JP6768193B2 - Flow control valve - Google Patents

Description

The present invention relates to a flow rate adjusting valve for adjusting the flow rate of a liquid flowing through a flow path. In particular, the present invention relates to a flow rate adjusting valve for adjusting the flow rate of tap water used in washroom equipment and the like.

The flow rate adjusting valve using the back pressure chamber and the pilot valve body has already been widely used because the main valve body can be operated with a small force. For example, Patent Document 1 also discloses its basic configuration and operating principle.

In this type of flow control valve, when closed, the main valve body provided in the flow path via an elastic element such as a diaphragm membrane is the pressure of the liquid contained in the back pressure chamber (flow path). It is urged in the valve closing direction by (depending on the supply pressure inside).

Then, at the time of opening, the pilot valve body is controlled so as to open the outflow hole provided in the main valve body. Specifically, the end of the outflow hole on the back pressure chamber side is opened. As a result, the liquid in the back pressure chamber begins to be discharged (supplied) through the outflow hole. At this time, the pressure inside the back pressure chamber decreases, so that the main valve body is opened.

When the liquid in the back pressure chamber begins to be discharged through the outflow hole, for example, new liquid flows into the back pressure chamber through the inflow hole provided in the main valve body. The main valve body moves to a position where the inflow amount into the back pressure chamber and the outflow amount discharged through the outflow hole described above are the same (the amount of liquid in the back pressure chamber does not fluctuate), and that position. Is held in. At this time, the outflow amount changes depending on the relative distance between the pilot valve body and the main valve body.

Since the main valve body moves based on the above principle, the position of the main valve body ultimately depends on the position of the pilot valve body. That is, by controlling the position of the pilot valve body, the position of the main valve body can be controlled, and thus the flow rate can be controlled.

Japanese Unexamined Patent Publication No. 2010-169131

In the above-mentioned type of flow rate adjusting valve, it is important to improve the positioning accuracy of the pilot valve body in order to realize more accurate flow rate adjustment.

In the course of various studies and experiments, the inventor has found that it is effective to avoid fluctuations in the direction (positive and negative fluctuations) of the force acting on the pilot valve body, especially when controlling a small flow rate. I found out.

The present invention has been made based on the above findings. An object of the present invention is to provide a flow rate adjusting valve that enables more accurate flow rate adjustment by avoiding fluctuations in the direction of the force acting on the pilot valve body.

The present invention is a flow rate adjusting valve for adjusting the flow rate of the liquid flowing through the flow path, the main valve body displaceably supported in the flow path via an elastic element, and the upstream side of the flow path. A back pressure chamber in which a liquid supplied from the main valve body at a predetermined pressure is accommodated and a force for urging the main valve body in the valve closing direction is generated by the liquid, and an upstream side of the flow path and the back pressure chamber. An inflow hole that communicates with, an outflow hole that communicates with the downstream side of the flow path and the back pressure chamber, a pilot valve body that opens and closes the outflow hole, and the pilot valve body that holds and holds the pilot valve body. A longitudinal member that moves the longitudinal member in its own axial direction, a rotating rotating member, and a rotating member that can rotate with the rotation of the rotating member, and can also move in the axial direction of the longitudinal member in conjunction with the rotation. The lifter and the longitudinal member are connected so as to move integrally in the axial direction, and the longitudinal member may be present with the liquid via a watertight seal. The cross-sectional area of the region extending continuously to both the back pressure chamber side region and the air side region where the liquid does not exist and penetrating the watertight seal of the longitudinal member is the back of the outflow hole. rather smaller than the opening area of the end of the pressure chamber side, wherein the longitudinal member includes a shaft member including a region through said watertight seal is configured to include a, a tip member for holding the pilot valve body, The tip member is slidably connected to the shaft member within a predetermined range in the axial direction, and an elastic member for urging the tip member in the valve closing direction is provided. It is a flow control valve characterized by this.

According to the present invention, since the configuration using the back pressure chamber and the pilot valve body is adopted, the main valve body can be operated with a small force.

Since the cross-sectional area of the region penetrating the watertight seal of the longitudinal member is smaller than the opening area of the end of the outflow hole on the back pressure chamber side, the holding force of the longitudinal member with respect to the influence of the force acting on the pilot valve body. The degree is smaller than the degree of the negative pressure change accompanying the change in the opening of the outflow hole.

The effect of this feature will be described in detail below with reference to the graphs of FIGS. 24 to 26.

As shown in FIG. 24, the conventional pilot valve body is held by a longitudinal member having a diameter of about three times the diameter of the outflow hole. This also applies to the flow rate control valve described in Patent Document 1 described above. In this case, the force that urges such a large-diameter longitudinal member in the valve opening direction (the atmospheric pressure that the cross section of the region that escapes to the atmosphere through the watertight seal receives and the water pressure that acts on the water contact surface of the longitudinal member Because (corresponding to the difference) is working sufficiently (due to valve closing, even if the force acting on the region blocking the outflow hole 13 of the longitudinal member changes from water pressure to atmospheric pressure, the force still urges in the valve opening direction. Is predominant (it is necessary to apply a downward force to close the valve), because even if it receives a large negative pressure just before the outflow hole closes, the holding force by the longitudinal member is still predominant. , There is no risk of blurring or fluctuation in the behavior of the pilot valve body, and the control of the pilot valve body is stable. However, since it is necessary to move a long-diameter longitudinal member in order to move the pilot valve body, relatively high energy is required.

As shown in FIG. 25, the present inventor examined the case where the diameter of the longitudinal member holding the pilot valve body and the diameter of the outflow hole were made similar in the process leading to the present invention. In this case, when the outflow hole is open, the holding force by the longitudinal member is sufficiently acting, but when the negative pressure just before the outflow hole is closed, the holding force by the longitudinal member is canceled out and the pilot It was found that the control of the pilot valve body became unstable due to fluctuations and fluctuations in the valve body behavior. This is because when the total force acting is close to zero, it swings positively and negatively and becomes unstable.

Therefore, as shown in FIG. 26, the present inventor examined the case where the diameter of the longitudinal member holding the pilot valve body was made smaller than the diameter of the outflow hole. In this case, when the opening degree of the pilot valve body is large, the holding force by the longitudinal member acts sufficiently, but the holding force by the longitudinal member due to the negative pressure gradually increasing as the opening degree of the pilot valve body becomes smaller. Is canceled out, and when the pilot valve body has a predetermined opening degree (point A in FIG. 26), the behavior of the pilot valve body may be shaken or fluctuated. However, at the opening degree (point A in FIG. 26), the flow rate is not small, so that high control accuracy is not required, that is, there is no practical problem. In the region of minute opening where high control accuracy is required to achieve so-called stable flow rate control at the time of closing, that is, stable movement and holding of the main valve body, the negative pressure is held by the longitudinal member. Since it is superior to force, there is no risk of blurring or fluctuation in the behavior of the pilot valve body, and the control of the pilot valve body is stable. Moreover, since it is sufficient to move the longitudinal member having a small diameter as the pilot valve body moves, a relatively low energy is sufficient. In addition, there is also an effect that the resistance due to the watertight seal when moving the longitudinal member is small. Further, the fact that the force acting on the pilot valve body is in the direction of closing at the time of closing also has an effect of enabling reliable valve closing without any other urging force.

The above examination results are not limited to the case where the shape of the opening cross section of the outflow hole or the cross section of the longitudinal member is circular. Therefore, in the present invention, the relationship between the opening area of the outflow hole and the cross-sectional area of the longitudinal member is defined. ing.

Further, in the present invention, the longitudinal member is configured to include a shaft member including a region penetrating the watertight seal and a tip member holding the pilot valve body.

As a result , only the cross-sectional area of the shaft member needs to be smaller than the opening area of the end of the outflow hole on the back pressure chamber side, and the cross-sectional area of the tip member can be freely designed. In other words, the length of the shaft member having a small cross-sectional area can be shortened by the amount of the tip member, and it is possible to suppress the occurrence of bending or bending of the shaft member.

Further, in the present invention, the tip member is connected to the shaft member so as to be relatively slidable in a predetermined range in the axial direction, and is elastic to urge the tip member in the valve closing direction. Members are provided.

This prevents the pilot valve body from being pressed against the outflow hole by an excessive force due to the cushioning action of the elastic member. Further, in this case, even when the shaft member is slightly tilted, the pilot valve body acts to follow the position of the outflow hole, and the valve closing operation can be reliably performed.

Further, preferably, the tip member has a flow path for liquid movement formed in at least a part of the radial outer surface.

In this case, it is possible to effectively prevent the presence of the liquid from hindering the movement when the tip member moves.

Further, preferably, the longitudinal member penetrates a part of the lifter, and the longitudinal member is engaged with the lifter via a retaining mechanism.

In this case, it is possible to reliably prevent the longitudinal member from coming off the lifter.

In this case, more preferably, the retaining mechanism has an E-ring.

In this case, even if the longitudinal member is thin, it can be securely fixed to the lifter. Further, since the longitudinal member can be made thinner, the contact area between the longitudinal member and each member can be reduced, and the sliding resistance generated between the longitudinal member and each member can be reduced.

Further, preferably, the longitudinal member is connected to the lifter in a state of being urged to one side in the axial direction by the urging connecting member.

In this case, since the longitudinal member is urged to one side in the axial direction, the pilot valve body is prevented from shaking or wobbling. This action is particularly effective in the vicinity of a predetermined opening degree (point A in FIG. 26) where the total force acting on the pilot valve body becomes zero.

According to the present invention, since the configuration using the back pressure chamber and the pilot valve body is adopted, the main valve body can be operated with a small force.

Since the cross-sectional area of the region penetrating the watertight seal of the longitudinal member is smaller than the opening area of the end of the outflow hole on the back pressure chamber side, the holding force of the longitudinal member with respect to the influence of the force acting on the pilot valve body. The degree is smaller than the degree of the negative pressure change accompanying the change in the opening of the outflow hole. As a result, in the region of minute opening where high control accuracy is desired to achieve so-called stable flow rate control at the time of closing, that is, stable movement and holding of the main valve body, the negative pressure is the longitudinal member. The control of the pilot valve body is stable because there is no risk of blurring or fluctuation in the behavior of the pilot valve body, which is superior to the holding force of the pilot valve body. Then, since it is sufficient to move the longitudinal member having a small cross-sectional area with the movement of the pilot valve body, a relatively low energy is sufficient. In addition, there is also an effect that the resistance due to the watertight seal when moving the longitudinal member is small. Further, the fact that the force acting on the pilot valve body is in the direction of closing at the time of closing also has an effect of enabling reliable valve closing without any other urging force.

It is a perspective view of the flow rate adjustment valve which concerns on one Embodiment of this invention. It is a vertical cross-sectional view of the flow rate adjustment valve of FIG. 1, and shows the valve closed state. It is a vertical cross-sectional view of the flow rate adjustment valve of FIG. 1, and shows the state immediately after the valve opening operation. It is a vertical cross-sectional view of the flow rate adjustment valve of FIG. 1, and shows the valve open state. It is an enlarged plan view of the main valve body of the flow rate adjustment valve of FIG. It is a front view which shows the pilot valve body, the longitudinal member, the urging connection member, and the E ring extracted from the flow rate adjustment valve of FIG. It is sectional drawing which shows the pilot valve body, the longitudinal member, the urging connection member, and the E ring extracted from the flow rate adjustment valve of FIG. It is a perspective view which shows the pilot valve body, the longitudinal member, the urging connection member, and the E ring extracted from the flow rate adjustment valve of FIG. It is a perspective view which shows the pilot valve body, the longitudinal member, the urging connection member, and the E ring extracted from the flow rate adjustment valve of FIG. It is an enlarged perspective view of the E ring of the flow rate adjustment valve of FIG. It is a perspective view of the joint member of the flow rate adjustment valve of FIG. It is a top view of the joint member of FIG. It is a front view of the joint member of FIG. FIG. 12 is a cross-sectional view taken along the line XIV-XIV of FIG. It is a cross-sectional view of XV-XV line of FIG. It is a perspective view of the stopper of the flow rate adjustment valve of FIG. It is a top view of the stopper of FIG. FIG. 17 is a cross-sectional view taken along the line XVIII-XVIII of FIG. It is a perspective view seen from diagonally above the lifter of the flow rate adjustment valve of FIG. It is a perspective view seen from diagonally lower side of the lifter of FIG. It is a vertical sectional view of the lifter of FIG. It is a perspective view of the back pressure chamber forming member of the flow rate adjustment valve of FIG. It is a front view of the back pressure chamber forming member of FIG. It is a graph which shows the relationship between the holding force by a conventional longitudinal member and the negative pressure acting on an outflow hole. It is a graph which shows the relationship between the holding force by a shaft member, and the negative pressure acting on an outflow hole when the diameter of a shaft member and the diameter of an outflow hole are about the same. It is a graph which shows the relationship between the holding force by a shaft member, and the negative pressure acting on an outflow hole when the diameter of a shaft member is smaller than the diameter of an outflow hole. It is a perspective view of the manual adjustment jig seen from diagonally above. It is a perspective view which looked at the manual adjustment jig from diagonally below. It is a perspective view of the flow rate adjustment valve at the time of work which adjusts the position of a joint member and a stopper using a manual adjustment jig. It is an exploded perspective view of the flow rate adjustment valve of FIG. It is an enlarged view of the area A (corresponding to the upper part of a drive unit) of FIG. It is an enlarged view of the area B (corresponding to the lower part of a drive unit) of FIG. It is an enlarged view of the region C (corresponding to the base) of FIG. It is an exploded perspective view of the drive unit, the base, and the main valve body viewed from diagonally above. It is an exploded perspective view of the drive unit, the base, and the main valve body viewed from diagonally below.

Next, the flow rate adjusting valve according to the embodiment of the present invention will be described with reference to the accompanying drawings.

[Constitution]
FIG. 1 is a perspective view of a flow rate adjusting valve according to an embodiment of the present invention, and FIGS. 2 to 4 are vertical cross-sectional views of the flow rate adjusting valve of FIG. FIG. 2 shows a valve closed state, FIG. 3 shows a state immediately after the valve opening operation, and FIG. 4 shows a valve opening state.

As shown in FIGS. 1 to 4, the flow rate adjusting valve 1 of the present embodiment is for adjusting the flow rate of the liquid flowing through the flow paths 2 and 3. The liquid is usually water or hot water. In FIGS. 2 to 4, the flow paths 2 and 3 extend in the left-right direction, but the flow rate adjusting valve 1 of the present embodiment is intended to be arranged so that the flow paths 2 and 3 extend in the vertical direction. ing. Specifically, it is intended that the flow path 2 on the upstream side is located vertically below and the flow path 3 on the downstream side is located vertically above.

As shown in FIGS. 2 to 4, the flow rate adjusting valve 1 of the present embodiment has a main valve body 10 displaceably supported in a flow path 3 on the downstream side via a diaphragm film 11 which is an elastic element. I have. The diaphragm film 11 and the main valve body 10 are integrally manufactured of resin.

A back pressure chamber forming member 20 is provided on the side opposite to the flow path 3 with the main valve body 10 interposed therebetween, and the back pressure chamber 4 is formed by the back pressure chamber forming member 20 and the main valve body 10. .. As will be described later, the back pressure chamber 4 accommodates a liquid (water or hot water) supplied at a predetermined pressure from the flow path 2 on the upstream side. Then, the pressure of the liquid generates a force that urges the main valve body 10 in the valve closing direction.

[Main valve body]
The main valve body 10 of the present embodiment has a shape substantially symmetrical around the axis X, and the center of gravity of the main valve body 10 exists on the axis X.

The main valve body 10 of the present embodiment has an abutting portion 15 that comes into contact with the valve seat 3s of the flow path 3 when seated on the flow path 3 on the downstream side when the valve is closed. The contact portion 15 is made of a material that is harder than the other parts of the main valve body 10.

In the present embodiment, the main valve body 10 is provided with two inflow holes 12 that communicate the flow path 2 on the upstream side and the back pressure chamber 4. The two inflow holes 12 are arranged so as to form a pair at symmetrical positions with respect to the axis X of the main valve body 10. FIG. 5 shows a plan view of the main valve body 10. Correspondingly, the upstream side flow path 2 has a wraparound flow path 2b that wraps around the inflow hole 12 located above the downstream side flow path 3 (in FIGS. 2 to 4). Further, as shown in FIGS. 2 to 4, each of the two inflow holes 12 is provided as a linear cross-sectional circular path in the main valve body 10.

Due to the arrangement as described above, the flow rate adjusting valve 1 of the present embodiment is arranged with respect to the flow paths 2 and 3 extending in the vertical direction, that is, the main valve body 10 is arranged so that the opening / closing direction is horizontal. At that time, one of the two inflow holes 12 is arranged in each of the upper region and the lower region with respect to the axis X of the main valve body 10.

Next, in the present embodiment, one outflow hole 13 that communicates the flow path 3 on the downstream side and the back pressure chamber 4 is provided in the main valve body 10. The outflow hole 13 is provided as a path having a circular cross section on the axis X of the main valve body 10.

[Longitudinal member]
Then, the pilot valve body 30 that opens and closes the end 13e (see FIG. 4) of the outflow hole 13 on the back pressure chamber side is held by the longitudinal member 32 and is moved in the axial direction of the longitudinal member 32 by the longitudinal member 32. It is supposed to be done.

A pilot valve body 30, a longitudinal member 32, an elastic resin member 72 which is an urging connecting member that connects the longitudinal member 32 in a state of being urged to one side in the axial direction with respect to a lifter 40 described later, and a longitudinal member. The E-ring 71, which is a retaining mechanism for engaging the member 32 and the lifter 40, is extracted and shown in FIGS. 6 to 9. FIG. 6 is a front view in a state where these members are assembled, FIG. 7 is a vertical sectional view of FIG. 6, FIG. 8 is a perspective view of these members viewed from diagonally above, and FIG. 9 is a perspective view. , It is a perspective view seen from diagonally below. FIG. 10 is an enlarged perspective view of the E-ring 71.

As shown in FIGS. 2 to 9, the longitudinal member 32 of the present embodiment includes a shaft member 32a including a region penetrating the back pressure chamber forming member 20 via a watertight seal 34 composed of two O-rings, and a pilot valve. It is configured to include a tip member 32b that holds the body 30 by adhesion, press-fitting, or the like.

As shown in FIGS. 6 and 7, the tip member 32b is slidably connected to the shaft member 32a within a predetermined range in the axial direction. Specifically, the upper side (in FIGS. 2 to 9) of the tip member 32b extends upward to surround the shaft member 32a and guide the sliding of each other. An elastic member 32c is provided between the tip member 32b and the shaft member 32a to urge the tip member 32b and the shaft member 32a in a direction away from each other. The elastic member 32c is a coil spring in this embodiment.

As shown in FIGS. 8 and 9, the tip member 32b is formed with a flow path 32g for moving the liquid on the outer surface in the radial direction.

As shown in FIGS. 2 to 4, the shaft member 32a extends continuously through the watertight seal 34 to both the back pressure chamber side region where the liquid can exist and the atmospheric side region where the liquid does not exist. ing. The cross-sectional area of the shaft member 32a, particularly the cross-sectional area of the region where the shaft member 32a penetrates the watertight seal 34, is smaller than the opening area of the end 13e of the outflow hole 13 on the back pressure chamber side. In the present embodiment, the cross section of the shaft member 32a is a uniform circular shape. A first spacer member 35 is provided on the outside (atmosphere side) of the watertight seal 34 in order to guide the axial movement of the shaft member 32a, and on the inside (back pressure chamber side) of the watertight seal 34. A second spacer member 36 is provided. As shown in FIG. 2, the second spacer member 36 extends in the hollow portion 21 of the back pressure chamber forming member 20 described later, and also has a function of guiding the movement of the tip member 32b in the hollow portion 21. Have.

[Stepping motor]
Subsequently, a configuration for moving the shaft member 32a in the axial direction will be described. In this embodiment, the stepping motor 60 is used for moving the shaft member 32a.

The stepping motor 60 of the present embodiment is a general stepping motor in which a rotary shaft 61 that is rotationally driven is exposed to the outside of the housing 62. The rotating shaft 61 is coupled to the rotating shaft receiving portion 56 of the joint member 50 shown in FIGS. 11 to 15. That is, the joint member 50 rotates integrally with the rotating shaft 61.

[Joint member]
11 is a perspective view of the joint member 50, FIG. 12 is a plan view of the joint member 50, and FIG. 13 is a front view of the joint member 50. As shown in FIGS. 11 to 13, the joint member 50 is provided with a stopper regulating portion 58 projecting to the outer peripheral side.

14 is a sectional view taken along line XIV-XIV of FIG. 12, and FIG. 15 is a sectional view taken along line XV-XV of FIG. As shown in FIGS. 14 and 15, a tubular fitting hole 54 having a substantially cross-shaped cross section and extending in the axial direction is provided inside the joint member 50.

A tubular stopper 80 cut out in a substantially C-shaped cross section as shown in FIGS. 16 to 18 is provided so as to surround the outer peripheral side of the joint member 50. 16 is a perspective view of the stopper 80, FIG. 17 is a plan view of the stopper 80, and FIG. 18 is a sectional view taken along line XVIII-XVIII of FIG. The stopper 80 limits the rotation range of the stopper regulating portion 58 of the joint member 50 to a predetermined range (for example, 90 °). Details of the stopper 80 will be described later.

[Lifter]
19 to 21 show the lifter 40 of the present embodiment extracted. FIG. 19 is a perspective view seen from above the lifter 40, FIG. 20 is a perspective view seen from below the lifter 40, and FIG. 21 is a vertical sectional view of the lifter 40.

As shown in FIGS. 19 to 21, the lifter 40 of the present embodiment is provided with a tubular fitting convex portion 45 projecting in a substantially cross section in the upper portion. Then, the fitting convex portion 45 is housed in the fitting hole 54 of the joint member 50, the joint member 50 and the lifter 40 are engaged in the rotational direction, and the joint member 50 and the lifter 40 are relative to each other. It guides the movement in the axial direction. Regarding this relative axial movement, as shown in FIGS. 2 to 4, a coil spring 73 as an urging member is interposed between the joint member 50 and the lifter 40, and the lifter 40 is always the joint member 50. (That is, the rotating shaft 61 (rotating member)) is urged toward the back pressure chamber.

The lower portion of the lifter 40 of the present embodiment is formed in a substantially hollow cylindrical shape, and is provided so that three protrusions 42 distributed at intervals of 120 ° in the rotational direction project inward and downward.

[Back pressure chamber forming member]
On the other hand, as shown in FIGS. 2 to 4, the back pressure chamber forming member 20 of the present embodiment has a hollow portion 21 formed in a hollow cylindrical shape on an extension line of the axis X of the main valve body 10. The tip member 32b of the longitudinal member 32 moves in the axial direction in the hollow portion 21.

Here, FIG. 22 is a perspective view of the back pressure chamber forming member 20 of the present embodiment, and FIG. 23 is a front view of the back pressure chamber forming member 20 of FIG. 21. As can be seen from FIGS. 22 and 23, the hollow portion 21 is defined by the cylindrical portion 22 on the upper side. Then, it abuts on each of the three protrusions 42 of the lifter 40 on the outer peripheral surface of the cylindrical portion 22, and as the lifter 40 rotates (combined with the urging force of the coil spring 73), the protrusions 42 are axially oriented. There are three guide slopes 23 that move the lifter 40 in the axial direction by guiding the lifter 40. An engaging protrusion 24 is provided on the lower side surface for coupling with the case member 91 described later.

The shaft member 32a is engaged with the shaft member receiving hole 43 (see FIGS. 19 and 21) of the lifter 40 that moves in the axial direction according to the above configuration. Specifically, as shown in FIGS. 2 to 4, an E-ring 71 as a retaining mechanism is press-fitted adjacent to the upper part of the shaft member receiving hole 43, and the shaft is fitted to the E-ring 71. The notch provided in the member 32a is engaged. Then, the elastic resin member 72 as the urging connection member is press-fitted into the elastic resin member receiving portion 47 (see FIG. 21) of the lifter 40 in a state where the upper end of the shaft member 32a is urged toward the back pressure chamber side. ing.

[Other parts]
In addition, in the present embodiment, the coil spring 73 as an urging member always urges the rotating shaft 61 of the stepping motor 60 in the same rotational direction via the joint member 50. As a result, the internal members of the stepping motor 60 are also offset in one direction in the rotation direction via the rotation shaft 61. Further, the coil spring 73 is urged with a force equal to or less than the detent torque of the stepping motor 60.

Further, the elastic force of the elastic member 32c of the longitudinal member 32 is smaller than the elastic force of the elastic resin member 72 as the urging connection member.

[Basic effects]
As shown in FIG. 2, when the valve is closed, the main valve body 10 provided in the flow path 3 via the diaphragm film 11 is charged with the pressure of the liquid contained in the back pressure chamber 4 (in the flow path 2). It is urged in the valve closing direction by (depending on the supply pressure of).

Then, at the start of valve opening, the pilot valve body 30 is controlled in order to open the outflow hole 13 provided in the main valve body 10.

Specifically, the stepping motor 60 is rotationally driven, and the joint member 50 starts rotating together with the rotating shaft 61. Along with this, the lifter 40 rotates due to the engagement between the fitting hole 54 of the joint member 50 and the fitting convex portion 45 of the lifter 40.

The protrusion 42 of the lifter 40 is always urged against the guide slope 23 by the coil spring 73, and is guided on the guide slope 23 as the lifter 40 rotates. As a result, the lifter 40 also moves in the axial direction.

The shaft member 32a is connected to the lifter 40 via the E-ring 71 and the elastic resin member 72, and moves in the axial direction as the lifter 40 moves in the axial direction. As a result, the pilot valve body 30 connected to the shaft member 32a moves in the axial direction.

When the end 13e of the outflow hole 13 on the back pressure chamber side is opened by moving the pilot valve body 30 in the axial direction away from the main valve body 10 (upward in FIG. 2), the inside of the back pressure chamber 4 is opened. The liquid begins to be discharged (supplied) into the flow path 3 on the downstream side through the outflow hole 13. This state is shown in FIG. At this time, since the pressure inside the back pressure chamber 4 decreases, the main valve body 10 is opened.

When the liquid in the back pressure chamber 4 begins to be discharged through the outflow hole 13, new liquid flows into the back pressure chamber 4 through the inflow hole 11 provided in the main valve body 10. The main valve body 10 moves to a position where the inflow amount into the back pressure chamber 4 and the outflow amount discharged through the outflow hole 12 are the same (the amount of liquid in the back pressure chamber 4 does not fluctuate). , Held in that position. This state is shown in FIG. At this time, the amount of outflow depends on the relative distance between the pilot valve body 30 and the main valve body 10.

Since the main valve body 10 moves as described above, the position of the main valve body 10 ultimately depends on the position of the pilot valve body 30. That is, by controlling the position of the pilot valve body 30, the position of the main valve body 10 can be controlled, and thus the flow rate can be controlled.

In the present embodiment, the lifter 40 is provided with three protrusions 42 distributed in the rotational direction, and the guide slope 23 guides the protrusions 42 as the lifter 40 rotates to guide the lifter 40 in the axial direction. It is designed to be moved to. According to such a configuration, the feed angle (the amount of axial movement with respect to the rotation angle) can be set larger than that of the so-called screw type which is used by rotating 360 degrees or more, so that the rotational movement can be changed to the axial movement. The conversion can be realized in a preferred manner. For example, the pilot valve body 30 can be greatly operated with a slight rotation, and the responsiveness is improved.

[Action and effect (1): Action and effect brought about by the shaft member 32a and the tip member 32b]
In the present embodiment, the cross-sectional area of the region of the shaft member 32a that penetrates the watertight seal 34 is smaller than the opening area of the end 13e of the outflow hole 13 on the back pressure chamber side. Therefore, with respect to the influence of the force acting on the pilot valve body 30, the degree of the holding force by the shaft member 32a is smaller than the degree of the negative pressure change accompanying the change in the opening degree of the outflow hole 13.

As described above, the conventional pilot valve body is held by a longitudinal member having a diameter of about three times the diameter of the outflow hole. In this case, as shown in FIG. 24, the force that urges such a large-diameter longitudinal member in the valve opening direction (atmospheric pressure received by the cross section of the region that escapes to the atmosphere through the watertight seal and the longitudinal member Because it works sufficiently (corresponding to the difference in water pressure acting on the water contact surface) (due to valve closure, even if the force acting on the region blocking the outflow hole 13 of the longitudinal member changes from water pressure to atmospheric pressure, it still opens. The force urging in the valve direction is predominant (it is necessary to apply a downward force to close the valve), and even if it receives a large negative pressure just before the outflow hole closes, the holding force of the longitudinal member Since it is still predominant, there is no risk of fluctuation or fluctuation in the behavior of the pilot valve body, and the control of the pilot valve body is stable.

As shown in FIG. 25, in the case of a modified example in which the diameter of the shaft member 32a and the diameter of the outflow hole 13 are made equal to each other, the holding force of the shaft member 32a sufficiently acts while the outflow hole 13 is open. However, when the negative pressure immediately before the outflow hole 13 is closed, the holding force of the shaft member 32a is canceled out, and the behavior of the pilot valve body 30 is shaken or fluctuated to control the pilot valve body 30. Becomes unstable. This is because when the total force acting is close to zero, it swings positively and negatively and becomes unstable. (When the force acting on the region closing the outflow hole 13 of the longitudinal member changes from water pressure to atmospheric pressure due to valve closing, the force urging in the valve opening direction disappears.)

On the other hand, in the present embodiment, the diameter of the shaft member 32a holding the pilot valve body 30 is made smaller than the diameter of the outflow hole 13. In this case, as shown in FIG. 26, when the opening degree of the pilot valve body 30 is large, the holding force by the shaft member 32a is sufficiently acting, but gradually as the opening degree of the pilot valve body 30 becomes smaller. The increasing negative pressure cancels out the holding force of the shaft member 32a, and when the pilot valve body 30 has a predetermined opening degree (point A in FIG. 26), the behavior of the pilot valve body 30 may fluctuate or fluctuate. .. However, at the opening degree (point A in FIG. 26), the flow rate is not small, so that high control accuracy is not required, that is, there is no practical problem. In the region of the minute opening where the highest control accuracy is desired at the time of closing, the negative pressure is superior to the holding force of the shaft member 32a, so that the behavior of the pilot valve body 30 fluctuates or fluctuates. Is not likely to occur, and the control of the pilot valve body 30 is stable. (When the force acting on the region closing the outflow hole 13 of the longitudinal member changes from water pressure to atmospheric pressure due to valve closing, the force urging in the valve closing direction becomes predominant (a downward force is applied to close the valve). No need to do).)

Moreover, according to the present embodiment, since it is sufficient to move the shaft member 32a having a small diameter for moving the pilot valve body 30, relatively low energy is sufficient. Further, there is also an effect that the resistance due to the watertight seal 34 when the shaft member 32a moves is small. Further, the fact that the force acting on the pilot valve body 30 is in the closing direction at the time of closing also has an effect of enabling reliable valve closing without any other urging force.

Further, in the present embodiment, the longitudinal member 32 is separated into a shaft member 32a including a region penetrating the watertight seal 34 and a tip member 32b holding the pilot valve body 30. As a result, only the cross-sectional area of the shaft member 32a needs to be smaller than the opening area of the end 13e on the back pressure chamber side of the outflow hole 13, and the cross-sectional area of the tip member 32b can be freely designed. In other words, the length of the shaft member 32a having a small cross-sectional area can be shortened by the amount of the tip member 32b. As a result, it is possible to prevent the shaft member 32a from being bent or bent.

Further, in the present embodiment, the tip member 32b is slidably connected to the shaft member 32a in a predetermined range in the axial direction, and the tip member 32b is connected between the tip member 32b and the shaft member 32a. An elastic member 32c is provided to urge the shaft member 32a and the shaft member 32a in a direction away from each other. As a result, it is avoided that the pilot valve body 30 is pressed against the outflow hole 13 with an excessive force due to the cushioning action of the elastic member 32c. Further, as a result, even when the shaft member 32a is slightly tilted, the pilot valve body 30 acts to follow the position of the outflow hole 13 so that the valve closing operation can be reliably performed.

Here, as a configuration for avoiding the pilot valve body 30 being pressed against the outflow hole 13 with an excessive force, the tip member 32b slides relative to the shaft member 32a in a predetermined range in the axial direction. An elastic member may be provided so as to be able to connect the tip member 32b and the upper surface of the hollow portion 21 (see FIGS. 2 to 4) in a direction away from each other.

Further, in the present embodiment, a flow path 32g for moving the liquid is formed on the radial outer surface of the tip member 32b. As a result, it is possible to effectively prevent the presence of the liquid from hindering the movement when the tip member 32b moves.

Further, in the present embodiment, the shaft member 32a penetrates a part of the lifter 40, and the shaft member 32a is engaged with the lifter 40 via the E-ring 71 which is a retaining mechanism. As a result, even if the shaft member 32a is thin, it can be securely fixed to the lifter 40. Further, since the shaft member 32a can be made thin, the contact area between the shaft member 32a and each member can be reduced, and the sliding resistance generated between the shaft member 32a and each member can be reduced.

Further, in the present embodiment, the pilot valve body 30 is adhered to one end of the tip member 32b. As a result, it is possible to effectively suppress the occurrence of "rattling" between the tip member 32b and the pilot valve body 30.

Further, in the present embodiment, the elastic force of the elastic member 32c of the longitudinal member 32 is smaller than the elastic force of the elastic resin member 72 which is the urging connection member. As a result, damage to the longitudinal member 32 can be effectively suppressed.

[Action and effect (2): Action and effect brought about by the elastic resin member 72]
In the present embodiment, the shaft member 32a is connected to the lifter 40 in a state of being urged to the back pressure chamber side in the axial direction by the elastic resin member 72 which is a urging connection member. As a result, the occurrence of backlash that may occur due to the connection mode between the shaft member 32a and the lifter 40 can be suppressed even more reliably. This, in combination with the fact that the coil spring 73 suppresses the occurrence of backlash that may occur between the rotating shaft 61 and the lifter 40, enhances the effect of suppressing hysteresis in the flow rate adjustment control.

Further, since the possibility of variation occurring in the positioning of the pilot valve body 30 is remarkably reduced, water can be reliably stopped even if the water stop region is minimized. This makes it possible to achieve both reliable water stoppage and quick responsiveness.

In addition, blurring and wobbling of the pilot valve body 30 are prevented.

Further, in the present embodiment, the direction in which the shaft member 32a is urged by the elastic resin member 72 with respect to the lifter 40 and the direction in which the lifter 40 is urged by the coil spring 73 with respect to the rotating shaft 61 are defined. Both are in the direction of closing the pilot valve body 30. As a result, the pilot valve body 30 can stably maintain the valve closed state even when the stepping motor 60 fails.

Further, in the present embodiment, the elastic resin member 72 rotates integrally with the lifter 40. As a result, a large torsional moment is not generated between the lifter 40 and the elastic resin member 72, and the generation of sliding resistance between the elastic resin member 72 and the lifter 40 is also reduced. Therefore, the torque applied to the stepping motor 60 is reduced. It is also possible to reduce the size of the stepping motor 60.

[Action / Effect (3): Action / Effect brought about by symmetrically arranged inflow holes 12]
According to the present embodiment, by adopting the form and arrangement of the main valve body 10 and the two inflow holes 12 as described above, each inflow hole is in a state where the pilot valve body 30 opens the outflow hole 13. The absolute value of the sum of the moments acting on the main valve body 10 based on the liquid flowing into the back pressure chamber 4 from 12 is approximately 0 Nm.

By adjusting the shape or arrangement of the main valve body 10 and the two inflow holes 12 so as to satisfy the above conditions, it is surely suppressed that the main valve body 10 is tilted during movement. ..

The moment acting on the main valve body 10 based on the liquid flowing into the back pressure chamber 4 from each of the two inflow holes 12 or the force acting by the moment may be actually measured, but the flow rate adjusting valve It can be evaluated by a computer-aided analysis method called CAE (Computer Aided Engineering) or CFD (Computational Fluid Dynamics), which is widely used in the design of 1. Specifically, by preparing a 3D model based on the dimensional data of the main valve body 10 and analyzing the flow of water using a computer, the direction or magnitude of the moment or force acting on the main valve body 10 Can be sought. As an example, "SCRYU / Tetra" provided by Software Cradle Co., Ltd. can be used.

In the present embodiment, the number of inflow holes 12 is "2", but the absolute value of the sum of the moments acting on the main valve body 10 based on the liquid flowing into the back pressure chamber 4 from each inflow hole 12. As long as it is 0.001 Nm or less, it may be three or more.

Further, in the present embodiment, the two inflow holes 12 are provided in the main valve body 10. As a result, the number, position, shape, size, and the like of the inflow holes 12 can be designed at the same time as the design of the main valve body 10.

Further, in the present embodiment, each of the two inflow holes 12 is provided as a linear path in the main valve body 10. As a result, the pressure loss in the inflow hole 12 is small, and the inflow of fluid and / or the discharge of air can be efficiently performed.

Further, the main valve body 10 of the present embodiment has a shape substantially symmetrical around the axis X, and the center of gravity of the main valve body 10 exists on the axis X. As a result, the balance with respect to the gravity of the main valve body 10 itself is good, and it is easy to design for suppressing the main valve body 10 from tilting during movement.

Further, in the present embodiment, the two inflow holes 12 are arranged so as to form a pair at symmetrical positions with the axis X of the main valve body 10 interposed therebetween. As a result, the moments acting on the main valve body 10 due to the inflow of liquid from the inflow holes 12 arranged in pairs cancel each other out, so that it is effective that the main valve body 10 is tilted during movement. Is suppressed.

Here, when the cross section of the inflow hole 12 is not isotropic, it is preferable that the paired inflow holes 12 are mirror image symmetric with respect to the axis of the main valve body 10 in the cross-sectional shape.

Further, in the present embodiment, when the main valve body 10 is arranged so that the opening / closing direction is horizontal, the two inflow holes 12 are located in the upper region and the lower side with respect to the axis X of the main valve body 10. One will be placed in each of the areas. In this case, in a situation where no fluid exists in the back pressure chamber 4 (for example, when the equipment is installed), the liquid flows in from the upper and lower inflow holes 12 in a well-balanced manner and the air is discharged, so that the internal replacement with the liquid is promoted. Is smooth, and the phenomenon of so-called air biting is unlikely to occur. In addition, air replacement when draining water is also smooth.

[Adjustment of stopper and its action effect]
Due to the variation (accumulation of variation of each member) that may occur in the assembly process of the flow rate adjusting valve 1 of the present embodiment, in order to realize the desired range of the stroke of the pilot valve body 30, the regulation range by the stopper 80 is set. , It is effective to adjust each individual flow rate adjusting valve 1.

Specifically, for example, regarding the valve closing position (the control position of the pilot valve body 30 on the valve closing side), if the margin is too small, there is a high concern that water stoppage failure will occur, and if the margin is too large, the valve opening responsiveness will increase. Since there is a problem of lowering, it is preferable to adjust the stroke of the pilot valve body 30 so that an appropriate valve closing position can be realized for each flow rate adjusting valve 1.

Therefore, in the flow rate adjusting valve 1 of the present embodiment, the stopper 80 is selectively held in either a temporarily fixed state in which the position can be changed or a fixed state in which the position cannot be changed. There is.

As shown in FIGS. 16 to 18, the stopper 80 of the present embodiment has a tubular shape cut out in a substantially C-shaped cross section in order to limit the rotation range of the stopper regulating portion 58 of the joint member 50. .. As a result, the cost of the stopper 80 itself can be kept low, and the arrangement of the stopper 80 can be easily accommodated in a small space.

Then, as shown by the arrow in FIG. 18, such a stopper 80 is sandwiched from both sides in the axial direction to expand the diameter, so that the position cannot be changed. By adopting such a configuration, switching between the temporarily fixed state and the fixed state of the stopper 80 is realized at a low cost. Further, since the force of the stopper 80 which has been pinched and expanded in diameter tries to return (reduces the diameter) acts in the direction of increasing the axial length of the stopper 80, the pinching pressure increases as a result. The fixed state becomes stable.

Specifically, in the case of the present embodiment, as shown in FIGS. 1 to 4, the stopper 80 includes a case member 91 arranged on the outer peripheral side of the lifter 40 and a lid fixed to the housing 62 of the stepping motor 60. It is sandwiched by the member 92 and is in a fixed state. On the contrary, in the state where the gap is interposed between the case member 91 and the lid member 92, the stopper 80 can rotate around its axis, that is, it is in a temporarily fixed state in which the position can be changed.

Since the lid member 92 also has a configuration for switching between the temporarily fixed state and the fixed state of the stopper 80 and a configuration for fixing the stepping motor 60, it contributes to suppressing an increase in the number of parts. ing.

In the present embodiment, the case member 91 and the lid member 92 are fastened to each other by one screw member 93 to hold the stopper 80, but even if the number of screw members 93 is two or more. Alternatively, a fastening member other than the screw member may be used.

Here, as can be seen from FIGS. 2 to 4, the rotation axis of the screw member 93 is offset with respect to the axis of the stopper 80. This prevents the stopper 80 from undesirably rotating and changing its position when the screw member 93 is operated.

Further, as can be seen from FIG. 18, the lower end of the stopper 80 of the present embodiment in the axial direction has an inclination 82 (a part of a conical surface whose inner peripheral side is recessed) in which the length in the axial direction increases toward the outer peripheral side. (Equivalent to) 82 is provided. With such a form, the stopper 80 is expanded in diameter in a well-balanced manner around the axis when the pressure is narrowed. Further, since the eccentricity of the member is unlikely to occur and the stopper 80 is stabilized in a state where the pressure is narrowed and the diameter is expanded, the fixed state in which the position of the stopper 80 cannot be changed is stable. A similar slope may be provided at the upper end of the stopper 80 in addition to or in place of the lower end of the stopper 80.

In the present embodiment, the length in the axial direction is further reduced toward the outer peripheral side on the upper surface of the case member 91 (shown in FIGS. 2 to 4) to which the pinching pressure is applied to the lower end in the axial direction of the stopper 80. An inclined surface 91t (corresponding to a part of a conical surface whose outer peripheral side is recessed) is formed. Also by this, the stopper 80 is expanded in diameter in a well-balanced manner around the axis when the pressure is narrowed. A similar inclined surface may be provided on the lower surface of the lid member 92 in addition to or instead of the upper surface of the case member 91.

In the present embodiment, a part of the stopper 80 is exposed to the outside from the window portion 92w provided on the lid member 92. Further, as shown in FIGS. 16 and 17, the stopper 80 is provided with a vertical stripe pattern that functions as a scale, and is further provided with a knob portion 81 for adjustment work. On the other hand, the mark 92i is also attached to the window portion 92w. By adjusting these relative positional relationships, the position of the stopper 80 can be adjusted for each individual flow rate adjusting valve 1.

Specifically, the case member 91 and the lid member 92 as the stopper holding members hold the stopper 80 in a temporarily fixed state in which the position can be changed. Specifically, a state in which a gap is interposed between the case member 91 and the lid member 92 (a state in which the lid member 92 is slightly floated) is maintained. In this state, the flow rate adjusting valve 1 is connected to the flow path, the stepping motor 60 is driven, and the water flow and water stop tests are performed. While performing the test, the knob portion 81 is rotated left and right to search for the position of the stopper 80 that can obtain the desired water stop control. Then, at the position of the stopper 80 found, the case member 91 and the lid member 92 are fastened to each other, and the stopper 80 is pinched to increase the diameter. As a result, the stopper 80 is in a fixed state in which the position cannot be changed.

The water flow and water stoppage tests may be performed using a manual adjustment jig 85 without using the stepping motor 60. 27 is a perspective view of the manual adjustment jig 85 viewed from diagonally above, FIG. 28 is a perspective view of the manual adjustment jig 85 viewed from diagonally below, and FIG. 29 is a joint member 50 using the manual adjustment jig 85. It is a perspective view of the flow rate adjustment valve 1 at the time of work which adjusts the position of a stopper 80.

Even when the manual adjustment jig 85 is used, the stopper 80 is held in a temporarily fixed state in which the position can be changed by the case member 91 and the lid member 92 as the stopper holding members. Specifically, a state in which a gap is interposed between the case member 91 and the lid member 92 (a state in which the lid member 92 is slightly floated) is maintained. On the other hand, the flow rate adjusting valve 1 is connected to the flow path with the stepping motor 60 (including the rotating shaft 61 and the housing 62) removed from the lid member 92.

Then, instead of the stepping motor 60, a manual adjustment jig 85 is connected to the joint member 50 to the rotation shaft receiving portion 56, and the joint member 50 and the stopper 80 are manually rotated using the manual adjustment jig 85 to pass through. Water and water stoppage tests are conducted. While conducting the test, the manual adjustment jig 85 is rotated left and right to search for the positions of the joint member 50 and the stopper 80 to obtain the desired water stop control. Then, at the position of the stopper 80 found, the case member 91 and the lid member 92 are fastened, and the stopper 80 is pinched to increase the diameter. As a result, the stopper 80 is in a fixed state in which the position cannot be changed.

As described above, according to the present embodiment, the position of the stopper 80 can be easily adjusted for each individual flow rate adjusting valve 1, so that the stroke of the valve body can be adjusted so that an appropriate valve closing position can be realized. This can be easily realized for each adjusting valve 1.

[Unitization of drive unit and its action effect]
An exploded perspective view of the flow rate adjusting valve 1 of the present embodiment is shown in FIG. In addition, enlarged views of regions A, B, and C in FIG. 30 are shown in FIGS. 31 to 33, respectively.

In the flow rate adjusting valve of the present embodiment, the members shown in FIGS. 31 and 32 are integrally unitized to form the drive unit 101. Then, the drive unit 101 can be integrally attached to and detached from the base 102 including the flow paths 2, 3 and the main valve body 10.

With such a configuration, it is sufficient to remove the drive unit 101 with respect to the base 102 during normal maintenance work. That is, it is not necessary to disassemble the inside of the drive unit 101. Therefore, the accumulation of variations among the members constituting the drive unit 101 does not change before and after the maintenance work. As a result, high flow rate adjustment performance can be maintained without readjustment of the regulation range by the stopper 80.

Further, with such a configuration, when the drive unit 101 is removed from the base 102, both the main valve body 10 and the pilot valve body 30 are exposed. Therefore, maintenance work for these valve bodies 10 and 30 can be performed quickly and easily. In particular, since the main valve body 10 having a high maintenance frequency (particularly the replacement frequency) is separate from the drive unit 101, the workability of the maintenance work is high.

In order to facilitate understanding of these circumstances, an exploded perspective view in which the drive unit 101 and the base 102 are removed from each other and the main valve body 10 of the base 102 is removed is shown in FIGS. 34 and 35. FIG. 34 is an exploded perspective view from diagonally above, and FIG. 35 is an exploded perspective view from diagonally below.

Further, in the present embodiment, the fastening member for fastening each component of the drive unit 101 and the assembly member for assembling the drive unit 101 and the base 102 are different types of members. Specifically, one screw member 93 that fastens the case member 91 and the lid member 92 to each other, and two screw members 96 that fix the housing 62 of the stepping motor 60 to the lid member 92 are special. It is a screw member. The special screw member means a deformed screw member that requires a special tool, such as a so-called star-shaped screw member. The assembly member 103 for assembling the unit 101 and the base 102 is composed of four ordinary screw members. As a result, it is effectively prevented that the screw members 93 and 96 in the drive unit 101 are accidentally removed during the removal work of the assembly member 103.

Further, in the present embodiment, as can be seen from FIG. 32, the assembling member 103, which is four ordinary screw members, extends in the same direction. As a result, the operability of these screw members is high. For example, it is possible to attach / detach the drive unit 101 to / from the base 102 without having to rotate the flow rate adjusting valve 1 or change the posture.

Further, in the present embodiment, the diaphragm film of the main valve body 10 is formed between the lower end of the back pressure chamber forming member 20 which is the lowermost end of the drive unit 101 and the corresponding receiving portion 102a (see FIG. 34) of the base portion 102. A continuous seal portion 11s (see FIG. 2) is interposed at 11. The diaphragm film 11 functions as a watertight member and prevents liquid from leaking from the back pressure chamber 4. On the other hand, the lower surface 91b (see FIG. 35) of the case member 91 of the drive unit 101 and the corresponding upper surface 102b (see FIG. 34) of the base 102 are in direct contact with each other.

As a result, it is possible to always provide a predetermined "seal allowance" to the seal portion 11s without performing torque management of the four screw members 103 which are assembly members. Further, there is no concern that the drive unit 101 will be tilted due to variations in the degree of assembly of the four screw members 103.

In the present embodiment, after the drive unit 101 is assembled, one screw member 93 that fastens the case member 91 and the lid member 92 to each other is arranged at a position that is difficult to access. This is effective in preventing the position of the adjusted stopper 80 from being erroneously changed.

[Intermediate concept (1) obtained from the present embodiment: From the viewpoint of the longitudinal member 32]
The flow rate adjusting valve 1 that can be extracted from the present embodiment includes a main valve body 10 displaceably supported in the flow paths 2 and 3 via an elastic element (for example, a diaphragm film 11), and a predetermined flow rate adjusting valve 1 from the upstream side 2 of the flow path. A back pressure chamber 4 in which a liquid (for example, water and / or hot water) supplied at the pressure of the above pressure is accommodated and a force is generated by the liquid to urge the main valve body 10 in the valve closing direction, and upstream of the flow path. An inflow hole 12 that communicates between the side 2 and the back pressure chamber 4, an outflow hole 13 that communicates between the downstream side 3 of the flow path and the back pressure chamber 4, a pilot valve body 30 that opens and closes the outflow hole 13, and a pilot valve. A longitudinal member 32 that holds the body 30 and moves the pilot valve body 30 in its own axial direction, a rotating rotating member (for example, the rotating shaft 61 of the motor), and a rotating member that can rotate as the rotating member rotates. A lifter 40 that can move in the axial direction of the longitudinal member 32 in conjunction with the rotation is provided. The lifter 40 and the longitudinal member 32 are connected so as to move integrally in the axial direction, and the longitudinal member 32 is connected to a region on the back pressure chamber side where a liquid can exist via the watertight seal 34. The cross-sectional area of the region extending continuously to both the region on the atmosphere side where the liquid does not exist and penetrating the watertight seal 34 of the longitudinal member 32 is larger than the opening area of the end 13e on the back pressure chamber side of the outflow hole 13. Is also small.

Due to such a feature, since the configuration using the back pressure chamber 4 and the pilot valve body 30 is adopted, the main valve body 10 can be operated with a small force.

Since the cross-sectional area of the region of the longitudinal member 32 penetrating the watertight seal 34 is smaller than the opening area of the end 13e of the outflow hole 13 on the back pressure chamber side, the longitudinal member 32 is longitudinally affected by the force acting on the pilot valve body 30. The degree of the holding force by the member 32 is smaller than the degree of the negative pressure change accompanying the change in the opening degree of the outflow hole 13.

In this case, as described with reference to FIG. 26, when the opening degree of the pilot valve body 30 is large, the holding force by the longitudinal member 32 is sufficiently acting, but the opening degree of the pilot valve body 30 is small. The holding force of the longitudinal member 32 is offset by the negative pressure that gradually increases, and when the pilot valve body 30 has a predetermined opening (point A in FIG. 26), the behavior of the pilot valve body 30 fluctuates or fluctuates. Can occur. However, at the opening degree (point A in FIG. 26), the flow rate is not small, so that high control accuracy is not required, that is, there is no practical problem. In the region of minute opening where high control accuracy is required to achieve so-called stable flow rate control at the time of closing, that is, stable movement and holding of the main valve body, the negative pressure is held by the longitudinal member. Since it is superior to force, there is no risk of blurring or fluctuation in the behavior of the pilot valve body, and the control of the pilot valve body is stable. (When the force acting on the region closing the outflow hole 13 of the longitudinal member changes from water pressure to atmospheric pressure due to valve closing, the force urging in the valve closing direction becomes predominant (a downward force is applied to close the valve). No need to do).)

Moreover, since it is sufficient to move the thin longitudinal member 32 for the movement of the pilot valve body 30, relatively low energy is sufficient. Further, there is also an effect that the resistance due to the watertight seal 34 when the longitudinal member 32 is moved is small. Further, the fact that the force acting on the pilot valve body 30 is in the closing direction at the time of closing also has an effect of enabling reliable valve closing without any other urging force.

Here, the shape of the opening cross section of the outflow hole 13 or the cross section of the longitudinal member 32 is not limited to the case of being circular.

Further, as described above, the longitudinal member 32 is preferably configured to include a shaft member 32a including a region penetrating the watertight seal 34 and a tip member 32b for holding the pilot valve body 30. In this case, only the cross-sectional area of the shaft member 32a needs to be smaller than the opening area of the end 13e on the back pressure chamber side of the outflow hole 13, and the cross-sectional area of the tip member 32b can be freely designed. In other words, the length of the shaft member 32a having a small cross-sectional area can be shortened by the amount of the tip member 32b, and the shaft member 32a can be prevented from being bent or bent.

Further, as described above, the tip member 32b is connected to the shaft member 32a so as to be relatively slidable in a predetermined range in the axial direction, and is an elastic member that urges the tip member 32b in the valve closing direction. It is preferable that 32c is provided. In this case, the cushioning action of the elastic member 32c prevents the pilot valve body 30 from being pressed against the outflow hole 13 with an excessive force. Further, in this case, even when the shaft member 32a is slightly tilted, the pilot valve body 30 acts to follow the position of the outflow hole 13 to ensure the valve closing operation.

Further, as described above, it is preferable that the tip member 32b has a flow path 32g for moving the liquid formed in at least a part of the outer surface in the radial direction. In this case, it is possible to effectively prevent the presence of the liquid from hindering the movement when the tip member 32b moves.

Further, as described above, it is preferable that the longitudinal member 32 penetrates a part of the lifter 40, and the longitudinal member 32 is engaged with the lifter 40 via a retaining mechanism. In this case, it is possible to reliably prevent the longitudinal member 32 from coming off the lifter 40. Further, the retaining mechanism preferably has an E-ring 71. In this case, even if the longitudinal member 32 is thin, it can be securely fixed to the lifter 40. Further, since the longitudinal member 32 can be made thinner, the contact area between the longitudinal member 32 and each member can be reduced, and the sliding resistance generated between the longitudinal member and each member can be reduced.

Further, as described above, it is preferable that the longitudinal member 32 is connected to the lifter 40 in a state of being urged to one side in the axial direction by the urging connecting member. In this case, since the longitudinal member 32 is urged to one side in the axial direction, the pilot valve body 30 is prevented from shaking or wobbling. This action is particularly effective in the vicinity of a predetermined opening degree (point A in FIG. 26) where the total force acting on the pilot valve body 30 becomes zero.

In the flow rate adjusting valve 1 according to the intermediate concept (1), the rotating member is not limited to the rotating shaft 61 of the stepping motor 60, and may be a rotating member that is manually rotated. That is, the flow rate adjusting valve 1 may be a manual flow rate adjusting valve.

[Intermediate concept (2) obtained from the present embodiment: From the viewpoint of the elastic resin member 72]
The flow rate adjusting valve 1 that can be extracted from the present embodiment includes a main valve body 10 displaceably supported in the flow paths 2 and 3 via an elastic element (for example, a diaphragm film 11) and a predetermined flow rate adjusting valve 1 from the upstream side 2 of the flow path. The back pressure chamber 4 in which the liquid (for example, water and / or hot water) supplied at the pressure of the above pressure is accommodated and the force for urging the main valve body 10 in the valve closing direction is generated by the liquid, and the upstream of the flow path. The inflow hole 12 that communicates the side 2 and the back pressure chamber 4, the outflow hole 13 that communicates the downstream side 3 of the flow path and the back pressure chamber 4, and the end 13e of the outflow hole 13 on the back pressure chamber side are opened and closed. For the rotation of the pilot valve body 30, the longitudinal member 32 that holds the pilot valve body 30 and moves the pilot valve body 30 in the axial direction of itself, the rotating rotating member (for example, the rotating shaft 61), and the rotating member. It is provided with a lifter 40 that is rotatable along with the movement and is also movable in the axial direction of the longitudinal member 32 in conjunction with the rotation. The lifter 40 and the longitudinal member 32 are connected so as to move integrally in the axial direction, and the longitudinal member 32 is shafted with respect to the lifter 40 by an urging connecting member (for example, an elastic resin member 72). It is connected in a urged state on one side of the direction.

Due to such a feature, since the configuration using the back pressure chamber 4 and the pilot valve body 30 is adopted, the main valve body 10 can be operated with a small force.

Since the longitudinal member 32 is connected to the lifter 40 in a state of being urged to one side in the axial direction by the urging connecting member, it is caused by the connection mode between the longitudinal member 32 and the lifter 40. The occurrence of backlash that may occur can be suppressed even more reliably. This enhances the effect of suppressing hysteresis in the flow rate adjustment control. Further, since the possibility of variation occurring in the positioning of the pilot valve body 30 is remarkably reduced, water can be reliably stopped even if the water stop region is minimized. As a result, it is possible to achieve both reliable water stoppage and quick response.

From the viewpoint of shifting the constituent members to one side, as described above, the lifter 40 is urged to one side in the axial direction by the urging member, for example, the coil spring 73, with respect to the rotating member (for example, the rotating shaft 61). Is preferable. In this case, the occurrence of backlash that may occur between the rotating member (for example, the rotating shaft 61) and the lifter 40 can be reliably suppressed. This enhances the effect of suppressing hysteresis in the flow rate adjustment control.

Further, as described above, the joint member 50 which engages with the lifter 40 in the rotational direction and transmits the rotation of the rotating member to the lifter 40 is provided, and the urging member (for example, the coil spring 73) is the joint member 50 and the lifter. It is preferable that the joint member 50, the urging member, and the lifter 40 rotate integrally by urging the 40 in a direction that is axially separated from each other. In this case, since the joint member 50, the urging member, and the lifter 40 rotate integrally, no twisting moment is applied to the urging member, and the relative positions of the rotating member and the joint member 50 are also fixed. Therefore, the rotational motion can be smoothly converted into the axial motion.

Further, as described above, the rotating member is the rotating shaft 61 of the motor, and the urging member (for example, the coil spring 73) always urges the rotating shaft 61 in the same rotational direction via the joint member 50. It is preferable to have. In this case, when a force is generated between the joint member 50 and the lifter 40 in the direction of separation, the force is also generated in the joint member 50 in the direction of rotation due to the engagement between the two. By transmitting the force in the rotating direction to the rotating shaft 61 of the motor, the internal members of the motor can be offset in one direction in the rotating direction via the rotating shaft 61. This enhances the effect of suppressing hysteresis in the flow rate adjustment control. If the motor is a stepping motor 60, flow rate control can be realized by computer control. Further, even when controlling a small flow rate, stable water discharge is possible by finely controlling the stepping motor 60. However, the motor is not limited to the stepping motor 60, and other types of motors may be used.

Further, as described above, it is preferable that the urging member (for example, the coil spring 73) is urged with a force equal to or less than the detent torque of the motor. In this case, it is not necessary to constantly supply electric power to the motor when maintaining the positioning state of the pilot valve body 30.

Further, as described above, the lifter 40 is provided with the protrusion 42, and the lifter 40 is brought into the axial direction by contacting the protrusion 42 of the lifter 40 and guiding the protrusion 42 in the axial direction as the lifter 40 rotates. It is preferable to have a guide slope 23 to be moved. In this case, since the feed angle (amount of axial movement with respect to the rotation angle) can be set larger than that of the so-called screw type used by rotating 360 degrees or more, the conversion of the rotational movement to the axial movement is a preferable embodiment. Can be realized with. According to this, the valve body can be greatly operated with a slight rotation, and the responsiveness is improved.

In particular, the lifter 40 is provided with a plurality of protrusions 42 in the rotation direction, and the lifter 40 abuts on each of the plurality of protrusions 42 of the lifter 40 and guides the protrusions 42 in the axial direction as the lifter 40 rotates. It is preferable to have a plurality of guide slopes 23 for moving the shaft in the axial direction. If there are a plurality of guide points due to the contact between the protrusion 42 and the guide slope 23, the conversion of the rotational motion into the axial motion is even smoother. For example, as described above, it is preferable that the plurality of protrusions 42 are provided with three equally distributed (arranged at 120 ° intervals) in the rotation direction.

Further, as described above, the lifter 40 is attached to the rotating member (for example, the rotating shaft 61) in the direction in which the longitudinal member 32 is urged to the lifter 40 by the urging connecting member (for example, the elastic resin member 72). It is preferable that the direction is the same as the direction urged by the urging member (for example, the coil spring 73). In this case, the hysteresis in the flow rate adjustment control can be suppressed more reliably.

Further, as described above, the longitudinal member 32 is urged to the lifter 40 by the urging connection member (for example, the elastic resin member 72), and the lifter 40 is attached to the rotating member (for example, the rotating shaft 61). The direction urged by the urging member (for example, the coil spring 73) is preferably the direction in which the pilot valve body 30 is closed. In this case, the pilot valve body 30 can stably maintain the valve closed state even when the rotating member fails.

Further, as described above, it is preferable that the pilot valve body 30 is adhered to one end of the longitudinal member 32. In this case, it is possible to effectively suppress the occurrence of "rattling" between the longitudinal member 32 and the pilot valve body 30.

Further, as described above, the longitudinal member 32 preferably has elasticity that expands and contracts in the axial direction. In this case, when the pilot valve body 30 is excessively pressed against the outflow hole 13, the excessive force can be absorbed by the elasticity of the longitudinal member 32.

Further, as described above, the elastic force of the longitudinal member 32 is preferably smaller than the elastic force of the urging connection member (elastic resin member 72). In this case, since the longitudinal member 32 is more likely to contract than the urging connecting member, damage to the longitudinal member 32 can be effectively suppressed.

Further, as described above, it is preferable that the urging connection member rotates integrally with the lifter 40. In this case, a large moment is not generated between the lifter 40 and the urging connection member, and the generation of sliding resistance between the urging connection member and the lifter 40 is also reduced, so that the torque applied to the rotating member is reduced. In addition, the rotating member (driving mechanism) can be miniaturized.

In the flow rate adjusting valve 1 according to the intermediate concept (2), the rotating member is not limited to the rotating shaft 61 of the stepping motor 60, and may be a rotating member that is manually rotated. That is, the flow rate adjusting valve 1 may be a manual flow rate adjusting valve.

[Intermediate concept (3) obtained from the present embodiment: From the viewpoint of the inflow hole 11]
The flow rate adjusting valve 1 that can be extracted from the present embodiment is supplied at a predetermined pressure from the main valve body 10 displaceably supported in the flow paths 2 and 3 via the diaphragm film 11 and the upstream side 2 of the flow path. An inflow hole that communicates the back pressure chamber 4 that accommodates the liquid and generates a force that urges the main valve body 10 in the valve closing direction, and the upstream side 2 of the flow path and the back pressure chamber 4. A 12 and an outflow hole 13 that communicates the downstream side 3 of the flow path with the back pressure chamber 4 and a pilot valve body 30 that opens and closes the outflow hole 13 are provided. A plurality of inflow holes 12 are provided, and in a state where the pilot valve body 30 opens the outflow holes 13, the main inflow holes 12 are based on the liquid flowing into the back pressure chamber 4 from each of the plurality of inflow holes 12. The sum of the moments acting on the valve body 10 cancels each other out (adjusted to be within 0.001 Nm).

Due to such a feature, since the configuration using the back pressure chamber 4 and the pilot valve body 30 is adopted, the main valve body 10 can be operated with a small force.

Then, in a state where a plurality of inflow holes 12 are provided and the pilot valve body 30 opens the outflow holes 13, the main valve is based on the liquid flowing into the back pressure chamber 4 from each of the plurality of inflow holes 12. Since the absolute value of the sum of the moments acting on the body 10 is adjusted to be within 0.001 Nm, the forces of tilting the main valve body 10 during movement cancel each other out, and the main valve body 10 cancels out. The posture of is stably maintained.

As described above, the moment acting on the main valve body 10 based on the liquid flowing into the back pressure chamber 4 from each of the plurality of inflow holes 12 is CAE (Computer Aided Engineering) widely used in the design of the flow rate adjusting valve 1. ) And CFD (Computational Fluid Dynamics), which can be evaluated by a computer-aided analysis method.

Further, as described above, it is preferable that the plurality of inflow holes 12 are provided in the main valve body 10. In this case, the number, position, shape, size, etc. of the inflow holes 12 can be designed at the same time as the design of the main valve body 10.

Further, as described above, it is preferable that each of the plurality of inflow holes 12 is provided as a linear path in the main valve body 10. In this case, since the pressure loss in the inflow hole 12 is small, the inflow of fluid and / or the discharge of air can be efficiently performed.

Further, as described above, it is preferable that the main valve body 10 has a shape substantially symmetrical around the axis X (see FIG. 2), and the center of gravity of the main valve body 10 exists on the axis X. In this case, since the main valve body 10 itself has a good balance with respect to gravity, it is easy to design to prevent the main valve body 10 from tilting during movement (during opening / closing operation).

Further, as described above, it is preferable that the plurality of inflow holes 12 are arranged so as to form a pair at symmetrical positions with the axis X of the main valve body 10 interposed therebetween. In this case, it is effective that the main valve body 10 is tilted during movement because the moments acting on the main valve body 10 due to the inflow of liquid from the inflow holes 12 arranged so as to form a pair cancel each other out. Is suppressed. It is preferable that the paired inflow holes 12 are mirror image symmetric with respect to the axis X of the main valve body 10 even in its (cross-sectional) shape. However, usually, the cross section of each inflow hole 12 is circular (isotropic).

Further, as described above, the main valve body 10 is arranged so that the opening / closing direction of the main valve body 10 is horizontal, and the plurality of inflow holes 12 are regions above the axis X of the main valve body 10. It is preferable that at least one is arranged in each of the lower region and the lower region. In this case, in a situation where the liquid does not exist in the back pressure chamber 4 (for example, when the equipment is installed), the liquid flows in from the upper and lower inflow holes 12 in a well-balanced manner and the air is discharged, so that the internal replacement with the liquid is promoted. Is smooth, and the phenomenon of so-called air biting is unlikely to occur. In addition, air replacement when draining water is also smooth.

Further, as described above, it is preferable that the main valve body 10 is fixed in the flow paths 2 and 3 via the diaphragm film 11 so as not to rotate around the axis X. In this case, if the position of the inflow hole 12 with respect to the main valve body 10 is appropriately positioned, it is easy to arrange the inflow hole at a desired relative position.

Further, as described above, the pilot valve body 30 is preferably driven by the stepping motor 60. In this case, the operation of the pilot valve body 30 can be controlled with high accuracy.

In the flow rate adjusting valve 1 according to the intermediate concept (3), the rotating member is not limited to the rotating shaft 61 of the stepping motor 60, and may be a rotating member that is manually rotated. That is, the flow rate adjusting valve 1 may be a manual flow rate adjusting valve.

[Intermediate concept (4) obtained from the present embodiment: From the viewpoint of the stopper 80]
The flow rate adjusting valve 1 that can be extracted from the present embodiment includes a rotating rotating member (for example, a rotating shaft 61), a lifter 40 that can move linearly with the rotation of the rotating member, and a linear direction with the linear movement of the lifter 40. A valve body that can be moved to (for example, a pilot valve body 30), a stopper 80 that limits the range of movement of the lifter 40 in a fixed state in which the position cannot be changed, and a temporary fixed state in which the position of the stopper 80 can be changed. It includes a stopper holding member (for example, a case member 91 and a lid member 92) that selectively holds in any of the fixed states.

With such a feature, the position of the stopper 80 can be changed while the stopper 80 is temporarily fixed. Specifically, for example, after holding the stopper 80 in a temporarily fixed state in which the position can be changed, water flow and water stoppage tests are performed while changing the position of the stopper 80 to adjust the water stoppage area. After the adjustment, the stopper 80 can be held in a fixed state in which the position cannot be changed. As a result, the stroke of the valve body (for example, the pilot valve body 30) can be adjusted so that an appropriate valve closing position can be realized for each individual flow rate adjusting valve 1.

As described above, the range in which the position of the stopper 80 can be changed in the temporarily fixed state includes the water stop region. In this case, after holding the stopper 80 in a temporarily fixed state where the position can be changed, the water stoppage test can be performed while changing the position of the stopper 80 to adjust the water stoppage region. Then, after the adjustment, the stopper 80 can be held in a fixed state in which the position cannot be changed. As a result, the stroke of the valve body can be adjusted so that an appropriate valve closing position can be realized for each individual flow rate adjusting valve 1.

Further, when at least the stopper holding member (for example, the case member 91 and the lid member 92) holds the stopper 80 in the temporarily fixed state like the window portion 92w of the lid member 92 of the present embodiment, at least one of the stopper 80s. It is preferable to have a structure that exposes the portion to the outside. In this case, it is easy to change the position of the stopper 80 by working on at least a part of the stopper 80 exposed to the outside. Further, it is preferable that at least a part of the stopper 80 is a knob portion 81 for adjustment work.

Further, as described above, when the stopper holding member (for example, the case member 91 and the lid member 92) holds the stopper 80 in the temporarily fixed state, the scale relating to the temporarily fixed position of the stopper 80 can be visually recognized from the outside. preferable. In this case, since the adjuster can visually recognize and utilize the scale when adjusting the water stop area or the like, it is easy to adjust the water stop area or the like while changing the position of the stopper. is there. Specifically, in the present embodiment, the position of the stopper 80 is determined by utilizing the relative positional relationship between the vertical stripe pattern and the knob portion 81 attached to the stopper 80 and the mark 92i provided on the window portion 92w. It is easy to adjust the water stop area while changing.

Further, as described above, the lifter 40 is adapted to rotate with the rotation of the rotating shaft 61 which is a rotating member, and the lifter 40 is provided with a protrusion 42, which hits the protrusion 42 of the lifter 40. The stopper 80 has a guide slope 23 that moves the lifter 40 in the direction of the rotation axis by guiding the protrusion 42 in the direction of the rotation axis in contact with the lifter 40, and the stopper 80 limits the rotation range of the lifter to 360. It is preferable to limit it to less than °. In this case, since the feed angle (amount of axial movement with respect to the rotation angle) can be set larger than that of the so-called screw type used by rotating 360 degrees or more, the conversion of the rotational movement to the axial movement is a preferred embodiment. Can be realized with. According to this, it becomes possible to move the valve body greatly with a slight rotation, and the responsiveness is improved.

Further, as described above, the rotating member has a joint member 50 that engages with the lifter 40 in the rotational direction and transmits the rotation to the lifter 40, and the joint member 50 is a stopper regulating portion that projects to the outer peripheral side. The stopper 80 has a tubular shape cut out in a substantially C-shaped cross section, surrounds at least a part of the outer peripheral side of the joint member 50, and is a stopper regulating portion 58 of the joint member 50. By limiting the rotation range, the rotation movement circumference of the lifter 40 is limited. In this case, it is easy to limit the rotation range of the lifter 40 to less than 360 °, and the space occupied by the stopper 80 for surrounding at least a part of the outer peripheral side of the joint member 50 is small, so that space can be saved. , The cost of the stopper 80 itself can be kept low.

Further, as described above, it is preferable that the stopper 80 is in a fixed state in which the position cannot be changed by being pinched from both sides in the axial direction to be in a diameter-expanded state. In this case, the force of the stopper that has been pinched and expanded in diameter acts in the direction of increasing the length in the axial direction, so that the pinching pressure increases as a result. The fixed state is stable. Further, since it is possible to flexibly design a configuration for switching between the temporarily fixed state and the fixed state of the stopper, the configuration can be realized at a low cost.

Further, as described above, the rotating member is the rotating shaft 61 of the stepping motor 60, and the stopper 80 is a case member 91 arranged on the outer peripheral side of the lifter 40 and a lid member fixed to the housing 62 of the stepping motor 60. It is configured to be sandwiched by the 92, and further includes a fastening member for fastening the case member and the lid member. In this case, since the lid member 92 serves both as a configuration for switching between the temporarily fixed state and the fixed state of the stopper 80 and a configuration for fixing the stepping motor 60, it is possible to suppress an increase in the number of parts.

Further, as described above, the case member 91 that houses the lifter 40, the lid member 92 that closes the case member 91 from above, and the fastening member that fastens the case member 91 and the lid member 92 (for example, a special screw member 93). It is preferable that at least a part of the stopper 80 is sandwiched between the case member 91 and the lid member 92 and fixed in position. In this case, since at least a part of the stopper 80 is fixed in position by the case member 91 and the lid member 92 by the force of sandwiching from above and below, the possibility that the stopper 80 moves undesirably after the position is fixed is reduced. .. It also has the effect of reducing the number of parts.

Also in this case, as described above, the stopper 80 has a tubular shape notched in a substantially C-shaped cross section, and is pinched from both sides in the axial direction to expand the diameter, so that the position cannot be changed. It is preferable to be in a fixed state. In this case, the space occupied by the stopper 80 can be kept small, and the cost of the stopper 80 itself can be kept low. Further, the force of the stopper 80 that has been pinched and expanded in diameter acts in the direction of increasing the length in the axial direction to return (reduce the diameter) to the original position, and as a result, the pinching pressure increases. The fixed state is stable. Further, since it is possible to flexibly design a configuration for switching between the temporarily fixed state and the fixed state of the stopper 80, the configuration can be realized at a low cost.

Further, also in this case, as described above, the rotating member is the rotating shaft of the motor, the case member 91 is arranged on the outer peripheral side of the lifter 40, and the lid member 92 is fixed to the housing of the motor. The stopper 80 is preferably pressed by the case member 91 and the lid member 92. In this case, since the lid member 92 also serves as a configuration for switching between the temporarily fixed state and the fixed state of the stopper 80 and a configuration for fixing the motor, it is possible to suppress an increase in the number of parts.

Further, as described above, the rotating member is preferably the rotating shaft 61 of the stepping motor 60. In this case, the flow rate control can also be realized by computer control. Further, even when controlling a small flow rate, stable water discharge is possible by finely controlling the stepping motor 60.

Further, as described above, it is preferable that the fastening member is one or more screw members 93, and each rotation axis of the screw member 93 is offset with respect to the axis of the stopper 80. In this case, since it is suppressed that the stopper 80 is rotated even if each of the screw members 93 is operated, the stopper 80 undesirably rotates to change the position when each of the screw members 93 is operated. It is suppressed.

Further, as described above, it is preferable that one end or both ends of the stopper 80 in the axial direction are provided with an inclination 82 such that the length in the axial direction increases toward the outer peripheral side. In this case, since the stopper 80 is stabilized in a state where the pressure is narrowed and the diameter is expanded, the eccentricity of the member is unlikely to occur, and the fixed state in which the position of the stopper 80 cannot be changed is stable.

Further, as described above, the surface at which the member applying the pinching pressure to one end of the stopper 80 in the axial direction comes into contact with the stopper is an inclined surface whose length in the axial direction decreases toward the outer peripheral side. Is preferable. Also in this case, since the stopper 80 is stabilized in a state where the pressure is narrowed and the diameter is expanded, the eccentricity of the member is unlikely to occur, and the fixed state in which the position of the stopper 80 cannot be changed is stable.

The stopper 80 of the present embodiment regulates the rotation range of the lifter 40 by restricting the rotation of the stopper regulating portion 58 of the joint member 50, but regulates the linear movement range of the lifter 40. It may be installed so as to. Specifically, for example, a protrusion may be provided on the outer peripheral side of the lifter 40, and a stopper may be installed on the inner peripheral side of the case member 91 to regulate the movement range of the protrusion.

Further, two flow rate adjusting valves 1 having any of the above characteristics are provided, one of the two flow rate adjusting valves 1 is connected to a water supply source, and the other of the two flow rate adjusting valves 1 is a hot water supply. A hot water mixing faucet system characterized by being connected to a source may be provided. In this case, stable mixing of hot and cold water can be performed.

Further, in the method for manufacturing the flow rate adjusting valve 1 having any of the above characteristics, the stopper holding member (for example, the case member 91 and the lid member 92) holds the stopper 80 in a temporarily fixed state in which the position can be changed. A temporary fixing step, an adjustment step of adjusting the water stop region by performing a water flow and water stop test while changing the position of the stopper 80 while the stopper 80 is held in the temporarily fixed state, and the adjustment step. After that, a manufacturing method can be provided characterized in that the stopper holding member is provided with a fixing step of holding the stopper 80 in a fixed state in which the position cannot be changed.

By this method, the stroke of the valve body (pilot valve body 30) can be adjusted so that an appropriate valve closing position can be realized for each flow rate adjusting valve.

Further, in the method for manufacturing the flow rate adjusting valve 1 having the joint member 50 as described above, the stopper 80 is held in a temporarily fixed state in which the position of the stopper 80 can be changed to the stopper holding member (for example, the case member 91 and the lid member 92). In the temporary fixing step of making the stopper 80 and the stopper 80 held in the temporarily fixed state, the water flow and water stoppage tests are performed while changing the position of the stopper 80 together with the joint member 50 to adjust the water stoppage region. A manufacturing method can be provided characterized by comprising an adjusting step and, after the adjusting step, a fixing step of holding the stopper 80 in a fixed state in which the position of the stopper 80 cannot be changed.

Also by this method, the stroke of the valve body (pilot valve body 30) can be adjusted so that an appropriate valve closing position can be realized for each flow rate adjusting valve. When changing the position of the stopper 80 together with the joint member 50, it is preferable to use the manual adjustment jig 85.

In the flow rate adjusting valve 1 according to the intermediate concept (4), the rotating member is not limited to the rotating shaft 61 of the stepping motor 60, and may be a rotating member that is manually rotated. That is, the flow rate adjusting valve 1 may be a manual flow rate adjusting valve.

Further, the valve body of the flow rate adjusting valve 1 according to the intermediate concept (4) may be the main valve body 10 of the flow rate adjusting valve 1 (including a configuration having no pilot valve body), or a back pressure chamber. It may be a pilot valve body 30 that moves the main valve body 10 by utilizing the pressure of 4.

[Intermediate concept (5) obtained from the present embodiment: From the viewpoint of the drive unit 101]
The flow rate adjusting valve 1 that can be extracted from the present embodiment includes a rotating rotating member (for example, a rotating shaft 61), a lifter 40 that can move linearly with the rotation of the rotating member, and a linear direction with the linear movement of the lifter 40. A valve body (for example, a pilot valve body 30) that can be moved to a valve body, and a base 102 having a valve seat (for example, an end 13e on the back pressure chamber side of the outflow hole 13) that comes into contact with the valve body when the valve body is closed. ing. Then, a group of constituent members including a rotating shaft 61, a lifter 40, and a pilot valve body 30, which are rotating members, are integrally unitized to form a drive unit 101, and the drive unit 101 refers to the base 102. It is integrally removable.

Due to such a feature, it is sufficient to remove the drive unit 101 with respect to the base 102 during normal maintenance work, and it is not necessary to disassemble the drive unit 101. Therefore, the accumulation of variations among the members constituting the drive unit 101 does not change before and after the maintenance work. As a result, high flow rate adjustment performance can be maintained without readjustment of the regulation range by the stopper 80.

As described above, when the drive unit 101 is removed from the base 102, the valve body is exposed. In this case, maintenance work on the valve body is extremely easy.

The valve body of the flow rate adjusting valve 1 according to the intermediate concept (5) may be the main valve body 10 of the flow rate adjusting valve 1 (including a configuration having no pilot valve body), or the back pressure chamber 4. It may be a pilot valve body 30 that moves the main valve body 10 by using pressure.

As in the above-described embodiment, the valve body is the pilot valve body 30, and the base 102 includes the main valve body 10 supported in the flow paths 2 and 3 via the diaphragm film 11, and the drive unit 101 A back pressure chamber 4 is formed between the main valve body 10 and an inflow hole 12 for communicating the upstream side 2 of the flow path and the back pressure chamber 4, and the downstream side 3 of the flow path and the back pressure chamber 4 are provided. When the outflow hole 13 communicating with the pressure chamber 4 is provided to be opened and closed by the pilot valve body 30, the main valve body 10 having a high maintenance frequency is separated from the drive unit 101 for maintenance. Workability is high.

Further, as in the above-described embodiment, the drive unit 101 has a back pressure chamber forming member 20 facing the main valve body 10, and the longitudinal member 32 connecting the pilot valve body 30 to the lifter 40 is watertight. When the back pressure chamber forming member 20 is penetrated through the seal 34, and the lifter 40, the longitudinal member 32, and the pilot valve body 30 are linearly movable with respect to the back pressure chamber forming member 20, the rotating member And since the lifter 40 is shielded from the liquid by the watertight seal 34, the range of parts that can be adopted is widened.

Further, as described above, a fastening member for fastening each component of the drive unit 101 and an assembling member for assembling the drive unit 101 and the base 102 are further provided, and the fastening member and the assembling member are of different types. It is preferably a member. In this case, it is possible to effectively prevent the fastening member from being accidentally removed during the removal work on the assembly member.

In particular, it is more preferable that the fastening member is a special screw member 93 or 96, and the assembly member is a normal screw member 103. In this case, it is possible to prevent the fastening member from being accidentally removed during the removal work for the assembly member without requiring a special cost. The special screw member means a deformed screw member such as a so-called star-shaped screw member.

Further, as described above, the assembling member for assembling the drive unit 101 and the base 102 is preferably a plurality of screw members 103 extending in the same direction. In this case, since the plurality of screw members 103 that are the assembly members are aligned in the same direction, the operability of the plurality of screw members 103 is high. Specifically, the flow rate adjusting valve 1 can be attached to and detached from the base 102 of the drive unit 101 without having to rotate or change the posture.

Further, as described above, a watertight member (for example, a seal portion 11s) is provided between a part of the drive unit 101 and a part of the base 102, and the other part of the drive unit 101 and the base 102 It is preferable that it is in contact with the other part. In this case, while the watertight member can exert a watertight function in a desired region, a predetermined "seal allowance" can always be obtained by contacting the assembly member 103 without performing torque management, for example. Further, even when the assembly members 103 are provided at a plurality of locations, there is no concern that the drive unit 101 will be tilted due to variations in the degree of assembly thereof.

Further, as described above, the drive unit 101 has a stopper 80 that limits the movement range of the lifter 40 in a fixed state in which the position cannot be changed, a temporary fixed state in which the position of the stopper 80 can be changed, and the fixed state. When the stopper holding member (for example, the case member 91 and the lid member 92) which is selectively held by any of the above is further provided, and the stopper holding member holds the stopper 80 in the temporarily fixed state. It is preferable that at least a part of the stopper 80 is exposed to the outside of the drive unit 101. In this case, even after assembling the drive unit 101, it is easy to change the position of the stopper 80 by working on at least a part of the stopper 80 exposed to the outside.

In the flow rate adjusting valve 1 according to the intermediate concept (5), the rotating member is not limited to the rotating shaft 61 of the stepping motor 60, and may be a rotating member that is manually rotated. That is, the flow rate adjusting valve 1 may be a manual flow rate adjusting valve.

1 Flow rate adjustment valve 2 Flow path (upstream side)
2b Circumference flow path 3 Flow path (downstream side)
3s Valve seat 4 Back pressure chamber 10 Main valve body 11 Diaphragm membrane (an example of elastic element)
11s seal (an example of watertight member)
12 Inflow holes (2)
13 Outflow hole 13e End of outflow hole on the back pressure chamber side 15 Contact part (hard material)
20 Back pressure chamber forming member 21 Hollow part 22 Cylindrical part 23 Guide slope (3 places)
24 Engagement protrusion 30 Pilot valve body 32 Longitudinal member 32a Shaft member 32b Tip member 32c Elastic member 32g Flow path for liquid movement (cut part)
34 Watertight seal 35 1st spacer member 36 2nd spacer member 40 Lifter 42 Protrusions (3 places)
43 Shaft member receiving hole 45 Fitting convex part 47 Elastic resin member receiving part 50 Joint member 54 Fitting hole 56 Rotating shaft receiving part 58 Stopper regulating part 60 Stepping motor 61 Rotating shaft 62 Housing 71 E-ring (Example of retaining mechanism)
72 Elastic resin member (an example of urging connection member)
73 Coil spring (an example of urging member))
80 Stopper 81 Knob part 82 Tilt 85 Manual adjustment jig 91 Case member 91t Tilt surface 91b Bottom surface 92 Lid member 92w Window part 92i Mark 93 Special screw member (fastening member)
96 Special screw member (fastening member)
101 Drive unit 102 Base 102a Base receiving part 102b Top surface of base 103 Ordinary screw member (assembly member)
X Main valve body axis

Claims (5)

A flow rate adjustment valve for adjusting the flow rate of liquid flowing through the flow path.
A main valve body displaceably supported in the flow path via an elastic element,
A back pressure chamber in which a liquid supplied at a predetermined pressure from the upstream side of the flow path is accommodated and a force is generated by the liquid to urge the main valve body in the valve closing direction.
An inflow hole that communicates the upstream side of the flow path with the back pressure chamber,
An outflow hole that communicates the downstream side of the flow path with the back pressure chamber,
A pilot valve body that opens and closes the outflow hole,
A longitudinal member that holds the pilot valve body and moves the pilot valve body in its own axial direction.
Rotating members and
A lifter that can rotate with the rotation of the rotating member and can move in the axial direction of the longitudinal member in conjunction with the rotation.
With
The lifter and the longitudinal member are connected so as to move integrally in the axial direction.
The longitudinal member extends continuously through the watertight seal to both the back pressure chamber side region where the liquid can exist and the atmospheric side region where the liquid does not exist.
The cross-sectional area of the region through the watertight seal of the longitudinal member, rather smaller than the opening area of the back pressure chamber side end of the outflow hole,
The longitudinal member
A shaft member including a region penetrating the watertight seal and
The tip member that holds the pilot valve body and
Is composed of
The tip member is slidably connected to the shaft member in a predetermined range in the axial direction.
A flow rate adjusting valve characterized in that an elastic member for urging the tip member in the valve closing direction is provided . The flow rate adjusting valve according to claim 1 , wherein the tip member is formed with a flow path for moving a liquid at least a part of a radial outer surface. The elongate member extends through a portion of the lifter,
The flow rate adjusting valve according to claim 1 or 2 , wherein the longitudinal member is engaged with the lifter via a retaining mechanism. The flow rate adjusting valve according to claim 3 , wherein the retaining mechanism has an E-ring. The flow rate according to any one of claims 1 to 4 , wherein the longitudinal member is connected to the lifter in a state of being urged to one side in the axial direction by the urging connecting member. Adjustment valve.

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