JP2019211045A - Device for switching plurality of ports and adjustment flow rate - Google Patents

Abstract

To provide a device for switching a plurality of ports and adjusting a flow rate, which has a simple structure and is easy to control.SOLUTION: A device for switching a plurality of ports and adjusting a flow rate comprises: a housing 40; a plurality of flow passages 21f to 21i provided in the housing 40; a plurality of valves V1 to V4 for opening and closing the respective flow passages 21f to 21i; and an interlocking mechanism 30A for opening and closing the respective flow passages 21f to 21i by interlocking valves V1 to V4. The interlocking mechanism 30A is composed of a plurality of cams 31A to 31D and a shaft 31s. The valves V1 to V4 are needle valves, and the flow passages 21f to 21i are opened and closed by a reciprocating operation in the axial direction of the needle valves.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a multi-port switching and flow rate adjusting device.

  In the field of fluid-driven machines, hydraulic equipment dominates, but in recent years, with the development of corrosion-resistant materials, environmental and human-friendly water pressure drive technology is being reviewed. Although the history of hydraulic drive equipment is old, there are still few technologies for accurately controlling medium- and high-pressure water for moving fluid drive actuators used in industrial equipment and robot arms, etc., and equipment for realizing those controls Therefore, it is desired to develop a water 4-port directional switching valve capable of adjusting the flow rate.

  In the field of hydraulic pressure, a general 4-port directional switching servo valve and proportional valve can control the flow rate and direction of oil, but there are very few devices for water having similar functions. This is because water has a lower viscosity and higher incompressibility than oil, and therefore, there are many internal leaks in the same dimensions as hydraulic equipment, making it difficult to function.

  For example, Patent Document 1 proposes a spool-type hydraulic servo valve having the same structure as that generally used for hydraulic pressure. Patent Document 2 proposes a rotary hydraulic servo valve.

Junzo Urata and five others, "Development of hydraulic servo valves", Transactions of the Japan Society of Mechanical Engineers (Part B), Vol.63, No.610 (1997-6), p.194-201 Kenji Suzuki, “Development of Rotary Rotary Servovalves”, p.61-62, [Search May 24, 2018] <http://www.jfps.jp/ifpex2017/pdf/IFPEX2017_31.pdf>

  However, the spool type described in Non-Patent Document 1 is expensive, has a complicated structure, and requires high-precision manufacturing. Although the thing of a nonpatent literature 2 can be manufactured at comparatively low cost, highly accurate manufacture is needed. In both Non-Patent Document 1 and Non-Patent Document 2, water flows due to internal leakage even in the fully closed position (neutral position). Therefore, in order to stop the actuator such as a cylinder in the middle, control is performed by attaching a sensor to the actuator. Need to do.

  SUMMARY OF THE INVENTION The present invention solves the above-mentioned conventional problems, and an object thereof is to provide a multi-port switching and flow rate adjusting device that is simple in structure and easy to control.

  The present invention provides a housing, a plurality of flow paths provided in the housing, a plurality of flow path opening / closing members for opening / closing each flow path, and the flow paths opening / closing members in conjunction with each other. An interlocking mechanism for opening and closing the road is provided.

  According to the present invention, it is possible to provide a multi-port switching and flow rate adjusting device that is simple in structure and easy to control. In addition, since the flow rate can be almost zero at the neutral position, the actuator can be stopped without feedback control.

It is a block diagram which shows the case where a double acting cylinder is driven in the multiple port switching and flow control apparatus of 1st Embodiment. It is sectional drawing which shows the multiple port switching and flow control apparatus of 1st Embodiment. 2A is a sectional view taken along line IIIA-IIIA in FIG. 2, FIG. 2B is a sectional view taken along line IIIB-IIIB in FIG. 2, FIG. 2C is a sectional view taken along line IIIC-IIIC in FIG. FIG. It is sectional drawing which shows the 1st communication state of the multiple port switching and flow volume adjusting device of 1st Embodiment. 4A is a cross-sectional view taken along the line VA-VA in FIG. 4, FIG. 4B is a cross-sectional view taken along the line VB-VB in FIG. 4, FIG. 4C is a cross-sectional view taken along the line VC-VC in FIG. FIG. It is sectional drawing in which the multiple port switching and flow control apparatus of 1st Embodiment shows a 2nd communication state. 6A is a cross-sectional view of VIIA-VIIA in FIG. 6, FIG. 6B is a cross-sectional view of VIIB-VIIB in FIG. 6, FIG. 6C is a cross-sectional view of VIIC-VIIC in FIG. FIG. It is a graph which shows the relationship between the rotation angle of a cam, and a flow volume. It is sectional drawing which shows the multiple port switching and flow volume adjustment apparatus of 2nd Embodiment. 9A is a cross-sectional view taken along the line XA-XA in FIG. 9, FIG. 9B is a cross-sectional view taken along the line XB-XB in FIG. 9, FIG. 9C is a cross-sectional view taken along the line XC-XC in FIG. FIG. It is sectional drawing which shows the 1st communication state of the multiple port switching and flow volume adjustment apparatus of 2nd Embodiment. 11A is a XIIA-XIIA sectional view of FIG. 11, FIG. 11B is a XIIB-XIIB sectional view of FIG. 11, FIG. 11C is a XIIC-XIIC sectional view of FIG. 11, and FIG. FIG. It is sectional drawing which shows the 2nd communication state of the multiple port switching and flow volume adjustment apparatus of 2nd Embodiment. (A) is a XIVA-XIVA sectional view of FIG. 13, (b) is a XIVB-XIVB sectional view of FIG. 13, (c) is a XIVC-XIVC sectional view of FIG. 13, and (d) is a XID-XIVD sectional view of FIG. FIG. It is a block diagram which shows the case where a single acting cylinder is driven in the multiple port switching and flow control apparatus of 3rd Embodiment. (A) is a block diagram which shows the case where a bidirectional | two-way fluid rotary motor is driven in the multiple port switching and flow control apparatus of 1st Embodiment, (b) is sectional drawing which shows the internal structure of a bidirectional | two-way fluid rotary motor. is there.

Hereinafter, modes for carrying out the present invention (hereinafter referred to as “embodiments”) will be described in detail with reference to the drawings as appropriate.
(First embodiment)
FIG. 1 is a configuration diagram illustrating a case where a double-acting cylinder is driven in the multiple-port switching and flow rate adjusting device of the first embodiment. In addition, FIG. 1 is a case where the multi-port switching and flow rate adjusting device has 4 ports, and shows a fully closed state.
As shown in FIG. 1, a hydraulically driven double acting cylinder 100A (hydraulic driving device) includes a multi-port switching and flow rate adjusting device 1A, a double acting cylinder 11 (driving unit, actuator), a pump 12, a water supply source (liquid supply). Source) 13, relief valve 14, and piping 21a, 21b, 21c, 21d, 21e. Reference numeral 1B and the like will be described later in a second embodiment.

  The multi-port switching and flow rate adjusting device 1A includes valves V1, V2, V3, V4 (flow channel opening / closing members), flow channels 21f, 21g, 21h, 21i (multiple flow channels), and an interlocking mechanism 30A. Yes.

  The double-acting cylinder 11 includes a cylindrical tube 11a, a piston 11b that slides in the tube 11a in the axial direction, a rod 11c that is fixed to the piston 11b and extends in the axial direction, and end plates 11d and 11e provided at both ends of the tube 11a. It has. The double acting cylinder 11 has a first cylinder chamber Q1 surrounded by a tube 11a, a piston 11b and an end plate 11d, and a second cylinder chamber Q2 surrounded by the tube 11a, a piston 11b and an end plate 11e. . The first cylinder chamber Q1 and the second cylinder chamber Q2 are reciprocated in the axial direction by being filled with water (liquid, working fluid), respectively.

  The double-action cylinder 11 is connected to one end of a pipe 21a so as to communicate with the first cylinder chamber Q1. The other end of the pipe 21a is connected to the A port 15 (first port on the cylinder side) of the multi-port switching and flow control device 1A. In addition, one end of the pipe 21b is connected to the double acting cylinder 11 so as to communicate with the second cylinder chamber Q2. The other end of the pipe 21b is connected to the B port 16 (cylinder side second port) of the multi-port switching and flow control device 1A.

  In the multi-port switching and flow control device 1A, a P port 17 (a first port on the water supply source side) and a T port 18 (a second port on the water supply source side) are formed on the water supply source 13 side. One end of the piping 21c is connected to the P port 17. The other end of the pipe 21 c is connected to the water supply source 13. The T port 18 is connected to one end of the pipe 21d. The other end of the pipe 21 d is connected to the water supply source 13.

  The pump 12 is provided in the pipe 21c, sucks water from the water supply source 13, and supplies the water to the P port 17 of the multi-port switching and flow control device 1A. The pump 12 is ON / OFF controlled by a control device (not shown).

  The water supply source 13 stores water filling the first cylinder chamber Q1 and the second cylinder chamber Q2 of the double-acting cylinder 11, and stores water returned from the first cylinder chamber Q1 and the second cylinder chamber Q2. It is.

  The relief valve 14 is provided in a pipe 21e that connects the pipe 21c and the pipe 21d. One end of the pipe 21 e is connected to the pipe 21 c between the P port 17 and the pump 12. The relief valve 14 is opened when an excessive pressure is applied to the multi-port switching and flow regulating device 1A and the double-acting cylinder 11, and the valves V1 to V4 and piping of the multi-port switching and flow regulating device 1A are opened. 21a to 21e, flow paths 21f to 21i have a function of protecting the double acting cylinder 11 and the like.

  The valves V1 to V4 of the multiple port switching and flow rate adjusting device 1A have the same configuration, and can control the flow rate.

  The interlocking mechanism 30A operates the valves V1, V2, V3, and V4 in an interlocking manner, and includes a camshaft 31 and a drive unit 32 having a servo motor SM that rotates the camshaft 31 in both forward and reverse directions. ing. Further, by using the servo motor SM, the rotation angle of the cam shaft 31 can be set at various positions. Details of the interlocking mechanism 30A will be described later.

  FIG. 2 is a cross-sectional view showing a fully closed state of the multi-port switching and flow control device of the first embodiment. In FIG. 2, for convenience of explanation, the double-acting cylinder 11, the pump 12, the water supply source 13, the relief valve 14, and the pipes 21 a to 21 e are removed from the hydraulically driven double-acting cylinder 100 </ b> A in FIG. It is shown. The case where water is used as the working fluid will be described.

  As shown in FIG. 2, the multi-port switching and flow rate adjusting device 1A includes a housing 40A, flow paths 21f, 21g, 21h, 21i (a plurality of flow paths), valves V1 to V4 (flow path opening / closing members), And an interlocking mechanism 30A.

  The housing 40A is provided with flow paths 21f to 21i, valves V1 to V4, and an interlocking mechanism 30A, and is configured in a substantially square block shape by, for example, an aluminum alloy casting. Note that FIG. 2 illustrates a state in which the housing 40A is integrally formed, but actually, the housing 40A is configured by dividing the blocks into a plurality of blocks and combining them through packing. .

  Further, in the housing 40A, valves V1 to V4 are arranged in the horizontal direction from one end side (the left side in the figure) to the other end side (the right side in the figure). Further, the valves V1 to V4 are arranged at equal intervals. Further, the valves V1 to V4 are attached from the upper side of the housing 40A.

  Further, the P port 17 and the T port 18 are arranged to face each other in the housing 40A. The P port 17 is formed on the left side surface of the housing 40A. The T port 18 is formed on the right side surface of the housing. Further, an A port 15 and a B port 16 are formed below the T port 18 on the right side surface of the housing 40A. 2 illustrates the case where the A port 15 and the B port 16 are arranged up and down for convenience of explanation, the A port 15 and the B port 16 may be arranged side by side in the horizontal direction. Can be changed as appropriate.

  In addition, a flow path 21f that connects the P port 17 to the A port 15 is formed in the housing 40A. The flow path 21f includes a flow path 21f1 extending horizontally from the P port 17 to the position of the valve V1, a flow path 21f2 extending vertically downward from the tip of the flow path 21f1, and an A port from the lower end of the flow path 21f2. And a flow path 21 f 3 extending in the horizontal direction toward 15. The channel 21f2 is formed with a smaller diameter than the channels 21f1 and 21f3.

  Further, a flow path 21g connected to the B port 16 from the middle of the flow path 21f is formed in the housing 40A. The flow path 21g includes a flow path 21g1 extending further in the horizontal direction from the flow path 21f1, a flow path 21g2 extending downward in the vertical direction from the flow path 21g1, and a horizontal direction from the lower end of the flow path 21g2 toward the B port 16. And a flow path 21g3 extending in the direction. The channel 21g2 is formed with a smaller diameter than the channels 21g1, 21g3.

  In addition, a flow path 21 i that connects the T port 18 to the flow path 21 g 3 is formed in the housing 40 A. The flow path 21i includes a flow path 21i1 extending from the T port 18 to the position of the valve V4 in the horizontal direction, and a flow path 21i2 extending downward from the flow path 21i1 in the vertical direction and communicating with the flow path 21g3. Yes. The channel 21i2 is formed with a smaller diameter than the channels 21i1 and 21g3.

  The housing 40A is formed with a flow path 21h that extends from the middle of the flow path 21i to the middle of the flow path 21f. The flow path 21h includes a flow path 21h1 that extends further in the horizontal direction from the flow path 21i1, and a flow path 21h2 that extends downward in the vertical direction from the flow path 21h1 and communicates with the flow path 21f3. The channel 21h2 has a smaller diameter than the channels 21h1 and 21f3.

  The valve V1 includes a valve box 41, a needle valve 42A, a presser plate 43, and a coil spring 44. The valves V2 to V4 are configured similarly to the valve V1.

  The valve box 41 of the valve V1 has a recess 41a formed so that the upper surface is open, and a through hole 41b extending downward in the vertical direction so as to communicate with the flow path 21f1 from the bottom surface of the recess 41a. . Further, the axial center of the through hole 41b coincides with the axial center of the flow path 21f2. The through hole 41b is formed so that the needle valve 42A is slidable and thicker than the flow path 21f2.

  In the valve box 41 of the valve V2, the axial center of the through hole 41b coincides with the axial center of the flow path 21g2. In the valve box 41 of the valve V3, the axial center of the through hole 41b coincides with the axial center of the flow path 21h2. In the valve box 41 of the valve V4, the axial center of the through hole 41b coincides with the axial center of the flow path 21i2.

  The needle valve 42A has a base portion 42a disposed in the recess 41a and a pin portion 42b that is fixed to the lower end of the base portion 42a and is slidably inserted into the through hole 41b. The pin portion 42b is formed with a smaller diameter than the base portion 42a. A tip end (lower end) of the pin portion 42b is formed with a tapered portion 42c that is inserted into the opening (valve seat) vs1 of the flow path 21f2 so as to freely advance and retract. A disc-shaped flange 42d is formed on the upper end of the base 42a. The edge of the opening vs1 is circular. The tapered portion 42c has a circular cross section. Therefore, the valve V1 is closed in a state where the peripheral surface of the tapered portion 42c is in contact with the entire edge of the opening vs1.

  The presser plate 43 is formed in a ring shape, is inserted through the needle valve 42A, contacts the lower surface of the flange 42d, and does not fall off from the needle valve 42A.

  The coil spring 44 is inserted into the recess 41 a in a compressed state, and one end (lower end in the figure) in the axial direction is supported by the bottom surface of the recess 41 a and the other end (upper end in the figure) is supported by the presser plate 43. Due to the elastic force of the coil spring 44, a force that urges the needle valve 42A upward is acting.

  The valve V2 penetrates so that the tip of the needle valve 42B crosses the flow path 21g1, and is inserted into the opening (valve seat) vs2 of the flow path 21g2 so as to be able to advance and retreat. The valve V3 penetrates so that the tip of the needle valve 42C crosses the flow path 21h1, and is inserted into the opening (valve seat) vs3 of the flow path 21h2 so as to be able to advance and retreat. The valve V4 penetrates the tip of the needle valve 42D so as to cross the flow path 21i1, and is inserted into the opening (valve seat) vs4 of the flow path 21i2 so as to freely advance and retract. Note that the valves V2 to V4 are configured such that the valves V2 to V4 are closed in a state where the peripheral surface of the tapered portion 42c is in contact with the entire edges of the openings vs2 to vs4, similarly to the valve V1.

  The camshaft 31 of the interlocking mechanism 30A has a shaft 31s extending from one end of the housing 40A toward the other end. The shaft 31s is rotatably supported by bearings 31t and 31t provided at both ends of the housing 40A. Further, cams (plate cams) 31A, 31B, 31C, 31D are fixed to the shaft 31s. The cam 31A is disposed at a position in contact with the needle valve 42A of the valve V1. The cam 31B is disposed at a position in contact with the needle valve 42B of the valve V2. The cam 31C is disposed at a position in contact with the needle valve 42C of the valve V3. The cam 31D is disposed at a position in contact with the needle valve 42D of the valve V4.

  The drive unit 32 applies rotational force to the shaft 31s in both forward and reverse directions, so that all the cams 31A to 31D rotate simultaneously. The valves V1 to V4 open and close as the cams 31A to 31D rotate. Moreover, the drive part 32 can set the rotation angle of the axis | shaft 31s in steps by using servomotor SM (refer FIG. 1).

  3A is a sectional view taken along line IIIA-IIIA in FIG. 2, FIG. 3B is a sectional view taken along line IIIB-IIIB in FIG. 2, FIG. 3C is a sectional view taken along line IIIC-IIIC in FIG. It is IIID sectional drawing. 3A to 3D are cross-sectional views when viewed from the X direction in FIG.

  As shown in FIG. 3A, the cam 31A has a first cam surface m1 formed with the same radius R1 from the center of the shaft 31s. The first cam surface m1 extends from the point P1 in FIG. 3A to the point P2 through the cam surface on the right side of the drawing. The point P1 to the point P2 is an angle range of about 180 degrees. The cam 31A has a second cam surface m2 formed so that the radius R2 from the center of the shaft 31s gradually decreases. The second cam surface m2 has an angle range of about 140 degrees from point P2 to point P3 in FIG.

  In the valve V1 shown in FIG. 3A, the cam 31A is in contact with the needle valve 42A at the position of the point P2. That is, the needle valve 42A is in contact with the upper end of the needle valve 42A (the upper end in the axial direction on the side opposite to the tip) at the position with the largest radius. In this state, the needle valve 42A is pushed down most against the urging force of the coil spring 44, and the opening vs1 of the flow path 21f2 is closed by the needle valve 42A.

  As shown in FIG. 3B, the cam 31B has a first cam surface m3 formed with the same radius from the center of the shaft 31s. The first cam surface m3 extends from the point P4 in FIG. 3B to the point P5 through the left cam surface in the drawing. The point P4 to the point P5 is an angle range of about 180 degrees. The cam 31B has a second cam surface m4 formed so that the radius from the center of the shaft 31s gradually decreases. The second cam surface m4 has an angle range of about 140 degrees from the point P5 to the point P6 in FIG.

  In the valve V2 shown in FIG. 3B, the cam 31B is in contact with the needle valve 42B at the point P5. That is, the needle valve 42B is in contact with the upper end of the needle valve 42B (the upper end in the axial direction on the opposite side of the tip) at the position with the largest radius. In this state, the needle valve 42B is pushed down most against the urging force of the coil spring 44, and the opening vs2 of the flow path 21g2 is closed by the needle valve 42B.

  As shown in FIG. 3C, the cam 31C is configured similarly to the cam 31B. As shown in FIG. 3D, the cam 31D is configured similarly to the cam 31A.

  Thus, the cam 31A corresponding to the valve V1 and the cam 31D corresponding to the valve V4 have the same shape and the same arrangement. The cam 31B corresponding to the valve V2 and the cam 31C corresponding to the valve V3 have the same shape and the same arrangement. The cams 31B and 31C are arranged so that the left and right sides of the cams 31A and 31D are reversed.

  As shown in FIGS. 3A to 3D, when the valves V1 to V4 are all closed, the communication between the P port 17 (see FIG. 2) and the A port 15 (see FIG. 2) is blocked. Therefore (because the opening vs1 of the flow path 21f2 is closed by the needle valve 42A), the water from the P port 17 is blocked at the position of the needle valve 42A of the flow path 21f1. Further, since the communication between the P port 17 (see FIG. 2) and the B port 16 (see FIG. 2) is blocked (the opening vs2 of the flow path 21g2 is closed by the needle valve 42B), the P port 17 Water is blocked at the position of the needle valve 42B in the flow path 21g1 through the gap formed between the needle valve 42A and the flow path 21f1 (see FIG. 3B).

  Further, since the communication between the T port 18 (see FIG. 2) and the A port 15 (see FIG. 2) is blocked (the opening vs3 of the flow path 21h2 is closed by the needle valve 42C), the T port 18 The water returning to is blocked at the position of the needle valve 42C in the flow path 21h1. Further, since the communication between the T port 18 (see FIG. 2) and the B port 16 (see FIG. 2) is blocked (the opening vs4 of the flow path 21i2 is closed by the needle valve 42D), the T port 18 The water returning to is blocked at the position of the needle valve 42C in the flow path 21i1.

FIG. 4 is a cross-sectional view showing the first communication state of the multiple port switching and flow rate adjusting device of the first embodiment.
As shown in FIG. 4, in the multi-port switching and flow rate adjusting device 1A, when the shaft 31s rotates in a predetermined direction by the driving force of the driving unit 32, the valves V1 to V4 operate in conjunction with each other. That is, when the shaft 31s rotates by a predetermined angle, the valves V1 and V4 are opened while the valves V2 and V3 are closed. At this time, the P port 17 and the A port 15 communicate with each other by operating the needle valve 42A so that the opening vs1 of the flow path 21f2 is opened. Further, the T port 18 and the B port 16 communicate with each other by operating the needle valve 42D so that the opening vs4 of the flow path 21i2 is opened.

  Thereby, the water sucked up from the water supply source 13 (see FIG. 1) by the pump 12 (see FIG. 1) is introduced into the P port 17 and led out from the A port 15 through the flow paths 21f1, 21f2, and 21f3. The The water led out from the A port 15 is introduced into the first cylinder chamber Q1 (see FIG. 1) of the double acting cylinder 11 through the pipe 21a (see FIG. 1). When water is introduced into the first cylinder chamber Q1, the internal pressure (water pressure) of the first cylinder chamber Q1 increases, and the piston 11b (see FIG. 1) operates in the direction of expanding the first cylinder chamber Q1.

  Further, the operating force of the piston 11b (see FIG. 1) pushes the water in the second cylinder chamber Q2 (see FIG. 1) back to the B port 16 through the pipe 21b (see FIG. 1). The water pushed back to the B port 16 is pushed back from the T port 18 through the flow paths 21g3, 21i2, and 21i1. The water pushed back from the T port 18 is returned to the water supply source 13 via the pipe 21d (see FIG. 1).

  Further, since the valve V3 is closed, even if the water flowing from the P port 17 to the A port 15 enters the flow path 21h2 from the flow path 21f3, it may leak into the flow path 21h1 communicating with the T port 18. Absent. Further, since the valve V2 is closed, even if water returned to the B port 16 enters the flow path 21g2 from the flow path 21g3, it does not leak into the flow path 21g1 communicating with the P port 17.

5A is a sectional view taken along the line VA-VA in FIG. 4, FIG. 5B is a sectional view taken along the line VB-VB in FIG. 4, FIG. 5C is a sectional view taken along the line VC-VC in FIG. It is VD sectional drawing. 5A to 5D are cross-sectional views seen from the X direction in FIG. 4, similarly to FIG. 3.
The cam 31A shown in FIG. 5A is a state in which the cam 31A shown in FIG. 3A is rotated by a predetermined angle (for example, 45 degrees) in the W1 direction (counterclockwise direction). Thereby, the cam 31A rotates while the second cam surface m2 slides on the upper end of the needle valve 42A. Since the second cam surface m2 is formed so that the radius from the center of the shaft 31s gradually decreases from the point P2 to the point P3, the needle valve 42A gradually rises due to the elastic force of the coil spring 44. As a result, the tip of the needle valve 42A comes out of the opening vs1 of the flow path 21f2, so that the valve V1 is opened. When the valve V1 is opened, water from the flow path 21f1 flows into the flow paths 21f2 and 21f3.

  The cam 31B shown in FIG. 5B is a state in which the cam 31B shown in FIG. 3B is rotated in the W1 direction (counterclockwise direction) by the same angle (for example, 45 degrees). Thereby, the cam 31B rotates while the first cam surface m3 slides on the upper end of the needle valve 42B. Since the first cam surface m3 is formed with the same radius from the center of the shaft 31s from the point P5 to the point P4, the needle valve 42B does not lift up.

  Since the cam 31C shown in FIG. 5C operates in the same manner as the valve V2, the needle valve 42C does not rise. Since the cam 31D shown in FIG. 5D operates in the same manner as the valve V1, the needle valve 42D is gradually raised by the elastic force of the coil spring 44. As a result, the tip of the needle valve 42D comes out of the opening vs4 of the flow path 21i2, and thus the valve V4 is opened. When the valve V4 is opened, water from the flow paths 21g3 and 21i2 flows into the flow path 21i1.

FIG. 6 is a cross-sectional view showing the second communication state of the multi-port switching and flow control device of the first embodiment.
As shown in FIG. 6, in the multiple port switching and flow rate adjusting device 1 </ b> A, the valves V <b> 1 to V <b> 4 operate in conjunction with each other when the shaft 31 s rotates in the direction opposite to that in FIG. That is, when the shaft 31s rotates by a predetermined angle, the valves V2 and V3 are opened while the valves V1 and V4 are closed. At this time, the needle valve 42B is operated to open the opening vs2 of the flow path 21g2, so that the P port 17 and the B port 16 communicate with each other. Further, the needle port 42C operates to open the opening vs3 of the flow path 21h2, whereby the T port 18 and the A port 15 communicate with each other.

  Thereby, the water sucked up from the water supply source 13 (see FIG. 1) by the pump 12 (see FIG. 1) is introduced into the P port 17 and passes through the flow paths 21f1, 21g1, 21g2, and 21g3 from the B port 16. Derived. The water led out from the B port 16 is introduced into the second cylinder chamber Q2 (see FIG. 1) of the double acting cylinder 11 through the pipe 21b (see FIG. 1). When water is introduced into the second cylinder chamber Q2, the internal pressure (water pressure) of the second cylinder chamber Q2 increases, and the piston 11b (see FIG. 1) operates in the direction of expanding the second cylinder chamber Q2.

  Further, the operating force of the piston 11b (see FIG. 1) pushes the water in the second cylinder chamber Q1 (see FIG. 1) back to the A port 15 through the pipe 21a (see FIG. 1). The water pushed back to the A port 15 is pushed back from the T port 18 through the flow paths 21f3, 21h2, 21h1, and 21i1. The water pushed back from the T port 18 is returned to the water supply source 13 via the pipe 21d (see FIG. 1).

  Further, since the valve V4 is closed, even if the water flowing from the P port 17 to the B port 16 enters the flow path 21i2 from the flow path 21g3, it may leak into the flow path 21i1 communicating with the T port 18. Absent. Further, since the valve V1 is closed, even if the water flowing from the A port 15 to the T port 18 enters the flow path 21f2 from the flow path 21f3, it may leak into the flow path 21f1 communicating with the P port 17. Absent.

7A is a sectional view taken along the line VIIA-VIIA in FIG. 6, FIG. 7B is a sectional view taken along the line VIIB-VIIB in FIG. 6, FIG. 7C is a sectional view taken along the line VIIC-VIIC in FIG. It is VID sectional drawing.
The cam 31A shown in FIG. 7A is a state in which the cam 31A shown in FIG. 3A is rotated in the W2 direction (clockwise direction) by the same angle (for example, 45 degrees). Thereby, the cam 31A rotates while the first cam surface m1 slides on the upper end of the needle valve 42A. Since the first cam surface m1 is formed with the same radius from the center of the shaft 31s from the point P2 to the point P1, the needle valve 42A is not lifted by the biasing force of the coil spring 44.

  The cam 31B shown in FIG. 7B is a state in which the cam 31B shown in FIG. 3B is rotated by a predetermined angle (for example, 45 degrees) in the W2 direction (clockwise direction). Thereby, the cam 31B rotates while the second cam surface m4 slides on the upper end of the needle valve 42B. The second cam surface m4 is formed such that the radius from the center of the shaft 31s gradually decreases from the point P5 to the point P6, so that the needle valve 42B gradually rises due to the elastic force of the coil spring 44. As a result, the tip of the needle valve 42B comes out of the opening vs2 of the flow path 21g2, so that the valve V2 is opened. When the valve V2 is opened, water from the flow path 21g1 flows into the flow paths 21g2 and 21g3.

  Since the cam 31C shown in FIG. 7C operates in the same manner as the cam 31B, the needle valve 42C gradually rises due to the elastic force of the coil spring 44. As a result, the tip of the needle valve 42C comes out of the opening vs3 of the flow path 21h2, so that the valve V3 is opened. When the valve V3 is opened, water from the flow paths 21f3 and 21h2 flows into the flow path 21h1. Since the cam 31D shown in FIG. 7D operates in the same manner as the valve V1, the needle valve 42D is not lifted by the urging force of the coil spring 44.

  FIG. 8 is a graph showing the relationship between the cam rotation angle and the flow rate. In FIG. 8, the direction of the rotation angle is not considered. Further, as shown in FIGS. 3A and 3D, the state where the cams 31A and 31D are in contact with the needle valves 42A and 42D at the point P2 is 0 degrees, as shown in FIGS. 3B and 3C. In addition, the state where the cams 31B and 31C are in contact with the needle valves 42B and 42C at the point P5 is defined as 0 degree.

  Since the cam 31A has the second cam surface m2 formed so that the radius decreases from the point P2 toward the point P3, the needle valve 42A comes out of the opening vs1 of the flow path 21f2, so that the flow path The opening vs1 of 21f2 gradually expands. That is, as shown in FIG. 8, as the rotation angle (servo motor stroke) increases (see FIG. 3 (a) → FIG. 5 (a)), the flow rate of water flowing from the flow path 21f1 to the flow path 21f2 increases. To do.

  As with the cam 31A, the cam 31D has a flow rate of water flowing from the flow path 21i2 to the flow path 21i1 as the rotation angle (servo motor stroke) increases (see FIG. 3 (d) → FIG. 5 (d)). To increase.

  Since the cam 31B has the second cam surface m4 formed so that the radius decreases from the point P5 to the point P6, the needle valve 42B exits from the opening vs2 of the flow path 21g2, so that the flow path The opening vs2 of 21g2 gradually expands. That is, as shown in FIG. 8, as the rotation angle (servo motor stroke) increases (see FIG. 3 (b) → FIG. 7 (b)), the flow rate of water flowing from the flow path 21g1 to the flow path 21g2 increases. To do.

  As with the cam 31D, the cam 31C has a flow rate of water flowing from the flow path 21h2 to the flow path 21h1 as the rotation angle (servo motor stroke) increases (see FIG. 3 (c) → FIG. 7 (c)). To increase.

  As described above, the multi-port switching and flow rate adjusting device 1A according to the first embodiment includes the housing 40A, the flow paths 21f to 21i provided in the housing 40A, and the plurality of channels that open and close the flow paths 21f to 21i. Valves V1 to V4 and an interlocking mechanism 30A that opens and closes the flow paths 21f to 21i by interlocking a plurality of valves V1 to V4 are provided. According to this, since the plurality of valves V1 to V4 can be interlocked and moved simultaneously by the interlocking mechanism 30A, the control of the valves V1 to V4 is simplified and the operation mechanism (structure) of the valves V1 to V4 is simplified. Can be.

  In the first embodiment, the interlocking mechanism 30A includes a plurality of cams 31A to 31D and a shaft 31s that open and close the valves V1 to V4. By controlling the valves V1 to V4 with the cams 31A to 31D, the flow rate of the working fluid can be easily controlled.

  In the first embodiment, the flow path opening / closing members are needle valves 42A to 42D, and the flow paths 21f to 21i (flow paths) are opened and closed by the reciprocating operation in the axial direction G of the needle valves 42A to 42D. According to this, by opening and closing the valves V1 to V4 by the axial operation of the needle valves 42A to 42D, when water is used as the working fluid, internal leakage can be suppressed, and almost zero flow rate can be realized at the neutral position. The performance as the multiple port switching and flow rate adjusting device 1A for water can be improved. Further, since the flow rate can be reduced to zero at the neutral position, when the multi-port switching and flow rate adjusting device 1A is applied to the hydraulic drive cylinder 100A, the actuator (double-acting cylinder 11) is stopped without feedback control at the neutral position. It becomes possible.

  In the first embodiment, the cams 31A to 31D include the first cam surfaces m1 and m3 formed with the same radius R1, and the second cam surfaces m2 and m4 formed so that the radius R2 gradually decreases. (See FIGS. 3, 5, and 7). According to this, the first cam surfaces m1 and m3 slide on the needle valves 42A to 42D, so that the needle valves 42A to 42D can be kept closed, and the second cam surfaces m2 and m4 are in the needle valve 42A. The opening degree of the needle valves 42A to 42D can be controlled (changed) by sliding to ~ 42D.

  In the first embodiment, the needle valves 42A to 42D penetrate from the direction orthogonal to the flow paths 21f to 21i (flow paths 21f1, 21g1, 21h1, and 21i1), and the flow paths 21f to 21i pass through the needle valves 42A to 42D. The apertures vs1, vs2, vs3, vs4 are opened and closed by the tip (tip 42c). According to this, the valves V1 to V4 can be opened and closed without sliding the needle valves 42A to 42D, and the internal leakage of the working fluid can be suppressed.

  Moreover, in 1st Embodiment, the working fluid which flows into the some flow paths 21f-21i is water. According to this, compared with working fluids, such as oil_pressure | hydraulic, environmental load can be eased.

  In the first embodiment, the multi-port switching and flow rate adjusting device 1A can be connected to the double-acting cylinder 11 for use. According to this, it can be applied to various drive devices such as a wheel loader, a dump truck bed, a biped walking robot, a SCARA robot, a crawler, a crane, an industrial robot, a telescopic arm, and a robot arm.

(Second Embodiment)
FIG. 9 is a cross-sectional view showing the multiple port switching and flow rate adjusting device of the second embodiment. In addition, FIG. 9 has shown the multi-port switching and flow control apparatus 1B in a fully closed state.
As shown in FIG. 9, the multi-port switching and flow rate adjusting device 1B (multiple-port switching device) includes a housing 40B, flow paths 21f, 21g, 21h, 21i (multiple flow paths), and valves V10, V20, V30. , V40 (channel opening / closing member) and an interlocking mechanism 30B.

  The housing 40B is provided with flow paths 21f to 21i, valves V10 to V40, and an interlocking mechanism 30B, and is configured in a substantially square block shape by, for example, an aluminum alloy casting. Although FIG. 9 shows a state in which the casing 40B is integrally formed, the casing 40B is actually configured by dividing into a plurality of blocks and combining them using packing. .

  In the housing 40B, valves V10 to V40 are arranged in the horizontal direction from one end side (the left side in the drawing) to the other end side (the right side in the drawing). Further, the P port 17 and the T port 18 are arranged to face each other in the housing 40B. The P port 17 is formed on the left side surface of the housing 40B. The T port 18 is formed on the right side surface of the housing. Further, an A port 15 and a B port 16 are formed below the T port 18 on the right side surface of the housing 40B.

  Further, a valve box 45 penetrating from one end side to the other end side is formed in the housing 40B. In the valve box 45, valves V10 to V40 are arranged side by side in the axial direction. Moreover, the valve box 45 is divided into right and left by the sealing member 42a in the center of the axial direction. Valves V10 and V20 are arranged on one side divided by the seal member 42a, and valves V30 and V40 are arranged on the other side. Further, bearings 42b and 42b that rotatably support the shaft 31s of the interlocking mechanism 30B are provided at both ends of the valve box 45.

  A flow path 21f that connects the P port 17 to the A port 15 is formed in the housing 40B. The flow path 21f includes a flow path 21f4 extending in the horizontal direction from the P port 17, and a flow path 21f5 extending downward in the vertical direction from the tip of the flow path 21f4. The tip of the channel 21f4 extends to between the valves V10 and V20. The flow path 21f5 communicates with a flow path (space) 21f6 formed between the valve V10 and the valve V20.

  Further, the channel 21f has a channel 21f7 extending downward from the lower part of the channel 21f6. The flow path 21f has a flow path 21f8 extending in the horizontal direction from the lower end of the flow path 21f7 toward the A port 15. The channel 21f7 is formed with a smaller diameter than the channels 21f4 and 21f8. Further, the valve V10 is located in the opening vs10 (valve seat) of the flow path 21f7.

  The channel 21g has a channel 21g7 extending downward from the lower part of the channel 21f6. The flow path 21g has a flow path 21g8 extending in the horizontal direction from the lower end of the flow path 21g7 toward the B port 16. The channel 21g7 is formed with a smaller diameter than the channels 21f4 and 21g8. A valve V20 is located at the opening vs20 (valve seat) of the flow path 21g7.

  In the housing 40B, a flow path 21h connected from the T port 18 to the A port 15 is formed. The flow path 21h includes a flow path 21h4 extending in the horizontal direction from the T port 18 and a flow path 21h5 extending downward in the vertical direction from the tip of the flow path 21h4. The tip of the channel 21h4 extends to between the valves V30 and V40. The flow path 21h5 communicates with a flow path (space) 21h6 formed between the valve V30 and the valve V40.

  The flow path 21h has a flow path 21h7 that extends downward from the lower portion of the flow path 21h6 and communicates with the flow path 21f8. The flow path 21h7 is formed with a smaller diameter than the flow paths 21h4 and 21f8. Further, the valve V30 is located in the opening vs30 (valve seat) of the flow path 21h7.

  The channel 21i has a channel 21i7 that extends downward from the lower part of the channel 21h6 and communicates with the channel 21g8. The flow path 21i7 is formed with a smaller diameter than the flow paths 21h4 and 21g8. Further, the valve V40 is located in the opening vs40 (valve seat) of the flow path 21i7.

  The valve V10 has a rotating body 33 formed in a substantially cylindrical shape that rotates while sliding in the valve box 45, and the rotating body 33 is fixed to a shaft 31s. A cutout portion 32 </ b> A is formed on the outer peripheral surface of the rotating body 33. The cutout portion 32A is formed in a tapered shape so as to be gradually separated from the peripheral wall surface of the flow path 21f6 toward the adjacent valve V20.

  The valve V20 includes a rotating body 33 formed in a substantially cylindrical shape that slides in the valve box 45, and is fixed to the shaft 31s. The rotating body 33 is formed with a notch 32B similar to the valve V10. This notch 32B is formed in a taper shape so as to gradually separate from the peripheral wall surface of the flow path 21f6 toward the adjacent valve V10.

  The valves V30 and V40 are also arranged so that the notches 32C and 32D are formed on the outer peripheral surface of the rotating body 33 and the notches 32C and 32D are opposed to each other as in the valves V10 and V20.

10A is a cross-sectional view taken along the line XA-XA in FIG. 9, FIG. 10B is a cross-sectional view taken along the line XB-XB in FIG. 9, FIG. 10C is a cross-sectional view taken along the line XC-XC in FIG. 10A to 10D are cross-sectional views when viewed from the X direction in FIG.
As shown in FIG. 10A, the rotating body 33 of the valve V10 has an outer peripheral surface m10 having the same radius R1. This outer peripheral surface m10 is an angle range of 180 degrees or more from the point P10 to the point P20 in FIG. The cutout portion 32A of the valve V10 is formed so that the volume of the cutout gradually increases from both ends in the circumferential direction toward the center. In other words, the space sandwiched between the surface of the notch 32A and the peripheral wall surface of the valve box 45 is formed so as to gradually increase from both ends in the circumferential direction toward the center.

  Further, the valve V10 is closed when the outer peripheral surface m10 of the rotating body 33 is positioned in the opening vs10 of the flow path 21f7. Further, the notch 32A is located on the upper left in the figure so as not to overlap the opening vs10.

  As shown in FIG. 10B, the valve V20 is closed when the outer peripheral surface m10 of the rotating body 33 is positioned in the opening vs20 of the flow path 21g7. Further, the notch 32B is located on the upper right side in the figure so as not to overlap the opening vs20.

  As shown in FIG. 10C, the valve V30 is closed when the outer peripheral surface m10 of the rotating body 33 is positioned in the opening vs30 of the flow path 21h7. In addition, the notch 32C is located on the upper right side in the figure so as not to overlap the opening vs30.

  As shown in FIG. 10D, the valve V40 is closed when the outer peripheral surface m10 of the rotating body 33 is positioned in the opening vs40 of the flow path 21i7. Further, the notch 32D is located on the upper left in the figure so as not to overlap the opening vs40.

  As shown in FIGS. 10A and 10D, the notch 32A of the valve V10 and the notch 32D of the valve V40 have the same shape and the same arrangement. Further, as shown in FIGS. 10B and 10C, the notch 32B of the valve V20 and the notch 32C of the valve V30 have the same shape and the same arrangement.

  As shown in FIGS. 10A to 10D, when all the valves V10 to V40 are closed, the communication between the P port 17 (see FIG. 9) and the A port 15 (see FIG. 9) is blocked. Therefore (because the opening vs10 is closed by the outer peripheral surface m10), the flow path 21f is blocked at the position of the flow path 21f6. Further, since the communication between the P port 17 and the B port 16 (see FIG. 9) is blocked (since the opening vs20 is closed by the outer peripheral surface m10), the flow path 21g is blocked at the position of the flow path 21f6. ing.

  Further, since the communication between the T port 18 (see FIG. 9) and the A port 15 is blocked (the opening vs30 is closed by the outer peripheral surface m10), the flow channel 21h is blocked at the position of the flow channel 21h7. ing. Further, since the communication between the T port 18 and the B port 16 is blocked (since the opening vs40 is closed by the outer peripheral surface m10), the flow channel 21i is blocked at the position of the flow channel 21i7.

FIG. 11 is a cross-sectional view showing the first communication state of the multi-port switching and flow control device of the second embodiment.
As shown in FIG. 11, in the multi-port switching and flow rate adjusting device 1B, when the shaft 31s is rotated by the driving force of the driving unit 32, the valves V10 to V40 are rotated in conjunction with each other. That is, when the shaft 31s rotates by a predetermined angle, the valves V10 and V40 are opened while the valves V20 and V30 are closed. At this time, the P port 17 and the A port 15 communicate with each other by the rotation of the cutout portion 32A of the rotating body 33 and opening of the opening vs10 of the flow path 21f7. Further, the notch 32D of the rotating body 33 rotates to open the opening vs40 of the flow path 21i7, whereby the T port 18 and the B port 16 communicate with each other.

  As a result, the water sucked from the water supply source 13 (see FIG. 1) by the pump 12 (see FIG. 1) is introduced into the P port 17 and passes through the flow paths 21f4, 21f5, 21f6, 21f7, 21f8 and the A port. 15 is derived. The water led out from the A port 15 is introduced into the first cylinder chamber Q1 (see FIG. 1) of the double acting cylinder 11 through the pipe 21a (see FIG. 1). When water is introduced into the first cylinder chamber Q1, the internal pressure (water pressure) of the first cylinder chamber Q1 increases, and the piston 11b (see FIG. 1) operates in the direction of expanding the first cylinder chamber Q1.

  Further, the operating force of the piston 11b (see FIG. 1) pushes the water in the second cylinder chamber Q2 (see FIG. 1) to the B port 16 through the pipe 21b (see FIG. 1). The water pushed out to the B port 16 is pushed out from the T port 18 through the flow paths 21g8, 21i7, 21h6, 21h5, 21h4. The water pushed out from the T port 18 is returned to the water supply source 13 (see FIG. 1) via the pipe 21d (see FIG. 1).

  Further, since the valve V30 is closed, even if the water flowing from the P port 17 to the A port 15 enters the flow path 21h7 from the flow path 21f8, it may leak into the flow path 21h6 communicating with the T port 18. Absent. Further, since the valve V20 is closed, when water flows from the B port 16 to the T port 18, even if it enters the flow path 21g7 from the flow path 21g8, the water leaks into the flow path 21f6 communicating with the P port 17. There is nothing.

12A is a cross-sectional view taken along the line XIIA-XIIA in FIG. 11, FIG. 12B is a cross-sectional view taken along the line XIIB-XIIB in FIG. 11, FIG. 12C is a cross-sectional view taken along the line XIIC-XIIC in FIG. It is XIID sectional drawing.
The valve V10 shown in FIG. 12A is a state in which the rotating body 33 is rotated by a predetermined angle (for example, 90 degrees) in the W10 direction (counterclockwise direction) shown in FIG. Thereby, after the rotary body 33 slides on the inner wall surface of the valve box 45, the notch 32A of the rotary body 33 faces the opening vs10. Thereby, the water supplied from the P port 17 through the flow paths 21f4, 21f5, and 21f6 flows into the flow paths 21f7 and 21f8 from the opening vs10 through the notch 32A. At this time, the notch 32A is formed so that the notch is increased from the point P10. Therefore, depending on the position of the notch 32A (rotation angle, stroke of the servo motor of the drive unit 32), the flow path 21f7 from the opening vs10. The flow rate flowing into the pipe changes (rises).

  The valve V20 shown in FIG. 12B is in a state in which the rotating body 33 is rotated in the W10 direction (counterclockwise direction) shown in FIG. 10B by the same angle (for example, 90 degrees). Thereby, the rotator 33 rotates while sliding on the inner wall surface (circumferential wall surface) of the valve box 45. Even if the same angle as the valve V10 is rotated, the notch 32B does not face the opening vs10, so the valve V20 remains closed.

  The valve V30 shown in FIG. 12C is a state in which the rotating body 33 is rotated in the W10 direction (counterclockwise direction) shown in FIG. 10C by the same angle (for example, 90 degrees). Thereby, the rotating body 33 rotates while sliding on the inner wall surface of the valve box 45. Even if the same angle as the valves V10 and V20 is rotated, the notch 32C does not face the opening vs30, so the valve V30 remains closed.

  The valve V40 shown in FIG. 12 (d) is in a state where the rotating body 33 is rotated in the W10 direction (counterclockwise direction) shown in FIG. 10 (d) by the same angle (for example, 90 degrees). Thereby, after the rotary body 33 slides on the inner wall surface of the valve box 45, the notch 32D of the rotary body 33 faces the opening vs40. As a result, the water returned from the B port 16 through the flow paths 21g8 and 21i7 flows into the flow paths 21h6, 21h5, and 21h4 from the opening vs40 through the notch 32D. At this time, the notch 32D is formed so that the notch is increased from the point P10. Therefore, depending on the position of the notch 32D (the rotation angle, the stroke of the servo motor of the drive unit 32), the flow path 21h6 extends from the opening vs40. , 21h5, 21h4 flows (changes).

FIG. 13 is a cross-sectional view showing the second communication state of the multiple port switching and flow rate adjusting device of the second embodiment.
As shown in FIG. 13, in the multi-port switching and flow rate adjusting device 1 </ b> B, when the shaft 31 s rotates in the direction opposite to that in FIG. 11 by the driving force of the driving unit 32, the valves V <b> 10 to V <b> 40 rotate together. That is, when the shaft 31s rotates by a predetermined angle, the valves V20 and V30 are opened while the valves V10 and V40 are closed. At this time, the notch 32A of the rotating body 33 of the valve V20 opens the opening vs20 of the flow path 21g7, whereby the P port 17 and the B port 16 communicate with each other. Further, the notch 32C of the rotating body 33 of the valve V30 rotates to open the opening vs30 of the flow path 21h7, whereby the T port 18 and the A port 15 communicate with each other.

  As a result, the water sucked up from the water supply source 13 (see FIG. 1) by the pump 12 (see FIG. 1) is introduced into the P port 17 and passes through the flow paths 21f4, 21f5, 21f6, 21g7, 21g8 to the B port. 16 is derived. The water led out from the B port 16 is introduced into the second cylinder chamber Q2 (see FIG. 1) of the double acting cylinder 11 through the pipe 21b (see FIG. 1). When water is introduced into the second cylinder chamber Q2, the internal pressure (water pressure) of the second cylinder chamber Q2 increases, and the piston 11b (see FIG. 1) operates in the direction of expanding the second cylinder chamber Q2.

  Further, the operating force of the piston 11b (see FIG. 1) pushes the water in the first cylinder chamber Q1 (see FIG. 1) to the A port 15 through the pipe 21a (see FIG. 1). The water pushed out to the A port 15 is pushed out from the T port 18 through the flow paths 21f8, 21h7, 21h6, 21h5, 21h4. The water pushed out from the T port 18 is returned to the water supply source 13 (see FIG. 1) via the pipe 21d (see FIG. 1).

  Further, since the valve V40 is closed, even if water enters the flow path 21i7 from the flow path 21g8 in the P port 17 to the B port 16, water flows into the flow paths 21h6, 21h5, and 21h4 communicating with the T port 18. There is no leakage. Further, since the valve V10 is closed, even if water enters the flow path 21f7 from the flow path 21f8 from the A port 15 to the T port 18, water flows into the flow paths 21f6, 21f5, and 21f4 communicating with the P port 17. There is no leakage.

14A is a XIVA-XIVA sectional view of FIG. 13, FIG. 14B is a XIVB-XIVB sectional view of FIG. 13, FIG. 14C is a XIVC-XIVC sectional view of FIG. 13, and FIG. It is XIVD sectional drawing.
The valve V10 shown in FIG. 14A is a state in which the rotating body 33 is rotated by a predetermined angle (for example, 90 degrees) in the W20 direction (clockwise direction) shown in FIG. Thereby, even after the rotating body 33 slides on the inner wall surface of the valve box 45, the notch 32A does not face the opening vs10, so the valve V10 remains closed.

  The valve V20 shown in FIG. 14B is in a state in which the rotating body 33 is rotated in the W20 direction (clockwise direction) shown in FIG. 10B by the same angle (for example, 90 degrees). Thereby, after the rotary body 33 slides on the inner wall surface of the valve box 45, the notch 32B of the rotary body 33 faces the opening vs20. Thereby, the water supplied from the P port 17 (see FIG. 13) through the flow paths 21f4, 21f5, and 21f6 flows into the flow paths 21g7 and 21g8 from the opening vs20 through the notch 32B. At this time, since the notch 32B is formed so that the notch is larger from the point P30, the flow path from the opening vs20 depends on the rotation position of the notch 32B (rotation angle, stroke of the servo motor of the drive unit 32). The flow rate flowing into 21g7 changes (rises).

  The valve V30 shown in FIG. 14C is in a state in which the rotating body 33 is rotated in the W20 direction (clockwise direction) shown in FIG. 10C by the same angle (for example, 90 degrees). Thereby, after the rotary body 33 slides on the inner wall surface of the valve box 45, the notch 32C of the rotary body 33 faces the opening vs30. Thereby, the water pushed out from the A port 15 through the flow paths 21f8 and 21h7 flows into the flow paths 21h6, 21h5 and 21h4 from the opening vs30 through the notch 32C. At this time, the notch 32C is formed so that the notch becomes larger from the point P30, so that the flow path from the opening vs30 depends on the rotation position of the notch 32C (rotation angle, stroke of the servo motor of the drive unit 32). The flow rate flowing into 21h6 changes (rises).

  The valve V40 shown in FIG. 14D is in a state in which the rotating body 33 is rotated in the W20 direction (clockwise direction) shown in FIG. 10D by the same angle (for example, 90 degrees). Thereby, even after the rotating body 33 slides on the inner wall surface of the valve box 45, the notch 32D does not face the opening vs40, so the valve V40 remains closed.

  As described above, the multi-port switching and flow rate adjusting device 1B according to the second embodiment includes the housing 40B, the channels 21f to 21i provided in the housing 40B, and the plurality of channels that open and close the channels 21f to 21i. Valves V10 to V40 and an interlocking mechanism 30B that interlocks the plurality of valves V10 to V40. According to this, since a plurality of valves V10 to V40 can be interlocked and moved simultaneously by the interlocking mechanism 30B, the control of the valves V10 to V40 is simplified and the operation mechanism (structure) of the valves V1 to V4 is simplified. Can be.

  In the second embodiment, the valves V <b> 10 to V <b> 40 have a rotating body 33 that slides and rotates in the flow paths 21 f to 21 i, and the flow paths 21 f to 21 i are formed on the outer peripheral surface of the rotating body 33. It is opened and closed by the rotation of the notches 32A to 32D. According to this, by operating the valves V10 to V40 by the cam, the opening degree of the valves V10 to V40 can be controlled, and the flow rate of the working fluid can be controlled.

  In the second embodiment, the notches 32A to 32D are formed so that the space formed between the notches 32A to 32D and the flow paths 21f to 21i changes in the circumferential direction. According to this, the flow rate of the working fluid can be controlled with a simple structure.

(Third embodiment)
FIG. 15 is a configuration diagram illustrating a hydraulically driven double-acting cylinder provided with a three-port switching device as the multiple-port switching device of the third embodiment.
As shown in FIG. 15, the hydraulic drive double acting cylinder 100B (hydraulic drive double acting cylinder) includes a 3 port switching device (multiple port switching device) 1C, a single acting cylinder 11A (driving unit, actuator), a pump 12, and water. A supply source (liquid supply source) 13, a relief valve 14, and pipes 21a, 21c, 21d, and 21e are provided.

  The three-port switching device 1C includes valves V1 and V3 (channel opening / closing members), channels 21f and 21h (a plurality of channels), and an interlocking mechanism 30C.

  The single acting cylinder 11A includes a cylindrical tube 11a, a piston 11b that slides in the axial direction in the tube 11a, a rod 11c that is fixed to the piston 11b and extends in the axial direction, and end plates 11d and 11e. The single acting cylinder 11A has a cylinder chamber Q1 surrounded by a tube 11a, a piston 11b, and an end plate 11d. Further, the single acting cylinder 11A has a coil spring 11f (biasing member) for biasing the piston 11b to the cylinder chamber Q1 in a cylinder chamber surrounded by the tube 11a, the piston 11b, and the end plate 11e. The first cylinder chamber Q1 is filled with water (liquid, fluid).

  Further, in the single acting cylinder 11A, one end of a pipe 21a is connected to the cylinder chamber Q1. The other end of the pipe 21a is connected to the A port 15 of the 3-port switching device 1C.

  The valves V1 and V3 are configured in the same manner as the valves V1 and V3 in the first embodiment. That is, the 3-port switching device 1C has a configuration in which the valves V2, V4 and the flow paths 21g1, 21g2, 21g3 are removed from the multiple-port switching and flow rate adjusting device 1A of the first embodiment of FIG. The valves V1 and V3 may have the same configuration as the valves V10 and V30 in the second embodiment.

  In such a three-port switching device 1C, the valve V1 is opened and the valve V3 is closed by the interlock mechanism 30C, so that the P port 17 and the A port 15 communicate with each other. Thereby, the water of the water supply source 13 is introduced into the P port 17 from the pipe 21 c by the power of the pump 12. The water led out from the A port 15 is introduced into the cylinder chamber Q1 through the pipe 21a. By introducing water into the cylinder chamber Q1, the internal pressure of the cylinder chamber Q1 rises, and the piston 11b operates in a direction to expand the cylinder chamber Q1 against the urging force of the coil spring 11f.

  In the three-port switching device 1C, the valve V1 is closed and the valve V3 is opened by the interlock mechanism 30C, so that the A port 15 and the T port 18 communicate with each other. Thereby, the water in the cylinder chamber Q1 is pushed out to the A port 15 by the urging force of the coil spring 11f, and returned to the water supply source 13 through the flow path 21h and the pipe 21.

  As described above, the 3-port switching device 1C of the third embodiment is similar to the first embodiment in that the housing 40A, the plurality of flow paths 21f and 21h provided in the housing 40A, the flow paths 21f, A plurality of valves V1, V3 for opening and closing 21h, and an interlocking mechanism 30C for opening and closing the flow paths 21f, 21h by interlocking the valves V1, V3 are provided. Thereby, since the plurality of valves V1, V3 can be interlocked and moved simultaneously by the interlocking mechanism 30C, the control of the valves V1, V3 is simplified and the structure of the valves V1, V3 can be simplified.

FIG. 16A is a block diagram showing a case where a bidirectional fluid rotary motor is driven in the multi-port switching and flow control device of the first embodiment, and FIG. 16B is a cross section showing an internal structure of the bidirectional fluid rotary motor. FIG.
As shown in FIG. 16 (a), the hydraulic motor 100C (hydraulic driving device) is a bidirectional fluid rotary motor 9 (driving unit) instead of the double acting cylinder 11 (direct acting cylinder) of FIG. It is. The bidirectional fluid rotary motor 9 has a cylindrical housing 9a and an output shaft 9b protruding from the axial direction of the housing 9a. The output shaft 9b rotates in both forward and reverse directions so that the object can be driven.

  As shown in FIG. 16 (b), the bidirectional fluid rotary motor 9 is attached to a fixed wall 9c formed on the inner wall of the housing 9a, concentrically with the housing 9a, and to be rotatable with respect to the housing 11. An output shaft 9b, a part of which is always in contact with the fixed wall 9c, and a vane 9d extending radially from the output shaft 9b and having a tip slidably in contact with the inner wall of the housing 9a. Yes. The bidirectional fluid rotary motor 9 has two hydraulic chambers defined by the inner wall surface of the housing 9a, the output shaft 9b, and the vane 9d. Pipes 21a and 21b for introducing and discharging fluid are connected to each hydraulic chamber.

  Thus, since the flow rate can be reduced to zero at the neutral position, when the multi-port switching and flow rate adjusting device 1A is applied to the hydraulic motor 100C, the actuator (bidirectional fluid drive motor 9) is not feedback controlled at the neutral position. Can be stopped.

  In addition, this invention is not limited to above-described embodiment, Various modifications are included. For example, the multi-port switching and flow control devices 1A and 1B and the 3-port switching device 1C have been described as examples, but the present invention may be applied to a switching device having 5 or more ports. In the first embodiment, the cams 31A to 31D have been described by taking plate cams as an example. However, other types of cams such as groove cams may be combined.

  In the above-described embodiment, the drive unit 32 having the single servo motor SM (motor) has been described as an example. However, the present invention is not limited to such a configuration, and a plurality of servos are provided. The drive unit may be configured by connecting motors SM (motors) in parallel. For example, two motors (needle valves, etc.) may be combined (8, 9, etc.), or a combination of three motors (needle valves, etc.). Any combination may be used.

1A, 1B Multiple port switching and flow control device 9 Bidirectional fluid drive motor (drive unit)
DESCRIPTION OF SYMBOLS 11 Double acting cylinder 11A Single acting cylinder 11a Tube 11b Piston 11c Rod 11d, 11e End plate 11f Coil spring 12 Pump 13 Water supply source (liquid supply source)
14 Relief valve 15 A port 16 B port 17 P port 18 T port 21a, 21b, 21c, 21d, 21e Piping 21f, 21g, 21h, 21i flow path (multiple flow paths)
21f1, 21f2, 21f3, 21g1, 21g2, 21g3, 21h1, 21h2, 21i1, 21i2 Flow path 30A, 30B, 30C Interlocking mechanism 31 Camshaft 31s Shaft 31t Bearing 31A, 31B, 31C, 31D Cam 32 Drive 32A, 32B, 32C, 32D Notch 33 Rotating body 40A, 40B Housing 41A, 42B, 42C, 42D Needle valve 44 Coil spring 45 Valve box vs1, vs2, vs3, vs4, vs10, vs20, vs30, vs40 Opening m1, m3 First cam surface m2 , M4 Second cam surface Q1 First cylinder chamber Q2 Second cylinder chamber V1, V2, V3, V4, V10, V20, V30, V40 Valve (channel opening / closing member)
100A, 100B Water pressure driven double acting cylinder 100C Water pressure motor

Claims (9)

The body,
A plurality of flow paths provided in the housing;
A plurality of channel opening and closing members for opening and closing each channel;
A multi-port switching and flow rate adjusting device comprising an interlocking mechanism for opening and closing each of the flow paths by interlocking the plurality of flow path opening and closing members. In the multiple port switching and flow control device according to claim 1,
The interlocking mechanism is constituted by a plurality of cams and shafts, and is a multi-port switching and flow rate adjusting device. In the multiple port switching and flow control device according to claim 1,
The flow path opening / closing member is a needle valve,
The multi-port switching and flow rate adjusting device, wherein the flow path is opened and closed by an axial reciprocation of the needle valve. In the multiple port switching and flow control device according to claim 2,
The cam has a first cam surface formed with the same radius from the rotation center of the shaft, and a second cam surface formed so that the radius from the rotation center of the shaft is gradually reduced. A multi-port switching and flow rate adjusting device characterized by that. In the multiple port switching and flow control device according to claim 3,
The needle valve operates in a direction perpendicular to the flow path;
The multi-port switching and flow rate adjusting device, wherein the flow path has an opening that is opened and closed by a tip of the needle valve. In the multiple port switching and flow control device according to claim 5,
A multi-port switching and flow rate adjusting device characterized in that an axial direction of the needle valve and an axial direction of the flow path in which the opening is formed coincide with each other. In the multiple port switching and flow control device according to claim 1,
The channel opening / closing member has a rotating body that slides and rotates in the channel,
The multi-port switching and flow rate adjusting device, wherein the flow path is opened and closed by a rotation operation of a notch formed in an outer peripheral surface of the rotating body. In the multiple port switching and flow control device according to claim 7,
The multiport switching and flow rate adjusting device, wherein a space formed between the notch and the flow path is changed in a circumferential direction. In the multi-port switching and flow control device according to claim 1 or 7,
The multi-port switching and flow rate adjusting device, wherein the working fluid flowing through the plurality of flow paths is water.

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