WO1998049450A1 - Systeme de transmission pour moteurs hydrauliques - Google Patents

Systeme de transmission pour moteurs hydrauliques Download PDF

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Publication number
WO1998049450A1
WO1998049450A1 PCT/JP1998/001921 JP9801921W WO9849450A1 WO 1998049450 A1 WO1998049450 A1 WO 1998049450A1 JP 9801921 W JP9801921 W JP 9801921W WO 9849450 A1 WO9849450 A1 WO 9849450A1
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WO
WIPO (PCT)
Prior art keywords
pressure
valve
hydraulic
port
hydraulic pump
Prior art date
Application number
PCT/JP1998/001921
Other languages
English (en)
Japanese (ja)
Inventor
Sadao Nunotani
Naoki Ishizaki
Original Assignee
Komatsu Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Komatsu Ltd. filed Critical Komatsu Ltd.
Publication of WO1998049450A1 publication Critical patent/WO1998049450A1/fr

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/123—Drives or control devices specially adapted therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2271—Actuators and supports therefor and protection therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F15B2011/0243—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits the regenerative circuit being activated or deactivated automatically

Definitions

  • the present invention relates to a hydraulic motor drive system such as a hydraulic motor for a winch that rotationally drives a winch of a hydraulic crane and a hydraulic motor for traveling that rotationally drives a crawler belt of a hydraulic excavator. is there.
  • a hydraulic motor drive system such as a hydraulic motor for a winch that rotationally drives a winch of a hydraulic crane and a hydraulic motor for traveling that rotationally drives a crawler belt of a hydraulic excavator.
  • a drive system shown in Fig. 1 is known as a system for driving a traveling hydraulic motor that rotationally drives a crawler belt of a hydraulic shovel.
  • This drive system basically includes a hydraulic pump 1, an operation valve 2, and a counterbalance valve 3. Then, by switching the operation valve 2 from the neutral position a to the first position b, pressure oil is supplied to one port 5 of the hydraulic motor 4, and the discharge pressure of the hydraulic pump 1 exceeds a predetermined pressure. Then, the counterbalance valve 3 moves from the neutral position c to the first position d, and the return pressure oil of the other port 6 of the hydraulic motor 4 is moved to the first position d of the counterbalance valve 3.
  • the hydraulic fluid flows into the tank 7 through the first position b of the operation valve 2, and the hydraulic motor 4 is driven to rotate in the negative direction.
  • the hydraulic motor 4 is rotated by an external force to perform a pumping operation. Pressure drops.
  • the counterbalance valve 3 moves toward the neutral position c, and the other side of the hydraulic motor 4 The flow of the pressure oil discharged from the port 6 is stopped or throttled, thereby restricting the flow of the return pressure oil from the hydraulic motor 4 and braking the hydraulic motor 4.
  • the counterbalance valve 3 When the operation valve 2 is in the second position e, the counterbalance valve 3 is switched to the second position f, and operates as described above.
  • the drive system of the hydraulic motor for the winch that rotationally drives the winch of the hydraulic crank has the same configuration and operation as the drive system shown in FIG. 1 described above.
  • the hydraulic motor drive system for the hydraulic excavator traveling and the hydraulic motor for the winch of the hydraulic crane are mounted between the operation valve 2 and the hydraulic motor 4.
  • a brake valve 3 is provided, and when the hydraulic motor 4 is rotated by an external force, the counterbalance valve 3 is moved toward the neutral position c so that a braking force is applied to the hydraulic motor 4. Configuration.
  • the drive system with the regenerative function described above is hydraulically operated. It can be applied to hydraulic motors for running vehicles and winches for hydraulic crane.
  • a throttle 9a is provided in the drain circuit 7a, and the upstream side of the throttle 9a is connected to the pump discharge path 1a via the check valve 9b, and the return oil is It is conceivable that pressure is generated to regenerate into the pump discharge path 1a.
  • the pressure of the return oil must be higher than the pump discharge pressure.
  • the valve 3 When the valve 3 is in the neutral position c or the opposite position, the oil returns to the drain circuit 7a and the oil stops flowing.
  • the operating valve 2 is set to the first position b to supply pressure oil to one port 5 of the hydraulic motor 4, and the counterbalance valve 3 is set to the first position d by the pressure of the first pressure receiving portion 3a.
  • the counterbalance valve 3 is Since the pressure of the second pressure receiving portion 3b of FIG. 3 becomes higher than the pressure of the first pressure receiving portion 3a, the counter balance valve 3 becomes the neutral position c or the second position f. Return to a and oil stops flowing.
  • an object of the present invention is to provide a hydraulic motor drive system that can solve the above-described problem. Disclosure of the invention
  • a first aspect of the hydraulic motor drive system according to the present invention for achieving the above object is as follows.
  • a neutral position provided between the hydraulic motor and the operation valve, wherein a return pressure oil from the hydraulic motor does not flow through the operation valve, and a flow position through which the return pressure oil flows through the operation valve;
  • the hydraulic pump is switched to a circulation position when the discharge pressure of the hydraulic pump exceeds a predetermined pressure, and is switched to a neutral position when the discharge pressure oil of the hydraulic pump is equal to or lower than a predetermined pressure.
  • a counter balance valve that is prohibited from switching to the neutral position by return pressure oil when the circulation position is reached by the discharge pressure
  • a hydraulic motor drive system wherein the regenerative circuit is connected to a discharge path of the hydraulic pump via a check valve.
  • the operating valve is switched to supply the discharge pressure oil of the hydraulic pump to one port of the hydraulic motor, and when the discharge pressure becomes high, the counterbalance valve is placed in the circulation position and the hydraulic motor is turned off. Return pressure oil flows to the tank via the counterbalance valve, operating valve, and regenerative circuit. At the same time, the counterbalance valve does not operate to the neutral position due to the pressure of the return pressure oil.
  • the return pressure oil from the hydraulic motor can be regenerated and reused in the discharge path of the hydraulic pump.
  • the regenerative circuit be provided with a back pressure valve which is brought into the throttle communication position by a spring force and becomes the communication position when the discharge pressure of the hydraulic pump is higher than a set pressure.
  • the back pressure valve When the discharge pressure of the hydraulic pump is higher than the set pressure by rotating the hydraulic motor with the discharge pressure oil of the hydraulic pump, the back pressure valve is in the communicating position. When the hydraulic motor is rotated by external force and the discharge pressure of the hydraulic pump is lower than the set pressure, the back pressure valve is in the throttle communication position.
  • the hydraulic motor when the hydraulic motor is rotating with the hydraulic oil discharged from the hydraulic pump, the return hydraulic oil from the hydraulic motor flows smoothly to the tank and the pressure does not increase.
  • the hydraulic motor can be rotated with a driving torque corresponding to the pressure of the discharge pressure oil of the hydraulic pump. Also, when the hydraulic motor is rotated by an external force, the pressure of the return pressure oil flowing in the regenerative circuit increases, and the return pressure oil flows into the discharge path of the hydraulic pump.
  • the counterbalance valve is held at a neutral position by a spring force, and when the discharge pressure of a hydraulic pump supplied to one of the pressure receiving parts exceeds a predetermined pressure, the counterbalance valve becomes one of the circulation positions and the other becomes the circulation position. If the discharge pressure of the hydraulic pump supplied to the pressure receiving section exceeds a predetermined pressure, it will be the other circulation position,
  • a second aspect of the present invention provides The discharge pressure oil of the hydraulic pump is supplied and controlled to the left and right hydraulic motors via the left and right pressure compensation valves and the left and right operation valves, respectively.
  • the hydraulic pump is switched to the circulation position when the discharge pressure of the hydraulic pump exceeds a predetermined pressure, and is switched to the neutral position when the discharge pressure oil of the hydraulic pump is equal to or lower than a predetermined pressure.
  • Left and right counterbalance valves are provided, which are prevented from switching to the neutral position by return pressure oil by being returned to the circulation position by the discharge pressure of the hydraulic pump,
  • the return pressure oil from the left and right hydraulic motors respectively communicates with the left and right regenerative circuits flowing out of the left and right operation valves by the pressure of the first pressure receiving portion and the throttle communication position by the pressure of the second pressure receiving portion.
  • Left and right back pressure valves are respectively communicates with the left and right regenerative circuits flowing out of the left and right operation valves by the pressure of the first pressure receiving portion and the throttle communication position by the pressure of the second pressure receiving portion.
  • the first pressure receiving portions of the left and right back pressure valves are respectively connected to the output sides of the left and right pressure compensating valves,
  • the left and right pressure compensating valves are respectively formed with a first port and a second port which are shut off when the opening area is small and communicate with each other when the opening area is large,
  • the first ports of the left and right pressure compensating valves communicate with the second ports of the left and right back pressure valves, respectively, and the first ports of the left and right pressure compensating valves communicate with each other,
  • This is a hydraulic motor drive system in which second ports of the left and right pressure compensating valves are respectively connected to left and right load pressure introduction paths.
  • the return oil of the driven hydraulic motor is regenerated during left-right turning, and excess hydraulic oil can be supplied to the driven hydraulic motor by that amount, so that a decrease in vehicle speed can be reduced.
  • each pressure compensating valve when descending, the opening area of each pressure compensating valve is small and the load pressure does not act on the second pressure receiving part of the back pressure valve, so that the back pressure valve is in the communicating position, and the return pressure oil of the left and right hydraulic motors is Not regenerated.
  • FIG. 1 is a circuit diagram of a conventional hydraulic motor drive system.
  • FIG. 2 is a circuit diagram of a hydraulic motor drive system according to the first embodiment of the present invention.
  • FIG. 3 is a cross-sectional view showing a specific structure of the operation valve, the back pressure valve, the check valve, and the pressure compensating valve according to the first embodiment.
  • FIG. 4 is a cross-sectional view showing a specific structure of the counterbalance valve according to the first embodiment.
  • FIG. 5 is a traveling hydraulic circuit diagram showing the second embodiment of the present invention.
  • FIG. 6 shows the operation valve, the back pressure valve, the check valve, and the pressure of the second embodiment. It is sectional drawing which shows the specific structure of a force compensating valve.
  • FIG. 7 is a traveling hydraulic circuit diagram showing the third embodiment of the present invention.
  • FIG. 8 is a cross-sectional view showing a specific structure of the operation valve, the back pressure valve, the check valve, and the pressure compensating valve according to the third embodiment.
  • the discharge path 11 of the hydraulic pump 10 is connected to the pump port 14 of the operation valve 13 via the pressure compensating valve 12.
  • the first actuator port 15 of the operation valve 13 is connected to one port 18 of the hydraulic motor 17 via the first main circuit 16.
  • the second port 19 of the operation valve 13 is connected to the other port 21 of the hydraulic motor 17 via the second main circuit 20.
  • the regenerative port 22 of the operation valve 13 communicates with the tank 24 in the regenerative circuit 23.
  • the regenerative circuit 23 is provided with a back pressure valve 25.
  • the upstream side of the back pressure valve 25 in the regenerative circuit 23 is connected to the output side of the pressure compensating valve 12 in the discharge path 11 of the hydraulic pump 10 by a check valve 26.
  • the tank port 27 of the operation valve 13 is connected to the tank 24.
  • a counterbalance valve 30 provided between the first main circuit 16 and the second main circuit 20 is held at a neutral position A by a spring 31 and a first valve acting on the first pressure receiving portion 32 is actuated.
  • the pressure of the main circuit 16 acts on the second pressure receiving section 3 3
  • the switching to the first position B is performed, and the pressure of the second main circuit 20 acting on the second pressure receiving part 33 is changed to the first pressure receiving part.
  • switching to the second position C is performed.
  • the first pressure receiving portion 32 of the counterbalance valve 30 is connected to the operation valve 13 closer to the operation valve 13 than the check valve 35 in the first main circuit 16 in the first circuit 34.
  • the first circuit 34 has an aperture 36. An intermediate portion between the throttle 36 and the first pressure receiving portion 32 of the first circuit 34 is communicated with and blocked from the tank by the first switching valve 37.
  • the first switching valve 37 is pushed toward a shut-off position by a spring 38 and pushed toward a communication position by a counterbalance valve 30.
  • the power center balance valve 30 is in the neutral position A or the first position B, the first switching valve 37 is in the shut-off position.
  • the counterbalance valve 30 is at the second position C, the first switching valve 37 is at the communication position.
  • the second pressure receiving portion 33 of the counterbalance valve 30 is connected to the operation valve 13 closer to the operation valve 13 than the check valve 35 in the second main circuit 20 in the second circuit 39.
  • the second circuit 39 has an aperture 40. An intermediate portion between the throttle 40 and the second pressure receiving portion 33 of the second circuit 39 is communicated with the tank by the second switching valve 41 and is shut off.
  • the second switching valve 41 is pushed toward the shut-off position by the spring 42 and pushed toward the communication position by the counterbalance valve 30.
  • the second switching valve 41 is in the shut-off position.
  • the second switching valve 41 is in the communicating position.
  • the back pressure valve 25 is pushed to the throttle communication position by a spring 43, It is pushed to the communicating position by the discharge pressure of the hydraulic pump 10 acting on 4 4.
  • the discharge pressure of the hydraulic pump 10 causes the pressure to rise due to the passing pressure loss of the operation valve 13 and switches the counter balance valve 30 to the first position B or the second position C.
  • the communication position is established when the value becomes equal to or greater than the sum of the switching pressure.
  • the pressure compensating valve 12 is a conventionally known pressure compensating valve composed of a load tick valve 45 and a pressure reducing valve 46.
  • the higher pressure of the first main circuit 16 and the second main circuit 20 is detected by the shuttle valve 47.
  • the pressure detected by the shuttle valve 47 acts on the pressure compensating valve 12 (reducing valve 46) as its own load pressure.
  • the output side of the pressure reducing valve 46 of all the pressure compensating valves 12 is connected to the load pressure detecting circuit 48 so that the highest load pressure is detected. is there.
  • the hydraulic pump 10 is of a variable displacement type, and its displacement is controlled by a displacement control valve 49 and a displacement control cylinder 50, as conventionally known, between the load pressure of the load pressure detection circuit 48 and the pump discharge pressure.
  • the differential pressure is controlled to be constant.
  • the pressure compensating valve 12 functions when a plurality of actuators are simultaneously operated, the operation thereof is omitted.
  • the tank pressure in the first and second main circuits 16 and 20 becomes the tank pressure, so that the counter balance valve 30 is in the neutral position A. Since the opening area of the operation valve 13 is zero, the capacity of the hydraulic pump 10 becomes the minimum and the discharge pressure thereof becomes the lowest. As a result, the back pressure valve 25 is at the throttle communication position.
  • the hydraulic motor 17 is driven to rotate in one direction by the discharge pressure oil of the hydraulic pump 10 supplied to one port 18.
  • the hydraulic motor 17 performs a pumping action, so that the pressure of one port 18 decreases and the other port 2 1 discharges pressure oil.
  • the discharge pressure of the hydraulic pump 10 decreases, and the back pressure valve 25 is throttled to the communication position.
  • the return pressure oil from the hydraulic motor 17 is throttled by the back pressure valve 25 and flows out to the tank 24, so that the back pressure of the regenerative circuit 23 becomes higher than the pump discharge pressure.
  • the pressure oil in the regenerative circuit 23 flows from the check valve 26 to the discharge path 11.
  • the counterbalance valve 30 since the second pressure receiving portion 33 of the counterbalance valve 30 communicates with the tank by the second switching valve 41, the counterbalance valve 30 is in the neutral position by the pressure of the regenerative circuit 23. It cannot be A or the second position C.
  • the spool port 61 of the main body 60 is provided with a pump port 62 (14), first and second ports 63, 64, and first and second actuators.
  • One port 65, 66 (15, 19), 1st. 2nd regenerative port 67, 68 (22), 1st. 2nd tank port 69, 70 ( 2 7) is formed. Insert the spool 7 1 into the spool hole 6 1 It is inserted to make operation valve 13.
  • the pump port 62 is shut off from the first and second ports 63, 64.
  • the first actuator port 65, the first regenerating port 67, and the first tank port 69 communicate with each other.
  • the second actuator port 66, the second regenerating port 68, and the second tank port 70 communicate with each other.
  • the first port 63 and the second port 64 communicate with each other through a communication path 72 indicated by a dotted line.
  • the return pressure oil flowing into 66 flows into the second regenerating port 68.
  • the first actuating port 65 and the first regenerating port 67 continue to communicate, and the first regenerating port 67 and the first tank port 69 are cut off.
  • the return pressure oil that has flowed into the cut-out port 65 flows into the first regeneration port 67.
  • the first and second regeneration ports 67 and 68 communicate with the first and second regeneration ports 73 and 74, respectively, so that the first regeneration port 73 and the second regeneration port 73 are connected to each other.
  • G 74 communicates with a communication hole 75 shown by a dotted line.
  • the first regeneration port 73 communicates with the pump port 62 via a check valve 76.
  • the second regenerating port 74 communicates with the tank port 78 through a notch 77a of the back pressure valve spool 77 fitted in a spool hole 60a of the valve body 60. .
  • the back pressure valve spool 77 is held at a position shown in the drawing by a spring 79 and cuts off the second regenerating port 74 to communicate with a tank port 78 by a 77a. That is, it is the same as when the back pressure valve 25 in FIG. 2 is in the throttle communication position.
  • the back pressure valve spool 77 When the pressure of the pump port 62 becomes equal to or higher than the set pressure, the back pressure valve spool 77 is pressed by the pressure to move the second regenerating port 74 and the tank port 78 to the small diameter portion. It is the position where communication is performed at 7 7 b. In other words, this is the same as when the back pressure valve 25 in FIG. 2 is in the communicating position.
  • the set pressure has a value not less than (switching pressure of the counterbalance valve 30 + pressure loss of the operation valve 13).
  • the check valve 76 is formed by inserting a port 81 into a sleeve 80 screwed into a hole 60b coaxial with the spool hole 60a, and The port 81 is pressed in the shut-off direction by the pressure of the spring 82 and the pump port 62, and communicates with the pressure of the first regeneration port 73 acting on the step 81a of the port 81. It is configured to be pushed in the direction. Thus, when the pressure of the second regeneration port 73 is higher than the pressure of the pump port 62, the second regeneration port 73 is communicated with the pump port 62.
  • a spool 92 is inserted and inserted into a spool hole 60 c of the valve body 60 to communicate and shut off an inlet port 90 and an outlet port 91, thereby constituting a one-way valve 45. are doing .
  • the pressure reducing valve 46 is formed by a screw 93 that is fitted in a hole 60 d coaxial with the spool hole 60 c and pushes the spool 92 in the communicating direction.
  • the discharge pressure oil of the hydraulic pump 10 is supplied to the inlet port 90, and the outlet port 91 communicates with the pump port 62.
  • the piston 93 moves in a direction away from the spool 92 by the pressure of the first pressure receiving chamber 94, and moves in a direction to push the spool 92 by the pressure of the second pressure receiving chamber 95. Further, the first pressure receiving chamber 94 communicates with the second port 63, and the piston 93 receives its own load pressure.
  • the return pressure oil flowing into the second actuator port 66 is supplied from the second regeneration port 68 to the first and second regeneration ports. It flows into ports 73 and 74.
  • the back pressure valve spool 77 stakes in the spring 79 and moves to the left, and the return pressure oil of the second regeneration port 74 is applied to the tank port. Flow to 7-8. As a result, the back pressure of the first and second regeneration ports 73 and 74 is low.
  • the first * second main ports 102, 103 and the first and second return ports 100, 104 are provided in the spool holes 101 of the valve body 100, respectively.
  • Form 105 The spool 106 is inserted into the spool hole 101, and the spool 106 is set to the neutral position by the left and right springs 107.
  • first pressure receiving part 32 When pressure oil flows into one pressure chamber 108 (first pressure receiving part 32), the spool 106 moves to the left and the second main port 103 and the second return port 1 0 5 communicates.
  • the pressure oil flows into the other pressure chamber 109 (second pressure receiving part 33)
  • the spool 106 moves to the right and the first main port 102 and the first return port 110 4 communicates.
  • the first pressure chamber 108 communicates with the first main port 102 via a first oil hole 110 (34) and a fine hole 111 (36) drilled in the spool 106. ing.
  • the second pressure chamber 109 communicates with the second main port 103 via a second oil hole 112 (39) and a hole 113 (40) drilled in the spool 106. I have.
  • Sleeves 114 are attached to both left and right sides of the valve body 100, respectively.
  • a tank port 115 is formed around the outer periphery of the sleeve 114, and the tank port 115 is formed by a hole 114 through the sleeve 114. It communicates with port 1 17 on the inner circumference of.
  • a piston 119 is fitted in the sleeve 114, and the piston 119 is pushed by the spring 120 toward the spool 106. Between the first pressure chamber 108 and port 117 or between the second pressure chamber 109 and port The connection between the two is blocked.
  • the piston 119 provided on the left side is pushed by the spool 106 to move the second pressure chamber 109. It communicates with tank port 1 15 at port 1 17 and hole 1 16. As a result, the second pressure chamber 109 communicates with the dunk from the tank port 115.
  • the second switching valve 41 in FIG. 2 is constituted by the piston 119 and the like provided on the left side.
  • the piston 110 provided on the right side is pushed by the spool 106 to cause the first pressure chamber 108 to move. It communicates with tank port 1 15 at port 1 17 and hole 1 16. As a result, the first pressure chamber 108 communicates with the tank from the tank port 115.
  • the first switching valve 37 in FIG. 2 is constituted by the pistons 119 and the like provided on the right side.
  • the hydraulic motor drive system shown in Fig. 2 is applied to a drive system that drives the left and right traveling hydraulic motors of a hydraulic shovel with a single hydraulic pump, as in the second embodiment shown in Fig. 5. By doing so, it is possible to prevent the traveling speed from decreasing when turning left and right.
  • the left and right control valves 13 are set to the first position E, the left control valve 13 has a large metering opening area, and the right control valve 13 has a small mating opening area.
  • the left hydraulic motor 17 is the driving side and the right hydraulic motor 17 is the driven side and turns in the direction of arrow a
  • the right hydraulic motor 17 is in the braking state and is driven.
  • Pressure PL 2 is counterbalun
  • the driving pressure PL 1 of the left hydraulic motor 17 becomes high corresponding to the running resistance and the turning resistance. Therefore, the inlet pressure P 1 of the left operating valve 13 Is higher than the inlet pressure P 2 of the right control valve 13. That is, the load pressure of the left hydraulic motor 17 becomes higher than the load pressure of the right hydraulic motor 17.
  • the pressure reducing valve 46 of the pressure compensating valve 12 on the driving side (left side) is pushed rightward by the load pressure PL 1, and the opening degree of the opening check valve 45 increases, and the driven The pressure compensating valve 12 on the right side (right side) is depressed to the left by the load pressure PL 1 on the driving side (right side) to push the check valve 45 to the closing side, and the load check is performed.
  • the opening of the valve 45 becomes small.
  • the discharge pressure of the variable displacement hydraulic pump 10 increases, the constant horsepower control works, the displacement decreases, and the flow rate flowing into the hydraulic motor 17 on the drive side decreases. It decreases and the vehicle speed decreases.
  • the return oil of the right hydraulic motor 17 is boosted by the back pressure valve 25 and is regenerated to the discharge path 11. For this reason, only the flow rate regenerated in the discharge passage 11 is supplied to the left hydraulic motor 17, so that the decrease in vehicle speed is reduced.
  • the operation valve 13 is the same as that of the first embodiment, and the first 'second regenerative ports 67, 68 are connected to one regenerative port through an oil passage 130. Connect to port 1 3 1.
  • the regenerating port 13 1 communicates with and is shut off from the tank port 78 by the back pressure valve spool 77, and communicates with the tank port 78 via the notch 77 a.
  • Port on the shaft hole 13 of the back pressure valve spool 77 of the back pressure valve 25 13 3 is inserted, and this port 13 3 is pushed by the spring 13 4 to close the regeneration side port 13 5 and the pump side port 13 36.
  • the port 133 is pushed in the closing direction by the pump pressure acting on the proximal end surface 133a on the spring chamber 133 side, and is communicated with the return pressure oil acting on the distal end surface 133b. Pushed in the direction. This constitutes the check valve 26.
  • check valve 26 The operations of the check valve 26 and the back pressure valve 25 are the same as those in the first embodiment.
  • the valve body 60 is provided with a suction valve 140 for communicating the first port 63 and the first tank port 69.
  • the suction valve 140 pushes the valve 141 to the shut-off position with the port pressure (return oil) acting on the spring 144 and the spring chamber 144, and the port pressure becomes the tank pressure.
  • the valve 14 1 stakes in the spring 14 2 and moves in the opening direction.
  • the back pressure valve 25 is pushed toward the communicating position by the spring 43 and the pressure of the first pressure receiving portion 150, and is moved to the throttle communication position by the pressure of the second pressure receiving portion 151. It is pushed toward.
  • the first pressure receiving section 150 is connected to the output side of the pressure compensating valve 12 so that the output pressure of the pressure compensating valve 12 acts.
  • the second pressure receiving section 15 1 is connected to a first port 15 2 formed on a pressure reducing valve 46 of the pressure compensating valve 12.
  • the second port 15 3 formed in the pressure reducing valve 46 is a load pressure introduction path. Connected to 1 5 4.
  • This load pressure introduction path 154 is connected to the load pressure port 155 of the operation valve 13.
  • the first port 152 formed in the pressure reducing valve 46 of the left and right pressure compensating valves 12 is in communication with the circuit 1556.
  • the left and right control valves 13 are in the first position E, the left control valve 13 has a large METAINE opening area, and the right control valve 13 has a small METAN opening area.
  • the driving pressure PL 2 is the set pressure of the counterbalance valve 30, and the driving pressure PL 1 of the left hydraulic motor 17 is a high pressure corresponding to the running resistance and the turning resistance.
  • the inlet pressure P 1 of the control valve 13 is higher than the inlet pressure P 2 of the right control valve 13. That is, the load pressure of the left hydraulic motor 17 becomes higher than the load pressure of the right hydraulic motor 17.
  • the pressure reducing valve 46 of the pressure compensating valve 12 on the driving side (left side) is pushed rightward by the load pressure PL i, so that the opening of the check valve 45 becomes large, and the driven side ( The pressure compensating valve 12 of the right side) and the pressure reducing valve 4 6 of the second side are pushed to the left by the load pressure PL 1 on the driving side (the right side), and the mouth check valve 45 is pushed to the closing side.
  • the opening of 5 becomes smaller.
  • the opening area of the load check valve 45 of the left pressure compensating valve 12 is large. Therefore, the first port 152 and the second port 153 of the pressure reducing valve 46 communicate with each other, and a high load pressure flows through the first port 152.
  • the opening area of the load check valve 45 of the pressure compensating valve 12 on the right is small and the connection between the first port 152 and the second port 153 is shut off. ing.
  • the left load pressure acts on the second pressure receiving portion 15 1 of the right back pressure valve 25, and the pressure is higher than the output pressure of the right pressure compensating valve 12 acting on the first pressure receiving portion 150. High, so the back pressure valve 24 is in the throttle communication position>
  • the return oil of the right hydraulic motor 17 is boosted by the back pressure valve 25 and is regenerated to the output side of the right pressure compensating valve 12.
  • the flow supplied from the right pressure compensating valve 12 to the right hydraulic motor 17 for the hydraulic oil discharged from the hydraulic pump 10 is reduced by the regenerated flow, so that the left Is supplied to the hydraulic motor 17, and as a result, the decrease in vehicle speed is reduced.
  • the load pressure of the left and right hydraulic motors 17 becomes high.
  • the opening area of the load check valves 45 of the left and right pressure compensating valves 12 becomes large, and the first ports 15 2 formed on the pressure reducing valves 46 of the left and right pressure compensating valves 12 become larger.
  • the second ports 15 3 communicate with each other. Therefore, the vehicle travels straight with the load pressure of the left and right hydraulic motors 17 being the same.
  • the load pressure does not act on the second pressure receiving portions 15 1 of the left and right back pressure valves 25, so that the respective back pressure valves 25 are connected to each other by the springs 43.
  • the return oil of the left and right hydraulic motors 17 flows out to the tank without being regenerated, and only the discharge pressure oil of the hydraulic pump 10 is supplied to the left and right hydraulic motors 17, so that the heat balance is maintained. Is improved.
  • the back pressure valve spool 77 is set to the communication position by the spring 79, and the regenerative port 13 1 is connected to the tank port 78.
  • the back pressure valve spool 77 has an oil hole 160 communicating the pump port 62 with the spring chamber 79a (first pressure receiving portion 150).
  • a pressure chamber 16 1 (second pressure receiving section 15 1) is formed between the pressure chamber 16 and the valve body 60.
  • the back pressure valve spool 77 is pushed rightward by the pressure of the spring 79 and the spring chamber 79a to the communication position shown in the figure, and is moved leftward by the pressure of the pressure receiving chamber 161.
  • the back pressure valve 25 is the same as the back pressure valve 25 shown in FIG.
  • An auxiliary port 162 is formed in the pressure reducing valve 46, and a slit 163 that connects the first pressure receiving chamber 94 and the auxiliary port 162 is formed in the piston 93.
  • the auxiliary port 16 2 communicates with the pressure receiving chamber 16 1 to become the first port 15 2 shown in FIG. 7, and the first pressure receiving chamber 94 becomes the second port 15 shown in FIG. It becomes 3.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Système de transmission pour moteurs hydrauliques. Ce système comporte une soupape (13) de commande pour alimenter un moteur (17) hydraulique en huile pressurisée provenant d'une pompe (10) hydraulique, et pour faire passer l'huile pressurisée sortant du moteur hydraulique dans un circuit (23) de régénération, et un équilibreur (30) placé entre le moteur hydraulique et la soupape de commande. L'équilibreur peut être réglé dans une position neutre, dans laquelle il empêche l'huile pressurisée sortant du moteur de s'écouler vers la soupape de commande, et une position ouverte dans laquelle il fait passer l'huile sortant du moteur vers la soupape de commande, et est conçu de manière à passer en position ouverte lorsque la pression de sortie de la pompe hydraulique dépasse un niveau prescrit et à passer en position neutre lorsque la pression de sortie de la pompe hydraulique est égale ou inférieure au niveau prescrit. Lorsqu'il est réglé en position ouverte par la pression de sortie de la pompe hydraulique, l'huile hydraulique de retour empêche l'équilibreur de revenir en position neutre, Le circuit de régénération est connecté à une voie (11) de sortie de la pompe hydraulique par un clapet (26) anti-retour. Ce système permet de régénérer et de réutiliser l'huile pressurisée sortant du moteur hydraulique.
PCT/JP1998/001921 1997-04-25 1998-04-24 Systeme de transmission pour moteurs hydrauliques WO1998049450A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP10870397A JP3736657B2 (ja) 1997-04-25 1997-04-25 油圧モータの駆動システム
JP9/108703 1997-04-25

Publications (1)

Publication Number Publication Date
WO1998049450A1 true WO1998049450A1 (fr) 1998-11-05

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Application Number Title Priority Date Filing Date
PCT/JP1998/001921 WO1998049450A1 (fr) 1997-04-25 1998-04-24 Systeme de transmission pour moteurs hydrauliques

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JP (1) JP3736657B2 (fr)
WO (1) WO1998049450A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4693952B2 (ja) * 2000-02-10 2011-06-01 株式会社小松製作所 油圧モータを用いた油圧駆動装置と油圧モータ
JP2004011168A (ja) * 2002-06-04 2004-01-15 Komatsu Ltd 建設機械
CN105927601B (zh) * 2016-05-19 2018-01-26 武汉船用机械有限责任公司 一种提升液压系统
CN107975509A (zh) * 2017-12-27 2018-05-01 徐工集团工程机械有限公司 行走马达集成阀盖及行走马达

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54158403U (fr) * 1978-04-27 1979-11-05
JPS6113004U (ja) * 1984-06-28 1986-01-25 新キャタピラ−三菱株式会社 液圧再生回路
JPS62147703U (fr) * 1986-03-12 1987-09-18
JPH0687466U (ja) * 1993-05-27 1994-12-22 株式会社小松製作所 走行用油圧回路

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54158403U (fr) * 1978-04-27 1979-11-05
JPS6113004U (ja) * 1984-06-28 1986-01-25 新キャタピラ−三菱株式会社 液圧再生回路
JPS62147703U (fr) * 1986-03-12 1987-09-18
JPH0687466U (ja) * 1993-05-27 1994-12-22 株式会社小松製作所 走行用油圧回路

Also Published As

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JPH10299706A (ja) 1998-11-10
JP3736657B2 (ja) 2006-01-18

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