JPH073271B2 - Flow controller - Google Patents

Description

TECHNICAL FIELD The present invention relates to a flow rate control device for controlling the flow rate of a fluid flowing in a fluid passage, for example, a water amount control device for controlling the amount of water supplied to a heat exchanger for a water heater. Alternatively, the present invention relates to a flow rate control device suitable for use in a fuel amount control device that controls the amount of fuel supplied to a burner.

[Prior Art] Conventionally, as a flow rate control device, for example, there is a water amount control device that controls the amount of water supplied to a heat exchanger for a water heater.

Such a water amount control device 100, as shown in FIG.
Control chamber 111, axial fluid passage 112 and radial fluid passage 11
A housing 110 having three, a valve body 120 slidably supported by the housing 110, which reciprocates in the axial direction while rotating in the control chamber 111, and a threaded movable sleeve connected to the valve body 120. A gear motor (not shown) for rotating the valve element 120 to reciprocally move the valve element 120 in the axial direction.

In this water amount control device 100, the valve body 120 is reciprocally displaced by a gear motor to change the degree of communication between the axial fluid passage 112 and the radial fluid passage 113 via the control chamber 111, that is, the opening area of the fluid passage. It controls the amount of water.

It should be noted that the water amount control device 100 axially moves the valve head 121 of the valve body 120 in the axial direction when, for example, reducing the amount of water flowing from the radial fluid passage 113 into the control chamber 111 and causing the water to flow out to the axial fluid passage 112. Power is added to.

The water pressure of the water flowing in the radial fluid passage 113 is P ₁ , the water pressure of the water flowing in the axial fluid passage 112 is P ₂ , the cross-sectional area of the valve rod portion 122 of the valve body 120 is S ₁ , the valve head of the valve body 120. When the cross-sectional area of 121 is S ₂ , the formula of the axial load of the valve body 120 when the valve body 120 is stopped is W ₁ = P ₁ × (S ₂ −S ₁ ) …… right figure Axial load applied in the direction W ₂ = P ₂ × S ₂ …… Axial load applied in the left direction in the figure [Problems to be solved by the invention] However, when the water amount control device 100 reduces the water amount, Since the water pressure P ₁ is significantly larger than the water pressure P ₂ , the axial load W ₁ applied to the valve head 121 of the valve body 120 in the right direction in the figure is significantly larger than the axial load W ₂ applied in the left direction in the figure. The valve body 120 becomes larger and the valve body 120 is pushed rightward in the drawing. Therefore, the water amount control device 100 starts the valve body 120 from the state where the water amount is reduced.
There is a problem in that the valve body 120 cannot be easily moved because a large force is required when the water amount is increased by shifting it to the left in the drawing.

Further, in the conventional water amount control device 100, when the water flows through the axial fluid passage 112 and the radial fluid passage 113, the valve head 121 and the housing 110 provided at the tip of the valve rod portion 122 of the valve body 120. Since the water flows only through one communication passage formed between and, the passage resistance when water passes through the communication passage is large, and the maximum flow rate value cannot be taken. There was also a problem. Furthermore, in order to increase the value of the maximum flow rate, it is necessary to increase the size of the above-mentioned communication passage, which causes a problem of increasing the size of the water amount control device 100.

An object of the present invention is to provide a flow rate control device capable of smoothly moving the displacement means with a small force by counteracting and counteracting a reverse axial load applied to the valve body when the flow rate is reduced. It is in.

Further, the object of the present invention is to reduce the passage resistance of the fluid,
It is an object of the present invention to provide a flow rate control device capable of setting a large flow rate value of the maximum flow rate and preventing an increase in size even if a large flow rate value of the maximum flow rate is set.

[Means for Solving the Problem] A flow rate control device of the present invention includes a control chamber in which a flow rate of a fluid is controlled, and a first fluid passage which is provided adjacent to the control chamber in the radial direction and is always in communication with the control chamber. , And a housing having a second fluid passage that is adjacent to one side of the control chamber in the axial direction and that communicates with the first fluid passage through the control chamber, and is slidably supported by the housing. The flow rate control device includes a displacement unit that axially reciprocates in the control chamber, and a drive unit that axially reciprocally drives the displacement unit.

The housing is adjacently provided on the opposite side to the second fluid passage side in the axial direction of the control chamber, and communicates with the first fluid passage via the control chamber, the pressure equalizing chamber, and the displacement means. Is provided so as to project from the control chamber and the second fluid passage when seated, and to project inward from the inner circumference, and when the displacement means sits, the control chamber and the pressure equalizer are provided. It has a 2nd division part which divides with a room.

Further, the displacement means is a valve body in which a communication hole that always communicates the pressure equalizing chamber and the second fluid passage is formed, and the valve body is the first partitioning portion only at a minimum flow rate. Is substantially seated on the other side, and the others are provided so as to project outward from the first valve part that opens the first partition part and the outer periphery, and is substantially seated on the second partition part at the minimum flow rate, and at least at the maximum flow rate. It has a 2nd valve part which opens the 2nd division part.

It should be noted that the opening time and the closing time of the first partition and the second partition may be shifted.

[Operation] By displacing the valve body in the axial direction by the drive means, the first and second valve portions of the valve body are separated from the first and second partition portions of the housing, and the first fluid passage is provided via the control chamber. And the second
The fluid passage communicates with each other, and the first fluid passage and the second fluid passage communicate with each other through the control chamber, the pressure equalizing chamber, and the communication hole. Therefore, the fluid path in the housing is the fluid path that flows through the first fluid passage, the control chamber, and the second fluid passage, and the first fluid passage,
Two passages are formed such as a control chamber, a pressure equalizing chamber, a communication hole, and a fluid passage that flows through the second fluid passage. As a result, as compared with the case where only one fluid flow path is formed in the housing, even if the valve element is axially displaced by the same displacement amount, the fluid that passes through the fluid path The passage resistance is reduced and a large amount of fluid flows in the housing.

When the flow rate of the fluid is minimized, the first valve portion of the valve body is substantially seated in the first partition portion of the housing to partition the control chamber and the second fluid passage, and the valve is provided in the second partition portion of the housing. Since the second valve portion of the body is substantially seated and the control chamber and the pressure equalizing chamber are partitioned, both fluid paths in the housing are shut off, and almost no fluid flows in the housing, and the flow rate becomes the minimum.

At this time, a load in the axial direction is applied to the valve body by the pressure in the first fluid passage and the pressure in the second fluid passage, but the pressure equalizing chamber and the second fluid passage are formed through the communication hole formed in the valve body. And are in communication. Therefore, the pressure in the pressure equalizing chambers on both sides of the valve body in the axial direction and the pressure in the second fluid passage are substantially the same, so that the loads applied to the valve body from both sides in the axial direction are canceled out, and Almost no axial load is applied to the body.

[Advantages of the Invention] By forming two fluid passages in the housing, it is possible to reduce the passage resistance of the fluid passing through the housing. For this reason, since the flow rate value of the maximum flow rate can be set large, the range of flow rate control from the flow rate value of the minimum flow rate that narrows the flow rate to the flow rate value of the maximum flow rate becomes wide. Further, since the flow rate value of the maximum flow rate can be set large without forming a large passage in the housing, it is possible to reduce the size of the flow rate control device.

Further, at the time of the minimum flow rate, the reverse axial load applied to the valve body is balanced and canceled to drive the valve body from the state of the minimum flow rate to the state of the maximum flow rate. In this case, the valve body can be smoothly moved with a small force by the drive means. Therefore, the valve element can be easily reciprocated even if a small drive unit is used to drive the valve element.

Further, when the flow rate is at a minimum, the load in the opposite axial direction applied to the valve body is counterbalanced so as to cancel the load, so that the axial unbalanced load of the valve body with respect to the housing can be suppressed. Therefore, uneven wear of the sliding portion between the housing and the valve body can be reduced, and the durability of the sliding portion can be improved.

[Embodiment] A flow rate control device of the present invention will be described based on an embodiment shown in Figs. 1 to 5.

FIG. 1 and FIG. 4 show the first embodiment of the present invention and are views showing a water amount control device for a water heater.

The water amount control device 1 includes a variable throttle valve 2 and a drive mechanism 5.
Equipped with.

The variable throttle valve 2 has a housing 3 and a valve body 4.

The housing 3 has a tubular shape and has a control chamber 30, a first fluid passage 31 and a second fluid passage 32 formed therein.

The control chamber 30 is a tubular first chamber (control chamber of the present invention) 30a which is always in communication with the first fluid passage 31 when the amount of water is most restricted by the axial position of the valve body 4 (minimum flow rate). , Second fluid passage 3
It is divided into a cylindrical second chamber (equal pressure equalizing chamber of the present invention) 30b which is provided on the opposite side of 2 and is disconnected from the communication with the first fluid passage 31.

The first fluid passage 31 is adjacent to the control chamber 30 in the radial direction. Further, the first fluid passage 31 is formed in the radial direction with respect to the valve body 4, and the upper end in the drawing is a connecting portion 31a between a water pipe (not shown) that connects the public water pipe and the housing 3, The lower end in the figure is an inlet port 31b facing the control chamber 30.

The second fluid passage 32 is provided adjacent to the control chamber 30 in the axial direction, and communicates with the first fluid passage 31 via the control chamber 30. Further, a water supply pipe that is formed coaxially with the valve body 4, has a left end in the drawing as an outlet port 32a facing the control chamber 30, and a right end in the drawing as a heat exchanger for a water heater (not shown) and the housing 3. It is a connecting portion 32b with (not shown).

The housing 3 includes a main body 33, a first sleeve 34, a second sleeve
It is composed of a sleeve 35 and an annular plate 36.

At the inner circumference of the main body 33, when the amount of water is most throttled, a first valve seat (first partition portion) 37 that slidably contacts the valve body 4 to partition the first fluid passage 31 and the second fluid passage 32 Is provided.

The first sleeve 34 is arranged in the main body 33. On the inner circumference of the first sleeve 34, a second valve seat (the first valve seat (second chamber) 30a that divides the control chamber 30 into a first chamber 30a and a second chamber 30b by slidingly contacting the valve body 4 when the amount of water is most reduced. 2 compartments) are provided.

The second sleeve 35 slidably supports the valve body 4 and the drive mechanism 5, and at the same time, an inner peripheral screw 37 that meshes with the drive mechanism 5.
Are formed.

The valve body 4 is the displacement means of the present invention, and has a first valve portion 41, a second valve portion 42, a valve rod 43 and a communication hole 44.

The first valve portion 41 changes the degree of communication between the first fluid passage 31 and the second fluid passage 32 via the control chamber 30 according to the axial position. That is, the first valve portion 41 changes the degree of throttling of the water amount according to the axial position. One side surface of the first valve portion 41 faces the first fluid passage 31, and the other side surface faces the second fluid passage 32. Then, the outer peripheral surface of the first valve portion 41 is brought into sliding contact with the first valve seat 37 of the main body 33 when the amount of water is minimized.

The second valve portion 42 changes the degree of communication between the first fluid passage 31 and the second chamber 30b of the control chamber 30 according to the axial position. One side surface of the second valve portion 42 faces the first fluid passage 31, and the other side surface faces the second chamber 30b. The outer peripheral surface of the second valve portion 42 has a second surface of the first sleeve 34 when the amount of water is most reduced.
It is slidably contacted with the valve seat 38.

The valve rod 43 is formed integrally with the first valve portion 41 and the second valve portion 42, and the end portion of the valve rod 43 is fixed to the drive mechanism 5 slidably supported by the second sleeve 35. .

The communication hole 44 is formed inside the valve rod 43, and the second fluid passage 32 is formed.
And the second chamber 30b are communicated with each other, and one side of the first valve portion 41 (second
The side surface of the fluid passage 32 side and the other side of the second valve portion 42 (second chamber 30)
It is for applying the same amount of water pressure in opposite directions to the side of (b side).

An O-ring 45 is mounted between the outer peripheral surface of the valve rod 43 and the inner peripheral surface of the second sleeve 35, and between the inner peripheral surface of the main body 33 and the outer peripheral surface of the second sleeve 35. An O-ring 46 is attached.

The drive mechanism 5 is the drive means of the present invention and has a gear motor 51 and a movable sleeve 52.

The gear motor 51 controls the axial position of the valve element 4 by displacing the movable sleeve 52 by a predetermined amount in the rotating direction according to the amount of energization. This gear motor 51 has a second sleeve 35.
The motor case 54 is fastened to a mounting plate 53 fixed to the. Further, the gear motor 51 is spline-coupled to the movable sleeve 52.

The movable sleeve 52 has the end portion of the valve rod 43 fitted therein,
An outer peripheral screw 55 that meshes with the inner peripheral screw 39 of the second sleeve 35 is formed on the outer periphery on one side, and a gear motor 51 is formed on the outer periphery on the other side.
And a spline 56 for spline connection is formed. When the movable sleeve 52 is rotationally driven by the gear motor 51, the movable sleeve 52 moves in the axial direction while rotating in the second sleeve 35, and axially displaces the valve rod 43 that integrally operates.

The operation of the water amount control device 1 of this embodiment will be described with reference to FIGS. 1 to 4.

When the gear motor 51 is energized and the movable sleeve 52 is rotated, the movable sleeve 52 is axially displaced in the second sleeve 35 along with the valve rod 43 of the valve body 4. Then, the valve rod 43 stops at a predetermined axial position, and the first fluid passage 31 moves to the control chamber.
The amount of water flowing into the second fluid passage 32 through the first chamber 30a of the housing 30 has a predetermined throttle amount (first amount) depending on the axial position of the first valve portion 41 with respect to the first valve seat 37 of the housing 3. Aperture amount). Further, the amount of water flowing from the first fluid passage 31 to the second fluid passage 32 through the first chamber 30a and the second chamber 30b of the control chamber 30 and the communication hole 44 of the valve body 4 is the second valve of the housing 3. seat
According to the axial position of the second valve portion 42 with respect to 38, it is throttled by a predetermined throttle amount (second throttle amount).

Therefore, normally, the water pressure P of the water flowing through the second fluid passage 32 is
₂ becomes lower than the water pressure P ₁ of the water flowing through the first fluid passage 31.

Therefore, in the housing 3, the first fluid passage 31 → the first chamber 30a of the control chamber 30 → the communication passage between the first valve seat 37 and the first valve portion 41 → the first fluid passage 32 is formed. Path, first fluid passage 31 → first chamber 30a of control chamber 30 → communication passage between second valve seat 38 and second valve portion 42 → second chamber 30b of control chamber 30 → communication of valve element 4 The passage resistance of water passing through the inside of the housing 3 can be reduced by forming two fluid passages, that is, the hole 44 and the second fluid passage that flows through the second fluid passage 32. For this reason, since the flow rate value of the maximum flow rate can be set large, the range of flow rate control from the flow rate value of the minimum flow rate that narrows the flow rate to the flow rate value of the maximum flow rate becomes wide. Moreover, since the flow rate value of the maximum flow rate can be set large without forming a large passage in the housing 3, it is possible to reduce the size of the water volume control device 1, particularly the housing 3.

Next, at the minimum flow rate when the amount of water is most throttled by the valve body 4, the first valve portion of the valve body 4 is attached to the first valve seat 37 of the housing 3.
41 is substantially seated and the first chamber 30a of the control chamber 30 and the second fluid passage 32
And the second valve portion 42 of the valve body 4 is substantially seated on the second valve seat 38 of the housing 3 so that the first chamber 30a and the second chamber 3 of the control chamber 30 are separated.
By partitioning with 0b, the communication between the first fluid passage 31 and the second fluid passage 32 is blocked via the first chamber 30a of the control chamber 30, so that it becomes difficult for water to flow.

At this time, the internal pressure of the first fluid passage 31 (the first fluid passage 31
P _{1 which} is equal to the water pressure of the water inside) becomes larger than the internal pressure of the second fluid passage 32 (equal to the water pressure of the water inside the second fluid passage 32) P ₂ . In this embodiment, the internal pressure P ₁ of the first fluid passage 31 acts on the first valve portion 41 of the valve body 4 in the rightward direction in the figure, and further on the second valve portion 42 in the leftward direction in the figure. Therefore, loads of the same magnitude in opposite directions cancel each other out, and no axial load is generated. Regarding the internal pressure P ₂ of the second fluid passage 32, since the second chamber 32b and the second fluid passage 32 communicate with each other through the communication hole 44 formed in the valve rod 43, the valve body 4 The internal pressure of the second fluid passage 32 and the second chamber 30 which come into contact with both sides in the axial direction of the
The internal pressure of b is the same. Therefore, the first of the valve body 4
A side surface of the valve portion 41 on the second fluid passage 32 side and a second chamber of the second valve portion 42.
Since the axial loads applied to the side surface on the 30b side cancel each other out, the axial load applied to the valve body 4 is almost eliminated.

Therefore, it is possible to eliminate the axial load applied to the valve body 4 when the amount of water is squeezed most by the valve body 4. Therefore, even when the valve body 4 is displaced leftward in the drawing by the drive mechanism 5 for the purpose of changing the degree of restriction of the amount of water,
Since no load is applied in the axial direction of the valve body 4,
The valve body 4 can be smoothly displaced by the driving mechanism 4 with a small force. Moreover, since the valve body 4 does not apply an unbalanced load to the housing 2 and the movable sleeve 52 in the axial direction, the inner peripheral screw 39 of the second sleeve 35 and the outer peripheral screw 55 of the movable sleeve 52 are not worn. Without, the durability of these sliding parts can be improved.

Therefore, even when controlling the water amount of high water pressure by the water amount control device 1, the load biased in the axial direction of the valve body 4 is not applied, and the valve body 4 can be smoothly displaced with a small force. Torque and small gear motor
51 can be used.

Further, by opening and closing the water stop valve provided in the water supply pipe connecting the heat exchanger for water heater and the housing 3, the water pressure and the amount of water in the fluid passage are changed, especially when the water stop valve is closed. The water pressure P ₂ of the second fluid passage 32 may be higher than the water pressure P ₁ of the first fluid passage 31.

However, in this embodiment, the first valve portion is passed through the communication hole 44.
The same load as the load applied to the side surface of the second fluid passage 32 side of 41 is also applied to the side surface of the second valve portion 42 on the second chamber 30b side. Therefore, even when the water pressure P ₂ of the second fluid passage 32 becomes larger than the water pressure P ₁ of the first fluid passage 31, the valve body 4 is not pushed leftward in the drawing. Therefore, since the valve body 4 does not vibrate in the axial direction, it is possible to prevent the generation of resonance noise. Also, valve stem
The O-ring 45, which is mounted between the outer peripheral surface of 43 and the inner peripheral surface of the second sleeve 35, separates from the water pressure P ₁ of the first fluid passage 31, which becomes high water pressure when the amount of water is most throttled. It is hard to wear because it is done.

Further, in the conventional device, the water amount is restricted by a part of the outer peripheral surface of the valve head and the inner peripheral surface of the housing.
Since the amount of water is throttled by both 41 and the second valve portion 42, the flow of water becomes smooth and the flow noise of water passing through the housing 2 is reduced.

FIG. 5 shows the second embodiment of the present invention and is a diagram showing a water amount control device.

In this embodiment, the outer peripheral surface of the second valve portion 42 and the first sleeve 34 are
An O-ring 47 is attached between the second valve seat 38 and Therefore, even when the amount of water is squeezed most, that is, the first
Even when the internal pressure of the fluid passage 31 becomes higher than the internal pressure of the second fluid passage 32, the water flowing from the first fluid passage 31 does not leak to the second chamber 30b of the control chamber 30. Therefore, the internal pressure of the second fluid passage 32 and the internal pressure of the second chamber 30b are surely the same.

(Modification) In the present embodiment, the present invention is used in the water amount control device that controls the amount of water supplied to the heat exchanger for hot water heater, but the present invention is used in the fuel amount control device that controls the amount of fuel supplied to the burner. May be.

In the present embodiment, the gear motor is used as the driving means, but as the driving means, an actuator that reciprocally shifts the shifting means in the axial direction by hydraulic pressure or the like may be used.

In this embodiment, the example in which the fluid flows from the first fluid passage to the second fluid passage has been shown, but the fluid may flow from the second fluid passage to the first fluid passage.

The fluid passage on the upstream side may be connected to a water supply pipe connecting the heat exchanger and the housing. The downstream fluid passage may be connected to a hot water supply pipe that connects the housing to a hot water supply place such as a bath or a kitchen.

The valve rod, the first valve portion and the second valve portion may be separately formed.

[Brief description of drawings]

1 and 4 show a first embodiment of the present invention. First
FIG. 4 is a sectional view showing the water amount control device, FIG. 2 is a side view showing the water amount control device, FIG. 3 is a front view showing the water amount control device, and FIG. 4 is another side view showing the water amount control device. FIG. 5 shows a second embodiment of the present invention and is a sectional view showing a water amount control device. FIG. 6 is a sectional view showing a conventional water amount control device. In the figure, 1 ... Water amount control device (flow rate control device), 2 ... Variable throttle valve, 3 ... Housing, 4 ... Valve body (transition means), 5 ...
... Drive mechanism (drive means), 30 ... Control room, 30a ... First
Room (control room), 30b ... Second room (equalizing chamber), 31 ... First
Fluid passage, 32 ... Second fluid passage, 37 ... First valve seat (first
Compartment), 38 …… Second valve seat (Second compartment), 41 …… First
Valve part, 42 …… Second valve part, 44 …… Communication hole

Claims (1)

[Claims] 1. A control chamber in which a flow rate of a fluid is controlled, a first fluid passage which is provided adjacent to the control chamber in a radial direction thereof and which is always in communication with the control chamber, and adjacent to one side of the control chamber in the axial direction. A housing provided with a second fluid passage that communicates with the first fluid passage through the control chamber; and a displacement means that is slidably supported by the housing and that reciprocates in the axial direction in the control chamber. A flow rate control device comprising: a drive unit that axially reciprocally drives the displacement unit, wherein (a) the housing is adjacent to a side opposite to the second fluid passage side in the axial direction of the control chamber. A pressure equalizing chamber that is provided and communicates with the first fluid passage via the control chamber, a first partitioning portion that partitions the control chamber and the second fluid passage when the transition means is seated, and an inner circumference It is provided so as to project inward, and the displacement means is seated At this time, the control chamber and the pressure equalizing chamber have a second partitioning portion, and (b) the transition means internally has a communication hole that always connects the pressure equalizing chamber and the second fluid passage. A first valve portion that substantially seats in the first partition portion only when the flow rate is minimum and that otherwise opens the first partition portion,
And a second valve portion that is provided so as to project outward from the outer periphery and that is substantially seated in the second partition portion at the minimum flow rate and that opens the second partition portion at least at the maximum flow rate. apparatus.