• 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 pump has an inlet, an outlet, and a fluid displacement mechanism operable to pump fluid from the inlet to the outlet. A cheek plate (30) in the pump is movable to control a flow of fluid from the outlet back to the inlet and thereby to vary the fluid flow to a hydraulic system supplied by the pump. Acting on different and unequal surface areas of the cheek plate are two fluid pressure forces. One fluid pressure force is provided by fluid pressure in a cheek plate control chamber (35). The force acts with a spring (31) biasing force to bias the cheek plate into a position blocking the flow of fluid from the outlet back to the inlet. The second fluid pressure force acts on the cheek plate against the spring force and the first fluid pressure force. A first orifice communicates the pump outlet with the hydraulic system, a second orifice (70) communicates the system (63) with the control chamber, and a third orifice communicates the control chamber with the pump inlet. The second and third orifices are sized relative to each other to provide, at a predetermined rate of flow to the system, a fluid pressure in the control chamber (35) which has a ratio to system pressure generally equal to the ratio of (a) the area of the cheek plate surface on which the second fluid pressure force acts to (b) the area of the cheek plate surface on which the first fluid pressure force acts.
    公开号:SU1074415A3
    申请号:SU813313396
    申请日:1981-07-06
    公开日:1984-02-15
    发明作者:Генри Дратчас Гильберт
    申请人:Трв Инк (Фирма)；
    IPC主号:
    专利说明:

    Isothermally refers to pumps, in particular to booster booster pumps, designed for use in vehicle steering control systems. A pump is known for creating a flow of fluid into the system, comprising a housing (having an inlet and an outlet, pumping means). in the housing to form a pumping chamber and operated for pumping fluid from the inlet to the outlet, a control device for maintaining a substantially constant flow of fluid into the system at frequencies of rotation of the pump above a predetermined frequency in the form of a side plate controlling fluid flow from the output back to the entrance, placed in the housing with the formation of the control chamber and with the possibility of movement after the disintegration of the forces acting on it, including the first and second pressure forces learn the media acting on the first and second surfaces of the side plate and the spring force, the first pressure force of the fluid created by the pressure of the fluid in the chamber. The direction of the spring is directed towards the side of the side plate to block the flow of the fluid from the output back to the inlet, and the second force of the fluid pressure to the side plate in the direction opposite to the action of the spring force and the first force of the fluid pressure, l. I. The disadvantage of this pump is the presence of a complicatedly designed servo valve and the fact that the serv.lap valve does not have stabilization. A pump is known to create a flow of fluid into a system, comprising a housing, having inlet and outlet pumping means located in the housing to form a pumping chamber and driven to pump fluid from inlet to outlet, a control device for maintaining, permanently the flow of fluid into the system at frequencies of rotation of the pump above a predetermined frequency in the form of a side plate controlling the flow of fluid from the outlet back to the inlet located in the housing to form a chamber after the unbalance of forces acting on it, including the first and second fluid pressure forces acting respectively on the first and second surfaces of the side plate and the spring force, the first fluid pressure force created by the fluid pressure in the chamber control, directed along with the spring towards the side of the side of the pressure grip to the position of blocking the flow of fluid from the outlet back to the entrance, and the second pressure force of the fluid to the side plate in the side It is opposite to the force of the spring and the first force, the pressure of the fluid 2. The disadvantage of this pump is the presence of a complicated servo valve with its stabilization system. A: The purpose of the invention is to simplify the design of the pump. This goal is achieved in that the pump for creating a fluid flow into the system, comprising a housing, having an inlet and an outlet, pumping means located in the housing to form a pumping chamber and actuating for pumping fluid from the inlet to the outlet, the control device for maintaining a substantially constant flow of fluid into the system at frequencies of rotation of the pump above a given frequency in the form of a side plate, controlling the flow of fluid from the outlet back to the input, placed in with the formation of a control chamber and with the possibility of displacing the forces acting on it after unbalancing,. first and second pressure forces of the fluid, acting respectively on the first and second surfaces of the side plate, and spring force, with the first pressure force of the fluid created by the pressure of the fluid in the control chamber being directed by BNiecTe with spring force to the side of the spin side the plates in the position of blocking the flow of fluid from the outlet back to the inlet, and the second force of the fluid pressure on the side plate in the direction opposite to the force of the spring and the first force of the fluid pressure It contains means for maintaining a continuous flow of fluid from the system to the control chamber and from the control chamber to the equilibration input, when the pump reaches a predetermined rotational frequency, made in the form of a first hole that connects the control chamber to the pump inlet, the second hole, connecting the system control chamber, and a third hole that communicates the output of the pump with the system 4Oi, and the ratio of the areas of the second and first surfaces of the side plate is equal to the ratio of the fluid flow in laziness to the pressure of the fluid in the system, - -: The pump may contain fuse. a pressure valve with a shut-off element that responds to pressure in the control chamber; FIG. 1 shows a pump in longitudinal section; FIG. 2 is a section A-A in FIG. one; in fig. 3 - a cut on, 1; in fig. 4 is a schematic representation of a fluid flow control system when the side plate is in the shut off position; in fig. 5 - the same as in the bypass position; in fig, b is a graph of the pump operating characteristics. The pump includes a housing 1 with a housing 2, in which there are inlet and outlet (not shown), pumping means, made in the form of a cam washer 3 installed radially relative to the housing 1 using h pins (not shown), an annular rotor 4 connected by means of a spline connection 5 with the inlet shaft b, located in the housing 1 with the formation of the pumping chamber 7 In the slots 8 of the rotor 4 sliding shoes 9 are installed. Pockets 11, Plate 12 is provided with inlet ports (not shown), co. with pumping pockets 11 and with the pump inlet, and outlet ports (not shown) communicated with pumping pockets 11 and with the pump outlet. The pump contains a control device to maintain,. essentially a steady stream of fluid into the system at frequencies of rotation of the pump above a predetermined part in the form of a side plate 13 with a sealing ring 14 located in the casing 2 of the housing 1 with the formation of the control chamber 15, the spring 16 is located in the control chamber 15 , pressing the side plate 13 towards the side of the pumping means. The side plate 13 has a first surface 17 and a second one. surface 18, consisting of two sections 19 and 20, for which the pressure of the fluid and the pumping pockets are connected to the first outlet of the pump. The area of the second surface 18 is smaller than the area of the first surface 17. The pump also contains means for maintaining a continuous flow of fluid from the systems (not shown) into the chamber, the control 15 and from the control chamber 15 to the input for balancing the forces when the pump reaches the predetermined frequency in the form of the first hole 21, which connects the control chamber 15 to the pump inlet, the second hole 22, which connects the system to the control chamber 15, and the third hole 23, which connects the outlet to the system, the first hole 21 is very small and both It ensures, very mgshy flux leakage at the pump entrance. The second hole 22 provides a differential between the pressure in the system and the pressure in the control chamber 15. The third hole 23 provides the difference between the pressure at the pump outlet and the pressure in the system. The dimensions of the first, second and third holes 21-23 are important for balancing the forces acting on the side plate 13. For flow through the first hole 21 and the second hole 22, two equations can be written: Q, cft, L (Q.j2scft. Where c is constant ; -the expenses through the first and second openings 21 and 22, respectively; A22, the areas of the first and second openings 21 and 22, respectively; LR2, ILR22, pressure on either side of the first and second openings 21 and 22, respectively. -JbP.;, Q2ic. Since systhetsy sa der | cpra Aeni nallern up After conversion, we get .- 2 Rkamera otpravleii Thus, the ratio of pressure in the system to the pressure in the control chamber is equal to the ratio of squares of the areas of the second and first holes 22 and 21, respectively, plus one. the value is constant. Consequently, the ratio system) / control chamber is a constant value and remains constant even when the pressure in the system changes, the force of the fluid pressure acting on the side plate 13 and pushing from pumping agents, it can be considered as a housing of two components, A and B (Fig. 5). One component A of the second force is created by pressure in the system, and the other B is created as a result of a pressure difference on both sides of the third port 23. On the other hand, the pressure acting on the second surface 18 of the side plate 13 includes the pressure in the system (pressure in the system is equal to the pressure in the pipeline 24) plus the differential pressure on both sides of the third hole 23. Thus, component A of the second force is equal to pressure in the system multiplied by the area of the second surface 18 of the side plate 13. Component 3 of the second force is equal to dy pressure on both sides of the third openings 23 multiplied by the area of the second surface 18 (FIG. 5)
    Since the ratio of the pressure in the system to the pressure in the control chamber; is determined by the relative size of the holes 21,22, then this dependence can be used to balance the forces acting on the side plate 13. In this case, the A component of the second force created by the pressure in the system acting on the side plate 1J balances the first force created by the pressure in control chamber 15. However, component A does not balance the spring forces.
    The component B of the second force acts on the side plate 13 against the action of the force of the spring 16. The third hole. 23 provides a difference between the pressure at the outlet of the pump and the pressure in the system. The size of this hole 23 is such that when the required constant flow is reached. Into the system, the differential pressure on both sides of the opening 23 has a value which ensures the creation of a second force constituting B on the side plate 13 equal to the spring 16. For safety, a safety valve 25 with a locking element 26 is provided in the side plate 13.
    As the flow rate to the system exceeds the required flow rate, the pressure drop on both sides of the third hole 23 increases and the resulting increase in the B component of the second force causes the side plate 13 to move. When the side plate 13 moves, the spring 16 compresses more and more, the amount of the side plate movement 13 is relatively small, yet the force of the spring 16 will increase slightly. As a result, a large pressure difference is required on both sides of the hole 23, necessary to balance the force of the spring. us 16,
    The graph (Fig. 6) shows a slight increase in the flow rate at the outlet with increasing frequency of rotation of the pump. This increase indicates the need for a greater pressure drop on both sides of the hole 23, which is necessary to balance the force of the spring 16 when it is compressed.
    In the course of pump operation, its performance is ensured in accordance with the curve shown in FIG. 6, the curve shows that with a pump rotation frequency equal to zero, the pump performance is zero. As the speed increases above zero, the capacity of the pump increases linearly to point X on the curve. In this interval, the pressure acting on the area of the second surface 18 of the side plate 13 gradually increases, the pressure acting on the surface 17 also gradually increases in a given dependence on the pressure in the system, due to the size of the holes 21 and 22, the pressure differential on both sides of the hole 23 is increased, but not enough to ensure that the acting on the side plate is created. 13, the second force B is equal to the preload of the spring 16, while the spring plate 16 acts on the side plate 13.
    Thus, when increasing (The pump rotation speed from zero to the frequency corresponding to point X on the curve shown in Fig. 6, the side plate 13 remains in the shutdown position shown in Fig. 4, when the pump rotation frequency reaches the frequency corresponding to point X on the curve ( Fig. 6), component B of the second force will balance the preload of the spring 16. In addition, the pressure in the control chamber 15 multiplied by the surface area 17 is equal to the pressure in the system multiplied by the area of the second surface 18 of the side plate 13 ( L moiety A second force), therefore, when the pump reaches a rotational speed corresponding to the point. on the curve shown in Figure 6, the side plate 13 adjacent to the pumping means, and acting on the side plate 13 forces the pressure fluid and the force of the spring 16 are balanced.
    As the frequency of rotation of the pump rises above the frequency corresponding to point X on the curve (FIG. 6), the flow through the opening 23 instantly increases, which causes a limited increase in the differential pressure on both sides of the opening 23. Consequently, the instantaneous increase
    The pressure acting on the second surface 18 of the side plate 13 causes simultaneous imbalance of the forces acting on the side plate 13. In particular, as a result of an increase in the pressure differential on both sides of the aperture 23, component B of the second force increases. The side plate is moved to the right, moving away from the pumping facilities from the position shown in FIGS. 1 and 4, which allows the fluid to bypass: The latter leads to a decrease in pump performance to a value equal to the flow rate (flow rate) at point X on the curve shown in FIG. 6
    After stabilization of the transient pressures and flow rates, the side plate 13 is balanced in one of the bypass positions. At this point, the frequency of rotation of the pump and the pressure on the output of the pump is greater than the frequency of rotation and the outlet pressure at point X in the curve of FIG. b. However, since the side plate 13 is at a short distance from the pumping means in the bypass position, providing: fluid bypass from the outlet windows of the pump to the inlet, the fluid flows from the pump into the system with essentially the same flow rate as at point x of fig. 6. In addition to reacting to changes in the pump speed, the control unit responds to changes in system pressure.
    An increase in pressure in the system decreases the flow rate in the system and there is a limited decrease in the pressure differential on both sides of the orifice 23. This will cause a decrease in the B component of the second force and an instantaneous imbalance of the forces acting on the side plate 13. The side plate 13 will move
    to the left, reducing the bypass fluid and thereby maintaining a constant required flow rate into the system. When the pressure in the system decreases, the flow into the system increases and the differential pressure on both sides of the opening 23 increases. The component B of the second force acting on the side plate 13 also increases. As a result, the side plate 13 moves to the right, increasing the bypass of the fluid and that MJM keeping the flow in the system substantially constant. .
    The forces acting on the side plate 13 are balanced when
    5, the pump capacity reaches the required constant flow, i.e. at point X on the curve shown in FIG. b.
    Balancing forces provide
    0 through holes, the holes 21, 22 provide a continuous flow of fluid from the system from the pump outlet through the control chamber 15 to the pump inlet, not needed
    5 servo valve to release pressure from the control chamber 15 to control the position of the side plate 13.
    For safety, a side valve 13 is provided with a safety valve 25 with a locking element 26 opening when a predetermined pressure is reached in the control chamber 15. When the predetermined pressure is reached and the valve 25 opens, the depressurise relieves pressure from the control chamber 15 to the pump inlet. In this case, the maximum bypass of the fluid immediately occurs, since the side plate 13 moves away from the pumping elements of the pump to the right In the extreme position.
    Performing the pump in this way will simplify its design.
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    权利要求:
    Claims (2)
    [1]
    AS A FLUID IN A SYSTEM, comprising a housing having an inlet and an outlet, pumping facilities located. in the housing with the formation of a pumping chamber and actuated to pump fluid from inlet to outlet, a reinforcing device for maintaining a substantially constant flow of fluid into the system at frequencies of rotation of the pump above a predetermined frequency in the form of a side plate controlling the flow of fluid from exit back to the input located in the housing with the formation of the control chamber and with the possibility of movement after unbalancing the forces acting on it, including the first and second forces of pressure of the fluid food acting on the first and second surfaces of the side plate, respectively, and the force of the spring, and the first force of the pressure of the fluid created by the pressure of the fluid in the control chamber is directed, together with the force of the spring, to the side of the pressed side plate in the blocking position of the fluid flow from the outlet back to the inlet, and the second fluid pressure force is directed to the side plate in the direction opposite to the action of the spring force and the first fluid pressure force, about τη and which, in order to simplify Instruction, it contains means for maintaining a continuous flow of fluid from the system No. i to the control chamber and from the control chamber to the inlet for balancing forces when the pump reaches a predetermined speed, made in the form of a first hole communicating the control chamber with the pump inlet, the second hole , communicating the system with the control chamber, and the third hole, communicating the pump output with the system, the ratio of the areas of the second and first surfaces of the side plate pg. in relation to the pressure of the fluid in the chamber control to the pressure of the fluid in the system.
    [2]
    2. The pump according to π. 1, the only reason is that it contains a safety valve having a shut-off element that responds to pressure in the control chamber.
    >
    I of the fluid pressure created by the pressure of the fluid in the control chamber is directed, together with the spring hoop, to the side of the side plate pressing in the blocking position of the fluid flow from the outlet back to the inlet, and the second fluid pressure force to the side plate opposite the action of the force of the spring and the first '0 force, pressure of the fluid (2].
    The disadvantage of this pump is the presence of a complex servo valve with its stabilization system. ‘
    The purpose of the invention is to simplify the design of the pump.
    This goal is achieved by the fact that the pump to create a fluid flow into the system, comprising a housing having an inlet and an outlet, pumping means located in the housing to form a pumping chamber and actuated to pump fluid from the inlet to the outlet, a control device for maintaining essentially constant flow of fluid into the system at pump speeds above a predetermined frequency in the form of a lateral plate controlling the flow of fluid from the outlet back to the inlet located in the housing e with the formation of a control chamber and with the possibility of displacement after unbalancing, the forces acting on it, including the first and second forces of the pressure of the fluid, acting respectively on the first and second surfaces of the side plate, and the force of the spring, the first force of the pressure of the fluid, created by the pressure of the fluid in the control chamber, is directed together with the spring force towards the side of the side plate, to the blocking position of the fluid flow from the outlet back to the inlet, and the second pressure force of the fluid s - in the side plate in the direction opposite the action of the spring force and the first fluid pressure force
    '. the medium contains means for maintaining a continuous flow of fluid from the system to the control chamber and from the control chamber to the input for balancing the forces when the pump reaches a predetermined speed, made in the form of a first hole,. communicating a control chamber with a pump inlet, a second opening communicating a system with a control chamber, and a third. a hole communicating a pump output with a system, the ratio of the areas of the second and first surfaces of the side plate being equal to the ratio of the fluid pressure in the control chamber to the fluid pressure in system.
    类似技术:
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    US4142841A|1979-03-06|Variable displacement pump control
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    同族专利:
    公开号 | 公开日
    ES503710A0|1982-04-16|
    AR227432A1|1982-10-29|
    EP0043947A1|1982-01-20|
    ES8204081A1|1982-04-16|
    JPS6137471B2|1986-08-23|
    US4408963A|1983-10-11|
    EP0043947B1|1984-07-25|
    AU7238681A|1982-01-14|
    BR8104301A|1982-03-23|
    JPS5773884A|1982-05-08|
    MX154583A|1987-10-07|
    DE3165046D1|1984-08-30|
    CA1164728A|1984-04-03|
    AU541890B2|1985-01-24|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2759423A|1952-11-28|1956-08-21|Vickers Inc|Power transmission|
    US2818813A|1954-09-09|1958-01-07|Vickers Inc|Power transmission|
    US2809588A|1955-03-07|1957-10-15|Vickers Inc|Power transmission|
    US3578888A|1969-04-18|1971-05-18|Abex Corp|Fluid pump having internal rate of pressure gain limiting device|
    US3713757A|1971-03-18|1973-01-30|Gen Motors Corp|Hydraulic energy translating device|
    US3822965A|1972-11-02|1974-07-09|Trw Inc|Pumps with servo-type actuation for cheek plate unloading|
    US3930759A|1974-06-03|1976-01-06|Trw Inc.|Integral housing pump with servo controlled cheek plate|
    US4014630A|1974-06-03|1977-03-29|Trw Inc.|Power steering pump|
    US4008002A|1975-11-07|1977-02-15|Sperry Rand Corporation|Vane pump with speed responsive check plate deflection|JPH059313B2|1984-03-29|1993-02-04|Honda Motor Co Ltd|
    US4834631A|1988-04-04|1989-05-30|Carrier Corporation|Separator and biasing plate|
    GB2262568B|1991-12-21|1995-01-04|Bryan Nigel Victor Parsons|Sealing in an oscillatory rotary engine|
    GB9417477D0|1994-08-31|1994-10-19|Mcdonald Donald A|Rotary hermetic refrigeration motor/compressor|
    EP1715186A3|2005-04-21|2007-10-24|ixetic Hückeswagen GmbH|pump|
    US7438542B2|2005-12-19|2008-10-21|Dana Automotive Systems Group, Llc.|Fluid pump assembly|
    US9127674B2|2010-06-22|2015-09-08|Gm Global Technology Operations, Llc|High efficiency fixed displacement vane pump including a compression spring|
    JP2016109029A|2014-12-05|2016-06-20|株式会社デンソー|Vane type pump and fuel vapor leakage detecting device using the same|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US06/166,407|US4408963A|1980-07-07|1980-07-07|Power steering pump|
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