• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A valve includes a modulation chamber (65) for sending and receiving fluid through a first port of the chamber, a feed chamber (64), and a buffer tank (62) for sending and receiving a second fluid through a buffer tank port. The valve also includes a passageway (66) between the buffer tank and the supply chamber, and a removable piston module (68) inside the valve, the piston module being configured to open and close a control device flow. The piston module comprises a rod (70), a modulating piston (76) attached to the rod and movable within the modulation chamber, a supply piston (74) attached to the removable rod therein of the supply chamber, and a buffer piston (72) attached to the removable rod within the passageway and the supply chamber. The piston module also includes a buffer piston deflection (66) that allows restricted flow passage between the supply chamber and the buffer tank when the buffer piston is located in the passageway.
    公开号:FR3031157A1
    申请号:FR1562614
    申请日:2015-12-17
    公开日:2016-07-01
    发明作者:Iii Earl Jean Lavallee
    申请人:Hamilton Sundstrand Corp；
    IPC主号:
    专利说明:

    [0001] 1 GRADUAL HISTORIC INITIATOR START-UP VALVES Pneumatic valves are one of several components of a system that controls the flow of fluid through a system. Pneumatic valves are control devices that are powered by a fluid under pressure, normally air. In many circumstances, the pneumatic pressure is supplied to the valve drive portion from a pressure source. The valve drive portion converts pneumatic pressure into mechanical force to operate or activate a control mechanism in a feed line, pipe or pipe. The control mechanism can be an isolation valve having only two positions, open and closed, the open position allowing the flow to pass and the closed position stopping the flow. The control mechanism can also be a control valve that can modulate the flow of the fluid that it controls. For example, the control valve can allow fluid passage in 1% increments from 0% to 100%. There are several different types of control mechanisms that can be connected to a pneumatically driven drive, such as ball valves, butterfly valves or gate valves. These valves can be used in many applications such as pneumatic tools, industrial processes and environmental control systems of an aircraft. In one example, a pneumatic valve may be part of a control mechanism of a butterfly valve controlled by a pneumatically driven drive in a purge system of an environmental control system of an aircraft. In this example, the pneumatic pressure can come from a high pressure feed line to ultimately control a butterfly valve that modulates the flow of pressurized air through a pipe, tube or pipe into an environmental control system. 'a plane. In this example, careful attention must be given to flow rates and pressures, given that the environmental control system is essential for the operation of an aircraft. SUMMARY In one embodiment, a valve includes a modulation chamber for sending and receiving fluid through a first port of the chamber, a feed chamber, and a buffer tank for sending and receiving a fluid. a second fluid through a port of the buffer tank. The valve also includes a passageway between the buffer tank and the supply chamber, and a removable piston module within the valve, the piston module being configured to open and close a flow control device. The piston module comprises a rod, a modulating piston fixed to the rod and movable inside the modulation chamber, a supply piston fixed to the removable rod inside the feed chamber, and a 15 buffer piston attached to the removable rod inside the passageway and the feed chamber. The piston module also includes a deflection buffer piston that allows a restricted flow passage between the supply chamber and the buffer tank when the buffer piston is located in the passageway. Another embodiment is a method for controlling a valve with an actuator having a modulating chamber, a buffer tank, a feed chamber, a passageway and a piston module having modulating pistons, With the supply and buffer connected together, the modulation piston being removable in the modulation chamber, the supply piston is removable in the supply chamber and the buffer piston is removable between the passageway and the buffer tank, and wherein a deflection buffer piston allows a restricted flow passage between the supply chamber and the buffer tank when the buffer piston is located in the passageway. The method includes connecting a port of the modulation chamber to an upstream pressure to cause movement of the piston module that opens the valve. The method also includes venting air from the feed chamber to the buffer tank and then to the upstream source at a first velocity when the buffer piston is in the passage, and at a second velocity when the buffer piston is located in the buffer tank. BRIEF DESCRIPTION OF THE FIGURES FIG. 1 is a schematic view of a pneumatic control system. FIG. 2 is a schematic view of a purge control system and a sectional view of an integrating valve in a first state. FIG. 3 is a schematic view of a purge control system is a sectional view of an integrator valve in a second state. DETAILED DESCRIPTION FIG. 1 is a schematic view of a purge control system 10, which includes a high pressure inlet pipe 12, a low pressure inlet pipe 14, a bleed pipe 16, an isolation valve 18 , a check valve 20, a purge flow outlet line 22, an integral check valve 24 and a discharge conduit 26. The isolation valve 18 comprises an isolation valve body 28 and a check valve drive. The purge control system 10 also includes an isolating valve control conduit 32, a buffer pipe of the isolation valve 34, a bypass valve 36 and a conduit Isolation valve modulation module 38. Integral valve 24 comprises integral valve body 40 and integral valve drive 42. Purge control system 10 also includes an integral valve control conduit 44, a buffer pipe of the integral flap 46, u a valve deflection conduit incorporating 48 and an integral valve modulating conduit 50. The purge control system 10 also includes TM1 and TM2 torque motors and torque motor controls 52 and 54 and a control 53. Also illustrated in FIG. 1 are HP high pressure streams, LP low pressure streams and a purge stream B. The high pressure inlet pipe 12 connects to the inlet of the isolation valve 18 and the pipe of the Control of the isolation valve 32. A bleed line 16 is connected to the outlet of the isolation valve 18. A low pressure line 14 connects to the inlet of the non-return valve 20. The outlet of the valve The non-return valve 20 is connected to a second outlet of the bleed line 16, which has a single outlet. The single inlet of the bleed line 16 is connected to the purge flow outlet line 22, which connects to the integral valve inlet 24 and the integral valve control line 44. The outlet integral valve 24 is connected to a discharge line 26 which can connect to other components in a purge system, environmental control system or other system using pressurized air. The body of the isolation valve 28 and the drive of the isolation valve 30 are physically and mechanically connected. In the same way, the integrated valve body 40 and the integral valve drive 42 are physically and mechanically connected. The isolation valve control line 32, which connects to a high pressure inlet line 12, also connects to the buffer duct of the isolation valve 34 and the isolation deflection duct 36. Another end of the isolating buffer conduit 34 connects to an input, which may be an isolation valve drive port 30. The other end of the isolation valve deflection conduit 36 connects to a TM1 torque motor. Also connected to the torque motor TM1 'is an isolation modulation line 38, which connects to a second input, or port, of the isolation valve 30 drive. A control input 52 is electrically connected to the TM1 torque motor. The integral check valve control line 44, which connects to an outlet line of a purge stream 22, also connects to the integrating valve buffer line 46 and the integral deflection line 48. The integrated buffer line 46 also connects to an input, which may be a port of the integral valve drive 42. The other end of the integral valve deflection conduit 48 connects to the TM1 torque motor. Also connected to the torque motor TM1 is an integral modulation line 50, which connects to a second input, or port, of the isolation valve drive 42. A control input 54 is electrically connected to the torque motor. TM2. Control inputs 52 and 54 are also electrically connected to control 53.
    [0002] The lines of the purge system 10 may be metal or plastic pipes or tubes, or any other material capable of conveying pressurized air. This includes a high pressure inlet line 12, a low pressure inlet line 14, a purge line 16, a purge flow outlet line 22, an isolation valve control line 32, a buffer pipe of the isolation valve 34, an isolation valve bypass duct 36, a modulating duct of the isolation valve 38, an integral valve control duct 44, a buffer duct incorporating the flap 46, a an integral valve deflection conduit 48 and an integrated valve modulating conduit 50.
    [0003] The HP high pressure stream may be supplied to the purge system 10 from a high pressure compressor of a turbine engine or other high pressure source. The high-pressure stream HP then passes into a high-pressure inlet pipe 12 from which it can either pass through an isolation valve 18 or be stopped by an isolation valve 18. The isolation valve 18 may be a butterfly valve, a ball valve, a ball valve, a valve gate or any other type of valve capable of isolating the flow. The low pressure stream LP may be supplied to the purge system 10 from a low pressure source of a gas turbine engine or other low pressure source within the environmental control system. 'a plane. The low pressure stream LP then passes into a low pressure inlet line 14 and then encounters the nonreturn valve 20. The nonreturn valve 20 allows the flow to pass only from the inlet pipe of the flow to the low pressure 14 to purge line 16 and check valve 20 prevents flow from purge line 16 to low-pressure inlet line 16. When isolation valve 18 is open, the flow HP high pressure continues to bleed pipe 16 where it becomes purge flow B.
    [0004] When the isolation valve 18 is closed, the low pressure stream LP can pass through the check valve 20 and into the purge line 16, where the low pressure stream LP becomes the purge stream B. this point, either the high pressure stream HP or the low pressure stream LP becomes the purge stream B. The purge flow B then passes through the outlet line 30 of the purge stream 22 where it meets the inlet of the In this embodiment, integral valve 24 is a butterfly type valve, but may be of any type of control valve capable of being pneumatically driven. The integral valve 24 may be modulated to allow the purge flow B to pass through the integrating valve 24 at flow rates ranging from 0 to 100% of the maximum flow rate of the purge flow B. Following passage through With integral valve 24, purge flow B passes through a discharge line 26 where purge flow B is evacuated from purge system 10 to another larger part of the purge system, or to another part of the system. environmental control. Before the purge flow B enters the integral valve 24, a portion of the purge flow B will enter the integral valve control conduit 44. The integral valve control conduit 44 will then dispense this portion of the flow of the flow. purge B to the buffer duct of integral valve 46 and of the integral valve bypass duct 48. The portion of the purge flow B entering the buffer duct of integral valve 48 will continue to a chamber of the integral valve drive 42. This part of the purge system B entering the TM2 torque motor will be checked through nozzles inside the TM2 torque motor. Depending on the control signals from the control 53 to the input of the control 54, the torque motor TM2 will direct the air towards the drive of the integrating valve 42 to cause the opening or closing, staggered, of an operating mechanism within the valve body 40. The control 53 may receive control inputs from system sensors located downstream or upstream of the purge system 10. For example, the control 53 may receive control inputs from pressure sensors, temperature sensors, differential pressure sensors or flow rates. The control 53 can then determine, based on these inputs, whether any downstream component of the purge system 10 requires a flow. This functionality is described in more detail in FIG. 2. Similarly, before the HP high pressure stream enters the isolation valve 18, a portion of the HP high pressure stream will enter the isolation control line 32. The control line The isolation valve 32 will then deliver this portion of the HP high pressure stream to the buffer pipe of the isolation valve 34 and to the bypass duct of the isolation valve 36. The portion of the HP high pressure stream entering the buffer pipe of the isolation valve 24 will continue to a chamber of the isolation valve 30 drive. The portion of the HP high pressure stream entering the TM1 torque motor will be inspected through nozzles inside the TM1 torque motor. Depending on the control signals from the control 53 through the input of the control 52, the torque motor TM1 will direct the air towards the integral valve drive 30 to cause the opening or closing of a operating mechanism within the valve body 28. FIG. 2 is a schematic view of a portion of a purge control system 10 and a sectional view of an integrator valve 24 in a first state. The purge control system 10 of FIGS. 2 and 3 comprises a valve incorporating 24, an outlet pipe 22, an exhaust pipe 26, an integral valve control line 44, an integrated damper valve line 46, an integral valve buffer line 48, a pipe integrated valve modulation module 50 and a TM2 torque motor. The TM2 torque motor includes a discharge line 56, an upstream nozzle 58 and a downstream nozzle 60. Also displayed within the torque motor TM2 is an inner portion of the integral valve buffer line 48b and an internal part of the valve modulation line incorporating 50b. The outer portion of the integrated buffer pipe 48a and the outer portion of the integrated valve modulating line 50a are also included in the purge control system 10. The integral valve 24 comprises a valve body incorporating 40, a motor 20 integral integrating valve body comprises a disk 80. The integral drive includes a buffer tank 62, a feed chamber 64 and a modulation chamber 65. The integral valve 24 also includes a channel. 66 and a piston module 68. The piston module 68 comprises a piston rod 70, a buffer piston 72, a supply piston 74, a modulation piston 76 and a deflection of the buffer piston 78. Also shown are purge flow B, the ends E1 and E2, the supply force Fs and the modulation force Fm. In accordance with FIG. 1, the outlet pipe of the purge stream 22 connects to an inlet of the integral valve 24. The outlet of the integral valve 24 is connected to a discharge pipe 26. Also connected to the outlet pipe of the purge stream 22 is an integral check valve control line 44, which also connects to the integrating valve buffer line 46 and the deflection line incorporating 48, 3031157 8 specifically to the integral deflection line 48a. The integrated buffer pipe 46 also connects to the drive of the integral valve 42 at the buffer reservoir 62 near the end E1. The integral deflection line 48a is extended in the torque motor TM2 in which it becomes the pipe. of integral deviation 48b. Inside the TM2 torque motor the integral deflection line 48b connects to the integral valve modulating line 50 and the outlet line 56. The upstream nozzle 58 is located in the integral deflection line 48b upstream. of this connection. Located downstream of this connection in the discharge pipe 56 is a downstream nozzle 60.
    [0005] The upstream nozzle 58 and the downstream nozzle 60 are connected to each other by a connection (not shown) causing one nozzle to open when the other is closed, and vice versa. Further downstream in the exhaust pipe 56 is the termination of the exhaust pipe 56 to the outside. The modulation line 50b is the portion of the modulation line 50 connected to the integral deflection line 48a. The modulation line 50b extends outside the TM2 torque motor where it becomes the portion of the supply line 50a, possibly connecting to the modulation chamber 65 at the end E2. A control input 54 is electrically connected to the torque motor TM2. Inside the integral valve drive 42 there is a piston module 68. The buffer piston 72 resides within the passageway 66, which is located between the buffer reservoir 62 and a small chamber. The buffer piston 72 is connected to the end of the piston rod 70 closest to the end E1 of the integral valve drive 42. The deflection of the buffer piston 78 is a hole or other passage that passes through the buffer piston 72 or otherwise bypasses the buffer piston 72. The modulation piston 76 is connected to the piston rod 70 at the end of the piston rod 70 closest to the end E2 of the piston. 42. The modulation piston 76 is located inside the modulation chamber 65. The supply piston 74 is located between the buffer piston 72 and the modulation piston 76 in the feed chamber. 64, where the supply piston 74 is rel The buffer piston 72, the supply piston 74 and the modulating piston 76 may be attached to the piston rod 70 by means of pins, a welding method, or 3031157 9 other means or fasteners. Or, the buffer piston 72, the supply piston 74 and the modulation piston 76 can be integrated in a single piece with the piston rod 70. A link 82 is also connected to the piston rod 70. also connects to the disk 80, which is located within the integral valve body 40. The piston module 68 is removable within the integral valve drive 42. However, the modulation piston 76 is only removable. within the modulation chamber 65 and the supply piston 74 is only removable within the feed chamber 64. The buffer piston 72 is removable within a passageway 66 and can move from the passageway 66 to the buffer reservoir 62, but it can not move into the feed chamber 64. The buffer piston 72 forms a seal in the passageway 66, allowing very little or no of air to flow through the tam piston Similarly, the supply piston 74 forms a seal in the feed chamber 64, and the modulating piston 76 forms a seal in the modulation chamber 65. The disc 80, in the closed position (as shown in FIG. 2), forms a seal in the integral valve body 40 and thus in the purge flow evacuation pipe 22. The seal prevents the purge flow from flowing from the purge flow discharge pipe 22 to the purge flow pipe 22. the discharge pipe 26. The deflection of the buffer piston 78 is a passageway which allows the fluid to pass through the buffer piston 72. The deflection of the buffer piston 78 may be a hole drilled through the buffer piston 72, may be a space in the seal around the buffer piston 72, or another port or passage within the integral valve drive 42 connecting the buffer reservoir 62 to the feed chamber 64. The link 82 is connected to pivotable way to the piston rod 70. The link 82 converts a linear movement of the piston module 68 into a rotational movement of the disc 80. The disc 80 is shown in the closed position, preventing the purge flow B from flowing to the evacuation 26. The other features of FIG. 2 are presented below, together with FIG. 3, to further describe the operation of the integral valve 24 in the purge system 10.
    [0006] 3031157 FIG. 3 is a schematic view of a portion of a purge control system 10 and a sectional view of an integral valve 24 in accordance with FIG. 2, but in a second state. The components and connections of FIG. 3 are all in accordance with FIG. 2, but the positions of the components differ. In the state illustrated in FIG. 3, the buffer piston 72 is located inside the buffer tank 62, and only the piston rod 70 is (partially) in the passageway 66. The modulation piston 76 is located in the modulation chamber 65, but it is located closer to the end E1 than the modulation piston 76 of the first state shown in FIG. 2. The supply piston 74 is located in a supply chamber 64, but is located closer to the E1 end than the modulation piston 76 of the state shown in FIG. 2. The portion of the link 80 connected to the piston rod 70 is located closer to the end E1 than the portion of the link 80 connected to the piston rod 70 in the state shown in FIG. 2. This change of position causes the disc 80 to rotate within the body of the valve 40, creating a partially open state, in which the purge flow B can pass through the integrating valve 24 and to the conduit. evacuation 26. When the piston module 68 is positioned according to FIG. 2, the disk 80 is in the closed position, preventing the purge flow B from passing through the integral valve 24. In this state, the upstream nozzle 58 will be in a closed position preventing the purge flow B from flowing to the integrated valve supply duct 50. However, part of the purge flow B will flow through the integrated valve control pipe 44 to a deflecting duct 48 incorporating the valve, where it will be stopped at the nozzle in In the same way, part of the purge flow B will flow through the integrated valve control line 44 to the buffer pipe 25 of the integral valve 46 and into the buffer tank 62. The buffer tank 62 will be pressurized by the purge flow B. Another portion of the purge flow B will flow through the deflection of the buffer piston 78 and into the feed chamber 64, where the purge flow B will be stopped by the supply piston 74, and will put under pressi we have the feeding chamber 64.
    [0007] The portion of the purge stream B that pressurizes the feed chamber 64 will apply pressure to the side of the supply piston 74 closer to the end 11a. This pressure causes the formation of the force Fs, illustrated in FIG. FIGs. 2 and 3. When the nozzle 58 is closed, the nozzle 60 will open, exposing the end of the modulation piston 76 closest to the E2 end to ambient pressures, which will be lower than the pressure in the flow. This causes the force Fs to be greater than the force Fm, maintaining the position of the piston module 68 shown in FIG. 2, and thus maintaining the position of the disk 80 illustrated in FIG. 2. As shown in FIG. 1, the control 53 can determine, based on a control input, that a component downstream of the purge system 10 requires a flow. In this case, it is desirable to allow the purge system B to pass through the integral valve 24. Then, the control 53 can send a control signal to the control input 54 of the TM2 torque motor ordering TM2 d. The TM2 torque motor can then open the nozzle upstream 58, simultaneously with the closure of the downstream nozzle 60. This allows the purge flow B to flow into the modulation chamber 65. the side of the modulation piston 76 closest to the end E2, causing the pressure to increase acting on the side of the modulation piston 76 closest to the end E2. The area of the face of the modulating piston 76 is larger than the air of the face of the supply piston 74. When F = P * A, (where F is the force, P is the pressure and A is a area), the same pressure acting on the face of the modulation piston 76 causes the force Fm to be larger than the force Fs. In many cases, the force Fm may become larger than the force Fs, even when the pressure acting on the modulation piston 76 is smaller than the pressure acting on the supply piston 74. Therefore, when the nozzle The upstream 58 begins to open and the downstream nozzle 60 begins to close, the pressure acting on the modulating piston 76 begins to increase and the force Fm also begins to increase. Due to the fact that the face area of the modulation piston 76 is greater than the face area of the supply piston 74, the force Fm will become larger than the force Fs before the pressure acting on the modulation piston 76 is equal to the pressure acting on the supply piston 74. When the force Fm becomes larger than the force Fs, the force balance on the piston module 68 will cause the piston module 68 to move in the direction of the force Fm. When the force Fm becomes larger than the force Fs and the piston module 68 moves in the direction of the force Fm, the fluid in the supply chamber 64 will be compressed by the supply piston 74, increasing the pressure In the same way, the buffer piston 72 will compress the fluid inside the buffer tank 62, increasing the pressure of the fluid inside the buffer tank 62. As the pressure inside the buffer tank 62 and the feed chamber 64 increases, the fluid 10 in these chambers will naturally flow to lower pressure volumes connected to the buffer tank 62 and the chamber In this case, the buffer tank 62 and the supply chamber 64 are connected to the buffer pipe 46 and the outlet pipe of the purge stream 22, which will have a lower pressure than that of the buffer tank 62. and of Thus, the fluid in these chambers will move toward the buffer line 46, the integral valve control line 44 and the purge flow outlet line 22. More specifically, the fluid from The buffer reservoir 62 will move to the buffer line 46, the integral valve control line 44 and the purge flow outlet line 22. The fluid from the feed chamber 64 will move through the piston deflection. buffer 78, to the buffer tank 62, then to the buffer line 46 and to the outlet line of the purge stream 22. However, the fluid from the supply chamber 64 will move out of the supply chamber 64 to a reduced speed. The reason for this is that the deflection of the buffer piston 78 is physically small, having a small sectional area, and therefore a high pressure drop with respect to that of the integrating valve buffer line 46. The pressure drop of the deflection of the buffer piston 78 causes the passage of the volume of fluid inside the feed passage 64 through the deflection of the buffer piston 78 at a flow rate lower than the flow rate of the fluid from the buffer reservoir 62 and circulating to the buffer line 46, the integral valve control line 44 and the purge flow outlet line 22. This causes a buffered movement of the piston module 68. In other words, the movement of the piston module 68 caused by the force Fm which is greater than the force Fs is limited by the flow restriction caused by the buffer deviation 78. As shown in FIG. 3, when the piston module 68 continues to move in the direction of the force Fm, the buffer piston 72 will eventually be moved out of the passageway 66. Once the buffer piston 72 is moved out of the wayway 66 and in the buffer tank 62, the rate of flow of the fluid flowing out of the feed chamber 64 is no longer limited by the deflection of the buffer piston 78, because the fluid can circulate around the buffer piston 72 and towards the buffer pipe 46, the integral valve control line 44 and the outlet pipe of the purge stream 22.
    [0008] This allows the piston module 68 to move faster than when the buffer piston 72 is in the passageway 66. When the piston module 68 moves because the force Fm becomes larger than the force Fs (and any other The force acting on the piston module 68), the link 82 will articulate, pivoting the disc 80, and allowing the purge flow B to begin to flow through the integral valve 24 and to the discharge pipe 26. The piston module 68 can continue to move in the direction of the force Fm until the piston module 68 rotates the disc 80 to a fully open position. At this point, or at any position of the disc 80, the control 53 can maintain the position of the disc 80 by balancing the force Fm and the force Fs eh controlling the flow of fluid through the upstream nozzle 58 and the downstream nozzle 60. In addition, the control 53 may determine that the flow rate of the purge flow B flowing through the integral valve 24 must be reduced. In order to reduce the flow rate of the modulation flow M, the control 53 can send a control signal to the control input 54 of the torque motor TM2 instructing the TM2 to close the integrating flap 24. The torque motor TM2 can then begin to close the upstream nozzle 58 and simultaneously open the downstream nozzle 60. This allows the fluid inside the modulation chamber 65 which is on the side of the modulation piston 76 closest to the E2 side ( which will have a higher pressure than that of the integrated modulation line 50, the evacuation line 56, and the ambient pressure) to flow out of the modulation chamber 65 outward, resulting in the decrease pressure acting on the side of the modulation piston near the E2 end. This causes the decrease of the force Fm. Optionally, an upstream nozzle 58 continues to close and the downstream nozzle 60 continues to open, the force Fm will become smaller than the force Fs. When the force Fs becomes larger than the force Fm (or any other force acting on the piston module 68) the piston module 68 will begin to move in the direction of the force Fs. When the piston module 68 moves in the direction of the force Fs, the link 82 will articulate, pivoting the disc 80 to a closed position, resulting in the reduction of the flow rate of purge B of the integral valve 24. When the disc 80 When it reaches a fully open position (as shown in FIG 2), the flow rate of the purge flow B through the integrating valve 24 will stop. In some embodiments of the purge system 10, the fluid volume upstream of the integral valve 24 may be much smaller than the volume of the fluid downstream of the integral valve 24. In some embodiments, the volume pressure upstream will often be higher than the downstream volume pressure when the disc 80 of the integral flap 24 is closed. Therefore, when the disk 80 begins to open, even slightly, the relatively high pressure of the purge stream B will flow rapidly downstream to the larger volume at lower pressure. This causes a high pressure drop, or rapid pressure dissipation, of the system volume upstream of the integral valve 24. Due to this rapid pressure dissipation, the pressure inside the buffer tank 62 will decrease rapidly as the volume of the purge flow B flows rapidly through the integrating valve buffer line 46, the integral control line 44, the outlet line of the purge flow 22, through the disk 80 and through the discharge pipe 26 to the lower pressure volume downstream of the integral valve 24.
    [0009] Normally, in the prior art, this rapid dissipation of the pressure would result in a reduction of the feed force Fs, resulting in rapid movement of the piston module 68, causing a rapid opening of the disc 80. When the disc 80 opens more rapidly, the pressures upstream of the disk 80 fall further, resulting in a faster movement of the piston module 68 and a faster opening of the disk 80. To summarize this common scenario in the prior art, once the disk 80 is started, or slightly open, the pressure upstream of the disk 80 dissipates rapidly forcing the disk 80 to a fully open position. Then, a control system monitoring the conditions of the environmental control system must counteract this phenomenon by using the TM2 torque motor.
    [0010] However, in the present invention this phenomenon is greatly reduced by the additional chambers, plunger and deflection passages of the present invention which are not part of the prior art. In this new technique, the rapid reduction in pressure caused by the fission of the disc 80 always causes the rapid decrease of the pressure in the buffer tank 62 while the purge flow B 10 passes through the integral valve 24. Nevertheless, the pressure in the feed chamber 64 will not decrease rapidly.The reason is that the pressurized volume of the feed chamber 64 can not flow easily through the deflection of the buffer piston 78, because the deviation of the piston The pad 78 is physically small, with a small sectional area and, therefore, has a high pressure drop with respect to the integral valve check line 46. The pressure drop of the buffer piston deflection 78 prevents the volume of the valve. purge flow B within the feed passage 64 to pass through the deflection of the buffer piston 78 at a high flow rate. As a result, the pressure in the feed chamber 64 can not easily dissipate and hence the force Fs will not decrease easily and the piston module 68 will move in a controlled manner, opening the disc 80 in a similar. Essentially, the rapid opening of the disk 80 is prevented in a condition of rapid pressure dissipation. The rapid opening of the disk 80 is undesirable because the controllability of the volumes and flow rates that the disk 80 regulates will be lost or reduced, and the controllability of an environmental control system is critical. However, it is not always desirable to inhibit the fast action of the disk 80. At lower disk angles, or when the disk begins to open, it is desirable to prevent the fast opening of the disk. 80, but at larger disk angles, e.g., when the disk 80 is half open, it may be desirable to quickly adjust the disk 80 from the half open position to the fully open position. The passageway 66 allows this.
    [0011] When the piston module 68 moves in the direction of the force Fm, possibly, the buffer piston 72 will move out of the passageway 66 and into the buffer tank 62. When this occurs, as shown in FIG. 3, the purge flow volume B in the buffer tank 62 can circulate around the buffer piston 72 and in the feed chamber 64. And, the volume of the purge flow B located in the feed chamber 64 can circulating around the buffer piston 72 and in the buffer tank 62. Notably, the volume of the purge flow B located in the feed chamber 64 is not forced to flow through the deflection passage 78. This means that the volume of fluid acting on the supply piston 74 is no longer restricted by the flow restriction of the deflection passage 78. Therefore, when the buffer piston 72 is in this configuration (illustrated in FIG. , the torque motor TM2 can adjust the nozzles 58 and 60, obtain an increase in the force Fm, causing a rapid movement of the piston module 68 when the volume of the purge flow B in the buffer tank 62 feed chamber 64 can quickly to move in the 15 cond In summary, after the displacement of the buffer piston 72 out of the passageway 66, as shown in FIG. 3, the TM2 torque motor can quickly manipulate the adjustment weight of the disk 80, allowing for rapid regulation of the flow and pressure of the purge flow B passing through the integral valve 24. The result is that the integral valve 24 prevents unwanted effects of rapid opening due to rapid pressure dissipation at near-closed disk positions 80 (at lower disk angles), while providing fast action and pressure control and the flow rate of the purge flow B when the disk 80 is more open (at larger disk angles). In other words, the integral valve 24 has a gradual opening characteristic. The deflection of the buffer piston 78 may be sized to have the same front area as the upstream nozzle 58 at a given setting of the nozzle 58 as the nozzle 58 begins to open. This prevents the purge flow B from flowing out of the feed chamber 64 through the deflection of the buffer piston 78 to the buffer reservoir 62 at a rate greater than the flow of the purge flow B through the nozzle and to the modulation chamber 65. This contributes to the prevention of the rapid opening of the disk 80 due to rapid dissipation of the pressure. The integral check valve control line 44, integral check valve line 46, integral valve deflection 48, integral modulating line 50 and evacuation line 56 may be lines, pipes, ports or any passageway that can withstand a pressurized flow. These passageways may be made of metal, plastic or any other suitable material for the passage of a pressurized fluid. The piston rod 70, the buffer piston 72, the supply piston 74 and the modulating piston 76 may be made of steel, aluminum, plastic or any other material allowing the piston module 68 to operate in accordance with this disclosure. Disk 80, although described as a disc similar to that found in a butterfly valve, may be a ball, a grid, or any flow modulator. The nozzles 58 and 60 may have a single orifice or multiple orifices and may have any geometric shape for modulating the flow of fluid under pressure. The link 82 is illustrated in connection with a piston rod 70 between the supply piston 72 and the supply piston 74; however, the link 82 may be connected to the piston rod 70 anywhere, as long as the functionality of the link 82 described herein is maintained. The link 82 may be pinned, or otherwise mounted in rotation, as long as the link 82 can transform a linear movement of the piston module 68 into a rotational movement of the disc 80.
    [0012] Although the present disclosure discloses a valve which is used in a purge system of an environmental control system, the pneumatic valve described above may be used in any pneumatic control system. In addition, the pneumatic valve described herein can be applied to the hydraulic system or to any hydraulically actuated valve.
    [0013] Discussion of Possible Embodiments The following are non-exclusive descriptions of possible embodiments of the present invention. In one embodiment, a valve includes a modulation chamber for sending and receiving fluid through a first port of the chamber, a feed chamber, and a buffer tank for sending and receiving a fluid. a second fluid through a port of the buffer tank. The valve also includes a passageway between the buffer tank and the supply chamber, and a removable piston module within the valve, the piston module being configured to open and close a flow control device. The piston module comprises a rod, a modulating piston attached to the rod and movable within the modulation chamber, a supply piston attached to the removable rod within the feed chamber, and a buffer piston attached to the removable rod within the passageway and the feed chamber. The piston module also includes a deflection buffer piston that allows restricted flow passage between the supply chamber and the buffer tank when the buffer piston is located in the passageway. The valve of the preceding paragraph may optionally include, additionally and / or optionally, any of the following characteristics, configurations and / or components. The supply piston, the modulating piston and the buffer piston 20 may have piston face areas, and the areas of the front surface of the piston buffer and the front surface of the supply piston may each be smaller than the front area of the modulation piston. The deflection of the buffer piston may comprise a channel through the buffer piston.
    [0014] The fluid may be air and the valve may be pneumatic. A system may include the valve, and may also include a pipe, an upstream pressure source is a downstream component. The flow control device may be located in the pipe. The system may include a torque motor for controlling the flow of the second fluid.
    [0015] The torque motor may include an upstream nozzle positioned upstream of the port of the modulation chamber and a downstream nozzle positioned downstream of the port of the modulation chamber, the nozzles being controlled to open and close. The upstream nozzle may have a face area equivalent to a face area 5 of the deflection. The downstream component may have a volume that is larger than a volume located upstream of the pneumatic valve. The upstream pressure source can bleed air from a compressor section of a gas turbine engine.
    [0016] The downstream component may be a component of an environmental control system of an aircraft. The system may also include a control for sending control signals to the torque motor, wherein the control signals instruct the torque motor to open and close the upstream and downstream nozzles.
    [0017] Another embodiment consists of a method for controlling a valve with an actuator having a modulation chamber, a buffer tank, a feed chamber, a passageway and a piston module having modulating pistons, With the supply and buffer connected together, the modulating piston being removable in the modulation chamber, the supply piston is removable in the feed chamber and the buffer piston is removable between the passageway and the buffer tank, and wherein a deflection buffer piston allows a restricted flow passage between the supply chamber and the buffer tank when the buffer piston is located in the passageway. The method includes connecting a port of the modulation chamber to an upstream pressure to cause movement of the piston module that opens the valve. The method also includes venting air from the supply chamber to the buffer tank and then to the upstream source at a first velocity when the buffer piston is in the passage, and at a second velocity when the buffer piston is located in the buffer tank. The method of the preceding paragraph may optionally include, additionally and / or optionally, any of the additional characteristics, configurations and / or components, or steps.
    [0018] The port of the modulation chamber can connect at ambient pressure to cause movement of the piston module that closes the valve. Although the invention has been described with reference to one or more exemplary embodiments, those skilled in the art will understand that various modifications may be made to the elements described herein, and equivalents may be used in their place without depart from the scope of the invention. In addition, several modifications may be made to adapt a given situation or material to the teachings of this invention without departing from the essential scope thereof. Thus, it is contemplated that this invention is not limited to the particular disclosed embodiment or embodiments, but that this invention will include all embodiments that are within the scope of the appended claims.
    权利要求:
    Claims (15)
    [0001]
    1. A valve comprising: a modulation chamber (65) for sending and receiving a fluid through a first chamber port; a feed chamber (64); a buffer tank (62) for sending and receiving a second fluid through a chamber port; a passageway (66) between the buffer tank (62) and the feed chamber (64); a piston module (68) removable within the valve, wherein the piston module is configured to open and close a flow control device, the piston module comprising: a rod (70); a modulating piston (76) attached to the rod and removable within the modulation chamber (65); a supply piston (74) attached to the shaft and removable within the feed chamber (64); a buffer piston (72) secured to the rod and removable within the passageway (66) and the feed chamber (64); and a buffer piston deflection (78) which allows restricted flow passage between the feed chamber (64) and the buffer tank (62) when the buffer piston (72) is located in the passageway (66).
    [0002]
    The valve of claim 1, wherein the supply piston (74), the modulating piston (76) and the buffer piston (72) have piston face areas, and wherein the face area of the piston buffer piston and the front surface of the supply piston are each smaller than the front area of the modulation piston (76). 3031157 22
    [0003]
    The valve of claim 1, or 2, wherein the deflection of the buffer piston (78) comprises a channel through the buffer piston (72).
    [0004]
    The valve of claim 1, 2 or 3, wherein the fluid is air and the valve is pneumatic.
    [0005]
    5. System comprising the valve according to any one of the preceding claims, and further comprising a pipe, an upstream pressure source and a downstream component. 10
    [0006]
    The system of claim 5, wherein the flow control device is located in the conduit.
    [0007]
    The system of claim 5 or 6 and further comprising a torque motor (TM1, TM2) for controlling the flow of a second fluid.
    [0008]
    The system of claim 7, wherein the torque motor (TM1, TM2) comprises an upstream nozzle (58) positioned upstream of the port of the modulation chamber and a downstream nozzle (60) positioned downstream of the port of the modulation chamber, the nozzles 20 being controlled to open and to close.
    [0009]
    The system of claim 8, wherein the upstream nozzle (58) has a face area equivalent to the face area of the deflection. 25
    [0010]
    The system of any one of claims 7 to 9, further comprising a control (53) for sending control signals to the torque motor (TM1, TM2), wherein the control signals instruct the torque motor open and close the upstream and downstream nozzles (58, 60). 3031157 23
    [0011]
    11. System according to any one of claims 5 to 10, wherein the downstream component has a volume that is larger than the volume upstream of the pneumatic valve. 5
    [0012]
    The system of any one of claims 5 to 11, wherein the upstream pressure source is purge air from a compressor section of a gas turbine engine.
    [0013]
    The system of claim 12, wherein the downstream component is a component of an environmental control system of an aircraft.
    [0014]
    A method of controlling a valve with an actuator having a modulation chamber (65), a buffer tank (62), a feed chamber (64), a passageway (66) and a piston module ( 68) having modulation, supply and buffer pistons connected together, the modulation piston (76) being removable in the modulation chamber, the supply piston (74) is removable in the supply chamber and the buffer piston (72) is removable between the passageway and the buffer tank, and wherein a buffer piston deflection (78) permits a restricted flow passage between the supply chamber and the buffer tank when the buffer piston is located in the passageway, the method comprising: connecting a port of the modulation chamber to an upstream pressure to cause movement of the piston module which opens the valve venting the air from the chamber supply to the tank 25 ta mpon and then to the upstream source at a first speed when the buffer piston is in the passage, and at a second speed when the buffer piston is located in the buffer tank.
    [0015]
    15. The method of claim 14 and further comprising: connecting the port of the modulation chamber (65) to an upstream pressure to cause movement of the piston module (68) which closes the valve.
    类似技术:
    公开号 | 公开日 | 专利标题
    FR3031157A1|2016-07-01|
    FR2997746A1|2014-05-09|VALVE ASSEMBLY
    EP2778364B1|2015-10-14|Device for controlling the power supply of a system with a fluid
    EP2414242B1|2013-05-08|Fuelling device for propulsion of a launcher
    FR2884867A1|2006-10-27|DEVICE FOR REGULATING AIR FLOW CIRCULATING IN A ROTARY SHAFT OF A TURBOMACHINE
    EP2740981B1|2015-05-20|Valve with double control level and device for de-icing an air intake of an aircraft nacelle including said valve
    FR2470721A1|1981-06-12|DEVICE FOR MAINTAINING IN A CENTRAL POSITION A STEERING SYSTEM FOR A MOTOR VEHICLE
    EP2006587A1|2008-12-24|Watertight valve system
    WO2012164224A1|2012-12-06|Turbomachine with blow‑off valves located at the intermediate case
    EP3366588A1|2018-08-29|Method for ventilating a dynamic air channel and environmental control device and vehicle using said method
    FR2782344A1|2000-02-18|ENGINE BRAKE DEVICE FOR AN INTERNAL COMBUSTION ENGINE PROVIDED WITH AN EXHAUST GAS TURBOCHARGER
    EP1715264A1|2006-10-25|Improved expansion valve for air conditioning circuit
    FR2887595A1|2006-12-29|DEVICE ACTUATED BY A FLUID TO IMPLEMENT A MECHANISM DURING AN EMERGENCY
    FR2931884A1|2009-12-04|LOW NOISE EJECTOR FOR A TURBOMACHINE
    WO2015049453A1|2015-04-09|Jet pump for turbomachine lubrication chamber depressurization circuit
    FR3016657A1|2015-07-24|SYSTEM FOR PRESSURIZING A COOLING CIRCUIT OF AN INTERNAL COMBUSTION ENGINE EQUIPPED WITH A TURBOCHARGER UNIT
    EP2356359B1|2019-06-05|Blast cannon with mobile piston
    FR2492459A1|1982-04-23|METHOD AND DEVICE FOR REGULATING THE IDLE SPEED OF CONTROLLED IGNITION ENGINES
    EP3803118A1|2021-04-14|Device and method for compressing a low-pressure gas
    FR2509842A1|1983-01-21|TEMPERATURE AND PRESSURE CONTROL DEVICE FOR AN AIR CONDITIONING SYSTEM
    FR2479399A1|1981-10-02|PNEUMATICALLY ASSISTED RESTRAINT VALVE
    EP2623918B1|2016-08-24|Pneumatic launching device
    WO2021123418A1|2021-06-24|Station for regulating the circulation of a gas between two gas networks
    WO1990002899A1|1990-03-22|High pressure valve usable particularly in a fluid jet cutting tool
    BE430294A|
    同族专利:
    公开号 | 公开日
    US20160186885A1|2016-06-30|
    US9933085B2|2018-04-03|
    FR3031157B1|2021-06-11|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE1123875B|1960-06-21|1962-02-15|Forkardt Paul Kg|Pressure fluid operated control valve|
    US3746046A|1971-12-20|1973-07-17|Honeywell Inc|Dry torque motor servo valve|
    GB1396356A|1972-09-07|1975-06-04|Monotype Corp Ltd|Pneumatic actuator|
    US6708489B2|2001-08-03|2004-03-23|Parker & Harper Companies, Inc.|Pneumatic actuator|
    US9110475B2|2013-06-13|2015-08-18|Hamilton Sundstrand Corporation|Integral filter and regulator for valve|US10241523B2|2016-07-13|2019-03-26|Ge Aviation Systems, Llc|Differential pressure regulating shut-off valve|
    CN107131057B|2017-06-07|2018-08-17|长沙理工大学|A kind of O＆M method of gas turbine energy reutilization system|
    CN107165724B|2017-06-07|2018-08-17|长沙理工大学|A kind of gas turbine energy reutilization system|
    法律状态:
    2016-11-21| PLFP| Fee payment|Year of fee payment: 2 |
    2017-11-21| PLFP| Fee payment|Year of fee payment: 3 |
    2019-11-20| PLFP| Fee payment|Year of fee payment: 5 |
    2020-10-16| PLSC| Publication of the preliminary search report|Effective date: 20201016 |
    2020-11-20| PLFP| Fee payment|Year of fee payment: 6 |
    2021-11-18| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    US14/584,455|US9933085B2|2014-12-29|2014-12-29|Integrating valve with soft start|
    [返回顶部]