JP2005315296A - Rotary selector valve for hydraulic device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary selector valve for hydraulic device capable of properly changing over a pilot passage even where a plurality of selector valves are connected in series arrangement while the construction is small sized. <P>SOLUTION: Each rotary selector valve is furnished with a P1 port changeover valve element part 10 which is formed at the forefront of a rotor 5 and has the same diameter as the changeover valve element part, and in the part 10 a passage hole 73 is provided penetrating in the radial direction. When the rotor 5 is in the neutral position, one end of the passage hole 73 is put in communication with a P1 port pressure leading passage 32 (pilot passage). Also in the neutral condition, the other end of the hole 73 is put in communication with a DR port 19 (drain passage connection hole). A check valve 77 to flow the working oil only toward an oil returning hole 33 is installed between the DR port 19 and the oil returning passage 33. The DR port 19 and the check valve 77 are provided at the forefront of a valve housing 4 where the P1 port changeover valve element part 10 is accommodated. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a rotary switching valve for a hydraulic device that switches, for example, rotation / stop and rotation direction of a hydraulic motor by rotation of a rotor.

  2. Description of the Related Art Conventionally, a switching valve is used to switch an operating state of a hydraulic motor or a hydraulic cylinder that is a drive source for a marine hydraulic winch or a construction machine. As a conventional switching valve for a hydraulic device of this type, there is one configured as shown in Patent Document 1, for example. The switching valve shown in Patent Document 1 is a spool valve in which a spool is reciprocally supported by a valve housing, and the spool has a forward rotation position on one end side in the axial direction, a reverse rotation position on the other end side, The operating state of the hydraulic motor is switched by positioning it at any one of the neutral position (stop position) between these two positions.

  This conventional spool type switching valve is provided with balance chambers at both ends in the axial direction of the spool in order to balance the pressure of the hydraulic oil leaked by the internal leak, and these balance chambers communicate with each other in the valve housing. A communication path is provided, and the communication path is connected to the drain path. The drain passage is connected to a drain pipe attached to the valve housing.

  Usually, the drain pipe is connected to a hydraulic oil tank located far away from the operation position where the switching valve is provided. For this reason, this type of spool-type switching valve requires a long drain pipe, and there is a problem that troublesome piping work must be performed. In order to avoid such problems, a rotary type switching valve that returns internal leakage to the hydraulic oil return passage is used instead of the spool type switching valve in accordance with the purpose of use.

  Conventional rotary switching valves position hydraulic oil such as hydraulic cylinders and hydraulic motors (hereinafter referred to as hydraulic equipment) by positioning a rotor rotatably provided in the valve housing in one or the other of the rotational directions. And the hydraulic oil return passage for guiding the hydraulic oil discharged from the hydraulic equipment to the hydraulic oil tank, and the rotor is positioned at the neutral position. The hydraulic device is configured to be shut off by interrupting the communication. The hydraulic equipment may be provided with a pressure release brake, and the rotary switching valve connected to this type of hydraulic equipment operates the pilot passage for pressurization of the pressure release brake at the neutral position. The pilot passage is connected to the oil return passage, and in other states, the pilot passage is connected to the hydraulic oil supply passage.

  Further, when a plurality of hydraulic devices are driven by a single hydraulic pressure supply pump, a conventional rotary type switching valve may be used by connecting a plurality of switching valves in series so as to form a so-called series circuit. is there. In this case, a hydraulic oil supply pump is connected to the hydraulic oil supply port (the inlet of the hydraulic oil supply passage) of the first rotary type switching valve, and the hydraulic oil return port (the outlet of the hydraulic oil return passage) is connected to the first The hydraulic oil supply port of 2 rotary type switching valves is connected. When the other switching valve is connected to the hydraulic oil return port of the second rotary type switching valve, the hydraulic oil supply port of the switching valve is connected, and when the other switching valve is not connected. A hydraulic oil tank is connected.

  When a plurality of switching valves are connected in series in this way, for example, when the first rotary switching valve is in a neutral state, the hydraulic pressure of the same pressure as the supply side acts on the hydraulic oil return port. Hydraulic pressure is also applied to the pilot passage connected in the valve housing. Therefore, in this case, braking cannot be performed by the pressure release brake of the hydraulic device connected to the first rotary switching valve.

For this reason, a rotary type switching valve connected to a hydraulic device having a pressure release type brake is equipped with a brake switching valve for switching connection / cutoff of only the pilot passage. The brake switching valve includes a spool that moves due to a pressure difference between the hydraulic oil supply passage and the hydraulic oil return passage of the rotary type switching valve, and when the rotary type switching valve is in a neutral state, the pilot passage serves as a drain passage. Configured to connect.
In addition, the applicant could not find prior art documents closely related to the present invention by the time of filing other than the prior art documents specified by the prior art document information described in this specification. .
JP-A-8-100805 (FIG. 1)

  As described above, when a plurality of switching valves are connected in series, the conventional rotary switching valve has to be equipped with a switching valve dedicated for a brake, which increases the cost. Note that when the rotary type switching valve is configured to have the function of the switching valve dedicated to the brake, the rotary type switching valve must not be increased in size.

  The present invention has been made to solve such a problem. A rotary type switching valve for a hydraulic device capable of correctly switching a pilot passage even when a plurality of switching valves are connected in series while reducing the size is provided. The purpose is to provide.

  In order to achieve this object, a rotary type switching valve for a hydraulic device according to the present invention includes a passage switching rotor and a pressure compensation type flow rate adjusting valve, and is operated by rotating the rotor to operate the hydraulic oil supply passage. A hydraulic device rotary that replaces the oil return passage, connects the hydraulic oil supply passage to the pilot passage of the driven device, and connects the hydraulic oil return passage to the pilot passage by bringing the rotor into a neutral state. A pilot switching valve body part having the same diameter as the switching valve body part in a part of the rotor, a passage hole penetrating in the radial direction is provided in the pilot switching valve body part, In the neutral state, one end of the passage hole is connected to the pilot passage, and the other end is connected to the drain passage connection port and the hydraulic oil return passage side from the drain passage connection port. Through a check valve to flow only to the dynamic oil return passage side connected to the hydraulic fluid return passage is a check valve and these drain passage connection hole which is provided in the valve housing.

  According to a second aspect of the present invention, there is provided a rotary switching valve for a hydraulic device according to the first aspect of the present invention, wherein the rotor and the pressure compensation type flow control valve are parallel to each other. Provided in the housing, the pilot switching valve body of the rotor is positioned below the pressure adjusting means of the pressure compensation type flow regulating valve.

  A rotary type switching valve for a hydraulic device according to a third aspect of the present invention is the rotary type switching valve for a hydraulic device according to the first or second aspect of the present invention, wherein the pilot passage is connected to a pressure release brake. This is a pressure passage, and the hydraulic oil return passage is connected to the hydraulic oil supply passage of another hydraulic device.

  When the rotor of the rotary type switching valve for a hydraulic device according to the present invention is in a neutral state, the pilot passage is connected to the drain passage by the passage hole of the pilot switching valve body, and the hydraulic oil return passage is defined by the check valve. Be isolated. For this reason, when using a plurality of switching valves connected in series, the hydraulic pressure in the hydraulic oil return passage is not shut off by the check valve and transmitted to the pilot passage. At this time, the pilot passage is opened. can do.

Therefore, although the rotary type switching valve for a hydraulic device according to the present invention is a rotary type switching valve, it is not necessary to use another switching valve for switching the pilot passage, so that the cost can be reduced. it can.
Further, the rotary switching valve for a hydraulic device has the pilot switching valve body formed in a part of the rotor, and the drain housing connection port and the check valve are integrally provided in the valve housing. The pilot passage switching passages, members, and the like can be provided close to the portion where the hydraulic oil supply passage and the hydraulic oil return passage are switched. For this reason, even when using a plurality of switching valves connected in series, the pilot passage is connected to the drain passage and opened.

  According to the second aspect of the present invention, since these members are arranged in parallel with the front end portion of the rotor and the one end portion of the pressure compensation type flow rate adjusting valve being aligned, the rotor is a pilot switching valve as compared with the prior art. Despite being formed longer than the body portion, the occupied volume of the entire switching valve can be made equal to that of the conventional switching valve.

  Since the rotary type switching valve for the hydraulic device according to the invention described in claim 3 is configured to perform switching of the hydraulic oil passage and switching of the pilot passage by one rotor, it is dedicated to the pressure release type brake. Without using a switching valve, it can be incorporated into a series circuit formed by connecting a plurality of switching valves in series. For this reason, by incorporating the rotary type switching valve according to the present invention into a series circuit that drives a plurality of hydraulic devices by a single hydraulic pump, the hydraulic device having a pressure release type brake can be operated in a state where the brake operates correctly. Can be used in circuit. Therefore, it is possible to provide a hydraulic apparatus equipped with a hydraulic device having a brake while reducing costs.

Hereinafter, an embodiment of a rotary switching valve for a hydraulic device according to the present invention will be described in detail with reference to FIGS.
1 is a left side view of a rotary type switching valve for a hydraulic device according to the present invention, FIG. 2 is a rear view as seen from the operation lever side, FIG. 3 is a plan view, FIG. 4 is a right side view, and FIG. It is also a front view. 6 is a longitudinal sectional view of a rotary type switching valve for a hydraulic device according to the present invention, FIG. 7 is a side view of the rotor, FIG. 8 is a sectional view of the rotor, and FIG. FIG. 2B is a cross-sectional view taken along the line BB in FIG. 7, and FIG. 1C is a cross-sectional view taken along the line CC in FIG. 9 is a sectional view taken along line IX-IX in FIG. 8, and FIG. 10 is a sectional view taken along line XX in FIG. 11 is a sectional view taken along line XI-XI in FIG. 6, FIG. 12 is a sectional view taken along line XII-XII in FIG. 6, and FIG. 13 is a sectional view taken along line XIII-XIII in FIG.

  14 is a left side view of the valve housing, FIG. 15 is a bottom view of the valve housing, FIG. 16 is a sectional view taken along line XVI-XVI in FIG. 14, FIG. 17 is a longitudinal sectional view of the valve housing, and FIG. FIG. 19 is a cross-sectional view taken along line XVIII, FIG. 19 is a cross-sectional view taken along line XIX-XIX in FIG. 14, and FIG. 20 is a hydraulic circuit diagram of a rotary type switching valve for a hydraulic device according to the present invention.

  In these drawings, the reference numeral 1 indicates a rotary switching valve for a hydraulic device according to this embodiment. The rotary type switching valve 1 rotates / stops the hydraulic motor as a hydraulic device indicated by reference numeral 2 in FIG. 20, switches the rotational direction, increases / decreases the rotational speed, and adjusts the rotational speed of the hydraulic motor 2. The pressure release brake 3 is switched to the non-braking state when the motor rotates and also switched to the braking state when the motor is stopped.

  As shown in FIGS. 1 to 6, the rotary switching valve 1 includes a rotor 5 and a pressure-compensated flow rate adjusting valve 6 provided in parallel in a valve housing 4. As shown in FIGS. 7 to 10, the rotor 5 is formed with four switching valve body portions 7 to 10 and is rotatably fitted in the valve hole 11 of the valve housing 4. Further, one end (operating side end) of the rotor 5 protrudes out of the valve housing 4 through the cover 12 that closes the operating side opening (the right side opening in FIG. 6) of the valve hole 11. An operation lever 13 is attached. The rotor 5 and the operating lever 13 are in a normal rotation position where the operating lever 13 is inclined to the right side in the drawing from the neutral position shown by a solid line in FIG. 2, and the operating lever 13 is inclined to the left side in the drawing. It rotates between the reverse position. The opening on the counter-operation side of the valve hole 11 is closed by a cover 14 attached to the counter-operation side of the valve housing 4. As shown in FIG. 5, the cover 14 is provided with a click mechanism 14 a for giving a sense of moderation when the rotor 5 rotates from the neutral position or returns to the neutral position.

  As shown in FIG. 1, the valve housing 4 has a hydraulic oil supply port 15 (hereinafter simply referred to as P port) and a hydraulic oil return port 16 (hereinafter simply referred to as T port) formed on one side. As shown in FIG. 4, first and second hydraulic motor connection ports 17 and 18 (hereinafter, these ports are simply referred to as A port and B port) and a drain pipe (not shown) are connected to the other side. A drain port 19 (hereinafter simply referred to as a DR port) is formed. Further, on the upper surface of the valve housing 4, as shown in FIG. 3, a pilot port 21 (hereinafter referred to simply as P1 port) connected to the release pilot passage 20 of the pressure release brake 3 is provided. A hydraulic gauge mounting port 22 is formed. In FIG. 3, the P1 port 21 and the hydraulic system attachment port 22 are depicted in a state where the plugs 21a and 22a are screwed.

As shown in FIG. 6, the P port 15 is positioned at the central portion of the valve housing 4 in the axial direction (left-right direction in FIG. 6), and as shown in FIG. 11 is connected to the valve hole 11 by passages 15a and 15b extending in the vertical direction and the right and left directions. A hydraulic oil supply pipe 24 to which hydraulic oil is supplied from the hydraulic oil supply pump 23 (see FIG. 20) is connected to the P port 15.
As shown in FIG. 16, the T port 16 is positioned on the operation side of the valve housing 4 and is connected to the valve hole 11 by a passage 16a extending in the valve housing 4 to the side (upper side in the figure). Yes. The T port 16 is connected to a hydraulic oil supply passage of a hydraulic oil tank or other rotary type switching valve (not shown).

The A port 17 and the B port 18 are positioned on both sides of the P port 15 in the axial direction of the rotor 5 as shown in FIG. 6, and the other side of the valve housing 4 (see FIG. 16). Are connected to the valve hole 11 by passages 17a and 18a extending downward). A forward rotation supply passage 25 (see FIG. 20) of the hydraulic motor 2 is connected to the A port 17, and a reverse rotation supply passage 26 of the hydraulic motor 2 is connected to the B port 18.
As shown in FIG. 16, the DR port 19 is positioned at the front end portion of the valve housing 4 and is connected to the valve hole 11 by a passage 27 extending in the valve housing 4 to the other side (downward in the figure). ing. The DR port 19 is connected to a drain pipe (not shown). The DR port 19 constitutes a drain passage connection port in the present invention. The DR port 19 is closed by screwing a plug (not shown) when the rotary switching valve 1 is not provided in the series circuit.

  As shown in FIG. 3, the P1 port 21 is positioned on one side of the valve housing 4 on the opposite side of the valve housing 4, and a passage 28 (see FIG. 12) that extends vertically in one side of the valve housing 4. The valve hole 11 is connected by a passage 29 (see FIG. 16) connected to the lower end of the passage 28 and extending in the valve housing 4 to the operation side, and two passages 30 and 31 extending from the passage 29 to the other side. It is connected to the. The hydraulic fluid passage that communicates the P1 port 21 and the valve hole 11 in this manner is hereinafter referred to as a P1 port pressure guiding passage 32. As described above, the pilot passage 20 for releasing the brake 3 (see FIG. 20) is connected to the P1 port 21. The P1 port pressure guiding passage 32 and the opening pilot passage 20 constitute a pilot passage in the present invention.

The operation side end and the non-operation side end of the valve hole 11 are connected to two hydraulic oil return passages 33 and 34 extending in the axial direction at the lower end of the valve housing 4 as shown in FIGS. 35 and 36 are connected.
As shown in FIG. 6, the pressure compensating flow rate adjusting valve 6 is provided at the upper end of the valve housing 4. The flow rate adjusting valve 6 is a spool valve, and a spool 42 that is reciprocally fitted in the valve hole 41, and a compression coil spring 43 that urges the spool 42 to one end side (right side in FIG. 6). A relief valve 45 that opens when the pressure of the spring chamber 44 that houses the compression coil spring 43 exceeds a predetermined pressure, a cover 46 that closes the opening on one end side of the valve hole 41, and the like.

The spool 42 is configured to switch connection / disconnection between an annular recess 47 formed in the valve hole 41 and one tank pressure chamber 48 thereof. As shown in FIG. 11, the annular recess 47 is connected to the P port 15 by the passages 15a and 15b. The oil pressure in the annular recess 47 acts on one end surface of the spool 42 by a pressure guide hole 42 a formed in the spool 42. The tank pressure chamber 48 is formed between the small diameter portion of the spool 42 and the valve hole 41 and is connected to the lower valve hole 11 by a passage 49. The passage 49 is connected to the T port 16 via a return oil chamber 51 formed between the small diameter portion 5a of the rotor 5 and the valve hole 11 and the passage 16a.
As shown in FIG. 12, the spring chamber 44 of the pressure compensation flow rate adjusting valve 6 is connected to the passage 28 (P1 port pressure guiding passage 32) extending downward from the P1 port 21 via a throttle 52. ing.

As shown in FIG. 6, the relief valve 45 is configured to urge the valve body 54 provided in the valve hole 53 so as to reciprocate in the closing direction by the elastic force of the compression coil spring 55. . The relief valve 45 constitutes a pressure adjusting means in the present invention. An oil chamber 56 located downstream of the valve body 54 in the relief valve 45 is provided in the lower valve hole 11 by an annular recess 57 formed in the valve hole 41 and a passage 58 extending downward from the annular recess 57. And connected to the hydraulic oil return passages 33 and 34 via the return oil chamber 59 formed between the valve hole 11 and the small diameter portion 5 b of the rotor 5 and the passage 36. Yes.
The elastic force of the compression coil spring 55 of the relief valve 45 is obtained by reciprocating the load receiving member 60 attached to the front end of the compression coil spring 55 on the opposite side of the valve body 54 with the adjusting bolt 61. Adjusted. The adjusting bolt 61 is fixed to the relief valve cover 62 by a lock nut 63.

  As shown in FIG. 7, the rotor 5 includes an A port switching valve body portion 7 slidably fitted in the valve hole 11, a P port switching valve body portion 8, and a B port switching valve body portion. 9 and a P1 port switching valve body 10 are formed. Of these switching valve bodies, the A port switching valve body 7 located on the most operating side (the right side in FIG. 7) is connected to the passage 17a connected to the A port 17, as shown in FIG. A U-shaped supply passage groove 64 and a return passage groove 65 are formed on the outer peripheral portion at equal intervals in four locations in the circumferential direction. The supply passage groove 64 opens into a supply oil chamber 66 formed between the small diameter portion 5 c of the rotor 5 and the valve hole 11 on the side opposite to the A port switching valve body portion 7. The return passage groove 65 opens into the return oil chamber 51 formed on the operation side of the A-port switching valve body 7.

  As shown in FIG. 6, the A port switching valve body 7 according to this embodiment closes the A port 17 in a state where the rotor 5 is in the neutral position, and the operating lever 13 is moved to the right side in FIG. The A port 17 is connected to the supply oil chamber 66 through the supply passage groove 64 and the rotor 5 is positioned at the reverse rotation position. 17 is configured to be connected to the return oil chamber 51 through the return passage groove 65. Further, as shown in FIG. 8A, the A port switching valve body portion 7 is provided with a pressure guide hole 7 a penetrating in the radial direction of the rotor 5. As shown in FIG. 16, the pressure introducing hole 7a is for guiding the hydraulic pressure from the passage 17a to the balance chamber forming concave portion 17b facing the passage 17a of the A port 17 and the valve hole 11.

  As shown in FIGS. 6 and 11, the P port switching valve body 8 is formed at a position facing the valve hole side opening of the passage 15 a connected to the P port 15. Further, as shown in FIG. 11, the valve body 8 is formed so as to partition the inside of the valve hole 11 into an A port chamber 67 and a B port chamber 68. As shown in FIG. 6, the A port chamber 67 and the B port chamber 68 are provided between the P port switching valve body 8 and the A port switching valve body 7. 66 and a supply oil chamber 69 formed between the small-diameter portion 5 d of the rotor 5 and the valve hole 11 on the opposite side of the P-port switching valve body 8.

As shown in FIG. 6, the P-port switching valve body 8 according to this embodiment closes the P-port 15 in a state where the rotor 5 is positioned at the neutral position, and positions the rotor 5 at the normal rotation position. Thus, the P port 15 is connected to the A port chamber 67 and the supply oil chambers 66 and 69, and the rotor 5 is positioned at the reverse rotation position, whereby the P port 15 is connected to the B port chamber 68 and the supply oil chambers 66 and 69. It is configured to be connected to.
Further, as shown in FIG. 8B and FIG. 11, the P port switching valve body 8 is provided with a pressure guide hole 8 a penetrating in the radial direction of the rotor 5. As shown in FIG. 11, the pressure guide hole 8a is for guiding the hydraulic pressure from the passage 15b to the balance chamber forming recess 15c facing the passage 15b of the P port 15 and the valve hole 11.

  As shown in FIGS. 6 and 12, the B port switching valve body 9 is formed at a position facing the valve hole side opening of the passage 18a connected to the B port 18, and the A port switching Similarly to the valve body 7, a supply passage groove 71 and a return passage groove 72 are formed. The supply passage groove 71 of the B port switching valve body 9 opens into a supply oil chamber 69 formed between the B port switching valve body 9 and the P port switching valve body 8. ing. On the other hand, the return passage groove 72 opens into the return oil chamber 59 formed between the B port switching valve body 9 and a P1 port switching valve body 10 described later.

As shown in FIG. 6, the B-port switching valve body 9 according to this embodiment closes the B port 18 in a state where the rotor 5 is in the neutral position, and positions the rotor 5 in the normal rotation position. Thus, the B port 18 is connected to the return oil chamber 59 via the return passage groove 72, and the B port 18 is connected to the supply oil chamber via the supply passage groove 71 by positioning the rotor 5 in the reverse rotation position. 69 to be connected.
Further, as shown in FIGS. 8C and 12, the B port switching valve body portion 9 is provided with a pressure guide hole 9 a penetrating in the radial direction of the rotor 5. As shown in FIG. 16, the pressure introducing hole 9a is for guiding the hydraulic pressure from the passage 18a to the balance chamber forming recess 18b facing the passage 18a of the B port 18 and the valve hole 11.

  As shown in FIG. 6, the P1 port switching valve body 10 is formed at the tip of the rotor 5 and below the relief valve 45. Further, as shown in FIGS. 6 and 13, the P1 port switching valve body 10 is provided with a passage hole 73 penetrating in the radial direction. The passage hole 73 extends in the left-right direction with the rotor 5 and the operation lever 13 positioned at the neutral position, and as shown in FIG. 16, is one side (lower side in the figure) from the valve hole 11. And the passage 27 extending from the valve hole 11 to the other side.

  Further, as shown in FIGS. 6, 7, and 13, the P1 port switching valve body 10 includes a balance passage 10 a that extends in a direction orthogonal to the passage hole 73, and an axial direction of the rotor 5. An extending balance passage 10b is formed. The balance passage 10 a is formed so as to penetrate the P1 port switching valve body 10 in the radial direction and to be connected to the passage hole 73. As shown in FIG. 6, the balance passage 10 b penetrates the P1 port switching valve body 10 in the axial direction of the rotor 5, and the return oil chamber 59, the valve hole 11, and the small diameter portion 5 e of the rotor 5. And an oil chamber 81 formed therebetween.

  The passage 74 extending to one side from the valve hole 11 communicates the inside of the valve hole 11 with the P1 port pressure guiding passage 32. As shown in FIG. 16, the passage 27 extending to the other side from the valve hole 11 is connected with a passage 75 extending to the counter-operation side at a connection portion with the DR port 19. As shown in FIGS. 13 and 19, the passage 75 includes a passage 76 extending downward, a check valve 77 provided at a lower end portion of the passage 76, and the check valve 77 to the inside of the valve housing 4. It is connected to the hydraulic oil return passage 34 via an extending passage 78.

The check valve 77 is configured to flow the pressure oil only to the hydraulic oil return passage 33 side (lower side in FIG. 13).
As shown in FIGS. 13 and 16, the check valve 77 and the DR port 19 are provided at a portion surrounding the P1 port switching valve body 10 of the rotor 5 at the front end portion of the valve housing 4. It is provided so as to be located on the same plane as the valve body 10. Therefore, the DR port 19 and the check valve 77 are also positioned below the relief valve 45 of the flow rate adjusting valve 6. By adopting this configuration, as shown in FIG. 6, the rotary switching valve 1 includes a front end of a cover 14 attached to an end of the valve housing 4 on the counter-operation side, and a lock nut of the relief valve 45. The tip of 63 is located at substantially the same position in the front-rear direction.

  In the rotary type switching valve 1 configured as described above, the operating oil supplied to the P port 15 is changed to P by swinging the operating lever 13 to the right in FIG. 2 and switching the rotor 5 to the normal rotation position. A hydraulic motor is provided by a hydraulic oil supply passage including the passages 15a and 15b from the port 15, the A port chamber 67, the supply oil chamber 66, the supply passage groove 64 of the A port switching valve body 7, and the passage 17a. 2 is supplied to the second forward supply passage 25. At this time, hydraulic pressure is applied from the supply oil chambers 66 and 69 to the release pilot passage 20 of the brake 3 through the P1 port pressure guiding passage 32, and the brake 3 is brought into a non-braking state. Note that the brake 3 immediately enters the braking state when the hydraulic pressure supplied to the hydraulic motor 2 disappears even if the rotary switching valve 1 is in the normal rotation state or the reverse rotation state.

  On the other hand, at this time, the B port 18 has the passage 18a, the return passage groove 72 of the B port switching valve body 9, the return oil chamber 59, the passage 36, the return passages 33 and 34, and the passage 35. The hydraulic oil return passage 51 including the return oil chamber 51 and the passage 16 a is connected to the T port 16. For this reason, the hydraulic oil discharged from the hydraulic motor 2 passes through the hydraulic oil return passage and the T port 16 and is discharged out of the rotary switching valve 1 (the hydraulic oil supply passage of the second switching valve).

In the rotary switching valve 1 according to this embodiment, the operating oil supply passage and the hydraulic oil return passage are interchanged by swinging the operating lever 13 to the left in FIG. 2 and switching the rotor 5 to the reverse rotation position. . That is, at this time, the P port 15 is connected to the B port 18 via the passages 15a and 15b, the B port chamber 68, the supply oil chamber 69, the supply passage groove 71, and the passage 18a. 17 is connected to the T port 16 by a passage 17a, a return passage groove 65, a return oil chamber 51, and a passage 16a. Further, the hydraulic pressure is applied to the P1 port 21 during reverse rotation as well as during normal rotation.
The flow rate of the hydraulic oil supplied from the rotary type switching valve 1 to the hydraulic motor 2 at the time of forward rotation and reverse rotation is constant even if the discharge pressure of the hydraulic oil supply pump 23 fluctuates. It is controlled by the flow rate adjusting valve 6.

  In the rotary type switching valve 1, the P port 15 is closed by the P port switching valve body 8 by positioning the operating lever 13 in the neutral position as shown by the solid line in FIG. 17 and B port 18 are closed by A port switching valve body 7 and B port switching valve body 9. At this time, the spool 42 of the flow rate adjusting valve 6 is advanced by hydraulic pressure, and the passages 15 a and 15 b from the P port 15, the annular recess 47 and the tank pressure chamber 48 of the flow rate adjusting valve 6, the passage 49, and the return oil chamber 51. And the passage 16a and the T port 16 are supplied to the other switching valve.

  In this neutral position, the passage 27 and the passage 74 in the valve housing 4 are communicated with each other by the passage hole 73 of the P1 port switching valve body 10 of the rotor 5, and the P1 port pressure guiding passage 32 is communicated with the DR port 19. Is done. For this reason, the hydraulic pressure supplied to the brake 3 of the hydraulic motor 2 decreases, and the hydraulic motor 2 is braked by the brake 3. At this time, the pressure of the hydraulic oil return system of the rotary switching valve 1 is the same as the pressure of the hydraulic oil supply system. At this time, since the check valve 77 is closed, the return passage 33 is closed. , 34 through the passage 78, passage 76, passage 75, etc., the hydraulic oil does not leak into the DR port 19.

Therefore, the rotary switching valve 1 for the hydraulic device according to this embodiment does not use any other switching valve for switching the opening pilot passage 20 of the brake 3, and the opening pilot passage 20 is surely provided. Can be opened.
Further, in the rotary switching valve 1 for a hydraulic device according to this embodiment, a P1 port switching valve body portion 10 is formed at the tip portion of the rotor 5, and a DR port is provided at the front end portion of the valve housing 4 corresponding to this tip portion. 19 and the check valve 77 are provided so that these pilot passage switching passages and members are brought close to the switching valve body portions 7 to 9 for switching the hydraulic oil supply passage and the hydraulic oil return passage to make the passage compact. Can be provided.

Further, the rotary switching valve 1 for a hydraulic device according to this embodiment has these members arranged in parallel with the front end portion of the rotor 5 and the front end portion of the pressure compensation flow rate adjusting valve 6 aligned in the vertical direction. Therefore, although the rotor 5 is formed to be longer by the length of the P1 port switching valve body portion 10 as compared with the conventional case, the occupied volume of the entire switching valve can be made equal to the conventional size.
In addition, the hydraulic type rotary switching valve 1 according to this embodiment has a configuration in which the switching of the hydraulic oil passage and the switching of the pilot passage (the pilot passage 20 for releasing the brake 3) is performed by one rotor 5. Therefore, a plurality of switching valves can be incorporated in a so-called series circuit connected in series without using a switching valve dedicated to the pressure release brake 3.
For this reason, by connecting the rotary switching valve 1 according to this embodiment to a hydraulic circuit that drives a plurality of hydraulic motors 2, 2... By a single hydraulic pump 23, the hydraulic motor 2 having a pressure release brake 3. Can be provided in the hydraulic circuit with the brake 3 operating correctly.

In the above-described embodiment, the example in which the P1 port switching valve body 10 is provided at the tip of the rotor 5 has been described. However, the rotary switching valve for a hydraulic device according to the present invention is limited to such a limitation. The position where the P1 port switching valve body 10 is provided can be changed as appropriate. For example, the P1 port switching valve body portion 10 can be provided at the base end portion (operation lever side end portion) of the rotor 5 or the central portion in the axial direction.
In the above-described embodiment, the example in which the rotor 5 and the pressure-compensated flow rate adjusting valve 6 are provided in one valve housing 4 has been described. However, the shape of the housing can be changed as appropriate. For example, the rotor 5 and the flow rate adjusting valve 6 can be accommodated in a rotor housing and a flow rate adjusting valve housing that are formed separately, and the two housings can be connected to each other.

  Furthermore, the position of each port opened to the valve housing 4 is not limited to the position shown in the above embodiment, and can be changed as appropriate. For example, the DR port 19 opening on one side surface of the valve housing 4 can be formed on the upper surface of the valve housing 4. In the above-described embodiment, the vertical position of each member and the hydraulic oil passage (for example, the upper surface of the valve housing 4) is described in an installation form in which one end portion that accommodates the rotor 5 in the valve housing 4 is positioned below. However, the rotary switching valve according to the present invention can be installed on the base or the like so that the end (the upper end in the embodiment) of the valve housing 4 on the flow rate adjusting valve 6 side is positioned below. The end of the valve housing 4 on the rotor side or the end of the flow rate adjusting valve can be attached to a base or the like in a state where the axial direction of the rotor 5 is oriented in the vertical direction. Thus, even if the installation form is different from the present embodiment, each member and operation can be performed by considering the end of the valve housing on the rotor side (the end opposite to the flow regulating valve) as the bottom. The position of the oil passage coincides with the position described in the present embodiment.

For this reason, the statement that “the pilot switching valve body portion is positioned below the pressure adjusting means of the pressure compensation type flow regulating valve” described in claim 2 of the claim is that the rotor is the flow regulating valve. In the installation mode located above, including positioning the pilot switching valve body part above the pressure adjustment means of the pressure compensation type flow rate adjustment valve, and in the installation mode in which the axis of the rotor is oriented in the vertical direction And positioning the pilot switching valve body side to the side of the pressure adjusting means of the pressure compensation type flow regulating valve.
In the above-described embodiment, the hydraulic motor is used as the driven hydraulic device. However, the hydraulic motor is not limited to the hydraulic motor, but can be used for other hydraulic devices such as a hydraulic cylinder.

It is a left view of the rotary type switching valve for hydraulic apparatuses which concerns on this invention. It is the rear view seen from the operation lever side of the rotary type switching valve for hydraulic devices concerning the present invention. 1 is a plan view of a rotary switching valve for a hydraulic device according to the present invention. It is a right view of the rotary type switching valve for hydraulic apparatuses which concerns on this invention. 1 is a front view of a rotary switching valve for a hydraulic device according to the present invention. It is a longitudinal cross-sectional view of the rotary type switching valve for hydraulic apparatuses which concerns on this invention. It is a side view of a rotor. It is sectional drawing of a rotor. It is the IX-IX sectional view taken on the line in FIG. It is the XX sectional view taken on the line in FIG. It is the XI-XI sectional view taken on the line in FIG. It is the XII-XII sectional view taken on the line in FIG. 13 is a cross-sectional view taken along line XIII-XIII in FIG. It is a left view of a valve housing. It is a bottom view of a valve housing. It is the XVI-XVI sectional view taken on the line in FIG. It is a longitudinal cross-sectional view of a valve housing. It is the XVIII-XVIII sectional view taken on the line in FIG. It is the XIX-XIX sectional view taken on the line in FIG. 1 is a hydraulic circuit diagram of a rotary switching valve for a hydraulic device according to the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Rotary type switching valve for hydraulic devices, 2 ... Hydraulic motor, 4 ... Valve housing, 5 ... Rotor, 6 ... Pressure compensation type flow regulating valve, 7 ... Valve body part for A port switching, 8 ... Valve for P port switching Body part: 9 ... B port switching valve body part, 10 ... P1 port switching valve body part, 11 ... valve hole, 15 ... hydraulic oil supply port (P port), 16 ... hydraulic oil return port (T port), DESCRIPTION OF SYMBOLS 17 ... 1st hydraulic motor connection port (A port), 18 ... 2nd hydraulic motor connection port (B port), 20 ... Opening pilot passage, 32 ... P1 port pressure guide passage, 45 ... Relief valve 73 passage holes.

Claims (3)

  A passage switching rotor and a pressure-compensated flow rate adjustment valve are provided. By rotating the rotor, the hydraulic oil supply passage and the hydraulic oil return passage are switched, and the hydraulic oil supply passage is connected to the pilot of the driven device. A hydraulic type rotary switching valve for connecting the hydraulic oil return passage to the pilot passage by connecting the passage to a neutral state, and the same part of the rotor as the switching valve body portion. A pilot switching valve body portion having a diameter is provided, a passage hole penetrating in the radial direction is provided in the pilot switching valve body portion, and one end portion of the passage hole is connected to the pilot passage in the neutral state, and the other end Is connected to the hydraulic oil return passage through a drain passage connection port and a check valve that is located on the hydraulic oil return passage side from the drain passage connection port and flows the hydraulic oil only to the hydraulic oil return passage side. Rotary type switching valve hydraulic apparatus, wherein a check valve and these drain passage connection hole formed in the valve housing.   2. The rotary type switching valve for a hydraulic device according to claim 1, wherein the rotor and the pressure compensation type flow regulating valve are provided in the valve housing in parallel with each other, and the pilot switching valve body portion of the rotor is provided on the pressure compensating type flow regulating valve. A rotary type switching valve for a hydraulic device positioned below the pressure adjusting means. 3. The rotary switching valve for a hydraulic device according to claim 1 or 2, wherein the pilot passage is a pressurizing passage for the pressure release brake and the hydraulic oil return passage is connected to a hydraulic oil supply passage of another hydraulic device. Rotary type switching valve for hydraulic equipment.

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