JPH0337641B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an energy-saving cavitation prevention circuit using a variable displacement pump (hereinafter referred to as variable pump).

[Conventional technology]

Recently, as an energy-saving hydraulic circuit, the applicant has installed in the pump line of a variable pump a throttle switching valve with a pilot passage that is closed in the switching position and open in the neutral position leading to the tank, and A bypass type pressure compensation valve is connected between the pump line and the tank to control the differential pressure before and after the throttle in the throttle switching valve to a constant value, and
The pump line is connected to the pilot chamber of a discharge rate control valve that switches and connects the discharge rate control section of the variable pump to the pump line and the tank, while the pump line is connected to the spring chamber of the discharge rate control valve through a throttle. At the same time, by connecting the spring chamber to the pilot passage of the throttle switching valve via a pilot line, the bypass type pressure compensation valve can also serve as a surge absorption valve, and the surge absorption valve can be omitted. Moreover, when the throttle switching valve is in the neutral state, the spring chamber of the discharge rate control valve is communicated with the tank through the pilot passage, and the discharge rate of the variable pump is reduced to an extremely small amount by operating the discharge rate control valve. He proposed a control system to eliminate power loss when in neutral (Japanese Patent Application No. 56-214413, Japanese Patent Application No. 117140-1982).

[Problem to be solved by the invention]

However, the inventor of the present invention has discovered that the energy-saving hydraulic circuit described above has the following problems. That is, when an attempt is made to return the throttle switching valve (particularly one connected to ABR) to neutral and stop the actuator, the actuator (for example, a hydraulic motor) moves by itself due to inertia. At this time, as mentioned above, because the swash plate of the variable pump was suddenly returned to neutral (feathering position), the pressure in the tank line suddenly decreased, and the pressure was already low.
Since the actuator is self-propelled, it becomes difficult to replenish oil from the tank line, causing cavitation.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to solve the above-mentioned problem, and to maintain the energy-saving effect and to control the discharge amount control section of the variable pump to the neutral position when the throttle switching valve is returned to the neutral position. The purpose is to prevent cavitation from occurring by delaying the return.

[Means to solve the problem]

To achieve the above object, the present invention provides a pump line of a variable displacement pump with a pilot passage that is closed in a switching position and opened in a neutral position and leads to a tank, and a pilot passage that communicates with a load port in a switching position and that communicates with a tank in a neutral position. ABR with a feedback passage communicating with the tank port and a load port communicating with the tank port in the neutral position.
A bypass type pressure is provided, in which a connecting type throttle switching valve is interposed, and the differential pressure before and after the throttle in the throttle switching valve is controlled to be constant between the pump line and the pump line connecting the tank port and the tank. A discharge amount control valve to which a compensation valve is connected, the feedback passage is connected to the spring chamber of the bypass type pressure compensation valve, and a discharge amount control section of the variable displacement pump is selectively connected to the tank of the pump line. The pump line is connected to the pilot chamber of the discharge amount control valve, and the pump line is connected to the spring chamber of the discharge amount control valve via a throttle, and the spring chamber is connected to the pilot passage of the throttle switching valve via the pilot line. The spring chamber of the discharge amount control valve is connected to the tank through the pilot passage when the throttle switching valve is in the neutral state, and a chamber is formed outside the spring chamber of the discharge amount control valve. A part of the spool of the discharge amount control valve is slidably penetrated through the partition wall between the chamber and the spring chamber to project into the chamber, and the chamber is connected to the chamber through a line having a throttle valve. communicating with the pilot line to provide resistance to the discharge of fluid in the chamber when the throttle switching valve is in neutral;
It is characterized in that the movement of the spool of the discharge amount control valve is delayed.

[Effect]

When the throttle switching valve is in the neutral state, the spring chamber of the discharge rate control valve communicates with the tank through the pilot passage, so that the discharge rate of the variable pump becomes extremely small due to the operation of the discharge rate control valve. controlled, eliminating power loss when the throttle switching valve is in neutral. Furthermore, a chamber is formed outside the spring chamber of the discharge amount control valve, and a partition wall between this chamber and the spring chamber is provided with a chamber.
A part of the spool of the discharge amount control valve is slidably penetrated to protrude into the chamber, and the chamber is communicated with the pilot line via a line having a throttle valve. When the switching valve is in the neutral state, the throttle valve provides resistance to the discharge of the fluid in the chamber, and the movement of the spool of the discharge rate control valve is delayed, and the response of the discharge rate control section of the variable pump is delayed. , the pump flow rate is maintained for a while, and when the throttle switching valve is in the neutral state, the pump flow rate flows out to the tank line via the feedback passage through the bypass type pressure compensating valve whose spring chamber communicates with the tank. Even if the line pressure is maintained and the actuator operates with inertia,
Cavitation can be prevented from occurring in the line on the load port side that communicates with the tank line via the ABR-connected throttle switching valve.

〔Example〕

Hereinafter, the present invention will be explained in detail with reference to illustrated embodiments.

In FIG. 1, 1 is, for example, a variable pump consisting of a swash plate type variable displacement piston pump whose swash plate is always biased in the direction of maximum inclination to discharge the maximum flow rate, and 2 is connected to the discharge port of variable pump 1. 3 is an ABR-connected throttle switching valve that is interposed in the pump line 2 and has a pump port P, load ports A, B, and tank port R; 4 is an operating direction and speed controlled by the throttle switching valve 3; This is a hydraulic motor.

The throttle switching valve 3 has the functions of a throttle valve and a directional switching valve, and furthermore, in the neutral position, the tank 5
while in the switching position, the throttle switching valve 3
In addition to the feedback passage 7 that communicates with the downstream side of the throttle (not shown) to detect the load pressure,
A pilot passage 8 is provided which is open in the neutral position and communicates with the tank 5, and which is closed in the switched position.

Further, from the pump line 2 upstream of the throttle switching valve 3, a bypass line 12 that leads to the tank 11 via the tank line 75 is branched,
A bypass type pressure compensation valve 13 is interposed in the bypass line 12, and the spring chamber 14 of the pressure compensation valve 13 is connected to the load pressure detection port on the primary side of the feedback passage 7 of the throttle switching valve 3 via the pilot line 15. Connected to 7a. Therefore, when the throttle switching valve 3 is switched, the bypass type pressure compensation valve 13 is operated by the spring 16 of the spring chamber 14.
The differential pressure before and after the throttle of the throttle switching valve 3 is controlled to a constant value corresponding to the spring pressure of , and excess fluid is discharged to the tank 11. Also, a bypass line 12 downstream of the bypass type pressure compensation valve 13 is provided.
is connected to a tank line 75 connected to the tank port R of the throttle switching valve 3.

Further, a chamber 21a on the anti-spring side of the swash plate control cylinder 21 as a discharge amount control section of the variable pump 1 is provided.
is connected to the pump line 2 and the tank 23 via the 3-port throttle switching valve 22, which is an example of a discharge amount control valve.
This makes it possible to switch connections between the two. The pump line 2 is connected to the pilot chamber 24 of the discharge rate control valve 22 via a pilot line 25, while the spring chamber 26 of the discharge rate control valve 22 is connected to a pilot line 28 with a throttle 27 interposed in the middle. It is connected to the pump line 2 via a pilot line 29, and to the primary port 8a of the pilot passage 8 of the throttle switching valve 3 via a pilot line 29. The spring pressure of the spring 30 in the spring chamber 26 of the discharge amount control valve 22 is set smaller than the spring pressure of the spring 16 in the spring chamber 14 of the bypass type pressure compensation valve 13.

Furthermore, as the specific structure is shown in FIG. 2, a chamber 82 is formed outside the spring chamber 26 of the discharge amount control valve 23 with a partition wall 81 in between. On the other hand, the spool 83 of the discharge amount control valve 22 has a spring chamber 2.
A piston portion 83a is integrally formed, which extends through the chamber 82 and extends through the partition wall 81 in a slidable manner. The chamber 82 is connected to the pilot line 28 via a line 86 having a throttle valve 85 with a check valve as an example of a throttle valve.

In FIG. 2, 88 is a spacer and 89 is a drain port. In the specific structure shown in FIG. 2, the same components as those in FIG. 1 are given the same reference numerals and their explanations will be omitted.

Further, a tank 35 is connected to the spring chamber 26 of the discharge amount control valve 22 via a pilot line 34 having a pilot relief valve 33 interposed therebetween.

In the cavitation prevention circuit configured as described above, it is assumed that the throttle switching valve 3 is located at the switching position _S1 and the hydraulic motor 4 is rotated in one direction.

At this time, the spring chamber 26 of the discharge amount control valve 22 communicates with the pump line 2 via the throttle 27 and the pilot line 28, and the pilot passage 8 of the throttle switching valve 3 is closed. The pressure in the spring chamber 26 and the chamber 82 is the same as the pressure in the pump line 2, and the pressure in the discharge rate control valve 2 is the same as that in the pump line 2.
The second pilot compartment 24 is also connected to the pilot line 25.
Since it is connected to the pump line 2 via the pump line 2, the pressure is the same as that of the pump line 2. Therefore, due to _the spring force of the spring 30 of the discharge amount control valve 22, the chamber 21a of the swash plate control cylinder 21 on the opposite spring side communicates with the tank 23 through the discharge amount control valve 22. However, the swash plate control cylinder 21 inclines the swash plate to the maximum inclination side to discharge the maximum flow rate.

On the other hand, at the switching position _S1 of the throttle switching valve 3, the feedback passage 7 communicates with the rear part of the throttle of the throttle switching valve 3.
A load pressure is introduced into the spring chamber through a pilot line 15, and a bypass type pressure compensating valve 13 controls the differential pressure before and after the throttle to be constant, and discharges excess fluid to the tank 11.

In this way, at the switching position S ₁ (the same applies to S ₂ ) of the throttle switching valve 3, the pressure of the throttle of the throttle switching valve 3 is compensated by the valve control method using the bypass type pressure compensation valve 13. Since its responsiveness is quick and excess fluid can be discharged to the tank 11 through the bypass pressure compensation valve 13, the bypass pressure compensation valve 13 can function as a surge absorption valve to absorb surge pressure.

Next, suppose that the hydraulic motor 4 is overloaded for some reason and the hydraulic motor 4 is stopped.

Then, the pressure in pump line 2 increases,
Pilot relief valve 3 to which the pressure is led
3 operates to enter a relief state, and the pressures in the spring chamber 26 and chamber 82 of the discharge amount control valve 22 are controlled to the set pressure. For this reason, the discharge amount control valve 22
is the symbol position so that the differential pressure between the pilot chamber 24 and the spring chamber 26 becomes the spring pressure of the spring 30.
It may be located at symbol position V ₁ or symbol position V ₂ , and during steady state it is located between them to control the discharge flow rate of variable pump 1 . At this time, the pressure of the fluid discharged from the variable pump 1 is
The pressure is high according to the set pressure in step 3, but
The discharge flow rate is such that the differential pressure before and after the small throttle 27 of the pilot line 28 becomes a value equivalent to the spring pressure of the spring 30 of the discharge amount control valve 27, so it is extremely small and reduces power loss. Can be done with less
Energy saving effect can be achieved.

Note that in the relief state where the hydraulic motor 4 is stopped, no fluid flows through the throttle switching valve 3, so the pressures in the pilot chamber 38 and spring chamber 16 of the bypass type pressure compensation valve 13 are the same. The bypass type pressure compensating valve 13 is stopped in a closed state by the spring force of the spring 16.

Next, it is assumed that the throttle switching valve 3 is suddenly positioned at the neutral position S ₀ while the hydraulic motor 4 is rotating.

Then, the pilot passage 8 of the throttle switching valve 3
is opened and communicated with the tank 5, and the spring chamber 26 and the chamber 82 of the discharge amount control valve 22 are connected to the tank 5 via the pilot line 29 and the pilot passage 8.
The spool 8 of the discharge amount control valve 22
3 moves to the right in FIG.
is located at symbol position V ₂ in FIG. 1, and attempts to reduce the discharge flow rate of the variable pump 1. However, even if the spool 83 tries to move to the right in FIG. Since it is discharged into the tank 5 only through the valve part 85a, the movement of the spool 83 is delayed, and the response of the swash plate control cylinder 21 of the variable pump 1 is delayed, and the response of the swash plate control cylinder 21 of the variable pump 1 is delayed accordingly. The discharge flow rate will be maintained. Therefore, there is hydraulic oil discharged from the bypass type pressure compensation valve 13 to the tank line 75, and the pressure in the tank line 75 is maintained for a while. Therefore, even if the hydraulic motor 4 moves by itself due to inertia at the neutral position S ₀ of the throttle switching valve 3, the pressure in the tank line 75 is maintained, so cavitation is prevented from occurring. Ru.

Thereafter, while discharging the hydraulic oil in the chamber 82 outside the spring chamber 26 of the discharge amount control valve 22 toward the tank 5, the spool 83 of the discharge amount control valve 22 is
Discharge amount control valve 22 is located on the right side of the figure, and is located at symbol position V ₂ in FIG. The variable pump 1 is located at the symbol position V ₁ or V ₂ , and is normally located in the middle, so that the pressure of the pump line 2 becomes the spring pressure of the spring 30. control the discharge flow rate. The discharge flow rate of the variable pump 1 is an extremely small amount because the pressure difference before and after the small throttle 27 of the pilot line 28 becomes the spring pressure of the spring 30. Since the pressure is extremely low, corresponding to the spring pressure of the spring 30, power loss is reduced. In other words, the spring chamber 26 of the discharge amount control valve 22 is
By communicating with the variable pump 1, the variable pump 1 is caused to perform an unload operation in which both the discharge pressure and the discharge flow rate are small.

At this time, the hydraulic oil that has flowed into the spring chamber 26 of the discharge amount control valve 22 through the pilot line 28 having the throttle 27 is transferred to the check valve equipped throttle valve 8.
The spring chamber 2 is discharged into the tank 5 through the pilot line 29 without passing through the spring chamber 2.
Therefore, the discharge pressure during unloading of the variable pump 1, so-called feathering, is a low pressure corresponding to approximately the spring pressure of the spring 30, and power loss is small. Also, at this time,
Since the pilot line 29 is filled with flowing fluid, the pressure in the spring chamber 26 and chamber 82 is quickly increased when the throttle switching valve 3 is next switched to operate the discharge amount control valve 22. , the response can be made faster, and since hydraulic oil is supplied to the chamber 82 through the check portion 85b of the throttle valve with check valve 85, the response can be made faster.

Further, at this time, the spring chamber 14 of the bypass type pressure compensation valve 13 is communicated with the tank 5 via the pilot line 15 and the feedback passage 7, but the spring pressure of the spring 16 of the spring chamber 14 is controlled by the discharge amount control. Since the spring pressure of the spring 30 of the valve 22 is greater, the bypass pressure compensation valve 13 remains closed.

FIG. 3 shows a modification in which the present invention is used as a hydraulic circuit for a hydraulic shovel. Parts having the same functions as those shown in FIG.

In FIG. 3, 50 is a pilot valve for constant horsepower control, and signal transmission means 51 such as a link mechanism.
The pump is operated by a signal from the swash plate indicating the discharge amount of the variable pump 1 transmitted through the pump line 2 and a pressure signal of the pump line 2, so that the horsepower obtained by multiplying the discharge pressure and discharge flow rate of the variable pump 1 becomes constant. It is located at symbol position M ₁ or M ₂ to control the discharge amount control section 21, and when the discharge flow rate is excessive with respect to the discharge pressure, it is located at symbol position M ₂ and controls the discharge amount control valve 21. Regardless of the operating state of variable pump 22, fluid is supplied to the discharge rate control section 21 through line 52 to reduce the discharge rate of variable pump 1, and if the discharge rate is too small relative to the discharge pressure, the above-mentioned The pilot valve 22 is located at symbol position _M1 ,
In this case, since a check valve 54 is provided in the line 52, the discharge amount control valve 21 is controlled depending on the symbol position of the discharge amount control valve 22.

Further, 13a is a priority type pressure compensation valve having a primary port 56, a normally open pressure reducing port 57, and a normally closed bypass port 58, and also functions as a bypass type pressure compensation valve. and the pressure reduction port 57 by controlling the opening degree between the pressure reduction port 57 and the pressure reduction port 57.
While preferentially pressure-compensating the side priority line 59, excess fluid is discharged from the bypass port 58.

Further, 61 is a shuttle valve that selects the maximum load pressure of the throttle switching valves 3a, 3b connected to the priority line 59 and transmits it to the spring chamber of the priority type pressure compensation valve 56;
Reference numeral 2 designates a shuttle valve that selects the maximum load pressure of the throttle switching valves 3, 3 and transmits it to the spring chamber of the bypass type pressure compensation valve 13. The hydraulic oil discharged from the bypass type pressure compensation valve 13 is supplied to the tank line 75.

Further, the pilot passages 8, 8, 8, 8 of each of the throttle switching valves 3, 3, 3a, 3a are connected in series to a pilot line 29, so that all the throttle switching valves 3,
Only when 3, 3a, 3a are in the neutral position,
The spring chamber of the discharge amount control valve 22 is communicated with the tank 5 to perform unload operation of the variable pump 1.

Further, 65, 65 is a hydraulic motor for traveling the hydraulic excavator, 66 is a hydraulic motor for swinging, 67 is a hydraulic cylinder for an arm, 68 is a hydraulic cylinder for a boom,
69 is a hydraulic cylinder for the bucket.

Note that in FIG. 3, the circuit configuration on the left half is substantially the same as the circuit configuration on the right half, so a description thereof will be omitted.

In each of the above embodiments, the throttle switching valves 3, 3, 3a, 3
A is used, but the throttle valve and the switching valve may be provided separately.

〔Effect of the invention〕

As is clear from the above description, the present invention provides a pump line of a variable pump with a pilot passage that is closed in the switching position and open in the neutral position and leads to the tank, and a pilot passage that communicates with the load port in the switching position and in the neutral position. It has a feedback path that communicates with the tank, and the load port and tank port communicate with each other in the neutral position.
An ABR connection type throttle switching valve is provided, and a bypass type pressure compensation that controls the differential pressure before and after the throttle in the throttle switching valve to a constant level between the pump line and the pump line connecting the tank port and the tank. Connect the valve, and connect the feedback passage to the spring chamber of this bypass type pressure compensation valve.
and connecting the pump line to a pilot chamber of a discharge rate control valve that selectively connects the discharge rate control section of the variable pump to the pump line and the tank;
A pump line is connected to the spring chamber of the discharge amount control valve via a throttle, and the spring chamber is connected to a pilot passage of the throttle switching valve via a pilot line, so that when the throttle switching valve is in neutral, A spring chamber of the discharge rate control valve is communicated with the tank via the pilot passage, and a chamber is formed outside the spring chamber of the discharge rate control valve, and a partition wall between the chamber and the spring chamber is provided with: A part of the spool of the discharge amount control valve is slidably penetrated to protrude into the chamber, and the chamber is communicated with the pilot line via a line having a throttle valve. When the switching valve is in the neutral state, the throttle valve provides resistance to the discharge of the fluid in the chamber, delays the movement of the spool of the discharge amount control valve, delays the response of the discharge amount control section of the variable pump, and temporarily ,
By maintaining the pump flow rate and tank line pressure, cavitation can be prevented even when the actuator operates with inertia, and the discharge flow rate and discharge pressure when unloading the variable pump are small, especially when the pump is unloaded. Since the fluid discharged from the spring chamber does not pass through the throttle valve, pressure does not build up in the spring chamber. Therefore, the discharge pressure during feathering of the variable pump can be reduced, reducing power loss. can.

[Brief explanation of the drawing]

FIG. 1 is a circuit diagram of an embodiment of the present invention, FIG. 2 is a sectional view of a discharge amount control valve, and FIG. 3 is a circuit diagram of a modified example. 1...variable pump, 2...pump line, 3...
... Throttle switching valve, 4 ... Hydraulic motor, 8 ... Pilot passage, 13 ... Bypass type pressure compensation valve, 22
... Discharge rate control valve, 27 ... Throttle, 29 ... Pilot line, 81 ... Partition wall, 82 ... Chamber, 8
3... Spool, 85... Throttle valve with check valve,
86...line.

Claims (1)

[Claims] 1. In the pump line 2 of the variable displacement pump 1 there is a pilot passage 8 which is closed in the switching position and open in the neutral position and leads to the tank, and a feedback passage which in the switching position communicates with the load port A or B and in the neutral position with communication with the tank. In addition to having a passage 7, an ABR connection type throttle switching valve is provided in which the load ports A and B communicate with the tank port R in the neutral position, and the pump line 2 and the tank port R are connected to the tank. A bypass type pressure compensation valve 13 for controlling the differential pressure before and after the throttle in the throttle switching valve at a constant level is connected between the tank line and the tank line, and the feedback passage 7 is connected to the spring chamber of the bypass type pressure compensation valve 13. , and a pilot chamber 24 of a discharge rate control valve 22 that selectively connects the discharge rate control section 21 of the variable displacement pump 1 to the pump line 2 and the tank 23.
The pump line 2 is connected to the spring chamber 26 of the discharge amount control valve 22 via a throttle 27, and the spring chamber 26 is connected to the throttle switching valve via a pilot line 29. The spring chamber 2 of the discharge amount control valve 22 is connected to the pilot passage 8 of the discharge amount control valve 22 when the throttle switching valve is in the neutral state.
6 is communicated with the tank via the pilot passage 8, and the spring chamber 2 of the discharge amount control valve 22 is connected to the tank through the pilot passage 8.
A chamber 82 is formed on the outside of the spring chamber 26, and a partition wall 81 between the chamber 82 and the spring chamber 26 is provided with the discharge amount control valve 2.
A part of the spool 83 of No. 2 is slidably penetrated to protrude into the chamber 82, and
2 is connected to the pilot line 29 through a line 86 having a throttle valve 85, so that when the throttle switching valve 3 is in the neutral state, the throttle valve 85 provides resistance to the discharge of the fluid in the chamber 82. A cavitation prevention circuit characterized in that the movement of the spool 83 of the discharge amount control valve 22 is delayed.