CN101000046A - Control valve for variable displacement compressor - Google Patents
Control valve for variable displacement compressor Download PDFInfo
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- CN101000046A CN101000046A CN 200710001398 CN200710001398A CN101000046A CN 101000046 A CN101000046 A CN 101000046A CN 200710001398 CN200710001398 CN 200710001398 CN 200710001398 A CN200710001398 A CN 200710001398A CN 101000046 A CN101000046 A CN 101000046A
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Abstract
In a control valve for a variable displacement compressor, for controlling the discharge flow rate of refrigerant to be constant, to dispense with a check valve in a refrigerant outlet port of the compressor. The control valve includes a first control valve that controls the passage cross-sectional area of a refrigerant passage through which refrigerant passes from a discharge chamber of the compressor to a refrigerant outlet port thereof, and a second control valve that controls the flow rate of refrigerant allowed to flow from the discharge chamber to a crankcase such that a differential pressure (Pdh-Pdl) across the first control valve generated by the refrigerant passing therethrough becomes constant. The control valve is configured such that when a solenoid section is not energized, a first valve element is engaged with a piston to forcibly fully open the second control valve. The piston has an outer diameter equal to the inner diameter of a second valve seat, so that the discharge pressure Pdl on a refrigerant outlet port side is inhibited from adversely affecting the fully-opening operation of the second control valve, to thereby maintain the fully-closed state of the first control valve. This makes it possible to dispense with a check valve conventionally provided in the refrigerant outlet port.
Description
Technical field
The present invention relates to a kind of control valve that is used for variable displacement compressor, relate more specifically to a kind of like this control valve that is used for variable displacement compressor, it is used for the refrigeration agent Flow Control from compressor discharge is made constant flow rate.
Background technique
For in the refrigeration cycle that is used in car air conditioner with the compressor of compressed refrigerant, employing can change the variable displacement compressor of the volume (discharge amount) of refrigeration agent, so that obtain enough cooling capacities, and be not subjected to limit as the rotating speed of the motor in driven compressor source.In such variable displacement compressor, parallel the ground pistons reciprocating with the rotatingshaft that rotates by engine-driving and be connected to the wobble plate (wobbler (swash plate)) that is assemblied on the rotatingshaft, and by this wobble plate is rotated, change the stroke of piston, thereby the volume of control compressor, that is the discharge amount of refrigeration agent.
In order to change the angle of inclination of wobble plate, by the part of refrigerant compressed being introduced in the airtight airtight crankcase, and change the balance of the pressure on the both sides that act on each piston that links to each other with wobble plate so that the pressure in the crankcase changes.
Usually, by being controlled at the control valve that is used for compressor that is provided with in the path that is communicated with between discharge chamber and the crankcase, feasible connection by control valve is allowed to or blocks, and changes the pressure in the crankcase.So, when control valve is set to predetermined valve lift, if the rotating speed of motor increases, then the pressure that is incorporated into the crankcase from discharge chamber increases so that the angle vertical with rotatingshaft approached at the angle of inclination of wobble plate, thereby is controlled to the volume of compressible refrigeration agent less.On the contrary, when the rotating speed of motor reduced, the pressure of introducing in the crankcase reduced, thereby is controlled to the volume of compressible refrigeration agent bigger.Therefore, variable displacement compressor be controlled such that no matter the rotating speed of motor how, the constancy of volume of the refrigeration agent of discharging.
The control valve that is used for it for use is controlled the method for the volume of variable displacement compressor, for example, generally well-knownly be, make the swabbing pressure Ps in the suction chamber keep constant, and make swabbing pressure Ps and the differential pressure between the discharge pressure Pd in the discharge chamber in the suction chamber keep constant.Also be well known that, make from the flow velocity of the refrigeration agent of compressor discharge become constant (for example opening 2001-107854 communique ([0035]～[0036] section and Fig. 3)) referring to the Japanese unexamined patent publication No. spy.
According to open disclosed this control valve that is used for variable displacement compressor in the 2001-107854 communique the Japanese unexamined patent publication No. spy, by the differential pressure between two pressure monitoring points of sensor, thereby grasp the flow velocity that is inhaled into the refrigeration agent in the suction chamber indirectly, and described control valve is controlled the flow velocity that is incorporated into the refrigeration agent the crankcase from discharge chamber, make the flow velocity be inhaled into the refrigeration agent in the suction chamber become constant, thereby will become constant from the flow speed control of the refrigeration agent of compressor discharge.
As a comparison, also known a kind of control valve that is used for variable displacement compressor, it has saved the sensor (for example opening 2004-116349 communique ([0102]～[0108] section and Figure 12) referring to the Japanese unexamined patent publication No. spy) that is used to detect two differential pressures between the pressure monitoring point.This control valve comprises: first control valve, its control allow to flow to from the discharge chamber of compressor the flow velocity of refrigeration agent of the refrigerant outlet of compressor; Second control valve, it uses its barrier film to come the differential pressure of sensing first control valve front and back, and the flow velocity of refrigeration agent that allows to flow into the crankcase of compressor from discharge chamber is controlled based on this differential pressure, with the volume of change compressor, thereby the flow speed control of first flow of refrigerant that control valve allows is become constant; And solenoid portion, it sets the flow velocity of first flow of refrigerant that control valve allows, and these parts are all along same axis arranged.According to this control valve, first control valve forms a variable orifice, the area of passage of the refrigerant passage of this variable orifice is set according to the variation of external condition by solenoid portion, and the differential pressure before and after the described variable orifice of the second control valve sensing, and the pressure in the control crankcase, make differential pressure become and equal predetermined value.Therefore, the differential pressure of setting for before and after the variable orifice of specific passageways area is remained on described predetermined value, thereby will become constant from the flow speed control of the refrigeration agent of compressor discharge.
Open in the 2004-116349 communique in disclosed traditional control valve above-mentioned Japanese unexamined patent publication No. spy, when the compressor shut-down operation, the ability of its compression and refrigerant emission suddenly disappears, thereby has put upside down discharge chamber and the pressure dependence between the refrigerant outlet in the first control valve downstream that is in high pressure.Such action is not that second control valve is controlled to the minimum volume side, but it is controlled to the maximum volume side.In order to address this problem, dispose traditional control valve like this, that is, suppose one-way valve to be set, thereby prevent that first control valve is subjected to the adverse effect of the pressure at refrigerant outlet place when compressor stops at the refrigerant outlet place.Therefore, use the variable displacement compressor of traditional control valve owing to the problem that one-way valve has increases manufacture cost must be set.
Summary of the invention
Made the present invention at the problems referred to above, its purpose is to provide a kind of control valve that is used for variable displacement compressor, this control valve is such type, and it is at the flow velocity that need not to be provided with at the refrigerant outlet place of compressor the refrigeration agent of control discharging under the situation of one-way valve.
In order to address the above problem, the invention provides a kind of control valve that is used for variable displacement compressor, this control valve comprises: first control valve, and this first control valve is controlled described first refrigeration agent that control valve allows flows to the refrigerant outlet of this compressor from the discharge chamber of described compressor flow velocity; Second control valve, this second control valve is controlled described second refrigeration agent that control valve allows flows into the crankcase of described compressor from described discharge chamber flow velocity based on the differential pressure before and after described first control valve, changing the volume of described compressor, thereby the flow speed control of described first flow of refrigerant that control valve allows is become constant; And solenoid portion, this solenoid portion is set the flow velocity of described first flow of refrigerant that control valve allows, wherein, described control valve is formed into for the pressure in the downstream side of described first control valve insensitive, and when described solenoid portion is in not "on" position, described first control valve is in buttoned-up status, and described second control valve is in full open position, even when the pressure in the downstream side of described first control valve was equal to or higher than the pressure of upstream side of described first control valve, described second control valve also was forced to remain on full open position.
To know above and other objects of the present invention, feature and advantage in conjunction with the accompanying drawings from following explanation, accompanying drawing only shows the preferred embodiments of the present invention by way of example.
Description of drawings
Fig. 1 is the integrally-built central longitudinal sectional view according to first embodiment's the control valve that is used for variable displacement compressor;
Fig. 2 is the local amplification view according to the structure of the valve portion of first embodiment's control valve;
Fig. 3 is the central longitudinal sectional view according to the structure of second embodiment's the control valve that is used for variable displacement compressor;
Fig. 4 is the central longitudinal sectional view according to the structure of the 3rd embodiment's the control valve that is used for variable displacement compressor;
Fig. 5 is the central longitudinal sectional view according to the structure of the 4th embodiment's the control valve that is used for variable displacement compressor;
Fig. 6 is the central longitudinal sectional view according to the structure of the 5th embodiment's the control valve that is used for variable displacement compressor;
Fig. 7 is the central longitudinal sectional view according to the structure of the 6th embodiment's the control valve that is used for variable displacement compressor;
Fig. 8 is the central longitudinal sectional view according to the structure of the 7th embodiment's the control valve that is used for variable displacement compressor;
Fig. 9 is the central longitudinal sectional view according to the structure of the 8th embodiment's the control valve that is used for variable displacement compressor;
Figure 10 A to Figure 10 C is the view that is used to illustrate the characteristic of barrier film, wherein Figure 10 A shows the state that does not apply differential pressure on barrier film, Figure 10 B shows the state that barrier film moves by differential pressure, and Figure 10 C shows differential pressure and is applied to state on the mobile barrier film along the direction opposite with movement direction; And
Figure 11 A to Figure 11 B is the explanatory drawing that shows according to the structure of the differential pressure sensing part of the 8th embodiment's control valve, wherein Figure 11 A shows the situation of the pressure in the refrigerant outlet that pressure in the discharge chamber of compressor is higher than compressor, and Figure 11 B shows the situation that pressure in the discharge chamber is lower than the pressure in the refrigerant outlet.
Embodiment
Describe embodiments of the invention below with reference to accompanying drawings in detail.
Fig. 1 is the integrally-built central longitudinal sectional view according to the control valve that is used for variable displacement compressor of first embodiment of the invention.Fig. 2 is the local amplification view of expression according to the structure of the valve portion of first embodiment's control valve.
The control valve 10 that is used for variable displacement compressor comprises the first control valve 10A, the second control valve 10B and solenoid portion 10C, first control valve 10A control flows to the path cross-section area of refrigerant passage of the refrigerant outlet of compressor from the discharge chamber of compressor for high-pressure refrigerant, second control valve 10B control is supplied to the flow velocity of the refrigeration agent of crankcase from the discharge chamber of compressor, solenoid portion 10C sets the path cross-section area of the refrigerant passage of the first control valve 10A, and these parts all are arranged on the same axis.
The first control valve 10A and the second control valve 10B have first main body 11 and second main body 12 that is press fitted in first main body 11.First main body 11 and second main body 12 are provided with port one 3, port one 4 and port one 5.When being installed in control valve 10 in the compressor, port one 3 is communicated with the discharge chamber of compressor, the refrigeration agent that is used for being in discharge pressure Pdh is introduced the first control valve 10A, port one 4 is communicated with the refrigerant outlet of compressor, be used for being in the refrigeration agent of discharge pressure Pd1 from first control valve 10A discharging, port one 5 is communicated with the discharge chamber of compressor, is used for the refrigeration agent that is in discharge pressure Pdh2 is introduced the second control valve 10B.Second main body 12 be formed with port one 6 foremost, port one 6 is communicated with the crankcase of compressor, is used for being in from the second control valve 10B discharging refrigeration agent of pressure P c.
Although control valve 10 can be applied to such variable displacement compressor, promptly this compressing mechanism causes when installing control valve 10 within it, the port one 3 that is in discharge pressure Pdh all is communicated with the discharge chamber of this compressor with the port one 5 that is in discharge pressure Pdh2, yet preferably control valve 10 is applied to such variable displacement compressor, promptly this compressing mechanism causes the port one 3 that is in discharge pressure Pdh directly is communicated with discharge chamber, and the port one 5 that is in discharge pressure Pdh2 is communicated with the outlet of the oil separator in the downstream side that is arranged in discharge chamber.This makes the second control valve 10B that a large amount of compressor lubricant oils that contain in the refrigeration agent are returned, and controls the pressure P c in the crankcase simultaneously.
The first control valve 10A has the path that axial perforation second main body 12 forms, thereby this path is communicated with between port one 3 that is in discharge pressure Pdh and the port one 4 that is in discharge pressure Pd1.Rigidity has been press-fitted first valve seat 17 in this path, and in the downstream side of this first valve seat 17 being furnished with the first valve element 18 toward and away from the mode of first valve seat, 17 motions.
The first valve element 18 has with the integrally formed hollow tube-shape portion of the perforation axially extended mode of valve opening, and rigidity has been press-fitted guide 19 in this hollow tube-shape portion.Guide 19 is promoted by the valve closing direction of spring 20 along the first control valve 10A.Guide 19 is configured to make the part of the inwall sliding contact of itself and first main body 11 to have internal diameter equal outer diameters with first valve seat 17, therefore the discharge pressure Pdh of inlet port 13 equally acts on the first valve element 18 and the guide 19 along corresponding two opposite directions, to prevent discharge pressure Pdh the control operation of the first control valve 10A is had a negative impact.
The second control valve 10B has second valve seat 31 and the second valve element 32, second valve seat 31 be press fitted into vertically connect second main body 12 that forms ports having 16 foremost in, the second valve element 32 makes the second valve element 32 can open and close port one 6 at upstream side can be arranged in the upstream side of second valve seat 31 toward and away from the mode of second valve seat, 31 motions.The second valve element 32 is kept by second main body 12 with being axially moveable, and is installed on the piston 33 that forms differential pressure sensing part.More particularly, piston 33 is constructed with valve element base portion accommodating part 34, this valve element base portion accommodating part piston with second valve seat, 31 facing surfaces in recessed, be used for the base portion of the spring 35 and the second valve element 32 is arranged in this accommodating part 34, and the opening end of accommodating part 34 carried out swaged forging released by spring 35 to prevent the second valve element 32.Can relax the collision impact that when the second control valve 10B closes apace fully, between the second valve element 32 and second valve seat 31, produces like this.
In addition, the spring 37 that piston 33 is disposed between piston 33 and the spring acceptance division 36 promotes along the valve closing direction of the second control valve 10B, and spring acceptance division 36 is press fitted into second main body 12 from the side rigidity towards port one 4.Spring 37 is set to and makes spring force promote the spring force of the first control valve 10A along the valve closing direction less than spring 20.In addition, piston 33 forms from its extension part 38 in solenoid portion 10C extends to the first valve element 18.Packing ring 39 is fixed to the end of extension part 38 by swaged forging.Packing ring 39 engages with the stepped part that forms on the first valve element 18.Therefore, when the first control valve 10A closed fully, piston 33 was opened direction by the first valve element 18 along the valve of the second control valve 10B and is forced pulling, and therefore the second control valve 10B can remain on full open position.In addition, piston 33 is configured to the internal diameter that external diameter equals first valve seat 17, thereby when piston 33 engages with the first valve element 18, prevents that piston 33 is subjected to the adverse effect of discharge pressure Pdl.
In addition, the second control valve 10B has membranaceous seal ring 40 and 41 (for example being formed by rubber), and described seal ring is the gap between the packed-piston 33 and second main body 12 by the pressure in the port one 4 and 15. Seal ring 40 and 41 is arranged between the stepped part of second main body 12 and the spring acceptance division 36 and between the stepped part and second valve seat 31 of second main body 12.
When being installed in control valve 10 in the compressor, circumferentially be provided with the O shape ring 64 that is used at the O shape ring 61 that seals between port one 3 and the port one 4, is used for encircling 62, is used for the O shape ring 63 that between port one 5 and port one 6, seals and is used between port one 3 and atmosphere, sealing in the periphery upper edge of first main body 11 and second main body 12 the O shape that seals between port one 4 and the port one 5.
As the control valve 10 of above formation in, when the rotation of the drive force of the launched machine of compressor, compressor sucks refrigeration agent from suction chamber and compresses and refrigerant compressed is discharged.
At this moment, when solenoid portion 10C does not switch on (as shown in Figure 1), the first control valve 10A is forced to close fully by the Driving force of spring 20, and because piston 33 is opened the direction pulling by the first valve element 18 along the valve of the Driving force of antagonistic spring 37, thereby the second control valve 10B opens fully.Therefore, owing to all introduce crankcase via the second control valve 10B from the ownership cryogen of discharge chamber's discharge, thereby compressor is in the minimum volume serviceability.As mentioned above, when solenoid portion 10C does not switch on, compressor is in the minimum volume serviceability, thereby control valve 10 can be applicable to such variable displacement compressor, and this variable displacement compressor must not be used for compressor and Driven Compressor are rotated the magnetic clutch that switch control is carried out in the driving force transmission between the used motor.
So, when compressor start, to solenoid portion 10C supply control electric current.Along with the increase of control electric current, plunger 53 is spurred by core 51, thereby the first valve element 18 is promoted to top shown in Figure 1 by bar 54.Along with moving upward of the first valve element 18, the piston 33 that engages with the first valve element 18 of the second control valve 10B is also promoted to top shown in Figure 1 by spring 37, be seated on second valve seat 31 up to the second valve element 32, thereby close the second control valve 10B fully.Therefore, owing to all stop to introduce the crankcase from the ownership cryogen of discharge chamber's discharge, thereby compressor converts the maximum volume operation at this moment to.
When the control electric current further increases, the first valve element 18 continues to raise, but in the second control valve 10B that moves along the valve closing direction along with the rising of the first valve element 18, the second valve element 32 that the motion of piston 33 is seated on second valve seat 31 stops, and therefore the first valve element 18 separates with piston 33.
After this, when control electric current when remaining on predetermined value, the first valve element 18 stops at such position, and at this place, the Driving force corresponding to the opposing solenoid force of the Driving force of this predetermined value and spring 20 of solenoid portion 10C balances each other.Before the control current value changed, the stop position of the first valve element 18 was constant.As mentioned above, the first valve element 18 is stopping after first valve seat 17 raises, thereby the first control valve 10A is set as the intended path cross-section area with respect to its refrigerant passage, flowing through with the refrigeration agent that is in discharge pressure Pdh that allows inlet port 13 has the refrigerant passage of described intended path cross-section area, thereby is in the refrigeration agent of discharge pressure Pdl from port one 4 dischargings.
When refrigeration agent is flowed through the first control valve 10A, produce predetermined differential pressure (Pdh-Pdl=Δ P) before and after the first control valve 10A.Because the discharge pressure Pdh2 of refrigeration agent that is supplied to the port one 5 of the second control valve 10B is substantially equal to the discharge pressure Pdh of the refrigeration agent of the port one 3 that is supplied to the first control valve 10A, therefore can be by the differential pressure Δ P that produces before and after the piston 33 sensings first control valve 10A.
Heretofore, compressor is operated to its maximum volume, thereby discharge pressure Pdh increases at present, and also increases through the flow velocity of the refrigeration agent of the first control valve 10A.When the flow velocity of refrigeration agent becomes greater than predetermined value, the Driving force of opening direction along valve that is produced by the differential pressure that is applied to piston 33 (Pdh2-Pdl ≈ Δ P) has overcome the Driving force of spring 37, make the second valve element 32 away from 31 motions of second valve seat, thereby open the second control valve 10B.This makes introduces crankcase from the refrigeration agent of discharge chamber's discharge, has begun the variable volume of compressor like this.
After this, when thereby the flow velocity through the refrigeration agent of the first control valve 10A increases the differential pressure Δ P that makes before and after the first control valve 10A and increases, piston 33 senses the variation of differential pressure and further opens the second control valve 10B, thereby controls compressor along the direction of the volume that reduces compressor.In addition, when the differential pressure Δ P before and after thereby the flow velocity of the refrigeration agent of the first control valve 10A that flows through reduces to make the first control valve 10A reduces, piston 33 senses the variation of differential pressure and the second control valve 10B is moved along the valve closing direction, thereby controls compressor along the direction of the volume that increases compressor.
At this moment, although in the second control valve 10B, will be to port one 4 from the refrigeration agent that is in discharge pressure Pdh2 of port one 5 supply by the clearance leakage between piston 33 and second main body 12, however the leakage of refrigeration agent quilt is sealed by the seal ring 41 of discharge pressure Pdh2 pressurizing and deformation.In addition, although leak into the guide 19 by the part that the guide 19 and first main body 11 are in slidable contact with each other from the refrigeration agent that is in discharge pressure Pdh of port one 3 supplies, and further leak in the port one 4 by one-way valve 21, yet can the operation of control valve 10 and compressor not had a negative impact owing to leak, thereby so slight leakage can be ignored.
As mentioned above, differential pressure Δ P before and after the piston 33 sensings first control valve 10A of the second control valve 10B, this differential pressure Δ P is produced by the refrigeration agent that passes through the first control valve 10A that is set at the intended path cross-section area, and second control valve 10B control is supplied to the flow velocity of the refrigeration agent of crankcase, makes differential pressure Δ P keep constant.This makes control valve 10 to control compressor, thereby makes refrigeration agent to discharge with the corresponding flow velocity of the control electric current that is supplied to solenoid portion 10C.
Next the operation that description is made the control valve 10 that is in above-mentioned state of a control stop.
So that when stopping compressor, the solenoid force of setting the rise of the first control valve 10A disappears when stopping suddenly to solenoid portion 10C supply control electric current, thereby the first control valve 10A closes at once fully by the Driving force of spring 20.This makes the valve element 18 of winning to pulling piston 33 in below shown in Figure 1, thereby opens the second control valve 10B forcibly fully.This makes compressor convert the minimum volume operation to.
When compressor converts minimum volume when operation to, reduce fast from the discharge pressure Pdh of compressor, but because the first valve element 18 is in buttoned-up status, thereby reduce gradually at the discharge pressure Pdl at the refrigerant outlet place of compressor.Therefore, follow closely and stop after solenoid portion 10C supply control electric current, discharge pressure Pdl becomes sometimes and is higher than discharge pressure Pdh.Under these circumstances, because discharge pressure Pdl acts on the first valve element 18 and the one-way valve 21 along the valve closing direction, thereby first control valve 10A be maintained at buttoned-up status, simultaneously since piston 33 with have identical compression area with the first valve element 18 that piston 33 engages, thereby the second control valve 10B can not operate because of discharge pressure Pdl but remains on full open position.At this moment, refrigeration agent is sealed by seal ring 40 from the leakage of port one 4 to port one 5 through the gap between second main body 12 and the piston 33.
As mentioned above, even when the discharge pressure Pdl in the refrigerant outlet side of compressor becomes when being equal to or higher than discharge pressure Pdh in discharge chamber's side of compressor, the first control valve 10A also can remain on buttoned-up status, this makes the control valve 10A that wins play the effect that is similar to the one-way valve in the refrigerant outlet that is arranged on compressor traditionally, and the second control valve 10B can remain on full open position, and this makes compressor convert the minimum volume serviceability really to.This means the one-way valve that has saved in the refrigerant outlet that is arranged on compressor traditionally.
Fig. 3 is the central longitudinal sectional view according to the structure of second embodiment's the control valve that is used for variable displacement compressor.In Fig. 3, the function element identical or equivalent with the function of the element that occurs in Fig. 1 represented by identical reference character, and omitted detailed description.
Be that according to second embodiment's control valve 70 and difference it is not equipped with the one-way valve 21 that is formed on the guide 19 according to first embodiment's control valve 10.
More particularly, in the first control valve 70A of control valve 70, the guide 19 with operation therewith of linking to each other with the first valve element 18 comprises hollow tube-shape portion with closed end and the slide part integrally formed with this hollow tube-shape portion, this slide part extends radially outwardly from the opening end of this hollow tube-shape portion, makes the outer circumferential face of extension part slide on the inner wall surface of first main body 11.The bar 54 of solenoid portion 70C extends in the hollow tube-shape portion, thus with the closed end butt of this hollow tube-shape portion.In addition, guide 19 has the intercommunicating porosity 19a that forms in the sidepiece of hollow tube-shape portion, so that the pressure among the solenoid portion 70C equals the discharge pressure Pdh at the upstream side of the first control valve 70A all the time.According to identical with according to first embodiment's control valve 10 of the further feature of the structure of second embodiment's control valve 70.
In the control valve 70 that as above constitutes, at first, when solenoid portion 70C does not switch on, as shown in Figure 3, the first control valve 70A closes fully by the Driving force of spring 20, and because the first valve element 18 of the first control valve 70A is opened the piston 33 that direction is forced the differential pressure of pulling sensing first control valve 70A front and back along valve, thereby the second control valve 70B opens fully.This allows discharge chamber and crankcase to communicate with each other by the second control valve 70B, so compressor is in the minimum volume serviceability.
Then, when to solenoid portion 70C supply control electric current, increase along with the control electric current, the bar 54 of solenoid portion 70C raises the first valve element 18 of the first control valve 70A, thereby the first control valve 70A begins to open, and the second control valve 70B begins to move along the valve closing direction with interlock mode.After this, when the second control valve 70B closed, compressor was in the maximum volume serviceability.After the second control valve 70B closed, the first control valve 70A was positioned at and control electric current corresponding raised position, and sets and control the corresponding path cross-section area of electric current for, and not with the second control valve 70B interlocking.
When compressor converts the maximum volume serviceability to, increase through the flow velocity of the refrigeration agent of the first control valve 70A.When the differential pressure before and after the first control valve 70A was equal to or greater than predetermined value, the piston 33 of this differential pressure of sensing was done in order to opening the second control valve 70B, thereby makes the variable volume of compressor.
If when control valve 70 is in state of a control, make solenoid portion 70C outage, then the first control valve 70A closes fully by spring 20 at once, and to the buttoned-up status transition period, the second control valve 70B suffers restraints and is forced to open fully at the first control valve 70A.This has sharply reduced the discharge pressure Pdh in the discharge chamber, reduces the discharge pressure Pdl at the refrigerant outlet place of compressor gradually simultaneously, thereby has put upside down the relation between discharge pressure Pdh and the discharge pressure Pdl.Yet, the first valve element 18 of one joint has identical compression area with piston 33 each other, thereby it is insensitive to discharge pressure Pdl, even thereby discharge pressure Pdl becomes and is higher than discharge pressure Pdh, also can keep the buttoned-up status of the first control valve 70A and the full open position of the second control valve 70B.
Fig. 4 is the central longitudinal sectional view according to the structure of the 3rd embodiment's the control valve that is used for variable displacement compressor.In Fig. 4, the function element identical or equivalent with the function of the element that occurs in Fig. 1 and Fig. 3 represented by identical reference character, and omitted detailed description.
According to the 3rd embodiment's control valve 80 be that according to first and second embodiments' control valve 10 and 70 difference its structure forms public port for two port ones 3 that pass through from the refrigeration agent guiding of discharge chamber and 15 and simplified by making.
More particularly, in control valve 80, its first control valve 80A has the first valve element 18 of the upstream side that is arranged in first valve seat 17.The first valve element 18 has the through hole that axial perforation forms, and hollow tube-shape portion 81 rigidity of extending by valve opening are press fitted in this through hole.Hollow tube-shape portion 81 is integrally formed with the piston 82 that can be arranged in axially slidably in first main body 11.The hollow portion of hollow tube-shape portion 81 extends in the piston 82, make this hollow portion be communicated with the opposition side of a side that forms hollow tube-shape portion 81, and the hollow portion that extends through piston 82 forms refrigerant passage 83, and discharge pressure Pdh is introduced among the solenoid portion 80C by this refrigerant passage.In addition, the spring 20 that is disposed between the end face of the piston 82 and second main body 12 of piston 82 promotes along the valve closing direction of the first control valve 80A.In addition, piston 82 is configured to make it to have big external diameter in the side towards the second control valve 80B, thereby the first control valve 80A has such valve arrangement, and wherein when the Driving force of spring 20 during greater than the Driving force of solenoid portion 80C, the gap between first main body 11 and the piston 82 is sealed.
In the second control valve 80B, be formed with port one 6 in the central authorities foremost of second main body 12, and the inner opening end of port one 6 forms second valve seat.The second valve element 32 is arranging toward and away from the mode of second valve seat motion.The second valve element 32 is integrally formed with the hollow cylinder 84 that can be arranged in axially slidably in second main body 12.The external diameter of hollow cylinder 84 is identical with the external diameter of the piston 82 of the first control valve 80A, and this hollow cylinder is formed with a plurality of intercommunicating porosities simultaneously.In addition, hollow cylinder 84 makes first valve seat, 17 rigidity of the first control valve 80A press fit into its inside.Between first valve seat 17 and piston 82, be provided with spring 37, be used for promoting hollow cylinder 84 along the valve closing direction of the second control valve 80B.
In the control valve 80 that as above constitutes, at first, when solenoid portion 80C does not switch on, as shown in Figure 4, because first valve seat 17 and the first valve element, 18 butts, thereby the first control valve 80A closes fully by the Driving force of spring 37, and in the second control valve 80B, because first valve seat 17 that is rigidly fixed to hollow cylinder 84 makes the first valve element 18 and its butt by spring 37, thereby be maintained at the fully open position with the integrally formed second valve element 32 of hollow cylinder 84.This allows discharge chamber and crankcase to communicate with each other by the second control valve 80B, so compressor is in the minimum volume serviceability.
Then, when to solenoid portion 80C supply control electric current, increase along with the control electric current, the bar 54 of solenoid portion 80C promotes the piston 82 of the first control valve 80A to top shown in Figure 4, thereby the moving element of the first control valve 80A and the first control valve 80B moves along the valve closing direction of the second control valve 80B together.After this, thereby be seated in when closing the second control valve 80B on second valve seat when the second valve element 32, compressor converts the maximum volume serviceability to.So, when piston 82 when the valve closing direction of the second control valve 80B is pushed, the first valve element 18 raises from first valve seat 17 gradually, thereby opens the first control valve 80A gradually.Subsequently, the first valve element 18 stops at and controls the corresponding raised position of electric current, and the first control valve 80A sets and control the corresponding path cross-section area of electric current for.
When compressor converts the maximum volume serviceability to, increase through the flow velocity of the refrigeration agent of the first control valve 80A, thereby produce differential pressure before and after the first control valve 80A.This differential pressure is formed first valve seat 17 of differential pressure sensing part and the cross-section area of hollow cylinder 84 receives.When differential pressure is equal to or greater than predetermined value, thereby first valve seat 17 of senses differential pressure and hollow cylinder 84 effects are opened the second control valve 80B so that the variable volume of compressor.
At this moment, when discharge pressure Pdh increases and compressor when being controlled in predetermined volume, the second control valve 80B opens the direction operation to control volume along the direction that reduces volume along valve, and when discharge pressure Pdh reduced, the second control valve 80B operated to control volume along the direction that increases volume along the valve closing direction.At this moment, although the first control valve 80A also changes along with the variation of discharge pressure Pdh, the volume of compressor is determined according to the control balance between the first control valve 80A and the second control valve 80B, thereby this volume is configured to predetermined volume basically.
If when control valve 80 is in state of a control, make solenoid portion 80C outage suddenly, then the first control valve 80A is closed fully by spring 20 at once, and to the buttoned-up status transition period, the second control valve 80B suffers restraints and is forced to open fully at the first control valve 80A.This has sharply reduced the discharge pressure Pdh in the discharge chamber, and reduces the discharge pressure Pdl in the refrigerant outlet of compressor gradually, makes the discharge pressure Pdl at refrigerant outlet place become at present to be higher than discharge pressure Pdh in the discharge chamber.Yet, each other first valve seat 17, the first valve element 18 and the hollow cylinder 84 that engage of one along shown in Figure 4 upward to the compression area that receives discharge pressure Pdl, identical with piston 82 along the compression area that downward direction shown in Figure 4 receives discharge pressure Pdl, thus control valve 80 has insensitive structure to discharge pressure Pdl.Therefore, be higher than discharge pressure Pdh, still keep the buttoned-up status of the first control valve 80A and the full open position of the second control valve 80B even discharge pressure Pdl becomes.
Fig. 5 is the central longitudinal sectional view according to the structure of the 4th embodiment's the control valve that is used for variable displacement compressor.In Fig. 5, the function element identical or equivalent with the function of the element that occurs in Fig. 4 represented with identical reference character, and omitted detailed description.
Be according to the 4th embodiment's control valve 90 and difference, improved control valve 90 in the speed of after state of a control carries out the transition to halted state, returning suddenly state of a control once more according to the 3rd embodiment's control valve 80.
More particularly, in control valve 90, the first valve element 18 and hollow tube-shape portion 81 form one each other, and axial linearly the perforation is formed with refrigerant passage 83.Hollow tube-shape portion 81 is fixed to piston 82 to connect the extension mode, and the opening and closing at the end face of the opening end on the side of solenoid portion 90C by bar 54 of refrigerant passage 83.By this structure, control valve 90 has such valve arrangement, wherein when solenoid portion 90C does not switch on (as shown in Figure 5), the port one 3 that confession discharge pressure Pdh introducing is passed through communicates with each other with the inside of solenoid portion 90C, and when solenoid portion 90C switches on, introduce for discharge pressure Pdh between the inside of the port one 3 that passes through and solenoid portion 90C be communicated with blocked.
In said structure, the basic operation according to the 3rd embodiment's control valve 80 of the basic operation of control valve 90 and Fig. 4 is identical.Yet, when at control valve 90 suddenly after state of a control conversion or carrying out the transition to halted state, at once to solenoid portion 90C energising so that its when turning back to state of a control once more, bar 54 makes the first valve element 18 raise the opening end of cutting out hollow tube-shape portion 81 simultaneously.When even the first valve element 18 when raising slightly, the also corresponding rising of piston 82, thus open gap between the piston 82 and first main body 11, the refrigeration agent that will still be in maximum discharge pressure P dl thus is introduced in the space that forms between piston 82 and the solenoid portion 90C.This makes on piston 82 effect one Driving force, this Driving force cause the first control valve 90A to open the direction operation along valve, and this helps solenoid portion 90C to make to win control valve 90A to open the direction operation along valve.Shortened like this and opened the required time of the second control valve 90B fully, thereby made control valve 90 can return its initial state of a control quickly.
Fig. 6 is the central longitudinal sectional view according to the structure of the 5th embodiment's the control valve that is used for variable displacement compressor.In Fig. 6, the function element identical or equivalent with the function of the element that occurs in Fig. 1 and Fig. 5 represented with identical reference character, and omitted detailed description.
In control valve 100 according to the 5th embodiment, will be according to the structure applications of the 4th embodiment's control valve 90 in control valve 10 according to first embodiment, it has the port one 3 and 15 that forms independently of one another, described port is used for respectively refrigeration agent being introduced the first control valve 10A and the second control valve 10B, improvements according to the 4th embodiment's control valve 90 are that the pressure P c in the crankcase opens directive effect on the second control valve 90B along valve in addition.
More particularly, in control valve 100, second main body 12 foremost on be formed with second valve seat 31, this second valve seat is formed with the port one 5 that is used to introduce discharge pressure Pdh2, and the second valve element 32 is supported in the mode relative with second valve seat 31 by second main body 12 with being axially moveable.The end on the side of solenoid portion 100C of the second valve element 32 extends to the chamber for the port one 3 of introducing discharge pressure Pdh, and is press fitted in the described end of the second valve element 32 by joining portion 101 rigidity that the closure of the hollow cylinder 84 of the first control valve 100A keeps.Between the joining portion 101 and the first valve element 18, be furnished with spring 35, be used for promoting the second valve element 32 along the valve closing direction.In addition, the end face on the opposition side of a side that receives spring 35 at joining portion 101 is tapered, thereby when the second valve element 32 is seated on second valve seat 31, can the closed second valve element 32 and support gap between second main body 12 of the second valve element 32.
In the control valve 100 that as above constitutes, its operation is identical with the operation according to the 4th embodiment's control valve 90 basically.Yet the second control valve 100B is configured to the axial relative two ends that the discharge pressure Pdh that will roughly be equal to each other and discharge pressure Pdh2 are applied to the second valve element 32 respectively.This makes control valve 100 to carry out control operation in response to the differential pressure between the pressure that is applied to first valve seat 17 and hollow cylinder 84 from axially relative both sides, and is not subjected to the adverse effect from the pressure P c of crankcase.
Fig. 7 is the central longitudinal sectional view according to the structure of the 6th embodiment's the control valve that is used for variable displacement compressor.In Fig. 7, the function element identical or equivalent with the function of the element that occurs in Fig. 1 represented with identical reference character, and omitted detailed description.
In control valve 110 according to the 6th embodiment, although its first control valve 110A and solenoid portion 110C have and extremely identical structure according to first embodiment's control valve 10, the second control valve 110B has the different structure with the second control valve 10B.
More particularly, in the second control valve 110B of control valve 110, differential pressure sensing part is formed by the valve element holding part 111 and the bellows 112 that keep the second valve element 32, the axial relative two ends of bellows 112 closely are connected to the upper end shown in Figure 7 of valve element holding part 111 and the upper end shown in Figure 7 of spring acceptance division 36 respectively, thus but bellows 112 axial stretchings.So also with the piston 33 similar differential pressure sensings parts of the second control valve 10B in, valve element holding part 111 makes the second valve element 32 according to the differential pressure between discharge pressure Pdh2 and the discharge pressure Pdl and axial motion, thereby can adjust the valve stroke of the second control valve 110B.In addition, because bellows 112 separates between port one 5 that is in discharge pressure Pdh2 and the port one 4 that is in discharge pressure Pdl, thereby can thoroughly prevent owing to the differential pressure between pressure P dh2 and the Pdl makes freezing medium leakage.This structure of the second control valve 110B makes can save seal ring 40 and 41 used in the second control valve 10B.
In the control valve 110 that as above constitutes, its operation is identical with the operation according to first embodiment's control valve 10, thereby the omission detailed description.
Fig. 8 is the central longitudinal sectional view according to the structure of the 7th embodiment's the control valve that is used for variable displacement compressor.In Fig. 8, the function element identical or equivalent with the function of the element that occurs in Fig. 3 represented by identical reference character, and omitted detailed description.
Be that according to the 7th embodiment's control valve 120 and difference it has simpler structure according to second embodiment's control valve 70.More particularly, in the first control valve 120A of control valve 120, the respective ends of the first valve element 18 and coupled guide 19 and the respective inner walls sliding contact of first main body 11 and second main body 12 make win valve element 18 and guide 19 axially motion under stable status.In addition, guide 19 has the intercommunicating pore 121 that the part of connecting forms, the part that this part connects near the bar 54 with solenoid portion 120C.
The second control valve 120B comprises piston 33 and is fixed to the bar 122 of piston 33, the differential pressure between the discharge pressure Pdh2 at piston 33 sensing ports 15 places and the discharge pressure Pdl at port one 4 places.One end of bar 122 forms the second valve element 32 of the second control valve 120B, and the other end of bar 122 forms the joining portion, when solenoid portion 120C does not switch on, the first valve element 18 of the first control valve 120A engages with this joining portion, and this other end cooperates with the first valve element 18 and forms the valve element of a valve, and this valve element opens and closes the refrigerant passage that the central authorities that axially connect first valve element 18 and guide 19 form.In addition, be provided with spring 37 between the seal ring 40 of the first control valve 120A and the first valve element 18, this spring promotes piston 33 along the valve closing direction of the second control valve 120B.Although spring 37 should promote piston 33 with respect to second main body 12, it is configured to promote piston 33 with respect to the first valve element 18, so that reduce load on spring and simplified structure.
According to control valve 120, when solenoid portion 120C did not switch on, spring 20 promoted the first valve element 18 to below shown in Figure 8, thereby closed the first control valve 120A fully, and the first valve element 18 is to below pull lever 122 shown in Figure 8, thereby opens the second control valve 120B fully.At this moment, because the joining portion of the first valve element 18 and bar 122 is fluid-tight engagement each other, thereby the refrigerant passage that the central authorities that connect the first valve element 18 and guide 19 form is closed, and the refrigeration agent that is in discharge pressure Pdh leaks by the position that the guide 19 and first main body 11 are in slidable contact with each other, and makes pressure among the solenoid portion 120C near discharge pressure Pdh.
When solenoid portion 120C switched on, bar 54 promoted the first valve element 18 by guide 19 to top shown in Figure 8, thereby opened the first control valve 120A.Piston 33 is also promoted to top shown in Figure 8 in the mode that upwards promotes interlocking with the first valve element 18 by spring 37, and when 32 of the second valve elements were put, the second control valve 120B was fully closed.When the first valve element 18 is further upwards promoted, with the bar 122 of the first valve element, 18 fluid-tight engagement away from the first valve element 18, thereby the refrigerant passage that the central authorities that connect the first valve element 18 and guide 19 form is opened, thereby solenoid portion 120C is communicated with so that the pressure in this solenoid portion equals discharge pressure Pdl with port one 4.
When the state of a control that is elevated to predetermined value by the control electric current that is supplied to solenoid portion 120C from the first valve element 18 wherein stops to solenoid portion 120C supply control electric current suddenly, the first control valve 120A closes fully, and the second control valve 120B opens fully, is closed in the refrigerant passage that forms in the central authorities of the first valve element 18 and guide 19 simultaneously fully.This makes compressor convert the minimum volume serviceability to, thereby discharge pressure Pdh and Pdh2 in discharge chamber's side sharply reduce, and the discharge pressure Pdl among the solenoid portion 120C leaks in the port one 3 by the position that the guide 19 and first main body 11 are in slidable contact with each other, thereby makes discharge pressure Pdl near the discharge pressure Pdh that sharply reduces.Therefore, thereby about equally discharge pressure Pdh and the Pdh2 of sharply reducing to become each other is applied on the axial relative two ends of moving element, the first valve element 18 and piston 33 of the guide 19 that is made into integration each other, and therefore the buttoned-up status of the first control valve 120A and the full open position of the second control valve 120B are almost only kept by the load of spring 20.
Fig. 9 is the central longitudinal sectional view according to the structure of the 8th embodiment's the control valve that is used for variable displacement compressor.Figure 10 A to Figure 10 C is the view that is used to illustrate the characteristic of barrier film, wherein Figure 10 A shows the state that does not apply differential pressure on the barrier film, Figure 10 B shows the state that barrier film moves by differential pressure, and Figure 10 C shows differential pressure and is applied to state on the mobile barrier film along the direction opposite with movement direction.Figure 11 A and Figure 11 B are the schematic representation of expression according to the structure of the differential pressure sensing part of the 8th embodiment's control valve, wherein Figure 11 A shows the situation of the pressure in the refrigerant outlet that pressure in the discharge chamber of compressor wherein is higher than compressor, and Figure 11 B shows the situation that pressure in the discharge chamber wherein is lower than the pressure in the refrigerant outlet.In Fig. 9, Figure 11 A and Figure 11 B, the function element identical or equivalent with the function of the element that occurs in Fig. 8 represented with identical reference character, and omitted detailed description.
More particularly, in control valve 130, nearly all element of the first control valve 130A and the second control valve 130B all is the pressed part that is formed by extruded tube, and by being press-fitted or swaged forging fits together these pressed parts.
In the first control valve 130A, the core 51 that stretches out from yoke 59 by swaged forging foremost aduncate first main body 131 of an end is fixed to solenoid portion 130C, and the 3rd main body 133 rigidity that second main body 132 and an end form first valve seat 17 are press fitted in first main body 131.In the 3rd main body 133, can be furnished with bell guide 19 axially slidably, and the bell bar acceptance division 134 with intercommunicating pore 121 is press fitted in the guide 19.Guide 19 on an end of the side of the second control valve 130B outside be equipped with the first valve element 18, and this guide is disposed in its other end and the spring between the projection that forms on the inside of main body 133 20 promotes along the valve closing direction.
Second main body 132 has the opening end that is provided with barrier film 135, this barrier film is made by polyimide, be used between port one 5 that is in discharge pressure Pdh2 and the port one 4 that is in discharge pressure Pdl, sealing, and the differential pressure between sensing discharge pressure Pdh2 and the discharge pressure Pdl.The peripheral part of barrier film 135 is clipped between first ring, 136 and second ring 137, and its central part is clipped between spider 138 and the lip part 139.Opening end by swaged forging second main body 132 makes first ring, 136 and second ring 137 be fixed to second main body 132 with the state that barrier film 135 is clipped in therebetween with the 4th main body 140.On the other hand, the central part by bar 141 being press fitted into spider 138 and the second control valve 130B with the integrally formed hollow tube-shape second valve element 32 of lip part 139 in, with spider 138 and lip part 139 barrier film 135 is clipped in fixed to one another being in the same place of state therebetween.It should be noted that, the peripheral part with barrier film 135 of first ring 136 and second ring 137 becomes with the section construction that central part is clipped in the middle, make first ring, 136 internal diameter be made as internal diameter, and the external diameter of spider 138 is made as the external diameter greater than lip part 139 greater than second ring 137.In addition, first ring 136 has stepped part, and it is formed for limiting the block piece 142 that barrier film 135 moves from the extended part of this stepped part.
The 5th cup-shaped main body 143 is press fitted in the 4th main body 140.The central authorities of the 5th main body 143 bottoms are formed with the valve opening of the second control valve 130B, and the opening of this valve opening forms the port one 6 that leads to crankcase.Bar 141 extends through the valve opening of the second control valve 130B, and is assemblied in going up foremost of bar 141 outside the spring acceptance division 144.Between the bottom of the 5th main body 143 and spring acceptance division 144, be inserted with spring 37, be used for promoting the second valve element 32 along the valve closing direction.
According to above-mentioned control valve 130, when solenoid portion 130C does not switch on, thereby spring 20 promotes guide 19 to below shown in Figure 9 and closes the first control valve 130A fully, simultaneously guide 19 is to below pull lever 141 shown in Figure 9, thereby opens the second control valve 130B fully up to spider 138 and block piece 142 butts.At this moment, because guide 19 and bar 141 be fluid-tight engagement each other, the refrigeration agent that is in discharge pressure Pdh leaks in first main body 131 by the position that guide 19 and the 3rd main body 133 are in slidable contact with each other, thereby makes pressure among the solenoid portion 130C near discharge pressure Pdh.
When solenoid portion 130C switched on, bar 54 promoted the first valve element 18 by guide 19 to top shown in Figure 9, thereby opened the first control valve 130A.Bar 141 is also promoted to top shown in Figure 9 in the mode that upwards promotes interlocking with the first valve element 18 by spring 37, and when 32 of the second valve elements were put, the second control valve 130B was fully closed.When the first valve element 18 is further upwards promoted, with the bar 141 of guide 19 fluid-tight engagement away from guide 19, make solenoid portion 130C by being communicated with port one 4, thereby the pressure among the solenoid portion 130C become and equal discharge pressure Pdl in the hole that extends through for bar 141 of guide 19 central authorities and the intercommunicating pore 121 of bar acceptance division 134.
After this, when control electric current when remaining on predetermined value, the first valve element 18 stops at such position, and at this place, the Driving force corresponding to the opposing solenoid force of the Driving force of this predetermined value and spring 20 of solenoid portion 130C balances each other.The first valve element 18 raises and stops from first valve seat 17, thereby be set at for the refrigerant passage of the first control valve 130A and make refrigerant passage have predetermined path cross-section area, thereby the refrigeration agent that is in discharge pressure Pdh that allows inlet port 13 is flowed through and is had the refrigerant passage of described predetermined path cross-section area, and the refrigeration agent that is in discharge pressure Pdl enters the refrigerant outlet of compressor from port one 4.When refrigeration agent is flowed through the first control valve 130A, produce predetermined differential pressure Δ P before and after the first control valve 130A.Because discharge pressure Pdh2 is approximately equal to discharge pressure Pdh, thereby by the differential pressure Δ P that produces before and after the barrier film 135 sensings first control valve 130A.Barrier film 135 drives the therewith second valve element 32 of motion, thereby control is supplied to the flow velocity of the refrigeration agent of crankcase by the second control valve 130B.Therefore, control valve 130 provides control, make compressor with the corresponding flow velocity refrigerant emission of the control electric current that is supplied to solenoid portion 130C.
When the state of a control that is elevated to predetermined value by the control electric current that is supplied to solenoid portion 130C from the first valve element 18 wherein stops to solenoid portion 130C supply control electric current suddenly, the first control valve 130A closes fully, and the second control valve 130B opens fully, closes the hole of guide 19 central authorities simultaneously.This makes compressor convert the minimum volume serviceability to, thereby the discharge pressure Pdh and the Pdh2 of discharge chamber's side sharply reduce, and the discharge pressure Pdl among the threaded pipe part 130C leaks in the port one 3 by the position that the guide 19 and first main body 11 are in slidable contact with each other, thereby makes discharge pressure Pdl near the discharge pressure Pdh that sharply reduces.Therefore, the discharge pressure Pdl that reduces gradually is applied to guide 19 from the side towards port one 4, and the discharge pressure Pdh that sharply reduces is applied to the inside of guide 19, so the buttoned-up status of the first control valve 130A and the full open position of the second control valve 130B are kept in the load of differential pressure between them and spring 20.
At this moment, when noting the timesharing of differential pressure detecting part as can be known, effective compression area of barrier film 135 changes according to the stroke that it moves.Shown in Figure 10 A, effective compression area of barrier film 135 depends on the area of a circle, and this diameter of a circle (effective diameter b) is the centre distance of the circle of curvature a of corresponding wavy part.Here, when becoming from illustrated top applied pressure P1 greater than from illustrated below applied pressure P2 the time, the central part of barrier film 135 moves down, shown in Figure 10 B.At this moment, because the interior perimembranous of each wavy part also moves with this central part, thereby the increase of the curvature of wavy part, and centre of curvature moves inward, thereby effective diameter becomes the effective diameter b1 less than effective diameter b, has reduced effective compression area thus.Here, shown in Figure 10 C, when the state downforce P2 that moves when the central part at barrier film 135 becomes greater than pressure P 1, wavy part is expanded alone to expand towards pressure P 1, this makes centre of curvature outwards move, thereby make effective diameter become effective diameter b2, increased effective compression area thus greater than effective diameter b.
This situation is corresponding to such situation, that is, stop suddenly to solenoid portion 130C supply control electric current, thereby the discharge pressure Pdl that makes in the downstream side of the first control valve 130A is higher than the discharge pressure Pdh2 of side at its upstream.Under these circumstances, move along the valve closing direction by the feasible second valve element 32 of the differential pressure of discharge pressure Pdl between discharge pressure Pdh2 with barrier film 135 motions.More particularly, when solenoid portion 130C cuts off the power supply, load by spring 20 is opened the second control valve 130B fully, but following closely, when discharge pressure Pdl becomes when being higher than discharge pressure Pdh2, act on the second control valve 130B along the valve closing direction in response to the barrier film 135 of differential pressure.Therefore, particularly when differential pressure is very big, can not keep the buttoned-up status of the first control valve 130A and the full open position of the second control valve 130B.
On the contrary, control valve 130 is configured to, and when discharge pressure Pdl becomes when being higher than discharge pressure Pdh2, the increase that acts on the power on the second control valve 130B along the valve closing direction is restricted.Therefore, the effective diameter c2 that only needs to make the barrier film 135 that obtains when discharge pressure Pdl is higher than discharge pressure Pdh2 is less than the effective diameter c1 that is higher than the barrier film 135 that discharge pressure Pdl obtains as discharge pressure Pdh2.As Figure 11 A and Figure 11 B with shown in the amplification form, this is by following realization, promptly, make the corresponding internal diameter of first ring, 136 and second ring 137 that respective surfaces with barrier film 135 is clipped in the middle differ from one another, and make also the spider 138 that respective surfaces with barrier film 135 is clipped in the middle and the corresponding external diameter of lip part 139 differ from one another.More particularly, the internal diameter of the stepped part of first ring 136 is set at the internal diameter greater than second ring 137, and the external diameter of spider 138 is set at the external diameter greater than lip part 139 simultaneously.Yet effective diameter c1 is set at the internal diameter of first valve seat that equals the first control valve 130A, makes when the first control valve 130A is in closed condition, and the compression area of barrier film 135 is identical with the compression area of the first valve element 18 that is used to receive discharge pressure Pdl.Should be noted that at the distance setting between the periphery of first ring interior week of 136 and spider 138 to be to equal second distance of encircling between the periphery of 137 interior week and lip part 139.
Therefore, when keeping Pdl＜Pdh2 shown in Figure 11 A, the wavy part of barrier film 135 is limited by the spider 138 with big external diameter and first ring 136 that has than large diameter, and at this moment, effective compression area of barrier film 135 is definite by effective diameter c1.On the other hand, when keeping Pdl＞Pdh2 shown in Figure 11 B, the wavy part of barrier film 135 is limited by the lip part 139 with less external diameter and second ring 137 with less internal diameter, and at this moment, effective compression area of barrier film 135 is definite by effective diameter c2.As mentioned above, when the outage of solenoid portion 130C make from discharge pressure Pdl less than the status transition of discharge pressure Pdh2 when discharge pressure Pdl is higher than the state of discharge pressure Pdh2, make effective compression area of barrier film 135 become littler, therefore can reduce by differential pressure generating act on power on the second control valve 130B along the valve closing direction, this makes can carry out the shut-down operation of car air conditioner smoothly.
Because the control valve that is used for variable displacement compressor according to the present invention is configured to make it insensitive for the pressure in the downstream side of first control valve, thereby become when being higher than pressure in the discharge chamber when pressure at the refrigerant outlet place, the pressure that also can prevent the refrigerant outlet place along the directive effect that increases the compressor volume on second control valve.This makes can save the one-way valve at the refrigerant outlet place that is arranged on compressor traditionally, and the favourable part of doing like this is to reduce the cost of compressor.
Below only be considered as the illustration of the principle of the invention.In addition, owing to those skilled in the art will readily appreciate that numerous modifications and variations, thereby do not expect the present invention is limited to illustrated and described exact configuration and application, therefore, all suitable modifications and equivalent all can be regarded as falling within the scope of the present invention in claims and the equivalent thereof.
Claims (26)
1, a kind of control valve that is used for variable displacement compressor, this control valve comprises: first control valve, this first control valve is controlled described first refrigeration agent that control valve allows flows to the refrigerant outlet of this compressor from the discharge chamber of described compressor flow velocity; Second control valve, this second control valve is controlled this second refrigeration agent that control valve allows flows into the crankcase of described compressor from described discharge chamber flow velocity based on the differential pressure before and after described first control valve, changing the volume of described compressor, thereby the flow speed control of described first flow of refrigerant that control valve allows is become constant; And solenoid portion, this solenoid portion is set the flow velocity of described first flow of refrigerant that control valve allows,
Wherein, described control valve is formed into for the pressure in the downstream side of described first control valve insensitive, and when described solenoid portion is in not "on" position, described first control valve is in buttoned-up status, and described second control valve is in full open position, even when the pressure in the downstream side of described first control valve was equal to or higher than the pressure of upstream side of described first control valve, described second control valve also was forced to remain on full open position.
2, control valve according to claim 1 is characterized in that,
Described first control valve has the first valve element, and this first valve element has the raised position of setting according to the Driving force of described solenoid portion, and it is resisted the Driving force of described solenoid portion and is pushed along the valve closing direction;
The second valve element that described second control valve has differential pressure sensing part and divided maintenance by described differential pressure detecting part, described differential pressure sensing partly has the identical compression area of compression area with the part of the described first valve element, this part is received in the pressure in the downstream side of described first control valve when the described first valve element is in the closed position, and the differential pressure between the pressure in the downstream side of the pressure of described differential pressure sensing part sensing described first control valve front and back upstream side that produce, described first control valve and described first control valve; And
When the state of a control of from described solenoid portion described first control valve being set in described solenoid portion carries out the transition to not "on" position, be pushed power move to the described first valve element of complete closed position with during described state of a control away from the described differential pressure detecting part of the described first valve element divide and engage, thereby make the described second valve element move to the fully open position.
3, control valve according to claim 2 is characterized in that, described second control valve, described first control valve and described solenoid portion arrange successively along same axis, wherein:
Described first control valve has: first port, and this first port is formed on a side of described solenoid portion, is used for introducing refrigeration agent from described discharge chamber; Second port, this second port is formed on a side of described second control valve, is used for refrigeration agent is entered described refrigerant outlet; First valve seat, this first valve seat are arranged between described first port and described second port; And the described first valve element, this first valve element to be can being arranged in the downstream side of described first valve seat toward and away from the mode of described first valve seat motion, and
Described second control valve has: the 3rd port, and the 3rd port separates with described second port by described differential pressure sensing part, is used for introducing refrigeration agent from described discharge chamber; Its axis forms in the opposition side upper edge of described first control valve for the 4th port, the 4th port, is used for refrigeration agent is entered described crankcase, and described differential pressure sensing part is pushed along the valve closing direction; Second valve seat, this second valve seat are arranged in described the 4th port; And the described second valve element, this second valve element be arranged on the upstream side of described second valve seat and by described differential pressure sensing part keeping toward and away from the mode of described second valve seat motion.
4, control valve according to claim 3, it is characterized in that, described first control valve has: guide, this guide is arranged in the space that is communicated with described first port slidably along the axis of the described first valve element, and link to each other with the described first valve element by valve opening, be used to guide the axial motion of the described first valve element; And spring, this spring is arranged between described guide and described first valve seat, is used for promoting the described first valve element along the valve closing direction.
5, control valve according to claim 4, it is characterized in that, described guide has the identical compression area of compression area with the part of the described first valve element, this part is received in the pressure of the upstream side of described first control valve when the described first valve element is in the closed position, and this guide is received in the pressure along the valve closing direction of described first control valve of the upstream side of described first control valve.
6, control valve according to claim 5 is characterized in that, the described first valve element is arranged in the space that is communicated with described second port slidably along the axis of described first control valve.
7, control valve according to claim 5, it is characterized in that, described first valve element and coupled described guide have a refrigerant passage and the one-way valve that axial perforation forms, this one-way valve is used for the pressure on a side of described second port in described refrigerant passage and becomes when being higher than pressure on a side of described solenoid portion in the described refrigerant passage, closes described refrigerant passage.
8, control valve according to claim 6, it is characterized in that, described first valve element and coupled described guide have a refrigerant passage and the valve that axial perforation forms, this valve engages with described differential pressure detecting part branch when the described first valve element is forced to make the described second valve element move to the fully open position, thereby closes described refrigerant passage.
9, control valve according to claim 4 is characterized in that, described guide is provided with intercommunicating porosity, and this intercommunicating porosity is used for making the pressure of described solenoid portion to equate with the pressure of the upstream side of described first control valve.
10, control valve according to claim 3, it is characterized in that, described second control valve has as the piston of described differential pressure sensing part and the spring that promotes described piston along the valve closing direction, this piston is used for receiving at its place, axially relative two ends from the pressure of described second port and from the pressure of described the 3rd port, thereby operates according to the differential pressure between these pressure.
11, control valve according to claim 10 is characterized in that, described spring is arranged between described piston and the described first valve element.
12, control valve according to claim 10, it is characterized in that, described second control valve has membranaceous seal ring, this membranaceous seal ring be arranged between the main body that is formed on described piston and keeps described piston with being axially moveable, at least one of the opening end in the gap of described second port and described the 3rd port openings, be used for by this gap of wiper seal from described second port or described the 3rd port.
13, control valve according to claim 12, it is characterized in that, described second control valve have described piston with the described second valve seat opposing end faces in the valve element base portion accommodating part that forms, and the base portion of the described second valve element with the state that is pushed along the valve closing direction and in case anti-avulsion from mode be contained in the described valve element base portion accommodating part.
14, control valve according to claim 3 is characterized in that, described second control valve has: bellows, and the axial opposite end of this bellows closely links to each other with the described differential pressure sensing part that keeps the described second valve element; And main body, this body shaft is held described differential pressure sensing part to movably, and described bellows can make described second port and described the 3rd port sealing by axial stretching simultaneously.
15, control valve according to claim 3, it is characterized in that, described second control valve has the barrier film as described differential pressure sensing part, this barrier film so that the mode of described the 3rd port and described second port sealing be arranged between described second port and described the 3rd port, be used for receiving from the pressure of described second port and from the pressure of described the 3rd port, so that the described second valve element is operated by the differential pressure between these pressure at its axial facing surfaces place.
16, control valve according to claim 15, it is characterized in that, described barrier film closely is connected to a main body with such state, promptly, the periphery of this barrier film is clipped between first ring and second ring, the central part of this barrier film be clipped in spider and and have between the integrally formed lip part of the described second valve element of hollow cylindrical shape, described barrier film is fixed to a bar with described spider and described lip part, the mode that this bar extends with axial perforation is assemblied on the described barrier film.
17, control valve according to claim 16, it is characterized in that described barrier film is configured to: its compression area that is used to receive pressure equals the compression area that is used for receiving from described second port pressure of the described first valve element when described first control valve is in closed condition when the pressure in described the 3rd port is higher than pressure in described second port.
18, control valve according to claim 17, it is characterized in that, described barrier film is configured such that the internal diameter of the internal diameter of described second ring less than described first ring, and make the external diameter of described lip part less than the external diameter of described spider, thereby make the compression area that is used to receive pressure of when the pressure in described second port is higher than pressure in described the 3rd port described barrier film, be used to receive the compression area of pressure during less than the pressure that is higher than when pressure from described second port from described the 3rd port.
19, control valve according to claim 2, it is characterized in that, described second control valve, described first control valve and described solenoid portion are arranged successively along same axis, and described first control valve has: first port, this first port is formed on a side of described solenoid portion, is used for refrigeration agent is entered described refrigerant outlet; Second port, this second port is formed on a side of described second control valve, is used for introducing refrigeration agent from described discharge chamber; First valve seat, this first valve seat are arranged between described first port and described second port; And the described first valve element, this first valve element is can be arranged in the upstream side of described first valve seat toward and away from the mode of described first valve seat motion, and described second control valve has: the 3rd port, its axis forms the 3rd port in the opposition side upper edge of described first control valve, and the refrigeration agent that is used for introducing described second port enters described crankcase; Hollow cylinder, this hollow cylinder make described first valve seat be fixed to its inside and arrange with the state that is pushed along the valve closing direction with being axially moveable, thereby form described differential pressure sensing part; And the second valve element, this second valve element and described hollow cylinder are integrally formed, are used to open and close described the 3rd port.
20, control valve according to claim 19, it is characterized in that, described first control valve comprises: piston, this piston is slidably disposed in the space that is communicated with described first port along the axis of the described first valve element, and link to each other with the described first valve element by valve opening, be used to guide the axial motion of the described first valve element; And spring, this spring is arranged on described piston and holds between the main body of described piston, is used for promoting the described first valve element along the valve closing direction.
21, control valve according to claim 20, it is characterized in that, described piston structure becomes to make external diameter identical with the external diameter of the described hollow cylinder of described second control valve, thereby forbids the pressure of described piston sensing in the downstream side of described first control valve when the described first valve element is in the closed position.
22, control valve according to claim 20, it is characterized in that, described first valve element and coupled described piston have the refrigerant passage that axial perforation forms, and are used for the feasible pressure of introducing the refrigeration agent of described second port and are received by the end face towards described solenoid portion via described refrigerant passage.
23, control valve according to claim 22 is characterized in that, when the bar of described solenoid portion promoted the described first valve element, described refrigerant passage was closed by described bar.
24, control valve according to claim 2, it is characterized in that, described second control valve, described first control valve and described solenoid portion are arranged successively along same axis, and described first control valve has: first port, this first port is formed on a side of described solenoid portion, is used for refrigeration agent is entered described refrigerant outlet; Second port, this second port is formed on a side of described second control valve, is used for introducing refrigeration agent from described discharge chamber; First valve seat, this first valve seat are arranged between described first port and described second port; And the described first valve element, this first valve element is can be arranged on the upstream side of described first valve seat toward and away from the mode of described first valve seat motion, and described second control valve has: the 3rd port, the 3rd port are used for refrigeration agent is entered described crankcase; Its axis forms in the opposition side upper edge of described first control valve for the 4th port, the 4th port, is used for introducing refrigeration agent from described discharge chamber; Hollow cylinder, this hollow cylinder are arranged in the space that is communicated with described second port and make described first valve seat be rigidly fixed to its inside with the state that is pushed along the valve closing direction, thereby form described differential pressure sensing part; Second valve seat, this second valve seat are arranged in described the 4th port; And the second valve element, this second valve element is arranged to make the one end relative with described second valve seat, and its other end is pushed along the valve closing direction with respect to the described first valve element, thereby engages with described hollow cylinder, and can be toward and away from described second valve seat motion.
25, control valve according to claim 24, it is characterized in that, described first control valve comprises: piston, this piston is arranged in the space that is communicated with described first port slidably along the axis of the described first valve element, and link to each other with the described first valve element by valve opening, be used to guide the axial motion of the described first valve element; And spring, this spring is arranged on described piston and holds between the main body of described piston, be used for promoting the described first valve element along the valve closing direction, and the described first valve element has the refrigerant passage that axial perforation forms, and this refrigerant passage is closed by the bar of described solenoid portion when described bar promotes the described first valve element.
26, control valve according to claim 25, it is characterized in that, described piston structure becomes to make its part that receives the pressure of described first port along the valve closing direction to have the identical external diameter of external diameter with the described hollow cylinder of described second control valve, thereby forbids the pressure of described piston sensing in the downstream side of described first control valve when the described first valve element is in the closed position.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006004395 | 2006-01-12 | ||
| JP2006004395 | 2006-01-12 | ||
| JP2006039365 | 2006-02-16 | ||
| JP2006238904 | 2006-09-04 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101000046A true CN101000046A (en) | 2007-07-18 |
Family
ID=38692143
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200710001398 Pending CN101000046A (en) | 2006-01-12 | 2007-01-12 | Control valve for variable displacement compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101000046A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113646539A (en) * | 2019-03-20 | 2021-11-12 | 丹佛斯有限公司 | Compressor unit with damped axial check valve for discharge outlet |
-
2007
- 2007-01-12 CN CN 200710001398 patent/CN101000046A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113646539A (en) * | 2019-03-20 | 2021-11-12 | 丹佛斯有限公司 | Compressor unit with damped axial check valve for discharge outlet |
| CN113646539B (en) * | 2019-03-20 | 2023-08-04 | 丹佛斯有限公司 | Compressor unit with damped axial check valve for discharge outlet |
| US11976747B2 (en) | 2019-03-20 | 2024-05-07 | Danfoss A/S | Compressor unit with a damped axial check valve for a discharge outlet |
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