CN100396916C - Control valve of variable displacement compressor - Google Patents
Control valve of variable displacement compressor Download PDFInfo
- Publication number
- CN100396916C CN100396916C CNB2004800024867A CN200480002486A CN100396916C CN 100396916 C CN100396916 C CN 100396916C CN B2004800024867 A CNB2004800024867 A CN B2004800024867A CN 200480002486 A CN200480002486 A CN 200480002486A CN 100396916 C CN100396916 C CN 100396916C
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- valve
- control
- variable displacement
- displacement compressor
- crankcase
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- 238000006073 displacement reaction Methods 0.000 title claims abstract description 54
- 239000003507 refrigerant Substances 0.000 claims abstract description 59
- 230000009471 action Effects 0.000 claims abstract description 3
- 230000008859 change Effects 0.000 claims description 14
- 230000006870 function Effects 0.000 claims description 5
- 230000003872 anastomosis Effects 0.000 claims description 4
- 230000008447 perception Effects 0.000 claims description 4
- 230000006835 compression Effects 0.000 abstract description 8
- 238000007906 compression Methods 0.000 abstract description 8
- 230000008014 freezing Effects 0.000 abstract 1
- 238000007710 freezing Methods 0.000 abstract 1
- 239000002826 coolant Substances 0.000 description 12
- 238000007599 discharging Methods 0.000 description 10
- 238000005057 refrigeration Methods 0.000 description 8
- 230000008676 import Effects 0.000 description 6
- 239000010802 sludge Substances 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 4
- 238000001556 precipitation Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000037361 pathway Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Images
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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/184—Valve controlling parameter
- F04B2027/1854—External parameters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/184—Valve controlling parameter
- F04B2027/1859—Suction pressure
Abstract
A control valve of a variable displacement compressor capable of improving compression efficiency by reducing the circulated amount of refrigerant in the variable displacement compressor, comprising a ball valve (11) controlling the flow rate of the refrigerant flowing from a delivery chamber to a crank chamber, a spool valve (12) controlling the flow rate of the refrigerant flowing from the crank chamber to a suction chamber, a diaphragm (13) sensing a suction pressure (Ps), and a solenoid (14) setting the suction pressure, wherein the spool valve (12) is formed so as to start flow rate control after the ball valve (11) is fully closed or nearly fully closed and the ball valve (11) is formed so as to start flow rate control after the spool valve (12) is minimally opened or nearly minimally opened. Because an area in which the ball valve (11) and the spool valve (12) are simultaneously opened can be almost eliminated when the flow rate controls of these valves are switched, the flow rate of the refrigerant circulating inside the variable displacement compressor and not contributing to freezing action can be minimized to increase the efficiency of the variable displacement compressor.
Description
Technical field
The present invention relates to a kind of control valve of variable displacement compressor, particularly a kind of in the refrigeration cycle of Vehicular air conditioner the control valve of employed variable displacement compressor.
Background technique
In Vehicular air conditioner, because indefinite,, make its refrigeration output keep constant and be not subjected to the influence of engine speed so need control to this aircondition as the rotating speed of the motor of its power source.At such requirement, use can change the ramp type variable displacement compressor of refrigerant discharge capacity usually.Be arranged in the crankcase and the variable swash plate in angle of inclination carries out oscillating motion by the rotation of running shaft, by this oscillating motion, a plurality of pistons carry out back and forth movement along the direction parallel with running shaft, and thus, this variable displacement compressor carries out suction, compression, the discharge of refrigerant.At this moment, make variation in pressure in the crankcase by utilizing control valve, and change the angle of inclination of swash plate, and change the stroke of piston, thereby change the discharge capacity of refrigerant.
Such control valve is configured in usually and is communicated with on the coolant channel of discharging chamber and crankcase, is the flow of the refrigerant of Pd by control from the head pressure that the discharge chamber imports to crankcase, the pressure P c in the control crankcase.The refrigerant that imports to crankcase is discharged to suction chamber by fixed throttle port, this control valve utilizes pressure-sensitive parts such as film spare for example to come suction pressure Ps in the perception suction chamber, and control imports the flow of the refrigerant in the crankcase, so that this suction pressure Ps maintenance is constant.
And, also control valve can be configured on the coolant channel that is communicated with crankcase and suction chamber, and fixed throttle port be set discharging between chamber and the crankcase, thereby the flow from the refrigerant of crankcase discharge is controlled.
Use in these two types of control valves any one variable displacement compressor, all from discharging the chamber to crankcase, perhaps on the passage from the crankcase to the suction chamber, series connection is provided with the constant fixed throttle port of aisle spare.Thereby, in the variable displacement compressor of one of them that has used described control valve, because portion carries out circuit refrigerant and becomes many within it, so can cause compression efficiency to reduce inevitably.
Following control valve was also proposed (for example, Japanese kokai publication sho 58-158382 communique, Fig. 3), promptly, be communicated with the coolant channel of discharging chamber and crankcase and on the coolant channel that is communicated with crankcase and suction chamber, disposing two valves respectively, these two valves are operated with mutual linkage manner, thereby control simultaneously flows into the flow of refrigerant of crankcase and the flow of the refrigerant of discharging from crankcase.Thus, because control by control valve, thereby when the coolant channel of be communicated with discharging chamber and crankcase with when being communicated with in the coolant channel of crankcase and suction chamber either party refrigerant flow increase, then can control the flow that makes the opposing party reduces, so can reduce flow, thereby utilize control valve just can constitute the high variable displacement compressor of compression efficiency with described structure at the refrigerant of variable displacement compressor inner loop.
In addition, the control valve that has also proposed following scheme (for example, Japanese kokai publication sho 64-41680 communique, Fig. 2), it constitutes: the coolant channel of be communicated with discharging chamber and crankcase be communicated with on the coolant channel of crankcase and suction chamber, dispose two valves respectively, these two valves are operated with mutual linkage manner, thereby refrigeration passage is opened and when being in state of a control, will be closed another refrigeration passage therein.Thus because control valve control one of them refrigeration passage flow the time, another refrigeration pathway closure carries out circuit refrigerant so can further reduce in variable displacement compressor inside.
But, dispose the aforementioned control valve of valve respectively at inlet side and outlet side for the described wherein crankcase of Japanese kokai publication sho 58-158382 communique, in two valves that move with linkage manner, because when one of them is closed, another is opened, so must have wherein two zones that valve is all opened, therefore the refrigerant flow in the compressor inner loop can only be reduced to a certain degree, existence can not substantially improve the problem points of compression efficiency.
In addition, a back control valve of another valve closing during the described valve open therein of Japanese kokai publication sho 64-41680 communique, under suction pressure is reduced to situation smaller or equal to first setting pressure, because the coolant channel between crankcase and the suction chamber (outlet side) is closed fully, so the pressure in the crankcase is responsive to the minor variations reaction of the valve of the coolant channel (inlet side) between discharge chamber and the crankcase.But, under the situation that excessive pressure in crankcase rises, even make the aperture at the valve of inlet side change, can not reduce the gas refrigerant that is trapped in the crankcase, be accompanied by the minimizing of discharge capacity, suction pressure rises to naturally more than or equal to till second setting pressure, and the coolant channel of outlet side is opened, and the pressure in the crankcase is reduced.And the pressure that is accompanied by in the crankcase reduces, and discharge capacity increases, and suction pressure is reduced to smaller or equal to first setting pressure, repeats described circulation once more, produces vibration (hunting) phenomenon in other words.As mentioned above, in the structure of this back one control valve, existence can not obtain the problem points of stable control performance.
Summary of the invention
The present invention proposes in view of described problem, and its purpose is to provide a kind of control valve of variable displacement compressor, can obtain stable control performance, and the refrigerant circulation quantity of variable displacement compressor inside is reduced, thereby can improve compression efficiency.
In the present invention, in order to solve described problem, a kind of control valve of variable displacement compressor is provided, this control valve is by the pressure in the control crankcase, the discharge capacity of refrigerant is changed, it has: first valve, be configured between the discharge chamber and described crankcase of described variable displacement compressor, and be used to control the refrigerant flow that flows to described crankcase from described discharge chamber; Second valve, be configured between the suction chamber of described crankcase and described variable displacement compressor, be used for when described first valve is controlled the flow of the refrigerant that flows to described crankcase from described discharge chamber, to be minimum prearranging quatity from the flow control that described crankcase flows to the refrigerant of described suction chamber, and, be used for closing fully or when closing fully, control flows to the flow of the refrigerant of described suction chamber from described crankcase at described first valve; With pressure-sensitive portion, the suction pressure of the described suction chamber of perception is to change the lifting capacity of described first valve and second valve.
Control valve according to such variable displacement compressor, second valve that the flow of the refrigerant of the suction chamber that flows to variable displacement compressor from crankcase is controlled, close fully or near after closing fully at first valve, begin to carry out flow control, and first valve also becomes minimum aperture or near after the minimum aperture, begins to carry out flow control at second valve.By this structure, can be with from discharging the chamber to crankcase, flow from crankcase to the suction chamber flowing refrigerant again, promptly, the flow control of refrigerant that circulates in variable displacement compressor inside and do not play refrigeration is at bottom line, and the pressure that suppresses in the crankcase rises too sensitively.Consequently, can obtain stable controllability, and improve compression efficiency and improve.
Described and other purpose, feature and advantage of the present invention, as example of the present invention, the following explanation that will be associated by the accompanying drawing with the expression preferred embodiment is in addition clear and definite.
Description of drawings
Fig. 1 is the schematic representation of structure of the control valve of expression variable displacement compressor of the present invention.
Fig. 2 represents to set for first part that opens and closes the control valve of time to amplify explanatory drawing.
Fig. 3 is that first figure of characteristic that opens and closes the control valve of time is set in expression for.
Fig. 4 represents to set for second part that opens and closes the control valve of time to amplify explanatory drawing.
Fig. 5 is that second figure of characteristic that opens and closes the control valve of time is set in expression for.
Fig. 6 represents to set for the 3rd part that opens and closes the control valve of time to amplify explanatory drawing.
Fig. 7 is that the 3rd figure of characteristic that opens and closes the control valve of time is set in expression for.
Fig. 8 is that explanatory drawing is amplified in the part that is illustrated in the control valve of inlet side and outlet side formation fixed throttle port.
Fig. 9 is that the 4th figure of characteristic that opens and closes the control valve of time is set in expression for.
Figure 10 is the schematic representation that is illustrated in the control valve of inlet side and outlet side formation fixed throttle port.
Figure 11 is that the 5th figure of characteristic that opens and closes the control valve of time is set in expression for.
Figure 12 is the schematic representation of the mechanical type control valve structure of expression variable displacement compressor.
Figure 13 is the schematic representation of the mechanical type control valve structure of expression variable displacement compressor.
Figure 14 is the fixed throttle port function schematic representation of the mechanical type control valve structure of variable displacement compressor independently that expression makes second valve.
Embodiment
Below, with reference to accompanying drawing embodiments of the invention are elaborated.
Fig. 1 is the schematic representation of structure of the control valve of expression variable displacement compressor of the present invention.
The control valve of variable displacement compressor of the present invention is provided with in the following order: the solenoid (solenoid) 14 that constitutes the ball valve 11 of first valve, the guiding valve 12 that constitutes second valve, the film spare 13 that constitutes pressure-sensitive portion and formation pressure configuration part.
It is the refrigerant of Pd that ball valve 11 imports head pressure from the discharge chamber of variable displacement compressor, and the flow of the refrigerant that imports of control is with pressure to be the crankcase that the refrigerant of Pc1 supplies to variable displacement compressor.It is the refrigerant of Pc2 that guiding valve 12 imports pressure from crankcase, and supplies to the flow of the refrigerant in the suction chamber of variable displacement compressor with the action linkage manner control with ball valve 11.Film spare 13 bears the suction pressure Ps of suction chamber, if suction pressure is lower than predetermined suction pressure set point, then film spare 13 will make ball valve 11 and guiding valve 12 change in location, so that the pressure in the crankcase rises.By the pressure in the crankcase is risen, and reduce the discharge capacity of compressor, result, the suction pressure of aircondition are controlled near the predetermined suction pressure set point.14 pairs of film spares 13 of solenoid apply actuates load, thereby sets the suction pressure set point, and this is actuated load and sets according to the current value of supplying with from the outside.
The valve body 16 that guiding valve 12 has valve seat 15 and can freely plug with respect to valve opening is provided with predetermined gap 17 between valve seat 15 and valve body 16.When valve body 16 was inserted in the valve opening, this gap 17 constituted the constant fixed throttle port of aisle spare between crankcase and suction chamber, and described gap 17 is decided by the stability of the swash plate of variable displacement compressor.And, valve body 16 and the axle 18 formation one that are used to drive ball valve 11, a valve body 16 and axle 18 anastomosis parts 19 by the tapered frusto-conical in cross section engage.
The characteristic of the vibration of these guiding valve 12 corresponding variable capacity compressors, controllability, stability etc. can freely change in the mode that has with switching time of the switching asynchronism(-nization) of ball valve 11, wherein the operations linkage of ball valve 11 and guiding valve 12.By change as with spools 18 end of the end of the valve body 16 of the boundary of anastomosis part 19 and the valve body 20 that contacts ball valve 11 between distance, valve body 16 ends are changed along axial direction residing position when ball valve 11 is closed fully, and can easily carry out the change of the switching time of ball valve 12.
In addition, ball valve 11 moves by making axle 18 rights towards Fig. 1, and valve body 20 is moved towards the direction of opening, by being arranged on the maximum opening that stepped part 21 and the butt that is formed at the stepped part 22 on the main body on the axle 18 limits ball valve 11.
Fig. 2 is that expression is set first part that opens and closes the control valve of time for to amplify explanatory drawing and Fig. 3 be that first figure of characteristic that opens and closes the control valve of time is set in expression for.
This first switching time is the time consistent with the switching time of guiding valve 12 switching time that makes ball valve 11, and when ball valve 11 was closed fully, the end of the valve body 16 of guiding valve 12 kept aliging with the open end of solenoid one side of valve seat 15.
Thus, when the valve body 16 of guiding valve 12 when axial direction moves, the characteristic of this control valve is as shown in Figure 3.In Fig. 3, transverse axis is represented axle 18 stroke, and initial point represents that the stepped part 21 of axle 18 is connected on the stepped part 22 of main body and when being positioned at position by goal valve 11 1 sides (when perhaps, solenoid does not have energising).The longitudinal axis of Fig. 3 is represented the opening area of ball valve 11 and guiding valve 12.And, represent the variation of the opening area of ball valve 11 by the line shown in the Pd-Pc, and represent the variation of the opening area of guiding valve 12 by the line shown in the Pc-Ps.
For this first switching time.During ball valve 11 was opened, guiding valve 12 had the opening area that is equivalent to gap 17, and as fixed throttle port.When axle 18 towards solenoid 14 side shiftings and during the s1 of in-position, ball valve 11 is closed fully by the in place of its valve body 20.When axle 18 during further to solenoid 14 side shiftings, the end of axle 18 leaves the valve body 20 of ball valve 11, and ball valve 11 remains on full-shut position, and guiding valve 12 begins to open from the state as fixed throttle port, and its opening area increases gradually corresponding to the stroke of axle 18.When this ball valve 11 is closed fully, can not flow in the crankcase by the compressed refrigerant of this control valve, but, by sucking and the piston of compression refrigerant and make piston be accommodated in gap between wherein the cylinder slidably, a spot of blow-by leakage is to crankcase, thus, (=Pc1=Pc2) the control of the pressure P c in can the March axle box.
Fig. 4 is that expression is set second part that opens and closes the control valve of time for and amplified explanatory drawing, and Fig. 5 is that second figure of characteristic that opens and closes the control valve of time is set in expression for.
This second switching time is the time of time ratio ball valve 11 that guiding valve 12 the is opened time lag of closing, and when ball valve 11 was closed fully, guiding valve 12 still was in closed condition (fixed throttle port state).For this reason, compare with first situation that opens and closes the time, the end and being connected between the tip of the axis on the valve body 20 of ball valve 11 of ball valve 11 1 sides of valve body 16 is only reduced apart from a, thereby when ball valve 11 was closed, the valve body 16 that makes guiding valve 12 was positioned at valve opening near the end of ball valve 11 1 sides.
Thus, for the second switching time, as shown in Figure 5, if axle 18 to solenoid 14 1 side shiftings, then at first ball valve 11 is closed when axle 18 in-position s1 fully.At this moment, guiding valve 12 has the opening area that is equivalent to gap 17.Axle is 18 further to solenoid 14 1 side shiftings, and during the s2 of in-position, guiding valve 12 begins to open.
Fig. 6 is that expression is set the 3rd part that opens and closes the control valve of time for to amplify explanatory drawing and Fig. 7 be that the 3rd figure of characteristic that opens and closes the control valve of time is set in expression for.
The 3rd switching time was to make opening the time early 11 shut-in times of time ratio ball valve of guiding valve 12.For this reason, compare with first situation that opens and closes the time, make valve body 16 only strengthen distance b near the end of ball valve 11 1 sides and the distance that is connected between the tip of the axis on the valve body 20 of ball valve 11, when ball valve 11 is closed, the valve body 16 that makes guiding valve 12 near the end of ball valve 11 1 sides than valve seat 15 more close solenoid 14 1 sides.
Thus, for the 3rd switching time, as shown in Figure 7, when axle 18 towards solenoid 14 side shiftings, then get to when reaching position s1 when axle 18, guiding valve 12 at first begins to open, when spool 18 in-position s2, ball valve 11 is closed fully then.
Fig. 8 is illustrated in the part that inlet side and outlet side be formed with the control valve of fixed throttle port to amplify explanatory drawing, and Fig. 9 is that the 4th figure of characteristic that opens and closes the control valve of time is set in expression for.In addition, in Fig. 8, give identical label for the component parts identical with component parts shown in Figure 1.
This control valve is formed with fixed throttle port at the inlet side of crankcase and two sides of outlet side.In this control valve, the end portion of the axle 18 of valve body 20 sides of butt ball valve 11 forms the shape of spool, and has gap 24 between the inwall of the periphery of the butt end 23 of valve body 20 butts and valve opening.Be positioned at when closing fully at ball valve 11, thereby this gap 24 is formed in the constant fixed throttle port of aisle spare between pressing chamber and the crankcase in valve opening.This fixed throttle port is arranged in refrigerant and is directed to crankcase by gas leakage and passes through the zone of guiding valve 12 controls from the refrigerant flow of crankcase discharge, is used for stably keeping from discharging the flow of chamber to the refrigerant of crankcase importing.Distance between the on-station position of rear end of this butt end 23 (position of beginning diameter reduction) and valve body 20 is a distance c.And, in current embodiment, to close fully and valve body 20 when keeping being connected on the butt end 23 at ball valve 11, the end of the valve body 16 of guiding valve 12 and the valve of guiding valve 12 are closed and are set to the value identical with distance c apart from d between the initial position.
Such control valve has following properties: as shown in Figure 9, at first when solenoid was not switched on, because the stepped part 21 of axle 18 is connected on the stepped part 22 of main body, so ball valve 11 is in full open position, and guiding valve 12 was in the fixed throttle port state.
By increasing solenoidal electrical current, ball valve 11 changes to the direction that reduces opening area from full open position, and guiding valve 12 is kept the fixed throttle port state.Then, when axle 18 moved to position s1, the rear end of butt end 23 arrived the on-station position of valve body 20, and the valve body 16 of guiding valve 12 arrives the valve that leaves the fixed throttle port state and begins open position.When axle 18 when position s1 is moved further, the rear end of butt end 23 enters valve opening, becomes the state of fixed throttle port, and guiding valve 12 changes to the direction that increases opening area from the state of fixed throttle port.
Then, the opening area of open area ratio fixed throttle port that the fixed throttle port state of this ball valve 11 is maintained to this ball valve 11 is little, and last ball valve 11 is in place to become buttoned-up status.
In addition, here, distance c with get identical value apart from d, but the characteristic of corresponding variable capacity compressor, by the increase and decrease apart from d, can easily change the switching time of guiding valve 12.
Figure 10 is illustrated in the schematic representation that inlet side and outlet side form the control valve of fixed throttle port, and Figure 11 is that the 5th figure of characteristic that opens and closes the control valve of time is set in expression for.In addition, in Figure 10, give identical label to the component parts identical with component parts shown in Figure 1.
In this control valve, be configured in the valve between compressor and the crankcase and be configured in crankcase and suction chamber between valve all utilize corresponding guiding valve 11a and 12 to constitute.The valve body 16 of guiding valve 12, axle 18 and the valve body 20a of guiding valve 11a form as one, and the diameter of this valve body 20a is less than the diameter that is supported on the axle 18 on the main body, and are provided with gap 24 between the inwall of valve body 20a and valve opening.In addition, the diameter of the part between this valve body 20a and axle 18 is reduced to form spool-shape.And when guiding valve 12 was in valve and cuts out the initial position, the valve that the rear end of valve body 20a (position that diameter begins to dwindle) and valve body 20a enter valve opening cuts out between the initial position to have apart from e.
At this moment control valve has following characteristic: as shown in figure 11, at first when solenoid is not switched on, because axle 18 stepped part 21 is connected on the stepped part 22 of main body, so guiding valve 11a is in the state of opening fully, and guiding valve 12 cuts out fully and is in the state of fixed throttle port.
By increasing solenoidal electrical current, the rear end of the valve body 20a of guiding valve 11a changes to the direction that reduces opening area near valve opening and from full open position, and guiding valve 12 is kept the fixed throttle port state.Then, when axle 18 moved to position s1, guiding valve 11a arrived valve and closes the initial position, and the valve body 16 of guiding valve 12 arrives the initial position of opening of leaving the fixed throttle port state.When axle 18 when position s1 is moved further, valve body 20a enters valve opening, thus guiding valve 11a becomes the fixed throttle port state and keeps this state, and guiding valve 12 changes to the direction that increases opening area from the fixed throttle port state.
In above embodiment, the electric control valve is illustrated, this control valve is as the device of the suction pressure Ps that sets suction chamber, used by can freely set the solenoid of a setting value (pressure control point) from the control electric current of outside.The mechanical type control valve that suction pressure Ps is set at fixed value describes below.
Figure 12 is the schematic representation of structure of the mechanical type control valve of expression variable displacement compressor.In addition, in Figure 12, give identical label, and omit its detailed description the component parts identical with component parts shown in Figure 1.
This control valve disposes in the following order: constitutes the ball valve 11 of first valve, constitutes the guiding valve 12 of second valve, constitute the film spare 13 of pressure-sensitive portion, and the spring 25 that constitutes the pressure configuration part.
This control valve also constitutes, and during ball valve 11 its opening areas of control were changeable, guiding valve 12 was as fixed throttle port, and when ball valve 11 was in buttoned-up status, guiding valve 12 its opening areas of control can change.Certainly, the characteristic of corresponding described variable displacement compressor, the switching time of this guiding valve 12 can be set at any in described first to the 3rd switching time.
Film spare 13 disposes disk 26 on the surface of spring 25 sides, by this disk 26, spring 25 promotes film spare 13 towards the direction of guiding valve 12.This spring 25 is adjusted to the elastic load that has corresponding to predetermined suction pressure control point.Thereby, when the suction pressure Ps from suction chamber that is born is lower than predetermined suction pressure control point, 13 pairs of ball valves 11 of film spare and guiding valve 12 imposed loads, so that the pressure of crankcase rises, control valve is controlled the discharge capacity of variable displacement compressor thus, thereby the suction pressure of aircondition is controlled near the predetermined suction pressure control point.
Certainly, this control valve also can constitute the control valve that was set to for the 4th switching time, that is, thereby constitute fixed throttle port shown in Figure 8, thereby on each refrigerant inlet side of crankcase and outlet side, form fixed throttle port by forming butt end 23 at the end of axle 18.
Figure 13 is the schematic representation of structure of the mechanical type control valve of expression variable displacement compressor.In addition, in Figure 13, give identical label to the component parts identical, and omit its detailed description with Fig. 1 and component parts shown in Figure 10.
This control valve disposes in the following order: constitutes the guiding valve 11a of first valve, constitutes the guiding valve 12 of second valve, constitute the film spare 13 of pressure-sensitive portion, and the spring 25 that constitutes the pressure configuration part.
Guiding valve 11a has the structure identical with valve shown in Figure 10, thereby current control valve has the characteristic of the 5th switching time shown in Figure 11.
This control valve also bears the suction pressure Ps from suction chamber, so that guiding valve 11a, 12 lifting capacity cover plate, thereby the pressure in the control crankcase makes suction pressure Ps keep constant.
Figure 14 is the schematic representation of structure of the control valve of expression variable displacement compressor, and wherein the effect of the fixed throttle port of second valve is independent.In addition, in Figure 14, give identical label, and omit its detailed description the component parts identical with component parts shown in Figure 1.
Control valve utilization shown in Figure 1 is arranged on the function that gap 17 between the inwall of the valve body 16 of guiding valve 12 and valve opening provides fixed throttle port, different therewith, current control valve forms the fixed throttle port 27 with the opening area that equates with the opening area that utilizes described gap 17 to form in main body.In this case, make gap 17 minimums that are arranged between valve body 16 and the valve opening inwall.Thus, when the coolant channel between crankcase and the suction chamber narrowed down owing to guiding valve 12, cryogen flow was to bigger fixed throttle port 27 1 sides of diameter, and do not flow to less clearance 17.Consequently, have by precipitation and be included in the effect that the sludge in the refrigerant can make the changes in flow rate of refrigerant reduce.
Promptly, if the gap 17 between the inwall of the valve body 16 of guiding valve 12 and valve opening for example is 0.1mm, be that diameter is the hole of 1mm then at fixed throttle port 27 with the opening area that equates with this gap 17, if being deposited in sludge on the inwall of valve body 16 or valve opening inwall or fixed throttle port 27, for example to assemble 0.1mm thick, then gap 17 is almost stopped up by sludge, thereby the diameter of fixed throttle port 27 only is reduced to and is 0.8mm, and this makes that the variation of the refrigerant flow that causes because of the sludge precipitation is less.And because refrigerant mainly flows through the fixed throttle port 27 that flows easily, the amount that therefore exists the refrigerant that flows through narrow gap 17 less and be difficult for the advantage of precipitation sludge.
In addition, for the structure that fixed throttle port 27 and the guiding valve 12 that constitutes second valve are set up in parallel, exemplified the situation that is applied to the control valve with solenoid 14 shown in Figure 1 and be illustrated, but can be suitable for too for Figure 12 and mechanical type control valve shown in Figure 13.
As mentioned above, in the present invention, control valve constitutes and comprises: first valve is used to control the flow that flows to the refrigerant of crankcase from the discharge chamber; Second valve is used to control the flow that flows to the refrigerant of suction chamber from crankcase; Pressure-sensitive portion is used for the perception suction pressure; And the pressure configuration part, be used to set suction pressure Ps.After first valve was closed fully or nearly closed fully, second valve began to carry out flow control, and after second valve became minimum aperture or approaching minimum aperture, first valve began to carry out flow control.Thus, when switching the control of first valve and second valve, because do not have first valve and second valve to be in the zone of the state of valve open simultaneously, so can be with from discharging the chamber to crankcase, again from the flow of crankcase to the suction chamber flowing refrigerant, promptly, circulate in the inside of variable displacement compressor and the flow control of refrigerant that do not play refrigeration at bottom line, thereby can improve the efficient of variable displacement compressor.And then, because having, second valve make the flow that flows into the refrigerant of suction chamber from crankcase become the fixed throttle port function of minimum predetermined amount of flow, thus can stably regulate the pressure in the crankcase, thus can obtain fine control performance.
Described content is only represented principle of the present invention.To those skilled in the art, can carry out various changes and modifications, the invention is not restricted to the concrete structure and the application examples of described represented, explanation, variation that all are suitable and equivalent can be thought to drop in the scope of the present invention that claims and equivalent thereof form.
Claims (12)
1. the control valve of a variable displacement compressor, it can make the discharge capacity of refrigerant change by the pressure in the control crankcase, it is characterized in that having:
First valve is configured between the discharge chamber and described crankcase of described variable displacement compressor, is used to control the flow that flows to the refrigerant of described crankcase from described discharge chamber;
Second valve, be configured between the suction chamber of described crankcase and described variable displacement compressor, be used for when described first valve is controlled the flow of the refrigerant that flows to described crankcase from described discharge chamber, to flow to the flow control of refrigerant of described suction chamber at the prearranging quatity of minimum from described crankcase, and, be used for closing fully or when closing fully, control flows to the flow of the refrigerant of described suction chamber from described crankcase at described first valve;
Pressure-sensitive portion, the suction pressure of the described suction chamber of perception is to change the lifting capacity of described first valve and second valve.
2. the control valve of variable displacement compressor according to claim 1 is characterized in that,
Described second valve has the gap between the diameter of the diameter that is arranged on valve opening and valve body, it is the fixed throttle port function of minimum prearranging quatity that this gap has the flow control that is used for flowing to the refrigerant of described suction chamber from described crankcase, and wherein said valve body is inserted into the described valve opening when described first valve control flows to the refrigerant flow of described crankcase from described discharge chamber.
3. the control valve of variable displacement compressor according to claim 1 and 2 is characterized in that,
Described control valve has one, this valve opening that runs through described second valve extend and with described valve opening on same axis, be used for the on-off action of described second valve is passed to described first valve.
4. the control valve of variable displacement compressor according to claim 3 is characterized in that,
Described axle has the anastomosis part that engages with described valve body, and this anastomosis part forms frusto-conical.
5. the control valve of variable displacement compressor according to claim 3 is characterized in that,
One end portion of described axle and the valve body butt of described first valve also form and make this end portion have spool-shape.
6. the control valve of variable displacement compressor according to claim 3 is characterized in that,
Described axle can contact with the valve body of described first valve and separate.
7. the control valve of variable displacement compressor according to claim 3 is characterized in that,
One gap is arranged between the diameter of valve opening of the diameter of the described the tip of the axis part on the valve body that is connected to described first valve and described first valve, and this gap has the fixed throttle port function that the refrigerant flow that will flow to described crankcase from described discharge chamber is controlled to be minimum prearranging quatity.
8. the control valve of variable displacement compressor according to claim 1 is characterized in that,
Described first valve is a guiding valve.
9. the control valve of variable displacement compressor according to claim 1 is characterized in that,
Described control valve has fixed throttle port, itself and described second valve be arranged in parallel, and when described discharge chamber flows to the refrigerant flow of described crankcase, will be controlled to be minimum prearranging quatity from the refrigerant flow that described crankcase flows to described suction chamber in the control of described first valve.
10. the control valve of variable displacement compressor according to claim 1 is characterized in that,
Described control valve has the pressure configuration part, and it applies described pressure-sensitive portion and actuates load to set the pressure control point of control valve.
11. the control valve of variable displacement compressor according to claim 10 is characterized in that,
Described pressure configuration part is to actuate the solenoid that load is set described pressure control point by applying according to external signal.
12. the control valve of variable displacement compressor according to claim 10 is characterized in that,
Described pressure configuration part is a spring of setting described pressure control point by elastic force.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003013890 | 2003-01-22 | ||
| JP013890/2003 | 2003-01-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1738971A CN1738971A (en) | 2006-02-22 |
| CN100396916C true CN100396916C (en) | 2008-06-25 |
Family
ID=32767372
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800024867A Expired - Lifetime CN100396916C (en) | 2003-01-22 | 2004-01-21 | Control valve of variable displacement compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20050254961A1 (en) |
| EP (1) | EP1589223B1 (en) |
| JP (1) | JP4547332B2 (en) |
| KR (1) | KR100984214B1 (en) |
| CN (1) | CN100396916C (en) |
| WO (1) | WO2004065789A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110462212A (en) * | 2017-03-28 | 2019-11-15 | 伊格尔工业股份有限公司 | Capacity control drive |
| US11536389B2 (en) | 2017-08-28 | 2022-12-27 | Eagle Industry Co., Ltd. | Electromagnetic valve |
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| JP4456906B2 (en) * | 2004-03-25 | 2010-04-28 | 株式会社不二工機 | Control valve for variable capacity compressor |
| JP2006083837A (en) * | 2004-08-19 | 2006-03-30 | Tgk Co Ltd | Variable displacement compressor control valve |
| JP4925800B2 (en) * | 2006-11-30 | 2012-05-09 | カルソニックカンセイ株式会社 | Control valve for variable displacement compressor |
| US8424567B2 (en) * | 2009-12-18 | 2013-04-23 | Cameron International Corporation | Bi-directional valve with cavity pressure relief |
| JP5458965B2 (en) * | 2010-03-08 | 2014-04-02 | 株式会社豊田自動織機 | Capacity control mechanism in variable capacity compressor |
| CN101985926B (en) * | 2010-10-22 | 2013-01-09 | 四川金科环保科技有限公司 | Hydraulic piston compressor displacement stepless adjustment method |
| JP2013144957A (en) * | 2012-01-16 | 2013-07-25 | Japan Climate Systems Corp | Variable displacement compressor |
| JP6149206B2 (en) | 2013-07-04 | 2017-06-21 | 株式会社テージーケー | Control valve for variable capacity compressor |
| US10066618B2 (en) * | 2014-11-05 | 2018-09-04 | Mahle International Gmbh | Variable displacement compressor with an oil check valve |
| JP6500185B2 (en) * | 2016-02-25 | 2019-04-17 | 株式会社テージーケー | Control valve for variable displacement compressor |
| JP6500186B2 (en) * | 2016-02-25 | 2019-04-17 | 株式会社テージーケー | Control valve for variable displacement compressor |
| CN108779768B (en) * | 2016-03-17 | 2020-05-12 | 伊格尔工业股份有限公司 | Capacity control valve |
| JP6714274B2 (en) * | 2016-06-13 | 2020-06-24 | 株式会社テージーケー | Control valve for variable capacity compressor |
| CN107489791B (en) | 2016-06-13 | 2020-12-04 | 株式会社Tgk | Control valve for variable displacement compressor |
| KR102051661B1 (en) | 2017-05-30 | 2019-12-04 | 한온시스템 주식회사 | Control valve and variable capacity type compressure |
| JP6910871B2 (en) * | 2017-07-14 | 2021-07-28 | サンデン・オートモーティブコンポーネント株式会社 | Variable capacitance compressor |
| KR20190092234A (en) * | 2018-01-29 | 2019-08-07 | 한온시스템 주식회사 | Control system for a compressor, electronic control valve for the same, and compressor with the same |
| JP7289604B2 (en) * | 2018-08-08 | 2023-06-12 | イーグル工業株式会社 | capacity control valve |
| CN110469497A (en) * | 2019-08-14 | 2019-11-19 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and refrigeration equipment with it |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP1589223B1 (en) | 2019-04-24 |
| JP4547332B2 (en) | 2010-09-22 |
| US20050254961A1 (en) | 2005-11-17 |
| KR20050094868A (en) | 2005-09-28 |
| EP1589223A4 (en) | 2011-03-16 |
| EP1589223A1 (en) | 2005-10-26 |
| WO2004065789A1 (en) | 2004-08-05 |
| KR100984214B1 (en) | 2010-09-28 |
| JPWO2004065789A1 (en) | 2006-05-18 |
| CN1738971A (en) | 2006-02-22 |
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Owner name: VALEO THERMAL SYSTEMS (JAPAN) CO. Free format text: FORMER NAME OR ADDRESS: CO.,LTD. ZEXEL VALEO AIR CONDITIONING |
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Address after: Saitama Prefecture, Japan Patentee after: VALEO THERMAL SYSTEMS JAPAN Corp. Address before: Saitama Prefecture, Japan Patentee before: ZEXEL VALEO CLIMATE CONTROL Corp. |
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Address after: Saitama Prefecture, Japan Patentee after: Valeo Japan Co.,Ltd. Address before: Saitama Prefecture, Japan Patentee before: VALEO THERMAL SYSTEMS JAPAN Corp. |
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Effective date of registration: 20170324 Address after: Saitama Prefecture, Japan Patentee after: Valeo Japan Co.,Ltd. Patentee after: TGK Co.,Ltd. Address before: Saitama Prefecture, Japan Patentee before: Valeo Japan Co.,Ltd. |
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