Shower switching faucet and pipe connection structure

Abstract

To provide a shower switching faucet having durability and not complicating a structure.SOLUTION: A connecting member 33 which is a second pipe is inserted inside a fixing member 31 which is a first pipe, and a watertight state is formed between the two, as described later. Female screws 31a, 31a protruding inward are formed on an inner wall surface of the fixing member 31, and male screws 33a, 33a protruding outward are formed on an outer wall surface of the connecting member 33. The female screws 31a, 31a and the male screws 33a, 33a form a double-thread screw, forming a multiple-thread screw mechanism to be screwed on by the rotation of less than 180 degrees. A convex shape 31a1 serving as an engaging convex portion is formed on a screwing surface which is an upper surface of the female screw 31a, and a concave shape 33a1 serving as an engaging concave portion is formed on a lower surface of the male screw 33a, so that they are engaged by concave-convex engagement at a connection completion position which is a screwing completion position.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The present invention relates to a shower switching faucet that can switch between shower water spouting and straight water spouting, and a pipe body connecting structure. [Background technology]

[0002] A shower faucet that can switch between shower and straight water discharge switches between a straight water discharge flow path that passes through the center and a shower water discharge flow path that discharges water in a shower-like manner from around it by turning a knob or the like. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 3729198 [Patent Document 2] Patent No. 6556470 [Patent Document 3] Utility model registration No. 3241138 [Patent Document 4] JIPP No. 63-076069 [Patent Document 5] Japanese Patent Publication No. 59-174457 Summary of the Invention [Problem to be solved by the invention]

[0004] The structure for switching the flow path that receives the tap water pressure is required to be durable enough to withstand the frequent switching of discharge. In addition, there are cases where a shower / straight water switching faucet is required at the outlet of the mixer of an electrolytic hypochlorous water generator. Because impurities such as chlorides accumulate over long-term use, when it becomes necessary to remove and attach the switching mechanism that switches between shower and straight water for various reasons, including cleaning and maintenance, if it is fixed with a normal screw, it would need to be turned more than three times, making it difficult to remove and attach.

[0005] The mixer in FIG. 6 of Patent Document 2 allows switching between shower spouting and straight spouting with a knob, but has the following drawbacks. 1) It cannot be quickly replaced with a hose adapter. 2) Because it has a built-in gear mechanism, it is difficult to disassemble and assemble. 3) As dirt accumulates, the operating force increases. In particular, if dirt accumulates on the gear mechanism, the load increases.

[0006] Patent Document 3 improves on 1) of Patent Document 2. For example, it states, "...the electrolyzed water discharge port of the mixer is fitted with a shower cap or a hose cap to which an extension hose can be connected... (Claim 4)." However, it has the following drawbacks. When switching between shower and straight water discharge, it is necessary to remove parts and assemble multiple parts. 1: When using straight water discharge, remove the cap and hose adapter. 2: When using shower water discharge, attach the shower cap.

[0007] Patent Document 4 discloses a "shower / straight water discharge" switching mechanism that can be switched by rotating a knob 90 degrees. The structure is relatively simple, and disassembly and assembly are not difficult. This type of device, with O-rings added to the sliding surfaces and sealing parts, is still in use today. Specifically, the water flow from the original main pipe branches into two, which are joined by a rotating sliding surface, and then the branch pipes merge into one discharge pipe. A drawback is that if this merger pipe is short, the water discharge becomes turbulent.

[0008] This type of device is often mounted and fixed using friction, either by "compressing the flat packing with screws and fixing it with the resulting friction" or by "inserting a rubber hole and fixing it with friction." However, there was a problem that "every time it was fixed, the position of the switch knob would shift," making it difficult to specify (limit) the knob position for shower or straight. There was also the problem that if the knob switching torque was too high, the fixing screw would loosen. Patent Document 1 shows a mechanism in which a semicircular convex part is provided on the root of the male screw and a concave groove is provided on the crest of the female screw, and the mechanism locks the screws when the screws are rotated and positioned by the convex-concave engagement. However, although this type is also suitable for temporary fixing, it is prone to coming loose when a large torque is applied.

[0009] where: "The switch knob (with a radius of 2.5 cm) remains fixed even when a force of 50 N is repeatedly applied." "Even if you put it on and take it off more than 1,000 times, the fixing power will not decrease (it will not wear out)" Let's set a standard like this.

[0010] The reason for this is that the cylindrical deformation deflection of the resin is used when riding over it, and the riding height is thought to be around 0.5mm. If the corner of the hook tip exceeds the stress limit, the corner will break and a C-surface will form. (If the hook width is 2 and C0.4, then the area is 0.4 x √2 x 2 ≒ 1, and in the case of resin with an allowable shear stress of 50N / mm^2 (square millimeters), the hook tip will deform to C0.4 when a load of 50N is applied. If there are two hooks, the total allowable load is 100N. If the maximum allowable load for the male screw outer diameter (φ25) is 100N, the maximum allowable load at knob position R25 is half that, 50N (allowable torque 125cNm). The hook has rounded corners at C0.4 and catches in the grooves, and if the catch height is 0.8 or less, the R or C surface will come into contact and it will be easy to come off. In this way, "contact between straight (vertical) surfaces" is important to obtain a large fixing force.

[0011] As in the present invention, if the hooking height is about 1.4 mm, even if R0.4 occurs at the corner of the hook, the range where the straight surfaces contact each other remains as h1.4-R0.4-R0.4=0.6, making it possible to secure the fastener in a way that can withstand large forces. It is difficult to achieve deformation deflection over 1,000 times with a 25mm diameter screw thread with a radial hook height of 1.4mm or more using only the elastic deflection of resin. It is also difficult to withstand a load of 50N (torque 125cNm). Patent Document 5 shows a structure that locks the bottle cap after tightening it. However, since the only deflection is the elastic deformation of the resin, repeated attachment and detachment weakens the force required to remove it. Also, it is difficult to achieve a large hook height, such as 1.4 mm.

[0012] The present invention provides a shower switching faucet or pipe connecting structure that is durable and has a simple structure. The objective is also to provide a durability of more than 1,000 times, a fastening that will not loosen even when a switching torque of 125 cNm or more is applied, a fastening that can be detached with one turn of the screw or less, and a fastening position of the switching knob that can be reproduced at the specified angle every time. [Means for solving the problem]

[0013] The present invention is a shower switching faucet that can switch between shower water spout and straight water spout, and comprises a fixed member connected to the upstream side of a waterway, and a switching mechanism that is detachably connected to the fixed member and switches between shower water spout and straight water spout, the fixed member having a first pipe body, the switching mechanism having a second pipe body, the first pipe body and the second pipe body being connectable with a screw mechanism that can be connected and disconnected in less than one turn, and the screw mechanism being configured with a concave-convex engaging structure that can engage with each other in the disconnection direction at the connection completion position.

[0014] In the above configuration, the shower switching faucet is composed of a fixed member and a switching mechanism, with the fixed member having a first pipe and the switching mechanism having a second pipe. The first pipe and the second pipe are connected by a screw mechanism that can be connected and disconnected in less than one turn, and this screw mechanism engages with each other due to a concave-convex engagement structure at the connection completion position. Because they engage with each other in the disconnection direction, they become more engaged when attempting to disconnect, making it difficult to disconnect. An example of a screw mechanism that can be connected and disconnected in less than one turn is a multiple-start screw mechanism.

[0015] In another aspect of the present invention, the screw mechanism is configured as a single-start screw or a multiple-start screw mechanism. In another aspect of the present invention, the first tube and the second tube are watertight with an O-ring interposed therebetween, and support protrusions are formed alternately on the wall surfaces of the first tube and the second tube facing each other to support the O-ring from the direction opposite to the insertion direction. In another aspect of the present invention, the support projection is formed of a large projection and a small projection, and the small projection is also formed at a position facing the mating support projection.

[0016] In another aspect of the present invention, a hole is formed in both or one of the first and second tubes at a position that overlaps in the insertion direction with the position at which the concave-convex engagement structure is formed. Furthermore, in another aspect of the present invention, the concave-convex engagement structure of the multiple-thread screw mechanism has an engagement protrusion provided on the threading surface of one of the multiple-thread screws, and the other multiple-thread screw has a thick portion formed thereon that is thick enough to allow the engagement protrusion to enter and form an engagement recess into which it can engage, and on the side of the first and second tubes where the one of the multiple-thread screws is formed, a guide protrusion is formed that slides against the thick portion when disengaging, causing it to move in a predetermined trajectory.

[0017] In another aspect of the present invention, the multiple thread mechanism has a cut surface formed at the start or end of the threads. Furthermore, in another aspect of the present invention, there is provided a pipe connection structure for connecting a first pipe and a second pipe, wherein the first pipe and the second pipe can be connected and disconnected in less than one rotation, and an O-ring is interposed between the first pipe and the second pipe to create a watertight state, and support protrusions are formed on the wall surfaces of the first pipe and the second pipe facing each other to support the O-ring from the direction opposite to the insertion direction in a staggered manner. In another aspect of the present invention, the support projection is formed of a large projection and a small projection, and the small projection is also formed at a position facing the opposing support projection. Furthermore, in another aspect of the present invention, the first tube and the second tube can be connected and disconnected in less than one rotation using a multiple-thread screw mechanism, and an engaging protrusion is provided on the threaded surface of one of the multiple-thread screws, while the other multiple-thread screw has a thick portion that is thick enough to allow the engaging protrusion to enter and form an engaging recess into which it can engage, and the side of the first tube and the second tube where the one of the multiple-thread screws is formed has a guide protrusion that slides against the thick portion when disengaging, causing it to move in a predetermined trajectory. In another aspect of the present invention, the multiple-start screw mechanism has a cut surface formed at the start or end of the threads. [Effects of the Invention]

[0018] In the shower switching faucet of the present invention, the first pipe body on the fixed member side and the second pipe body on the switching mechanism side are connected by a multiple thread mechanism, and can be connected and disconnected in less than one turn.Furthermore, the concave-convex engagement structure ensures concave-convex engagement at the complete connection position, so it will not loosen. [Brief explanation of the drawings]

[0019] [Figure 1] 1 is an overall perspective view of a shower switching faucet to which the present invention is applied; [Figure 2] This is an assembly parts diagram of the water discharge mechanism of a shower switching faucet. [Figure 3] This is an assembly parts diagram of the water discharge mechanism of a shower switching faucet. [Figure 4] FIG. 1 is a development view of the process of threading a multiple-start screw. [Figure 5] FIG. 1 is a development view of the process of threading a multiple-start screw. [Figure 6] FIG. 1 is a development view of the process of threading a multiple-start screw. [Figure 7] FIG. 1 is a development view of the process of threading a multiple-start screw. [Figure 8]FIG. 1 is a development view of the process of threading a multiple-start screw. [Figure 9] FIG. 2 is a perspective view of the first pipe body as seen from below. [Figure 10] FIG. 4 is a partially cutaway side view of a second tube body. [Figure 11] 10 is a schematic diagram showing deformation of an O-ring during the process of threading a multiple-start screw. FIG. [Figure 12] 10 is a schematic diagram showing deformation of an O-ring during the process of threading a multiple-start screw. FIG. [Figure 13] 10 is a schematic diagram showing deformation of an O-ring during the process of threading a multiple-start screw. FIG. [Figure 14] 10 is a schematic diagram showing deformation of an O-ring during the process of threading a multiple-start screw. FIG. [Figure 15] 10A and 10B are schematic diagrams showing deformation of an O-ring during the process of threading a multiple-start screw according to a modified example. [Figure 16] 10A and 10B are schematic diagrams showing deformation of an O-ring during the process of threading a multiple-start screw according to a modified example. [Figure 17] 10A and 10B are schematic diagrams showing deformation of an O-ring during the process of threading a multiple-start screw according to a modified example. [Figure 18] 10A and 10B are schematic diagrams showing deformation of an O-ring during the process of threading a multiple-start screw according to a modified example. [Figure 19] FIG. 10 is a schematic diagram showing force vectors when an O-ring is deformed. [Figure 20] 10 is a graph showing the height and reaction force when the O-ring is deformed. [Figure 21] FIG. 10 is a schematic diagram showing force vectors of a connecting member and a water channel switching member. [Figure 22] 10 is a graph showing displacement when a normal force is applied to two recessed portions of a connecting member. [Figure 23] FIG. 10 is a schematic diagram showing force vectors of a connecting member and a water channel switching member. DETAILED DESCRIPTION OF THE INVENTION

[0020] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows an overall perspective view of a shower switching faucet to which the present invention is applied, and FIGS. 2 and 3 show assembly parts diagrams of the water discharge mechanism of the shower switching faucet. The shower switching faucet 10 to which the present invention is applied comprises a mixer body 20 that houses a cartridge (not shown) and a shower switching mechanism 30 that is detachable from the mixer body 20. The shower switching mechanism 30 comprises a fixing member 31 connected to the upstream side of the water channel, a switching ring 32, a connecting member 33, a water channel switching member 34, and a water discharge cap 35. The switching ring 32, connecting member 33, water channel switching member 34, and water discharge cap 35 constitute a switching mechanism 36 that switches between shower water discharge and straight water discharge. The switching ring 32 and water discharge cap 35 together form a faucet section that houses the connecting member 33 and water channel switching member 34.

[0021] The switching mechanism 36 is formed by sequentially placing the water channel switching member 34 and the connecting member 33 on the upward-opening water discharge cap 35, then placing the roughly ring-shaped switching ring 32 over them, and screwing and fixing the switching ring 32 and the water discharge cap 35 together. In this integrated state, the switching ring 32, the water channel switching member 34, and the water discharge cap 35 are immobile, while the connecting member 33 is rotatable relative to them within a range of approximately 90 degrees. The fixing member 31 is fixed to the mixer body 20, and the connecting member 33 is detachably fixed to this fixing member 31. As a result, the switching ring 32, the water channel switching member 34, and the water discharge cap 35 are held rotatable within a range of 90 degrees relative to the mixer body 20.

[0022] In this way, the fixing member 31 can be connected at its upper end to the underside of the mixer body 20, and can be detachably connected at its lower end to the switching mechanism 36. The connecting member 33 can be detachably attached to the fixing member 31 so as to be watertight and airtight, and when attached, the entire switching mechanism 36 is supported by the fixing member 31 via the connecting member 33. As will be described later, several O-rings are attached at necessary locations to ensure a watertight state. In this embodiment, the fixing member 31 serves as the first tubular body, and the connecting member 33 serves as the second tubular body.

[0023] 4 to 8 show the screwing process of the multiple thread mechanism in exploded views. A second pipe, namely, a connecting member 33, is inserted inside a first pipe, namely, a fixing member 31, and a watertight state is formed between the two, as will be described later. Female threads 31a, 31a that protrude inward are formed on the inner wall surface of the fixing member 31, and male threads 33a, 33a that protrude outward are formed on the outer wall surface of the connecting member 33. The female threads 31a, 31a and the male threads 33a, 33a form a double-start thread, and in this embodiment, they are threaded together with a rotation of less than 180 degrees. In other words, a multiple-start screw mechanism is formed that threads together with less than one rotation. In this embodiment, a multiple-start screw mechanism using a double-start screw as an example is used, but this is merely an example. A single-start screw that engages with less than one turn can also be used, or a screw mechanism that forms an engagement state with just a small amount of rotation between the two. Furthermore, a locking portion that can hook a protrusion on the outside of one of the tubes and a locking portion on the outside of the other tube can also be used to secure the first and second tubes.

[0024] With this double-thread thread, when water pressure applies a force that tries to separate the connecting member 33 from the fixing member 31, a force is applied that presses the male thread 33a against the upper surface of the female thread 31a. In response to this, a convex shape 31a1 that serves as an engaging convex portion is formed on the threading surface, which is the upper surface of the female thread 31a, so that they engage with each other at the complete connection position, which is the complete screwing position, and a concave shape 33a1 that serves as an engaging concave portion is formed on the threading surface, which is the lower surface of the male thread 33a. The convex shape 31a1 is wedge-shaped, gradually rising toward the completion direction in the rotation direction during screwing, and the concave shape 33a1 is recessed in approximately the same shape to accommodate the wedge-shaped convex shape 31a1 and prevent disengagement in the engaged state. The direction in which the convex shape 31a1 protrudes and the direction in which the concave shape 33a1 recesses are in the direction in which they engage with each other in the disconnection direction, and when force is applied in the disconnection direction, the convex and concave portions engage more easily. In other words, the convex and concave portions are more likely to engage with each other in the disconnection direction.

[0025] To form the recessed shape 33a1, a thickened portion 33a2 is formed on the side of the male thread 33a. Also, a guide protrusion 31b is formed alongside the female thread 31a to form a gap large enough to allow the thickened portion 33a2 to pass through. Note that due to the removal process during resin molding, the female thread 31a is left with a gap portion 31a2 corresponding to the position where the guide protrusion 31b is formed.

[0026] 4 shows the state where the connecting member 33 begins to be screwed into the fixed member 31. When the male thread 33a is placed under the female thread 31a other than the female thread 31a that is to be screwed, and the connecting member 33 is rotated, the thick portion 33a2 begins to slide along the female thread 31a that is to be screwed. At this time, the tip of the thick portion 33a2 enters the gap between the female thread 31a and the guide protrusion 31b. The thick portion 33a2 is sandwiched between the female thread 31a and the guide protrusion 31b, and has almost no freedom of movement in the insertion / removal direction, but it can still rotate.

[0027] Here, cut surfaces 33a3, 31a3 are formed at the start and end of the threads forming the male screw 33a and the female screw 31a so that they do not interfere with each other when they are screwed together and come close to each other. FIG. 5 shows the state where the tip of the thick portion 33a2 of the male screw 33a has rotated until it abuts against the inclined surface of the wedge-shaped convex portion 31a1 formed on the male screw 33a.

[0028] At this point, the rear end of the thick portion 33a2 has almost no overlap with the guide protrusion 31b, but there is still a small overlap, and the inclined portion 31b1 formed on the guide protrusion 31b and the inclined portion 33a2a formed on the upper surface of the rear end of the thick portion 33a2 are beginning to face each other.

[0029] FIG. 6 shows a further rotated state. When the tip of thick portion 33a2 of male thread 33a abuts against the inclined surface of wedge-shaped convex portion 31a1 formed on male thread 33a and the male thread 33a continues to rotate, the tip of thick portion 33a2 rides up onto the inclined surface of convex portion 31a1, causing male thread 33a to move in the insertion direction. At this time, inclined surface 31b1 formed on guide convex portion 31b and inclined surface 33a2a formed on the upper surface of the rear end of thick portion 33a2 rotate while facing each other, so the inclined surfaces slide against each other, allowing the male thread 33a to move unhindered in the insertion direction.

[0030] 7 shows the state after further rotation. With further rotation, thick portion 33a2 of male thread 33a moves along the top of convex shape 31a1 of female thread 31a, and at some point convex shape 31a1 and concave shape 33a1 come face to face.

[0031] FIG. 8 shows the state immediately after the convex shape 31a1 and the concave shape 33a1 are brought into contact with each other. When the convex shape 31a1 and the concave shape 33a1 come into contact with each other, the male thread 33a moves from a state in which it rides on the convex shape 31a1 of the female thread 31a to a state in which the convex shape 31a1 and the concave shape 33a1 are engaged with each other. The wedge-shaped convex shape 31a1 and the concave shape 33a1 are shaped to prevent rotation in the direction opposite to the screwing direction when fastening. In other words, fastening is easy, and once fastened, the screwing is difficult to loosen. However, if the connecting member 33 is pushed in the insertion direction, the convex shape 31a1 no longer interferes with the concave shape 33a1, so in the pushed-in state, it is easy to rotate in the direction to loosen the screwing. In some cases, the user may overtighten the connecting member 33 in the screw tightening direction after the convex shape 31a1 and the concave shape 33a1 are engaged with each other. It is effective to provide a stopper wall 31s shown in Figures 21 and 23 further back than the convex shape 31a1 of the female screw 31a, so that the end of the male screw 33a hits against it and prevents it from rotating.

[0032] In this manner, the connecting member 33 is attached to the fixed member 31. That is, the entire switching mechanism 36 is supported by the fixed member 31 and the mixer body 20 via the connecting member 33. However, there may arise a situation where it is desired to remove the entire switching mechanism 36 from the fixed member 31 and the mixer body 20 for some reason.

[0033] In this case, the male thread 33a and the female thread 31a are engaged with each other by a concave-convex engagement structure as shown in Figure 8, and the engagement cannot be released by rotating them as they are. To release the engagement, the connecting member 33 is pushed toward the fixed member 31 as shown in Figure 7. By pushing it, the concave shape 33a1 comes out of the convex shape 31a1, and the engagement between the concave and convex parts is released. Once the engagement between the concave and convex parts is released, the connecting member 33 and the fixed member 31 can rotate relative to each other in the direction that releases the engagement between them. The state when rotation has begun is shown in Figure 6. If further rotation is attempted, the inclined surface 33a2a of the thick portion 33a2 comes into contact with the inclined surface 31b1 formed on the guide protrusion 31b, and the connecting portion 33 is pushed back from the fixed member 31 along the angle of the inclined surface. Figure 5 shows the state in which the thick portion 33a2 has been pushed back until it begins to get between the guide protrusion 31b and the female thread 31a.

[0034] When further rotated in the direction of releasing the screwing, because cut surface 33a3 is formed at the tip of male thread 33a, i.e., at the end of the thread, and cut surface 31a3 is formed at the rear end of one female thread 31a, i.e., at the start, both cut surfaces 33a3, 31a3 face each other when rotated, and instead of colliding with each other, they can rotate past each other while avoiding collision. If rotated in this manner, coupling member 33 will be released from screwing with fixed member 31 by a rotation of less than 180 degrees, and switching mechanism 36 can be removed from mixer body 20. In this way, the guide protrusion 31b can be moved along a predetermined path by sliding against the thick portion 33a2 when disengaging.

[0035] FIG. 9 shows a perspective view of the first pipe body as seen from below, and FIG. 10 shows a partially cutaway side view of the second pipe body. The first pipe, the fixing member 31, has a cylindrical section 31c formed downward from the center, which serves as a waterway, and the second pipe, the connecting member 33, can be inserted into this cylindrical section 31c, and the two are tightly fitted together with an O-ring 37 between them to ensure a watertight state.

[0036] When the O-ring 37 is installed, a circular groove is usually formed surrounding the insertion / removal direction to support the O-ring. When the two cylinders are inserted into each other, the O-ring remains supported on one side and is compressed between the inner surface of the outer cylinder and the outer surface of the inner cylinder, ensuring a watertight seal. In this case, the O-ring does not move in the insertion / removal direction.

[0037] However, a plurality of support protrusions 31c1 are formed at predetermined intervals on the outer peripheral surface of tubular portion 31c of fixing member 31 in the direction opposite to the insertion direction. Also, a plurality of support protrusions 33c1 are formed at predetermined intervals on the inner peripheral surface of connecting member 33 in the direction opposite to the insertion direction. The formation intervals of these support protrusions 31c1, 33c1 are the same, and they are formed so as to be in staggered positions at the end position of screwing of fixing member 31 and connecting member 33. In this embodiment, support protrusion 31c1 is short, and support protrusion 33c1 has a wide shape that is roughly trapezoidal.

[0038] At the position where the connection between the fixing member 31 and the connecting member 33 is completed, i.e., at the screwing end position, the support protrusions 31c1 and 33c1 are in staggered positions, and when the insertion direction is taken as the reference, the O-ring 37 abuts against multiple support protrusions 31c1 on one side and against multiple support protrusions 33c1 on the other side. Note that the staggered positions do not require one to be in the center of the other, as long as one is between the other two.

[0039] Referring now to FIG. 10, the connecting member 33 has a thick portion 33a2 of the male thread 33a, and a hole 33d is formed along the thick portion 33a2 so as to penetrate the cylindrical body.

[0040] The thick portion 33a2 is the portion where the recessed engagement portion of the concave-convex engagement structure is formed. A hole is formed through the tube body at a position that overlaps the formation position of this concave-convex engagement structure in the insertion direction. The presence of this hole makes the concave-convex engagement structure more flexible in the insertion direction. In the concave-convex engagement structure, the side where the recessed engagement portion is formed climbs up over the convex engagement portion, so by forming it to be more flexible, the total deflection can be the O-ring's compressive deformation, deflection deformation, and elastic deformation of the resin. The height of the concave-convex (hook) can be set very large, improving the strength and durability of the hook portion. Less force is required for the flexible engagement and release operations, improving operability. Figure 20 is a graph of the height and reaction force when the O-ring is deformed. The spring constant is almost constant up to a deflection of 1.5 mm, at which point a force of 40 N is generated. 22 shows the displacement when a normal force is applied to the two recessed portions 33a1 of the connecting member 33. The deflection when a force of 40 N is applied is 0.18 mm. It can be seen that the total deflection height can be set to 1.5 + 0.18 = 1.68 mm. In the actual product, the total deflection height was reduced by 20% to 1.4 mm. The O-ring deformation was 1.25 mm, the resin deformation was 0.15 mm, and the reaction force was about 28 N. The resin deformation deflection was less than half of the maximum allowable deflection, improving durability against repeated use. Such holes can be formed not only on the side of the connecting member 33 but also on the side of the fixing member 31. In other words, they may be formed on both or either of the first pipe body and the second pipe body.

[0041] 11 to 14 are schematic diagrams showing deformation of the O-ring during the threading process of the multiple thread mechanism. As described above, at the end of thread engagement, the male thread 33a and the female thread 31a are in a state where the convex shape 31a1 fits into the concave shape 33a1, resulting in a convex-concave engagement. As shown in Figure 11, the O-ring 37 abuts against multiple support protrusions 31c1 on one side and multiple support protrusions 33c1 on the other side. The protrusions of the support protrusions 31c1 and 33c1 are set so that the O-ring 37 is substantially linear at the end of thread engagement.

[0042] At the end of the threading operation, if the connecting member 33 is pushed in the insertion direction, the convex shape 31a1 will no longer interfere with the concave shape 33a1. Therefore, as the connecting member 33 is pushed in the insertion direction, the support protrusion 31c1 begins to abut against the O-ring 37, as shown in Fig. 12. As the connecting member 33 is pushed further, the straight O-ring 37 is bent toward the support protrusion 33c1, as shown in Fig. 13, resulting in a wavy flexure along the circumferential direction. At the same time, the concave shape 33a1 gradually moves away from the convex shape 31a1, and finally they no longer interfere with each other.

[0043] The O-ring 37, both immediately before and after being bent, exerts a force that tries to return to its original state as much as possible due to its elasticity. This force constantly biases the support protrusions 31c1, 33c1 in the direction of separation. In other words, because the fixing member 31 and the connecting portion 33 are biased in the direction of separation, at the end of the threaded engagement, the male thread 33a and the female thread 31a are biased so that the convex shape 31a1 fits into the concave shape 33a1, maintaining the convex-concave engagement state. Therefore, unless a large force is applied, the engagement will not naturally be released.

[0044] There are two types of deformations in the shape of the O-ring: (1) compression deformation, in which the wire diameter d is compressed, and (2) bending deformation, in which the entire O-ring is deformed into a wavy shape. The detachable structure of the present invention can be achieved with only (1), but the compression rate (crushing rate) of a typical O-ring is 40% of the wire diameter, and with a wire diameter of φ1.9 mm, the compression deformation alone is approximately 0.8 mm. This limits the height at which the convex shape 31a1 catches on the concave shape 33a1 to approximately 0.8 mm. Generally, in resin molding dies, blades with a radius of 0.2 to 0.3 mm are formed at the corners. Assume that the initial corner radius of the hook is 0. If the compressive tensile strength of the resin is 40N / mm^2 (square millimeters), and if a torque of 20N is applied to one side of the hook during operation, the corner will break due to shear failure, and a C-surface may be formed. If the cross-sectional area of ​​the fracture surface, surface C, is 0.5 mm^2, the height of the engagement between the male and female threads is 1.5 mm, so a surface C of C0.33 (= 0.5 / 1.5) mm can occur due to shear failure. If this corner's C0.3mm wears down to R0.4mm through repeated attachment and detachment, the hook's hooking height of 0.8mm will remove the straight part and make it more likely to come off. but, If the hook height is 1.4 mm, the straight section length of 0.4 mm will remain even after wear (= 1.4 - R0.5 - R0.5), so sufficient fixing strength will be obtained even after wear. From the above, it has been found that the hooking height of the hook part is small at 0.8 mm, and a height of about 1.4 mm is necessary, so this structure is primarily based on utilizing not only the compressive deformation of the O-ring but also its flexural deformation.

[0045] 15 to 18 are schematic diagrams showing deformation of the O-ring during the threading process of the multiple thread mechanism according to the modified example. In this modification, in addition to the support protrusion 31c1, small support protrusions 31c2, 31c2 with a small protrusion height are formed on the side of the fixing member 31. The small support protrusions 31c2, 31c2 are formed between the support protrusions 31c1 and 31c1, and because they have a small protrusion height, as described above, they only have an effect toward the end when the connecting member 33 is pushed in the insertion direction. Here, the support protrusion 31c1 corresponds to the large protrusion, and the small support protrusion 31c2 corresponds to the small protrusion. The small support protrusion 31c2, which is a small protrusion, is formed in a position that faces the mating support protrusion 33c1 at the end of the screwing position.

[0046] By doing so, the O-ring 37 can be used with a standard wire diameter of 1.9 mm (diameter) or with a thick wire diameter of 2.2 mm (diameter). Figure 15 shows the state at the end of the screwing. In the figure, the O-ring 37 shown with a solid line has a standard wire diameter of 1.9 mm (diameter). The dashed line shows the O-ring 37 with a thick wire diameter of 2.2 mm (diameter). In the case of the O-ring 37 with a standard wire diameter of 1.9 mm (diameter), the support protrusion 31c1 is in contact with the O-ring 37, but in the case of the O-ring 37 with a thick wire diameter of 2.2 mm (diameter), the tip of the support protrusion 31c1 is pushed in by 0.3 mm, the difference in wire diameter. The reaction force caused by the pushing acts to press the connecting portion 33 against the fixing member 31. Regardless of the O-ring 37's wire diameter, a watertight state can be maintained in this state.

[0047] Figure 16 shows the state in which the coupling portion 33 is pushed in the insertion direction, releasing the engagement between the convex portion 31a1 of the male thread 33a and the concave portion 33a1 of the female thread 31a. At this time, a portion of the O-ring 37 is sandwiched between the support protrusion 33c1 and the small support protrusions 31c2, 31c2. In the case of an O-ring 37 with a standard wire diameter of 1.9 mm, the distance between the support protrusion 33c1 and the small support protrusions 31c2, 31c2 is set to 1.9 mm, so that although the O-ring 37 comes into contact with the support protrusion 33c1, it is not deformed by being pushed in. The reaction force generated when the support protrusion 31c1 pushes in the O-ring 37 is the same as that shown in Figures 11 to 14.

[0048] However, in the case of O-ring 37 with a thick wire diameter of 2.2 mm, in addition to the O-ring 37 being pressed and deformed by the height of small support protrusions 31c2, 31c2 at the portion sandwiched between support protrusion 33c1 and small support protrusions 31c2, 31c2, support protrusion 31c1 also presses O-ring 37 by an additional 0.3 mm. The reaction force generated by these forces is stronger than that shown in Figures 11 to 14.

[0049] By forming the small support protrusions 31c2, 31c2 in this manner, in addition to the O-ring 37 with a standard wire diameter of 1.9 mm (diameter), even an O-ring 37 with a thick wire diameter of 2.2 mm (diameter) can be used with only a slight increase in reaction force.

[0050] FIG. 17 shows the state in which the coupling element 33 is rotated in a direction to release the threaded engagement while being pushed in the insertion direction. Furthermore, FIG. 18 shows the state in which the thick portion 33a2 of the male thread 33a descends along the slope of the convex portion 31a1 of the female thread 31a. The O-ring 37 is bent in a wave-like shape to allow the engagement to be released by pushing the coupling element 33 in by the height of the convex portion 31a1. After release, when the coupling element 33 is rotated so that the thick portion 33a2 of the male thread 33a no longer overlaps the convex portion 31a1 of the female thread 31a, the support protrusion 31c1 no longer needs to bend the O-ring 37. Furthermore, because the coupling element 33 is rotated in a direction to release the threaded engagement, the engagement angle between the male thread 33a and the female thread 31a decreases, and the relative overlap between the coupling element 33 and the fixing member 31 also decreases. As a result, the tip of the support protrusion 31c1 moves away from the surface of the O-ring 37, as shown in FIG. 18.

[0051] FIG. 19 is a schematic diagram showing the force vectors when the O-ring is deformed. There are valleys between the multiple support protrusions 33c1, and the boundary leading to the valleys is a slope. The position of the support protrusion 31c1 may be above the horizontal plane of the valley, but it may also be closer to the slope on the left side, in which case the following effects are obtained. When a user attempts to remove the shower unit by applying a force Fhy from bottom to top to the water discharge cap 35, water channel switching member 34, etc., as shown in Figure 19, the connecting member 33 is pressed upward, and the support protrusion 33c1 (and the slope and valley) presses the O-ring 37 upward. A load P2 is applied to the fixed member 31. The load P2 is an oblique load applied from the slope and is divided into component forces p2x and p2y. The component force p2y is the force with which the O-ring 37 presses the protrusion 31c1 to the right. At the same time, the slope of the connecting member 33 receives a reaction force g2x'. This becomes a torque that rotates the connecting member 33 counterclockwise. (If there are six protrusions 31c1, the torque is 6×g2x'.) The torque causes the connecting member 33 to rotate, but the concave shape 33a1 is pressed against the convex shape 31a1 and the connecting member 33 cannot rotate. In Figure 19, if the height of the convex support protrusion 31c1 is 1.4 mm and the height of the convex support protrusion 33c1 is 0.8 mm, the O-ring 37 will bend 0.8 mm like a snake. Assume that the support protrusion 31c1 sinks into the O-ring 37, causing a compressive deformation of 0.6 mm. The total displacement is 1.4 mm, and no load P3 is generated.

[0052] Figure 20 is a graph of the height and reaction force when the O-ring is deformed. When the support protrusion 33c1 is pressed from below with a force of Fhy = 38N, the connecting member 33 (concave shape 33a1) rises 1.4 mm and no longer interferes with the convex shape 31a1. At this time, the torque 6 × g2x' is generated, so the connecting member 33 can be rotated and detached from the fixing member 31 by the rotation torque caused by the application of vertical pressure, even without the user intentionally rotating it. By utilizing this torque, users can enjoy the following benefits when removing the bolt: It is a two-step action: 1) press down from below, then 2) rotate counterclockwise. 1) If you press from below, a counterclockwise torque proportional to the pressure from below will be generated in conjunction with the torque in 2), making it easier to attach and detach.

[0053] However, there are cases where the user is weak and can only apply a vertical pressure of 25 N (= p2y × 6). From the graph in Figure 20, when the vertical pressure is 25 N, the displacement height is 1.1 mm. If the slope angle on both sides of the support protrusion 33c1 is 45°, p2x=p2y=25 / 6=4.2N Furthermore, a reaction force g2x' to p2x acts on the right slope of the support protrusion 33c1.

[0054] Figure 21 is a schematic diagram showing the connecting member and the waterway switching member. The figure shows the state in which the connecting member 33 having the concave shape 33a1 is raised by 1.1 mm, leaving a 0.3 mm high catch in the concave-convex engagement with the convex shape 31a1. When contact is made between contacts with an angle R of 0.3 mm, the contact angle θ = asin(0.15 / 0.3) = 30°. The vertical force Fhy applied by hand is absorbed by the fixing member 31, but the resulting torque, half of 6 × g2x' × R6.8 (3 × g2x' × R6.8 = 3 × 4.2 × 6.8 = 85 Nmm), acts on one side of the concave-convex engagement structure, causing the corner R of the concave shape 33a1 of the connecting member 33 to press horizontally against the corner R of the convex shape 31a1 of the fixing member 31. If the effective radius of the trapezoidal screw is R11.5, the resulting horizontal force is 7.4 N (= 85 / 11.5). At the contact point of the R angle, a reaction force F4 occurs at an angle of 30°, so The horizontal component of the force is f4x=3×g2x'=7.4N, The normal component of the force is f4y=f4x×tan30°=7.4 / √3=4.3N This becomes:

[0055] FIG. 22 shows the displacement when a normal force is applied to the two recessed shapes 33a1 of the connecting member 33, and FIG. 23 shows a schematic diagram of the force vector when the user applies additional torque. If the user manually applies an additional torque of 8 x g2x' x R6.8, the torque will be reduced by half. 4×g2x'×R6.8 (=4×4.2×6.8=114Nmm) acts on one of the hook parts that make up the concave-convex engagement structure. If the radius of the hook part is R11.6mm, then The additional horizontal force generated is 10 N (= 114 / R11.6), which increases the horizontal force to 17.4 N (= 7.4 + 10). Also, the vertical component of the force is f4y = f4x × tan30° = 17.4 / √3 = 10N. A total vertical force of 20 N is generated at the two hook portions, and the resulting displacement is 0.12 mm, as can be seen from the graph in Figure 22. At this time, even if the connecting member 33 is stationary, only the recessed shape 33a1 deforms and moves upward by 0.12 mm, and the hooking height decreases by 0.12 mm from 0.3 mm to 0.18 mm.

[0056] As a result, the contact points between the corners with R0.3mm also move. As for the contact angle, it increases to θ = asin((0.3 - 0.09) · 0.3) = 44.4°, so the normal component of force f4y also increases. f4y=f4x×tan44.4°=17.4*0.98=17.1N. The total vertical force at the two locations is 34.2 N. Then, from the graph in Figure 20, the vertical displacement generated at O-ring 37 is 1.35 mm. The displacement of the hook portion due to the normal force f4y is 0.17 mm according to the graph in Figure 22, and the total displacement of the hook portion and O-ring 37 is 1.52 mm. In other words, this is larger than the height of support protrusion 31c1, 1.4 mm, and so the hook portion can be removed.

[0057] In this way, even if the initial normal force Fhy applied by the user is insufficient to disengage the hook portion, once the contact of the hook portion in the concave-convex engagement structure reaches the R-shaped portion, the torque coupled with the normal force and the additional torque applied by the user will generate a normal component force f4y at the R-shaped portion of the hook portion, causing upward deformation. This will move the contact point on the R-shaped portion, increasing the contact angle θ. This will then increase the normal force due to the wedge effect. As a result, as the additional torque increases and the normal component force f4y becomes greater than the initial normal force Fhy, the displacement of the O-ring 37 will also increase. Providing a rounded corner on the hook reduces the straight portion of the total hooking height of 1.4 mm, which has the disadvantage of making it easier to remove, but with an appropriate rounded corner, even if the user does not apply enough vertical force Fhy in the first stage of removal, the rotational torque in the second stage can be expected to have a significant effect in allowing the hook to be removed smoothly.

[0058] Incidentally, the internal pressure of the waterway can increase. When the internal pressure increases, as in the case of Figure 10, pressure is applied to the underside of O-ring 37, so conventionally, the upper side of O-ring 37 is designed to be fully supported. However, in the structure of the present invention, the upper side of O-ring 37 is partially supported by support protrusion 31c1. The area of ​​O-ring 37 where support protrusion 31c1 is not installed will bend upward in response to the pressure. Therefore, with the sealing structure of the present invention, it is necessary to understand the pressure, amount of deflection, and maximum allowable pressure depending on the application. The maximum operating pressure for a shower faucet equipped with an electrolytic hypochlorous acid generator is about 0.02 MPa. The maximum operating pressure of the water supply is 0.74 MPa.

[0059] In this example, a φ1.9 mm O-ring 37 was used and an internal pressure of 0.74 MPa was applied, and no water leaks occurred. If used with tap water, it will be necessary to reduce the pressure with a pressure reducing valve or change the shape conditions. Referring to the graph in Figure 20, it can be seen that a force of approximately 24 N is required to displace the object by 1 mm. 1) The force with which the six support protrusions 31c1 press the O-ring 37 from above 2) Friction force on the inside and outside of O-ring 37 is the resultant force of Let's calculate the friction force 2). If the compression allowance of O-ring 37 is 0.2 mm, the stress per unit circumference is 0.5 N / mm^2. If the circumference of O-ring 37 is 43 mm, the compression force is 21.5 N.

[0060] If the coefficient of friction is 0.24, a frictional force of approximately 5 N is generated inside and outside the O-ring 37. The total frictional force inside and outside is 10 N. 14 N, obtained by subtracting the frictional force of 10 N from the pressing force of 24 N, is the actual force applied to and deflecting the O-ring 37. 14 N / 6 = 2.3 N is the force applied from each support protrusion 31 c 1. Here, the Young's modulus of an O-ring with a hardness of 70 is 5 MPa, the spatial distance L between the support projections 33c1 is 4 mm, and the deflection amount δ is calculated as follows: δ=PL^3 / 48EI≒1 The actual deflection amount matches the calculated value. The underside of the O-ring 37 is supported by six support protrusions 33c1, so a force of 24N / 6=4N is required at each point for the O-ring 37 to overcome the frictional force and bend upward.

[0061] The area of ​​each support protrusion 33c1 is about 5mm^2, so the pressure is 4N / 5mm^2=0.8MPa However, when the O-ring 37 bends due to the pressure of the liquid or gas, there are six support protrusions 33c1 on the underside of the O-ring 37, and pressure is less likely to act on this area. There are six valleys where there are no support protrusions 33c1, and each has an area of ​​7mm^2. When a load of 4N is applied to each of these areas, the pressure becomes 0.6MPa. However, since the support protrusion 31c1 exists above the valley range, the bending cannot continue. At about 0.6 MPa, it is thought that the displacement of the O-ring 37 will be less than 1 mm. Although it is possible to estimate the pressure and amount of deflection at which the O-ring 37 bends, accurate calculations are difficult, so it is preferable to confirm by actual measurement.

[0062] If you want to increase the pressure resistance, 1) Increase the wire diameter and hardness of the O-ring, 2) Increasing the number of support protrusions 31c1; 3) Reducing the gap at the outer end of the cylindrical portion 31c increases pressure loss. 4) Reduce the height of the gap where the O-ring 37 deflects upward (=height of the support protrusion 31c1), 5) It is possible to increase the radial compression allowance of the O-ring 37 (to prevent leakage even if the O-ring 37 bends like a bellows). On the other hand, if you want to intentionally create a leak at the low pressure stage and have it function like a safety valve, you can do the opposite adjustment.You can also change to a sealing ring that is more flexible, such as a Y-ring.

[0063] In this way, the detachable structure for the pipe body of the present invention can be used for connecting pipes other than shower faucets, and a pressure reducing function can also be added thereto.

[0064] It goes without saying that the present invention is not limited to the above-described embodiments. - Applying mutually replaceable components and configurations disclosed in the above embodiments by appropriately changing their combinations. Although not disclosed in the above embodiments, members and configurations that are publicly known and can be mutually substituted for the members and configurations disclosed in the above embodiments may be appropriately substituted, and their combinations may be changed and applied. Although not disclosed in the above embodiments, members and configurations may be substituted by those skilled in the art based on publicly known techniques as substitutes for the members and configurations disclosed in the above embodiments, and the combinations may be changed and applied. is disclosed as an embodiment of the present invention.

[0065] Furthermore, in this embodiment The outer cylindrical portion of the fixing member 31 may have an angular range that does not include the convex portion 31a1 cut away, The female screws 31a, 31a on almost the entire circumference of the inner wall are limited to an angle range of less than 90° only around the convex shape 31a1, and the rest are cut off or In one example, the male threads of the connecting member 33 are limited to an angle range of less than 90° only around the recessed shape 33a1, and the rest of the threads are cut off to form a pipe connection structure.

[0066] The thread pitch may also be zero. Although this type of shape eliminates the ease of attachment and detachment afforded by threaded engagement, the simple shape reduces costs, making it effective as a connecting structure for pipes that are not frequently attached or detached. In other words, it can be used as a shower switching faucet that is attached to a water faucet to switch between a straight water spout and a shower water spout, as well as a hose adapter that attaches a hose to a water faucet. [Explanation of symbols]

[0067] 10...Shower switching faucet, 20...Mixer body, 30...Shower switching mechanism, 31...Fixing member, 31a...Female screw, 31a1...Convex shape, 31a2...Gap portion, 31a3...Cut surface, 31b...Guide convex portion, 31b1...Sloped portion, 31c...Cylindrical portion, 31c1...Support protrusion, 31c2...Small support protrusion, 32...Switching ring, 33...Connecting member, 33a...Male screw, 33a1...Concave shape, 33a2...Thick portion, 33a2a...Sloped portion, 33a3...Cut surface, 33c1...Support protrusion, 33d...Hole, 34...Waterway switching member, 35...Water outlet cap, 36...Switching mechanism, 37...O-ring.

Claims

1. A shower switching faucet that can switch between shower spouting and straight spouting, comprising a fixed member connected to the upstream side of the waterway, and a switching mechanism that is detachably connected to the fixed member and switches between shower spouting and straight spouting, the fixing member has a first pipe, and the switching mechanism has a second pipe; The first pipe body and the second pipe body can be connected to each other by a screw mechanism that can be connected and disconnected in less than one rotation, The shower switching faucet is characterized in that the screw mechanism has a concave-convex engagement structure that can engage with each other in the disconnection direction at the connection completion position.

2. The shower switching faucet according to claim 1, wherein the screw mechanism is a single-start screw or a multiple-start screw mechanism.

3. The shower switch faucet described in claim 1, characterized in that the first pipe body and the second pipe body are watertight with an O-ring interposed therebetween, and support protrusions are formed on the wall surfaces of the first pipe body and the second pipe body facing each other, in a staggered manner, to support the O-ring from the direction opposite to the insertion direction.

4. 4. The shower switching faucet according to claim 3, wherein the support protrusion comprises a large protrusion and a small protrusion, and the small protrusion is also formed at a position facing the mating support protrusion.

5. The shower switching faucet as described in claim 1, characterized in that both or one of the first pipe body and the second pipe body have holes formed therethrough at a position that overlaps with the position where the concave-convex engagement structure is formed in the insertion direction.

6. The shower switch faucet described in claim 2, characterized in that the concave-convex engagement structure of the multiple-start screw mechanism has an engagement convex portion on the threaded surface of one of the multiple-start screws, and the other multiple-start screw has a thick portion that is thick enough to allow the engagement convex portion to enter and form an engagement concave portion into which the engagement convex portion can enter and engage, and on the side of the first pipe body and the second pipe body where the one multiple-start screw is formed, a guide convex portion is formed that slides against the thick portion when disengaging, causing the pipe body to move in a predetermined trajectory.

7. The shower switching faucet according to claim 2, wherein the multiple thread mechanism has a cut surface formed at the beginning or end of the threads.

8. The first pipe and the second pipe are connected by a protrusion provided on the outside of either pipe; A pipe body connecting structure in which the other pipe is connected by a locking portion provided on the outside of the other pipe, which can hook and fix the protrusion, The first pipe body and the second pipe body can be connected and disconnected in less than one rotation, and A pipe connection structure characterized in that an O-ring is interposed between the first pipe body and the second pipe body to create a watertight state, and support protrusions are formed on the wall surfaces of the first pipe body and the second pipe body facing each other so as to support the O-ring from the direction opposite to the insertion direction in a staggered manner.

9. 9. The pipe connecting structure according to claim 8, wherein the support projection is formed of a large projection and a small projection, and the small projection is also formed at a position facing the mating support projection.

10. The first pipe body and the second pipe body can be connected and disconnected by a multiple thread screw mechanism in less than one rotation, An engaging protrusion is provided on the threaded surface of one of the multiple-start threads, and the other multiple-start thread has a thick portion formed therein that is thick enough to form an engaging recess into which the engaging protrusion can enter and engage, A pipe connection structure characterized in that a guide protrusion is formed on the side of the first pipe body and the second pipe body where one of the multiple threads is formed, which slides against the thick-walled portion when disengaging, thereby moving the pipe body in a predetermined trajectory.

11. 11. The pipe connection structure according to claim 10, wherein the multiple thread mechanism has a cut surface formed at the start or end of the threads.

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