JP2022007867A - Applicator - Google Patents

Abstract

To provide an applicator whose assemblability when manufactured can be improved.SOLUTION: An applicator includes: a housing part storing coating liquid; a piston sliding in the housing part; a screw shaft in which a screw is formed on a peripheral surface; a feeding portion for performing feeding operation; a rotational cam body; and a transmitting cam body. The screw part screwed in the screw shaft is provided at the back of the housing part, the rotational cam body is rotated by the feeding operation of the feeding portion, and the screw shaft and the screw part are relatively rotated to move the screw shaft forward. The piston is moved forward by the screw shaft and feeds coating liquid housed in the housing part to an application body. In the applicator, at least one of the screw shaft, the rotational cam body, and the transmitting cam body is formed into a longitudinally symmetrical shape.SELECTED DRAWING: Figure 1

Description

The present invention relates to a coating tool that feeds out liquid contents such as a cosmetic liquid, a correction fluid, and ink for a brush by a knock operation and supplies the liquid contents to the coating body.

Conventionally, a knock-type coating tool that converts a knocking operation into a rotary operation and feeds out a coating liquid has been proposed (see Patent Document 1).

Since this applicator is provided with a cam surface on the end surface of a cylindrical rotating body, there is a limit value in the feeding force. When the coating liquid is oil-based, the viscosity is high, so that the coating tool of Patent Document 1 is not suitable for feeding out the coating liquid.

On the other hand, Patent Document 2 proposes a coating tool capable of increasing the feeding force by the guide groove and the protrusion.

Japanese Unexamined Patent Publication No. 2009-254419 Japanese Unexamined Patent Publication No. 2011-194820

Since the applicator has a plurality of shaft-shaped parts, a process of aligning the front and back of the shaft-shaped parts is required at the time of manufacturing the applicator, which becomes a work load, but a technique for reducing such a work load. Was unproposed.

In view of such circumstances, the present invention provides a coating tool capable of improving assembling property at the time of manufacturing.

In the present invention, the accommodating portion for storing the coating liquid, the piston sliding in the accommodating portion, the screw shaft having a screw formed on the peripheral surface, the feeding body for feeding operation, the rotating cam body, and the transmission cam. A body is provided, a screw portion to be screwed to the screw shaft is provided behind the accommodating portion, and a rotary cam body is rotated by a feeding operation to the feeding body to rotate the screw shaft and the screw portion relative to each other to form a screw shaft. In a coating tool that is advanced and the piston is advanced by a screw shaft to supply the coating liquid to be accommodated in the accommodating portion to the coating body.
The coating tool is characterized in that at least one of the screw shaft, the rotating cam body, and the transmission cam body is formed in a front-rear symmetrical shape.

In the present invention, it is preferable that the piston is formed in a symmetrical shape in the front-rear direction.

In the present invention, it is preferable that the threaded portion is formed, and an inclined surface whose diameter increases from the rear portion to the front surface is formed on the inner surface of the screw that accommodates the rotating cam body, the transmission cam body, and the feeding body.

In the present invention, a front shaft is provided at the front end of the shaft cylinder so as to cover the periphery of the coating body, and a main fitting portion and a temporary fitting portion are formed on the front shaft and the shaft cylinder, respectively. The cylinder has its own detent ribs, and the detent ribs do not engage with each other during the initial fitting state in which the temporary fitting portions of the shaft cylinder and the forehead are engaged with each other, while the main fitting is performed. It is preferable that the respective anti-rotation ribs are engaged with each other in the main fitting state in which the joint portions are fitted to each other.

In the present invention, the relative rotation between the rotary cam body and the screw shaft is restricted, and the rotary cam body is rotated by the feeding operation of the transmission cam body to the feeding body, and is screwed to the screw shaft. A screw body having a threaded portion is provided behind the accommodating portion, and when the feeding body is operated, the rotating cam body rotates to advance the piston and apply a coating liquid to be accommodated in the accommodating portion. It is preferable to supply to.

According to the applicator of the present invention, at least one of the screw shaft, the rotary cam body, and the transmission cam body is formed in a front-rear symmetrical shape, so that front-rear alignment can be omitted and assembly at the time of manufacture can be omitted. It can have an excellent effect of improving sexuality.

It is an overall view of the cap attached state of the coating tool which concerns on embodiment of this invention, (a) is a view from the front, (b) is a front view from one direction, (c) is a circumferential direction from (b). It is a front view in a state of being rotated by 90 degrees, and (d) is a vertical cross-sectional view along the DD line of (b). 1 is an overall view of the applicator of FIG. 1 at the start of use, where FIG. 1A is a front view from one direction and FIG. 1B is a vertical sectional view. 1 is an overall view of the knock pressing state during use of the applicator of FIG. 1, in which FIG. 1A is a front view from one direction and FIG. 1B is a vertical sectional view. It is an overall view after the end of use of the applicator of FIG. 1, in which (a) is a front view from one direction and (b) is a vertical sectional view. It is a component diagram of the feeding mechanism in the coating tool of FIG. 1, (a) is a perspective view, (b) is a front view, (c) is a vertical sectional view along the line CC of (d), (d). Is a front view in a state of being rotated 90 degrees from (b), and (e) is a vertical cross-sectional view taken along the line EE of (b). 5 is a component diagram of the feeding mechanism in a knocked state, in which FIG. 5A is a perspective view, FIG. 5B is a front view, FIG. 5C is a vertical sectional view taken along line CC of FIG. Is a front view in a state of being rotated 90 degrees from (b), and (e) is a vertical cross-sectional view taken along the line EE of (b). It is a component diagram of the state in which the screw body is removed from the feeding mechanism of FIG. 5, in which (a) is a perspective view, (b) is a front view, and (c) is a vertical sectional view taken along the line CC of (d). , (D) is a front view in a state of being rotated 90 degrees from (b), and (e) is a vertical sectional view taken along the line EE of (b). FIG. 7 is a component diagram showing a knocked state (pressed state) in a state where the screw body is removed from the feeding mechanism of FIG. 7, where (a) is a perspective view, (b) is a front view, and (c) is C of (d). -A vertical cross-sectional view taken along line C, (d) is a front view in a state of being rotated 90 degrees from (b), and (e) is a vertical cross-sectional view taken along line EE of (b). FIG. 1 is a component diagram of a screw body in the applicator of FIG. 1, in which (a) is a front view, (b) is a front view, and (c) is a vertical cross-sectional view taken along the line CC of (d). (D) is a front view in a state of being rotated 90 degrees from (b), (e) is a vertical sectional view along the line EE of (b), (f) is a perspective view from the rear, and (g) is. It is a view from the rear. It is a component diagram of the feeding body in the coating tool of FIG. 1, (a) is a perspective view, (b) is a front view, (c) is a front view, and (d) is DD of (e). A vertical cross-sectional view along the line, (e) is a front view rotated 90 degrees from (c), (f) is a vertical cross-sectional view along the FF line of (c), and (g) is a perspective view. (H) is a rear view. FIG. 1 is a component diagram of a rotary cam body in the coating tool of FIG. 1, in which (a) is a perspective view, (b) is a front view, (c) is a vertical sectional view along the CC line of (e), and (d). ) Is a vertical cross-sectional view along the DD line of (e), and (e) is a view from one direction. It is a component view of the transmission cam body in the coating tool of FIG. 1, (a) is a view from one direction, (b) is a perspective view, (c) is a front view, and (d) is (c) to 90. A front view in a state of being rotated by a degree, (e) is a vertical cross-sectional view along the line EE of (c), and (f) is a view from another direction. FIG. 1 is a component diagram of a screw shaft in the applicator of FIG. 1, in which (a) is a perspective view, (b) is a front view, (c) is a front view rotated 90 degrees from (b), and (d). Is a view from the rear. FIG. 3 is a perspective view of a component diagram in a state where the screw shaft is oriented in the axial direction with respect to the rotary cam body in the applicator of FIG. 1. The parts of the piston in the applicator of FIG. 1, (a) is a perspective view, (b) is a front view, (c) is a sectional view taken along the line CC of (b), and (d) is a rear view. It is a view from. It is a component diagram of a joint (seal ball receiver) in the applicator of FIG. 1, (a) is a perspective view from the front, (b) is a view from the front, and (c) is a view from the C direction of (a). Front view (view view), (d) is a side view rotated 90 degrees from (c), (e) is a vertical sectional view along the line EE of (b), and (f) is from the rear. (G) is a perspective view from the rear. FIG. 1 is an operation explanatory view based on a schematic diagram of a screw body, a rotating cam body, a transmission cam body, and a feeding body for explaining the cam operation in the coating tool of FIG. 1, where (a) is an explanatory diagram of each part and (b) an initial state. The figure and (c) show the figure of the state at the start of knocking, respectively. Similar to FIG. 17, it is an operation explanatory diagram by a schematic diagram, (a) is a state diagram when knocking is completed, (b) is a state diagram when knocking is released and returning starts, and (c) is a state diagram when knocking is completely done. The phase diagram in the returned initial state is shown. 1A is a component diagram of the shaft cylinder in the applicator, where (a) is a perspective view, (b) is a front view, (c) is an enlarged perspective view of the front end portion, and (d) is a front view. (E) is a vertical cross-sectional view along the line EE of (b), (f) is a front view rotated 90 degrees from (d), and (g) is along the line GG of (b). It is a vertical sectional view. It is a component diagram of the front axis of the applicator of FIG. 1, (a) is a perspective view from the front, (b) is a perspective view from the front, (c) is a front view, and (d) is D of (a). -A vertical sectional view along the D line, (e) is a perspective view from the rear, and (f) is a perspective view from the rear. In the applicator of FIG. 1, the stopper ring is removed from the applicator (ready for use) and is an explanatory view of the initial mating state, (a) is a front view, and (b) is a vertical cross-sectional view of the front part. , (C) is a cross-sectional view taken along the line CC of (b), and (d) is an enlarged explanatory view of the D portion of (b). In the coating tool of FIG. 21, it is an explanatory view in which the toe shaft is in the main fitting state to the shaft cylinder, (a) is a front view, (b) is a vertical cross-sectional view of the front portion, and (c) is (b). The cross-sectional view taken along the line CC of (d) is an enlarged explanatory view of the D portion of (b). In the coating tool of FIG. 21, it is an explanatory view in which the front shaft and the shaft cylinder are temporarily fitted, (a) is a front view, (b) is a vertical cross-sectional view of the front portion, and (c) is (b). ) Is a cross-sectional view taken along the line CC, and (d) is an enlarged explanatory view of the D portion of (b).

Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 23.

FIG. 1 shows the unused state of the applicator, FIG. 2 shows the start of use, FIG. 3 shows the knock pressing state, and FIG. 4 shows the end of use.

As shown in FIGS. 1 to 4, the applicator according to the embodiment has an accommodating portion 10b for storing the coating liquid, a piston 12 sliding in the accommodating portion 10b, and a male screw thread portion 14a on the peripheral surface. The formed screw shaft 14 is provided in the shaft cylinder 10, a feeding body 20 for feeding operation is provided, and the rotary cam body 16 whose relative rotation with the screw shaft 14 is restricted and the feeding body 20. A transmission cam body 18 that rotates the rotary cam body 16 by a feeding operation and a screw body 22 having a screw portion 22b screwed to the screw shaft 14 are provided behind the accommodating portion 10b, and the feeding body 20 is operated. As a result, the rotary cam body 16 rotates and the piston 12 is advanced to supply the coating liquid contained in the housing portion 10b to the coating body 24. In the coating tool, the screw shaft 14 housed inside the screw body 22 , The rotary cam body 16 and the transmission cam body 18 (at least one example thereof) are formed in a front-to-back symmetrical shape.

In the applicator, a feeding mechanism A including a screw body 22, a screw shaft 14, a rotating cam body 16, a transmission cam body 18, a spring 18c, and a feeding body 20 is arranged in a shaft cylinder 10.

When the applicator is not in use, as shown in FIG. 1, the cap 28 and the stopper ring 34 are attached, and the stopper ring 34 is in a state in which the tip shaft 26 is positioned forward and the seal ball 36a is fitted. At the start of use, as shown in FIG. 2, the stopper ring 34 is removed and the seal ball 36a falls into the accommodating portion 10b. As shown in 4, the piston 12 is located at the front end of the accommodating portion 10b.

5 and 6 are component diagrams of the feeding mechanism A, FIG. 5 shows a non-knocked state, and FIG. 6 shows a knocked state. 7 and 8 are component diagrams in a state where the screw body 22 is removed from the feeding mechanism A, FIG. 7 shows a non-knock state, and FIG. 8 shows a knock state. 9 is a screw body 22, FIG. 10 is a feeding body 20, FIG. 11 is a rotary cam body 16, FIG. 12 is a transmission cam body 18, FIG. 13 is a screw shaft 14, and FIG. 14 is a rotary cam body 16 with a screw shaft 14 as an axis. FIG. 15 is a component diagram of the piston 12 and FIG. 16 is a component diagram of the joint 36 in a state oriented in the direction.

(Feeding mechanism A)
As shown in FIGS. 5 and 6, in the feeding mechanism A, the rotation cam body 16 and the rotary cam body 16 in which the relative rotation with the screw shaft 14 is restricted and the cam portions 16a and 16b are formed in the front portion and the rear portion, respectively, A cam portion 18a for engaging with the rear cam portion 16b of 16 is formed in the front portion, and the transmission cam body 18 having the protrusion 18b formed on the side surface portion and the protrusion 18b of the transmission cam body 18 are guided. A feeding body 20 having a guide groove 20a and rotating the transmission cam body 18 via the guide groove 20a and the protrusion 18b by forward / backward movement, and a feeding body 20 repelling the feeding body 20 backward and the transmission cam body 18 facing forward. A tubular portion having a built-in spring 18c that repels the cam, a transmission cam body 18, a rotary cam body 16, a spring 18c, a screw shaft 14, and a feeding body 20, and a rearward facing cam portion 22c integrally formed therein. It has a screw body (corresponding to a "fixed cam body") 22 having a screw portion 22b screwed to the screw shaft 14 at the rear portion and a screw portion 22b at the rear portion.

In addition to the above configuration, the screw body 22, the rotary cam body 16, and the screw shaft 14 have a deformed hole in the screw portion of the screw body 22 to regulate relative rotation with the screw shaft 14 according to the cross section of the screw shaft 14. Further, the feeding mechanism may be configured such that a screw portion of a female screw is formed on the inner circumference of the rotary cam body 16 and the screw portion is screwed with a male screw on the outer peripheral surface of the screw shaft 14.

The guide groove 20a of the feeding body 20 is formed diagonally at an angle with respect to the axial direction (front-back direction of the coating tool).

In the knock-type applicator, when the feeding body 20 is advanced by a knocking operation with respect to the feeding mechanism A, the forward movement is transmitted in one direction of the transmission cam body 18 by the guide groove 20a and the protrusion 18b. In the embodiment, it is converted into a rotation operation in the forward rotation direction of the axis), and the cam portion 18a of the transmission cam body 18 meshes with the cam portion 16b at the rear of the rotation cam body 16 to rotate the transmission cam body 18. When the rotary cam body 16 is rotationally operated and the piston 12 is advanced by the advancement of the screw shaft 14, while the extension body 20 is retracted by the elastic force of the spring 18c by releasing the knock operation, the guide groove The retracting motion is converted into a rotational motion in the other direction of the transmission cam body 18 (in the embodiment, the axis forward facing left rotation direction) by the 20a and the protrusion 18b to return to the original position and in front of the rotary cam body 16. The cam portion 16a of the portion meshes with the cam portion 22c of the tubular portion 22a, the rotational operation of the rotary cam body 16 is restricted, and the operation of the screw shaft 14 and the piston 12 is restricted.

(Applicant body 24)
As shown in FIGS. 1 to 3, in the coating tool, the coating body 24 is attached to the front end portion 10a of the axle tube (rear shaft) 10 by the front shaft 26. The coating body 24 is not particularly specified as long as it is a material that can be coated by impregnating a coating liquid such as a resin fiber bundle or a porous body, but in the embodiment, the trailing ends are bundled by melting to form a flange shape. ..

(Coating liquid)
The coating liquid contained in the accommodating portion 10b of the shaft cylinder 10 is a cosmetic liquid, ink for writing tools, and a chemical solution, but in particular, when the cosmetic liquid has a high viscosity (preferably a viscosity of 300 mPa · s or more), it can be easily fed out.

In the embodiment, the liquid oily cosmetic can be accommodated and used in the accommodating portion 10b. Suitable liquid oily cosmetics in this embodiment are (a) 5 to 40% by weight of hydrocarbon ether, (b) 20 to 60% by weight of low boiling point silicone oil, and (c) 2 to 10% by weight of silicone resin. , (D) 2 to 10% by weight of one or more thickeners selected from the group consisting of crosslinked methylpolysiloxane, inulin stearate, and sucrose fatty acid ester, and (e) 10 to 40% by weight of powder. % And at least volatile hydrocarbons.

Further, suitable as another liquid oily cosmetic is (a) 20 to 75% by weight of isododecane and (b) one or more of (b) trimethylsilicicic acid, alkyl acrylate, and alkyl acrylate copolymers 2 to 2 to It contains at least 25% by weight and (c) 2 to 25% by weight of one or more powders selected from carbon black, iron oxide, and dark blue.

Further, under the conditions of a viscosity of 40 mPa · s to 400 mPa · s at 25 ° C. and a shear rate of 76.6 / s, and 25 ° C. and 65% RH, the average initial evaporation rate up to 1 minute immediately after application by the filter paper method was determined. It is preferably 0.15 to 2.00 mg / sec.
If the viscosity exceeds 400 mPa · s, the feeling of use deteriorates due to the increase in the viscosity of the cosmetic, which is not preferable. If the viscosity is less than 40 mPa · s, it tends to bleed on the skin, which is not preferable for use.
If the initial evaporation rate exceeds 2.00 mg / sec, the evaporation rate is too fast, and the "spread" of the cosmetics becomes extremely poor, which is not preferable for use. Further, when the initial evaporation rate is less than 0.15 mg / sec, the sticky feeling of the cosmetic after application remains for a long time, and the longevity of the makeup deteriorates, which is not preferable in use.
The initial evaporation rate is 25 ° C., 65% RH, accurately weigh about 1 g of cosmetics on a filter paper of φ90 mm, measure the weight 1 minute after weighing again, and weigh the weight before and after the measurement. From the difference, the initial evaporation rate is calculated by the following formula.
Initial evaporation rate (mg / sec) = (W ₀ -W ₁ ) ÷ 60 × 1000
Here, W ₀ and W ₁ are as follows.
W ₀ : Weight of cosmetics weighed on filter paper immediately after the start of measurement (g)
W ₁ : Weight of cosmetics on filter paper 1 minute after the start of measurement (g)

When the liquid oily cosmetic is stored in the storage portion 10b, it is preferable to use polybutylene terephthalate resin (PBT resin) as the material of the shaft cylinder 10.
(Whole applicator)

In the applicator, as shown in FIG. 1, the front end portion 10a of the axle cylinder (rear shaft) 10 is formed to have a smaller diameter in a stepped manner than the portion of the accommodating portion 10b in the axle cylinder 10. The cap 28 is detachably fitted to the front end portion 10a of the shaft cylinder 10 so as to cover the tip shaft 26 and the coating body 24. There is a pipe joint 30 in the inner part of the portion fitted in the front end portion 10a of the shaft cylinder 10 of the front shaft 26, and the flange of the rear end portion of the coating body 24 is provided at the tip end portion of the pipe joint 30 and the inner surface portion of the front shaft 26. The coating body 24 is fixed by sandwiching it. A SUS or resin pipe 32 extends from the central hole of the pipe joint 30 into the coating body 24 and is arranged so that the coating liquid can be circulated toward the tip of the coating body 24 by the pipe 32.

The cap 28 abuts on the outer peripheral surface side of the stepped and narrowed portion (stepped portion 10c) of the front end portion 10a of the barrel 10 with the front facing surface thereof (see FIG. 1). Further, the inner peripheral surface side of the step portion 10c faces the inside of the coating liquid accommodating portion 10b backward, and the piston 12 abuts on the surface in the rearward direction at the forward end to regulate the position ( See Figure 4).
The screw body 22 has a function of advancing the piston 12 in the accommodating portion 10b and feeding the coating liquid toward the applicator body 24 in the front portion of the shaft cylinder 10 as the coating liquid accommodating portion 10b. A feeding mechanism A including a screw shaft 14, a rotating cam body 16, a transmission cam body 18, a spring 18c, and a feeding body 20 is arranged. In the shaft cylinder 10, a stirring body 10d for stirring the coating liquid together with the coating liquid is housed in the accommodating portion 10b. The stirring body 10d may be a metal or resin ball or a rod-shaped body.

In the applicator, as shown in FIG. 1, a stopper ring 34 that keeps the toe shaft 26 in an unused state when not in use is located between the front end surface of the stepped portion 10c of the barrel 10 and the rear end surface of the toe shaft 26. Intervenes in. A tubular seal joint 36 is fitted in the front end portion 10a of the shaft cylinder 10. The seal joint 36 is fitted with a seal ball 36a that seals the accommodating portion 10b when the applicator is in an unused state.

When the user starts using the pipe joint 30, the rear end portion of the pipe joint 30 is sealed by removing the stopper ring 34 and pressing the front end portion 10a of the shaft cylinder 10 backward with the front shaft 26 as shown in FIG. It is pushed into the joint 36 and the seal ball 36a is dropped into the accommodating portion 10b to open the accommodating portion 10b. By operating the feeding mechanism A, the piston 12 advances and the coating liquid is supplied to the coating body 24 through the seal joint 36, the pipe joint 30, and the pipe 32.

As shown in FIGS. 1 and 2, the inner cap 28a and the urging spring 28b are arranged inside the cap 28. The applicator has a structure in which the inner cap 28a urged by the spring 28b comes into airtight contact with the outer peripheral surface of the front shaft 26 when the applicator is not used or is not used. Therefore, it prevents the coating body 24 from drying.

(Feeding mechanism A)
The structure of each component in the feeding mechanism A will be described below.

As shown in FIGS. 5 to 6, the feeding mechanism A has a screw shaft 14, a feeding body 20, a rotating cam body 16, a transmission cam body 18, and a spring 18c mounted in the screw body 22. 7 to 8 show a state in which the screw body 22 is removed. Each component of the feeding mechanism A is shown in FIGS. 9 to 16. Each part will be described below.

(Screw body 22)
As shown in FIG. 9, the screw body 22 has a substantially cylindrical shape with open front and rear, and the front screw portion (corresponding to the “female screw portion”) 22b has a stepped smaller diameter than the tubular portion 22a. It has become.
A cam portion 22c is formed on the inner surface of the front end portion of the tubular portion 22a.
The threaded portion 22b extends substantially in a cylindrical shape from the front end of the tubular portion 22a, but is formed in a bifurcated shape by a tip cracked portion 22b1 cut in the axial direction, and is elastically deformable in the radial direction. A plurality of threads (for example, 1 to 3) that can be screwed to the screw shaft 14 are formed so as to project inward on the inner peripheral portion of the threaded portion 22b. Further, a flange-shaped blade portion 22b3 for contacting the inner peripheral surface of the barrel 10 is formed on the outer peripheral portion of the screw portion 22b.

On the outer peripheral portion of the tubular portion 22a, convex ribs 22a2 are formed so as to extend in a plurality of axial directions in order to rotate around the inner surface of the shaft cylinder 10. A window portion 22a1 is located behind the rib 22a2.
The ribs 22a2 have a structure in which the ribs 22a2 are locked to the vertical ribs 10f (see FIG. 19) on the inner surface of the barrel 10, and the screw body 22 is prevented from rotating to prevent rotation failure at the time of knocking.

As shown in FIG. 9, a thin-walled portion 22a3 having an inclined surface whose diameter increases from the rear to the front is formed on the inner surface of the tubular portion 22a. Specifically, on the inner surface of the tubular portion 22a, the thin-walled portion 22a3 is formed in a state in which two portions are cut out in a semi-circular shape from the rear end surface of the tubular portion 22a toward the window portion 22a1. be. The other portion of the tubular portion 22a and the thin-walled portion 22a3 are continuous via a semicircular step 22a31.

The step 22a31 sandwiching the thin portion 22a3 is formed in a semicircular or triangular shape from the rear end portion of the tubular portion 22a to the window portion 22a1 (see FIGS. 9 (c) and 9 (e)). The shape of the thin portion 22a3 is not limited to this.

Since the thin portion 22a3 is formed, the screw body is in a state where the piston 12, the screw shaft 14, the rotary cam body 16, the transmission cam body 18, the spring 18c, and the feeding body 20 are assembled (see FIGS. 7 and 8). When mounting in the tubular portion 22a of 22, the feeding body 20 is pushed in. At that time, the protrusion 20b of the feeding body 20 abuts on the step 22a31 of the thin-walled portion 22a3 and is guided to rotate or position the protrusion 20b so as to slide into the window portion 22a1 and the protrusion 20b enters the window portion 22a1.

Therefore, when the protrusion 20b is attached to the tubular portion 22a of the feeding body 20, the protrusion 20b is not aligned with the window portion 22a1 in the circumferential direction, and the feeding body 20 is simply inserted into the tubular portion 22a to form the window. Since the protrusion 20b can be fitted into the portion 22a1 and alignment is not required, the work efficiency can be improved.

Further, since the screw portion 22b is bifurcated at the tip cracked portion 22b1, the screw portion 22b can be elastically deformed and mounted by pushing the screw shaft 14 into the screw portion 22b when assembling the screw shaft 14. Therefore, since the screw shaft 14 can be assembled without having to be screwed into the screw portion 22b by turning the screw shaft 14, it is possible to enable easy and reliable mounting on the production line and significantly reduce the work load.

Further, the screw body 22 is formed with a cam portion 22c having a plurality of inclined surfaces in the rearward direction in the tubular portion 22a behind the screw portion 22b, and the rotary cam body 16 is formed on the cam portion 22c in the subsequent direction. The forward cam portions 16a of the above are arranged so as to face each other (see FIG. 5).

As shown in FIG. 9, since the rearward facing cam portion 22c is integrally formed inside the tubular portion 22a of the screw body 22 by the inclined surface, the number of parts is increased as compared with the case where the cam portion 22c is provided separately. Can be reduced. Further, at the time of assembly, the inner female thread 22b2 of the screw portion 22b is screwed with the screw shaft 14. The blade portion 22b3 on the outer peripheral portion hits the contact portion with the inside of the barrel 10, and the blade portion 22b3 having a partially thin wall is formed to prevent the screw body 22 from opening due to shrinkage during molding. There is. The blade portion 22b3 is assembled so as to be in contact with the vertical rib 10f (see FIG. 19) on the inner surface of the barrel 10. The number of blades 22b3 is preferably two from the viewpoint of satisfying the filling amount of the coating liquid and preventing opening. Further, the formation of the cracked portion 22b1 improves the degree of freedom in designing the molding die, which can lead to cost reduction.

The window portion 22a1 of the tubular portion 22a has a structure that engages with the protrusion 20b of the feeding body 20 so that the feeding body 20 does not rotate when the feeding body 20 is pressed. It is possible to prevent ejection defects (see FIGS. 5 and 6).
As shown in FIGS. 5 and 9, a flange 22d for abutting and positioning the rear end of the cylinder 10 (see FIG. 1) is formed at the rear end of the tubular portion 22a with an enlarged diameter.
Further, at a front position adjacent to the flange 22d of the tubular portion 22a, unevenness 22e for locking to the inner surface of the rear end portion of the shaft cylinder 10 is formed on the outer periphery of the plurality of rows.
The window portion 22a1 is formed so as to penetrate the unevenness 22e in the radial direction. Since the unevenness 22e and the window portion 22a1 are formed at substantially the same position in the axial direction of the screw body 22, the resin wraps around the unevenness 22e and the flange 22d due to the space inside the window portion 22a1 in injection molding. Since it is easy to make, the screw body 22 has a shape in which molding defects such as sink marks are unlikely to occur.

Further, on the inner surface of the screw body 22, as shown in FIG. 9, the thin-walled portion 22a3 extends to the position of the window portion 22a1. The step 22a31 of the thin portion 22a3 is located so that the triangular front end apex overlaps with the window portion 22a1. On the inner surface of the screw body 22, the guide groove 22f is formed along the axial direction from the window portion 22a1 to the central portion of the shaft. The guide groove 22f is guided by sliding a guide protrusion 20d (see FIG. 10) described later.
Since the guide groove 22f is continuous with the thin wall portion 22a3 at the position of the window portion 22a1, the guide protrusion 20d abuts on the step 22a31 and is guided to the guide groove 22f when the feeding body 20 is assembled to the screw body 22. It is a structure.

(Delivery body 20)
As shown in FIG. 10, the feeding body 20 (knocking body) has a substantially cylindrical shape with a closed rear end, and a pair of guide grooves 20a penetrating the inner and outer peripheral surfaces thereof are axially in the front portion thereof. On the other hand, it is formed diagonally with an angle.

The feeding body 20 is moved forward by the guide groove 20a and the protrusion 18b on the side surface of the transmission cam body 18 when the feeding body 20 is advanced by the user knocking on the outer periphery of the closed rear end surface. Is converted into a rotational operation of the transmission cam body 18, and the rotary cam body 16 is rotationally operated by the rotation of the transmission cam body 18 to advance the screw shaft 14 and advance the piston 12 (. See FIGS. 5 and 6).

Further, as shown in FIGS. 7, 8 and 10, a cantilever-shaped arm portion 20b1 that can be elastically deformed is formed on the rear side portion of the feeding body 20 by a U-shaped notch, and the arm portion 20b1 thereof is formed. A protrusion 20b is formed on the outside of the.
Further, on the outer peripheral surface of the arm portion 20b1 at the front position, the guide projection 20d is formed so as to project outward in pairs at the corresponding positions in the circumferential direction of the projection 20b.

Here, as shown in FIG. 9, in the screw body 22, the top of the step 22a31 of the thin-walled portion 22a3 is located at the window portion 22a1 and the guide groove 22f is formed from the window portion 22a1 toward the front. The wall thickness of the formed portion of the guide groove 22f is substantially the same as that of the thin wall portion 22a3.
When assembling the screw body 22 to the feeding body 20, the feeding body 20 is pushed into the screw body 22 from behind and assembled.
When the feeding body 20 advances with respect to the screw body 22 by pushing in and assembling, the guide protrusion 20d first abuts on the step 22a31 and rotates so that the circumferential position is toward the window portion 22a1 and the relative angle is changed. It can be decided.
When the feeding body 20 is further pushed in, the guide projection 20d passes through the window portion 22a1 and is guided into the guide groove 22f, and proceeds along the guide groove 22f. Since the protrusion 20b is at the same position in the circumferential direction as the guide protrusion 20d, the protrusion 20b is smoothly fitted into the window portion 22a1 by advancing along the guide groove 22f of the guide protrusion 20d without being displaced in the window portion 22a1.

Therefore, the feeding body 20 can be assembled by simply pushing it in from the rear without positioning it on the screw body 22 (see FIGS. 5 and 6 for the fitted state).
Therefore, the guide protrusion 20d has a function of fitting the position in the circumferential direction into the guide groove 22f to guide the guide, and a function of positioning the rear protrusion 20b so as to smoothly fit the guide protrusion 20b toward the window portion 22a1.

Further, as shown in FIGS. 7, 8 and 10, the outer peripheral surface of the rear portion of the feeding body 20 is formed with a diameter slightly larger than the front portion behind the step portion 20f on the entire circumference. A large diameter portion rearward from the step portion 20f is in contact with the inner peripheral surface of the tubular portion 22a of the screw body 22 so as to maintain airtightness between the feeding body 20 and the tubular portion 22a (FIGS. 5 and 6). reference).

Further, on the outer peripheral surface of the rear portion of the step portion 20f, a pair of second projections 20e are formed so as to project in a rib shape in the diameter expansion direction. The second protrusion 20e projects to the outer peripheral surface of the feeding body 20 in pairs at the same position in the circumferential direction as the protrusion 20b and the guide protrusion 20d.
Since the second protrusion 20e abuts (or is close to) the inner peripheral surface (thin wall portion 22a3) of the tubular portion 22a in a state where the feeding body 20 is mounted in the screw body 22, the second projection 20e is supported on the tubular portion 22a. On the other hand, it acts to prevent the feeding body 20 from rattling (see FIGS. 5 and 6).

(After this, the paragraph number will be carried down.)
Further, as shown in FIG. 10, a guide portion 20c is formed on the inner peripheral portion of the front portion of the feeding body 20 to guide the protrusion 18b (see FIG. 12) to the guide groove 20a when the transmission cam body 18 is assembled. .. The guide portion 20c is a thin portion formed on the inner circumference from the front end edge of the feeding body 20 to the periphery of the guide groove 20a, and is formed at two locations corresponding to the guide groove 20a. A stepped portion 20c1 is formed from the thin-walled guiding portion 20c in a stepped manner to connect to another thick-walled portion. Two guide portions 20c are formed. The width between the step portions 20c1 and 20c1 sandwiching the guide portions 20c extends almost half of the peripheral edge of the feeding body 20 at the front end edge thereof, becomes narrower toward the rear, and corresponds to the guide groove 20a in the vicinity of the guide groove 20a. It is formed (or narrow or wide). The widths of the steps 20c1 and 20c1 are formed in a substantially triangular slope or wedge shape (see FIG. 10D). Adjacent guide portions 20c may overlap or be spaced at the front end edge (may be spaced between the stepped portions 20c1 or may be formed from a portion inserted from the front end edge).

At the time of assembly, the transmission cam body 18 is mounted in the feeding body 20 from the front. In this case, since the transmission cam body 18 has no front and rear positions, it is not necessary to position the front and rear positions, and the work load is small. When the transmission cam body 18 is inserted into the feeding body 20, the protruding portions 18b that protrude in pairs hit the step portions 20c1 and 20c1 and are guided to fit into the paired guiding portions 20c. Then, as the transmission cam body 18 enters the rear, the protrusion 18b hits the step portions 20c1 and 20c1 and is guided by the guide portion 20c to slide and fit into the guide groove 20a.

Therefore, since the protrusion 18b is guided and fits into the guide groove 20a simply by inserting the transmission cam body 18 into the feeding body 20, it is not necessary to position the protrusion 18b in the guide groove 20a in the circumferential direction, and positioning is unnecessary. Therefore, the work man-hours are small and it is extremely efficient.
again,

(Symmetrical parts)
In the applicator, among the components, the rotary cam body 16 as shown in FIG. 11, the transmission cam body 18 as shown in FIG. 12, and the screw shaft 14 as shown in FIG. 13 are formed in a symmetrical shape in the front-rear direction. .. These parts will be described.

(Rotating cam body 16)
As shown in FIG. 11, the rotary cam body (feeding cam) 16 has a symmetrical shape between the front surface side 16F and the rear surface side 16R, and has a substantially cylindrical shape having a hollow portion.

An outer peripheral cam portion 16o and an inner peripheral cam portion 16i are formed on the front side 16F and the rear side 16R, respectively. The same function is obtained regardless of whether the front side 16F or the rear side 16R is oriented and mounted in the screw body 22.

In the rotary cam body 16, the front cam portion 16a involved in the feeding mechanism A shown in FIG. 5 is the outer peripheral side cam portion 16o, and the rear cam portion 16b is the inner peripheral side cam portion 16i.

As shown in FIG. 5, the rotary cam body 16 is formed with forward and backward cam portions 16a and 16b in the front portion and the rear portion in the axial direction, respectively, and is formed in the front portion of the transmission cam body 18. The cam portion 18a is arranged so as to face the rearward cam portion 16b of the rotary cam body 16.

As shown in FIG. 11, a protrusion for preventing the inner peripheral surface of the internal through hole 16c from rotating is formed. The protrusion 16c1 engages with a notch 14c on a flat surface on the outer peripheral surface of the screw shaft 14 (see FIG. 13) to regulate the relative rotation between the rotary cam body 16 and the screw shaft 14, and is relative to each other. It has a function that enables the advancement and retreat of Shinji in the axial direction.

(Transmission cam body 18)
As shown in FIG. 12, the transmission cam body 18 has a large diameter at the central portion, and the front and rear portions having a slightly smaller diameter than the central portion extend back and forth in a cylindrical shape, and the front end surface and the rear end surface thereof. It is a cam portion (18a) on which a cam is formed. The protrusions 18b are projected in pairs from the facing outer peripheral surfaces of the central portion. In the central portion, a pair of notches 18b1 penetrating the inner and outer peripheral surfaces are formed so as to sandwich the forming portion of the protrusion 18b. In the central portion, the portions sandwiched by the notches 18b1 and 18b1 are formed so as to be elastically deformable.

In the assembled state, as shown in FIGS. 5 and 6, the front portion of the transmission cam body 18 has a slightly smaller diameter than the central portion and is inserted into the tubular rear portion of the rotary cam body 16 to form the transmission cam body. The cam portion 18a at the front portion of 18 faces the cam portion 16b.

The cam portion 18a of the transmission cam body 18 and the rearward cam portion 16b of the rotary cam body 16 mesh with each other when the transmission cam body 18 rotates in one direction when they are in contact with each other, and conversely, the transmission cam body It is formed in a sawtooth shape so that the meshing can be easily disengaged when the 18 is rotated in the other direction.

Specifically, as schematically shown in FIG. 17 described later, the cam portion 18a of the transmission cam body 18 is a sawtooth having a plurality of triangular peaks inclined in one direction (eg, clockwise rotation direction) of the slope. , The rearward cam portion 16b of the rotary cam body 16 is a sawtooth having a plurality of triangular peaks inclined in the other direction of the slope (eg, the counterclockwise rotation direction).

When the forward cam portion 16a of the rotary cam body 16 and the rearward cam portion 22c in the tubular portion 22a of the screw body 22 are in contact with each other, the rotary cam body 16 rotates in the other direction. It is formed in a sawtooth shape that sometimes meshes, and conversely, the meshing easily disengages when the rotary cam body 16 rotates in one direction. Specifically, as schematically shown in FIG. 17 described later, a plurality of triangular peaks inclined in one direction (eg, right rotation direction) of the forward cam portion 16a slope of the rotary cam body 16 are formed. The rearward cam portion 22c in the tubular portion 22a of the screw body 22 is a sawtooth having a plurality of triangular ridges inclined in the other direction (eg, counterclockwise rotation direction) of the slope.

The feeding body 20 arranged in the tubular portion 22a of the screw body 22 has a structure that can move within a certain range in the axial direction in a state where the relative rotation with the screw body 22 is restricted.

Specifically, as shown in FIGS. 5 and 6, the structure that can move in the axial direction by the regulation of relative rotation has a protrusion 20b on the outside of the cantilever-shaped arm portion that can be elastically deformed on the side portion of the feeding body 20. This is due to the configuration in which the protrusion 20b is formed and is fitted into the axially long window portion 22a1 of the tubular portion 22a so as to be movable back and forth. Further, the protrusion 18b of the transmission cam body 18 fits into the guide groove 20a, and the spring 18c is interposed between the feeding body 20 and the transmission cam body 18 to repel each other. The spring 18c is preferably a coil spring made of metal, resin or the like.

In the assembled state, the cam formed on the outer periphery of the rear end of the rotary cam body 16 and the cam formed on the rear end of the transmission cam body 18 are not involved in the cam operation.

(Screw shaft 14)
As shown in FIG. 13, in the screw shaft 14, male screw screw portions 14a and 14a are formed on the outer peripheral surface of the outer peripheral surface in an arcuate pair in the radial direction, and the screw portions 14a and 14a are connected to each other. Flat notches 14c and 14c are formed between them. Further, the screw shaft 14 has a front-rear symmetrical shape in the axial direction, and a fitting portion that is fitted into the main body 12a (see FIG. 15) of the piston 12 to rotate and prevent it from coming off at the front end portion and the rear end portion. 14b is formed. The fitting portion 14b has flange-shaped ribs formed on the outer peripheral surface of a cylindrical portion extending to the front end portion and the rear end portion of the screw shaft 14.

When the screw shaft 14 is mounted on the rotary cam body 16, as shown in FIG. 14, the front end portion or the rear end portion of the screw shaft 14 is inserted into the internal through hole 16c in the rotary cam body 16 in the axial direction. do. At the time of assembly, the flat notch 14c of the screw shaft 14 engages with the protrusion 16c1 of the rotary cam body 16 by insertion. Since the screw shaft 14 has a symmetrical shape in the front-rear direction at the time of insertion, it is not necessary to consider the front-rear position, so that positioning in the front-rear direction becomes unnecessary and the work is simple.

(Piston 12)
As shown in FIG. 15, the piston 12 has a front-back symmetry and an axisymmetric shape. The piston 12 is formed with a main body 12a having a hole into which the fitting portion 14b (see FIG. 13) of the screw shaft 14 is fitted, and a sealing portion 12b whose diameter is expanded in the front-rear direction so as to surround the main body 12a. In the hole of the main body 12a, a concavo-convex portion is formed in which the fitting portion 14b is rotatable and the back-and-forth movement is restricted to engage with the fitting portion 14b. Further, the seal portion 12b is in sliding contact with the inner surface of the barrel 10 to make the accommodating portion 10b liquidtight (see FIG. 3).

(Seal joint 36)
As shown in FIG. 16, the seal joint 36 is formed with a small-diameter portion 36b for receiving the seal ball 36a (see FIG. 1) inside, and the stirring body 10d and the seal ball 36a are sealed behind the seal joint 36. A convex portion 36c that prevents the joint 36 from being closed is extended and formed. A flange portion 36d having an enlarged diameter is formed at the front end portion. The flange portion 36d abuts on the end surface of the front end portion 10a of the barrel 10 to regulate the dive into the front end portion 10a (see FIG. 1).

Next, the feeding operation (knocking operation) of the coating tool of the above-described embodiment will be described with reference to FIGS. 2, 3, and 17 to 18.

FIG. 2 shows the non-knocked state (in-situ) of the applicator, and FIG. 3 shows the knocked state. In the feeding mechanism A, FIG. 5 shows a non-knocking time, and FIG. 6 shows a knocking time. 17 to 18 are operation explanatory views based on a schematic diagram of the screw body 22, the rotary cam body 16, the transmission cam body 18, and the feeding body 20 in the feeding mechanism. FIG. 17A shows an explanatory diagram of each part, FIG. 17B shows a diagram of an initial state, FIG. 17C shows a diagram of a state at the start of knocking, and FIG. 18A shows a diagram of the state when knocking is completed. A state diagram, (b) is a state diagram when the knock is released and the return starts, and (c) is a state diagram in the initial state where the knock is completely returned.

In the knock-type coating tool, the user knocks the outer periphery of the rear end surface of the feeding body 20 to advance the feeding body 20 as shown in FIG.

As shown in FIG. 17A, the forward movement is converted into a rotational movement (one direction: indicated by reference numeral F) of the transmission cam body 18 by the guide groove 20a and the protrusion 18b on the side surface of the transmission cam body 18 during the feeding operation. do. The angle of rotation of the transmission cam body 18 is indicated by θ in the figure, and the knock stroke of the feeding body 20 is indicated by reference numeral L.

The rotation of the transmission cam body 18 causes the rotary cam body 16 to rotate in one direction to advance the screw shaft 14 and advance the piston 12. On the other hand, when the pressing is released, the feeding body 20 returns to the rear, and the transmission cam body 18 rotates in the other direction and returns to the original position.

Specifically, as shown in FIGS. 17 (b) to 17 (c) to 18 (a), first, when the feeding body 20 is pressed forward, the elastic force of the spring 18c (see FIG. 3) is obtained. The feeding body 20 moves forward against the above. As a result, the protrusion 18b slides along the guide groove 20a, and the transmission cam body 18 rotates in one direction (arrow F direction). As shown in FIGS. 17B to 17C, the rotation of the transmission cam body 18 in one direction causes the teeth of the cam portions 18a and 16b of the transmission cam body 18 and the rotary cam body 16 to be in contact with each other to mesh with each other. The rotary cam body 16 starts to rotate.

After FIG. 17C, when the protrusion 18b slides backward along the guide groove 20a until the feeding body 20 reaches the bottom dead center and the rotating cam body 16 rotates, the front of the rotating cam body 16 When the teeth of the directional cam portion 16a get over the teeth of the rearward facing cam portion 22c in the tubular portion 22a by one pitch or more and reach the bottom dead center as shown in FIG. 18A. Fits on the next pitch of teeth.

By the operations shown in FIGS. 17 (b) to 17 (c) and 18 (a), the knock operation of the feeding body 20 is transmitted from the rotation of the transmission cam body 18 to the rotation of the rotating cam body 16, and the rotating cam body 16 The screw shaft 14 (not shown) rotates by rotation and moves forward by the action of the female screw (female thread) 22b2 of the screw portion 22b. By advancing the screw shaft 14, the piston 12 advances in the accommodating portion 10b and feeds the coating liquid toward the coating body 24.

On the other hand, when the pressing operation of the feeding body 20 is released, as shown in the order of FIGS. 18A to 18C, the feeding body 20 moves rearward due to the elastic force of the spring 18c, so that the guide groove 20a The protrusion 18b slides forward along the line, and the transmission cam body 18 rotates in the other direction (opposite direction of F). The front-facing cam portion of the rotary cam body 16 and the teeth of the rear-facing cam portion in the tubular portion 22a of the screw body 22 mesh with each other to restrict the rotation of the rotary cam body 16, so that the transmission cam body 18 is restricted. Only rotates (see FIGS. 18 (b)-(c)).

Then, the teeth of the cam portions 18a and 16b in contact with each other of the transmission cam body 18 and the rotary cam body 16 are disengaged from each other, and when the teeth are advanced by one pitch or more, they are overcome and fitted into the teeth of the next pitch. , The rotation of the transmission cam body 18 in the other direction is not transmitted to the rotary cam body 16, and fits into the tooth adjacent to one pitch in the rotary cam body 16. In that case, the initial state is returned by one pitch as shown in FIG. 18 (c).

As an example of the knock mechanism, the knock stroke is 2 mm.
When the user knocks and feeds out, the feeding body 20 advances by 1 mm by knocking 1 mm, and the protrusion 18b of the transmission cam body 18 moves (rotates) along the guide groove 20a diagonally opened in the feeding body 20. .. When the knock is 2 mm, the knock limit is reached and the protrusion 18b of the transmission cam body 18 is completely rotated. During that time, the rotary cam body 16 rotates (see FIGS. 17 (b) to (c) and 18 (a)).

When the knock operation is released, the feeding body 20 returns to the rear and the protrusion 18b of the transmission cam body 18 rotates in the opposite direction along the guide groove 20a, but the cam of the transmission cam body 18 and the cam of the rotary cam body 16 mesh with each other. Is open and only the transmission cam body 18 rotates in the opposite direction, and the rotary cam body 16 does not rotate (FIGS. 18 (a) to 18 (c)).

Consider the conditions for the rotation angle θ.
When the knocking stroke L of the feeding body 20 is knocked, the transmission cam body 18 rotates by a rotation angle of θ degrees. Assuming that the rotation angle of one peak of the transmission cam body 18 and the rotary cam body 16 (rear cam portion 16b) is B, the relationship of "θ>B" is required.

That is, if the rotation angle θ is not larger than the rotation angle B of one mountain, the mountain of the cam portion cannot be overcome.

Further, the angle at which the forward-facing cam portion 16a of the rotary cam body 16 advances over the cam portion 22c of the screw body 22 when knocked to the end is set as C, and similarly, the rotary cam body 16 moves when the knock is returned to the original position. Assuming that the angle further advanced after passing over the transmission cam body 18 is A, θ = A + B + C, and by appropriately setting A and C to rotate excessively, “θ> B” can be obtained.

If A or C is small (small), it may not be possible to overcome the cam due to the tolerance or variation of parts, and if it is too large, the knock stroke must be increased unnecessarily, which is inefficient.

Considering one embodiment, if the cams are arranged in 12 equal parts, B = 360/12 = 30 degrees. If A and C are set to 7.05 degrees, the angle of rotation due to knocking becomes θ = 30 + 7.05 + 7.05 = 44.1 degrees. That is, the rotation angle due to knocking becomes 44.1 degrees.

According to the knock-type applicator of the embodiment, when the guide groove 20a of the feeding body 20 is formed diagonally at an angle with respect to the axial direction and the feeding body 20 is advanced by the knocking operation, the said The forward motion is converted into a rotational motion in one direction of the transmission cam body 18 by the guide groove 20a and the protrusion 18b, and the cam portion of the transmission cam body 18 meshes with the cam portion at the rear of the rotary cam body 16 to transmit the transmission. The rotation of the cam body 18 causes the rotary cam body 16 to rotate, and the screw shaft 14 advances to advance the piston 12, while the knock operation is released to retract the feeding body 20 by the elastic force of the spring 18c. At that time, the guide groove 20a and the protrusion 18b convert the retracting motion into a rotational motion in the other direction of the transmission cam body 18 to return to the original position, and the cam portion at the front portion of the rotary cam body 16 is By engaging with the cam portion of the tubular portion 22a, the rotational operation of the rotary cam body 16 is restricted and the operation of the screw shaft 14 and the piston 12 is restricted. The pressing force of the piston 12 can be transmitted without loss of force, and in the case of feeding out a highly viscous content, the operation feeling can be further lightened while preventing the loss of knocking force.

At the same time, since the tubular portion 22a in which the rearward facing cam portion 22c is integrally formed is provided on the screw body 22, the cam portion is not provided on the separate body, so that it is compared with the one provided on the separate body. Therefore, the number of parts can be reduced and manufacturing can be facilitated.

Further, when the feeding body 20 is pressed forward, the protrusion 18b slides along the guide groove 20a and the transmission cam body 18 rotates in one direction, so that the transmission cam body 18 and the rotating cam body 18 are rotated. The cam portions facing each other of 16 mesh with each other, and the cam portion facing forward of the rotating cam body 16 and the cam portion facing backward in the tubular portion 22a are disengaged, so that the rotating cam body 16 rotates. It is transmitted, and the screw shaft 14 is rotated by the rotation of the rotary cam body 16 and is advanced by the action of the female screw of the screw portion 22b. Then, when the pressing operation of the feeding body 20 is released, the feeding body 20 moves rearward due to the elastic force of the spring 18c, so that the protrusion 18b slides along the guide groove 20a and the transmission cam. The body 18 rotates in the other direction, the cam portions of the transmission cam body 18 and the rotary cam body 16 in contact with each other are disengaged, and the cam portion of the rotary cam body 16 facing forward and the tubular shape of the screw body 22 are disengaged. By engaging the rearward cam portion in the portion 22a, the rotation of the transmission cam body 18 in the other direction is prevented from being transmitted to the rotary cam body 16. The piston 12 can be smoothly pushed out by repeating the above pressing operation of the feeding body 20.

Further, each cam portion in the rearward cam portion of the transmission cam body 18 and the rotary cam body 16, the forward cam portion of the rotary cam body 16 and the rearward cam portion in the tubular portion 22a of the screw body 22. If the tooth pitch is the same and the phases of the teeth of the rearward cam portion and the forward cam portion of the rotary cam body 16 are out of phase, the cam teeth of the rotary cam body 16 are formed before the knock operation of the feeding body 20. Is fitted into the cam teeth of the tubular portion 22a, and the cam portion of the transmission cam body 18 is out of phase with the rearward teeth of the rotary cam body 16 when the delivery body 20 is knocked. The transmission cam body 18 rotates with the advance of 20. Then, when the knocking of the feeding body 20 is released, the cam portions of the rotating cam body 16 and the tubular portion 22a are surely engaged with each other, and the return rotation of the rotating cam body 16 can be surely prevented.

If a ring-shaped seal body (elastic body such as rubber or elastomer) is positioned in a circumferential shape between the outer circumference of the feeding body 20 and the inner circumference of the tubular portion 22a of the screw body 22, the ring-shaped seal body is formed. The sealing body can secure the airtightness from the feeding body 20 to the rear and surely prevent the contents from drying and deteriorating.

In the applicator of the embodiment, as shown in FIG. 3, a toe shaft 26 is provided on the front end portion 10a of the shaft cylinder 10 so as to cover the periphery of the applicator body 24, and the toe shaft 26 and the shaft cylinder 10 are fully fitted to each other. A portion and a temporary fitting portion are formed, and the front shaft 26 and the shaft cylinder 10 each have a detent rib (reference numeral 46 in FIG. 19 and reference numeral 38 in FIG. 20), and the shaft cylinder 10 and the shaft cylinder 26 are formed. In the initial fitting state (see FIG. 23) in which the temporary fitting portions are engaged with each other, the detent ribs are not engaged with each other, while in the main fitting state in which the main fitting portions are fitted with each other. The structure is such that the detent ribs are engaged with each other (see FIG. 22).

The main fitting and the temporary fitting will be described with reference to the parts drawing of the shaft cylinder 10 of FIG. 19 and the parts drawing of the toe shaft 26 of FIG.

(Shaft tube 10)
The shaft cylinder 10 will be described.

As shown in FIG. 19, the shaft cylinder 10 has a substantially cylindrical shape. The front end portion 10a of the shaft cylinder 10 is formed on the front side of the main body having the accommodating portion 10b and has a smaller diameter than the main body. As shown in FIG. 19C, the front end portion 10a has two ribs (front main fitting portion 42F, rear main fitting portion 42R) as main fitting portions 42 at intervals. It is formed in an annular shape on the outer circumference.

In the main fitting portion 42, the rib on the coating portion side, that is, the front side of the main fitting portion 42F is a temporary fitting portion 44 whose front side has a stepped diameter expansion. Specifically, in the front end portion 10a of the barrel 10, the front outer diameter is formed to be smaller than the rear outer diameter with the main fitting portion 42F as a boundary, and the step portion is close to a right angle. The step portion on the front side of the joint portion 42F is the step portion of the temporary fitting portion 44.

On the outer peripheral surface of the front end portion 10a of the shaft cylinder 10, a backlash prevention portion 50 that supports the front shaft from the inside in the radial direction at the time of temporary fitting is formed. Specifically, a backlash prevention portion 50 made of ribs at the time of temporary fitting is formed along the axial direction between the main fitting portion 42F on the front side and the main fitting portion 42R on the rear side.

Further, the outer diameters of the main fitting portion 42F on the front side and the main fitting portion 42R on the rear side are different. In front of the temporary fitting portion 44, a detent rib 46 that prevents the toe shaft 26 from rotating with respect to the barrel 10 is formed.

As shown in FIG. 19, the shaft cylinder 10 has a reduced diameter at the front end portion 10a, but a concave-convex stepped fitting portion 10e is formed on the inner peripheral surface of the rear end portion. Further, a vertical rib 10f is formed so as to project inward and extend in the axial direction slightly behind the central portion.

When the screw body 22 (see FIG. 1) is attached to the shaft cylinder 10, the screw body 22 is inserted forward from the opened rear end portion of the shaft cylinder 10, and the screw body 22 is attached to the vertical rib 10f on the outer periphery of the screw body 22. While moving forward, it fits in.

A threaded body 22 having a cylindrical shape with a closed rear end and whose rotation is restricted is fitted into the fitting portion 10e, and the rear end of the feeding body 20 is rearward to the shaft cylinder 10. It is exposed from the edge (see FIG. 1).

(Front axis 26)
FIG. 20 is a component diagram of the toe shaft 26.

As shown in FIG. 20, the front shaft 26 exhibits a substantially cone shape in which the front portion is tapered from the rear portion. On the inner circumference of the front shaft 26, the stepped rear end side surface of the front rib 54, which is a temporary fitting portion for temporary fitting with the temporary fitting portion 44 (see FIG. 19) of the front end portion 10a of the shaft cylinder 10. The front rib 54 and the rear rib 56 that are main-fitted with the main fitting portion 42 (42F, 42R) (see FIG. 19) of the front end portion 10a are formed over substantially the entire circumference. Since the front rib 54 and the rear rib 56 are formed over substantially the entire circumference, the temporary pulling force between the front shaft 26 and the shaft cylinder 10 in the initial mating state is improved, and the front shaft 26 during transportation or the like is improved. It is possible to prevent the shaft cylinder 10 from falling off.

The front rib 54 and the rear rib 56 have a substantially trapezoidal cross-sectional shape along the axial direction. The cross-sectional shape of the ribs 54 and 56 is not limited to a trapezoidal shape having edges at the corners, and may be a chamfered corner or an arc shape.

In the front shaft 26, the inner circumference of the front portion is formed in a cylindrical inner circumference shape for accommodating the coating body 24, and the engagement step portion 26a for fitting the pipe joint 30 is formed on the inner circumference of the central portion. Further, an annular uneven portion 26b for fitting and fixing the cap 28 is formed on the outer peripheral surface of the toe shaft 26.

The front side of the engaging step portion 26a of the front shaft 26 is the inner circumference of the rear portion, and a plurality of detent ribs 38 for vertical grooves for preventing rotation are formed inside the uneven portion 26b.

On the inner circumference of the front shaft 26, a stepped locking portion 26c with which the flange 24a of the coating body 24 abuts is formed in front of the engaging step portion 26a. A triangular groove is formed in the locking portion 26c before and after the step. Since the groove induces the hair on the ear neck when the coating body 24 is attached, it is possible to prevent the ear neck from tipping over (turning in the opposite direction).

When the applicator of the embodiment is started to be used from an unused state, it becomes an initial fitting state shown in FIG. 21, a main fitting state shown in FIG. 22, and a temporary fitting state shown in FIG. 22 which is slightly pushed in.

When the applicator is in an unused state, the tip shaft 26 is held via the stopper ring 34 to maintain the initial fitting state temporarily fitted to the shaft cylinder 10 (see FIG. 1).

In order to start the use, first, the user removes the stopper ring 34 and sets the tip shaft 26 into a state in which the tip shaft 26 is not pushed toward the shaft cylinder 10 side (initial fitting state). In this case, as shown in FIG. 21, the front rib 54 of the front shaft 26 abuts on or is located in front of the temporary fitting portion 44 of the barrel 10, and the rear rib 56 is the front and rear main fitting portion 42 (main fitting portion 42). It is located depressed between the fitting portions 42F and 42R). The seal ball 36a is fitted in the seal joint 36. The detent rib 46 of the shaft cylinder 10 is not engaged with the detent rib 38 of the toe shaft 26. Therefore, the leading shaft 26 can freely rotate with respect to the shaft cylinder 10. The rear rib 56 of the front shaft 26 is positioned so as to be depressed between the front and rear main fitting portions 42 (main fitting portions 42F, 42R), but for preventing backlash between the main fitting portions 42F and 42R. Since the backlash prevention portion 50 made of the ribs of the above supports the rear rib 56 of the front shaft 26, the backlash of the front shaft 26 can be prevented.

When preparing for use, the toe shaft 26 is slightly pushed into the shaft cylinder 10 from the initial fitting state to reach the temporary fitting state shown in FIG. 23. Also in this case, the front rib 54 of the front shaft 26 is in contact with the temporary fitting portion 44 of the shaft cylinder 10 and is positioned. The backlash prevention portion 50 supports the rear rib of the front shaft 26 to prevent backlash. In this state, the detent rib 38 of the front shaft 26 is inserted into and engaged with the detent rib 46 of the shaft cylinder 10, so that the front shaft 26 and the shaft cylinder 10 are detented.

Then, when the front shaft 26 is pushed in from the temporary fitting state of FIG. 23, the front rib 54 gets over the main fitting portion 42F on the front side from the temporary fitting portion 44 and engages with the main fitting portion 42F. Further, the rear rib 56 gets over the main fitting portion 42R and engages with the rear rib 56. This fitting state is shown in FIG. 22. The tip shaft 26 moves in the axial direction by approximately the length of the stopper ring 34, and is in a state of main fitting in which the tip shaft 26 is directly fitted to the shaft cylinder 10. At the same time, the detent rib 38 of the front shaft 26 is completely inserted into the detent rib 46 of the shaft cylinder 10, so that the detent rib of the shaft cylinder 10 can be more reliably detented to the front shaft 26.

According to the coating tool of the embodiment, the main fitting portion 42 (42F, 42R) and the temporary fitting portion 44 are formed on the shaft cylinder 10, and the shaft cylinder 10 is formed on the inner circumference of the toe shaft 26. The front rib 54 for temporary fitting with the temporary fitting portion 44 of the front end portion 10a, and the front rib 54 and the rear rib 56 for main fitting with the main fitting portion 42 (42F, 42R) of the front end portion 10a are omitted. It is formed all around. The shaft cylinder 10 has a detent rib 46, and the toe shaft 26 has a detent rib 38.

As shown in FIG. 21, in the initial fitting state (before the temporary fitting portion 44 and the front rib 54 engage with each other) before the temporary fitting of the shaft cylinder 10 and the front shaft 26, the detent ribs 46, The 38s are not engaged with each other. It is in a relative rotatable state.

On the other hand, as shown in FIG. 23, in the temporary fitting state (the temporary fitting portion 44 and the front rib 54 are engaged with each other), the detent ribs 46 and 38 are engaged with each other to be in the detent state. ..

Further, as shown in FIG. 22, the front shaft 26 and the shaft cylinder 10 are connected by being in the main fitting state (the main fitting portion 42 (42F, 42R), the front rib 54, and the rear rib 56). It becomes ready for use.

Therefore, when the user removes the toe shaft 26 in addition to the stopper ring 34 at the start of use, even if the toe shaft 26 is refitted and finally fitted, the detent ribs 46 and 38 are in a state of engaging with each other. , Can be press-fitted without misalignment. Therefore, it is possible to prevent liquid leakage due to insufficient press-fitting.

Further, when the detent rib 46 of the shaft cylinder 10 and the detent rib 38 of the front shaft 26 are engaged with each other and the shaft cylinder 10 and the front shaft 26 are in a detent state, when the user turns the front shaft 26. It is possible to prevent the coating body 24, which is a bundle of brush ears and fibers, from being twisted.

Further, since the temporary pulling force (pulling force when the stopper ring 34 is present) in the initial mating state can be strengthened, the leading shaft 26 can be prevented from falling off from the shaft cylinder 10 during transportation or the like.

The application tool of the present invention can be used for a cosmetic application tool such as a cosmetic product.

10 Shaft cylinder 10a Front end 10b Accommodation 10c Step 10d Stirrer 10e Fitting 10f Vertical rib 12 Piston 12a Main body 12b Seal 14 Screw shaft 14a Thread 14b Fitting 14c Notch 16 Rotating cam body 16a Cam 16b Cam part 16c Internal through hole 16c1 Protrusion 18 Transmission cam body 18a Cam part 18b Protrusion part 18c Spring 20 Feeding body 20a Guide groove 20b Protrusion 20b1 Arm part 20c Guidance part 20c1 Step part 20d Guide protrusion 20e Second protrusion 20f Step part 22 Screw Body 22a Cylindrical part 22a1 Window part 22a2 Rib 22a3 Thin-walled part (inclined surface)
22a31 Step 22b Threaded part 22d Flange 22e Unevenness 22f Induction groove 24 Coating body 24a Flange 26 Pilot shaft 28 Cap 30 Pipe joint 32 Pipe 34 Stopper ring 36 Seal joint 36a Seal ball 36b Small diameter part 36c Convex part 36d Flange part 38 Anti-rotation rib 42 Main fitting part 44 Temporary fitting part 46 Anti-rotation rib on the front shaft 50 Backlash prevention part 54 Front rib 56 Rear rib A Feeding mechanism

Claims (5)

An accommodating portion for storing the coating liquid, a piston sliding in the accommodating portion, a screw shaft having a screw formed on the peripheral surface, a feeding body for feeding operation, a rotating cam body, and a transmission cam body are provided. A screw portion to be screwed to the screw shaft is provided behind the accommodating portion, and the rotary cam body is rotated by the feeding operation to the feeding body to rotate the screw shaft and the screw portion relative to each other to advance the screw shaft and screw. In a coating tool in which a piston is advanced by a shaft to supply a coating liquid to be stored in the housing portion to a coating body.
A coating tool characterized in that at least one of the screw shaft, the rotary cam body, and the transmission cam body is formed in a front-rear symmetrical shape. The coating tool according to claim 1, wherein the piston is formed in a symmetrical shape. 2. Coating tool. A toe shaft is provided at the front end of the barrel so as to cover the periphery of the coating body.
A main fitting portion and a temporary fitting portion are formed on the toe shaft and the shaft cylinder, respectively.
The toe shaft and the shaft cylinder have their own detent ribs,
In the initial fitting state in which the temporary fitting portions of the barrel and the tip shaft are engaged with each other, the respective detent ribs are not engaged with each other, while the main fitting portions are fitted with each other in the main fitting state. The coating tool according to any one of claims 1 to 3, wherein the detent ribs are sometimes engaged with each other. The relative rotation between the rotary cam body and the screw shaft is restricted, the rotary cam body is rotated by the feeding operation of the transmission cam body to the feeding body, and the formation of a screw portion screwed to the screw shaft is formed. The screw body is provided behind the housing portion, and when the feeding body is operated, the rotating cam body rotates to advance the piston so as to supply the coating liquid to be stored in the housing portion to the coating body. The coating tool according to any one of claims 1 to 4, wherein the coating tool is characterized by the above.

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