Internal safety valve assembly to be used with load regulators

FIELD: machine building.

SUBSTANCE: load regulator including an internal safety valve assembly comprises a casing having a loading diaphragm set between the first shell and the second shell. The first shell and the first side of the loading diaphragm form the first chamber and the second shell and the second side of the loading diaphragm form the second chamber. The unit of the safety valve is connected to the loading diaphragm. The unit of the safety valve comprises a safety valve seat fitted by a hole which forms a passage providing for hydraulic connection of the first chamber and the second chamber, and a safety valve gate connected so that it is able of moving together with the safety valve seat. The safety valve gate can move from the safety valve seat to the outlet position providing for the flow of fluid medium between the first chamber and the second chamber as a response to the output pressure that dramatically exceeds the pressure at which the load regulator moves into closed position.

EFFECT: higher reliability of a device.

23 cl, 11 dwg

 

The technical field to which the invention relates.

The present invention relates generally to controllers for fluid medium and, more specifically, to an internal relief valve device for use with load controllers.

The level of technology

In control systems of technological processes use different field devices to control the process parameters. Regulators for fluid widespread in all control systems of technological processes to manage the pressures of a different fluid (e.g., liquids, gases, and so on). Regulators for fluid typically used to convey pressure fluid to a smaller value and/or substantially constant value. In particular, the regulator for a fluid medium has an input opening, which usually takes the fluid with a relatively high pressure, and provides relatively low and/or essentially constant pressure in the exit hole.

When moving process fluid with high pressure through the control technology regulator reduces the pressure of the fluid medium at least at one point and delivers this fluid environment having a low or negative pressure in the subsystem or other acceptance points. For example, the gas regulator, associated with piece of equipment (e.g., copper)may accept gas with a relatively high pressure, from the gas source and can bring the gas to a low, essentially constant pressure suitable to enable its safe and effective use of equipment.

To prevent situations in which the pressure downstream of the flow (i.e. the pressure at the exit hole) reaches dangerous levels, the regulators for fluid typically contain devices for protection against excessive pressure. Devices for protection against excessive pressure is functionally connected to the controller for the fluid and come into force (for example, if the pressure downstream of the fluid flow exceeds a specified value) to prevent unwanted (e.g., dangerous) increasing the pressure in the source located downstream flow. Some devices for protection against excessive pressure (such as disable device) interrupt the flow of process fluid is directed to the source located downstream of the flow to the return manually these devices.

However, in some cases, the increase in pressure of a fluid medium, for example due to temperature changes can cause an undesirable reduction in dei is a journey of devices for protection against excessive pressure. To prevent unwanted actuation devices for protection against excessive pressure by some well-known spring-loaded regulators for fluid contain an internal relief valve, which is made in one piece with the regulator for a fluid medium. Internal relief valve releases of process fluid environment, such as atmosphere, while increasing the pressure of process fluid, for example due to temperature changes. If the pressure of the process fluid downstream of the flow exceeds the set internal pressure relief valve, this valve opens and releases the fluid into the atmosphere. Device for protection against excessive pressure comes into effect, if the pressure at the exit hole exceeds the pressure in spite of the production fluid through the internal relief valve. Examples of such known spring-loaded regulators that contain an internal relief valve, are regulators series S201 and S202, produced by Fisher International.

Some well-known regulators, such as regulators with pressure, not releasing the fluid into the atmosphere, and as a result, internal pressure relief valve cannot be made in one piece with the regulator. In these controllers is the ora with a load of additional external pressure relief valve is used to prevent unwanted actuation or frequent switching devices for protection against excessive pressure, for example due to temperature changes in the process fluid. However, for such external relief valve often requires additional installation works, pipe-laying, production costs, supply of materials and service, which leads to increased costs.

Disclosure of inventions

In one implementation options of the load regulator with internal relief valve device includes a housing, in which between the first shell and the second shell is loading aperture. The first shell and the first side of the load of the diaphragm to form the first chamber and the second shell and the second side of the load of the diaphragm to form a second camera. Device for the pressure relief valve is connected with the loading aperture. Device for the safety valve contains the seat of the safety valve having an opening which forms a passage for the hydraulic connection of the first and second chambers, and the bolt relief valve connected to move with the seat of the safety valve. The bolt relief valve moves in the direction from the seat of the safety valve in the exhaust position and thereby provides the possibility of leakage of fluid between the first chamber and veronneau in response to the output pressure, which is significantly more than the pressure at which the load controller moves to the closed position.

In another implementation, the load controller having internal structure for the pressure relief valve includes a diaphragm located in the body of the regulator between the first chamber and the second chamber and configured to move at least between a first position, second position and third position in response to pressure of the process fluid that is detected by the second camera. Saddle pressure relief valve connected to the diaphragm so that the saddle valve and the diaphragm moves between the first position, second position and third position, with the seat of the safety valve has an opening forming a passage for the hydraulic connection of the first and second chambers. The bolt relief valve connected to the slidable seat of the safety valve to communicate with the hole and prevents the flow of fluid between the first and second chambers when the diaphragm and the seat of the safety valve is moved between the first and second positions; and in response to the pressure at the exit hole, which is significantly more than the pressure at which the load controller includes the closed position, the bolt relief valve moves in the direction from the seat of the safety valve in the third position and allows flow of fluid between the first and second chambers.

In another variant implementation of the internal relief valve device for use with load controllers contains the seat of the safety valve having a cylindrical housing and the first flange part. The first flange portion includes a support surface, which interacts with the first side of the diaphragm, if the device for the pressure relief valve is in the closed position, and moves away from the first side of the diaphragm when the load regulator is in the exhaust position. Between the second flange part of the saddle valve and part of the load regulator is bias element. Shifting element shifts the first side of the diaphragm in the direction of the support surface. The limiter move is at least within a part of the load controller and communicates with the seat of the safety valve so that the interaction limiter move and seat of the safety valve causes movement of the supporting surface in the direction from the first side of the diaphragm when the diaphragm moves in n the Board to stop moving.

In one embodiment, the implementation of an internal device for a safety valve for use with load controllers includes means for providing hydraulic communication between the first and second chambers of the actuator, and the specified second chamber hydraulically connected to the outlet of the load controller. Internal relief valve device further comprises means for controlling the means forming a hydraulic connection, which provides the possibility of leakage of fluid between the first chamber and the second chamber in response to pressure of fluid in the exit hole, which is significantly more pressure corresponding to the onset of closure of the regulator.

Brief description of drawings

Figure 1 shows a known regulator for a fluid with pressure, carried out in conjunction with the known load controller.

Figure 2 shows the cross-section of a known load controller shown in figure 1.

Figure 3 shows a portion of another known load controller, which is implemented with known internal relief valve device.

On figa shows a load controller according to one implementation options with internal relief valve device is creation.

On FIGU shows a cross-section of the load controller shown in figa.

On figa shows a cross-section of the load regulator with internal relief valve device according to another implementation variant.

On FIGU shows another cross-section of the load controller shown in figa.

On figs shows one implementation options of the shutter valve used in the load controller shown in figa and 5B.

On figa shows a cross section of one implementation options of the load regulator with internal relief valve device according to another implementation variant.

On FIGU shows another cross-section of the load controller shown in figa.

7 shows a cross section of one implementation options of the load regulator with internal relief valve device according to another implementation variant.

The implementation of the invention

Usually regulators for fluid transform the flow of fluid in accordance with read by the pressure downstream of the flow and thereby maintain the pressure in the processing system in a valid and/or permanent limits. Regulators for fluid usually contain dia is raga, which is functionally connected with the gate valve by connecting (e.g., arm) to move the gate valve and the valve seat to stop or transmittance of the fluid flow between the inlet and the outlet. Regulators for fluid usually regulate the flow and pressure of the process fluid using the specified control force or load acting on the first side of the diaphragm, and thereby move the shutter valve in the first direction. The second side of the diaphragm is hydraulically connected to the fluid medium in the output hole, and the force with which the acts specified fluid on the diaphragm, causing it to move in a second direction opposite the first direction. Thus, the diaphragm moves the shutter valve in response to a differential between the pressure of the fluid in the output port (i.e. a force acting on the second side of the diaphragm) and specified by the governing force (i.e. a force acting on the first side of the diaphragm and thereby changes the flow through the regulator to achieve essentially constant pressure output.

In one implementation options of the spring controller includes a load element in the form of a bias element (e.g. a spring), which acts on the first side of the diaphragm from the data managing stress. In another implementation, regulator with pressure includes a load element in the form of a load pressure filed by the regulator, which operates with a given regulatory force on the first side of the diaphragm. Regulators with pressure usually provide more precise control of output pressure and at higher costs and higher pressures at the outlet compared with spring controllers. Thus, regulators with pressure are more preferable in comparison with spring controllers, if you want higher precision adjustment of the pressure downstream of the flow (for example, when measuring).

In addition, regulators for fluid medium which have a maximum design pressure of the fluid at the outlet below the maximum design pressure of the fluid at the entrance, usually need protection against excess pressure. In other words, devices for protection against excessive pressure are often necessary for technological applications, in which the inlet pressure exceeds the outlet pressure, and prevent the situation when the pressure of the fluid downstream of the flow exceeds a preset value (for example, dangerous pressure) or becomes greater than the inlet pressure. Device for safe shutdown and devices from which legiunea real values are two types of devices for protection against excessive pressure, used together with regulators for fluid. Device for safe shutdown normally detects the output pressure (pressure downstream of the flow) and closes the regulator for a fluid medium, thereby preventing the flow of fluid through the regulator if the pressure downstream of the flow reaches the preset value. Device to track typically contains a first or working regulator installed in series with the second controller. The second valve is normally detects the pressure downstream of the flow (i.e. the control pressure and controls the pressure downstream of the flow regulator stops working pressure pressure control downstream flow.

In use, the pressure regulator moves to the closed position, thereby preventing the flow of fluid through the regulator, if located downstream flow intake process fluid decreases, and/or a source located downstream of the flow is turned off (i.e. goes essentially to zero consumption). For example, if the consumption of downstream flow is greatly reduced or stopped altogether (for example, in the case of zero flow), the shutter valve in the regulator for fluid tightly interacts with the valve seat, thereby obstructing the twua the flow of fluid through the regulator (i.e. is moved to the closed position). However, in some cases, due to corrosion, damage to the components of the controller, driving sand, pipe scale, etc. the gate valve can be sufficiently pressed against the valve seat, and thus provides the possibility of continuing the flow of process fluid between an inlet and outlet of the regulator and, hence, growth pressure downstream of the flow (for example, regulatory pressure). Devices for protection against excessive pressure-activated if the pressure downstream of the flow is increased to an undesirable level (for example, a dangerous level), and thereby prevent excessive pressure increase in the consumer located downstream flow. Thus, devices for protection against excessive pressure often provide control pressure relief or pressure limiting and thereby prevent deterioration of the technological system, which can be caused by excessive pressure.

If the gate valve is properly pressed (for example, closely) to the valve seat, and the pressure of the fluid between the outlet and the consumer, the downstream flow below a preset safe level of pressure, the device for protection against excessive pressure is not activated. T is m, not less process fluid typically remains captured between the output side of the gate valve of the regulator and the consumer, the downstream flow. In some cases, the pressure of the fluid between the outlet and the consumer, the downstream flow may depend on the pressure increases due to, for example, increasing the temperature of the surrounding air. The increase in pressure indicated captured fluid in the output port may cause an activation device for protection against excess pressure. To prevent unwanted activation of the device for protection against excess pressure due to temperature changes in spring controllers typically include an internal relief valve that relieves pressure at the exit hole or expelling excess fluid to the atmosphere. Device for protection against excessive pressure usually has a pressure setpoint that is higher than the setpoint pressure, internal pressure relief valve that is activated if the pressure of the fluid in the output hole is significantly greater than the pressure setpoint internal relief valve.

However, regulators with pressure not connected with the outside atmosphere, and, thus, internal pressure relief valve may not be integer the van with the main controller. Specified no internal relief valve can cause unwanted or unexpected activation devices for protection against excessive pressure in situations in which the pressure of process fluid in the output hole increases due to, for example, temperature changes, if the regulator is in the closed position. Thus, regulators with pressure usually are not used with devices for protection against excessive pressure, since devices for protection against excessive pressure tends to unwanted activation in such applications. To prevent unwanted activation devices for protection against excessive pressure regulator with pressure is usually to connect with an external relief valve. But this approach requires additional hardware, maintenance, installation work, the workforce and, thus, increasing costs. Alternatively, instead of regulators with pressure and, thus, instead of external safety valves are commonly used automatic controllers indirect action. However, the automatic regulators indirect actions are very complex and therefore relatively expensive.

Some known load regulators contain HV the internal safety valve device, which produces or removes process the fluid, if the process fluid in the output hole of the main controller has a set pressure, which causes the beginning of the lock-load regulator. The controller moves to the closed position when the flow of fluid through the load controller is stopped (for example, if the consumption of downstream flow is essentially zero). However, release or dispose of process fluid into the atmosphere every time you log a load regulator in the closed position or while in the specified position may be undesirable, because the closed position may occur frequently and, thus, into the atmosphere can throw a large number of process fluid. For example, these known load regulators usually are not suitable for technological applications that use hazardous fluid environment (e.g., natural gas), because the relief valve load regulator begins to release or retract process fluid to the atmosphere in the closed position, the load controller or when switching to the specified position. Thus, for applications that use hazardous fluid environment, the preferred safety valve, which does not from what grew in the beginning of the lock-out. In other words, there is a need for a safety valve device having offset pressure and thereby providing a substantial range of insensitivity or significant operational separation between the closed position of the load controller and the descent position of the safety valve.

In practice, load controllers are functionally connected with the main controller for the fluid. As indicated above, the load regulators create pressure, ensuring the specified regulatory effort for the main controller. However, the main valve is normally moves to the closed position (i.e. provides essentially zero flow) when the output pressure of the fluid that is greater than the output pressure of the fluid at which the load controller moves to the closed position. As stated above, the known load regulators containing an internal relief valves, usually begin to produce or to divert the fluid into the atmosphere at the beginning of the closed position of the load controller. As a result, in a situation of excessive pressure load regulator starts to let out or take in the atmosphere of the process the fluid before the closed position of the main regulator. In addition, in these known load regulator is no means of pressure control, wherein the load controller starts the discharge or exhaust of fluid to the atmosphere, so that the final position can be set to activate if the output pressure of the fluid exceeds the pressure of the fluid, which causes the locking of the main controller.

As a result, the inability to control the start point of the pressure relief or installation load of the regulator (i.e. the pressure at which the load controller relieve pressure) causes the load regulator to discharge or take in the atmosphere of the fluid at outlet pressure that is lower than the pressure of the fluid at the outlet, wherein the main controller moves to the closed position. Discharge or dispose of process fluid into the atmosphere every time the load regulator is in the closed position, leads to the release into the atmosphere of large quantities of process fluid. For example, the process fluid can escape into the atmosphere for a long time, if the consumption of downstream flow causes a pressure increase in the exit hole to the level at which the load controller moves to the closed position (and thus begins to release into the atmosphere of the process fluid environment), but which is below the pressure that causes the transition of the main is the slider in the closed position. As a result, regulators with pressure usually are not suitable for technological applications that use hazardous fluid medium (e.g., natural gas). Thus, it is preferable to load the controller has performed the reset pressure, if the pressure of the fluid at the outlet is close to the pressure that causes the transition to the closed position as the load controller and the main controller. In addition, the configuration load controller to transition to the closed position when the pressure that is greater than the pressure that causes the transition of the main regulator in the closed position, is undesirable because of the load, the regulator has the tendency to self-regulation of fluid and takes control of the pressure downstream of the flow and thus carries out unwanted and/or inappropriate management of pressure downstream of the flow.

Internal relief valve device according to one of the variants of implementation, described herein, provides for the offset of the pressure activated safety valve by forming a substantial range of insensitivity or significant separation between the outlet pressure of the main regulator, which takes place or begins closed position load, the loading regulator, and outlet pressure of the main regulator, which takes place or begins the position of the pressure relief or point of discharge internal relief valve. In addition, an internal relief valve device according to one of the variants of implementation, described herein, provides for the offset of the pressure between the outlet pressure of the main regulator, which takes place or begins closed position of the main regulator and outlet pressure of the main regulator, which takes place or begins the reset internal relief valve, part of the load of the regulator. In other words, an internal relief valve device according to one of the implementation options described here, controls the displacement of the pressure between the pressure of the fluid at the output, which causes the start position reset internal relief valve device and the pressure of the fluid at the output, which causes the beginning of a closing load of the regulator and/or the main controller. In the described implementation, the offset pressure is set so that the pressure at which the internal pressure relief valve load control is set to reset, was much more pressure on the output, when the cat the rum principal regulator is in the closed position, and the outlet pressure at which the load regulator is in the closed position.

Thus, the described safety valve device according to one implementation options provides an adjustable force for a given pressure relief valve, so that activation of the specified relief valve can be carried out at different predetermined pressures of the fluid at the outlet. In addition, an internal relief valve device according to one of the variants of implementation, described herein, may preferably be integrated with regulators, pressure to provide increased accuracy by a significant minimize unwanted discharge or diversion in the atmosphere of the process fluid and/or prevent unwanted or unexpected activation devices for protection against excessive pressure, which is functionally connected with load controllers and/or primary regulators. Thus, the safety valve device according to one of the implementation options described here provides the use of devices for protection against excessive pressure together with regulators with pressure without the use of external safety valve.

Before discussing Podrobnosti the internal relief valve device according to one implementation options describes the known example of the controller 100 with the load pressure to the fluid, shown in figure 1. As shown in figure 1, a known regulator 100 includes a known regulator 102 to the load pressure, which provides regulatory pressure or load to the primary controller 104. External relief valve 106 is hydraulically connected with the main controller 104 so that the controller 100 could be used with hazardous process fluid medium, such as, for example, natural gas. The device 108 for protection against excess pressure can also be hydraulically connected to the controller 100. External relief valve 106 may be hydraulically connected between the controller 104 and device 108 to prevent unexpected activation device 108. However, the external pressure relief valve 106 requires additional installation works, supply of materials, labor, maintenance, etc. which increase costs. In another embodiment of the invention instead of the controller 102 and the outer valve 106 may be used the automatic regulator with a control channel. However, such known automatic controllers with the control channel are more complex and expensive.

As shown in figure 1, the main controller 104 according to one implementation options contains the actuator 110, which is functionally connected to the valve 112, with input from Erste 114 and the outlet 116. The actuator 110 includes a node 118 main diaphragm located between the first housing 120 of the actuator and the second casing 122 of the actuator. The first housing 120 forms a load chamber 124 and the second housing 122 forms a control chamber 126. The controller 102 has an input load hole 128, hydraulically connected to the inlet 114 of the valve 112, and the output load of the hole 130, which is in hydraulic communication with the load chamber 124 and provides the load pressure in the load chamber 124.

The valve 112 includes a housing 132 of the valve, which is connected with the lower casing 122 of the actuator. The saddle 134 valve accommodated in the housing 132 of the valve and forms a working hole 136 through which fluid can flow between the inlet 114 and outlet 116. The shutter valve 138, which is connected with the first end 140 of the piston rod 142 of the valve, contain sealing disk 144 (for example, an elastic sealing disk), which is activated and interacts with the saddle 134 and thereby prevents leakage of fluid between the inlet 114 and outlet 116. Guide rod 146 combines the rod 142 of the valve and the sealing disk 144 at least one of the lower housing 122 of the actuator body 132 of the valve and valve seat 134. Not shown on the drawing guide 146 includes at least one passage located in the hydraulic is communication with the outlet 116 and the camera 126 regulatory pressure.

Node 118 of the diaphragm includes an aperture 148 which supports the plate 150 of the diaphragm and which has a first side or surface 152 that is open to load the camera 124, and a second side or surface 154 that is open to the chamber 126 regulatory pressure. Aperture 148 is functionally connected to the gate 138 by means of the rod 142 and the lever 156 and causes the shutter 138 to move in the direction of the saddle 134 and thereby prevents leakage of fluid between the inlet 114 and outlet 116, when the diaphragm 148 is moved in the direction to the camera 126. The lever 156 is connected to the aperture 148 through plate 150 and node 160 hours pusher. The first end 162 of the node 160 hours follower interacts with the second side 154 of the diaphragm 148 through plate 150, and the second end 164 of the node 160 is functionally connected with the closing spring 166 through the slot of the spring or screw 168, made with the possibility of regulation. The closing spring 166 is located in the housing 170 for the spring between the adjustable slot 168 for spring and the second socket 172 for spring (for example, Cabinet body portion 170 for spring). The closing spring 166 provides a predetermined load or force that moves the aperture 148 in the direction of the load chamber 124 via node 160 hours pusher, which in turn causes peremeshany the shutter 138 of the valve in the direction to seat valve 134, thus preventing the flow of fluid through the valve 112 (e.g., in the closed position). The force with which a closing spring 166 may be selected (e.g., increased or decreased) by means of an adjustable socket 168. In addition, the plate 150 includes a passage or bypass hole 174, which provides the hydraulic connection of the load chamber 124 and chamber 126 regulatory pressure and, thus, the hydraulic connection of the load of the outlet 130 of the controller 102 and the outlet 116 of the main regulator 104.

On figa shows a cross section of a known load controller 102 shown in figure 1. As shown in figures 1 and 2, the controller 102 includes an upper housing 202 and lower housing 204, which are connected together by means of connecting elements 206. Load aperture 208 is located between the upper housing 202 and lower housing 204. The upper housing 202 and the first side 210 of the load of the diaphragm 208 to form the first chamber 212. Load spring 214 is located between the first slot 216 and second adjustable socket 218. In the shown embodiment, the first chamber 212 hydraulically connected, for example, with the atmosphere.

The first slot 216 for spring connected to the plate 220 of the load of the diaphragm, which supports the load of the aperture 208. Regulus is Thor 222 load spring (for example, screw) communicates with the second slot 218 and thereby provides the length of the load spring 214 (e.g., compresses or releases the load spring 214) and, thus, choice (e.g., increase or decrease) the value of a given force or load at which the load spring 214 acts on the first side 210 of the load of the diaphragm 208.

The lower housing 204 and the second side 224 of the load of the diaphragm 208 at least partially form a second chamber 226, the load inlet 128 and load the hole 130. The second chamber 226 hydraulically connected to the load output aperture 130 through channel 228 and, thus, is in hydraulic communication with the load chamber 124 (Fig 1) main controller 104. The saddle 230 load valve is located in the lower housing 204 and forms a working hole 232 between the load inlet 128 and load the outlet 130. The shutter 234 load valve functionally connected to the load aperture 208 through the load shaft 236 of the valve plate 220 of the load of the diaphragm. The second spring 238 is located between the second slot 240 and gate 234 and moves the shutter 234 in the direction of the seat 230. The stiffness of the second spring 238 is usually significantly less than the stiffness of the load spring 214. In the example shown, the second end 242 is zagruzochnogo rod 236 contains soft or resilient seat 244, which communicates with the connecting seat 246, connected to a plate 220 of the load of the diaphragm.

As shown in figures 1 and 2, in use the inlet 114 is in hydraulic communication with, for example, gas source, which delivers the fluid at a relatively high pressure. The outlet 116 of the valve 112 is in hydraulic communication with the downstream flow to the consumer or other intermediate device consuming process fluid environment with the required (low) pressure.

The controller 102 typically regulates inlet pressure of the fluid in the inlet port 114 and thereby provides or produces the required load pressure in the load chamber 124 of the main controller 104. To achieve the necessary load pressure of the load spring 214 has a shutter 234 load relative to the valve seat 230 in such a way as to restrict the flow of fluid between the load inlet 128 and load the outlet 130. Thus, the load pressure depends on the force with which the load spring 214 acts on the load aperture 208 and, thus, the shutter 234, determining its position relative to the seat 230. The setpoint is required at the times of pressure can be selected regulatory power, with which the load spring 214 acts on the first side 210 of the diaphragm 208 by means of an adjusting screw 222.

With increasing consumption in the output hole 116, the pressure of the fluid in the output hole 116 is immediately reduced. The second chamber 226 controller 102 detects the reduction of the pressure of process fluid in the output aperture 116 through the channel 228 and bypass hole 174. Thus, when reducing the pressure of process fluid in the load output hole 130 and, consequently, decreasing the force acting on the second side 224 of the diaphragm 208, which must be less than the specified power for a load spring 214 acts on the first side 210 of the diaphragm 208, the specified load spring 214 causes the moving load of the diaphragm 208 toward the second chamber 226. If the load aperture 208 is moved toward the second chamber 226, the shutter 234 withdraws from the seat 230 and thereby provides the possibility of leakage of fluid through the working hole 232 between the load inlet 128 and load the outlet 130 (for example, in the open position) and thus causes a pressure increase in the load output hole 130.

The main controller 104 provides the load pressure in the load chamber 124. In turn specified agrozone pressure acts on the first side 152 of the diaphragm 148 and causes movement of the diaphragm 148 in the direction to the camera 126 regulatory pressure (for example, in the downstream direction relative to figure 1). If the diaphragm 148 is moved in the direction to the camera 126, the aperture 148 causes the lever 156 to move the shutter 138 in the direction from seat 134 and thereby provides the possibility of leakage of fluid through the working hole 136 between the inlet 114 and outlet 116 to meet the needs of the consumer, which is located downstream of the stream.

On the contrary, by reducing or disabling consumption in the output hole or downstream of the flow pressure of process fluid in the specified output hole 116 is increased. Increasing the pressure at the exit hole 116 is detected by the second chamber 226 of the controller 102 through the bypass hole 174 in plate 150 and the channel 228. The pressure at the exit orifice acts on the second side 224 of the load of the diaphragm 208. The force acting on the second side 224, overcomes the force with which the load spring 214 acts on the first side 210, when the pressure of the fluid in the load output hole 130 acts on the second side 224 of the load aperture 208 with a force that exceeds the force with which the load spring 214 acts on the first side 210 of the load of the diaphragm 208. In this case, the load aperture 208 is moved toward the first chamber 212, and thereby causes p is Emesene shutter 234 in the direction of the saddle 230, and thereby restricts the flow of fluid through the working hole 232. The second spring 238 moves the shutter 234, whereupon the specified shutter tightly interacts with the saddle 230 (for example, in the closed position), being thus preventing the flow of fluid through the working hole 232 between the load inlet 128 and load the outlet 130, and thus reduces the supply of the load pressure in the load chamber 124.

The controller 102 is in the closed position when the shutter 234 tightly interacts with the saddle 230 and provides a reliable seal and thus prevents the flow of fluid through the working hole 232 between the load inlet 128 and load the outlet 130. In the load pressure in the load chamber 126 is reduced. Thus, in the closed position, the force acting on the second side 154 of the diaphragm 148 through the second chamber 126 due to the increased pressure of the fluid in the output hole 116, causes movement of the diaphragm 148 in a direction to load the camera 124 (i.e. in an upward direction relative to the drawing). Moving the aperture 148 in the direction towards the first chamber 124 causes the lever 156 to move the shutter 138 in the direction of the saddle 134 of the valve 112. The closing spring 166 moves the aperture 148 in which upravlenii to the first chamber 152 (for example, up) and forces the bolt 138 to sealed engagement with the seat 134, thereby preventing leakage of fluid between the inlet 114 and outlet 116. The main controller 104 is in the closed position when the shutter 138 tightly interacts with the saddle 134 and thereby provides essentially zero flow through the main regulator 104 (i.e., from the inlet 114 to the outlet 116). The controller 102 is locked when the pressure of the fluid in the exit hole that is less than the pressure of the fluid in the output hole, causing the locking of the primary controller 104. Otherwise, the controller 102 seeks to regulate the fluid and takes control of the pressure downstream of the flow if the primary controller 104 is locked when the pressure of fluid that is less than the pressure of the fluid at which locked the controller 102, and thus creates unwanted and/or inappropriate regulating the pressure downstream of the flow. If the shutter 138 tightly interacts with the saddle 134, between the outlet 116 and the consumer, the downstream flow (not shown), remains trapped compressed air.

In some cases, due to corrosion, damage to the components of the regulator, zapesochivaniya, pipe scale, and so on, the gate 138 of the valve core reg the Torah 104 may not provide a reliable seal when interacting with the saddle valve 134. The result of processing fluid from the high pressure from the inlet 114 will continue to flow to the outlet 116. Therefore, the pressure downstream of the flow in the exit hole 116 will grow (despite the fact that the valve 112 is in the closed position), as the consumption of the consumer, downstream flow, significantly reduced (for example, in the case of essentially zero consumption). The device 108 for protection against excess pressure is activated if the pressure of the fluid in the output hole 116 is increased to a specified level (for example, to a specified safe level).

In addition, in some cases, when the main controller 104 is in the closed position, to process the fluid remaining between the outlet 116 and the consumer, the downstream flow may be under the influence of increased temperature and thus cause an increase in the pressure of the fluid in the output hole 116. This increase in pressure of the fluid in the output hole 116 due to the increase in temperature can also cause activation of the device 108. As described above, since the load chamber 124 is not open to the atmosphere, outer safety valve 106 is normally connected to the controller 100 and thereby prevents neo is published activation device 108. However, the use of external relief valve 106 together with the controller 102 and the device 108 may be undesirable and/or expensive.

Figure 3 shows a known load controller 300, which contains built-in internal safety valve 302 according to one implementation options. Components of the controller 300, which is essentially similar or identical to the components of the controller 102, indicated by reference numbers corresponding to the components shown in figure 1, they are identical or similar, so will not be described in detail again. Corresponding descriptions of these components described above with reference to figures 1 and 2.

Internal relief valve 302 includes a saddle 304 safety valve, which is functionally connected with the aperture 208 through the plate 220 of the diaphragm. Saddle 304 has an opening 306, which is hydraulically connected to the first chamber 212 and the second chamber 226. Soft shutter rod 244 236 load valve communicates with the hole 306 saddle 304, thereby preventing (e.g., blocking) leakage of fluid between the first and second chambers 212 and 226, respectively.

In use, when the pressure of the fluid in the load output hole 130 acts on the second side 224 of the load aperture 208 with the force of Kotor is less power, with which the load spring 214 acts on the first side 210, the soft shutter 244 communicates with the hole 306 seat 304 and thereby prevents leakage of fluid between the first and second chambers 212 and 226. Load aperture 208 is moved toward the first chamber 212 (e.g., in an upward direction against the force of the applied load spring 214 in orientation relative to figure 3), if the pressure of the fluid in the load output hole 130 acts on the second side 224 of the load aperture 208 with a force equal to the load applied load spring 214, or exceeds it. Saddle 304, which is connected with the load aperture 208 through the plate 220 of the load of the diaphragm away from the soft shutter 244 and provides the hydraulic connection of the second chamber 226 and the first chamber 212, thereby providing a pressure relief or venting of the fluid, for example, into the atmosphere. Thus, the controller 300 provides the position of the discharge pressure, if the pressure of the fluid in the second chamber 226 acts with a force that causes a transition of the controller 300 in the closed position (i.e. at the beginning of the lock).

Thus, the controller 300 according to one implementation options commonly used with safe process fluid medium, such as air, and is not suitable for the sing hazardous environments such as natural gas. More specifically, the controller 300 is not suitable for hazardous environments, because the safety valve 302 produces or removes the fluid into the atmosphere every time I move into a closed position, which can occur frequently, or when it is in closed position. Thus, the controller 300 is not suitable for hazardous applications, such as applications with hazardous fluid environments typically require the use of a safety valve, which begins to manufacture or to divert the fluid into the atmosphere when the locking controller 300.

In addition, when connecting to this controller, as, for example, the main controller 104 shown in figure 1, the controller 300 starts to release or retract the fluid when the pressure of the fluid at the outlet, which is less than the pressure of the fluid at the outlet, wherein the main controller 104 moves to the closed position. In addition, these ratios cannot be fixed, because the controller 300 no controls offset pressure between the pressure of the fluid at the output, which causes the transition of an internal relief valve 302 in the position of the discharge pressure, and the pressure of the fluid at the output, which causes a transition to the closed position of the main controller 104.

On figa shown n the pepper section of the loading regulator 400 according to one implementation options, which can be used together with the main controller 104 according to one implementation options, shown in figure 1. The controller 400 includes an internal relief valve device or node 402, which provides a significant offset (for example, the offset pressure) or a substantial range of operating difference between the outlet pressure of the regulator, which takes place or begins closed position controller 400, and the output pressure of the regulator, which takes place or begins the final position of the internal device 402. In addition, the internal device 402 when connected functionally with the main controller (for example, the main controller 104 shown in figure 1) is reset when the pressure of the fluid at the outlet, which is much larger than the pressure of the fluid at the exit, which takes place or begins closed position of the main controller 104. In other words, the internal unit 402 controls the displacement of the pressure between the pressure of the fluid at the outlet, wherein the internal device 402 starts the transition to the reset, and the pressure fluid outlet, wherein the main controller and/or load the controller starts the transition to the closed position. On FIGU shows another cross section of the controller 400 according to the VA is Ianto implementation, shown in figa illustrating the internal structure 402 in position reset.

As shown in figa and 4B, the controller 400 includes a housing 404 having a loading diaphragm 406 is located between the first housing 408 and the second housing 410. The first housing 408 and the first side 412 of the loading diaphragm 406 to form the first chamber 414. Load spring 416 is located in the first building 408 between the first slot 418 for spring and adjustable second slot 420 for spring. Load spring 416 acts on the first side 412 of the loading diaphragm 406 and causes movement of the load aperture 406 in the direction of the second housing 410 (e.g., in the downward direction in the orientation relative to figa and 4B). The first chamber 414 has an outlet or hole 422 providing hydraulic connection of the first chamber 414, for example, with the atmosphere.

The second case 410 forms a passage between the loading inlet 424 and the loading outlet 426. Load inlet 424 hydraulically connected with the inlet (e.g., inlet port 114, as shown in figure 1) regulator (for example, controller 104), and the loading outlet 426 hydraulically connected with the load of the camera (for example, load the camera 126) of the principal regulator (for example, the main controller 104). The second case 410 and the second store is at 428 loading diaphragm 406 to form the second chamber 430. The second chamber 430 is in hydraulic connection with the loading outlet 426 through the channel 432 and thereby enables detection of changes in the pressure of process fluid in the output port (for example, in the output hole 116, as shown in figure 1) of the principal regulator (for example, the main controller 104). Saddle 434 load valve is located inside the second housing 410 and forms a working hole 437, through which process fluid can flow between the load inlet 424 and the loading outlet 426. The first end 438 of the rod 436 load valve functionally connected to the loading diaphragm 406, and the second end 442 contains the shutter 440 load valve. The shutter 440 functionally connected to the loading diaphragm 406 and moves in the direction of the load to the saddle 434 and thereby prevents the flow of fluid through the working hole 437 and withdraws from the seat 434, thereby providing the possibility of leakage of fluid through the working hole 437. The closing spring 444 is located between the gate 440 and the socket 446 for spring shutter valve, and provides the offset gate 440 in the direction of the seat 434.

Internal device 402 is configured to move from seat 448 relief valve in the discharge p is the situation and thus provides the possibility of leakage of fluid between the first chamber 414 and the second chamber 430 in response to the pressure, which is more than the pressure at which the regulator is in the closed position. In this example, the saddle 448 is connected with the loading diaphragm 406 through plate 450 of the diaphragm. Saddle 448 has a cylindrical housing 452, passing along the longitudinal axis 454, and a flange portion 456. A cylindrical housing 452 has a first cavity, or hole 458, the second cavity, or hole 460, the diameter of which is smaller than the diameter of the first hole 458, and the third hole 462, the diameter of which is smaller than the diameter of the first and second holes 458 and 460. First, second and third openings 458, 460 and 462 form a passage for the hydraulic connection of the first chamber 414 and the second chamber 430. The shutter 464 relief valve connected to the saddle 448 slidable and moves in the direction to the third hole 462 and thereby prevents leakage of fluid between the first and second chambers 414 and 430 and moves in the direction from the third hole 462, thereby providing the possibility of leakage of fluid between the first and second chambers 414 and 430. The shutter 464 communicates with the third hole 462 or block it, if the first part 466 of gate 464 is located in the second hole 460 seat 448.

Restrictive or fractional element 468 (for example, o-ring) is located at least between the part of the gate 464 and part of the saddle 448. Wapishana example, restrictive or friction element 468 is located in a channel or annular groove 470, made in the gate 464. However, in some other examples, restrictive or frictional member 468 may be located in a channel or annular groove made in the second hole 460 seat 448, or any other suitable location between the gate 464 and seat 448. In some other embodiments of a few o-rings and/or with several different sizes of o-rings (not shown) can be located at least between the part of the gate 464 and seat 448 and thus to provide more or less resistance or friction so that the internal activation device 402 could be carried out under various necessary given the pressures of the fluid in the exit hole.

In some other embodiments of at least a portion of the bolt 464 may be made for example of rubber, material TeflonŽ or any other material suitable for friction engagement with the saddle 448, to ensure significant bias pressure between the pressure of the fluid, which causes a transition to the closed position, and the pressure of the fluid, which causes a transition in the position of release. In other embodiments of the shutter 464 may include annular ridges, irregularities, protrusions, or any other suitable configuration and/or material is, interoperable shutter 464 seat 448, thereby providing a significant shift pressure. In other embodiments of the saddle 448 may include annular groove for receiving o-rings, gaskets, made for example of rubber, edges and/or other configurations and/or materials suitable for providing frictional engagement of the shutter 464 seat 448 to substantially offset the pressure.

In the closed position, the shutter 464 communicates with the third hole 462 saddle 448 (as shown in figa) and thereby prevents leakage of fluid between the first chamber 414 and the second chamber 430, and in the release position moves in the direction from the second hole 460 and the third hole 462 (as shown in figv) and thus provides the possibility of leakage of fluid between the first chamber 414 and the second chamber 430. Restrictive or friction element 468 provides a resistance (for example, due to frictional forces and thereby prevents movement of the seat 448 in the direction of the gate 464 (i.e. in the release position, as shown in figv), if the controller 400 is in the locked position (i.e. in the closed position, as shown in figa). In other words, the pressure at the exit hole (for example, an exhaust outlet 116) of the principal regulator (for example, osnovnoj the controller 104), which causes a transition of the controller 400 in the closed position, does not cause the device 102 to the open position or the position of the outlet in the beginning locking or after him. In contrast, requires an additional increase in pressure substantially above the pressure of the fluid required to move to the closed position, to overcome the resistance (for example, frictional resistance), created a restrictive element 468, and a translation device 402 to the reset.

In addition, when connected functionally with the main regulator 104 in the closed position of the main controller 104 does not cause the device 102 to the open position or the discharge position at the beginning of the closure of the main controller 104, or after it. In contrast, requires an additional pressure increase is significantly larger compared to the pressure required to move the main controller 104 in the closed position, to overcome the resistance (for example, frictional resistance), created a restrictive element 468, and a translation device 402 in the position of release. As shown in figv, in the exhaust position, the saddle 448 moved in the direction of the gate 464 and thus provides the possibility of leakage of fluid between the first chamber 414 and the second chamber 430.

In the shown example, the gate 464 is W is OK 472 and the flange portion 474. Safety bias element 476, for example a safety bias spring is located between the shoulder 478 saddle 448 and the flange part 474 gate 464 and shifts the shutter 464 toward the first end 438 of the load rod 436 valve. In the illustrated implementation, the first end 438 of the load rod 436 contains soft or resilient seat 480, which interacts with a valve 464 and thereby functionally connects the load gate 440 loading diaphragm 406. Thus, the gate 464 is free to oscillate separately from the load shaft 436, thereby helping to reduce misalignment between the load shaft 436, load gate 440, loading diaphragm 406, building 404, etc. In the load rod 436, the load gate 440, the loading diaphragm 406 and the housing 404 may be manufactured with greater tolerances and thus to reduce the manufacturing cost and to simplify the specified node.

To use the loading diaphragm 406 can be moved at least between a first position, second position and third position in response to pressure of the process fluid, detected in the load output hole 426. In the first position, the force of the load spring 416 acts on the first side 412 of the loading diaphragm 406 and causes the moving load dia is regmi 406 toward the second chamber 430. Aperture 406 is moved to the first position when the pressure of process fluid in the load output hole 426 acts on the second side 428 of the loading diaphragm 406 through the second chamber 430 with a first force which is less than the force of the load spring 416 acting on the first side 412 of the loading diaphragm 406. In turn, the loading diaphragm 406 moves the load gate 440 in the first position by means of a rod 436. In the first position the load gate 440 is moved in the direction of the load from the seat 434 and thereby provides the possibility of leakage of fluid between the load inlet 424 and the loading outlet 426 (e.g., in the open position).

In the open position, an internal relief valve device 402 is in the closed position and prevents the flow of fluid between the first chamber 414 and the second chamber 430. Protective spring 476 shifts the shutter 464 in the direction to an elastic saddle 480. High pressure fluid in the load input hole 424 is reduced to a load pressure (for example, the required load pressure) during the flow of fluid through the working hole 437 to load the outlet 426 depending on the position of the shutter 440 relative to the seat 434. Load dilleniidae to be filed, for example, in a load chamber (for example, a load chamber 124, as shown in figure 1) of the principal regulator (for example, the main controller 104 shown in figure 1). Load spring 416 may be adjusted (e.g., compressed or released) by means of an adjusting screw 482 to increase or decrease the force acting on the first side 412 of the loading diaphragm 406.

The second chamber 430 detects the pressure of the fluid in the load output hole 426 through the channel 432. The loading diaphragm 406 is moved to the second position (as shown in figa), if the pressure of process fluid in the load output hole 426 acts on the second side 428 of the loading diaphragm 406 with a second force which is greater (for example, a little more power for a load spring 416 acts on the first side 412 of the loading diaphragm 406. In turn, in the second position, the loading diaphragm 406 causes the moving gate 440 in the direction of the seat 434. The closing spring 444 shifts the shutter 440 in the direction of the saddle 434 and thereby ensures its tight interaction with the specified seat 434, preventing leakage of fluid between the load inlet 424 and the loading outlet 426 (i.e. in the closed position). Closed position occurs when the controller 400 prepa is equal to the flow of fluid between the load inlet 424 and the loading outlet 426. In the closed position of the safety spring 476 continues to shift the shutter 464 toward the first end 438 of the rod 436 and thereby prevents leakage of fluid between the first chamber 414 and the second chamber 430.

The restrictive element 468 provides frictional resistance and thereby restricts or stops the movement of the saddle 448 in the direction of the gate 464, when the loading diaphragm 406 is in the second position, and/or the controller 400 is in the closed position (as shown in figa). Thus, after reaching the closed position or the entrance to it (i.e., at the beginning of the transition to the closed position) of the safety valve device 402 is not in the release position, i.e. it does not provide the possibility of leakage of fluid between the first chamber 414 and the second chamber 430.

When connecting to a controller, such as the primary controller 104 shown in figure 1, the pressure of the fluid in the output hole 116 continues to increase, when the controller 400 is in the closed position. The increase of the pressure of the fluid in the output hole causes a transition of the primary controller 104 to the closed position (i.e. provides essentially zero flow between the inlet 114 and outlet 116). Thus, the main controller 104 is in the closed position, if davleniya environment in the output hole 116 more pressure of the fluid in the output hole 116, when the controller 400 is in the closed position. As a result, according to one implementation options of the internal relief valve device 402 stops the hydraulic communication between the first chamber 414 and the second chamber 430 in the early locking of the main controller 104. Thus, the internal relief valve device 402 is configured to (for example, by limiting element 468) reset when the pressure of the fluid that is greater than the pressure of the fluid, causing the beginning of the main locking knob.

To overcome forces (e.g. friction force)applied a restrictive element 468, the pressure of the fluid in the load output hole 426 acts on the second side 428 of the loading diaphragm 406 through the second chamber 430 with power, which is much more power, which operates a fluid medium to cause a transition of the controller 400 in the closed position (as well as more elastic force with which the load spring 416 acts on the first side 412 of the loading diaphragm 406).

By increasing the pressure of process fluid in the load output hole 426 (and, as a consequence, the transition of the main regulator 104 to the closed position), the loading diaphragm 406 and saddle 448 relief valve is moved to the third position (the AK is shown in figv) in the direction towards the first chamber 414, and thus cause separation or movement of the shutter 464 in the direction from the saddle 448 and thereby provide the possibility of leakage of fluid between the first and second chambers 414 and 430. In other words, an internal relief valve device 402 prevents the discharge or dispose of process fluid when moving to the closed position or at the beginning of the specified transition to the closed position controller 400 and/or the main controller 104. On the contrary, an internal relief valve device 402 relieve pressure or diverts the fluid if the pressure at the exit hole considerably more pressure in the exit hole, which causes the specified closed position, but less than the pressure in the exit hole, which causes activation of the device for protection against excessive pressure (e.g., device 108, shown in figure 1), which is functionally connected to the controller 400 according to one implementation options.

Thus, if the load aperture 406 and saddle 448 is moved from the second position (which corresponds to the closed position, shown in figa, in the third position (which corresponds to the position of the pressure relief), shown in figv, internal relief valve device 402 provides the possibility of leakage of the fluid is between the first chamber 414 and the second chamber 430. As a result, according to one implementation options, restrictive element 468 provides a significant range of insensitivity or significant separation between a closed position controller 400 and/or the main controller 104 and the position of the resetting of the safety valve device 402. In use with natural gas, in which it is necessary to provide regulatory pressure 2 psi (13.8 kPa) (for example, the pressure downstream of the flow or the pressure at the exit hole), the reset internal relief valve device 402 may be set or configured to activate when the pressure of the fluid in the output aperture value 3 psi (20.7 kPa). This setpoint is greater pressure of the fluid at which the controller 400 moves to the closed position (for example, 2.2 lbs per square inch (15,18 kPa)), and more pressure fluid, when in the closed position moves the main controller 104 (for example, 2.8 pounds per square inch (19,32 kPa)but less than the pressure at which must be activated device overpressure (for example, 4.5 pounds per square inch (31,05 kPa)).

In other words, the restrictive element 468 controls the displacement of the pressure between the pressure of the fluid in the output is the hole, which causes the transition of an internal relief valve device 402 in the position of the discharge pressure, and the pressure of the fluid in the exit hole, which causes the beginning of the main locking knob and/or load control. Thus, the safety valve device 402 according to one implementation options enables the use of devices for protection against excessive pressure together with regulators with pressure without the use of external safety valve (for example, external relief valve 108 shown in figure 1).

On figa shows a cross-section of the load controller 500 according to one implementation options, carried out together with an internal relief valve device or node 502 according to another implementation variant. On FIGU shows another cross section of the controller 500 according to a variant implementation, shown in figa illustrating an internal relief valve device or node 502 in the position of the descent. On figs shows the shutter 504 of the safety valve, which can be used with an internal relief valve device 502 according to one implementation options. Components of the controller 500, which, in fact, p is dobni or identical to the components of the controller 400, described above are denoted by reference numbers corresponding to the components shown in figa and 4B, which they are identical or similar, so will not be described in detail again. Corresponding descriptions of these components described above with reference to figa and 4B.

As shown in figa and 5B, an internal relief valve device or node 502 according to one implementation options contains the shutter 504 relief valve connected to the saddle 506 relief valve slidable and having at least one restrictive or friction element 508 (for example, a sealing ring located between the gate 504 and 506 saddle. The saddle 506 has a cylindrical body 510 with a flange 512. A cylindrical housing 510 has a hole or passage 514, which provides the hydraulic connection of the first and second chambers 414 and 430, if the controller 500 is in position reset (as shown in figv). The flange 512 communicates with the second side 428 of the loading diaphragm 406 and thereby connects the saddle 506 with the aperture 406. The first end of the rod 520 516 load of the valve is connected with the first or load gate valve 518, and the second end 522 of the specified stem connected to the gate 504. The shutter 518 interacts with the saddle 434 and thereby prevents the flow of fluid IU the load control inlet 424 and the loading outlet 426 and moves in the direction from the seat 434, thereby providing the possibility of leakage of fluid between the load inlet 424 and the loading outlet 426. In the shown embodiment, the implementation of restrictive element 508 is located in the groove 524, made in the shutter 504, and provides a seal preventing leakage of fluid between the first chamber 414 and the second chamber 430, if the first part 526 gate 504 is located in the first part 528 passage 514.

As shown in figs, the shutter 504 comprises a cylindrical housing portion 530 having a cavity 532, intended for receiving the second end 522 of the rod 516. The cavity 532 may have a shape that is complementary to the shape of the second end 522 of the rod 516. As shown in the drawing, the second end of the rod 522 516 according to one implementation options shrunk into the cavity 532 gate 504. However, in other embodiments of the rod 516 may be connected to the shutter 504 threaded and/or may be connected to the shutter 504 by any other suitable mechanism (mechanisms) mounting. The connection rod 516 shutter 504 eliminates the use of a safety spring (for example, a relief spring 476 shown in figa and 4B).

In use, the increase in pressure of the fluid in the load output hole 426 acts with a force on the second side 28 of the loading diaphragm 406 and shifts the load aperture 406 in the direction towards the first chamber 414. The pressure of the fluid in the load output hole 426 that is greater than the force with which the load spring 416 acts on the first side 412 of the loading diaphragm 406, causes movement of a loading diaphragm 406 in the direction towards the first chamber 414. In turn, the closing spring 444 shifts the shutter 518 load valve toward the valve seat 434. The interaction of the shutter 518 seat 434, as shown in figa (i.e. in the closed position), prevents additional rectilinear displacement of the shutter 518 in the direction towards the first chamber 414. The result is also terminated linear displacement or movement of the shutter 504 in the direction towards the first chamber 414. However, the restrictive element 508 provides resistance, the overcoming of which requires the application of additional force, created process fluid medium to the second side 428 of the loading diaphragm 406 to move the saddle 506 in the direction of the gate 504. Thus, the restrictive element 508 controls the displacement of the pressure between the pressure of the fluid in the output hole of the regulator, which begins the transition internal relief valve device 502 in the release position, and the pressure of the fluid in the output hole of the regulator, which begins the transition load regulator in the closed position.

Pressure is the fluid in the load output hole 426, exceeding the pressure of the fluid at which the transition occurs in a closed position (as shown in figa), causes movement of a loading diaphragm 406 in the direction towards the first chamber 414, when the pressure increases to a level sufficient to overcome the resistance (for example, frictional resistance), created a restrictive element 508. When pressure fluid to a level sufficient to overcome the resistance of the restrictive element 508, 506 saddle, United with loading diaphragm 406 through plate 450 of the diaphragm also moves in the direction of the shutter 504, because the loading diaphragm 406 is moved to the third position shown in figv, and thereby provides the hydraulic connection of the first and second chambers 414 and 430. Although the drawing shows only one restrictive element 508, between the gate 504 and 506 saddle can be located several restrictive elements intended to increase or decrease the force required to translate an internal relief valve device 502 into the exhaust position as shown in figv.

According to some of the other options for implementing at least part of the shutter 504 may be performed, for example, of rubber, of a material TeflonŽ or any other material suitable for f is aktsionnogo interaction with the saddle 506 and, therefore, to ensure significant bias pressure between the pressure of the fluid at which the transition to the closed position, and the pressure of the fluid at which begins the transition into the exhaust position. According to other variants of realization of the shutter 504 may include annular ridges, irregularities, protrusions, or any other configuration and/or materials that provide interaction shutter 504 to 506 saddle suitable for substantial bias pressure. According to other variants of implementation of the saddle 506 may contain annular groove for receiving the sealing rings and gaskets, made for example of rubber, the protrusions and/or other elements and/or materials that provide frictional interaction of gate 504 to 506 saddle, suitable for substantial bias pressure.

In addition, similar to the controller 400 shown in figa and 4B, the controller 500 may be functionally connected with the main controller (for example, the main controller 104). Like the controller 400 according to one implementation options described above with reference to figa and 4B, an internal relief valve device 502 according to one implementation options that is included with the controller 500 may be configured or set by ability to activate when pressure fluid is environment in the output hole, exceeding the pressure of the fluid in the exit hole, which causes the transition of the main regulator in the closed position.

On figa shows another load controller 600, carried out together with an internal relief valve device or node 602 according to another implementation variant. On FIGU shows a cross section of one implementation options of the load controller shown in figa illustrating an internal relief valve device 602 in the exhaust position. Components of the controller 600, which is essentially similar or identical to the components of the controller 400, described above, is marked with reference numbers corresponding to the components shown in figa and 4B, which they are identical or similar, so will not be described in detail again. Corresponding descriptions of these components described above with reference to figa and 4B.

As shown in figa and 6B, an internal relief valve device 602 according to one implementation options contains the saddle 604 of the safety valve, the bias element 606 (for example, the safety spring and limiter 608 move. Saddle 604 contains the stem 610, the flange portion 612 and the upper part 614. Saddle 604 is connected with the loading diaphragm 406 through the plate 450. The flange portion 612 and heat sealing surface 616, suitable for the reception of a metal disk, a flexible disk, and/or any other disk or sealing element. Sealing surface 616 flange portion 612 interact with the second side 428 of the loading diaphragm 406 and prevents leakage of fluid between the first and second chambers 414 and 430, if the internal safety valve device 602 is in the closed position (as shown in figa). Bias element 606 is located between the second flange or surface 618 seat 604 and the surface of the first housing 408 or, as shown in the drawing, the first slot 418 for spring. Bias element 606 shifts the reference surface 618 (e.g., interacts with) seat 604 in the direction towards the second side 428 of the loading diaphragm 406. The limiter 608 is connected to the first housing 408, and at least part of the specified delimiter is located in the first chamber 414. The upper portion 614 are connected in a detachable way with the rod 610 via a connecting element 620.

In use, the pressure of process fluid in the load output hole 426 acting on the second side 428 of the loading diaphragm 406 with a force greater than the force with which the load spring 416 acts on the first side 412 of the loading diaphragm 406, causes a transition to the closed position (as shown in Fig.6 is), in which the shutter 440 communicates with the saddle 434 and prevents leakage of fluid between the load inlet 424 and the loading outlet 426. When connecting functionally controller 500 according to one implementation options with the main controller (for example, the main regulator 104) internal relief valve device 602 may be configured or set by ability to activate when the pressure of the fluid in the output hole is higher than the pressure of the fluid in the exit hole, which causes the transition of the main regulator in the closed position.

Fluid in the load output hole 426, the pressure which is greater than the pressure of the fluid corresponding to the transition to the closed position, forces the loading diaphragm 406 to continue moving in the direction towards the first chamber 414 (for example, to compress a load spring 416). In the upper part 614 seat 604 interacts with limiter 608 and restricts or stops additional rectilinear displacement or movement of the saddle 604 along axis 622 in the direction towards the first chamber 414. However, further increase in pressure in the output hole of the loading diaphragm 406 continues to move toward the first chamber 414 and thus causes compression of the bounding cell battery (included) is the 606 and moving loading diaphragm 406 from the sealing surface 616 (i.e. the flange portion 612) seat 604. In the result, fluid flows between the first chamber 414 and the second chamber 430 (i.e. in final position), for example to atmosphere through the outlet 422. Thus, the internal relief valve device 602 manages or provides the means to control the displacement of the pressure between the pressure of the fluid in the output hole of the regulator associated with the beginning of a transition internal relief valve device 602 to the reset, and the pressure of the fluid in the output hole of the regulator associated with the beginning of a transition of the load regulator in the closed position.

7 shows the load controller 700 implementation containing an internal relief valve device or node 702 according to another implementation variant. Components of the controller 700, which is essentially similar or identical to the components described above, the controller 400 denoted by reference numbers corresponding to the components shown in figa and 4B, which they are identical or similar, so will not be described in detail again. Corresponding descriptions of these components described above with reference to figa and 4B.

According to one implementation options of the internal relief valve device 702 includes a saddle 704 relief valve connected to the loading diaphragm 406. Saddle 704 has a cylindrical housing 706, passing along the longitudinal axis 708, and a flange portion 710. A cylindrical housing 706 has a cavity 712, the size of which is suitable to interact with the first end 438 of the rod 436 load valve or for its use (for example, elastic saddle 480). A cylindrical housing 706 also has a camera 714 containing gate 716 relief valve located in said chamber and having a first hole 718, which provides a hydraulic connection cavity 712 and chamber 714. In the shown implementation, the gate 716 is depicted in the form of a shut-off valve. Specified shutoff valve contains a ball 720, which is shifted in direction to the first hole 718 through a bias element 722 (e.g., springs). Bias element 722 is located between the slot 724 for the spring and ball 720.

In use, the saddle 704 and the loading diaphragm 406 is moved to the closed position (as shown in figa), when the pressure of process fluid in the load output hole 426 acts on the second side 428 of the loading diaphragm 406 with a force greater than the force with which the load spring 416 acts on the first side 412 of the loading diaphragm 406. In the closed position, the shutter 440 communicates with the saddle 434 and prevents leakage of fluid between the load input resp what rstam 424 and the loading outlet 426. When connecting functionally controller 500 according to one implementation options with the main controller (for example, with the main regulator 104) internal relief valve device 602 may be configured or set by ability to activate when the pressure of the fluid in the output hole is higher than the pressure of the fluid in the exit hole, wherein the main controller moves to the closed position. By increasing the pressure of the fluid in the load output hole 426 to a level above the pressure at which the controller 700 and/or the main controller is transitioned to the closed position, the loading diaphragm 406 and saddle continue 704 linear motion along the axis 708 in the direction towards the first chamber 414. As a result, the saddle 704 is moved in the direction from the first end 438 of the rod 436 and opens the first hole 718 for the fluid in the second chamber 430 or provides hydraulic connection with the specified fluid medium and, thus, the fluid in the load output hole 426 through the channel 432 or provides hydraulic connection with the specified fluid medium.

For the hydraulic connection of the first and second chambers 414 and 430 pressure of the fluid acts on the first side 726 of the ball 720 through the first hole 718 with a force that is greater than the force with which the offset is a first element 722 acts on the second side 728 balloon 720. If the pressure of the fluid overcomes the force with which a bias element 722, the ball 720 is moved from the first hole 718 in the direction towards the first chamber 414. In the result, fluid flows between the first and second chambers 414 and 430 (i.e. in the position of the discharge, as shown in figv) to output 422. Thus, the internal relief valve device 702 controls the displacement of the pressure between the pressure of the fluid in the output hole of the regulator associated with the beginning of a transition internal relief valve device 702 to the reset, and the pressure of the fluid in the output hole of the regulator associated with the beginning of a transition of the load regulator in the closed position.

Although the above describes some of the embodiments of the proposed device, the scope of patent protection is not limited to the described variants. In contrast, the present application covers the entire device and its components, rightly located within the volume defined by the points of the applied formulas literally or under the doctrine of equivalents.

1. The load regulator with internal relief valve device and containing:
the housing that contains the load aperture located between the first shell forming the first chamber together with the first side N. the loading aperture, and the second shell forming the second chamber together with the second side of the load of the diaphragm; and
site safety valve connected to the load aperture and containing:
the seat of the safety valve having an aperture forming a passage with providing a hydraulic connection between the first and second chambers; and
the bolt relief valve connected to move with the saddle valve and configured to move from the seat of the safety valve in the exhaust position enabling flow of fluid between the first and second chambers in response to the output pressure substantially above the pressure at which the load controller moves to the closed position.

2. The controller according to claim 1, wherein a node of the safety valve is arranged to move in the discharge position in response to the output pressure substantially above the pressure at which the main controller, functionally connected to a load controller, moves to the closed position, the main controller moves to the closed position when the pressure is substantially greater than the outlet pressure at which the load controller moves to the closed position.

3. The regulator according to claim 2, in which the node before sanitarnogo valve includes a seal or spring, made with the possibility of moving the safety valve in the discharge position in response to the output pressure substantially above the pressure at which the load controller moves to the closed position, or the pressure at which the main controller moves to the closed position.

4. The regulator according to claim 3, in which the seal or spring is located at least between the gate valve and part of the seat of the safety valve.

5. The regulator according to claim 3, in which the seal includes at least one sealing ring.

6. The regulator according to claim 1, additionally containing rod load valve, which is functionally connected with the load aperture and the first end of which is located the bolt load valve made with the possibility of interaction with the saddle load valve, located in the working bore of the housing between the loading inlet and load the outlet, preventing the flow of fluid through the working hole and can move from the seat load valve to ensure flow of fluid through the working hole.

7. The controller according to claim 6, additionally containing supple saddle, United with the second end of the rod load valve with providing interaction is the major shutter valve and providing a functional connection of the gate of the load valve and the load of the diaphragm.

8. The regulator according to claim 7, further containing a bias element configured to bias the gate of the safety valve in the direction of rod load valve.

9. The controller according to claim 6, in which the second end of the rod load valve is rigidly connected to the shutter of the safety valve.

10. The regulator according to claim 9, in which the shutter of the safety valve comprises a cylindrical housing part having a cavity for receiving the second end of the rod load valve.

11. The load regulator with internal relief valve device and containing:
the aperture located in the housing of the controller between the first chamber and the second chamber and configured to move at least between a first position, second position and third position in response to pressure of the process fluid, read using the second camera;
saddle pressure relief valve connected to the diaphragm so that the saddle valve and the diaphragm is configured to move between a first position, second position and third position, and the containing hole forming a passage with providing a hydraulic connection between the first and second chambers; and
the bolt relief valve connected to the discerning business is using sliding seat, safety valve and configured to interact with the hole to prevent leakage of fluid between the first and second chambers, if the diaphragm and the seat of the safety valve is moved between the first and second positions, and the ability to move from the seat of the safety valve in the third position with ensuring the flow of fluid between the first and second chambers in response to the output pressure substantially above the pressure at which the load controller moves to the closed position.

12. The controller according to claim 11, in which the shutter of the safety valve is configured to move from the seat of the safety valve in the third position with ensuring the flow of fluid between the first and second chambers in response to the output pressure substantially above the pressure at which the main controller, functionally connected to a load controller, moves to the closed position.

13. The controller according to claim 11, optionally containing o-ring or spring located at least between the gate valve and seat, a safety valve connected to the gate of the safety valve by setting the output pressure at which the shutter of the safety valve moves into the third position.

14. The controller according to claim 11, in which the first position used an open position in which the load regulator about who has the possibility of leakage of process fluid between the loading inlet and load outlet.

15. The controller according to claim 11, in which the second position is used in the closed position of the load regulator, which prevented the flow of process fluid between the loading inlet and load outlet.

16. The controller according to claim 11, in which the third position used exhaust position in which provided the possibility of leakage of fluid between the first chamber and the second chamber.

17. The controller according to claim 11, in which the seat of the safety valve comprises a cylindrical element having a flange part and a cavity.

18. The regulator 17, in which the shutter of the safety valve contains a check valve located at least inside of a cylindrical element seat of the safety valve.

19. The regulator 17, additionally containing rod load valve, gate load valve connected with the first end of the rod, and supple saddle, United with the second end of the rod and configured to interact with a part of the seat of the safety valve or shutter safety valve ensuring the functional connection of the gate of the load valve with a diaphragm, and a shutter load valve is located at some distance from the seat load clap is in the first position to allow flow of fluid between the loading inlet and load the outlet load controller and configured to communicate with a load the main valve is in the second position and the third position preventing flow of fluid between the loading inlet and load outlet.

20. Internal relief valve device for use with a load regulators containing:
means for providing a hydraulic connection between the first camera and the second camera actuator, hydraulically connected with the outlet of the load controller, which contains the seat of the safety valve having an aperture forming a passage with providing a hydraulic connection between the first and second chambers; and
means for controlling the means for providing hydraulic connection is made with the possibility of a leakage of fluid between the first chamber and the second chamber in response to the output pressure of the fluid, substantially exceeding the pressure related to the early closure of the regulator, which contain the bolt relief valve connected to move with the seat of the safety valve, and means to move the bolt relief valve in the direction from the hole of the seat of the safety valve.

21. The device according to claim 20, in which the means for controlling the means for providing hydraulic what about the connection between the first chamber and the second chamber contains a sealing ring, located at least between the gate valve and part of the seat of the safety valve.

22. The device according to claim 20, in which the means for controlling the means for providing hydraulic connection between the first chamber and the second chamber contains a spring at least partially located inside the seat of the safety valve and configured to bias the gate of the safety valve to the hole seat of the safety valve.

23. The device according to claim 20, in which the pressure related to the early closure of the regulator, used pressure related to the early closure of the load regulator, or pressure related to the early closure of the main regulator.



 

Same patents:

FIELD: process engineering.

SUBSTANCE: invention relates to instrument making and can be used in the systems of control over various processes. Invention covers several versions of temperature controller. Temperature controller comprises the case with fluid inlet communicated via first flow channel with fluid outlet and heat carrier inlet communicated via second flow channel with heat carrier outlet. Heat carrier inlet is made integral with controller case. Heating chamber case is plugged in controller case to make the chamber between heat carrier inlet and outlet. At least the part of aforesaid first flow channel is located inside the case while heat carrier flows via its inlet to heat working fluid in said first flow channel separating said fluid from heat carrier.

EFFECT: expanded performances.

17 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: fluid medium control includes an actuator, a valve and a housing of a balanced channel, which is located inside the valve for flow conditioning in order to convert a turbulent flow inside the valve to laminar flow when fluid medium reaches a receiving section of a Pitot tube located inside the outlet valve opening. The balanced channel housing includes an opening passing through a side wall and located between the valve channel and the outlet opening. The above opening includes a partial obstacle such as partition walls or a sieve, above which fluid medium flows to convert turbulent flow to laminar flow. There are versions of a fluid medium control design.

EFFECT: improving operating reliability of a control due to the fact that the preceding pressure in the flow direction does not influence on control of the following pressure in the flow direction.

23 cl, 11 dwg

FIELD: measurement equipment.

SUBSTANCE: system of pressure monitoring comprises a body, a hole in a hydraulic system made in a body, the first pressure relay arranged inside a body and having a hydraulic connection with a hole in a hydraulic system, and the second pressure relay arranged inside the body and having a hydraulic connection with a hole in the hydraulic system. The method to build a system of pressure monitoring includes stages, when: the first pressure relay is installed inside the body so that the first pressure relay is in hydraulic connection with the hole in the hydraulic system, and the second pressure relay is installed inside the body so that the second pressure relay is in hydraulic connection with the hole in the hydraulic system.

EFFECT: expansion of functional capabilities of a pressure monitoring system.

12 cl, 5 dwg

FIELD: machine building.

SUBSTANCE: gas pressure regulator is fitted with a drive, a control valve and a device of pressure-induced loading. The pressure-induced loading device provides for loading the drive diaphragm surface with pressure which counteracts the output pressure on the opposite diaphragm side with the latter pressure being controlled by the regulator. In case the output pressure is changed the diaphragm moves and shifts the controlling element in order to regulate the output pressure while the pressure-induced loading device keeps up the specified pressure. The pressure regulator can comprise a regulating shutter which compensates the force of input pressure on the controlling element.

EFFECT: increasing efficiency of standard gas pressure regulators.

21 cl, 4 dwg

Pressure regulator // 2490689

FIELD: machine building.

SUBSTANCE: regulator includes a housing with inlet and outlet cavities and between them a spring-loaded sensitive element in the form of a shell, a setting cavity with an elastic element, a seat, a shutoff element in the form of a disc with a conical surface. The housing is made of two halves in the form of bowls with flanging, and in it there introduced and installed with stiff connection is a cylinder with the above mentioned shell located in it with outer surface of the bottom towards the seat installed in the inlet cavity. A safety spring is introduced to prevent mismatch of the control system at abrupt opening of the network. Elastic element for spring loading of a sensitive element in the setting cavity uses working medium the pressure energy of which is controlled with a regulator.

EFFECT: enlarging application ranges.

1 dwg

FIELD: machine building.

SUBSTANCE: valve port comprises vale body, bearing valve port defining channel converging from inlet to outlet. Convergent channel minimizes effects of boundary layer separation to maximise port capacity. Said channel may be formed inside solid part to be screwed in valve body, or in cartridge fitted in valve body to slide and to be screwed therein. Fluid control device comprises also diaphragm drive furnished with control component arranged inside valve body to control fluid flow in said body.

EFFECT: ease of use maximised capacity at preset outlet pressure.

23 cl, 5 dwg

FIELD: machine building.

SUBSTANCE: gas pressure control with a drive, a control valve and an auxiliary device. Information on outlet pressure is supplied to the drive and the auxiliary device by means of a Pitot tube located at the control valve outlet. End of the first nozzle of the Pitot tube is connected to the drive, thus providing communication between a control cavity of the drive and a membrane and outlet pressure at the outlet to maintain outlet pressure on the drive in compliance with the specified value. End of the second nozzle of the Pitot tube is connected to the auxiliary device, thus providing communication between internal area of the auxiliary device and outlet pressure at the outlet to respond to outlet pressure variations at deviation of outlet pressure from specified values of the range of normal pressure. There is a structural version of design of gas pressure control and a double-control mechanism for the above pressure control, automatic control of fluid medium pressure.

EFFECT: automatic fluid medium pressure control.

27 cl, 9 dwg

FIELD: machine building.

SUBSTANCE: measuring tube with function of pressure averaging contains: measuring part that has open end made with the possibility of location near outlet of fluid regulation device; attachment part located at an angle relatively the measuring part and made with the possibility of location near control unit of fluid regulation device and slot made in measuring part and going from the said open end to attachment part. When installing measuring tube in fluid regulation device measuring part can average the pressure in outlet and the said measuring tube transfers averaged pressure to control unit.

EFFECT: increase of fluid pressure measurement accuracy.

15 cl, 7 dwg

FIELD: machine building.

SUBSTANCE: gas pressure control includes an actuator equipped with a gate made from elastic material, a seat, inlet, outlet and control chambers; a throttle, a setting device with a control valve, a membrane unit and an adjustment mechanism. At that, inlet chamber of the actuator is connected through the throttle via a channel to the control chamber, the setting device and the outlet chamber. According to the proposal, the control includes a matching unit consisting of a chamber for gas cleaning from mechanical impurities and humidity; pneumatically operated shutoff and control device of normally open type; at that, throttle is built into the matching unit between gas cleaning chamber and shutoff and control device, and gas cleaning chamber is located on the side of inlet chamber, and setting device is connected to the shutoff and control device and outlet chamber.

EFFECT: improving operating characteristics.

9 cl, 4 dwg

FIELD: transport.

SUBSTANCE: invention relates to space technology and may be used for stabilisation of preset engine thrust by correction of spaceship motion. Tank with working medium (WMT) has three chambers. All supercharge gas (SG) is kept in extra permanent-volume tank (EPVT) adjoining WMT wall opposite the bellows. In case current and preset fuel pressures differ, defined are valid current SG temperature and pressure between bellows and EPVN, fuel mass residue, current SG volume, SG portion of EPVT required to reach operating pressure proceeding from current pressure in EPVT and interchamber channel cross-section, as well as duration of transfer of this portion into central chamber. Interchamber valves are opened and closed at preset time.

EFFECT: increased and stable thrust, accurate computation of correction parameters.

2 dwg

FIELD: pneumatics and automatics, namely reducing and sustaining predetermined level of pressure of compressed gas in pneumatic drives of transporting and other machines, in tanks of fuel system of automobile transport at pumping fuel.

SUBSTANCE: reduction pneumatic valve includes housing with inlet and outlet ducts, calibrated orifice in inlet duct preventing increase of output pressure; spring-loaded stepped throttling valve; membrane type control unit having seat rigidly secured to membrane and elastic sealing member for minimizing change of effective surface area of membrane due to its minimum bending; valve member in the form of spherical head for reducing sealing effort, compensating membrane shift and providing intensified discharge of compressed air; filter placed at inlet of orifice for preventing clogging.

EFFECT: enhanced operational reliability, prevention of outlet pressure exceeding predetermined value, effective relief of compressed air, lowered sealing effort due to compensation of membrane shift.

3 cl, 3 dwg

FIELD: measuring equipment.

SUBSTANCE: device has thermocouple 1 with seam 2, fixedly packed in tubular case 3 with longitudinal groove 4. tubular case 3 on thread enters screw holder 5, which by its outer screw profile is screwed into coils of set-point spring 6, fixedly held on heating element 7. Outwardly bent end 8 of spring 6 is inserted into longitudinal groove 4 of tubular case 3. spring 6 is provided with sensor 9 for axial displacement of spring and sensor 10 for dynamic pressure force. Rotation of screw holder 5 shall be performed until seam 2 stops against heating element 7 to the point, when sensor 9 and sensor 10 will determine, that step S of spring 6 increased to controlled value, which matches reliable contact of seam 2 with heating element 7.

EFFECT: determined moment of contact of seam between thermocouple and heating element during manual movement of screw holder.

2 cl, 1 dwg

FIELD: engineering of devices for automatic maintenance of pressure of working substance at given level, possible use in systems for supplying natural gas to industrial and communal consumers.

SUBSTANCE: device has body with input and output hollows, locking valve, membrane sensitive mechanism, adjusting valve. Adjusting valve is controlled by membrane drive by second order lever, lever for contact interaction of rod of adjusting valve.

EFFECT: increased device operation reliability.

2 dwg

FIELD: possible use as an adjuster of flow-force characteristics of a liquid.

SUBSTANCE: adjuster contains body 1 with internal portion 2, consisting of control hollow 3, coaxial input 4 and output 5 hollows, between which adjusting organ 6 is positioned, made in form of locking element 7, rigidly connected to rod 8, and spring 9 of locking element 7. control hollow 3 is made in form of two side cylinder-shaped branches 10, connecting input 4 and output 5 hollows.

EFFECT: simplified construction of adjuster of flow-force characteristics and decreased hydraulic losses during adjusting.

1 dwg

Gas reducer // 2290682

FIELD: engineering of gas reducers.

SUBSTANCE: gas reducer contains body 1 with saddle 2 and lid 3, superstructure section, including superstructure screw 4, spring 5, membrane 6 with supporting plate 7 and pusher 8, reducing valve, consisting of hollow body 9 with through channel and thickening 10, balancing chamber 14, connected to hollow 21 of working pressure of body 1 and provided with controlling valve 17. Balancing chamber 14 may be made in body 1, or in its stopper 16, while reducing valve is mounted in the chamber with circular gap relatively to the wall of the latter. Chamber is provided with controlling valve, as spring of which spring of reducing valve is used.

EFFECT: low unevenness coefficient, low dimensions and weight of reducer.

5 cl, 1 dwg

FIELD: automatic control.

SUBSTANCE: device comprises housing, lid, adjusting spring, control members for adjusting specified parameters, and chamber that receives the diaphragm. The diaphragm divides the space of the chamber into the above-diaphragm space connected with the gas pipeline to be controlled and under-diaphragm space connected with the atmosphere. The diaphragm is mounted on the movable rod. The rod passes through the diaphragm at its center and causes the pusher to move. The pusher is connected with the second rod that is perpendicular to the first rod and connected with the third rod. The shutoff valve is mounted on the third rod. The rod of the shutoff valve is oriented parallel to the rod of the diaphragm. The second chamber of the device is positioned in the space between the lid and housing from the side of the lid. The second chamber receives the second diaphragm that is shaped similar to the first diaphragm and separates the second chamber into above-diaphragm space and under-diaphragm space. The under-diaphragm space is in communication with the atmosphere and defines a space between the lid and the second diaphragm. The second diaphragm is mounted on the same rod as the first diaphragm for permitting the above-diaphragm spaces of both of the chambers to be interconnected by means of a passage made in the hollow rod. The second chamber is defined by the cylindrical hollow housing mounted on the lid and receives the a baffle at its center provided with diaphragm for permitting the rod of the diaphragms to pass through them. The rod of the diaphragms is connected with the pusher by means of a bushing. The bushing has side passage oriented parallel to the diaphragms for connection of the above-diaphragm spaces.

EFFECT: enhanced reliability and precision.

2 dwg

FIELD: valving systems.

SUBSTANCE: device comprises pulse tube that connects the control space of pilot with the receiver of the static outlet pressure and is connected with the inner chamber and switch mounted at the site of pipe joint made of e.g. three-position cock. The flexible coupling controls the space between the side and flanges of the inlet and outlet branch pipes depending on the switch position.

EFFECT: expanded functional capabilities.

1 dwg

FIELD: pipeline engineering.

SUBSTANCE: fluid pressure regulator comprises housing provided with a flange having a number of projections shaped into lugs. Each projection has at least one opening made for permitting receiving a fastening member. The regulator has valve provided with the seat, valve plate, valve rod connected with the plate, and valve guide member that locks the rod of the valve. The lever has the first end connected with the valve rod and second end connected with the diaphragm. The force is applied to the rod from the side of the lever in the direction virtually perpendicular to the longitudinal axis of the valve rod. The valve rod has stop member that arrests the valve rod and the plate against movement with respect to the seat of the valve.

EFFECT: enhanced reliability.

21 cl, 8 dwg

FIELD: engineering industry; regulator engineering.

SUBSTANCE: regulator of gas pressure contains valve located on a rod, saddle, central hole, feeler connected by means of lever transmission with a rod. In the valve and in rod channel for a gas supply in a compensating cavity is executed. This cavity is organised by protective and compensating membranes. Regulator has located in a peripheral edge part of the valve the channel for an inlet (input) of gas. Central face part of the valve from periphery has an overlapping element, forming under itself a cavity for a gas course.

EFFECT: productivity gain of the device due to rising of its throughput.

3 cl, 1 dwg

FIELD: heating.

SUBSTANCE: valve unit (1) includes housing with inlet (2) and outlet (3), valve 1 (6) with seat (8) and gate (7) and valve 2 (10) providing stable pressure drop at valve 1 (6). Valve 1 (6) is located in the first part of unit body (A) whereas valve 2 (10) is situated in the second part (B) of unit body. Besides, first part (A) and second part (B) of unit body are interconnected. Pressure transfer channel (28) from outlet (3) to membrane side (24), which is opposite to valve 1 (6) crosses parting surface (C) between the first (A) and second (B) parts of unit body.

EFFECT: simplification of valve unit design.

10 cl, 2 dwg

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