JP3526483B2 - Flow control valve - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flow rate adjusting valve, and more particularly to a flow rate adjusting valve having a pressure compensating flow rate control function, and is preferably applied to an operating hydraulic circuit of an actuator driving switching valve of a construction machine or the like. To obtain a flow control valve.

[0002]

2. Description of the Related Art As described above, the flow rate adjusting valve of the present invention is preferably applied to an operating hydraulic circuit of an actuator drive switching valve, and so a hydraulic circuit of this type will be briefly described first. . In FIG. 7, the hydraulic circuit is basically configured such that the pilot pressure from the pilot valve 30 is supplied to the pilot lines 10 and 10 'and the flow control valve 1 with pressure compensation.
The hydraulic packs 41a, 41b of the switching valve 30 (the oil chamber 42 of
a, 42b) and operating the spool 43 of the switching valve 40, the pressure oil from the hydraulic pump 16 is discharged to the pump discharge line 16a, the actuator lines 18a, 1
The load 20 is supplied to and discharged from the actuator 18 via the 8b and the tank line 22a, and the load 20 is thereby driven.

It is known that, in the above-mentioned structure, the flow control valve with pressure compensation is provided to delay the operation speed (response operation time) of the switching valve operated by the pilot valve. If not provided for the delay,
The start and stop speed of the actuator operated by the switching valve becomes sharp, and a large shock (shock) is generated especially when stopped.
Will occur. That is, in FIG. 8, the response time t3 of the switching valve is shown as a change time t3 with respect to the pressure Pv in the hydraulic pack. This time t3 corresponds to the pilot pressure Pp shown in FIG. It is clear that there is a considerable time delay compared to the change time (pilot valve operating time) t1.

[0004]

However, the conventional device, that is, the flow rate adjusting valve (flow rate control valve with pressure compensation) in the operating hydraulic circuit has the following drawbacks.

That is, as described above, the conventional device can alleviate the shock of the actuator by delaying the response time of the switching valve. However, the control action of the flow control valve with pressure compensation in this delay operation. Compares the amount of pressure oil supplied and discharged when the actuator is started and stopped by controlling the moving speed of the switching valve spool so that the amount of pressure oil discharged from the hydraulic pack of the switching valve is a relatively small constant amount. It is configured to set a fixed amount that is relatively small. That is, the response time t3 of the switching valve is delayed by a gentle constant gradient as shown in FIG.

Therefore, in the above-mentioned conventional device, a considerable delay time is required to achieve sufficient shock relaxation, in other words, the switching valve has a considerable response delay with respect to the operation of the pilot valve. As a result, the problem that the movement of the actuator does not match the driver's sensation in the actual operation of the device (operation discomfort) has occurred. This difficulty obviously reduces the safety and operability of the entire device. In order to solve this difficulty, it is proposed to add another control valve that complements the valve characteristic to the flow control valve with pressure compensation.
This method gives rise to other drawbacks such as making the device large and expensive.

Therefore, an object of the present invention is to alleviate a shock when an actuator is stopped without causing a feeling of strangeness in operation, for example, in an operation hydraulic circuit of a construction machine or the like.
If both is to provide a flow control valve which can be made compact.

[0008]

In order to achieve the above object, a flow rate adjusting valve according to the present invention is a valve body formed in a cylindrical shape.
And the inner portion provided along the longitudinal direction at the center of the valve body.
It is fixed in the cavity, and it is long in the outer peripheral surface excluding the vicinity of both ends.
Direction passage groove and a longitudinal hole inside
The fixed sleeve and sliding inside the hole of the fixed sleeve.
A movable sleeve that is built in as much as possible and has a longitudinal hole inside.
The slide and the movable sleeve are installed so that they can slide within the hole.
The outer peripheral surface is formed into a substantially cylindrical shape with one end closed.
A mantle with a longitudinal passage groove in the
Pressure with a throttle provided in the middle of the oil chamber provided in the direction
A flow controller with force compensation and an opening on one end face of the valve body
The rear chamber that communicates with the passage groove provided on the outer peripheral surface of the outer jacket.
A first end formed with, and opened at the other end of the valve body,
Before communicating with the passage groove provided on the outer peripheral surface of the fixed sleeve
Inflow of oil from the front chamber with the second end formed chamber
Only when moving the flow controller with pressure compensation in the inflow direction
Accordingly, the outer peripheral surface of the mantle part of the flow control part with pressure compensation is
Opening / closing connection in which the groove passage connects the front chamber and the rear chamber.
By the touch part, the fixed sleeve and the movable sleeve,
The flow rate is variable only when the oil flows from the rear chamber.
Of the variable throttle part that controls the
A passage hole that connects the passage groove and the internal oil chamber is formed.
The flow rate is controlled to be constant only when the oil flows from the rear chamber.
Control orifice and the movable sleeve to the variable throttle.
The first spring that urges the spring in the direction in which the
Direction of opening the opening / closing contact part of the flow control part with force compensation
A second spring for urging the
To the chamber, make sure that the opening / closing contact is always fully open and oil is
From the chamber to the opening / closing contact part and the flow control part with pressure compensation.
While flowing through the passage groove provided on the outer peripheral surface, from the rear chamber
A constant flow rate was passed from the beginning of the oil flow to the front chamber.
Pass through the control orifice of the flow rate controller with pressure compensation
In addition to the flow rate, the opening degree is large at the beginning of oil flow.
As the time elapses, the opening moves toward full closure.
From the rear chamber to the front through the variable throttle
The oil passes through the passage groove provided on the outer circumference of the fixed sleeve.
By doing so, the flow rate of oil changes with time,
And the rear chamber and the front chamber
Arrangement in which the oil flow in the chamber is in the direction along the axial direction
It is characterized by being . In addition, the flow rate control according to the present invention
The valve is a tubular valve body and the central portion of the valve body.
It is fixed in the lumen provided along the longitudinal direction.
Provide a passage groove in the longitudinal direction on the outer peripheral surface excluding the vicinity of the end,
A fixing sleeve with a longitudinal hole inside
Built in to allow sliding in the hole of the fixed sleeve,
A movable sleeve having a longitudinal hole, and the movable sleeve
-Provided to be slidable in the hole of the hub and closed at one end
Is formed in a substantially cylindrical shape and has a longitudinal passage groove on the outer peripheral surface.
In the middle of the cloaked section and the oil chamber provided in the center in the longitudinal direction.
A flow controller with pressure compensation having a throttle provided in
Open on one end surface of the valve body, and on the outer peripheral surface of the outer jacket portion.
A first end portion having a rear chamber communicating with the provided passage groove
And an opening at the other end of the valve body, the outer periphery of the fixed sleeve
Second end formed with an anterior chamber communicating with a passage groove formed in the surface
And the pressure-compensated flow only when oil flows from the front chamber
According to the movement of the quantity control section in the inflow direction, the flow with the pressure compensation
The groove passage on the outer peripheral surface of the outer cover portion of the quantity control unit and the front chamber
An opening / closing contact portion that communicates with the rear chamber, and the fixed three
A rear chamber and a movable sleeve.
Variable throttle that variably controls the flow rate only when these oils flow in
And the oil inside the passage groove and the inside of the flow controller with pressure compensation.
Oil from the rear chamber, which is composed of a passage hole communicating with the chamber.
Control orifice that controls the flow rate to a constant value only when the inflow of
And the one in which the variable throttle part closes the movable sleeve.
A first spring for urging in the opposite direction, and the flow controller with pressure compensation
Urging the opening / closing contact part in the direction of opening
Pressure increases as the pressure moves to the front chamber side of the movable sleeve.
And a second spring configured to
From the rear chamber to the rear chamber with the opening / closing contact section always fully open.
Is the flow rate from the front chamber to the opening / closing contact part and the pressure compensation
While flowing through the passage groove provided on the outer peripheral surface of the control unit,
From the rear chamber to the front chamber, a constant flow rate from the beginning of oil flow
Control orifice of the flow controller with pressure compensation to pass
In addition to the flow rate passing through the section, at the beginning of the oil flow, its opening degree
Is large, and its opening becomes fully closed as time passes.
The variable throttle section and the opening / closing contact section that decrease toward
Provided on the outer periphery of the fixed sleeve from the rear chamber via
The oil flow rate by passing the oil into the passage groove
Can be configured to decrease over time.
In addition, the oil flow in the rear chamber and the oil flow in the front chamber are both
It is characterized in that the arrangement is along the direction.

[0009]

[0010]

[0011]

The flow rate adjusting valve of the present invention is formed between this control section and the valve body in addition to the original pressure compensating flow rate control section arranged in the central portion of the valve body, and is provided on the rear chamber side. It has a variable throttle part which further adjusts the passage control flow rate by the said control part according to a fluid pressure. Therefore, when this flow rate adjusting valve is applied to the operation hydraulic circuit of the actuator driving switching valve, the discharge pattern of the pressure oil in the switching valve hydraulic pack is such that the variable throttle section changes the throttle opening degree as described above. Since the pressure is adjusted according to the fluid pressure on the chamber side, the transition from the initial rapid discharge region to the final slow discharge region is performed. In other words, the stopping operation of the actuator is changed from the rapid operation to the low speed operation. Therefore, according to the present invention, the response time of the switching valve is shortened to eliminate the uncomfortable feeling of operation, and at the same time, the stopping operation of the actuator is buffered, and the shock at the time of stopping is sufficiently mitigated. Further, since the flow rate adjusting valve has both the control and variable throttle parts integrally formed in the valve body, it is obvious that the structure thereof can be made compact.

[0012]

Embodiments of the flow rate adjusting valve according to the present invention will be described in detail below with reference to the accompanying drawings. For convenience of explanation, the same components as those of the conventional structure shown in FIGS. 7 and 8 are designated by the same reference numerals, and detailed description thereof will be omitted.

In FIG. 1, the flow rate adjusting valve of the present invention is
FIG. 8 shows a case where the present invention is applied to an operating hydraulic circuit of the conventional actuator drive switching valve shown in FIG. 7. Note that, in FIG. 1, since the operating hydraulic circuit is symmetrical, only the left half part thereof is shown, and the part including the hydraulic pump and the actuator is not shown. That is, the hydraulic circuit
Basically, the pilot pressure from the pilot valve 30 is introduced into the oil chamber 42a of the hydraulic pack 41a of the switching valve 30 via the pilot line 10, the flow rate adjusting valve 50 and the pilot line 14, and the spool 43 of the switching valve 40 is introduced. By operating the, the pressure oil from the hydraulic pump 16 (see FIG. 7) is supplied to and discharged from the actuator 18 to drive the load 20.

However, the flow rate control valve 50 of the present invention applied to the hydraulic circuit is basically a flow rate control unit with pressure compensation in which the spring pressure of the spring 52a arranged in the central portion of the valve body 51 is loaded. 52, and a variable throttle unit 53 formed between the control unit 52 and the valve body 51 and adjusting the opening degree in accordance with the fluid pressure Pv on the rear chamber 57 side of the valve body 51. Thus, the fluid flow rate when passing from the rear chamber 57 side of the valve body 51 to the front chamber 56 side is controlled via the control unit 52 and the variable throttle unit 53, and is further adjusted. Before further describing the flow rate adjusting valve 50, the pilot valve 30 and the switching valve 40 of the present invention having such a configuration will be briefly described below.

First, the operation of the pilot valve 30 will be described. When the lever 30a rotates to the left side in the drawing, the cap 31 descends to compress both springs 32a and 32b, and the spring 32a moves the spool 33 downward. And the other opening / closing portion 34b is opened, whereby the pilot line 10 is closed by the pilot pump 35.
Connected to.

On the other hand, at this time, the pressure oil from the pilot pump 35 passes through the in-spool passage 33a in the pilot valve 30 and is also introduced into the oil chamber 36, which causes the spool 33 to move upward, contrary to the above. The opening / closing portion 34b is pushed up (pushed back) to close the opening / closing portion 34b, and the opening / closing portion 34a is opened. Then, finally, the spool 33 is balanced at a position where the pushing-down force due to the spring pressure of the spring 32a acting on the spool 33 and the pushing-up force due to the oil chamber 36 pressure are balanced. That is, as shown in FIG. 3, the spring 32a is compressed corresponding to the operation angle θ of the lever 30a, and the oil chamber 36 is proportional to the spring pressure of the spring 32a.
The internal pressure (pressure in the pilot line 10) Pp is automatically set via the spool 33.

Next, as described above, the changeover valve 40 has the pilot pressure introduced into the oil chamber 42a of the hydraulic pack 41a (specifically, the oil chamber 4 generated thereby).
The spool 43 is operated via the pressure Pv in 2a. In this case, the spool 43 compresses the spring 44a (44b) in the oil chamber from the neutral position shown in the drawing, thereby stopping the stopper 45a. It is configured to move between the maximum strokes Lmax regulated by (45b).

Therefore, the flow rate adjusting valve 50 will be further described below. Here, the flow rate adjusting valve 50 is composed of a pressure compensating flow rate control section 52 and a variable throttle section 53, and the former is a normal pressure compensating section. As described above, the flow control valve is constituted. Therefore, the following description is limited to the latter. That is, the variable throttle portion 53 is formed between the valve element 51 and the pressure-compensated flow rate control portion 52, as described above. Here, the flow rate adjustment valve 50 includes the outer jacket portion 52 b of the control portion 52. The spring 54 is provided from the front chamber 56 side toward the rear chamber 57 side so as to be liquid-tightly contacted with the control portion 52, provided on the outer peripheral portion of [see also FIG. 2 (a)].
The movable sleeve 54, to which the spring force of a is applied, and the outer peripheral portion of the movable sleeve 54. The movable sleeve 54 is fixed to the valve body 51 so as to keep the movable sleeve 54 slidably and liquid-tightly at the interval l. And a fixed sleeve 55. Further, the variable throttle portion 53 is formed by, for example, two passage holes 55a and 55b on the fixed sleeve 55 on the sliding surface of the movable sleeve 54 and the fixed sleeve 55. Reference numeral 5 in the figure
Reference numeral 8 indicates a stopper.

Therefore, the operating hydraulic circuit according to the present invention operates as follows. That is, first, when the lever 30a of the pilot valve 30 is operated to drive the actuator and the pilot pressure oil is sent to the pilot line 10, the pressure oil first reaches the flow rate adjusting valve 50 and the inner diameter hole of the stopper 58 thereof. To the front chamber 56, and the outer cover 52b of the control unit is moved to the right from the illustrated state by a distance l to open the open / close contact unit 52c, thereby opening / closing the open / close unit 52c and the passage groove 52d. And through the passage hole 52e and flows into the rear chamber 57 [see the solid arrow in (a) of FIG. 2]. Then, this pressure oil further reaches the switching valve 40 via the pilot line 14, and the spool 43
As described above, is moved to and from the actuator by moving during the maximum stroke Lmax corresponding to the pilot pressure (pressure Pv in the oil chamber 42a). That is, the actuator is driven.

In such a state, the pilot valve 30 is returned to the neutral position in order to stop the actuator (here, the switching valve spool 4 in the above state).
3 has moved the full stroke Lmax, and pilot valve 3
If it is assumed that the return of 0 is operated suddenly), the pilot valve 30 is connected to the tank line 22a, and the pressure in the pilot line 10 (pilot pressure Pp) suddenly disappears. The regulating valve 50 operates as follows. That is, in the flow rate adjusting valve 50, the pressure in the front chamber 56 (the pilot pressure Pp) is
As described above, the pressure in the rear chamber 57 (the pressure Pv in the switching valve oil chamber 42a) gradually decreases while the pressure rapidly decreases as described above (this will be described later). After moving to the left side in the drawing once against the spring pressure of the spring 54a, it returns to the position shown in the drawing as the pressure in the rear chamber 57 decreases. At this time, the pressure-compensated flow rate control unit 52 (the outer cover 52b thereof) has already returned to the illustrated position (the position where the opening / closing contact part 52c is closed) against the spring pressure of the spring 52a. Therefore, in the above process, the pressure oil in the oil chamber 42a of the switching valve 40 is directed toward the front chamber 56 side from the rear chamber 57 side of the flow rate adjusting valve 50 as the spool 43 returns to the neutral position, and its pressure compensation is performed. It is discharged via the attached flow rate control unit 52 and the variable throttle unit 53.

Such discharge is set to a relatively small, substantially constant amount in one of the pressure compensation flow rate control units 52, which passes through the passage hole 52c '[see the dotted arrow in FIG. 2 (a)]. However, in the other variable throttle portion 53, both the passage holes 55a and 55b (and the passage groove 55c, the opening portion 55).
The initial large discharge amount passing through d) is gradually reduced to the middle discharge amount passing through only one passage hole 55b to the final zero discharge amount at which both passage holes are closed. A passage hole 52c 'provided in the pressure compensating flow rate controller 52 is provided.
As shown in FIG. 2B, the outer peripheral portion of the outer jacket portion 52b is flattened to form passage grooves 52d, and the passage holes 52c 'are formed in a part of the flat passage grooves 52d. Is formed by opening one end of the.

Therefore, the flow rate control unit 5 with pressure compensation.
It is clear that the pressure oil discharge pattern passing through 2, 53 (that is, the flow rate control valve 50) shifts from the initial rapid discharge region to the final slow discharge region. That is, FIG.
Is the pressure P in the oil chamber of the switching valve 40.
The response (actuation) time t2 regarding v is shown to correspond to the above-mentioned conventional response time t2 (see FIG. 8). As can be seen from these, the response time t2 is considerably shortened as a whole. Also, the pressure Pv in the oil chamber is terminated sufficiently slowly at the end thereof.

Therefore, according to the operating hydraulic circuit of the present invention, the response time of the switching valve is shortened to eliminate the uncomfortable feeling of operation, and at the same time, the stopping of the actuator is buffered.
The shock at the time of stopping is also sufficiently reduced. Further, in the flow rate adjusting valve of the present invention, it is obvious that the structure thereof is made compact because the control and the pressure compensating flow rate control section of the variable throttle are integrally formed in the valve body.

FIG. 6 shows another embodiment of the flow rate adjusting valve according to the present invention. Flow control valve 50 'of this embodiment
In the flow rate adjusting valve 50 of the previous embodiment, the spring pressure of the spring 52a loaded on the pressure compensating flow rate control unit 52 is increased in accordance with the movement of the movable sleeve 54 to the front chamber 56 side. In addition, one end thereof is configured to be locked to the stopper 58. With this configuration, the rear chamber 5
The amount of pressure oil when being discharged from the 7 side to the front chamber 56 side is also in the pressure compensation flow rate control unit 52 according to the decrease in the pressure in the rear chamber 57 (from the initial stage to the final stage of discharge). Since it can be reduced steplessly, the shock when the actuator is stopped can be further alleviated.

Although the preferred embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and many design changes can be made without departing from the spirit thereof. For example, the number and shape of the passage holes forming the variable throttle portion can be set differently from those in the above-described embodiment. Further, it goes without saying that the flow rate control valve of the present invention can be applied to other various hydraulic circuits other than the operating hydraulic circuit.

[0026]

As described above, the flow rate control valve according to the present invention has a tubular valve body and a central portion of the valve body.
Fixed in the lumen provided along the longitudinal direction of the
The outer peripheral surface excluding the vicinity of both ends is provided with a passage groove in the longitudinal direction,
And a fixing sleeve with a longitudinal hole inside,
Built-in to allow sliding in the hole of the fixing sleeve,
A movable sleeve having a hole in the longitudinal direction, and the movable sleeve.
It is provided so that it can slide in the hole of the rib and one end is closed.
Formed in a substantially cylindrical shape and has a longitudinal passage groove on the outer peripheral surface.
The outer cover provided and the oil chamber provided in the center in the longitudinal direction.
Flow control unit with pressure compensation having a throttle provided therein
And an outer periphery of the outer jacket portion that opens at one end surface of the valve body.
First end formed with a rear chamber communicating with a passage groove formed in the surface
And an opening at the other end of the valve body and outside the fixed sleeve.
A second chamber having a front chamber communicating with the passage groove provided on the peripheral surface.
With pressure compensation only at the end and when oil flows in from the front chamber
With the pressure compensation according to the movement of the flow controller in the inflow direction
The groove passage on the outer peripheral surface of the outer jacket of the flow rate control unit is the front chamber.
And an opening / closing contact portion that connects the rear chamber to the fixed chamber,
And the movable sleeve, the rear chamber
Variable throttle that variably controls the flow rate only when oil flows in from
And the oil inside the passage groove and the inside of the flow controller with pressure compensation.
Oil from the rear chamber, which is composed of a passage hole communicating with the chamber.
Control orifice that controls the flow rate to a constant value only when the inflow of
And the one in which the variable throttle part closes the movable sleeve.
A first spring for urging in the opposite direction, and the flow controller with pressure compensation
The second bar for urging the opening / closing contact portion in the direction of opening.
The opening / closing connection from the front chamber to the rear chamber.
When the contact is always fully open, the oil is
Touch part, passage provided on the outer peripheral surface of the flow controller with pressure compensation
Oil flows from the rear chamber to the front chamber while flowing through the groove.
The pressure-compensated flow for passing a constant flow rate from the beginning
In addition to the flow rate passing through the control orifice section of the quantity control section,
The opening is large at the beginning of the oil flow, and as time passes
Therefore, it is possible that the degree of opening decreases toward full closure.
Outer circumference of the fixed sleeve from the rear chamber through the variable throttle
By passing oil to the passage groove provided in
Configure the oil flow rate to decrease over time
At the same time, the flow of oil in the rear chamber and the front chamber
It is also characterized by being arranged along the axial direction
By, applying this flow control valve, for example, operating a hydraulic circuit of the actuator driving switch valve or the like, the discharge pattern of the pressure oil in the selector valve is shifted from the initial rapid emptying area to slow the discharge region of the end It Therefore, the response time of the switching valve is shortened to eliminate the uncomfortable feeling of operation, and at the same time, the stopping operation of the actuator is buffered, and the shock at the time of stopping is sufficiently alleviated. Further, the flow rate adjusting valve of the present invention,
Since both the control part and the variable throttle part are integrally formed in the valve body, there is an advantage that the structure can be made compact.

[Brief description of drawings]

FIG. 1 is a main part system diagram showing an embodiment of an operating hydraulic circuit to which a flow rate adjusting valve according to the present invention is applied together with a sectional structure of the valve.

2A is a partial enlarged cross-sectional view of the flow rate adjusting valve shown in FIG. 1, and FIG. 2B is a B- of the flow control unit with pressure compensation shown in FIG.
It is a B line sectional view.

FIG. 3 is a graph showing a relationship between a lever operation angle θ of the pilot valve shown in FIG. 1 and a pilot pressure Pp.

FIG. 4 is a graph showing an operation time t1 related to the pilot pressure Pp when the driving of the pilot valve shown in FIG. 1 (or FIG. 7) is stopped.

5 is a graph showing a response time t2 with respect to the pressure Pv in the oil chamber when the switching valve shown in FIG. 1 is stopped.

FIG. 6 is a sectional view of an essential part showing another embodiment of the flow rate control valve according to the present invention.

FIG. 7 is a circuit diagram corresponding to FIG. 1 showing a conventional operating hydraulic circuit.

8 is a graph showing a response time t3 regarding the pressure Pv in the oil chamber when the switching valve shown in FIG. 7 is stopped.

[Explanation of symbols]

10,14 Pilot line 22 tanks 22a tank line 30 pilot valve 30a operating lever 31 cap 32a, 32b spring 33 spools 33a passage 34a, 34b opening / closing part 35 Pilot pump 36 oil chamber 40 switching valve 41a hydraulic pack 42a Oil chamber 43 spool 44a spring 45a stopper 50, 50 'Flow control valve 51 valve body 52 Flow controller with pressure compensation 52a spring 52b mantle 52c Open / close contact part 52c 'passage hole 52d passage groove 52e passage hole 53 Variable diaphragm 54 Movable sleeve 54a spring 55 Fixed sleeve 55a, 55b passage holes 55c passage groove 55d opening 56 anteroom 57 Rear room 58 stopper

Front page continuation (58) Fields surveyed (Int.Cl. ⁷ , DB name) F16K 17/18-17/34 F15B 11/00-11/22

Claims (2)

(57) [Claims] 1. A valve body formed in a tubular shape, and a lumen provided in a central portion of the valve body along a longitudinal direction.
It is fixed to the outer peripheral surface excluding the vicinity of its both ends in the longitudinal direction.
A solid structure with a passage groove and a longitudinal hole inside.
The fixed sleeve and the fixed sleeve are built in so that they can slide within the holes.
A movable sleeve having a hole in the longitudinal direction, and a movable sleeve provided so as to be slidable within the hole.
It is formed in a substantially cylindrical shape with closed ends and is formed on the outer peripheral surface in the longitudinal direction.
With a passage groove and a throttle provided in the middle of a longitudinal oil chamber in the center
And a flow rate control unit with pressure compensation having an opening on one end face of the valve body, and an outer peripheral surface of the mantle part.
A first end portion having a rear chamber communicating with the provided passage groove
And open at the other end of the valve body, and on the outer peripheral surface of the fixed sleeve.
Second end formed with an anterior chamber communicating with the provided passage groove
And the flow control with pressure compensation only when oil flows from the front chamber
Flow control with pressure compensation according to the movement of parts in the inflow direction
Of the outer circumferential surface of the outer portion of the groove portion, the groove passage is provided in the front chamber and the rear chamber.
An open / close contact portion for communicating with the chamber, and the fixed sleeve and the movable sleeve.
The flow rate is variably controlled only when the oil flows from the rear chamber.
A variable throttle part, the passage groove of the flow control part with pressure compensation, and an internal oil chamber.
Oil passage from the rear chamber.
The control orifice that controls the flow rate only when the valve is turned on and the movable sleeve in the direction in which the variable throttle is closed.
With the first spring for urging and the flow control unit with pressure compensation, the opening / closing contact unit is opened.
A second spring for urging the opening / closing contact portion from the front chamber to the rear chamber.
In the state of oil, oil from the front chamber, the opening and closing contact portion, the pressure
Flow through the passage groove provided on the outer peripheral surface of the flow controller with compensation
On the other hand, from the rear chamber to the front chamber, the flow of oil will start from the beginning.
Control of the flow controller with pressure compensation for passing a constant flow rate
In addition to the flow rate passing through the orifice,
Has a large opening, and opens over time.
Through the variable throttle part where the degree decreases toward full closure
From the rear chamber to the outer circumference of the fixed sleeve.
The oil flow rate can be increased by passing the oil through the groove.
It is configured to decrease with the progress of
The oil flow in the rear chamber and the oil flow in the front chamber both follow the axial direction.
Flow rate control characterized by an arrangement that is in the opposite direction
valve. 2. A valve body formed in a tubular shape, and an inner lumen provided in a central portion of the valve body along a longitudinal direction.
It is fixed to the outer peripheral surface excluding the vicinity of its both ends in the longitudinal direction.
A solid structure with a passage groove and a longitudinal hole inside.
The fixed sleeve and the fixed sleeve are built in so that they can slide within the holes.
A movable sleeve having a hole in the longitudinal direction, and a movable sleeve provided so as to be slidable within the hole.
It is formed in a substantially cylindrical shape with closed ends and is formed on the outer peripheral surface in the longitudinal direction.
With a passage groove and a throttle provided in the middle of a longitudinal oil chamber in the center
And a flow rate control unit with pressure compensation having an opening on one end face of the valve body, and an outer peripheral surface of the mantle part.
A first end portion having a rear chamber communicating with the provided passage groove
And open at the other end of the valve body, and on the outer peripheral surface of the fixed sleeve.
Second end formed with an anterior chamber communicating with the provided passage groove
And the flow control with pressure compensation only when oil flows from the front chamber
Flow control with pressure compensation according to the movement of parts in the inflow direction
Of the outer circumferential surface of the outer portion of the groove portion, the groove passage is provided in the front chamber and the rear chamber.
An open / close contact portion for communicating with the chamber, and the fixed sleeve and the movable sleeve.
The flow rate is variably controlled only when the oil flows from the rear chamber.
A variable throttle part, the passage groove of the flow control part with pressure compensation, and an internal oil chamber.
Oil passage from the rear chamber.
The control orifice that controls the flow rate only when the valve is turned on and the movable sleeve in the direction in which the variable throttle is closed.
With the first spring for urging and the flow control unit with pressure compensation, the opening / closing contact unit is opened.
The spring pressure to the movable chamber front chamber side.
A second bar configured to increase in response to movement.
The opening / closing contact section is always fully opened from the front chamber to the rear chamber.
In the state of oil, oil from the front chamber, the opening and closing contact portion, the pressure
Flow through the passage groove provided on the outer peripheral surface of the flow controller with compensation
On the other hand, from the rear chamber to the front chamber, the flow of oil will start from the beginning.
Control of the flow controller with pressure compensation for passing a constant flow rate
In addition to the flow rate passing through the orifice,
Has a large opening, and opens over time.
The variable throttle section whose degree decreases toward full closure and
From the rear chamber to the outside of the fixed sleeve through the opening / closing contact portion.
By passing the oil through the passage groove provided on the circumference,
Configured to reduce the oil flow rate over time
At the same time, the flow of oil in the rear chamber and the front chamber,
All of them are arranged along the axial direction.
Flow control valve to be used.