JPS6347922B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a flow dividing and collecting valve that can perform both a flow dividing function and a flow collecting function.

BACKGROUND OF THE INVENTION For example, flow separation valves are widely used for the purpose of synchronously operating a plurality of hydraulic cylinders that drive booms of truck cranes that extend and retract in multiple stages. In order to supply hydraulic oil from one hydraulic source to multiple hydraulic cylinders and to have the multiple hydraulic cylinders operate at the same speed or at a predetermined constant speed ratio, it is necessary to supply hydraulic oil to each hydraulic cylinder. This is because it is necessary to keep constant the ratio of the flow rate of the hydraulic oil used and the flow rate of the hydraulic oil returned from each hydraulic cylinder to the tank.

Furthermore, since it is desirable that the boom expansion/contraction speed can be varied over a wide range, it is desirable that the flow dividing/collecting valve be able to perform flow dividing/collecting at an accurate ratio for a wide range of flow rates.

A flow dividing/collecting valve that can be used for such a purpose is known from Japanese Patent Laid-Open No. 74523/1983 and Japanese Utility Model Application No. 10015/1983. A flow dividing/collecting valve described in the former case is shown in FIG. 9, and a flow collector valve in the latter case is shown in FIG.

Each branch/collection valve has (a) one first port 10;
0, 2 second ports 102, spool chamber 10
4. A first liquid passage 106 and a second liquid passage 108 that connect the one first port 100 and the two second ports 102 via the spool chamber 104, respectively.
(b) A housing 110 that is slidably disposed in the spool chamber 104 and is normally held in a neutral position by two springs 112, but on pressure receiving surfaces facing oppositely to each other, Receiving the hydraulic pressure of the first hydraulic pressure chamber 114 and the second hydraulic pressure chamber 116 communicating with the first liquid passage 106 and the second liquid passage 108, when a pressure difference occurs between the two hydraulic pressure chambers, the hydraulic pressure is low. (c) a spool 118 that moves toward the hydraulic pressure chamber and changes the flow area of the first liquid passage 106 and the second liquid passage 108 so that the hydraulic pressures in both the hydraulic pressure chambers are equal;
The first liquid passage 106 and the second liquid passage 108 are provided in the portions closer to the first port 100 than the first hydraulic pressure chamber 114 and the second hydraulic pressure chamber 116, respectively, and are provided in the portions of the first liquid passage 106 and the second liquid passage 108 that are closer to the first port 100 than the first liquid pressure chamber 114 and the second liquid pressure chamber 116, respectively. First restricting means 120 and second restricting means 12 providing resistance
2. In any of the flow dividing/collecting valves, a state in which the dividing function is performed,
In the state where the flow collecting function is performed, the first hydraulic pressure chamber 114
The state of communication between the second hydraulic chamber 116 and the first liquid passage 106 and the second liquid passage 108 is switched by a pilot type switching valve 124 or 126.

In the diverting/collecting valve described in JP-A-54-74523, the hydraulic pressure in the first liquid passage 106 is equal to or equal to the liquid in the second liquid passage 108, whether it functions as a dividing valve or as a concentrating valve. When the pressure is lower than the pressure, the first hydraulic pressure chamber 114 is communicated with a portion of the first liquid passage 106 closer to the spool chamber 104 than the first throttle means 120, and the second hydraulic pressure chamber 116 is communicated with the first port 100. On the other hand, when the hydraulic pressure in the first liquid passage 106 is higher than the hydraulic pressure in the second liquid passage 108, the second hydraulic pressure chamber 116
2 is communicated with a portion closer to the spool chamber 104, and the first hydraulic chamber 114 is communicated with the first port 100. That is, when the hydraulic pressure in the first liquid passage 106 is lower than the hydraulic pressure in the second liquid passage 108, the hydraulic pressure chambers 11 on both sides of the spool 118
4, 116, the hydraulic pressure before and after the first throttle means 120 is introduced, and the hydraulic pressure in the first liquid passage 106 is guided to the second liquid passage 1
When the hydraulic pressure is higher than 08, the second throttle means 122
The hydraulic pressure before and after is guided. In a normal flow dividing valve or a flow collecting valve, the liquid pressure of the portion on the spool chamber side is guided from the throttle means of the first liquid passage and the second liquid passage to the hydraulic pressure chambers on both sides of the spool, and the spool is connected to both liquid passages. In contrast, in this branching/collecting valve, the hydraulic pressure difference itself generated by the variable throttle valves 120 and 122 operates. Since the spool 118 is actuated by the spool 118, the operating force of the spool 118 is greater than that of a normal diverter valve or collector valve, and accurate diverter ratio and collector ratio can be obtained in a relatively wide flow rate range.

On the other hand, in the dividing/collecting valve described in Utility Model Application No. 48-10015, the first throttle means 120 and the second restricting means 122 have a flow path area when the flow rate of liquid passing through the dividing/collecting valve is large. A variable throttle valve 128 is adopted, which increases the flow rate and reduces the flow path area when the flow rate is small, thereby making it possible to obtain accurate diversion and concentration ratios over a relatively wide flow rate range. There is.

Problems to be Solved by the Invention According to the above two types of flow dividing/collecting valves, a predetermined flow dividing/collecting function can be obtained even when the flow rate changes over a relatively wide range. The structure is complicated due to the use of switching valves,
There was a problem of high costs.

Means for Solving the Problem The present invention has been made to solve this problem, and includes (a) a housing having a first port, two second ports, and a first and second liquid passage. (b) a spool; and (c) a flow dividing valve having two throttling means, in which the spool is engaged with a first spool member and a second spool member so as to be able to approach and separate from each other by a certain distance in the axial direction. It shall include a spool member,
The space formed between both spool members is communicated with the first port, and the shape of the spool is
When the first and second spool members are furthest apart, when the spool moves due to the difference in hydraulic pressure between the first and second hydraulic pressure chambers, the flow of fluid in the hydraulic passage corresponding to the hydraulic pressure chamber on the side with lower hydraulic pressure occurs. When the passage area is reduced relative to the passage area of the liquid passage on the opposite side and the first and second spool members are closest to each other,
The flow area of the liquid passage corresponding to the hydraulic pressure chamber on the side where the liquid pressure is high is reduced relative to the flow area of the liquid passage on the opposite side. The variable throttle valve is configured with a variable throttle valve, and a throttle valve control means is provided to increase the flow path area of the variable throttle valve as the liquid flow rate increases at the first port. The key is to make it work as well.

Function In the flow dividing valve configured as above,
Even if the spool in which the first and second spool members move in the same direction, the spool in the extended state, that is, the spool in the extended state, and the spool in which the first and second spool members are closest to each other, in the contracted state, The direction of increase/decrease in area is reversed,
Both a flow dividing function and a flow collecting function can be obtained. In other words, the extendable and retractable spool itself performs the same function as the pilot type switching valve in the prior art.

Effects of the Invention Therefore, there is no need to provide a pilot type switching valve, and the structure of the device becomes simple, resulting in an effect of reducing manufacturing costs.

Moreover, the two throttle means are variable throttle valves controlled by the throttle valve control means, and the flow path area thereof increases as the liquid flow rate at the first port increases, so that the liquid flow rate is wide. Even when the hydraulic pressure varies over a range, it is possible to obtain accurate dividing and collecting ratios while avoiding an increase in hydraulic pressure loss, allowing multiple hydraulic actuators to operate synchronously in both forward and reverse directions, and This results in a flow splitting/collecting valve that is ideal for applications where the operating speed needs to be varied over a wide range.

Embodiments Hereinafter, some embodiments of the present invention will be described in detail based on the drawings.

Figures 1 and 2 are diagrams showing a flow divider/collector valve that can perform both a flow divider function and a flow collector function. Figure 1 shows the state in which it functions as a flow divider valve, and Figure 2 shows a flow collector valve. Indicates the state in which it is functioning as a

In FIG. 1, 2 is a housing, which is composed of a housing body 4 and auxiliary members 6, 6, and 7. The housing 2 includes one first port 8, two second ports 10, 11, and a spool chamber 12. A spool 14 is slidably fitted into the spool chamber 12. This spool 14 is axially engaged with a first spool member 16 and a second spool member 18 so as to be able to approach and separate by a distance d.
These two spool members 16,
18 is always a compression coil spring 20, 22,
22, approximately one half of the above distance. The spool 14 is fitted into the spool chamber 12 to form a first hydraulic chamber 24 and a second hydraulic chamber 26 on both sides of the spool chamber 12. Pressure chamber 2
Receives hydraulic pressure of 4,26.

The housing 2 has a first port 8 and a first hydraulic chamber 2.
4 and the second hydraulic pressure chamber 26 are provided. Two variable throttle valves 32 and 34 and a throttle valve control means 36 for controlling these are provided at the branching portion between these liquid passages 28 and 30 and the first port 8. The variable throttle valves 32 and 34 share a throttle body 38 and a throttle element 40. Throttle valve body 3
8 is a cylindrical member with both ends open, one opening concentrically communicates with the first port 8, and the other opening communicates with the inside of the spool chamber 12 through a communication hole 42 formed in the housing 2. Space 4 formed between first spool member 16 and second spool member 18
It is connected to 4. The throttle valve body 38 is press-fitted into a circular hole formed in the housing body 4.
Throttle holes 46 and 48, which are radial through holes, are formed in portions of the peripheral wall corresponding to the liquid passages 28 and 30, respectively, and have the same shape and size. These throttle holes 46 and 48 have a track-shaped cross-sectional shape in which two semicircles are connected by a rectangle, as shown in FIG. It forms a torus with a width that just covers the whole area. As is clear from FIG. 1, this throttle valve element 40 is formed integrally with an orifice member 50. The orifice member 50 is an annular member like the throttle valve 40, but the area of the central through hole is large enough to provide relatively low resistance to the liquid passing therethrough. These throttle valve element 40 and orifice member 50 are connected to each other by a cylindrical portion, and this cylindrical portion has a plurality of through holes 52 that penetrate in the radial direction.
is formed so that the liquid is also guided to the portions of the throttle holes 46 and 48 closer to the orifice member 50 than the throttle valve element 40. One compression coil spring 53 is provided on each side of the throttle valve element 40 and the orifice member 50,
These are placed in the original position, in this example, the throttle valve 4
0 is held in a neutral position where the center portions of the throttle holes 46 and 48 are closed.

The first hydraulic pressure chamber 24 and the second hydraulic pressure chamber 26 each have a plurality of holes 54 formed radially in the first spool member 16 and the second spool member 18,
An annular groove 56 formed on the inner peripheral surface of the spool chamber 12
and a second port 1 respectively by a liquid passage consisting of
Connected to 0 and 11. The opening on the annular groove 56 side of the hole 54 is arranged so that the entire opening is located within the annular groove 56 when the spool 14 is in the neutral position, but the spool 14 is located in the first hydraulic pressure chamber 24 or the second hydraulic pressure chamber. 26 side, a part of the opening of the hole 54 comes off from the annular groove 56, and the first hydraulic pressure chamber 2
4 and the second port 10 or the second hydraulic pressure chamber 26 and the second port 11, the area of the liquid passage is reduced.

The diverting/collecting valve configured as described above functions as a diverting valve when the pressure on the first port 8 side is high and the pressure on the second ports 10 and 11 is low. That is,
The liquid flowing in from the first port 8 is divided into two parts, passes through the liquid passages 28 and 30, reaches the hydraulic pressure chambers 24 and 26, and flows out from the second ports 10 and 11.

The liquid flowing in from the first port 8 is transferred to the throttle valve body 3.
8 flows in the axial direction and flows out from the restrictor holes 46 and 48 to the liquid passages 28 and 30. At this time, a pressure difference proportional to the square of the flow rate is generated before and after the orifice member 50, and this pressure difference causes The orifice member 50 then moves downward in FIG. 1 against the elastic force of the spring 53, and the throttle valve element 40 also moves downward. As a result, the portions of the throttle holes 46 and 48 that are blocked by the throttle valve element 40 change simultaneously, and as the flow rate at the first port 8 increases, the flow path areas of the variable throttle valves 32 and 34 become equal to each other. Increase while maintaining relationships. At this time, the throttle valve 40 and the variable throttle valve 32 (or 3
An example of the relationship between the pressure difference before and after 4) and the flow rate is shown in FIG. For comparison, Figure 4 shows the relationship between the flow rate and the hydraulic pressure difference in a fixed orifice with an unchanged flow rate, which is conventionally used as a restricting means, using a chain ^double -dashed ^line . It can be seen that the device of this embodiment can handle a flow rate range several times larger than that of the conventional device if the flow rate is allowed to fluctuate.

Next, the function of the spool 14 will be explained.
Now, if the liquid pressures at the two second ports 10 and 11 are equal, the spool 14 will not move from the neutral position shown in FIG. It will be discharged. However, when a difference occurs between the hydraulic pressures in the two second ports 10 and 11, for example, when the hydraulic pressure in the second port 10 becomes higher than the hydraulic pressure in the second port 11, the liquid in the first hydraulic pressure chamber 24 The pressure also becomes higher than the hydraulic pressure in the second hydraulic pressure chamber 26, and the spool 14 is moved to the second hydraulic pressure chamber 26 side where the hydraulic pressure is lower. Due to this movement, a part of the opening of the hole 54 of the second spool member 18 comes out of the annular groove 56, and the flow area of the liquid passage connecting the hydraulic pressure chamber 26 and the port 11 is reduced. This increases the throttling effect, thereby increasing the hydraulic pressure in the hydraulic chamber 26. On the other hand, on the first spool member 16 side, the hole 5
Since the entire opening of No. 4 is maintained within the annular groove 56, the flow area of the liquid passage connecting the hydraulic pressure chamber 24 and the port 10 remains unchanged, and the throttling effect remains unchanged. The movement of the spool 14 toward the second hydraulic pressure chamber 26 is performed until the hydraulic pressures in the first hydraulic pressure chamber 24 and the second hydraulic pressure chamber 26 become equal, and when the hydraulic pressures in both hydraulic pressure chambers become equal. Spool 14 stops. That is,
The spool 14 is connected to the first hydraulic pressure chamber 24 and the second hydraulic pressure chamber 26 so that the hydraulic pressure in the first hydraulic pressure chamber 24 and the second hydraulic pressure chamber 26 is kept equal regardless of the fluctuation in the hydraulic pressure in the two second ports 10 and 11.
This serves to change the flow area of the liquid passage connecting the ports 10, 11 and the ports 10, 11. In this way, the first hydraulic pressure chamber 24 and the second hydraulic pressure chamber 2
If the hydraulic pressure with 6 is maintained equal, variable throttle valve 3
Since the hydraulic pressure difference before and after valves 2 and 34 is kept equal, and the flow path areas of these variable throttle valves are made equal as described above,
The flow rates of liquid passing through these variable throttle valves are also kept equal. That is, even if there is a hydraulic pressure difference between the two second ports 10 and 11, the liquid supplied from the first port 8 is distributed to the second ports 10 and 11 by half.

Next, an explanation will be given of the operation when the flow dividing valve of this embodiment functions as a flow collecting valve. It functions as a flow collecting valve when the hydraulic pressure in the second ports 10 and 11 becomes higher than the hydraulic pressure in the first port 8. In this case, the first spool member 16 and the second spool member 18 are closest to each other as shown in FIG. First hydraulic chamber 24 and second hydraulic chamber 26
This is because the hydraulic pressure between the variable throttle valves 32 and 34 becomes higher than the hydraulic pressure in the space 44 by the difference in hydraulic pressure between the variable throttle valves 32 and 34.

Also, the orifice member 5 of the throttle valve control means 36
0 moves upward in FIG.
move upward. This direction of movement is opposite to the case where the flow diverter valve functions as described above, but the throttle valve 4
0 is the throttle hole 46 when there is no liquid flow.
and 48, and the throttle holes 46 and 48 are symmetrically shaped on both sides of this central position, so that the throttle action of the variable throttle valves 32 and 34 is exactly the same as when they function as flow divider valves. be.

Furthermore, even when the spool 14 functions as a flow collecting valve, it has the function of keeping the hydraulic pressures of the first hydraulic pressure chamber 24 and the second hydraulic pressure chamber 26 equal regardless of the hydraulic pressure difference between the second ports 10 and 11. In order to achieve this, the hydraulic pressure difference before and after the variable throttle valves 32 and 34 is kept equal. For example, two second ports 10 and 11
If the hydraulic pressure in the second port 10 increases from the state where the spool 14 is stopped at the neutral position shown in FIG. high, spool 1
4 to the second hydraulic pressure chamber 26 side. With this movement, a part of the opening of the hole 54 of the first spool member 16 comes off the annular groove 56, and the flow area of the liquid passage connecting the second port 10 and the first hydraulic pressure chamber 24 is reduced. As a result, the throttling effect increases, and the first hydraulic pressure chamber 2
4 fluid pressure decreases. On the other hand, in the second spool member 18, the opening of the hole 54 does not deviate from the annular groove 56, so the flow path area remains unchanged and the throttling effect also remains unchanged. Eventually, the spool 14 moves to a position where the hydraulic pressures in the first hydraulic pressure chamber 24 and the second hydraulic pressure chamber 26 become equal, and comes to rest. Hydraulic pressure chamber 26
If the hydraulic pressures of the variable throttle valves 32 and 3 are maintained equal,
4 is also kept equal, and the flow rate of the liquid passing through the variable throttle valves 32 and 34 despite fluctuations in the liquid pressure at the second ports 10 and 11, that is, the liquid flow rate at the ports 10 and 11. will be maintained at the same ratio as before the hydraulic pressure difference occurred.

Note that the throttle holes 46 and 48 are shaped as described above in consideration of ease of machining, and if machining becomes difficult, the variable throttle valves 32 and 48 can be used within a constant flow rate range. It is also possible to make the hydraulic pressure difference before and after 34 not substantially changed.

Furthermore, it is not essential that the two throttle holes 46 and 48 have the same shape and size, and by making them different, it is possible to set, for example, an arbitrary flow concentration ratio.

FIG. 5 shows another embodiment of the invention. In this embodiment, the throttle valve element 58 is wide enough to completely close the elongated throttle holes 60 and 62. Further, a rod 64 is extended from one end surface of the throttle valve element 58, and its tip portion passes through an auxiliary member 66 and projects to the outside of the housing 2. This protruding end portion is operatively connected to a discharge amount changing mechanism of a variable discharge displacement pump that pumps liquid to the main flow collecting valve by a coupling mechanism consisting of a lever or rod (not shown). When the discharge rate changing mechanism increases the discharge rate of the pump, the throttle valve element 58 is connected to increase the opening area of the throttle holes 60 and 62 by an amount commensurate with the increase. In this case, this connecting mechanism constitutes the throttle valve control means. Since the other parts are the same as those in the previous embodiment, the same parts are given the same reference numerals to indicate correspondence, and detailed explanation will be omitted.

Also in this embodiment, when the discharge capacity of the pump is increased and the flow rate of liquid passing through the flow dividing valve, that is, the flow rate of liquid at the first port 8 is increased, the flow path area of the variable throttle valves 68 and 70 is increased. Therefore, an increase in the hydraulic pressure difference before and after the variable throttle valves 68 and 70 is avoided, and it can be used in a wide flow rate range.

It should be noted that if the pump that pumps liquid to the dividing/collecting valve is not of the variable displacement type, the rod 64 can be connected to the accelerator operating mechanism that controls the rotational speed of the engine that is the driving source for the pump. They may be connected by a connecting mechanism. Since the rotation speed of the engine approximately corresponds to the discharge amount of the pump, the same effect as in the above embodiment is obtained by moving the throttle valve 58 by an amount commensurate with the increase in the flow rate of liquid passing through the flow dividing valve. It is possible.

Further, the variable throttle valve is not limited to one in which the throttle valve element moves in the axial direction, but may be a rotary type variable throttle valve in which the throttle valve element 72 is rotated by a shaft 74, as shown in FIG. It is also possible. Also in this embodiment, the variable throttle valves 76 and 7
8 shares a throttle valve main body 80 and a throttle valve element 72, and when the throttle valve element 72 is rotated, the flow passage area is changed at the same time. The opening areas of the throttle holes 82 and 84 formed in the throttle valve body 80 can be changed at the same time. As in the previous embodiment, the tip of the shaft 72 is made to protrude outside the housing and is operatively connected to the pump's discharge amount changing mechanism and the engine's accelerator operating mechanism.

Furthermore, as shown in FIGS. 7 and 8, if the throttle valve element 86 is capable of both rotation and axial movement, both the throttle holes 88 and 90 can be moved by the axial movement. Not only can the sum of the opening areas of the two aperture holes 8 be increased or decreased, but also the two aperture holes 8 can be
It is possible to increase the opening area of one of 8 and 90 while decreasing the opening area of the other. In other words, it is possible to make the split/concentrate ratio variable. The axial movement of the throttle valve element 86 can be controlled by the same throttle valve control means as in any of the above embodiments. Furthermore, the same effect can be obtained by moving the throttle valve main body 92 instead of moving the throttle valve element 86, or by moving one of them in the axial direction and rotating the other.

In the above embodiment, the two variable throttle valves both share the main body and the valve element, but the variable throttle valves are formed in the intermediate portions of the liquid passages 28 and 30, for example, in the two auxiliary members 6. One variable throttle valve is installed in each section, and the throttle valve elements of both variable throttle valves are rotated or moved in the axial direction in response to increases and decreases in the flow rate of liquid passing through the dividing and collecting valve. The object of the present invention can also be achieved by doing so.

In addition, it goes without saying that the present invention can be implemented with various modifications and improvements based on the knowledge of those skilled in the art without departing from the spirit of the present invention.

[Brief explanation of the drawing]

FIGS. 1 and 2 are front sectional views showing a state in which a flow dividing and collecting valve according to an embodiment of the present invention performs a flow dividing function and a state in which it performs a flow collecting function, respectively. FIG. 3 is a front view showing a part of the variable throttle valve in the above-mentioned flow dividing/collecting valve in cross section. FIG. 4 is a graph showing the operating characteristics of the flow dividing/collecting valve shown in FIGS. 1 to 3 in comparison with a conventional separating/collecting valve. FIG. 5 is a front sectional view of a flow dividing/collecting valve which is another embodiment of the present invention. FIG. 6 is a plan sectional view of a variable throttle valve in still another embodiment of the present invention. 7th
The figure is a perspective view of a variable throttle valve used in yet another embodiment of the present invention, and FIG. 8 is a plan sectional view of the variable throttle valve. FIG. 9 is a diagram showing the principle of an example of a conventional flow separation/collection valve, and FIG. 10 is a front sectional view showing another conventional flow separation/collection valve. 2: Housing, 8: First port, 10,1
1: second port, 12: spool chamber, 14: spool, 16: first spool member, 18: second spool member, 20, 22: compression coil spring,
24: First hydraulic pressure chamber, 26: Second hydraulic pressure chamber, 28,3
0: Liquid passage, 32, 34, 68, 70, 76, 7
8: variable throttle valve, 36: throttle valve control means, 38,
80, 92: Throttle valve body, 40, 58, 72, 8
6: Throttle valve, 44: Space, 46, 48, 60,
62, 82, 84, 88, 90: Aperture hole, 50:
Orifice member, 54: hole, 56: annular groove, 6
4: Rod, 74: Axis.

Claims (1)

[Claims] 1. One first port, two second ports, a spool chamber, and a first liquid that connects the one first port and the two second ports through the spool chambers. a housing having a passageway and a second liquid passageway; a housing slidably disposed in the spool chamber and always held in a neutral position by a spring; It receives the hydraulic pressure of the first hydraulic pressure chamber and the second hydraulic pressure chamber that communicate with the liquid passage and the second liquid passage, and when a pressure difference occurs between the two hydraulic pressure chambers, it moves to the hydraulic pressure chamber with lower hydraulic pressure. a spool that changes the flow area of the first liquid passageway and the second liquid passageway so that the hydraulic pressures of both the hydraulic pressure chambers are equal; and the first hydraulic pressure chamber of the first liquid passageway and the second liquid passageway; and two throttling means each provided in a portion closer to the first port than the second hydraulic pressure chamber and providing a predetermined resistance to the liquid flowing through that portion, wherein the spool is connected to a shaft. The spool member includes a first spool member and a second spool member that are engaged so as to be able to approach and separate from each other by a certain distance in the direction, and a space formed between the two spool members is communicated with the first port, and When the shape of the spool is such that the first and second spool members are furthest apart, when the spool moves due to the difference in hydraulic pressure between the first and second hydraulic pressure chambers, the hydraulic pressure on the side with lower hydraulic pressure increases. When the flow area of the liquid passage corresponding to the chamber is reduced relative to the flow area of the liquid passage on the opposite side, and the first and second spool members are closest to each other,
The flow path area of the liquid passage corresponding to the hydraulic pressure chamber on the side where the liquid pressure is high is reduced relative to the flow path area of the liquid passage on the opposite side, and the two throttle means are arranged in the flow path. It is composed of a variable throttle valve with a variable area, and is provided with a throttle valve control means that increases the flow path area of the variable throttle valve as the liquid flow rate increases at the first port, so that it can be used not only as a flow dividing valve but also as a flow concentrator. A flow dividing/collecting valve characterized in that it also functions as a valve. 2. The two variable throttle valves are provided at a branch part between the first liquid passage and the second liquid passage and share a throttle valve body and a throttle valve element, and the throttle valve body is connected to the first liquid passage and the second liquid passage. an opening communicating with one port and two throttle holes communicating with each of the first and second liquid passages, and the throttle valve element is slidably fitted within the throttle valve main body. 2. The flow dividing/collecting valve according to claim 1, which has a shape that allows the opening areas of the two throttle holes to be increased or decreased simultaneously. 3. The flow dividing/collecting valve according to claim 2, wherein the throttle valve element is rotatably fitted into the throttle valve main body, and the opening area of the throttle hole is changed by the rotation. 4. Claim 2, wherein the throttle valve element is fitted into the throttle valve body so as to be slidable in the axial direction, and the opening area of the throttle hole is changed by sliding in the axial direction. Divider/collector valve as described. 5. The throttle valve main body is a cylindrical member, a part of the cylindrical member forms at least a part of a liquid passage communicating with the first port, and the two throttle holes are formed in the peripheral wall of the cylindrical member. and the throttle valve control means includes means for applying an axial force to the throttle valve element of a magnitude corresponding to the flow rate of the liquid flowing within the cylindrical member, and the throttle valve control means is configured to set the throttle valve element in a neutral position. Claim 4, further comprising a spring that biases the throttle valve element toward the throttle valve and allows the throttle valve element to be moved from the neutral position by the axial force to change the opening area of the throttle hole. Divider/collector valve. 6. Claims in which the throttle valve control means is a connection mechanism that operatively connects the throttle valve element of the variable throttle valve and the capacity changing mechanism of a variable discharge displacement pump that pressure-feeds liquid to the flow dividing valve. Items 1 to 4
The flow dividing valve according to any of paragraphs. 7. A patent claim in which the throttle valve control means is a connection mechanism that operatively connects the throttle valve element of the variable throttle valve to an accelerator operation mechanism of an engine that is a driving source of a pump that pumps liquid to the flow dividing valve. The flow separating/collecting valve according to any one of items 1 to 4.