JPS58501284A - fluid control device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] Load adaptive driftwood control device The present invention generally relates to changes in the level of the controlled difference between the pump discharge pressure and the load pressure signal. If possible, the control 1 difference between 2 and 1" is 11. The present invention relates to a control device for a load response device that is automatically maintained at a constant level.

Background technology In further particular embodiments, the present invention provides for adjusting the pump discharge pressure in response to an external control signal. 1-d) load response with a controlled pressure differential variation between the force and the load pressure, if possible; The present invention relates to a control device for a device.

In still another specific aspect of the present invention, the control signal is transmitted to a pump discharge flow rate control device. An orifice located between the fluid motor that supplies the equipment and drives the equipment pump and load. A signal change control for a load responsive device that regulates and regulates the pressure differential acting across the system. related to control equipment.

The pump discharge flow rate control device adjusts the pump discharge pressure and load pressure in response to load pressure signal processing. Load-responsive devices that maintain a constant pressure difference between ing. In such a control device, a fluid motor that drives the pump and load of the device is required. The flow rate of fluid through an orifice placed between the It is independent of the force and load on the device. This type of load response device has several principles. It's very heavy. Such load responsive devices allow excellent control of the load This makes it possible to drive loads at very high device efficiencies. Such a load-responsive fluid control device is disclosed in U.S. Pat. No. 2,89 issued to Allen et al. No. 2,312 and the applicant's U.S. Patent No. 2,312 dated May 20, 1969. No. 3,444,689. Such a load-responsive fluid control device One disadvantage of this is that the control pressure differential must be selected and incorporated into the equipment design. and that the control pressure difference is kept constant under all operating conditions of the device. . of the differential pressure of the device for specific conditions related to controlling the flow, pressure, or load of the device. By adjusting the level of allocation.

Not only the control characteristics of the device are improved and the efficiency of the device is improved, but also the device independent adjustment of equipment performance while the load is controlled by the load-responsive directional control valve. section becomes possible.

Summary of the invention Therefore, one main object of the present invention is to control between pump discharge pressure and load pressure. The level of the difference, i.e. the pressure difference, can be changed while this control difference is Improved load response controller automatically maintained constant at a controlled level The goal is to provide a

Special table 1984-501284 (6) Another object of the present invention is to control the load of the device by connecting the pump and fluid motor of the device. While the pressure difference across the orifice between The area of the orifice may be varied or the area of the orifice may be kept constant. Due to the control differential, i.e. the pressure differential, acting across this orifice while The object of the present invention is to provide a load responsive control device that can achieve the above-mentioned results.

A further object of the invention is to control the metering orifice in response to an external control signal. To provide a load-responsive control device that allows a controlled pressure difference to be varied across the That is.

A further object of the invention is that the external control signal is Regulating the pressure differential acting across the metering orifice of a load-responsive directional control valve and? ! l can be controlled during which the load on the device is changed by changing the area of the metering orifice. The object of the present invention is to provide a response control device for a load that is controlled in a controlled manner.

A further object of the present invention is to provide a control signal supplied to a pump discharge flow rate controller. An orifice placed between the device's pump and the fluid motor that drives the load An object of the present invention is to provide a controller for a load responsive device that controls the pressure differential across a load responsive device.

Briefly stated: 1. The above objects and other additional objects and advantages of the present invention. changes the level of control difference between pump discharge pressure and load pressure, while this control The load-responsive pump controller allows the control difference to be kept constant and automatic at each controlled level. This is achieved by providing a novel dynamically maintained load responsive controller.

This control action, which responds to an external control signal, is based on the conventional one-leg pressure difference of a load-responsive device. In addition to the control effects, two parallel control inputs can be provided to the device. like this Controlled pressure differential during the conventional operating mode of the load response control device by Not only can the level of -! be adjusted to any desired value, but also -! load response By changing the control difference at any control position of the directional control valve, the load can be reduced completely. can be controlled.

Additional features of the invention are shown in the accompanying drawings and described in the detailed description below. It will become clear upon reference to the preferred embodiments of the invention.

Brief description of the drawing Figure 1 shows a schematic diagram of a fluid motor, a device pump, and a pump control device. for adjusting the level of control difference from some preselected level to zero level Illustrated diagram of the load response control device, Figure 2 shows the differential pressure control of Figure 1 with one fixed orifice added. Illustrated diagram of the device, Figure 6.1 Diagrammatic diagram of fluid motor, device pump and pump Leveling of the control difference from the minimum preselected value to the maximum level “with the control device” Illustrative diagram of a load-responsive control device for adjusting the bell, FIG. 1 and 6, along with body motors, equipment pumps, and pump control devices. Load response - Illustrated diagram of the device combined with the control device, Figure 5 shows the fluid motor and port for the device. Another implementation of the load-responsive control i@l device of FIG. 1 with pump and pump controller Illustrative diagram of the embodiment, Figure 6 schematically shows the load-responsive directional control valve and the differences between different types. An illustrative diagram of the load response control device shown in Fig. 5 in combination with a pressure restrictor, Fig. 68 shows a constant An illustration of a differential pressure control device that provides a preselected pressure difference, Figure 7 shows a load-responsive pump. An illustration of one structure of a load-responsive pump control device; FIG. 8 shows another structure of a load-responsive pump control device FIG. 9 is an illustrative diagram of yet another structure of the load-responsive pump control device, and FIG. The figure shows the manual operation sent to the load response control devices in Figures 1, 6, 4 and 5. Illustrated diagram of human control, Figure 11 shows the load response of Figures 1, 6, 4 and 5. Illustrated diagram of the hydraulic control input sent to the control device, Figure 12 is the same as Figure 1, Figure 4, and Figure 4. and an illustrative diagram of the mechanical control force transmitted to the load response control device in Figure 5, 1st Figure 6 shows the load response aspects of Figures 1, 6, 4 and 5] Illustrative diagram of the pneumatic pressure control input, and Figure 14 is sent to the load response control device in Figure 6. FIG. 3 is a schematic diagram of electromechanical control inputs.

Now, to explain FIG. 1, the illustrated hydraulic device is controlled by the discharge flow rate control device 12. It is equipped with a fluid pump 10 equipped with a discharge flow rate changing mechanism 11 that can be operated. . The discharge flow rate control device 12 is a load consisting of a differential control device indicated by the reference numeral 13 as a whole. Adjust the fluid delivery rate of fluid pump 10 into the response circuit. The differential pressure control device 13 A fluid motor 15 is shown interposed between a body pump 10 and a fluid motor 15 for actuating a load W. The level of the differential pressure generated in the variable orifice 14 is adjusted. Type of fluid pump 10 The equation can be constant volume or variable volume.

If the pump 10 is a constant displacement type, the discharge flow rate control device 12 (known as By-passing a portion of the fluid flow from the pump to the device's aperture 16 in a controlled manner. This allows the fluid to flow into the pump 10 through the discharge changer groove 11 and into the load response circuit. Adjust the discharge amount. If the pump 10 is a variable displacement type, the discharge flow rate is controlled. The control device 12 is a well-known method that changes the flow rate by changing the pump discharge rate. The amount of fluid discharged from the pump 107 to the load response circuit is adjusted via the adjustment mechanism 11. do.

In FIG. 1, the differential pressure control device 13 is separated for the purpose of illustrating the principle of the present invention. However, in actual application, the differential pressure control device 13 is the most common In one embodiment, it is configured integrally with the pump discharge flow rate control device 12 and as a part thereof. cormorant. The discharge flow rate control device 12 includes discharge lines 1T and 18 from the bottle 10. Sho 58-501284 (7) or another fluid energy source, i.e. a pump 19 with a bypass valve 20. It can also supply fluid energy. The discharge line 17 of the pump 12 is a load Check valve 21. to fluid motor 15 via variable orifice 14 and line 22 and is connected via line 23 to a fluid motor 24 which receives a load W□. . The load pressure signal Pw is passed through the line 22 and the signal check valve 25 to the fixed orifice. or variable orifice 26. Similarly, the load pressure of the fluid motor 24 Signal can be fixed or variable via signal check valve 27 and line 28 The signal is transmitted to the upstream side of the orifice 26 and downstream of the signal check valve 25. . Differential pressure control device 13 can be connected to a fixed or variable orifice via line 29. 26 and via a conduit 30 to the discharge flow rate control device 12 of the pump 10. is in contact with.

A differential pressure control device, generally designated 13, is connected to and controlled by hole 35. Introduction chamber 32 for guiding the control spool 36. A housing having a control chamber 33 and a discharge chamber 34 Equipped with Uzing 31. The control spool 36 has a throttle slot 38 and a control spool 36. A land 37 arranged between the main room 33 and the introduction chamber 32, and the introduction chamber 32 and the discharge chamber 3 4 and a flange 40. Control spring 41 controls Interposed in the discharge chamber 34 between the flange 40 of the control spool 36 and the housing 31 are doing. The discharge chamber 34 and the control chamber 33 are guided into the circular hole 42. An i-bend is formed by a sharp orifice formed by a shaft 43 with a slot 44. interconnected. The shaft portion 43 is an actuator 45 that responds to an external control signal 46. It is connected to the.

Now, to explain Fig. 2, the differential pressure side (i [l] device 13 a is 4 A shaft portion 43 having a metering orifice 42 and a metering slot 44 is connected to the fixed orifice 4. It is the same as the differential pressure control device 13 in FIG. 1 except that it is replaced with 2a.

Now, to explain Fig. 6, the same components as those used in Fig. 1 are shown. The minutes are indicated by the same symbols. 1 of the load response control device shown in Figs. The difference in jff, - is from the differential control device 137z and the fluid motors 14 and 24. The discharge M'' of the pump 10 is the phase of the load pressure signal of the flow rate control device 12. In the figure, the load pressure signal from the downstream side of signal check valves 25 and 27 is It is directly transmitted to the discharge flow rate control device 12 via the inlet 47. 10 pumps The discharge pressure signal is sent to the discharge line 11. Load check valve 21, fixed orifice valve or possible It is transmitted to the discharge flow rate control device 12 via the variable orifice 26 and the line 30. , and a differential pressure control device 13 is connected to this signal transmission path.

Now, to explain Figure 4, the components used in Figures 1 and 6 are shown below. The same components as the minutes are indicated by the same symbols in °C. The load response control device in Fig. 4 is the first Similar to the circuit shown in the figure, one differential pressure control device 13 and and a second differential pressure 'i control device 1 connected to the signal transmission circuit 48 similarly to the circuit of FIG. 3 is shown.

Now, to explain Fig. 5, the same constituent parts as shown in Fig. 1 are shown. They are the same and are indicated by symbols.

All of the basic load response circuits and equipment components in FIG. The load response circuit and device components shown in Figure 1, except for the differential pressure control assembly, are the same as those shown in Figure 1. are the same. The differential pressure control assembly 50 of FIG. 4 is similar to the differential pressure control device 13 of FIG. It is incorporated into the circuit.

and perform the same function. Differential pressure control assembly 50 includes two Although shown as being composed of component parts, these two component parts are combined. And it should be integrated into 120 sets of discharge flow rate control devices. differential pressure control assembly The body 50 includes a housing 52, a force introduction chamber 53, a force output chamber 54, and these chambers. a circular hole 55 arranged between and guiding a part 56 with a metering slot 57; A variable orifice valve 51 is provided. )@ section 56 is an external control signal 46 is coupled to an actuator 45 which is responsive to 46 . Differential pressure control assembly 50 A flow control valve 58 with a housing 59 is provided. Housing 59 is hole 6 2 and axially guides a weighing bin 63 with a weighing slot 64 It has one introduction chamber 6o and one discharge chamber 61. Measuring pin 63 is stopper 6 5 and is oriented to the position shown in the figure by a spring 66 housed in the discharge chamber 61. It has been biased in the past.

The introduction chamber 53 of the variable orifice valve 51 is connected to the conduit 28, the signal check valve 25 and Connected to the downstream side of 27.

- the force field outlet chamber is connected by a line 61 to the introduction chamber 60 of the flow control valve 58; Guidance The inlet chamber 6o is then connected to the discharge flow rate control device 12 of the pump 1o through the conduit 3°. ing.

Now, to explain Fig. 6, the same components as those used in Fig. 5 will be explained. The minutes are indicated by the same symbols. The basic load response control device shown in Figure 6 is a variable orifice 14 is replaced and different from a load-responsive directional control valve generally designated 68. The device is similar to that of FIG. 5 except that a differential pressure control valve 68a of the type ing. The directional control valve 68 has an introduction chamber 70 that guides a valve spool 78 and a first load chamber 7. 1. Second load chamber 72. First discharge chamber 73. Second discharge chamber 74, load pressure detection lower 5. 76 and a housing 69 having a hole 77. Valve spool 78 is metered with slots 82, 83, 84 and 85 and signal slots 86 and 87 It has lands 79, 80 and 81 and is actuated by a control lever 88. . The load pressure detection lowers 5 and 76 are connected upstream of the signal check valve 25 by a line 89. connected to the side. Similarly, the load that controls the load W2 through the fluid motor 91 The load pressure detection port of the response direction switching valve 9o is connected to the line upstream of the signal check valve 27. connected to the side. The downstream side of the signal check valves 25 and 27 is connected by a pipe 28. It is connected to an inlet 93 of a differential pressure control valve, generally indicated by the reference numeral 68a. differential pressure control Valve 68a carries a coil 95 and connects a solenoid, generally designated 97. A housing 94 for guiding a pole 96 is provided. The armature 96 is close to the inlet 93. It includes a conical surface 98 that can be selectively engaged with the sealing edge 99 and a relief hole xioo.

The holding spring 101 can be inserted between the armature 96 and the housing 94. . The coil 95 is connected to the outside of the housing 94 in a sealed connector 102. It is. Signals 46 from the outside are transmitted to the sealed connector 102.

The outlet 103 of the differential pressure control valve 68a is connected to the discharge flow rate control device 12 through the line 30. Will you continue? The line 104 is connected to an orifice connected to the reservoir 16. . This orifice can be fixed or variable. If this orif If the system is variable type.

It can be of the type built into the flow rate control valve 58 shown in FIG. Flow control valve 58 The structure of is described in detail with respect to FIG.

6a, the differential pressure control valve 681) engages the sealing edge 99. The constriction part O 98 having a conical surface 98a is connected to the spring 101 instead of the armature 96. It is similar to the differential pressure control valve 68a in FIG. 6, except that the bias is caused by a and n. ing.

Now, to explain Fig. 7, Fig. 1, Fig. 6, Fig. 4, Fig. 5, and Fig. 6 The variable discharge flow rate pump 10 shown in the figure includes a flow rate changing mechanism 11 and a discharge flow rate control device 12. We are prepared. The first pressure control signal is as shown in the control device of FIG. Outline 17 may be fixed orifice or variable orifice 26. Line 29, differential pressure It is transmitted to the discharge flow rate control device 12 via the side@l device 13 and line 30. No. 2 pressure signal 105 is transmitted directly from the maximum load of the device to the discharge flow control device 12. space 106. The discharge flow rate control device 12 is known in this technical field. Yo (as it is known.

Guided into the hole 108 and annular spaces 112, 113 and 114 Equipped with pilot square 107 with land 109, 110 and 111 defining It is growing. The pilot box 107 is a control box stored inside the control space 106. 115. Hole 108 is a drain connected to the device sump. core 116 and a °C exhaust core connected to chamber 118 and via leakage orifice 119. 116 as well as a control core 117 connected thereto. Chamber 118 is a flow rate changing mechanism 11 is actuated, the piston 120 is biased by a spring 121, and the piston 120 is biased by the spring 121. There is. The annular space 112 is connected to the discharge pressure of the pump 19 by a line 122. The flow rate changing mechanism 11 is connected to the reservoir 16 of the device by a line 123. Ru.

Now, to explain FIG. 8, the flow rate changing mechanism 11 and the discharge The basic configuration of the output flow rate control device 12 is the same as that shown in FIG. but However, the discharge flow control device 12 of FIG. 8 is responsive to the differential pressure control signal. space 1 14 is directly connected to the discharge line 17 by line 125 and is connected to the control space. 106 receives a control pressure signal 124. The control pressure signal 124 is on the differential pressure side @device 13 The load pressure signal is changed by

Now, to explain about Figure 9, Figure 9 shows the basic configuration of Figure 8. The fluid energy for controlling the legs and ponzo is the energy supplied by the pump 10. Instead of using a pump, another pump 19 is also supplied to the annular space 112.

Figure 9 shows the pump control system connected to the basic control system shown in Figure 1. There is.

Now, to explain Figure 10, The shaft portion 43 or 56 of the actuator 45 is positioned at the zero orifice by the spring 126. The lever 121 which transmits the external signal 46 is biased when rotated to the position. Act more directly [7].

Now, to explain further, Figure 11, Figure 6, Figure 4, and Figure 5. The shaft part 43 of the actuator 45 (56) is 1#Ij force--is 1゛corpse in 1st movement of Refice, 5th L and piston 1 Katsura 1.　&’〕raohpe). Fluid pressure is applied to the lever 131. Move down 1 L-me ε), f] name) River, blade base, ↑ from W 130 to Pinuto no' 1 2 9 ic 1. ! , m't': 71-6.

To explain, Fig. 1, 6th μm, 4th Figure. Shaft portion 43 of actuator 45 in Figure 5: f + (second 56 is spring 132 by Zero Merifis '07. u’i: II this time C, 1 7Lζ).

The solenoid 133 is connected to the human power current supply device 134 once by a line. The human-powered turtle flow side master device 34 is operated by the lever 135, and the leakage and power supply are removed. 136 is also powered.

Now, to explain FIG. 16, the shaft portion 43 of the differential pressure control device 13 is connected to the spring 137. Therefore, the shaft portion 43 is turned around the cliff and deflected to the extent that it also blocks the introduction chamber 33 and the discharge chamber 34. It is controlled by a leakage O-tsu solenoid 138. Amplifier 139 is further increased. ＠Electronic “A it?lJ # signal receives inputs 141, 142 and 143 The logic circuit, ie, the microprocessor 140, receives one bus.

Now, here are the phrases explaining Figure 14 and the control number 145.146 6J 2hi 14 7 is supplied with the logic circuit, i.e., the microprocessor 144 is supplied with external control. The control signal is transmitted via amplifier 148 to actuation control device 68a.

Now, let's explain about Fig. 1.The flow from fluid pump 10 to fluid motor 15. The flow rate of the fluid sent out is determined by the pressure 1u P□ and P through the flow rate changing fitting groove 11. 2) is adjusted by the discharge flow circuit a1'Mlt12. Mo1~mo pump 10 is of constant displacement type, the discharge flow control device 12 is in good condition (in a known manner, the pump The discharge specific force of the pump 10 is increased by storing 10 fluids in the reservoir 16. There is a constant output difference between P1 and the pressure signal P2 sent to the discharge flow rate control device 12. This is a differential pressure relief valve that maintains the pressure at a high level. If 7 also pump 10 is variable capacity side In the form f'L, the pump 0 discharge flow rate control device 16 changes the discharge amount of the pump 10. By this, the discharge pressure PIY discharge lTL amount of the pump 10 is sent to #iI side 1 clamp 12. This technical field maintains a level higher than the two-force signal P2 by a certain pressure difference. This is a well-known differential pressure compensator.

Therefore, regardless of the characteristics of the pump 10, the load-responsive discharge flow control device 12 is always Between the two inputs, that is, the pressures P2 and Pl, the upper discharge blade of the pump Automatically maintains a constant preselected pressure differential (differential pressure) relative to level fluctuations IJ　IJ-) The load response of either valve type or differential pressure compensator type 9. Discharge flow control devices are well known in the art. Figure 7, Figure 8 and and FIG. 9 will be explained in more detail.

Differential ratio IJ IJ-fusho-maf, B is the conventional load response using a differential pressure sleeve 1jt device In the control system, pressure 1) is always applied to one side of the motor, which receives the maximum load. This is the maximum load pressure Pw that has occurred. Therefore, in a conventional load-responsive controller , the pump discharge flow rate control device 12 always controls Bonzo I! regardless of the magnitude of the pressure Pw. 1 Output pressure I) l and maximum load pressure ■] w Maintaining a constant i = force difference for which song ΔP2 PI-Pw-maintain a constant relationship. Such load-responsive controllers are used to pump equipment. There is a constant pressure difference ΔP between the two ends of the orifice 140, which is placed between the pipe and the fluidization pipe. maintain. When a constant pressure difference is acting across the orifice 14, the orifice 14 The flow rate of the fluid through the orifice 14 is proportional to the area of the orifice, and the light body It is independent of the level of pressure in the motor. Therefore, in 5, the variable orifice 14 By changing the +IJi product, the fluid flow rate and load W to the fluid motor 15 can be changed. The speed can be adjusted and the specific area of each variable meritorium 14 can be adjusted according to the load W. It corresponds to a certain speed of the load W that remains constant regardless of changes in magnitude.

In the mechanism shown in Fig. 1, the relationship between the load pressure Pw and the signal pressure P2 is expressed by the symbol It is controlled by an outflow 1gl control device shown at 13 and an orifice 26. Figure 1 As shown in FIG. The TJ shaft portion 43 completely closes the metering orifice 7 and the control chamber 33 is connected to the discharge chamber 3. Assume that it is isolated from 4. The control spool 36 and its land 37 are connected to the control chamber 33. When entering the control chamber 33 there is a pressure corresponding to the preload of the control spring 41. occurs. When the marking part 43 moves to the right, the weighing slot 40 aligns with the circular hole 42. It moves outward to form an orifice area. control through this orifice area. A fluid flow from the drain chamber 33 to the discharge chamber 34 occurs. ? Ij! I # By spring 41 The biased control spool 36 moves from the right side to the left side and slides into the slot 38. The introduction room 32 and the control room 33 are communicated with each other. The pressure in the control variable 33 is As the control spool 36 rises in proportion to the cross-sectional area of the control spool 36, the introduction chamber 32 Adjustment f where a sufficient flow of pressure fluid to the control chamber 33 is throttled is returned to the upright position for control. The chamber 33 is maintained at one foot pressure corresponding to the preload of the control spring 41. Weighing slot 4 4 relative to the circular hole 4-2, the area of the metering orifice changes. .

A constant pressure is applied between the discharge chamber 34 and the control chamber 33 by the control spool 36. is automatically maintained across the metering slot 44 so that the The specific area of each is related to the magnitude of the pressure in the introduction chamber 32 (or the control chamber 33). A certain constant flow rate is supplied to the discharge chamber 34 and from the introduction chamber 32 to the control chamber 33. Equivalent to bell. Therefore, each load of @to 43 within the area of weighing slot 44 A vertical installation is related to the size of the load 1 = force Pw (the fixed orifice 26 is passed through the corresponds to a certain flow level and therefore a certain pressure drop ΔPx.

Referring to Figure 1, PI Pw = Δpyp1p2 = ΔP is determined by the pump control device. It will be understood that Pw P2 = ΔPx can be obtained by keeping it constant. Is it the above formula? By substituting and eliminating Pl and P2, we get the basic relationship ∆P7 - ∆P - ∆Px. You can get it. ΔPx is changed by the differential pressure control device 13 and is set to an arbitrary level of h. variable orifice 14'? : Δ acting across P, y can be maintained at any desired level. Therefore , responsive to control signal 46 when variable orifice 140 area is any particular head. The pressure difference ΔP, y can be changed from a maximum of 1 shift to zero, and the pressure difference ΔP, y can be changed from a maximum of 1 shift to zero, and the The specific level of is related to the variation of the load pressure Pw (automatically controlled directly to a constant level). Ru. Therefore, for a particular area in the valley of the variable orifice 14, the orifice 14 The pressure differential acting across the orifice 14 and the fluid flow rate through the orifice 14 are differentially controlled. The control device 13 can control the flow from a maximum of 1 to a minimum value, and the flow level in the valley can be controlled. is related to changes in load pressure Pw (automatically controlled immediately by the discharge flow rate control device). be controlled. Basic equation % formula % The flow control device performs conventional load response control using the maximum constant ΔP of the discharge flow rate control device 12. Return to control device operating mode. ΔPx=ΔP, so when ΔP7 becomes zero, tree.

The pump discharge pressure P1 becomes equal to the load pressure Pw, and the Loe variable orifice 14 The flow rate of fluid through becomes zero. When Δpx is larger than ΔP, the pump discharge The output pressure P1 becomes smaller than the load pressure Pw, so the load check valve 21 closes. sit down

In the load response control device shown in FIG. For each particular shift of ΔP7 kept constant by the device 13, the oJ variable orifice The area of each surface can be changed depending on the change in the load pressure Pw. corresponds to a specific flow rate of fluid entering the fluid motor regardless of the Conversely, variable 1 act across the orifice 14 for each specific area of the orifice 14 The pressure difference ΔP7 is changed by the differential pressure control device 13 via the discharge flow rate control device 12. and each specific pressure difference ΔP7 is independent of the change in the magnitude of the load pressure Pw. (corresponds to the specific flow rate of fluid entering the fluid motor 15. Therefore, the fluid motor The fluid flow to the tank 15 can be controlled by changing the area of the variable orifice 14 or by changing the pressure difference Δpy. With every modification, KviVilj can be controlled and the valleys of these control methods indicates the same control customization and control flow rate that is independent of the magnitude of the load pressure.

By combining one control action with another one can e.g. The command signal from the operator is sent to the differential pressure control device 13 (produced by rjlL) using the It is unique in that it can be used as a reference to the signal 46 of the computer used. A device is obtained.

In the explanation in Part 1, if the device pump responds to the load pressure of the fluid motor 15, I assumed. As is well known in this technical field, #, body motor 15 and The load specific force inertia signal from through the system and only the maximum load pressure is transmitted to the system controller. Let's go. Higher load when both fluid motors 15 and 24 are controlled simultaneously Only the fluid motor that controls the proportional control accepts a fluid flow of 1t.

Now, to explain FIG. It is similar to the differential pressure control device 13 in FIG. The actuator 45 shown in Fig. The movable variable metering orifice replaces the fixed metering orifice 42a. ing. However, the pressure adjustment part of both control devices is the same. Differential pressure in Figure 2 The control device 13a completes a constant ΔPx across the fixed orifice 26 and responds to the load. reducing the control pressure differential of the response device by exactly the same amount. Load response control device in Figure 2 is relatively thick in the discharge flow control device (the controlled pressure difference is at a low level) It is very useful to reduce the On the other hand, the response of the discharge flow rate control device is not adversely affected.

Next, referring to FIG. 3, the differential pressure control device 13 is the differential pressure control device 13 of FIG. and the control signal transmitted to the discharge flow control device 12 of the pump 10. By changing it, it functions in exactly the same manner.

However, the differential pressure control device 13 in FIG. 6 operates as shown in the device in FIG. Load pressure J? Instead of changing the control signal of w, the pump discharge pressure P is 1Vil. l　# Change the signal. In Fig. 6, the control load pressure signal Pw is 15 and 2.1. Logical system and line of signal check valves 25 and 27 It is directly transmitted to the discharge flow rate control device 12 via the channel 47. after that.

As understood from Figure 2, PI Pw - Δpy, pl - p2 = Δpx and P2 - Pw = ΔP, and ΔP is kept constant by pump control as described above. dripping From the above formula.

To erase Pl and P2, J:! Basics of llΔP7-ΔP→ΔPx The relationship between them will deepen. Δpx can be varied and kept constant at any level. The ΔPy temperature acting across the variable orifice 14 can be changed and adjusted to any desired level. can be kept constant. Considering the basic formula ΔP7−ΔP+ΔPx, ΔP If x=Q, then ΔP, y−ΔP, and the pressure of the discharge flow rate control device 12 is Return to conventional load-responsive controller operating mode with a minimum constant ΔP equal to the difference . Any axis of ΔPx different from zero acts across variable metering orifice 14. The pressure difference ΔF7 is larger than the level of the constant pressure difference ΔP of the discharge flow rate control device 12 ( increase Therefore, the load-responsive controller of FIG. The load response control device shown in FIG. Higher than a certain pressure difference ΔP level (controlling.

Now, to explain Fig. 4, the load response control device in section 1 and Fig. 6 is assembled. combined into a single device. One differential pressure control device 13 is controlled from outside. When the other differential pressure control device 1 is not activated in response to the control signal 49, 3 responds to the external load signal 46 by changing the load pressure signal. The load response control device shown in the figure operates in the same manner as described above to generate a control pressure difference ΔPy. The level of ΔP is changed from the maximum level of ΔP to zero. Conversely, if the differential pressure control device 13 When the other differential pressure is disabled in response to a control signal 46 from the The control device 13 changes the pump discharge pressure signal so that the control signal from the outside is controlled. 49, the load response control device of FIG. 3 operates and controls as described above. the level of the pressure difference Δpy from the minimum level of ΔP to any desired higher level. Change to file. Therefore, the combined load-responsive controller of FIG. py can be controlled from zero to any desired maximum of one shift.

Now, to explain FIG. 5, the load response control device and the differential pressure control device 50 are constructed. It is constructed in a manner very similar to the delivery control device 13 of FIG. 1, although it is different in construction. This is the same as the load responsive control device of FIG. Differential pressure control device 50 The main components, namely the variable orifice valve 51 and the flow control valve 58, are (Are these valves 51 and 58 shown separately in each example?) The meter is assembled together and located inside the discharge flow control device 12. is preferable. The flow rate control valve 58 of the differential pressure control device 50 guides the measuring bottle 63. ・Uzonda 59 is ready. The measuring bottle 63 is subjected to population pressure in the introduction chamber 60. , and also receives the pressure of the reservoir in the discharge chamber 61 and receives the biasing force of the spring 66 . introduction In response to the pressure in chamber 60, metering bottle 63 moves from left to right, measuring each specific pressure. The force level corresponds to a particular position of the metering bottle 63 relative to the housing 59, and the force level 66 responds to the biasing force of the load droplet.

The specific position of each metering bottle 63 relative to the housing 59 is determined by the introduction chamber 60 and the discharge chamber. 61 and corresponding to the specific flow area of the metering slot 64 that communicates with the metering slot. Weighing scale The shape of the lot 64 and the characteristics of the deflection spring 66 are responsive to the pressure in the introduction chamber 60. Depending on the change in the effective area of the orifice of the metering slot 64, the introduction chamber 60 may also be the discharge chamber. The 61 cycles are selected to provide a constant fluid flow rate during the comparison cycles. negative The shape of the metering slot 64 is introduced in order to obtain a special control customization of the load response control device. Any desired relationship between the flow from chamber 60 and its pressure level can be obtained. You can choose to

The flow rate control valve 58 maintains a constant flow rate in the introduction chamber 60 regardless of the pressure level in the introduction chamber 60. Assume that In this case, the flow control valve 58 is As is well known in the research field, it is possible to replace conventional flow control valves. Wear. A constant flow of fluid into the introduction chamber 60 is signaled by the fluid motor 15 or 24. Check box 21 and 25 logic system, variable orifice box 51 and line 67. The variable orifice square 51 on the upper side of the flow control valve 58 is A circular hole 55 is provided guiding a detail 56 with a metering slot 57. Round The displacement of the metering slot 57 beyond the hole 55 forms an orifice, which The effective area of the rift is controlled by an actuator 45 responsive to an external control signal 46. This can be changed by positioning the shaft portion 56 according to the method. Hole 5 with circular detail 56 5, the flow path area of the variable orifice cell 51 becomes a gap. that Therefore, the effective flow area of the variable orifice valve 51 is responsive to the external control signal 46. can be changed from zero to the selected maximum value. Variable orifice f valve 5 Since the flow rate of fluid through one tube is kept constant by the flow rate control valve 58, it is possible to The specific flow area of each valve 51 (in known manner, the load pressure p The variation of w and f corresponds to a specific pressure drop ΔPx without a groove. Therefore, the load pressure signal The number can be changed on the way to the discharge flow rate control device &12, and the differential pressure control device 50 The output drop ∆Px is kept constant by ∆P, y - ∆P - ∆Px. According to the basic equation, it corresponds to a certain value of the pressure difference Δpy. Therefore, in Figure 5 Load response control device ff111 #Special order is the load response control described in Figure 1 The device is identical and the pressure difference ΔPy is equal to ΔP from the outside between the maximum value and zero. are varied by the differential pressure controller 50 in response to the control signal 46 of the respective characteristics. be held constant at a certain level.

In the manner described above, the shape of the metering slot 64 and the biasing force 2 of the spring 66 There is an arbitrary difference between the pressure in the inlet chamber 60 and the flow rate of fluid through the variable orifice valve 51. can be selected to obtain the desired relationship. better exemplify For this purpose, the variable orifice valve 51 of FIG. 5 replaces the fixed orifice 42a of FIG. replaced by In this case, the fixed orifice 42a due to the increase in load pressure Due to the controlled increase in the flow rate of fluid through, the pressure difference ΔPx increases proportionally increases and therefore the pressure difference Δpy decreases proportionally.

Effectively reduces the gain of the load responsive controller as the load pressure increases. vice versa, The flow rate of fluid through the fixed orifice 42a is controlled by increasing the load pressure. The pressure difference ΔPx decreases proportionally in °C due to the decrease in pressure difference ΔI)y increases proportionally, and as the load pressure increases, the gain effect of the load-responsive control device increases. increase effectively. Good (as it is known, most fluent) in this technical field The stability margin of fluid flow and pressure control devices decreases with increasing device pressure. Ru. Therefore, the ability to adjust the gain of the controller with respect to the system pressure is of paramount importance. be. Due to the flow control valve 58, the rate of change of the pressure difference Δl)y with respect to the load pressure is constant. It is not necessary to keep it constant; it can be changed in any desired manner.

To explain Figure 6, the load 1 core response damping device in Figure 6 is the variable one in Figure 5. Orifice 14 is replaced by a load-responsive four-way valve, generally designated 68 in FIG. 5 except that a different type of differential pressure control valve 68a is used. Similar to a load responsive controller. Differential pressure control device 13 in Figure 1 or difference in Figure 5 The differential pressure control valve 68a, which can be replaced with the pressure control device 50, is the load of the west square 68. It is connected to pressure detection ports 15 and 16. Valve spool as shown in Figure 6 When 78 is in its neutral position, load pressure detection lower 5 and 76 are connected to land 8o. more closed and therefore shielded from the load pressure force residing within the load chamber 11 or 72. It has been cut off. Under such conditions, it is well known that the discharge flow rate is controlled in the 7t muni mode. The control device 12 is the maximum where the discharge pressure of the pump 1o\load BC is equal to ∆PK of the control device. Automatically maintain at small level. Move the masu spool 78 from its neutral position. - When displaced in one direction, the signal slot 86 or 87 first causes the load chamber 11 or or 72 are communicated by the load pressure detection lower 5 or 76.

The load chambers 71 and 72 are connected to the spool 78, the introduction chamber 70fi, and the first discharge chamber. 73 and the second discharge chamber 14 is still 5vfr. variable orifice When the valve 51 opens, the load pressure signal is transmitted to the discharge flow control device 12 and the metering orifice is Before the fluid opening to the fluid motor 15, the discharge flow control device 12f;! 0: Made Make it possible to move. If the masu spool 18 is further displaced in either direction, the In a known manner, the metering slot 83 or Km connects the load chambers 11 and 72 via 84. A metering orifice is formed between one side and the introduction chamber 70, and the other load chamber 71 or 7) is connected to the sump of the device through the weighing slot) 83t. Contact one of the exit rooms 13 and 14. This metering orifice is valve block 0-1. The displacement of 8 can be changed υ, and each position is independent of the size of load W1. Corresponds to a particular flow rate level of fluid entering fluid motor 15.

In addition to this control, control of differential pressure control valve 68a is performed in the manner described above with respect to FIG. It is possible to use a working platform. The whole is indicated by the symbol 68a, and one differential pressure control valve is Its body is designated by the code 97 and contains heninlenoid. Solenoid 97 is the housing 1 coil added to 94! 115 and guided to slide into the coil. It consists of an armature 96. The armature 96 cooperates with the sealing edge 99 to close the inlet. A conical surface 98 is provided to adjust the pressure difference ΔPx between the outlet port 93 and the outlet port 103. Ru. A coil 95 is placed between the armature 96 and the housing 94 in a demagnetized state. In order to make it possible to generate a backflow from the outlet 10.3 to the inlet 93, A relatively weak spring 101 can also be used. This feature is shown in the 6th diagram. Important when using the VC7 valve logic system instead of the valve logic/stem It may be. In Howsong 94, which is well-researched in this technical field, The connected connector 102 connects the coil 95 to an external terminal, and connects the coil 95 to an external terminal. An external signal 46' can be transmitted to. The solenoid is an electrical input signal. It is an electromechanical device that applies the principle of electromagnetism to generate output from a machine. . The power generated in the solenoid's solenoid 96 is a function of the input current. to coil 95 When the undercurrent flows t'L, each particular current level is transmitted to the armature 96. corresponds to the level of power of

Therefore, between the conical surface 98 of the armature 96 and the sealed edge 99 of the housing 94 The contact force is variable and controlled by human power current. This structure differs between certain models. It corresponds to a pressure throttle valve, and the pressure difference ΔPx between the inlet port 93 and the outlet port 103 is controlled by the kidney. The force generated in the armature 96 against the area surrounded by the sealing edge 99 is Therefore, the input current is supplied to the solenoid 97, and the input current is applied to the external signal 46. Automatically change proportionately. ...acts on the armature 96 inside the Uzong 94 The force due to pressure l is due to the pressure difference ΔPx acting on the area surrounded by the sealing edge 99 They are perfectly balanced except for the force due to the pressure exerted on them. Figure 7, Figure 8 O, L and 9 The discharge flow rate control device 12, which will be explained in more detail in the figures, is a two-way moving pilot. The valve is stored (-), so the discharge flow rate control device 12 also flows out and flows into the line 30. The incoming fluid flow is routed through line 104 and metering orifice to sump 16. nru. The flow rate of fluid through the fixed merit is good (in a known manner with respect to load pressure). The control response changes rapidly at low load pressures and requires a slow control response at high load pressures. This results in high energy losses in power. Therefore, the most likely type of line 1 The orinois in 04 automatically delivers fluid at a preselectable flow rate. This becomes the flow control valve 58 described in detail. This preselectable flow rate controls the discharge flow rate. The desired gain of the device 12 is determined by forceps 1iJ as a function of the load pressure or It can be independent of pressure. Figure 6 Check valve glue/Shirttle When using a valve logic system, line 104 and flow control valve 58 are connected to one another. It's unnecessary. First, to simplify the illustration of the operating principle of the differential pressure control valve 68a, the armature Child 96 is shown hydraulically unbalanced. Escape passage 1oo is 9 ( It can be connected directly to the inlet 93 through the cone of the conical surface 98 in a known manner. and the lower end of the relief passage 1oo has a diameter smaller than the diameter of the inlet 93. It is enlarged so that it slides into engagement with the new pin. In this way, the pressure difference is The effective area of the solenoid 97 can be significantly reduced, making it possible to reduce the size of the solenoid . Such a configuration is shown by the dotted line at armature 9 in Figure 6, and is The numbers are not marked.

In the valve, the pool 78 can be placed at any particular location corresponding to any particular area of the metering orifice. When the load W is displaced to the position, the load W is proportionally controlled by the action of the differential pressure control valve 68a. The saliva in the valley of the pressure difference Δpy is kept at a constant level υ by the discharge flow rate control device 12. The fluid flowing into the motor 15 is maintained automatically and regardless of the magnitude of the load Wl. corresponds to a specific flow level of the fluid. The load W2 is controlled by the direction control valve 90. It will be done. The structure of the directional control valve 90 can be the same as the structure of the directional control valve 68. .

Now, to explain FIG. 6A, the differential pressure control device, generally designated by the reference numeral 68b, is It has a similar function to the differential pressure control valve 68a, but in a well-known manner, the inlet 93 A certain pressure difference can be generated between the outlet port 103 and the outlet port 103. This pressure difference is It is proportional to the preload of spring 101a-. The control ΔP of the device is reduced by this pressure difference. Shimero 几 produces a much smaller lateral leg pressure difference ΔPy. The device in Figure 6A The relatively large control pressure difference of the output flow controller 12 is reduced to a lower level. It is very useful for increasing the efficiency of the discharge flow rate control device 12. Sponsor is not affected.

Now, to explain Fig. 7, it shows a load responsive flow rate control device for a pump. . If the pump 10 is a constant displacement type, the flow rate changing mechanism 11 is This is a differential pressure IJ valve well known in the technical field. Moshi Pump If 10 is of the variable displacement type, the flow rate changing mechanism 11 is of the type in this technical field. (This is a known differential pressure compensator. The pilot valve 107 is on one side. and the biasing force of the control spring 115 as well as the load pressure signal 105 and the other side. The pump discharge pressure signal is received at the pump discharge pressure signal. The pump discharge pressure signal is shown in Figure 7. It can be changed by the differential pressure control device 13. This is the pilot valve 107 The modulation position is reached in a well-known manner by the action of forces.

In this modulation position, the pilot valve 107 controls the position of the piston 120; Adjust the discharge pressure in the discharge line 17 to match the pressure in the space 114 and the control space. maintain a constant pressure difference between the pressure inside the base 106 and the pressure inside the base 106. This constant pressure difference The preload of the control spring 115 is determined by the preload of the control spring 115, and this preload is applied to the pilot valve 107. is equal to the quotient divided by the cross-sectional area of Pilot valve 107 controls flow rate changing mechanism 11 When doing so, the energy supplied by the pump 19 is used.

Now, to explain Fig. 8, there is fluid in the space 14 as well as in the discharge line 17. while the flow rate changing mechanism 11 changes the energy supplied from the pump 10. I am using it. In conventional control of load response control 'i11 devices, the pressure signal 1 24 are supplied directly from the equipment load, and the n control spaces 94 are also supplied with a small amount of fluid. It is designed to leak sound. In the load response control device of the present invention, the load pressure The force signal is modified by the differential pressure controller 13 and becomes a pressure signal 124.

Now, to explain Fig. 9, the pump load response control device in Fig. 9 is shown in Fig. 8. Same pump controller as shown, but using energy supplied from pump 19. I am using it. Figure 9 shows a pump control device connected to the basic equipment shown in Figure 1. 7 is shown. The differential pressure control device n13 is connected to the space 106 and is 1. In this way, the control signal is changed to connect the pump 10 and the load. Change the effective pressure difference that occurs at the refice. Figures 1 and 6 to 5 As mentioned above, differential pressure control device #13 controls the discharge flow rate shown in the schematic diagram of the pump. It is shown in the Muni state (7), which is separately connected to the control device, as shown in Figure 9. The components of the differential pressure control device 13 are integrated with the discharge flow rate control device of the pump 10. That will be the part.

Now, to explain Figure 10, The shaft portion 43 of the actuator 45 has a zero orifice due to the 1 piece 56 and 2126 pieces. The lever 127 can be rotated to the position and operated directly by the lever 127. It will be done. Lever 127 provides an external signal 46 in the form of manual actuation.

Now, to explain Fig. 11, the apertures in Figs. The shaft portion 43 or 56 of the actuator 45 is positioned at the zero orifice by the spring 128. The piston 129 is biased when rotated to the position and actuated directly by the piston 129. . Fluid pressure is high (pressure generation actuated by known m-c lever 131) The raw material 13 of J' is supplied to the piston 129. Therefore, the design in Figure 11 The position generates an external signal 46 in the form of a fluid pressure signal.

Now, to explain Fig. 12, the apertures in Figs. The shaft portion 43 or 56 of the actuator 45 is located at the zero orifice position of n132. biased towards the is activated.

The solenoid 133 is connected to the input diverter 1Vtljf111 device 134 by a line. has been done. The incoming current control device 134 is actuated by a lever 135 and its The power source 136 also receives power. Therefore, the device of FIG. An external signal 46 in the form of a current proportional to the displacement of 23 is generated.

Now, to explain FIG. 16, the shaft portion 43 of the differential pressure control device 13 is connected to the spring 137. This causes the shaft portion to turn and bias the introduction chamber 33 to a position that also blocks the discharge chamber 34. It is being The shaft part 43 is completely resistant to pressure and has a very small stroke. It can be activated through the flow, and the effect of the sword is negligible. Controls the flow rate as low as 10 J) at low pressure. Anyway, if the weighing slot The area of the cut 44 gives a linear function to the displacement of the shaft portion 43 and is located in front of the orifice. If the pressure is chosen so that it remains constant, the force of the flow will also be linear, The force of the spring is then increased to slightly change the combined displacement rate of the spring. Cap part 4 3 is directly connected to the solenoid 138. Solenoid from electrical input signal It is an electromechanical device that applies the principles of electromagnetism to produce an output. solenoid The position of the armature of the terminal is a function of the input terminal when biased by the spring.

When a current is passed through the coil.

The resulting magnetic force moves the armature from the demagnetized position to the energized position do. When biased by a spring, the solenoid for each particular current level There is a correspondingly fixed specific position that the nod reaches. Current from zero to maximum rating When varied, the armature is Moves in one direction in a predictable manner from a fully retracted position to a fully extended position. move. The force generated by solenoid 126 is so small that logic The input current controlled by microprocessor 128 is also small. next , microprocessor 128 responds to different types of transducers to calculate speed, force, and Depending on the position, the load on the device can be applied directly or its action can be controlled by the operator. In addition to its functions, the maximum power and power within the maximum capacity of the structure of the machine are also within the limits of its horsepower. The required operation can be performed with a minimum amount of energy within a short period of time.

Now, referring to FIG. 14, the logic circuit or microprocessor 144 The spider control signal is connected to amplifier 148 in a manner similar to that described with respect to FIG. directly to the differential pressure control valve 68a. Differential pressure side H valve 63a is a solenoid The pressure difference is created in response to the input current in the manner described above through the combination of adjust.

Although the preferred embodiment of the present invention has been illustrated and described in detail above, the present invention is not as illustrated. The present invention is not limited to the precise shape and structure described and is understood by those skilled in the art. The present invention, with various modifications and variations as claimed, came to mind when I understood it. It will be understood that this may be done without departing from the scope of the Act.

Ftc, 3 F/64 Special clothing (Sho 58-50128405) F/Cr5 F no G9 36 Submission of translation of written amendment (1.'1 Act, Article 184-7, Paragraph 1) 1982X+: 4 month 79th Commissioner of the Patent Office 1. Display of patent application: paT/us31101121, title of invention: Load response flow body control device 3. Patent applicant Address (residence) United States of America 44022 Ono X Io (=+-1.

Moreland Hills, Moorwood Drive 0 Name (Name): Budozuitsuhi, Tadeusuzu 4, Agent Address: 33 Yumishin Otemachi Hilding, 2-1 Otemachi-chome, Chiyoda-ku, Tokyo 100 1 5. Submission date of Supplementary IL: 7727/72, Claims (1) Discharge flow rate control [1 device (1'2), fluid motor receiving load pressure ( 15) and a pump (10) having a discharge device (16); and a control orifice device (14, 83, 84), a valve device (107) and a device (120, 121); The pressure differential acting across the position (107) is maintained at a predetermined level and the control to maintain a constant pressure difference across the control orifice temporary locations (14, 83, 84). @The first control device (107, 115) that can be operated via the 1st control device (12) and the pressure difference across the @valve device (107) is kept constant at the predetermined level. The controlled orifice installation (14, 133, 84) The first system 1111 is configured to change the level of the constant pressure difference. 7.115) a second control surface (13, 50, 68a) operable through the A fluid control device characterized by:

(2) In the fluid control device according to claim 1, the control orifice device characterized in that the position (14, 83, 84) has a variable area orifice device. Fluid control device.

(3) In the fluid control device according to claim 1, the control orifice device A station (14, 83, 84) connects the fluid sweater (15) to the pump (10) and a directional control valve system actuated to selectively connect to said evacuation device (16); 1. A fluid control device comprising: a station (68).

(4) In the fluid control device according to claim 1, the second control device ( 13) is the constant pressure reducing device (36°41) and the above constant pressure reducing device (36, 41). The orifice device (26) on the flow side and the lower A [of the constant pressure reduction device (36, 41)] a flow orifice device (44).

(5) In the fluid control device according to claim 1, the second control device (5) 0) is a constant flow control device (58) connected to the discharge device (16); It is equipped with an oJ variable control orifice device (51) on the ball flow side of the quantity control device (58). A fluid control device characterized by:

(6) In the fluid control device according to claim 4, the second control device in AU (68a) is connected to the fluid restriction device (95, 96) and the discharge device (16). and a flow rate control device (58) downstream of the fluid restriction device (95, 96). A fluid control device characterized by:

(7) In the fluid control device according to claim 1, the second control device (1 3) the constant pressure difference acting across the control orifice device (14) The level of the school is kept constant at the predetermined level (107) (22, 26, A fluid control device characterized in that it has a diameter of 29,30°1)).

(8) In the fluid control device according to claim 1, the second control @ device (1 3) acts across the control orifice device (14)', -: ■Note-1 The valve device (10) keeps the level of the constant pressure difference constant at a predetermined level. 7)'a: for changing the saliva higher than the level of said pressure difference acting across A stream characterized by having a device (17, 21, 26, 29, 30, 12) Body control device.

(9) In the fluid control device according to claim 1, the valve device (107) is a first control chamber (114) receiving pressure upstream of the control orifice device (14). ) and can be changed by the second control device (13, 50, 68a). a second control chamber (10) receiving pressure downstream of the control orifice device (14); 6) A fluid control device capable of communicating with.

(10) In the fluid control device according to claim 1, the 9F device (10 7) is the control orientation changed by the second control device (13, 50, 68a). It can communicate with the first control room (114) which receives the pressure on the upstream side of the fiss device (14). a second control chamber ( 136).

1.11) In the fluid control device according to claim 1, the second control device (13,5[1,68a) is a device (45,1 02) A fluid control device comprising:

Claims (1)

[Claims] (1,) A pump (10) having a discharge flow control device (12) and a pump (10) that receives a load pressure. and a fluid motor (15). A control mechanism interposed between the pump (10) and the fluid motor (15) a control orifice device (14) and a pressure acting across said control orifice device (14)'aj. and a control device (101, 115, 13) for the discharge flow rate control device (12) that operates to maintain the force difference at a predetermined level, and the control device operates to maintain the pressure difference at a predetermined level. 1. The level of said pressure difference is maintained constant at two levels. A load-responsive fluid control device characterized in that it comprises a device (13) operable to change the flow rate. (2) A pump (10) having a discharge flow rate control device (12) and a pump (10) having a discharge flow rate control device (12) and a and a fluid motor (15). a control orifice device (14) interposed between the pump (10) and the fluid motor (15) and a valve device (1o7) for maintaining a constant pressure difference across the valve at a predetermined level; ) to maintain a constant pressure difference across the A first control device (107, 115) that connects a valve device (107) and a device (115) that can be actuated via t7 via a recording tOB flow rate control device (12) and a valve device (107) intersect. said control while the pressure difference remains constant at said predetermined level. Controlled pressure differential level variation across the controlled orifice device (14) a second control device (13) which operates via said first control device (107, 115) to further increase said load responsive fluid control device. (3) The load-responsive fluid control device according to claim 1, characterized in that the discharge flow rate control device (12) of @Kibonno (10) includes a bypass flow rate control device (20). load-responsive fluid control device. (4) In the load responsive fluid control device according to claim 1, the discharge flow rate control device (12) of the pump (10) includes a discharge flow rate changing device (11). A load-responsive fluid control device with special features. (5) a pump (10) having a discharge flow rate control device (12) and an outlet (11); a fluid motor (15) receiving load pressure; and the outlet (17) of the pump (10) and the fluid motor. (15) interposed between a control orifice device (14) and a device for transmitting a first pressure signal from the outlet (17) of said pump; A control having a device (30) for transmitting a second pressure signal from the load pressure; a signal transmitting device (18, 30); the first pressure signal and the second pressure signal to maintain a constant pressure difference across the control orifice device (14). a control device (101, 115) for the discharge flow rate control device (12) of the pump (10), which has a hinge valve device (107) that operates to change the discharge flow rate Z of the pump (10); The pressure difference acting across the valve arrangement (107) while the control orifice device (14) is kept constant at a predetermined level. and a control signal changing device (13) of said control signal transmitting device (30) which is operative to change the level of said constant pressure difference. A load-responsive fluid control device with characteristics. (6) In the load responsive fluid control device according to claim 5, the control A special feature of the load-responsive fluid control device is that the orifice device (14) comprises a variable area orifice device (83, 84). (7) In the load responsive fluid side'@ device according to claim 5, the discharge flow rate control device (12) of the pump (10) is provided with a bypass flow rate control device (20). The load-responsive fluid side O! 4 devices. (8) The load-responsive fluid control device according to claim 5, characterized in that the discharge flow rate control device (12) of the pump (10) includes a pump discharge rate changing device (11). Load-responsive fluid control temporary location. (9) In the load-responsive fluid control device according to claim 5, the control signal changing device (13 in FIG. 3) modifying the first pressure signal to increase the controlled pressure across the control orifice device; the level of force difference acting across the valve arrangement (107); A load response control device, characterized in that it has a temporary position (36, 26, 44) operable to change the load response to a value higher than the load response level. 10. A load-responsive fluid control device according to claim 9, wherein the first device (36, 26, 44) operable to modify the pressure signal is a constant pressure reduction device (36); A load-responsive fluid control system comprising: an orifice device (26) upstream of the constant pressure reduction device (36); and a flow orifice device (44) downstream of the constant pressure reduction device (36). Place. 0υ In the load-responsive fluid-side device according to claim 9, said temporary position (50) operable to change said first pressure signal is connected to a flow orifice device (51) and said flow orifice table. The flow control device (58) downstream of the installation (51) and the A load-responsive fluid-side device characterized by: u2, the load responsive fluid control device according to claim 9, in which the pump said suspension (50) having a device (45) responsive to an external force control signal (46) operable to modify said first pressure signal from said pressure outlet (17); A load-responsive fluid control device characterized by: 03) In the load responsive fluid control i11 device according to claim 5, the control A control signal changing device (13 in Figure 1) changes the second pressure signal from the load pressure (30). the level of said controlled pressure differential across said control orifice device (14) is changed to a value lower than said constant pressure differential level acting across said valve device (107); It has a hanging device (36, 26° 44) that operates on A load-responsive fluid control device characterized by: 0 leakage The load responsive fluid control device according to claim 16, wherein the second pressure Said device (36, 26, 44) operable to change the force signal is a constant pressure reduction device. an orifice device (26) upstream of said constant pressure reduction temporary placement (36); and a flow orifice device (44) downstream of said constant pressure reduction device (36). Load response fluid side 49 position. 15. The load responsive fluid control system of claim 16, wherein the device (50) is operable to modify the second pressure signal and includes a flow orifice device (51) and a flow orifice device (51). A load-responsive fluid control device characterized by comprising: (51) a downstream flow rate control ll] calibration (58); 06) a load-responsive fluid control device according to claim 16; , the load pressure load-responsive fluid, characterized in that said device (50) operative to modify said second pressure signal from a force comprises a device (45) responsive to an external control signal (46); Control device. (17) In the load responsive fluid control device according to claim 5, the control signal a device (13 in Figure 6) operable to change the first pressure signal from the pump outlet (17); 1. A load-responsive fluid control device, characterized in that it has a device (13 in FIG. 1) that can be operated to change the load. (1- A pump (10) having a discharge flow rate control device (12) and an outlet (17), a fluid motor (15) receiving load pressure, a temporary discharge station (16), and the outlet of the pump (10) (17) and a directional control valve (68) interposed between the fluid motor (15) and the discharge device (16), and the directional control valve (68) is connected to the fluid motor (15). a control orifice device (83, 84) selectively interconnected to the pump (10) and the evacuation device (16) and between the outlet (17) of the pump (10) and the motor (15); ) of said pump (10) to maintain a pressure differential across said control orifice arrangement (83, 84) at a controlled constant level. A first control side 1 device (107, 115) that operates via the discharge flow rate side # device (12) and a front and a second control device (68a) operable to change the constant pressure difference sound (19+) Load responsive fluid according to claim 18. In the control device, the control device A load responsive fluid control device characterized in that the control orifice device (83, 84) comprises a variable area orifice device (83, 84, 80). (20) In the load responsive fluid control device according to claim 18, the pump The discharge flow rate control device (12) of the pump (10) is equipped with a bypass flow rate control device (20)! A load-responsive fluid control device with characteristics. Qυ In the load-responsive fluid control device according to claim 18, it is a % characteristic that the mJ discharge flow rate control device (12) of the pump (10) is provided with a discharge flow rate changing device (11). Load responsive fluid control device. (2',!J A pump (10) having a discharge flow rate control device (12) and an outlet (17), a fluid motor (15) receiving load pressure, a discharge device (16), a front a directional control valve (68) interposed between the outlet (17) of the pump (10), the fluid motor 5) and the discharge device (16); ) is operative to provide a control orifice arrangement between the outlet (17) of the pump (10) and the fluid motor (15) before the fluid motor (15). a first valve arrangement (78) for selectively interconnecting the pump (10) and the evacuation device (16); A constant load pressure detection port device (75, 76) formed in the directional control valve (68) that can selectively communicate with the pump outlet (15) and a a control signal transmission device (18, 30) having a device (18) for transmitting a first pressure signal and a device (30) for transmitting a second pressure signal from the load pressure detection port device (75, 76); ), in communication with said first pressure signal and said second pressure signal and for altering the output flow rate of said pump (10) to traverse a second valve arrangement (107). said pump (10) having a second valve arrangement (107) operable to maintain a constant pressure differential at a predetermined level and to maintain a constant pressure differential across said control orifice device (83, 84); A control device (107, 115) of the discharge flow rate control device (12). the pressure difference acting across the second valve arrangement (107) is at the predetermined level; A control signal is operated to vary the level of the controlled constant pressure differential across the control orifice device (83, 84) while the control orifice device (83, 84) is maintained at -. A control signal changing device (68a) for a signal transmission device (30). (2. In the load response control device according to claim 22, the first valve device (18) has a neutral position where the load pressure detection port device (15, 76) is closed. When the 1-valve device (78) is displaced from the neutral position, it first connects the load pressure detection port device (75° 76) to the 1iiJ bonzo (1) before connecting the pump (10) to the fluid motor (15). 10) A load-responsive fluid control device, characterized in that it is connected to the control device (101, 115) of the discharge flow rate control device (12).1,!,a Load response according to claim 22 A load-responsive fluid control device, characterized in that it comprises the control orifice device (83, 84) or the variable area orifice device (83, 84, 80). In the load responsive fluid control device according to item 22, the port A load-responsive fluid control device, characterized in that the discharge flow control device (12) of the pump (10) comprises a bypass flow control device (20). 001 In the load responsive fluid control φ2 position according to claim 22, the range A load-responsive fluid control device comprising the discharge flow rate control device (12) or the discharge rate changing device (11) of the pop-up (10). CD In the load-responsive fluid control device according to claim 22, 51'\i the controlling side 1 signal changing device (13 in Fig. 6) changes the control side 1 signal changing device (13 in Fig. 6) 1 change the pressure signal across the control valve arrangement (14); and apply the level of the controlled power differential across the second valve arrangement (107). A load-responsive fluid control device characterized in that it comprises a hinge device (36, 26, 44) operative to change the level of said constant pressure difference to a value higher than said level. (2) In the load responsive fluid control device according to claim 27, the first pressure Said device (36, 26, 44) operable to modify the force signal is a constant pressure reducing device. an orifice arrangement (26) upstream of the constant pressure reduction device (36); and a flow orifice device (44) downstream of the constant pressure reduction device (36). (29) In the load responsive fluid control device according to claim 28, the orifice device (26) on the -upstream side of the constant pressure reducing device (36) has an orifice area adjuster. A load-responsive fluid control device, characterized in that it has a knot device (68a, 68b). (30) A load-responsive fluid control device according to claim 28, characterized in that the flow orifice 'J [(83,84) comprises a variable area orifice device (83,84,80). A load-responsive fluid control device. Gυ In the load responsive fluid control device according to claim 27, the first pressure Said device (50) operable to modify the force signal comprises a flow orifice device (51) and a pressure responsive flow control device (58) downstream of said flow orifice device (51). A load-responsive fluid control device characterized by: 62. The load responsive fluid control device according to claim 61, wherein the flow orientation is Note that the orifice Hft (5i) has a variable area orifice device (57). A load-responsive fluid control device with characteristics. (c) In the load-responsive fluid control device according to claim 27, the device (50, 13) that operates to change the first pressure signal from the pump outlet receives an external control signal. A load-responsive fluid control device comprising: a device (45) responsive to (46). (2) In the load-responsive fluid control device according to claim 66, the device (45) that responds to an external control signal (46) includes a device (127) operated by mechanical force. A load-responsive fluid control device characterized by: (13!51 In the load responsive fluid control device according to claim 36, said device responsive to a control signal (46) from the unit! t (45) is actuated by fluid pressure. A load-responsive fluid control device comprising a device (130°131). (Support) F. In the load-responsive fluid control device according to claim 66, the external Load response wave system #device, characterized in that said device (45) responsive to a control signal (46) from said device comprises an electrically-hydraulic actuated device (133). 6η In the load responsive fluid control device according to claim 66, the external D. 11J device (45) responsive to the control signal (46) of the device operated by electromechanical power. A load-responsive fluid control device characterized by comprising a device (140, 138, 43). Place. (To) In the load responsive fluid control device according to claim 22, A number changing device (13 in FIG. 1) modifies the second pressure signal from the load detection port device (75, 76) to traverse the controlled orifice device (83, 84). a suspension device operable to vary the level of the controlled pressure differential directly below the level of the constant pressure differential acting across the second valve arrangement (107); A load-responsive fluid control device comprising: (36, 26, 44). (3) In the load-responsive fluid control device (36, 26, 44) according to claim 68, the second a flow orifice device (16) downstream of the constant pressure reduction device (36); and a flow orifice device (44) downstream of the constant pressure reduction device (36). A load response wave system #device characterized by: t4t) In the load-responsive fluid control device according to claim 69, the orifice device (26) on the upstream side of the constant pressure reduction device (36) comprises an orifice area adjustment device (51)'f. A load response wave regime #device characterized by: (4υ In the load responsive fluid control device according to claim 69, the orifice device (44) includes a variable area orifice device (44, 43). (42) A load-responsive fluid control system according to claim 68 [alpha] in which the device ft (50) is operable to modify the second pressure signal and is connected to a flow orifice system. A load-responsive fluid control device comprising a pressure-responsive flow control device (58) downstream of the flow orifice device (51). +4.1 In the load responsive fluid control device according to claim 42, the flow A load responsive fluid control device characterized in that the orifice Hit (51) comprises a variable area orifice device (57, 45). (44) In the load responsive fluid control device according to claim 68, the negative The second pressure signal from the load detection port device (75, 76) is operative to change the pressure signal. A load-responsive fluid control device, characterized in that said device (50, 13) comprising a device (45) responsive to an external D-control signal (46). (45) The load-responsive fluid control device according to claim 44, wherein the device (45) responsive to an external control signal (46) includes a device (127) operated by mechanical force. A load-responsive fluid control device characterized by: (46) A load-responsive fluid control device according to claim 44, wherein the device (45) responsive to an external control signal (46) comprises a device (13o, 131) operated by fluid pressure. A load-responsive fluid control device characterized by: (4) A load-responsive fluid control device according to claim 44, wherein the device (45) responsive to an external control signal (46) comprises an electro-hydraulic actuated device (133). (48) In the load responsive fluid control device according to claim 44, the device (45) responsive to an external control signal (46) is electrically A load-responsive fluid control device, characterized in that it comprises a mechanically actuated device (140, 138, 43). 149) A load-responsive fluid control device according to claim 22, in which the control A control signal changing device (13 in FIGS. 1 and 6) operates to change the first pressure signal at the pump outlet (1711, etc.) and a control signal changing device (13 in FIG. 6) operates to change the first pressure signal at the pump outlet (1711, etc.); a device (13 in Figure 1) operable to modify said second pressure signal from a pressure sensing device (15, 76). ) a fluid pump (10) having a flow control device (12) and an outlet (17), a plurality of fluid motors (15, 91) receiving load pressure; A plurality of directional control valves (68, 9(1)) interposed between the discharge device (16) and each of the fluid motors (15, 91), Directional control valve (68, 90) (one side of the motor (15, 91) is selectively interconnected to the pump (10) and the discharge device (16) to connect the pump (1o) and one of said fluid motors (15, 91). The first valve device (78) further includes a first valve device (78) for controlling mJ original fluid mode. a load pressure detection port device (75, 76) formed on each of the directional control valves (68, 90) selectively communicating with one side of the directional control valve (68, 90); a control signal phasing device (25, 27) connected to said load pressure sensing device (75, 76) and operative to transmit the highest load pressure signal to the control pressure region (28); a control signal comprising: a device (30) for transmitting a first pressure signal from said pumping force; and a device (3o) for transmitting a second pressure signal from said control pressure region (28). a transmission device (18, 30), the first pressure signal and the second pressure; a second valve system capable of communicating with the force signal and changing the discharge flow rate of said pump (10); Said control of the directional control valve (68 or 90) which maintains at a predetermined level a relatively constant pressure differential acting across the position (107) and the orifice device (83, 84) thereby receiving the most tube load pressure. ) will operate to maintain a constant pressure difference across the a control device (107, 115) for a discharge current control device (12) of the pump (1 o) having a second valve device (107); (, 107) of the directional control valve (6th to 1st is 90) which receives the highest load pressure while the pressure difference iJ is held constant at the specified level Control orifice device (83, 84)' (<transversely controlled front a control signal changing device (13, 50) of the control signal transmitting device (18, 30) operative to change the level of the constant pressure difference. Device. (5υ In the load responsive fluid control device according to claim 50, the pump The discharge flow rate control device (12) of the pump (10) controls the bypass flow rate m! A load-responsive fluid control device comprising an I control device (20). (52) In the load-responsive fluid control device according to claim 50, the discharge current current control device (12) of the pump (10) is a pump discharge flow rate changing device (il)'fz! : A load-responsive fluid control device characterized by comprising: (53) A load-responsive fluid control device according to claim 50 JJl. Then, the control signal changing device (13 in FIG. 6) changes the first pressure signal at the pump outlet (17) a. The level of the pressure difference 'a: @the second valve device (i07) has a device (36, 43) operable to change the level of the pressure difference to a value higher than the level of the constant pressure difference acting across Y. A load responsive fluid control device characterized by: 54) In the load response control device according to claim 50, the control signal changing device (13 in FIG. 1) changes the second pressure signal in the control pressure region (28) a. The level of the controlled pressure difference of tMI across the controlled orifice device (83, 84) of mJ is changed to the second: l'f device 107)=! A load-responsive driftwood control device characterized in that it has a load-responsive driftwood control device (36, 43) operative to directly change the pressure difference below the level of a constant pressure difference of MiI acting across it. Place. (5) In the load-responsive fluid control device according to claim 50, the signal change device (13 in FIG. 6) changes the first pressure signal of the pump output (17) 711. The device (36, 43) that operates in such a manner that the control pressure region A load-responsive fluid control system characterized in that it comprises a device (13 of FIG. 1) operable to modify said second pressure signal from a region (28).