JP2011236964A - Solenoid valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a solenoid valve with which resposiveness can be enhanced by decreasing flow force reacting in a reverse direction to the moving direction of a spool.SOLUTION: A spool 20, disposed movable in both directions along an axial direction inside of a cylindrical sleeve 10, has a first land 21 which opens and closes an input port 12 and a second land 22 which opens and closes a discharge port 14. An electromagnetic actuator 40 switches between connection and interception of the input port 12 and the discharge port 14 by moving the spool 20 to the other direction along axis, and controls the oil pressure outputted from the output port 13. A guide member 60 protruding to the outside of the diameter of an axis part 24 which connects the first land 21 and the second land 22 of the spool 20 guide an operation oil flowing from the input port 12 to the output port 13. In this manner, the dynamic pressure of the operation oil inputted from the input port 12 is suppressed from acting on an exterior wall 29 of the first land 21 side in the axial direction of the second land 22.

Description

  The present invention relates to a spool type solenoid valve.

  Conventionally, an electromagnetic valve that performs hydraulic control of an automatic transmission for a vehicle is known. This type of solenoid valve includes a spool that can reciprocate in the axial direction inside a cylindrical sleeve. The sleeve has an input port, an output port, and a discharge port in order from one side in the axial direction. The spool has a first land that opens and closes the input port, a second land that opens and closes the discharge port, and a shaft portion that connects the first land and the second land. When the electromagnetic actuator moves the spool in one axial direction, opens the input port by the first land, and closes the discharge port by the second land, hydraulic pressure is output from the output port.

By the way, when the electromagnetic actuator moves the spool in one axial direction, if the dynamic pressure of the hydraulic fluid flowing from the input port to the other axial direction acts on the outer wall on the first land side in the axial direction of the second land, A force opposite to the direction of movement is generated. This force is called flow force. When the movement of the spool is hindered by the flow force, it takes a long time until the opening of the input port reaches the target area, and there is a concern that the responsiveness of the solenoid valve is deteriorated.
In Patent Document 1, a concave portion that is recessed in the radial direction is formed in the shaft portion of the spool, and the dynamic pressure of the hydraulic oil acting on the spool is reduced by the concave portion.

JP 2008-202680 A

However, the fact that the hydraulic oil flows from the input port to the second land side and the dynamic pressure of the hydraulic oil acts on the outer wall of the second land in the axial direction on the first land side is excluded by the recess formed in the shaft portion. Have difficulty. For this reason, the flow force may not be sufficiently reduced.
The present invention has been made in view of the above problems, and an object of the present invention is to provide an electromagnetic valve capable of enhancing the responsiveness by reducing the flow force acting in the direction opposite to the moving direction of the spool. is there.

According to the first aspect of the present invention, the cylindrical sleeve has an input port for inputting fluid pressure, an output port for outputting fluid pressure, and a discharge port for discharging fluid. A spool provided inside the sleeve so as to be capable of reciprocating in the axial direction includes a first land that slides on the inner wall of the sleeve and opens and closes the input port, a second land that slides on the inner wall of the sleeve and opens and closes the discharge port, and A shaft portion that connects the first land and the second land is provided. The electromagnetic actuator switches the communication between the input port and the discharge port by moving the spool in the axial direction, and controls the fluid pressure output from the output port. The guide portion protruding outward from the diameter of the shaft portion of the spool guides the fluid flowing from the input port to the output port.
When the electromagnetic actuator moves on the spool, the input port is opened by the first land, and the discharge port is closed by the second land, fluid pressure is output from the output port. At this time, the fluid flowing in from the input port is guided to the output port by the guide portion protruding outward from the diameter of the shaft portion of the spool. For this reason, it is suppressed that the dynamic pressure of the fluid which flows in from an input port acts on the outer wall at the side of the 1st land of the 2nd land in the axial direction. As a result, the flow force acting in the direction opposite to the moving direction of the spool can be reduced. Therefore, the spool can be quickly moved to the target phase, and the response of the fluid pressure output from the output port to the energization of the electromagnetic actuator can be enhanced.

  According to the invention which concerns on Claim 2, the radial outer wall of a guide part is a taper shape which inclines in the radial inside from the 2nd land side toward the 1st land side. Thereby, the fluid flowing in from the input port is guided to the output port along the radial outer wall of the guide portion. For this reason, since the dynamic pressure of the fluid flowing in from the input port is suppressed from acting on the outer wall on the first land side in the axial direction of the second land, the flow force can be reduced.

  According to the third aspect of the present invention, the guide portion has the second land to such an extent that the fluid flowing in from the input port can be prevented from directly hitting the outer wall on the first land side in the axial direction of the second land. The outer diameter on the side is formed slightly smaller than the inner diameter of the sleeve. For this reason, it is suppressed that the dynamic pressure of the fluid flowing in from the input port acts on the outer wall on the first land side in the axial direction of the second land, and the flow force can be reliably reduced.

  According to the invention which concerns on Claim 4, the outer wall of the radial direction of a guide part is the curved surface shape dented in the radial direction inner side and the axial direction 2nd land side. Thereby, it becomes easy to guide the fluid flowing in from the input port to the output port. For this reason, it is suppressed that the dynamic pressure of the fluid flowing in from the input port acts on the outer wall on the first land side in the axial direction of the second land, and the flow force can be reliably reduced.

  According to the invention which concerns on Claim 5, the outer wall of the radial direction of a guide part is the curved surface shape which protrudes to a radial direction outer side and the axial direction 1st land side. This makes it difficult for the outer wall in the radial direction of the guide portion to receive the dynamic pressure of the fluid input from the input port. Therefore, the flow force can be reduced.

According to the invention which concerns on Claim 6, a cylindrical sleeve has an input port into which fluid pressure is input, and an output port which outputs fluid pressure. A spool provided inside the sleeve so as to be capable of reciprocating in the axial direction includes a first land that slides on the inner wall of the sleeve to open and close the input port, a second land that slides on the inner wall of the sleeve, and a first land and a second land. It has a shaft portion connecting the land. The electromagnetic actuator switches the communication state between the input port and the output port by moving the spool in the axial direction, and controls the fluid pressure output from the output port. The guide portion protruding outward from the diameter of the shaft portion of the spool guides the fluid flowing from the input port to the output port.
When the electromagnetic actuator moves on the spool and the input port is opened by the first land, fluid pressure is output from the output port. At this time, the fluid flowing in from the input port is guided to the output port by the guide portion protruding outward from the diameter of the shaft portion of the spool. For this reason, it is suppressed that the dynamic pressure of the fluid which flows in from an input port acts on the outer wall at the side of the 1st land of the 2nd land in the axial direction. Therefore, the flow force can be reduced and the responsiveness of the electromagnetic valve can be increased.

It is sectional drawing of the solenoid valve by 1st Embodiment of this invention. It is sectional drawing of the solenoid valve by 1st Embodiment of this invention. It is the elements on larger scale of III of FIG. It is the elements on larger scale of IV of FIG. It is the elements on larger scale of the solenoid valve by 2nd Embodiment of this invention. It is the elements on larger scale of the solenoid valve by 3rd Embodiment of this invention. It is the elements on larger scale of the solenoid valve by 4th Embodiment of this invention. It is the elements on larger scale of the solenoid valve by 5th Embodiment of this invention.

Hereinafter, a plurality of embodiments according to the present invention will be described with reference to the drawings.
(First embodiment)
A solenoid valve according to a first embodiment of the present invention is shown in FIGS. The electromagnetic valve 1 of this embodiment is used for an automatic transmission of a vehicle, and performs pressure control of hydraulic oil as a fluid.
First, the basic configuration of the electromagnetic valve 1 will be described.
As shown in FIG. 1, the electromagnetic valve 1 includes a sleeve 10, a spool 20, an electromagnetic actuator 40, a guide portion 60, and the like.
The sleeve 10 is formed in a cylindrical shape, and includes a feedback port 11, an input port 12, an output port 13, and a discharge port 14 in order from the axial coil spring 30 side. The input port 12 is connected to a hydraulic pump (not shown), and hydraulic pressure is input from the hydraulic pump. The output port 13 is connected to a load of an automatic transmission (not shown) and is connected to the feedback port 11 by a hydraulic pipe (not shown). The discharge port 14 is open to the atmosphere.

The spool 20 is provided inside the sleeve 10 so as to be capable of reciprocating in the axial direction. The spool 20 includes a first land 21, a second land 22, and a third land 23 that are formed so that the outer diameter is slightly smaller than the inner diameter of the sleeve 10. The spool 20 has an outer diameter smaller than that of the first land 21 and the second land 22, and includes a shaft portion 24 that connects the first land 21 and the second land 22, and the first land 21 and the third land 22. 23 has a connecting portion 25 for connecting to. A guide portion 60 is provided on the outer wall of the shaft portion 24 so as to protrude radially outward. The guide unit 60 will be described later.
A communication chamber 15 is formed between the first land 21 and the second land 22 to communicate the output port 13 or the discharge port 14 with the input port 12. Further, a feedback chamber 16 to which hydraulic pressure is supplied from the feedback port 11 is formed outside the diameter of the connecting portion 25.

  The first land 21 slides with the inner wall of the sleeve 10 to open and close the input port 12. The second land 22 slides with the inner wall of the sleeve 10 to open and close the discharge port 14. The first land 21 and the second land 22 have notches 27 and 28 that are recessed in the radial direction, respectively. The third land 23 has an outer diameter smaller than the outer diameters of the first land 21 and the second land 22. The sleeve 10 corresponds to the outer diameter of the third land 23, and the inner diameter of the feedback port 11 on the coil spring 30 side is smaller than the inner diameter of the feedback port 11 on the input port 12 side. For this reason, the third land 23 is in sliding contact with the inner wall of the sleeve 10 on the coil spring 30 side of the feedback port 11.

  One end of the coil spring 30 is locked to the recess 32 of the lid member 31 fixed to the sleeve 10, and the other end is locked to the recess 26 provided at the end of the spool 20 opposite to the electromagnetic actuator 40. Yes. The coil spring 30 biases the spool 20 toward the electromagnetic actuator 40 side.

The electromagnetic actuator 40 includes a yoke 41, a fixed core 42, a movable core 43, a coil 44, and the like.
The yoke 41 is formed in a cylindrical shape from a magnetic material. The yoke 41 is caulked at one end in the axial direction to a flange 17 provided on the outer diameter side of the sleeve 10 and is caulked at the cover 45 at the other end in the axial direction.
The fixed core 42 is made of a magnetic material. The fixed core 42 includes a cylindrical accommodating portion 46 that accommodates the movable core 43, a suction portion 47 that is provided on one of the accommodating portions 46 and sucks the movable core 43, and a accommodating portion between the accommodating portion 46 and the suction portion 47. The magnetic diaphragm 48 is thinner than 46 and is integrally formed.
The movable core 43 is made of a magnetic material and is provided inside the accommodating portion 46 of the fixed core 42 so as to be reciprocally movable in the axial direction.

The coil 44 is wound around a bobbin 49 formed of an insulator between the fixed core 42 and the yoke 41, and is electrically connected to the terminal 51 of the connector 50.
A plunger 53 is provided in a hole 52 formed in the axial direction of the fixed core 42 so as to be reciprocally movable in the axial direction. The plunger 53 has one end in contact with the movable core 43 and the other end in contact with the end of the spool 20.
When a current is supplied from the connector 50 to the coil 44, the coil 44 generates a magnetic field, and a magnetic flux flows through a magnetic circuit formed by the yoke 41, the fixed core 42 and the movable core 43. Thereby, the movable core 43 is attracted by the magnetic force to the suction portion 47 of the fixed core 42. Then, the plunger 53 that contacts the movable core 43 displaces the spool 20 toward the coil spring 30 against the urging force of the coil spring 30.

Next, a characteristic configuration of the present embodiment will be described.
As shown in FIG. 3, a guide portion 60 that protrudes radially outward is provided on the outer wall of the shaft portion 24. The radial outer wall 61 of the guide portion 60 is inclined radially inward from the second land 22 side toward the first land 21 side, and has an outer diameter on the first land 21 side than an outer diameter on the second land 22 side. It is formed in a small taper shape. The taper angle of the outer wall 61 in the radial direction of the guide portion 60 is formed at an angle that allows the hydraulic oil flowing from the input port 12 to be guided to the output port 13. For this reason, the hydraulic oil flowing in from the input port 12 is guided to the outer wall 61 in the radial direction of the guide portion 60 and flows toward the inner wall of the output port 13 as indicated by an arrow A.
The guide portion 60 is formed so that the outer diameter of the cylindrical portion 62 on the second land side is slightly smaller than the inner diameter of the sleeve 10. The outer diameter of the cylindrical portion 62 is substantially the same as the outer diameter of the first land 21 and the outer diameter of the second land 22. For this reason, it is suppressed that the hydraulic fluid which flows in from the input port 12 directly hits the outer wall 29 on the first land 21 side in the axial direction of the second land 22.

1 and 3 show a state where the coil 44 of the electromagnetic actuator 40 is not energized. In this state, the cylindrical portion 62 of the guide portion 60 is located closer to the input port 12 in the axial direction than the inner wall of the output port 13 on the discharge port 14 side. Thereby, the communication state of the input port 12 and the discharge port 14 is maintained.
On the other hand, FIGS. 2 and 4 show a state in which the coil 44 of the electromagnetic actuator 40 is energized. In this state, the cylindrical portion 62 of the guide portion 60 is located closer to the discharge port 14 in the axial direction than the inner wall of the output port 13 on the input port 12 side. For this reason, the communication state of the input port 12 and the output port 13 is maintained.

Next, the operation of the electromagnetic valve 1 will be described.
When the coil 44 of the electromagnetic actuator 40 is not energized, the second land 22 opens the discharge port 14 as shown in FIGS. For this reason, the hydraulic pressure supplied from the input port 12 is discharged from the discharge port 14 via the communication chamber 15 from the gap between the inner wall of the sleeve 10 and the first land 21 or the notch 27 of the first land 21. Accordingly, no hydraulic pressure is output from the output port 13.

When the coil 44 of the electromagnetic actuator 40 is energized, the movable core 43 is attracted to the suction portion 47 of the fixed core 42 and the plunger 53 displaces the spool 20 toward the coil spring 30 as shown in FIGS. . As a result, the first land 21 opens the input port 12. Moreover, the 2nd land 22 obstruct | occludes the discharge port 14, and the input port 12 and the discharge port 14 transfer to the interruption | blocking state from a communication state. For this reason, the hydraulic pressure supplied from the input port 12 is output from the output port 13 to the load of the automatic transmission (not shown) via the communication chamber 15.
When the coil 44 of the electromagnetic actuator 40 is switched from the non-energized state to the energized state, the hydraulic oil flowing into the communication chamber 15 from the input port 12 is indicated by an arrow A in FIG. 3 and an arrow B in FIG. Then, it is guided by the radial outer wall 61 of the guide portion 60 and flows toward the inner wall of the output port 13 on the discharge port 14 side. Thereby, the hydraulic oil flowing into the communication chamber 15 from the input port 12 is suppressed from flowing directly to the communication chamber 15 on the second land 22 side from the guide portion 60.

  A part of the hydraulic pressure output from the output port 13 to the load of the automatic transmission (not shown) is supplied from the feedback port 11 to the feedback chamber 16. Due to the balance between the hydraulic pressure acting on the area corresponding to the difference in outer diameter between the first land 21 and the third land 23, the biasing force of the coil spring 30, and the attractive force of the electromagnetic actuator 40, the spool 20 is brought into a predetermined position. I'll pan. Thereby, the hydraulic pressure output from the output port 13 is adjusted.

  In the present embodiment, the hydraulic oil that is energized to the electromagnetic actuator 40 and flows into the communication chamber 15 from the input port 12 is guided to the output port 13 by the guide unit 60. For this reason, it is suppressed that the dynamic pressure of the hydraulic fluid which flows in from the input port 12 acts on the outer wall 29 on the first land side in the axial direction of the second land. Thereby, the flow force which acts in the direction opposite to the direction in which the electromagnetic actuator 40 moves the spool 20 can be reduced. Therefore, the electromagnetic actuator 40 can quickly move the spool 20 to the target phase, and the responsiveness of the hydraulic fluid output from the output port 13 to the energization of the electromagnetic actuator 40 can be improved.

  In the present embodiment, the outer diameter of the cylindrical portion 62 of the guide portion 60 is formed to be approximately the same as the outer diameter of the first land 21 and the outer diameter of the second land 22. Thereby, the hydraulic oil flowing in from the input port 12 is prevented from directly hitting the outer wall 29 on the first land 21 side in the axial direction of the second land 22. Therefore, the flow force can be reliably reduced.

(Second Embodiment)
FIG. 5 shows a partially enlarged view of the solenoid valve according to the second embodiment of the present invention. Hereinafter, in the plurality of embodiments, substantially the same components as those in the first embodiment described above are denoted by the same reference numerals and description thereof is omitted.
In the present embodiment, the outer wall 71 in the radial direction of the guide portion 70 is formed in a curved shape that is recessed inward in the radial direction and recessed toward the second land 22 in the axial direction. For this reason, the hydraulic oil flowing in from the input port 12 is reliably guided to the output port 13 along the curved outer wall 71 of the guide portion 70 as indicated by an arrow C. For this reason, it is suppressed that the dynamic pressure of the hydraulic fluid input from the input port 12 acts on the outer wall 29 of the second land 22 on the first land 21 side in the axial direction. Therefore, the flow force can be reliably reduced. Furthermore, the shape of the outer wall 71 of the guide part 70 is difficult to receive the dynamic pressure of the hydraulic oil flowing in the communication chamber 15 in the radial direction. Therefore, the flow force can be reliably reduced.

(Third embodiment)
FIG. 6 shows a partially enlarged view of the electromagnetic valve according to the third embodiment of the present invention. In the present embodiment, the radial outer wall 81 of the guide portion 80 is formed in a curved shape protruding outward in the radial direction and protruding toward the first axial land 21 side. For this reason, the hydraulic oil flowing in from the input port 12 is guided to the inner wall of the output port 13 on the discharge port 14 side along the curved outer wall 81 of the guide portion 80 as indicated by an arrow D. Further, the shape of the outer wall 81 of the guide portion 80 is difficult to receive the dynamic pressure of the hydraulic oil flowing in the communication chamber 15 in the axial direction. Therefore, the flow force can be reliably reduced.

(Fourth embodiment)
FIG. 7 shows a partially enlarged view of the solenoid valve according to the fourth embodiment of the present invention. In the present embodiment, the guide portion 90 has a second taper portion 93 on the second land 22 side with respect to the cylindrical portion 92. Even in such a configuration, the hydraulic oil flowing in from the input port 12 is guided to the output port 13 along the outer wall 91 of the guide portion 90 as indicated by an arrow E, so that the flow force can be reduced. .

(Fifth embodiment)
FIG. 8 shows a partially enlarged view of the solenoid valve according to the fifth embodiment of the present invention. In this embodiment, the sleeve 10 has an input port 12 and an output port 13 and does not have a discharge port. The first land 21 of the spool 20 opens and closes the input port 12. The second land 22 slides with the inner wall of the sleeve 10 opposite to the input port 12 of the output port 13.

  Also in this embodiment, when the spool 20 is displaced to the left in FIG. 8 and the input port 12 is opened, hydraulic pressure is output from the output port 13. At this time, the hydraulic oil flowing into the communication chamber 15 from the input port 12 is guided to the outer wall 61 in the radial direction of the guide portion 60 and flows toward the inner wall of the output port 13 as indicated by an arrow F. Thereby, it is suppressed that the dynamic pressure of the hydraulic fluid which flows in from the input port 12 acts on the outer wall 29 on the first land side in the axial direction of the second land. Therefore, the flow force can be reduced and the responsiveness of the electromagnetic valve can be increased.

(Other embodiments)
In the above embodiments, the electromagnetic valve used in the automatic transmission of the vehicle has been described. On the other hand, the present invention may be used for various devices that perform hydraulic control of hydraulic oil, such as a hydraulic valve timing adjusting device.
In the above embodiments, the outer diameter of the guide portion is formed to be substantially the same as the outer diameter of the first land and the outer diameter of the second land. On the other hand, according to the present invention, the outer diameter of the guide portion may be smaller than the outer diameter of the first land and the outer diameter of the second land.
As described above, the present invention is not limited to the above-described embodiment, and can be implemented in various forms within the scope of the invention in addition to combining the plurality of embodiments.

1 ... Solenoid valve,
10 ... Sleeve,
12 ・ ・ ・ Input port,
13 ・ ・ ・ Output port,
14 ... discharge port,
20 ・ ・ ・ Spool,
21 ... 1st land,
22 ... 2nd land,
24 ... shaft part,
30: Coil spring,
40 ・ ・ ・ Electromagnetic actuator,
60, 70, 80, 90 ... guide section

Claims (6)

A cylindrical sleeve having an input port for inputting fluid pressure, an output port for outputting fluid pressure, and a discharge port for discharging fluid;
A first land that slides on the inner wall of the sleeve and opens and closes the input port, a second land that slides on the inner wall of the sleeve and opens and closes the discharge port, and connects the first land and the second land. A spool having a shaft portion and provided inside the sleeve so as to be reciprocally movable in the axial direction;
An electromagnetic actuator that switches communication or blocking between the input port and the discharge port by moving the spool in the axial direction, and controls a fluid pressure output from the output port;
An electromagnetic valve comprising: a guide portion that protrudes outside the diameter of the shaft portion of the spool and guides the fluid flowing in from the input port to the output port.   2. The solenoid valve according to claim 1, wherein an outer wall in a radial direction of the guide portion is tapered from the second land side toward the first land side and is inclined inward in the radial direction.   The guide portion has an outer diameter on the second land side to such an extent that the fluid flowing in from the input port can be prevented from directly hitting the outer wall on the first land side in the axial direction of the second land. The electromagnetic valve according to claim 1 or 2, wherein is formed to be slightly smaller than an inner diameter of the sleeve.   The electromagnetic valve according to any one of claims 1 to 3, wherein an outer wall in a radial direction of the guide part has a curved shape that is recessed inward in the radial direction and in the second land side in the axial direction.   The electromagnetic valve according to any one of claims 1 to 3, wherein an outer wall in a radial direction of the guide portion has a curved shape protruding outward in the radial direction and toward the first land in the axial direction. A cylindrical sleeve having an input port to which fluid pressure is input and an output port for outputting fluid pressure;
A first land that slides on the inner wall of the sleeve to open and close the input port; a second land that slides on the inner wall of the sleeve; and a shaft portion that connects the first land and the second land; A spool provided inside the sleeve so as to be capable of reciprocating in the axial direction;
An electromagnetic actuator that switches a communication state between the input port and the output port by moving the spool in an axial direction, and controls a fluid pressure output from the output port;
An electromagnetic valve comprising: a guide portion that protrudes outside the diameter of the shaft portion of the spool and guides the fluid flowing in from the input port to the output port.

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