• 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 device for the optimized hydraulic control of at least one double-acting cylinder (1) of a working machine with a hydraulic pressure converter (A) which is hydraulically connected to a first surface of piston, at a second surface of the piston and at least one pressure accumulator (11), the pressure converter (A) being configured so that the hydraulic energy of a high pressure volume flow carried by the first piston surface to the pressure converter (11) is capable of being accumulated entirely or at least partially by said at least one pressure accumulator (11) connected and that the cylinder chamber of the second piston surface of the cylinder (1) is capable of being filled by the converter (A) with a low pressure volume flow.
    公开号:FR3035925A1
    申请号:FR1654041
    申请日:2016-05-04
    公开日:2016-11-11
    发明作者:Philipp Hahn；Volker Gliniorz；Guillaume Bonnetot
    申请人:Liebherr Mining Equipment Colmar SAS；
    IPC主号:
    专利说明:

    [0001] FIELD OF THE INVENTION The invention relates to a device for the optimized hydraulic control of at least one double-acting cylinder of a working machine.  In working machines, cylinders are used to actuate any accessory devices or for a tilting movement of arrows systems.  The lifting movement is generally done against the load, the retraction movement of the piston rod is made against against pressure by the load.  In known jack circuits in moving work machines, the retraction of the pressurized piston rod is effected by a throttle control to slow down the speed of retraction.  During throttling, the potential energy of the volume flow under pressure that is displaced by the load to the jack is transformed into heat.  The existing potential energy is not only destroyed but the cooling energy must be provided for the release of heat within the machine.  [0003] A common embodiment of hydraulic cylinders in mobile work machines is the differential cylinder.  When the latter is retracted with a throttle and an urgent load, it must be ensured that the cylinder chamber on the rod side is reloaded.  This is possible, on the one hand, by adding a corresponding supply volume flow by the working pumps, and, on the other hand, it is possible to perform a corresponding refill of the cylinder chambers on the shank side by a return of the strangled volume flow.  By the return of the strangulated volume flow, a division thereof according to the surface ratio of the hydraulic cylinders is performed.  By this, one part is conducted in the chambers of the rod side cylinders and the other part is conducted in the tank.  It is desirable during the accumulation of potential energy, to obtain the most volume of displaced oil possible at the highest pressure possible.  On the basis of the current circuits with a partial amount return to the rod side chambers of the cylinders, only a partial amount of the displaced oil volume is available for accumulation.  The partial amount returned is, in addition, based on the throttling control, reduced from a high level of pressure to a low pressure level.  This results in three disadvantages.  The amount of oil is divided, part of the energy is destroyed by the throttling control and the dissipated heat must, in addition, be spurned by the cooling system of the machine.  The object of the invention is to overcome the disadvantages described above and to provide optimized energy operation of one or more cylinders of a mobile working machine.  The object of the invention is achieved with a device for the optimized hydraulic control of energy of at least one double-acting cylinder of a working machine with a hydraulic pressure converter.  The converter is connected to a first piston surface of the cylinder and to a second surface of the piston, that is to say in a differential cylinder on the one hand to the piston chamber and on the other hand to the annular chamber.  In addition, at least one pressure accumulator is hydraulically connected to the pressure converter.  The configuration of the converter and its connection to the cylinder and to the pressure accumulator is carried out in such a way that the hydraulic energy of a high-pressure volume flow conveyed by the first piston surface to the pressure converter is suitable for being compensated or accumulated entirely or at least partially by said at least one connected accumulator.  In addition, the volume flow taken at the low pressure side of the pressure converter is fed to the cylinder chamber of the second piston surface of the cylinder, whereby the cylinder chamber of the second piston surface of the cylinder is adapted to be filled during the movement of the piston, thus by the converter, with a hydraulic medium.  More particularly, in a jack in the form of a differential cylinder, the annular chamber is supplied with the necessary hydraulic volume.  [0008] The hydraulic design of the device is therefore distinguished by the fact that, in addition to the almost lossless pressure conversion from an incoming high pressure level to a low pressure level for filling (i.e. reloading) of the cylinder chamber increasing the volume of the cylinder, it can be obtained simultaneously a complete or at least partial accumulation of the potential energy released by the movement of the cylinder.  For example, the reloading of the cylinder chamber of the cylinder, when it increases its volume, is effected by the fact that the pressure converter 30 displaces the hydraulic medium necessary for this and transports it to the jack.  This displacement is at a low pressure level, that is to say that there is a low pressure volume flow, since the high pressure level of the volume flow of the cylinder is compensated by the hydraulic accumulator.  The device can be used for controlling a single cylinder or a plurality of cylinders.  For example, the cylinders are connected in parallel, as for a parallel arrangement of two lifting cylinders on the boom.  [0010] In a possible design, the pressure converter comprises a primary cylinder and a secondary cylinder which are connected to each other by their piston rods.  In this context, it is conceivable to use two double acting cylinders as primary cylinder and secondary cylinder, preferably two differential cylinders coupled to each other by their piston rods.  According to an alternative, the pressure converter may comprise as primary cylinder and secondary cylinder, a double-acting cylinder, for example a differential or tandem cylinder, and a single-acting cylinder, in particular a plunger cylinder.  According to an advantageous embodiment, the first piston surface of the cylinder is connected to a piston surface of the primary cylinder, so that the first piston surface of the cylinder urges said piston surface of the primary cylinder with a high pressure. .  And the pressure accumulator can be connected to a cylinder chamber of the primary cylinder or the secondary cylinder.  The only condition is that said cylinder chamber acts against the piston surface of the primary cylinder on which the high pressure acts.  By this way of connection, it is ensured that the high pressure supplied by the pressure accumulator to the pressure converter, or at least a large part of the high pressure level, can be compensated or accumulated by the pressure accumulator.  By appropriate selection of the ratio between the two piston surfaces, the pressure accumulator can, in addition, be selectively loaded with a higher pressure or a lower pressure than the high pressure level of the cylinder.  According to an alternative embodiment, the first piston surface of the cylinder urges a piston surface of the primary cylinder with a high pressure and the high pressure accumulator is connected to a cylinder chamber of the primary or secondary cylinder, the surface The piston piston is preferably smaller in area than the piston surface of the primary cylinder biased with the high pressure.  In a pressure converter with two differential cylinders coupled to one another, the high pressure outlet of the cylinder can be connected to the annular chamber of the primary cylinder and the high pressure accumulator can be connected to either the piston chamber of the primary cylinder is at the piston chamber of the secondary cylinder.  According to an alternative embodiment of the pressure converter with a differential cylinder and a plunger cylinder, there is the possibility of connecting the high pressure outlet of the cylinder to the cylinder chamber of the primary cylinder, that is to say of the differential cylinder, and to connect the high-pressure accumulator either to the annular chamber of the primary cylinder or, alternatively, to the chamber of the plunger cylinder.  For one embodiment of the pressure converter with a tandem cylinder as a primary cylinder and a plunger as a secondary cylinder, the high pressure side of the cylinder can be connected to a first annular chamber of the primary cylinder while the high pressure accumulator is connected to either the second annular chamber of the primary cylinder or to the plunger chamber.  For the filling or reloading of the jack, the first piston surface of the jack can urge a piston surface of the primary cylinder with a high pressure and the second piston surface of the jack can be connected at the same time to a surface of piston of the primary cylinder or the secondary cylinder of the pressure converter.  To ensure a lower pressure level at the output of the pressure converter, which is used for filling the cylinder chamber increasing in volume of the cylinder, it is useful that the piston surface of the primary cylinder biased with high pressure. is larger on the surface than the piston surface that moves the hydraulic medium necessary for filling the cylinder.  For the control of the actuation of the cylinder, including the retraction movement of the piston rod caused by the load, the first piston surface of the cylinder 20 can be connected to the primary cylinder of the pressure converter by a valve of switching or a proportional valve to control or regulate the volume flow between the two components.  The piston movement of the cylinder, in particular the retraction movement, is thus only possible when the integrated switching or proportional valve releases the volume flow.  In addition, by the use of a proportional valve, the flow rate can be controlled or regulated to thereby influence the speed of movement of the ram piston.  Alternatively or in addition, the pressure converter can be connected to the second piston surface of the cylinder by an additional switching or proportional valve.  With such a connection, the piston movement, in particular the retraction movement, of the jack is only possible when the switching or proportional valve releases the hydraulic connection.  In addition, the use of the proportional valve makes it possible to control / regulate the speed of the piston movement of the cylinder.  According to a particularly preferred embodiment of the invention, the pressure converter is connected to one or more hydraulic consumers for supplying them, via the pressure converter, with accumulated hydraulic energy coming from the accumulator. pressure.  For connecting said one or more hydraulic consumers to the pressure converter, at least one common proportional valve or proportional valve may be used or the consumers are connected to the pressure converter via individual proportional valve or switching valves.  In the hydraulic connection between the pressure converter and the second piston surface of the cylinder, at least one discharge valve to the hydraulic reservoir can be interposed between the pressure converter and the second piston surface 10 of the cylinder.  An excess volumetric flow of the low pressure volume flow made available by the pressure converter for filling the cylinder can be returned to the tank via the discharge valve, thereby controlling the pressure level inside the chamber. cylinder to be filled with the cylinder.  In addition, at least one non-return valve may be interposed between the converter and the jack to prevent or block a volume flow back from the cylinder.  The pressure accumulator used may be a bladder accumulator, a piston accumulator, a membrane accumulator or a spring accumulator.  It is also conceivable that the pressure accumulator be configured as an external component connected to the pressure converter appropriately.  According to an alternative, a direct integration of the pressure accumulator with the pressure converter is conceivable.  When external hydraulic consumers are supplied with hydraulic medium from the pressure accumulator, there may be insufficient supply of hydraulic fluid from the pressure converter.  The pressure converter can then be connected to the hydraulic reservoir by a re-suction valve to compensate for a volume removal of the pressure accumulator when feeding one or more hydraulic consumers.  The re-suction valve is configured, for example, as a non-return valve 30 which allows only a volume flow of the tank towards the pressure converter.  In addition to the device according to the invention, the present invention also relates to a working machine, in particular a construction machine or crane, with at least one jack and a device according to the present invention.  For the working machine, the same advantages and characteristics as those discussed with respect to the device of the invention result.  For this reason, a repetition of description is omitted.  According to a particularly preferred embodiment of the working machine, the jack is capable of being actuated by an applied load.  Thus, for example, the jack 5 is a lifting cylinder for actuating an arrow of the working machine.  By the arrow, a load acts on the cylinder, which load triggers an actuation without pressure of the cylinder, as a rule a retraction movement without pressure of the piston rod in the cylinder.  The resulting energy is recovered by the fact that the energy released is likely to be accumulated almost entirely by means of the device or more precisely by its pressure accumulator.  In other words, the jack is adapted to be controlled by an applied load, in particular by lowering the boom, and the energy of the volume flow displaced by the load is able to be accumulated by the device in a pressure accumulator.  At the same time, the increasing volume of the cylinder of the cylinder can be recharged simultaneously with a hydraulic medium from the pressure converter.  It is also conceivable that one or more hydraulic consumers of the working machine are adapted to be powered alternately from the pressure accumulator of the device or from an alternative hydraulic supply of the machine.  Ideally, the primary supply of the external hydraulic consumers is provided from the pressure accumulator and an emergency power supply, in case of failure of the device or in the event of complete discharge of the pressure accumulator, is ensured. by an alternative energy source.  Other features and advantages of the invention will appear in the explanatory description which follows, with reference to the accompanying drawings and given solely by way of example, illustrating several embodiments of the invention and in which: FIG. 1 represents a first exemplary embodiment of the device according to the invention; FIG. 2 represents a second exemplary embodiment of the device according to the invention; FIG. 3 represents a third embodiment of the device according to the invention; FIG. FIG. 4 represents a fourth exemplary embodiment of the device according to the invention, FIG. 5 represents a fifth embodiment of the device according to the invention, and FIG. 6 represents a sixth exemplary embodiment of FIG. device according to the invention.  An overall view of the hydraulic circuit which represents the invention described here, is shown in FIGS. 1 to 6.  The circuit with the cylinder 1 is part of a working machine, for example a crane or a construction machine.  The jack or cylinders 1 serve as a lifting cylinder to perform a lifting movement of the boom system of the machine.  When the boom system is lowered, the boom load acts on the cylinder 1 and makes possible a retracting movement of the piston rod in the cylinder.  The circuit according to the invention is distinguished by the fact that, during a retraction movement of the cylinder or cylinders 1 under pressure, the existing potential energy can be accumulated using a hydraulic accumulator 11 and a pressure converter A, B, C.  In addition, by the circuits shown, an energy-efficient filling 20 is made possible on the rod side of the cylinder (s) 1.  The invention is further distinguished by a parallel integration in a working machine, for example a crane or a construction machine, which also makes possible a trouble-free operation of all consumers in case of failure of the accumulator 11.  The pressure converter A, B, C ensures, together with the accumulator 11, 25 that the volume of oil on the bottom side of the cylinder or jacks 1 is collected and that the potential energy contained therein can be accumulated using the hydraulic accumulator 11.  At the same time, the hydraulic pressure converter A, B, C performs the filling of the rod sides of the cylinder or cylinders 1 by moving the necessary volume of oil for this purpose.  This oil displacement is effected at a low pressure level since the high pressure level at the bottom side is compensated by the hydraulic accumulator 11.  The lowering speed can be adjusted by a throttle valve 9 between the hydraulic pressure converter A, B, C and the rod side of the cylinders 1.  The filling or rather reloading of the rod sides of the cylinders 1 is distinguished as "energy efficient" by the fact that the throttling point 9 to adjust the lowering speed of the hydraulic cylinders needs only to generate relatively low pressure losses.  The described circuit can be operated with three different pressure converters A, B and C and respectively in two different circuits.  These are distinguished from each other only by the arrangement of the hydraulic accumulator 11 and the configuration of the pressure converter A, B, C.  For all circuits, it matters what follows.  When the accumulation action must be triggered, a force must be applied to the cylinder 1, force which causes the retraction of the cylinder 1.  By this, a pressure is generated on the bottom side of the cylinder 1 which determines the potentially available energy.  This potential energy must be received by a hydraulic accumulator 11.  By the hydraulic valve 14, in the form of a switching valve or a proportional valve, a connection is created between the bottom side and the connection 15 of the pressure converter A, B, C.  On the basis of a balance of forces inside the pressure converter A, B, C, a pressure is established at the outlet 16.  Until the actuation of the hydraulic valve 9, no retraction movement of the cylinder 1 can be effected.  By a proportional control of the hydraulic valve 9, the output of an oil volume of the pressure converter A, B or C is made possible and at the same time the retraction speed of the cylinder 1 is determined.  By the hydraulic valve 9, it is made possible to this volume flow to arrive through the non-return valve 4 in the chamber of the rod side of the cylinder 1.  By the configuration of the pressure converter A, B or C, an outgoing volume flow is generated at the outlet 16 when a volume flow is received at the connection 15.  Through the discharge valve 6, the excess volume flow, which is not necessary for filling the chamber on the rod side of the cylinder 1, is conducted under an adjustable prestressing pressure to the discharge valve 6, to the tank 7.  When the accumulation action is stopped, the normal control for the retraction of the jack 1 can be triggered.  For this, the hydraulic valves 9 and 14 are closed.  By a proportional control of the hydraulic valve 5, the volume flow from the bottom side of the cylinder 1 chamber is conducted via the non-return valve 4 in the rod side chamber of the cylinder 1.  The amount of excess oil on the bottom side of the cylinder 1 is conducted under an adjustable discharge pressure via the discharge valve 6 in the tank 7.  The normal servocontrol of the cylinder 1 to raise or lower without accumulation action is performed via the connectors 2 and 3.  A flow of the volume flow conveyed to the connection 2 to the reservoir is prevented by the non-return valve 4.  In order to reuse the hydraulic energy in the hydraulic accumulator 11, the hydraulic valves 9 and 14 are kept closed.  By a switching or proportional actuation of the hydraulic valve 13, a volume flow under pressure can be taken out through the connector 15 of the pressure converter.  By drawing a volume flow at the connection 15 of the pressure converter A, B or C, a lack of volume flow is generated at the low pressure connection 16.  The missing volume flow is conveyed via the re-aspiration valve 8.  All kinds of hydraulic accumulators can be used as hydraulic accumulator 11.  Embodiments in the form of bladder accumulators, piston accumulators, diaphragm accumulators or spring accumulators are conceivable.  In addition, a direct integration of the accumulator 11 into the pressure converter A, B, C is possible.  The invention is not limited to a kind or type of energy storage medium.  For bladder or piston accumulators, use will most often be made of nitrogen or a mixture of nitrogen.  In addition, the use of a combination of different pressure converters as well as different accumulators is possible in different combinations.  The valves shown can be used as individual 2/2 way valves or as a combination on a valve stem.  Here, proportional or switching control is also possible.  According to the embodiment of FIG. 1, the pressure converter A comprises two differential cylinders which are coupled to each other by their piston rods.  The primary cylinder comprises the piston A3, the piston chamber A2 and the annular chamber A4.  The secondary cylinder comprises the piston chamber A6 and the annular chamber A5.  Upon actuation of the hydraulic valve 14, a connection between the bottom side of the cylinder 1 and the upper annular chamber A4 of the pressure converter A1 is created via the connection 15 and the bottom side pressure of the cylinder 1 is applied to the annular surface of the piston A3.  The upper piston chamber A2 of the pressure converter A is connected to a hydraulic accumulator 11.  The lower piston chamber A6 of the pressure converter A is connected to the reservoir 10 or to the environment.  The lower annular chamber A5 of the pressure converter A1 is first closed by a hydraulic valve 9 via the low pressure outlet 16.  On the basis of a balance of forces at the piston A3 of the pressure converter A, a pressure is established in the lower annular chamber A5.  By forces opposing pressures in the upper piston chamber A2 and in the upper annular chamber A4, the pressure in the lower annular chamber A5 is reduced as opposed to the pressure on the bottom side of the cylinder 1.  Until the actuation of the hydraulic valve 9 at the outlet 16, no retraction movement of the cylinder 1 can be effected.  By proportional servo-control of the hydraulic valve 9, an escape of the volume of oil from the lower annular chamber A4 via the outlet 16 is made possible.  Through the hydraulic valve 9, this volume flow arrives via the non-return valve 4 into the chamber on the rod side of the cylinder 1.  By the configuration of the piston A3, a proportional volume flow is displaced from the lower annular chamber A5 upon receiving a volume flow in the upper annular chamber A2.  By the discharge valve 6, the excess volume flow which is not necessary for filling the chamber on the rod side of the cylinder 1, is led to the tank 7 under an adjustable discharge pressure at the discharge valve 6.  The embodiment of Figure 2 also uses the pressure converter A according to Figure 1, the connection to the cylinder 1 and the accumulator 11 is however different.  Upon actuation of the hydraulic valve 14, a connection is created between the bottom side of the cylinder 1 and the upper piston chamber A2 of the pressure converter A via the connector 15 and the bottom side pressure of the cylinder 1 is applied to the upper piston surface of the piston A3.  The lower piston chamber A6 of the pressure converter A is connected to a hydraulic accumulator 11.  The lower annular chamber A5 of the pressure converter A is connected to the tank 10 or to the environment.  The upper annular chamber A4 of the pressure converter A is first closed with a hydraulic valve 9 via the outlet 16.  On the basis of a balance of forces at the piston A3 of the pressure converter A, a pressure is established in the upper annular chamber A4.  By the opposing forces of the pressures in the upper piston chamber A2 and the lower piston chamber A6, the pressure in the upper piston chamber A4 is reduced as opposed to the bottom-side pressure of the cylinder 1.  Until actuation of the hydraulic valve 9 to the connector 16, no retraction movement of the cylinder 1 can be effected.  By proportional control of the hydraulic valve 9, an exhaust of the volume of oil from the upper annular chamber A4 via the connector 16 is made possible.  By means of the hydraulic valve 9, this volume flow arrives via the non-return valve 4 into the chamber on the rod side of the cylinder 1.  By the configuration of the piston A3, a proportional volume flow is displaced from the upper annular chamber A4 upon receiving a volume flow in the upper piston chamber A2.  By the discharge valve 6, the excess volume flow which is not necessary for filling the chamber on the rod side of the cylinder 1, is led to the tank 75 under an adjustable discharge pressure at the discharge valve 6.  Figure 3 shows an embodiment with a different pressure converter B.  This consists of a differential cylinder with the piston chamber B2, the piston B3 and the annular chamber B4.  The secondary cylinder is a plunger with the rod chamber B5.  Upon actuation of the hydraulic valve 14, a connection is created between the bottom side of the cylinder 1 and the piston chamber B2 of the pressure converter B via the connector 15 and the bottom side pressure of the cylinder 1 is applied to the piston surface B3.  The annular chamber B4 of the pressure converter B is connected to a hydraulic accumulator 11.  The rod chamber B5 of the pressure converter B is first closed with a hydraulic valve 9 via the coupling 16.  On the basis of a balance of forces at the piston B3 of the pressure converter B, a pressure is established in the rod chamber B5.  By the opposing forces of the pressures in the piston chamber 82 and in the annular chamber B4, the pressure in the rod chamber B5 is reduced as opposed to the bottom side pressure of the cylinder 1.  Until actuation of the hydraulic valve 9 at the connector 16, no retraction movement of the cylinder 1 can be effected.  By a proportional control of the hydraulic valve 9, an exhaust of the oil volume of the rod chamber B5 via the connector 16 is made possible.  Through the hydraulic valve 9, this volume flow arrives via the non-return valve 4 into the chamber on the rod side of the cylinder 1.  By the configuration of the piston 83, a proportional volume flow is displaced from the rod chamber B5 upon receiving a volume flow in the piston chamber B2.  By the discharge valve 6, the excess volume flow which is not necessary for filling the chamber on the rod side of the cylinder 1, is led to the tank 7 under an adjustable discharge pressure at the discharge valve 6.  [0039] The embodiment of FIG. 4 also uses the pressure converter B according to FIG. 3, placed against a modified connection.  Upon actuation of the hydraulic valve 14, a connection is created between the bottom side of the cylinder 1 and the piston chamber B2 of the pressure converter B via the connector 15 and the bottom side pressure of the cylinder 1 is applied to the surface piston piston B3.  The rod chamber B5 of the pressure converter B is connected to a hydraulic accumulator 11.  The annular chamber B4 of the pressure converter B is first closed with a hydraulic valve 9 via the connector 16.  On the basis of a balance of forces at the piston B3 of the pressure converter B, a pressure is established in the annular chamber B4.  By the opposing forces of pressures in the piston chamber B2 and in the rod chamber B5, the pressure in the annular chamber B4 is reduced as opposed to the bottom side pressure of the cylinder 1.  Until actuation of the hydraulic valve 9 to the connector 16, no retraction movement of the cylinder 1 can be effected.  By proportional control of the hydraulic valve 9, an exhaust of the oil volume of the annular chamber B4 via the connector 16 is made possible.  Through the hydraulic valve 9, this volume flow arrives via the non-return valve 4 into the chamber on the rod side of the cylinder 1.  By the configuration of the piston B3, a proportional volume flow is displaced from the annular chamber B4 when receiving a volume flow in the piston chamber B2.  Through the discharge valve 6, the excess volume flow which is not necessary for filling the rod-side chamber of the cylinder 1, is led to the tank 7 under an adjustable discharge pressure at the discharge valve 6.  The embodiment of Figure 5 uses the pressure converter C which consists of a cylinder in tandem with the upper annular chamber C2, the piston C3 and the lower annular chamber C4.  By its piston rod, the tandem cylinder is coupled to the plunger which comprises the rod chamber C5.  Upon actuation of the hydraulic valve 14, a connection is created between the bottom side of the cylinder 1 and the upper annular chamber C2 of the pressure converter C via the connection 15 and the bottom side pressure of the cylinder 1 is applied to the upper annular surface C2 of the piston C3.  The lower annular chamber C4 of the pressure converter C is connected to a hydraulic accumulator 11.  The rod chamber C5 of the pressure converter C 25 is first closed with a hydraulic valve 9 via the connector 16.  On the basis of a balance of forces at the piston C3 of the pressure converter C, a pressure is established in the rod chamber C5.  By the opposing forces of pressures in the upper annular chamber C2 and in the lower annular chamber C4, the pressure in the stem chamber C5 is reduced as opposed to the bottom side pressure 30 of the ram 1.  Until actuation of the hydraulic valve 9 to the connector 16, no retraction movement of the cylinder 1 can be effected.  By proportional control of the hydraulic valve 9, an exhaust of the oil volume of the rod chamber C5 via the connector 16 is made possible.  Through the hydraulic valve 9, this volume flow arrives via the non-return valve 4 into the chamber on the rod side of the cylinder 1.  By the configuration of the piston C3, a proportional volume flow is displaced from the stem chamber C5 upon receiving a volume flow in the upper annular chamber C2.  By the discharge valve 6, the excess volume flow which is not necessary for filling the chamber on the rod side of the cylinder 1, is led to the tank 7 under an adjustable discharge pressure at the discharge valve 6.  [0041] The last embodiment of FIG. 6 provides, with respect to the embodiment of FIG. 5, only a modified connection of the pressure converter C.  Upon actuation of the hydraulic valve 14, a connection is created between the bottom side of the cylinder 1 and the upper annular chamber C2 of the pressure converter C via the connector 15 and the bottom side pressure of the cylinder 1 is applied to the surface Annulus C2 of the piston C3.  The stem chamber C5 of the pressure converter C is connected to a hydraulic accumulator 11.  The lower rod chamber C4 of the pressure converter C1 is first closed with a hydraulic valve 9 via the coupling 16.  On the basis of a balance of forces at the piston C3 of the pressure converter C1, a pressure is established in the lower annular chamber C4.  By the opposing forces of the pressures in the upper annular chamber C2 and in the stem chamber C5, the pressure in the lower annular chamber C4 is reduced as opposed to the bottom side pressure of the cylinder I.  Until actuation of the hydraulic valve 9 to the connector 16, no retraction movement of the cylinder 1 can be effected.  By proportional control of the hydraulic valve 9, an exhaust 20 of the oil volume of the lower annular chamber C4 via the connector 16 is made possible.  Through the hydraulic valve 9, this volume flow arrives via the non-return valve 4 into the chamber on the rod side of the cylinder 1.  By the configuration of the piston C3, a proportional volume flow is displaced from the lower annular chamber C4 when receiving a volume flow in the upper annular chamber C2.  By the discharge valve 6, the excess flow volume which is not necessary for filling the rod side chamber of the cylinder 1, is led to the tank 7 under an adjustable discharge pressure at the discharge valve 6.  [0042] The invention is further distinguished by the fact that the system for the accumulation of hydraulic energy is made so that the system is not necessary for a regular operation of the machine.  If the accumulator system fails, the machine can continue to operate normally.
    权利要求:
    Claims (13)
    [0001]
    REVENDICATIONS1. Device for the optimized hydraulic control of at least one double-acting cylinder (1) of a working machine with a hydraulic pressure converter (A, B, C) which is hydraulically connected to a first piston surface of the cylinder, to a second surface of the piston and at least one pressure accumulator (11), the pressure converter (A, B, C) being configured so that the hydraulic energy of a high pressure volume flow transported by the first piston surface of the pressure converter (11) is capable of being accumulated entirely or at least partially by said at least one pressure accumulator (11) connected and that the cylinder chamber of the second piston surface of the cylinder (1) ) is able to be filled by the converter (A, B, C) with a low pressure volume flow.
    [0002]
    2. Device according to claim 1, characterized in that the pressure converter (A, B, C) comprises a primary cylinder and a secondary cylinder which are connected to each other by their piston rods, being provided as primary cylinder and secondary cylinder is two double-acting cylinders, in particular two differential cylinders, or a double-acting cylinder, for example a differential or tandem cylinder, and a single-acting cylinder, in particular a plunger cylinder.
    [0003]
    3. Device according to claim 2, characterized in that the first piston surface of the cylinder (1) biases a piston surface of the primary cylinder with a high pressure and that the high pressure accumulator (11) is connected to a chamber cylinder cylinder of the primary or secondary cylinder whose piston surface acts against the piston surface of the primary cylinder on which the high pressure acts, so that a large part of the high pressure level can be compensated or accumulated by the pressure accumulator (11).
    [0004]
    4. Device according to any one of the preceding claims, characterized in that the first piston surface of the cylinder (1) biases a piston surface of the primary cylinder with a high pressure and the second piston surface of the cylinder (1). is connected to a piston surface of the primary or secondary cylinder, the piston surface preferably being smaller in area than the piston surface of the primary cylinder biased with the high pressure.
    [0005]
    5. Device according to any one of the preceding claims, characterized in that the first piston surface of the cylinder (1) is connected to the primary cylinder of the pressure converter (A, B, C) by a switching valve or a proportional valve.
    [0006]
    6. Device according to any one of the preceding claims, characterized in that the pressure converter (A, B, C) is connected to the second surface of the cylinder (1) by a switching valve or a proportional valve.
    [0007]
    7. Device according to any one of the preceding claims, characterized in that the pressure converter (A, B, C) is connected to one or more hydraulic consumers which are adapted to be fed via the pressure converter (A, BC), in accumulated hydraulic energy from the pressure accumulator (11), said one or more hydraulic consumers being connected to the pressure converter (A, B, C) preferably by at least one switching valve or a valve proportional.
    [0008]
    8. Device according to any one of the preceding claims, characterized in that at least one discharge valve (6) to the hydraulic reservoir (7) is interposed 15 between the pressure converter (A, B, C) and the second piston surface of the cylinder (1) in order to conduct the excess volume flow in the tank (7), and / or at least one non-return valve (4) is interposed to prevent a return volume flow from the cylinder (1). ).
    [0009]
    9. Device according to any one of the preceding claims, characterized in that the pressure accumulator (11) is a bladder accumulator, a piston accumulator, a membrane accumulator or a spring accumulator, the accumulator of pressure (11) being preferably configured as an external component connected to the pressure converter (A, B, C) or being integrated with the pressure converter (A, B, C).
    [0010]
    10. Device according to any one of the preceding claims, characterized in that the pressure converter (A, B, C) is connected to the hydraulic reservoir (7) by a re-suction valve (8) to compensate a sampling the volume of the pressure accumulator (11) when feeding one or more hydraulic consumers.
    [0011]
    11. Work machine, especially construction machine or crane, with at least one cylinder (1) and a device according to any one of the preceding claims. 30
    [0012]
    12. Working machine according to claim 11, characterized in that the jack (1) is adapted to be controlled by an applied load, in particular by the lowering of the boom, and that the energy of the volume flow displaced by the load is able to be accumulated by the device in a pressure accumulator (11) and the increasing volume of the cylinder of the cylinder (1) can be recharged simultaneously with a hydraulic medium. 5
    [0013]
    Working machine according to claim 11 or 12, characterized in that one or more hydraulic consumers of the working machine are adapted to be fed alternately from the pressure accumulator (11) of the device or from an alternative hydraulic supply of the machine.
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    同族专利:
    公开号 | 公开日
    DE102015005920A1|2016-11-10|
    US20170023025A1|2017-01-26|
    AU2016202937A1|2016-11-24|
    FR3035925B1|2020-01-24|
    AU2016202937B2|2020-01-30|
    US10072680B2|2018-09-11|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE2830770C2|1978-07-13|1983-10-06|Eckart Prof. Dr.-Ing. 3005 Hemmingen Doege|Electromagnetic drive device|
    US5058384A|1990-09-20|1991-10-22|University Of British Columbia|Digital actuator|
    US8286426B2|2005-11-29|2012-10-16|Digital Hydraulic Llc|Digital hydraulic system|
    PL2295171T3|2009-09-15|2013-04-30|Richard Oberle|Method and hydraulic switching assembly for operating a metal pressure casting assembly|
    DE102014005352B4|2014-04-11|2016-03-10|Hoerbiger Automatisierungstechnik Holding Gmbh|machine press|DE102014206461A1|2014-04-03|2015-10-08|Thyssen Krupp Elevator Ag|Elevator with a braking device|
    DE102014104865A1|2014-04-04|2015-10-08|Thyssenkrupp Ag|Elevator with a braking device|
    DE102018108620B4|2018-04-11|2019-07-04|Parker Hannifin EMEA S.à.r.l|Hydraulic circuit arrangement for a cold or hot chamber die casting machine for the production of metal components|
    WO2020216440A1|2019-04-24|2020-10-29|Volvo Construction Equipment Ab|A hydraulic device, a hydraulic system and a working machine|
    CN112723166B|2020-12-28|2022-02-15|中联重科股份有限公司|Hydraulic control module, hydraulic control system and engineering machinery|
    法律状态:
    2017-05-25| PLFP| Fee payment|Year of fee payment: 2 |
    2018-05-17| PLFP| Fee payment|Year of fee payment: 3 |
    2019-02-01| PLSC| Search report ready|Effective date: 20190201 |
    2019-05-24| PLFP| Fee payment|Year of fee payment: 4 |
    2020-05-23| PLFP| Fee payment|Year of fee payment: 5 |
    2021-05-22| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102015005920.3A|DE102015005920A1|2015-05-07|2015-05-07|Device for energy-optimized hydraulic control of at least one double-acting working cylinder|
    DE102015005920.3|2015-05-07|
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