JP2002013656A - Multiple string valve for hydraulic work machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To select the direction of a cylinder port arbitrarily according to the kind of a hydraulic work machine and to improve workability of connection work of a hydraulic pipe which is connected to the cylinder port and maintenance work or the like. SOLUTION: In a fourth surface 74, which is in parallel with the lengthwise direction of a switching spool and at right angles with respect to a first surface formed with cylinder ports 38A, 38B, of a multiple string valve main unit 24, a plurality of bolt insertion holes inserted in the inside the multiple valve unit 24 in a direction at a right angle to the lengthwise direction of the switching spool are provided; additionally an opening part respectively communicating with a pump port 26 and a tank port is provided; and single unit valves 122A, 122B of two kinds with a direction of the cylinder port reversed to each other can be connected to the fourth surface 74.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a multiple valve for a hydraulic working machine mounted on a hydraulic working machine having a plurality of hydraulic actuators such as a hydraulic cylinder.

[0002]

2. Description of the Related Art As a hydraulic working machine having a plurality of hydraulic actuators such as a hydraulic cylinder, there is a civil engineering / loading machine called a backhoe loader. As shown in FIG. 11, the backhoe loader is provided with a loader unit 12 and a backhoe unit 14 provided in front of and behind the vehicle body 10, and each hydraulic actuator 16 that drives the loader unit 12 and the backhoe unit 14 has Are arranged such that the pressure oil discharged from the hydraulic pump is supplied through the respective switching valves.

In such a hydraulic working machine such as a backhoe loader, the switching valves are arranged in front of the driver's seat so that the operator can operate the hydraulic actuator 16 in the driver's seat. It is often integrated as a multiple valve as shown.

[0004]

However, since the multiple valve described in Japanese Utility Model Laid-Open No. 3-111660 has all the cylinder ports opened in the same direction, such a multiple valve is not used. When mounted on a backhoe loader, as shown in FIG. 12, a first multiple valve 18A having a cylinder port opening forward and a second multiple valve 18B having a cylinder port opening rearward. To the bracket 20 provided in front of the driver's seat. For this reason, there is a problem that not only a relatively large mounting space is required, but also connection work of the hydraulic piping and maintainability are hindered.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems. It is an object of the present invention to enable the direction of a cylinder port to be arbitrarily selected according to the type of a hydraulic working machine. It is an object of the present invention to provide a multiple valve for a hydraulic working machine capable of improving workability such as connection work of a hydraulic pipe and maintenance work.

[0006]

To achieve the above object, the present invention provides a pump port connected to a hydraulic pump of a hydraulic working machine and a return oil returned from a hydraulic actuator of the hydraulic working machine to a tank. A multiple valve body having a tank port for discharging and a plurality of cylinder ports for supplying pressure oil supplied to the pump port to the hydraulic actuator; and a plurality of cylinder ports, each of which is perpendicular to a first surface on which the cylinder port is formed. A multiple valve for a hydraulic working machine, comprising: a plurality of switching spools provided between the opposed second and third side surfaces and provided in the multiple valve body; A fourth parallel to the longitudinal direction of the switching spool and perpendicular to the plane on which the cylinder port is formed.
A plurality of bolt insertion holes penetrating through the inside of the multiple valve body in a direction perpendicular to the longitudinal direction of the switching spool, and an opening communicating with the pump port and the tank port, respectively, It is characterized in that two types of single valves whose cylinder port directions are opposite to each other can be connected to the fourth surface.

In this case, the multiple valve body can have a detection core for detecting the supply pressure to the hydraulic actuator and / or a plurality of pressure compensation spools for compensating the operating pressure of the hydraulic actuator. It is preferable that each of the pressure compensating spools has a signal pressure passage communicating with each other, and the signal pressure passage is opened in a surface where the bolt insertion hole and the opening are formed.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIG.
This will be described with reference to FIGS. Note that the same parts as those shown in FIG.

FIG. 1 is a perspective view of a multiple valve for a hydraulic working machine according to an embodiment of the present invention and a single valve connected to the valve. 2 is a plan view of the multiple valve for a hydraulic working machine shown in FIG. 1 and a single valve connected to the valve. FIG. 3 is a bottom view thereof.
FIG. 4 is a side view thereof. 1 to 4, reference numeral 22 denotes a multiple valve for a hydraulic working machine according to an embodiment of the present invention, and a multiple valve body 24 of the multiple valve 22 includes a pump port 26 and a tank port 28. A plurality of (for example, 12) cylinder ports 38 are provided.
A, 38B are provided (see FIGS. 2 and 3).

The pump port 26 is formed on the upper surface of the multiple valve main body 24 in the figure, and the pressure oil discharged from the hydraulic pump 30 is supplied to the pump port 26 via the pump line 32. ing. On the other hand, the tank port 28 is formed on the lower surface of the multiple valve body 24 in the figure, and a tank line 36 communicating with the tank 34 is connected to the tank port 28.

The cylinder ports 38A and 38B are formed on the upper surface of the multiple valve main body 24 in the figure, and inside the multiple valve main body 24, as shown in FIG.
A, 38B, the cylinder cores 40A, 40B communicating with the pump port 26, the pump cores 42A, 42B,
A tank passage 44 communicating with the tank port 28 is formed, and half (for example, six) switching spools 46 of half the cylinder ports 38A and 38B are provided so as to be movable in the longitudinal direction. Further, a plurality of pressure compensating spools 50 for compensating the operating pressure of the hydraulic actuator 16 are provided in the multiple valve body 24 in correspondence with the switching spool 46, and a pressure relief core 86A that releases a pressure higher than a set pressure is provided. , 86B via the tank passage 44
Valves 84A and 84B that discharge to the cylinder port 38
A, 38B.

The pump passages 42A and 42B are formed between the cylinder core 40A and the cylinder core 40B.
A detection core 48 for detecting a pressure supplied to the hydraulic actuator 16 is provided between the pump passage 42A and the pump passage 42B. On the other hand, the tank passage 44 is formed below the detection core 48 in the drawing, and the return oil returned from the hydraulic actuator 16 to the cylinder port 38A (or 38B) is the auxiliary tank core 60A (or 60B).
And an annular passage 62 to be introduced into the tank passage 44.

The detection core 48 is for detecting the pressure supplied to the hydraulic actuator 16. Between the detection core 48 and the pump passages 42A and 42B, the pressure oil flowing into the detection core 48 is supplied to the cylinder core. Supply cores 58A and 58B for introduction into 40A and 40B are formed.

The switching spool 46 has a cylinder port 38.
It is provided in the multiple valve main body 24 between two opposing sides perpendicular to the plane on which A and 38B are formed. The switching spool 46 is connected to the pump passages 42A, 42A.
Notches 47A, 47 for introducing the pressure oil in B through the detection core 48 and the check valve 56 to the supply core 58A or 58B.
B, and a notch 49 for introducing return oil flowing from the hydraulic actuator 16 into the cylinder port 38A or 38B into the auxiliary tank core 60A or 60B.
A, 49B.

The pressure compensating spool 50 has a front chamber 66 in which a check valve 72 for closing the throttle 68 by the spring force of a compression coil spring 70 is provided. The pressure compensating spool 50 is connected to the signal passage 6 communicating with each other.
The signal path 64 communicates with the detection core 48 via the front chamber 66 and the throttle 68. Therefore, when a plurality of switching spools 46 are simultaneously operated, the detection core 48 having the highest pressure is selected by the check valve 72, and the pressure in the selected detection core 48 is transmitted to the signal passage 6.
4 is supplied to the chamber 64a in the pressure compensating spool 50 through the pressure control spool 4, and acts to reduce the cross-sectional area of the annular passage 62 by moving each spool 50 upward, thereby supplying the light-load and high-load cylinders. Balance the amount of pressurized oil.

Notches 47A, 47B and 49A, 49
B is formed opposite to the central portion and both intermediate portions of the switching spool 46, and supplies pilot pressure oil to an oil chamber 54A formed on the right end side of the switching spool 46 in the drawing, for example.
When the switching spool 46 strokes a predetermined amount to the left in the drawing from the position shown in the drawing by the pressure of the pilot pressure oil,
Since the pump passage 42B and the detection core 48 communicate with each other via the notch 47B, the pressure oil discharged from the hydraulic pump 30 is supplied to the pump port 26, the pump passage 42B, the notch 47B,
Detection core 48, check valve 56, supply core 58A, notch 5
2A, the cylinder core 40A and the cylinder port 38A are supplied to the hydraulic actuator 16 and the return oil returned from the hydraulic actuator 16 to the cylinder port 38B at this time is supplied to the cylinder core 40B, the notch 49B, the auxiliary tank core 60B, the annular passage 62, It is discharged to the tank 34 via the tank passage 44 and the tank port 28.

Conversely, pilot pressure oil is supplied to an oil chamber 54B formed on the left end side of the switching spool 46 in the figure, and the switching spool 46 is moved rightward in the figure from the position shown in the figure by the pressure of the pilot pressure oil. When the stroke is a predetermined amount, the pump passage 42A and the detection core 48 communicate with each other via the notch 47A, so that the pressure oil discharged from the hydraulic pump 30 is pump port 26, the pump passage 42A, the notch 47A, the detection core 48, Check valve 56, supply core 58B, notch 52
B, the cylinder oil 40B, and the supply oil to the hydraulic actuator 16 via the cylinder port 38B. At this time, the return oil returned to the cylinder port 38A from the hydraulic actuator 16 returns to the cylinder core 40A, the notch 49A, the auxiliary tank core 60A, the annular passage 62, It is discharged to the tank 34 via the tank passage 44 and the tank port 28.

In FIG. 2 and FIG. 3, reference numeral 74 denotes a cylinder port 3 which is parallel to the longitudinal direction of the switching spool 46.
8A and 38B, the side surface of the multiple valve body 24 is shown at right angles. The side surface 74 is provided with a plurality (for example, four) of bolt insertion holes 76 and an opening 78.
A, 78B, 78C, 78D are provided (see FIG. 6).

The bolt insertion holes 76 pass through the inside of the multiple valve main body 24 in a direction perpendicular to the longitudinal direction of the switching spool 46. Each of the bolt insertion holes 76 has an opening 78A to 78D.
The single valve 122 is provided on the side surface 74 of the multiple valve body 24 in which
Bolts 80 (see FIG. 4) for joining A, 122B and cover body 84 are inserted. Here, the single valve 122A has the same configuration as that shown in FIG. 5, and a pair of cylinder ports is provided on the check valve side with respect to the spool.

The openings 78A, 78B, 78C and 78D communicate with the pump passages 42A, 42B, the tank passage 44 and the signal passage 64, respectively, so that the pump port 26 is opened via the pump passages 42A and 42B. Parts 78A and 78B and communicate with the tank port 28
Is communicated with the opening 78C through the tank passage 44. The openings 78A to 78D are sealed around the periphery thereof by seal members 82A, 82B, 82C, and these seal members 82A to 82C are connected to the side surface 7 of the multiple valve body 24.
4 is held in an annular groove.

FIG. 9 is a sectional view showing the internal structure of a single valve 122B in which a pair of cylinder ports are provided on the opposite side of the single valve 122A. A single valve body 124 of the single valve 122B has a pair of cylinders. Port 138A, 138B
Are provided respectively. These cylinder ports 1
38A and 138B are cylinder ports 38 of the multiple valve 22.
A and 38B are formed on the opposite side, that is, on the lower surface of the single valve main body 124 in the drawing.
Cylinder cores 140A, 140B communicating with cylinder ports 138A, 138B, pump passages 142A, 142
B and the tank passage 144 are formed,
A switching spool 146 is provided movably in the longitudinal direction. Further, inside the single valve body 124, a pressure compensation spool 1 for compensating the operating pressure of the hydraulic actuator is provided.
50, and safety valves 184A, 184B for releasing a pressure higher than the set pressure to the tank passage 144 via the pressure relief cores 186A, 186B are provided corresponding to the cylinder ports 138A, 138B.

The pump passages 142A and 142B are formed between the cylinder core 140A and the cylinder core 140B, and are provided between the pump passages 142A and 142B for detecting the supply pressure to the hydraulic actuator 16. A detection core 148 is provided. On the other hand, the tank passage 144 is formed below the detection core 148 in FIG.
The return oil returned to 8A (or 138B) is introduced into the tank passage 144 via the auxiliary tank core 160A (or 160B) and the annular passage 162.

The detection core 148 is connected to the hydraulic actuator 16
The pressure oil flowing into the detection core 148 is supplied between the detection core 148 and the pump passages 142A and 142B.
Supply cores 158A, 1 for introduction into OA, 140B
58B are formed.

The switching spool 146 is connected to the cylinder port 1
It is provided in the unitary valve main body 124 between two opposing side surfaces perpendicular to the surface on which 38A and 138B are formed. The switching spool 146 is connected to the pump passage 14.
2A and 142B detect pressure oil in the core 148 and the check valve 15
6 has cutouts 147A and 147B for introduction into the supply core 158A or 158B, and the cylinder port 138A or 13
8B is returned to the auxiliary tank core 160A or 1A.
60B have cutouts 149A and 149B for introduction.

The pressure compensation spool 150 has a front chamber 166 in which a compression coil spring 170 is provided.
A check valve 172 that closes the throttle 168 with the spring force of. The pressure compensation spool 150 is connected to the signal path 1.
The signal path 164 communicates with the detection core 148 via the front chamber 166 and the throttle 168. The operation of the pressure compensation spool 150 is the same as the operation of the pressure compensation spool 50 described above.

Notches 147A, 147B and 149
A and 149B are formed opposite to each other at the center and both intermediate portions of the switching spool 146.
The pilot pressure oil is supplied to an oil chamber 154A formed on the right end side of the drawing in FIG. 46, and when the switching spool 146 strokes a predetermined amount to the left in the drawing from the position shown in FIG. And detection core 14
8 communicates with each other through the notch 147B, so that the pressure oil in the pump passage 142B is released from the notch 147B, the detection core 148,
The return oil supplied to the hydraulic actuator 16 through the check valve 156, the supply core 158B, the notch 149B, the cylinder core 140B, and the cylinder port 138B is returned to the cylinder port 138A from the hydraulic actuator 16 at this time. Tank passage 1 through section 152A, auxiliary tank core 160A, and annular passage 162.
44.

Conversely, pilot pressure oil is supplied to an oil chamber 154B formed at the left end side of the switching spool 146 in the drawing, and the pressure of the switching spool 14
6 strokes a predetermined amount from the illustrated position to the right in the figure, the pump passage 142A and the detection core 148 are notched.
47A, the pressure oil in the pump passage 142A flows through the notch 147A, the detection core 148, and the check valve 15A.
6, is supplied to the hydraulic actuator 16 through the supply core 158A, the notch 149A, the cylinder core 140A, and the cylinder port 138A.
6 is returned to the cylinder port 138B from the cylinder core 140B, the notch 152B, the auxiliary tank core 1
60B, it is introduced into the tank passage 44 via the annular passage 162.

2 and 3, reference numeral 174 denotes a single valve body 124 parallel to the longitudinal direction of the switching spool 146 and perpendicular to the cylinder ports 138A and 138B.
The side surface 174 is provided with a plurality (for example, four) of bolt insertion holes 176 and with openings 178A, 178B, 178C, 178D (see FIG. 10).

The bolt insertion hole 176 passes through the inside of the single valve body 124 in a direction perpendicular to the longitudinal direction of the switching spool 146.
Valve body 2 by means of bolts 80 passing through 6,176
4 and can be connected.

Openings 178A, 178B, 178C, 1
78D is the pump passage 142A, the pump passage 142
B, the tank passage 144 and the signal passage 164, respectively, and these openings 178 A to 178 D connect the side surface 174 of the single valve body 124 to the side surface 7 of the multiple valve body 24.
4 are formed at positions corresponding to the openings 78A to 78D when they are overlapped. In addition, opening part 178A-
178D surrounds the periphery with seal members 182A, 182B,
182C, these sealing members 18
2A to 182C are held in annular grooves formed on the side surface 174 of the single valve body 124.

In this embodiment constructed as described above, for example, the side face 174 of the single valve body 124 is butted against the side face 74 of the multiple valve body 24, and the multiple valve body 24 and the single valve body 124 are joined by bolts 80. Then, the single valve body 124
Pump passages 142A, 142B, tank passage 144, and signal passage 164 provided in openings 178A-17.
8D and the multiple valve body 2 through the openings 78A to 78D
The pump passages 42A and 42B, the tank passage 44, and the signal passage 64 provided in the pump 4 respectively communicate with each other, and the multiple valve body 24 and the single valve body 124 are integrated as one valve body.

Therefore, in this embodiment, by connecting the single valve 122A or 122B to the side surface 74 of the multiple valve body 24, the direction of the cylinder port can be arbitrarily selected according to the type of hydraulic working machine mounted. Accordingly, workability such as connection work of a hydraulic pipe connected to the cylinder port and maintenance work can be improved.

In the above-described embodiment, the opening 78 is provided.
Since the periphery of A to 78D and 178A to 178D are sealed by the seal members 82A to 82C and 182A to 182C, the pressure oil from the hydraulic pump 30 leaks from the joint between the multiple valve body 24 and the single valve body 124. Can be prevented.

The present invention is not limited to the above-described embodiment, and various changes can be made without departing from the gist of the present invention.

[0035]

As described above, according to the present invention,
A multiple valve for hydraulic work machine that can select the direction of cylinder port arbitrarily according to the type of hydraulic work machine and can improve workability such as connection work of hydraulic piping connected to cylinder port and maintenance work Can be provided.

[Brief description of the drawings]

FIG. 1 is a perspective view of a multiple valve for a hydraulic working machine according to an embodiment of the present invention.

FIG. 2 is a plan view of the multiple valve for a hydraulic working machine shown in FIG. 1;

FIG. 3 is a bottom view of the multiple valve for a hydraulic working machine shown in FIG. 1;

FIG. 4 is a side view of the multiple valve for a hydraulic working machine shown in FIG. 1;

FIG. 5 is a sectional view of the multiple valve body shown in FIG. 2;

FIG. 6 is a side view of the multiple valve body shown in FIG. 2;

FIG. 7 is a sectional view taken along line XX of FIG. 6;

FIG. 8 is a sectional view taken along line YY of FIG. 6;

FIG. 9 is a sectional view of the single valve body shown in FIG. 2;

FIG. 10 is a side view of the single valve body shown in FIG. 2;

FIG. 11 is a side view of the backhoe loader.

FIG. 12 is a view showing a conventional multiple valve.

[Explanation of symbols]

 Reference Signs List 10 backhoe loader 16 hydraulic actuator 22 multiple valve 24 multiple valve main body 26 pump port 28 tank port 30 hydraulic pump 34 tank 38A, 38B cylinder port 42A, 42B pump passage 44 tank passage 46 switching spool 48 detection core 50 pressure compensation spool 62 Annular passage 64 Signal passage 74 Side surface 76 Bolt insertion hole 78A, 78B, 78C, 78D Opening 122A, 122B Single valve 124 Single valve body 138A, 138B Cylinder port 146 Switching spool 142A, 142B Pump passage 144 Tank passage

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Shigeru Nakayama 4-5676 Hibarigaoka, Zama-shi, Kanagawa F-term (reference) 3H051 AA10 BB02 BB03 BB10 CC11 CC15 FF07 FF15 3H089 BB15 DB47 DB75 FF07 GG02 HH09 HH12 HH23 JJ01

Claims (5)

[Claims] 1. A pump port connected to a hydraulic pump of a hydraulic working machine, a tank port for discharging return oil returned from a hydraulic actuator of the hydraulic working machine to a tank, and a pressure oil supplied to the pump port. A multiple valve body having a plurality of cylinder ports for supplying to a hydraulic actuator; and a multi-valve body between opposed second and third side surfaces perpendicular to the first surface on which the cylinder ports are formed. A multiple valve for a hydraulic working machine, comprising: a plurality of switching spools provided in a communication valve body, wherein the cylinder port of the multiple valve body is parallel to a longitudinal direction of the switching spool. A plurality of bolt insertion holes penetrating through the inside of the multiple valve body in a direction perpendicular to the longitudinal direction of the switching spool are provided on a fourth surface perpendicular to the surface formed with An opening for each communicating with Pupoto and the tank port is provided, the hydraulic working machine for the multiple-valve in which the direction of the fourth surface to the cylinder port is characterized in that the connectable conflicting two unitary valve. 2. The multiple valve for a hydraulic working machine according to claim 1, wherein the multiple valve body has a detection core for detecting a supply pressure to a hydraulic actuator. 3. The multiple unit for a hydraulic working machine according to claim 1, wherein the multiple valve body has a plurality of pressure compensating spools for compensating an operation pressure of a hydraulic actuator. valve. 4. Each of the pressure compensating spools has a signal pressure passage communicating with each other.
The multiple valve for a hydraulic working machine as described. 5. The multiple valve for a hydraulic working machine according to claim 6, wherein the signal pressure passage is opened on a surface where the bolt insertion hole and the opening are formed.