JPH0448969B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Applicability] The present invention is a control device for a hydraulically driven load, in which, on the inflow side, the load is connected from a hydraulic oil source, such as a pump, to a supply pipe, to a pressure compensation Hydraulic oil is supplied through the valve, connection piping, inflow side valve of the control valve device, and inflow side load piping, and the outflow side load piping,
The control valve device can be connected to the reservoir via the outflow side valve and the return pipe, and the control device has a signal pipe, and the signal pipe has a first branch pipe connected to the inflow side load pipe; and a second branch pipe connected to the return pipe and equipped with a throttle, for sending out a signal pressure, the signal pressure being in phase with the spring and in reverse phase with the compensation pressure derived from the connection pipe. , acting on the pressure compensating valve, the hydraulic oil source being in particular dependent on the signal pressure.

BACKGROUND OF THE INVENTION A control device of this type is known from German Patent Application No. 2514624. The load pressure derived from the load line via the signal line controls the pressure compensation valve in such a way that the same pressure drop preset by the spring of the pressure compensation valve is always present at the inlet valve. This means that an amount of hydraulic oil is supplied to the load that depends on the opening degree of the inlet valve and does not depend on whether the load pressure changes. A prerequisite for this is that a sufficiently high pressure always exists at the inlet of the pressure compensation valve. This is achieved either by constantly pumping in a corresponding excess amount of hydraulic fluid or by adjusting the pumping amount as a function of the load. For that purpose, the corresponding regulating device should be controlled either by a signal pressure or, if there are several loads operated in parallel order, by a signal pressure characteristic of the highest load. I can do it.

According to this control device, the load can be driven to a considerable extent independently of the load and the feed amount. The movement to be monitored is therefore protected against disturbances. Of course, this movement
Even the control form called "load sensing" often has a long response time due to its complexity. This occurs, for example, when lifting a load using a crane and the load value increases rapidly from zero to a certain predetermined magnitude.

[Purpose of the invention]

The present invention is a control device for a hydraulically driven load, in which the load, on the inflow side, has a hydraulic source,
For example, from the pump, supply piping, pressure compensation valve,
Hydraulic oil is supplied through the connection piping, the inflow side valve of the control valve device, and the inflow side load piping, and it can be connected to the reservoir through the outflow side load piping, the outflow side valve of the control valve device, and the return piping. and
The signal pipe further includes a first branch pipe connected to the inflow side load pipe, and a second branch pipe connected to the return pipe and equipped with a throttle, and sends out signal pressure. and the signal pressure acts on the pressure compensation valve in phase with the spring and in reverse phase with the compensation pressure derived from the connection pipe, and the hydraulic oil source is a regulating device dependent on the signal pressure. The object of the present invention is to provide a control device for a hydraulically driven load that can rapidly stabilize the operation to be controlled. be.

[Structure and operation of the invention]

Such an object of the present invention is that the signal pipe is connected to a third
In order to form a pressure distribution device that is connected to the connecting pipe via a branch pipe and includes the first branch pipe, the second branch pipe, and the third branch pipe, the first branch pipe, the This is achieved by providing a throttle in each of the second branch pipe and the third branch pipe.

According to this configuration, the signal pressure is not equal to the load pressure, but is a combination of the load pressure portion and the compensation pressure portion. Therefore, when the load oscillates, the flow rate no longer remains constant, but decreases as the load increases and increases as the load decreases. Since this has a buffering effect on the system, a stable state is quickly reached.

It is desirable to be able to set at least a certain portion of the aperture. In this way, the load pressure dependence and the compensation pressure dependence can be changed significantly, so that the best adaptation to each particular case is achieved.
It is most desirable to obtain rapid stabilization with as little load dependence as possible. At least a portion of the aperture may be shut off or omitted if desired.

According to a preferred embodiment of the invention, the throttle in the third branch pipe can be displaced together with the inlet and outlet valves, but in opposition to them with respect to the throttle function. Therefore, the signal pressure increases as the opening degree of the inflow side valve and the outflow side valve increases. Therefore, in the region of large throughflows, the signal pressure increases, the dependence on the compensation pressure becomes stronger, and in the case of relatively rapid movements of the load, a relatively strong damping effect occurs, as desired.

It is also desirable to provide a check valve in the first branch pipe that opens toward the inflow side load pipe. In that case, even if the load pressure exceeds the compensation pressure due to insufficient supply of hydraulic oil, the signal This prevents hydraulic oil from flowing out from the load into the reservoir (tank) due to excessive pressure.

The control device consists of a double-acting control valve device (the load piping is alternately connected to the inflow side and the outflow side by this control valve device) and a signal piping (the load piping is alternately connected to the inflow side and the outflow side by the control valve device). in accordance with German Patent Publication No. 25 14 624), for at least one direction of action of the load. It is advantageous to have two complete pressure distribution systems, of which at least a third branch line can be shut off from the control valve system in the other direction of operation. In this case, the current target damping control is applied to the load that can be driven in both directions. In that case, a normal load sensing control takes place in each other direction of action, and likewise a damping control according to the invention.

This damping control can be carried out, by way of example, by having two complete pressure distribution devices and having all three distribution lines of each of these distribution devices alternately able to be shut off from the control valve arrangement. All branch pipes are closed off from their associated pipes when not in use, so that the two pressure distribution devices can be adjusted completely independently of each other.

In a control device equipped with one pressure compensation valve common to both operating directions, a second branch pipe is provided in common to the two pressure distribution devices, and only the first and third branch pipes of these pressure distribution devices are controlled. It may also be possible to alternately shut off the valve device. In this case, a leakage oil flow through the second branch line occurs continuously, thus also in the neutral position. The structure is greatly simplified by eliminating the need for one second branch pipe and both closing members.

The control valve device has an axial spool with a plurality of lands cooperating with a plurality of annular grooves in a bore, the bore having a central annular groove connected to the connecting pipe; the axial spool has one load pipe connector juxtaposed on both sides thereof, one return annular groove, and one signal annular groove connected to the signal pipe; It has a central land, one return land juxtaposed on both sides of the central land, a signal land, and a boundary land,
Two passages extend through the axial spool, each passage communicating a groove between the center land and the return land with a groove between the signal land and the boundary land. , any one of these grooves
First, the construction becomes even simpler starting from the control device according to FIG. 2 of German Patent Publication No. 2514624, in which when the axial spool is displaced from its neutral position, it communicates with the adjacent signal annular groove. . In particular, both channels have a first restriction and the return land has a cross-sectional shape that tapers towards the adjacent signal land so as to form a third restriction in each case. You can do it like this. This allows the main part of the pressure distribution device to be contained inside the existing axial spool.

According to a further advantageous embodiment of the invention, the inner bore has on both sides outside the signal annular groove a switching annular groove which is connected to the connecting line via a third branch line in each case; The spool has a terminal land on each side outwardly of the boundary land, and each passageway has a communication section between the boundary land and the terminal land to a groove between the boundary land and the terminal land, and the groove has a terminal land on each side of the boundary land. The switching annular groove is communicated with the switching annular groove when the switching groove is displaced from the switching annular groove. In this case, extra switching means are arranged at both ends of the axial spool for connecting the second branch line for the respective direction of action to the signal line.

According to a further advantageous embodiment of the invention, the flow channel has an extension extending to the central land with a third restriction, and the inflow hole of the extension extends to the outer circumference of the land. In the neutral position, the central part is contained within the width of the annular groove in the central part. According to this configuration, all parts of the pressure distribution device are arranged within the confines of the axial spool.

In addition, a spring-loaded check valve that opens in the flow direction of the relevant restriction may be provided in the shunt of either or both of the restriction of the first branch pipe and the restriction of the third branch pipe. is desirable.

This check valve limits the pressure drop that occurs across the associated throttle and thus the characteristic variable that determines the output or efficiency of the load connected to the control device.
Due to the check valve in the first branch pipe, the flow rate to the input of the load does not exceed a certain maximum value. Due to the check valve in the third branch pipe, the pressure at the input of the load does not exceed a certain maximum value. These two limitations are achieved with a relatively small valve.

It is particularly desirable that the spring loading the check valve be adjustable. In that case, each of the above maximum values is
It can be set according to the operating conditions at the time. Since separate first and third branch pipes are normally used for both directions of action, it is also possible to set the maximum values for both directions of action to different values.

Next, preferred embodiments of the present invention will be described with reference to the drawings.

〔Example〕

In the simplified hydraulic circuit diagram of FIG. 1, hydraulic oil from a hydraulic oil source 3 is supplied to a load 1 of the hydraulic circuit via a control device 2. As shown in FIG. Hydraulic oil source 3
is equipped with a flow rate regulating device 4 for controlling the amount of oil to be pumped. As an example, a variable displacement or variable volume pump or a constant displacement or constant volume pump with an adjustable outflow valve is used. The control device 2 has a pressure regulating valve 5 and a control valve device 6, and the control valve device 6 has at least an inflow side valve 7 and a discharge side valve 8, and these valves 7, 8
can be simultaneously and commonly adjusted from the outside.

The pressure regulating valve 5 and the control device 6 may have an axial spool or a rotating spool or may be of any other type.

Hydraulic oil is supplied from the hydraulic oil source 3 to the inflow chamber 13 of the load 1 via an inflow pipe 9, a pressure regulating valve 5, a connection pipe 11 equipped with a check valve 10, an inflow side valve 7, and an inflow side load pipe 12. reach. The outflow chamber 14 includes an outflow side load pipe 15, an outflow side valve 8, and a return pipe 1.
6 and is connected to a reservoir 17.

The signal pipe 18 is connected to the inflow side load pipe 12 via the first branch pipe 19, to the connection pipe 11 via the second branch pipe 20, and further to the return pipe 16 via the third branch pipe 21. There is. These three branch pipes 19, 20, 21 each have one
The first aperture 2 has two apertures.
2. They are called a second diaphragm 23 and a third diaphragm 24. The second diaphragm 23 is manually adjusted, and the third diaphragm 24
can be adjusted together with the inflow side valve 7 and the outflow side valve 8, but the throttle function can be adjusted in the opposite phase to these. A check valve 25 that opens toward the inflow side load pipe 12 is disposed in the first branch pipe 19 .

The throttles 22, 23, and 24 form a pressure distribution device 26, and this pressure distribution device 26 connects the load pressure P _B in the inflow side load pipe 12 and the connection pipe 11.
Signal pressure representing a mixing function with compensation pressure P _K in
It is used to establish P _S in the signal pipe 18. This signal pressure P _S is led to the control input 27 of the pressure regulating valve 5, where it is in phase with the spring 28.
However, the compensation pressure supplied via the control input 29
It acts in the opposite phase to P _K. That is, the compensation pressure P _K is
It is greater than the signal pressure P _S by a certain value predetermined by the spring 28 . The signal pressure P _S is also supplied to the control input 30 of the flow regulating device 4 so that more hydraulic oil is supplied when the demand increases.

The control device 2 actually consists of two modules, one of which is a pressure regulating valve 5.
, the other module 32 has a control valve arrangement 6 , and both modules 31 , 32 have associated parts of the signal line 18 . module 31,
32 is connected between the supply section 33 and the load section 34.

A check valve 35 loaded by an adjustable spring 36 is arranged in the branch of the throttle 22 in the first branch line 19 . A check valve 37 loaded by an adjustable spring 38 is arranged in the branch of the throttle 24 in the third branch line 21 . Two check valves 35,3
7 is in the flow direction of each throttle 22, 24,
That is, the signal pipe 18 is opened toward the inflow side load pipe 12 and the return pipe 16.

The hydraulic circuit schematically shown in FIG.
is adapted to the upward direction of motion. This upward movement is induced in a conventional manner, for example as shown in FIGS. 8-11.

In the following description of the operation, it is assumed that the control device is equipped with an axial spool as shown in FIGS. 8-11. In Figures 2 to 4, the moving distance x of the axial spool is plotted on the horizontal axis, the pressure P is plotted in the upper diagram, and the flow rate Q of hydraulic oil per unit time is plotted in the lower diagram on the vertical axis. These diagrams correspond to movements in a certain direction from the neutral position. A certain dead stroke a is required before the valve opens, and after this dead stroke the opening cross-sectional area of the valve increases linearly with the travel distance.

In FIG. 2, the extreme case in which the throttles 23, 24 are completely closed is considered. This corresponds to normal load sensing operation. Signal pressure P _S is equal to load pressure P _B. The compensation pressure P _k is greater than this by a certain predetermined value. Therefore, a low compensation pressure P _K1 occurs at a relatively low load pressure P _B1 , and a high compensation pressure P _K2 occurs at a relatively high load pressure P _B2 .
The magnitude of these pressures remains constant over the entire moving distance x. This means that the flow rate Q ₁ at low load is exactly equal to the flow rate Q ₂ at high load.

FIG. 3 shows another extreme case in which the diaphragm 22 is fully closed. In this case, the signal pressure P _S is
It is a fractional value of the compensation pressure P _K determined by the resistance of 3 and 24 at each moment. As the opening of the valve increases,
Correspondingly, the compensation pressure and therefore the signal pressure P _S increases. Flow rate for relatively low load pressure P _B1
The respective characteristic curves of Q ₁ and flow rate Q ₂ for a relatively high load pressure P _B2 rise very steeply and are considerably separated from each other. The respective characteristic curves for intermediate load pressures are characteristic curves Q ₁ ,
The curve is intermediate between Q ₂ and has a similar trend to these. This means that the change in flow rate when the load pressure changes becomes very large.

FIG. 4 shows a mixture of these two extremes, where three apertures 22, 23, 24
are all open. As can be seen from this figure, the curve of the signal pressure P _S at least at relatively low load pressures P _B1 and, for a moderate range of travel distances, also at relatively high load pressures P _B2
Although not exactly, it is approximately horizontal. These flow rates Q ₁ , Q ₂ still show an extensive non-feed rate dependence according to FIG. 2, but to a certain extent a load dependence.

FIG. 5 shows the dynamic behavior with respect to the transition of the transient state after redrawing FIG. 2 on the time axis. That is, in FIG. 5, the compensation pressure P _K and the load pressure P _B are plotted against time.
Due to complete load independence, the flow rate (proportional like arrow q) is a constant value. This provides no buffering effect.

FIG. 6 is also a diagram obtained by similarly redrawing FIG. 3. A very sharp buffering occurs. As shown in FIG. 3, bottom, flow control is virtually no longer possible.

By combining the two effects as in FIG. 4, the diagram in FIG. 7 is obtained. As can be seen, the magnitude of the arrow q decreases as the pressure load increases and increases as the pressure load decreases, thus creating an available damping effect. At the same time, control that is almost independent of the feeding amount becomes possible over the entire moving distance range.

When the pressure drop across the throttle 22 exceeds the pressure preset by the spring 36, the check valve 35 is opened. Therefore, a certain upper limit exists for the pressure drop. The signal pressure P _S can only be greater than the load pressure P _B by this pressure drop. compensation pressure
P _K is maintained at a value larger than this signal pressure P _S by a value corresponding to the spring 28 . Even if the inlet valve 7 attempts to open further, the maximum flow rate set value will not be exceeded because of the pressure compensation valve 5.

The check valve 37 is opened when the pressure drop across the throttle 24 exceeds a value set by the spring 38. Therefore, the signal pressure P _S is larger than the reservoir pressure by this pressure drop. The compensation pressure P _K is greater than the signal pressure P _S by a value set by the spring 28 . Since this pressure value is fixed, the load pressure P _B cannot exceed a certain upper limit value.

FIG. 8 shows an embodiment of a double-acting control valve device. In FIG. 8, the reference numerals used in FIG. 1 plus 100 are used.
The control valve arrangement has an axial spool 135 which is displaceable in a bore 136 by a displacement device 137 (shown schematically) in either direction from the neutral position shown. The displacement device 137 can be actuated electrically, by voltage, hydraulically, or by any other method. Inner hole 136
has an annular groove 138 in the center, and the connecting pipe 111 is connected to this annular groove. Connectors to the load pipes 112, 115 are provided on both sides thereof, and two return annular grooves 1 are provided on both outer sides thereof.
39 and 140 are formed, respectively, and these annular grooves 139 and 140 are connected to the return pipe 116. Furthermore, there are signal annular grooves 141 and 142 on both sides of the outer side, and these annular grooves 14
1 and 142 are connected to each other by a pipe 143 and also to a signal pipe 118. Furthermore, switching annular grooves 144 and 145 are formed on the outside thereof. The axial spool 135 is provided with a land 146 in the center for closing the annular groove 138 in the center in both directions at a neutral position. On both sides, there is one return land 147, 14.
8, and these lands connect the return grooves 139, 140 to the adjacent load pipes 11 in the neutral position.
2,115 towards the deadline, in the direction of both opposite sides,
By having a tapered cross-section, e.g. one or more inclined axial grooves, the third aperture 124,1
24'. On both sides of the outer side there are signal lands 149, 150 which, in the neutral position, close off the signal annular grooves 141, 142 towards both sides of the bore 136. Furthermore, following that, Boundary Land 151, 15
2 and terminal lands 153 and 154. The axial spool 135 has two channels 119 and 11.
9' are formed, and these channels form two first branch pipes. First channel 119
The groove 155 between the center land 146 and the return land 147, the groove 156 between the signal land 149 and the boundary land 151, and the boundary land 151
and the groove 157 between the terminal land 153 and the terminal land 153 . A first restrictor 12 is provided in the first portion of the flow path 119.
2 and a check valve 125. Similarly, the second flow path 1
19' connects the grooves 158, 159, and 160.

When the axial spool 135 moves to the right from the illustrated neutral position, the grooves 156, 157 communicate with the signal annular groove 141 or with the switching annular groove 144. This means that not only the first branch pipe 119 but also the second branch pipe 120 are connected to the signal pipe 118. Since the annular groove 121' between the return land 147 and the signal land 149 is separated from the signal annular groove 141, the annular groove 121 with the aperture 124
Only the third branch pipe is connected to the signal pipe 118 as a third branch pipe. When moving in the opposite direction, the previously active apertures 122, 123, 124 are separated and the three apertures 122', 123', 124'
becomes the active state.

In the embodiment shown in FIG. 9, the reference numerals used in FIGS. 1 and 2 plus 200 and 100, respectively, are used. The main difference with the embodiment of FIG.
20 and an extension part 220' of the flow path 219', and these extension parts have inlet holes 261, 261' on the outer periphery of the central land 246,
These inlet holes are located in such a way that, in the neutral position, they are still included in the width area of the central annular groove 238. Therefore, upon displacement from the neutral position, the extension portion 22
Any one of 0,220' has no effect.
In this way, all elements of the two pressure distribution devices can reside inside the axial spool 235. An outer switching annular groove controlled from the switching land is therefore unnecessary.

In the embodiment shown in FIG. 10, reference numerals starting with 300 are used. In this embodiment, the second branch pipe 320 common to both pressure distribution devices is
It is always disposed between the connection pipe 300 and the signal pipe 318. The structure of the spool is correspondingly simplified.

In the embodiment of FIG. 11, reference numerals starting at 400 are used. In this embodiment, for one control direction, ie, for leftward movement of the axial spool 435, the three throttles 422', 42
Only one pressure distribution device with 3', 424' is used. This corresponds to one part of the arrangement according to FIG. For control to the other side, a throttle 422 is simply provided, and a connection in the sense of the second and third branch piping is omitted. Therefore, in this control device, only load sensing control is performed.

If the throttle (for example throttle 22) is to have a fixed value, it is only necessary to select the internal cross-sectional area of branch pipe 19 accordingly. As an example, in FIG. 8, the cross-sectional area of channel 119 or channel 119' can be selected such that a sufficiently large throttling resistance exists. Therefore, there is no need to prepare a special set of apertures.

Instead of the illustrated axial spool, a rotating spool may be used as the control valve arrangement. 3rd aperture 2
4 does not need to be formed on the land of the axial spool, but may be formed on the inner hole. Also, instead of that,
A separate throttle valve connected to the axial spool may also be used.

[Brief explanation of the drawing]

FIG. 1 is a schematic circuit diagram of the control device according to the invention for a certain direction of movement of the load, and FIG. 2 is a diagram showing the movement distance X of the control valve device when the second and third branch pipes are closed. Figure 3 is a diagram showing pressure P and flow rate Q plotted separately, and Figure 4 is a diagram similar to Figure 2 when the first branch pipe is closed.
The figure is a diagram similar to Figure 2 when restricting all three branch pipes, and Figure 5 is the same diagram as Figure 2.
Figure 6 is a diagram similar to Figure 5 shown in the settings of Figure 3; 5, FIG. 8, FIG. 9, FIG. 10, and FIG. 11 are longitudinal sectional views showing the first to fourth embodiments of the double-acting control valve device, respectively. It is. Explanation of symbols, 1...Load, 2...Control device,
3...Hydraulic oil source, 5...Pressure compensation valve, 6...Control valve device, 7...Inflow side valve, 8...Outflow side valve, 9...
...Supply piping, 11...Connection piping, 12...Inflow side load piping, 15...Outflow side load piping, 16...
... Return pipe, 18 ... Signal pipe, 19 ... First branch pipe, 20 ... Second branch pipe, 21 ... Third branch pipe, 22, 23, 24 ... Throttle, 26 ... Pressure distribution device.

Claims (1)

[Scope of Claims] 1. A control device for a hydraulically driven load, in which the load, on the inflow side, is connected from a hydraulic source, such as a pump, to a supply pipe, a pressure compensation valve, a connecting pipe, and a control valve device. Hydraulic oil is supplied through the inflow side valve and inflow side load piping, and can be connected to the reservoir via the outflow side load piping, the outflow side valve of the control valve device, and return piping, and furthermore, the signal piping. The signal pipe has a first branch pipe connected to the inflow side load pipe, and a second branch pipe connected to the return pipe and equipped with a throttle, and sends out a signal pressure, and the signal pipe Pressure acts on the pressure compensating valve in phase with the spring and in phase with the compensating pressure derived from the connecting pipe, and the hydraulic oil source is a hydraulic fluid equipped with a regulating device dependent on the signal pressure. In the control device for a driven load, the signal pipe is connected to the connection pipe via a third branch pipe, and the first branch pipe, the second branch pipe, and the third branch pipe For a hydraulically driven load, wherein a throttle is disposed in each of the first branch pipe, the second branch pipe, and the third branch pipe to form a pressure distribution device including: control device. 2. Control device for a hydraulically driven load according to claim 1, characterized in that at least part of the throttle is adjustable. 3. Claim 1, characterized in that the throttle in the second branch pipe is configured to be movable together with the inflow side valve and the outflow side valve so that the throttle action is in the opposite phase to these. term or second
A control device for a hydraulically driven load according to paragraphs. 4. According to any one of claims 1 to 3, the first branch pipe has a check valve that is opened toward the inflow side load pipe. Control device for hydraulically driven loads. 5 A control device for a hydraulically driven load, in which the load is connected, on the inflow side, from a hydraulic source, for example, a pump, to a supply pipe, a pressure compensation valve, a connecting pipe, an inflow side valve of a control valve device, and an inflow side. Hydraulic oil is supplied through the load piping, and it can be connected to the reservoir via the outflow side load piping, the outflow side valve of the control valve device, and the return piping, and further has a signal piping, so that the signal The piping includes a first branch pipe connected to the inflow side load pipe and a second branch pipe connected to the return pipe and equipped with a restriction, and sends out a signal pressure, and the signal pressure is in phase with the spring. and for a hydraulically driven load having a regulating device acting on the pressure compensating valve and in reverse phase with the compensating pressure derived from the connecting pipe, the hydraulic oil source being dependent on the signal pressure. The control device includes a pressure distribution system in which the signal pipe is connected to the connection pipe via a third branch pipe, and includes the first branch pipe, the second branch pipe, and the third branch pipe. In order to form a device, a throttle is disposed in each of the first branch pipe, the second branch pipe, and the third branch pipe, and the control valve device is arranged in the inflow side load pipe and the outflow side load pipe. Piping can be connected alternately to an inflow side and an outflow side, and the signal piping can be alternately closed off by the control valve device via the first branch pipe,
A control device for a hydraulically driven load connected to said inlet load piping and said outlet load piping, respectively, wherein said pressure distribution device includes a complete pressure distribution means, in at least one direction of action of the load. Control for a hydraulically driven load is provided, characterized in that at least the second branch of the pressure distribution device can be shut off by the control valve arrangement in the other direction of action of the load. Device. 6. Control device for a hydraulically driven load according to claim 5, characterized in that at least part of the throttle is adjustable. 7. Claim 5, characterized in that the throttle in the second branch pipe is configured to be movable together with the inflow side valve and the outflow side valve so that the throttle action is in the opposite phase to these. Section or 6th
A control device for a hydraulically driven load according to paragraphs. 8. According to any one of claims 5 to 7, the first branch pipe has a check valve that opens toward the inflow side load pipe. Control device for hydraulically driven loads. 9 said pressure distribution device comprises two complete pressure distribution means, a first branch pipe of each said complete pressure distribution means;
Hydraulically driven according to any one of claims 5 to 8, characterized in that the second branch pipe and the third branch pipe can be alternately closed off by the control valve device. Control device for loading. 10 the pressure compensating valve is common to both directions of action of the load, the pressure distribution device comprising two pressure distribution means with a common third branch pipe, the first A hydraulically driven load according to any one of claims 5 to 8, characterized in that the branch pipe and the second branch pipe can be alternately closed off by the control valve device. Control device for. 11 A control device for a hydraulically driven load, in which the load is connected, on the inflow side, from a hydraulic source, for example, a pump, to a supply pipe, a pressure compensation valve, a connecting pipe, an inflow side valve of a control valve device, and an inflow side Hydraulic oil is supplied through the load piping, and it can be connected to the reservoir via the outflow side load piping, the outflow side valve of the control valve device, and the return piping, and further has a signal piping, so that the signal The piping includes a first branch pipe connected to the inflow side load pipe and a second branch pipe connected to the return pipe and equipped with a restriction, and sends out a signal pressure, and the signal pressure is in phase with the spring. and for a hydraulically driven load having a regulating device acting on the pressure compensating valve and in reverse phase with the compensating pressure derived from the connecting pipe, the hydraulic oil source being dependent on the signal pressure. The control device includes a pressure distribution system in which the signal pipe is connected to the connection pipe via a third branch pipe, and includes the first branch pipe, the second branch pipe, and the third branch pipe. In order to form a device, a throttle is disposed in each of the first branch pipe, the second branch pipe, and the third branch pipe, and the control valve device is arranged in the inflow side load pipe and the outflow side load pipe. Piping can be connected alternately to an inflow side and an outflow side, and the signal piping can be alternately closed off by the control valve device via the first branch pipe,
each of which is connected to the inlet load pipe and the outlet load pipe, the pressure distribution device comprising two complete pressure distribution means and provided for at least one direction of action of the load; At least a second branch pipe of the pressure distribution device is configured such that it can be shut off by the control valve arrangement in the other direction of action of the load, and a first branch pipe, a second branch pipe of each of the complete pressure distribution means. and a third branch pipe configured to be alternately closed off by the control valve device, the control valve device comprising a plurality of lands cooperating with a plurality of annular grooves of one bore. each one comprising an axial spool, the inner hole being juxtaposed with a central annular groove connected to the connecting pipe on both sides thereof;
one load pipe connection, one return annular groove each, and one each signal annular groove connected to the signal pipe, the axial spool being juxtaposed with a central land on both sides thereof; one return land each, a signal land and a boundary land, and including two channels, each channel defining a groove between the central land and the return land;
grooves between the signal land and the boundary land, each one of the grooves being in communication with the adjacent signal annular groove when the axial spool is displaced from a neutral position; In a control device for a hydraulically driven load configured,
Each of the two flow paths is provided with a first restriction, and the return land is tapered in cross section towards an adjacent signal land so as to form a respective second restriction. A control device for a hydraulically driven load, characterized by comprising: 12 A control device for a hydraulically driven load, in which the load is connected, on the inflow side, from a hydraulic source, for example, a pump, to a supply pipe, a pressure compensation valve, a connecting pipe, an inflow side valve of a control valve device, and an inflow side. Hydraulic oil is supplied through the load piping, and it can be connected to the reservoir via the outflow side load piping, the outflow side valve of the control valve device, and the return piping, and further has a signal piping, so that the signal The piping includes a first branch pipe connected to the inflow side load pipe and a second branch pipe connected to the return pipe and equipped with a restriction, and sends out a signal pressure, and the signal pressure is in phase with the spring. and for a hydraulically driven load having a regulating device acting on the pressure compensating valve and in reverse phase with the compensating pressure derived from the connecting pipe, the hydraulic oil source being dependent on the signal pressure. The control device includes a pressure distribution system in which the signal pipe is connected to the connection pipe via a third branch pipe, and includes the first branch pipe, the second branch pipe, and the third branch pipe. In order to form a device, a throttle is disposed in each of the first branch pipe, the second branch pipe, and the third branch pipe, and the control valve device is arranged in the inflow side load pipe and the outflow side load pipe. Piping can be connected alternately to an inflow side and an outflow side, and the signal piping can be alternately closed off by the control valve device via the first branch pipe,
are connected to the inflow side load piping and the outflow side load piping, respectively, the pressure distribution device includes two pressure distribution means, and is provided with respect to at least one acting direction of the load,
at least a second branch pipe of the pressure distribution device is configured such that it can be shut off by the control valve device in the other direction of action of the load;
said pressure compensating valve is common to both directions of action of said load, said pressure distribution device comprising two pressure distribution means with a common third branch pipe, said first branch of each pressure distribution means The pipe and the second branch pipe are
The control valve arrangement is configured to be alternately closed off by the control valve arrangement, the control valve arrangement comprising an axial spool with a plurality of lands cooperating with a plurality of annular grooves of a bore; Each inner hole has an annular groove in the center connected to the connecting pipe, one load pipe connection part juxtaposed on both sides thereof, one return annular groove each, and one each connected to the signal pipe.
the axial spool comprises a central land, one return land juxtaposed on both sides thereof, a signal land and a boundary land, and includes two flow passages; Each of the channels connects a groove between the center land and the return land to a groove between the signal land and the boundary land, one of the grooves each connecting the groove in the axial direction. In a control device for a hydraulically driven load configured to communicate with the adjacent signal annular groove when the spool is displaced from a neutral position, each of the two flow paths has one first Hydraulically driven load comprising a throttle, characterized in that the return lands have a tapered cross section towards an adjacent signal land so as to each form a second throttle. Control device for. 13 The inner bore comprises switching annular grooves connected to connecting pipes via each one of the third branch pipes on both sides of the outer side of the signal annular groove, and the axial spool has a terminal land. , on both sides outwardly of the boundary land, each passage having a connection to a groove between the boundary land and the termination land, the groove having a connection to a groove in which the axial spool is in a neutral position. Claim 1, characterized in that the switch is configured to communicate with the switching annular groove when the switch is displaced from the switch.
13. A control device for a hydraulically driven load according to claim 1 or 12. 14. Each of the channels includes a third restriction and an extension extending to the land in the center, and the inflow hole of the extension is connected to the annular groove in the center at the outer periphery of the land in the neutral position. Claim 11 or 12, characterized in that it is within the scope of
A control device for a hydraulically driven load as described in paragraphs.