Control device

Abstract

The invention relates to a control device for hydraulic consumers, in particular for controlling the controlled inertial operation of at least one hydraulic rotary drive, for example a vibration motor (10) after shutdown thereof, comprising at least:-a corresponding hydraulic consumer,-a pressure balancing device (DW), and-a pressure limiting valve (DB), the pressure limiting valve acts on a control side (c) of the pressure balancing device (DW), and if a control pressure acting on another control side (d) of the pressure balancing device (DW) opposite the one control side (c), which is detected by a control connection (12) on the input connection (E), is greater than a control pressure applied on the one control side (c), the pressure limiting valve is actuated by the control connection (12) on the input connection (E). The invention relates to a pressure equalizing device which releases a fluid flow present at an input connection (E) thereof via an output connection (A) in the direction of a low-pressure side (3), such as a tank (T).

Description

Field of the Invention

[0001] The present invention relates to a control device for a hydraulic consumer, in particular for controlling the controlled inertial operation of at least one hydraulic rotary drive, such as a vibration motor, after it has been switched off. The invention also relates to a valve, preferably for use in such a control device. Background Art

[0002] Today, hydraulic rotary drives are braked or purposefully made to run inertially in different ways. Such rotary drives are commonly used in conventional road rollers. The associated road rollers have a so-called vibrating rim for compacting the ground, and a hydraulic motor with eccentrically arranged mass blocks is installed in the vibrating rim. In technical terms, the associated device is also referred to as a vibration motor. Vibration can be activated or deactivated by switching the pump supply on and off (usually in the form of a conventional hydraulic pump). However, when the vibration is deactivated, due to the inertia of the mass, the vibration motor will still continue to run for a certain shutdown time. However, this continued operation of the vibration motor is not desired, so the mass blocks must be purposefully braked and the vibration motor must be brought to controlled inertial operation.

[0003] There are different hydraulic solutions for braking the motor, and among them, a solution that conforms to the current state of the art is exemplarily introduced in this patent Figure 1 A two-way two-position seat valve is used here. When the valve is not energized, it is used to guide the oil supply from the hydraulic pump to the low-pressure side of the hydraulic reservoir circuit (usually in the form of a tank) without pressure, or when the valve is energized, it blocks the relevant oil flow to the tank, so that the oil flows as a whole to the vibration motor to drive the vibration motor. Another two-way two-position seat valve downstream of the vibration motor is used to block the oil from flowing to the tank when the valve is not energized, or to guide the oil to the tank without pressure when the valve is energized. In practice, this means that during the vibration operation, the two seat valves must be continuously energized, which is correspondingly energy-consuming. To switch off the vibration, the two seat valves are de-energized, and during the inertial operation, the volume flow downstream of the vibration motor generated by the mass inertia of the motor can only be guided to the tank through a throttle orifice and a pressure limiting valve.

[0004] For cost reasons, in this known solution, the pressure limiting valve is often used together with other required valves (such as two check valves) on the machine side or the road roller side. This means that the braking pressure is preset by the pressure limiting valve on the machine side, and the inertial operation time can be determined by the diameter of the throttle orifice. However, this known solution strongly depends on temperature, and the braking process is difficult to calculate, especially when a high braking torque appears at the beginning of the process and a relatively low braking torque appears at the end of the process. Summary of the Invention

[0005] Starting from this prior art, the present invention is based on the following task: to improve the known solution.

[0006] The control device having the features of claim 1 as a whole solves the relevant tasks. It is hereby stipulated that the control device according to the invention at least comprises:

[0007] - a corresponding hydraulic consumer,

[0008] - a pressure balancing device, and

[0009] - a pressure limiting valve,

[0010] The pressure limiting valve acts on a control side of the pressure balancing device. Once the control pressure acting on the other control side of the pressure balancing device, which is opposite to the said one control side and is obtained through the control connection part on the input connection part, is greater than the control pressure applied to the said one control side of the circulating pressure balancing device, the pressure balancing device releases the fluid flow existing at its input connection part towards the low-pressure side, for example, in the direction of the tank, through the output connection part.

[0011] In this way, the control device according to the invention can also be integrated in a space-saving manner in a single valve, which is also the subject matter of the invention according to independent claim 13. When the vibration drive device is activated, in which the oil flow to the tank is blocked by an independent switching valve, due to the pressure supply unit, in the case of using a conventional hydraulic pump, a fluid pressure is established on the inflow side of the vibration motor, which controls the main valve or the motor inertia running valve, and thus an almost pressureless circulation to the tank is achieved. In the fully controlled state, the main valve has a very large opening cross-section, which results in a very low circulating pressure (3 bar at 60 liters per minute). Since pressure is always applied to the inflow side of the relevant motor during vibration operation, the main valve also remains continuously controlled.

[0012] Only when the vibration motor is deactivated, that is, when the pressure supply device is disconnected, does the pressure on the inflow side of the vibration motor decrease, and the main valve or the motor inertia running valve closes. During this shutdown process, the pressure on the outflow side of the vibration motor keeps rising until the pressure limiting valve of the control device opens. As a result, the pressure in the control connection part or the control pipeline (the control connection part or the control pipeline guides the pressure to the inflow side of the pressure balancing device) is greater than the pressure on the spring side of the pressure balancing device, so that the pressure balancing device opens towards the tank, and thus the outflow side of the vibration motor is connected to the low-pressure side or the tank side of the device.

[0013] The combination of a pressure balancing device and a pressure limiting valve allows for pressure regulation that maintains the pressure constant until the motor stops. Thus, this pressure regulation generates a constant braking torque that can be freely adjusted within the range of 50 to 230 bar. By means of a preferred combination of throttle orifices (where throttle orifices are provided upstream and downstream of the branch, and the control line on the spring side of the pressure balancing device is connected to this branch), the dynamic characteristics of the braking system can be adjusted. The pressure balancing device is preferably designed as a circulating pressure balancing device, i.e., the volume flow can be kept constant independently of the pressure.

[0014] Not only the pressure limiting valve, but also the pressure balancing device and the main valve can be hydraulically actuated purely, which results in reliable operation. In addition, compared to electrically actuated switching valves, the associated hydraulic valve concept is energy-saving during operation and is thus energy-efficient.

[0015] The control device can also be used for series operation with multiple motors without the multiple motors influencing each other. For this, separate tank lines are used, which are connected to the pressure limiting valve on the output side. In this way, for example, a front and rear road roller with two vibrating rims (one in front and one behind), i.e., two motors in this regard, can be controlled with a single control device.

[0016] The braking pressure mentioned can be adjusted independently of the pressure limiting valve, thus enabling a braking process that protects the material.

[0017] Other advantageous embodiments of the control device and the valve are the subject of the dependent claims. Description of the Drawings

[0018] The control device according to the invention and the valve will be explained in more detail below based on an embodiment. Here, in a schematic and non-scale drawing:

[0019] Figure 1 A control device according to the prior art is shown in the form of a hydraulic circuit diagram;

[0020] Figure 2 A control device according to the solution of the invention is shown in this regard in contrast to Figure 1 different ones based on a hydraulic circuit diagram according to Figure 1 and;

[0021] Figure 3 A view of the valve is shown in the form of a longitudinal sectional view, which integrates the main components of the control device according to Figure 2 into one valve housing. Detailed Description of the Invention

[0022] According to Figure 1The hydraulic circuit diagram shows the main components of a control device according to the prior art. A hydraulic consumer in the form of a vibration motor 10 is connected to a hydraulic supply circuit 36. The vibration motor 10 uses a so-called vibrations bandage within the scope of a conventional road roller to compact the ground, in which a hydraulic motor is arranged with a mass block arranged eccentrically. The vibration can be activated or deactivated by switching on and off the pressure supply device P in the case of using a hydraulic pump 20 that can be driven by a motor (not shown). When the vibration is deactivated, due to the inertia of the mass, the vibration motor 10 continues to run. In this regard, the vibration motor 10 is connected on its inflow side 22 via a hydraulic connecting line 11 to the fluid delivery side of the hydraulic pump 20 with supply pressure. On the outflow side 18 of the vibration motor 10, the motor 10 is in turn connected as part of the hydraulic supply circuit 36 to a valve device denoted as a whole by 13.

[0023] The valve device 13 has an electrically controllable two-way poppet valve 15, which is arranged downstream of the vibration motor 10 in the direction of fluid flow, for blocking the oil from flowing back to the tank T in the shown non-energized state or for guiding the oil to the tank T without pressure in another switching position when energized. In addition, another electrically controllable two-way poppet valve 17 is connected between the hydraulic connecting line 11 and the return line 19 leading to the tank, and this return line leads to the output side of the first poppet valve 15.

[0024] To switch off the vibration of the motor 10, the two valves 15, 17 are not energized and thus occupy their switching positions as shown in Figure 1 Then, the volume flow generated by the mass inertia of the vibration motor 10 on the outflow side 18 can only be guided to the tank T via the throttle orifice 21 and the main pressure limiting valve 23. In addition to the throttle orifice 21, two spring-loaded check valves 25 and 27 are also used. One check valve 25 opens in the direction of the pressure limiting valve 23, and the other check valve 27 is connected into the connecting line between the line 11 and the connecting part of the fluid-guiding line located between the check valve 25 and the pressure limiting valve 23, and the pressure limiting valve leads out with its output end in the direction of the tank T. However, the main pressure limiting valve 23 can also be part of the hydraulic working circuit (not shown) of the working machine, i.e., the road roller, in combination with the two check valves 25, 27. This means in practice that the braking pressure is preset by the main pressure limiting valve 23, and the coasting time is determined by the throttle orifice diameter of the throttle orifice 21. The relevant known solutions strongly depend on temperature, and the braking process has proven to be less constant, where the braking torque is high at the beginning of the braking process and low when the braking process is approaching the end.

[0025] Starting from this prior art, from now on according to Figure 2The circuit diagram explains the control device according to the invention in more detail. Here, the above description of the prior art also applies to the solution according to the invention, and the same components are provided with the same reference numerals accordingly.

[0026] The solution of the control device for a hydraulic damper according to the invention is also used in particular for controlling the coasting operation of a hydraulic rotary drive (for example a vibration motor 10 shown in a road working machine not shown, such as a road roller). In addition to the corresponding hydraulic damper, the control device also has a pressure balancing device DW (Druckwaage) and a pressure limiting valve DB. The pressure limiting valve DB acts on a control side c of the pressure balancing device DW. Once the control pressure acting on the other control side d of the pressure balancing device DW, which is opposite to the one control side c and is obtained at the control connection 12 at the input connection E of the pressure balancing device DW, is greater than the control pressure applied to the one control side c, the pressure balancing device releases the fluid flow present at its input connection E towards the low pressure side 3 (for example the housing T) via the output connection A. For this purpose, a branch 24 is provided in the connecting line 54 for guiding the fluid from the input connection E of the pressure balancing device DW to the inflow side of the pressure limiting valve DB. Starting from this branch, a control line 26 leads to the one control side c of the pressure balancing device DW. The pressure of an energy store in the form of a pressure spring Y also acts on the relevant one control side c of the pressure balancing device DW.

[0027] The vibration motor 10 is in turn fluidly connected via a hydraulic connecting line 11 to a pressure supply device P with a hydraulic pump 20. This forms the inflow side 22 for the vibration motor 10. As part of the hydraulic supply circuit 36, the vibration motor 10 is connected on its outflow side 18 to a return line 19 which preferably transitions integrally into a connecting line 16 to which the input connection E of the pressure balancing device DW is connected. For this purpose, the pressure balancing device DW is connected to the connecting line 16 by means of a connection 2. After the branch which is the connection 2 of the pressure balancing device DW on the connecting line 16, a main valve 14 is incorporated into this connecting line. The main valve is connected on its input side to the connecting line 16 and on its output side via a corresponding connecting line to the low pressure side 3 which leads to the housing T in the case of a housing connection. In Figure 2 which, both the pressure balancing device DW and the main valve 14 are shown in their positions blocking the fluid passage.

[0028] For the hydraulic control of the main valve 14, the main valve is connected to the pressure supply device P on a control side a in such a way that the control connection is connected to the pressure supply connection 1 located in the supply line 11. Conversely, the opposite control side b of the main valve 14 is connected in a fluid-conducting manner to the output of the pressure limiting valve DB via the control line 4 or the control connection, where the relevant output of the pressure limiting valve DB is permanently connected via a suitable fluid-conducting housing line to the low-pressure side 3 leading to the housing T. In this regard, the output pressure of the pressure limiting valve DB acts together with the energy store in the form of the pressure spring X via the control line 4 or the relevant control line connection on the said other control side b of the main valve 14.

[0029] Furthermore, the output connection A of the pressure equalizing device DW is connected in the direction of the low-pressure side 3 downstream of the main valve 14 in the direction of fluid flow into the connecting line 16.

[0030] The pressure limiting valve DB is loaded on its respective opposite control sides e, f, on the one hand e by its input pressure and on the other hand f by its output pressure together with the energy store in the form of the pressure spring Z, the spring force of which is adjustable. The inflow side of the pressure limiting valve DB is connected here to the fluid-conducting connection 54, which leads to the input connection E of the pressure equalizing device DW. On the output side, the pressure limiting valve DB is connected, on the one hand as already described, to the control line 4 or the control line connection, which leads to the said other control side b of the main valve 14, and on the other hand to the housing line 29.

[0031] As Figure 2 is further derived, the pressure limiting valve DB has a throttle orifice B1 arranged in front of it on its input side and another throttle orifice B2 is inserted upstream of the already mentioned branch 24 with the control line 26 in the direction of fluid flow, more precisely into the fluid-conducting connection 54 between the input connection E of the pressure equalizing device DW and the branch 24.

[0032] Particularly advantageously, a filter 30, preferably a filter in the form of a slotted screen, can be inserted into the fluid-conducting connection 54 between the said other throttle orifice B2 and the input connection E of the pressure equalizing device DW. The relevant slotted screen - filter element is common in valve technology and will therefore not be discussed in detail at this point. As Figure 2 is further derived, a shut-off valve 32 and another pressure limiting valve 34 are inserted downstream of the pressure supply device P in the direction of fluid flow for protecting the hydraulic supply circuit 36 for the respective hydraulic consumer in the form of the vibration motor 10. In Figure 2In the switching position of valve 32 shown, the valve is in its open position and thus shorts the pressure supply device P in the direction of the low-pressure side 3, i.e., the vibration motor 10 is not supplied with pressure-preset fluid from the hydraulic pump 20 side and is thus shut down in this regard. In contrast, if the shut-off valve 32 enters its other blocking switching position, the associated pressureless cycle ends, and the vibration motor 10 is put into operation by the pressure fluid of the source P present accordingly on its inflow side 22.

[0033] When the hydraulic consumer in the form of the vibration motor 10 is shut down (e.g., because the hydraulic pump 20 is switched off, or the switching valve 32 enters its short-circuit position shown in Figure 2 ), the vibration motor 10 runs coasting. However, in doing so, the supply pressure in the hydraulic connection line 11 leading to the vibration motor 10 decreases during shutdown, and thus the supply pressure at the supply pressure connection 1 also disappears, with the result that the main valve 14 or the motor coasting valve closes, which until now in its open position led the fluid return flow on the outflow side 18 through the return line 19 and the connection line 16 and the low-pressure side 3 to the reservoir tank T.

[0034] However, during the coasting operation of the vibration motor 10, the pressure on the outflow side 18 continues to rise until the directly controlled pressure limiting valve DB opens. As a result, the pressure in the control line 26 leading to one control side c of the pressure equalizing device DW drops, with the result that the fluid pressure in the control connection 12 acting on the other control side d of the pressure equalizing device DW becomes greater than the fluid pressure present on the said one control side c of the pressure equalizing device DW, which causes the pressure equalizing device DW to be operated, which then in this regard establishes a fluid connection between the input connection E and the output connection A, which leads to the low-pressure side 3.

[0035] The pressure equalizing device DW is preferably designed as a circulating pressure equalizing device and is thus a directly controlled spring-loaded spool-type throttle valve or proportional valve and is closed in the Figure 2 normal position shown. Thus, the pressure equalizing device DW has the following task: to adjust a pressure setting independent of the volume flow at the connection E. The adjusted pressure depends on the pressure at the surface c. Thus, pressure limitation is achieved independent of the volume flow, and thus the braking torque remains constant when the vibration motor 10 brakes.

[0036] In order to manipulate the pressure limiting valve into one of its open positions, the required control pressure on the control side e is obtained at the location of the input connection E of the pressure equalizing device DW here, and is brought via the connecting portion 54 for guiding the fluid, the filter 30, the throttle orifice B2, via the branch portion 24 to the throttle orifice B1, and further to the input side of the pressure limiting valve DB.

[0037] The main valve or the motor coasting valve 14 has its own pressure protection (Druckabsicherung) in this regard, such that the braking pressure can be adjusted independently of the main pressure protection. Thus, the set braking pressure (i.e., braking torque) acting on the motor 10 can remain constant over the entire braking process, from which the coasting time for the motor 10 results. In this regard, the braking concept according to the invention is more protective for the vibration motor 10, since the braking pressure can be selected to be less than the main pressure protection. Figure 2 The separate housing line 29 shown therein (which is led on the output side to the low-pressure side 3 of the control device) allows multiple motors (not shown) to also be connected in series with the main valve or the motor coasting valve 14 without influencing each other. In this way, multiple vibration motors 10 (not shown) can be manipulated with one control device, in particular with regard to the coasting manipulation of the respective motors 10.

[0038] According to Figure 2 the main valve components of the control device, such as the pressure limiting valve DB, the pressure equalizing device DW, the main valve 14 and the two throttle orifices B1 and B2 can be combined into a structural unit in a common valve housing 40 according to the illustration according to Figure 3 In addition, the filter 30 can be integrated into the valve together here. Furthermore, Figure 3 all the connections and control sides in Figure 2 are marked as in

[0039] The valve housing 40 (which can consist of a valve block) has a main piston 44 of the main valve 14 that is longitudinally displaceable within the valve space 42 of the valve housing, and the pressure equalizing device DW and the pressure limiting valve DB are in turn integrated into this main piston. The valve space 42 extends through the valve housing 40 along a common longitudinal axis 45, and the valve space 42 is closed outwardly by a screwed-in part 47 that is screwed into the valve housing 40 along a screwing-in section 49. In addition, the interior of the valve housing 40 is sealed relative to the surrounding environment using a conventional annular seal 51 between the screwed-in part 47 and the outside of the valve housing 40. The valve space 42 is dimensioned in terms of its length parallel to the longitudinal axis 45 in any case such that the main piston 44 can move from its position in Figure 3The lower position shown reaches the upper position in which the upper side of the main piston 44 can bear against the inner shoulder 53 on the inside of the screwed-in part 47. In the relevant upper operating position, the main piston 44 permits the connection of the guiding fluid between the input connection E and the output connection A of the pressure equalizing device DW, or the connection of the guiding fluid between the connection 2 of the connecting line 16 and the low-pressure side 3, which low-pressure side is also constructed in the valve housing 40 as a housing connection leading to the housing T.

[0040] For the relevant possible movement of the main piston 44, the valve housing 40 has a pressure supply connection 1 on the bottom side, which can be connected to a hydraulic connecting line 11 leading to the pressure supply device P, and which pressure supply connection leads into the valve space 42 at a location opposite a free end side (as a control side a) of the main piston 44, and the main piston 44 is loaded by an energy storage means in the form of a pressure spring X on the side (as the other control side b) opposite the control side a. Furthermore, the valve housing 40 has a control line connection 4 here, which, as a radially passing part in the valve housing 40, leads into the valve housing 40 on the other control side b of the main piston 44. If the fluid pressure at the pressure supply connection 1 is thus greater than the combined counter-pressure of the pressure spring X and the fluid pressure at the control line connection 4, the main piston 44 of the main valve 14 rises and connects the connection 2 to the connection 3 or the connection E to the connection A as already described. In this regard, the main valve 14 then occupies its open position starting from its closed position shown in Figure 3 the figure.

[0041] The main piston 44 also has a piston space 46 in which the control piston 48 of the pressure equalizing device DW is guided so as to be longitudinally displaceable, the control piston being loaded by an energy storage means in the form of a pressure spring Y on one of its control sides c, and the control piston being in fluid connection with the connection 2 for connecting the connecting line 16 with its other control side d. When the control piston 48 moves against the action of the energy storage means Y, the housing connection or the return connection 3 in the valve housing 40 is in fluid connection with the control piston 48 via at least one throttling part DS in the main piston 44 and a surrounding groove 50 in the control piston 48, and this surrounding groove is in fluid connection with the connection 2 for the connecting line 16 via at least one inclined passage 55 in the main piston 44 in each movement of the control piston 48. It goes without saying that, as is common in valve technology, there can be a plurality of fluid connection parts or through parts, for example in the form of the throttling part DS or the inclined passage 55. According to the illustration in Figure 3 the corresponding inclined passage 55 is arranged below the throttling part DS in the main piston 44 when viewed in the direction of the common longitudinal axis 45 in any case.

[0042] As Figure 3 further obtained in, the lower end portion of the main piston 44 is closed by a closing plug 57, which in the valve position shown in Figure 3 adjoins the port of the pressure supply connection 1 in the valve housing 40 at a preset axial distance parallel to the longitudinal axis 45. In the region of the upper end portion of the closing plug 57, the control connection 12 leads to the inside of the valve space 42, which in turn can consist of a plurality of transverse holes in the main piston 44. Wherein, in the position of the control piston 48 of the pressure equalizing device DW shown, the relevant control connection is substantially covered, provided that lug-shaped protrusions are arranged on the lower side of the control piston 48, which can support on the upper side of the closing plug 57 and delimit fluid passages therebetween, so that the fluid pressure present through the input connection E or connection 2 can act on the lower free end side of the control piston 48 of the pressure equalizing device DW. For a uniform fluid pressure distribution, the connections E, A or 2, 3 lead into an annular space in the valve housing 40, which annular space uniformly surrounds the valve piston 44. In addition, the respective inclined channels 55 lead with their lower free connection sides into an annular protrusion 59 in the valve housing 40, which annular protrusion transitions into a lower valve annular space with a larger diameter, and the connections E, 2 lead into this valve annular space.

[0043] On the lower free end side corresponding to another control side d of the pressure equalizing device DW, which control side adjoins the connection 2 for connecting the pipeline 16 in this regard, a central recess 52 is introduced into the control piston 48 for receiving a filter 30 in the form of a slit sieve, and a throttle hole B2 is connected upward to the filter, which throttle hole leads fluidically into a spring space 56 with a pressure spring Y in this regard. Thus, in the control piston 48, a fluidically guiding connection 54 is permanently established between the connection 2 and the spring space 56 of the pressure equalizing device DW with the pressure spring Y.

[0044] In the direction of observation towards Figure 3 looking, above the pressure equalizing device DW in the main piston 44, a stepped control piston 58 of the pressure limiting valve DB is guided concentrically and longitudinally displaceably with respect to the longitudinal axis 45. This control piston is loaded on one of its control sides f by a pressure spring Z serving as an energy storage. In addition, the control piston 58 of the pressure limiting valve DB extends with its valve tip 60 along its lower side into a fluidically guiding connection 62 between the spring space 56 of the pressure equalizing device DW and the piston space 64 of the control piston 58 of the pressure limiting valve DB, simultaneously forming a throttle hole B1. Where the valve tip 60 abuts against a mating inner channel on the inner side of the main piston 44 that guides in the direction of the throttle hole B1, the control side e of the pressure limiting valve DB is realized.

[0045] The spring force of the pressure spring Z of the pressure limiting valve DB can be adjusted by means of an adjusting drive 66. Herein, by means of a screwed-in body 61 that can be screwed into the upper free end of the main piston 44, an adjusting member 63 that can move longitudinally in the main piston 44 is movable. The upper free end of the pressure spring Z bears on this adjusting member 63, and the pressure spring bears with its other lower free end against the valve disk 65 of the pressure limiting valve DB. If the screwed-in body 61 is screwed further into the main piston 44, the adjusting member 63 moves downward, which results in an increase in the pre-tensioning force for the pressure spring Z, and the pressure spring applies an increased spring force to the valve disk 65 of the control piston 58 of the pressure limiting valve DB in this regard. During the guiding of the pressure spring Z within the main piston 44, the pressure spring X is guided on the outer peripheral side of the main piston 44 concentrically with the pressure spring Z. Herein, the lower end of the pressure spring X bears on a projection that is part of the other control side b of the main valve 14. The other upper end of the pressure spring X bears correspondingly on the inner shoulder of the screwed-in part 47, and this inner shoulder is delimited on the outer peripheral side by the screwed-in section 49. For the outward tight closure of the valve housing 40, the screwed-in part 47 can be provided with a closure plug 67 on its upper side.

[0046] Furthermore, the connecting part 68 is introduced into the main piston 44 of the main valve 14 in the form of at least one transverse hole, and this connecting part fluidically connects the spring chamber 70 with the pressure spring Z of the pressure limiting valve DB to the control line connection part 4 in the valve housing 40. The bearing surface of the pressure spring Z on the valve disk 65 constitutes, in this regard, the other control side f of the pressure limiting valve DB, and this other control side is fluidically connected to the control line connection part 4 through the connecting part 68 in each moving position of the main piston 44, and this control line connection part leads into an annular space that is enlarged in terms of diameter in the valve housing 40. For improving the longitudinal guiding of the valve disk 65, the valve disk has a guiding pin 69 on its upper side, and this guiding pin is loosely seated on the upper side of the control piston 58 or on the valve disk 65 and is guided longitudinally movable in a longitudinal recess in the adjusting member 63. According to Figure 2 All the main components of the control device according to Figure 2 are arranged coaxially with each other along the longitudinal axis 45 in the valve housing 40 in groups, and surprisingly for a person skilled in the art of such control devices, he can combine a plurality of individual valves according to the circuit diagram according to Figure 3 in the valve structure according to There is no corresponding solution in the prior art.

Claims

1. A control device for a hydraulic consumer, in particular for controlling the controlled inertial operation of at least one hydraulic rotary drive, such as a vibration motor (10) after its shutdown, the control device comprising at least: - a corresponding hydraulic consumer, - a pressure balancing device (DW), and - a pressure limiting valve (DB), The pressure limiting valve acts on a control side (c) of the pressure balancing device (DW). Once the control pressure acting on the other control side (d) of the pressure balancing device (DW) opposite to the one control side (c) and obtained through the control connection (12) on the input connection (E) is greater than the control pressure applied to the one control side (c), the pressure balancing device releases the fluid flow present at its input connection (E) towards the low-pressure side (3), such as the direction of the housing (T), through the output connection (A).

2. The control device according to claim 1, characterized in that, The pressure limiting valve (DB) is applied to the one control side (c) of the pressure balancing device (DW) together with an energy storage, such as a pressure spring (Y).

3. The control device according to claim 1 or 2, characterized in that, A hydraulically controllable main valve (14) is connected into the connecting line (16) to which the input connection (E) of the pressure balancing device (DW) is connected, and by operating the main valve (14), the connecting line (16) is connected to the low-pressure side (3).

4. The control device according to any one of the preceding claims, characterized in that, The connecting line (16) leads to the outflow side (18) of the corresponding hydraulic consumer, which is supplied with pressure-preset fluid on its inflow side (22) by a pressure supply device (P), such as a hydraulic pump (20).

5. The control device according to any one of the preceding claims, characterized in that, For the hydraulic control of the main valve (14), one control side (a) of the main valve is connected to the pressure supply device (P), and the other control side (b) of the main valve can be loaded with the output pressure of the pressure limiting valve (DB), preferably jointly loaded with the output pressure of the pressure limiting valve and an energy storage, such as a pressure spring (X), through the control line (4).

6. The control device according to any one of the preceding claims, characterized in that, The output connection (A) of the pressure balancing device (DW) is connected into the connecting line (16) downstream of the main valve (14) towards the low-pressure side (3) in the fluid flow direction.

7. The control device according to any one of the preceding claims, characterized in that, The pressure limiting valve (DB) is loaded on its opposite control sides (e, f) on the one hand with its input pressure, and on the other hand jointly loaded with its output pressure and an energy storage, such as a pressure spring (Z), and the spring force of the pressure spring is preferably adjustable.

8. The control device according to any one of the preceding claims, characterized in that, The pressure limiting valve (DB) has a throttle orifice (B1) on its inflow side.

9. The control device according to any one of the preceding claims, characterized in that, Another throttle orifice (B2) is connected into the connection (28) leading to the input connection (E) of the pressure balancing device (DW) upstream of the branch (24) of the control line (26) leading to the one control side (c) of the pressure balancing device (DW) in the fluid flow direction.

10. The control device according to any one of the preceding claims, characterized in that, A filter is connected between the other throttle orifice (B2) and the input connection (E) of the pressure balancing device (DW).

11. The control device according to any one of the preceding claims, characterized in that, When viewed in the fluid flow direction, a shut-off valve (32) and preferably another pressure limiting valve (34) are connected downstream of the pressure supply device (P) for protecting the hydraulic supply circuit (36) against the corresponding hydraulic consumer.

12. The control device according to any one of the preceding claims, characterized in that, The pressure balancing device (DW) is a circulating pressure balancing device.

13. A valve, in particular for use within a control device according to any one of the preceding claims, characterized in that, In the valve housing (40), not only the main valve (14) and the pressure balancing device (DW) but also the pressure limiting valve (DB) are integrated.

14. The valve according to claim 13, characterized in that, The valve housing (40) houses a main piston (44) that is longitudinally movable in the valve space (42) of the valve housing. The pressure balancing device (DW) and the pressure limiting valve (DB) are integrated in the main piston in sequence.

15. The valve according to claim 13 or 14, characterized in that, The valve housing (40) has a pressure supply connection (1) that leads into the valve space (42) at a location that is opposite to the free end side of the main piston (44) as the one control side (a). The main piston (44) is loaded by an energy storage device, in particular a pressure spring (X), on the side opposite to the one control side (a) as the other control side (b). And the valve housing (40) has a control line connection (4) that opens into the valve housing (40) on the other control side (b) of the main piston (44).

16. The valve according to any one of claims 13 to 15, characterized in that, The main piston (44) has a piston space (46) in which a control piston (48) of the pressure balancing device (DW) is guided longitudinally movably. The control piston is loaded by an energy storage device, preferably an energy storage device in the form of a pressure spring (Y), on one of its control sides (c). And the control piston is in fluid connection with a connection (2) for connecting the connecting line (16) with its other control side (d). And when the control piston (48) moves against the action of the energy storage device (Y), a housing connection or a return connection (3) in the valve housing (40) can be connected to a groove (50) in the control piston (48) in a fluid-guiding manner through at least one throttling part (DS) in the main piston (44). The groove is in fluid connection with the connection (2) for the connecting line (16) during each movement of the control piston (48).

17. The valve according to any one of claims 13 to 16, characterized in that, A recess (52) is introduced on the free end side of the control piston (48). The free end side is the other control side (d) of the pressure balancing device (DW) that is adjacent to the connection (2) for the connecting line (16). The recess is used to accommodate a throttle hole (B2) and preferably additionally used to accommodate a filter (30), such as a slit sieve. And in the control piston (48), a fluid-guiding connection (54) is established between the connection (2) for the connecting line (16) and the spring space (56) with the pressure spring (Y) of the pressure balancing device (DW).

18. The valve according to any one of claims 13 to 17, characterized in that, A control piston (58) of a pressure limiting valve (DB) is guided longitudinally displaceably in a main piston (44), the control piston is loaded on one of its control sides (f) by a pressure spring (Z) serving as an energy storage, and the control piston (58) of the pressure limiting valve (DB) engages with a valve tip (60) into a connecting portion (62) of a guiding fluid between a spring space (56) of a pressure equalizing device (DW) and a piston space (64) of the control piston (58) of the pressure limiting valve (DB), and a throttle orifice (B1) is arranged in the piston space.

19. The valve according to any one of claims 13 to 18, characterized in that, The spring force of the pressure spring (Z) of the pressure limiting valve (DB) can be adjusted by means of an adjusting drive (66).

20. The valve according to any one of claims 13 to 19, characterized in that, A connecting portion (68) is introduced into the main piston (44) of the main valve (14), the connecting portion connects the spring space (70) of the pressure limiting valve (DB) with the pressure spring (Z) to a control line connection (4) in the valve housing (40).

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