Fully Compensated Fluid Control Valve

This invention relates generally to direction and flow control valves capable of proportionally controlling a number of loads under positive and negative load conditions.

In more particular aspects this invention relates to fluid control valves provided with positive and negative load compensation.

In still more particular aspects this invention relates to negative load compensation, of a direction and flow control valve, in which fluid flow from each of the actuator ports is individually compensated.

Closed center fluid control valves, pressure compensated for control of positive and negative loads, are desirable for a number of reasons. They permit load control with reduced power losses and therefore increased system efficiency. They also permit simultaneous proportional control of multiple positive and negative loads. Such fluid control valves are shown in my U.S. Pat. No. 4,180,098, issued Dec. 5, 1979 and also in my U.S. Pat. No. 4,222,409, issued Sept. 16, 1980. The negative load compensation of the valves of those patents suffers from certain unobvious disadvantages.

In the valve of U.S. Pat. No. 4,180,098 the flow of fluid, under negative load pressure, is delivered from one load chamber, through passage leading past two transfer tubes in the comparatively long transverse core, to the negative load compensator and therefore is subjected to a substantial pressure drop, before it enters the compensator, while the fluid flow from the other load chamber directly enters the compensator. This factor influences the magnitude of the control pressure differential in a different way for each of the load chambers and is therefore undesirable. The existance of large resistance to flow in the exhaust branch of the circuit also decreases efficiency, when controlling a positive load while the valve size becomes larger and the transfer tubes themselves create an additional cost.

In the valve of U.S. Pat. No. 4,222,409 the flow of fluid, under negative load pressure is delivered from one load chamber, through a passage provided in the hollow spool, to the negative load compensator providing large resistance to flow, large unbalance in control pressure differentials, severe limitation in maximum fluid flow through the valve, large throttling and therefore efficiency loss, increase in valve length and increase in cost.

It is therefore a principle object of this invention to provide a pressure compensated valve with an identical fluid flow path and identical minimum resistance to flow from both load chambers to the negative load compensator, resulting in identical control differential at minimum efficiency loss.

Another object of this invention is to provide a pressure compensated valve with two identical negative load throttling circuits, in which fluid flow from each load chamber, subjected to negative load pressure is individually controlled.

It is a further object of this invention to provide a pressure compensated valve with a simplified low resistance exhaust circuit, adaptable to negative load compensation by a compensator provided with two sets of individual negative load throttling slots.

Briefly the foregoing and other additional objects and advantages of this invention are accomplished by providing novel negative load compensation for a flow control valve, in which fluid under negative load pressure, from each actuator port, is individually throttled to provide an identical control pressure differential, while also providing an exhaust circuit with greatly reduced resistance to flow.

Additional objects of this invention will become apparent when referring to the preferred embodiment of the invention as shown in the accompanying drawing and described in the following detailed description.

The drawing is a longitudinal sectional view of an embodiment of a flow control valve provided with a single positive and negative load compensator equipped with two sets of negative load throttling slots, also showing a longitudinal sectional view of an embodiment of a pilot valve amplifying stage controlling the compensator with system lines, second flow control valve, system actuator, system pump and system reservoir shown diagrammatically.

Referring now to the drawing, an embodiment of a flow control valve, generally designated as 10, is shown interposed between diagrammatically shown fluid motor 11 driving load W and a pump 12, of a fixed displacement or variable displacement type, driven by a prime mover, not shown. Fluid flow from the pump 12 to flow control valve 10 and a circuit of diagrammatically shown flow control valve 13 is regulated by pump flow control 14. If pump 12 is of a fixed displacement type, pump flow control 14 is a differential pressure relief valve, which, in a well known manner, by bypassing fluid from pump 12 to a reservoir 15, maintains discharge pressure of pump 12 at a level, higher by a constant pressure differential, than load pressure developed in fluid motor 11. If pump 12 is of a variable displacement type, pump flow control 14 is a differential pressure compensator, well known in the art, which by changing displacement of pump 12, maintains discharge pressure of pump 12 at a level, higher by a constant pressure differential, than load pressure developed in fluid motor 11.

The flow control valve 10 is of a fourway type and has a housing 16 provided with a bore 17, axially guiding a valve spool 18. The valve spool 18 is equipped with lands 19, 20 and 21, which in neutral position of the valve spool 18, as shown in the drawing isolate a fluid supply chamber 22, load chambers 23 and 24 and outlet chambers 25 and 26. Lands 19, 20 and 21, of valve spool 18, are provided with metering slots 27, 28, 29 and 30 and timing slots 31, 32, 33 and 34. Negative load sensing ports 35 and 36 are positioned between load chambers 23 and 24 and outlet chambers 26 and 25. Positive load sensing ports 37 and 38 are located between supply chamber 22 and load chambers 23 and 24. Negative load throttling slots 39, of control spool 40, equipped with throttling edges 41, connect the outlet chamber 26 with an exhaust chamber 42, which in turn is connected to reservoir 15, while negative load throttling slots 39a, equipped with throttling edges 41a, connect the outlet chamber 25 with an exhaust chamber 42a, which in turn is connected to reservoir 15.

The pump 12, through its discharge line 43, is connected to an inlet chamber 44. The inlet chamber 44 is connected through positive load throttling slots 45, on control spool 40, provided with throttling edges 46, with the fluid supply chamber 22. Bore 47 axially guides the control spool 40, which is biased by control spring 48, contained in control space 49, towards position as shown. The control spool 40 at one end projects into control space 49, the other end projecting into chamber 50, connected to the reservoir 15. A pilot valve assembly, generally designated as 51, comprises a housing 52, provided with a bore 53, slidably guiding spool 54 and free floating piston 55. The spool 54 is provided with lands 56, 57 and 58, defining annular spaces 59 and 60. Annular space 61 is provided within the housing 52 and communicates directly with bore 53. The free floating piston 55 is provided with a land 62, which defines annular spaces 63 and 64 and is provided with extension 65, selectively engageable with land 58 of the spool 54. The spool 54 at one end projects into control space 66 and engages, with land 56 and spring retainer 67, a pilot valve spring 68. Control space 66 communicates through line 69 with check valves 70 and 71. The check valve 70 is connected by passage 72 with positive load sensing ports 37 and 38. The check valve 71 communicates through line 73 and check valves 71a and 71b with the outlet chambers 25 and 26. Annular space 61, of the pilot valve assembly 51, communicates through line 74 with control space 49 and also communicates through leakage orifice 75, with annular space 60, which in turn is connected to reservoir 15. Annular space 59 communicates through lines 76 and 77 which check valves 78 and 79. Check valve 78 is connected to discharge line 43 and check valve 79 is connected through line 80, with outlet chambers 25 and 26. Annular space 64 is connected by line 81 with the supply chamber 22. Annular space 63 is connected by line 82 and passage 83 with negative load sensing ports 36 and 35. Positive load sensing ports 37 and 38 are connected through passage 72, line 84 and a check valve 85 and a signal line 86 with the pump flow control 14. Control space 66 is connected through a leakage device 87 with the reservoir 15. Leakage device 87 may be of a straight leakage orifice type, or may be a flow control device, passing a constant flow from control space 66 to the reservoir 15. The leakage device 87 comprises a housing 88, provided with bore 89 guiding a spool 90, which defines spaces 91, 92 and 93. The spool 90 is provided with throttling slots 94, leakage orifice 95 and is biased by a spring 96. The load chambers 23 and 24 are connected, for one way fluid flow, by check valves 97 and 98, to schematically shown system reservoir, which also might be a pressurized exhaust manifold of the entire control system, as shown in the drawing.

The preferable sequencing of lands and slots of valve spool 18 is such, that when displaced in either direction from its neutral position, as shown in the drawing, one of the chambers 23 or 24 is connected by timing slots 32 or 33 to the positive load sensing port 37 or 38, while the other load chamber is simultaneously connected by timing slots 31 or 34 with negative load sensing port 35 or 36, the load chamber 23 or 24 being isolated from the supply chamber 22 and outlet chambers 25 and 26. Further displacement of valve spool 18 from its neutral position connects load chamber 23 or 24 through metering slot 28 or 29 with the supply chamber 22, while simultaneously connecting the other load chamber through metering slot 27 or 30 with outlet chamber 25 or 26.

As previously described the pump flow control 14, in a well known manner, will regulate fluid flow, delivered from pump 12, to discharge line 43, to maintain the pressure in discharge line 43 higher, by a constant pressure differential, than the highest load pressure signal transmitted through the check valve system to signal line 86. Therefore, with the valve spool 18 of flow control valve 10, in its neutral position blocking positive load sensing ports 37 and 38, signal pressure input to pump flow control 14 from signal line 86 will be at minimum pressure level, corresponding with the minimum standby pressure of the pump 12.

Assume that the load chamber 23 is subjected to a positive load and that the control pressure differential of the pilot valve assembly 51 is higher than the control pressure differential of the pump flow control 14. The pilot valve assembly 51 is shown on the drawing with the spool 54 in its equilibrium modulating position and with land 57 blocking the annular space 61. With the control system at rest the pilot valve spring 68 will move the spool 54 all the way to the left, connecting annular space 60 with annular space 61 and therefore connecting control space 49 with system reservoir. Under those conditions the control spool 40 will be maintained by the control spring 48 in the position as shown in the drawing. The initial displacement of the valve spool 18 to the right will connect, in a manner as previously described, the load chamber 23, subjected to positive load pressure, with positive load sensing port 37, while also connecting the load chamber 24 with negative load sensing port 35. The positive load pressure signal from positive load sensing port 37 will be transmitted through passage 72, line 84, check valve 85 and signal line 86 to the pump flow control 14 and, in a manner as previously described, will raise the discharge pressure of the pump 12 to a level, higher by a constant pressure differential, than the positive load pressure existing in the load chamber 23.

Further displacement of the valve spool 18 to the right will create a metering orifice through metering slot 29, between the load chamber 23 and the supply chamber 22, while also creating through metering slot 27 a similar metering orifice between the load chamber 24 and the outlet chamber 25. Therefore, fluid flow from the supply chamber 22 to the load chamber 23 will take place at a constant pressure differential, automatically maintained by the pump flow control 18, with the control spool 40 remaining in the position as shown in the drawing and with spool 54 in a position all the way to the left. Therefore the flow into the load chamber 23 will be proportional to the area of the metering orifice and therefore to the displacement of the valve spool 18 from its neutral position and independent of the magnitude of the load W.

Assume that while controlling positive load W through the flow control valve 10, a higher load pressure signal is transmitted from the schematically shown flow control valve 13 through the check valve 99 and signal line 86 to the pump flow control 14. The discharge pressure of the pump 12 will proportionally increase, increasing the pressure differential between the supply chamber 22 and the load chamber 23. The spool 54, of the pilot valve assembly 51, is subjected to the pressure differential between supply chamber 22 and the load chamber 23, since the annular space 64 is connected by line 81 to the supply chamber 22 and the control space 66 is connected by lines 69 and 69a, the check valve 70, passage 72 and positive load sensing port 37 to the load chamber 23. The increasing pressure differential between the pressure in the supply chamber 22 and the pressure in the load chamber 23 will move the spool 54 from left to right, against the biasing force of the pilot valve spring 68, into a modulating position, as shown in the drawing, increasing pressure in the control space 49, which will move the control spool 40 from right to left, into a position in which it will throttle fluid flow between the inlet chamber 44 and the supply chamber 22. Therefore, the spool 54, in its modulating position, will automatically throttle, by control spool 40, the fluid flow from the inlet chamber 44 to the supply chamber 22 to maintain the pressure differential between the supply chamber 22 and the load chamber 23, at a constant predetermined level, equivalent to preload in the pilot valve spring 68 and higher than the constant pressure differential of the pump flow control 14. Therefore, irrespective of the pump pressure level, the pilot valve assembly 51 will automatically control the throttling action of the control spool 40, to maintain a constant pressure differential between the supply chamber 22 and the load chamber 23, and across the metering orifice, created by displacement of the metering slot 29. During this control action the free floating piston 55 will be subjected to the pressure differential between the supply chamber 22 and the load chamber 24, which is subjected to minimum pressure and therefore it will be maintained in a position all the way to the left, out of contact with the spool 54.

Assume that load chamber 23 is subjected to negative load pressure and that the valve spool 18 was moved to the left, connecting the negative load pressure with the negative load sensing port 36, while also connecting the pressure at minimum level in the load chamber 24 with the positive load sensing port 38. The negative load pressure, from the negative load sensing port 36, will be transmitted through passage 83 and line 82 to annular space 63, where it will react on the cross-sectional area of the free floating piston 55, moving the spool 54 to the right, against the biasing force of the pilot valve spring 68, connecting annular space 59 with annular space 61 and therefore connecting annular space 59 with control space 49. The pump discharge pressure in control space 49 will move the control spool 40 all the way from right to left, isolating with throttling edges 41 the outlet chamber 26 from the exhaust chamber 42, while also isolating with throttling edges 41a the outlet chamber 25 from the exhaust chamber 42a.

Further displacement of the valve spool 18 to the left will create a metering flow orifice through metering slot 30, between the load chamber 23 and the outlet chamber 26, while also creating a similar metering orifice, through metering slot 28, between the load chamber 24 and the supply chamber 22, the supply chamber 22 being completely isolated from the inlet chamber 44 by the position of the throttling edges 46. The negative load pressure from the load chamber 23, will be transmitted through created metering orifice to the outlet chamber 26, which is completely isolated from the exhaust chamber 42 by the position of control spool 40. The pressure in the outlet chamber 26 will rise, will open check valves 71a and 71, close check valves 71b and 70 and will be transmitted through line 69 to the control space 66, where it will react on the cross-sectional area of spool 54. The rising pressure in control space 66 will move the spool 54 and the free floating piston 55 into a modulating position, as shown in the drawing, regulating the pressure in control space 49 and therefore also regulating the position of the control spool 40. The control spool 40 will move from left to right into a throttling position, in which fluid flow from the outlet chamber 26 to the exhaust chamber 42 will be sufficiently throttled, to maintain a constant pressure differential between the load chamber 23 and the outlet chamber 26. The magnitude of this constant pressure differential, the same as that developed when controlling a positive load, is dictated by the preload of the pilot valve spring 68. Therefore the pilot valve assembly 51 will automatically control the throttling action of the control spool 40, to maintain a constant pressure differential between the load chamber 23 and the outlet chamber 26, irrespective of the magnitude of the negative load. Since during control of negative load the supply chamber 22 is completely isolated from the inlet chamber 44, the make-up fluid flow into the load chamber 24 will be supplied, either from the pressurizing exhaust manifold or from the system reservoir by the check valve 98. While controlling negative load annular space 59 is connected, through check valves 79 and 71a, with the outlet chamber 26. If the pump discharge pressure is greater than the negative load pressure in the outlet chamber 26, the check valve 78 will open, the check valve 79 will close and annular space 59 will be subjected to pump pressure, the energy from the pump being utilized to control position of the control spool 40. If the pump is at its standby pressure, which is usually the case when controlling a negative load, the higher negative load pressure will open the check valve 79, close the check valve 78 and be transmitted to annular space 59. Therefore under those conditions the energy to control the position of the control spool 40 will be supplied from the negative load. While controlling a negative load from the load chamber 23 the outlet chamber 26 will be pressurized by the throttling action of negative load throttling slots 39 and the outlet chamber 25, isolated from the load chamber 24 by the land 19, will be connected through negative load throttling slots 39a to the exhaust chamber 42a, which in turn is connected to reservoir 15. The check valve 71b will remain closed isolating the outlet chamber 25 from the negative load pressure in outlet chamber 26.

Assume that the load chamber 24 is subjected to negative load pressure and that the valve spool 18 was moved to the right, connecting through signal slot 31 the negative load pressure with the negative load sensing port 35, while also connecting the pressure at minimum level in the load chamber 23 with the positive load sensing port 37. The negative load pressure, from the negative load sensing port 35, will be transmitted through passage 83 and line 82 to annular space 63, where it will react on the cross-sectional area of the free floating piston 55, moving the spool 54 to the right, against the biasing force of the pilot valve spring 68, connecting annular space 59 with annular space 61 and therefore connecting annular space 59 with control space 49. The pump discharge pressure in control space 49 will move the control spool 40 all the way from right to left, isolating with throttling edges 41 the outlet chamber 26 from the exhaust chamber 42, while also isolating with throttling edges 41a the outlet chamber 45 from the exhaust chamber 42a.

Further displacement of the valve spool 18 to the left will create a metering flow orifice through metering slot 27, between the load chamber 24 and the outlet chamber 25, while also creating a similar metering orifice, through metering slot 28, between the load chamber 23 and the supply chamber 22, the supply chamber 22 being completely isolated from the inlet chamber 44 by the position of the throttling edges 46. The negative load pressure from the load chamber 24 will be transmitted through created metering orifice to the outlet chamber 25, which is completely isolated from the exhaust chamber 42a by the position of control spool 40. The pressure in the outlet chamber 25 will rise, will open check valves 71b and 71, close check valves 71a and 70 and will be transmitted through line 69 to control space 66 where it will react on the cross-sectional area of spool 54. The rising pressure in control space 66 will move the spool 54 and the free floating piston 55 into a modulating position, as shown in the drawing, regulating the pressure in control space 49 and therefore also regulating the position of the control spool 40. The control spool 40 will move from left to right into a throttling position, in which fluid flow from the outlet chamber 25 to the exhaust chamber 42 will be sufficiently throttled, to maintain a constant pressure differential between the load chamber 24 and the outlet chamber 25. The magnitude of this constant pressure differential, the same as that developed when controlling a positive load is dictated by the preload of the pilot valve spring 68. Therefore the pilot valve assembly 51 will automatically control the throttling action of the control spool 40, to maintain a constant pressure differential between the load chamber 24 and the outlet chamber 25, irrespective of the magnitude of the negative load. Since during control of negative load the supply chamber 22 is completely isolated from the inlet chamber 44 the make-up fluid flow into the load chamber 23 will be supplied, either from the pressurized exhaust manifold or from the system reservoir by the check valve 97. While controlling negative load annular space 59 is connected, through check valves 79 and 71b, with the outlet chamber 25. If the pump discharge pressure is greater than the negative load pressure in the outlet chamber 25, the check valve 78 will open, the check valve 79 will close and annular space 59 will be subjected to pump pressure, the energy from the pump being utilized to control the position of the control spool 40. If the pump is at its standby pressure, which is usually the case when controlling a negative load, the higher negative load pressure will open the check valve 79, close the check valve 78 and be transmitted to annular space 59. Therefore under those conditions the energy to control the position of the control spool 40 will be supplied from the negative load. While controlling a negative load from the load chamber 24 the outlet chamber 25 will be pressurized by the throttling action of negative load throttling slot 39a and the outlet chamber 26, isolated from the load chamber 23 by the land 21, will be connected through negative load throttling slots 39 to the exhaust chamber 42, which in turn is connected to reservoir 15. The check valve 71a will remain closed isolating the outlet chamber 26 from the negative load pressure in outlet chamber 25.

During control of negative load the control arrangement, as shown in the drawing, uses two identical individual circuits, each of them throttled by separate negative load throttling slots. The control of negative load from the load chamber 23 uses metering slot 30, the outlet chamber 26, negative load throttling slots 39 and the exhaust chamber 42. The control of negative load from the load chamber 24 uses metering slot 27, the outlet chamber 25, negative load throttling slots 39a and the exhaust chamber 42a. Since the configuration and resistance to flow of passages interconnecting individual load chambers to the individual negative load throttling slots is identical and since the two sets of the negative load throttling slots, positioned on the control spool 40, are identical, the control characteristics of the negative load control from individual load chambers is identical, providing a unique negative load control system for a fully compensated flow control valve. In this way not only the position of the valve spool 18 provides identical flow control characteristics, in control of bidirectional negative loads, making it ideally suited for control of a load using a microprocessor without load position feedback, but the resistance to the flow of the exhaust passages becomes minimal in control of positive load and the cored exhaust passages of the valve become simple and inexpensive.

The leakage device 87 connects control space 66 with the system reservoir. The leakage device 87 may take the form of a simple orifice, or may be of a compensated type, as shown in the drawing, permitting a constant flow, at a very low flow level, from control space 66. Such a leakage flow is necessary to permit the spool 54 to move from left to right. Such a movement will close the check valves 70 and 71, the displaced fluid from control space 66 being passed by the leakage device 87. The spool 90 of the leakage device 87, in a well known manner throttles, by throttling slots 94, the fluid flow from space 92 to space 93, to maintain space 93 at a constant pressure, equivalent to preload in the spring 96. Since space 93 is maintained at constant pressure and since space 91 is connected to system reservoir, there exists a constant pressure differential across leakage orifice 95, corresponding to a constant flow from control space 66 and independent of the pressure level in control space 66.

The leakage orifice 75 is provided between annular space 61 and system reservoir. Use of such a leakage orifice, well known in the art, increases the stability margin of the pilot valve control.

The pilot valve assembly 51 is phased into the control circuit of the flow control valve 10 in such a way, that it is used to control the throttling action of control spool 40 during control of both positive and negative loads. This arrangement provides not only a less expensive but a more stable control, with identical pressure differential, while controlling positive and negative loads.

The pilot valve assembly 51 utilizes the energy supplied either by the pump or the negative load in control of control spool 40. This two stage type control uses minimum flows through the load sensing ports and therefore provides a very fast responding control, completely eliminating the influence of the flow forces acting on the control spool 40.

Although the preferred embodiment of this invention has been shown and described in detail it is recognized that the invention is not limited to the precise form and structure shown and various modifications and rearrangements as will occur to those skilled in the art upon full comprehension of this invention may be resorted to without departing from the scope of the invention as defined in the claims.