CN2641411Y - Back pressure balancing type small pressure valve - Google Patents
Back pressure balancing type small pressure valve Download PDFInfo
- Publication number
- CN2641411Y CN2641411Y CN 03273673 CN03273673U CN2641411Y CN 2641411 Y CN2641411 Y CN 2641411Y CN 03273673 CN03273673 CN 03273673 CN 03273673 U CN03273673 U CN 03273673U CN 2641411 Y CN2641411 Y CN 2641411Y
- Authority
- CN
- China
- Prior art keywords
- piston
- valve
- cavity
- passage
- back pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Safety Valves (AREA)
Abstract
The utility model discloses a back pressure balance type minimum pressure valve, which is often applied in the gas circuit system of gas compressor and comprises a valve body(1), an air inlet cavity channel(a), an air outlet cavity channel(b), a pilot valve(2), a piston(5) and a piston return spring(6). The utility model is characterized in that: the utility model also comprises an enclosed back pressure cavity(e), wherein the back pressure cavity(e) and air inlet cavity channel(a) are respectively arranged at the two sides of piston(5); the back pressure cavity(e) is communicated with the air inlet cavity channel(a). The function of back pressure cavity is to balance the partial force on the piston so as to reduce the stress of the piston return spring, further increase the service life of spring, reduce the outline dimension and weight of spring and minimum pressure valve and increase the comprehensive performance of minimum pressure valve. Compared with the prior art, the utility model has the advantages of long service, life, small volume, large flux and good performance.
Description
Technical field
The utility model relates to a kind of minimum pressure valve, is usually used in the air-channel system of gas compressor.
Background technique
Minimum pressure valve is extensive use of in the gas compressor industry, its main effect has two: the one, make after the compressor start immediately externally air feed, preferentially set up the required circulating pressure of lubricating fluid, guarantee the lubricated of compressor, when gas pressure reaches setting pressure, minimum pressure valve is just opened, outside air feed, otherwise minimum pressure valve is closed condition; The 2nd, when air compressor stopped air feed, minimum pressure valve played pilot valve, prevented gas backstreaming.
Present used pressure minimum valve arrangement as shown in Figure 1 and Figure 2 in the gas compressor industry, Fig. 1 is the single piston reset spring minimum pressure valve of small flow, Fig. 2 is the double joint piston reset spring minimum pressure valve (wherein is cylindrical spring, and another root is a spring sheet) of big flow.They comprise: valve body 1, air inlet cavity a, the cavity b that gives vent to anger, pilot valve 2, piston 5, piston cylinder 7 etc., be provided with the spring that is used for piston reset between piston and the piston cylinder, their working principle is: pressurized gas enters from air inlet cavity a, act on the pilot valve 2, when the gas pressure at air inlet cavity a place reaches certain value, pilot valve 2 moves up with piston 5, and gas is discharged from the cavity b that gives vent to anger; When compressor quits work, the pressure at air inlet cavity a place descends suddenly, and the pressurized gas of pilot valve 2 tops keeps original pressure, add the effect of pilot valve Returnning spring 4, pilot valve 2 moves downward, rapidly air inlet cavity a is blocked,, play one-way valve so the gas of the cavity b that gives vent to anger can't flow backwards.Subsequently, big piston 5 compresses pilot valve 2 under the effect of piston reset spring 6 and move down, and waits for the beginning of task down.Not only working principle is identical for pilot valve among Fig. 1 and Fig. 2, and its main something in common is: the power that pressurized gas acts on the pilot valve is born by spring fully.When latus rectum increases, adopt two big springs.
Minimum pressure valve from small flow to big flow can find out obviously that obvious variation has taken place spring, and therefore the performance of valve also has corresponding variation.The structure of rill metered valve is little, and open and shut characteristic is good, and is highly sensitive; The valve of big flow must use the very big hard spring of rigidity, thereby make the structure heaviness of valve, open and shut characteristic is poor, sensitivity reduces, and easily produce the vibration of spring and cause the pulsation of air pressure, the direction that has retrained the past big flow of minimum pressure valve to a great extent develops, and this is the shortcoming that existing minimum pressure valve exists.
Summary of the invention
The purpose of this utility model is to overcome above-mentioned the deficiencies in the prior art part, provide a kind of and can reduce spring stress, improve spring and valve performance and life-span, reduce the volume of spring and valve, the novel back-pressure balance formula minimum pressure valve of raising valve flow.
Designed a kind of back-pressure balance formula minimum pressure valve according to above-mentioned purpose, comprise valve body 1, air inlet cavity a, the cavity b that gives vent to anger, pilot valve 2, piston 5, piston reset spring 6, the back pressure cavity e that also comprises a closure simultaneously, this back pressure cavity e and air inlet cavity a lay respectively at the both sides of piston 5; Described back pressure cavity e communicates with air inlet cavity a through passage.
Passage between described back pressure cavity e and the air inlet cavity a can be built-in channel, and a valving that is used for single effect can be set in this passage, performance that can more effective raising valve; Described built-in channel can be made of the upper channel d that passes piston, the middle passage f between piston and pilot valve, the lower channel c that passes pilot valve; Be provided with pilot valve Returnning spring 4 in the middle passage f; The valving that is used for single effect can be a ball 3, and this ball 3 also can replace with other shapes, has needed only single effect; This ball 3 preferably is arranged in the confluce of passage f and lower channel c; Described pilot valve Returnning spring 4 can act on the ball 3 or act directly on the pilot valve 2.
Also the valving of single effect can be set in the built-in channel between described back pressure cavity e and the air inlet cavity a, but be provided with the performance that the valving that is used for single effect can more effective raising valve in the passage.
Passage between described back pressure cavity e and the air inlet cavity a can also be external passage, the valving of single effect can be set in this external passage, also this device can be set, but be provided with the performance of the more effective raising valve of the valving that is used for single effect in the passage.
Described piston reset spring 6 can be positioned at the piston rod of piston 5, also can be sleeved on the piston rod.
Described piston reset spring 6 can be positioned at back pressure cavity a inside, also can be positioned at the outside of back pressure cavity.
The stressed complete elastic force by spring of the piston of the minimum pressure valve of prior art comes balance, when the suction port diameter of valve is done greatly, at this moment the very big hard spring of necessary employing rigidity comes the stress balance with piston, even adopt dual spring to come balance (as shown in Figure 2) with it, thereby make the structure heaviness of valve, and elasticity is hard more, assembling and debugging are difficult more, the open and shut characteristic of valve is bad, the low and easy pulsation that produces the vibration of spring and cause air pressure of sensitivity.The power major part that the utility model acts on the piston is come balance by back pressure, the stressed suction port latus rectum of valve that is not subjected to of spring retrains, so the latus rectum of valve and flow can strengthen arbitrarily, and spring is stressed very little, therefore the size of spring is little, and the volume of whole valve also just reduces.Because the size of spring is little, the generation vibration is little, and is therefore little to the generation pulsating nature of gas, and the life-span of spring is also high.Because the rigidity of spring is little, assembling and debugging are easy, and the open and shut characteristic of valve is good, and is highly sensitive, and the life-span is long.
The stressed complete elastic force by spring of piston comes balance in the prior art, make that the piston reset spring size is big, add that piston reset spring is installed in the apical position of piston, this increases the height of whole valve to some extent, in preferred implementation of the present utility model, come balance by back pressure in that piston portion is stressed, reduce the stressed of spring, make on the little basis of piston reset spring size, use suitable square law device piston reset spring again, make the height of whole valve reduce, more embodied the utlity model has the little advantage of volume.
In sum, compared with prior art, the utlity model has the advantage that the life-span is long, volume is little, flow is big, performance is good.
Description of drawings
Fig. 1 is the single piston reset spring minimum pressure valve structural representation of prior art;
Fig. 2 is the double joint piston reset spring minimum pressure valve structural representation of prior art;
Fig. 3,4,5,6 is respectively the structural representation of four kinds of mode of executions of the utility model back-pressure balance formula minimum pressure valve;
Fig. 7 is the stressed schematic representation of the minimum pressure valve of prior art;
Fig. 8 is the stressed schematic representation of minimum pressure valve of preferred implementation shown in Figure 3;
The piece number of accompanying drawing is represented:
1, valve body 2, pilot valve 3, ball 4, pilot valve Returnning spring
5, piston 6, piston reset spring 7, piston cylinder 8, spring sheet
A, air inlet cavity b, the cavity c that gives vent to anger, lower channel d, upper channel
E, back pressure cavity f, middle passage g, external chennel
Embodiment
In order to deepen understanding of the present utility model, the utility model is described in further detail below in conjunction with embodiment and accompanying drawing, and this example only is used to explain the utility model, does not constitute the qualification to the utility model protection domain.
Fig. 3 shows a kind of mode of execution of the utility model minimum pressure valve, comprise valve body 1, air inlet cavity a, the cavity b that gives vent to anger, pilot valve 2, ball 3, pilot valve Returnning spring 4, piston 5, piston reset spring 6, piston cylinder 7 etc., be provided with a back pressure cavity e between piston and the piston cylinder, passage between back pressure cavity e and the air inlet cavity a is a built-in channel, and this passage is made of the upper channel d that passes piston, the middle passage f between piston and pilot valve, the lower channel c that passes pilot valve; Be provided with pilot valve Returnning spring 4 in the middle passage f; Ball 3 is arranged in the confluce of passage f and lower channel c; This ball 3 can be made with rubber, also can select for use other shapes or material to replace, as long as play single effect; Described pilot valve Returnning spring 4 can act on the ball 3, also can act directly on the pilot valve 2.Described piston reset spring 6 is sleeved on the piston rod of piston 5, and is positioned at back pressure cavity e.
When compressor starts work, when catch pot is inflated, gas enters in the valve from air inlet cavity a, (power of pushing ball open was very little for the ball 3 of passage f ingress during gas was pushed open, can ignore), and enter back pressure cavity e by middle passage f and upper channel d, and acting on the back side of piston 5 forming back pressure in the back pressure cavity e, the gas of making a concerted effort to come balance air inlet cavity a of the elastic force of counterpressure and spring 6 acts on the power on the pilot valve 2.When the gas pressure at air inlet cavity a place continues to increase, when the pressure that gas acts on pilot valve 2 equaled making a concerted effort of back pressure and piston reset spring 6, pilot valve 2 was in the threshold state of opening.When the gas pressure at air inlet cavity a place continues to increase, when gas acts on pressure on the pilot valve 2 just greater than the making a concerted effort of back pressure and piston reset spring 6, pilot valve 2 trace open circuits, gas begins to discharge from the cavity b that gives vent to anger.When air inlet cavity a place pressure reached setting pressure, valve was just opened fully, and gas is discharged from the cavity b that gives vent to anger with peak rate of flow.When compressor quits work, no longer when the catch pot air feed, the pressure at air inlet cavity a place descends suddenly, and the pressure of pilot valve 2 tops keeps original pressure, add the effect of pilot valve Returnning spring 4, pilot valve 2 moves downward, and ball 3 also blocks up lower channel c simultaneously, pilot valve 2 is shut, and reaches to prevent gas refluence phenomenon.Subsequently, piston 5 moves down in the effect of piston reset spring 6, and pilot valve 2 is compressed, and waits for the beginning of task down.
Mode of execution shown in Figure 4 is that with the difference of mode of execution shown in Figure 3 back pressure cavity e is arranged between piston rod top and the piston cylinder, and piston reset spring 6 is installed in the piston rod, and is positioned at back pressure cavity inside.
The mode of execution of Fig. 3 and Fig. 4 can also be done conversion slightly in addition, promptly the piston reset spring among Fig. 36 is retrofitted in the piston rod, just the position on piston rod top; Piston reset spring 6 among Fig. 4 can be sleeved on the piston rod.
Fig. 5 and Fig. 6 change the passage between back pressure cavity e and the air inlet cavity a into an external passage, and the valving of single effect can be set in the passage, if but be provided with the performance that the valving that is used for single effect can more effective raising valve.The pilot valve Returnning spring 4 of Fig. 5 and two kinds of schemes of Fig. 6 acts directly on the pilot valve 2, need not ball 3.The scheme of other structures and working principle and Fig. 3 and Fig. 4 is basic identical.
Utilize mechanical model to introduce the working principle of minimum pressure valve below again, wherein the power of pilot valve Returnning spring 4 is very little, can omit and disregard.Advantage of the present utility model can embody from the force analysis of piston 5, and Fig. 7 is the stressed schematic representation of the minimum pressure valve of prior art: the lower end is subjected to the pressure P of gas, and top is subjected to the power of the doing F of piston reset spring 6
1Fig. 8 is the stressed schematic representation of Fig. 3 scheme back-pressure balance formula minimum pressure valve of the present utility model: the lower end is subjected to the pressure P of gas, and the upper end is subjected to the pressure P of gas and the power of the doing F of piston reset spring 6
2The stressed size that draws piston reset spring 6 separately according to mechanical equilibrium is as follows:
The stressed F of the piston reset spring 6 of the minimum pressure valve of prior art
1:
F
1=PS
1S
1-gas acts on the area on the small piston.
The stressed F of Fig. 3 scheme back-pressure balance formula minimum pressure valve piston reset spring 6 of the present utility model
2:
F
2=P (S
1-S
2)=PS
0S
2-gas acts on the area on the big piston;
S
0The section area of-big piston bar.
When the suction port latus rectum of two kinds of valves equates with initiation pressure, because S
0＜＜S
1So, F
2＜＜F
1, promptly the required spring force of back-pressure balance formula minimum pressure valve is much smaller than the spring force of prior art.
The stressed complete elastic force by spring of the piston of the minimum pressure valve of prior art comes balance, when the suction port diameter of valve is done greatly, at this moment the very big hard spring of necessary employing rigidity comes the stress balance with piston, even adopt dual spring to come balance (as shown in Figure 2) with it, thereby make the structure heaviness of valve, and elasticity is hard more, assembling and debugging are difficult more, the open and shut characteristic of valve is bad, the low and easy pulsation that produces the vibration of spring and cause air pressure of sensitivity.The power major part that the utility model acts on the piston is come balance by back pressure, the stressed suction port latus rectum of valve that is not subjected to of spring retrains, so the latus rectum of valve and flow can strengthen arbitrarily, and spring is stressed very little, therefore the size of spring is little, and the volume of whole valve also just reduces.Because the size of spring is little, the generation vibration is little, and is therefore little to the generation pulsating nature of gas, and the life-span of spring is also high.Because the rigidity of spring is little, assembling and debugging are easy, and the open and shut characteristic of valve is good, and is highly sensitive, and the life-span is long.
Claims (10)
1, a kind of back-pressure balance formula minimum pressure valve, comprise valve body (1), air inlet cavity (a), the cavity of giving vent to anger (b), pilot valve (2), piston (5), piston reset spring (6), it is characterized in that: also comprise the back pressure cavity (e) of a closure, this back pressure cavity (e) and air inlet cavity (a) lay respectively at the both sides of piston (5); Described back pressure cavity (e) communicates with air inlet cavity (a) through passage.
2, minimum pressure valve according to claim 1 is characterized in that: the passage between back pressure cavity (e) and the air inlet cavity (a) is a built-in channel, is provided with the valving that is used for single effect in this passage.
3, minimum pressure valve according to claim 2 is characterized in that: described passage is by the upper channel that passes piston (d), the middle passage (f) between piston and pilot valve, lower channel (c) formation of passing pilot valve.
4, minimum pressure valve according to claim 3 is characterized in that: be provided with pilot valve Returnning spring (4) in the middle passage (f); The valving that is used for single effect is a ball (3), and this ball (3) is arranged in the confluce of passage (f) and lower channel (c).
5, minimum pressure valve according to claim 4 is characterized in that: pilot valve Returnning spring (4) acts on ball (3) and goes up or act directly on the pilot valve (2).
6, minimum pressure valve according to claim 1 is characterized in that: the passage between back pressure cavity (e) and the air inlet cavity (a) is a built-in channel, is not provided with the valving that is used for single effect in this passage.
7, minimum pressure valve according to claim 1 is characterized in that: the passage between back pressure cavity (a) and the air inlet cavity (a) is external passage (g), is provided with the valving that is used for single effect in this passage.
8, minimum pressure valve according to claim 1 is characterized in that: the passage between back pressure cavity (a) and the air inlet cavity (a) is external passage (g), is not provided with the valving that is used for single effect in this passage.
9, according to claim 1 to 4 any one or any one described minimum pressure valve of claim 6 to 8, it is characterized in that: described piston reset spring (6) is positioned at the piston rod of piston (5) or is sleeved on the piston rod.
10, according to claim 1 to 4 any one or any one described minimum pressure valve of claim 6 to 8, it is characterized in that: described piston reset spring (6) is positioned at the inside or the outside of back pressure cavity (a).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 03273673 CN2641411Y (en) | 2003-08-19 | 2003-08-19 | Back pressure balancing type small pressure valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 03273673 CN2641411Y (en) | 2003-08-19 | 2003-08-19 | Back pressure balancing type small pressure valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2641411Y true CN2641411Y (en) | 2004-09-15 |
Family
ID=34301623
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 03273673 Expired - Lifetime CN2641411Y (en) | 2003-08-19 | 2003-08-19 | Back pressure balancing type small pressure valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2641411Y (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100380033C (en) * | 2003-08-19 | 2008-04-09 | 查谦 | Back-pressure balancing minimum pressure valves |
| CN101427058B (en) * | 2006-03-06 | 2012-11-14 | 极点技术Pmc股份有限公司 | Suction valve |
| CN103357201A (en) * | 2013-07-30 | 2013-10-23 | 中国人民解放军后勤工程学院 | Oil pump vehicle evacuation oil-gas separator |
| CN104632747A (en) * | 2015-01-27 | 2015-05-20 | 西京学院 | Hydraulic balance valve |
| CN110259744A (en) * | 2019-05-28 | 2019-09-20 | 中国船舶重工集团公司第七一九研究所 | One kind is latent to use superposing type hydraulic backpressure valve |
| CN111043321A (en) * | 2019-12-20 | 2020-04-21 | 隆尧县正蝶阀门有限公司 | Pilot-operated electromagnetic valve |
-
2003
- 2003-08-19 CN CN 03273673 patent/CN2641411Y/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100380033C (en) * | 2003-08-19 | 2008-04-09 | 查谦 | Back-pressure balancing minimum pressure valves |
| CN101427058B (en) * | 2006-03-06 | 2012-11-14 | 极点技术Pmc股份有限公司 | Suction valve |
| CN103357201A (en) * | 2013-07-30 | 2013-10-23 | 中国人民解放军后勤工程学院 | Oil pump vehicle evacuation oil-gas separator |
| CN104632747A (en) * | 2015-01-27 | 2015-05-20 | 西京学院 | Hydraulic balance valve |
| CN110259744A (en) * | 2019-05-28 | 2019-09-20 | 中国船舶重工集团公司第七一九研究所 | One kind is latent to use superposing type hydraulic backpressure valve |
| CN110259744B (en) * | 2019-05-28 | 2020-07-31 | 中国船舶重工集团公司第七一九研究所 | Latent stack formula hydraulic pressure back pressure valve that uses |
| CN111043321A (en) * | 2019-12-20 | 2020-04-21 | 隆尧县正蝶阀门有限公司 | Pilot-operated electromagnetic valve |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1490545A (en) | Back-pressure balancing minimum pressure valves | |
| CN1316592A (en) | Changable displacement compressor able to reducing noise produed | |
| CN2641411Y (en) | Back pressure balancing type small pressure valve | |
| CN202746133U (en) | Spring type gas-liquid supercharging constant pressure pump | |
| CN201628032U (en) | One-way non-return pipe joint | |
| CN2854130Y (en) | Gas pressure pump | |
| CN1264785A (en) | Electronically controlled hydraulically-driven common-pipe (tracl) air inlet and exhaustion system for IC engine | |
| CN1699780A (en) | Oil-gas spring | |
| CN106703928B (en) | Exhaust valve control execution system directly driven by servo oil | |
| CN203272330U (en) | Single-acting micro cylinder | |
| CN1871435A (en) | Reciprocating compressor with enlarged valve seat area | |
| CN200968275Y (en) | Air cylinder structure of septum compressor | |
| CN107601353A (en) | A kind of gas type Freight trailer lowering or hoisting gear | |
| CN109372607A (en) | Multistage draining exhaust valve and its working method | |
| CN209244627U (en) | Multistage draining exhaust valve | |
| CN203717502U (en) | Lifting system balance valve for mining dump truck | |
| CN208982395U (en) | A kind of new ceramics cylinder | |
| CN1903626A (en) | Tyre air inflating device of tyre road pressing machine | |
| CN2588073Y (en) | Pressure increased potential energy pump | |
| CN201693796U (en) | Multipurpose pressure device | |
| CN201080985Y (en) | Adjustable type shock absorber | |
| CN214534504U (en) | High-performance pressure reducing valve | |
| CN2849229Y (en) | Eccentrically arranged valve type oil pumping pump | |
| CN216768550U (en) | Hydraulic thread cartridge valve | |
| CN200949659Y (en) | High-pressure Pneumatic controlled valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Effective date of abandoning: 20080409 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |