Applicator

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

Technical Field

[0001] The present invention relates to an applicator that supplies liquid contents such as lotion, correction fluid, and ink for a brush by a knocking operation and supplies them to an application body.

Background Art

[0002] Conventionally, a knocking-type applicator that converts a knocking operation into a rotational operation to feed out a coating liquid has been proposed (see Patent Document 1).

[0003] Since this applicator has a cam surface provided on the end face of a cylindrical rotating body, there is a limit value for the feeding force. When the coating liquid is an oil-based type, the viscosity is high, so the applicator of Patent Document 1 is not suitable for feeding out the coating liquid.

[0004] On the other hand, in Patent Document 2, an applicator capable of increasing the feeding force by a guide groove and a protrusion has been proposed.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0006] Since the applicator has a plurality of shaft-like parts, a process of aligning the front and rear of the shaft-like parts is required during the manufacture of the applicator, which becomes a work load, but a technique for reducing that kind of work load has not been proposed.

[0007] In view of such circumstances, the present invention provides an applicator capable of improving the assemblability during manufacture.

Means for Solving the Problems

[0008] The present invention provides an applicator comprising a storage section for storing an applicator liquid, a piston that slides within the storage section, a screw shaft with threads formed on its circumferential surface, a dispensing body for dispensing operations, a rotating cam body, and a transmission cam body, wherein a screw portion that screws onto the screw shaft is provided at the rear of the storage section, and dispensing operations on the dispensing body rotate the rotating cam body, causing the screw shaft and the screw portion to rotate relative to each other and advance the screw shaft, thereby advancing the piston and supplying the applicator liquid stored in the storage section to the applicator, The applicator 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-to-back symmetrical shape.

[0009] In the present invention, it is preferable that the piston is formed in a front-to-back symmetrical shape.

[0010] In the present invention, it is preferable that the inner surface of the screw body, which houses the screw portion, the rotating cam body, the transmission cam body, and the feed body, has an inclined surface that widens in diameter from the rear to the front.

[0011] In the present invention, a front shaft is provided at the front end of the shaft cylinder, covering 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, and the front shaft and the shaft cylinder each have anti-rotation ribs, and it is preferable that the anti-rotation ribs do not engage with each other in the initial fitting state when the temporary fitting portions of the shaft cylinder and the front shaft engage with each other, while the anti-rotation ribs engage with each other in the main fitting state when the main fitting portions engage with each other.

[0012] In the present invention, it is preferable that the relative rotation between the rotating cam body and the screw shaft is restricted, the rotating cam body rotates when the transmission cam body is fed out to the feed body, a screw body with a threaded portion that screws onto the screw shaft is provided at the rear of the housing, and the rotating cam body rotates when the feed body is operated, causing the piston to advance and supplying the coating liquid stored in the housing to the coating body. [Effects of the Invention]

[0013] According to the applicator of the present invention, since at least one of the screw shaft, the rotating cam body, and the transmission cam body is formed in a front-to-back symmetrical shape, front-to-back alignment can be omitted, resulting in the excellent effect of improved assembly during manufacturing. [Brief explanation of the drawing]

[0014] [Figure 1] This is an overall view of the applicator with the cap attached according to an embodiment of the present invention, where (a) is a view from the front, (b) is a front view from one direction, (c) is a front view rotated 90 degrees circumferentially from (b), and (d) is a longitudinal cross-sectional view along the DD line of (b). [Figure 2] Figure 1 shows an overall view of the applicator at the start of use, where (a) is a front view from one direction and (b) is a longitudinal cross-sectional view. [Figure 3] Figure 1 shows an overall view of the knock-press state of the applicator during use, where (a) is a front view from one direction and (b) is a longitudinal cross-sectional view. [Figure 4] Figure 1 shows the overall view of the applicator during and after use, where (a) is a front view from one direction and (b) is a longitudinal cross-sectional view. [Figure 5] Figure 1 shows the component diagram of the dispensing mechanism in the applicator, where (a) is a perspective view, (b) is a front view, (c) is a longitudinal section view along the CC line of (d), (d) is a front view rotated 90 degrees from (b), and (e) is a longitudinal section view along the EE line of (b). [Figure 6] Figure 5 shows the parts of the dispensing mechanism in the knocking state, where (a) is a perspective view, (b) is a front view, (c) is a longitudinal section view along the CC line of (d), (d) is a front view rotated 90 degrees from (b), and (e) is a longitudinal section view along the EE line of (b). [Figure 7] Figure 5 shows the parts with the screw body removed from the feeding mechanism, where (a) is a perspective view, (b) is a front view, (c) is a longitudinal section view along line CC of (d), (d) is a front view rotated 90 degrees from (b), and (e) is a longitudinal section view along line EE of (b). [Figure 8] This is a component diagram showing the knocking state (pressing state) of the feeding mechanism of FIG. 7 with the screw body removed. (a) is a perspective view, (b) is a front view, (c) is a longitudinal sectional view taken along the C-C line of (d), (d) is a front view in a state rotated 90 degrees from (b), and (e) is a longitudinal sectional view taken along the E-E line of (b). [Figure 9] This is a component diagram of the screw body in the applicator of FIG. 1. (a) is a view from the front, (b) is a front view, (c) is a longitudinal sectional view taken along the C-C line of (d), (d) is a front view in a state rotated 90 degrees from (b), (e) is a longitudinal sectional view taken along the E-E line of (b), (f) is a perspective view from the rear, and (g) is a view from the rear. [Figure 10] This is a component diagram of the feeding body in the applicator of FIG. 1. (a) is a perspective view, (b) is a view from the front, (c) is a front view, (d) is a longitudinal sectional view taken along the D-D line of (e), (e) is a front view in a state rotated 90 degrees from (c), (f) is a longitudinal sectional view taken along the F-F line of (c), (g) is a perspective view, and (h) is a view from the rear. [Figure 11] This is a component diagram of the rotating cam body in the applicator of FIG. 1. (a) is a perspective view, (b) is a front view, (c) is a longitudinal sectional view taken along the C-C line of (e), (d) is a longitudinal sectional view taken along the D-D line of (e), and (e) is a view from one direction. [Figure 12] This is a component diagram of the transmission cam body in the applicator of FIG. 1. (a) is a view from one direction, (b) is a perspective view, (c) is a front view, (d) is a front view in a state rotated 90 degrees from (c), (e) is a longitudinal sectional view taken along the E-E line of (c), and (f) is a view from the other direction. [Figure 13] This is a component diagram of the screw shaft in the applicator of FIG. 1. (a) is a perspective view, (b) is a front view, (c) is a front view in a state rotated 90 degrees from (b), and (d) is a view from the rear. [Figure 14] This is a perspective view of a component diagram of the rotating cam body in the applicator of FIG. 1 with the screw shaft oriented in the axial direction. [Figure 15]It is a component diagram of the piston in the applicator of FIG. 1, where (a) is a perspective view, (b) is a front view, (c) is a cross-sectional view taken along the C-C line of (b), and (d) is a view from the rear. [Figure 16] It is a component diagram of the 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, (c) is a front view (view) seen from the C direction of (a), (d) is a side view in a state rotated 90 degrees from (c), (e) is a longitudinal cross-sectional view taken along the E-E line of (b), (f) is a perspective view from the rear, and (g) is a view from the rear. [Figure 17] It is an operation explanatory diagram using schematic diagrams of the screw body, rotary cam body, transmission cam body, and feeding body for explaining the cam operation in the applicator of FIG. 1. (a) is an explanatory diagram of each part, (b) is a diagram of the initial state, and (c) is a diagram of the state at the start of the knock. [Figure 18] Similar to FIG. 17, it is an operation explanatory diagram using schematic diagrams. (a) is a state diagram when the knock is completed, (b) is a state diagram when the knock is released and the return starts, and (c) is a state diagram at the initial state when the knock is completely returned. [Figure 19] It is a component diagram of the shaft cylinder in the applicator of FIG. 1. (a) is a perspective view, (b) is a view from the front, (c) is an enlarged perspective view of the front end, (d) is a front view, (e) is a longitudinal cross-sectional view taken along the E-E line of (b), (f) is a front view in a state rotated 90 degrees from (d), and (g) is a longitudinal cross-sectional view taken along the G-G line of (b). [Figure 20] It is a component diagram of the tip shaft in the applicator of FIG. 1. (a) is a view from the front, (b) is a perspective view from the front, (c) is a front view, (d) is a longitudinal cross-sectional view taken along the D-D line of (a), (e) is a view from the rear, and (f) is a perspective view from the rear. [Figure 21] In the applicator of FIG. 1, it is an explanatory diagram of the state where the stopper ring is removed from the applicator (ready for use) and in the initial fitting state. (a) is a front view, (b) is a longitudinal cross-sectional view of the front part, (c) is a cross-sectional view taken along the C-C line of (b), and (d) is an enlarged explanatory diagram of the D part of (b). [[ID=,20]] [Figure 22]Figure 21 is an explanatory diagram of the applicator in which the front shaft is fully fitted into the shaft, with (a) being a front view, (b) being a longitudinal section view of the front part, (c) being a section view along line CC of (b), and (d) being an enlarged explanatory diagram of part D of (b). [Figure 23] Figure 21 is an explanatory diagram of the applicator in which the front shaft and the shaft cylinder are in a state of temporary fitting, with (a) being a front view, (b) being a longitudinal section view of the front part, (c) being a section view along line CC of (b), and (d) being an enlarged explanatory diagram of part D of (b). [Modes for carrying out the invention]

[0015] Embodiments of the present invention will be described below with reference to Figures 1 to 23.

[0016] Figure 1 shows the applicator in its unused state, Figure 2 shows it at the start of use, Figure 3 shows it in the knock-pressed state, and Figure 4 shows it at the end of use.

[0017] As shown in Figures 1 to 4, the applicator according to the embodiment includes a storage section 10b for storing the coating liquid, a piston 12 that slides within the storage section 10b, and a screw shaft 14 with a male screw thread 14a formed on its circumferential surface, all of which are provided within a shaft cylinder 10. A dispensing body 20 is provided for dispensing operations, and a rotating cam body 16 whose relative rotation with respect to the screw shaft 14 is restricted, a transmission cam body 18 that rotates the rotating cam body 16 when the dispensing operation on the dispensing body 20 is performed, and a screw body 22 with a screw thread 22b that screws onto the screw shaft 14 is provided behind the storage section 10b. The dispensing device is configured such that when the dispensing body 20 is operated, the rotating cam body 16 rotates, the piston 12 moves forward, and the coating liquid stored in the storage section 10b is supplied to the applicator 24. In this applicator, the screw shaft 14, the rotating cam body 16, and the transmission cam body 18 (at least one example of which) housed inside the screw body 22 are formed in a front-to-back symmetrical shape.

[0018] In the applicator, a dispensing mechanism A, consisting of a screw body 22, a screw shaft 14, a rotating cam body 16, a transmission cam body 18, a spring 18c, and a dispensing body 20, is arranged inside the shaft cylinder 10.

[0019] When unused, the applicator has a cap 28 and a stopper ring 34 attached, as shown in Figure 1. The stopper ring 34 is positioned with the front shaft 26 forward and the seal ball 36a fitted into it. When starting use, as shown in Figure 2, the stopper ring 34 is removed and the seal ball 36a falls into the housing 10b. When knocked, the piston 12 is pressed by the feed body 20 as shown in Figure 3, and when finished using, the piston 12 is positioned at the front end of the housing 10b as shown in Figure 4.

[0020] Figures 5 and 6 are component diagrams of the feeding mechanism A, with Figure 5 showing the non-knocked state and Figure 6 showing the knocked state. Figures 7 and 8 are component diagrams of the feeding mechanism A with the screw body 22 removed, with Figure 7 showing the non-knocked state and Figure 8 showing the knocked state. Figure 9 is a component diagram of the screw body 22, Figure 10 is a component diagram of the feeding body 20, Figure 11 is a component diagram of the rotating cam body 16, Figure 12 is a component diagram of the transmission cam body 18, Figure 13 is a component diagram of the screw shaft 14, Figure 14 shows the screw shaft 14 facing axially on the rotating cam body 16, Figure 15 is a component diagram of the piston 12, and Figure 16 is a component diagram of the coupling 36.

[0021] (Advancement mechanism A) As shown in Figures 5 and 6, the feeding mechanism A has a rotating cam body 16 whose relative rotation with respect to the screw shaft 14 is restricted and which has cam portions 16a and 16b formed on its front and rear ends, respectively, a transmission cam body 18 which has a cam portion 18a formed on its front end for engaging with the rear cam portion 16b of the rotating cam body 16 and a projection 18b formed on its side, and a guide groove 20a which guides the projection 18b of the transmission cam body 18, and the mechanism moves back and forth via the guide groove 20a and the projection 18b The device comprises a feed body 20 that rotates the transmission cam body 18, a spring 18c that springs the feed body 20 backward and the transmission cam body 18 forward, and a screw body (corresponding to a "fixed cam body") 22 that houses the transmission cam body 18, the rotating cam body 16, the spring 18c, the screw shaft 14, and the feed body 20, and has a cylindrical portion 22a at the rear with a rearward-facing cam portion 22c integrally formed inside, and a screw portion 22b at the front that screws onto the screw shaft 14.

[0022] In addition to the above configuration, the screw body 22, rotating cam body 16, and screw shaft 14 may also be configured such that the screw portion of the screw body 22 has a specially shaped hole to match the cross-section of the screw shaft 14 and restrict relative rotation with the screw shaft 14, and the rotating cam body 16 has a female screw portion formed on its inner circumference and the screw portion is screwed into the male screw on the outer circumference of the screw shaft 14.

[0023] Furthermore, the guide groove 20a of the dispensing body 20 is formed at an angle with respect to the axial direction (the front-to-back direction of the applicator).

[0024] In the above-described knock-type applicator, when the dispensing body 20 is advanced by a knock operation relative to the dispensing mechanism A, the guide groove 20a and projection 18b convert this forward movement into a rotational movement of the transmission cam body 18 in one direction (in this embodiment, the clockwise rotational direction toward the front of the shaft), and the cam portion 18a of the transmission cam body 18 engages with the rear cam portion 16b of the rotating cam body 16, and the rotation of the transmission cam body 18 rotates the rotating cam body 16, causing the piston 12 to advance as the screw shaft 14 moves forward. On the other hand, when the knock operation is released and the spring 18c retracts the feed body 20, the guide groove 20a and projection 18b convert the retraction movement into a rotational movement of the transmission cam body 18 in the other direction (in this embodiment, the left rotation direction toward the front of the axis), returning it to its original position. Furthermore, the cam portion 16a at the front of the rotating cam body 16 engages with the cam portion 22c of the cylindrical portion 22a, restricting the rotational operation of the rotating cam body 16 and thereby restricting the operation of the screw shaft 14 and the piston 12.

[0025] (Coated body 24) As shown in Figures 1-3, in the applicator, the applicator body 24 is attached to the front end 10a of the shaft (rear shaft) 10 by the front shaft 26. The applicator body 24 is not particularly specified as long as it is made of a material that can be impregnated with the coating liquid, such as a bundle of resin fibers or a porous material, but in this embodiment, the rear end is bundled by melting to form a flange shape.

[0026] (Application liquid) The coating liquid stored in the housing section 10b of the barrel 10 can be a cosmetic liquid, writing instrument ink, or a chemical solution, but it is particularly easy to dispense a cosmetic liquid with high viscosity (preferably 300 mPa·s or higher).

[0027] In this embodiment, a liquid oily cosmetic can be contained in the containment section 10b. Suitable liquid oily cosmetic in this embodiment contains (a) 5 to 40% by weight of hydrofluoroether, (b) 20 to 60% by weight of low boiling point silicone oil, (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 cross-linked methylpolysiloxane, inulin stearate, and sucrose fatty acid ester, and (e) 10 to 40% by weight of powder and at least volatile hydrocarbons.

[0028] Another suitable liquid oily cosmetic composition contains at least (a) 20-75% by weight of isododecane, (b) 2-25% by weight of one or more of trimethylsiloxiliate, alkyl acrylate, or alkyl acrylate copolymer, and (c) 2-25% by weight of one or more powders selected from carbon black, iron oxide, and Prussian blue.

[0029] Furthermore, it is preferable that the viscosity at 25°C and a shear rate of 76.6 / s is 40 mPa·s to 400 mPa·s, and that the average initial evaporation rate up to 1 minute immediately after coating by the filter paper method is 0.15 to 2.00 mg / sec under the conditions of 25°C and 65% RH. Viscosity exceeding 400 mPa·s is undesirable because the increased viscosity of the cosmetic product worsens its feel during use. Conversely, viscosity below 40 mPa·s is undesirable because it tends to seep easily on the skin. If the initial evaporation rate exceeds 2.00 mg / sec, the evaporation rate is too fast, resulting in extremely poor spreadability of the cosmetic product, which is undesirable for use. Conversely, if the initial evaporation rate is less than 0.15 mg / sec, the sticky feeling of the cosmetic product after application may linger for a long time, and the makeup's longevity may be reduced, which is also undesirable for use. The initial evaporation rate is calculated by accurately weighing approximately 1 g of cosmetic onto a φ90 mm filter paper under conditions of 25°C and 65% RH, measuring the weight again immediately after weighing and 1 minute later, and using the following formula based on the weight difference before and after measurement. Initial evaporation rate (mg / sec) = (W0 - W1) ÷ 60 × 1000 Here, W0 and W1 are as follows: W0: Weight (g) of cosmetic product weighed onto filter paper immediately after the start of measurement. W1: Weight of cosmetic product on filter paper 1 minute after measurement starts (g)

[0030] When the liquid oily cosmetic is contained in the storage section 10b, it is preferable to use polybutylene terephthalate resin (PBT resin) as the material for the shaft 10.

[0031] (Entire applicator) In the applicator, as shown in Figure 1, the front end 10a of the shaft (rear shaft) 10 is formed to be narrower in diameter in a stepped manner than the housing portion 10b inside the shaft 10. A cap 28 is detachably fitted onto the front end 10a of the shaft 10, covering the front shaft 26 and the applicator 24. A pipe joint 30 is located on the inside of the portion of the front shaft 26 that is fitted into the front end 10a of the shaft 10. The tip of the pipe joint 30 and the inner surface of the front shaft 26 clamp the flange at the rear end of the applicator 24, thereby fixing the applicator 24. A pipe 32 made of SUS or resin extends from the central hole of the pipe joint 30 into the applicator 24, and the pipe 32 allows the applicator liquid to flow toward the front end of the applicator 24.

[0032] The outer circumferential surface of the stepped, narrowed portion (stepped portion 10c) at the front end 10a of the shaft cylinder 10 is in contact with the cap 28 on its forward-facing surface (see Figure 1). The inner circumferential surface of the stepped portion 10c faces the inside of the coating liquid storage portion 10b in a rearward direction, and the piston 12 contacts this rearward-facing surface when it is at its forward end, thereby regulating its position (see Figure 4). The front part of the shaft cylinder 10 serves as a coating liquid storage section 10b, and the rear part houses a dispensing mechanism A consisting of a screw body 22, a screw shaft 14, a rotating cam body 16, a transmission cam body 18, a spring 18c, and a dispensing body 20, which has the function of dispensing the coating liquid toward the coating body 24 by advancing a piston 12 within the storage section 10b. The shaft cylinder 10 houses a stirring body 10d within the storage section 10b together with the coating liquid for stirring the coating liquid. The stirring body 10d may be a metal or resin ball or a rod-shaped body.

[0033] In the applicator, as shown in Figure 1, a stopper ring 34 is interposed between the front end surface of the stepped portion 10c of the shaft cylinder 10 and the rear end surface of the shaft cylinder 26 to maintain the front shaft 26 in an unused state when not in use. A cylindrical seal joint 36 is fitted inside the front end portion 10a of the shaft cylinder 10. This seal joint 36 has a seal ball 36a fitted inside to seal the housing portion 10b when the applicator is in an unused state.

[0034] When the user begins use, as shown in Figure 2, by removing the stopper ring 34 and pressing the front shaft 26 backward against the front end 10a of the shaft cylinder 10, the rear end of the pipe joint 30 is pushed into the seal joint 36, dropping the seal ball 36a into the housing 10b and opening the housing 10b. By operating the dispensing mechanism A, the piston 12 moves forward and the coating liquid is supplied to the coating body 24 through the seal joint 36, pipe joint 30, and pipe 32.

[0035] As shown in Figures 1 and 2, the cap 28 has an inner cap 28a and a biasing spring 28b arranged inside. The applicator is structured so that when not in use, the inner cap 28a, biased by the spring 28b, airtightly contacts the outer surface of the front shaft 26. This prevents the applicator 24 from drying out.

[0036] (Advancement mechanism A) The structure of each component in the feeding mechanism A is described below.

[0037] As shown in Figures 5 and 6, the feeding mechanism A consists of a screw shaft 14, a feeding body 20, a rotating cam body 16, a transmission cam body 18, and a spring 18c, all mounted inside the screw body 22. Figures 7 and 8 show the state with the screw body 22 removed. The individual components of the feeding mechanism A are shown in Figures 9 to 16. Each part is described below.

[0038] (Screw body 22) The screw body 22, when in its individual form, has a roughly cylindrical shape with open ends, as shown in Figure 9, and the front threaded portion (corresponding to the "female threaded portion") 22b is stepped in diameter compared to the cylindrical portion 22a. A cam portion 22c is formed on the inner surface of the front end of the cylindrical portion 22a. The threaded portion 22b extends in a generally cylindrical shape from the front end of the cylindrical portion 22a, but is divided into two by a split portion 22b1 cut in the axial direction, and is elastically deformable in the radial direction. Multiple (for example, 1 to 3) female threads 22b2 that can be screwed onto the screw shaft 14 are formed on the inner circumference of the threaded portion 22b, protruding inward. In addition, flange-shaped wing portions 22b3 are formed on the outer circumference of the threaded portion 22b to abut against the inner surface of the shaft cylinder 10.

[0039] Multiple convex ribs 22a2 are formed on the outer circumference of the cylindrical portion 22a, extending in the axial direction to prevent rotation relative to the inner surface of the shaft cylinder 10. A window portion 22a1 is located behind the ribs 22a2. The rib 22a2 is designed to engage with the vertical rib 10f (see Figure 19) on the inner surface of the barrel 10, preventing rotational problems during knocking by preventing the screw body 22 from rotating.

[0040] As shown in Figure 9, a thin-walled portion 22a3 is formed on the inner surface of the cylindrical portion 22a, with an inclined surface that widens in diameter from the rear to the front. More specifically, on the inner surface of the cylindrical portion 22a, the thin-walled portion 22a3 is formed by cutting out two semicircular sections in a thin manner from the rear end surface of the cylindrical portion 22a toward the window portion 22a1. The other parts of the cylindrical portion 22a and the thin-walled portion 22a3 are continuous via a semicircular step 22a31.

[0041] The step 22a31 sandwiching the thin-walled portion 22a3 is formed in a semicircular or triangular shape from the rear end of the cylindrical portion 22a to the window portion 22a1 (see Figures 9(c) and (e)). The shape of the thin-walled portion 22a3 is not limited to this.

[0042] Since a thin-walled portion 22a3 is formed, when the piston 12, screw shaft 14, rotating cam body 16, transmission cam body 18, spring 18c, and feed body 20 are assembled and installed inside the cylindrical portion 22a of the screw body 22 (see Figures 7 and 8), the feed body 20 is pushed in. At that time, the projection 20b of the feed body 20 comes into contact with the step 22a31 of the thin-walled portion 22a3, is guided to rotate and position, and slides into the window portion 22a1, with the projection 20b entering the window portion 22a1.

[0043] Therefore, when attaching the dispensing body 20 to the cylindrical portion 22a, the projection 20b does not need to be aligned circumferentially with respect to the window portion 22a1. Simply inserting the dispensing body 20 into the cylindrical portion 22a will allow the projection 20b to be fitted into the window portion 22a1, eliminating the need for alignment and thus increasing work efficiency.

[0044] Furthermore, since the threaded portion 22b is bifurcated at the split end 22b1, when assembling the screw shaft 14, the screw shaft 14 can be pushed into the threaded portion 22b, causing the threaded portion 22b to elastically deform and be installed. Therefore, assembly can be performed without the need to rotate the screw shaft 14 and screw it into the threaded portion 22b, enabling easy and reliable installation on the manufacturing line and significantly reducing the workload.

[0045] Furthermore, the screw body 22 has a cam portion 22c formed within the cylindrical portion 22a behind the screw portion 22b, which has multiple rearward-facing inclined surfaces, and the forward-facing cam portion 16a of the rotating cam body 16 is positioned opposite the rearward-facing cam portion 22c (see Figure 5).

[0046] As shown in Figure 9, a rearward-facing cam portion 22c is integrally formed inside the cylindrical portion 22a of the screw body 22 by an inclined surface, thus reducing the number of parts compared to when the cam portion 22c is provided as a separate part. Also, during assembly, the inner female threads 22b2 of the screw portion 22b engage with the screw shaft 14. The wing portion 22b3 on the outer circumference contacts the inside of the shaft cylinder 10, and by forming a wing portion 22b3 that is partially thinned, it prevents the screw body 22 from opening due to shrinkage during molding. The wing portion 22b3 is assembled so as to contact the vertical rib 10f (see Figure 19) on the inner surface of the shaft cylinder 10. Two wing portions 22b3 are preferable to satisfy the amount of coating liquid filling and to prevent opening. In addition, the formation of the split end portion 22b1 improves the design freedom of the molding die, which can lead to cost reduction.

[0047] The window portion 22a1 of the cylindrical portion 22a is designed to engage with the projection 20b of the dispensing body 20, preventing the dispensing body 20 from rotating when pressed. This prevents dispensing failures (see Figures 5 and 6). As shown in Figures 5 and 9, a flange 22d is formed at the rear end of the cylindrical portion 22a with an enlarged diameter to abut against and position the rear end of the shaft cylinder 10 (see Figure 1). Furthermore, multiple grooves 22e are formed on the outer circumference of the cylindrical portion 22a at a forward position adjacent to the flange 22d, for engaging with the inner surface of the rear end of the shaft cylinder 10. The window portion 22a1 is formed so as to penetrate the uneven surface 22e in the radial direction. Since the formation locations of the uneven surface 22e and the window portion 22a1 are in almost the same position in the axial direction of the screw body 22, the resin can easily flow around the uneven surface 22e and flange 22d during injection molding because the inside of the window portion 22a1 is empty space, resulting in a shape that is less prone to molding defects such as shrinkage in the screw body 22.

[0048] Furthermore, on the inner surface of the screw body 22, as shown in Figure 9, a thin-walled portion 22a3 extends to the position of the window portion 22a1. The step 22a31 of the thin-walled portion 22a3 has a triangular front end that overlaps with the window portion 22a1. On the inner surface of the screw body 22, a guide groove 22f is formed along the axial direction from the window portion 22a1 to the central part of the shaft. The guide groove 22f is guided by sliding a guide projection 20d (see Figure 10), which will be described later. Since the guide groove 22f is continuous with the thin-walled portion 22a3 at the position of the window portion 22a1, when the dispensing body 20 is assembled to the screw body 22, the guide projection 20d comes into contact with the step 22a31 and is guided into the guide groove 22f.

[0049] (Distributing unit 20) The dispensing body 20 (knock body), when in its individual form, has a generally cylindrical shape with a closed rear end, as shown in Figure 10, and a pair of guide grooves 20a are formed at its front end, penetrating the inner and outer surfaces and angled diagonally with respect to the axial direction.

[0050] The dispensing body 20 is advanced by the user knocking on the outer circumference of its closed rear end face. The guide groove 20a and the projection 18b on the side of the transmission cam body 18 convert this advancement into rotational motion of the transmission cam body 18. The rotation of the transmission cam body 18 causes the rotating cam body 16 to rotate, which in turn advances the screw shaft 14 and the piston 12 (see Figures 5 and 6).

[0051] Furthermore, as shown in Figures 7, 8, and 10, a cantilever-shaped arm portion 20b1 that is elastically deformable is formed on the rear side of the extending body 20 by a U-shaped notch, and a projection 20b is formed on the outside of the arm portion 20b1. Furthermore, on the outer circumferential surface of the anterior position of the arm portion 20b1, a pair of guiding projections 20d are formed, projecting outward at corresponding positions in the circumferential direction of the projection 20b.

[0052] Here, as shown in Figure 9, the top of the step 22a31 of the thin-walled portion 22a3 is located in the window portion 22a1, and a guide groove 22f is formed extending forward from the window portion 22a1. The thickness of the area where the guide groove 22f is formed is approximately the same as that of the thin-walled portion 22a3. When assembling the screw body 22 to the feed mechanism 20, the feed mechanism 20 is pushed onto the screw body 22 from behind to complete the assembly. When the feed mechanism 20 advances relative to the screw body 22 by pushing and assembling it, the guide projection 20d first comes into contact with the step 22a31 and rotates so that its circumferential position faces the window portion 22a1, thereby determining the relative angle. When the dispensing body 20 is pushed further, the guide projection 20d passes through the window portion 22a1 and is guided into the guide groove 22f, where it moves along the guide groove 22f. Since projection 20b is in the same position as the guide projection 20d in the circumferential direction, the forward movement of the guide projection 20d along the guide groove 22f causes projection 20b to smoothly fit into the window portion 22a1 without any displacement.

[0053] Therefore, the retractable body 20 can be assembled simply by pushing it in from the rear without having to position it on the screw body 22 (see Figures 5 and 6 for the fitted state). Therefore, the guiding projection 20d has the function of guiding by fitting its circumferential position into the guiding groove 22f, and the function of positioning the rear projection 20b so that it fits smoothly toward the window portion 22a1.

[0054] Furthermore, as shown in Figures 7, 8, and 10, the outer circumferential surface of the rear of the dispensing body 20 is formed so that the diameter is slightly larger behind the stepped portion 20f than at the front, all the way around. The larger diameter portion behind the stepped portion 20f contacts the inner circumferential surface of the cylindrical portion 22a of the screw body 22, maintaining airtightness between the dispensing body 20 and the cylindrical portion 22a (see Figures 5 and 6).

[0055] Furthermore, a pair of second projections 20e are formed on the outer circumferential surface behind the stepped portion 20f, projecting in a rib-like manner in the expanding radial direction. The second projections 20e project in pairs onto the outer circumferential surface of the dispensing body 20 at the same position in the circumferential direction as projections 20b and guiding projections 20d. The second projection 20e contacts (or is close to) the inner circumferential surface (thin-walled portion 22a3) of the cylindrical portion 22a when the extension body 20 is installed inside the screw body 22, thereby preventing the extension body 20 from wobbling relative to the cylindrical portion 22a (see Figures 5 and 6).

[0056] Furthermore, as shown in Figure 10, a guide portion 20c is formed on the inner circumference of the front part of the dispensing body 20 to guide the projection 18b (see Figure 12) into the guide groove 20a when the transmission cam body 18 is assembled. This guide portion 20c is a thin-walled portion formed by hollowing out the inner circumference from the front edge of the dispensing body 20 to the area around the guide groove 20a, and is formed in two locations corresponding to the guide groove 20a. A stepped portion 20c1 is formed that connects the thin-walled guide portion 20c to other thick-walled portions in a stepped manner. Two guide portions 20c are formed. The stepped portions 20c1 sandwiching each guide portion 20c, the width of which spans approximately half of the circumference at the front edge of the dispensing body 20, narrows towards the rear, and is formed to a width (or narrow, wide) corresponding to the guide groove 20a near the guide groove 20a. The stepped portions 20c1, and the width between them, are formed in the shape of a roughly triangular slope or wedge (see Figure 10(d)). Adjacent guide portions 20c may overlap at their front edges or have a gap between them (they may have a gap between the stepped portions 20c1, or they may be formed from portions that extend beyond the front edges).

[0057] During assembly, the transmission cam body 18 is installed inside the feed body 20 from the front. In this case, since the transmission cam body 18 has no front or back, front or back positioning is not required, resulting in less workload. When the transmission cam body 18 is inserted into the feed body 20, the pair of protruding projections 18b hit the stepped portions 20c1, 20c1 and are guided to fit into the pair of guide portions 20c. As the transmission cam body 18 moves backward, the projections 18b hit the stepped portions 20c1, 20c1, are guided into the guide portion 20c, and slide into the guide groove 20a.

[0058] Therefore, simply inserting the transmission cam body 18 into the feed body 20 guides the projection 18b into the guide groove 20a, eliminating the need to position the projection 18b circumferentially within the guide groove 20a. This eliminates the need for positioning, resulting in fewer work steps and extremely high efficiency.

[0059] (Symmetrical parts) In the applicator, among its components, the rotating cam body 16 as shown in Figure 11, the transmission cam body 18 as shown in Figure 12, and the screw shaft 14 as shown in Figure 13 are formed in a front-to-back symmetrical shape. These components will be described below.

[0060] (Rotating cam body 16) The rotating cam body (feed-out cam) 16, as a standalone unit, has a symmetrical shape between its front side 16F and rear side 16R, as shown in Figure 11, and exhibits a generally cylindrical shape with a hollow section.

[0061] A cam portion 16o is formed on the outer circumference of the front side 16F and a cam portion 16i on the inner circumference of the rear side 16R, respectively. The same function is achieved regardless of which side, the front side 16F or the rear side 16R, is facing when it is installed inside the screw body 22.

[0062] The rotating cam body 16 is involved in the feeding mechanism A shown in Figure 5, with the front cam portion 16a being the outer circumferential cam portion 16o and the rear cam portion 16b being the inner circumferential cam portion 16i.

[0063] As shown in Figure 5, the rotating cam body 16 has forward-facing and rear-facing cam portions 16a and 16b formed on its axial front and rear portions, respectively, and a cam portion 18a formed on the front portion of the transmission cam body 18 is arranged opposite to the rear-facing cam portion 16b of the rotating cam body 16.

[0064] As shown in Figure 11, a projection is formed on the inner circumferential surface of the internal through-hole 16c to prevent rotation. This projection 16c1 engages with a flat notch 14c on the outer circumferential surface of the screw shaft 14 (see Figure 13), restricting the relative rotation between the rotating cam body 16 and the screw shaft 14, thereby enabling relative axial forward and backward movement.

[0065] (Transmission cam body 18) As shown in Figure 12, the transmission cam body 18, when in its individual form, has a large diameter in the central part, with slightly smaller diameter front and rear parts extending forward and backward in a cylindrical shape, forming a cam section (18a) with cams formed on the front and rear end surfaces. A pair of projections 18b protrude from the opposing outer circumferential surfaces of the central part. In the central part, a pair of notches 18b1 are formed, penetrating the inner and outer circumferential surfaces, flanking the locations where the projections 18b are formed. In the central part, the portion sandwiched between the notches 18b1 is formed to be elastically deformable.

[0066] In the assembled state, as shown in Figures 5 and 6, the front part of the transmission cam body 18 is slightly narrower in diameter than the central part and is inserted into the cylindrical rear part of the rotating cam body 16, so that the cam portion 18a of the front part of the transmission cam body 18 faces the cam portion 16b.

[0067] The cam portion 18a of the transmission cam body 18 and the rearward-facing cam portion 16b of the rotating cam body 16 are formed in a sawtooth shape so that when they are in contact with each other, they mesh when the transmission cam body 18 rotates in one direction, and conversely, they easily disengage when the transmission cam body 18 rotates in the other direction.

[0068] Specifically, as outlined in Figure 17 described later, the cam portion 18a of the transmission cam body 18 is a sawtooth with multiple triangular peaks inclined in one direction of the slope (e.g., clockwise rotation), and the rearward-facing cam portion 16b of the rotating cam body 16 is a sawtooth with multiple triangular peaks inclined in the other direction of the slope (e.g., counterclockwise rotation).

[0069] The forward-facing cam portion 16a of the rotating cam body 16 and the rearward-facing cam portion 22c within the cylindrical portion 22a of the screw body 22 are formed in a sawtooth shape that allows them to mesh when the rotating cam body 16 rotates in one direction while in contact with each other, and conversely, to easily disengage when the rotating cam body 16 rotates in one direction. Specifically, as schematically shown in Figure 17 described later, the forward-facing cam portion 16a of the rotating cam body 16 has a sawtooth shape with multiple triangular peaks inclined in one direction (e.g., clockwise rotation) on its slope, and the rearward-facing cam portion 22c within the cylindrical portion 22a of the screw body 22 has a sawtooth shape with multiple triangular peaks inclined in the other direction (e.g., counterclockwise rotation) on its slope.

[0070] The feed mechanism 20, which is disposed within the cylindrical portion 22a of the screw body 22, is structured to be movable within a certain range in the axial direction while its relative rotation with respect to the screw body 22 is restricted.

[0071] Specifically, the structure that allows axial movement by restricting relative rotation is, as shown in Figures 5 and 6, formed by a projection 20b on the outer side of an elastically deformable cantilever-shaped arm on the side of the feed body 20, and the projection 20b is fitted back and forth into an axially long window portion 22a1 of the cylindrical portion 22a. In addition, the projection 18b of the transmission cam body 18 fits into the guide groove 20a, and a spring 18c is interposed between the feed body 20 and the transmission cam body 18 to create a resilient structure between them. The spring 18c is preferably a coil spring made of metal or resin.

[0072] In the assembled state, the cam formed on the outer circumference of the rear end of the rotating cam body 16 and the cam formed on the rear end of the transmission cam body 18 are not involved in cam operation.

[0073] (Screw shaft 14) As shown in Figure 13, the screw shaft 14, when viewed from the axial direction, has male threaded portions 14a, 14a formed on its outer circumference in radially opposite arc-shaped portions, with flat notches 14c, 14c formed between the threaded portions 14a, 14a. The screw shaft 14 is also symmetrical in the axial direction, and fitting portions 14b are formed at the front and rear ends to fit into the body 12a of the piston 12 (see Figure 15) and allow it to rotate and prevent it from coming loose. The fitting portions 14b have flange-shaped ribs formed on the outer circumference of cylindrical portions extending from the front and rear ends of the screw shaft 14.

[0074] When attaching the screw shaft 14 to the rotating cam body 16, as shown in Figure 14, the front or rear end of the screw shaft 14 is inserted into the internal through hole 16c of the rotating cam body 16 in the axial direction. During assembly, the flat notch 14c of the screw shaft 14 engages with the projection 16c1 of the rotating cam body 16 upon insertion. Furthermore, since the screw shaft 14 has a front-to-back symmetrical shape, there is no need to consider its front-to-back position during insertion, thus eliminating the need for positioning in the front-to-back direction and simplifying the work.

[0075] (Piston 12) As shown in Figure 15, the piston 12 has a shape that is symmetrical both front to back and axially. The piston 12 has a body 12a with a hole into which the fitting portion 14b of the screw shaft 14 (see Figure 13) is fitted, and a sealing portion 12b that encloses the body 12a and is widened in diameter front to back. Inside the hole of the body 12a, there is a protrusion and recess that engages with the fitting portion 14b so that it can rotate and its front to back movement is restricted. In addition, the sealing portion 12b slides against the inner surface of the shaft cylinder 10 to make the housing portion 10b liquid-tight (see Figure 3).

[0076] (Seal fitting 36) As a standalone component, the seal joint 36 has a narrow diameter portion 36b inside for receiving the seal ball 36a (see Figure 1), as shown in Figure 16, and a protrusion 36c extending to the rear to prevent the agitator 10d or the seal ball 36a from blocking the seal joint 36. The front end has an enlarged flange portion 36d. The flange portion 36d abuts against the end face of the front end 10a of the shaft cylinder 10 to restrict it from sliding into the front end 10a (see Figure 1).

[0077] Next, the dispensing operation (knock operation) of the applicator in the above-described embodiment will be explained with reference to Figures 2, 3, and 17-18.

[0078] Figure 2 shows the applicator in its non-knocked state (original position), and Figure 3 shows the state when knocked. In the dispensing mechanism A, Figure 5 shows the non-knocked state, and Figure 6 shows the knocked state. Figures 17 and 18 are schematic diagrams illustrating the operation of the screw body 22, rotating cam body 16, transmission cam body 18, and dispensing body 20 in the dispensing mechanism. Figure 17(a) shows an explanatory diagram of each part, (b) shows the initial state, and (c) shows the state at the start of knocking. Figure 18(a) shows the state when knocking is completed, (b) shows the state when knocking is released and the device begins to return, and (c) shows the initial state when the knock is fully returned.

[0079] In a knock-type applicator, the user advances the dispensing body 20 by knocking the outer circumference of the rear end surface of the dispensing body 20, as shown in Figure 3.

[0080] As shown in Figure 17(a), during the feeding operation, the guide groove 20a and the projection 18b on the side of the transmission cam body 18 convert the forward movement into a rotational movement of the transmission cam body 18 (unidirectional: indicated by the symbol F). The rotation angle 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 the symbol L.

[0081] The rotation of the transmission cam body 18 causes the rotating cam body 16 to rotate in one direction, advancing the screw shaft 14 and thus advancing the piston 12. On the other hand, when the pressure is released, the feed body 20 returns to the rear, and the transmission cam body 18 rotates in the other direction and returns to its original position.

[0082] More specifically, as shown in Figures 17(b) to 17(c) and 18(a), when the dispensing body 20 is pressed forward, it moves forward against the elastic force of the spring 18c (see Figure 3). This causes the projection 18b to slide along the guide groove 20a, and the transmission cam body 18 rotates in one direction (direction of arrow F). As shown in Figures 17(b) to 17(c), this 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 rotating cam body 16, which are in contact with each other, to mesh, and the rotating cam body 16 begins to rotate.

[0083] From Figure 17(c) onward, the projection 18b slides backward along the guide groove 20a until the feed body 20 reaches the bottom dead center, and as the rotating cam body 16 rotates, the teeth of the forward-facing cam portion 16a of the rotating cam body 16 advance by one pitch or more and overcome the teeth of the rearward-facing cam portion 22c inside the cylindrical portion 22a, and as shown in Figure 18(a), when it reaches the bottom dead center, it engages with the teeth of the next pitch.

[0084] As shown in Figures 17(b)-(c) and 18(a), the knocking operation of the dispensing body 20 is transmitted from the rotation of the transmission cam body 18 to the rotation of the rotating cam body 16. This rotation of the rotating cam body 16 causes the screw shaft 14 (not shown) to rotate, and it moves forward due to the action of the female threads (female screw threads) 22b2 of the screw portion 22b. This forward movement of the screw shaft 14 causes the piston 12 to move forward within the housing 10b and dispense the coating liquid toward the coating body 24.

[0085] On the other hand, when the pressing operation of the dispensing body 20 is released, as shown in order in Figures 18(a) to (c), the dispensing body 20 moves backward due to the elastic force of the spring 18c, causing the projection 18b to slide forward along the guide groove 20a, and the transmission cam body 18 rotates in the opposite direction (opposite to F). The teeth of the forward-facing cam portion of the rotating cam body 16 and the teeth of the rearward-facing cam portion in the cylindrical portion 22a of the screw body 22 mesh together, restricting the rotation of the rotating cam body 16, so that only the transmission cam body 18 rotates (see Figures 18(b) to (c)).

[0086] Then, the teeth of the cam portions 18a and 16b of the transmission cam body 18 and the rotating cam body 16 that are in contact with each other disengage, and after advancing more than one pitch, the tooth moves over and engages with the tooth of the next pitch. As a result, the rotation of the transmission cam body 18 in the other direction is not transmitted to the rotating cam body 16, and the tooth of the rotating cam body 16 engages with the tooth one pitch away. In this case, the initial state of moving back one pitch is returned as shown in Figure 18(c).

[0087] As an example of a knock mechanism, the knock stroke is set to 2 mm. When the user knocks the lever to extend it, the lever body 20 advances 1 mm for every 1 mm knock, causing the projection 18b of the transmission cam body 18 to move (rotate) along the guide groove 20a that is diagonally opened in the lever body 20. When the knock reaches 2 mm, the lever reaches its limit and the projection 18b of the transmission cam body 18 completes its rotation. During this time, the rotating cam body 16 rotates (see Figures 17(b)~(c) and 18(a)).

[0088] When the knocking operation is released, the extension body 20 returns to the rear and the projection 18b of the transmission cam body 18 rotates in the opposite direction along the guide groove 20a. However, the engagement between the cam of the transmission cam body 18 and the cam of the rotating cam body 16 is released, causing only the transmission cam body 18 to rotate in the opposite direction, while the rotating cam body 16 does not rotate (Figures 18(a) to (c)).

[0089] Let's consider the conditions for the rotation angle θ mentioned above. When the extension body 20 is knocked by a knock stroke L, the transmission cam body 18 rotates by an angle θ. If B is the rotation angle of one tooth between the transmission cam body 18 and the rotating cam body 16 (rear cam portion 16b), then the relationship "θ > B" is required.

[0090] In other words, if the rotation angle θ is greater than the rotation angle B of one peak, it will not be able to overcome the peak of the cam.

[0091] Furthermore, if we define C as the angle at which the forward-facing cam portion 16a of the rotating cam body 16 advances past the cam portion 22c of the screw body 22 when the knock is completed, and similarly, if we define A as the angle at which the rotating cam body 16 advances further after overcoming the transmission cam body 18 when the knock is returned to its original position, Since θ = A + B + C, we can set "θ > B" by appropriately adjusting A and C to account for the extra rotations.

[0092] If A or C is too small (too little), the parts may not be able to overcome the cam due to tolerances and variations in the components, and if it is too large, the knock stroke must be increased unnecessarily, which is inefficient.

[0093] Considering one embodiment, if the cams are equally spaced at 12 degrees, then B = 360 / 12 = 30 degrees. If A and C are set to 7.05 degrees, then the rotation angle due to knocking becomes θ = 30 + 7.05 + 7.05 = 44.1 degrees. In other words, the rotation angle due to knocking is 44.1 degrees.

[0094] In the knock-type dispenser of this embodiment, the guide groove 20a of the dispensing body 20 is formed at an angle with respect to the axial direction, and when the dispensing body 20 is advanced by the knock operation, the guide groove 20a and the projection 18b convert the advancement motion into a rotational motion of the transmission cam body 18 in one direction, the cam portion of the transmission cam body 18 engages with the rear cam portion of the rotating cam body 16, and the rotation of the transmission cam body 18 rotates the rotating cam body 16, causing the piston 12 to advance as the screw shaft 14 moves forward, while when the knock operation is released, the spring 18c's elastic force pushes the dispensing body forward. When the dispensing body 20 is retracted, the guide groove 20a and projection 18b convert the retraction motion into rotational motion in the other direction of the transmission cam body 18, returning it to its original position. Furthermore, the cam portion at the front of the rotating cam body 16 engages with the cam portion of the cylindrical portion 22a, restricting the rotational operation of the rotating cam body 16 and thereby restricting the operation of the screw shaft 14 and the piston 12. As a result, the force applied when the dispensing body 20 is knocked can be transmitted to the pressing force of the piston 12 without any loss of force, and when dispensing high-viscosity contents, the operation can be made even lighter while preventing loss of knocking force.

[0095] In addition, since a cylindrical portion 22a with a rearward-facing cam portion 22c integrally formed inside is provided on the screw body 22, the number of parts can be reduced and manufacturing can be simplified compared to a design where the cam portion is provided separately.

[0096] Furthermore, when the dispensing body 20 is pressed forward, the projection 18b slides along the guide groove 20a, causing the transmission cam body 18 to rotate in one direction. The opposing cam portions of the transmission cam body 18 and the rotating cam body 16 engage with each other, and the engagement between the forward-facing cam portion of the rotating cam body 16 and the rearward-facing cam portion in the cylindrical portion 22a disengages, transmitting the rotation to the rotating cam body 16. This rotation of the rotating cam body 16 causes the screw shaft 14 to rotate, and it moves forward due to the action of the female thread of the screw portion 22b. When the pressing operation of the dispensing body 20 is released, the dispensing body 20 moves backward due to the elastic force of the spring 18c, causing the projection 18b to slide along the guide groove 20a, and the transmission cam body 18 to rotate in the other direction. This disengages the cam portions of the transmission cam body 18 and the rotating cam body 16 that are in contact with each other, and the forward-facing cam portion of the rotating cam body 16 and the rearward-facing cam portion in the cylindrical portion 22a of the screw body 22 engage, preventing the rotation of the transmission cam body 18 in the other direction from being transmitted to the rotating cam body 16. By repeatedly performing the above pressing operation of the dispensing body 20, the piston 12 can be smoothly pushed out.

[0097] Furthermore, if the pitch of the teeth of the rearward-facing cam portion of the transmission cam body 18 and the rotating cam body 16 is the same as that of the forward-facing cam portion of the rotating cam body 16 and the rearward-facing cam portion within the cylindrical portion 22a of the screw body 22, and if the teeth of the rearward-facing cam portion and the forward-facing cam portion of the rotating cam body 16 are formed with a phase difference, then the cam teeth of the rotating cam body 16 are engaged with the cam teeth of the cylindrical portion 22a before the knocking operation of the dispensing body 20, and when the knocking operation of the dispensing body 20 is performed, the cam portion of the transmission cam body 18 is out of phase with the rearward-facing teeth of the rotating cam body 16, so the transmission cam body 18 rotates as the dispensing body 20 moves forward. Then, when the knocking of the dispensing body 20 is released, the cam portions of the rotating cam body 16 and the cylindrical portion 22a reliably mesh with each other, and the rotation of the rotating cam body 16 can be reliably prevented from rotating in the reverse direction.

[0098] Furthermore, if a ring-shaped sealing body (an elastic material such as rubber or elastomer) is positioned circumferentially between the outer circumference of the dispensing body 20 and the inner circumference of the cylindrical portion 22a of the screw body 22, the ring-shaped sealing body can ensure airtightness from the dispensing body 20 to the rear, thereby reliably preventing drying and deterioration of the contents.

[0099] In the applicator of this embodiment, as shown in Figure 3, a front shaft 26 is provided at the front end 10a of the shaft 10, covering the periphery of the applicator 24. A main fitting portion and a temporary fitting portion are formed on both the front shaft 26 and the shaft 10. The front shaft 26 and the shaft 10 each have anti-rotation ribs (reference numeral 46 in Figure 19, reference numeral 38 in Figure 20). In the initial fitting state where the temporary fitting portions of the shaft 10 and the front shaft 26 engage with each other (see Figure 23), the anti-rotation ribs do not engage with each other. On the other hand, in the main fitting state where the main fitting portions engage with each other (see Figure 22), the anti-rotation ribs engage with each other.

[0100] The final fitting and temporary fitting will be explained using the parts diagram of the shaft cylinder 10 in Figure 19 and the parts diagram of the front shaft 26 in Figure 20.

[0101] (Shaft tube 10) Let's explain the shaft cylinder 10.

[0102] As shown in Figure 19, the shaft cylinder 10 is generally cylindrical. The front end 10a of the shaft cylinder 10 is located in front of the main body where the housing portion 10b is located, and is formed with a smaller diameter than the main body. As shown in Figure 19(c), two spaced ribs (front main fitting portion 42F and rear main fitting portion 42R) are formed around the outer circumference of the front end 10a as the main fitting portion 42.

[0103] In the main fitting portion 42, the rib of the main fitting portion 42F on the coating side, i.e., the front side, is a temporary fitting portion 44 with a stepped diameter at its front. Specifically, at the front end portion 10a of the shaft cylinder 10, the outer diameter in front of the main fitting portion 42F is formed to be smaller than the outer diameter at the rear, creating a step that is nearly perpendicular, and the step at the front of the main fitting portion 42F becomes the step of the temporary fitting portion 44.

[0104] A rattle prevention portion 50 is formed on the outer circumferential surface of the front end portion 10a of the shaft cylinder 10, which supports the front shaft radially from the inside during temporary fitting. Specifically, a rattle prevention portion 50 consisting of ribs for temporary fitting is formed between the front main fitting portion 42F and the rear main fitting portion 42R along the axial direction.

[0105] Furthermore, the outer diameters of the front main fitting portion 42F and the rear main fitting portion 42R are different. A rotation-preventing rib 46 is formed in front of the temporary fitting portion 44 to prevent the front shaft 26 from rotating relative to the shaft cylinder 10.

[0106] As shown in Figure 19, the shaft cylinder 10 has a reduced diameter at its front end 10a, but a recessed and stepped fitting portion 10e is formed on the inner circumferential surface of the rear end. In addition, a longitudinal rib 10f is formed slightly towards the rear of the central part, protruding inward and extending in the axial direction.

[0107] When attaching the screw body 22 (see Figure 1) to the shaft cylinder 10, the screw body 22 is inserted forward from the rear end of the opening of the shaft cylinder 10, and then advanced and fitted into the vertical rib 10f while attaching the outer circumference of the screw body 22.

[0108] A cylindrical extension body 20 with a closed rear end is fitted into a fitting portion 10e on which a screw body 22 is mounted with its rotation restricted, and the rear end of the extension body 20 is exposed from the rear end of the shaft cylinder 10 (see Figure 1).

[0109] (front axis 26) Figure 20 is a component diagram of the front shaft 26.

[0110] As shown in Figure 20, the front shaft 26 has a roughly cone shape, tapering towards the front than towards the rear. The inner circumference of the front shaft 26 has a stepped rear end side surface of the front rib 54, which is a temporary fitting part for temporary fitting with the temporary fitting part 44 (see Figure 19) of the front end 10a of the shaft cylinder 10, and the front rib 54 and rear rib 56, which are formed to permanently fit with the main fitting parts 42 (42F, 42R) (see Figure 19) of the front end 10a, are formed over almost the entire circumference. The formation of the front rib 54 and rear rib 56 over almost the entire circumference improves the temporary pull-out force between the front shaft 26 and the shaft cylinder 10 in the initial fitting state, and prevents the front shaft 26 from falling out of the shaft cylinder 10 during transport, etc.

[0111] The front rib 54 and rear rib 56 have a roughly trapezoidal cross-sectional shape along the axial direction. However, the cross-sectional shape of ribs 54 and 56 is not limited to a trapezoidal shape with sharp corners; it may also have chamfered corners or an arc shape.

[0112] In the front shaft 26, the inner circumference of the leading portion is formed in a cylindrical shape to accommodate the coated body 24, and an engagement step portion 26a for fitting the pipe joint 30 is formed on the inner circumference of the central portion. In addition, an annular grooved portion 26b is formed on the outer surface of the front shaft 26 for fitting and fixing the cap 28.

[0113] The part of the front shaft 26 in front of the engagement step portion 26a is the rear inner circumference, and multiple rotation-preventing ribs 38 with vertical grooves for preventing rotation are formed on the inside of the uneven portion 26b.

[0114] On the inner circumference of the front shaft 26, a stepped locking portion 26c is formed in front of the engaging step portion 26a, against which the flange 24a of the coating body 24 abuts. Triangular grooves are formed on both sides of the step in the locking portion 26c. The grooves guide the bristles of the brush head when the coating body 24 is attached, thereby preventing the brush head from turning inside out (facing the wrong way).

[0115] When the applicator of the embodiment is used from an unused state, it enters the initial fitting state shown in Figure 21, the full fitting state shown in Figure 22, and the slightly pushed-in temporary fitting state shown in Figure 22.

[0116] When unused, the applicator maintains an initial fitted state in which it is temporarily fitted to the shaft 10 by holding the front shaft 26 via the stopper ring 34 (see Figure 1).

[0117] To begin use, the user first removes the stopper ring 34 and leaves the front shaft 26 in an unpushed position (initial fitting state) relative to the shaft cylinder 10. In this case, as shown in Figure 21, the front rib 54 of the front shaft 26 is in contact with or positioned in front of the temporary fitting portion 44 of the shaft cylinder 10, and the rear rib 56 is positioned between the front and rear main fitting portions 42 (main fitting portions 42F, 42R). The seal ball 36a is fitted into the seal joint 36. The anti-rotation rib 38 of the front shaft 26 is not engaged with the anti-rotation rib 46 of the shaft cylinder 10. Therefore, the front shaft 26 can rotate freely relative to the shaft cylinder 10. The rear rib 56 of the front shaft 26 is positioned recessed between the front and rear main fitting portions 42 (main fitting portions 42F and 42R), but the anti-loosening portion 50, which consists of a rib for preventing looseness between the main fitting portions 42F and 42R, supports the rear rib 56 of the front shaft 26, thereby preventing looseness of the front shaft 26.

[0118] When preparing for use, the front shaft 26 is pushed slightly into the shaft cylinder 10 from the initial fitted state to the temporary fitted state shown in Figure 23. In this case as well, the front rib 54 of the front shaft 26 abuts against the temporary fitting portion 44 of the shaft cylinder 10 to position it. The anti-play portion 50 supports the rear rib of the front shaft 26 to prevent play. In this state, the anti-rotation rib 38 of the front shaft 26 is inserted into and engages with the anti-rotation rib 46 of the shaft cylinder 10, thereby preventing the front shaft 26 and the shaft cylinder 10 from rotating.

[0119] Then, when the front shaft 26 is pushed in from the temporary fitting state shown in Figure 23, the front rib 54 moves over the front main fitting portion 42F from the temporary fitting portion 44 and engages with the main fitting portion 42F. Also, the rear rib 56 moves over the main fitting portion 42R and engages. This results in the main fitting state shown in Figure 22. The front shaft 26 moves axially by approximately the length of the stopper ring 34 and enters the main fitting state where it is directly fitted into the shaft cylinder 10. At the same time, the anti-rotation rib 38 of the front shaft 26 is fully inserted into the anti-rotation rib 46 of the shaft cylinder 10, making the anti-rotation of the shaft cylinder 10 relative to the front shaft 26 more secure.

[0120] In the applicator of this embodiment, the shaft 10 has a main fitting portion 42 (42F, 42R) and a temporary fitting portion 44 formed thereon. The inner circumference of the front shaft 26 has a front rib 54 for temporary fitting with the temporary fitting portion 44 of the front end portion 10a of the shaft 10, and a front rib 54 and a rear rib 56 that fully fit with the main fitting portion 42 (42F, 42R) of the front end portion 10a, extending almost the entire circumference. The shaft 10 has an anti-rotation rib 46, and the front shaft 26 has an anti-rotation rib 38.

[0121] As shown in Figure 21, in the initial fitting state before the shaft cylinder 10 and the front shaft 26 are temporarily fitted (before the temporary fitting portion 44 and the front rib 54 engage with each other), the anti-rotation ribs 46 and 38 do not engage with each other. Relative rotation is possible.

[0122] On the other hand, as shown in Figure 23, in the temporary fitting state (when the temporary fitting portion 44 and the front rib 54 engage with each other), the anti-rotation ribs 46 and 38 engage with each other, creating an anti-rotation state.

[0123] Furthermore, as shown in Figure 22, the front shaft 26 and the shaft cylinder 10 are connected when the main fitting state is reached (main fitting portion 42 (42F, 42R) and the front rib 54 and rear rib 56 are together), making it usable.

[0124] Therefore, if the user removes the front shaft 26 in addition to the stopper ring 34 when starting use, the anti-rotation ribs 46 and 38 will engage with each other when the front shaft 26 is reattached and the fitting is completed, so it can be press-fitted without misalignment. Thus, leakage due to insufficient press-fitting can be prevented.

[0125] Furthermore, the anti-rotation ribs 46 of the shaft 10 and the anti-rotation ribs 38 of the front shaft 26 engage with each other, preventing the shaft 10 and the front shaft 26 from rotating. This prevents the brush tip or the applicator 24, which is made up of bundled fibers, from twisting when the user rotates the front shaft 26.

[0126] Furthermore, the temporary pull-out force in the initial fitted state (the pull-out force when the stopper ring 34 is present) can be increased, which prevents the front shaft 26 from falling out of the shaft cylinder 10 during transport or other situations. [Industrial applicability]

[0127] The applicator of the present invention can be used as an applicator for cosmetic products and other cosmetic products. [Explanation of Symbols]

[0128] 10 shaft cylinder 10a Front end 10b Storage area 10c Step section 10d stirring body 10e Fitting part 10f vertical rib 12 pistons 12a Main Unit 12b Seal section 14 Screw shaft 14a Threaded part 14b Fitting part 14c Notch 16 Rotating cam body 16a Cam section 16b Cam section 16c Internal through hole 16c1 protrusion 18 Transmission cam body 18a Cam section 18b Protrusion 18c spring 20 Distributing Units 20a Guide groove 20b protrusion 20b1 Arm 20c induction section 20c1 Stepped section 20d guide protrusion 20e 2nd protrusion 20f stepped section 22 Screw body 22a Cylindrical part 22a1 Window section 22a2 Rib 22a3 Thin wall part (slanted surface) 22a31 Step 22b Screw part 22d flange 22e unevenness 22f guide groove 24 Coating 24a flange 26 Tip axis 28 caps 30 Pipe Fittings 32 pipes 34 Stopper Rings 36 Seal fittings 36a Seal Ball 36b Narrow diameter part 36c protrusion 36d Flange section 38. Anti-rotation rib for shaft cylinder 42 main fitting section 44 Temporary fitting section 46. ​​Anti-rotation rib for the front shaft 50 Anti-vibration part 54 Front Rib 56 Rear rib A. Feed mechanism

Claims

1. An applicator comprising a shaft having a storage section for storing an applicating liquid, wherein the applicating liquid stored in the storage section is supplied to an applicator, A tip shaft is provided at the front end of the barrel, covering the area around the coating body. The front shaft and the shaft barrel each have a main fitting portion and a temporary fitting portion formed therein. The aforementioned front shaft and shaft cylinder each have anti-rotation ribs, An applicator characterized in that, in the initial fitting state in which the temporary fitting portions of the shaft cylinder and the front shaft engage with each other, the respective anti-rotation ribs do not engage with each other, while in the final fitting state in which the main fitting portions engage with each other, the respective anti-rotation ribs engage with each other.

2. The applicator according to Claim 1, characterized in that the shaft contains at least (a) 5 to 40% by weight of hydrofluoroether, (b) 20 to 60% by weight of low-boiling point silicone oil, (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 cross-linked methylpolysiloxane, inulin stearate, and sucrose fatty acid ester, and (e) 10 to 40% by weight of powder, and the viscosity at 25°C and shear rate of 191.5 / s is less than 400 mPa·s and the average initial evaporation rate up to 1 minute immediately after application by the filter paper method is 0.15 to 2.00 mg / sec.

3. The applicator according to Claim 1, characterized in that the shaft contains at least (a) 20 to 75% by weight of isododecane, (b) 2 to 25% by weight of one or more of trimethylsiloxiliate, alkyl acrylate, or alkyl acrylate copolymer, and (c) 2 to 25% by weight of one or more of powders selected from carbon black, iron oxide, and Prussian blue, and the applicator contains a liquid oily cosmetic having a viscosity of less than 400 mPa·s at 25°C and a shear rate of 191.5 / s, and an average initial evaporation rate up to 1 minute immediately after application by the filter paper method of 0.15 to 2.00 mg / sec.

4. The applicator according to claim 1, wherein a stopper ring for maintaining an unused state is interposed in the shaft, a cylindrical seal fitting is fitted inside the shaft, and the seal fitting is formed with a protrusion extending to the rear.

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