JP2012237339A - Hydraulic system of hydraulic working machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic system of a hydraulic working machine, capable of minimizing influences of degraded responsiveness of an actuator with respect to a speed control and maintaining good operability comparable to a spool type flow volume control valve.SOLUTION: The system includes: a motor capacity control means, which decreases a capacity of a variable capacity motor 23 when the pressure detected by a pressure gauge 27 is larger than the pressure detected by a pressure gauge 28, increases the capacity of the variable capacity motor 23 when the pressure detected by the pressure gauge 27 is smaller than the pressure detected by the pressure gauge 28, and fixes the capacity of the variable capacity motor 23 when the pressure detected by the pressure gauge 27 is equal to the pressure detected by the pressure gauge 28; a power regenerative detour oil path 30 branched from a power regenerative oil path 22; and a recovery regulation control means including a controller 25 and a recovery regulation valve 31, for performing control to guide a part of a flow volume in the power regenerative oil path 22 to the power regenerative detour oil path 30 when the flow volume of the power regenerative oil path 22 is equal to or larger than a predetermined flow volume.

Description

  The present invention relates to a hydraulic system for a hydraulic working machine that is provided in a hydraulic working machine such as a hydraulic excavator and has a function of regenerating excess energy in a hydraulic circuit as power.

  Power regeneration technology is used to improve the efficiency of the hydraulic system of hydraulic working machines. A hydraulic system of such a hydraulic working machine will be described using an example of a hydraulic excavator disclosed in Patent Document 1.

  In Patent Document 1, two hydraulic pump motors driven by an electric motor are connected to two ports of a double-acting hydraulic cylinder, respectively. The double-acting hydraulic cylinder is a single-sided rod type, and the piston pressure receiving areas on the expansion side and the contraction side are different, so the capacity of the two hydraulic pump motors is a ratio corresponding to the piston pressure receiving area. The speed and direction of the hydraulic cylinder are controlled by the controller controlling the rotational speed and direction of the electric motor that drives the hydraulic pump motor based on the operation amount of the operation lever. Furthermore, an oil passage that passes through a spool-type flow control valve controlled by a controller is provided in parallel between the oil passage connecting the bottom side of the hydraulic cylinder and the hydraulic pump motor. When the operation amount of the operation lever is smaller than the predetermined value, the hydraulic oil discharged from the hydraulic cylinder is controlled to pass through the flow control valve, and the operation amount of the operation lever exceeds the predetermined value. When exceeding, the hydraulic oil discharged from the hydraulic cylinder is controlled so as to flow directly into the hydraulic pump motor without passing through the flow control valve. With this configuration, good speed controllability of the hydraulic cylinder is ensured by the flow control valve in the fine operation region, and when the fine operation region is exceeded, direct connection to the hydraulic pump motor provides good power regeneration. We are trying to ensure efficiency.

JP 2002-349505 A

  In the prior art disclosed in Patent Document 1 described above, when the fine operation region is exceeded, the speed of the hydraulic cylinder is controlled only by the rotational speed control of the hydraulic pump motor, so that good regeneration efficiency can be ensured, but response to lever operation. There is a problem that it is difficult to secure the sex.

  The present invention has been made from the actual situation in the above-described prior art, and its purpose is to minimize the influence of responsiveness deterioration on the speed control of the actuator, and to ensure good operability equivalent to the spool type flow control valve. It is to provide a hydraulic system for a hydraulic working machine.

  In order to achieve this object, the present invention relates to a rotational power generating means, and a hydraulic working machine that generates rotational power by supplying rotational power from the rotational power generating means to a hydraulic pump and operates an actuator by the hydraulic power. In the hydraulic system, the hydraulic oil discharge oil path from the actuator is connected to the spool of the flow control valve controlled by lever operation, and the discharge operation from the hydraulic oil discharge oil path First power detection means provided in the flow control oil passage and the power regeneration oil passage are branched into a power regeneration oil passage that is an oil passage connected to a variable capacity motor that converts hydraulic power of oil into reusable energy. And when the pressure of the second pressure detecting means and the pressure of the first pressure detecting means is larger than the pressure of the second pressure detecting means, When the pressure of the first pressure detection means is smaller than the pressure of the second pressure detection means, the capacity of the variable displacement motor is increased, and when the pressures of the first pressure detection means and the second pressure detection means are the same. Motor capacity control means for fixing the capacity of the variable capacity motor, a power regeneration detour oil path branched from the power regeneration oil path, and the power regeneration oil path when the flow rate of the power regeneration oil path is equal to or higher than a predetermined flow rate And regenerative restriction control means for controlling so as to guide a part of the flow rate to the power regeneration detour oil passage.

  In the present invention configured as described above, the pressure of the first pressure detection means and the pressure of the second pressure detection means are controlled to be the same pressure. The fact that the pressure of the first pressure detection means and the pressure of the second pressure detection means are controlled to the same pressure means that the pressure detection section of the first pressure detection means and the pressure detection section It is the same as that the pressure loss of each oil passage section which generate | occur | produces between the pressure detection parts of 2 pressure detection means is the same. Here, assuming that the pipe resistance of the two oil passage sections is an orifice restrictor, and applying a general relational expression in which the amount of oil flowing through the orifice is proportional to the product of the opening area of the orifice and the square root of the pressure loss, If the pressure loss in the passage section is the same, it can be said that the flow rates flowing through the two oil passages are always at a constant ratio. That is, controlling the pressure of the first pressure detection means and the pressure of the second pressure detection means to be the same pressure means that the flow rates of the flow control oil passage and the power regeneration oil passage are controlled to a fixed ratio. means. Thus, by setting the flow rates of the flow control oil passage and the power regeneration oil passage to a fixed ratio, a flow rate is always generated in the flow control oil passage when the actuator is operating. Therefore, when the flow rate control valve is adjusted by lever operation to change the flow rate change of the flow rate control oil passage, the change in the flow rate necessarily affects the speed of the actuator. Reflected. Furthermore, since the flow rate ratio between the flow control oil passage and the power regeneration oil passage is always constant, the speed change amount of the actuator is always constant with respect to the flow change amount of the flow control oil passage due to lever operation, and good operability is achieved. Can be obtained. In addition, when the flow rate of the power regeneration oil passage exceeds the predetermined flow rate, a part of the flow rate is branched to the power regeneration bypass oil passage. Can be carried out stably. In addition, since the maximum flow rate of the power regeneration oil passage can be set large, even if a part of the flow rate is branched to the power regeneration bypass oil passage, the average inflow flow rate to the variable capacity motor increases, resulting in a large regeneration efficiency. Can be obtained.

  Further, the present invention is the above invention, wherein when the flow rate of the power regeneration oil passage exceeds the allowable flow rate of the variable displacement motor, the flow rate exceeding the allowable flow rate is not guided to the variable displacement motor, and the power regeneration is performed. It is characterized by being guided to the tank through a bypass oil passage.

  In the present invention configured as described above, the motor capacity control means only performs control to maintain a constant flow rate ratio between the flow control oil path and the power regeneration oil path, and the regenerative restriction control means does not allow the variable capacity motor. Since only the control of flowing the flow rate exceeding the flow rate to the tank through the power regeneration bypass oil passage is performed, both controls do not interfere with each other. If it is configured to return the flow rate that exceeds the allowable flow rate of the variable capacity motor to the flow control oil passage, it is necessary to further control the flow rate ratio between the flow control oil passage and the power regenerative oil passage and the spool opening area of the flow control valve. Become. Therefore, compared with such a configuration, the present invention can have a simple system configuration.

  Further, according to the present invention, in the above invention, an electronic control regulator that adjusts the capacity of the variable displacement motor, a regenerative restriction valve that includes an electromagnetic proportional valve provided in the power regeneration bypass oil passage, and a command capacity of the electronic control regulator A controller that controls the regenerative restriction valve so as to open the power regenerative detour oil passage when larger than a predetermined value, and the motor capacity control means includes the controller and the electronic control regulator, The regeneration restriction control means includes the controller and the regeneration restriction valve.

  In the present invention configured as described above, another means such as a flow meter for detecting the flow rate of the power regeneration oil passage is separately provided by estimating the flow rate of the power regeneration oil passage by the controller from the command capacity of the electronic control regulator. A simple configuration can be achieved without any problem.

  According to the present invention, in the above invention, the first pressure detection means comprises a first pressure detection oil passage that branches from the flow control oil passage, and the second pressure detection means branches from the power regeneration oil passage. The motor capacity control means includes a motor capacity control cylinder that adjusts the capacity of the variable capacity motor, and a motor capacity control spool that switches between supply and discharge of pressure oil in the motor capacity control cylinder. The first pressure detection oil passage and the second pressure detection oil passage are opposed to and connected to pressure receiving portions having the same area provided at both ends of the motor capacity control spool, and the regenerative restriction control means includes the power regeneration bypass When the regenerative restriction valve comprising a hydraulic pilot flow control valve provided in the oil passage and the motor capacity control cylinder are positioned on the side where the motor capacity is larger than the predetermined stroke, Some of the flow rate of the power regenerative oil passage is characterized by comprising a regenerative limiting valve pilot pressure control means for controlling a command pilot pressure for the regeneration limiting valve to direct to the power regenerative bypass oil passage.

  According to the present invention configured as described above, another means such as a flow meter for detecting the flow rate of the power regenerative oil passage is separately provided by mechanically estimating the flow rate of the power regenerative oil passage from the stroke of the motor capacity control cylinder. A simple configuration can be achieved without any problem.

  Further, the present invention is the above invention, wherein the regenerative restriction valve pilot pressure control means includes a pilot pump, a spool valve portion of the motor displacement control cylinder, and the regenerative restriction valve via the spool valve portion. A regenerative restriction valve control oil passage for guiding the pilot pressure, and the regenerative restriction valve pilot pressure control means detects the pressure detected by the second pressure detection oil passage more than the pressure detected by the first pressure detection oil passage. When high, when the spool valve portion of the motor capacity control cylinder and the pilot pump are connected, and the spool valve portion of the motor capacity control cylinder is located on the side where the motor capacity is larger than a predetermined stroke, The regenerative restriction valve control oil passage and the regenerative restriction valve are connected.

  The present invention configured as described above enables a system configuration that does not use electronic control by controlling the command pilot pressure of the regenerative restriction valve mechanically, that is, by a hydraulic circuit, from the stroke of the motor displacement control cylinder. In an environment with a lot of radio noise, more stable control can be realized as compared with the case where electronic control is used.

  In the present invention, the pressure of the first pressure detection means and the pressure of the second pressure detection means are controlled to the same pressure, and the flow rate of the flow control oil passage and the power regeneration oil passage is set to a fixed ratio, so that the actuator When operating, a flow rate is always generated in the flow control oil passage. Therefore, when the flow rate control valve is adjusted by lever operation to change the flow rate change of the flow rate control oil passage, the change in the flow rate necessarily affects the speed of the actuator. Reflected. Furthermore, since the flow rate ratio between the flow control oil passage and the power regeneration oil passage is always constant, the speed change amount of the actuator is always constant with respect to the flow change amount of the flow control oil passage due to lever operation, and good operability is achieved. Can be obtained. In addition, when the flow rate of the power regeneration oil passage exceeds the predetermined flow rate, a part of the flow rate is branched to the power regeneration bypass oil passage. Can be carried out stably. That is, the present invention can minimize the influence of the deterioration of the responsiveness to the speed control of the actuator, can ensure good operability in accordance with the spool type flow control valve, and can obtain workability with higher accuracy than before. In addition, since the maximum flow rate of the power regeneration oil passage can be set large in the present invention, even if a part of the flow rate is branched to the power regeneration bypass oil passage, the average inflow rate to the variable capacity motor is increased, A large regeneration efficiency can be obtained.

It is a side view which shows the hydraulic excavator mentioned as an example of the hydraulic working machine with which the hydraulic system which concerns on this invention is provided. FIG. 2 is an electric / hydraulic circuit diagram showing a first embodiment of a hydraulic system according to the present invention provided in the hydraulic excavator shown in FIG. 1. It is a flowchart which shows the process sequence in the controller with which 1st Embodiment is equipped. FIG. 3 is an enlarged view of a main part of FIG. 2. It is a hydraulic circuit diagram which shows 2nd Embodiment of this invention. It is a figure which shows operation | movement of 2nd Embodiment. It is a figure which shows an example of the flow volume change of a hydraulic-oil discharge oil path and a power regeneration oil path with respect to time in 1st Embodiment.

  Embodiments of a hydraulic system for a hydraulic working machine according to the present invention will be described below with reference to the drawings.

  FIG. 1 is a side view showing a hydraulic excavator exemplified as an example of a hydraulic working machine provided with a hydraulic system according to the present invention.

  As shown in FIG. 1, the excavator includes a traveling body 1, a revolving body 2 disposed on the traveling body 1, and a work device 3 that is rotatably attached to the revolving body 2. . The working device 3 includes a boom 4 that is connected to the swing body 2 so as to be rotatable in the vertical direction, an arm 5 that is connected to the tip of the boom 4 so as to be rotatable in the vertical direction, and a vertical motion at the tip of the arm 5. And a bucket 6 that is pivotably connected in the direction. The working device 3 includes a boom cylinder 4 a that operates the boom 4, an arm cylinder 5 a that operates the arm 5, and a bucket cylinder 6 a that operates the bucket 6. A cab 7 is provided on the revolving structure 2, and a machine room 8 in which a hydraulic pump or the like is accommodated is provided behind the cab 7.

  FIG. 2 is an electric / hydraulic circuit diagram showing a first embodiment of a hydraulic system according to the present invention provided in the excavator shown in FIG.

  The rotational power generation means 11 shown in FIG. 2 is a device that converts the energy of electricity or fossil fuel such as an electric motor or an engine into rotational power. The output shaft of the rotational power generation means 11 is the hydraulic pump 12 or the pilot pump 13. The hydraulic pump 12 and the pilot pump 13 are driven by the rotational power generation means 11 mechanically connected to the input shaft. The rotational power generation means 11 performs control to keep the rotation speed of the output shaft substantially constant.

  The hydraulic pump 12 is a device that generates hydraulic power that drives an actuator 14 to be described later. The hydraulic pump 12 can adjust the flow rate of hydraulic oil discharged per revolution, so that the hydraulic oil can be operated even when the rotational speed of the input shaft is constant. It is possible to change the discharge flow rate. The capacity of the hydraulic pump 12 is a regulator (not shown) based on an operation amount of a lever 15 (pilot pressure generated by a pilot valve 16 described later), a discharge pressure of the hydraulic pump 12, a load margin ratio of the rotating power generation means 11, and the like. Controlled by.

  The pilot pump 13 is a device that generates a pilot pressure used for controlling hydraulic equipment, which will be described later, and the flow rate of hydraulic oil discharged per rotation is fixed. The hydraulic oil discharged from the pilot pump 13 returns to the hydraulic oil tank 18 via the pilot relief valve 17, and the pressure in the pilot circuit is held at the set pressure of the pilot relief valve 17.

  The actuator 14 is, for example, the above-described boom cylinder 4a, that is, a double-acting single rod hydraulic cylinder, and is connected to the hydraulic pump 12 serving as a power source via a flow control valve 19. The flow control valve 19 is a three-position, four-port hydraulic pilot switching valve that operates with a pilot pressure adjusted by the pilot valve 16. When the pilot valve 16 is operated to the A side by the lever 15, the right side of the flow rate control valve 19 in this figure becomes a high pressure, and the spool of the flow rate control valve 19 moves to the left side. Then, the hydraulic pump 12 and the A port of the actuator 14 are connected, the actuator 14 performs a contracting operation, and the hydraulic oil discharged from the hydraulic oil discharged from the B port of the actuator 14 passes through the hydraulic oil discharge oil passage 20. The flow control oil passage 21 and the power regeneration oil passage 22 are branched, the hydraulic oil in the flow control oil passage 21 passes through the flow control valve 19 and returns to the hydraulic oil tank 18, and the hydraulic oil in the power regeneration oil passage 22 has a variable capacity. It passes through the motor 23 and returns to the hydraulic oil tank 18. When the actuator 14 is contracting (when the pilot valve 16 is operated to the A side), the switching valve 24 provided in the power regeneration oil passage 22 is in the open position, and the actuator 14 A part of the hydraulic oil discharged from the B port can pass through the variable displacement motor 23.

  On the other hand, when the pilot valve 16 is operated to the B side, the left side of the flow control valve 19 in FIG. 2 becomes high pressure, and the spool of the flow control valve 19 moves to the right side. Then, the hydraulic pump 12 and the B port of the actuator 14 are connected, the actuator 14 performs an extension operation, and the hydraulic oil discharged from the A port of the actuator 14 passes through the flow control valve 19 and returns to the hydraulic oil tank 18. When the actuator 14 is extending (when the pilot valve 16 is operated to the B side), the switching valve 24 provided in the power regeneration oil passage 22 is in the closed position, and the hydraulic pump The hydraulic oil supplied from 12 is supplied to the actuator 14 without flowing into the variable displacement motor 23.

  The output shaft of the variable displacement motor 23 is mechanically connected to the hydraulic pump 12 (the same applies to the rotational power generation means 11 and the pilot pump 13). Since the variable capacity motor 23 can change the hydraulic oil suction flow rate per rotation, the suction flow rate can be changed even if the output shaft rotation speed is constant. Since the variable displacement motor 23 and the hydraulic pump 12 are mechanically connected, the variable displacement motor 23 is always rotating. Therefore, when pressure oil is flowing into the input port of the variable capacity motor 23, the motor acts to generate the driving torque of the hydraulic pump 12 and assist the rotational power generation means 11, but sufficient hydraulic oil flows. When there is no oil, the hydraulic oil is sucked up from the makeup oil passage 29 to act as a pump, so that torque is absorbed (loss). In the first embodiment, in order to minimize the loss in this case, the variable displacement motor 23 is composed of a variable displacement motor having a minimum displacement of zero (no hydraulic oil is sucked or discharged even if the motor rotates). Yes.

  The first embodiment also includes first pressure detecting means provided in the flow control oil passage 21, such as a pressure gauge 27, second pressure detecting means provided in the power regeneration oil passage 2, such as a pressure gauge 28, and an actuator. Is provided with a pressure detection means, for example, a pressure gauge 100, to the pilot line that is boosted when the operation of contracting is performed (when the pilot valve 16 is operated to the A side).

  Further, in the first embodiment, when the pressure of the pressure gauge 27 is larger than the pressure of the pressure gauge 28, the capacity of the variable capacity motor 23 is reduced, and when the pressure of the pressure gauge 27 is smaller than the pressure of the pressure gauge 28. In addition, motor capacity control means is provided for increasing the capacity of the variable capacity motor 23 and fixing the capacity of the variable capacity motor 23 when the pressure gauge 27 and the pressure gauge 28 have the same pressure.

  Further, the first embodiment includes a power regeneration bypass oil passage 30 that is branched from the power regeneration oil passage 22 and communicated with the hydraulic oil tank 18. The power regeneration detour oil passage 30 is branched from a power regeneration oil passage 22 portion located between the connection point between the power regeneration oil passage 22 and the makeup circuit 29 and the switching valve 24. In the first embodiment, regenerative restriction control is performed to control a part of the flow rate of the power regeneration oil path 22 to the power regeneration bypass oil path 30 when the flow rate of the power regeneration oil path 22 is equal to or higher than a predetermined flow rate. Means are provided.

  In addition, the first embodiment includes an electronic control regulator 26 that adjusts the capacity of the variable capacity motor 23, and a regeneration limiting valve 31 that is an electromagnetic proportional valve provided in the power regeneration bypass oil passage 30. In addition, an electric signal output from the pressure gauges 27, 28, 100 is converted into pressure values, and an electronic control regulator 26 and a controller 25 for controlling the regenerative restriction valve 31 are provided based on these pressure values.

  In the first embodiment, the motor capacity control means described above includes the controller 25 and the electronic control regulator 26, and the regeneration limit control means described above includes the controller 25 and the regeneration limit valve 31.

  The operation of the first embodiment configured as described above will be described with reference to FIG.

  (A) The main flow in the figure shows the flow from the start to the stop of the hydraulic excavator. Among them, S1, S2, and S3 indicate the principle in the controller 25. First, when the hydraulic excavator is activated, the controller 25 sets the displacement command value q of the variable displacement motor 23 to qmin (zero in this embodiment) and the opening area command value A of the regenerative restriction valve 31 to zero. Then, electrical signals corresponding to the electronic control regulator 26 and the regeneration limiting valve 31 are output (S1). Subsequently, in process A, the capacity command value q of the variable capacity motor 23 and the opening area command value A of the regenerative restriction valve 31 at that time are determined (S2). Thereafter, electrical signals corresponding to q and A determined in S2 are output to the electronic control regulator 26 and the regeneration limiting valve 31 (S3). If the excavator is in a stopped state, the flow is terminated. If the hydraulic excavator is not in a stopped state (if it is still in an operating state), the flow returns to S2 to repeat the flow.

  Next, the process of determining the displacement command value q of the variable displacement motor 23 and the opening area command value A of the regeneration limiting valve 31 in the process A will be described with reference to FIG. First, based on the electrical signals output from the pressure gauges 27, 28, 100, the respective pressure values P1, P2, Pp are acquired. When Pp <δ, a routine (process B) for minimizing the capacity of the variable capacity motor 23 is performed. δ is set to several percent with respect to the full range of the pressure Pp, and when the pilot valve 16 is not operated to the A side due to a slight fluctuation of the pressure Pp itself or electrical noise of the pressure gauge, that is, This is a threshold value for preventing an unnecessary control command from being issued to the variable displacement motor 23 when the actuator 14 is not performing a reduction operation. At this time, the switching valve 24 provided in the power regeneration oil path 22 is in a position where the oil path is blocked by the spring force, and no flow rate is generated in the power regeneration oil path 22. And since the detection parts 27a and 28a of the pressure gauges 27 and 28 are connected, the pressure of both the detection parts 27a and 28a at this time, that is, the pressure P1 detected by the pressure gauge 27 and the pressure gauge 28 are detected. The pressure P2 is almost equal P1 = P2 (the pressure difference due to the height difference is minute and can be ignored).

  When the pilot valve 16 is operated to the A side and the pressure Pp is increased and δ ≦ Pp, the target capacity calculation of the variable capacity motor 23 is performed in the process A. In the process A, the capacity command value q of the variable capacity motor 23 is determined so that P2 is substantially equal to P1. Specifically, in the case of P2 <P1-ε, the displacement command value q of the variable displacement motor 23 and the opening area command value A of the regeneration limit valve 31 are adjusted in a direction to reduce the flow rate of the power regeneration oil passage 22 (Processing D). In the case of P1-ε ≦ P2 ≦ P1 + ε, the current q and A are held, and in the case of P1 + ε <P2, q and A are adjusted in the direction of increasing the flow rate of the power regeneration oil passage 22 (Process C). Note that ε is a dead zone for stabilizing the control, which is about several percent of the P2 maximum pressure, but this is determined by assuming a range in which malfunction can be sufficiently prevented with respect to the measurement error of the pressure gauge used. .

  In the process B shown in FIG. 3C, the capacity command value q of the variable capacity motor 23 is set to the minimum capacity qmin, the opening area target value A of the regenerative restriction valve 31 is set to zero, and the process ends.

  In the process C shown in FIG. 3D, the capacity command value q of the variable capacity motor 23 is increased by Δq. At this time, if q does not exceed the maximum capacity qmax, the process ends. On the other hand, when q exceeds the maximum capacity qmax, q = qmax is set, and the opening area command value A of the regeneration limiting valve 31 is further increased by ΔA. At this time, if A exceeds the maximum opening area Amax, the process is terminated with A = Amax.

  In process D shown in FIG. 3E, when the opening area command value A is zero, the capacity command value q of the variable capacity motor 23 is decreased by Δq. At this time, if q does not fall below the minimum capacity qmin, the process ends. If q falls below the minimum capacity qmin, the process ends with q = qmin. On the other hand, when the opening area command value A is larger than zero, A is decreased by ΔA. At this time, if A is greater than or equal to zero, the process is terminated, and if A is less than zero, the process is terminated with A = 0.

  As described above, in the first embodiment, when the variable capacity motor 23 is equal to or less than the maximum capacity by the processes in the processes C and D, the flow rate of the power regeneration oil passage 22 is adjusted by the capacity of the variable capacity motor 23 to obtain the variable capacity. When the motor 23 reaches the maximum capacity, the flow rate of the power regenerative oil passage 22 is adjusted by adjusting the flow rate of the power regenerative bypass oil passage 30 by the regenerative restriction valve 31.

Here, the relationship between controlling P1 and P2 to be substantially equal and the flow rates of the flow rate control oil passage 21 and the power regeneration oil passage 22 will be described. When a flow rate is generated in the oil passage, the downstream pressure drops due to the pipe resistance. The pipe resistance between the flow control oil passage 21 and the branch portion 32 of the power regeneration oil passage 22 and the detection portion 27a of the pressure gauge 27 is virtually equal between the equivalent throttle 44 and between the branch portion 32 and the detection portion 28a of the pressure gauge 28. , The equivalent resistance area 45 (orifice cross-sectional area) is Ao1 and Ao2. Further, the pressure of the branch portion 32 is PA, the flow rate of the flow rate control oil passage 21, and the flow rate of the power regeneration oil passage 22 are Q1 and Q2, respectively. The equivalent throttle does not have to be intentionally provided for the purpose of imparting pressure loss on the hydraulic circuit, and pressure loss such as a hose or a joint is used to explain the function of this embodiment. It is explicitly shown on the circuit. Applying to the general formula for pressure loss in orifice restriction,
Q1 = C · Ao1√ {2 (Pa−P1) / ρ}
Q2 = C · Ao2√ {2 (Pa−P2) / ρ}
C: Flow coefficient, ρ: Working density, and the relationship between Q1 and Q2 is
Q2 = Q1 · (Ao2 / Ao1) √ (Pa−P2) / (Pa−P1)
It becomes. Here, when P1 and P2 are the same pressure,
√ {(Pa−P2) / (Pa−P1)} = 1
Because
Q2 = Q1 · Ao2 / Ao1
Thus, it can be seen that the flow rate ratio between Q1 and Q2 is determined by the equivalent opening area ratio between the equivalent throttle 44 and the equivalent throttle 45. Here, the equivalent throttle 44 and the equivalent throttle 45 are pipe resistances, and their equivalent opening areas are fixed numerical values. Therefore, the flow rate ratio of Q1 and Q2 is controlled to a fixed ratio.

  The outline of the configuration and operation of the first embodiment is as described above, but a supplementary explanation is also given with reference to FIG. 4 regarding the transient state in a series of operations when the actuator 14 is contracted (when regeneration is performed). To do.

  First, when the lever 15 is not operated, the pilot pressure acting on the flow control valve 19 and the switching valve 24 of the power regeneration oil passage 22 from the pilot valve 16 is a tank pressure (nearly zero). In this state, the flow rate control valve 19 is in the center position by the spring force at both ends of the spool, and the switching valve 24 is in the position to close the oil passage by the spring force, so the flow rates of the flow rate control oil passage 21 and the power regeneration oil passage 22 are. Is zero. At this time, the controller 25 makes a determination of Pp <δ, issues a command to the electronic control regulator 26 to set the target capacity of the variable capacity motor 23 to the minimum capacity, and the capacity of the variable capacity motor 23 is zero.

  Next, when the pilot valve 16 is operated to the A side from the state in which the lever 15 is not operated, immediately after the operation, the spool of the flow control valve 19 starts to move to the left side, and the hydraulic pump 12 and the A port of the actuator 14 are connected. The oil passage and the oil passage connecting the hydraulic oil tank 18 and the B port of the actuator 14 begin to open. The pilot pressure also acts on the switching valve 24 of the power regenerative oil passage 22 to push the spring and the oil passage starts to open, and the flow control oil passage 21 gradually starts to generate a flow rate. Since a pressure loss occurs when the flow rate is generated, the pressure decreases toward the downstream, and the pressure P1 of the flow control oil passage 21 becomes smaller than the pressure Pa of the branch portion 32. On the other hand, since no flow rate has yet occurred in the power regeneration oil passage 22, no pressure loss occurs, and Pa = P2. Here, in a state where P2 ≦ P1 + ε, the variable displacement motor 23 is still in the control state of zero displacement, and no flow rate is generated in the power regeneration oil passage 22. Further, as time advances and P1 + ε <P2, the value of the target capacity of the variable capacity motor 23 in the controller 25 starts to increase. As time further advances, the target capacity command value from the controller 25 to the electronic control regulator 26 also increases appropriately, and a flow rate corresponding to the capacity of the variable capacity motor 23 is generated in the power regeneration oil passage 22. When a flow rate is generated in the power regeneration oil passage 22, P2 becomes smaller than Pa due to pressure loss.

  If this state continues, the state of P1−ε ≦ P2 ≦ P1 + ε is eventually reached, and the capacity of the variable displacement motor 23 at that time is held. When the displacement command value q of the variable displacement motor 23 exceeds the maximum displacement qmax in the state of P1 + ε <P2, the opening area command value A of the regeneration limit valve 31 in the controller 25 increases, and the power regeneration oil path A part of the flow rate 22 is guided to the power regeneration bypass oil passage 30, bypasses the variable capacity motor 23, and is guided to the hydraulic oil tank 18. For this reason, also in the flow rate range exceeding the absorption flow rate of the variable capacity motor 23, the flow rate of the power regeneration oil passage 22 increases until the state of P1-ε ≦ P2 ≦ P1 + ε is reached. In this way, P2 is controlled to be substantially equal to P1, and as described above, the flow rate Q2 of the power regenerative oil passage is adjusted to a fixed ratio with respect to the flow rate Q1 of the flow rate control oil passage 21.

  Next, the case where the lever 15 is returned from the state where the pilot valve 16 is operated to the A side and the flow rate Q2 of the power regenerative oil passage 22 is adjusted to a fixed ratio with respect to Q1 will be described. When the lever 15 starts to be returned, the spool of the flow control valve 19 starts to move to the right, the oil passage connecting the hydraulic pump 12 and the A port of the actuator 14, and the oil connecting the hydraulic oil tank 18 and the B port of the actuator 14. The road begins to close. At this time, the flow rate Q1 of the flow rate control oil passage 21 starts to gradually decrease. When the flow rate Q1 decreases, the pressure loss at the equivalent throttle 44 decreases, so the pressure P1 increases. Then, when time advances and the state of P2 <P1-ε is reached, in the state where the regenerative restriction valve 31 is open, the opening area command value A of the regenerative restriction valve 31 in the controller 25 is decreased, and the opening area command value When A is zero, the value of the capacity command value q of the variable capacity motor 23 decreases, the capacity of the variable capacity motor 23 decreases accordingly, and the flow rate Q2 of the power regeneration oil path 22 decreases. As the flow rate Q2 decreases, the pressure loss at the equivalent throttle 45 decreases, and the pressure P2 increases. Thus, control is performed so that P2 follows P1, and readjustment is performed so that Q1 and Q2 have a fixed ratio.

  By the way, when the operation of returning the lever 15 is performed slowly, the flow rate Q2 decreases while maintaining a fixed ratio with respect to Q1, but when the lever 15 is returned suddenly, the flow rate control oil path The situation where the readjustment of the flow reduction of the power regeneration oil passage 22 cannot catch up with the flow reduction of 21 occurs. In this situation, when the lever 15 is returned to the neutral (no operation) state, the switching valve 24 of the power regeneration oil passage 22 is also moved to the position where the oil passage is closed, and the flow of hydraulic oil in the power regeneration oil passage 22 is forced. Is blocked. At this moment, since the variable displacement motor 23 has a certain capacity which is not zero, by sucking the hydraulic oil from the makeup oil passage 29, cavitation due to insufficient supply flow rate to the suction port is prevented and variable. While suppressing an increase in absorption torque (power loss) due to the pumping action of the capacity motor 23, damage to the variable capacity motor 23 is minimized. Further, since the pilot pressure Pp becomes zero when the lever 15 returns to the neutral position, the controller 25 makes a determination of Pp <δ and sets the target capacity of the variable capacity motor 23 to the minimum capacity with respect to the electronic control regulator 26. And finally the capacity of the variable capacity motor 23 returns to zero. In this way, when a sudden lever return operation is performed, the actuator 14 can be suddenly stopped regardless of the capacity state of the variable displacement motor 23, so that danger due to delay of the stop of the actuator 14 in an emergency is prevented. can do.

  In the first embodiment described above, since the flow rate is always generated in the flow rate control valve 19 when the actuator 14 is operated, the flow rate adjusting action in the flow rate control valve 19 generated in response to the change in the lever operation amount. Is always reflected in the operating speed of the actuator 14. Naturally, since the flow rate control by the variable displacement motor 23 that is inferior in response to the flow rate control valve 19 is included, the response to the lever operation of the present embodiment is that the total flow rate of the hydraulic oil supplied to and discharged from the actuator 14 is This is inferior to a hydraulic system of a conventional general hydraulic working machine that flows to the flow control valve 19. However, by setting the flow rate ratio between the flow control oil passage 21 and the power regenerative oil passage 22 so that the poor responsiveness falls within a problem-free level in accordance with the responsiveness of the flow control of the variable capacity motor 23, it is practical. Sex can be secured. Furthermore, in this first embodiment, since the flow rate ratio between the flow control oil passage 21 and the power regeneration oil passage 22 is always constant, the speed change amount of the actuator 14 with respect to the flow change amount of the flow control oil passage 21 by lever operation. Is always constant, and good operability can be obtained. In addition, when the flow rate of the power regeneration oil passage 22 becomes equal to or higher than the predetermined flow rate, a part of the flow rate is branched to the power regeneration bypass oil passage 30, so that the flow rate exceeding the allowable flow rate does not flow to the variable capacity motor 23. The above control can be stably performed. That is, this first embodiment can minimize the influence of the deterioration of the responsiveness to the speed control of the actuator 14, can ensure good operability according to the spool type flow control valve, and can obtain highly accurate workability. .

  Further, according to the first embodiment, since the maximum flow rate of the power regeneration oil passage 22 can be set large, even if a part of the flow rate is branched to the power regeneration bypass oil passage 30, the variable capacity motor 23 The average inflow flow rate into the water increases, and a large regeneration efficiency can be obtained. This point will be described with reference to FIG. FIG. 7 shows an example of changes in the flow rates of the hydraulic oil discharge oil passage 20 and the power regeneration oil passage 22 with respect to time. In FIG. 7, C0 is the flow rate of the hydraulic oil discharge oil passage 20, and C1 is the flow rate of the power regeneration oil passage 22 at a setting in which the maximum flow rate of the power regeneration oil passage 22 is kept within the allowable flow rate Qm of the variable capacity motor 23. , C2 indicates the flow rate of the power regeneration oil path 22 when the maximum flow rate of the power regeneration oil path 22 is set to a value exceeding the allowable flow rate Qm of the variable capacity motor 23. C1 and C2 both change at a flow rate of a fixed ratio with respect to C0. However, as shown in the section S, since the flow rate exceeding Qm branches to the power regeneration bypass oil passage 30, the portion of C2 ′ is a variable capacity motor. 23 does not flow. Therefore, when the maximum flow rate of the power regeneration oil passage 22 is set to a value exceeding the allowable flow rate Qm of the variable capacity motor 23 (C2), it is not possible to regenerate all the power flowing into the power regeneration oil passage 22. However, since C2 can take a larger average flow rate than C1, it can be seen that C2 can regenerate larger power. The maximum flow rate of the power regeneration oil passage 22, that is, the change of the flow rate ratio between the flow control oil passage 21 and the power regeneration oil passage 22 is changed from the branch portion 32 of the flow control oil passage 21 and the power regeneration oil passage 22 from the pressure gauge. This is possible by intentionally adjusting the pressure loss in each oil passage section that occurs between the 27 detection units 27a and the detection unit 28a of the pressure gauge 28. Further, by estimating the flow rate of the power regenerative oil passage 22 with the controller 25 from the command capacity of the electronic control regulator 26, it is simple without providing another means such as a flow meter for detecting the flow rate of the power regenerative oil passage 22. It can be set as a simple structure.

  In the first embodiment, as described above, when the flow rate of the power regeneration oil passage 22 exceeds the allowable flow rate of the variable displacement motor 23, the flow rate exceeding the allowable flow rate is changed to the variable displacement motor 23. Without being led to the tank 18 via the power regeneration bypass oil passage 30. In the first embodiment configured as described above, the motor capacity control means performs only control for keeping the flow rate ratio between the flow rate control oil passage 21 and the power regeneration oil passage 22 constant, and the regenerative restriction control means is variable. Since only the control of flowing the flow rate exceeding the allowable flow rate of the capacity motor 23 to the tank 18 via the power regeneration bypass oil passage 30 is performed, both controls do not interfere with each other. If the flow rate that exceeds the allowable flow rate of the variable displacement motor 23 is returned to the flow rate control oil passage 21, the flow rate ratio between the flow rate control oil passage 21 and the power regeneration oil passage 22 and the spool opening area of the flow rate control valve 19 are set. Further control is required. Therefore, compared with such a configuration, the first embodiment can have a simple system configuration.

  Next, a second embodiment of the present invention will be described with reference to FIGS. In addition, the part which is common in 1st Embodiment is abbreviate | omitted, and only a different part is demonstrated.

  In the second embodiment, the first pressure detection means provided in the flow control oil passage 21 includes a first pressure detection oil passage 50 branched from the flow control oil passage 21, and the second pressure detection means 50 is provided in the power regeneration oil passage 22. The pressure detection means includes a second pressure detection oil passage 51 that branches from the power regeneration oil passage 22.

  Further, a motor capacity control means for controlling the capacity of the variable capacity motor 23, a motor capacity control cylinder 52 for adjusting the capacity of the variable capacity motor 23, and a motor capacity control for switching between supply and discharge of pressure oil in the motor capacity control cylinder 52. And a spool 53. The first pressure detection oil passage 50 and the second pressure detection oil passage 51 are connected to the pressure receiving portions having the same area provided at both ends of the motor capacity control spool 53 so as to face each other.

  Further, a switching valve 54 is provided in the first pressure detection oil passage 50, and a switching valve 55 is provided in the oil passage connecting the motor capacity control spool 53 and the motor capacity control cylinder 52.

  Further, the second embodiment is a regenerative restriction control means for controlling so that a part of the flow rate of the power regeneration oil passage 22 is guided to the power regeneration bypass oil passage 30 when the flow rate of the power regeneration oil passage 22 is equal to or higher than a predetermined flow rate. However, when the motor capacity control cylinder 52 is located on the side where the motor capacity is larger than the predetermined stroke, the part of the flow rate of the power regeneration oil path 22 is transferred to the power regeneration bypass oil path 30. Regenerative limiting valve pilot pressure control means for controlling the command pilot pressure of the regenerative limiting valve 101 so as to guide is included.

  The regenerative restriction valve pilot pressure control means includes a pilot pump 13, a spool valve portion 52a of the motor displacement control cylinder 52, and a regenerative restriction that guides the pilot pressure of the pilot pump 13 to the regenerative restriction valve 101 via the spool valve portion 52a. And a valve control oil passage 56. The regenerative restriction valve pilot pressure control means is configured so that when the pressure detected by the second pressure detection oil passage 51 is higher than the pressure detected by the first pressure detection oil passage 50, the spool valve portion 52a of the motor capacity control cylinder 52 is used. And the pilot pump 13 are connected, and the regenerative restriction valve control oil passage 56 and the regenerative restriction valve 101 are connected when the spool valve portion 52a of the motor capacity control cylinder 52 is positioned on the side where the motor capacity is larger than the predetermined stroke. It is something to be made.

  As shown in FIG. 6A, the spool valve portion 52a of the motor capacity control cylinder 52 has 5 ports (A to E), and one end side protrudes from the housing to adjust the capacity of the variable capacity motor 23. It is a mechanism. When the spool valve portion 52a moves rightward, the motor capacity increases, and when the spool valve portion 52a moves leftward, the motor capacity decreases. When the lever 15 is not operated, the spool valve portion 52a is positioned on the left side by the compression spring provided at the right end portion of the spool valve portion 52a, and the motor capacity is minimized. Further, the variable displacement motor 23 of the second embodiment is configured to increase the displacement when a flow rate is generated at the inlet port (the compression spring of the motor displacement control cylinder 52 is compressed and the spool valve portion 52a is moved to the right. The direction to be automatically changed in the direction of Therefore, the motor displacement control cylinder 52 applies a pilot pressure to the B port to reduce the displacement against the automatic displacement adjustment operation of the variable displacement motor 23 (the repulsive force of the compression spring of the motor displacement control cylinder 52). In the same direction as that). When the spool valve portion 52a moves to the right and the motor capacity is near the maximum capacity, the opening area of the E port that has been connected to the hydraulic oil tank 18 gradually decreases until a new opening area of the A port. By gradually increasing, the pressure of the C port connected to the regenerative restriction valve 101 is gradually increased, and the regenerative restriction valve 101 is gradually opened accordingly.

  A motor capacity control spool 53 is connected to the A and B ports of the motor capacity control cylinder 52, and the pilot pump 13 is connected to the motor capacity control spool 53. Further, a first pressure detection oil passage 50 and a second pressure detection oil passage 51 are connected to both ends of the motor capacity control spool 53, and the motor capacity control spool is set according to the pressure difference between the two pressure detection oil passages 50 and 51. 53 moves. When the pressure P1 of the first pressure detection oil passage 50 is high, the spool 53 moves to the right, the pilot pump 13 is connected to the B port of the motor capacity control cylinder 52, and the motor capacity decreases. When the pressure P2 of the second pressure detection oil passage 51 is high, the spool 53 moves to the left side, the B port of the motor capacity control cylinder 52 is connected to the tank, the thrust of the motor capacity control cylinder 52 disappears, and the variable capacity motor 23 The motor capacity increases due to the automatic capacity adjustment function. In the second embodiment, the springs at both ends of the motor capacity control spool 53 are set so that the spool is in the center position when P1 and P2 are at the same pressure. When the lever 15 is not operated (at neutral), the switching valve 54 is in a position where the first pressure detection oil passage 50 and the second pressure detection oil passage 51 are connected, and P1 and P2 have the same pressure. Therefore, the motor capacity control spool 53 is in the center position.

  When the lever 15 is operated to reduce the actuator 14, the spool of the flow control valve 19 moves to the left as shown in FIG. 6B, and the switching valve 55 shown in FIG. The closed position, the switching valve 24 is opened, and the switching valve 54 is switched to a position where the first pressure detection oil passage 50 and the spool oil passage are communicated with each other. Then, the hydraulic oil discharged from the actuator 14 returns from the spool of the flow control valve 19 to the hydraulic oil tank 18 through the hydraulic oil discharge oil passage 20 and the flow control oil passage 21, and pressure loss is caused by the equivalent throttle 44. Occur. Immediately after the start of the lever operation, hydraulic oil tends to flow through the power regeneration oil passage 22, but no pressure loss has occurred in the equivalent throttle 45 because the variable displacement motor 23 is in the zero displacement position and no flow is generated. Absent.

  Therefore, the motor capacity control spool 53 moves to the left, and the B port of the motor capacity control cylinder 52 communicates with the hydraulic oil tank 18 as shown in FIG. At the same time, due to the pressure generated in the power regeneration oil path 22, the capacity of the variable capacity motor 23 automatically starts to increase, and a flow rate is generated in the power regeneration oil path 22. When a flow rate is generated in the power regenerative oil passage 22, a pressure loss is generated in the equivalent throttle 45, and the pressure P2 detected in the second pressure detection oil passage 51 starts to decrease, and the state shown in FIG. Then, when the flow rate of the power regenerative oil passage 22 increases and P2 becomes equal to or lower than a predetermined pressure with respect to the pressure P1 of the first pressure detection oil passage 50, the motor capacity control spool 53 moves to the right side (( e) As shown in the figure, the pilot pressure acts on the B port of the motor capacity control cylinder 52 to reduce the motor capacity.

  Further, when the variable displacement motor 23 is near the maximum capacity, the A port and the C port connected to the pilot port of the regenerative restriction valve 101 communicate with each other as described above. At this time, as shown in FIG. If P2 is still larger than P1, since the motor displacement control spool 53 is on the left side, the pilot pressure acts on the pilot port of the regenerative restriction valve 101 via the A and C ports of the motor displacement control cylinder 52. The restriction valve 101 is opened. When the regenerative restriction valve 101 is opened, a part of the flow rate of the power regeneration oil passage 22 is guided to the power regeneration bypass oil passage 30 and bypasses the variable capacity motor 23 and flows into the hydraulic oil tank 18. That is, a flow rate exceeding the capacity of the variable capacity motor 23 can be supplied to the power regeneration oil passage 22.

  In this way, the capacity of the variable capacity motor 23 is automatically adjusted so that P2 has the same pressure as P1. As described in the first embodiment, controlling P2 to be the same pressure as P1 is the same as controlling the flow rate ratio of Q1 and Q2 to a fixed ratio. Therefore, even in the second embodiment, as in the first embodiment, the influence of the deterioration of the responsiveness to the speed control of the actuator 14 is minimized, and a good operability equivalent to the spool type flow control valve is achieved. Can be ensured, and highly accurate workability can be obtained.

  Further, according to the second embodiment, another means such as a flow meter for detecting the flow rate of the power regeneration oil path 22 is estimated by estimating the flow rate of the power regeneration oil path 22 from the stroke of the motor capacity control cylinder 52. A simple configuration can be obtained without providing it separately. Furthermore, according to the second embodiment, a system that does not use electronic control by controlling the command pilot pressure of the regenerative restriction valve 31 mechanically, that is, by a hydraulic circuit, from the stroke of the motor displacement control cylinder 52. The configuration is possible, and more stable control can be realized in an environment with a lot of radio noise as compared with the case where electronic control is used.

DESCRIPTION OF SYMBOLS 1 Traveling body 2 Revolving body 3 Working apparatus 4 Boom 4a Boom cylinder 11 Rotational power production | generation means 12 Hydraulic pump 13 Pilot pump 14 Actuator 15 Lever 16 Pilot valve 18 Hydraulic oil tank 19 Flow control valve 20 Hydraulic oil discharge oil path 21 Flow control oil Path 22 Power regeneration oil path 23 Variable capacity motor 24 Switching valve 25 Controller 26 Electronic control regulator 27 Pressure gauge (first pressure detecting means)
28 Pressure gauge (second pressure detection means)
30 Power regeneration detour oil passage 31 Regenerative restriction valve 32 Branching portion 44 Equivalent restriction 45 Equivalent restriction 50 First pressure detection oil passage (first pressure detection means)
51 Second pressure detection oil passage (second pressure detection means)
52 Motor capacity control cylinder 52a Spool valve part 53 Motor capacity control spool 54 Switching valve 55 Switching valve 56 Regenerative restriction valve control oil path 100 Pressure gauge 101 Regenerative restriction valve

Claims (5)

In a hydraulic system of a hydraulic working machine that generates rotational power by supplying rotational power to a hydraulic pump from the rotational power generating means and generating hydraulic power and operating an actuator by the hydraulic power,
The hydraulic oil discharge hydraulic path from the actuator is connected to the spool of the flow control valve controlled by lever operation. Branch to a power regenerative oil path that is an oil path connected to a variable capacity motor that converts to reusable energy,
First pressure detecting means provided in the flow control oil passage, second pressure detecting means provided in the power regeneration oil passage,
When the pressure of the first pressure detection means is larger than the pressure of the second pressure detection means, the capacity of the variable displacement motor is reduced, and the pressure of the first pressure detection means is lower than the pressure of the second pressure detection means. Motor capacity control means for increasing the capacity of the variable capacity motor when the pressure is smaller, and fixing the capacity of the variable capacity motor when the pressures of the first pressure detection means and the second pressure detection means are the same;
A power regeneration detour oil passage branched from the power regeneration oil passage;
Regeneration restriction control means for controlling so that a part of the flow rate of the power regeneration oil path is guided to the power regeneration bypass oil path when the flow rate of the power regeneration oil path is equal to or higher than a predetermined flow rate is provided. Hydraulic system for work equipment. In the hydraulic system of the hydraulic working machine according to claim 1,
When the flow rate of the power regenerative oil passage exceeds the allowable flow rate of the variable capacity motor, the flow rate exceeding the permissible flow rate is guided to the tank via the power regeneration detour oil path without being guided to the variable capacity motor. A hydraulic system for a hydraulic working machine. In the hydraulic system of the hydraulic working machine according to claim 1 or 2,
When the electronic control regulator that adjusts the capacity of the variable capacity motor, the regenerative restriction valve that consists of an electromagnetic proportional valve provided in the power regeneration bypass oil passage, and the command capacity of the electronic control regulator is larger than a predetermined value, A controller for controlling the regenerative restriction valve so as to open the power regeneration detour oil passage,
The motor capacity control means includes the controller and the electronic control regulator,
The hydraulic system for a hydraulic working machine, wherein the regenerative restriction control means includes the controller and the regenerative restriction valve. In the hydraulic system of the hydraulic working machine according to claim 1 or 2,
The first pressure detection means comprises a first pressure detection oil passage branched from the flow control oil passage, the second pressure detection means comprises a second pressure detection oil passage branched from the power regeneration oil passage,
The motor capacity control means includes a motor capacity control cylinder that adjusts the capacity of the variable capacity motor, and a motor capacity control spool that switches between supply and discharge of pressure oil in the motor capacity control cylinder,
The first pressure detection oil passage and the second pressure detection oil passage are opposed to and connected to pressure receiving portions having the same area provided at both ends of the motor capacity control spool,
When the regenerative restriction control means is positioned on the side where the regenerative restriction valve composed of a hydraulic pilot flow control valve provided in the power regeneration bypass oil passage and the motor capacity control cylinder are larger than a predetermined stroke, A regenerative limiting valve pilot pressure control means for controlling a command pilot pressure of the regenerative limiting valve so as to guide a part of the flow rate of the power regenerative oil path to the power regenerative detour oil path. Hydraulic system. In the hydraulic system of the hydraulic working machine according to claim 4,
The regenerative restriction valve pilot pressure control means includes a pilot pump, a spool valve portion of the motor capacity control cylinder, and a regenerative restriction valve control oil that guides the pilot pressure of the pilot pump to the regenerative restriction valve via the spool valve portion. The regenerative restriction valve pilot pressure control means includes the motor displacement control cylinder when the pressure detected by the second pressure detection oil passage is higher than the pressure detected by the first pressure detection oil passage. When the spool valve portion of the motor displacement control cylinder is located on the side where the motor displacement is larger than a predetermined stroke, the regenerative restriction valve control oil passage and the pilot pump are connected. A hydraulic system for a hydraulic working machine, wherein a regenerative restriction valve is connected.