JP4695019B2 - Water faucet - Google Patents

Description

  The present invention relates to a water faucet, and more particularly to a water faucet in which a valve body is switched between a forward position and a backward position by a thrust lock mechanism and held at each position.

Conventionally, a faucet provided with a thrust lock mechanism, in which the valve body is switched between a forward position and a backward position by the thrust lock mechanism and held at each position, is known.
For example, Patent Literature 1 below discloses a water faucet equipped with this type of thrust lock mechanism.

  Here, the thrust lock mechanism is configured such that (a) the rotor and (b) its driving cam surface abut on the first driven cam surface of the rotor by forward movement, and the rotor is brought to the first stopper position by cam action. (C) The guide cam surface is brought into contact with the second driven cam surface of the rotor by a biasing force in the backward direction of the rotor by the biasing means, and the rotor is driven by the cam action. The lock is further released to the second stopper position or the backward allowance position in the same direction as the rotational drive direction, and the rotor is locked at the second stopper position and the lock release is allowed at each second rotational movement of the rotor. And a lock portion for alternately moving the valve body forward and backward as the rotor moves forward and backward, and alternately holds the valve body at the forward position and the backward position.

However, in the case of a conventional faucet with a thrust lock mechanism, the rotor is vigorously rotated to the first stopper position by the cam action of the driving cam surface and the first driven cam surface by the forward movement of the driving element. There is a problem that the collision sound generated in the sound is generated as a loud operation sound.
When the operation noise is large in this way, the operation sound is noticeable especially when the faucet is used in a narrow bathroom, a washroom, etc., and the user feels uncomfortable.

  On the other hand, when the heart cam mechanism is used instead of the thrust lock mechanism to reduce the operation sound, the click feeling (moderation feeling) during operation is insufficient and unreliable, and the operation feeling (operation feeling) during faucet operation deteriorates. Therefore, it gives a low-level feeling to the user.

JP 2001-98596 A

  The present invention is based on the circumstances as described above, and it is possible to reduce the operation sound when the thrust lock mechanism is operated, and to ensure an appropriate click feeling (moderation feeling) and to have a good operation feeling. It was made for the purpose of providing a faucet with a mechanism.

  Thus, according to the first aspect of the present invention, (a) the rotor and (b) its driving cam surface is brought into contact with the first driven cam surface of the rotor by forward movement, and the rotor is moved by cam action. A driving element that rotates at a predetermined angle to the first stopper position, and (c) the guide cam surface is brought into contact with the second driven cam surface of the rotor by the biasing force of the rotor in the backward direction by the biasing means. The rotor is further rotated by the cam action in the same direction as the rotational driving direction to the second stopper position or the retreat allowable position, and the second stopper position with respect to the rotor is rotated for each rotation of the rotor. A thrust lock mechanism that alternately performs locking and unlocking that allows backward movement, and moves the valve body forward and backward as the rotor moves forward and backward. Faucet adapted to hold the valve body alternately between the position and the retracted position Fraud and mitigating risk inclination angle of the first driven cam surface, characterized in that no smaller angle than the inclination angle of the second follower cam surfaces.

  According to a second aspect of the present invention, in the first aspect, the drive cam surface and the first driven cam surface have different inclination angles.

Effects and effects of the invention

  As described above, according to the present invention, in the water faucet with the thrust lock mechanism, the inclination angle of the first driven cam surface of the rotor that contacts the drive cam surface of the drive element is the second angle that contacts the guide cam surface of the lock portion. The angle is smaller than the inclination angle of the driven cam surface.

  That is, in the prior art, the inclination angle of the first driven cam surface and the inclination angle of the second driven cam surface are the same, but in the present invention, the inclination angle of the first driven cam surface is set to the second driven cam surface. According to the present invention, the rotor is rotated to the first stopper position by the cam action of the drive cam surface and the first driven cam surface by the forward movement of the driver. It is possible to reduce the momentum at the time of operation, and it is possible to reduce the collision sound, that is, the operation sound when the rotor is stopped at the first stopper position.

Therefore, when a faucet with a thrust lock mechanism is used in a narrow bathroom or washroom, it can solve the problem of generating a loud operating sound and causing discomfort to the user. Can be used. Further, in the present invention, by using the thrust lock mechanism, an appropriate click feeling can be given during operation.
When the rotor is rotated to the second stopper position by the cam action of the guide cam surface of the lock portion and the second driven cam surface of the rotor based on the biasing force of the rotor in the backward direction by the biasing means. However, if the inclination angle of the second driven cam surface is reduced to match the first driven cam surface in order to reduce the operation sound at this time, the rotor is rotated in the same direction. There is a risk that the rotational force of the rotor may deteriorate due to the weak force.

When the rotor is rotationally driven by the forward movement of the driver, the forward force of the driver and the backward force of the urging means act on the rotor from both directions, and these rotate the rotor. However, when the rotor is rotated by the cam action of the guide cam surface in the lock portion, only the force in the backward direction of the urging means acts on the rotor. When the inclination angle of the second driven cam surface is a small angle, there is a risk that the rotor will not rotate smoothly due to the weak rotational force.
In the present invention, however, the second driven cam surface is rotated by the cam action of the guide cam surface and the second driven cam surface by securing the inclined angle of the second driven cam surface at a large angle with respect to the inclined angle of the first driven cam surface. Smooth rotation can be ensured when the child is rotated.

In the present invention, the inclination angle of the drive cam surface on the driver side and the first driven cam surface on the rotor side can be made different (claim 2).
By doing so, the driving cam surface and the first driven cam surface can be brought into line contact instead of surface contact, and the contact resistance is reduced with respect to the surface contact, and the rotor is rotated more stably. be able to.
In this case, the inclination angle of the drive cam surface can be made larger than the inclination angle of the first driven cam surface.
In this way, it is possible to effectively increase the rotational driving force of the rotor due to the cam action of the drive cam surface and the first driven cam surface while reducing the inclination angle of the first driven cam surface.

Next, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 shows the main part of a faucet that performs pilot water discharge and flow rate adjustment (flow control). In FIG. 1, reference numeral 10 denotes a body in the faucet, which forms a main water channel inside the faucet. A secondary inflow water channel 12 and a secondary outflow water channel 14 are formed.

In this embodiment, the entire valve mechanism is configured as a detachable valve cartridge 16 as a single unit. In the figure, reference numeral 18 denotes a cartridge case of the valve cartridge 16, which is divided into an upper part 18-1 and a lower part 18-2, and these are the later-described backs forming an intermediate part of the cartridge case 18. The pressure chamber forming member 54 is elastically connected.
The valve cartridge 16 is fixed in a state of being prevented from being pulled out by screwing a fixing nut 19 into the body 10 while being inserted into the body 10.

  In FIG. 1, reference numeral 20 denotes a main valve comprising a diaphragm valve provided on the main water channel. The main valve 20 comprises a resin-made hard main valve body 22 and a rubber diaphragm film 24 held thereby.

The main valve 20 moves back and forth in the vertical direction in the figure with respect to the main valve seat 25 to open and close the main water channel and to change the opening of the main water channel.
Specifically, the main water channel is blocked by sitting on the main valve seat 25, and the main water channel is opened by separating from the main valve seat 25 upward in the figure.
Moreover, the opening degree of the main water channel is changed in magnitude according to the distance from the main valve seat 25, and the flow rate of water flowing through the main water channel, that is, the flow rate from the water discharge portion is adjusted.

A back pressure chamber 26 is formed behind the upper side of the main valve 20 in the figure.
The back pressure chamber 26 causes the internal pressure to act on the main valve 20 as a pressing force in the downward valve closing direction in the figure.
The main valve 20 is provided with an introduction small hole 28 that passes through the main valve 20 and allows the primary inflow water passage 12 and the back pressure chamber 26 to communicate with each other.
The introduction small hole 28 leads the water from the inflow water channel 12 to the back pressure chamber 26 and increases the pressure of the back pressure chamber 26.

The main valve 20 is also provided with a pilot water channel 30 as a water drainage channel that passes through the main valve 20 and communicates the back pressure chamber 26 and the secondary outflow water channel 14.
The pilot water channel 30 draws the water in the back pressure chamber 26 to the outflow water channel 14 and reduces the pressure in the back pressure chamber 26.

  As shown in FIG. 1, the main valve 20 is provided with a through-hole penetrating in the axial direction at the center thereof, and serves as a discharge water pilot valve and a flow control pilot valve. The pilot water channel 30 is formed between the outer peripheral surface of the pilot valve 34 and the inner peripheral surface of the through hole.

As shown in FIGS. 4 and 5, the main valve 20 is integrally provided with a pilot valve seat 36 having an annular shape around the axis of the main valve 20 along the inner peripheral surface of the through hole. .
Reference numeral 38 denotes a seal portion in the pilot valve seat 36, which holds an O-ring 40 as an elastic seal ring having an annular shape inside the annular groove.

The pilot valve 34 is fitted to the pilot valve seat 36 so as to be movable back and forth in the vertical direction in the figure along the axis of the main valve 20.
Specifically, the pilot valve 34 has a circular cross section and has a seal portion 42 having the same outer diameter in the vertical direction in the drawing, that is, the forward and backward direction, and an annular recess 44 on the lower side (lower side in the drawing). Have.
Each end of the annular recess 44 in the axial direction is a tapered surface that gradually decreases in diameter toward the smallest diameter portion of the recess 44, and a stepped portion is provided at each end on the large diameter side of the tapered surface. 48 and 50 are formed.

FIG. 1 shows the state of the pilot valve 34 when the water is stopped. At this time, the pilot valve 34 has the seal portion 42 in the radial direction over the entire circumference with respect to the pilot valve seat 36 via the O-ring 40. It is in the state which made the elastic contact and sealed between the pilot valve 34 and the pilot valve seat 36 watertight.
At this time, the main valve 20 is seated on the main valve seat 25, and the main water channel is closed.

4 and 5 show the action at the time of flow adjustment (flow rate adjustment) by the movement of the pilot valve 34.
In this embodiment, the pilot valve 34 does not close the pilot water channel 30 during flow adjustment, and only the opening of the pilot water channel 30 is changed by the movement.
The amount of rotation operation with respect to the later-described rotating sleeve 84 is so regulated.

In this embodiment, as shown in FIG. 4 (I), when the pilot valve 34 moves backward upward in the figure, the clearance between the pilot valve 34 and the pilot valve seat 36 becomes large, and the inside of the back pressure chamber 26 is increased. A large amount of water escapes to the outflow water channel 14 side through the pilot water channel 30, and the pressure in the back pressure chamber 26 decreases.
Therefore, the main valve 20 moves backward in the figure due to the pressure difference with the inflow water passage 12, and the pressure in the inflow water passage 12 and the pressure in the back pressure chamber 26 are balanced as shown in FIG. 4 (II). The backward movement of the main valve 20 stops at the position.
That is, the main valve 20 moves backward so as to follow the backward movement of the pilot valve 34, and the main valve 20 also stops when the pilot valve 34 stops.

  As the main valve 20 moves backward, the gap between the main valve 20 and the main valve seat 25 becomes large, and the amount of water flowing from the inflow water channel 12 into the outflow water channel 14 increases.

  When the pilot valve 34 is further moved backward in the figure from this state, the main valve 20 follows the backward movement of the pilot valve 34 so that the pressure in the back pressure chamber 26 and the pressure in the inflow water passage 12 are balanced. Then, it moves backward, further increasing the opening of the main water channel and increasing the flow rate of water flowing through the main water channel (see FIG. 4 (III)).

  On the other hand, when the pilot valve 34 moves forward downward in the drawing as shown in FIG. 5 (I), between the pilot valve 34 and the pilot valve seat 36, more specifically, the seal portion 42 and the pilot valve seat in the pilot valve 34. The clearance between the O-ring 40 and the O-ring 40 held by the pipe 36 is reduced, that is, the opening of the pilot water passage 30 is reduced, and the amount of water flowing from the back pressure chamber 26 to the outflow water passage 14 is reduced. The pressure increases.

For this reason, the main valve 20 moves forward downward in the figure due to the increased pressure, and stops at a position where the pressure of the back pressure chamber 26 and the pressure of the inflow water passage 12 are balanced.
At this time, the gap between the main valve 20 and the main valve seat 25 is reduced, that is, the opening of the main water passage is reduced, and the flow rate of water flowing through the main water passage is reduced (see FIG. 5 (II)).

  Then, when the pilot valve 34 further moves downward in the figure from this state, the opening of the main water channel is further reduced, and the flow rate of water flowing through the main water channel is further reduced (see FIG. 5 (III)).

In FIG. 1, reference numeral 54 denotes a back pressure chamber forming member having an inverted cup shape, and the back pressure chamber 26 is formed inside thereof.
The back pressure chamber forming member 54 also serves as a main valve presser.

The back pressure chamber forming member 54 holds an O-ring 52 as an annular seal ring having a pair of elasticity.
These O-rings 52 are in elastic contact with the outer peripheral surface of the first shaft portion 62 of the working shaft 60 described later over the entire circumference, and thus, between the first shaft portion 62 and the back pressure chamber forming member 54, that is, the back pressure chamber. 26 is sealed watertight.
An O-ring 56 is also held on the outer peripheral surface of the lower portion 18-2 of the cartridge case 18, and the space between the O-ring 56 and the body 10 is sealed in a watertight manner.

In FIG. 1, reference numeral 60 denotes a working shaft that causes the pilot valve 34 to act on the applied operating force. The working shaft 60 is a control shaft portion that extends in the axial direction with a uniform circular cross section and a uniform outer diameter. The first shaft portion 62 and the cylindrical second shaft portion 64 are divided into two in the axial direction.
The pilot valve 34 is integrally formed at the lower portion of the first shaft portion 62 serving as the control shaft portion in the figure.
The cylindrical second shaft portion 64 is provided with a female screw 66 on the inner peripheral surface thereof.

On the other hand, the first shaft portion 62 has a large-diameter head 68 that can be relatively moved three-dimensionally by a ball joint 67 at its upper end, and a male screw 70 is provided on the outer peripheral surface of the head 68. ing.
The male screw 70 of the first shaft portion 62 is screwed into the female screw 66 of the second shaft portion 64.

In the action shaft 60, the first shaft portion 62 moves forward and backward in the vertical direction in the drawing by the screw feeding action of the female screw 66 and the male screw 70.
That is, the entire working shaft 60 is expanded and contracted as a whole by the screw feed of the female screw 66 and the male screw 70.

The head 68 on the first shaft 62 side is formed with flat engaging surfaces 72 that are parallel to each other as shown in FIG. The sandwiching piece 74 is sandwiched, and the sandwiching action of these sandwiching pieces 74 prevents the first shaft portion 62 from rotating.
That is, the rotation preventing member 76 prevents the first shaft 62 from moving forward and backward in the figure by the rotation of the second shaft 64.
As the first shaft 62 moves forward and backward in the figure, the pilot valve 34 that is integrally formed on the tip side of the first shaft part 62 is integrally moved forward and backward in the figure, thereby the pilot valve. The position of 34 is changed in the same direction.

  Here, the rotation-preventing member 76 has a circular pedestal portion 78, and the pedestal portion 78 is fixed to the back pressure chamber forming member 54 below the pedestal portion 78.

In FIG. 1, reference numeral 80 denotes a drive mechanism for driving the first shaft portion 62 of the working shaft 60, that is, the pilot valve 34 integrally formed therewith, and a push button (driver) 82 having a bottomed cylindrical shape. And a rotating sleeve (locking portion) 84 and a rotor 86 constituting an element of a thrust lock mechanism (see FIG. 2).
The rotating sleeve 84 is a portion that adjusts the flow rate by moving the main valve 20 following the movement by moving the pilot valve 34 forward and backward as shown in FIGS. The button 82 is a part for switching the position of the pilot valve 34 between a valve closing position that is a forward position and a valve opening position that is a raised position for each depression.

As shown in FIG. 1, the lower portion of the rotary sleeve 84 is assembled to the upper portion 18-1 of the cartridge case 18 so as to be rotatable and fitted in a state of being secured.
The push button 82 is fitted in the rotary sleeve 84 and is movable in the axial direction, that is, in the vertical direction in the figure with respect to the rotary sleeve 84.
On the outer peripheral surface of the push button 82, a vertical protrusion 87 is fitted in a vertical recess 88 on the inner surface of the rotary sleeve 84, and the push button 82 rotates integrally with the rotation of the rotary sleeve 84. Yes.
That is, the rotational movement of the rotary sleeve 84 is transmitted to the push button 82.

The push button 82 also has a vertical recess 90 formed on the inner peripheral surface thereof, and a vertical protrusion provided on the outer peripheral surface of the second shaft portion 64 as a female screw member in the working shaft 60. The strips 91 are fitted, and the second shaft portion 64 rotates integrally with the push button 82.
That is, when the rotary sleeve 84 is rotated, the rotary motion is transmitted to the second shaft portion 64 via the push button 82, and the second shaft portion 64 rotates.
A guide protrusion 92 is provided on the outer peripheral surface of the push button 82.
The guide projection 92 is inserted into the insertion groove 94 of the rotary sleeve 84 to provide guidance when the push button 82 slides in the vertical direction.

At the lower end of the push button 82, as shown in FIG. 3, engaging teeth 96 having a mountain shape are continuously provided at a predetermined pitch along the circumferential direction.
On the lower surface of the engaging tooth 96, there is formed a drive cam surface 98 for rotating the rotor 86 directly below by a cam action by the vertical movement of the push button 82, that is, the downward forward movement and the upward backward movement. .

The rotor 86 is composed of a ring-shaped member, and engaging teeth 100 protruding upward in the figure in a mountain shape are provided at a plurality of circumferential positions (here, four positions).
In addition, an engagement tooth 102 having a sawtooth shape protruding outward is provided at the same position in the circumferential direction and is also provided upward.

The inner engagement tooth 100 has a first driven cam surface 104 corresponding to the drive cam surface 98 of the push button 82 on the upper surface along one oblique side.
Here, the inclination angle θ ₁ of the first driven cam surface 104 is the same as that of the drive cam surface 98 on the push button 82 side.

On the other hand also in the outside of the engaging teeth 102, the upper surface along its hypotenuse is the second driven cam surface 106 which is inclined at an angle theta _2.
In this embodiment, the first driven cam surface 104 Yes inclined angle so that different the second driven cam surface 106, the inclination angle theta ₂ of the second driven cam surface 106 forms the acute angle, the contrast 1 the inclination angle theta ₁ of the driven cam surface 104 is a small angle.

2 and 1, the lower surface of the rotor 86 is supported by the upper surface of the outward flange portion 108 of the second shaft portion 64. The upper surface of the flange portion 108 is shown in FIG. It rotates and slides in the direction indicated by the arrow.
As shown in FIGS. 1 and 2, the lower end of the flange portion 108 of the second shaft portion 64 is brought into contact with the upper end of a metal coil spring (biasing means) 110, and the coil spring ( An urging force by 110 (hereinafter simply referred to as a spring) is exerted upward with respect to the second shaft portion 64. That is, the urging force of the spring 110 in the backward direction is applied to the rotor 86 and the push button 82 via the second shaft portion 64 and to the first shaft portion 62 screwed to the second shaft portion 64. It is exerted upward.

As shown in detail in FIG. 3, the rotating sleeve 84 is provided with a guide portion 112 projecting inwardly on its upper inner peripheral surface.
The guide portion 112 has engaging teeth 114 at the lower end.
An inclined guide cam surface 116 corresponding to the second driven cam surface 106 of the rotor 86 for rotating the rotor 86 by cam action is also formed on the lower surface of the engagement tooth 114.
Here, the inclination angle of the guide cam surface 116 is the same as that of the second driven cam surface 106 of the rotor 86.
In the guide portion 112, the insertion grooves 94 extending in the vertical direction as described above are formed at predetermined intervals in the circumferential direction. When the rotor 86 is in a rotational position in which the engaging tooth 102 having an outward projecting shape is positioned in the insertion groove 94, the engaging tooth 102 is inserted into the insertion groove 94 to move upward in the figure. Backward movement is allowed.

On the other hand, the engaging tooth 114 engages with the engaging tooth 102 and holds and locks the engaging tooth in its advanced state, that is, the lowered state in the figure. That is, the pilot valve 34 is held and locked in the closed position.
In the present embodiment, the guide portion 112 shown in FIG. 3 and the rotating sleeve 84 having the guide portion 112, the push button 82 having the engaging teeth 96 and the drive cam surface 98 at the lower end, the rotor 86 directly below the push button 82, and these are directed upward. A thrust lock mechanism is constituted by a spring 110 or the like that biases the spring.

In this embodiment, a forced rotation ring 118 having a function of forcibly rotating the rotor 86 when the push button 82 is pushed is provided below the second shaft portion 64.
As shown in FIG. 1, the forced rotation ring 118 is placed on the pedestal portion 78 of the anti-rotation member 76.
The forced rotation ring 118 has a cylindrical shape as a whole, and an inward flange portion 120 is provided at the lower end thereof. The flange portion 120 and the outward flange portion of the second shaft portion 64 are provided. A spring 110 is interposed between the two and 108.

The forced rotation ring 118 also has a flange portion 120 serving as a slip washer. When the rotation sleeve 84 rotates, that is, when the second shaft portion 64 that rotates together with the rotation sleeve 84 rotates, the forced rotation ring 118 is also rotated. Prevents the spring 110 from being twisted and deformed as the second shaft portion 64 rotates by slipping on the pedestal portion 78 of the anti-rotation member 76.
As a result, the upward elastic force of the spring 110 can be applied with the set appropriate elastic force.

The forced rotation ring 118 is integrally provided with a plurality of claws 122 protruding upward at predetermined intervals in the circumferential direction along the upper end thereof. The upper surfaces of these claws 122 are inclined cam surfaces 124.
When a downward force is exerted on the rotor 86 by the push button 82, these cam surfaces 124 are formed on the corner portion 126 (see FIG. 3) on the lower surface of the second engaging tooth 102 having a protruding shape of the rotor 86. The rotor 86 abuts and forcibly rotates counterclockwise in FIG. 3 by its cam action.

  However, the rotor 86 is based on the biasing force of the spring 110 when its rotational resistance, that is, the sliding resistance of the second shaft portion 64 with respect to the upper surface of the flange portion 108 and the sliding resistance of the push button 82 with respect to the drive cam surface 98 is small. Then, before contacting the cam surface 124 of the forced rotation ring 118, the cam action of the drive cam surface 98 of the push button 82 and the first driven cam surface 104 of the rotor 86 causes the cam surface 124 of the forced rotation ring 118 to Rotate before touching.

However, when the rotor 86 is used for a long period of time, the sliding resistance gradually increases due to wear powder generated on the sliding surface.
Therefore, even if the push button 82 is pushed downward, the rotor 86 may not rotate lightly and smoothly.
At this time, even if the rotor 86 does not rotate smoothly, when the push button 82 is pushed down strongly, the corner portion 126 of the engaging tooth 102 of the rotor 86 is brought into contact with the cam surface 124 of the forced rotation ring 118. As a result, the rotor 86 is forcibly rotated by the cam surface 124 of the forced rotation ring 118.

In the present embodiment, when the rotary sleeve 84 is rotated directly or via an operation member provided separately, the second shaft portion 64 of the action shaft 60 is rotated integrally therewith, and the female screw 66 and the male screw are rotated by the rotation. The second shaft portion 62 of the action shaft 60, that is, the pilot valve 34 moves forward and backward in FIG. 1 by screw feed with 70, thereby adjusting the flow rate.
On the other hand, when the push button 82 is pushed in, the pilot valve 34 is switched between the closed position shown in FIG. 6 and the opened position shown in FIG. The thrust lock mechanism holds the position at each position.

FIGS. 8 and 9 specifically show the operation of the thrust lock mechanism that switches the pilot valve 34 between the valve closing position and the valve opening position each time the push button 82 is pushed, and holds the position at each position. ing.
FIG. 8I shows the closed state of the pilot valve 34, that is, the water stop state. At this time, the engagement teeth 102 of the rotor 86 are engaged with the engagement teeth 114 of the guide portion 112 of the rotation sleeve 84. Therefore, the rotor 86 is held in a locked state at the lowered position, that is, the forward position in FIG. That is, the pilot valve 34 is kept closed.

In this state, as shown in (II), when the push button 82 is pushed downward in the figure, the rotor 86 is pushed downward against the upward biasing force of the spring 110, and the rotor 86 is engaged. The engagement between the teeth 102 and the engagement teeth 114 of the guide portion 112 is released.
Then, due to the cam action between the drive cam surface 98 of the push button 82 and the first driven cam surface 104 of the rotor 86, the rotor 86 is rotated by a predetermined angle in the left direction in the figure, and the engagement teeth 96 of the push button 82 are obtained. And the engagement tooth 100 of the rotor 86 are just stopped meshing with each other (first stopper position). FIGS. 8 (III) and 8 (A) show the state at this time.

  At this time, as shown in (III) and (B), the second driven cam surface 106 of the rotor 86 is opposed to the next guide cam surface 116 in the rotation direction of the guide portion 112, where (IV) When the pushing force applied to the rotor 86 is removed as shown in the drawing, the rotor 86 is lifted by a small distance together with the push button 82 and the second shaft portion 64, that is, the action shaft 60 by the biasing force of the spring 110. The second driven cam surface 106 of 102 abuts on the guide cam surface 116 of the guide portion 112.

Then, due to the cam action of the guide cam surface 116 and the second driven cam surface 106, the rotor 86 further rotates in the direction indicated by the arrow in the figure, and is engaged as shown in FIGS. 8 (V) and 8 (B). The tooth 102 reaches the position of the insertion groove 94 of the guide portion 112.
Here, when the engaging teeth 102 are fitted into the fitting grooves 94, the rotor 86 is moved backward together with the push button 82 and the action shaft 60 by the biasing force of the spring 110 (FIG. 9 (VI)), and the pilot valve 34 becomes a valve open state (water discharge state), a flow of water is generated in the main water channel, and water is discharged from the water discharge portion in the faucet.

  When the push button 82 is pushed in again from this valve-opened state, the rotor 86 is lowered from the raised position, and when the engaging tooth 102 is removed from the fitting groove 94, the rotor 86 is moved to the drive cam surface 98 and the first driven cam. By the cam action with the surface 104, it rotates and moves in the arrow direction (left direction) in FIG. 9 (VII), and the engagement tooth 100 of the rotor 86 meshes with the next engagement tooth 96 in the rotation direction of the push button 82. Thus, the next one-pitch rotational motion of the rotor 86 is stopped there (FIG. 9 (VIII)).

When the pushing force on the push button 82 is removed in this state, the rotor 86 is lifted by a small distance from the lowest position by the biasing force of the spring 110, and the second driven cam surface 106 of the engaging tooth 102 guides the guide portion 112. The cam surface 116 comes into contact with the cam surface 116 (FIG. 9 (IX)), and further, the cam 86 causes the rotor 86 to continue to rotate in the left direction in the figure, so that the engaging teeth 102 of the rotor 86 are moved to the guide portion 112. The second engaging position 114 is engaged (second stopper position), and the rotation of the rotor 86 is stopped there (FIG. 9 (X)).
The state shown in FIG. 9 (X) is the same state as shown in FIG. 8 (I), and the water faucet is in a water stop state here.

  According to the present embodiment as described above, the inclination angle of the first driven cam surface 104 in the rotor 86 is set to a small angle with respect to the inclination angle of the second driven cam surface 106. The forward movement can weaken the momentum when the rotor 86 rotates by the cam action of the drive cam surface 98 and the first driven cam surface 104, and the collision sound, that is, the operation sound when the rotation of the rotor 86 is stopped is reduced. can do.

Therefore, when the faucet with the thrust lock mechanism of the present embodiment is used in a narrow bathroom or a washroom, it is possible to solve the problem of generating a loud operation sound and causing discomfort to the user. You will be able to use a faucet.
Moreover, since the thing of this embodiment uses the thrust lock mechanism, it can give an appropriate click feeling at the time of operation | movement.

  On the other hand, since the inclination angle of the second driven cam surface 106 of the rotor 86 is large with respect to the inclination angle of the first driven cam surface 104, the rotor 86 is rotated with the guide cam surface 116 of the guide portion 112. The rotational force at the time of rotating by the cam action of the child 86 with the second driven cam surface 106 can be increased, and smooth rotation of the rotor 86 can be ensured.

Although the embodiment of the present invention has been described in detail above, this is merely an example.
For example, in the above-described embodiment, the inclination angle of the first driven cam surface 104 in the rotor 86 and the inclination angle of the drive cam surface 98 of the push button 82 are the same angle, but these inclination angles may be different. is there.
In this case, the cam surfaces are not in surface contact but in line contact, and the contact resistance is reduced with respect to the surface contact so that the rotor 86 can be rotated more stably. When the engaging tooth 100 of the push button 82 stops rotating at the meshing position of the push button 82 with respect to the engaging tooth 96, the collision between the surface and the line can be made (the engaging teeth 96, 100 have different mountain shapes), and rotation. It is possible to further reduce the collision sound at the time of stopping, that is, the operation sound.
In addition, this invention can be comprised with the form which added the various change in the range which does not deviate from the meaning.

It is a figure which shows the principal part of the water tap of one Embodiment of this invention. It is a figure which decomposes | disassembles and shows each member of the principal part of the embodiment. It is a figure which expands and shows the principal part of FIG. It is operation | movement explanatory drawing of the embodiment. FIG. 5 is an operation explanatory diagram following FIG. 4. It is another effect explanatory view of the embodiment. FIG. 7 is an operation explanatory diagram showing an operation state different from FIG. 6. It is action | operation explanatory drawing of the thrust lock mechanism in the same embodiment. FIG. 9 is an operation explanatory diagram following FIG. 8.

Explanation of symbols

34 Pilot valve 82 Push button (Driver)
84 Rotating sleeve (locking part)
86 Rotor 98 Drive cam surface 104 First driven cam surface 106 Second driven cam surface 116 Guide cam surface

Claims (2)

(a) the rotor, and (b) the driving cam surface of the rotor is brought into contact with the first driven cam surface of the rotor by forward movement, and the rotor is rotated by a predetermined angle to the first stopper position by the cam action. (C) The guide cam surface is brought into contact with the second driven cam surface of the rotor by the biasing force of the rotor in the backward direction by the biasing means, and the rotor is rotated by the cam action. A lock that further rotates in the same direction as the drive direction to the second stopper position or the allowable backward position, and allows the rotor to be locked and retracted at the second stopper position for each rotational movement of the rotor. A thrust lock mechanism having a lock portion for alternately releasing and moving the valve body forward and backward as the rotor moves forward and backward, and moving the valve body to the forward position and the backward position. In the faucet adapted to hold the position alternately, the first driven cam A faucet characterized in that the inclination angle of the surface is smaller than the inclination angle of the second driven cam surface.   The water faucet according to claim 1, wherein the drive cam surface and the first driven cam surface have different inclination angles.

Images