JP2008008386A - Multiple selector valve - Google Patents

Abstract

An object of the present invention is to downsize a valve body 31.
SOLUTION: Supply ports 36 and 37 are formed on both sides of an introduction port 38 provided in the center, and pressure fluid flowing into the introduction port 38 from one of the supply ports 36 or 37 passes through a compensator valve 39. Thus, the bridge passage 40 is supplied. The supply ports 36 and 37 are eccentric to the opposite side to the position of the compensator valve 39 with respect to the axial center of the spool 32.
[Selection] Figure 1

Description

  The present invention relates to a multiple switching valve in which a plurality of valve bodies are connected in series and a compensator valve is incorporated in the valve body.

  Conventionally, this type of multiple-type switching valve described in Patent Document 1 has been known. FIG. 3 shows a conventional multiple switching valve. In the multiple switching valve shown in FIG. 3, a spool 2 is slidably incorporated in the valve body 1. The valve body 1 has a pair of actuator ports 3 and 4 and a tank passage 5 provided outside the actuator ports 3 and 4. Further, the valve body 1 is formed with a pair of supply ports 6, 7 communicating with the pump, and an introduction port 8 is formed between the supply ports 6, 7. The supply ports 6 and 7 configured as described above communicate with supply ports of other multiple switching valves (not shown) in a direction perpendicular to the paper surface.

  The introduction port 8 can communicate with the bridge passage 10 via the compensator valve 9. The compensator valve 9 is provided with a pressure chamber 11 on the side opposite to the introduction port 8, and this pressure A spring 12 is provided in the chamber 11. Therefore, the compensator valve 9 maintains the illustrated normal position by the action of the spring 12 as long as no pressure acts on the introduction port 8. Of the actuators connected to the multiple switching valve and other multiple switching valves (not shown), the pressure chamber 11 includes a shuttle valve (not shown), a check valve, etc. provided in the valve body. The maximum load pressure selected by the maximum load pressure selection means is derived.

  The compensator valve 9 configured as described above is configured so that the pressure action on the introduction port 8 side with respect to the compensator valve 9 overcomes the action force obtained by adding up the maximum load pressure of the pressure chamber 11 and the spring force. Open the communication port 13. Therefore, the pressure on the introduction port 8 side is controlled to be higher than the maximum load pressure by an amount corresponding to the spring force of the spring 12, and so-called load sensing control is performed.

  On the other hand, the spool 2 has a first annular groove 14 formed in the center thereof, and second annular grooves 15 and 16 formed on both sides of the first annular groove 14. Further, third annular grooves 17 and 18 are formed outside the second annular grooves 15 and 16. When the spool 2 is in the neutral position shown in the figure by the action of the centering spring s, the first annular groove 14 corresponds to the introduction port 8 and the communication between the supply ports 6 and 7 and the introduction port 8 is blocked. . In the figure, reference numerals 19 and 20 denote notches formed on the side surfaces of the second annular grooves 15 and 16, and reference numerals 21 and 22 denote notches formed on both side surfaces of the first annular groove 14.

  Now, when the spool 2 is moved from the neutral position to the right in the drawing, the supply port 6 and the introduction port 8 communicate with each other via the notch 19 of the second annular groove 15, and the notch 22 of the first annular groove 14. The supply port 7 and the introduction port 8 communicate with each other. Accordingly, the discharge fluid of the pump P is guided from the supply ports 6 and 7 to the introduction port 8 via the notches 19 and 22, and the compensator valve 9 is opened by the pressure guided to the introduction port 8.

When the compensator valve 9 is opened as described above, the pressure fluid is supplied to the bridge passage 10 via the communication port 13 of the compensator valve 9 and from the bridge passage 10 via the third annular groove 17. Then, it is supplied from the actuator port 3 to an actuator not shown. The return fluid from the actuator flows to the actuator port 4 and is guided from the actuator port 4 to the tank passage 5 via the third annular groove 18.
JP 2004-293614 A

  In the conventional multiple switching valve as described above, the thickness between the hole for incorporating the compensator valve 9 and the supply ports 6 and 7 must be increased to some extent from the standpoint of maintaining strength. Therefore, the width of the valve body 1 in the direction orthogonal to the spool 2 is inevitably increased. If the width of the valve body 1 is increased in this way, the entire apparatus is increased in size accordingly. In particular, in a multiple type switching valve, if the size of each switching valve is increased, the overall size of the multiple switching valve tends to be further increased. As the size of the multi-valve increases as described above, various problems occur such as an increase in installation space.

Moreover, although the valve body 1 incorporating the compensator valve may be assembled with a valve body not incorporating the compensator valve, the valve body not incorporating the compensator valve is usually relatively small. Then, when the valve main body 1 incorporating the compensator valve is assembled with a valve main body not incorporating the compensator valve, it is matched with the smaller valve main body.
In order to meet the above needs, for example, when trying to reduce the width of the valve body, that is, the width in the direction perpendicular to the spool, the conventional switching valve interferes with the supply port and the bridge passage. was there.
Furthermore, since the maximum load pressure selection means such as the shuttle valve and the check valve must be separately provided as described above, a space for providing this maximum load pressure selection means must be secured in the valve body. Therefore, there is also a problem that the valve main body is increased in size to ensure the space.

  An object of the present invention is to provide a multiple switching valve that can reduce the size of a valve body without interference of passages, ports and the like.

  According to the present invention, the valve main body is formed between the pair of supply ports connected to the pump, a pair of supply ports connected to the pump, and a movement position of the spool. An introduction port that communicates with any one of the supply ports; an actuator port that communicates with the actuator; a bridge passage that is supplied with fluid guided to the introduction port and communicates with the actuator port according to the movement position of the spool; A compensator valve incorporated in the flow path process between the introduction port and the bridge passage, and when the spool is in the normal position, the communication between the supply port and the introduction port is cut off, while the spool is When moved, one of the supply port and the introduction port is inserted through the first annular groove formed in the spool. DOO communicates the supplied pressure fluid from the supply port and assume the compensator valve, multiple-type switching valve was configured to guide the actuator port via the second annular groove formed in the bridge passage and the spool. The pair of supply ports is characterized in that it is eccentric to the opposite side of the position of the compensator valve with respect to the axis of the spool.

According to the first invention, the pair of supply ports are eccentric to the opposite side of the position of the compensator valve with respect to the axis of the spool, so the width of the valve body in the direction perpendicular to the spool is reduced. However, the supply port does not interfere with a bridge passage or the like located on the compensator valve side. In other words, since the supply port does not interfere with a bridge passage or the like located on the compensator valve side, the valve body can be downsized.
Furthermore, by making the supply port eccentric with respect to the spool as described above, a large opening area of the supply port can be secured on one side of the spool. Thus, since the opening area of a supply port can be taken large, when this supply port functions as a channel | path which leads to another multiple type | mold switching valve, the pressure loss can be suppressed to the minimum.

  In the embodiment shown in FIGS. 1 and 2, a spool 32 is slidably incorporated in the valve body 31. The valve body 31 is formed with a pair of actuator ports 33 and 34, and a tank passage 35 is provided outside the actuator ports 33 and 34. Further, the valve body 31 is formed with a pair of supply ports 36 and 37 communicating with the pump, and an introduction port 38 is formed between the supply ports 36 and 37. The supply ports 36 and 37 thus configured communicate with a pump (not shown) and communicate with the supply ports of other multiple-type switching valves in a direction perpendicular to the paper surface.

  The introduction port 38 can communicate with the bridge passage 40 via the compensator valve 39, but the supply ports 36 and 37 are on the opposite side of the spool 32 from the compensator valve 39. Eccentric.

  The compensator valve 39 is configured as follows. That is, the valve body 41 of the compensator valve 39 is formed in a cylindrical shape, and a partition wall 42 is formed in the cylindrical valve body 41, and the partition wall 42 is used as a boundary to open to the introduction port 38 side. It is divided into a first cylindrical portion 43 and a second cylindrical portion 45 that opens to the pressure chamber 44 side. The first cylindrical portion 43 is formed with a communication portion 46 composed of a port. When the valve body 41 is moved by the pressure action on the introduction port 38 side, the communication portion 46 opens into the bridge passage 40. I have to.

  As shown in FIG. 2, the second cylindrical portion 45 has a circular inner periphery, and a check poppet 47 is slidably incorporated in the circular second cylindrical portion 45. The poppet body 48 of the check poppet 47 has a polygonal columnar shape, and the poppet main body 48 having the polygonal columnar shape is incorporated in a second cylindrical portion 45 having a circular inner periphery, whereby the poppet body 48 and the second A gap 49 is formed between the inner periphery of the cylindrical portion 45. The gap 49 formed in this way becomes a passage leading to the pressure chamber 44. Note that the pressure chamber 44 communicates with the pressure chamber of another multiple switching valve.

The poppet body 48 is formed with conical poppet portions 50 and 51 at both ends thereof. One of the poppet portions 50 is configured to open and close the seat portion 52 formed on the partition wall 42. ing. When the seat portion 52 is opened, the bridge passage 40 communicates with the pressure chamber 44 via the gap 49, and when the seat portion 52 is closed, the communication between the bridge passage 40 and the pressure chamber 44 is interrupted. The
The reason why the poppet portions 50 and 51 are provided at both ends of the poppet main body 48 as described above is to eliminate the direction of assembling the check poppet 47. Reference numerals 53 and 53 in the figure denote load check valves for preventing the pressure on the actuator ports 33 and 34 from flowing backward.

In the valve body 31 as described above, the spool 32 is slidably incorporated. The spool 32 has both ends facing the pilot chambers 54 and 54 and is provided in the pilot chambers 54 and 54. The centering springs 55, 55 normally keep the spool 32 in the neutral position shown in the figure.
When the spool 32 is in the neutral position shown in the figure, the first annular groove 56 provided substantially at the center of the spool 32 corresponds to the introduction port 38 and the communication between the introduction port 38 and the supply ports 36 and 37 is blocked. I have to.

  Further, notches 57 and 58 are formed on both sides of the first annular groove 56, and the notches 57 and 58 are opened in a direction in which fluid flows out from the supply port 36 or 37 to the introduction port 38. . Thus, the notches 57 and 58 function as notches into which the fluid flows, so that the generation of the fluid force can be suppressed as much as possible compared to the notches formed on the fluid outflow side.

  Further, second annular grooves 59, 60 are formed on both sides of the spool 32. When the spool 32 moves to the right in the drawing, the bridge passage 40 and the actuator port 33 are passed through the second annular groove 59. And the actuator port 34 and the tank passage 35 communicate with each other through the other second annular groove 60. Further, when the spool 32 moves in the left direction of the drawing, the bridge passage 40 and the actuator port 34 communicate with each other via the other second annular groove 60, and the actuator port 33 and the tank passage via one second annular groove 59. 35 communicates.

  Now, when a pilot pressure is applied to one pilot chamber 54 and the spool 32 is moved to the right in the drawing, the supply port 37 communicates with the introduction port 38 via the notch 58 of the first annular groove 56. Accordingly, the pressure fluid flowing into the supply port 37 is guided to the introduction port 38 and the compensator valve 39 moves against the pressure action of the pressure chamber 44 by the action of the pressure in the introduction port 38. When the compensator valve 39 moves in this way, the communicating portion 46 opens with respect to the bridge passage 40, so that the pressure fluid guided to the introduction port 38 passes through the load check valve 53 and one second annular ring. It flows out from the actuator port 33 through the groove 59. Then, the return fluid of the actuator flowing in from the other actuator port 34 is discharged to the tank passage 35 through the other second annular groove 60.

  When the bridge passage 40 communicates with the actuator as described above, the load pressure of the actuator at that time acts on the poppet portion 50 of the check poppet 47. At this time, if the load pressure on the actuator port 33 side is higher than the pressure guided to the pressure chamber 44, the check poppet 47 rises to open the seat portion 52. When the seat portion 52 is thus opened, the load pressure on the actuator port 33 side is guided to the pressure chamber 44 and from the pressure chamber 44 to a regulator (not shown). This regulator controls the discharge pressure of a pump (not shown) so as to be higher than the set pressure by the load pressure of the pressure chamber 44.

  However, since the pressure chamber 44 communicates with the pressure chambers of other multiple switching valves, the pressure in the pressure chamber 44 is the highest load pressure among the actuators connected to the multiple switching valves. Will be guided. Therefore, the pressure led to the regulator is also led to the highest load pressure of each actuator, and the regulator is such that the discharge pressure of the pump is maintained at a pressure higher than the highest load pressure by a set pressure. Will be controlled. In other words, so-called load sensing control is performed by the maximum load pressure guided to the pressure chamber.

  In the embodiment described above, the supply ports 36 and 37 are eccentric to the side opposite to the compensator valve 39 with respect to the axis of the spool 32. For example, as shown in the drawing, the bridge passage 40 Can be divided into an upstream passage 40a and a downstream passage 40b with the load check valve 53 as a base point, and the downstream passage 40b can be brought close to the spool 32 together with the load check valve 53. In other words, even if the load check valve 53 and the downstream passage 40b are brought close to the spool 32, the load check valve 53 and the downstream passage 40b do not interfere with the supply ports 36 and 37.

  Therefore, the width of the valve body 31 in the direction orthogonal to the spool 32 can be reduced by the amount that the load check valve 53 and the downstream side passage 40b are brought closer to the spool 32. Further, since the compensator valve 39 incorporates the check poppet 47 as the maximum load pressure selection means, the size of the valve body 31 is smaller than that of the conventional one in which the maximum load pressure selection means is incorporated at another location. it can.

Further, the check poppet 47 incorporated in the compensator valve 39 of this embodiment has a poppet body 48 formed in a polygonal column shape, and a gap 49 serving as a passage is formed in combination with the inner periphery of the second cylindrical portion 45. For example, a special passage for communicating the bridge passage 40 and the pressure chamber 44 is not necessary. Since no special passage is required in this way, the valve body 31 can be reduced in size accordingly.
Further, by making the supply ports 36 and 37 eccentric with respect to the spool 32 as described above, a large opening area of the supply ports 36 and 37 on one side of the spool 32 can be secured. Since the opening area of the supply ports 36 and 37 can be increased in this way, when the supply ports 36 and 37 function as a passage in the direction perpendicular to the paper surface leading to the other multiple switching valve, the pressure loss is reduced. Can be minimized.

It is sectional drawing of this embodiment. It is sectional drawing of a compensator valve | bulb. It is sectional drawing of the conventional multiple changeover valve.

Explanation of symbols

31 Valve body 32 Spool 33, 34 Actuator port 36, 37 Supply port 38 Introduction port 39 Compensator valve 40 Bridge passage 41 Valve body 42 of compensator valve Partition wall 43 First cylindrical portion 44 Pressure chamber 45 Second cylindrical portion 46 Communication portion 47 Check poppet 48 Poppet body 49 Clearance 50, 51 Poppet portion 52 Sheet portion 56 First annular groove 59, 60 Second annular groove

Claims (1)

  The valve body is formed between the spool slidably incorporated in the valve body, a pair of supply ports connected to the pump, and the pair of supply ports. An introduction port communicating with the port; an actuator port communicating with the actuator; a fluid guided to the introduction port; a bridge passage communicating with the actuator port according to a moving position of the spool; an introduction port; Compensator valve incorporated in the flow path process with the bridge passage, and when the spool is in the normal position, the communication between the supply port and the introduction port is blocked, while the spool moves to either Any one of the supply ports communicates with the introduction port through a first annular groove formed in the spool. In the multiple switching valve configured to guide the pressure fluid supplied from the supply port to the actuator port via the second annular groove formed in the compensator valve, the bridge passage, and the spool, the pair of supply ports are connected to the spool. A multiple switching valve that is eccentric to the opposite side of the position of the compensator valve with respect to the shaft center.

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