JP4996346B2 - Constant flow valve - Google Patents

Description

  The present invention relates to a constant flow valve that can supply a fluid represented by water to a device at a constant flow rate regardless of fluctuations in supply pressure.

  For example, a hot water heater is equipped with a constant flow valve so that there is no problem even if the supply pressure of tap water varies. As an example, there are constant flow valves known from Patent Document 1 and Patent Document 2.

  First, the constant flow valve of Patent Document 1 is a coil that is installed in a fluid flow path, and that expands and contracts a valve body that varies the passage hole area of a fluid according to fluid pressure fluctuations according to fluid pressure fluctuations. It is formed by a shape spring. Then, the gap between the windings of the coiled spring constituting the valve body is made to correspond to the passage hole area which is variable according to the pressure fluctuation of the fluid, and the passage hole area by the gap between the windings of the coiled spring And the spring load characteristic of the coiled spring is set to be non-linear so that the product of the square root of the differential pressure of the fluid with the coiled spring as a boundary is substantially constant.

According to the constant flow valve of Patent Document 1, for example, the pressure loss on the low pressure side of the tap water supply pressure can be reduced to 0.2 kg / cm ² or less, so that the tap water supply pressure is 0.3 kg / cm ² . Even in a low pressure area, for example, in the case of a hot water heater, the set flow rate (15 l / min in the embodiment) can be sufficiently supplied. Therefore, not only can the hot water heater be used soundly but also sufficient hot water can be used, so that the user can be satisfied. Further, by providing the coil spring with a constant flow rate control function, the structure of the valve can be simplified and the parts can also be simplified, so that mass production can be achieved and man-hours can be greatly reduced. Therefore, it is possible to widely provide low-cost constant flow valves with good performance.

  In addition, the constant flow valve of Patent Document 2 causes the valve element to expand and contract in response to fluid pressure fluctuations, and to allow the gaps between the windings to correspond to the passage hole areas that are variable in response to fluid pressure fluctuations. It is formed by a conical coil spring. Then, in the fluid primary side region of the conical coiled spring forming the valve body, the seat plate portion sandwiched by the upstream spring seat portion, and the free end from the seat plate portion toward the downstream side And a wing portion extending, formed of a flexible elastic material, and by suppressing the ridgeline of each winding of the conical coiled spring by the restraining force generated by the fluid pressure difference between the front and back of the substantially flat surface portion of the wing portion, A buffer member that suppresses the swing of each winding is disposed. A valve assembly is formed by engaging a damper member having a piston located at the center of a conical coil spring forming a valve body with an upstream spring seat portion and a seat plate portion of a buffer member. . Then, a bottomed damper cylinder having a damper hole is disposed on the center line of the valve assembly, and a damper member piston is fitted into the damper hole of the damper cylinder so as to be slidable in the vertical direction. Configure the device. Further, the piston cannot be rotated with respect to the damper hole.

According to the constant flow valve of Patent Document 2, first, by giving a constant flow control function to the conical coil spring, the structure of the valve can be simplified and the parts can be simplified. The man-hours can be greatly reduced. Therefore, it is possible to widely provide low-cost constant flow valves with good performance. By providing the damper device, even if the valve assembly in which the conical coil spring and the propeller-shaped buffer member are engaged by the damper member tries to vibrate vigorously in the axial direction, the vibration is absorbed and removed. The movement is controlled smoothly. Therefore, the constant flow characteristics are stabilized, and the factor as a trigger for generating vibration is eliminated. Further, the contact relationship between the valve peripheral members that are in a face-to-face relationship in the valve portion is relatively good, and the constant flow characteristics are stabilized. Further, since the fitting portion between the piston and the damper hole is structured such that the operation in the rotational direction is impossible, the valve seat environment of the conical coil spring forming the valve body does not change.
Japanese Patent No. 2571335 Japanese Patent No. 3164786

By the way, in the constant flow valve of patent document 2, the conical shape which makes a valve body by the play resulting from the extremely small play in the non-rotatable fitting part of a piston and a damper hole, specifically a polygonal fitting part. The coiled spring is slightly displaced in the rotational direction, the direction along the center line, and the orthogonal direction.
As a result, there is a concern that the positional relationship with the water passage hole portion on the bottom surface of the valve support housing is slightly broken, which affects the pressure receiving / operability of the conical coiled spring forming the valve body. That is, there is a concern that the flow characteristics may vary due to vertical play, and that there may be variations in the flow characteristics when the mounting posture of the constant flow valve changes, especially when the constant flow valve is upside down with the damper part facing up. In this case, there is a concern that the flow rate characteristics vary due to rotation in the horizontal direction.
The same concern can be considered when the piston and the damper hole are rotatable fitting portions.

An object of the present invention is to improve a variation in flow characteristics caused by play in the vertical direction in a constant flow valve provided with a valve body and a damper device by a conical coil spring.
Another object of the present invention is to improve the variation in flow characteristics when the mounting posture changes.

In order to solve the above-described problems, the invention according to claim 1 includes a conical coil spring forming a valve body, and a damper member having a piston located at a small diameter end of the conical coil spring, In a constant flow valve provided with a valve support housing that supports a large-diameter end of the conical coiled spring, and a damper hole that is provided in the valve support housing and into which the piston is fitted, the conical shape A spring in which a large-diameter end of a coiled spring is interposed between the valve support housing with an elastic body, and a convex portion is engaged with a recess facing the valve support housing in the diametrical direction to prevent the spring from coming off. The presser is pressed by a presser member on which the presser bodies are stacked .

  The invention according to claim 2 is the constant flow valve according to claim 1, wherein a groove is formed in the valve support housing, and the elastic body is disposed in the groove.

According to the present invention, the conical coiled spring that forms the valve body is fixed so that the large-diameter end thereof is pressed against the elastic body interposed in the valve support housing and does not move. This eliminates the variation in the flow characteristics caused by the play of the valve and improves the accuracy of the constant flow valve.
Further, when the mounting posture is changed, in particular, the variation in the flow characteristics when the damper portion is turned upside down or when it is rotated sideways can be eliminated, and the accuracy of the constant flow valve can be improved.
Furthermore, as a result of increasing the accuracy of the flow rate, water can be saved in a hot water heater, a toilet, a washroom, and the like.

Hereinafter, the best mode for carrying out the present invention will be described in detail with reference to the drawings.
(Embodiment 1)
FIG. 1 shows a configuration of a first embodiment of a constant flow valve to which the present invention is applied. FIG. 1 shows a constant flow valve installed vertically, 10 is a valve support housing, 11 is a valve support plate, and 12 is 13 is a damper cylinder, 14 is a damper hole, 16 is an engaging recess, 17 is a groove, 20 is a valve body (conical coiled spring), 21 is a small diameter end, 22 Is a large diameter end portion, 30 is a buffer member, 31 is a seat plate, 32 is a blade, 40 is a damper member, 41 is a piston, 50 is a pressing member (spring holder), 51 is a large diameter portion, 52 is a notch portion, 60 Is a spring presser, 61 is an engaging convex part, 62 is a damper member presser, and 70 is an elastic body.

As described in detail in Patent Document 2, the valve support housing 10 is provided so as to be divided into a water supply pipe (not shown), and is made of a synthetic resin having a cylindrical shape that is stabilized in the water supply pipe. Thus, it is in contact with the water supply pipe and is airtightly fitted by rubber packing. The valve support housing 10 may be made of metal.
The valve support housing 10 is provided in a circumferential direction on a valve support plate 11 that is integrally provided so as to divide the inside of the water supply pipe as shown in a water supply pipe such as a hot water heater, a toilet, and a washroom. And a plurality of through-holes (water-passing hole portions) 12 spaced apart from each other, and a damper cylinder 13 that projects from the center portion toward the downstream side and constitutes a part of the damper device. The damper cylinder 13 has a bottomed damper hole 14.

The conical coiled spring 20 forming the valve body is made of metal, and is a non-linear characteristic with a downward slope that the characteristic of the change state of the passage hole area with respect to the amount of displacement decreases toward the close contact side.
The buffer member 30 is made of flexible synthetic rubber or synthetic resin and has a propeller shape. The buffer member 30 has a disc-shaped seat plate 31 having a through-hole in the center and a radial direction (for example, a seat) from the periphery of the seat plate 31. The blade 31 extends in the diametrical direction of the plate 31 and has a function of preventing surging of the coiled spring 20.
The damper member 40 is a disc-shaped member, and integrally has a piston 41 at the center thereof.

The buffer member 30 and the small-diameter end 21 of the coiled spring 20 are engaged with each other with the damper member 40 interposed between the ring 42 and the damper member 40 together with the damper member 40 to form a valve assembly. ing.
The damper member 40 is made of synthetic resin, but may be made of metal. The ring 42 is made of synthetic resin and has a function of protecting the seat plate 31 portion of the buffer member 30 formed of flexible synthetic rubber or synthetic resin from the winding end angle of the coiled spring 20. is there. The ring 42 may be made of metal.
Further, a spring pressing body 60 having a damper member presser 62 for pressing the damper member 40 is mounted in the valve support housing 10. The spring retainer body 60 is made of synthetic resin, and the spring retainer body 60 is formed with a through hole (water passage hole portion) as shown in the figure. The spring pressing body 60 may be made of metal.

The damper device is configured by inserting and coupling the piston 41 of the valve assembly into the damper hole 14 of the damper cylinder 13 with the surrounding fluid interposed therebetween. The function of this damper device is to control the smooth movement by the braking action by absorbing the movement by the resistance of the intervening fluid in the damper hole 14 when the valve assembly is vigorously vibrated in the axial direction by the fluid. Is. Therefore, by appropriately adjusting the fitting gap of the diameter of the damper hole 14 with respect to the diameter of the piston 41, the amount of fluid entering and exiting the damper hole 14 is adjusted, and the degree of buffering for smooth operation is determined.
The sectional shape of the damper hole 14 and the piston 41 is formed in a polygonal shape, so that the valve assembly is slidable in the vertical direction, but the rotational direction is limited. In addition, the cross-sectional shape of the fitting portion of the piston 41 with respect to the damper hole 14 is not limited to a polygon, and any shape that can limit the rotation direction may be used. For example, the relationship between a key groove and a key may be used.

  As described in detail in the above-mentioned Patent Document 2, when the above constant flow valve receives the water pressure from the water supply line in the state before the start of use, the valve assembly senses the pressure in the pressure receiving area, Responding to the downstream side against the spring force of the conical coil spring 20, the flow control is stabilized. On the other hand, this response causes the piston 41 to be pushed up in the damper device, but gradually reaches the stable position of the flow control while receiving the resistance of the intervening fluid in the damper hole 14. The time until stabilization is determined by the amount of intervening fluid pushed out from the fitting gap of the piston 41.

  When the flow rate control is stable, the valve assembly moves up and down in response to constantly changing water pressure, but the upward movement is pulled up by the spring force of the conical coil spring 20. In this case, in the damper device, since the piston 41 is retracted from the damper hole 14, the surrounding fluid is drawn into the damper hole 14 from the fitting gap of the piston 41. Therefore, also in this case, the piston 41 receives the resistance of the intervening fluid in the damper hole 14. In this way, the valve assembly operates slowly due to the resistance of the damper device in any movement against vertical movement. Accordingly, when the valve assembly is subjected to vibration, whether external or internal, the operation is similarly slow, and the nature of the vibration is changed smoothly, and as a result, surging is prevented. Further, even during the progress of preventing surging by the damper device, vibrations coming from the natural frequency of the conical coiled spring 20 are suppressed by the propeller-shaped buffer member 30.

  According to the above constant flow valve, as will be described in detail in Patent Document 2, the conical coiled spring 20 that forms the valve element causes less fluid passage resistance and very little pressure loss. In addition to the effect of becoming a thing and the anti-surging effect obtained by the use of the propeller-shaped cushioning member 30, by providing a damper device, even if the valve assembly tries to vibrate vigorously in the axial direction, the vibration is absorbed. Are removed and the movement is controlled smoothly. In addition, since the cross-sectional shape of the fitting portion between the piston 41 and the damper hole 14 is a polygonal shape, a structure incapable of operation in the rotational direction is obtained, so that the valve seat environment of the conical coiled spring 20 is reduced. There is no change. Therefore, the constant flow characteristics are stabilized, and the factor as a trigger for generating vibration is eliminated. Further, the contact relationship between the valve peripheral members that are in a face-to-face relationship in the valve portion is relatively good, and the constant flow characteristics are stabilized.

  In the above constant flow valve, the large-diameter end 22 of the conical coiled spring 20 forming the valve body is overlaid on the valve support plate 11. A spring holder 50, which is an annular pressing member provided inside the valve support housing 10, is superimposed on the large-diameter end 22 of the conical coiled spring 20 that forms the valve body.

  Here, for example, when a resin pressing member (spring holder) 50 is press-fitted into the valve support housing 10, the assemblability is deteriorated compared to the conventional product, and the recyclability is also deteriorated as compared with the conventional one because it is difficult to disassemble. Further, when used in a high temperature environment, the press-fitting portion of the presser member 50 and the valve support housing 10 may creep-deform, and the force for holding the positions of the coiled spring 20 and the valve support housing 10 is deteriorated. However, there is a concern that the stability of the flow rate characteristic is impaired.

  For example, when the large-diameter end 22 of the coil spring 20 is sandwiched between the rubber pressing member (spring holder) 50 and the valve support plate 11, the stability of the flow rate is improved from the conventional product. The rubber pressing member 50 needs to escape during the operation of the propeller-shaped buffer member 30 and forms a thin wall portion or a notch portion. Therefore, deformation of the rubber pressing member 50 is caused. There is a concern that the holding force at the position of the large-diameter end portion 22 of the coiled spring 20 with respect to 10 may be reduced.

  Therefore, in the embodiment, as illustrated, an annular groove 17 is formed in the outer peripheral portion of the valve support plate 11. A rubber ring 70 which is an annular elastic body is disposed in the groove 17. In this manner, the large-diameter end 22 of the conical coiled spring 20 forming the valve body is overlaid on the rubber ring 70 disposed in the groove 17 of the valve support plate 11. Then, a spring holder 50 that is a pressing member provided inside the valve support housing 10 is placed on the large-diameter end 22 of the conical coiled spring 20 that forms the valve body. The pressing member (spring holder) 50 is pressed against the large-diameter end portion 22 of the coiled spring 20 by a spring pressing body 60 attached to the inside of the valve support housing 10.

  As shown in FIG. 2, the presser member (spring holder) 50 has a large-diameter portion 51 that abuts the inside of the valve support housing 10 at the upper portion to avoid interference of the blades 32 of the buffer member 30. A pair of notches 52 are formed in the diameter direction. The pressing member (spring holder) 50 is made of synthetic resin, but may be made of metal or rubber.

  Further, by mounting the spring pressing body 60 in the valve support housing 10, the spring pressing body 60 is overlapped on the large diameter portion 51 of the spring holder 50 that is a pressing member. That is, the engaging convex portion 61 facing the diametrical direction formed on the outer periphery of the lower portion of the spring pressing body 60 is engaged with the engaging concave portion 16 facing the diametrical direction formed on the upper portion of the valve support housing 10 to The presser body 60 is mounted in the valve support housing 10 to prevent it from coming off. As shown in the figure, the spring retainer 60 is integrally provided with a damper member retainer 62 spanned in the diametrical direction inside the upper portion.

  As a result, the conical coiled spring 20 forming the valve body has a large-diameter end 22 fixed to the valve support plate 11 via the rubber ring 70, and a through-hole in the bottom surface of the valve support housing 10. Since the positional relationship between the (water passage hole) 12 and the conical coiled spring 20 can be held in a restrained state, the conical coiled spring 20 forming the valve body does not move.

  Therefore, the variation in flow characteristics due to play in the direction along the center line of the constant flow valve can be eliminated, and when the mounting posture of the constant flow valve is changed, for example, when it is rotated sideways, Since the variation can be eliminated, the accuracy of the constant flow valve can be improved.

In addition, since it is not necessary to consider the creep deformation due to the press-fitting of the resin part as described above, it is possible to improve the performance in a high temperature environment.
As a result, the accuracy of the flow rate can be increased, so that water can be saved in a hot water heater, a toilet, a washroom, or the like.

(Modification 1 of the presser member)
FIG. 4 shows a first modification of the presser member (spring holder) 50, which has a sufficient casing size (outer diameter of the valve support housing 10), and the end winding of the conical coiled spring 20 that forms the valve body. As shown in the figure, a presser member (spring holder) 50 having no notch for avoiding interference of the blades 32 of the buffer member 30 may be used.
Thus, since the notch part which avoids interference of the blade | wing 32 of the buffer member 30 is unnecessary by the change of arrangement | positioning, a deformation | transformation of the form of the pressing member (spring holder) 50 in the case of rubber | gum is small, for example.
Accordingly, the position holding force between the conical coiled spring 20 and the valve support housing 10 forming the valve body is improved as compared with the case of the rubber pressing member of concern as described above, and the flow stability is provided. Is possible.

Further, even when the countermeasure against surging is not necessary, that is, when the buffer member 30 is not necessary, the pressing member (spring holder) 50 having no notch as shown in FIG. 4 can be used.
The same effect can be obtained even when the pressing member (spring holder) 50 and the spring pressing body 60 are integrated.
Further, even when the large-diameter end portion 22 of the conical coil spring 20 forming the valve body is press-fitted between the inner diameter side of the valve support housing 10 and the outer shape side of the pressing member (spring holder) 50, the same applies. The effect is obtained.

(Modification 2 of the presser member)
FIG. 5 shows a second modification of the presser member (spring holder) 50. With respect to the presser member (spring holder) 50 having a notch 52 that avoids interference of the blade 32 of the buffer member 30, By providing the rib 53 as shown in the figure and providing a groove corresponding to the rib 53 on the inner peripheral side of the valve support housing 10, the position of the notch portion 52 can be reliably brought out.

(Modification 1 of elastic body)
FIG. 6 shows a first modification of the elastic body (rubber ring) 70, in which ribs 71 are formed on the inner periphery and outer periphery of one surface side of the rubber ring 70. FIG. 7 shows an enlarged cross section of the inner and outer ribs 71.
You may make it support the large diameter edge part 22 of the conical coil-shaped spring 20 which makes | forms a valve body by the rib 71 side of the inner periphery and outer periphery of such a rubber ring 70. FIG.

(Modification 2 of elastic body)
FIG. 8 shows a second modification of the elastic body (rubber ring) 70, and ribs 72 along the radial direction are formed at equal intervals in the circumferential direction on one surface side of the rubber ring 70.
The large-diameter end portion 22 of the conical coiled spring 20 forming the valve body may be supported on the rib 72 side formed at equal intervals in the circumferential direction along the radial direction of the rubber ring 70. .

The ribs 72 are not necessarily provided at regular intervals, and the number of the ribs 72 is arbitrary.
Further, the rubber ring 70 may be integrally formed or bonded to the groove 17 of the valve support plate 11.
Further, the rubber ring 70 may be directly provided on the valve support plate 11 without providing the groove 17.

(Modification 3 of elastic body)
FIG. 9 shows a third modification of the elastic body (rubber ring) 70. A protrusion 73 is provided on one surface side of the rubber ring 70, for example, at a diametrically opposed position, and the valve support plate 11 (or groove 17) side. In this case, a hole corresponding to the protrusion 73 may be formed, and the protrusion 73 may be inserted into the hole to fix the rubber ring 70 to the valve support plate 11.

(Modification 3 of the presser member)
FIG. 10 shows a third modification of the presser member (spring holder) 50, and this presser member (spring holder) 50 includes a presser convex portion 54 on the large diameter portion 51. The presser convex portions 54 are equally arranged at four places in the illustrated example.
The elastic body (rubber ring) 70 may be pressed against the valve support plate 11 (or the groove 17) with such a pressing convex portion 54.

The shape, size, and width of the presser convex portion 54 can be arbitrarily set.
In addition, the number of the presser convex portions 54 is not limited to the four-place uniform arrangement in the illustrated example, and may be one or two, three, five, or more, and the plurality of presser members 54 may be arranged equally. It may be uneven.

(Modification 4 of elastic body)
FIG. 11 shows a fourth modification of the elastic body. This elastic body (rubber) 80 is partially or partially provided on the valve support plate 11 without the groove 17. The elastic body (rubber) 80 has a quadrangular shape in the illustrated example.
The large-diameter end 22 of the conical coil spring 20 that forms the valve body may be supported by such a partially provided rectangular elastic body (rubber) 80.

(Modification 5 of elastic body)
FIG. 12 shows a fifth modification of the elastic body. This elastic body (rubber) 80 is provided on the valve support plate 11 having no groove 17 so as to partially face each other. It has a round shape.
The large-diameter end portion 22 of the conical coiled spring 20 constituting the valve body may be supported by such a partially provided round elastic body (rubber) 80.

The size of the elastic body (rubber) 80 can be freely set in the layout.
Further, the number of elastic bodies (rubbers) 80 may be one, three, four, or more, and the arrangement of the plurality of elastic bodies (rubbers) 80 may be uniform or non-uniform.

In the above embodiment, the constant flow valve installed in the vertical direction has been described, but the same effect can be obtained even when the posture of the constant flow valve is upside down with the damper portion facing up.
That is, when the constant flow valve is upside down with the damper portion facing up, the conical coiled large-diameter end that forms the lower valve body floats off the valve support plate, so the vertical direction There is concern about variations in flow characteristics due to play.
However, according to the present invention, the conical coiled large-diameter end that forms the valve body is fixed with respect to the valve support housing and does not move. In the case of the reverse direction, it is possible to eliminate the variation in the flow rate characteristic due to the play in the vertical direction, and hence the accuracy of the constant flow valve can be improved.

In the above embodiment, the constant flow valve is provided with a buffer member. However, the present invention is not limited to this and may be a constant flow valve without a buffer member.
Further, regarding the fitting portion between the damper hole and the piston, in the embodiment, the cross-sectional shape is a polygonal non-rotatable structure, but the cross-sectional shape may be a circular structure and a rotatable structure.
Furthermore, in the embodiment, the conical coil spring forming the valve body is made of metal, but may be made of SMA (Shape Memory Alloy) or synthetic resin.
Further, the method of fixing the large-diameter end portion of the conical coil-shaped spring forming the valve body and the valve support housing is not limited to the above-described embodiments but is arbitrary.
Furthermore, the specific arrangement of the constant flow valves, the type of fluid to be flow controlled, and the like are arbitrary, and other specific details such as the structure can be changed as appropriate.

BRIEF DESCRIPTION OF THE DRAWINGS It is the center longitudinal cross-sectional view which shows the structure of Embodiment 1 of the constant flow valve to which this invention is applied, and shows the constant flow valve installed in the vertical direction. It is a perspective view of the pressing member of FIG. It is a perspective view of the elastic body of FIG. It is a perspective view which shows the modification 1 of a pressing member. It is a perspective view which shows the modification 2 of a pressing member. It is a perspective view which shows the modification 1 of an elastic body. It is an expanded sectional view of FIG. It is a perspective view which shows the modification 2 of an elastic body. It is a perspective view which shows the modification 3 of an elastic body. It is a perspective view which shows the modification 3 of a pressing member. FIG. 11 is a perspective view showing a fourth modification of the elastic body and showing the inside of the valve support housing. FIG. 10 is a plan view showing the inside of a valve support housing, showing a modified example 5 of the elastic body.

Explanation of symbols

10 Valve support housing 11 Valve support plate 12 Through hole (water passage hole)
13 Damper cylinder 14 Damper hole 16 Engaging recess 17 Groove 20 Valve body (conical coil spring)
21 Small-diameter end portion 22 Large-diameter end portion 30 Buffer member 31 Seat plate 32 Blade 40 Damper member 41 Piston 42 Ring 50 Holding member 51 Large-diameter portion 52 Notch portion 53 Rib 54 Pressing convex portion 60 Spring pressing body 61 Engaging convex portion 62 Damper member presser 70 Elastic body 71 Rib 72 Rib 73 Projection 80 Elastic body

Claims (2)

A conical coil spring forming a valve body, a damper member having a piston positioned at the small diameter end of the conical coil spring, and a valve support for supporting the large diameter end of the conical coil spring In a constant flow valve provided with a housing and a damper hole provided in the valve support housing and fitted with the piston,
An elastic body is interposed between the large-diameter end of the conical coiled spring and the convex portion is engaged with a concave portion opposed to the valve support housing in the diametrical direction. A constant flow valve characterized in that a spring presser body that is prevented from coming off is pressed by a stacked presser member. Forming a groove in the valve support housing;
The constant flow valve according to claim 1, wherein the elastic body is disposed in the groove.

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