JP2012037012A - Flow-regulating valve device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flow-regulating device capable of performing an accurate constant differential pressure operation and accurately regulating a flow rate even in such a state that the throttle of a constant differential pressure valve greatly narrows the flow passage.SOLUTION: The flow-regulating device 15 includes a flow-regulating valve 18 and a constant differential pressure valve 64 that keeps a differential pressure constant between the primary side pressure Pand the secondary side pressure Pof a main valve 20 in the flow-regulating valve 18. The throttle 94 of a valve element 66 in the constant differential pressure valve 64 is formed of a flange that protrudes in a radial direction.

Description

  The present invention relates to a flow control device that performs flow rate adjustment, and more particularly to a flow control device that includes a constant differential pressure valve.

2. Description of the Related Art Conventionally, a flow control device that keeps the flow rate of water passing through a valve or an orifice constant at a flow rate corresponding to the flow path area of the water passage portion of the valve or orifice is known.
For example, this kind of flow regulating device is disclosed in Patent Document 1 below.

FIG. 9 shows a specific example.
In the figure, reference numeral 200 denotes a main body in the flow regulating device, and a main valve 204 in the flow regulating valve (flow rate regulating valve) 202 is provided on the flow path inside.
Reference numeral 206 denotes a primary flow path that is an upstream flow path with respect to the main valve 204. Water sent through the primary flow path 206 passes through the main valve 204. It flows through the gap between the main valve seat 214 (this gap can also be considered as a variable orifice) and flows to the secondary side flow path 208, and further flows through the output side flow path 210 and flows out to the outside.

Reference numeral 216 denotes an electromagnetic pilot valve in the flow control valve 202, and this electromagnetic pilot valve 216 has a plunger type pilot valve body 218 seated on the pilot valve seat 220 and closes the pilot flow path 222 to close the pressure in the pressure chamber 224. And the increase in pressure causes the main valve 204 to close.
On the other hand, by separating the pilot valve body 218 upward from the pilot valve seat 220 in the figure, the pilot flow path 222 is opened to the pressure chamber 224 and the pressure in the pressure chamber 224 is lowered to open the main valve 204. .

The body body 200 inside and the secondary flow path 208, the differential pressure ΔP of the primary pressure _{P 1} of the primary-side flow passage 206 and the secondary side pressure _{P 2} of the secondary-side flow path 208 = _{(P 1} constant differential pressure valve 226 to the -P ₂₎ is constant is provided.

228 is a diaphragm-type valve element that has a main body, and has a cylindrical portion 230, and is fitted into the fitting hole 232 of the main body 200 in a vertically and watertight manner so as to be slidable. .
A primary pressure chamber 234 is formed on the lower side of the valve body 228 in the figure, and the primary pressure P _{1 of the} primary flow path 206 is introduced into the primary pressure chamber 234 through the communication path 236.

The valve body 228 (including the upper surface of the cylindrical portion 230) that the lower surface has form a primary-side pressure receiving surface 238 for receiving upwardly in FIG primary side pressure P ₁ of the primary-side flow path 206, also the upper surface There forms a secondary pressure receiving surface 240 for receiving the secondary pressure P ₂ on the secondary side flow path 208 downward in FIG.
This relative valve body 228, and the biasing force of the coil spring 242 is made to act in the same direction as the direction of action of the secondary side pressure P _2.

In the constant differential pressure valve 226, the balance between the primary side pressure P ₁ exerted upward in the drawing against the valve body 228, a biasing force in the opposite direction in the drawing applied to the downward secondary pressure P ₂ and the coil spring 242 The valve body 228 moves in the vertical direction in the figure so as to cause
Specifically, when the primary pressure P ₁ of the primary-side flow path 206 by the fluctuation of the supply pressure is increased, pushing up upward in the figure by the inlet pressure P ₁ to the valve body 228 has its increased constant differential pressure valve 226 It is done.

Then, the throttle portion 244 formed at the upper end of the cylindrical portion 230 approaches the sheet surface 246, and the restriction on the secondary side flow path 208 by the throttle portion 244 and the sheet surface 246 becomes large, and the secondary side flow path. 208 secondary pressure _{P 2} increases the.
Then, the valve body 228 stops moving at a position where the secondary pressure P ₂ and the primary pressure P ₁ increased by the movement balance each other.

Further, when the primary pressure P ₁ on the contrary decreases, the valve body 228 moves downward in the figure at a relatively increased secondary side pressure P _2, and the primary pressure P ₁ and the secondary side pressure P _The valve body 228 stops at a position where it is balanced with ₂ .
In this way, the valve body 228 operates so as to always keep the differential pressure ΔP between the primary side pressure P ₁ and the secondary side pressure P ₂ constant.

In this flow control device, the flow rate of water passing through the main valve 204 becomes a constant flow rate according to the opening degree of the main valve 204.
Specifically, when the flow path area of the gap between the main valve body 212 and the main valve seat 214 is a, the flow rate of water flowing through the main valve 204 is a flow rate represented by the following equation (1). Q.

但し式（１）中ｃは定数で、ΔＰはＰ_１とＰ_２との差圧，ρは水の比重である。

In equation (1), c is a constant, ΔP is the differential pressure between P ₁ and P _2, and ρ is the specific gravity of water.

Since ΔP is kept constant by the constant differential pressure valve 226 as shown in the equation (1), the flow rate Q of water flowing through the main valve 204 is kept constant.
Further, when the opening degree of the main valve 204 changes, the flow rate is kept constant according to the changed opening degree, that is, the flow passage area a after the change.

That is, in the flow regulating valve device, a constant but the flow rate of water flowing through the flow path by changing the opening degree of the main valve 204 is adjusted, the adjusted flow rate despite variations in the inlet pressure P ₁ A constant flow rate is maintained by the action of the differential pressure valve 226.

In the constant pressure control valve 226 in the flow regulating device, the secondary pressure P ₂ is applied to the upper surface in the drawing of the throttle portion 244 formed at the upper end of the cylindrical portion 230, that is, the upper surface facing the seat surface 246. The original constant differential pressure operation can be performed in the state.

However, as shown in FIG. 10, when the throttle 244 approaches the sheet surface 246 and narrows the flow path, the flow rate of water flowing between the throttle 244 and the sheet surface 246 increases, so that Due to the pressure drop, a pressure P ₃ lower than the secondary pressure P ₂ acts on the upper surface of the throttle portion 244 in the figure. That is, the pressure difference is not (P ₁ −P ₂ ) but (P ₁ −P ₃ ) at the action site of the pressure P ₃ .

Then, the pressure acting on the upper surface of the throttle portion 244 becomes weaker by (P ₂ -P ₃ ) than the original secondary pressure P ₂ , and as a result, the valve body 228 is in the drawing more than the original correct control position. upward many moving to cause to increase the secondary pressure P _2, resulting in less than the original flow rate water flow by reducing the differential pressure _{ΔP = (P 1 -P 2)} .
That constant differential pressure operation of the constant differential pressure valve 226, the constant-differential pressure operation becomes inaccurate especially become differential pressure smaller the primary pressure P ₁ is higher (P 1 _{-P 3)} is large, and thus the flow regulation valve device In this case, the flow control operation becomes inaccurate.

The above example is an example in which the primary pressure P ₁ and the secondary pressure P ₂ for the openable / closable valve are made a constant differential pressure by a constant differential pressure valve. The situation is the same when a fixed and constant orifice is provided.

In addition, there exists what was disclosed by the following patent document 2 as a prior art with respect to this invention.
However, the one disclosed in Patent Document 2 cannot solve the problem of the present invention, and the one disclosed in Patent Document 2 is different from the present invention.

JP 2009-24780 A JP 2003-56443 A

  The present invention is based on the above situation, and can perform an accurate constant differential pressure operation even under the condition that the throttle portion of the constant differential pressure valve is greatly throttled, so that the flow rate can be adjusted accurately. It is made for the purpose of providing a valve regulating apparatus.

Accordingly, the first aspect of the present invention comprises (a) a valve or an orifice, and (b) (a) a slidably fitted in the fitting hole, and the primary side flow path with respect to the valve or orifice. receiving side pressure P ₁ in one of the primary pressure receiving surface, the secondary flow path secondary valve element which receives the other secondary side pressure receiving face opposite to the pressure P ₂ of the primary side pressure receiving surface of the , and (b) has a spring for applying a biasing force in the direction of action of the secondary side pressure P ₂ with respect to the valve body, a throttle portion provided on the distal end side of the valve body by the movement of the valve body , by changing the aperture for the flow path between the contactable sheet surface the narrowed portion, the constant differential pressure valve to maintain the pressure difference between the primary side pressure P ₁ and the secondary side pressure P ₂ at a constant, A flow control device that maintains the flow rate of water passing through the valve or orifice at a flow rate corresponding to the flow area of the water passage portion of the valve or orifice by the action of the constant differential pressure valve The throttle portion is formed by a flange portion protruding outward in the radial direction along the seat surface from the position of the outer surface fitted in the fitting hole.

  According to a second aspect of the present invention, in the first aspect, the valve body is divided into a ring-shaped tip portion including the throttle portion and a main body portion of the valve body, and the tip portion and the main body portion are pivoted. It is assembled in a fitted state in the direction.

  According to a third aspect of the present invention, in the second aspect of the present invention, the distal end portion and the main body portion are fitted into a state in which the elastic ring is elastically compressed through an annular elastic ring made of an elastic body. To do.

Effects and effects of the invention

  As described above, according to the present invention, the throttle portion of the valve body in the constant differential pressure valve is formed by a flange portion that protrudes radially outward along the seat surface from the position of the outer surface that fits into the fitting hole. It is a thing.

  According to the present invention, the pressure applied to the upper surface of the flange portion forming the throttle portion, that is, the surface facing the seat surface, and the lower surface of the flange portion positioned on the opposite side of the lower surface of the flange portion, ie, the seat surface, are as described above. Cancels the pressure applied in the opposite directions and cancels each other.

  Therefore, the pressure applied to the throttle portion can be prevented from affecting the operation of the constant differential pressure valve, and the constant differential pressure valve can be accurately operated at a constant differential pressure. Therefore, an accurate flow control operation in the flow control device can be ensured.

  In the present invention, according to claim 2, the valve body may be divided into a ring-shaped tip portion including a throttle portion and a main body portion, and the tip portion and the main body portion are assembled in an axially fitted state. it can.

If the valve body has a straight shape in the axial direction (the direction of the axis of the fitting hole) until the outer surface of the valve element reaches the tip, the valve element can be fitted into the fitting hole from the tip side and assembled. However, according to the present invention, when the throttle part of the valve body, that is, the flange part is provided in a shape projecting radially outward from the position of the outer surface fitting into the fitting hole, the valve body is It cannot be fitted into the fitting hole from the side and assembled.
In this case, it is conceivable that the valve body can be assembled by making the main body of the flow control device into a divided structure, but in this case, the number of parts of the device increases, and labor is required for assembly. It takes a lot.

However, if the valve body of the constant differential pressure valve is divided into the ring-shaped tip portion including the throttle portion formed by the flange portion and the main body portion of the valve body according to claim 2, the downstream side of the throttle portion is provided. Insert the ring-shaped tip part through the flow path to a position facing the fitting hole, and in that state, insert the valve body body part into the fitting hole from the tip side, so that the ring-shaped tip part and the body The part can be easily fitted in the axial direction, and the valve body can be assembled to the main body.
In this case, since it is not necessary to divide the main body for assembling the valve body, the number of parts can be reduced, which is advantageous in terms of cost.

  The ring-shaped tip and the main body of the valve body can be fitted and assembled in a state where the elastic ring is elastically compressed via an annular elastic ring made of an elastic body. ).

  By doing so, it is possible to seal between the ring-shaped tip portion and the main body portion which are separated from each other by the annular ring, and a large frictional force based on the elastic repulsive force of the elastic ring. Therefore, it is possible to prevent the ring-shaped tip and main body from coming off.

  In this case, an annular groove is provided on one of the front end portion and the main body portion on the mating side surface with respect to the other, and an elastic ring is fitted therein, and the other side on the mating side surface is against the elastic ring. Thus, an engaging portion that engages in the pulling direction can be provided.

It is a figure at the time of applying the flow control apparatus of one Embodiment of this invention to an automatic water tap. It is the figure which expanded and showed the principal part of the constant differential pressure | voltage valve in the flow valve apparatus of FIG. It is a figure of the principal part of other embodiment of this invention. It is the figure which decomposed | disassembled and showed the principal part of the same embodiment. It is a figure of other embodiment of this invention. It is a figure of other embodiment of this invention. It is explanatory drawing of operation | movement of the embodiment. It is a figure at the time of applying the flow control valve apparatus of the embodiment to the washing valve of a toilet bowl. It is a figure which shows the conventional flow control valve apparatus. It is a figure for demonstrating the problem of the conventional flow control apparatus.

Next, embodiments of the present invention will be described in detail with reference to the drawings.
In FIG. 1, 10 is a water discharge part of the automatic water faucet, and 12 is a water discharge port provided in the water discharge part 10.
Reference numeral 14 denotes a flow channel for supplying water toward the water discharge unit 10, and the flow control valve device 15 of the present embodiment is provided on the flow channel 14.

Reference numeral 16 denotes a main body in the flow regulating device 15, and a main valve 20 in the flow regulating valve (flow rate regulating valve) 18 is provided on the internal flow path.
The main valve 20 includes a diaphragm main valve body 26 including a holding member 22 made of a hard resin and a rubber diaphragm film 26 held by the holding member 22, and a main valve seat 28 for seating the diaphragm main valve body 26. Have.
Here, the main valve seat 28 is constituted by an upper end portion of a cylindrical portion 30 that rises upward in the drawing.

  Reference numeral 32 denotes a primary flow path that is an upstream flow path with respect to the main valve 20. Water sent through the primary flow path 32 passes through the main valve 20. A secondary-side flow path that includes a flow path inside the cylindrical portion 30 and a flow path that follows the flow path through a clearance S between the main valve seat 28 (this clearance S can also be considered as a variable orifice). 34 and further supplied to the water discharge section 10 through the outlet side flow path 36.

Reference numeral 38 denotes a pressure chamber formed behind the main valve body 26. The pressure chamber 38 causes the internal pressure to act on the main valve body 26 as a pressing force in the valve closing direction.
The main valve body 26 is provided with an introduction small hole 40 that passes through the main valve body 26 and communicates the primary flow path 32 and the pressure chamber 38.
The introduction small hole 40 introduces the water in the primary side flow path 32 into the pressure chamber 38 and increases the pressure in the pressure chamber 38.

The main body 16 is provided with a pilot flow path 42 as a drainage flow path for communicating the pressure chamber 38 with the downstream side of the main valve 20, here, a secondary pressure chamber 80 described later.
Here, the pilot flow path 42 draws water in the pressure chamber 38 to the downstream side, and lowers the pressure in the pressure chamber 38.

A pilot valve (electromagnetic pilot valve) 44 that constitutes the flow control valve 18 together with the main valve 20 is provided on the pilot flow path 42.
The pilot valve 44 includes a plunger-type pilot valve body 46, a pilot valve seat 47 for seating the plunger-type pilot valve body 46, an electromagnetic coil 48 for opening the pilot valve body 46 by generating an electromagnetic force by energization, and the pilot valve body 46. It has a spring 50 that biases it in the middle and downward direction to keep it in a closed state.

  In this pilot valve 44, the rubber seal portion 52 at the tip of the pilot valve body 46 is seated on the pilot valve seat 47, whereby the pilot flow path 42 is disconnected and the pilot valve body 46 is removed from the pilot valve seat 47 in the figure. The pilot flow path 42 is brought into a communicating state by being separated upward.

In this embodiment, the flow control valve 18 closes the pilot flow path 42 by closing the pilot valve 44 as described above.
Then, the pressure of the pressure chamber 38 is increased by the water guided to the pressure chamber 38 through the introduction small hole 40 penetrating the main valve body 26, and the pressing force in the valve closing direction against the main valve body 26 is increased. Here, the main valve body 26 is seated on the main valve seat 28, and the valve is closed.

On the other hand, when the pilot valve body 46 is opened, the pilot flow path 42 is brought into a communication state, so that water in the pressure chamber 38 is drawn to the downstream side through the pilot flow path 42, where the pressure in the pressure chamber 38 decreases. Thus, the main valve body 26 is pushed upward in the figure by the pressure of the water supply in the primary side flow path 32 to open the valve.
Here, the water in the primary channel 32 flows through the main valve 20 to the downstream side, and is supplied to the water discharge unit 10.

The water discharger 10 is provided with a sensor 54 that senses the hand that has been pushed out (senses the human body). The sensor 54 and the electromagnetic coil 48 of the pilot valve 44 are electrically connected to the controller 56. It is connected.
When the sensor 54 senses a human body, the pilot valve 44 is opened under the control of the controller 56. That is, the main valve 20 constituting the flow control valve 18 together with the pilot valve 44 is opened.
On the other hand, when the sensor 54 is in a human body non-sensing state, the pilot valve 44 is closed, the main valve 20 is closed here, and the water supply to the water discharge unit 10 is stopped. That is, water discharge from the water discharge port 12 is stopped.

The main body 16 is provided with a flow rate adjusting shaft (flow rate adjusting member) 58 that adjusts the water flow rate by adjusting the opening of the main valve 20 when the main valve body 26 is opened.
The flow rate adjusting shaft 58 is inserted into an insertion hole 59 provided in the main body body 16, and is screwed to the female screw portion of the main body body 16 at the male screw shaft portion 60 so as to be movable back and forth in the vertical direction, that is, in the axial direction in the figure. ing.

  The flow rate adjusting shaft 58 is provided with an engaging groove 61 for engaging a tool on the upper surface of a portion protruding upward from the main body 16 in the figure. The flow rate adjusting shaft 58 adjusts the screwing amount by engaging and rotating the tool in the engaging groove 61, and changes the position of the lower end thereof up and down.

  In this embodiment, the valve opening position when the main valve body 26 is opened, that is, the rising position is determined by the vertical position of the flow rate adjusting shaft 58. That is, in the main valve body 26, the rising position when the valve is opened is determined by following the up and down movement of the flow rate adjusting shaft 58 in the vertical direction.

In this embodiment, when the pilot valve 44 is turned on / off while the flow rate adjusting shaft 58 is maintained at a fixed position, the main valve body 26 is turned on / off accordingly. The opening degree of the main valve body 26 at this time is determined by the main valve body 26, specifically, a projecting portion 62 provided at the center portion hitting the lower end of the flow rate adjusting shaft 58. That is, it is determined by the position of the flow rate adjusting shaft 58. Therefore, if the position of the flow rate adjusting shaft 58 is upward, the opening degree of the main valve body 26 is increased, and the flow rate of water flowing through the main valve 20 is increased.
On the other hand, when the position of the flow rate adjusting shaft 58 is downward, the opening of the main valve body 26 is small, and the flow rate of water passing through the main valve 20 is small.
Therefore, in this embodiment, the flow rate of water when the main valve 20 is opened can be changed by adjusting the position of the flow rate adjusting shaft 58 up and down.

The body body 16 inside and above the secondary channel 34, the differential pressure ΔP of the primary pressure P ₁ of the primary-side flow path 32 and the secondary side pressure P ₂ of the secondary-side flow path 34 = P constant differential pressure valve 64 for the ₁ -P ₂ constant is provided.

Reference numeral 66 denotes a diaphragm-type valve element that is the main body, and includes a rubber diaphragm film 68 and a hard resin holding member 70 that holds the diaphragm film 68.
The valve body 66 has a cylindrical portion 72 in the upper part in the figure, and is fitted in the cylindrical part 72 so as to be slidable in the vertical direction in the figure in a circular fitting hole 74 of the main body body 16.

A primary pressure chamber 76 is formed on the lower side of the valve body 66 in the figure, and the primary pressure P _{1 of the} primary flow path 32 is introduced into the primary pressure chamber 76 through the communication path 78.
The valve body 66 is formed in a primary-side pressure receiving surface 79 in the figure lower surface in the drawing upward receive the primary pressure P _1.

Reference numeral 80 denotes a secondary pressure chamber formed around the valve body 66. The secondary pressure chamber 80 is provided in the secondary pressure chamber 80 through the axial passage 82 in the cylindrical portion 72 and the radial passage 84 below the fitting hole 74. side pressure P ₂ is introduced.
The valve body 66, narrowed portion overall top surface including the cylindrical portion 72 is formed a secondary side pressure P ₂ at the flange portion of which (provided later forms the secondary side pressure receiving surface 86 for receiving downward in the drawing Except 94).

The secondary pressure chamber 80 is housed a coil spring 88, the urging force of the coil spring 88 is exerted in the same direction as the direction of action of drawing downwards, i.e. secondary pressure P ₂ with respect to the valve body 66 ing.
The coil spring 88 has a lower end in contact with the valve body 66 in the drawing, and an upper end in contact with the main body body 16 in the secondary pressure chamber 80 upward in the drawing.

The valve body 66 has an annular groove between the cylindrical portion 72 and a lower large-diameter portion 90 having a larger diameter than that of the cylindrical portion 72, and a donut-shaped rubber film (other material having elasticity) 92) may be fitted so as to be capable of relative movement by a minute stroke in the axial direction, that is, in the vertical direction in the figure.
The rubber film 92 is pressed upward in the figure by the differential pressure between the secondary pressure chamber 80 and the pressure on the outlet side flow path 36 side, and is secondary through the gap between the cylindrical portion 72 and the fitting hole 74. It serves to prevent the pressure in the pressure chamber 80 from leaking.

The valve body 66 has a throttle portion 94 on the distal end side (upper end side in the figure), and the throttle portion 94 and a seat surface 96 on the body body 16 side (this seat surface 96 can contact the throttle portion 94. a surface in which) and without the effect of throttling the flow of the flow path between the differential pressure [Delta] P = P ₁ -P ₂ of a primary side pressure P ₁ and the secondary side pressure P ₂ on the basis of their action constant To hold.

Specifically, when the primary pressure P ₁ of the primary-side flow path 32 by fluctuations in the water supply pressure increases, pushed upward in the figure by the inlet pressure P ₁ the valve element 66 has its increased constant differential pressure valve 64 It is done.
Then stop for the secondary flow path 34 by the throttle portion 94 and the seat surface 96 becomes large, the secondary side pressure P ₂ on the secondary side flow path 34 is increased. The valve body 66 is the mobile elevated secondary pressure P ₂ and by the primary side pressure P ₁ is moved stops at balanced positions.

Further, when the primary pressure P ₁ on the contrary decreases, the valve body 66 moves downward in the figure at a relatively increased secondary side pressure P _2, and the primary pressure P ₁ and the secondary side pressure P _The valve body 66 is stopped at a position where ₂ is balanced.
In this way, the valve element 66 operates so as to always keep the differential pressure ΔP between the primary pressure P ₁ and the secondary pressure P ₂ constant.
Therefore, as derived from the above equation (1), the flow rate of water passing through the main valve 20 becomes a constant flow rate according to the opening degree of the main valve 20.
Therefore, in this embodiment, when a hand is put out in front of the sensor 54 of the water discharge unit 10 and water is discharged from the water discharge port 12, water can be discharged from the water discharge port 12 at a constant flow rate corresponding to the opening of the main valve 20.

FIG. 2 shows in detail the configuration of the diaphragm 94 and its surroundings.
As shown in the drawing, in this embodiment, on the distal end side of the valve body 66, the outer surface 98 that fits into the fitting hole 74 in the valve body 66 extends along the seat surface 96 in the radial direction in parallel with the seat surface 96. A flange portion projecting outward is integrally provided, and a throttle portion 94 is formed by the flange portion.
Specifically, the distance between the valve body 66 and the seat surface 96 is the narrowest in the portion of the restricting portion 94 formed of a flange portion, and the size of the restrictor of the flow path is between the restricting portion 94 and the seat surface 96. It depends on the interval.

  A portion of the distal end surface (upper end surface in the drawing) of the valve body 66 that is radially inward of the throttle portion 94 moves to the left in the drawing, that is, toward the axial center of the valve body 66 as the seat moves away. A tapered surface 100 that is separated from the surface 96 is formed, and a radially inner portion of the distal end surface of the valve body 66 with respect to the throttle portion 94 has a concave shape that is recessed downward in the drawing.

Accordingly, when the valve body 66 greatly restricts the flow of the flow path with the throttle portion 94 positioned in the immediate vicinity of the seat surface 96, the pressure drop occurs at the portion of the throttle portion 94, and the distal end surface and the outer surface 98 of the valve body 66 secondary side pressure P ₂ on the inner side of the portion acting downward in FIG than.

Meanwhile, with respect to the upper surface of the diaphragm portion 94 is low pressure P ₃ than the secondary side pressure P ₂ acting downward in figure, the same pressure for drawing the lower surface of the diaphragm portion 94 made of the flange portion P ₃ acts upward, their pressures cancel each other, it is canceled.
Therefore only the secondary side pressure P ₂ for the distal end surface of the valve body 66 acts downward, the action of the pressure P ₃ is eliminated.

  In the present embodiment, the pressure applied to the throttle portion 94 can be prevented from affecting the operation of the constant differential pressure valve 64, and the constant differential pressure valve 64 can be accurately operated at a constant differential pressure. Therefore, an accurate flow adjustment operation in the flow adjustment valve device 15 can be ensured.

  In the case where the valve body 66 is provided with a flange portion projecting radially outward as described above and the throttle portion 94 is formed by the flange portion, the throttle portion 94 is integrated with the valve body 66. If configured, the valve body 66 cannot be fitted into the fitting hole 74 upward in FIG.

  In this case, it is conceivable to divide the ring-shaped tip portion including the throttle portion 94 from the main body portion of the valve body 66 and screw them together. In that case, the ring-shaped tip portion and the main body portion are connected to each other. It is difficult to connect the screws.

FIGS. 3 and 4 show one means for solving this problem. Here, the ring-shaped tip portion 102 including the throttle portion 94 and the main body portion 104 of the valve body 66 are divided and the tips. The portion 102 and the main body portion 104 are fitted into a state where the elastic ring 106 is elastically compressed through an annular elastic ring (here, O-ring) 106 made of an elastic body such as rubber, and then assembled. There is no.
Note that the ring-shaped tip 102 has a height dimension (axial dimension) positioned on the upper side (back side) of the fitting hole 74 in the drawing through the opening on the right side of the outlet channel 36 in the drawing. The dimensions can be inserted up to.

Here, the main body 104 is provided with an annular ring groove 108 over the entire circumference, and the elastic ring 106 is held in the fitted state.
On the other hand, an engagement portion 110 that engages with the elastic ring 106 in the removal direction is provided at the distal end portion 102 in a ring shape so as to protrude radially inward.

The engaging portion 110 is provided with a guide surface 112 having a tapered surface so that the engaging portion 110 can easily move over the elastic ring 106 to a lower position thereof.
Here, the upper surface of the engaging portion 110 is a tapered surface 111 that gradually decreases in diameter downward in the drawing.
On the other hand, a stepped portion 114 is provided on the annular groove 108 side, and the lower surface of the stepped portion 114 is a tapered surface 115 that gradually decreases in diameter downward in the figure.

  According to this example, the ring-shaped distal end portion 102 is inserted into the body body 16 through the outlet side flow passage 36, specifically, at the upper position of the fitting hole 74 in the drawing as shown in FIG. 3B. In the state where the elastic ring 106 is held in the annular groove 108 of the main body 104 in the valve body 66, the main body 104 is fitted into the fitting hole 74 of the main body body 16 upward from below in the figure. The main body portion 104 and the front end portion 102 can be assembled in a fitted state via the elastic ring 106, and at the same time, the valve body 66 can be assembled to the main body body 16.

At this time, the main body portion 104 and the ring-shaped tip portion 102 in a fitted state are elastically compressed by the elastic ring 106 in the radial direction, and are prevented from coming off by a large frictional force based on the elastic reaction force.
In addition, since the engagement portion 110 that engages with the elastic ring 106 in the removal direction is provided on the distal end portion 102 side, the removal of the distal end portion 102 from the main body portion 104 is more due to the physical engagement force. It is surely prevented.

  Further, the elastic ring 106 is sandwiched between the tapered surface 115 of the main body portion 104 and the tapered surface 111 of the front end portion 102 in an elastically compressed state, so that the front end portion 102 faces downward in the figure, that is, the support surface of the main body portion 104. A force in a direction to press against 117, that is, a force in a direction opposite to the pulling direction is applied.

  According to the embodiment of FIGS. 3 and 4, the tip portion 102 and the main body portion 104 which are divided from each other can be easily assembled, and the main body portion 104 of the valve body 66 can be easily assembled to the main body body 16 side. Can do.

Further, since it is not necessary to divide the main body 16 into a plurality of parts for assembling the valve body 66, the number of parts constituting the main body 16 is increased, and inconveniences such as requiring a lot of labor for assembling are avoided. In addition, the cost can be reduced.
Further, there is an advantage that the elastic ring 106 can seal between the ring-shaped tip portion 102 and the main body portion 104 which are divided from each other.

In the present invention, instead of the flow control valve 18, the flow control device 15 may be configured by providing an orifice 116 having a fixed and constant flow path area as shown in FIG.
In FIG. 5, the other parts are basically the same as in the above embodiment.

6 and 7 show still another embodiment of the present invention.
In this embodiment, as shown in FIG. 7, a through hole is provided in the central portion of the main valve body 26 in the axial direction (vertical direction in the figure). A pilot flow path 42 is formed between the outer surface of the inserted drive shaft 118.

  A pilot valve body 120 is integrally formed on the drive shaft 118, and a pilot valve seat 122 having an annular shape around the through hole is formed on the main valve body 26 side, and a seal member is provided on the pilot valve seat 122. 124 is held.

  FIG. 7A shows that the pilot valve body 120 is watertightly elastically fitted to the seal member 124 of the pilot valve seat 122 to close the pilot flow path 42, and the main valve body 26 is seated on the main valve seat 28. The state where the main valve body 26 is closed is shown.

When the pilot valve body 120 is lifted upward in the figure together with the drive shaft 118 from this state, and a gap is formed between the pilot valve body 120 and the seal member 124 (state of FIG. 7B), the pilot flow path here 42 is in communication with the pressure chamber 38, and the water in the pressure chamber 38 flows out to the secondary channel 34 through the pilot channel 42.
Then, the pressure in the pressure chamber 38 decreases, and the main valve body 26 is pushed upward by the primary side pressure P _{1 of the} primary side flow path 32 in the drawing.

When the main valve body 26 is pushed upward and the gap between the pilot valve body 120 and the seal member 124 of the pilot valve seat 122 is reduced, the flow rate of water flowing out from the pressure chamber 38 through the pilot flow path 42 is reduced.
As a result, the pressure in the pressure chamber 38 increases, and when the increased pressure in the pressure chamber 38 is balanced with the primary pressure P ₁ and the secondary pressure P ₂ , the main valve body 26 moves. Stops.
FIG. 7C shows the state at this time.
In the state shown in FIG. 7C, the main valve body 26 is spaced upward from the main valve seat 28 and is opened, where water flows from the primary channel 32 to the secondary channel 34. To do.
At this time, a certain minute gap (following gap) is maintained between the pilot valve body 120 and the seal member 124 of the pilot valve seat 122.

Thereafter, the main valve body 26 moves in the same direction following the upward movement of the pilot valve body 120 in the figure while maintaining this constant follow-up gap, and the distance from the main valve seat 28 is increased. That is, the valve opening is increased.
Accordingly, the flow rate of water from the primary side flow path 32 to the secondary side flow path 34 increases.

  On the other hand, when the pilot valve body 120 moves downward in the figure, the main valve body 26 follows the movement of the pilot valve body 120 and closes the valve while maintaining the small constant follow-up gap. The flow rate of water passing through the main valve 20 is decreased.

  Finally, as shown in FIG. 7A, when the pilot valve body 120 is elastically fitted to the seal member 124 of the pilot valve seat 122 and the pilot valve 126 is closed, the main valve 20 is also closed here. The primary side flow path 32 and the secondary side flow path 34 are blocked, and the flow of water from the primary side flow path 32 to the secondary side flow path 34 is stopped.

  In FIG. 6, reference numeral 130 denotes a driving mechanism that transmits the driving force of an electric motor (here, a stepping motor) 128 serving as a driving source to the driving shaft 118, that is, the pilot valve body 120, and moves it in the vertical direction in the figure. The drive mechanism 130 includes a cylindrical rotating body 132 that rotates integrally with the output shaft 131 of the electric motor 128.

The rotating body 132 has a female threaded portion 134 on its inner peripheral surface, and a male threaded portion 138 on the outer peripheral surface of the advance / retreat member 136 is screwed into the female threaded portion 134.
Here, the advance / retreat member 136 is urged upward in the figure by the coil spring 140.
The upper and lower ends of the drive shaft 118 are screwed to the advance / retreat member 136 so that the drive shaft 118 moves integrally with the advance / retreat member 136 in the vertical direction in the figure.

In this embodiment, when the rotating body 132 is rotated by the electric motor 128, the advance / retreat member 136 is moved forward and backward in the figure by screw feed, and the drive shaft 118, that is, the pilot valve body 120 is also moved in the up-down direction in the figure. Move forward and backward.
As the pilot valve body 120 advances and retreats, the main valve body 26 follows this and moves up and down in the vertical direction in the figure to increase or decrease the valve opening, thereby changing the main valve body 26 and the main valve seat 28. The flow rate of the water flowing through the flow path is adjusted by changing the gap S between the two and the large or small gap.
In the embodiment shown in FIGS. 6 and 7, the other parts are basically the same as those in the above embodiment.

Flow regulation valve device 15 of this embodiment, the valve opening degree of the main valve 20 is continuously and finely adjustable by an electric motor 128, besides regardless primary pressure P _1, the main valve 20 The flow rate of water can be adjusted by the flow rate according to the valve opening degree, and the flow rate can be kept constant by the action of the constant differential pressure valve.
Therefore, the flow regulating device 15 of this embodiment can be suitably applied as, for example, a toilet flushing valve shown in FIG.

For example, it can be suitably applied as a rim cleaning valve 142 for supplying cleaning water to a toilet rim to wash the toilet rim, or as a jet cleaning valve 144 for jetting cleaning water from a jet nozzle toward a drain trap and cleaning the toilet. It is.
In this case, the cleaning water can flow stably at the set flow rate regardless of the fluctuation of the supply water pressure or even at the installation site where the supply water pressure is low. The amount of water can be adjusted finely by the movement of 26 and the amount of water can be adjusted.

  Although the embodiment of the present invention has been described in detail above, this is merely an example, and the flow control device of the present invention can be applied as a flow control device in various other water supply facilities other than the above automatic faucet. For example, the present invention can be configured in various forms without departing from the spirit of the present invention.

15 Flow control device 18 Flow control valve (Flow control valve)
32 Primary side flow path 34 Secondary side flow path 50 Spring 64 Constant pressure valve 66 Valve element 74 Fitting hole 79 Primary side pressure receiving surface 86 Secondary side pressure receiving surface 94 Restriction portion 96 Seat surface 98 Outer surface 102 Tip portion 104 Main body Part 106 elastic ring 108 annular groove 110 engaging part 116 orifice

Claims (3)

(B) a valve or orifice, (ii) (a) slidably fitted into the fitting hole, the primary flow path the one primary side to the primary side pressure P ₁ of the relative valve or orifice receiving at the pressure receiving surface, the valve body for receiving the other of the secondary side pressure receiving face opposite to the secondary side flow path outlet pressure P ₂ the primary side pressure receiving surface, and (b) the valve body to A seat having a spring that applies a biasing force in the acting direction of the secondary pressure P ₂ , and a seat provided on the distal end side of the valve body by the movement of the valve body and capable of contacting the throttle section by changing the aperture for flow channel in the surface, anda constant differential pressure valve to maintain the pressure difference between the primary side pressure P ₁ and the secondary side pressure P ₂ constant, it passes through the valve or orifice In a flow control device that keeps the flow rate of water to be constant at a flow rate corresponding to the flow path area of the water passage part of the valve or orifice by the action of the constant differential pressure valve,
The flow regulating device according to claim 1, wherein the throttle portion is formed by a flange portion that protrudes radially outward along the seat surface from a position of an outer surface that fits into the fitting hole.   2. The valve body according to claim 1, wherein the valve body is divided into a ring-shaped tip portion including the throttle portion and a body portion of the valve body, and the tip portion and the body portion are assembled in an axially fitted state. A flow control device characterized by that.   3. The flow regulating device according to claim 2, wherein the tip and the main body are fitted in a state in which the elastic ring is elastically compressed through an annular elastic ring made of an elastic body.

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