JP2006307977A - Pressure control valve and automatic transmission controller using it - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact and inexpensive pressure control valve having a simple configuration and reduced number of parts and to provide an automatic transmission controller using it. <P>SOLUTION: A spool 20 reciprocates and moves by command pressure P<SB>sol</SB>in a command passage 230, and amount of oil flowing from an input passage 200 to an output passage 210 is adjusted to control oil pressure in the output passage 210. The output passage 210 adds engagement oil pressure to a clutch 2. A feedback passage 220 is communicated with the output passage 210. A damper chamber 250 is formed between the spool 20 and a piston 40 and is communicated with the command passage 230. A spring 30 is arranged on the opposite side to the piston 40 for the spool 20. The piston 40 is provided on the same shaft by facing the spool 20. Travel of the piston 40 to a spool 20 side is regulated by locking in a step 18. The spool 20 is locked in the piston 40 to regulate its travel to a piston 40 side. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a pressure control valve that adjusts a flow rate of a fluid flowing from an input passage to an output passage according to a reciprocating position of a spool, and an automatic transmission control device using the pressure control valve.

Conventionally, a pressure control valve that adjusts the output pressure of the output passage by controlling the flow rate of fluid flowing from the input passage to the output passage by reciprocating a spool accommodated in the valve body so as to be reciprocally movable is known. (For example, refer to Patent Document 1).
In Patent Document 1, the piston is installed facing the spool, and the piston reciprocates according to the pressure pulsation applied between the spool and the piston, thereby reducing the pulsation of the command pressure and, as a result, the pulsation of the output pressure. Trying to reduce.

However, in Patent Document 1, an accumulator body installed in a valve body supports a piston so that the piston can reciprocate, and the accumulator body locks a spring that urges the spool in one direction of the reciprocation. Furthermore, the accumulator body restricts the movement of the piston to the spool side. As a result, in Patent Document 1, since the number of parts of the pressure control valve increases and the configuration becomes complicated, the manufacturing cost of the pressure control valve increases.
The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a pressure control valve that has a simple configuration, has a small number of parts, is small and inexpensive, and an automatic transmission control device using the pressure control valve.

According to the first to seventh aspects of the present invention, the flow rate of the fluid flowing from the input passage to the output passage is controlled by the reciprocating position of the spool, and the damper member is installed to face the spool in one of the reciprocating directions of the spool. A damper chamber is formed between the damper member.
According to this configuration, since the damper member is displaced according to the pressure pulsation in the damper chamber, the pressure pulsation in the damper chamber can be reduced. Therefore, even if pulsation occurs in the command pressure applied to the command passage, the pressure member pulsation of the command pressure can be reduced by displacing the damper member according to the pressure pulsation of the damper chamber communicating with the command passage. Thereby, the pressure pulsation of the output passage can be reduced.

In addition, since the damper member is installed facing the spool, the installation space for the spool and the damper member can be reduced as much as possible, and the pressure control valve can be downsized. Furthermore, since the configuration of the fluid passage connected to the pressure control valve can be simplified, the fluid passage can be easily processed.
Further, according to the first to seventh aspects of the present invention, the spool urging member that urges the spool toward the damper member side is disposed on the opposite side of the damper member with respect to the spool. As a result, since the spool urging member can be locked on the inner wall surface of the housing, the number of parts is reduced and the configuration of the pressure control valve is simplified. Therefore, the manufacturing cost of the pressure control valve can be reduced.

Further, since the displacement of the damper member to the spool side is regulated by the stopper formed on the inner wall surface of the housing, it is not necessary to newly install a stopper for regulating the displacement of the damper member to the spool side. As a result, an increase in the number of parts is prevented, and the configuration of the pressure control valve is simplified.
According to the second aspect of the present invention, when the pressure on the output passage side suddenly increases and the pressure on the feedback passage is applied to the spool in the direction of moving toward the damper member, the pressure on the command passage communicating with the damper chamber is quickly increased. Even if the pressure cannot be lowered, the damper member moves away from the spool and moves in the direction of increasing the volume of the damper chamber due to the pressure increase in the damper chamber, so that the spool quickly moves to the damper member side in accordance with the displacement of the damper member. When the spool moves to the damper member side, the flow rate of the fluid flowing from the input passage to the output passage is reduced, and the pressure increase on the output passage side is quickly suppressed.

According to the invention described in claim 3, since the damper member also serves as the stopper of the spool, it is not necessary to newly provide a stopper for restricting the movement of the spool toward the damper member. Therefore, the number of parts is reduced and the configuration of the pressure control valve is simplified.
According to the invention of claim 4, in the invention of claim 3, when the pressure in the damper chamber increases, the spool separates from the damper member faster than the damper member moves in the direction away from the stopper. Thereby, it is possible to prevent the spool from excessively moving toward the damper member, and to limit the reciprocating range of the spool to a predetermined range.

According to the sixth aspect of the invention, since the damper member is an elastic member that expands and contracts by the fluid pressure in the damper chamber, an urging member such as a spring that urges the damper member to the spool side becomes unnecessary. Therefore, the number of parts on the damper member side can be reduced as much as possible.
According to the seventh aspect of the present invention, since the pressure control valve according to any one of the first to sixth aspects is used in the automatic transmission control device that switches the shift by controlling the engagement and release of the plurality of friction elements, the automatic transmission control The device can be miniaturized.

  Further, in the invention according to claim 7, when the pressure applied to the friction element is increased from the output passage of the pressure control valve by using the pressure control valve according to claim 2, the friction element starts engaging. If the pressure in the output passage and the feedback passage is suddenly increased, the damper member moves in the direction of increasing the volume of the damper chamber in accordance with the movement of the spool to the damper member side. The spool quickly moves in the direction in which the fluid flow rate to the output passage decreases. Thereby, since the rapid pressure rise of an output channel is suppressed, the engagement shock of a friction element can be prevented.

Hereinafter, a plurality of embodiments showing embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
A pressure control valve according to a first embodiment of the present invention is shown in FIG. In the present embodiment, the pressure control valve 10 is used in an automatic transmission control device that controls engagement and disengagement of friction elements of the automatic transmission, and controls the hydraulic pressure applied to the clutch 2 that is a friction element.

The spool 20 and the piston 40 are accommodated in the housing 12 of the pressure control valve 10 so as to be reciprocally movable. When the diameter of the accommodation hole 14 of the housing 12 that accommodates the spool 20 is D ₁ and the diameter of the accommodation hole 16 of the housing 12 that accommodates the piston 40 is D ₂ , D ₁ <D ₂ . Therefore, a step 18 due to a diameter difference is formed between the accommodation hole 14 and the accommodation hole 16.

In the housing 12, an input passage 200, an output passage 210, a feedback passage 220, a command passage 230, and drain passages 240, 242, and 244 are formed. The input path 200, to produce the engagement pressure applied to the clutch 2, is subjected to any source pressure P _in the line pressure or the like. The output passage 210 is connected to the clutch 2 and applies a hydraulic pressure corresponding to the reciprocating position of the spool 20 to the clutch 2. The feedback passage 220 is in communication with the output passage 210. A command pressure P _sol that supports the hydraulic pressure applied to the clutch 2 from an electromagnetic valve (not shown) is applied to the command passage 230. In this embodiment, a linear solenoid valve is used as an electromagnetic valve that applies command pressure. The drain passages 240, 242, and 244 are opened to an oil pan or the like. The damper chamber 250 is formed between the spool 20 and the piston 40 and communicates with the command passage 230.

The spool 20 is formed with lands 22, 24, and 26 that slide with the inner peripheral surface of the accommodation hole 14 in this order from the piston 40 side. The lands 22, 24, and 26 are connected to each other by an axis having a smaller diameter than the lands 22, 24, and 26. In the position of the spool 20 on the left side shown in FIG. 1, the gap between the input passage 200 and the output passage 210 is sealed by the land 24, and almost no hydraulic oil flows from the input passage 200 to the output passage 210. On the other hand, as shown on the right side of FIG. 1, when the spool 20 moves downward in the direction of FIG. 1 away from the piston 40, the amount of oil flowing from the input passage 200 to the output passage 210 increases, and the pressure in the output passage 210 becomes To rise. The command pressure P _{sol in the} command passage 230 is applied to the spool 20 in the downward direction of FIG. Further, the hydraulic pressure in the feedback passage 220 is applied to the spool 20 in the upward direction of FIG. 1, that is, in the direction in which the hydraulic pressure in the output passage 210 decreases.

The spring 30 as a spool urging member is installed on the opposite side of the piston 20 with respect to the spool 20. One end of the spring 30 is locked to the spool 20, and the other end is locked to the bottom inner wall surface of the accommodation hole 14. The biasing force of the spring 30 is applied in the direction of biasing the spool 20 toward the piston 40 side.
The piston 40 as a damper member is formed in a bottomed cylindrical shape, with the bottom facing the spool 20 side. The piston 40 is restrained from moving as a displacement toward the spool 20 by being locked to the step 18 as a stopper. One end of the spring 50 is locked to the spring seat 60 and the other end is locked to the bottom inner wall of the piston 40. The spring seat 60 is formed in a plate shape, and is attached to the accommodation hole 16 across the radial direction.

Here, the cross-sectional area S ₁ of the receiving hole 14, the cross-sectional area of the receiving hole 16 when the S _2, is _{S 1 = π (D 1/} 2) 2, S 2 = π (D 2/2) 2 . Then, F ₁ the spring load of the spring 30, the spring load of the spring 50 and _{F 2, (F 1 / S} 1) <(F 2 / S 2) and so that the spring load F _1, F _2, Cross-sectional areas S ₁ and S ₂ are set

As a result, the hydraulic pressure in the damper chamber 250 rises, and the hydraulic pressure at which the spool 20 starts to move away from the piston 40 in the left side state in FIG. 1 is P ₁ , and the piston 40 from the step 18 in the left side state in FIG. Assuming that the hydraulic pressure at which movement starts in the away direction is P ₂ , P ₁ <P ₂ . Therefore, in the state on the left side of FIG. 1, when the hydraulic pressure in the damper chamber 250 increases, the spool 20 moves before the piston 40.

Next, the operation of the pressure control valve 10 will be described.
(1) When the clutch 2 is not instructed to be engaged and the command pressure P _sol is low, the spool 20 and the piston 40 are at the positions shown in FIG. The piston 40 is locked to the step 18, and the spool 20 is locked to the bottom outer wall of the piston 40. In the state shown in FIG. 2A, since the gap between the input passage 200 and the output passage 210 is sealed by the land 24, the hydraulic oil supplied to the input passage 200 hardly flows into the output passage 210. Therefore, the hydraulic pressure in the output passage 210 is almost atmospheric pressure.
(2) Next, when the command pressure P _sol rises and P ₁ <P _sol <P ₂ , the spool 20 _{resists the urging} force of the spring 30 from the piston 40 as shown in FIG. Leave. However, since P _sol <P ₂ , the piston 40 remains locked to the step 18 by the urging force of the spring 50.

Thus, since the spool 20 moves before the piston 40 in response to the increase in the hydraulic pressure in the damper chamber 250, the spool 20 is prevented from excessively protruding to the piston 40 side. Therefore, for example, as a result of excessive movement of the spool 20 toward the piston 40, it is possible to prevent the rider from returning to the original position after riding on a step near the feedback passage 220.
When the spool 20 moves to the position shown in FIG. 2B, hydraulic fluid is supplied from the input passage 200 to the output passage 210, and the hydraulic pressure in the output passage 210 increases from atmospheric pressure.

(3) When the command pressure P _sol further rises and P ₁ <P ₂ <P _sol , the piston 40 moves away from the step 18 against the urging force of the spring 50. Then, the spool 20 is so further moves the spring 30 side as shown in (C) of FIG. 2, the hydraulic pressure P _out is increased the output passage 210, substantially equal to the original pressure P _in.

Here, when the command pressure P _sol rises and the spool 20 moves to the position shown in FIG. 2B or FIG. 2C, hydraulic oil is supplied to the clutch 2. Then, when the hydraulic oil is filled in the clutch 2, the clutch 2 starts to be engaged. When the clutch 2 starts to be engaged, the hydraulic pressure in the output passage 210 and the feedback passage 220 increases. Then, the spool 20 tends to move toward the piston 40 by the hydraulic pressure of the feedback passage 220. As a result, the hydraulic pressure in the damper chamber 250 increases.

  The piston 40 moves away from the spool 20 when the hydraulic pressure in the damper chamber 250 rises and overcomes the urging force of the spring 50. As a result, the spool 20 quickly moves toward the piston 40 as the hydraulic pressure in the output passage 210 and the feedback passage 220 increases, so that the amount of oil flowing from the input passage 200 to the output passage 210 decreases. Thereby, the engaging force of the clutch 2 rises gently. Therefore, it is possible to prevent the engagement shock from occurring in the clutch 2.

  In contrast to the configuration of the first embodiment described above, in the comparative embodiment shown in FIG. 3, the spool 20 and the piston 40 are separated from each other on different axes. As described above, when the spool 20 and the piston 40 are installed on different axes, the space required for configuring the pressure control valve becomes larger than the configuration in which the spool 20 and the piston 40 are installed coaxially as in the first embodiment. In the comparative embodiment, the configuration of the oil passage connected to the spool 20 and the piston 40 is complicated.

  Further, in the configuration of the comparative form, the spool 20 is locked by the stopper 62. In order to restrict the movement of the stopper 62, for example, a member corresponding to the spring seat 60 used in the first embodiment is used. On the piston 40 side as well, a member corresponding to the spring seat 60 used in the first embodiment is used to lock the piston 40 with the stopper 62 and restrict the movement of the stopper 62.

In such a configuration of the pressure control valve of the comparative form, the pressure control valve is increased in size, the number of parts of the pressure control valve is increased, and the configuration of the pressure control valve becomes complicated.
On the other hand, in the first embodiment, since the piston 40 is installed coaxially with the spool 20 so as to face the spool 20 in one of the reciprocating directions of the spool 20, the installation space for the spool 20 and the piston 40 is made as small as possible. The pressure control valve 10 can be reduced in size.

In the first embodiment, the configuration of the oil passage connected to the pressure control valve 10 is simplified, so that the oil passage can be easily formed in the housing 12.
In the first embodiment, the movement of the piston 40 toward the spool 20 is locked by the step 18 of the housing 12, and the movement of the spool 20 toward the piston 40 is locked by the piston 40. It is not necessary to newly install the spool 20 and the stopper of the piston 40 in place of the piston 40. Therefore, the number of parts is reduced, and the configuration of the pressure control valve 10 is simplified. Therefore, the manufacturing cost of the pressure control valve 10 can be reduced.

(Second Embodiment)
A second embodiment of the present invention is shown in FIG. In addition, the same code | symbol is attached | subjected to the substantially same component as 1st Embodiment.
In the pressure control valve of the second embodiment, instead of the piston 40, the spring 50, and the spring seat 60 of the first embodiment, an elastic member 80 such as rubber constitutes a damper member. The elastic member 80 has a shape contracted to some extent, and is engaged with the step 18 and the inner wall of the bottom of the housing hole 16 of the housing 12 and is housed in the housing hole 16. The elastic member 80 is disposed coaxially with the spool 20 so as to face the spool 20 in one of the reciprocating directions of the spool 20. The step 18 of the second embodiment is formed in a tapered shape that decreases in diameter toward the spool 20. When the spool 20 is locked to the elastic member 80, the movement of the spool 20 toward the elastic member 80 is restricted.

The hydraulic pressure in the damper chamber 250 increases, and the hydraulic pressure at which the spool 20 starts moving in the direction away from the elastic member 80 in the left state in FIG. 4 is P ₁ , and the elastic member 80 moves away from the step 18 in the left state in FIG. When the hydraulic pressure begins to move in the direction P _2, such that the P ₁ <P _2, the elastic coefficient of the elastic member 80, and the spring load of the spring 30 is set.
In the second embodiment, since the elastic member 80 is used as the damper member, the spring 50 that urges the piston 40 as in the first embodiment is unnecessary. Therefore, the number of parts on the damper member side can be reduced.

(Other embodiments)
Instead of the configuration of the plurality of embodiments described above, the movement of the spool 20 toward the damper member may be locked by the inner wall surface of the housing 12 or may be locked by a newly installed stopper.
Further, the damper member may be displaced at the same time as the spool 20 or before the spool 20 in accordance with the increase in the hydraulic pressure in the damper chamber 250.

In addition, the solenoid valve that applies the command pressure to the command passage 230 may be duty-controlled. In this case, the pressure pulsation generated in the command pressure can be reduced by displacing the damper member in accordance with the pressure pulsation in the damper chamber 250, so that the pressure pulsation in the output passage 210 can be reduced.
In the above embodiments, the pressure control valve of the present invention is used as the hydraulic control valve of the automatic transmission control device. However, the pressure control valve of the present invention may be used for other devices.

It is sectional drawing which shows the pressure control valve by 1st Embodiment of this invention. It is explanatory drawing which shows the action | operation of the pressure control valve of 1st Embodiment. It is sectional drawing which shows the comparison form of 1st Embodiment. It is sectional drawing which shows the pressure control valve by 2nd Embodiment of this invention.

Explanation of symbols

2 clutch (friction element), 10 pressure control valve, 12 housing, 18 step (stopper), 20 spool, 30 spring (spool biasing member), 40 piston (damper member, movable member), 50 spring (damper biasing member) ), 80 Elastic member (damper member), 200 input passage, 210 output passage, 230 command passage, 250 damper chamber

Claims (7)

A housing having an input passage, an output passage and a command passage;
A spool that is reciprocally accommodated in the housing, reciprocates by a fluid pressure applied to the command passage, and adjusts a flow rate of fluid flowing from the input passage to the output passage according to a reciprocating position;
A damper member which is accommodated in the housing so as to face the spool in one of the reciprocating directions of the spool, forms a damper chamber with the spool, and is displaced according to the fluid pressure in the damper chamber;
A spool biasing member that biases the spool toward the damper member;
With
The damper chamber communicates with the command passage,
The spool biasing member is installed on the opposite side of the damper member with respect to the spool;
A pressure control valve, wherein a stopper for restricting displacement of the damper member toward the spool is formed on an inner wall surface of the housing.   The housing has a feedback passage communicating with the output passage, and the pressure of the feedback passage is applied in a direction in which the spool moves toward the damper member and the flow rate of fluid flowing from the input passage to the output passage decreases. The pressure control valve according to claim 1.   The pressure control valve according to claim 1 or 2, wherein movement of the spool toward the damper member is restricted by being locked to the damper member. The spool starts pressure in the direction away from the damper member against the biasing force of the spool biasing member, P ₁ , and the damper member starts displacement in the direction away from the stopper. 4. The pressure control valve according to claim 3, wherein P ₁ <P _2, where P ₂ is a pressure in the damper chamber.   5. The damper member according to claim 1, wherein the damper member is a movable member that reciprocates by fluid pressure in the damper chamber, and further includes a damper biasing member that biases the movable member toward the spool. The pressure control valve according to one item.   The pressure control valve according to any one of claims 1 to 4, wherein the damper member is an elastic member that expands and contracts due to fluid pressure in the damper chamber. In an automatic transmission control device that switches a shift by controlling engagement and release of a plurality of friction elements,
The pressure control valve according to any one of claims 1 to 6, wherein the pressure control valve controls a pressure applied to the friction element from the output passage in accordance with a pressure applied to the command passage. Transmission control device.

Images