• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a hydraulic unit (1) having two pressure connections (2, 3) for supplying a plurality of devices (4, 5), in particular hydraulic rescue devices, comprising a first hydraulic circuit (8) having a first pump arrangement (12) and a first pressure connection ( 2) and a second hydraulic circuit (9) having a second pump arrangement (15) and a second pressure connection (3), the pump arrangements (12, 15) being driven simultaneously by a common drive (18), and by means of a first directional control valve (15). 26) of the first hydraulic circuit (8) with the second hydraulic circuit (9) is connectable and by means of a second directional control valve (28) of the second hydraulic circuit (9) with the first hydraulic circuit (8) is connectable. In this case, the directional control valves (26, 28) have a spring (30, 31) acting in the direction of a starting position and a first control line (34) extends from the first hydraulic circuit (8) or the second hydraulic circuit (9) to the first directional control valve (26). and from the second hydraulic circuit (9) or from the first hydraulic circuit (8) a second control line (35) to the second directional control valve (28).
    公开号:AT516181A4
    申请号:T50717/2014
    申请日:2014-10-08
    公开日:2016-03-15
    发明作者:
    申请人:Weber Hydraulik Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a hydraulic unit with at least two pressure connections according to the preamble of claim 1 and a method for the demand-oriented supply of one or more hydraulically driven devices with hydraulic fluid by means of a hydraulic unit according to the preamble of claim 13.
    Hydraulic power units are already known from the prior art, to which one or more hydraulic devices can be connected, which are actuated independently of one another and are also subject to varying working resistances. For example, such hydraulic units are often used to drive hydraulic Berge¬ devices, in particular with Ver¬brennungsmotorantrieb, as these allow a mobile and independent use derar¬tiger devices. Since with simultaneous operation of two devices on a hydraulic circuit only the device with the lower working resistance is driven, with such hydraulic units each pressure connection is assigned a separate hydraulic circuit with its own pump. In order to make better use of the drive power of a hydraulic unit and for the purpose of increasing the operating speed of a driven device, it is known, by means of manual venting, to adjust the volume flow of a hydraulic circuit to which no or an inactive device is connected These switching operations are usually carried out by a separate operator in agreement with the operators of the devices. When personnel resources are scarce, a separate operator for the hydraulic unit is possibly not available and must therefore dispense with the demand-dependent diversion of the volume flows which is advantageous in the intermittent operation of the devices.
    The object of the invention is to avoid the disadvantages of the prior art and to provide a hydraulic unit with reduced operating effort
    The object of the invention is achieved by a hydraulic unit with the features of claim 1.
    Characterized in that the directional control valves have a spring acting in the direction of a starting position and from the first hydraulic circuit or the second hydraulic circuit a first control line to a first directional control valve acting on the first Be¬ tätigungsglied and from the second hydraulic circuit or the first Hydraulik¬ a second control line to a on the second directional valve acting second actuator is running, the demand-based bypassing Hydraulik¬ fluid from a hydraulic circuit to another hydraulic circuit without the intervention of an operator is possible and thereby substantially facilitates the handling of such hydraulic unit.
    An embodiment in which the first and / or the second control line is designed as a hydraulic control line and acts on the second or first directional valve directly or by means of a control member in the form of a pilot valve is advantageous. The switching operations can thereby be reliably triggered because the pressure in the individual hydraulic circuits provides indications of the respective operating state of a device.
    Additionally or alternatively, it is possible for the first and / or second control line to be designed as an electrical control line and to be connected directly or via a pilot control element, for example by means of an electromagnetic control unit, in particular a magnetic coil. Pilot valve acts on the second or first directional control valve. In this case, the operating state of the connected devices e.g. be actively selected by these switches or sensors and are used as a basis for switching operations. The switching signals can also be converted and further processed using a logic circuit.
    To use the hydraulic unit at different pressure levels, it is of advantage if the first pumping elements comprise at least one high-pressure element with smaller flow rate and at least one low-pressure element with larger Förder¬ amount and the second pumping elements at least one Hochdruckele¬ment with smaller flow and at least one low-pressure element with Include larger flow rate and the directional control valves are arranged in the outgoing of the Niederdru¬ckelementen fluid lines. As the pressure level in the connected devices increases, the volumetric flow supplied to them can be reduced and thus the required power can be adapted to the maximum power of the drive. The switching of the various pressure stages can, as known from the prior art by means of druckgesteuer¬ter directional control valves.
    In order to be able to achieve a high operating speed with low working resistance, it can be provided that the delivery rate of the low-pressure elements of a hydraulic circuit is at least twice the delivery rate of the high-pressure elements of the same hydraulic circuit. As a result, at low pressure levels, a large volume flow can be provided at the pressure ports.
    One possible embodiment of the hydraulic unit is that in the initial position of the directional control valves of these, a flow path from the respective fluid line of the one hydraulic circuit to the connecting line to the other hydraulic circuit is opened. In this case, by default, a volume flow of hydraulic fluid from one hydraulic circuit is diverted to another hydraulic circuit, and this volume flow is to some extent only retrieved when the pressure rises.
    It can further be provided that the first connecting line extends from the first directional control valve to the second directional control valve and the second connecting line extends from the second directional control valve to the first directional control valve, the second directional control valve leading a flow path from the first connecting line in a first switching position to a second pressure connection second fluid line or in another switching position to the fluid container and the first directional valve a flow path from the second connecting line in a first
    Switching position can produce to a first pressure connection leading first fluid line or in another switching position to the fluid container. For the control of the fluid flows are thereby further options available and the Flydraulikaggregat can respond even better to the requirements of the device.
    In order to use the unneeded volume flow of another Flydraulikkreises even at high pressure level in Flydraulikkreis a working device, it can be provided that a Flydraulikkreis at least two Flochdruckelemen te includes, of which at least one is connected via a fluid line directly to the pressure connection and at least one can be connected via the directional control valve with another and Flydraulikkreis. In this embodiment, both in the low pressure range as well as in the fluid pressure range, demand-based and performance-optimized allocation of the volume flows can take place.
    Furthermore, it is possible to divert the entire volume flow of a Flydraulikkreises to another Flydraulikkreis when all first fluid lines means one or more first-way valves and means of one or more first connecting lines or transition lines with at least one second fluid line of the second Flydraulikkreises and / or all second fluid lines means one or a plurality of second directional valves and by means of one or more second connecting lines or transition lines with at least one ers¬ten fluid line of the first Flydraulikkreises are connectable. The Betriebszustandbzw. the pressure level of a device no longer supplied with hydraulic fluid can no longer be determined by simple means, e.g. a control line from the Flydraulikaggregater, therefore, for resetting the volume flow diversion suitable other measures must be taken, e.g. a coordinated alternating operation of the devices, which, however, can also take place without a separate operator for the flow control unit. One possibility for switching the Be¬triebsart could consist in that of the non-hydraulic fluid supplied device by means of a switch and an electrical control line, a signal for the provision of the volume flow redirection is generated, whereby again a simultaneous supply of both devices is given.
    One way to achieve an operation with multiple pressure levels is that in one of the fluid lines of a hydraulic circuit downstream of a pumping element, a pressure switching valve is arranged, which is controlled via an outgoing from another fluid line of the same hydraulic circuit pressure control line, whereby upon pressure increase in the other fluid line from Druck¬ switching valve, a flow path from the pumping element to the fluid container is made. As a result, the high-pressure flow rate can be easily reduced as needed and the power of the drive optimally utilized.
    Structurally advantageous and especially for mobile use proven Pumpenano¬rdnungen arise when the first pumping elements and the second pump elements are arranged to each other as in a radial piston pump.
    Ensuring adequate oil supply to the pump assemblies is possible for a wide variety of applications when suction lines from the pumping elements lead into the fluid container. The shape and position of the Fluidbehäl¬ters is largely arbitrary in this case and can beoperated with smaller quantities.
    The object of the invention is also achieved by a method for supplying one or more hydraulically drivable devices, in particular hydraulic rescue devices, with hydraulic fluid by means of a hydraulic unit having at least two pressure connections according to claim 13, in which in a first hydraulic circuit with a first pump arrangement Volume flow of at least two first pumping elements are summarized and led to a first pressure port and in a second hydraulic circuit with a second pump arrangement by means of second fluid lines, the volume flows of at least two second pumping elements zusammenge¬ gripped and passed to a second pressure port, wherein the the first pumping elements and the second pumping elements are simultaneously driven by a common drive and wherein, as required, the volumetric flows are distributed to the pressure connections by means of a first directional valve one of the first fluid lines is connected via a first connecting line to a second fluid line in the second hydraulic circuit and at least one of the second fluid lines is connected via a second connecting line to a first fluid line in the first hydraulic circuit by means of a second directional valve, characterized in that the directional control valves by means of a Spring are brought into a starting position and a switching operation of the first directional control valve by a first actuator, which is controlled by one of the first hydraulic circuit or from the second hydraulic circuit outgoing and extending to the first actuating member first control line is effected, anda switching operation of the second directional valve by a second actuator, which is driven by one of the second hydraulic circuit or from the first hydraulic circuit emanating and extending to the second actuator second control line, is effected.
    If two or more devices are activated in a hydraulic unit according to the invention, each of the devices is automatically supplied with about half or a corresponding proportion of the total delivery volume, with only one activated device, this approximately the total delivery volume is supplied.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    In each case, in a highly simplified, schematic representation:
    Fig. 1 is a hydraulic diagram of a hydraulic unit according to the invention;
    FIG. 2 shows a hydraulic diagram of a further embodiment of a hydraulic unit; FIG.
    3 is a hydraulic diagram of a further embodiment of a hydraulic unit;
    4 shows a hydraulic diagram of a further embodiment of a hydraulic unit;
    5 is a hydraulic diagram of a further embodiment of a hydraulic unit and
    6 is a hydraulic diagram of a further embodiment of a hydraulic unit.
    1 shows a simplified and schematic diagram of a hydraulic unit 1 for the ready supply of two or more hydraulically driven devices. For this purpose, the hydraulic unit 1 has at least two pressure ports 2 and 3 and, on the left-hand pressure port 2 in FIG. 1, a first device 4, for example in the form of a mountain shears, a spreading cylinder or a spreader, can be connected. In Fig. 1, a second device 5 is shown with dashed lines, which can be connected to the right-hand pressure port 3. The devices 4, 5 each have a fluid supply 6 through which the volume flow provided by the pressure ports 2, 3 is supplied and furthermore each have a fluid return 7, with which a volume flow is again supplied to the hydraulic unit 1. Details of the fluid return 7 on the devices 4, 5 and on the hydraulic unit 1 are not illustrated or explained at this point, only simple return lines are required for this purpose. To control the volume flow at the devices 4, 5, these are equipped, for example, with 4/3-way valves, with which in the basic position of the valve in idling a circulation of the hydraulic fluid at a low pressure level is possible and in the other valve positions two different directions of movement of the Ge¬räte. 4 , 5 can be selected.
    To supply the pressure connections 2, 3, the hydraulic unit 1 comprises two hydraulic circuits 8 and 9 indicated by dashed and dotted lines, from which hydraulic fluid 10 is taken from a fluid container 11 and supplied to the pressure ports 2, 3. The first hydraulic circuit 8 comprises a first pump arrangement 12, which consists of at least two pumping elements 13 and 14. Analogously, the second hydraulic circuit 9 comprises a second pump arrangement 15 which comprises at least two pumping elements 16 and 17. The pumping elements 13, 14, 16, 17 are based on the displacement principle and can thereby build up very high pressures, for example up to 1000 bar. Furthermore, the pumping elements 13, 14, 16, 17 and possibly further pumping elements may be part of a hydraulic pump in the form of a radial piston pump, axial piston pump or similar pump types with a plurality of displacement elements.
    The pumping elements 13, 14 of the first pump arrangement 12 and the pumping elements 16, 17 of the second pumping arrangement 15 are driven by a common drive 18, wherein the drive 18 may comprise, for example, an electric motor. For a mobile use, the use of an internal combustion engine 19 is also advantageous as a drive since there is a large spatial independence of current sources. The volume flows generated by the first pumping elements 13 and 14 are conducted via first fluid lines 20 and 21 to the first pressure port 2, wherein the at least two first fluid lines 20 and 21 can also be combined in a first manifold 22 in front of the first pressure port 2. Analogously, the volume flows generated by the second pumping elements 16 and 17 are conducted via second fluid lines 23 and 24 to the second pressure port 3, wherein here also the second fluid lines 23 and 24 can be led together before the second pressure port 3 to form a second manifold 25. The fluid lines 20, 21 and 23, 24 are shown in the form of arrows to illustrate the volume flows guided through them.
    In order to simplify the illustration, FIG. 1 does not show any fluid lines in which the hydraulic element 10 is returned to the fluid container 11 largely without pressure within the fly hydraulic circuits 8 or 9 or by the devices 4 or 5.
    In principle, it is provided that the volumetric flow of the first pump arrangement 12, ie the first pump elements 13 and 14, is provided at the first pressure connection 2 for the first apparatus 4 and, analogously, at the second pressure connection 3 for the second apparatus 5 Volumetric flow of the second Pumpenanordnung 15, ie the second pumping elements 16 and 17 is provided. If no device 4, 5 is connected to one of the pressure ports 2, 3, it is absolutely necessary to ensure measures known from the state of the art that the volume flows generated by the pump elements 13, 14, 16, 17 return to the fluid reservoir 11 without damaging the fly hydraulic unit 1 be supplied.
    This can be, for example, a pressure relief valve arranged upstream of the pressure connections 2, 3, which is actuated manually and the volume flows are supplied to the pressure connections 2, 3 only after connection of a device 4 or 5.
    The power converted in a hydraulic circuit 8 or 9 is proportional to the product of the volume flow rate and the fluid pressure level. Since the power of the drive 18, for example a combustion engine 19 used in the hydraulic power unit 1 is limited, the pressure at the pressure connections 2bzw. 3 available adjustable flow at a certain pressure upwards limited. At low back pressure by the connected device 4bzw. 5, the flow rate is additionally limited by the highest driving speed of the drive 18, for example, by the maximum speed of the engine 19. In practice, however, it can be assumed that the drive speed is largely constant, for which reason a largely constant total delivery quantity is supplied by the pump assemblies 12, 15, and these, adapted to the available drive power, have to be divided into volume flows with different pressure levels ,
    From the prior art, it is known to provide a possibility in a generic hydraulic unit 1 to at least partially redirect the volume flow available in a hydraulic circuit 8 or 9 into the respective other hydraulic circuit 9 or 8, whereby the power of the drive 8 can be exploited better and at a pressure port 2 and 3, a volume flow can be used, which goes beyond the volume flow provided by the respective pump assembly 12 and 15 respectively. In this way, if no volumetric flow is required at one of the pressure ports 2 or 3, since no device is connected or the device is in an inactive state, an increased volumetric flow can be made available at the other pressure port, whereby an attached one Device increased working speeds or Wirkkräfte can be achieved. For this, if necessary, diversion of a volume flow from the first hydraulic circuit 8 to the second hydraulic circuit 9, the first hydraulic circuit 8 has a first directional valve 26 to which the first fluid line 21 is connected via a first connecting line 27 to a second fluid line 24 in the second hydraulic circuit 9 can. Likewise, a second directional control valve 28 is arranged in the second hydraulic circuit 9 in a second fluid line 24 and the second fluid line 24 can be connected to the first fluid line 21 via a second connecting line 29.
    From the prior art it is known to use directional control valves, which are manually operated, and a manual changeover operation is required for the demand-oriented allocation of the volume flows. In practice, hydraulic units known from the state of the art are handled in such a way that an operator working with a recovery device issues commands corresponding to an operator on the hydraulic unit. For the demand-based allocation of the volume flows to the devices, therefore, a separate operating man is required in the prior art.
    In a hydraulic unit 1 according to the invention, a separate operator is not required for the demand-based allocation of the volume flows, since the directional control valves 26 and 28 execute automated switching operations.
    For this purpose, the directional control valves 26, 28 have a spring 30, 31 which acts in the direction of a starting position and furthermore comprise an actuating member 32, 33, with which the volume flow is either fed to the respective pressure port 2 or 3 or via the connecting line 27 or 29 in each case to the other Hydrau¬likkreis 9 or 8 is redirected. The first actuating element 32 acting on the first directional control valve 26 is actuated via a control line 34, which in the illustrated exemplary embodiment extends from the second hydraulic circuit 9 to the actuating element 32 and the second actuating element 33 acting on the second directional control valve 28 is actuated via a control line 35 which in this Ausführungs¬beispiel from the first hydraulic circuit 8 to the actuator 33 extends.
    In the illustrated embodiment, the switching position of the directional control valve 30 is determined by the pressure prevailing in the second hydraulic circuit 9, since the control lines 34 and 35 are hydraulic control lines, in which the pressure in a fluid line of the other hydraulic circuit to the
    Actuator of the directional control valve of the other hydraulic circuit is Übertragungs.Mit such a hydraulic unit 1, the 2bzw at a pressure port. 3 provided volume flow to be increased by a pumping element 17 and 14 of the other hydraulic circuit 9 and 8, whereby the Arbeitsge¬schwindigkeit a connected device 4 and 5 can be increased without a manual adjustment of the directional valves 26, 28 would be required.
    The control lines 34 and 35 may also be electrical control lines, with which status information from the respective other hydraulic circuit 9 or 8, eg pressure levels or switch positions on the devices 4, 5 are transmitted to the Betätigungs¬ member 32 and 33 of the considered hydraulic circuit 8, 9 and the aforementioned switching operations can be effected.
    If, for example, the device 4 connected to the hydraulic unit 1 is a hydraulically driven rescue cylinder, different operating states occur when it is used. When the rescue cylinder is idling, the hydraulic fluid 10 may be directed to the relief cylinder switching valve and back to the fluid tank 11 at a low pressure level. When retracting or extending the rescue ram without load, there is only a low working resistance, which is based in the internal friction of the rescue ram and in line resistance and this entry or exit movement takes place at a comparatively low pressure level of up to about 30 bar. This retraction or extension movement should be able to be carried out at the highest possible speed for reasons of saving time and is therefore the provision of a large Volu¬menstroms of advantage and can due to the relatively low pressure levels and the drive 18 to apply the necessary power.
    In the case of external loading of the rescue ram, it works against a higher working resistance and thereby increases the required fluid pressure and must also be provided by the hydraulic unit 1. The pressure level typically increases up to 700 (1000) bar and, because of the limited power of the drive 18, the volume flow under high pressure must be reduced.
    In the case of the hydraulic unit 1 shown in FIG. 1, this can be done, for example, by leading only the volumetric flow of the first pumping element 13 to the pressure port 2 during a pressure increase at the pressure port 2, while the volumetric flow of the pumping element 14 is controlled by a pressure-controlled valve, for example Switching pressure of 150 to 250 bar to Fluidbehäl¬ter 11 is returned. The pumping element 14 thereby requires only a comparatively small proportion of the drive power, and a correspondingly higher proportion of the drive power for the pumping element 13, which must generate the high working pressure, is available.
    In Fig. 1, the initial position of the directional control valves 26 and 28, which is effected by the Fe¬dern 30 and 31, such that the volume flow of the pumping elements 14 and 17 respectively in the respective hydraulic circuit 8, 9 remains and thus to the pressure port 2 and 3 respectively to be led. However, other embodiments are possible.
    The control lines 34 and 35 may also be electrical control lines with which electrical signals are transmitted from the respective other hydraulic circuit or from a device connected thereto to the actuating member of the relevant hydraulic circuit. Electrical control signals can be generated by switching elements on the connected device or by pressure-voltage converters in the hydraulic circuit.
    The actuators 32, 33 may, for. B. be implemented as control spool for hydraulic control lines 34, 35 or as solenoid valves for electrical control lines 34,35 in corresponding directional control valves.
    FIG. 2 shows a diagram of a further embodiment of a hydraulic unit 1 according to the invention, wherein the components which have already been described in connection with FIG. 1 described embodiment are provided with the same Bezugszei¬chen, and is largely omitted repetitions of the component descriptions.
    The connectable to the hydraulic unit 1 device 4 is formed in the illustrated Ausfüh¬rungsbeispiel by a hydraulic recovery device 36 and includes a double-acting hydraulic cylinder in which a piston separates two working spaces within the hydraulic cylinder from each other. The direction of movement of the lifting device 36 depends on in which of the working spaces the hydraulic fluid 10 fed through the fluid supply 6 is conducted by means of a switching valve 37. The hydraulic fluid 10 displaced from the respective other working space is returned to the hydraulic unit 1 via the fluid return 7 , When the device 4 is connected, the fluid circuit from the pressure port 2 via fluid supply 6, device 4 and fluid return 7 leads back to a return port 38 and return line 39 on the hydraulic unit 1 or directly back to the fluid container 11.
    In dashed lines, a second device 5 is indicated, which can also be connected to the Hydrau¬likaggregat 1.
    The drive 18, the pump assemblies 12 and 15 and the fluid lines 20, 21, 23, 24 or manifolds 22, 25 correspond to the embodiment described with reference to FIG. 1, but the lines in FIG. 2 are represented by dashes and not as in Fig. 1, by block arrows.
    The embodiment according to FIG. 2 differs from that in FIG. 1 in that the directional control valves 26 and 28 are pressed by the springs 30 and 31, respectively, into a starting position, in which a flow path from the first fluid line 21 of the first Hydraulic circuit 8 is open to the connecting line 27 to the other hydraulic circuit 9. In this embodiment, therefore, the volume flow delivered by the pumping element 14 in the initial position of the directional control valve 26 is diverted to the other hydraulic circuit 9. Similarly, in the second hydraulic circuit 9, the output position of the directional control valve 28 is such that the volume flow delivered by the pumping element 17 is diverted to the first hydraulic circuit 8.
    Since the pump arrangements 12 and 15 usually have identical delivery rates, this "crossing" of volume flows between the two hydraulic circuits 8 and 9 has no noticeable effect on the volume flows or pressures provided at the pressure ports 2 and 3.
    The actuator 32, with which the first directional control valve 26 is switched against the action of the spring 30 from the starting position, is in turn addressed by a first control line 34, which in this embodiment, however, starts from the first hydraulic circuit 8 itself, namely from the first fluid line 20, which leads from the pumping element 13 to the first pressure port 2.
    As a result of this embodiment, the first hydraulic circuit 8, when the pressure in the fluid line 20 rises to a certain extent, retrieves the volume flow diverted from the pumping element 14 to the second hydraulic circuit 9 for its own requirements. Likewise, the second hydraulic circuit 9 can retrieve the in the starting position of the second directional valve 28 to the first hydraulic circuit 8 bypassed volume flow of the pumping element 17, if necessary, to its own pressure port 3.
    As already explained, with such a hydraulic unit 1, a device 4, 5 can be supplied with different pressure levels of the hydraulic fluid 10, whereby due to the predetermined power of the drive 18 at low pressure, a large volume flow and at high pressure, only a small volume flow is provided can. In order to make this possible, provision can be made for individual pumping elements, for example the pumping elements 14 and / or 17, to be redirected directly to the fluid container 11 when the pressure level in the working device rises by means of a valve, not shown, and thus to reduce the proportion of the flow rate under high pressure.
    Furthermore, it is possible that the pumping elements 13 and 14 of the pump arrangement 12 or the pumping elements 16 and 17 of the pump arrangement 15 have different sized delivery rates. At a certain drive intensity of the drive 18, for example a reference speed, it can be provided that the pumping element 14 has a larger delivery capacity than the pumping element 13 and thus is well suited for the supply with a large volume flow at comparatively low pressure level, while the smaller pumping element 13 with its smaller delivery capacity for providing a comparatively small
    Volumetric flow at high pressure level is optimally suited. For the design of such multi-stage pumps, reference is made to the prior art known in this regard.
    An inventive hydraulic unit 1 has, for example, the following För¬dermengen, which are dependent on the respective operating situation. As a reference intensity of the drive 18, for example, a speed of 3000 / min is assumed. The two pumping elements 13 and 16 of the hydraulic circuits 8, 9 have at this reference intensity a flow rate of, for example, in each case 0.7 l / min and the pumping elements 14 and 17 have, for example, a flow rate of 2.0 l / min. The pumping elements 13 and 16 can thus 40bzw as high-pressure elements. 41 and the two larger pumping elements 14 and 17 may be referred to as low pressure elements 42 and 43, respectively.
    In one embodiment of the hydraulic unit according to FIG. 1, the following delivery rates result when two devices 4, 5 are used. If two devices 4, 5 are connected to the pressure ports 2, 3, they are flowed through in idling at a pressure level of up to about 20 bar , As a delivery quantity, the volume flow of 2.7 l delivered by the pump arrangement 12 is available at the pressure connection 2. Likewise, the second device 5 is provided by the pressure port 3 with a flow rate of 2.7 l / min.
    If, for example, an adjusting movement is initiated at low resistance at the device 4, the pressure increases to over 20 bar, whereby a switching signal is sent to the second directional valve 28 via the control line 35 and the volumetric flow of the pumping element 17 is diverted to the first hydraulic circuit 8 and thereby at the first pressure port 2, a flow rate of 4.7 l / min is available. As a result, if only one device is activated, this can achieve a significantly higher operating speed. If, for example, the device 5 is also activated with a low load resistance, a changeover signal is transmitted to the first directional control valve 26 via the control line 34 due to the pressure rise in the second fluid line 23, the changeover process being effected by the actuation element 32. As a result, the volumetric flow delivered by the pumping element 14 is diverted to the second hydraulic circuit 9 and, in turn, is available to the devices 4, 5, as in the idling mode, in each case 2.7 l / min. The increased operating speed of the devices 4bzw. 5 can therefore always be used automatically if only one of the devices 4, 5 is actuated.
    If a high resistance to operation occurs on a device 4, the volume flow delivered by the pump element 14 is diverted to the fluid container 11 by means of a valve, not shown in FIG. 2, and the drive power of the drive 18 is largely available for the first pump element 13 , with which at the reference speed of 3000 / min, a flow rate of 0.7 l / min at the pressure port 2 can be provided. The pressure level is approximately between the switching pressure of less than 250 bar, which, when exceeded, shuts off the flow rate of the pumping element 14 and the system pressure limited by a pressure relief valve from about 750 bar to 1000 bar.
    The great advantage of the hydraulic unit 1 according to the invention is that these switching operations for the demand-oriented allocation of the volume flow to the pressure ports 2 and / or 3 need not be performed by an operator, but because of the directional control valves 26, 28.
    In the embodiment shown in FIG. 2, the device 4 is supplied from the pressure connection 2 at idle with a flow rate of 2.7 l / min, which consists of a subset of 0.7 l / min from the high-pressure element 40 of the first hydraulic circuit 8 and a subset of 2.0 l / min composed of the low pressure element 43 of the second hydraulic circuit. With a pressure increase by activating the device 4 with a low resistance to work, the volume flow of the low-pressure element 42 is additionally conducted at a delivery rate of 2.0 l / min to the pressure port 2, whereby a total of 4.7 l / min is available hen no volume flow for a second device 5 is required.
    In Figs. 1 and 2 are known from the prior art measures that allow a two-stage printing operation, for example, pressure relief valves, throttle valves, check valves, etc. are not shown or described in detail.
    FIG. 3 schematically shows a further embodiment of a fly-hydraulic unit 1, which may be independent of itself, wherein the same reference numerals or component designations are used again for identical parts as in the preceding FIGS. 1 and 2. To avoid unnecessary repetition, reference is made to the description in the preceding Figs. 1 and 2 reference.
    In this embodiment, leading from the first Flydraulikkreis 8 on the first directional control valve 26 connecting line 27 leads to the second directional control valve 28 and is in this the supplied via the connecting line 27 volume flow depending on the switching position of the directional valve 28 either via a return line 39 in the fluid container 11 derived or via a flow path in the directional control valve 28 with the volume flow supplied by the second pumping element 17 in the second fluid conduit 24 and in succession provided via the second manifold 25 with the second pressure connection 3.
    Analogously, the connection line 29 leading from the second fly-control circuit 9 to the second directional control valve leads to the first directional control valve in the first fly-control circuit 8and we supply the volume flow delivered via the connection line 29 to the fluid reservoir 11 via a return line 39, depending on the switching position of the valve 26 the volumetric flow delivered by the pumping element 14 is summarized and provided in sequence via the manifold 22 at the first pressure port 2.
    In addition, as shown, check valves 44 may be provided in the connecting lines 27, 29, with which an undesired flow direction reversal or pressure propagation in an undesired direction can be prevented.
    Also in the pumping elements 14 and 17, which are provided as low-pressure elements 42 and 43 with the symbol ND, check valves 44 may be provided in the outgoing of these fluid lines 21 and 24. Further, a check valve 44 may be provided in the fluid passages between the directional control valves 26, 28 and the pressure ports 2, 3 so as not to allow pressure propagation to the low pressure region as the pressure level at the pressure ports 2, 3 increases.
    The pumping elements 13, 14, 16, 17 in Fig. 3 are, as already described with reference to FIGS. 1 and 2, provided with a drive, not shown, with which the Pum¬pelemente are driven simultaneously. In order to adapt the delivery rates provided at the pressure connections 2, 3, a pressure changeover valve 45 is provided in the first hydraulic circuit 8 with which the volume flow delivered by the pumping element 14, ie a low pressure element 42, no longer reaches the pressure connection 2, but rather into the Fluidbehälter11 is passed. The switching of the pressure changeover valve 45 is effected via a control line 46, which leads out of the first fluid line 20, with which the fluid pressure prevailing at the pressure connection 2 is conducted to the pressure changeover valve 45 and this triggers a changeover operation by means of an actuating element (not shown), if due to an increasing pressure in the control In this way, a spring 47 causing the starting position of the pressure changeover valve 45 is overcome.
    Similarly, in the second hydraulic circuit 9, a pressure changeover valve 48 is provided, with which the volume flow delivered by the second pumping element 17 is no longer directed to the second pressure connection 3, particularly into the fluid container 11, when a limiting pressure is exceeded. A control line 49 effecting the switchover acts on the pressure level existing between the second pump element 16, the high pressure element 41 and the second pressure port 3, and if a restoring force caused by a spring 50 is exceeded, the volumetric flow of the pump element 17 to the fluid reservoir 11 is effected. The power of the drive in these cases is therefore predominantly sufficient for the drive of the high-pressure elements 40 and 41 and can be overcome with the connected devices 4, 5 and high Arbeitswie¬derstände.
    To protect the hydraulic unit 1 may further be provided that each hydraulic circuit 8, 9 is provided with a pressure relief valve 51, which limits the anda pressure ports 2 and 3 maximum provided pressure and the maximum pressure is set such that a bursting of components of the hydraulic unit 1 avoided is. The maximum pressure, for example, an upper limit of 750 to 1000 bar is set.
    The operation of the directional control valves 26, 28 in FIG. 3 essentially corresponds to that of the embodiment shown in FIG. 2, since the volumetric flow delivered by the pumping element 14, 15 is conducted to the respective other hydraulic circuit in its initial position and during a switching operation of the directional control valve 26 or Due to an increasing pressure in the control line 34 or 35, the volume flow is retrieved again into the respective considered hydraulic circuit 8 or 9 and directed to the respective pressure connection 2 or 3.
    In the illustrated embodiment, both directional control valves 26 and 28 are shown in the initial position and is returned directly from the valve of the volume flow diverted from the other hydraulic circuit 9 and 8 via a return line 39 substantially without pressure in the fluid container 11. If, for example, a device 4 is actuated at the pressure port 2 and the fluid pressure thereby increases, a switching process of the directional control valve 26 is effected via the control line 34 and the volume flows of the pumping elements 13, 14 and 17 are supplied to the pressure port 2 in this case. This means an increased operating speed of a device 4 compared to a supply by only one hydraulic circuit 8 alone.
    If an increase in pressure is effected at both pressure ports 2 and 3 by actuation of a connected device 4 or 5, hydraulic fluid is no longer transmitted via the connection lines 27 and 29, and each pressure port 2, 3 is in each case connected through the hydraulic circuit 8 , 9 alone.
    In Fig. 4, a further and optionally independent embodiment of a hydraulic unit 1 is shown, again using the same reference numerals or component designations as in the preceding Figs. 1 to 3 are used. To avoid unnecessary repetition, reference is made to the detailed description in the preceding Figures 1 to 3.
    The hydraulic unit 1 according to FIG. 4 differs from the embodiment in FIG. 3 in the integration of the directional control valves 26 and 28, in which the volume flows delivered by the pumping elements 14 and 17 are effected in the initial position effected by the springs 30 and 31 are provided within the own Hydraulikkreis 8 and 9 at the respective pressure port 2 and 3, respectively underst with a pressure increase in the other hydraulic circuit 9 and 8, a diversion of a volumetric flow takes place. The actuators, which are activated by the control lines 34 and 35, are not shown in Fig. 4 for reasons of space.
    FIG. 4 further shows that optional pressure relief valves 52 can be provided in the hydraulic circuits 8 and 9 in each case upstream of the pressure ports 2 and 3, with which a substantially unpressurized return of hydraulic fluid to the fluid reservoir 11 can be established, in the event that none Device is connected to the respective pressure port 2 or 3. These pressure relief valves 52, which can also be used in other embodiments of the hydraulic unit 1, can be operated manually or else part of a clutch system in which both the fluid supply 6 and the fluid return 7 of the device (see FIG. 1) are connected in a coupling process. The pressure relief valve 52 may be formed in this case as a by-pass valve in the pressure port 2 and 3, respectively.
    FIG. 4 further shows that in each case a pressure limiting valve (DBV) 53 can be arranged downstream of the pumping elements 14, 17, which can be designed as low-pressure elements 42 and 43, which then becomes effective in the illustrated exemplary embodiment. when the hydraulic fluid from the directional valves 26bzw. 28 is diverted to the other hydraulic circuit 9 and 8 respectively and in den¬sem due to a high resistance to working a very high fluid pressure is the vorhan¬. The volume flow of the pumping elements 42 and 43 can be derived in this case via the pressure relief valve 53 into the fluid container 11. As a limit pressure, from which a pressure limiting valve 53 opens, a pressure is selected which corresponds to the switching pressure of the pressure changeover valves 45 and 48, so that the pressure drops the volume flows of the low pressure elements 42, 43 are no longer directed to the pressure ports 2 and 3 respectively. A Druckbegrenzungs¬ valve 53 can structurally the pressure switching valves 45, 48 correspond.
    FIG. 5 shows a further embodiment of a fly-hydraulic unit 1, which is possibly independent of itself, again using the same reference numerals or component designations for the same parts as in the preceding FIGS. 1 to 4. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding FIGS. 1 to 4 or referenced.
    In this embodiment, the operation of the directional control valves 26 and 28 is the same as in the embodiment described with reference to FIG. 3, and a hydraulic circuit 8 where no device is connected to the pressure port 2 or the connected device is idle will be part of the flow of volute to the other hydraulic circuit 9 diverted. The leading to the directional control valve 26 first fluid line 21 leads in this embodiment, not only the volume flow of the pumping element 14, but also the flow of a further Pumpe¬lements 54 and can be redirected via the directional control valve 26 to the other hydraulic circuit 9. While the pumping element 14 is designed as a low-pressure element 42, which has a comparatively high delivery rate, the pump element 54 is designed as a high-pressure element 55, which has a comparatively small delivery rate. In the illustrated position of the directional control valve 26, both volume flows of the pumping elements 14 and 54 are thus diverted via the first connection line 27 to the second hydraulic circuit 9. If no elevated volume flow is required in this, since the connected device is idling, this redirected flow is discharged via the return line 39 to the fluid tank 11. At a pressure increase in the second hydraulic circuit 9, this volume flow is directed to the second pressure port 3, since the second
    Directional valve 28 is switched via the control line 35 of the second hydraulic circuit. At the pressure port 3, the delivery rate of the second hydraulic circuit 9 is thus increased by the delivery rate of the pumping elements 14 and 54. In a further increase in pressure in the second hydraulic circuit 9, which causes a transition to the high pressure region, the volume flow of the Pumpen¬lements 14, which is yes designed as a low pressure element 42, via the pressure switching valve 45 directly into the fluid reservoir 11 is derived and only the Vo ¬ Lumenstrom of the pumping element 54, which is designed as a high pressure element 55, redirected to the second hydraulic circuit 9. Thus, even at high pressure operation at the second pressure port 3 of the hydraulic circuit 9, a flow rate increased by the volume flow of the high pressure element 55 is available.
    Similarly, an additional pumping element 56 is arranged in the second hydraulic circuit 9, which is designed as a high-pressure element 57 and the volumetric flow provided at the pressure port 2 of the first hydraulic circuit 8 can be increased by the delivery rate of this high-pressure element 57 and possibly also by the volumetric flow of the low-pressure element 43 in the second hydraulic circuit 9. By this embodiment, in which even at high working resistance and high pressure level, a volume flow can be redirected from the non-active hydraulic circuit to the other hydraulic circuit, even at high Arbeitswi¬derstand the power of the drive 18 can be optimally utilized and the working speed of a device even at high working resistance be maximized.
    The control of the pressure switching valves 45 and 48 via Steuerleitun¬gen 46 and 49 with the force acting on the high pressure elements 55 and 57 fluid pressure.
    FIG. 6 shows another embodiment of a hydraulic unit 1, which may be independent of itself, and in which again identical reference numerals or component designations are used for the same parts as in the preceding FIGS. 1 to 5. To avoid unnecessary repetition, reference is made to the detailed description in the preceding FIGS. 1 to 5 or referenced.
    In this embodiment of the hydraulic unit 1, the volume flow provided at a pressure connection can, if required, be increased by the delivery rate of all pump elements of another hydraulic circuit.
    In the exemplary embodiment according to FIG. 6, for example, the volume flow of the pumping elements 13 and 14 can be diverted via the path element 26 to the second hydraulic circuit 9, whereby the control of the volume flow of the pump element 14, which can be designed as a low-pressure element 42, takes place on the basis of the preceding exemplary embodiments , For diverting the volume flow of the pumping element 13, which is designed as a high-pressure element 40, serves a in the first fluid line 20 arranged shut-off valve 58 and a between pumping element 13 and shut-off valve 58 and leading to another first fluid line 21 leading transition line 59. The shut-off valve 58 is in its durcheine A shut-off of the shut-off valve 58 by means of a control line 61 which leads from the second fluid line 23 in the second hydraulic circuit 9 to the check valve 58.With a pressure increase in the second Hydraulic circuit 9 so the first Fluidlei¬ line 20 is shut off from the pumping element 13 to the pressure port 2 and the Volu¬menstrom the pumping element 13 via the transition line 59 to the directional control valve 26, from which it passes through the first connecting line 27 to the second hydraulic circuit 9 in a row , By analogous design of the second hydraulic circuit 9 with a shut-off valve 62, a transition line 63 and a spring 64, the volumetric flow of the pumping element 16 can be redirected to the first hydraulic circuit 8 analogously.
    In this way, the volume flows of other unillustrated pumping elements can be requested from each other hydraulic circuit and thereby automatically the amount of delivery provided at the respective pressure connection can be increased.
    Because both hydraulic circuits 8 and 9 have such a transfer function or diversion function in the exemplary embodiment shown, only the hydraulic circuit that requests the volume flow of the other pump elements before the other hydraulic circuit can provide the increased delivery rate at the pressure port. The activation of the shut-off valves 58, 62 is carried out at a pressure below about 25 bar, whereby at non-actuated devices, so in idle mode, the required base pressure is available at both pressure ports and the respectively earlier activated device provided the flow of all Pumpelemen¬te available gets.
    In the transition lines 59 and 60 Drosselele¬mente 65 are also advantageously arranged 66 and 66, with which in the first fluid line 20 and derzweiten second fluid line 23, a back pressure is built up for the optionally required control of the directional control valves 26, 28 and the shut-off valves 58th , 62dient.
    The hydraulic fluid 10 advantageously passes via suction lines from the fluid reservoir 11 to the pumping elements.
    The exemplary embodiments show possible design variants of the hydraulic unit 1, wherein it should be noted at this point that the invention is not limited to the specific embodiments shown, but also various combinations of the individual embodiments are possible with each other and this possibility of variation is based on the teaching of technical practice by objective invention within the skill of those skilled in this technical field.
    Furthermore, individual features or combinations of features from the different embodiments shown and described can also represent solutions that are inventive, inventive or inventive.
    The problem underlying the independent inventive solutions can be taken from the description. All statements on ranges of values in the description given herein are to be understood as including any and all subsections thereof, for example, the indication 1 to 10 should be understood as encompassing all subranges, starting from the lower bound 1 and the upper bound 10, i. all subregions begin with a lower limit of 1 or greater and end at an upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.
    Finally, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component designations, wherein the disclosures contained in the entire description mutatis mutandis to the same parts with the same Bezugsbe or. same component names can be transferred. Also, the location information chosen in the description, such as up, down, laterally, etc. related to the directly described and illustrated figure and these conditions are to be transferred in a change in position mutatis mutandis to the new situation.
    Above all, the individual in Figs. 1; 2; 3; 4; 5; The embodiments shown in FIG. 6 form the subject of independent solutions according to the invention. The related objects and solutions according to the invention can be found in the detailed descriptions of these figures.
    For the sake of order, it should finally be pointed out that for a better understanding of the structure of the hydraulic unit 1, this or its constituent parts have been shown partly unevenly and / or enlarged and / or reduced in size.
    List of Reference Numerals 1 Hydraulic unit 31 Spring 2 Pressure connection 32 Actuator 3 Pressure connection 33 Actuator 4 Device 34 Control line 5 Device 35 Control line 6 Fluid supply 36 Recovery device 7 Fluid return 37 Switching valve 8 Hydraulic circuit 38 Return connection 9 Hydraulic circuit 39 Return line 10 Hydraulic fluid 40 Floch pressure element 11 Fluid reservoir 41 Floch pressure element 12 Pump arrangement 42 Low pressure element 13 Pump element 43 Low pressure element 14 Pumping element 44 Check valve 15 Pump arrangement 45 Pressure changeover valve 16 Pump element 46 Control line 17 Pump element 47 Spring 18 Drive 48 Pressure changeover valve 19 Internal combustion engine 49 Control line 20 First fluid line 50 Spring 21 First fluid line 51 Pressure limiting valve 22 First manifold 52 Pressure relief valve 23 Second fluid line 53 Pressure relief valve 24 Second fluid line 54 Pump element 25 Second manifold 55 High pressure element 26 First directional valve 56 Pump element 27 First connection Suction line 57 High-pressure element 28 Second-way valve 58 Shut-off valve 29 Second connecting line 59 Transition line 30 Spring 60 Spring 61 Control line 62 Shut-off valve 63 Transition line 64 Spring 65 Throttling element 66 Throttling element
    权利要求:
    Claims (13)
    [1]
    1. Hydraulic unit (1) with at least two pressure connections (2, 3) for demand-supply of one or more hydraulically driven devices (4, 5), in particular hydraulic rescue equipment, with hydraulic fluid (10) from a fluid container (11) comprising a first hydraulic circuit (8) with a first pump arrangement (12) comprising at least two first pump elements (13, 14), of which first fluid lines (20, 21) lead to a first pressure port (2), at least one second hydraulic circuit (9) with a second pump arrangement (15) from at least two second pump elements (16, 17) lead from second fluid lines (23, 24) to a second pressure port (3), the first pump elements (13, 14) and the second pump elements (16, 17 ) are simultaneously driven by a common drive (18), and wherein by means of a first directional valve (26) at least one of the first fluid lines (21) via a first connecting line (27) with a second fluid line (24) in the second hydraulic circuit (9) connectable and by means of a second directional control valve (28) at least one of the second fluid lines (24) via a second Verbindungslei¬ (29) with a first fluid line (21) in the first hydraulic circuit (8) is connectable , characterized in that the directional control valves (26, 28) have a spring (30, 31) acting in the direction of an initial position and a first control line (34) from the first hydraulic circuit (8) or from the second hydraulic circuit (9) to ei¬nem extending from the second hydraulic circuit (9) or the first hydraulic circuit (8) a second control line (35) to a second actuator (33) acting on the second directional control valve (28).
    [2]
    Second hydraulic unit (1) according to claim 1, characterized in that the first and / or second control line (34, 35) is formed as a hydraulic control line and acts directly or by means of a pilot valve on the second or first directional control valve (28, 26).
    [3]
    3. Hydraulic unit (1) according to claim 1, characterized in that the first and / or second control line (34, 35) is designed as an electrical control line and by means of an electromagnetic actuator directly or with pilot control member on the second directional control valve or first Directional control valve (28, 26) acts.
    [4]
    4. Hydraulic unit (1) according to one of claims 1 to 3, characterized ge indicates that the first pumping elements (13,14) at least one Hochdru¬ckelement (40) with a smaller flow rate at a reference intensity of the drive (18) and at least one Low pressure element (42) with a larger flow rate at the reference intensity comprise and the second pump elements (16,17) comprise at least one high pressure element (41) with a smaller flow rate and at least one Nieder¬druckelement (43) with a larger flow and the directional control valves (26,28) in the from the low pressure elements (42, 43) outgoing fluid lines (21,24) are arranged.
    [5]
    5. Hydraulic unit (1) according to claim 4, characterized in that the delivery rate of the low pressure elements (42, 43) of a hydraulic circuit (8, 9) is at least twice the delivery rate of the high pressure elements (40, 41) of the same hydraulic circuit (8, 9).
    [6]
    6. Hydraulic unit (1) according to one of claims 1 to 5 characterized ge characterized in that in the initial position of the directional control valves (26, 28) of theseein flow path from the respective fluid line (21,24) of the one hydraulic circuit (8, 9) Connecting line (27, 29) to the other hydraulic circuit (9, 8) is opened.
    [7]
    7. Hydraulic unit (1) according to one of claims 1 to 6, characterized ge indicates that the first connecting line (27) from the first directional control valve (26) to the second directional control valve (28) and the second connecting line (29) from the second directional control valve (28 ) to the first directional control valve (26), the second directional control valve (28) providing a flow path from the first connection line (27) in a first switching position to a second fluid line (24) leading to the second pressure connection (3) and to the fluid container (11) in another switching position and the first directional control valve (26) can produce a flow path from the second connecting line (29) in a first switching position to a first fluid line (21) leading to the first pressure connection (2) and to the fluid container (11) in a further switching position. can produce
    [8]
    8. Flydraulikaggregat (1) according to claim 7, characterized in that a hydraulic circuit (8) comprises at least two high-pressure elements (40, 55), at least one of which via a fluid line (20) directly to the pressure port (2) is connected and at least one via the directional control valve (26) with another hydraulic circuit (9) is connectable.
    [9]
    9. Hydraulic unit (1) according to one of claims 1 to 8, characterized ge indicates that all the first fluid lines (21,22) by means of one or more first directional control valves (26) and by means of one or more first Verbin¬dungsleitungen (27 , 59) with at least one second fluid line (23, 24) of the second hydraulic circuit (9) and / or all second fluid lines (23, 24) by means of one or more second directional control valves (28) and by means of one or more second connecting lines (29, 63) with at least a first fluid line (20,21) of the first hydraulic circuit (8) are connectable.
    [10]
    10. Hydraulic unit (1) according to one of claims 1 to 9, characterized in that in one of the fluid lines (21) of a hydraulic circuit (8) is arranged downstream of a pumping element (14) a pressure switching valve (45) via a pressure control line (46) is actuated from a different fluid line (20) of the same hydraulic circuit (8), whereby a flow path from the pump element (14) to the fluid container (11) is triggered by the pressure changeover valve (45) when the pressure rises in the other fluid line (20) ) will be produced.
    [11]
    11. Hydraulic unit (1) according to one of claims 1 to 10, characterized ge indicates that the first pumping elements (13, 14) and the second Pumpele¬mente (16,17) are arranged to each other as in a radial piston pump.
    [12]
    12. Hydraulic unit (1) according to one of claims 1 to 11, characterized in that of the pumping elements (13, 14, 16, 17, 40, 41, 42, 43, 54, 55, 56, 57) suction lines in the Lead fluid container (11).
    [13]
    13. A method for supplying to at least two hydraulically drivable devices (4, 5), in particular hydraulic rescue equipment, with Hydraulik¬ fluid (10) by means of a hydraulic unit (1) with at least two Druckanschlüs¬sen (2, 3) at in which in a first hydraulic circuit (8) with a first pump arrangement (12) by means of first fluid lines (20, 21) volume flows of at least two first pumping elements (13, 14) are combined and fed to a first pressure port (2) and in a second hydraulic circuit (9) with a second pump arrangement (15) by means of second fluid lines (23, 24) the volume flows of at least two second pumping elements (16, 17) are combined and directed to a second pressure connection (3), the first pumping elements (13, 14) and the second pumping elements (16, 17) are simultaneously driven by a common drive (18) and wherein, for the purpose of allocating the volume flows to the pressure connections (2, 3), m at least one of the first fluid lines (21) is connected via a first connecting line (27) to a second fluid line (24) in the second hydraulic circuit (9) and to at least one of the second fluid lines (28) by means of a second directional valve (28). 24) via a second connecting line (29) with a first fluid line (21) in the first hydraulic circuit (8) is connected, characterized in that the directional control valves (26, 28) by means of a spring (30, 31) are moved to an initial position and a switching operation of the first directional control valve (26) by a first actuating member (32) which is controlled by a first control line (34) emanating from the first hydraulic circuit (8) or from the second hydraulic circuit (9) and extending to the first actuating member (32) is, and a switching operation of the second directional control valve (28) by a zweit¬tes actuator (33), of one of the second hydraulic circuit (9) or vomersten hydraulic circuit (8) outgoing and the second actuating member (33) extending second control line (35) is actuated, is effected.
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    同族专利:
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    US20160102687A1|2016-04-14|
    US10041508B2|2018-08-07|
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    EP3012463A1|2016-04-27|
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    法律状态:
    优先权:
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