CN101545553B - Pressure control valve - Google Patents
Pressure control valve Download PDFInfo
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- CN101545553B CN101545553B CN200810087715XA CN200810087715A CN101545553B CN 101545553 B CN101545553 B CN 101545553B CN 200810087715X A CN200810087715X A CN 200810087715XA CN 200810087715 A CN200810087715 A CN 200810087715A CN 101545553 B CN101545553 B CN 101545553B
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Abstract
The invention discloses a pressure control valve, which comprises a valve body (1), a high-pressure cavity (51), a low-pressure cavity (61) and a valve element (2), wherein the high-pressure cavity (51) and the low-pressure cavity (61) are arranged in the valve body (1) and are communicated by a throttling passage (7); the valve element (2) is arranged in an inner cavity (11) of the valve body (1) and can reciprocally move relative to an opening (71) which is arranged on the throttling passage (7) and faces the high-pressure cavity (51) to control the opening degree of a valve opening (71); and the high-pressure cavity (51) and the inner cavity (11) are mutually isolated through sealing and a connecting passage is arranged between the low-pressure cavity (61) and the inner cavity (11). The pressure control valve disclosed by the invention can control the change of the pressure difference between a high-pressure side and a low-pressure side of the system so as to directly control the pressure of a cooling agent of the high-pressure side.
Description
Technical field
The present invention relates to the refrigeration cycle technical field, particularly a kind of pressure controlled valve.
Background technique
The mankind are faced with more and more serious environmental problem at present, and wherein depletion of the ozone layer and greenhouse effect problem receive global concern day by day.Chloro-fluoro-hydrocarbons (the being commonly called as freon) refrigeration working medium (being refrigeration agent) that tradition is used in the cooling cycle system is the artificial-synthetic compound, evaporate into to be difficult in the atmosphere being decomposed, but can the ozone decomposition molecule, ozonosphere is done great damage.Though substitute hydrogen fluorohydrocarbon class refrigeration working medium does not damage the ozone layer, its greenhouse effect are obvious.Though the mankind can make great efforts synthetic better refrigeration working medium in the future, but take a long view, original non-existent material is produced in a large number and is used on the earth, final result is that any non-nature is so the substitute materials that has damages all may for the ecological balance of the earth, so refrigeration agent is answered back to nature, promptly enable various natural refrigeration agents,, just meet the road of sustainable development as environmental friendliness materials such as ammonia, carbon dioxide, hydrocarbon, water, air.
Carbon dioxide is a kind of natural refrigeration agent, helps environmental protection, and also the cycle performance with conventional refrigerants is suitable for carbon dioxide refrigeration circuit performance simultaneously, is therefore thought that extensively arranged huge development prospect.
The cooling cycle system that uses carbon dioxide and common chloro-fluoro-carbon kind, hydrogen fluorohydrocarbon class cooling cycle system have bigger different.Traditional compression-type refrigeration is when utilizing lower boiling liquid refrigerant (as chloro-fluoro-carbon kind, hydrogen fluorohydrocarbon class) carburation by evaporation, heat absorption realizes freezing from the medium of refrigeration space, this refrigerating method utilizes refrigeration agent gas-liquid two-phase conversion process, thereby realize constant temperature heat absorption and heat release, refrigeration agent is realized subcritical cycle in refrigeration system.But about 31 ℃ of the critical temperature of carbon dioxide, be lower than traditional artificial cooling agent, the cooling cycle system of use carbon dioxide is actually on transition point and moves, so be called overcritical circulation, to the heat release of extraneous space the time, what conventional refrigerants took place is condensation process, and the carbon dioxide refrigerating system generation is gas-cooled process.
Existing a kind of cooling cycle system of chloro-fluoro-carbon kind, hydrogen fluorohydrocarbon quasi-tradition refrigeration agent that uses comprises compressor, condenser, expansion valve and vaporizer, is connected to form circulation loop by pipeline.Usually refrigeration agent is compressed into the gas of High Temperature High Pressure by compressor, and sends into condenser, and condensation in condenser enters the evaporator evaporation of low voltage side then through expansion valve, thereby absorbs external heat.In system's running, mainly be evaporating pressure and the temperature of controlling low voltage side by expansion valve, the heat load of refrigerant flow and vaporizer is complementary, improve the working efficiency of system; For on high-tension side condenser, the condensing temperature of refrigeration agent mainly depends on the temperature and the flow of extraneous cooling medium, and condensing temperature is corresponding one by one with condensing pressure, therefore the on high-tension side pressure of expansion valve depends on the temperature and the flow of extraneous cooling medium basically, does not need to control specially in system.
For carbon dioxide refrigerating system, carry out overcritical circulation, in the generation of high pressure side refrigeration agent is not condensation process, but gas cooling process, its pressure and temperature is not corresponding one by one, but two variablees independently, although the carbon dioxide chilling temperature is subjected to the temperature and the flow restriction of extraneous cooling medium, pressure then directly is not restricted.On the one hand, in the supercritical carbon dioxide refrigeration system, on high-tension side Pressure characteristics has very big influence for the refrigerating efficiency of system; On the other hand, high side pressure can reach 70-150bar, is 7-10 times of refrigeration plant commonly used, and the reduction of the compressor capacity that the increase of pressure will cause decreases refrigerating capacity, and pressure further is increased to abnormal level, even can cause the shutdown of compressor.Therefore no matter be, different with common subcritical cycle refrigeration system from refrigerating efficiency or from security consideration, in the supercritical carbon dioxide refrigeration system, the device of directly high side pressure being regulated need be set.
Summary of the invention
The problem that the present invention solves provides a kind of pressure controlled valve, and this pressure controlled valve is used for the supercritical refrigeration cycle system, can directly control on high-tension side refrigerant pressure.
For addressing the above problem, the invention provides a kind of pressure controlled valve, comprising: valve body 1; High-pressure chamber 51 and the low-pressure chamber 61 that are provided with in the valve body 1 by 7 connections of throttling path; The spool 2 that is provided with in the inner chamber 11 of valve body 1, described spool 2 can come and go and move with respect to the valve port 71 to high-pressure chamber 51 driveed on the throttling path 7, to control the folding degree of described valve port 71; Isolated each other between described high-pressure chamber 51 and the inner chamber 11 by sealing, be provided with connecting path 8 between described low-pressure chamber 61 and the inner chamber 11; The parallel axes of the axis of described connecting path 8 and spool 2, and the distance between the axis of the axis of described connecting path 8 and spool 2 is greater than the maximum radius of spool 2, and connecting path 8 is communicated with the diapire of described inner chamber 11 towards an end of described inner chamber 11.
Preferably, described connecting path 8 is the bypass through hole, and the scope of its internal diameter is 0.8mm to 4mm.
Preferably, be provided with sealed member 9 between described high-pressure chamber 51 and the inner chamber 11.
Preferably, described sealed member 9 is a seal ring.
Preferably, comprise also spring 3 in the described inner chamber 11, that an end and spool 2 connect is set that the thrust of spring 3 is in spool 2.
Preferably, the other end of described spring 3 is provided with by being threaded in the spring adjustment seat 4 in the inner chamber 11, can regulate described spring 3 and be applied to thrust size on the described spool 2.
Preferably, the end of described spool 2 is taper, can come and go to move the area of passage that changes valve port in valve port 71.
Preferably, described spool 2 is provided with at least one groove 22, is provided with sealed member 9 ' in the described groove 22.
Preferably, described sealed member 9 ' is a seal ring.
Compared with prior art, the present invention has the following advantages: described pressure controlled valve comes down to make low-pressure chamber 61 identical with the refrigerant pressure of inner chamber 11 by connecting path, that is: the refrigerant pressure in the low-pressure chamber is introduced inner chamber, the state of equilibrium that the thrust of the refrigerant pressure by acting on the high-pressure chamber on the spool and the difference Δ F of the refrigerant pressure in the low-pressure chamber and spring reaches, regulate the area of passage between needle and the valve port, when on high-tension side pressure increases, increase the area of passage, make high-pressure chamber's step-down; When on high-tension side pressure reduces, reduce the area of passage, make high-pressure chamber's supercharging, thereby directly control the refrigerant pressure in the high-pressure chamber.Pressure controlled valve of the present invention is placed between the cooler outlet side and evaporator side of supercritical refrigeration cycle system, the difference of inflow evaporator pressure is come the on high-tension side pressure of control system after refrigerant pressure that can flow out according to cooler and the throttling expansion.
In addition, because the control unit of valve directly comes from the pressure and the difference of the pressure of low-pressure port and the balance of the formation of the spring thrust in the valve body of high pressure port, so the pressure control characteristic of valve and the temperature of refrigeration agent are irrelevant, just be not subjected to externally temperature influence yet, therefore can directly control on high-tension side pressure, the good reliability of control.
Description of drawings
By the more specifically explanation of the preferred embodiments of the present invention shown in the accompanying drawing, above-mentioned and other purpose, feature and advantage of the present invention will be more clear.Reference character identical in whole accompanying drawings is indicated identical part.Painstakingly do not draw accompanying drawing in proportion, focus on illustrating purport of the present invention.
Fig. 1 is a supercritical refrigeration cycle system schematic in the embodiment of the invention;
Fig. 2 is the structural representation of pressure controlled valve in the embodiment of the invention one;
Fig. 3 is the spool stress schematic representation among Fig. 1;
Fig. 4 is the schematic representation of Regulation spring seat in the embodiment of the invention one;
Fig. 5 is the structural representation of pressure controlled valve in the embodiment of the invention two;
Fig. 6 is the operative position schematic representation of bypass through hole in the embodiment of the invention two;
Fig. 7 is the structural representation of pressure controlled valve in the embodiment of the invention three.
Symbol description among the figure:
1: valve body, 11: inner chamber, 11a: lumen orifice;
2: spool, 21: needle, 22: groove, 23: spool end;
3: spring;
4: the spring adjustment seat;
5: high pressure port, 51: high-pressure chamber;
6: low-pressure port, 61: low-pressure chamber;
7: throttling path, 71: valve port;
8,8 ', 8 ": the bypass through hole;
9,9 ': sealed member;
10: compressor;
20: gas cooler;
30: inner heat exchanger;
40: pressure controlled valve;
50: vaporizer;
60: gas-liquid separator;
70: pipeline.
Embodiment
For above-mentioned purpose of the present invention, feature and advantage can be become apparent more, the specific embodiment of the present invention is described in detail below in conjunction with accompanying drawing.
A lot of details have been set forth in the following description so that fully understand the present invention.But the present invention can implement much to be different from alternate manner described here, and those skilled in the art can do similar popularization under the situation of intension of the present invention.Therefore the present invention is not subjected to the restriction of following public concrete enforcement.
Described schematic representation is an example, and it should not limit the scope of protection of the invention at this.
Be the embodiment that background discloses pressure controlled valve of the present invention with the supercritical carbon dioxide cooling cycle system below.
Fig. 1 is a supercritical refrigeration cycle system schematic in the embodiment of the invention.As shown in Figure 1, with the circular flow of refrigeration agent (carbon dioxide) to being order, described supercritical carbon dioxide cooling cycle system comprises: compressor 10, cooler 20, heat exchanger 30, pressure controlled valve 40, vaporizer 50 and gas-liquid separator 60, connect into the closed-loop path with pipeline 70, finishing with the carbon dioxide is the refrigeration cycle process of refrigeration agent.
The refrigeration agent that compressor 10 is used for sucking compresses; Cooler 20 is used for making refrigerant cools after compressor 10 compression by the heat exchange between cooling medium and refrigeration agent; Heat exchanger 30 is used to make the refrigeration agent of cooler 20 outlet sides and the refrigeration agent of vaporizer 50 outlet sides to carry out heat exchange, improves refrigerating efficiency; The high pressure port 5 of pressure controlled valve 40 is by the outlet side of heat exchanger 30 connection coolers 20, and low-pressure port 6 connects the suction side of vaporizers 50, is used to control the refrigerant pressure of heat exchanger 30 outlet sides, also is the pressure of cooler 20 outlet sides; Vaporizer 50 is used for the gas-liquid attitude refrigeration agent of the two-phase after the 40 throttling step-downs of evaporating pressure control valve, absorbs heat from cooling space; Gas-liquid separator 60 is arranged between the outlet side and heat exchanger 30 of vaporizer 50, is used for gaseous refrigerant is separated with liquid refrigerant and the unnecessary refrigeration agent of interim storage refrigeration cycle; Refrigeration agent through heat exchange in heat exchanger 30 flows into compressor 10 again, finishes the refrigeration cycle process.
Embodiment one
Fig. 2 is the structural representation of the pressure controlled valve of preferred version of the present invention.As shown in Figure 2, described pressure controlled valve 40 comprises: valve body 1; The high-pressure chamber 51 and the low-pressure chamber 61 that are provided with in the valve body 1, high-pressure chamber 51 and low-pressure chamber 61 are connected by throttling path 7, the high pressure port 5 of high-pressure chamber 51 connects the outlet side of cooler 20 by heat exchanger 30, the low-pressure port 6 of low-pressure chamber 61 connects the suction side of vaporizer 50, is provided with sealed member between high-pressure chamber 51 and the inner chamber 11; Be provided with spool 2 in the inner chamber 11 of valve body 1; Valve port 71 is positioned on the throttling path 7 and drives to high-pressure chamber 51; Spool 2 comes and goes when mobile with respect to valve port 71, and the end of its taper is that needle 21 comes and goes valve port 71 in and moves, thus the folding degree of control valve port 71, and adjusting is by the area of passage of refrigeration agent.
Be provided with connecting path between described low-pressure chamber 61 and the inner chamber 11 and be the bypass through hole 8 (for the major avenues of approach throttling path 7 of refrigeration agent, being bypass) among Fig. 2, make low-pressure chamber 61 identical, that is: the pressure in the low-pressure chamber 61 is introduced inner chamber 11 and act on the spool 2 with the refrigerant pressure of inner chamber 11; The axes intersect of the axis of bypass through hole 8 and spool 2, and between an angle R is arranged, the one end is driveed to low-pressure chamber 61, the other end is opened to inner chamber 11.Be provided with the spring 3 that an end and spool 2 connect in the inner chamber 11, the thrust of spring 3 is in spool 2, and the other end of spring is provided with spring adjustment seat 4, is connected with inner chamber 11 by screw thread.
Seal by the sealed member 9 in the groove 22 that is arranged on spool 2 between high-pressure chamber 51 and the inner chamber 11, spool 2 comes and goes when mobile with respect to valve port 71, the sealing that sealed member 9 guarantees between inner chamber 11 and the high-pressure chamber 51, simultaneously, also be provided with sealed member 9 ' on the spring adjustment seat 4, when guaranteeing the thrust of Regulation spring 3, inner chamber 11 is with respect to extraneous good seal.
Described pressure controlled valve 40 has the function of throttling, when valve port 71 is opened, in the low-pressure chamber 61 that enters low voltage side under the action of pressure by on high-tension side high-pressure chamber 51 after through the 7 throttling step-downs of throttling paths, enter vaporizer 50 evaporations then through refrigeration agent that heat exchanger 30 flows out from extraneous cooling space heat absorption.
Fig. 3 is the described spool stress of a present embodiment schematic representation.Ignored among the figure spool gravity and with the frictional force of sidewall.As shown in Figure 3, bypass through hole 8 makes low-pressure chamber 61 identical with the refrigerant pressure of inner chamber 11, that is: the refrigerant pressure in the low-pressure chamber 61 is introduced in the inner chamber 11 of sealing by above-mentioned bypass through hole 8, therefore the refrigerant pressure F1 in the inner chamber 11 and the thrust F2 acting in conjunction of spring 3 are pushed spool 2 to valve port 71, needle 21 is had go deep into the trend that valve port 71 reaches the minimizing flow area; Refrigeration agent in the high-pressure chamber 51 then applies opposite power F3 on spool 3, make the needle 21 of taper that the trend that reaches the increase flow area away from valve port 71 be arranged.
During system works, under the refrigerant pressure F3 in high-pressure chamber 51 and the thrust F2 acting in conjunction of refrigerant pressure F1 in the inner chamber 11 and spring, needle 21 on the spool 2 gos deep into certain distance in the valve port 71, at this moment, above-mentioned three power that act on the spool 2 reach state of equilibrium, be F3=F2+F1, form certain flow area between between needle 21 and the valve port 71, refrigeration agent in the high-pressure chamber 51 enters in the low-pressure chamber 61 through the valve port 71 with above-mentioned area of passage degree, flows to vaporizer 50 from low-pressure port 6.
When the pressure difference Δ F of refrigerant pressure F3 in the high-pressure chamber 51 and the refrigerant pressure F1 in the inner chamber 11 increases, be that F3-F1 becomes greatly, the equilibrium of forces state that acts on the spool 2 changes, when being F3＞F2+F1, needle 21 moves to the direction away from valve port 71, valve port 71 flow areas increase, thereby the refrigerant flow that flows through throttling path 7 increases, on high-tension side refrigerant pressure F3 is reduced, finally make the thrust F2 sum of refrigerant pressure F1 in the inner chamber 11 and spring 3 equal refrigerant pressure F3 in the high-pressure chamber 51 again, be F3=F2+F1, reach new state of equilibrium; When the pressure difference Δ F of refrigerant pressure F3 in the high-pressure chamber 51 and the refrigerant pressure F1 in the low-pressure chamber 61 reduces, that is: F3-F1 diminishes, the equilibrium of forces state that acts on the spool 2 changes, when being F3＜F2+F1, tapered needle 21 is to valve port 71 medial movement, valve port 71 flow areas reduce, thereby the refrigerant flow that flows through throttling path 7 reduces, on high-tension side refrigerant pressure F3 is increased, finally make the thrust F2 sum of refrigerant pressure F1 in the low-pressure chamber 61 and spring 3 equal refrigerant pressure F3 in the high-pressure chamber 51 again, be F3=F2+F1, reach new state of equilibrium.
Therefore, described pressure controlled valve comes down to make low-pressure chamber 61 identical with the refrigerant pressure of inner chamber 11 by bypass through hole 8, that is: the refrigerant pressure F1 in the low-pressure chamber 61 is introduced inner chamber 11, the state of equilibrium that the thrust F2 of the refrigerant pressure F3 by acting on the high-pressure chamber 51 on the spool 2 and the difference Δ F of the refrigerant pressure F1 in the low-pressure chamber 61 and spring 3 reaches, regulate the area of passage between needle 21 and the valve port 71, thereby directly control the refrigerant pressure in the high-pressure chamber 51.When pressure F3 increases, increase the area of passage, make high-pressure chamber's step-down; When pressure F3 reduces, reduce the area of passage, make high-pressure chamber's supercharging.
In addition, the thrust F2 size that described spring 3 acts on the spool 2 can be regulated, as shown in Figure 4, spring 3 one ends spring adjustment seat 4 is set, by Regulation spring adjustment seat 4 and relative position spring 3, promptly change the distance H of Fig. 4 medi-spring adjustment seat bottom and spool 2, then change described spring 3 and be applied to thrust F2 size on the described spool 2, thereby further change refrigerant pressure F3 in the described high-pressure chamber 51 of pilot pressure and the pressure difference Δ F of the refrigerant pressure F1 in the low-pressure chamber 61.The thrust F2 size that Regulation spring 3 acts on the spool 2 also can be in other way.
When occurring flow or pressure surge for making in the loop of cooling cycle system, the refrigerant pressure in the inner chamber 11 can in time reflect the variation of refrigerant pressure in the system, and the inside diameter D of bypass through hole 8 can not be too little; If but inside diameter D is excessive, as shown in Figure 2, because the opening of bypass through hole 8 in inner chamber 11 is over against spool 2, the refrigeration agent that flows out from bypass through hole 8 also can produce certain impact to spool 2, influence the state of equilibrium of spool 2, therefore in an embodiment of the present invention, the inside diameter D of described bypass through hole 8 is comparatively suitable in the 0.8mm-4mm scope, can reflect in time that the variation of refrigerant pressure in the system can not impact to spool because of flow is excessive again.
The above pressure controlled valve is because the control unit of valve directly comes from the pressure and the difference of the pressure of low-pressure port and the balance of the formation of the spring thrust in the valve body of high pressure port, so the pressure control characteristic of valve and the temperature of refrigeration agent are irrelevant, just be not subjected to externally temperature influence yet, therefore can directly control on high-tension side pressure, the good reliability of control.
In fact, the described pressure controlled valve of the embodiment of the invention can also be a preferred construction more, in case fluid stopping goes out the refrigeration agent of bypass through hole 8 spool 2 is produced certain impact, influences the state of equilibrium of spool 2, and then influence its pressure control characteristic, specifically in following examples, illustrate.
Embodiment two
Be provided with bypass through hole 8 ' between described low-pressure chamber 61 and the inner chamber 11, the pressure in the low-pressure chamber 61 introduced inner chamber 11 act on the spool 2, the axes intersect of the axis of bypass through hole 8 ' and spool 2 and between an angle R is arranged.Be with the difference of the pressure controlled valve shown in the embodiment one, an end of bypass through hole 8 is opened to inner chamber 11 among the embodiment one, its opening spool 2 moves to any position all facing to spool 2, and in the present embodiment, under the state that valve port 71 is opened fully, described bypass through hole 8 open the end face 23 that is higher than spool 2 to the opening of inner chamber 11, no matter spool moves to any position in inner chamber 11, described opening can not face toward spool 2; Even valve port 71 is opened fully, promptly as the 2 residing positions of spool among Fig. 5, the refrigeration agent that bypass through hole 8 ' flows to inner chamber 11 can not impact to spool 2, guarantees the stability of spool 2 equilibrium of forces described in embodiment one, thereby has improved pressure controlled reliability.
Angle R described in embodiment one and the embodiment two between the axis of the axis of bypass through hole and spool, the span of its angle is by the decision of the course of working of bypass through hole.Fig. 6 is the schematic representation of processing bypass through hole, as shown in Figure 6, on the idiosome of aluminium section bar, process high-pressure chamber 51, high pressure port 5, low-pressure chamber 61, low-pressure port 6 and the hole 11a that is used to form inner chamber, process bypass through hole 8 ' along illustrated A direction by hole 11a then, within the span of the angle between the axis of the axis of described bypass through hole 8 ' and spool 2, all must guarantee to process the bypass through hole by hole 11a, as shown in Figure 6, the axis of bypass through hole 8 ' is between position B and position C, its mid point b is the edge of opening point of hole 11a, and some c is the screw thread terminating point that mounting spring is adjusted seat 4 that is used in the 11a of hole.For example adopt drill bit can put in the 11a of hole and get out through hole 8 ', the edge of opening b that drill bit can contact hole 11a in the course of working guarantees simultaneously that also via openings is outside screw thread.
As seen, though the bypass through hole can be realized purpose of the present invention described in embodiment one and the embodiment two, but the processing of bypass through hole is not very convenient, machine shaping for ease of the bypass through hole, described pressure controlled valve can be the structure of the parallel axes of the axis of bypass through hole 8 and spool 2, specifically illustrates in following examples.
Embodiment three
Be provided with bypass through hole 8 between described low-pressure chamber 61 and the inner chamber 11 "; make the pressure in the low-pressure chamber 61 identical; the structure of the described pressure controlled valve of present embodiment and the main distinction of the foregoing description are; described bypass through hole 8 with the pressure of inner chamber 11 " axis and the parallel axes of spool, and bypass through hole 8 " axis and the distance between the axis of spool 2 greater than the maximum radius of spool 2; corresponding, the cross-sectional dimension of inner chamber 11 is above-mentioned relatively two embodiments also increase.Other structures of described pressure controlled valve are similar substantially to aforesaid embodiment.
Obviously, bypass through hole 8 in the pressure controlled valve described in the present embodiment " in the refrigeration agent that flows out can not impact to spool 2, guarantee the stability of spool 2 the above equilibrium of forces state, thereby improved pressure controlled reliability.In addition, consider bypass through hole 8 from course of working " the axis and the parallel axes of spool 2, also just with the parallel axes of valve chamber 11, along the easier processing of direction manufacturing bypass through hole of axis.
More than in all described pressure controlled valve of embodiment, establish groove on the spool 2, place sealed member in the described groove, between inner chamber 11 and high-pressure chamber 51, seal, also plural groove can be set, place sealed member respectively, to improve sealing.Sealed member can be a seal ring, but is not limited to the seal ring sealing, and those skilled in the art should know by inference, and the structure of other motive sealings is also within protection domain of the present invention.
Need to prove; connecting path 8 of the present invention also is not limited to the bypass through hole among the embodiment; as long as other forms of path can be communicated with low-pressure chamber and inner chamber all can be realized purpose of the present invention; for example, the bypass through hole for the structure that is provided with perpendicular to valve core axis also within protection domain.
The above only is preferred embodiment of the present invention, is not the present invention is done any pro forma restriction.Though the present invention discloses as above with preferred embodiment, yet be not in order to limit the present invention.Any those of ordinary skill in the art, do not breaking away under the technical solution of the present invention scope situation, all can utilize the method and the technology contents of above-mentioned announcement that technical solution of the present invention is made many possible changes and modification, or be revised as the equivalent embodiment of equivalent variations.Therefore, every content that does not break away from technical solution of the present invention, all still belongs in the scope of technical solution of the present invention protection any simple modification, equivalent variations and modification that above embodiment did according to technical spirit of the present invention.
Claims (8)
1. pressure controlled valve, comprise: valve body (1), high-pressure chamber (51) and the low-pressure chamber (61) that are provided with in the valve body (1) by throttling path (7) connection, the spool (2) that is provided with in the inner chamber (11) of valve body (1), it is characterized in that: described spool (2) can come and go mobile with respect to the valve port of driveing to high-pressure chamber (51) (71) on the throttling path (7), the end of described spool (2) is taper, can in valve port (71), come and go and move the area of passage that changes valve port, to control the folding degree of described valve port (71); Isolated each other between described high-pressure chamber (51) and the inner chamber (11) by sealing, be provided with connecting path (8) between described low-pressure chamber (61) and the inner chamber (11); The parallel axes of the axis of described connecting path (8) and spool (2), and the distance between the axis of the axis of described connecting path (8) and spool (2) is greater than the maximum radius of spool (2), and connecting path (8) is communicated with the diapire of described inner chamber (11) towards an end of described inner chamber (11).
2. pressure controlled valve according to claim 1 is characterized in that: described connecting path (8) is the bypass through hole, and the scope of its internal diameter is 0.8mm to 4mm.
3. pressure controlled valve according to claim 1 is characterized in that: be provided with sealed member (9) between described high-pressure chamber (51) and the inner chamber (11).
4. pressure controlled valve according to claim 1 is characterized in that: described sealed member (9) is a seal ring.
5. pressure controlled valve according to claim 1 is characterized in that: also comprise spring (3) in the described inner chamber (11), that an end and spool (2) connect is set, the thrust of spring (3) is in spool (2).
6. pressure controlled valve according to claim 5, it is characterized in that: the other end of described spring (3) is provided with by being threaded in the spring adjustment seat (4) in the inner chamber (11), can regulate described spring (3) and be applied to thrust size on the described spool (2).
7. pressure controlled valve according to claim 6 is characterized in that: described spring adjustment seat (4) is provided with sealed member (9 ').
8. pressure controlled valve according to claim 7 is characterized in that: described sealed member (9 ') is a seal ring.
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| Application Number | Priority Date | Filing Date | Title |
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| CN200810087715XA CN101545553B (en) | 2008-03-24 | 2008-03-24 | Pressure control valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200810087715XA CN101545553B (en) | 2008-03-24 | 2008-03-24 | Pressure control valve |
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| CN101545553A CN101545553A (en) | 2009-09-30 |
| CN101545553B true CN101545553B (en) | 2011-10-12 |
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| CN200810087715XA Active CN101545553B (en) | 2008-03-24 | 2008-03-24 | Pressure control valve |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104696555A (en) * | 2013-12-04 | 2015-06-10 | 上海宇航系统工程研究所 | A high-pressure high-flow helium relief valve |
| CN106151554A (en) * | 2015-04-24 | 2016-11-23 | 杭州三花研究院有限公司 | Electric expansion valve, the manufacture method of electric expansion valve and refrigerant system |
| CN114877401B (en) * | 2022-04-25 | 2023-07-21 | 山东圣华能源工程设计有限公司 | Geothermal energy heat exchange station system |
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|---|---|---|---|---|
| CN1290222A (en) * | 1998-02-11 | 2001-04-04 | 大陆-特韦斯贸易合伙股份公司及两合公司 | Pressure control valve |
| CN1432752A (en) * | 2002-01-11 | 2003-07-30 | 沃尔沃建造设备控股（瑞典）有限公司 | Guiding pressure rise controlling valve |
-
2008
- 2008-03-24 CN CN200810087715XA patent/CN101545553B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1290222A (en) * | 1998-02-11 | 2001-04-04 | 大陆-特韦斯贸易合伙股份公司及两合公司 | Pressure control valve |
| CN1432752A (en) * | 2002-01-11 | 2003-07-30 | 沃尔沃建造设备控股（瑞典）有限公司 | Guiding pressure rise controlling valve |
Non-Patent Citations (1)
| Title |
|---|
| JP特开2006-133016A 2006.05.25 |
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