JP2010112448A - Shift valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve responsiveness of hydraulic switching by improving leakage of operating oil between hydraulic ports. <P>SOLUTION: A shift valve 1 is provided with: a valve body 10 mounted into a valve hole 3; a plunger 30 installed in the valve body 10 so as to be reciprocatingly movable; a coil 11 for electromagnetically driving the plunger 30; first/second valve bodies 33, 34 moved by the plunger 30; first/second input ports 20, 21 respectively being a hydraulic port defined between the valve hole 3 and the valve body 10 and supplied with source pressure; first/second output ports 22, 23; and first/second drain ports 24, 25. Communication or non-communication between the first input port 20 and the first drain port 24 with respect to the first output port 22 is switched by the movement of the plunger 30 and the first valve body 33. Communication or non-communication between the second input port 21 and the second drain port 25 with respect to the second output port 23 is switched by the movement of the plunger 30 and the second valve body 34. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a shift valve that is mounted on a hydraulic control valve device or the like provided in an automatic transmission and is suitable for switching a hydraulic path.

Conventionally, as a shift valve which is an oil passage switching mechanism mounted on a hydraulic control valve device, for example, there is a spool valve as shown in Patent Document 1. This spool valve has a spool inserted into a valve hole of the valve body, and a plurality of hydraulic ports are defined in a gap between the spool and the valve hole. With the controlled signal pressure, the spool slides in the valve hole in the axial direction to switch the communication state of the plurality of hydraulic ports. Thereby, the distribution route of the supplied hydraulic pressure (original pressure) can be switched.
JP 2002-206651 A

  By the way, in the spool valve configured as described above, a predetermined clearance is required in the gap between the inner periphery of the valve hole and the outer periphery of the spool in order to ensure the axial slidability of the spool inside the valve hole. It is. However, since the plurality of hydraulic ports formed between the valve hole and the spool are partitioned by the sliding contact surface between the inner periphery of the valve hole and the outer periphery of the spool, the clearance is provided on the sliding contact surface. Therefore, a small amount of hydraulic fluid leaks from the high pressure side hydraulic port to the adjacent low pressure side hydraulic port. As described above, there is a problem that the hydraulic oil pressure is lowered due to the leakage of the hydraulic oil in the spool valve. This decrease in hydraulic pressure of the hydraulic oil is particularly noticeable at high temperatures when the viscosity of the hydraulic oil decreases.

  Therefore, in a hydraulic control valve device with a large number of installed spool valves, the amount of hydraulic oil leakage increases in proportion to the number of spool valves. Therefore, in order to secure the hydraulic pressure necessary for controlling each part, A large oil pump that can cope with the decrease is required. As a result, the size of the system such as the hydraulic control valve device may be increased, the structure may be complicated, or the operation efficiency may be reduced due to an increase in pump friction.

  Further, the conventional spool valve indirectly switches the oil path by inducing a signal pressure controlled by a solenoid to move the spool. Therefore, the operation responsiveness to the oil path switching control is not necessarily the best. In addition, in the conventional structure in which the spool is moved by inducing the signal pressure, there is a possibility that a hydraulic failure in the signal pressure path may occur. If this measure can be appropriately taken, there is room for improving the reliability of the system including the shift valve. There is.

  The present invention has been made in view of the above points, and its object is to leak hydraulic oil between hydraulic ports without causing a complicated structure or an increase in the number of parts as compared with a conventional spool valve. It is an object of the present invention to provide a shift valve that can effectively improve the hydraulic pressure and improve the response of hydraulic pressure switching.

  In order to solve the above-mentioned problems, a shift valve according to the present invention can be reciprocated in a valve body (10) inserted into a valve hole (3) of a valve housing (2) and mounted, and in the valve body (10). A plunger (30) that opens and closes a hydraulic oil flow path (15) provided in the valve body (10), a coil (11) that drives the plunger (30), and a movement direction of the plunger (30). A first valve body (33) and a second valve body (34) disposed on both outer sides and driven by the plunger (30) to open and close the flow path (15), and a first valve body provided in the flow path (15). 1. First valve body seating portion (16a) and second valve body seating portion (17a) on which the second valve body (33, 34) is respectively seated, and both ends of the plunger (30) in the moving direction are seated. 1 Plunger seat (18a) And a second plunger seat (18b), a hydraulic port defined between the valve hole (3) and the valve body (10) and connected to the flow path (15), and regulated to a predetermined pressure The first input port (20) and the second input port (21) to which the hydraulic oil is supplied, the first output port (22) capable of communicating with the first input port (20), and the first output port ( 22) a first drain port (24) capable of communicating with the second input port (21), a second output port (23) capable of communicating with the second input port (21), and a second drain port capable of communicating with the second output port (23). (25), and when the plunger (30) is driven and the first valve body (33) is moved accordingly, the first input port (20) and the first drain port (24) with respect to the first output port (22) are provided. Communication / non-communication with the plunger (3) ) And the movement of the second valve body (34) associated therewith, the communication between the second input port (21) and the second drain port (25) with respect to the second output port (23) is switched. It is characterized by. In addition, the code | symbol in parenthesis here has shown the code | symbol of the corresponding component of embodiment mentioned later as an example of this invention.

  According to the shift valve of the present invention, the flow of hydraulic oil provided in the valve main body by the plunger driven by the electromagnetic force of the coil installed in the valve main body and the first and second valve bodies moved by the plunger. By opening and closing the passage, it is configured to switch between communication and non-communication between a plurality of hydraulic ports defined between the valve hole and the valve body. Therefore, unlike the conventional spool valve, it is not configured to be partitioned by a sliding contact surface of a member (spool) that moves between adjacent hydraulic ports, so that there is no possibility that hydraulic fluid leaks between the hydraulic ports. Therefore, the hydraulic pressure drop due to hydraulic oil leakage in the shift valve does not need to occur, so the hydraulic oil pump can be downsized and the pump friction associated therewith can be reduced, and the hydraulic control valve device equipped with this shift valve The system efficiency can be improved, the configuration can be simplified, the weight can be reduced, and the cost can be reduced.

  Further, according to the shift valve of the present invention, since there is no portion corresponding to the sliding contact surface between the inner periphery of the valve hole and the outer periphery of the spool in the conventional spool valve structure, a high-accuracy clearance is provided in the gap between the component parts. There is no need to form. Therefore, it becomes possible to facilitate the machining process of the component parts such as the valve housing and the valve body, and to reduce the manufacturing cost of the parts.

  The shift valve according to the present invention has a coil and a plunger driven by the electromagnetic force of the coil built in the valve body, and the oil path is directly switched by the plunger driven by an electric signal. It is configured as follows. Thereby, compared with the valve | bulb which guides the signal pressure controlled with the conventional solenoid and moves a spool, the operation | movement responsiveness with respect to the switching control of an oil path can be improved. This point is particularly noticeable at low temperatures when the viscosity of the hydraulic oil is high. In addition, since the oil path is switched directly by the plunger driven by the electrical signal, it is not necessary to consider the hydraulic failure of the signal pressure path like the conventional spool valve, so the reliability of the system equipped with this shift valve Will improve. Furthermore, since there is no sliding portion that may cause malfunctions such as locking due to so-called contamination (such as sludge), the operational stability and durability of the shift valve are improved, and the reliability of the system is improved.

  In the shift valve having the above-described configuration, the contact portion between the first and second valve bodies (33, 34) and the first and second valve body seats (16a, 17a), or both ends of the plunger (30) ( 30a, 30b) and at least one of the contact portions between the first and second plunger seats (18a, 18b) in the moving direction of the first, second valve body (33, 34) or plunger (30). It is good to form in the taper surface shape which inclines so that the diameter may change along. According to this, if the contact portions of the first and second valve bodies or plungers and the corresponding contact portions of the seating portions are tapered surfaces having the same inclination angle, they are seated by surface contact. Therefore, even if they are tapered surfaces with different inclination angles, they can be seated in line contact. Further, when the first and second valve bodies are formed in a spherical shape as described below, the spherical surfaces of the first and second valve bodies contact linearly with the tapered surfaces of the first and second valve body seating portions. By doing so, it is possible to sit in line contact. By these, the sealing (sealing) performance of the closed part of a flow path can be improved. Therefore, it is possible to effectively prevent the hydraulic fluid from leaking due to the switching of the hydraulic port in the shift valve, and to improve the hydraulic response.

  In the shift valve configured as described above, the first valve body (33) and the second valve body (34) may be formed in a spherical shape. According to this, since the opening and closing of the flow path can be performed smoothly while ensuring the sealing performance of the closed portion of the flow path by the first and second valve bodies, it is possible to improve the responsiveness of the hydraulic pressure switching. it can.

  In the shift valve configured as described above, when the coil (11) is in a non-energized state, the flow path (15) between the first input port (20) and the first output port (22), and the second input port ( 21) and any one of the flow paths (15) between the second output port (23) are opened and the other is closed, and when the coil (11) is energized, the flow path ( It is good to comprise so that said one flow path (15) may be closed and the other flow path (15) may be opened by switching opening and closing of 15). According to this, only one of the first input port and the first output port or the second input port and the second output port can be selectively communicated, and the other can be closed. Become.

  Alternatively, when the coil (11) is in a non-energized state, the flow path (15) between the first input port (20) and the first output port (22), and the second input port (21) and the second output port The flow path (15) between the first input port (20) and the first output port (22) is closed when both of the flow paths (15) between the first input port (20) and the first output port (22) are closed. The flow path (15) between the second input port (21) and the second output port (23) is alternately opened, or when the coil (11) is in a non-energized state, The flow path (15) between the first input port (20) and the first output port (22) and the flow path (15) between the second input port (21) and the second output port (23) are both opened. When the coil (11) is energized, the first input port (20) and the first output port (22) Flow passage (15), the flow path between the second input port (21) and the second output port (23) (15) and may be configured to open the replacement. According to these, only one shift valve communicates only between the first input port and the first output port or between the second input port and the second output port. Non-communication with the three modes in the state of communication, or the state of communication only between the first input port and the first output port or between the second input port and the second output port It is possible to select and switch between the three modes in the state. Therefore, since it is possible to increase the number of hydraulic switching modes without increasing the number of shift valves installed, the hydraulic control can be performed without increasing the number of parts of the system equipped with this shift valve and complicating the structure. It becomes possible to improve the property.

  According to the shift valve of the present invention, it is possible to effectively improve the leakage of hydraulic oil between the hydraulic ports without increasing the number of parts or complicating the structure as compared with the conventional spool valve structure, and In addition, it is possible to improve the response of oil pressure switching.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
[First Embodiment]
FIG. 1 is a schematic cross-sectional side view showing a configuration of a shift valve 1 according to a first embodiment of the present invention. The shift valve 1 is capable of reciprocating into the valve body 10, a valve housing 2 including a valve body of a hydraulic control valve device provided in the automatic transmission, a valve body 10 inserted into the valve hole 3 of the valve housing 2, and And a flow path opening / closing member 40 composed of the plunger 30 and the first and second rods 31 and 32, and the first and second valve bodies 33 and 34, and the plunger 30 in the valve body 10. The built-in coil 11 is provided.

  The valve body 10 has an outer shape that is substantially cylindrical, and has a plurality of step portions having different diameters so that the diameter gradually increases from the left end in the axial direction toward the right end on the outer periphery. On the other hand, the valve hole 3 formed in the valve housing 2 has a substantially cylindrical shape having a stepped inner periphery along the outer shape of the valve main body 10. There are a plurality of locations that are slightly larger in diameter than the outer shape of the valve body 10 so that a gap is formed between the peripheral surface. A plurality of gaps formed between the outer peripheral surface of the valve body 10 and the inner peripheral surface of the valve hole 3 are hydraulic ports 20 to 25 through which hydraulic oil flows. In addition, a hydraulic oil flow path 15 extending linearly from one end to the vicinity of the other end along the axial direction is formed at the center (central axis portion) of the valve body 10. The flow path 15 communicates with the hydraulic ports 20-25. The hydraulic ports 20 to 25 are respectively a first input port 20, a first output port 22, a first drain port 24, a second drain port 25, a second output port 23, and a second input port from the left side in FIG. 21. The first input port 20 and the second input port 21 communicate with the same source pressure supply source 27 via an oil passage 26, and the hydraulic oil adjusted to a predetermined pressure (source pressure) from the source pressure supply source 27. Is to be supplied. The other hydraulic ports 22 to 25 also communicate with the outside through oil passages formed in the valve housing 2.

  O-rings (seal members) 14 are interposed in the gaps between the plurality of step portions formed on the outer periphery of the valve body 10 and the inner periphery of the valve hole 3. A gap between the inner periphery of the valve hole 3 and the outer periphery of the valve body 10 is sealed (sealed) by the O-ring 14. That is, the O-rings 14 attached to each step portion are provided between the first input port 20 and the first output port 22, between the first output port 22 and the first drain port 24, and between the second drain port 25 and the second output port 22. Seals are provided between the output ports 23, between the second output port 23 and the second input port 21, and between the second input port 21 and the open end 3 a of the valve hole 3. The valve body 10 inserted into the valve hole 3 is locked so as not to come out of the valve hole 3 by a locking member 4 made of a circlip or a stopper pin attached to the opening end 3a of the valve hole 3. .

  On the other hand, a substantially cylindrical plunger 30 is installed in the center of the flow path 15 formed in the valve body 10. The plunger 30 is installed so as to be able to reciprocate in the left-right direction, which is the longitudinal direction of the flow path. The plunger housing chamber 18 that houses the plunger 30 in the flow path 15 is formed to have an inner diameter that allows the inner circumferential surface to be in sliding contact with the outer circumferential surface of the plunger 30, and the plunger 30 is guided along the inner circumference of the plunger housing chamber 18. And is configured to be reciprocally movable. On the other hand, the coil 11 is built in the outer peripheral side of the plunger 30 in the valve body 10. The coil 11 is connected to a wiring 12 that passes through the valve body 10 and is led out from the open end 3 a of the valve hole 3. A coupler (connector) 13 is attached to the end of the wiring 12. The coil 11 is energized from an external power source via the wiring 12.

  Both the left end surface 30a and the right end surface 30b of the plunger 30 have a tapered surface shape that is inclined in a substantially conical shape along the axial direction, and the left end surface 30a of the plunger 30 is formed on the inner surface of the left end of the plunger storage chamber 18. A left seat (first plunger seat) 18a is provided, and a right seat (second plunger seat) for seating the right end surface 30b of the plunger 30 on the inner surface of the right end of the plunger storage chamber 18 is provided. 18b is provided. The left and right seat portions 18a and 18b are formed as substantially conical tapered surfaces having the same inclination as the left and right end surfaces 30a and 30b, respectively. Accordingly, when the plunger 30 moves to the left in the plunger storage chamber 18, the left end surface 30a of the plunger 30 is seated on the left seating portion 18a in surface contact, and the flow path 15 at the location of the left seating portion 18a is closed. . When the plunger 30 moves to the right in the plunger storage chamber 18, the right end surface 30b of the plunger 30 is seated on the right seat portion 18b in surface contact, and the flow path 15 at the location of the right seat portion 18b is closed.

  Moreover, the 1st rod 31 and the 2nd rod 32 of a linear bar-shape are protruded and formed from the right-and-left end surfaces 30a and 30b of the plunger 30 toward the axial direction outer side, respectively. Spherical first valve body 33 and second valve body 34 having a diameter larger than the diameters of first and second rods 31 and 32 are installed at the tips of first and second rods 31 and 32. Yes. The first and second rods 31 and 32 and the first and second valve bodies 33 and 34 are all installed in the flow path 15. The first and second valve body storage chambers 16 and 17 storing the first and second valve bodies 33 and 34 in the flow path 15 have an inner diameter larger than the outer diameter of the first and second valve bodies 33 and 34. The first and second valve bodies 33 and 34 are formed in a cylindrical shape, and the inner end surfaces in the axial direction with which the first and second valve bodies 33 and 34 abut are tapered first tapered seats (first 1 valve body seating portion) 16a and second seating portion (second valve body seating portion) 17a. As a result, when the first and second valve bodies 33 and 34 move to the center side in the axial direction, they are seated on the first seating portion 16a and the second seating portion 17a, respectively, and the flow paths 15 at those locations are closed. It is like that.

  The second valve body storage chamber 17 is provided with a spring (coil spring) 35 that urges the second valve body 34 to the left side. Therefore, in a steady state where no voltage is applied to the coil 11, the plunger 30, the first and second rods 31 and 32, and the first and second valve bodies 33 and 34 are biased to the left by the spring 35. The flow path opening / closing member 40 is stationary at the left full position in the flow path 15. When the coil 11 is energized in this state, an electromagnetic force is applied from the coil 11 to the plunger 30, the plunger 30 is driven in the right direction from the left end of the plunger storage chamber 18, and the flow path opening / closing member 40 moves to the right. ing. Note that the right end of the second valve body storage chamber 17 is an opening, and the opening is sealed by a pedestal 35 a of a spring 35.

  Here, the length between the tips of the first rod 31 and the second rod 32 is such that the first valve body 33 is seated on the first seat portion 16a and the second valve body 34 is seated on the second seat portion 17a. The dimension is set slightly longer than the interval between the first and second valve bodies 33 and 34 in the state. Therefore, when one of the first valve body 33 and the second valve body 34 is seated on the first seating portion 16a or the second seating portion 17a and closes the flow path 15 of the portion, In this state, the flow path 15 is opened away from the first seating portion 16a or the second seating portion 17a.

  In the present embodiment, the plunger 30 and the plunger housing chamber 18 have a shape that is bilaterally symmetric with respect to the center in the axial direction, and the first rod 31, the second rod 32, the first valve body 33, and the like. The second seat 34, the first seating portion 16 a of the first valve body storage chamber 16, and the second seating portion 17 a of the second valve body storage chamber 17 have the same shape and are symmetrically arranged.

  The first valve body storage chamber 16 defines a part of the first input port 20, and the second valve body storage chamber 17 defines a part of the second input port 21. The first output port 22 communicates with a position between the first valve body storage chamber 16 and the plunger storage chamber 18 in the flow path 15, that is, a position corresponding to the first rod 31. 23 communicates with the position between the second valve body storage chamber 17 and the plunger storage chamber 18 in the flow path 15, that is, the position corresponding to the second rod 32. The first drain port 24 communicates with a position near the left end in the plunger storage chamber 18, and the second drain port 25 communicates with a position near the right end in the plunger storage chamber 18.

  The operation of the shift valve 1 having the above configuration will be described. 2 (a) and 2 (b) are diagrams for explaining the operation of the shift valve 1. FIG. 2 (a) is a diagram showing a state in which the coil 11 is not energized, and FIG. It is a figure which shows the state which carried out. In the shift valve 1, the plunger 30 is moved to the right against the biasing force of the spring 35 by applying an electromagnetic force to the plunger 30 by energizing the coil 11. First, a steady state in which the coil 11 is not energized (during non-energization) will be described. At this time, as shown in FIG. 2A, the load applied from the hydraulic oil of the first input port 20 to the first valve element 33, and the load applied from the hydraulic oil of the second input port 21 to the second valve element 34 On the other hand, since the urging force of the spring 35 is applied to the second valve body 34 from the right side, the plunger 30 receives a load on the left side. For this reason, the first valve body 33 is pushed leftward by the first rod 31 to be separated from the first seating portion 16a, and the flow path 15 between the first input port 20 and the first output port 22 is opened. . As a result, the original pressure supplied from the first input port 20 flows into the first output port 22. At this time, since the left end surface 30a of the plunger 30 is seated on the left seating portion 18a of the plunger storage chamber 18, the flow path 15 between the first output port 22 and the first drain port 24 is blocked. It has become.

  On the other hand, in the second input port 21, the second valve body 34 is seated on the second seat portion 17 a by the urging force of the spring 35, so that the flow path 15 between the second input port 21 and the second output port 23 is closed. Is done. As a result, the original pressure supplied from the second input port 21 is cut off. Instead, the flow path 15 between the 2nd output port 23 and the 2nd drain port 25 opens because the right end surface 30b of the plunger 30 spaces apart from the right seat part 18b. As described above, when the coil 11 is not energized, the original pressure is supplied to the first output port 22 via the first input port 20, and the operating hydraulic pressure remaining in the second output port 23 is supplied from the second drain port 25. Discharged.

  Next, a state where the coil 11 is energized (during energization) will be described. When a current is passed through the coil 11, the plunger 30 moves to the right side by the electromagnetic force of the coil 11, so that the positional relationship of each part is reversed from when no current is applied. That is, as shown in FIG. 2B, the plunger 30 moves to the right against the urging force of the spring 35 applied to the second valve body 34. For this reason, the first valve body 33 moves to the right side with the pressure of the hydraulic oil as the first rod 31 moves backward, and is seated on the first seating portion 16a, between the first input port 20 and the first output port 22. The flow path 15 is closed. As a result, the original pressure supplied from the first input port 20 is shut off. Instead, the flow path 15 between the first output port 22 and the first drain port 24 is opened when the left end surface 30 a of the plunger 30 is separated from the left seating portion 18 a of the plunger storage chamber 18.

  On the other hand, in the second input port 21, the second valve body 34 pushed out by the second rod 32 is separated from the second seating portion 17a, and the flow path 15 between the second input port 21 and the second output port 23 is formed. Open. As a result, the original pressure from the second input port 21 is supplied to the second output port 23. At this time, since the right end face 30b of the plunger 30 is seated on the right seating portion 18b, the flow path 15 between the second output port 23 and the second drain port 25 is closed. As described above, when the coil 11 is energized, the original pressure is supplied to the second output port 23 via the second input port 21, and the operating hydraulic pressure remaining in the first output port 22 is discharged from the first drain port 24. Is done.

  As described above, according to the shift valve 1 of the present embodiment, the plunger 30 that is operated by the electromagnetic force of the coil 11 built in the valve body 10 and the first and second valve bodies 34 that are driven by the plunger 30. By opening and closing the hydraulic oil flow path 15 formed in the valve main body 10, a plurality of parts defined between the valve hole 3 of the valve housing 2 and the valve main body 10 mounted in the valve hole 3 are formed. It is configured to switch communication / non-communication between the hydraulic ports 20 to 25. Therefore, since it is not the structure partitioned by the sliding contact surface of the member (spool) which moves between adjacent hydraulic ports like the conventional spool valve, there exists a possibility that the hydraulic fluid may leak between the hydraulic ports 20-25. There is no. Therefore, it is not necessary to reduce the hydraulic pressure due to the leakage of hydraulic oil in the shift valve 1, so that the hydraulic oil pump can be reduced in size and the pump friction associated therewith can be reduced. It is possible to improve the efficiency of a system such as a valve device, simplify the configuration, reduce the weight, and reduce the cost.

  Further, according to the shift valve 1 of the present embodiment, since there is no sliding contact surface between the inner periphery of the valve hole 3 and the outer periphery of the spool as in the conventional spool valve structure, a high-accuracy clearance is provided in the gap between the component parts. There is no need to form. That is, as the processing accuracy of the inner periphery of the valve hole 3 and the outer peripheral surface of the valve main body 10, it is only necessary to secure a surface roughness that can prevent the O-ring 14 from being broken, so that the conventional spool valve can slide smoothly. The high-precision diameter tolerance and surface roughness required for this are not required. Accordingly, it is possible to facilitate the processing process of parts such as the valve housing (valve body) 2 and the valve body 10 and to reduce the manufacturing cost of the parts.

  Further, the shift valve 1 of the present embodiment incorporates a coil 11 and a plunger 30 driven by the electromagnetic force of the coil 11 in the valve body 10 and directly by the plunger 30 driven by an electric signal. The oil passage is switched. Therefore, the operation responsiveness to the oil path switching control can be improved as compared with the valve structure in which the spool is moved by inducing the signal pressure controlled by the conventional solenoid. This point is particularly noticeable at low temperatures when the viscosity of the hydraulic oil is high. In addition, since the oil passage is directly switched by the plunger 30 driven by an electric signal, it is not necessary to consider the hydraulic failure of the signal pressure path as in the conventional spool valve, so that the hydraulic control with the shift valve 1 is installed. The reliability of systems such as valve devices is improved. Furthermore, since there are no sliding parts in the shift valve 1 that may cause malfunctions such as locking due to so-called contamination (such as sludge), the operational stability and durability of the shift valve 1 are improved, and the system Reliability is improved.

  In the shift valve 1 of the present embodiment, both the end faces 30a and 30b of the plunger 30 and the left and right seating portions 18a and 18b of the plunger storage chamber 18 on which they are seated are arranged along the movement direction of the plunger 30. It is formed as a substantially conical tapered surface that inclines so that the inner diameter changes. The first and second seats 16a and 17a on which the first and second valve bodies 33 and 34 are seated are also formed as substantially conical tapered surfaces that are inclined so that the inner diameter thereof changes along the moving direction. ing. As a result, the closed portions of the flow path 15 by the first and second valve bodies 33 and 34 and the plunger 30 are sealed (sealed) in a planar shape, so that the sealing performance of the closed portions of the flow path 15 is improved. . Therefore, it is possible to effectively prevent the hydraulic oil from leaking due to the switching operation of the hydraulic ports 20 to 25, and to improve the hydraulic response.

  Moreover, in the shift valve 1 of this embodiment, the 1st valve body 33 and the 2nd valve body 34 are formed in the spherical shape. Thereby, the flow path 15 can be opened and closed smoothly while the sealing performance of the closed portion of the flow path 15 by the first and second valve bodies 33 and 34 is ensured.

[Second Embodiment]
Next, a shift valve according to a second embodiment of the present invention will be described. In the description of the second embodiment and the corresponding drawings, the same or corresponding components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted below. Further, matters other than those described below and matters other than those illustrated are the same as those in the first embodiment. FIG. 3 is a schematic sectional side view showing the shift valve 1-2 according to the second embodiment.

  Compared with the shift valve 1 of the first embodiment, the shift valve 1-2 of the present embodiment omits the spring 35 that biases the second valve body 34 to the left side, and the first and second rods 31. 32, the length between the tips is shortened. That is, the length between the tips of the first and second rods 31 and 32 in the present embodiment is such that both the first valve body 33 and the second valve body 34 are respectively connected to the first seating portion 16a and the second seating portion 17a. The length is slightly shorter than the distance between the first and second valve bodies 33 and 34 in the seated state. Further, the plunger 30 is set so as to be positioned at the center of the plunger housing chamber 18 when not energized. In this state, the first rod 31 is separated from the first valve body 33, and the second rod 32 is the first rod 32. The two valve bodies 34 are separated. Therefore, at the time of de-energization, the first and second valve bodies 33 and 34 are both seated on the first and second seating portions 16a and 17a and the hydraulic fluid passage 15 is blocked, and the first and second The supply of the original pressure to the output ports 22 and 23 is cut off. In the present embodiment, when the coil 11 is energized, the direction of the current flowing through the coil 11 can be switched, and the plunger 30 can be driven to the left side and the right side by switching the direction of the current.

  The operation of the shift valve 1-2 having the above configuration will be described. 4A to 4C are explanatory diagrams of the operation of the shift valve 1-2, FIG. 4A is a diagram showing a state where the coil 11 is not energized, and FIG. FIG. 4C is a diagram showing a state in which a current that causes the plunger 30 to move to the left is supplied to the coil 11. First, the case where the coil 11 is not energized will be described. At this time, as shown in FIG. 4A, the pressure of the hydraulic oil applied to the first valve body 33 from the first input port 20 causes the first valve body 33 to be pushed to the right side and be seated on the first seating portion 16a. The flow path 15 between the first input port 20 and the first output port 22 is blocked. Further, the pressure of the hydraulic oil applied to the second valve body 34 from the second input port 21 causes the second valve body 34 to be pushed to the left and to be seated on the second seating portion 17a. The flow path 15 between the two output ports 23 is blocked. On the other hand, since the plunger 30 is located in the center of the plunger storage chamber 18, the left seating portion 18a with the left end surface 30a of the plunger 30 and the right seating portion 18b are in a state of being separated from each other. It has become. As a result, the flow path 15 between the first output port 22 and the first drain port 24 is opened, and the flow path 15 between the second output port 23 and the second drain port 25 is opened. .

  Next, a case where a current that drives the plunger 30 to the right side is supplied when the coil 11 is energized will be described. In this case, as shown in FIG. 4B, the plunger 30 is driven to the right side by the electromagnetic force, and the second valve body 34 is pushed out by the second rod 32, so that the right side against the pressure of the hydraulic oil. Move to. Thereby, the 2nd valve body 34 is spaced apart from the 2nd seat part 17a, and the flow path 15 between the 2nd input port 21 and the 2nd output port 23 opens. At this time, since the right end surface 30b of the plunger 30 is seated on the right seating portion 18b of the plunger storage chamber 18, the flow path 15 between the second output port 23 and the second drain port 25 is closed. On the other hand, the first valve body 33 remains seated on the first seating portion 16 a with the pressure of the hydraulic oil supplied to the first input port 20. As described above, when the coil 11 is energized (when the plunger 30 is energized to the right), the original pressure from the second input port 21 is supplied to the second output port 23, while the original pressure from the first input port 20 is supplied. Is cut off, and the hydraulic pressure remaining in the first output port 22 is discharged from the first drain port 24. In addition, the 2nd drain port 25 is closed because the right end surface 30b of the plunger 30 is seated on the right seat part 18b.

  Next, a case where a current that drives the plunger 30 to the right side is supplied when the coil 11 is energized will be described. In this case, as shown in FIG. 4C, the plunger 30 is driven to the left side by the electromagnetic force, and the first valve body 33 is pushed out by the first rod 31, so that the left side resists the pressure of the hydraulic oil. Move to. Thereby, the 1st valve body 33 is spaced apart from the 1st seat part 16a, and the flow path 15 between the 1st input port 20 and the 1st output port 22 opens. At this time, since the left end surface 30a of the plunger 30 is seated on the left seating portion 18a of the plunger storage chamber 18, the flow path 15 between the first output port 22 and the first drain port 24 is closed. On the other hand, the second valve body 34 remains seated on the second seating portion 17 a by the pressure of the hydraulic oil supplied to the second input port 21. As described above, when the coil 11 is energized (when the plunger 30 is energized to the right), the original pressure from the first input port 20 is supplied to the first output port 22, while the original pressure from the second input port 21 is supplied. Is cut off, and the hydraulic pressure remaining in the second output port 23 is discharged from the second drain port 25. The first drain port 24 is closed because the left end surface 30a of the plunger 30 is seated on the left seating portion 18a.

  As described above, according to the present embodiment, supply of the original pressure only to the first output port 22 with the single shift valve 1-2 (communication of the first input port 20 and the first output port 22). Supply of the original pressure only to the second output port 23 (communication of the second input port 21 and the second output port 23) and interruption of the supply of the original pressure to both the first output port 22 and the second output port 23 It is possible to switch between three modes (blocking between the first input port 20 and the first output port 22 and blocking between the second input port 21 and the second output port 23). In the conventional spool valve structure, two sets of hydraulic paths including a supply side to which the original pressure is supplied and an output side to which the original pressure is output are provided, and switching between flow and blocking of these two hydraulic paths is individually performed. I couldn't. On the other hand, according to the shift valve 1-2 of the present embodiment, the number of hydraulic pressure switching modes can be increased without increasing the number of installed shift valves, so the shift valve 1-2 is mounted. It is possible to improve hydraulic controllability without increasing the number of system parts or complicating the structure.

[Third Embodiment]
Next, a shift valve 1-3 according to a third embodiment of the present invention will be described. FIG. 5 is a schematic sectional side view showing a shift valve 1-3 according to the third embodiment. Compared with the shift valve 1 of the first embodiment, the shift valve 1-3 of the present embodiment has a first valve body storage chamber 16 for storing the first valve body 33 and a second valve body 34 for storing the second valve body 34. The shape of the valve body storage chamber 17 is different. That is, the first and second valve body storage chambers 16 and 17 are seated on the outer end surfaces in addition to the seating portions (first and second valve body seating portions) 16a and 17a formed on the inner end surfaces in the axial direction. Portions (first and second valve body seating portions) 16b and 17b are formed. The outer seat portions 16b and 17b and the inner seat portions 16a and 17a have shapes and arrangements that are symmetrical with each other in the axial direction. In the first valve body storage chamber 16, the flow path 15 between the first input port 20 and the first output port 22 is closed by the first valve body 33 being seated on the outer seating portion 16b. The single valve body 33 is seated on the inner seating portion 16a, whereby the flow path 15 between the first output port 22 and the first drain port 24 is closed. In the second valve body storage chamber 17, the flow path 15 between the second input port 21 and the second output port 23 is closed because the second valve body 34 is seated on the outer seating portion 17b. The flow path 15 between the second output port 23 and the second drain port 25 is closed by the second valve body 34 being seated on the inner seating portion 17a.

  In the present embodiment, as in the second embodiment, the length between the tips of the first rod 31 and the second rod 32 is set so that both the first valve body 33 and the second valve body 34 are inside seating portions. It is set to be slightly shorter than the distance between the first and second valve bodies 33 and 34 in a state where they abut against the seat 16a and the seating portion 17a. Accordingly, both the first valve body 33 and the second valve body 34 can be seated on the inner seating portions 16a and 17a at the same time to block the flow path 15 of these portions. The plunger 30 is set so as to be positioned at the center of the plunger housing chamber 18 when not energized. In this state, the first rod 31 is separated from the first valve body 33 and the second rod 32 is the second valve. The state is separated from the body 34. In the present embodiment, the direction of the current that flows when the coil 11 is energized can be switched, and the plunger 30 can be driven to the left and right by switching the direction of the current. Therefore, at the time of de-energization, both the first valve body 33 and the second valve body 34 are seated on the inner seating portions 16 a and 17 a, and the flow path between the first input port 20 and the first output port 22. 15 and the flow path 15 between the second input port 21 and the second output port 23 are both opened, and the original pressure is supplied to both the first output port 22 and the second output port 23.

  The operation of the shift valve 1-3 having the above configuration will be described. 6A to 6C are explanatory diagrams of the operation of the shift valve 1-3, FIG. 6A is a diagram showing a state in which the coil 11 is not energized, and FIG. FIG. 6C is a diagram illustrating a state in which a current for causing the plunger 30 to move to the left is supplied to the coil 11. First, the case where the coil 11 is not energized will be described. At this time, as shown in FIG. 6A, the first valve body 33 is pushed to the right in the first valve body storage chamber 16 by the pressure of the hydraulic oil in the first input port 20, and the inner seating is performed. It is seated on the part 16a. As a result, the flow path 15 between the first input port 20 and the first output port 22 is opened, and the flow path 15 between the first output port 22 and the first drain port 24 is blocked. Further, the second valve body 34 is pushed to the left in the second valve body storage chamber 17 by the pressure of the hydraulic oil in the second input port 21 and is seated on the inner seating portion 17a. Thereby, the flow path 15 between the 2nd input port 21 and the 2nd output port 23 is opened, and the flow path 15 between the 2nd output port 23 and the 2nd drain port 25 is interrupted | blocked. As described above, when the coil 11 is not energized, the original pressure is supplied to the first output port 22 via the first input port 20 and also supplied to the second output port 23 via the second input port 21. The

  Next, a case where a current that drives the plunger 30 to the right side is supplied when the coil 11 is energized will be described. In this case, as shown in FIG. 6B, the plunger 30 is driven to the right side by the electromagnetic force, and the second valve body 34 is pushed out by the second rod 32, so that the right side against the pressure of the hydraulic oil. Move to. As a result, the second valve body 34 is separated from the second seating portion 17 a inside the second valve body storage chamber 17 and is seated on the outer seating portion 17 b. In this state, the right end surface 30b of the plunger 30 and the right seating portion 18b of the plunger storage chamber 18 are not in contact with each other, and the flow path 15 at the location of the right seating portion 18b is open. Accordingly, the flow path 15 between the second input port 21 and the second output port 23 is blocked, and the flow path 15 between the second output port 23 and the second drain port 25 is opened. On the other hand, the arrangement of the first valve body 33 does not change from the time of non-energization. As described above, when the coil 11 is energized (when the plunger 30 is biased to the right), the original pressure is supplied to the first output port 22 via the first input port 20, while the second input port 21 supplies the first pressure. The supply of the original pressure to the second output port 23 is shut off, and the operating hydraulic pressure remaining in the second output port 23 is discharged from the second drain port 25.

  Next, a description will be given of a case where a current is applied to drive the plunger 30 to the left side when the coil 11 is energized. In this case, as shown in FIG. 6C, the plunger 30 is driven to the left side by the electromagnetic force, and the first valve body 33 is pushed out by the first rod 31, so that the left side resists the pressure of the hydraulic oil. Move to. As a result, the first valve body 33 is separated from the first seating portion 16 a inside the first valve body storage chamber 16 and is seated on the outer seating portion 16 b. In this state, the left end surface 30a of the plunger 30 and the left seating portion 18a of the plunger storage chamber 18 are not in contact with each other, and the flow path 15 at the location of the left seating portion 18a is open. Accordingly, the flow path 15 between the first input port 20 and the first output port 22 is blocked, and the flow path 15 between the first output port 22 and the first drain port 24 is opened. On the other hand, the arrangement of the second valve body 34 does not change from the time of non-energization. As described above, when the coil 11 is energized (when the plunger 30 is biased to the left), the original pressure is supplied to the second output port 23 via the second input port 21, while the first input port 20 The supply of the original pressure to the first output port 22 is cut off, and the operating hydraulic pressure remaining in the first output port 22 is discharged from the first drain port 24.

  As described above, according to the configuration of the present embodiment, supply of the original pressure to both the first output port 22 and the second output port 23 (with the first input port 20 and Communication between the first output port 22 and communication between the second input port 21 and the second output port 23) and supply of the original pressure only to the first output port 22 (of the first input port 20 and the first output port 22) It is possible to switch between three modes: communication) and supply of the original pressure only to the second output port 23 (communication of the second input port 21 and the second output port 23). In the conventional spool valve structure, two sets of hydraulic paths including a supply side to which the original pressure is supplied and an output side to which the original pressure is output are provided, and the flow and interruption of these two sets of hydraulic paths are individually performed. It was not possible to switch. On the other hand, according to the shift valve 1-3 of the present embodiment, the number of hydraulic pressure switching modes can be increased without increasing the number of shift valves, and thus the shift valve 1-3 is mounted. It is possible to improve hydraulic controllability without increasing the number of system parts or complicating the structure.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible. It should be noted that any shape, structure, and material not directly described in the specification and drawings are within the scope of the technical idea of the present invention as long as the effects and advantages of the present invention are exhibited.

  For example, in the above embodiment, the first and second valve bodies 33 and 34 have a spherical shape. However, the first and second valve bodies 33 and 34 may have a shape other than the spherical shape. For example, when the first and second valve body seating portions 16a and 17a (16b and 17b) have a tapered surface shape as in the present embodiment, the seating surfaces of the first and second valve bodies 33 and 34 are along the same. By adopting a tapered surface shape, the first and second valve bodies 33 and 34 may be configured to be seated by surface contact with the tapered surface. In addition to the first and second valve bodies 33 and 34, the first and second valve body seats 16a and 17a (16b and 17b), both end faces 30a and 30b of the plunger 30, and the left and right seats (first The specific shape of the second plunger seating portions) 18a, 18b is not limited to the tapered surface shape, and the flow path 15 is accompanied by the movement of the plunger 30 and the first and second valve bodies 33, 34 in the axial direction. Other shapes may be used as long as the shape can be opened and closed. Further, the specific number, arrangement, shape, and the like of the plurality of hydraulic ports 20 to 25 included in the shift valve 1 (1-2, 1-3) are not limited to those shown in the above embodiment.

It is a schematic sectional side view which shows the shift valve concerning 1st Embodiment of this invention. It is operation | movement explanatory drawing of the shift valve concerning 1st Embodiment, and is a figure which shows the state which is not supplying with electricity to a coil. It is operation | movement explanatory drawing of the shift valve concerning 1st Embodiment, and is a figure which shows the state which supplied with electricity to the coil. It is a schematic sectional side view which shows the shift valve concerning 2nd Embodiment of this invention. It is operation | movement explanatory drawing of the shift valve concerning 2nd Embodiment, and is a figure which shows the state which is not supplying with electricity to a coil. It is operation | movement explanatory drawing of the shift valve concerning 2nd Embodiment, and is a figure which shows the state which sent the electric current which moves a plunger rightward to a coil. It is operation | movement explanatory drawing of the shift valve concerning 2nd Embodiment, and is a figure which shows the state which sent the electric current which moves a plunger to the left to a coil. It is a schematic sectional side view which shows the shift valve concerning 3rd Embodiment of this invention. It is operation | movement explanatory drawing of the shift valve concerning 3rd Embodiment, and is a figure which shows the state which is not supplying with electricity to a coil. It is operation | movement explanatory drawing of the shift valve concerning 3rd Embodiment, and is a figure which shows the state which sent the electric current which moves a plunger rightward to a coil. It is operation | movement explanatory drawing of the shift valve concerning 3rd Embodiment, and is a figure which shows the state which sent the electric current which moves a plunger to the left to a coil.

Explanation of symbols

1, 1-2, 1-3 Shift valve 2 Valve housing 3 Valve hole 10 Valve body 11 Coil 14 O-ring (seal member)
15 flow path 16 1st valve body storage chamber 16a 1st seat part (1st valve body seat part)
16b Seating part (first valve body seating part)
17 2nd valve body storage chamber 17a 2nd seat part (2nd valve body seat part)
17b Seating part (second valve body seating part)
18 Plunger storage chamber 18a Left seat (first plunger seat)
18b Right seat (second plunger seat)
20 first input port 21 second input port 22 first output port 23 second output port 24 first drain port 25 second drain port 27 source pressure supply source 30 plunger 30a left end surface 30b right end surface 31 first rod 32 second Rod 33 First valve body 34 Second valve body 35 Spring 40 Flow path opening / closing member

Claims (7)

A valve body to be inserted into the valve hole of the valve housing and mounted;
A plunger that is installed in the valve body so as to be reciprocally movable and opens and closes a flow path of hydraulic oil provided in the valve body; a coil that drives the plunger;
A first valve body and a second valve body which are respectively arranged on both outer sides in the movement direction of the plunger and are driven by the plunger to open and close the flow path;
A first valve body seating portion and a second valve body seating portion on which the first and second valve bodies provided in the flow path are respectively seated; a first plunger seating portion on which both ends of the plunger in the moving direction are seated; and A second plunger seat;
A hydraulic port defined between the valve hole and the valve body and connected to the flow path, the first input port and the second input port being supplied with hydraulic oil regulated to a predetermined pressure A first output port that can communicate with the first input port, a first drain port that can communicate with the first output port, a second output port that can communicate with the second input port, and the second A second drain port capable of communicating with the output port;
With
The driving of the plunger and the movement of the first valve body associated therewith switch the communication / non-communication between the first input port and the first drain port with respect to the first output port. A shift valve characterized in that communication between the second input port and the second drain port with respect to the second output port is switched by movement of the second valve body. At least one of the contact portions between the first and second valve bodies and the first and second valve body seating portions, or the contact portions between both ends of the plunger and the first and second plunger seating portions, 2. The shift valve according to claim 1, wherein the shift valve is formed in a tapered surface shape that is inclined so that a diameter thereof changes along a moving direction of the first and second valve bodies or the plunger. The shift valve according to claim 1 or 2, wherein the first valve body and the second valve body are formed in a spherical shape. When the coil is in a non-energized state, one of the flow path between the first input port and the first output port and the flow path between the second input port and the second output port are opened. The other is closed,
2. When the coil is energized, the opening and closing of the flow path is switched with respect to the non-energized state, whereby the one flow path is closed and the other flow path is opened. The shift valve according to any one of 1 to 3. When the coil is in a non-energized state, the flow path between the first input port and the first output port and the flow path between the second input port and the second output port are both closed,
When the coil is energized, the flow path between the first input port and the first output port and the flow path between the second input port and the second output port are alternately opened. 4. The shift valve according to claim 1, wherein the shift valve is configured. When the coil is in a non-energized state, the flow path between the first input port and the first output port and the flow path between the second input port and the second output port are both opened.
When the coil is energized, the flow path between the first input port and the first output port and the flow path between the second input port and the second output port are alternately opened. 4. The shift valve according to claim 1, wherein the shift valve is configured. A seal member is provided between the plurality of hydraulic ports in a gap between an inner periphery of the valve hole and an outer periphery of the valve body, and seals the gap between the plurality of hydraulic ports. The shift valve according to any one of claims 1 to 6.

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