JPS6246004Y2 - - Google Patents

Description

[Detailed description of the invention] <Industrial application field> The invention is applicable to directional control valves for hydraulic drive devices such as hydraulics,
More specifically, in a directional valve that controls flow path switching and flow rate by rotating a valve rotor housed in a housing, the range is changed by sliding the valve rotor relative to the housing in the axial direction. This invention relates to an adjustable directional control valve.

<Prior Art> Conventionally, this type of directional control valve generally adjusts the flow rate to the actuator by the rotation of the valve rotor, in other words, by the restriction of the valve rotor in the circumferential direction, that is, by the opening degree of the inlet port in the circumferential direction. It is configured to perform the following. Therefore, the flow rate corresponding to the rotational stroke (rotation angle) of the valve rotor is constant. For example, if you try to move a 40/m actuator with a 100/m directional control valve, the entire valve rotor will move. Operability is poor because the rotation stroke cannot be used effectively.

Therefore, in order to solve this problem, even if the maximum flow rate is 100/m, it would be possible if it could be configured so that it corresponds to the actuator so that, for example, the maximum flow to the actuator is only 40/m. This adjustment is generally called range adjustment.

By the way, conventional range adjustments that have been generally performed include (a) a method in which the spring pressure in the secondary pressure chamber (spring chamber) of a pressure compensation valve attached to a control valve can be adjusted from the outside; b) A method of preparing many types of valve rotors with different sizes of notches in the throttle part of the valve rotor, and replacing them each time. (c) A method of manufacturing a directional control valve with a larger capacity and improving it. In addition, there is a method of limiting the amount of rotation of the valve rotor.

<Problems to be solved by the invention> However, the above method has the following problems. In other words, method (a) is to increase or decrease the pressure of the spring to adjust the amount of rotation of the valve rotor and, therefore, the flow rate to the actuator relative to the circumferential opening of the inlet port. Therefore, the amount of adjustment can only be made within a very limited range. Next, method (b) involves manufacturing a large number of valve rotors and replacing them with ones corresponding to the actuator, which is costly and practically impossible to replace on site. Next, method (c) limits the amount of movement of the valve rotor in the rotational direction and adjusts the flow rate within its rotational stroke (rotation range), which reduces operability. Rather, this method does not amount to range adjustment.

The present invention focuses on the above points, and by simply sliding the valve rotor and housing relative to each other in the axial direction, the maximum flow rate to the actuator can be freely changed, thereby causing the valve rotor to rotate. It is an object of the present invention to provide a directional control valve that can adjust the flow rate to an actuator corresponding to the rotational stroke (rotation angle) of the valve rotor by making full use of the directional momentum.

<Means for Solving the Problems> The structure of the present invention for solving the above problems will be explained using FIGS. 1 to 14, which correspond to the embodiments. and a valve rotor 2, which has a direction switching part for switching a flow path and is rotatably housed in a rotor housing part 3 of the housing 1,
In a directional control valve that controls switching of the flow path by rotating the valve, (a) the valve rotor 2 and the housing 1 side are configured to be able to slide relative to each other in the axial direction; b) A cutout recess 11 communicating with the inlet port 5 is formed on the inner wall surface of the rotor housing portion 3, and a cutout recess 11 communicating with the inlet port 5 is formed on the outer peripheral surface of the valve rotor 2 at a position corresponding to the cutout recess 11 of the valve rotor 2. A constriction part 13 for adjusting the opening degree formed by notching is provided,
By sliding the valve rotor 2 or the housing 1 side in the axial direction, the opening degree of the throttle part 13 in the axial direction can be adjusted, and by rotating the valve rotor 2, the opening degree of the throttle part 13 can be adjusted. (c) The throttle section 13 is connected to the direction switching section 14 of the valve rotor 2 through a connecting passage 17, and the fluid pressure of the inlet port 5 is controlled by the throttle. The device is characterized in that it is configured to be introduced into the direction switching section 14 through the section.

<Operation> The above technical means operates as follows. Pressure fluid is sent in a fixed amount from a pump unit such as a hydraulic pump. Therefore, now, the valve rotor side 2 or housing 1
When sliding the side in the axial direction, the throttle part 1 of the valve rotor 2
3 in the axial direction, that is, the opening degree of the inlet port 5 in the axial direction gradually increases or decreases in the range from 0 to 100 in accordance with the amount of sliding of the throttle portion 13. This opening degree is adjusted depending on the target actuator. After adjusting the opening degree as described above, the valve rotor 2
and housing 1 are fixed in the axial direction.

In this state, when the valve rotor 2 is rotated left or right from the neutral position, the inlet port 5 maintains the axial opening set above and is closed to the load side (A Port 6 or B
port 7). Therefore, the pressure fluid is supplied to the actuator, but the flow rate to the load side is limited by the restriction in the circumferential direction of the restricting portion 13 within the range of the opening degree in the axial direction of the inlet port 5 set above, that is, The rotational position of the valve rotor 2 in the direction of rotation results in a stepless increase or decrease during the entire rotational stroke of the valve rotor.

The flow rate corresponding to the amount of rotation of the valve rotor 2 changes depending on the opening degree of the inlet port 5 in the axial direction.

<Example> Hereinafter, an example of the present invention will be described with reference to the drawings. 1 to 14 show a directional control valve showing one embodiment of the present invention. In these figures, 1
is a housing, and the housing 1 is equipped with a rotor housing part 3 for rotatably housing the valve rotor 2, a pump port 4, an inlet port 5 connecting the pump port 4 and the inlet side of the rotor housing part 3;
A port 6 and B port 7 (see Fig. 3) connected to the direction switching section (described later) of the rotor storage section 3, and a return port 8 selectively connected to both ports 6 and 7.
and a tank port 9 connected to the return port 8, and the pump port 4 has a pump part (not shown);
The A and B ports 6 and 7 are connected to the actuator section, and the tank port 9 is connected to the tank section. In addition, the pressure introduction chamber 1 of the rotor storage section 3
Notch recesses 11, 11 communicating with the inlet port 5 are formed facing each other on the inner wall surface on the 0 side.

The valve rotor 2 is rotatably and axially slidably housed in the rotor accommodating portion 3 of the housing 1.
One end protrudes outside the housing 1, and the valve rotor 2 is rotated in the forward and reverse directions within the storage portion 3 by operating the operating lever 12 attached to the protruding end 2a, or by using a motor or other means to switch the flow path as described later. It is configured as follows. The valve rotor 2 is provided with a throttle part 13 for opening adjustment, which is cut out and formed at a position corresponding to the notch recesses 11, 11 of the rotor storage part 3, and the throttle part 13 and the notch recesses 11, 11 are formed in the valve rotor 2. Notch recess 11 due to the relative positional relationship in the axial direction with
By changing the opening degree of the axial orifice constituted by It is configured to change the opening degree of the circumferential orifice constituted by the recessed part 11 and the throttle part 13, and to steplessly adjust the flow rate on the side of the actuator part within the range of the maximum flow rate set as described above. . In the embodiment, the throttle portions 13, 13 are formed by cutting the outer circumferential surface of the valve rotor 2 in parallel flat shapes, but the throttle portions 13, 13 are not flat, and for example, the throttle portions 13, 13 are cut in the direction described later. It may be curved concavely and cut out like the switching path of the switching part.
It may be formed on a straight line where the tangent lines A and B (see FIG. 10) of the constricted portions 13, 13 formed by the notches and the notch recesses 11, 11 intersect at right angles.

The valve rotor 2 is provided with a direction switching section 14 for switching the direction of the flow path.
Direction switching passages 15 and 16, which are curved in a crescent shape and cut out on the outer circumferential surface of
4 and a flow rate adjustment chamber 18 formed on the throttle section 13 side, the hydraulic pressure in the same chamber 18 is guided to the direction switching section side, and by rotating the valve rotor 2 in the forward or reverse direction, the flow is adjusted from the neutral position. The diaphragm section 1
3 is configured to introduce the throttled hydraulic pressure into the A port 6 or the B port 7. In this case, the switching means for switching the direction of the flow path may be a mechanism other than the one in the embodiment, and the key is to switch the flow path in synchronization with the throttle part by rotating the valve rotor 2. It is sufficient to configure it as follows.

Reference numerals 19 and 20 indicate cutout grooves provided on the outer circumferential surface of the valve rotor 2 to correspond to the direction switching passages 15 and 16. , 22, so that a part of the hydraulic pressure of the switching paths 15 and 16 is branched and introduced. 23 and 24 are lid bodies;
The lid body 23 also serves as a lid body for a pressure compensation valve, which will be described later.

Reference numeral 25 indicates a sliding mechanism of the valve rotor 2, and reference numeral 26 indicates a screw rod screwed onto the lid body 23. An annular flange 27 is formed at the tip of the screw rod 26, and the flange 27 is connected to the base end 2b of the valve rotor 2. The valve rotor 2 is configured to be rotatably engaged with the valve rotor 2 and to slide the valve rotor 2 in the axial direction (forward or backward) by rotating the screw rod 26, and 28 and 29 are nuts. In this case, the sliding mechanism of the valve rotor 2 may be a mechanism other than the one in the embodiment.

Reference numeral 30 denotes a pressure compensation valve built in the housing 1 in parallel with the valve rotor 2, and includes a cylinder 31 communicating with the pump port 4 and the tank port 9, and a slide piston 32 slidably housed in the cylinder 31. A primary pressure chamber 33 communicating with the pump port 4 is formed on one side of the piston 32;
The pressure on the pump side (primary pressure) is introduced into the primary pressure chamber 33 to act on the piston 32, and a secondary pressure chamber 34 is formed on the other side of the piston 32. When the rotor 2 is in a non-neutral position), the opening/closing circuit 35 selectively communicates with the load side, that is, one side of the direction switching path 15 or 16, to introduce pressure (secondary pressure) on the load side. It is configured. A spring 36 is housed in the secondary pressure chamber 34 and presses the piston 32 toward the primary pressure chamber 33. The piston 32 is operated by the pressure in the primary pressure chamber 33, the pressure in the secondary pressure chamber 34, and the spring. The effects of 36 are balanced and balanced. 37 is a stopper that restricts the movement of the piston 32 toward the primary pressure chamber, 38 is a variable relief portion formed to change the opening degree by sliding the piston 32 in the axial direction, and 39 is provided on the outer peripheral surface of the valve rotor 2. , a drain passage formed to communicate the opening/closing circuit 35 and the return port 8 when the valve rotor 2 is in the neutral position; 40 and 48 are legs for fixing the housing 1; A portion indicated by a chain line (code 0) indicates an opening formed by the throttle portion 13 of the valve rotor 2 and the notch recess 11 of the rotor storage portion 3.

In FIG. 1, the part indicated by the reference numeral 41 is a relief valve housing part located on the side of the pressure compensating valve 30 and provided in the lid body 23.
1 houses a relief valve, and the relief valve communicates with the secondary pressure chamber 34.

The directional control valve of the embodiment is constructed as described above, and its operation method and function will be explained next. First, adjustment of the maximum flow rate of fluid to the load side will be explained.

A fixed amount of fluid is sent to the pump port 4 from a supply unit such as a hydraulic pump. So, Natsu28,
29 and rotate the screw rod 26, for example, to the right (clockwise), the screw rod 26 slides to the right in FIG. 1, and this movement is transmitted to the valve rotor 2 through the flange 27. Therefore, the valve rotor 2 also slides to the right in the figure, and the distance X (first
0) becomes longer, the opening degree of the axial orifice formed by the constricted part 13 and the notched recess 11 gradually increases (see Fig. 12), and conversely, the threaded rod 26 is moved to the left (counterclockwise). direction), the valve rotor 2 slides to the left, and the distance X between the tangent line A and the bottom line C becomes shorter, so the opening degree of the orifice gradually becomes smaller. Therefore, with this, the maximum flow rate of the fluid flowing to the load side can be adjusted (range adjustment). After the above adjustment, nut 28,
29 to restrict movement of the valve rotor 2 in the axial direction.

Therefore, within the range of the maximum flow rate set as above, the valve rotor 2 is rotated to the left or right, and the circumference formed by the throttle part 13 of the valve rotor 2 and the notch recess 11 of the rotor storage part 3 is adjusted. The flow rate to the load side is adjusted by the opening degree of the orifice in the direction, and the direction of the flow path is changed at the same time.Next, the throttling operation and direction switching operation will be explained. Now, when the valve rotor 2 is in the state shown in the first diagram, that is, in the neutral position, the notched recesses 11, 11
is blocked by the outer peripheral surface of the valve rotor 2 (the 11th
13A), and the A and B ports 6, 7, connection path 17 and return port 8 of the direction switching unit 14 are also blocked (see FIGS. 3 and 14A). Therefore, the fluid is introduced into the primary pressure chamber 33 from the pump port 4, and the piston 32 is pushed toward the secondary pressure chamber 34 side by the pressure of the fluid, fully opening the variable relief portion 38, and the fluid is introduced into the variable relief portion. 38 and returns to the tank section from the tank port 9. In the above, the secondary pressure chamber 3
The fluid in the tank 4 passes through the drain passage 39, the return port 8, and returns to the tank portion from the tank port 9.

Then, when the lever 12 is operated and the valve rotor 2 is rotated, for example, to the right (clockwise) from the neutral position (the positions shown in FIGS. 13A and 14A), the notch recesses 11 As shown in FIG. 13B, as the throttle parts 13 and 13 rotate, they are gradually opened and the inlet port 5 and the connecting passage 17 are communicated with each other.
In line with this, as shown in Figure 14 (b), connecting path 1
7 is connected to the A port 6 by the direction switching path 15, and
The B port 7 is connected to the return port 8 by the direction switching path 16.
Therefore, the fluid from the pump port 4 passes through the inlet port 5, the pressure introduction chamber 10, the notched recesses 11, 11, the pressure adjustment chamber 18, the connection path 17, the switching path 15, and the A port 6 to the actuator. The return fluid passes through the B port 7, the switching path 16, the return port 8, and returns to the tank section from the tank port 9. The flow rate to the load side is adjusted steplessly by the throttle of the throttle section 13, that is, the rotational position of the valve rotor 2, within the range of the maximum flow rate set as described above.
On the other hand, the primary pressure chamber 33 of the pressure compensation valve 30 communicates with the pump port 4, and the secondary pressure chamber 34 communicates with the switching path 15 through the opening/closing circuit 35, the notch groove 20, and the communication groove 22. A part of the fluid (secondary pressure) in the switching path 15 is introduced into the pressure chamber 34,
Therefore, the primary pressure and the secondary pressure act on the piston 32, and the difference between the two pressures is kept constant (spring pressure).

Next, when the valve rotor 2 is rotated to the left (counterclockwise) from the neutral position, the notched recesses 11, 11 are gradually opened by the throttle parts 13, 13, and the inlet port 5 and the connecting path are opened as shown in FIG. 13C. 17 are connected, and as shown in FIG. The fluid is inlet port 5,
It passes through the pressure introduction chamber 10, the notched recesses 11, 11, is throttled by the throttle parts 13, 13, passes through the pressure adjustment chamber 18, the connection path 17, and the switching path 16, and is supplied to the actuator section from the B port 7, and is supplied to the actuator section from the A port 6. , switching path 1
5. Returns to the tank section from the tank port 9 through the return port 8, and the secondary pressure chamber 34 of the pressure compensation valve 30 is connected to the open/close circuit 35, the notch groove 19, and the communication path 21.
A part of the fluid in the switching path 16 is introduced into the secondary pressure chamber 34. Therefore, the primary pressure and the secondary pressure act on the piston 32 in the same manner as described above, and the piston 32 in equilibrium.

Note that in the embodiment, the valve rotor 2 is configured to slide in the axial direction with respect to the housing 1;
On the contrary, the housing 1 side may be configured to slide in the axial direction with respect to the valve rotor 2, or alternatively, a notched recess as in the embodiment may be provided between the valve rotor 2 and the rotor housing portion 3. A sleeve may be provided and the sleeve may be slid.

<Effects of the invention> The present invention is a directional control valve that switches the flow path and controls the flow rate by rotating a valve rotor that is rotatably housed in a housing. A notch recess communicating with the inlet port is formed on the inner wall surface of the rotor accommodating portion of the housing, and a valve rotor is provided at a position corresponding to the notch recess of the valve rotor. A throttle part for opening adjustment is formed by cutting out the outer peripheral surface of the valve, and by sliding the valve rotor or housing side in the axial direction, the opening degree of the throttle part in the axial direction can be adjusted. It is configured as follows.

Therefore, according to the present invention, the following main effects can be expected.

(a) The maximum flow rate to the actuator can be adjusted freely by simply sliding the valve rotor and housing side relative to each other in the axial direction, making range adjustment more efficient than with conventional technology. Therefore, a directional control valve with good operability can be obtained.

(b) By rotating the valve rotor, the flow path to the actuator section is switched and the flow rate is controlled. It is controlled steplessly by the throttle opening degree of the valve rotor, that is, the momentum of the valve rotor in the rotational direction.

Therefore, the total rotational stroke of the valve rotor,
In other words, the entire rotation range can be used 100% effectively to smoothly and precisely control the adjustment of the flow rate to the actuator.

[Brief explanation of the drawing]

The drawings show an embodiment of the directional control valve according to the present invention, in which Fig. 1 is a cross-sectional view, Fig. 2 is a cross-sectional view showing the main parts, and Fig. 3 is a cross-sectional view taken along the line - in Fig. 1. Fig. 4 is a side view of the valve rotor, Fig. 5 is a plan view thereof, Fig. 6 is a sectional view taken along the - line in Fig. 5, Fig. 7 is a sectional view taken along the - line in Fig. 5, and Fig. 8 is a sectional view taken along the - line in Fig. 5. FIG. 5 is a sectional view taken along the - line in FIG. 5, FIG. 9 is an explanatory enlarged sectional view of the aperture part, FIG.
The figure is a sectional view taken along the - line in Fig. 9, Fig. 12 is a developed explanatory view of the throttle part, Fig. 13 A, B, and C are explanatory diagrams showing the operating states of the throttle part, and Fig. 14 A, B, and C are explanatory diagrams showing the operating states of the throttle part. It is an explanatory view showing a switching operation state of a direction switching part. 1... Housing, 2... Valve rotor, 3... Rotor housing, 4... Pump port, 5... Inlet port, 6... A port, 7... B port, 8...
Return port, 9... Tank port, 11... Notch recess, 13... Throttle part, 14... Direction switching part, 1
5, 16...Direction switching road, 17...Connecting road, 25
...Sliding mechanism, 26 ... Screw rod, 27 ... Flange, 28, 29 ... Nut, A, B ... Tangent line, C
...Bottom line of notch recess 11, X...tangent line A and bottom line C
Distance between O...opening.

Claims (1)

[Claims for Utility Model Registration] A housing having a rotor housing, and a valve rotor having a direction switching unit for switching a flow path and rotatably housed in the rotor housing of the housing; In a directional control valve that controls flow path switching by rotation, (a) the valve rotor and the housing side are configured to be able to slide relative to each other in the axial direction; A notch recess communicating with the inlet port is formed on the inner wall surface of the rotor storage portion, and at a position corresponding to the notch recess of the valve rotor,
By providing a throttle part for opening adjustment formed by cutting out the outer peripheral surface of the valve rotor, and sliding the valve rotor or housing side in the axial direction,
The opening degree of the throttle part in the axial direction can be adjusted and the opening degree of the throttle part in the circumferential direction can be changed by rotating the valve rotor, (c) the throttle part is connected to the direction switching section of the valve rotor by a connecting passage, and is configured to introduce hydraulic pressure of the inlet port to the direction switching section via the throttle section.