CN1737370A - Control valve for variable displacement compressor - Google Patents
Control valve for variable displacement compressor Download PDFInfo
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- CN1737370A CN1737370A CNA2005100905620A CN200510090562A CN1737370A CN 1737370 A CN1737370 A CN 1737370A CN A2005100905620 A CNA2005100905620 A CN A2005100905620A CN 200510090562 A CN200510090562 A CN 200510090562A CN 1737370 A CN1737370 A CN 1737370A
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- Prior art keywords
- pressure
- valve
- receiving area
- crank press
- discharge pressure
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—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
- 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
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
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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
- F04B2027/184—Valve controlling parameter
- F04B2027/1854—External parameters
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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
- F04B2027/184—Valve controlling parameter
- F04B2027/1859—Suction pressure
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
A control valve for performing a Pd-Ps differential pressure control method in a variable displacement compressor adjusts the difference between an effective pressure-receiving area (A) on a discharge pressure side of an intermediate structure in which a valve element is made to move in unison with a shaft and an effective pressure-receiving area (B) on a suction pressure side of the intermediate structure, as required. This allows to obtain desired ''differential pressure crank pressure characteristics'' according to the specifications of the control valve. Changes in the effective pressure-receiving areas have almost no influence on ''electric current differential pressure characteristics'', i.e. the relationship between the value of the supplied electric current and the differential pressure (Pd-Ps), and hence it is possible to realize the changes in the effective pressure-receiving areas with ease.
Description
Technical field
The present invention relates to a kind of control valve that is used for variable displacement compressor, particularly relate to a kind of like this control valve that is used for variable displacement compressor, be used to control the discharge capacity of the refrigeration agent of discharging from the variable displacement compressor of car air conditioner.
Background technique
The compressor of refrigeration cycle that is used for car air conditioner is by engine-driving, and the rotating speed of this motor changes according to the running condition of vehicle, therefore can not carry out rotating speed control.In order to eliminate this inconvenience, employing can change the variable displacement compressor of the discharge capacity of refrigeration agent usually, so that can obtain enough refrigerating capacities under the situation that is not subjected to the engine speed restriction.
In typical variable displacement compressor, wobbler is arranged in the crankcase of airtight formation, like this, its angle of inclination can change, and drive to carry out oscillating motion by rotatablely moving of running shaft, and along refrigeration agent being sucked the relevant cylinder from suction chamber, compress this refrigeration agent by the oscillating motion of wobbler, then refrigerant compressed is expelled in the discharge chamber with piston that the parallel direction of running shaft moves back and forth.During this period, the angle of inclination of wobbler can change by the pressure that changes in the crankcase, thereby changes the stroke of piston, so that change the refrigeration agent discharge capacity.The control valve that is used for variable displacement compressor is controlled the variation in pressure of crankcase.
Usually, the control valve that is used for controlling changeably the discharge capacity of compressor makes the part of refrigerant decompression of discharging from discharge chamber with discharge pressure Pd, so that the refrigeration agent of decompression is introduced in the crankcase, and control pressure P c (crank press) in the crankcase by the volume of the cooling medium of controlling such introducing.For example, supply with foreign current, more specifically, realize control the amount of introducing refrigeration agent by method based on the swabbing pressure Ps in the suction chamber by the solenoid in being arranged on control valve (being used for controlling the actuating of the valve element of this control valve).In the method, this control valve sensing swabbing pressure Ps, and control with discharge pressure Pd and introduce the flow velocity of the refrigeration agent in the crankcase from discharge chamber, thereby swabbing pressure Ps is remained on predeterminated level.The value of swabbing pressure Ps can freely be provided with according to supplying with solenoidal magnitude of current when waiting to begin the variable displacement operation.
But, for as above-mentionedly carry out volume control according to swabbing pressure Ps, must arrange a compliant member versatilely, for example barrier film or bellows are used for the swabbing pressure Ps of sensing control valve, this will make that the ratio (scale) of control valve is relatively large.
In order to eliminate this inconvenience, adopt other method sometimes, this method is controlled (hereinafter, this control is called " control of Pd-Ps pressure difference ") according to the pressure difference (Pd-Ps) between discharge pressure Pd and swabbing pressure Ps.In this Pd-Ps pressure difference control, the pressure difference (Pd-Ps) of sensing between discharge pressure Pd and swabbing pressure Ps, and control with discharge pressure Pd and introduce the flow velocity of the refrigeration agent in the crankcase, thereby make pressure difference (Pd-Ps) remain on predeterminated level from discharge chamber.The control valve that is used for this controlling method is arranged to like this, promptly, make the intermediate (intermediate) (this intermediate for example comprises valve element and piston rod) be used to receive discharge pressure Pd the effective pressure receiving area, be equal to each other with the effective pressure receiving area of the intermediate that is used to receive swabbing pressure Ps, thereby payment is applied to the crank press Pc on the intermediate.By this structure, no matter crank press Pc how, the pressure difference (Pd-Ps) that the valve portion of control valve all passes through between discharge pressure Pd and swabbing pressure Ps (is for example carried out opening, referring to Japanese unexamined patent publication No. communique (spy opens) No.2003-328936, [0040] section to [0045] section, Fig. 3).
According to the control valve that is used for above-mentioned controlling method, discharge pressure Pd and swabbing pressure Ps are directly received by the valve element that is used for the pressure difference of sensing between them, therefore can omit above-mentioned compliant member.Particularly, because discharge pressure Pd by direct sensing, therefore can in the light of actual conditions react the variation in pressure of variable displacement compressor, but therefore volume control is realized on good response ground.
As mentioned above, at first, no matter crank press Pc how, carries out the control of Pd-Ps pressure difference according to the current value that is applied on the solenoid, thereby the pressure difference (Pd-Ps) between discharge pressure Pd and the swabbing pressure Ps is remained on predeterminated level.But, in fact, crank press Pc increases by boost pressure poor (Pd-Ps), and reversibly, pressure difference (Pd-Ps) also will be in the mode of the influence that is subjected to variations such as crank press Pc to a certain extent and changed.More particularly, when crank press Pc increased, pressure difference (Pd-Ps) for example increased with very little slope.
Although this phenomenon may be unsatisfactory when only considering the feature of control valve, when consider that the Pd-Ps pressure difference is controlled and the control of variable displacement compressor between coupling the time general such was the case with.More specifically, when pressure difference (Pd-Ps) is increased to a fixed value immediately in response to the variation of supplying with solenoidal current value, valve portion is opened immediately, and this has strengthened the response of the wobbler of variable displacement compressor, but can cause vibration or toning sometimes when volume is controlled.This makes and is difficult to stably carry out volume control.On the other hand, when pressure difference (Pd-Ps) when slowly raising, the response variation of wobbler.And even for identical current value, the value of pressure difference to be controlled (Pd-Ps) also changes along with the value of crank press Pc.This causes the hysteresis of volume control sometimes, and therefore the control for variable displacement compressor is not preferred.Therefore, preferably make pressure difference (Pd-Ps) raise with suitable response (slope) according to current value.For example, when the wobbler of variable displacement compressor is difficult to motion, need to increase response, so that improve the motion of wobbler, and when wobbler moves especially easily, need to reduce response, so that stablize the motion of wobbler.
For this reason, usually for example by change the feature that is used for promoting the spring of valve element according to the required feature of control valve along its moving direction, perhaps change solenoidal attraction force feature, regulate the influence degree (slope) that crank press Pc changes pressure difference (Pd-Ps).But, when the feature of spring or solenoidal attraction force feature such as above-mentioned variation, pressure difference feature (that is, in the relation of supplying with between solenoidal current value and the pressure difference (Pd-Ps)) also can change, and this makes and is difficult to carry out the overall adjustment operation.
Summary of the invention
The present invention considers the problems referred to above and makes, and the purpose of this invention is to provide a kind of control valve that is used for variable displacement compressor, this control valve is based on Pd-Ps pressure difference controlling method, the indicatrix that the indicatrix of the influence degree that this control valve can be easily changes the pressure difference between discharge pressure and swabbing pressure about crank press is set to expect.
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 is installed in this variable displacement compressor, be used for controlling the pressure of the crankcase of this compressor, thereby change the discharge capacity of refrigeration agent, it comprises: body, it has the discharge pressure mouth of the discharge pressure that is used to introduce compressor, be used for to pass to the crank press mouth of crankcase at the crank press that control valve produces, and the suction pressure port that is used to introduce swabbing pressure, and this discharge pressure mouth, crank press mouth and suction pressure port begin to be disposed in order from an end of this body; The valve element, it is towards being arranged on the valve seat motion between discharge pressure mouth and the crank press mouth and leaving this valve seat motion, be used for reducing the discharge pressure of introducing from the discharge pressure mouth, to produce crank press by the throttling passage that is formed between valve element and the valve seat; Axle, it supports the valve element along the direction that valve is opened or valve cuts out, and can operate ordinatedly with the valve element; And solenoid, it is connected with an end opposite with the discharge pressure mouth of described body, and comprise core, plunger and solenoid, this plunger can be made one with the valve element by described axle, and this solenoid is used to switch on so that produce the magnetic circuit that comprises plunger and core, wherein, by be adjusted in intermediate be used to receive the effective pressure receiving area of discharge pressure and intermediate be used to receive difference between the effective pressure receiving area of swabbing pressure, regulate the influence degree that crank press changes the pressure difference between discharge pressure and swabbing pressure, this intermediate forms by the valve element is made one each other with axle.
Should be noted in the discussion above that and introduced feature " plunger can be made one with the valve element by described axle " here, this plunger must directly not be connected with this axle, but can be connected with axle by separating the insertion object that forms with this.
By below in conjunction with the description of the drawings, will know above and other objects of the present invention, feature and advantage, this accompanying drawing shows the preferred embodiments of the present invention in the mode of example.
Description of drawings
Fig. 1 is the sectional view of expression according to the structure of the control valve embodiment of the invention, that be used for variable displacement compressor.
Fig. 2 is the local amplification view on top of the control valve of Fig. 1.
Fig. 3 A to 3C is the plotted curve that is used to explain the pressure difference crank press feature of the control valve that is used for variable displacement compressor.
Embodiment
Introduce embodiments of the invention below with reference to the accompanying drawings in detail.
Fig. 1 is the sectional view of expression according to the structure of control valve present embodiment, that be used for the variable volume compressor, and Fig. 2 is the local amplification view on top of the control valve of Fig. 1.
At first with reference to figure 1, this control valve is introduced the part refrigeration agent of discharging from unshowned variable displacement compressor, and in the refrigeration agent inflow crankcase that allows to be introduced, controls its flow velocity simultaneously.Be assembled into one and form this control valve by valve being formed part 1 and solenoid 2, this valve forms part 1 and comprises the valve portion that is used to regulate the refrigeration agent flow velocity, and this solenoid 2 is used to control the valve stroke of this valve portion.
Valve forms part 1 to have: the cylindrical upper portion body 3 of stepped shape hollow, and it has open upper end, defines the discharge pressure mouth 4 that is communicated with the discharge chamber of compressor in this open upper end, is used to receive discharge pressure Pd; And filter 5, its mode with the open upper end of covering top body 3 is covered on top body 3.Discharge pressure mouth 4 is communicated with crank press mouth 6 at the sidepiece split shed of the core of top body 3.This crank press mouth 6 is communicated with the crankcase of compressor, and pressure (crank press) Pc that is used for being controlled passes to crankcase.And, suction pressure port 7 is at the sidepiece split shed of the bottom of top body 3, be used for being communicated with so that introduce swabbing pressure Ps with the suction chamber of compressor, and the coolant channel that is connected with suction pressure port 7 becomes downwards its direction in top body 3, so that be opened in the lower end surface of top body 3.
Crankcase is communicated with in the top that chamber 8 is formed at top body 3 and between discharge pressure mouth 4 and crank press mouth 6, and it is full of crank press Pc.Lower central at top body 3 is formed with bullport 9, and the lower central that this bullport 9 passes top body 3 extends axially, and is used to make axle (back will be introduced) to insert wherein, so that guide this axle.Bullport 9 by in the top opening and is communicated with chamber 8 connections with crank.
Valve seat with cylindrical shape of stepped shape hollow forms parts 10, is arranged in the top of top body 3 in the mode of inserting in the crankcase connection chamber 8.
As shown in Figure 2, the upper end periphery that valve seat forms parts 10 press fit in the open upper end of top body 3, and the valve seat bottom that forms parts 10 passes crankcase and be communicated with chamber 8 and extend downwards, and diameter is owing to step reduces.This reduced diameter portion branch has root, and this root is formed with intercommunicating pore 11, is used for valve seat formed between parts 10 inside and outside being communicated with.And the bosom that valve seat forms parts 10 partly is formed with valve opening 12, and like this, space on discharge chamber's side and the space on crankcase side communicate with each other, and the edge of opening of the valve opening on crankcase side 12 forms valve seat 13.
Valve element 14 with can before and after the mode of axial motion be arranged in valve seat and form in the lower openings of parts 10.Valve element 14 comprises: holder 15, and it can form the inwall slip of parts 10 along valve seat; And ball 16, it press fit in the upper end core of holder 15.The diameter of the upper periphery of holder 15 reduces, and spring 17 is assemblied on this reduced diameter portion branch.Spring 17 is plugged in valve seat and forms between parts 10 and the holder 15, is used for along lifting off a seat 13 direction pushes ball 16.And the sidepiece of holder 15 is formed with intercommunicating pore 15a, and this intercommunicating pore 15a is used for and will be communicated with between holder 15 inside and outside.Ball 16 is operated ordinatedly with holder 15, and like this, it can rest against on the valve seat 13.The discharge pressure Pd that introduces from discharge pressure mouth 4 is owing to be depressurized by the throttling passage between ball 16 and valve seat 13, thereby produces crank press Pc.
Again with reference to figure 1, axle 18 with can before and after the mode of axial motion insert in the bullport 9 of top body 3.One end of axle 18 extends through holder 15, so that against this ball 16, and the other end extends downwards from top body 3.
As mentioned above, do not pass through ball 16 against valve element 14 because axle 18 is by holder 15, this ball 16 is arranged in the place ahead of holder 15, and axle 18 passes this holder 15 and extends, and therefore, valve element 14 works according to the principle of balance toy.Therefore as a result, suppress the transverse movement of valve element 14, and made axial motion before and after the steady state that valve element 14 can reduce with transverse load wherein.And because the transverse load that produces on valve element 14 by the axial motion of valve element 14 reduces, so the sluggishness of the opening and closing feature of control valve reduces, and suppressed the lateral displacement of valve element 14.Therefore, valve element 14 is closed fully.
The upper, open end of lower body 19 engages with the bottom of top body 3 by ca(u)lk, and the core 20 of solenoid 2 is threaded on the lower end of top body 3.Core 20 has the center hole 21 that passes it and axially form, and the top of core 20 is formed with: from the intercommunicating pore 22 of periphery extension to be communicated with center hole 21; And the intercommunicating pore 23 that is opened on the upper end of core 20, and an end of this intercommunicating pore 23 and coolant channel (it links to each other with suction pressure port 7) connection, and its other end is communicated with intercommunicating pore 22.By this structure, swabbing pressure Ps is received by the end of axle 18.
Sleeve 24 is arranged in the lower body 19.The retainer 25 of lid form is assemblied in the lower openings of sleeve 24, and as shown in Figure 1, and ring-shaped bearing parts 26 press fit in the interior week of retainer 25.And the core 20 and the plunger 27 that are threaded on the top body 3 are arranged in the sleeve 24.Plunger 27 is rigidly fixed on the axle 28, and this end of 28 extends through core 20 and enters in the opening of top body 3 lower ends, so that be bearing in this place, its other end is by support unit 26 supportings.Plunger 27 is limited by the stop ring 29 that is assemblied on the axle 28 towards the motion of axle 18.This make plunger 27 can not with situation that sleeve 24 contacts under before and after axial motion.And spring 30 is plugged between core 20 and the plunger 27, and spring 31 is plugged between plunger 27 and the support unit 26.
Along the housing 34 that the periphery of sleeve 24 is furnished with yoke 32, solenoid 33 and surrounds this yoke 32 and solenoid 33, they have constituted solenoid 2 with core 20 and plunger 27.Handle 36 (wire harness 35 passes this handle 36 and inserts) is assemblied in the bottom of housing 34, with the lower end of sealing solenoid 2.
Below in conjunction with the operation of variable displacement compressor, introduce the operation of the control valve that is used for variable displacement compressor.
In this control valve, the discharge pressure Pd of the refrigeration agent of introducing from discharge chamber acts on from above on the ball 16, as shown in Figure 1.On the other hand, introduce swabbing pressure Ps the central opening 21 from suction chamber, act on the axle 18 that leans with ball 16 from below by the gap between top body 3 and axle 28, as shown in Figure 1 by suction pressure port 7 and intercommunicating pore 23,22.Therefore, if the diameter of axle 18 diameter (that is, the diameter of bullport 9) and valve opening 12 is equal to each other, then the effective pressure receiving area that is used to receive swabbing pressure Ps that is used to receive the effective pressure receiving area of discharge pressure Pd and axle 18 of ball 16 is equal to each other.Therefore, the crank press Pc that is applied to by valve element 14 and axle 18 are made on the intermediate that one forms each other will offset, and be used to control the ball 16 formation pressure difference limens that flow into the refrigeration agent flow velocity in the crankcase from discharge chamber, it is operated by the pressure difference of sensing between discharge pressure Pd and swabbing pressure Ps.But, in the present embodiment, difference between above-mentioned effective pressure receiving area is for example regulated by of only increasing in them, thereby regulate about the indicatrix (pressure difference crank press indicatrix) of crank press, thereby make them become the indicatrix of hope the influence degree of the variation of the pressure difference between discharge pressure and the swabbing pressure.To introduce this adjusting below.
Be used for the control valve of variable displacement compressor, when not when electric currents are controlled in solenoid 33 supplies of solenoid 2, discharge pressure Pd promotes to open ball 16, so that ball 16 is in full open position.As a result, in this compressor, crank press Pc becomes more near discharge pressure Pd, thereby the difference between the relevant pressure on the opposite end that puts on each piston (this piston is arranged in the mode in the face of crankcase, is used for suction and compressed refrigerant) becomes minimum.This makes being used in the crankcase determine that the wobbler of stroke of piston has and makes the tilt angle of stroke minimum, thereby makes compressor come work with minimum injection rate or volume.
And when when the solenoid 33 of solenoid 2 is supplied maximum controlling current, plunger 27 is subjected to the attraction of core 20 and moves upward, and as shown in Figure 1, thereby axle 28 and 18 is pushed upwardly, as shown in Figure 1, so that ball 16 is in buttoned-up status.At this moment, refrigeration agent can be by unshowned fixed hole and from crankcase (this crankcase by this fixed hole and is communicated with suction chamber) inflow suction chamber, thereby makes crank press Pc be decreased to value near the swabbing pressure Ps in the suction chamber.This makes the difference maximum between the pressure on the opposite end be applied to each piston, thereby wobbler is had make the angle of inclination of stroke of piston maximum, and compressor is transformed into maximum volume work thus.
At this moment, when normally controlling with to the solenoid 33 supply predetermined control electric currents of solenoid 2 time, plunger 27 is attracted by core 20 according to the size of control electric current, and this core 20 produces the power that is used to make the prearranging quatity that plunger 27 moves upward, as shown in Figure 1.This masterpiece is the setting value effect of control valve, and this control valve is operated as defferential valve.Therefore, the pressure difference of this control valve sensing between discharge pressure Pd and swabbing pressure Ps, and the flow velocity of the refrigeration agent of control from discharge chamber's inflow crankcase, thereby, pressure difference is remained on and the corresponding value of being set by solenoid 2 of setting value.
To introduce the method for the pressure difference crank press indicatrix of regulating the above-mentioned control valve that is used for variable displacement compressor below.
In the present embodiment, this control valve is configured to the pressure difference crank press indicatrix that the difference between the effective pressure receiving area B of swabbing pressure side that can be by effective pressure receiving area A on the discharge pressure side that is adjusted in intermediate (this intermediate is made one each other and formed by making valve element 14 and axle 18) and intermediate obtains to wish, as shown in Figure 2.Should be known in that the effective pressure receiving area A on the discharge pressure side can regulate by the diameter of regulating valve opening 12, and can regulate by the diameter (that is the diameter of bullport 9) of adjusting axle 18 at the effective pressure receiving area B of swabbing pressure side.Fig. 3 A to Fig. 3 C is the plotted curve that is used to explain the pressure difference crank press indicatrix of control valve, wherein, Fig. 3 A represents the situation when effective pressure receiving area A and effective pressure receiving area B are equal to each other, Fig. 3 B represents the situation during less than effective pressure receiving area B as effective pressure receiving area A, and Fig. 3 C represents the situation during greater than effective pressure receiving area B as effective pressure receiving area A.
With reference to figure 3A, when when the effective pressure receiving area A on the discharge pressure side and the effective pressure receiving area B on the swabbing pressure side are equal to each other, even when being supplied to solenoidal current value fixedly, what the pressure difference (Pd-Ps) between discharge pressure Pd and swabbing pressure Ps also can be at crank press Pc influences the end microvariations.Pressure difference (Pd-Ps) changes along with the range value (Isol) of the electric current that is supplied to solenoid 2.
More specifically, be equal to each other at the effective pressure receiving area A of discharge pressure side with at the effective pressure receiving area B of swabbing pressure side, like this, at first crank press Pc will be cancelled, and pressure difference (Pd-Ps) will be predetermined value, and no matter crank press Pc how, but in fact, be difficult to eliminate fully the influence of crank press Pc, and in indicatrix, shown as gradient a little, as shown in Figure 3A.
With reference to figure 3B, when effective pressure receiving area A being set at less than effective pressure receiving area B, the effect balance of crank press Pc on intermediate (this intermediate forms by making valve element 14 and axle 18 make one each other) will lose, and become big along the crank press Pc effect degree that valve is opened direction.This makes that valve portion is easier to open.As a result, pressure difference (Pd-Ps) raises fast, and compares when being equal to each other with effective pressure receiving area B with effective pressure receiving area A, and the influence of crank press Pc is littler, and this has improved the response of the wobbler of compressor.
With reference to figure 3C, when effective pressure receiving area A being set at greater than effective pressure receiving area B, the effect balance of crank press Pc on intermediate (this intermediate forms by making valve element 14 and axle 18 make one each other) will lose, and become big along the effect degree of the crank press Pc of valve closing direction.This makes that valve portion is more difficult and opens.As a result, pressure difference (Pd-Ps) slowly raises, and compares when being equal to each other with effective pressure receiving area B with effective pressure receiving area A, and the influence of crank press Pc is bigger, and this has reduced the response of the wobbler of compressor.
As mentioned above, by being adjusted in the difference between effective pressure receiving area A and the effective pressure receiving area B, can change the pressure difference crank press indicatrix of control valve.Therefore, for example when comparing the response of the wobbler of wishing special raising compressor with the indicatrix of general control valve, only control valve need be configured such that effective pressure receiving area A is less than effective pressure receiving area B.On the contrary, when wishing to reduce the response of wobbler, only control valve need be configured such that effective pressure receiving area A is greater than effective pressure receiving area B when comparing with the indicatrix of general control valve.
As mentioned above, in control valve according to the present invention, be adjusted in the difference between the effective pressure receiving area B on the swabbing pressure side of effective pressure receiving area A on the discharge pressure side of intermediate (make one each other and form) and intermediate as required by making valve element 14 and axle 18.This feasible pressure difference crank press indicatrix that can obtain to wish according to the specification of control valve.The variation of effective pressure receiving area hardly can be to electric current pressure difference indicatrix (promptly, in current value that is supplied to solenoid 2 and the relation between the pressure difference between discharge pressure Pd and the swabbing pressure Ps) exert an influence, therefore can easily change the effective pressure receiving area.
According to control valve of the present invention, can obtain desired differential pressure crank press indicatrix (about the indicatrix of crank press) by the difference between the effective pressure receiving area on the swabbing pressure side of effective pressure receiving area on the discharge pressure side that is adjusted in intermediate (forming) and intermediate by making valve element and axle make one each other to the influence degree of the variation of the pressure difference between discharge pressure and swabbing pressure.Because the variation of effective pressure receiving area hardly can be to electric current pressure difference indicatrix (promptly, be supplied to solenoidal current value and the relation between the pressure difference between discharge pressure and the swabbing pressure) exert an influence, therefore can easily obtain desired differential pressure crank press indicatrix.
Above stated specification is just introduced principle of the present invention.And, because those skilled in the art will easily know multiple variation and change, therefore shown in the present invention is not limited to and described definite structure and application, therefore, can think that all suitable modification and equivalents all will drop in the scope of the invention that is limited by claims and equivalent thereof.
Claims (4)
1, a kind of control valve that is used for variable displacement compressor, this control valve is installed in this variable displacement compressor, is used for being controlled at the pressure of the crankcase of compressor, thereby changes the discharge capacity of refrigeration agent, and it comprises:
Body, it has the discharge pressure mouth of the discharge pressure that is used for introducing compressor, the crank press that is used for producing at control valve passes to the crank press mouth of crankcase and the suction pressure port that is used to introduce swabbing pressure, and this discharge pressure mouth, crank press mouth and suction pressure port begin to be disposed in order from an end of this body;
The valve element, it is towards being arranged on the valve seat motion between discharge pressure mouth and the crank press mouth and leaving this valve seat motion, be used for reducing the discharge pressure of introducing from the discharge pressure mouth, so that produce described crank press by the throttling passage that is formed between valve element and the valve seat;
Axle, it is opened or the valve closing direction supports described valve element along valve, and can operate ordinatedly with the valve element; And
Solenoid, it is connected with an end opposite with the discharge pressure mouth of body, and comprises core, plunger and solenoid, and this plunger can be made one with the valve element by described axle, and this solenoid is used to switch on and comprises the magnetic circuit of described plunger and core with generation
Wherein, by be adjusted in intermediate be used to receive the effective pressure receiving area of discharge pressure and intermediate be used to receive difference between the effective pressure receiving area of swabbing pressure, regulate the influence degree that crank press changes the pressure difference between discharge pressure and swabbing pressure, this intermediate forms by making described valve element and axle make one each other.
2, control valve according to claim 1 is characterized in that: a crankcase is communicated with chamber and is defined between the crank press mouth and valve seat of described body, and this crankcase is communicated with chamber and is full of the crank press that produced and valve planning in wherein,
Wherein, one bullport to be being formed in the body with the coaxial mode of the valve opening that limits described valve seat, and in a side opposite with described discharge pressure mouth, and this bullport leads to crankcase and is communicated with in the chamber and described axle inserts in this bullport, this bullport is used to guide this axle
Wherein, described reel structure becomes at a side joint opposite with crankcase connection chamber of bullport to receive swabbing pressure,
Wherein, being used to of described intermediate receives the effective pressure receiving area of discharge pressure and regulates by the section area size of valve opening, and
Wherein, the effective pressure receiving area that is used to receive swabbing pressure of described intermediate is regulated by the section area size of bullport.
3, control valve according to claim 2, it is characterized in that: the effective pressure receiving area that is used to receive discharge pressure of described intermediate is arranged to the effective pressure receiving area that is used to receive swabbing pressure greater than intermediate, thereby the influence degree that described crank press changes the pressure difference between discharge pressure and swabbing pressure is than bigger when these two effective pressure receiving areas are equal to each other.
4, control valve according to claim 2, it is characterized in that: the effective pressure receiving area that is used to receive discharge pressure of described intermediate is arranged to the effective pressure receiving area that is used to receive swabbing pressure less than intermediate, thereby the influence degree that described crank press changes the pressure difference between discharge pressure and swabbing pressure is than littler when these two effective pressure receiving areas are equal to each other.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004239161A JP2006057506A (en) | 2004-08-19 | 2004-08-19 | Control valve for variable displacement compressor |
| JP2004239161 | 2004-08-19 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1737370A true CN1737370A (en) | 2006-02-22 |
| CN100436813C CN100436813C (en) | 2008-11-26 |
Family
ID=35064917
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100905620A Expired - Fee Related CN100436813C (en) | 2004-08-19 | 2005-08-17 | Control valve for variable displacement compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20060039798A1 (en) |
| EP (1) | EP1628017A3 (en) |
| JP (1) | JP2006057506A (en) |
| KR (1) | KR20060050534A (en) |
| CN (1) | CN100436813C (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008045522A (en) * | 2006-08-21 | 2008-02-28 | Toyota Industries Corp | Refrigerant flow rate detecting structure in compressor |
| JP2008121636A (en) * | 2006-11-15 | 2008-05-29 | Toyota Industries Corp | Refrigerant flow volume detecting structure in compressor |
| JP5149580B2 (en) * | 2007-09-26 | 2013-02-20 | サンデン株式会社 | Capacity control valve, capacity control system and variable capacity compressor for variable capacity compressor |
| JP6340661B2 (en) | 2014-02-27 | 2018-06-13 | 株式会社テージーケー | Control valve for variable capacity compressor |
| JP2016020682A (en) | 2014-06-19 | 2016-02-04 | 株式会社テージーケー | Control valve for variable capacity type compressor |
| JP6340501B2 (en) | 2014-06-19 | 2018-06-13 | 株式会社テージーケー | Control valve for variable capacity compressor |
| JP2016014334A (en) | 2014-07-01 | 2016-01-28 | 株式会社テージーケー | Variable displacement compressor control valve |
| JP6528108B2 (en) | 2014-07-18 | 2019-06-12 | 株式会社テージーケー | Control valve for variable displacement compressor |
| DE102014116214B3 (en) * | 2014-11-06 | 2016-02-04 | Eto Magnetic Gmbh | Proportional valve, air conditioning compressor arrangement and operating method |
| EP3059445B1 (en) | 2015-02-23 | 2020-06-24 | TGK CO., Ltd. | Electromagnetic control valve of a variable displacement compressor |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5702235A (en) * | 1995-10-31 | 1997-12-30 | Tgk Company, Ltd. | Capacity control device for valiable-capacity compressor |
| JP3432995B2 (en) * | 1996-04-01 | 2003-08-04 | 株式会社豊田自動織機 | Control valve for variable displacement compressor |
| JP2001073939A (en) * | 1999-08-31 | 2001-03-21 | Toyota Autom Loom Works Ltd | Control valve for variable displacement compressor and variable displacement compressor |
| JP3963619B2 (en) * | 1999-11-05 | 2007-08-22 | 株式会社テージーケー | Compression capacity controller for refrigeration cycle |
| JP3943871B2 (en) * | 2001-07-25 | 2007-07-11 | 株式会社テージーケー | Variable capacity compressor and capacity control valve for variable capacity compressor |
| JP4446026B2 (en) | 2002-05-13 | 2010-04-07 | 株式会社テージーケー | Capacity control valve for variable capacity compressor |
| JP4152674B2 (en) * | 2002-06-04 | 2008-09-17 | 株式会社テージーケー | Capacity control valve for variable capacity compressor |
| JP2004137980A (en) * | 2002-10-18 | 2004-05-13 | Tgk Co Ltd | Displacement control valve for variable displacement compressor |
-
2004
- 2004-08-19 JP JP2004239161A patent/JP2006057506A/en active Pending
-
2005
- 2005-08-11 EP EP05017519A patent/EP1628017A3/en not_active Withdrawn
- 2005-08-17 US US11/205,064 patent/US20060039798A1/en not_active Abandoned
- 2005-08-17 CN CNB2005100905620A patent/CN100436813C/en not_active Expired - Fee Related
- 2005-08-18 KR KR1020050075462A patent/KR20060050534A/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| EP1628017A2 (en) | 2006-02-22 |
| JP2006057506A (en) | 2006-03-02 |
| CN100436813C (en) | 2008-11-26 |
| EP1628017A3 (en) | 2006-11-02 |
| US20060039798A1 (en) | 2006-02-23 |
| KR20060050534A (en) | 2006-05-19 |
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