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    • 专利摘要:
    In a hydraulic circuit for controlling a hydraulically driven machine (2), a displacement control (10) and a valve control (14) are connected in fluidic parallel. The displacement control (10) has a hydraulic machine (18) with two connections (A1, A2), which are connected to the machine (2) via a respective flow path (30, 32) to form a closed hydraulic circuit. The valve control (14) is connected to the engine (2) in an open hydraulic circuit. It is provided that the displacement control (10) provides the majority of the hydraulic drive power and thus the amount of fluid, while the valve control (10) compensates for deviations from a predetermined pressure, travel or speed control curve.
    公开号:AT516316A2
    申请号:T50805/2015
    申请日:2015-09-21
    公开日:2016-04-15
    发明作者:Rolf Heidenfelder
    申请人:Bosch Gmbh Robert；
    IPC主号:
    专利说明:

    HvdrauSSsche circuit Lind machine with a hydraulic circuit description
    The invention is based on a hydraulic circuit, for controlling a hydraulically driven machine or for controlling a hydraulic consumer. Furthermore, the invention relates to a machine with at least one hydraulic consumer, which is controllable via a hydraulic circuit
    From the post-published DE 10 2012 019 665 a hydraulic circuit for controlling a press is disclosed. This is, for example, a punching machine, a stamping machine, or a depth-forming machine for producing workpieces having upper and lower dies for imparting a pressing force to a workpiece. The hydraulic circuit here comprises a displacement control and a valve control.
    Furthermore, known from the prior art dynamic cylinder systems or actuators (Gleichgangü or Differenzenüalzzylinder) for die cushion applications or punch / Nibbelapplikationen with which a position and Kraftregeiung at least one cylinder takes place. For this purpose, highly dynamic servo-valves are used for control, which are designed for large Voiumenströme and high pressures and are provided in control plates. The control plates disadvantageously have an extremely large space requirement and have a high, heavyweight, the control plates can be arranged directly on a cylinder to be controlled. For Druckmitteiversorgung large hydraulic accumulator are provided, which are usually arranged directly on a Steuerpiattenderweisenden control block of the Zyiinder. For charging the hydraulic accumulators supply units with pressure-regulating pumps or constant-displacement pumps with a pressure switch and a charging device may be provided. The supply unit is fluidly and spatially disputed by the cylinder and control block. The supply unit is a simple and large-bore engine pump trap with high performance (for example, 150 to 25 kilowatts in draw cushion application). For this purpose, a large space-consuming Kühier-Fiiter-Kreisiäufe be used (at spie is wise with a power of 300 to 500kW in the Ziefikissenappiikation) and tanks (for example, with a capacity of 6000 to 12000 liters in Ziehkissenappiikation). The supply and control of the cylinder or cylinders then takes place via the servo-valves, which thus regulate large Voiumenströme (Qmax) and are designed for large pressure differences (delta-p-max), as already explained above. In the case of regulation, a high loss performance occurs disadvantageously, which leads to the cancellation of the pressure medium or of the oil and, moreover, causes a rapid aging of the oil.
    It is an object of the present invention; to provide a hyrauliische circuit, with the device-technically simple way a hydraulically driven machine is highly dynamic and controllable with high accuracy and eliminates the mentioned disadvantages. Furthermore, it is an object of the invention to provide a hydraulic driven machine with such a hydraulic circuit.
    The object with regard to the hydraulic circuit is achieved according to the features of claim 1 and with regard to the hydraulically driven machine according to the features of claim 1.
    Other advantageous developments of the invention are subject matter of further subclaims.
    According to the invention, a hydraulic circuit is provided for controlling a hydraulically-indicated machine, in particular a press, in particular a draw-cushion after a mechanical press, in particular a punch axis in a nibbling machine. The circuit; has a positive displacement control and a valve control, which are fluidly arranged parallel to each other. The displacer control has a displacer, in particular a hydromachine which is preferably replaceable in four-quadrant operation with two connections, preferably each of which supplies pressure medium and is dischargeable. A respective connection of the hydromachine is in each case connected to the hydraulically operated machine via a flow path. with which trapped hydraulic circuit can be formed. In contrast, the valve control is connectable to the machine in an open hydraulic circuit. Thus, the valve control is operated as an open circuit;
    This solution enables highly dynamic energy-optimized control of the hydraulically driven machine. For example, if the engine has a cylinder, it can be quickly retracted and retracted by the decanter control. Parallel valve control can then provide active, accurate control of the cylinder across the open circuit (on and off vofumen / pressure). If the valve control is usually much more compact than the displacement control, it can be fluidly closer to the cylinder of the hydraulically driven machine in a technically simple manner, thus shortening hydraulic flow paths. and there is a higher hydraulic stiffness between the valve control and the hydraulically-resistant machine, which in turn increases the quality of the control. Thus, by the hydraulic control, optimum control performance is achieved by shortening the "hydraulic springs" 1.
    With the circuit according to the invention, it is thus possible to operate high dynamic cylinder systems, such as for example cushioned applications, with very small valve control, which significantly reduces the loss of fit compared to the prior art explained in the introduction. A speed of the applications may, for example, be between 500 and 1500 mm / s and / or maximum attainment of the applications may be achieved on the shortest paths, such as 5 to 10 mm, and / or reaching the maximum speed of the application in the shortest times, such as 5 up to 10 ms, and / or a maximum application force can be achieved in the shortest times, such as 5 to 10 ms, for example, where the maximum force can be 20, 50, 100, 150 or 200 tons.
    With the circuit according to the invention can, as already stated, forhch dynamic cylinder systems, such as ZiehkbsenappllKationen or punching / Nibbelapplikationen, a comparatively small space having
    Valve control be used. In the prior art, valves for such applications are commonly used in the 25.50, or 63 nominal sizes. According to the invention, these are now replaced by the displacer, which is preferably large, low in wear and highly dynamic. For example, a motor of the company Häggiunds may be used as the hybraulic motor, which preferably conveys 1.2 or 5 yards / revolution. Preferably, the positive displacement control is designed in such a way. for example, it has a high lift volume at low speed, for example, about 5o rev / min gives about 2500 l / min. Such comparatively low speeds, say, for example, about 500 n / min, can be achieved faster than previously conventional speeds of about 3000 n / min.
    The solution according to the invention also has the advantage that the hydraulic accumulators or supply reservoirs designed for high pressure, which are designed for the beginning, can be replaced, for example, with a capacity of 20 to 1QG liter. As a substitute small hydraulic accumulator (high-pressure accumulator) can be used, for example, have between about 2 to 4 liters. A small hydraulic accumulator is sufficient to control the valve - for example a regulator / servo-valve! in the nominal size β or 10 »has to be supplied actively with Druckmittei. For the positive displacement control, a hydraulic accumulator (Vorspannspeicher) for the preparation of a universal supply, especially on the low pressure side. be provided, for example, 4 to 10 liters aufwesst. In addition, a small pressure control pump or constant pump may be provided for the storage charge. Thus, unlike the prior art, only two comparatively small hydraulic accumulators are used - one for the diverter control and one for the valve control. To regulate the hydraulic accumulator, in contrast to the prior art, only small pumps are necessary and thus only small pumps driving the pumps with comparatively low power.
    Furthermore, in the solution according to the invention, it is advantageous that, compared to the prior art, due to the comparatively small valve control, considerably less energy is destroyed at a maximum volume flow (Qmax) and at a maximum pressure difference (delta-p-mä'x). becomes.' Thus, a cooler-Filfer-Kreisiauf, for example, with a water supply, be made much smaller.
    Außerdeäm is advantageous in the inventive solution that only a small tank is required.
    In a further embodiment of the invention, during the provision of a hydraulic drive power of the positive displacement at the same time as the valve control, a deviation from a predetermined pressure control curve and / or a travel control curve and / or a speed control curve can be compensated. Thus, for example, large displacement speeds and thus large volume flows for controlling the hydraulically driven machine are possible with the displacement control. At the same time, regeia tasks can be optimally fulfilled with the highly dynamic valve control, in particular through short switching and control times.
    The Ds® positive displacement control is preferably designed to provide a majority of the drive power for the hydraulic powered machine.
    The valve control is preferably designed so that it can not provide the majority of the drive power for the hydraulic driven machine.
    Preferably, the hydraulic machine is designed such that it has a comparatively low inertia and thus high dynamics and a comparatively large displacement. Due to the large displacement, this is advantageously antrefobar with a vergieichweisegeringen speed. In a further embodiment of the invention, the hydraulic machine can be of a; This is preferably designed so that it has a relatively low inertia and thus a high dynamic and with a vergichichweise low speed is replaceable. The combination with low-inertia and large-volume Hydromachine leads to a positive displacement control, which is able to steer with high dynamics (number of cycles) and with a high speed the hydraulically driven machine. Thus, for example, a cylinder of the machine can be extended or retracted with high dynamics and speed. A change in a direction of rotation of the hydraulic machine can also be extremely fast here. The electric motor is, for example, a highly dynamic torque motor or servomotor. Such a hydraulic machine in combination with an electric motor is known, for example, from the subsequently published document DE 10 2013 221 410, in combination with the valve control, a high-dynamics control of the hydraulically driven machine can thereby be effected. For the electric motor, an "intelligent" regenerable Anthsb may be provided (HCS),
    Preferably, the electric motor serves for the main control and possibly also for the regulation of the hydraulically driven machine. The valve control can then have a "control / servo" valve, which in addition can actively control the machine most dynamically, and which is designed to cover what the displacement control can not physically and technically do. A nominal size of the valve is, for example, 6 or 10. "Active control" means preferably that up to the maximum pressure active pressure medium is supplied to the machine and discharged from the machine.
    The valve control preferably has a control valve. This can then be used to control the open circuit. The control valve is in this case preferably designed such that it has high dynamics and high accuracy with regard to a quantity of pressure medium to be controlled. Thus, advantageously, the valve control is used for precise control of the hydraulically specified machine. Furthermore, the control valve can easily be arranged very close to the hydraulically driven machine because it has a small space requirement compared to the hydraulic machine and the electric motor and compared with the previously described valves. For example, the control valve is a servo control valve ,
    Advantageously, the control valve is located as close as possible to the hydraulically driven machine. Since the valve control an extremely compact size and thus a small control disk or a Having small control block, it fiuidisch and spatially closer to the hydraulic machine compared to the state of the art ngeordne become. The "hydraulic spring" between the valve assembly and the machine is extremely short.
    Preferably, the Regelvenii! in a further embodiment, two working connections, a pressure connection and a tank connection. The Arbeltsanschiüsse can then with the hydraulic machined machine, for example, each with a working space of a
    Cylinder connected. In a first position, the first working flange can be connected to the tank connection and the second working flange can be connectable to the pressure flange via a valve slide of the control valve, and in second positions the second working flange can be connected to the tank connection and the first working connection to the pressure flange. It is conceivable that the Eeael valve includes third seats, which are preferably provided between first and second displays. For example, in the third display, the vent selector may connect all ports in a throttled manner, which allows the hydraulic driven machine or cylinder to be pressure compensated as a safety measure. Preferably, the Veniiischieber the Regeiventils is continuously adjustable.
    In a further embodiment of the invention, a Absehaltventii, which is preferably designed as a switching valve is provided. With this, the control valve can be decoupled from the hydraulic machine. Preferably, the Abschaitventii is fluidly disposed between the Regeivenlii and the machine.
    The shut-off valve may have two input ports with a respective input port connected to a respective working port of the throttle valve. Said the shut-off valve may have two working ports connected to the engine
    Advantageously, a hydraulic accumulator is connected to the pressure connection of the control valve. This can be designed such that a required working pressure for the hydraulically driven machine is available. Preferably, the hydraulic accumulator is a high pressure accumulator. The hydraulic accumulator can, for example, via a drain valve and / or upper a pressure relief valve! be connected to a tank. Furthermore, a pressure gauge may be provided for the high-pressure accumulator.
    Alternatively or in addition to the hydraulic accumulator, a hydraulic pump can be connected to the pressure flange of the control unit. The hydraulic pump is preferably a pressure-flow-controlled hydraulic pump. Preferably, a check valve is disposed between the hydraulic pump and the pressure flange of the control valve, which opens in the direction of pressure flow towards the regulator. In a further aspect of the invention, there is provided a pre-cooling means whereby one of the flow paths or both flow paths are hydraulically biasable at a predetermined pressure. The biasing device may be connected to one of the flow paths via a check valve or connected to a respective flow path via a check valve. The check valve in this case opens in a pressure medium flow direction towards the flow path. Preferably, the biasing device has a hydraulic accumulator which is connected to one or both flow paths. The connection is made via the check valve or check valves. The hydraulic accumulator can be connected to a tank via a drain valve and / or via a pressure limiting valve. In addition, preferably, a pressure gauge is provided. In another embodiment of the invention, the hydraulic accumulator is designed in such a way that a required preload pressure is available, with which the hydraulic accumulator is preferably a low-pressure accumulator. Alternatively or in addition to the hydraulic accumulator, a valve, in particular a pressure reducing valve, can be provided for prestressing. To apply the biasing pressure, this is connected to a hydraulic pump, in particular to a constant displacement pump.
    For rinsing the hydraulic circuit, a flushing device is provided, which is connected to at least one flow path and can be discharged via the pressure means from at least one beating pitch. The flushing device may be designed such that an influence on the pressure regulation and / or travel control and / or speed control of the machine is comparatively low or avoided. The control of the flushing device, ie a flushing operation, for example, takes place during a work piece during operation of the machine or if the cylinder should "stand still". inPositlonsregeiung, which is deactivated in the actual factory processing lse Spülvorrichtung and does not adversely affect the scheme. The purging device is connected to the flow path via an adjustable throttle, when it is attached to both flow paths, it is connected to it via an adjustable throttle. Furthermore, the flushing device has a flushing valve. with which a Druckmiiteiverblndung between one or both flow paths to a tank on and is controllable. The throttles are preferably located between the si matic flow paths and the purge line. The Spülventii example, manually or electromagnetically or hydraulically actu bar beh. Also conceivable is the Spoivenii! to be used as a safety valve on pressure relief.
    Preferably, the displacement control and the valve control are each double-secured and monitored. There may be one (or two) safety valves in one or both of the machine flow paths and the valve control. In this case, in a closed state of the safety valve, the associated flow path can be blocked and, in an opened state of the safety valve, the associated flow path can be opened. If a safety valve is provided for each respective flow path, then the hydromechanically äh driven machine flow table may be blocked in the event of blocked flow paths through the safety device. The safety valve or a respective safety valve can be opened and closed via an end valve. Actually, it is generei intended that you 2x times in a row (112.114), the safety valves, in both flow paths: -: -: -: -: - (68.70) depending on the required performance level or safety category, install and must !
    The safety valves in combination with the Ahschaitventii and / or with the third position of the Regeiventiis can then form a double or triple hedge for the valve control.
    The safety valves in combination with an electrical protective circuit for the displacement control also lead to a double protection. The protection circuit may be provided in a drive of the hydraulic machine. The protection circuit, for example, provides for safe drive release of the drive of the hydraulic machine. Furthermore, for example, a protective brake can be controllable on the electric motor drivable by the hydraulic machine with the protective shield.
    Preferably, a valve element of a respective safety valve, which may be designed as a logic valve, in the closing direction via a first pressure chamber (Zyiinöerraum) acted upon with pressure medium and further in üffnungsrlchiung a second pressure chamber (annulus) with pressure medium acted upon. Above the respective end valve, the first pressure chamber and the second pressure chamber of a respective logic valve can be connectable alternately to a tank or a pressure medium source.
    Furthermore, an interchangeable valve having an output flange and two input ports connecting the highest pressure input flange to the output flange may be provided. A respective end-to-end valve may be connected to the output flange to connect the output flange to one of the pressure chambers of a respective logic valve. The biasing system may then be connected to the first input port of the changeover valve and to the second input port of one of the firing paths.
    Advantageously, the flow paths can be connected to one another via at least one pressure limiting valve. The pressure relief valve is, for example, a pilot-operated pressure relief valve with a relief. The discharge is preferably accomplished by a disconnection vsnUi. In the closing direction, a valve of the pressure-limiting valve may be susceptible to the pressure of the hydraulic accumulator of the valve control. In a further embodiment of the invention, the Sirömungspfade überzwei Druckbegrenzyngsventiie be connected, which are ausgegebiidet according to the above explained aspects. The one pressure limiting valve! In this case, it can be actuated by the pressure medium in the first flow path and the other pressure limiting valve by the pressure medium of the second flow path.
    Advantageously, a further pressure limiting valve is provided, via which a flow path or both flow paths to the tank can be relieved. This may be implemented in accordance with one or more aspects of the above-described pressure relief valves.
    With a respective flow path, the pressure limiting valve is connected via a check valve, which respectively close in Druckmiteigömungsrichtung towards the flow path.
    According to the invention, a hydraulic driven machine has a hydraulic cylinder controlled by a circuit according to one of the preceding aspects.
    There may be provided a second hydraulic cylinder, which is also controlled by a circuit according to one of the preceding aspects.
    By way of example, the cylinder is a D-type finned or semi-finished cylinder, and in the case of a G leichga ngzyl Indian, there is probably no need for a delta decompression.
    Advantageously, the machine is a mechanical press and a cylinder forms a die cushion axis.
    Alternatively, the machine may be a nibble machine.
    Several embodiments of an inventive hydraulic circuit and a hydraulically indicated machine according to the invention are shown in the drawings. With reference to the figures of these drawings, the invention will now be explained in more detail.
    Show it
    1 shows a Schaltpian a hydraulic circuit according to the invention according to a first Ausführungsbeispiei,
    FIG. 2 is a diagram of a hydraulic circuit according to a second embodiment;
    FIGS. 3a to 3c each show a hydraulic circuit of a part of a hydraulic ...... bearing according to a third exemplary embodiment,
    FIGS. 4 and 5 each show a lift curve, a speed curve and a force curve, respectively, plotted over time and an operation of the hydraulic circuit I a | eigen |
    6 shows a Schaltpian the hydraulic circuit according to the invention according to a further embodiment,
    According to FIG. 1, a hydraulically driven machine 1 has a first cylinder 2 and a second cylinder 4. The machine 1 is, for example, a mechanical press, wherein the cylinder 4 can form a die cushion axis. The first cylinder 2 is controlled via a first hydraulic shank 6 and the second cylinder 4 via a second substantially identical hydraulic sheath 8. The hydraulic shafts 8 and 8 each have a displacement control 10 or 12 and a valve control 14 or Ϊ6. The displacement control 10,12 and the
    Valve control 14, 16 of a respective circuit 6, 8 are in this case arranged in fluid-parallel relationship to one another.
    The design of the circuits 8, 8 will now be explained in more detail below with reference to the circuit 8 of the cylinder 2. The displacer controller 10 has a hydraulic machine 18 which can be seen in the 4-quadrant bed. It is designed so that it has a large displacement and a low inertia. Further, the hydraulic machine 18 requested two ports AI, A2. It is drivable at a low speed by a controlled electric motor. This is a Torquemstor with a low inertia, Furthermore, this is designed so that it can be used at a low speed. Due to the low inertia and the low speeds, the Terikeotor thus has a high dynamic. The combination of the electric motor 20 with the hydraulic machine 18, which are designed according to the vorbeschrieherers way leads to a Vorredriebresusrung .. with the Within a short time high Volurnenströme can be converted, with which a piston 22 of the cylinder 2 with a high speed and retractable. Furthermore, fast changes in direction of the piston can result,
    According to FIG. 1, the piston 22 is connected on one side to a piston rod 24. The piston 22 separates in the cylinder 2 a first cylinder chamber 26 from a second cylinder chamber 28. In this case, the first cylinder space 26 is connected to the connection AI via a flow path 30 and to the connection Ä2 of the hydraulic machine 18 via a second flow path 32. The displacement control 10 thus forms with the cylinder 2 a closed hydraulic circuit.
    To the flow paths 30, 32 and the valve control 14 is completed, which is thus fiuidisch arranged parallel to the displacement control 10. The valve controller 14 has one-way adjustable control valve 34 (servo control valve). Via a working flange A, the control valve 34 is connected to the flow path 30 and via a working connection B to the flow path 32. Further, it is connected to a pressurized oil passage via a pressure port P and to a tank via a port T, and in the centered neutral positions 0 (third port position), a spool valve of the regulating valve 34 connects the ports A.B. P and I to each other. Based on the foundation 0, the " Valve slide of the control valve 34 in the direction of the first
    In this case, the printing end P is connected to the working flange B and the working end A is connected to the dancer T. If the valve slide is displaced in the opposite direction to the second show position b starting from the home positions δ, the pressure port P is connected to the working port A and the working flange B is connected to the tank port T. The control valve 34 is hereby designed such that it has very large courses of sound and registers. Since the hydraulic unit 18 has a large displacement and is thus available for the majority of the power of the cylinder 2, the control valve 34 can be made comparatively small. It is thus hochdynarnssch operable and has low switching and Regelzeiisn. Due to the small space requirement of the Regeiventils34 it can be flexibly arranged device-technically flexible to the cylinder 2 and thus also fluidly seen to be provided extremely close to the cylinder 2, resulting in a high hydraulic stiffness and thus to a high control quality of the cylinder 2. The steering valve 34 is hydraulically actuated, for example.
    For example, the piston 22 of the cylinder 2 is an upper piston, and a piston 38 of the cylinder 4 may be a LM piston cooperating to machine a workpiece.
    Referring to Fig. 2, a machine 38 has requested a cylinder 40 which is configured as a Gypsum Cylinder or Upright Gieichgangzyäsnder. Furthermore, it has a cylinder 42, which is also ausgestaitet as Gleichgangzylinder or sub-piston Gleichgleichzylinder. The cylinders 40, 42 are each controlled by a valve control, which are respectively arranged in a control block 46 and 48, Fiuidlsch parallel to the valve control is provided for a respective cylinder 40, 42, a displacement control 50 and 52, respectively. The valve control of the fire bus 46 and the displacement control SD are supplied by a power supply 54. The same applies to the valve control of the control block 48 and the displacement control 52, which are provided by a leakage control 56. For hydraulic supply of the valve controls in the control blocks 48, 48, a hydraulic supply unit 58 is provided. To control the hydraulic supply unit 58 and the valve controls of the control blocks 46 and 48, a control cabinet 80 with a logic and control unit is provided. Over a respective cylinder 40, 42 a mass 62 or 64 can be moved in each case. FIG. 3 a shows a hydraulic circuit 65 of a master piston. The cylinder or cylinder 66 is designed as a passage gear cylinder. Via a first flow path 68, it is connected to a port A1 of the hydraulic machine 18 and via a second flow path 70 to port A2 of the hydraulic machine 18. The hydraulic machine 18 is driven by an electric motor 20. Fluidically parailel valve control is provided with the control valve 34. In this case, a check valve 72, which opens in the pressure medium flow direction to the control valve 34, has an adjustable hydraulic pump 74, see FIG. 3c, connected to the pressure flange P. Between the check valve 72 and the control valve 34 there is connected a hydraulic accumulator 78, which is a high pressure accumulator. This is above a pressure limiting valve 78 to a tank 80, as shown in FIG. 3 c, above the hydraulic accumulator 76, a discharge valve 82 for discharging pressure medium to the tank 80. ...... assigned.
    The actuator shafts A, 8 of the control valve 34 are connected to the first and second flow paths 68, 70, respectively, via a shut-off valve 84 designed as a switching valve. The Abschaltventii 84 has a port X, which is connected to the Arbeitsanschususs Ades control valve 34 and a port Y, which is connected to the Arbeitsanschuuss 8 of the Regelventüs 34, via a Arbeitsanschuuss A Abschaltventii 84 with the second flow path 70 and a working port B with connected to the first flow path 88, in a first switching pitch of the shut-off valve 84, the ports A, B, X and Y are separated from each other. In a second display position, the working flange A is connected to the connection X and the working flange 3 is connected to the connection Y, in this display position the control valve 34 is thus connected to the flow paths 70 and 68, respectively, with its sleeve flange A.B.
    Further, the hydraulic circuit 65 has a hydraulic biasing device 88, which has a pressure reducing valve 88 having a pressure port P, a tank flange T, and a working port A. To the Druckanschius P is a constant pump 90.siehe figure 3c, connected. The tank connection T is connected to the tank 30 of FIG. 3c. Between the pressure port P and the Konsfantpumpe 90 a hinürnDruckreduzierventii 88 opening check valve 92 is arranged. Above the working port A is the pressure reducing valve 88 having the first and second ports
    Flow path 88, 70 connectable. In this case, the first flow path 68 can be connected to the safety barrel A via a check valve 94 and the second flow path 70 can be connected to the working port A via a check valve 96. The check valves 94, 96 open in each case in a pressure medium flow direction away from the pressure reducing valve 88. Thus, via the Constanfpumpe 90 and the Druckreduzlervenfii 88, the hydraulic Sch 65 can be biased to the cylinder 66 with a low pressure. In addition, the working port A is connected to a hydraulic accumulator 98 in the form of a low-pressure accumulator. This is about a pressure relief valve! 100 and a drain valve 102 connectable to the tank 80 of Figure 3c.
    According to FIG. 3 a, the hydraulic circuit 85 additionally has a flushing device 104. The latter has a flushing valve 106, by means of which both flow paths 88, 70 can be connected to the tank 80 from FIG. 3 c. The Schaitventi! Trained purge valve 108 has two armature ports A, B connected to respective flow paths 70 and 68, respectively. Furthermore, the flushing device 104 has two tank connections T connected to the tank 80. In a spring-biased first circuit of a valve spool of the flushing valve 108, all the ports are separated from each other. In a second shift formation, which can be manually or electromagnetically charged, the valve driver connects the working collar A with the first tank flange T and the working flange B with the second tank flange T. The working port A is the other one! connected via an adjustable throttle 108 m-f the flow path 70. The same applies to the working flange B, which is connected to the first flow path 68 via an adjustable throttle 110.
    To secure the hydraulic circuit 65 and the cylinder 86, first and second safety valves 112 and 114 are provided. These are each a logic valve. In this case, the first flow path 88 can be opened and lowered with the safety valve 112. With the dam safety valve 114, the second flow path 70 is then openable and controllable; in the controlled state of the flow peat 63.70, the return flow 34, the hydraulic machine IS, the biasing device 86 and the purging device 104 are separated from the cylinder 66. The safety valves 112, 114 are identical in design, for which reason, for the sake of simplicity, only the upper safety valve 112, which is shown in FIG. 3a, is explained in more detail below. The safety valve 112 designed as a logic valve is designed in the usual way. A Ventiikörper 116 limits a Zyiinderraum 118. practice He is in Sshiie statement of a · Spring force of a spring and a Endschaitventll 120 pressurizable means beaufschisgbar. Furthermore, the valve body 116 limits a annular space 122, via which it can be acted upon in the opening direction and against the spring force of the spring with pressure medium via the limit switching valve 120. The end-rail valve 120 has two work ports A, 8, a tank port T, and a pressure port P. O. Aripeitsanschuuss A is in this case connected to the cylinder chamber 118 and the working port B with the annular re 122. Tank port T is connected to tank 80 of Figure 3c. Above the pressure port P, the end valve 120 is connected to an output port & W of a shuttle 124. The shuttle 124 also has a first input port E1 and a second input port E2. The input port E2 is hydraulically connected to the biasing device 86 and the accumulator 98 by being connected to the circuit between the check valves 94 and 98 in a Nordic manner. Alternatively, it is conceivable to connect the input terminal E2 to the hydraulic accumulator 78. The other output connection E1, on the other hand, is connected to the second flow path 70. The input port E1 is thus preferably connected to a flow path in which the load pressure or weight pressure of the machine to be actuated acts. The higher pressure port E1 or E2 is then connected to the output sa to I u as AW and thus to the pressure port P of the end shift valve 120. The exhaust valve 12Q has a valve spool which is spring-biased over a Ven-down in a first scarf position a. In this, the annular space 122 of the safety valve 112 with the tank 80 and the Zyünderraum 118 with the Druckmittelqnelle, ie with dam flow path 70 or the biasing device 86, connected in this first Schaltsteliung a-thus the safety valve 112 is closed. Manually or electromagnetically, the valve spool of Endschaltventiis 120 can be moved to a second Schaltsteliung b, in this is then the cylinder chamber 118 with the tank and the annulus 122 with the Druckmititteiquelie. that is, connected to the flow path 70 or biasing device 88, with which the safety valve 120 is opened.
    The flow paths 86 and 70 can be connected to each other according to FIG. 3a via a first and a second pressure limiting valve 124, 126. The first pressure limiting valve 124 is in this case of the pressure medium in the flow path 7Q and the second DruckbegrenzungsventSS 126 from the pressure medium in the flow path 88 actu bar. Both pressure limiting valves 124, 128 are pilot-operated
    Pressure Relief Valves with Weed Relief in Poms of a Directional Valve 128. in the scarfing direction, a Vsntiikörper a respective pressure relief valve 124t 128 via a Sieuerleitung with pressure fluid from the hydraulic accumulator 78 and mitDruckmittel from the hydraulic pump 74. See Figure Sc, beaufsehelagbar. via the respective directional control valve 128, the pressure medium to the tank is discharged. Another pilot pressure relief valve 132 with relief is provided via first and second check valves 134.138; connected to the first flow & piad 68 and the second flow path 70, respectively. The check valves 134, 138 open in this case in each case in a direction of pressure to the pressure limiting valve 132. This can open a pressure connection to the tank 80. It is also in Schiießrichtung on the control line 130 from the pressure medium of the hydraulic accumulator 78 and the hydraulic pump "4, see Figure 3c, beaufschiscbar and debased via the directional control valve 128.
    The synchronous cylinder 88 in FIG. 3 a has a position measuring system 138. Furthermore, a pressure gauge 140 is attached to a respective cylinder space of the cylinder 88.
    According to FIG. 3b, a lower cylinder or cylinder 142 is shown. This is controlled according to the cylinder 88 of Figure 3a with a hydraulic circuit designed according to the hydraulic shaky 65. The cylinders 88 and 142 cooperate therewith and may be part of a mechanical press having a die cushion axis.
    According to FIG. 3c, an assembly 144 for supplying pressure to the hydraulic circuits of the cylinders 8Θ and 142 from FIGS. 3a and 3b is shown. The hydraulic pump 74, which can be adjusted via a pressure-flow regulator, is connected to the pressure connection Pdes Regsiventiis 34 via a pump line 148 via the check valve 72 from FIG. The hydraulic pump 74 is drivable by an electric motor 184. Furthermore, the electric motor 148 is coupled to the fixed displacement pump 90, which is connected to the pressure reducing valve 88 via a check line 180 via the check valve 92 in FIG. Both the pump line 148 and the pump line 150 can be relieved via a pressure limiting valve 152 to the tank 80. Furthermore, two fueling lines 154, 156 and one leakage line 158 are connected to the circuits 85 of the cylinders 66, 142 of FIGS. 3a and 3b, in which
    Tank line 154 is a cooling and RHervorriahtung 1Θ0 provided. The tank assembly 154 is preferably connected to the flushing device 1Q4.
    In the following, in the figures 4 and 5, are exemplary applications with dersrfindungsgemäSen hydraulic Circuit explained. As already explained, the hydraulic circuit should preferably be used for Sfanz Nihbelmaschinen or Zishkissenysteme having a Krad of 20, 30,45, 87,100: 150, 225 tons, etc., This may for example be a series. The hydraulic circuit can, of course, also be used in other hydraulic cylinder axles which have hitherto been driven with extremely large valves and large storage levels, with a great deal of energy being wasted and not optimally utilized.
    According to the upper diagram i: -! FIG. 4 shows a stroke s over a time t. The lower characteristic curve 162 shows a course of the upper piston and the upper characteristic curve 164 a passage of the sub-piston. The stroke s of the upper piston in this case has approximately einensinusförmigen run on. He executes a stroke h of about 1GÖ mm. A lifting force is then about 20 tons, for example. For example, a diameter of a piston may be about 0.1 mm and a cylinder rod about 110 mm. The one shown in the diagram For example, time slots z are about 1.5 seconds. A stroke of the sub-piston according to the characteristic 184 is about 100 mm, which is a pulling stroke. A diameter of the sub-piston may be about 125 mm and a diameter before its piston rod about 90 mm.
    The middle diagram in FIG. 4 shows the course of a speed v across the tent t. The lower characteristic curve 166 represents a course of the upper piston and the upper characteristic curve 168 a profile of the lower piston. The time interval z is again 1.5 seconds. For example, a maximum travel speed of the upper piston is about 800 mm / s (lower piston 10 tons). The displacer control for the top piston may in this case for example be driven at about 400-450 revolutions / ml and promote about 100 l / min. The maximum speed of the underbench can also be about 8ömm / s. For example, the positive displacement control of the submarine then conveys about 220 rpm and is driven at about 200-250 revolutions / min. in the lower diagram in FIG. 4, a force F is plotted over the time t. Lower curve 170 shows a curve of the upper cuff and upper curve 172 shows a curve of the lower curve. The Zeätintervall z is 1.5 sec. A pulling 174 takes place both at the bottom and at Oberkoiben with a pressure difference between the terminals of the respective displacement control of about 200 bar. The top piston will then have about 20 tons of force and the bottom piston about 10 tons of force. The curve portion 176 when submerged shows an ejection of about 1 ton and a pressure difference of about 25 bar. The duration is about 200 - 300 ms. The section 178 in the course of the upper piston at the characteristic curve 170 represents the dead weight of the piston,
    The diagrams of Figure 4 show a " Draw-cushion-application " Test. In this case, about 20 strokes are applied at a speed of about 600 mm / s and a conveying volume of about 15,000 cm ^.
    According to FIG. 5, a punch application is shown. Test dargestelit. Here, a Oberkoibenvorgesehen who have a force of about 20 tons auibringen The test is hierbeietwa with 8ÖÖ strokes / mln and a VerfahrgasehwIndigkaii of 800 mm / s and a delivery volume of up to 100 cm3. The upper diagram in FIG. 5 shows the course of the stroke s over the time t. A characteristic curve 180 shows the double stroke time 182, which is approximately 30 ms at 4 mm, approximately 35 ms at 8 mm and approximately 50 ms at 10 mm. Cycle time 184 may then be about 80 ms, about 70 ms, and about 11Q ms, respectively.
    According to the middle diagram in FIG. 5, in which the speed v is carried over time t, the maximum speed 186 may be about 450 mm / s, about 600 mm / s or about 650 mm / s. The cylinder may in this case have a piston with a diameter of about 160 mm and a piston rod with a diameter of about 110 mm. A volume flow can then be about 290 i / min. about 380 i / minbeziehungsweise about 420 l / min and a speed about 300 ümdrehungen / min, about 400 revolutions / min or about 450 revolutions / min. in the lower diagram in FIG. 5, the force F is shown over time t. The maximum force can be 20 firs and can be applied in a time interval 188 of about 5 -10 ms. The time interval 190 may be about 80 ms. about 70 ms or about 100 ms. A pressure difference in the displacement control can amount to about 200. FIG. 8 shows an alternative embodiment with regard to an arrangement of safety valves. The remaining hydraulic arrangements are not shown in Figure 6 for the sake of simplicity. Referring now to Figure 8, the smoothing cylinder 88 is formed with portions of the flow chutes 68 and 70. As shown in Figure 3s, the pressure limiting valves 124 and 128 are provided to the flow paths. In contrast to the embodiment in FIG. 3a, two safety valves 191 and 192 are arranged in the flow path 70. Furthermore, two safety valves 194.1S6 are also provided in the flow path 88. The safety valves 191, 192 hzw.194,198 a respective flow path 70 hzw. 88 are flushed in series. That is, the flow path 68 is not opened until both safety valves 194 and 198 are opened, if one of these safety valves 194, 196 is closed, then the flow path 68 is also blocked. The same applies to the flow path 70, which is then open when both safety valves 191, 192 are open. If one of the safety valves 191, 192 is closed, the flow path 70 is also blocked. The safety valves 191 to 196 are configured corresponding to the safety valves 112 and 114 of the figure 3a and may be hydraulically connected accordingly. By arranging two safety valves 191, 192, and 194, 196, respectively, in a respective flow path 70, SB, the safety of the hydraulic circuit 65 is further ......... ^ · ιιιιι: ι ::
    Disclosed is a hydraulic circuit in which a displacement control and a valve control are connected in parallel are. The displacer control is connected to a load with both connections, as in a closed circuit. The parallel valve control is operated as an open circuit. It is intended that the Verprängersteuerung the Hauptfei! the hydraulic drive train and thus provides fluid quantity, while the valve timing compensates for deviations from a predetermined pressure, "path" or speed control curve simultaneously.
    Reference numeral 1 Engine 2 Cylinder 4 Cylinder 8 Hydraulic circuit 8 Hydraulic circuit 10 Displacement control 12 Displacement control 14 Valve control 16 Valve control 18 Hydromachine 2.0 Electric motor 22 Piston 24 Piston rod 26 Cylinder space 28 Cylinder space 30 Flow ply 32 Flow path
    34 RegsiventH 36 Piston 38 Engine 40 Cylinder 42 Cylinder 44 Frame 46 Control block 48 Sieuerbiock SO Displacement control 52 Displacement control 54 Power electronics 58 Power electronics 58 Supply unit 60 Control cabinet o2 Fair 84 Ground 85 Hydraulic circuit 86 Equilibrium cylinder 88 Flow path 70 Flow path 72 Check valve 74 Hydraulic pump 78 Hydraulic accumulator 78 Pressure relief valve 80 Tank 82 Drain valve 84 Shut-off valve 88 Pretensioner 88 Pressure relief valve 90 Constant pump 92 Check valve 94 Check valve 98 Check valve 98 Hydraulic accumulator 100 Pressure relief valve1Ö2 Drain valve 104 Flushing device 106 Flush valve 108 Throttle 110 Throttle 112 Safety valve 114 Safety valve 118 Valve body 118 Cylinder chamber 120 End valve 122 Annulus 124 Pressure limiting valve 128 Pressure relief valve 128 Directional valve 130 Control line 132 Pressure relief valve 134 Check valve 136 Check valve 138 Position measuring system 140 Pressure measuring he 142 Cylinder 144 Aggregate 146 Pump line 148 Electric motor 150 Pump line 152 Pressure limiting valve 154 Tank line 156 Tank line 158 Leocage line 160 Cooling and Fiitioning device 182 Characteristic 164 Curve 166 Curve 168 Curve 170 Curve 172 Curve 1 4 Pull 176 Section 178 Section 180 Curve 182 Double stroke 184 Cycle time 186 Maximum speed 188 Time interval 190 Time interval 191 Safety valve 192 Safety valve194 Safety valve 196 Safety valveAI, A2, X, Y ConnectionA, S Working interfaceP Pressure connectionTarial closing0 Basic settingsa first displayb second switching positionAW positiongear1, E2 inlet connection
    权利要求:
    Claims (15)
    [1]
    Claims 1. A hydraulic circuit for controlling a hydraulically driven machine (2,4), wherein a displacer control {10} and a valve control {14} are operatively connected in parallel, characterized in that the displacer control (10) comprises a hydraulic machine (18) two ports (At, A2) connectable to the engine (2) via a flowpath (30, 32}, respectively, to form a fully closed hydraulic circuit, and wherein the valve control (14) is connected to the engine (2) in FIG connectable to an open hydraulic circuit,
    [2]
    2. A circuit according to claim 1, wherein at a provision of a hydraulic drive power of the positive displacement control (iö) with the valve control (14) deviations from a predetermined pressure curve and / or travel control curve and / or GesehwindigkeiisRegeikurve be compensated.
    [3]
    3. A circuit according to claim 1 or 2, wherein the valve control (14) during a start-up phase and / or a movement phase and / or a braking phase of the machine (2,4} and / or the Verdrängersfeuerung {10} pressure medium or led.
    [4]
    4. A circuit according to claim 1, 2 or 3, wherein the hydraulic machine (18) is derarteusgestaitet that it has a comparatively low inertia and a comparatively large displacement.
    [5]
    A circuit according to any one of claims 1 to 4, wherein the hydraulic machine (18) is driven by an electric motor (20) arranged to have a comparatively low inertia and a comparatively low speed,
    [6]
    6. circuit according to one; of the preceding claims, wherein the valve control {14} has a Regelvenill (34), which is ausgeiegt so. that it has high dynamics and high accuracy
    [7]
    7. A circuit according to claim 6, wherein a Abschaltvenii! {84} is provided. so that the control valve (34) is separable from the flow paths (88, 70).
    [8]
    8. A circuit according to claim 6 or 7, wherein a hydraulic accumulator (76) is connected to the control shaft (34), which is designed to derail a required working pressure for the machine (2).
    [9]
    A circuit according to any one of claims 8 to 8, wherein a hydraulic pump (74) is connected to the regulator (34).
    [10]
    A circuit according to any one of the preceding claims, wherein a biasing means (86) is provided for biasing one or both flow paths (6B, 70) at a predetermined hydraulic pressure.
    [11]
    11. A circuit according to one of the preceding claims, wherein a flushing device (104) is provided, which is closed at at least one flow path (08,70) and is entiassbarist on the pressure means, wherein the flushing device (104) is controlled such that an influence a Druckregeiung and / or Wegregeiung and / or Geschwindigkeitsregeiung the machine (2) is comparatively low or avoided.
    [12]
    A circuit according to any one of the preceding claims, wherein the pusher control (10) and the valve control (34) are dual-spaced and monitored.
    [13]
    13. A circuit according to any one of the preceding claims, wherein in a or two incisor machine (2) leading Shörmmgspfaden (68, 70) of the Verdrängersteiierung (10) and / or the valve control (14) a safety valve (112,114} or each more safety valves is or are arranged , wherein in a closed state of the safety valve (112,114) or the safety valves, the associated flow path (68, 70) is locked and in an open state of the safety valve (112, 114) or the safety valves, the associated flow path is open.
    [14]
    14. A circuit according to any one of the preceding claims, wherein the displacement control (IQ) is protected by an electrical protective circuit,
    [15]
    15. A hydraulically specified machine with a hydraulic cylinder (2) which is controlled in front of its circuit (1) gemöö one of the preceding claims.
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102014114149|2014-09-29|
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