second effective pressure to bear cross-section area, and this sectional area approximates or bears 80% of cross-section area greater than described first effective pressure.
3, be used to control the swash plate control mechanism of the adjustable swash plate oblique position of Wobble plate type refrigerant agent compressor according to crankshaft cavity pressure, described compressor comprises the compressor housing of a definite crankshaft cavity and induction chamber, and described swash plate control mechanism comprises:
The path that described crankshaft cavity and induction chamber are connected in the compressor housing;
A valve seat that surrounds described path;
One is matched with described valve seat closing the valve member of described path, the separatrix between described valve member and path, and when described valve member engaged with valve seat, the first effective pressure area on the valve member had been determined in this separatrix; With
Link to each other with described valve member, make described valve member move to the bellows that engages with described valve seat, the cross section of described bellows has been determined the second effective pressure area, and the first effective pressure area on the described valve member approximates or greater than 80% of the second effective pressure area on the described bellows.
4, swash plate control mechanism as claimed in claim 3 also has a spring part of described valve member being pushed to valve seat in described bellows.
5, swash plate control mechanism as claimed in claim 2, wherein said valve member is the truncated cone, the separatrix that it engages with described valve seat is a circumference.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92109295 CN1034136C (en) | 1992-07-10 | 1992-07-10 | Slant plate type refrigerant compressor with variable displacement mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92109295 CN1034136C (en) | 1992-07-10 | 1992-07-10 | Slant plate type refrigerant compressor with variable displacement mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1081235A true CN1081235A (en) | 1994-01-26 |
| CN1034136C CN1034136C (en) | 1997-02-26 |
Family
ID=4944066
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 92109295 Expired - Lifetime CN1034136C (en) | 1992-07-10 | 1992-07-10 | Slant plate type refrigerant compressor with variable displacement mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1034136C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1093913C (en) * | 1996-12-31 | 2002-11-06 | 万都空调株式会社 | Compressor for use in refrigeration system |
| CN101487645B (en) * | 2008-01-17 | 2012-07-18 | 思科普有限责任公司 | Refrigerant compressor arrangement |
-
1992
- 1992-07-10 CN CN 92109295 patent/CN1034136C/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1093913C (en) * | 1996-12-31 | 2002-11-06 | 万都空调株式会社 | Compressor for use in refrigeration system |
| CN101487645B (en) * | 2008-01-17 | 2012-07-18 | 思科普有限责任公司 | Refrigerant compressor arrangement |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1034136C (en) | 1997-02-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C15 | Extension of patent right duration from 15 to 20 years for appl. with date before 31.12.1992 and still valid on 11.12.2001 (patent law change 1993) | ||
| OR01 | Other related matters | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Shanghai Sandian Automobile Air Conditioner Co. Ltd. Assignor: Sanden Corp. Contract fulfillment period: 2006.3.25 to 2023.12.3 Contract record no.: 2009990000811 Denomination of invention: Slant plate type refrigerant compressor with variable displacement mechanism Granted publication date: 19961005 License type: Exclusive license Record date: 20090728 |
|
| LIC | Patent licence contract for exploitation submitted for record |
Free format text: EXCLUSIVE LICENSE; TIME LIMIT OF IMPLEMENTING CONTACT: 2006.3.25 TO 2023.12.3; CHANGE OF CONTRACT Name of requester: SHANGHAI SANDIAN CAR AIR CONDITIONER LIMITED LIABI Effective date: 20090728 |
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| C17 | Cessation of patent right | ||
| CX01 | Expiry of patent term |
Expiration termination date: 20120710 Granted publication date: 19970226 |