WO2020054837A1

WO2020054837A1 - Linear solenoid valve

Info

Publication number: WO2020054837A1
Application number: PCT/JP2019/036063
Authority: WO
Inventors: 智己石川; 秀一竹田; 真吾栗本
Original assignee: アイシン・エィ・ダブリュ株式会社
Priority date: 2018-09-13
Filing date: 2019-09-13
Publication date: 2020-03-19
Also published as: JP2020041687A

Abstract

This linear solenoid valve (1) is provided with: a solenoid part (2); a sleeve (15) having an inlet port (20a), an outlet port (20b), and a drain port (20c); and a spool (16) having a first land part (16b) and a second land part (16c). The first land part (16b) blocks an input hydraulic pressure (Pin) by means of an inlet port (20a)-side surface (16bb), and the spool (16) adjusts an output hydraulic pressure (Pout) by moving and thereby discharging the input hydraulic pressure (Pin) from the outlet port (20b). The outer diameters of the first land part (16b) and the second land part (16c) are made different so that the output hydraulic pressure (Pout) is also applied to the spool (16) as a feedback pressure in a direction from the outlet port (20b) toward the inlet port (20a) in the axial direction of the spool (16).

Description

Linear solenoid valve

技術 This technology relates to a linear solenoid valve that performs feedback control using output hydraulic pressure output from an output port.

For example, in a vehicle drive device such as an automatic transmission or a hybrid drive device, a hydraulic control device for hydraulically controlling engagement of a clutch or a brake is provided with a linear solenoid valve that regulates and outputs an engagement pressure. ing. Such a linear solenoid valve has an input port, an output port, a discharge port, and a feedback port. A part of the output oil pressure is supplied to the feedback oil chamber as a feedback pressure, and the feedback pressure is applied to the difference in valve area. Has a feedback structure for urging the valve in the direction of the electromagnetic portion of the solenoid (see Patent Document 1).

JP 2015-68481 A

However, the linear solenoid valve provided with a feedback port as in Patent Literature 1 has a problem that the overall length in the axial direction is increased by the amount of the feedback port. In addition, the feedback port needs to be provided with a difference in the diameter of the land portion of the spool. Therefore, the feedback port is generally arranged on the end side of the valve portion with respect to the other ports. Causes the flow rate of oil leaking from the feedback port to the end of the valve section, which hinders the reduction of the consumption flow rate of the linear solenoid valve. The driving load cannot be reduced, which hinders improvement in fuel efficiency of a vehicle equipped with the linear solenoid valve.

Therefore, it is an object of the present invention to provide a linear solenoid valve that can be shortened in the axial direction and has a reduced flow rate while having a feedback structure.

This linear solenoid valve is
A solenoid unit that drives the plunger according to the supplied current;
A sleeve having an input port, an output port, and a discharge port, each of which is constituted by a through hole and arranged in order in the axial direction,
A spool slidably inserted into the sleeve,
The spool has a first land portion and a second land portion, and the axial position is controlled by pressing the plunger, so that the first land portion allows the input port and the output port to be connected to each other. From the first position where the output port and the discharge port are communicated by the second land portion, and the input port and the output port are communicated by the first land portion and the second land portion Movable to a second position that shuts off the output port and the discharge port;
The first land portion, when the spool is at the first position, blocks input hydraulic pressure input to the input port by a side surface on the input port side in the axial direction, and the spool is moved to the second position by the second port. By moving toward the position, the output hydraulic pressure can be adjusted by allowing the input hydraulic pressure to flow out of the output port,
The first land portion and the second land portion so that output hydraulic pressure output from the output port also acts as feedback pressure on the spool in a direction from the output port to the input port in the axial direction of the spool. An outer diameter difference was provided between the land portion.

Thus, according to the present linear solenoid valve, while having a feedback structure, it is possible to shorten the axial direction and reduce the consumption flow rate.

FIG. 2 is a cross-sectional view showing the linear solenoid valve according to the first embodiment. FIG. 2 is a schematic sectional view showing a valve portion of the linear solenoid valve according to the first embodiment. FIG. 4 is a schematic cross-sectional view showing a valve portion of a linear solenoid valve according to a second embodiment. FIG. 9 is a schematic cross-sectional view illustrating a valve portion of a linear solenoid valve according to a third embodiment. FIG. 13 is a schematic cross-sectional view illustrating a valve portion of a linear solenoid valve according to a fourth embodiment. FIG. 14 is a schematic sectional view showing a valve section of a linear solenoid valve according to a fifth embodiment. FIG. 4 is a schematic cross-sectional view showing a valve section of a linear solenoid valve according to a first reference example. FIG. 4 is a schematic cross-sectional view showing a valve portion of a linear solenoid valve according to a second reference example.

<First embodiment>
Hereinafter, the first embodiment will be described with reference to FIGS. 1 and 2. FIG. 1 is a sectional view showing a linear solenoid valve according to the first embodiment, and FIG. 2 is a schematic sectional view showing a valve portion of the linear solenoid valve according to the first embodiment.

The linear solenoid valve 1 according to the first embodiment is a so-called normally closed type linear solenoid valve, which is used for a hydraulic control device mounted on a vehicle drive device such as an automatic transmission or a hybrid drive device. Yes, specifically, a linear solenoid valve that regulates the engagement pressure supplied to the hydraulic servo of the clutch or brake of the transmission mechanism, a linear solenoid valve that regulates the engagement pressure supplied to the lock-up clutch, and regulates the line pressure Therefore, it is used for a linear solenoid valve or the like that regulates a control pressure according to a throttle opening.

As shown in FIG. 1, the linear solenoid valve 1 has a solenoid part 2 and a valve part 3, and the valve part 3 is used by being mounted on a valve body 5 of a hydraulic control device (not shown). The solenoid portion 2 is slidably fitted to a coil 6 wound on a bobbin, a first core 7 and a second core 9 mounted so as to cover the coil 6, and a hollow portion of the second core 9. A plunger 10 inserted therein, a rod member 11 slidably disposed in a hollow member 8 fitted in the first core 7, and a yoke 12 covering the above members and integrally connected to the valve portion 3. And

The first and

second cores

7 and 9, the plunger 10 and the yoke 12 are made of a ferromagnetic material, and the portion between the rod member 11 and the first and

second cores

7 and 9 is made of a non-magnetic material. Is supplied from the terminal 13 to the coil 6, a magnetic flux circuit is formed which flows in the order of the first core 7 through the yoke 12, the second core 9, and the plunger 10, and the plunger 10 based on the magnetic flux circuit is formed. The pressing force is transmitted to the spool 16 of the valve section 3 via the rod member 11.

The valve section 3 has a sleeve 15 and a spool 16. The sleeve 15 has a cylindrical shape over substantially the entire length, and an outer peripheral surface 15 a of the sleeve 15 is inserted into the installation hole 5 a of the valve body 5. As a result, it is mounted on the valve body 5. The spool 16 is slidably fitted on the inner peripheral surface 15b of the sleeve 15. An enlarged diameter portion 15g is formed on one end of the sleeve 15, and the tip of the yoke 12 is caulked to the enlarged diameter portion 15g, so that the solenoid portion 2 and the valve portion 3 are integrally assembled. . A cap 17 is screwed and fixed to the other end, which is an end of the sleeve 15, to prevent the spool 16 from coming off inside the sleeve 15, and to end the cap 17 and the end of the spool 16 (details will be described later). The spring 19 as an urging member is contracted between the land portion 16d). In other words, the spring 19 is disposed on the side opposite to the solenoid portion 2 with respect to the spool 16 in the axial direction so as to urge the spool 16 in opposition to the pressing of the plunger 10. The opposite end of the spool 16 is in contact with the rod member 11 of the solenoid unit 2, and the spool 16 applies the pressing force of the plunger 10 and the urging force of the spring 19 (and the feedback pressure described later). Is controlled to a balanced position.

The sleeve 15 has an input port 20a, an output port 20b, and a drain port 20c which are formed by through holes penetrating from the outer peripheral surface 15a to the inner peripheral surface 15b. It communicates with each formed oil passage. Specifically, an input port 20a, an output port 20b, and a drain port 20c (discharge port) are formed in the sleeve 15 in the axial direction AX that is the moving direction of the spool 16 from the solenoid portion 2 side. An input oil pressure Pin such as a line pressure is input to the input port 20a, and an output oil pressure Pout serving as an engagement pressure supplied to a hydraulic servo or the like is output from the output port 20b. Then, the hydraulic pressure is discharged (EX) from the drain port 20c so as to be released to the atmosphere via the oil passage of the valve body 5.

The spool 16 has a land portion 16a, a land portion 16b (first land portion), a land portion 16c (second land portion), and a land portion 16d in this order from the side of the solenoid portion 2 in the axial direction. Each of the land portions has a smaller diameter than each land portion, and has a shaft portion 16e, a shaft portion 16f, and a shaft portion 16g connecting the land portions. Each land portion is formed so as to slide on the inner peripheral surface 15b of the sleeve 15, and more specifically, a sliding surface 16aa which is an outer peripheral surface of the land portion 16a, and a sliding surface which is an outer peripheral surface of the land portion 16b. The sliding surface 16ca, which is the outer peripheral surface of the land portion 16c, and the sliding surface 16da, which is the outer peripheral surface of the land portion 16d, are slidable with the inner peripheral surface 15b of the sleeve 15, respectively.

The

lands

16c and 16d are formed to have an outer diameter d1, and the

lands

16a and 16b are formed to have an outer diameter d2 larger than the outer diameter d1. In other words, the

lands

16a and 16b have a larger diameter than the

lands

16c and 16d. As a result, a pressure receiving area difference is set between the land portion 16b and the land portion 16c due to the outer diameter difference (d2-d1), and the output oil pressure Pout output from the output port 20b is applied to the output port 20b in the axial direction of the spool 16. , And acts as a feedback oil chamber 31 acting on the spool 16 as feedback pressure in a direction toward the input port 20a.

A notch N1 is formed at an end of the land 16b on the side of the input port 20a in the axial direction, and a notch N2 is formed at an end of the land 16c on the side of the drain port 20c in the axial direction. Have been. The function of the notches N1 and N2 will be described later.

Next, it will be described with reference to FIG. 2, the operation of the valve portion 3 ₁ of the first embodiment. As shown in FIG. 2, the spool 16 in the valve portion 3 _1, the pressing force F2 of the plunger 10 of the solenoid portion 2 (see FIG. 1), a spring 19 so that the the urging force FS (see FIG. 1) acts Is configured. An input oil pressure Pin such as a line pressure is input to the input port 20a, and when the solenoid unit 2 shown in FIG. 2 is de-energized, the spool 16 is moved by the urging force of the spring 19 to move the solenoid unit 2 in the axial direction. (The first position), the output port 20b and the drain port 20c communicate with each other, that is, the output hydraulic pressure Pout is discharged to zero pressure. In this state, the input oil pressure Pin is blocked by the side surface 16bb of the land portion 16b on the side of the input port 20a.

From this state, when the spool 16 is pressed against the urging force FS of the spring 19 by the pressing force F2 of the solenoid unit 2 to control the axial position, the land 16b moves toward the output port 20b. Accordingly, the input port 20a and the output port 20b communicate with each other through the notch N1 (see FIG. 1), and the input hydraulic pressure Pin is gradually discharged to the output port 20b, and the land 16c is connected to the drain port 20c. With the movement to the side, the output port and the drain port 20c are closed by the land portion 16c, and only the discharge by the notch N2 (see FIG. 1) is performed. That is, the discharge amount from the drain port 20c at the output port 20b is reduced. As the pressure decreases, the outflow from the input port 20a increases and the output hydraulic pressure Pout increases.

Thereafter, when the spool 16 is further pressed by the pressing force F2, the land portion 16b opens to the output port 20b, and the inflow from the input port 20a to the output port 20b increases, and the land portion 16c Closes the gap between the output port 20b and the drain port 20c, the amount of discharge from the output port 20b to the drain port 20c decreases, and finally the position where the spool 16 has moved most toward the spring 19 in the axial direction ( At the second position, the input oil pressure Pin of the input port 20a flows out as it is as the output oil pressure Pout of the output port 20b. The land portion 16d is disposed on the opposite side of the land portion 16c in the axial direction from the land portion 16b, and is configured to block leakage of hydraulic pressure discharged from the drain port.

In this way, the input hydraulic pressure Pin is accumulated around the shaft portion 16e of the spool 16 by the side surface 16bb of the land portion 16b on the side of the input port 20a and is blocked, and the input hydraulic pressure Pin is gradually moved to the output port 20b as the land portion 16b moves. By adjusting the magnitude of the output oil pressure Pout by letting the input oil pressure Pin flow out, the outflow amount (throttle amount) flowing from the inside of the sleeve 15 toward the output port 20b is adjusted. It is called "spill restriction".

When the output oil pressure Pout is increased by moving the spool 16 as described above, as described above, the output of the output port 20b is output to the feedback oil chamber 31 caused by the pressure receiving area difference between the land 16b and the land 16c. The hydraulic pressure Pout acts on the spool 16 to act as a feedback pressure corresponding to the output oil pressure Pout toward the solenoid portion 2 in the axial direction, that is, the spool 16 restricts the outflow of the input oil pressure Pin by the output oil pressure Pout. Feedback control is performed in the direction. Thus, the valve portion 3 ₁ of the linear solenoid valve 1 according to the first embodiment will be feedback oil chamber 31 is disposed inside the output port 20b in the axial direction.

Here, compared to the valve portion 3 ₁ of the linear solenoid valve 1 of the first embodiment, the valve portion 103 ₁ of the linear solenoid valve of the first reference example in which the outflow aperture shown in FIG. As shown in FIG. 7, the valve portion 103 ₁ of the first reference example, the input port 120a, the output port 120b, a sleeve 115 having a drain port 120c, and a feedback port 120d, sliding on the inner peripheral surface 115b of the sleeve 115 The spool 116 is provided with a land portion 116a, a land portion 116b, a land portion 116c, and a land portion 116d in order in the axial direction. A shaft portion 116e, a shaft portion 116f, and a shaft portion 116g for connecting the portions are provided. And, inside the feedback port 120d, a closing plate 115c arranged in a cylindrical shape straddling in the axial direction and an orifice 115d which is a through hole formed in the closing plate 115c are arranged to provide feedback. An oil chamber 131 is formed.

The valve unit 103 ₁ shown in FIG. 7, the partial feedback port 120d is provided, the axial direction is longer than the valve portion _{3 1.} That is, since the feedback pressure substantially equal to the output hydraulic pressure Pout acts on the feedback oil chamber 131, the feedback oil pressure is prevented from leaking between the land portion 116c and the inner peripheral surface 115b of the sleeve 115, and between the land portion 116c and the sleeve. It is necessary to ensure a long sealing between the inner surface 115b and the inner peripheral surface 115b of the sleeve 115 to secure the sealing property, and the axial length between the land portion 116c and the land portion 116d and the sleeve 115 becomes longer. However, the valve portion 3 ₁ of the first embodiment, the land portion 16d is the land portion 16b, which is disposed on the outermost end of the plurality of land portions including a land portion 16c, and the land portion 16a, a feedback Since there is no port, that is, there is no land portion constituting the feedback port, the sleeve 15 and the spool 16 can be shortened. Further, since the portion where the feedback pressure acts is the same as the output hydraulic pressure Pout, the sealing performance of the feedback pressure is achieved. a portion of securing is not necessary, even if the minute, the sleeve 15 can be shortened and the spool 16, i.e. it is possible to shorten the valve portion 3 _1.

Further, the valve portion 103 ₁ of the first reference example, even if the sleeve 115 and spool 116 to secure the sealing property as the long, the sealing property is limited, axial from the feedback port 120d (feedback oil chamber 131) The output hydraulic pressure Pout will leak to both sides in the direction. In particular, when the seal rings S4 and S5 are not disposed, the output hydraulic pressure Pout leaks between the outer peripheral surface 115a of the sleeve 115 and the valve body. On the other hand, the valve portion 3 ₁ of the first embodiment, (min output port 20b and the feedback oil chamber 31 is shared) minute feedback port is not, the output hydraulic pressure Pout are places is reduced leak, leak amount is small That is, the consumption flow rate of the linear solenoid valve 1 can be reduced.

By the way, as a method of eliminating the feedback port from the linear solenoid valve, a method of embedding a second spool for performing feedback control inside the first spool as in JP-A-2009-8158 is conceivable. The linear solenoid valve 1 according to the first embodiment has a smaller number of parts and can be reduced in price as compared with a case using such two spools.

As described above, the valve portion 3 ₁ according to the first embodiment, yet as it is possible to perform a feedback control, it is possible to shorten the axial direction and also possible to achieve a reduction in consumption flow rate Can be.

The valve unit 3 ₁ according to the first embodiment, since one in which pressure regulating the output hydraulic pressure Pout by outlet throttle as described above, the input hydraulic pressure Pin is an output port that was blocked by the side surface 16bb of the land portion 16b When the oil flows out to the outlet port 20b, the oil flows from the spool 16 toward the output port 20b in the outer diameter direction. Therefore, the jet flow based on the input oil pressure Pin does not directly hit the side surface 16bc on the side of the output port 20b (the drain port 20c) in the axial direction of the land portion 16b on the side with the larger outer diameter, and acts as a disturbance to the feedback pressure. Therefore, the accuracy of the feedback control can be improved.

<Second embodiment>
Next, a second embodiment in which the first embodiment is partially modified will be described with reference to FIG. FIG. 3 is a schematic cross-sectional view showing a valve portion of a linear solenoid valve according to the second embodiment.

Valve part 3 ₂ of the linear solenoid valve 1 according to the second embodiment is different from the first embodiment, as shown in FIG. 3, the seal ring S1 outer circumferential surface into three sleeves 15, S2, S3 It is provided with. In other words, the valve portion 3 ₂ which is inserted into the installation hole 5a of the valve body 5 (see FIG. 1), hydraulic leaks slightly between the outer peripheral surface 15a of the mounting hole 5a and the sleeve 15 of the valve body 5. In particular, the input hydraulic pressure Pin is input to the input port 20a, and the output hydraulic pressure Pout is output from the output port 20b. Therefore, by sealing both sides of these ports in the axial direction, the flow consumption of the linear solenoid valve 1 is reduced. It is possible to do.

Therefore, the valve portion 3 _2, in the outer periphery of the sleeve 15, the seal ring S1, located on the opposite side of the output port 20b to the input port 20a in the axial direction (first seal ring) in the axial direction A seal ring S2 (second seal ring) disposed between the input port 20a and the output port 20b, and a seal ring S3 (third seal ring) disposed between the output port 20b and the drain port 20c in the axial direction. Is provided.

Here, the valve portion 103 ₁ of the linear solenoid valve of the first reference example, since the output hydraulic pressure Pout is supplied to the feedback port 120d, have a seal ring S4, S5 arranged on both sides in the axial direction of the feedback port 120d For example, the leakage caused by the output oil pressure Pout cannot be reduced, and the consumption flow rate cannot be reduced. Therefore, when disposing the seal rings, it is necessary to dispose five seal rings S1, S2, S3, S4, and S5.

However, the valve portion 3 ₂ according to the second embodiment, since the feedback port is not may be sealed for the input port 20a and output port 20b, sharing the seal ring S2, 3 pieces of the seal ring S1, Only by arranging S2 and S3, the consumption flow rate can be reduced. Therefore, while the consumption flow rate can be reduced, the number of seal rings can be reduced and the cost can be reduced as compared with the one having the feedback port.

The linear solenoid valve 1 according to the second embodiment is the same as the first embodiment in other configurations, operations, and effects, and thus the description thereof is omitted.

<Third embodiment>
Next, a third embodiment in which the second embodiment is partially modified will be described with reference to FIG. FIG. 4 is a schematic sectional view showing a valve portion of a linear solenoid valve according to the third embodiment.

Valve unit 3 ₃ of the linear solenoid valve 1 according to the third embodiment is different from the second embodiment, as shown in FIG. 4, as the feedback oil chamber forming portion 15F that forms a feedback oil chamber 31, surrounded The sleeve 15 has a portion 15c and an orifice 15d.

The surrounding portion 15c is disposed astride the land portion 16b and the land portion 16c, and the outer peripheral side of the shaft portion 16f is slid on the sliding surface 16ba of the land portion 16b and the sliding surface 16ca of the land portion 16c. It is annularly formed and arranged so as to surround it, and forms a feedback oil chamber 31 inside. An orifice 15d, which is a through hole, is formed in the surrounding portion 15c, and is configured to communicate the output port 20b and the feedback oil chamber 31. The output oil pressure Pout of the output port 20b is input as the feedback pressure FB. It is configured as follows. Although not shown, the surrounding portion 15c is connected by being formed integrally with the sleeve 15, and is fixed so as not to be movable in the axial direction.

The feedback oil chamber forming portion 15F configured as described above buffers the output oil pressure Pout input to the feedback oil chamber 31 by the orifice 15d even if the output oil pressure Pout pulsates, and stabilizes the fluctuation of the feedback pressure. be able to. Further, even if the land 16b is opened to the output port 20b and the input oil pressure Pin flows out as a jet, the jet does not directly hit the feedback oil chamber 31 by the surrounding portion 15c. It can also be prevented.

For example, when the feedback oil chamber forming portion 15F is not provided as in the first and second embodiments, the magnitude of the hydraulic pressure output from the output hydraulic pressure Pout, in other words, the magnitude of the hydraulic pressure input to the input port 20a is small. Thus, the fluctuation of the feedback pressure is small, and there is no particular problem. In short valve portion of the third embodiment 3 ₃ is suitable for easily pulsation output hydraulic pressure as the performance of the linear solenoid valve 1, suitable for use as outputting large input hydraulic Pin temper pressure in the output hydraulic pressure Pout It is.

The linear solenoid valve 1 according to the third embodiment is the same as the first and second embodiments in other configurations, operations, and effects, and thus the description thereof is omitted.

<Fourth embodiment>
Next, a fourth embodiment in which the first to third embodiments are partially modified will be described with reference to FIG. FIG. 5 is a schematic cross-sectional view showing a valve portion of a linear solenoid valve according to a fourth embodiment.

This valve portion 3 ₄ of the linear solenoid valve 1 according to the fourth embodiment, as compared with the first to third embodiments, as shown in FIG. 5, when the solenoid portion 2 is de-energized, the spool 16 Is located at a position (first position) on the side of the solenoid portion 2 in the axial direction by the urging force of the spring 19, and the input hydraulic pressure Pin input to the input port 20a is applied to the sliding surface 16ba of the land portion 16b (first land portion). When the spool 16 moves, the land portion 16b opens the input port 20a and flows into the output port 20b as the output hydraulic pressure Pout. In a state where the spool 16 is moved to the position closest to the spring 19 (second position) and the input oil pressure Pin is output as the output oil pressure Pout almost as it is, the axial direction of the land portion 16c (second land portion) The output hydraulic pressure Pout is blocked by the side surface 16cb on the side of the output port 20b, and the output hydraulic pressure Pout of the output port 20b flows out (discharges) to the drain port 20c as it moves toward the solenoid unit 2. .

In this way, the input hydraulic pressure Pin is blocked by the sliding surface 16ba of the input port 20a of the land 16b to the input port 20a, and the input hydraulic pressure Pin gradually flows into the output port 20b as the land 16b moves. Adjusting the magnitude of the output hydraulic pressure Pout by performing the adjustment is referred to as “inflow restriction” because the flow amount (restriction amount) flowing from the input port 20a toward the inside of the sleeve 15 is adjusted.

In the valve unit 3 _4, the land portion 16b constitutes has set the pressure receiving area difference consists in diameter than the land portion 16c, these land portion 16b, a feedback oil chamber 31 between 16c. As a result, a feedback pressure corresponding to the output oil pressure Pout output from the output port 20b acts on the spool 16, that is, the spool 16 is feedback-controlled by the output oil pressure Pout so as to restrict the outflow of the input oil pressure Pin. Thus, even the valve portion 3 ₄ of the linear solenoid valve 1 according to the fourth embodiment will be feedback oil chamber 31 is disposed inside the output port 20b in the axial direction. Therefore, in the valve unit 3 ₄ according to the fourth embodiment, since the feedback port is not, despite those which can feedback control, it is possible to shorten the axial direction can be achieved also reduce the consumption flow .

Here, compared to the valve portion 3 ₄ of the linear solenoid valve 1 of the fourth embodiment, the valve portion 103 ₂ of the linear solenoid valve of the second reference example for the outflow aperture shown in FIG. As shown in FIG. 8, the valve portion 103 ₂ of the second reference example, the input port 120a, the output port 120b, a sleeve 115 having a drain port 120c, and a feedback port 120d, sliding on the inner peripheral surface 115b of the sleeve 115 The spool 116 has a land portion 116a, a land portion 116b, and a land portion 116c in the axial direction, and connects the land portions. A shaft portion 116e and a shaft portion 116f are provided. And, inside the feedback port 120d, a closing plate 115c arranged in a cylindrical shape straddling in the axial direction and an orifice 115d which is a through hole formed in the closing plate 115c are arranged to provide feedback. An oil chamber 131 is formed.

The valve unit 103 ₂ shown in FIG. 8, the partial feedback port 120d is provided, the axial direction is longer than the valve portion _{3 4.} In other words, since the feedback pressure substantially equal to the output hydraulic pressure Pout acts on the feedback oil chamber 131, the feedback pressure is prevented from leaking between the land portion 116a and the inner peripheral surface 115b of the sleeve 115 and between the land portion 116b and the sleeve 116b. It is necessary to secure the sealing property by long overlap in the axial direction between the inner peripheral surface 115b and the inner peripheral surface 115b, and the axial length of the land portion 116a and the land portion 116b and the sleeve 115 becomes longer. However, the valve unit 3 ₄ according to the fourth embodiment, the land portion 16c are disposed on the outermost end of the plurality of land portions including a land portion 16b, partial feedback port is not, that is, the feedback port The sleeve 15 and the spool 16 can be shortened by the absence of the lands, and the portion where the feedback pressure acts is the same as the output hydraulic pressure Pout. even minute, the sleeve 15 can be shortened and the spool 16, i.e. it is possible to shorten the valve unit 3 _4.

Further, the valve portion 103 ₂ of the second reference example, even if the sleeve 115 and spool 116 to secure the sealing property as the long, the sealing property is limited, axial from the feedback port 120d (feedback oil chamber 131) The output hydraulic pressure Pout will leak to both sides in the direction. In particular, when the seal rings S4 and S5 are not disposed, the output hydraulic pressure Pout leaks between the outer peripheral surface 115a of the sleeve 115 and the valve body. On the other hand, the valve portion 3 ₄ of the fourth embodiment, as shown in FIG. 5, the minute feedback port is not (min output port 20b and the feedback oil chamber 31 is shared), three seal rings S1, Only by arranging S2 and S3, it is possible to seal between the outer peripheral surface 15a of the sleeve 15 and the installation hole 5a of the valve body 5, so that the consumption flow rate can be reduced. Therefore, while the consumption flow rate can be reduced, the number of seal rings can be reduced and the cost can be reduced as compared with the one having the feedback port.

The shaft in the valve portion 3 ₄ according to the fourth embodiment, since a structure for the flowing diaphragm as described above, as the input pressure Pin is jet land portion 16b flows when opening the output port 20b Since it may flow into the outer periphery of the portion 16e and directly act on the side surface 16cb of the land portion 16c, there is a possibility that the accuracy of the feedback control is slightly lower than in the first to third embodiments. . On the other hand, in the structure of the outflow pressure in the first to third embodiments, the input oil pressure Pin enters between the

land portions

16a and 16b of the spool 16 and is blocked (see FIG. 2). Leakage may occur over the entire circumference between the inner peripheral surface 15b and the sliding surfaces 16aa, 16ba, and the consumption flow rate may increase.

However, in the structure of the inflow restrictor in which the input hydraulic pressure Pin is blocked by the sliding surface 16ba of the land portion 16b as in the fourth embodiment, the input port 20a is open to a part of the entire circumference. Therefore, the leakage between the inner peripheral surface 15b of the sleeve 15 and the sliding surface 16ba is only a part in the circumferential direction, and the consumption flow rate can be reduced as compared with the structure of the outflow restrictor.

Further, the valve portion 3 ₄ of the fourth embodiment, as compared with the first to third embodiments, the axial position of the input port 20a and the drain port 20c is reversed, i.e. drain to the side of the solenoid portion 2 The port 20c can be arranged, and the input port 20a can be arranged on the spring 19 side. Therefore, it is possible to cope with a case where the oil passage (oil passage for supplying line pressure or the like) communicating with the input port 20a cannot be arranged on the side of the solenoid unit 2 due to the arrangement of the oil passage in the valve body 5.

The linear solenoid valve 1 according to the fourth embodiment is the same as the first to third embodiments in other configurations, operations, and effects, and thus the description thereof is omitted.

<Fifth embodiment>
Next, a fifth embodiment in which the fourth embodiment is partially modified will be described with reference to FIG. FIG. 6 is a schematic sectional view showing a valve portion of a linear solenoid valve according to a fifth embodiment.

Valve section ₃₅ of the linear solenoid valve 1 according to the fifth embodiment is different from the fourth embodiment, as shown in FIG. 6, as a feedback oil chamber forming portion 15F that forms a feedback oil chamber 31, surrounded The sleeve 15 has a portion 15c and an orifice 15d. In addition, since the feedback oil chamber 31 is configured, the spool 16 is located between the land portion (fourth land portion) 16b and the land portion (fifth land portion) 16c in the axial direction and on the inner peripheral side of the output port 20b. A land portion 16h (sixth land portion) is formed at a position, and is located at a position on the inner peripheral side of the output port 20b, between the land portion 16h and the land portion 16c in the axial direction. Land portions 16i (seventh land portions) are formed so as to be arranged.

The surrounding portion 15c is disposed astride the land portion 16h and the land portion 16i. The outer peripheral side of the shaft portion 16f is slid on the sliding surface 16ha of the land portion 16h and the sliding surface 16ia of the land portion 16i. It is annularly formed and arranged so as to surround it, and forms a feedback oil chamber 31 inside. An orifice 15d, which is a through hole, is formed in the surrounding portion 15c, and is configured to communicate the output port 20b and the feedback oil chamber 31. The output oil pressure Pout of the output port 20b is input as the feedback pressure FB. It is configured as follows. Although not shown, the surrounding portion 15c is connected by being formed integrally with the sleeve 15, and is fixed so as not to be movable in the axial direction.

The feedback oil chamber forming portion 15F configured as described above buffers the output oil pressure Pout input to the feedback oil chamber 31 by the orifice 15d even if the output oil pressure Pout pulsates, and stabilizes the fluctuation of the feedback pressure. be able to. Further, in the valve unit ₃₅ which is configured as a structural diaphragm inlet, the land portion 16b opens the output port 20b, even if the input hydraulic pressure Pin flows into toward the interior of the sleeve 15 as a jet, the jet by the surrounding portion 15c Does not directly hit the feedback oil chamber 31, it is also possible to prevent disturbance in feedback control.

The linear solenoid valve 1 according to the fifth embodiment is the same as the first to fourth embodiments in other configurations, operations, and effects, and thus the description thereof is omitted.

<Summary of First to Fifth Embodiments>
This linear solenoid valve (1) (for example, see FIGS. 1 to 4)
A solenoid unit (2) for driving a plunger (10) according to the supplied current;
A sleeve (15) having an input port (20a), an output port (20b), and a discharge port (20c), each of which is constituted by a through hole and arranged in the axial direction in order;
A spool (16) slidably inserted into the sleeve,
The spool (16) has a first land portion (16b) and a second land portion (16c), and the position in the axial direction is controlled by pressing the plunger (10), so that the second land portion (16b) is controlled. The input port (20a) and the output port (20b) are shut off by one land portion (16b), and the output port (20b) and the discharge port (20c) are communicated by the second land portion (16c). From the first position, the input port (20a) and the output port (20b) are communicated by the first land portion (16b), and the output port (20b) is connected to the output port (20b) by the second land portion (16c). Movable to a second position to shut off the discharge port (20c),
When the spool (16) is at the first position, the first land portion (16b) transmits the input oil pressure (Pin) input to the input port (20a) to the input port (20a) in the axial direction. ), And the spool (16) moves toward the second position, so that the input hydraulic pressure (Pin) flows out of the output port (20b). (Pout) can be adjusted,
An output hydraulic pressure (Pout) output from the output port (20b) is applied to the spool (16) in a direction from the output port (20b) toward the input port (20a) in the axial direction of the spool (16). An outer diameter difference is provided between the first land portion (16b) and the second land portion (16c) so as to act also as a feedback pressure.

Thus, the linear solenoid valve 1 can be shortened in the axial direction while having the feedback structure, and the flow rate consumed can be reduced. In addition, when the input hydraulic pressure Pin dammed on the side surface 16bb of the land portion 16b flows out to the output port 20b, the jet flow based on the input hydraulic pressure Pin does not directly hit the side surface 16bc of the land portion 16b, and the feedback pressure is reduced. Acting as disturbance can be prevented, and the accuracy of feedback control can be improved.

In addition, the linear solenoid valve (1) (for example, see FIGS. 1 to 4)
The outer diameter of the first land portion (16b) is larger than the outer diameter of the second land portion (16c).

This makes it possible to provide an outer diameter difference between the land portion 16b and the land portion 16c.

In addition, the linear solenoid valve (1) (for example, see FIGS. 1 to 4)
The output hydraulic pressure (Pout) inside the output port (20b) acts on the pressure receiving area difference between the first land portion (16b) and the second land portion (16c), thereby acting as the feedback pressure. I do.

This allows the output oil pressure Pout to act on the spool 16 as feedback pressure.

Also, the linear solenoid valve (1) (for example, see FIG. 4)
The first land portion is formed inside the output port (20b), slidably abuts the first land portion (16b) and the second land portion (16c), and surrounds the spool (16). (16b) and the surrounding portion (15c) surrounding the second land portion (16c), and the output hydraulic pressure (Pout) formed so as to penetrate through the inside and outside of the surrounding portion (15c). And a feedback oil chamber forming portion (15F) having an orifice (15d) through which the fluid flows.

Accordingly, even if the output oil pressure Pout pulsates, the output oil pressure Pout input to the feedback oil chamber 31 can be buffered by the orifice 15d and the fluctuation of the feedback pressure can be stabilized. Further, even if the input oil pressure Pin flows out to the output port 20b as a jet, the jet does not directly hit the feedback oil chamber 31 by the surrounding portion 15c, so that disturbance in feedback control can be prevented.

In addition, the linear solenoid valve (1) (for example, see FIGS. 1 to 4)
The spool (16) is disposed on the opposite side of the second land (16c) in the axial direction from the first land (16b), and prevents leakage of hydraulic pressure discharged from the discharge port (20c). It has a third land part (16d) for blocking,
The third land portion (16d) is disposed at the end of a plurality of land portions including the first land portion (16b) and the second land portion (16c).

As a result, the land portion 16d is disposed at the end of the land portion of the spool 16, that is, since there is no land portion forming a feedback port as in the related art, the axial length of the linear solenoid valve 1 is reduced. be able to.

Also, the linear solenoid valve (1) (for example, see FIG. 6)
A solenoid unit (2) for driving a plunger (10) according to the supplied current;
A sleeve (15) having an input port (20a), an output port (20b), and a discharge port (20c), each of which is constituted by a through hole and arranged in the axial direction in order;
A spool (16) slidably inserted into the sleeve,
The spool (16) includes a fourth land portion (16b), a fifth land portion (16c), a sixth land portion (16h) arranged at a position facing the output port (20b), and A seventh land (16i) disposed at a position facing the port (20b) and between the sixth land (16h) and the fifth land (16c) in the axial direction. The input position (20a) and the output port (20b) are cut off by the fourth land portion (16b) by controlling the axial position by pressing the plunger (10). From a first position where the output port (20b) and the discharge port (20c) communicate with each other by a fifth land portion (16c), the input port (20a) and the output port ( 0b) and being movable by communicating and the fifth land portion (16c) to a second position for blocking said discharge port and said output port (20b) (20c),
The fourth land portion (16b) slides the input hydraulic pressure (Pin) input to the input port (20a) with the sleeve (15) when the spool (16) is at the first position. The input surface (16b) is blocked by the moving surface (16ba), and the input hydraulic pressure (Pin) flows from the input port (20a) by moving the spool (16) toward the second position. ) Is configured to be able to regulate the output hydraulic pressure (Pout) output from
Further, it is formed inside the output port (20b) and slidably abuts the sixth land portion (16h) and the seventh land portion (16i), and the sixth land portion around the spool (16). An output hydraulic pressure (Pout) is formed so as to penetrate the surrounding portion (15c) surrounding the land portion (16h) and the seventh land portion (16i) and the inside and outside of the surrounding portion (15c). And an orifice (15d) into which a feedback oil chamber is formed.
The output hydraulic pressure (Pout) also acts as feedback pressure on the spool (16) in a direction from the output port (20b) toward the input port (20a) in the axial direction of the spool (16). An outer diameter difference is provided between the sixth land portion (16h) and the seventh land portion (16i).

Thus, the linear solenoid valve 1 can be shortened in the axial direction while having the feedback structure, and the flow rate consumed can be reduced. Further, even if the output oil pressure Pout pulsates, the output oil pressure Pout input to the feedback oil chamber 31 can be buffered by the orifice 15d, and the fluctuation of the feedback pressure can be stabilized. Furthermore, even if the input hydraulic pressure Pin flows out to the output port 20b as a jet, the jet does not directly hit the feedback oil chamber 31 by the surrounding portion 15c, so that disturbance in feedback control can be prevented. In addition, since the input oil pressure Pin is a structure that is blocked by the sliding surface 16ba of the land portion 16b, leakage between the inner peripheral surface 15b of the sleeve 15 and the sliding surface 16ba is only a part of the circumferential direction, and the consumption flow rate is reduced. Reduction can be achieved.

Also, the linear solenoid valve (1) (for example, see FIG. 6)
The outer diameter of the seventh land portion (16i) is larger than the outer diameter of the sixth land portion (16h).

This makes it possible to provide an outer diameter difference between the land portion 16i and the land portion 16h.

Further, the linear solenoid valve (1) (for example, see FIGS. 1 to 4 and FIG. 6) is provided on the opposite side to the solenoid portion (2) with respect to the spool (16) in the axial direction. An urging member (19) for urging the spool (16) in opposition to the pressing of the plunger (10) is provided.

Accordingly, the position of the spool 16 can be controlled by the balance between the pressing of the plunger 10 and the urging force of the spring 19.

The linear solenoid valve (1) (see FIGS. 3 to 6, for example)
A first seal ring (S1) disposed on the outer periphery of the sleeve (15) and opposite to the output port (20b) with respect to the input port (20a) in the axial direction;
A second seal ring (S2) disposed on the outer periphery of the sleeve (15) and between the input port (20a) and the output port (20b) in the axial direction;
A third seal ring (S3) disposed on the outer periphery of the sleeve (15) and between the output port (20b) and the discharge port (20c) in the axial direction.

Thus, while the consumption flow rate can be reduced, the number of seal rings can be reduced and the cost can be reduced as compared with, for example, a device having a feedback port.

<Possibility of Other Embodiments>
In the linear solenoid valves 1 according to the first to fifth embodiments described above, the input port 20a and the output port 20b are disconnected when the solenoid portion 2 is not energized, and the output hydraulic pressure Pout is output from the output port 20b. The above description is of a normally closed type in which the output hydraulic pressure is in the non-output state, but the present invention is not limited to this. You may. In this case, the positional relationship in the axial direction between the solenoid portion and the spring for urging the spool is reversed, but the feedback pressure is still applied in the direction in which the input port is closed by the output hydraulic pressure. Further, in this case, the land portion at the end in the axial direction with which the spring comes into contact is disposed on the side of the solenoid portion, and a feedback port is formed between the land portion at the end and the solenoid portion. It is the same that there is no land portion to be made.

Further, the linear solenoid valve 1 according to the first to fifth embodiments has been described as being provided with the spring 19, but is not limited to this, and has no spring and controls the position of the spool only by the plunger of the valve portion. It does not matter.

In the second to fifth embodiments, an example in which a notch is not formed is described as an example. However, a notch may be formed in the same manner as in the first embodiment.

Furthermore, in the second to fifth embodiments, the case where the seal ring is disposed on the outer peripheral surface of the sleeve has been described. However, the present invention is not limited to this, and the seal ring is not disposed similarly to the first embodiment. It does not matter.

Further, in the feedback oil chamber forming portion 15F described in the third and fifth embodiments, the case where the surrounding portion 15c is formed in an annular shape to form the feedback oil chamber 31 has been described. However, the present invention is not limited to this. The shape may be any shape. For example, the same effect as the orifice is obtained by disposing the orifice 15d and disposing a slight gap between the land portion and the surrounding portion without providing the orifice 15d. Is also good.

In the first to third embodiments, the land portion 16b and the land portion 16c have been described as being separated from each other in the axial direction. However, these land portions are disposed adjacent to each other without any gap, that is, integrated. May be configured. Similarly, in the fifth embodiment, the case where the land portion 16h and the land portion 16i are arranged apart from each other in the axial direction has been described. However, these land portions are arranged adjacently without a gap, that is, integrally formed. It may be. Further, in the fifth embodiment, the case where the surrounding portion 15c is provided so as to slide over the land portion 16h and the land portion 16i has been described. However, for example, the land portion 16h is eliminated, and the surrounding portion 15c becomes the shaft portion. It may be provided so as to slide over the land 16f and the land 16i. In this case, the pressure receiving area due to the outer diameter of the land 16i is a portion where the feedback pressure acts.

Further, the structure of the linear solenoid valve 1 described in the present embodiment is not limited to the structure shown in FIG. 1 in particular, and various structures may be used as long as a structure in which a feedback pressure acts inside (inside) the output port is provided. The design can be changed.

The present linear solenoid valve can be used for an automatic transmission, a hybrid drive device, and the like mounted on a vehicle, and is particularly suitable for use in a device that requires a reduction in the axial direction and a reduction in oil consumption flow rate. .

DESCRIPTION OF SYMBOLS 1 ... Linear solenoid valve 2 ... Solenoid part 10 ... Plunger 15 ... Sleeve 15F ... Feedback oil chamber formation part 15c ... Enclosing part 15d ... Orifice 16 ... Spool 16b of FIGS. 1 to 4 ... First land part (land part)
16bb ... side view 16c of FIG. 1 thru | or 4 ... 2nd land part (land part)
16d: 3rd land part (land part)
16b in FIG. 6... Fourth land part (land part)
16c in FIG. 6—fifth land portion (land portion)
16h: 6th land part (land part)
16i: 7th land part (land part)
19 ... biasing member (spring)
20a ... input port 20b ... output port 20c ... discharge port (drain port)
Pin: input hydraulic pressure Pout: output hydraulic pressure S1: first seal ring (seal ring)
S2: Second seal ring (seal ring)
S3: Third seal ring (seal ring)

Claims

A solenoid unit that drives the plunger according to the supplied current;
A sleeve having an input port, an output port, and a discharge port, each of which is constituted by a through hole and arranged in order in the axial direction,
A spool slidably inserted into the sleeve,
The spool has a first land portion and a second land portion, and the axial position is controlled by pressing the plunger, so that the first land portion allows the input port and the output port to be connected to each other. From the first position where the output port and the discharge port are communicated by the second land portion, and the input port and the output port are communicated by the first land portion and the second land portion Movable to a second position that shuts off the output port and the discharge port;
The first land portion, when the spool is at the first position, blocks input hydraulic pressure input to the input port by a side surface on the input port side in the axial direction, and the spool is moved to the second position by the second port. By moving toward the position, the output hydraulic pressure can be adjusted by allowing the input hydraulic pressure to flow out of the output port,
The first land portion and the second land portion so that output hydraulic pressure output from the output port also acts as feedback pressure on the spool in a direction from the output port to the input port in the axial direction of the spool. With an outer diameter difference with the land,
Linear solenoid valve.
An outer diameter of the first land portion is larger than an outer diameter of the second land portion;
The linear solenoid valve according to claim 1.
The output hydraulic pressure inside the output port acts as the feedback pressure by acting on a pressure receiving area difference between the first land portion and the second land portion.
The linear solenoid valve according to claim 1.
The spool is formed inside the output port and slidably contacts the first land portion and the second land portion, and surrounds the space between the first land portion and the second land portion around the spool. An enclosing portion, and an orifice formed so as to penetrate the inside and the outside of the enclosing portion and through which the output oil pressure flows, comprising a feedback oil chamber forming portion,
The linear solenoid valve according to claim 1.
The spool has a third land portion disposed on an opposite side of the first land portion in the axial direction with respect to the second land portion and blocking leakage of hydraulic pressure discharged from the discharge port,
The third land portion is disposed at an end of a plurality of land portions including the first land portion and the second land portion,
The linear solenoid valve according to claim 1.
A solenoid unit that drives the plunger according to the supplied current;
A sleeve having an input port, an output port, and a discharge port, each of which is constituted by a through hole and arranged in order in the axial direction,
A spool slidably inserted into the sleeve,
The spool has a fourth land portion, a fifth land portion, a sixth land portion disposed at a position facing the output port, and a spool disposed at a position facing the output port, and the spool in the axial direction. And a seventh land portion disposed between the sixth land portion and the fifth land portion. The input position is controlled by the fourth land portion by controlling the axial position by pressing the plunger. From a first position in which a port and the output port are shut off and the output port and the discharge port are communicated by the fifth land portion, the input port and the output port are communicated by the fourth land portion; The fifth land portion is movable to a second position where the output port and the discharge port are shut off,
The fourth land portion, when the spool is at the first position, blocks input hydraulic pressure input to the input port by a sliding surface with the sleeve, and directs the spool toward the second position. By moving the input hydraulic pressure from the input port, the output hydraulic pressure output from the output port is configured to be adjustable,
Further, it is formed inside the output port, slidably abuts the sixth land portion and the seventh land portion, and provides a space between the sixth land portion and the seventh land portion around the spool. A feedback oil chamber forming portion having a surrounding portion to surround, and an orifice formed so as to penetrate the inside and outside of the surrounding portion to allow the output hydraulic pressure to flow,
The outer diameter of the sixth land portion and the seventh land portion is adjusted so that the output hydraulic pressure also acts as feedback pressure on the spool in a direction from the output port to the input port in the axial direction of the spool. Made a difference,
Linear solenoid valve.
An outer diameter of the seventh land portion is larger than an outer diameter of the sixth land portion;
The linear solenoid valve according to claim 6.
In the axial direction, a biasing member for biasing the spool is provided on the side opposite to the solenoid portion with respect to the spool, in opposition to the pressing of the plunger.
The linear solenoid valve according to claim 1.
A first seal ring disposed on the outer periphery of the sleeve and opposite to the output port with respect to the input port in the axial direction;
A second seal ring disposed on the outer periphery of the sleeve and between the input port and the output port in the axial direction;
A third seal ring disposed on the outer periphery of the sleeve and between the output port and the discharge port in the axial direction.
The linear solenoid valve according to claim 1.