CN109654269B - Balance piston type constant pressure valve - Google Patents
Balance piston type constant pressure valve Download PDFInfo
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- CN109654269B CN109654269B CN201811466170.3A CN201811466170A CN109654269B CN 109654269 B CN109654269 B CN 109654269B CN 201811466170 A CN201811466170 A CN 201811466170A CN 109654269 B CN109654269 B CN 109654269B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/20—Excess-flow valves
Abstract
The invention provides a balanced piston type constant pressure valve which comprises a valve body, wherein a fluid inlet and a fluid outlet are arranged on the valve body, a first piston with a piston rod is assembled in the valve body in a guiding and sliding manner, a piston inlet and a piston outlet which are communicated with the fluid inlet and the fluid outlet are formed in the first piston, a communicating pipe which is communicated with a rod cavity and a rodless cavity at two sides of the first piston is arranged on the valve body, the piston rod of the first piston extends out of the valve body and is connected with a constant force mechanism, the constant force mechanism comprises a shell which is fixedly connected to one side of the rod cavity of the valve body, the shell is provided with an atmosphere communicating port and a shell bottom connected with the valve body, a second piston is assembled in the shell in a guiding and sliding manner, the second piston is matched with the piston. The invention has the beneficial effects that: the constant-pressure valve disclosed by the invention does not depend on an adjusting spring, the use stability of the constant-pressure valve is improved by adopting the constant-force mechanism, the fluid output pressure is accurate, and the fluid output pressure is always kept stable along with the automatic adjustment of the first piston in use.
Description
The application is a divisional application of the following applications, the application date of the original application: year 2017, month 2 and day 3, application number of original application: 2017100633455, title of original application: a balance piston type constant pressure valve.
Technical Field
The invention relates to a balance piston type constant pressure valve.
Background
The temperature of a wellhead of a gas field water-producing gas well is low, about 4-7 ℃ in winter and about 14-16 ℃ in summer, and a shaft and a pipeline are easy to form hydrates and freeze blocking so as to cause frequent blockage. To prevent hydrate formation, natural gas hydrate inhibitors, such as methanol, are typically added to the natural gas to lower the hydrate formation temperature, thereby lowering the dew point of the natural gas and preventing hydrate formation. When the method is adopted, an alcohol injection pipeline and alcohol-containing sewage treatment equipment need to be configured, the implementation difficulty of the methanol injection process is high, and three disadvantages exist when methanol is used: firstly, methanol is toxic and has certain harm; secondly, the consumption of methanol is large, and the total cost is high; thirdly, the investment of alcohol injection and wastewater treatment equipment and supporting facilities is large.
Therefore, some gas fields are developed by adopting a clean production mode of 'underground throttling and low-pressure gas collection', the underground throttling technology is to install a throttler at a proper position of an oil pipe, so that the throttling and pressure-reducing expansion process of natural gas is generated in a well, and meanwhile, the throttled gas flow is heated by using the ground temperature, so that the temperature of the throttled gas flow can be greatly increased and is higher than the hydrate generation temperature under the condition of the throttled gas flow pressure, and the purpose of preventing and controlling the generation of hydrates in a shaft and a ground pipeline is achieved. The underground throttling technology can reduce the pressure of a shaft and a ground pipeline, the anti-blocking effect is obvious, compared with a high-pressure gas collection mode, the development mode can save the investment of a single-well alcohol injection pipeline and the daily alcohol injection material cost, and meanwhile, the pressure resistance grade of the ground gas collection pipeline is reduced, so that the wall thickness and the steel consumption of the ground gas collection pipeline can be greatly reduced, the oil construction cost is saved, the ground engineering investment is greatly reduced, and the development benefit of a gas field is effectively improved.
However, for some gas fields with relatively high water yield, for example, up to 72.5 square/day, the gas well has insufficient liquid carrying capacity and has a great drainage problem; meanwhile, the conventional downhole throttling technology is used in the high-yield liquid gas well, and due to the fact that a throttling device is installed in an oil pipe, a shaft is prone to being unsmooth, continuous liquid drainage production of the high-yield liquid gas well is not facilitated, liquid accumulation, flooding and production stop of the high-yield liquid gas well are prone to being caused, and the production performance of a gas field is severely limited.
In order to ensure that a high-yield liquid gas well carries liquid continuously and produces stably and the requirement of a gas field low-pressure gathering and transportation development mode must be met, therefore, under the condition that an underground throttle is not installed, a pressure reducing valve is generally installed at a well head to realize throttling and pressure reducing production of the high-yield liquid gas well, on one hand, the pressure of a ground pipeline is effectively reduced, the safety risk is reduced, and the investment is saved; on the other hand, the hydrate can be effectively prevented and controlled from being generated, the continuous and stable drainage production of a gas well is facilitated, and the gas field development benefit can be improved.
The output pressure after the decompression is all controlled through the regulating spring to common relief pressure valve in the market at present, if the bulletin number is CN201715057U, the china utility model patent that the bulletin date is 2011.01.19 discloses a balanced piston induction type pneumatic relief pressure valve, this relief pressure valve need set for output pressure with compression regulating spring through twisting the valve gap when using, twist simultaneously and change the valve gap, compression regulating spring can also make balanced piston roof pressure case downwards, thereby break away from between messenger's case and the disk seat and form an opening, the circulation passageway of fluid has also been counted like this and opened, make the fluid can advance from the air inlet, and go out from the gas outlet. When fluidic pressure is less than preset pressure, the opening can not change, and when fluidic pressure is greater than preset pressure, the ascending feedback pressure that the piston received is greater than the preset pressure of spring, and the piston upwards removes this moment, and the case also upwards removes under the reset spring effect, and the opening diminishes, and the opening reduces to no longer change after the certain degree, and the system reaches a balance, and the outlet pressure of relief pressure valve is stabilized and gets off. The pressure at the outlet of the pressure reducing valve is basically kept unchanged and is stabilized within a certain range by the circulation.
Although the traditional pressure reducing valve can play a role in reducing pressure, under the condition that the structural sizes of components such as a valve body, a valve core and the like are determined, the output pressure of the traditional pressure reducing valve completely depends on the preset state of an adjusting spring, the traditional pressure reducing valve needs to be adjusted manually before use, the adjusted output pressure is large or small, the output pressure can be known by the experience of operators or can be known only after the output pressure is measured, and if the traditional pressure reducing valve is not suitable, the traditional pressure reducing valve needs to be further adjusted, and the adjustment and the use are very inconvenient. In addition, the compression amount of the adjusting spring is continuously changed along with the fluctuation of the fluid input pressure, and along with the prolonging of the service time, the elastic force of the adjusting spring is reduced after the adjusting spring is compressed and restored for countless times, especially after the adjusting spring is corroded, scaled or blocked by impurities, the service performance of the adjusting spring is greatly reduced, the pressure reduction and the use effect of the pressure reducing valve are seriously influenced, and therefore the service life and the stability of the pressure reducing valve are poor.
Disclosure of Invention
The invention aims to provide a balance piston type constant pressure valve which does not depend on an adjusting spring, has higher use stability and has accurate and stable fluid output pressure.
In order to solve the technical problems, the invention adopts the following technical scheme:
a balanced piston type constant pressure valve comprises a valve body, wherein a fluid inlet and a fluid outlet are arranged on the valve body, a first piston with a piston rod is assembled in the valve body in a guiding sliding mode, a piston inlet and a piston outlet which are communicated with the fluid inlet and the fluid outlet are formed in the first piston, so that the pressure of the fluid outlet on the valve body can be adjusted through the movement of the first piston, a communicating pipe which is communicated with a rod cavity and a rodless cavity on two sides of the first piston is arranged on the valve body, the piston rod of the first piston extends out of the valve body and is connected with a constant force mechanism, the valve body is of a cylindrical structure with one end open and the other end closed, the opening forms the fluid outlet of the valve body, the fluid inlet is formed in the cylindrical wall of the valve body, the first piston is also of a cylindrical structure with one end open and the other end closed, the opening forms the piston outlet of the first piston, the first piston has a piston chamber therein communicating the piston inlet and the piston outlet.
Further, the piston inlet on the first piston is equal in inner diameter to the fluid inlet on the valve body.
The invention has the beneficial effects that: because the first piston is provided with the piston inlet and the piston outlet which are communicated with the fluid inlet and the fluid outlet on the valve body, when the first piston moves in the valve body, when the superposed opening degree of the piston inlet and the fluid inlet is larger, more fluid flows through, the pressure of the fluid outlet is larger at the moment, and when the superposed opening degree of the piston inlet and the fluid inlet is smaller, the pressure of the fluid outlet is reduced, so that the pressure of the fluid outlet on the valve body can be adjusted through the movement of the first piston;
because the valve body is provided with the communicating pipe which communicates the rod cavity and the rodless cavity at the two sides of the first piston, the fluid pressure of the rod cavity and the rodless cavity is equal, but the fluid pressure of the rod cavity and the rodless cavity on the first piston is unequal, because the rod cavity is provided with one more piston rod, the stressed cross-sectional area of the piston rod is smaller than the stressed area of the rodless cavity, the resultant force stressed by the first piston is towards one side of the rod cavity, and the resultant force is equal to the product of the fluid pressure and the cross-sectional area of the piston rod, namely, the first piston always tends to move towards one side of the rod cavity;
because the piston rod of the first piston extends out of the valve body and is connected with the constant force mechanism, the constant force mechanism can apply a constant force opposite to the direction of the resultant force to the piston rod, when the constant force value is equal to the resultant force value, the first piston keeps balance, the opening degree of the coincidence of the piston inlet and the fluid inlet is kept unchanged, the constant pressure valve outputs constant pressure fluid, the constant pressure value is equal to the set constant force value divided by the cross section area of the piston rod, and therefore when the constant pressure valve is set, a constant force value can be set according to the known cross section area of the piston rod, and the constant pressure value output by the constant pressure valve can be known;
when the constant-pressure valve is used, if the pressure of fluid entering the valve body changes, the constant force value of the constant-force mechanism does not change, so that the balance state of the first piston is broken, when the pressure of the fluid becomes higher, the first piston automatically moves to one side of the rod cavity, meanwhile, the opening degree of the coincidence of the piston inlet and the fluid inlet is reduced, the pressure of the fluid entering the valve body is automatically reduced until the first piston reaches balance again, and at the moment, the pressure of the fluid output by the constant-pressure valve is still the constant pressure value; on the contrary, when the fluid pressure is reduced, the first piston automatically moves to one side of the rodless cavity, meanwhile, the opening degree of the coincidence between the piston inlet and the fluid inlet is increased, the fluid pressure entering the valve body is automatically increased until the first piston is balanced again, and the fluid pressure output by the constant pressure valve is still the constant pressure value at the moment, namely, the first piston can automatically adapt to the change of the fluid pressure entering the valve body through self movement, so that the constant pressure valve always outputs a determined constant pressure value.
Therefore, the balance piston type constant pressure valve does not depend on the adjusting spring, but adopts a constant force mechanism, so that the risk that the use performance of the adjusting spring is changed is avoided, the use stability of the balance piston type constant pressure valve is improved, the fluid output pressure of the balance piston type constant pressure valve is accurate, the fluid output pressure can be known when the constant force value of the constant force mechanism is set, the fluid output pressure is always stable along with the automatic adjustment of the first piston during use, and the use effect is obvious.
Drawings
Fig. 1 is a schematic structural diagram of an embodiment of a balanced piston type constant pressure valve according to the present invention.
In the figure: 1. a first seal ring; 2. plugging with a thread; 3. a second seal ring; 4. a third seal ring; 5. an air inlet pipe; 6. a fourth seal ring; 7. a balance piston; 8. a first limit ring; 9. a valve body; 10. a communicating pipe; 11. a fifth seal ring; 12. a sixth seal ring; 13. a vacuum piston; 14. a housing; 15. a second stop collar; 16. a piston rod; 17. a first air inlet; 18. a second air inlet.
Detailed Description
The embodiment of the balanced piston type constant pressure valve is shown in fig. 1 and comprises a constant force mechanism and a balanced constant pressure mechanism which are arranged left and right, wherein the balanced constant pressure mechanism comprises a valve body 9, an air inlet pipe 5, a balanced piston 7, a piston rod 16, a communicating pipe 10, a first limiting ring 8 and sealing rings, and the constant force mechanism comprises a shell 14, a vacuum piston 13, a plug 2, a second limiting ring 15 and sealing rings.
The axis of the valve body 9 extends along the left-right direction, the valve body 9 is a cylindrical structure with a closed left end and an open right end, a fluid inlet and a fluid outlet for fluid to flow in and out are arranged on the valve body 9, the fluid outlet is formed by the openings at the upper right end of the valve body 9, and the right end of the valve body 9 can be directly connected with a low-pressure gas transmission pipeline. The fluid inlet is a first air inlet 17 arranged on the wall of the valve body 9, the axis of the first air inlet 17 is perpendicular to the axis of the valve body 9, an air inlet pipe 5 which is coaxial with the first air inlet 17 is further welded and fixed on the outer wall of the valve body 9, and the other end of the air inlet pipe 5 can be directly connected with a high-pressure pipeline.
The guide sliding seal is equipped with the first piston that has piston rod 16 in the inner chamber of valve body 9, this first piston is balanced piston 7, balanced piston 7 also is left end closure, the open tubular structure of right-hand member, set up the piston import and the piston export of intercommunication first air inlet 17 and fluid outlet on balanced piston 7, wherein the piston export comprises the uncovered of balanced piston 7 right-hand member, the piston import is for seting up the second air inlet 18 on the section of thick bamboo wall of balanced piston 7, have the piston chamber of intercommunication second air inlet 18 and piston export in the balanced piston 7.
The second inlet port 18 is used to coincide with and face the first inlet port 17 on the valve body 9, so as to form a certain opening degree for fluid to flow into the valve body 9, and the inner diameters of the first inlet port 17 and the second inlet port 18 are equal. In order to ensure the sealing performance, a third sealing ring 4 and a fourth sealing ring 6 are respectively arranged between the balance piston 7 and the inner wall of the valve body 9, and the third sealing ring 4 and the fourth sealing ring 6 are respectively positioned at the left side and the right side of the second air inlet 18.
Communicating ports are respectively formed in the left side and the right side of the balance piston 7 on the barrel wall below the valve body 9, a communicating pipe 10 is fixedly welded between the two communicating ports, the pipe diameter of the communicating pipe 10 is equal to the inner diameter of the communicating ports, and the communicating pipe 10 communicates with a rod chamber and a rodless chamber in the left side and the right side of the balance piston 7, so that the pressure intensity of the rod chamber and the pressure intensity of the rodless chamber are kept consistent. Therefore, after the fluid enters the piston cavity through the air inlet pipe 5, the first air inlet 17 and the second air inlet 18, a part of the fluid is discharged out of the valve body 9 and flows to the low-pressure air transmission pipeline at the downstream, and the other part of the fluid reaches the rod cavity at the left side of the balance piston 7 through the communicating pipe 10, so that the fluid pressure of the cavities at the left side and the right side of the balance piston 7 are kept equal.
The piston rod 16 of the balance piston 7 is relatively long and extends to penetrate out of the left closed end of the valve body 9, the piston rod 16 is in guiding sliding sealing fit with the valve body 9, and therefore the second sealing ring 3 is arranged between the inner hole of the valve body 9 and the piston rod 16.
The left end of the valve body 9 on one side with the rod cavity is in a stepped shaft shape, the small-diameter section of the valve body is a threaded section, a threaded hole is formed in the right end of a shell 14 of the constant force mechanism, and the shell 14 is fixedly connected with the valve body 9 through threads. The left end of the shell 14 is provided with a communication opening communicated with the atmosphere, the right end is a shell bottom, the shell bottom is also the bottom end of the threaded hole, and after the shell 14 is in threaded connection with the valve body 9, the shell bottom is in contact with the left end face of the valve body 9. The piston rod 16 extends out of the valve body 9 through the housing bottom and into the interior of the housing 14, the piston rod 16 being in a guided sliding sealing engagement with the housing bottom, so that a fifth sealing ring 11 is arranged between the piston rod 16 and the interior bore of the housing bottom.
The inner cavity of the housing 14 is equipped with a second piston in a guiding sliding sealing way, the second piston is a vacuum piston 13, the vacuum piston does not mean that the piston is vacuum, but the space between the vacuum piston 13 and the housing bottom is vacuum, in order to facilitate the vacuum-pumping operation, a plug 2 is detachably connected to the housing bottom of the housing 14, when the plug 2 is detached, the vacuum-pumping operation can be facilitated, so that the gas pressure between the vacuum piston 13 and the housing bottom can be detached or exhausted, the pressure of the part is zero, and after the plug 2 is installed, the vacuum state can be maintained, therefore, the plug 2 is equivalent to a pressure relief valve. In order to ensure good sealing effect, a first sealing ring 1 is arranged between the plug 2 and the inner hole of the shell bottom, and a sixth sealing ring 12 is arranged between the vacuum piston 13 and the inner wall of the shell 14.
The vacuum piston 13 and the piston rod 16 are in pushing fit, and in order to facilitate the fit, a pushing hole for accommodating the end of the piston rod 16 is formed in the end face of the vacuum piston 13 facing the piston rod 16.
The valve body 9 is internally provided with a second stopping structure for limiting the moving limit of the balance piston 7 to move rightwards, the second stopping structure can prevent the balance piston 7 from being separated from the valve body 9, in this embodiment, the second stopping structure is a first limiting ring 8 which is in threaded connection with the inner wall of the valve body 9, and when a first air inlet 17 on the valve body 9 and a second air inlet 18 on the balance piston 7 completely correspond to each other, namely the opening degree of the air inlets is maximum, the distance between the balance piston 7 and the first limiting ring 8 is very small, and at this time, the distance that the balance piston 7 can move rightwards is very limited. Of course, in other embodiments, when the opening degree of the air inlet is the maximum, the balance piston 7 and the first limit ring 8 may have a sufficient distance therebetween, or the second stopping structure is a limit pin disposed on the inner wall of the valve body 9, at this time, when the opening degree of the air inlet is the maximum, the balance piston 7 and the limit pin may be directly stopped and engaged, and the balance piston 7 cannot move rightward.
The housing 14 is provided with a first stop structure for limiting the movement limit of the vacuum piston 13 to move leftward, and the first stop structure can prevent the vacuum piston 13 from coming out of the housing 14, in this embodiment, the first stop structure is a second limit ring 15 screwed in the inner cavity of the housing 14, and the central hole of the second limit ring 15 forms a communication hole communicated with the atmosphere, but in other embodiments, the first stop structure can also be a limit pin arranged in the inner cavity of the housing 14.
The working principle of the balance piston type constant pressure valve is as follows: the constant pressure valve is used for being installed at a wellhead of a liquid gas well, replaces an existing adjusting spring type pressure reducing valve, throttles and reduces pressure of high-pressure liquid gas fluid, and keeps the pressure of the output fluid at a constant value. When the constant pressure valve is used, the air inlet pipe 5 is connected with a high-pressure pipeline, the right end opening of the valve body 9 is connected with a low-pressure air transmission pipeline, the initial state of the constant pressure valve is as shown in fig. 1, when high-pressure fluid is not introduced, the first air inlet 17 and the second air inlet 18 completely correspond to each other, the opening degree of the air inlets is the largest at the moment, it needs to be explained that the vacuum piston 13 is also basically located at the rightmost end of the shell 14 at the moment, namely, the space for the vacuum piston 13 to move rightwards is very limited, and at the moment, even if the first limit ring 8 is not arranged on the valve body 9, the vacuum piston 13.
When high-pressure liquid-gas fluid enters the piston cavity through the air inlet pipe 5, the first air inlet 17 and the second air inlet 18, the pressure in the piston cavity and the valve body 9 is instantly increased, the fluid enters the rod cavity on the left side of the balance piston 7 through the communication pipe 10, the pressure in the chambers on the left side and the right side of the balance piston 7 is equal, the pressure is P, the difference between the left force and the right force of the balance piston is determined to be left according to the condition that the force F is P A, the cross-sectional area of the piston is multiplied by P, and the force to the right force is multiplied by (the cross-sectional area of the piston-the cross-sectional area of the piston rod 16) multiplied by P, so that the balance piston 7 moves to the left, and the resultant force is the cross-sectional area multiplied.
After the balance piston 7 moves to the left, the vacuum piston 13 will be pushed by the piston rod 16, and for the vacuum piston 13, because the space between the vacuum piston and the bottom of the housing 14 is vacuum, the left force is only the thrust of the balance piston 7, and the right force is the atmospheric pressure x the cross-sectional area of the balance piston 7.
Of course, during the leftward movement of the balancing piston 7, the first inlet port 17 and the second inlet port 18 are gradually staggered, and the opening degree of the inlet ports gradually decreases, so that the pressure in the piston chamber gradually decreases, that is, the leftward resultant force on the balancing piston 7 gradually decreases, and when the pressure decreases to a certain degree, it is assumed that the pressure decreases to P1At this time, the cross-sectional area of the piston rod 16 is multiplied by P1When the pressure of the balance piston 7 is equal to the atmospheric pressure multiplied by the cross-sectional area of the balance piston 7, the balance piston 7 is stressed and is not moved any more, the opening degree of the air inlet is not changed any more, and the output pressure of the valve body 9 is stabilized at P1。
The pressure regulating and reducing process is carried out spontaneously without any external force driving and intervention, and the final output pressure P is constant due to the atmospheric pressure of 0.1MPa1When the cross-sectional area of the balance piston 7/the cross-sectional area of the piston rod 16 is equal to 0.1 × the cross-sectional area of the balance piston 7, it appears that the output pressure is completely determined by the ratio of the cross-sectional areas of the balance piston 7 and the piston rod 16, and under the condition that the structural sizes of other parts are not changed, the ratio of the cross-sectional areas of the balance piston 7 and the piston rod 16 is only changed to obtain a certain constant output pressure, so that the design time can be controlled by controlling the balance piston 7The cross-sectional area ratio of the piston rod 16 is used to obtain an optimal set output pressure, the larger the ratio, the larger the set output pressure, and vice versa.
In this embodiment, since the constant force mechanism and the balance constant pressure mechanism are in threaded connection, when the set output pressure needs to be adjusted, different output pressure values can be obtained only by completely disassembling the whole constant force mechanism and replacing the constant force mechanism with a balance piston of another specification, so that during manufacturing, a plurality of sets of constant force mechanisms can be manufactured, and the difference between different constant force mechanisms is the difference of the cross-sectional areas of the vacuum pistons.
When the pressure of the high-pressure fluid in the air inlet pipe 5 is always stable, the balance piston 7 is always kept in a balance state, the opening degree of the air inlet cannot be changed, and the output pressure is continuously kept stable. However, when the pressure of the high-pressure fluid in the intake pipe 5 is unstable, for example, when the pressure of the high-pressure fluid suddenly rises, the pressure in the piston cavity also increases instantaneously, the equilibrium state of the balance piston 7 is broken, the balance piston 7 moves to the left, the opening degree of the intake port decreases again, the pressure in the piston cavity decreases, and finally the balance piston 7 reaches balance again, so that the output pressure is always kept at the set value.
When the pressure of the high-pressure fluid is suddenly reduced, the pressure in the piston cavity is also instantaneously reduced, the balance state of the balance piston 7 is broken, the balance piston 7 moves rightwards, the opening degree of the air inlet is increased, the pressure in the piston cavity is increased, and finally the balance piston 7 is balanced again, so that the output pressure is always kept at a set value.
The circulation is repeated in this way, no matter what the pressure of the high-pressure fluid is, as long as the ratio of the cross-sectional areas of the balance piston 7 and the piston rod 16 is certain, the opening degree of the air inlet can be changed by the left and right movement of the balance piston 7, finally, the balance piston can be adjusted to be in a balance state, and meanwhile, the value of the output pressure is always constant, so that constant-pressure output is realized.
Of course, the self-adjusting process is related to the size of the first and second intake ports 17 and 18 and the pressure of the high-pressure fluid, besides the cross-sectional area ratio of the balance piston 7 to the piston rod 16, for example, if the pressure of the high-pressure fluid is suddenly increased, the balance piston 7 moves to the left quickly, if the pressure generated by the atmospheric pressure is hard to keep the balance piston balanced, the balance piston may block the first intake port 17, the opening of the intake port becomes 0, and the fluid may be blocked. However, after the part of the fluid is discharged from the valve body 9 and the low-pressure gas transmission pipeline, the balance piston moves rightwards again under the action of atmospheric pressure, the opening degree of the gas inlet is increased, and the fluid can enter the piston cavity.
According to the current production practice, the pressure of the liquid-gas fluid reaching the wellhead is generally dozens of megapascals, and the expected output pressure is about 4MPa, so that the pressure floating of the liquid-gas fluid is considered when the sizes of the first air inlet 17 and the second air inlet 18 are designed, the situation that the first air inlet 17 and the second air inlet 18 are completely staggered can be avoided, namely the air inlets always have certain opening degrees in the process that the balance piston moves left and right, and the situation that the liquid-gas fluid is cut off by a constant pressure valve to influence normal production is avoided.
Then, as mentioned above, the vacuum piston 13 is relatively close to the bottom of the housing 14, and there is no room for the balance piston 7 to move to the right, so that it is considered that, if the pressure of the liquid-gas fluid is lower than the set output pressure value, the atmospheric pressure will push the balance piston 7 to move to the right until the opening of the gas inlet becomes 0, so that the fluid is stopped, and thus the normal production cannot be performed. Therefore, the vacuum piston 13 is closer to the bottom of the shell 14, and the balance piston 7 has no space for moving rightwards, so that in case that the pressure of the liquid-gas fluid is lower than the set output pressure value, the fluid can directly enter the low-pressure gas transmission pipeline through the constant-pressure valve, and the constant-pressure valve is similar to an intermediate connecting pipe and does not play a role in pressure regulation.
In other embodiments of the balanced piston constant pressure valve: a second stop structure for preventing the first piston from falling off the valve body is not arranged in the valve body; the first stopping structure for preventing the second piston from falling off the shell is not arranged in the shell; the inner diameters of the piston inlet on the first piston and the fluid inlet on the valve body can also be unequal, for example, the inner diameter of the piston inlet is smaller than the inner diameter of the fluid inlet; the bottom of the shell can be provided with no plug, for example, the shell can be vacuumized through an atmospheric communication port and then assembled with a second piston; the valve body may not be a cylindrical structure with one end open and the other end closed, for example, both ends are closed, and one end of the valve body is provided with a small fluid outlet, or the fluid outlet is also arranged on the cylinder wall; the first piston also can not be a cylindrical structure with one open end and the other closed end, for example, the inner diameters of the piston inlet, the piston outlet and the piston cavity are all equal and are all smaller than the size of the end surface of the piston; the pushing hole formed in the end face, facing the piston rod, of the second piston can also be a threaded hole, and the second piston is firstly in threaded connection with the piston rod and then in pushing fit; the end surface of the second piston facing the piston rod can be not provided with a pushing hole, and the second piston can be directly matched with the piston rod in a pushing way; the constant force mechanism may also be another constant force device connected to the piston rod, such as an adjustable constant force output device disclosed in the chinese patent application with application publication No. CN103723648A, or a constant force output device that is not affected by disturbance of the air tube, such as one disclosed in the chinese patent application with application publication No. CN103511392A, or other types of constant force devices.
Claims (2)
1. The utility model provides a balanced piston formula constant pressure valve, includes the valve body, its characterized in that: the valve body is provided with a fluid inlet and a fluid outlet, a first piston with a piston rod is assembled in the valve body in a guiding sliding mode, the first piston is provided with a piston inlet and a piston outlet which are communicated with the fluid inlet and the fluid outlet, so that the pressure of the fluid outlet on the valve body can be adjusted through the movement of the first piston, the resultant force of fluid on the first piston, which is received by the first piston in the valve body, faces to one side of the rod cavity, the valve body is provided with a communicating pipe which is communicated with the rod cavity and the rodless cavity at two sides of the first piston, the piston rod of the first piston extends out of the valve body and is connected with a constant force mechanism, the constant force mechanism can apply a constant force opposite to the resultant force direction to the piston rod, the valve body is of a cylindrical structure with one end open and the other end closed, the opening forms the fluid outlet of the valve body, the fluid inlet is arranged on, The other end of the first piston is closed, the opening forms a piston outlet of the first piston, the piston inlet is formed in the cylinder wall of the first piston, and a piston cavity communicated with the piston inlet and the piston outlet is formed in the first piston.
2. The balanced piston constant pressure valve according to claim 1, wherein: the piston inlet on the first piston is equal in inner diameter to the fluid inlet on the valve body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811466170.3A CN109654269B (en) | 2017-02-03 | 2017-02-03 | Balance piston type constant pressure valve |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710063345.5A CN107061817B (en) | 2017-02-03 | 2017-02-03 | A kind of trequency piston type constant pressure valve |
| CN201811466170.3A CN109654269B (en) | 2017-02-03 | 2017-02-03 | Balance piston type constant pressure valve |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710063345.5A Division CN107061817B (en) | 2017-02-03 | 2017-02-03 | A kind of trequency piston type constant pressure valve |
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| Publication Number | Publication Date |
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| CN109654269A CN109654269A (en) | 2019-04-19 |
| CN109654269B true CN109654269B (en) | 2020-03-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201811466170.3A Active CN109654269B (en) | 2017-02-03 | 2017-02-03 | Balance piston type constant pressure valve |
| CN201710063345.5A Active CN107061817B (en) | 2017-02-03 | 2017-02-03 | A kind of trequency piston type constant pressure valve |
| CN201811467064.7A Active CN109707885B (en) | 2017-02-03 | 2017-02-03 | Balance piston type constant pressure valve |
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| CN201811467064.7A Active CN109707885B (en) | 2017-02-03 | 2017-02-03 | Balance piston type constant pressure valve |
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| CN109424332B (en) * | 2017-08-21 | 2021-09-03 | 中国石油化工股份有限公司华北油气分公司石油工程技术研究院 | Natural gas well constant pressure throttling arrangement |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN109707885A (en) | 2019-05-03 |
| CN107061817B (en) | 2019-01-22 |
| CN109654269A (en) | 2019-04-19 |
| CN109707885B (en) | 2020-04-07 |
| CN107061817A (en) | 2017-08-18 |
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