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 dispenses liquid contents, such as cosmetic liquid, correction fluid, or ink for writing brushes, by a knock operation and supplies the contents to an applicator body. [Background technology]

[0002] Conventionally, there has been proposed a knock-type applicator that converts a knock operation into a rotational motion to dispense an application liquid (see Patent Document 1).

[0003] This applicator has a cam surface on the end face of the cylindrical rotating body, so there is a limit to the force required for dispensing the application liquid. When the application liquid is oil-based, the viscosity is high, so the applicator of Patent Document 1 is not suitable for dispensing the application liquid.

[0004] In response to this, Patent Document 2 proposes an applicator that can increase the propelling force by using guide grooves and protrusions. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] JP 2009-254419 A [Patent Document 2] JP 2011-194820 A Summary of the Invention [Problem to be solved by the invention]

[0006] Because applicators have multiple shaft-shaped parts, a process of aligning the front and rear of the shaft-shaped parts is required during manufacturing of the applicator, which creates a workload, but no technology has yet been proposed to reduce this type of workload.

[0007] In view of the above circumstances, the present invention provides an applicator that can be easily assembled during manufacturing. [Means for solving the problem]

[0008] The present invention relates to an applicator comprising a storage section for storing an application liquid, a piston that slides within the storage section, a screw shaft having a thread formed on its circumferential surface, an advancing body for an advancing operation, a rotating cam body, and a transmission cam body, a screw portion that screws onto the screw shaft is provided at the rear of the storage section, and an advancing operation on the advancing body rotates the rotating cam body to rotate the screw shaft and the screw portion relatively to each other to advance the screw shaft, and the piston is advanced by the screw shaft to supply application liquid stored in the storage section to the applicator body, At least one of the screw shaft, the rotating cam body, and the transmission cam body is formed in a front-to-rear symmetrical shape.

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

[0010] In the present invention, it is preferable that the threaded portion is formed and that the inner surface of the threaded body that houses the rotating cam body, the transmission cam body, and the payout body is formed with an inclined surface that increases in diameter from the rear to the front.

[0011] In the present invention, it is preferable that a tip barrel is provided at the front end of the barrel so as to cover the periphery of the applicator, and that a permanent fitting portion and a temporary fitting portion are formed on each of the tip barrel and the barrel, and that the tip barrel and the barrel have their own anti-rotation ribs, and that in an initial fitted state in which the temporary fitting portions of the barrel and the tip barrel engage with each other, the respective anti-rotation ribs do not engage with each other, and conversely, in a permanent fitted state in which the permanent fitting portions engage with each other, the respective anti-rotation ribs 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 regulated, the transmission cam body rotates when the feeding body is fed, a screw body having a threaded portion that screws onto the screw shaft is provided behind the storage section, and the feeding body is operated to rotate the rotating cam body, thereby advancing a piston and supplying the coating liquid contained in the storage section to the coating body. Effect of the Invention

[0013] According to the applicator of the present invention, at least one of the screw shaft, the rotating cam body, and the transmission cam body is formed to be symmetrical in the front-to-rear direction, so that front-to-rear alignment can be omitted, resulting in the excellent effect of improving assembly during manufacturing. [Brief description of the drawings]

[0014] [Figure 1] 1A and 1B are overall views of an applicator according to an embodiment of the present invention with a cap attached, in which (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 sectional view taken along line DD in (b). [Diagram 2] 2A and 2B are overall views of the applicator in FIG. 1 at the start of use, where (a) is a front view from one direction, and (b) is a vertical cross-sectional view. [Diagram 3] 2A and 2B are overall views of the applicator of FIG. 1 in a knock-pressed state during use, in which (a) is a front view from one direction, and (b) is a vertical cross-sectional view. [Figure 4] 2A and 2B are overall views of the applicator of FIG. 1 during and after use, in which (a) is a front view from one direction, and (b) is a vertical cross-sectional view. [Diagram 5] 2A and 2B are component diagrams of the propelling mechanism in the applicator of FIG. 1, where (a) is a perspective view, (b) is a front view, (c) is a longitudinal sectional view taken along line CC in (d), (d) is a front view rotated 90 degrees from (b), and (e) is a longitudinal sectional view taken along line EE in (b). [Figure 6] 6A and 6B are component diagrams of the extension mechanism in a knocking state in FIG. 5, in which (a) is a perspective view, (b) is a front view, (c) is a longitudinal sectional view taken along line CC in (d), (d) is a front view rotated 90 degrees from (b), and (e) is a longitudinal sectional view taken along line EE in (b). [Figure 7] 6A and 6B are part diagrams showing the state in which the screw body is removed from the feed mechanism in FIG. 5, in which (a) is a perspective view, (b) is a front view, (c) is a longitudinal sectional view taken along line CC in (d), (d) is a front view rotated 90 degrees from (b), and (e) is a longitudinal sectional view taken along line EE in (b). [Figure 8] 8A and 8B are part drawings showing a knocking state (pressing state) in a state in which the screw body is removed from the feed mechanism in FIG. 7, in which (a) is a perspective view, (b) is a front view, (c) is a longitudinal sectional view taken along line CC in (d), (d) is a front view rotated 90 degrees from (b), and (e) is a longitudinal sectional view taken along line EE in (b). [Figure 9] FIG. 2 is a parts diagram of the screw body in the applicator of FIG. 1, where (a) is a front view, (b) is a front view, (c) is a longitudinal sectional view taken along line CC in (d), (d) is a front view rotated 90 degrees from (b), (e) is a longitudinal sectional view taken along line EE in (b), (f) is a perspective view taken from the rear, and (g) is a view taken from the rear. [Figure 10] FIG. 2 is a component diagram of the propellant in the applicator of FIG. 1, in which (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 line DD in (e), (e) is a front view rotated 90 degrees from (c), (f) is a longitudinal sectional view taken along line FF in (c), (g) is a perspective view, and (h) is a view from the rear. [Figure 11] 2A and 2B are part diagrams of a rotating cam body in the applicator of FIG. 1, where (a) is a perspective view, (b) is a front view, (c) is a longitudinal sectional view along line CC of (e), (d) is a longitudinal sectional view along line DD of (e), and (e) is a view from one direction. [Figure 12] 2A and 2B are component diagrams of a transmission cam body in the applicator of FIG. 1, in which (a) is a view from one direction, (b) is a perspective view, (c) is a front view, (d) is a front view rotated 90 degrees from (c), (e) is a longitudinal sectional view along line EE of (c), and (f) is a view from another direction. [Figure 13] 2A to 2D are part diagrams of the 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 behind. [Figure 14] FIG. 2 is a perspective view of a part diagram of the applicator in FIG. 1, in which a screw shaft is oriented axially toward a rotating cam body. [Figure 15]2A to 2D are part diagrams of a 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 line CC in (b), and (d) is a view seen from behind. [Figure 16] FIG. 2 is a parts diagram of a joint (seal ball receiver) in the applicator of FIG. 1, in which (a) is a perspective view from the front, (b) is a view from the front, (c) is a front view (view) from direction C of (a), (d) is a side view rotated 90 degrees from (c), (e) is a vertical cross-sectional view along line EE of (b), (f) is a perspective view from the rear, and (g) is a view from the rear. [Figure 17] 2A and 2B are schematic diagrams illustrating the screw body, the rotating cam body, the transmission cam body, and the propelling body, which explain the cam operation in the applicator of FIG. 1, in which (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 knocking. [Figure 18] Like Figure 17, these are schematic diagrams explaining the operation, with (a) showing the state when the knock has been completed, (b) showing the state when the knock has been released and the ball has started to return, and (c) showing the initial state when the knock has been completely released. [Figure 19] 2A and 2B are part diagrams of the barrel of the applicator of FIG. 1, in which (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 sectional view taken along line EE of (b), (f) is a front view rotated 90 degrees from (d), and (g) is a longitudinal sectional view taken along line GG of (b). [Figure 20] 2A and 2B are component diagrams of the tip barrel of the applicator of FIG. 1, in which (a) is a front view, (b) is a perspective view from the front, (c) is a front view, (d) is a longitudinal sectional view along line DD in (a), (e) is a rear view, and (f) is a rear perspective view. [Figure 21] 2A and 2B are explanatory diagrams of the applicator in FIG. 1 in a state in which the stopper ring has been removed from the applicator (preparatory state for use) and the applicator is in an initial fitting state, where (a) is a front view, (b) is a longitudinal sectional view of the front part, (c) is a sectional view along line CC in (b), and (d) is an enlarged explanatory view of part D in (b). [Figure 22]22A and 22B are explanatory diagrams showing the applicator in FIG. 21 in a state where the tip barrel is fully fitted into the barrel tube, where (a) is a front view, (b) is a longitudinal cross-sectional view of the front part, (c) is a cross-sectional view along line CC of (b), and (d) is an enlarged explanatory view of portion D of (b). [Figure 23] 22A and 22B are explanatory diagrams showing the applicator in FIG. 21 in a provisionally fitted state between the tip barrel and the barrel tube, where (a) is a front view, (b) is a longitudinal cross-sectional view of the front part, (c) is a cross-sectional view along line CC in (b), and (d) is an enlarged explanatory view of portion D in (b). DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0015] Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

[0016] Figure 1 shows the applicator in an unused state, Figure 2 at the start of use, Figure 3 in the pressed knock state, and Figure 4 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 application liquid, a piston 12 that slides within the storage section 10b, and a screw shaft 14 having a male screw portion 14a formed on its circumferential surface, which are provided within a barrel 10; an advancement body 20 for advancing the application liquid; 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 by an advancement operation on the advancement body 20; and a screw body 22 having a screw portion 22b that screws onto the screw shaft 14, which is provided at the rear of the storage section 10b; and the advancing body 20 is operated to rotate the rotating cam body 16 and advance the piston 12 to supply the application liquid stored in the storage section 10b to the applicator body 24. In this applicator, the screw shaft 14, the rotating cam body 16, and the transmission cam body 18 (at least one example of them) contained within the screw body 22 are formed in a front-to-rear symmetrical shape.

[0018] In the applicator, a feeding 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 feeding body 20 is disposed within a barrel 10.

[0019] When the applicator is not in use, the cap 28 and stopper ring 34 are attached, and the stopper ring 34 is in a state in which the front barrel 26 is positioned forward and the seal ball 36a is fitted in, as shown in Fig. 1. At the start of use, the stopper ring 34 is removed and the seal ball 36a falls into the storage section 10b, as shown in Fig. 2, and when knocking, the piston 12 is pushed by the propelling body 20 as shown in Fig. 3, and when use is finished, the piston 12 is located at the front end of the storage section 10b, as shown in Fig. 4.

[0020] Figures 5 and 6 are component diagrams of the feeding mechanism A, with Figure 5 showing the non-knocking state and Figure 6 showing the knocking 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-knocking state and Figure 8 showing the knocking state. Figure 9 shows the screw body 22, Figure 10 shows the feeding body 20, Figure 11 shows the rotating cam body 16, Figure 12 shows the transmission cam body 18, Figure 13 shows the screw shaft 14, Figure 14 shows the state in which the screw shaft 14 is axially oriented to the rotating cam body 16, Figure 15 shows the piston 12, and Figure 16 shows the joint 36.

[0021] (Extraction mechanism A) As shown in Figs. 5 and 6, the payout 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 at the front and rear, respectively, a transmission cam body 18 which has a cam portion 18a formed at the front for meshing with the cam portion 16b at the rear of the rotating cam body 16 and has a protrusion 18b formed at the side surface, and a guide groove 20a which guides the protrusion 18b of the transmission cam body 18, and which moves forward and backward via the guide groove 20a and the protrusion 18b. the screw shaft 14 and the feed body 20. The feed body 20 rotates the transmission cam body 18 by means of a spring 18c which urges the feed body 20 backward and the transmission cam body 18 forward. The feed body 20, the rotating cam body 16, the spring 18c, the screw shaft 14, and the feed body 20 are built in, and the screw body 22 (corresponding to a "fixed cam body") has a cylindrical portion 22a at its rear with a rearward-facing cam portion 22c integrally formed therein, and a screw portion 22b at its front which screws into the screw shaft 14.

[0022] In addition to the above configuration, the screw body 22, rotating cam body 16, and screw shaft 14 may have an extension mechanism in which the screw portion of the screw body 22 is made into an irregular hole to match the cross section of the screw shaft 14 and regulate the relative rotation with the screw shaft 14, and a female screw portion is formed on the inner circumference of the rotating cam body 16 and the screw portion is screwed into a male screw on the outer peripheral surface of the screw shaft 14.

[0023] The guide groove 20a of the propelling body 20 is formed at an angle to the axial direction (the front-rear direction of the applicator).

[0024] In the above-mentioned knock type applicator, when the propelling body 20 is advanced by a knock operation with respect to the propelling mechanism A, the advancing motion is converted into a rotational motion of the transmission cam body 18 in one direction (in this embodiment, a right rotation direction toward the front of the shaft) by the guide groove 20a and the protrusion 18b, and the cam portion 18a of the transmission cam body 18 engages with the cam portion 16b at the rear of the rotating cam body 16, and the rotation of the transmission cam body 18 rotates the rotating cam body 16, and the piston 12 advances with the advancement of the screw shaft 14, and one On the other hand, when the knock operation is released and the extension body 20 is retracted by the elastic force of the spring 18c, the guide groove 20a and the protrusion 18b convert this retraction motion into a rotational motion of the transmission cam body 18 in the other direction (in this embodiment, the axial forward left rotation direction) and return it to its original position, and 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 restricting the operation of the screw shaft 14 and piston 12.

[0025] (Applicator 24) 1 to 3, in the applicator, applicator body 24 is attached to front end 10a of barrel tube (rear barrel) 10 by front barrel 26. Applicator body 24 is not particularly specified as long as it is made of a material such as a resin fiber bundle or a porous body that can be impregnated with the application liquid and applied, but in the embodiment, the rear end is bundled by melting to present a flange shape.

[0026] (Coating solution) The application liquid contained in the storage portion 10b of the barrel 10 is a cosmetic liquid, ink for writing instruments, or a chemical solution, and this makes it easy to dispense the cosmetic liquid, especially one with a high viscosity (preferably a viscosity of 300 mPa·s or more).

[0027] In an embodiment, a liquid oil-based cosmetic can be stored in the storage section 10b and used. A suitable liquid oil-based cosmetic in this embodiment contains at least (a) 5 to 40 weight % of hydrofluoroether, (b) 20 to 60 weight % of low boiling point silicone oil, (c) 2 to 10 weight % of silicone resin, (d) 2 to 10 weight % of one or more thickeners selected from the group consisting of crosslinked methyl polysiloxane, inulin stearate, and sucrose fatty acid ester, (e) 10 to 40 weight % of powder, and a volatile hydrocarbon.

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

[0029] It is also preferred that the viscosity is 40 mPa·s to 400 mPa·s at 25°C and a shear rate of 76.6 / s, and that the average initial evaporation rate within 1 minute immediately after application by the filter paper method is 0.15 to 2.00 mg / sec under conditions of 25°C and 65% RH. If the viscosity exceeds 400 mPa·s, the increased viscosity of the cosmetic composition will cause a deterioration in the feeling of use, which is undesirable.On the other hand, if the viscosity is less than 40 mPa·s, the cosmetic composition will tend to bleed on the skin, which is undesirable in use. If the initial evaporation rate exceeds 2.00 mg / sec, the cosmetic spreads extremely poorly due to the excessively fast evaporation rate, which is undesirable for use. Also, if the initial evaporation rate is less than 0.15 mg / sec, the cosmetic remains sticky for a long time after application and the cosmetic wear time is reduced, which is undesirable for use. The initial evaporation rate is calculated by accurately weighing approximately 1 g of cosmetic onto a φ90 mm filter paper in an environment of 25°C and 65% RH, measuring the weight again one minute after weighing, and calculating the initial evaporation rate from the difference in weight before and after the measurement using the following formula. Initial evaporation rate (mg / sec) = (W0-W1) ÷ 60 × 1000 Here, W0 and W1 are as follows. W0: Weight (g) of the cosmetic weighed on the filter paper immediately after the start of measurement W1: Weight of the cosmetic on the filter paper 1 minute after the start of measurement (g)

[0030] When the liquid oil-based cosmetic material is stored in the storage portion 10b, the barrel 10 is preferably made of a polybutylene terephthalate resin (PBT resin). (Whole applicator)

[0031] In the applicator, as shown in Fig. 1, the front end 10a of the barrel (rear barrel) 10 is formed to have a stepped diameter smaller than the portion of the storage section 10b inside the barrel 10. A cap 28 is detachably fitted to the front end 10a of the barrel 10, covering the front barrel 26 and the applicator body 24. A pipe joint 30 is provided on the inside of the portion of the front barrel 26 that is fitted into the front end 10a of the barrel 10, and the flange of the rear end of the applicator body 24 is sandwiched between the tip of the pipe joint 30 and the inner surface of the front barrel 26 to fix the applicator body 24. A pipe 32 made of SUS or resin is arranged to extend from the central hole of the pipe joint 30 into the applicator body 24, and the pipe 32 allows the application liquid to flow toward the tip of the applicator body 24.

[0032] The outer peripheral surface of the stepped portion (step portion 10c) of the front end portion 10a of the barrel 10 is in contact with the cap 28 on its forward facing surface (see FIG. 1). The inner peripheral surface of the step portion 10c faces rearward into the application liquid storage portion 10b, and the piston 12 contacts the rearward facing surface at the forward end to regulate its position (see FIG. 4). The front part of the barrel 10 is a storage section 10b for the coating liquid, and the rear part is provided with a delivery mechanism A, which comprises a screw body 22, a screw shaft 14, a rotating cam body 16, a transmission cam body 18, a spring 18c, and a delivery body 20, and has the function of advancing a piston 12 in the storage section 10b to deliver the coating liquid toward an applicator 24. The barrel 10 accommodates an agitator 10d for agitating the coating liquid together with the coating liquid in the storage section 10b. The agitator 10d may be a ball or rod-shaped body made of metal or resin.

[0033] 1, a stopper ring 34 that maintains front barrel 26 in an unused state when the applicator is unused is interposed between the tip surface of stepped portion 10c of barrel tube 10 and the rear end surface of front barrel 26. A cylindrical seal joint 36 is fitted into front end portion 10a of barrel tube 10. A seal ball 36a that seals housing portion 10b is fitted into seal joint 36 when the applicator is unused.

[0034] When the user starts to use the pen, as shown in Fig. 2, the stopper ring 34 is removed and the front barrel 26 is pressed backward against the front end 10a of the barrel tube 10, so that the rear end of the pipe joint 30 is pushed into the seal joint 36, causing the seal ball 36a to drop into the storage section 10b and opening the storage section 10b. By operating the feeding mechanism A, the piston 12 moves forward and the application liquid is supplied to the applicator body 24 through the seal joint 36, the pipe joint 30 and the pipe 32.

[0035] As shown in Figures 1 and 2, cap 28 has inner cap 28a and biasing spring 28b disposed therein. The applicator is structured so that inner cap 28a biased by spring 28b abuts airtightly against the outer circumferential surface of front barrel 26 when the applicator is not in use or is not in use. This prevents applicator body 24 from drying out.

[0036] (Extraction mechanism A) The structure of each component in the payout mechanism A will be described below.

[0037] As shown in Figures 5 and 6, the payout mechanism A has the screw shaft 14, payout body 20, rotating cam body 16, transmission cam body 18, and spring 18c mounted inside the screw body 22. Figures 7 and 8 show the state with the screw body 22 removed. The individual parts of the payout mechanism A are shown in Figures 9 to 16. Each part will be explained below.

[0038] (Threaded body 22) The threaded body 22 alone has a generally cylindrical shape that is open at the front and rear as shown in FIG. 9, with the front threaded portion (corresponding to the "female threaded portion") 22b having a stepped diameter smaller than that of the cylindrical portion 22a. A cam portion 22c is formed on the inner surface of the front end portion of the cylindrical portion 22a. The threaded portion 22b extends from the front end of the cylindrical portion 22a in a generally cylindrical shape, but is bifurcated by a split end 22b1 cut in the axial direction, allowing elastic deformation in the radial direction. A plurality of (e.g., 1 to 3) female threads 22b2 that can be screwed onto the screw shaft 14 are formed on the inner periphery of the threaded portion 22b and protrude inward. A flange-shaped blade portion 22b3 that abuts against the inner periphery of the shaft cylinder 10 is formed on the outer periphery of the threaded portion 22b.

[0039] A plurality of convex ribs 22a2 are formed on the outer periphery of the cylindrical portion 22a so as to extend in the axial direction in order to prevent the cylindrical portion 22a from turning against the inner surface of the barrel 10. A window portion 22a1 is formed and positioned behind the ribs 22a2. The rib 22a2 is structured to engage with a vertical rib 10f (see FIG. 19) on the inner surface of the barrel 10, and prevents rotation of the threaded body 22, thereby preventing malfunction of the threaded body 22 during knocking.

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

[0041] The step 22a31 sandwiching the thin 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 FIGS. 9(c) and 9(e)). The shape of the thin portion 22a3 is not limited to this.

[0042] Since the thin-walled portion 22a3 is formed, when the piston 12, screw shaft 14, rotating cam body 16, transmission cam body 18, spring 18c, and feeding body 20 are mounted in an assembled state (see Figs. 7 and 8) into the cylindrical portion 22a of the screw body 22, the feeding body 20 is pushed in. At that time, the protrusion 20b of the feeding body 20 comes into contact with the step 22a31 of the thin-walled portion 22a3 and is guided to rotate and be positioned, and slides toward the window portion 22a1, and the protrusion 20b fits into the window portion 22a1.

[0043] Therefore, when attaching the extension body 20 to the tubular portion 22a, there is no need to circumferentially align the protrusion 20b with respect to the window portion 22a1; simply inserting the extension body 20 into the tubular portion 22a allows the protrusion 20b to be fitted into the window portion 22a1, and since no alignment is required, work efficiency can be improved.

[0044] In addition, since the threaded portion 22b is bifurcated at the split end 22b1, when the threaded shaft 14 is assembled, the threaded portion 22b can be elastically deformed and assembled by pushing the threaded shaft 14 into the threaded portion 22b. Therefore, assembly can be performed without turning the threaded shaft 14 to screw it into the threaded portion 22b, which allows easy and reliable assembly on the manufacturing line and significantly reduces the workload.

[0045] In addition, the screw body 22 has a cam portion 22c with multiple rearwardly inclined surfaces formed within the cylindrical portion 22a rearward of the screw portion 22b, and the forward cam portion 16a of the rotating cam body 16 is arranged opposite the rearward cam portion 22c (see Figure 5).

[0046] As shown in FIG. 9, the cam portion 22c facing backward is integrally formed inside the cylindrical portion 22a of the screw body 22 by an inclined surface, so that the number of parts can be reduced compared to the case where the cam portion 22c is provided separately. In addition, when assembling, the female thread 22b2 on the inside of the screw portion 22b is screwed with the screw shaft 14. The wing portion 22b3 on the outer periphery abuts on the contact portion with the inside of the shaft tube 10, and the wing portion 22b3 is formed with a partially thin wall, thereby preventing the screw body 22 from opening due to shrinkage during molding. The wing portion 22b3 is assembled so as to abut on the vertical rib 10f (see FIG. 19) on the inner surface of the shaft tube 10. The number of the wing portions 22b3 is preferably two in order to satisfy the filling amount of the coating liquid and prevent opening at the same time. In addition, the formation of the split end portion 22b1 improves the degree of freedom in designing the molding die, which can lead to cost reduction.

[0047] The window 22a1 of the cylindrical portion 22a is structured to engage with the protrusion 20b of the propelling body 20, so that the propelling body 20 does not rotate when the propelling body 20 is pressed. This makes it possible to prevent ejection failure (see Figs. 5 and 6). As shown in Figs. 5 and 9, a flange 22d for abutting against and positioning the rear end of the barrel 10 (see Fig. 1) is formed at the rear end of the cylindrical portion 22a with an enlarged diameter. Furthermore, at a front position adjacent to the flange 22d of the cylindrical portion 22a, a plurality of projections and recesses 22e for engaging with the inner surface of the rear end portion of the barrel 10 are formed on the outer periphery. A window portion 22a1 is formed so as to penetrate the irregularities 22e in the radial direction. The locations where the irregularities 22e and the window portion 22a1 are formed are substantially in the same position in the axial direction of the threaded body 22, and therefore, since there is space inside the window portion 22a1 during injection molding, resin can easily flow into the irregularities 22e and the flange 22d, and thus the shape of the threaded body 22 is less likely to have molding defects such as sink marks.

[0048] 9, a thin-walled portion 22a3 extends to the position of the window portion 22a1 on the inner surface of the threaded body 22. A triangular front end apex of a step 22a31 of the thin-walled portion 22a3 overlaps with the window portion 22a1. A guide groove 22f is formed in the inner surface of the threaded body 22 along the axial direction from the window portion 22a1 to the central portion of the shaft. The guide groove 22f guides a guide protrusion 20d (see FIG. 10) described later by sliding therein. The guide groove 22f is continuous with the thin portion 22a3 at the position of the window portion 22a1, so that when the payout body 20 is assembled to the screw body 22, the guide projection 20d abuts against the step 22a31 and is guided into the guide groove 22f.

[0049] (Propulsion body 20) As shown in FIG. 10, the payout body 20 (knock body) alone has a roughly cylindrical shape with a closed rear end, and a pair of guide grooves 20a are formed in the front part of the payout body 20, penetrating the inner and outer circumferential surfaces and obliquely at an angle to the axial direction.

[0050] When the user knocks on the outer periphery of the closed rear end face of the payout body 20, the forward movement of the payout body 20 is converted into a rotational movement of the transmission cam body 18 by the guide groove 20a and the protrusion 18b on the side of the transmission cam body 18, and the rotation of the transmission cam body 18 rotates the rotating cam body 16, moving the screw shaft 14 forward and the piston 12 forward (see Figures 5 and 6).

[0051] As shown in Figures 7, 8 and 10, a cantilever-like arm portion 20b1 that is elastically deformable is formed on the rear side of the payout body 20 by a U-shaped notch, and a protrusion 20b is formed on the outside of the arm portion 20b1. Further, on the outer circumferential surface of the arm portion 20b1 at a front position, a pair of guide projections 20d are formed at corresponding positions in the circumferential direction of the projection 20b so as to project outward.

[0052] 9, the top of the step 22a31 of the thin-walled portion 22a3 is located at the window portion 22a1, and a guide groove 22f is formed from the window portion 22a1 toward the front in the threaded body 22. The thickness of the portion where the guide groove 22f is formed is substantially the same as that of the thin-walled portion 22a3. When the screw body 22 is assembled to the payout body 20, the payout body 20 is pushed into the screw body 22 from behind. When the payout body 20 advances relative to the screw body 22 by being pushed in for assembly, 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 payout body 20 is further pushed in, guide protrusion 20d passes through window portion 22a1 and is guided into guide groove 22f, and proceeds along guide groove 22f. Since protrusion 20b is at the same position as guide protrusion 20d in the circumferential direction, guide protrusion 20d advances along guide groove 22f, so that protrusion 20b fits smoothly into window portion 22a1 without being misaligned.

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

[0054] 7, 8 and 10, the outer peripheral surface of the rear part of the payout body 20 is formed with a step 20f behind it that is slightly larger in diameter all around. The larger diameter part behind the step 20f contacts the inner peripheral surface of the cylindrical part 22a of the threaded body 22, maintaining airtightness between the payout body 20 and the cylindrical part 22a (see Figs. 5 and 6).

[0055] Further, a pair of second projections 20e are formed on the outer peripheral surface of the rear of the step portion 20f, protruding in the radially expanding direction like ribs. The second projections 20e protrude in pairs on the outer peripheral surface of the payout body 20 at the same positions in the circumferential direction as the projections 20b and the guide projections 20d. When the payout body 20 is mounted within the screw body 22, the second protrusion 20e abuts (or is adjacent to) and supports the inner surface (thin-walled portion 22a3) of the tubular portion 22a, thereby preventing the payout body 20 from rattling relative to the tubular portion 22a (see Figures 5 and 6).

[0056] (From this point onwards, the paragraph numbers will be incremented.) As shown in FIG. 10, the forward inner periphery of the delivery body 20 is provided with a guide portion 20c that guides the protrusion 18b (see FIG. 12) into the guide groove 20a when the transmission cam body 18 is assembled. The guide portion 20c is a thin portion formed by hollowing out the inner periphery from the front end edge of the delivery body 20 to the periphery of the guide groove 20a, and is formed in two places corresponding to the guide groove 20a. A step portion 20c1 is formed that connects the thin guide portion 20c to another thick portion in a stepped manner. Two guide portions 20c are formed. The width between the step portions 20c1, 20c1 that sandwich each guide portion 20c extends over almost half of the periphery at the front end edge of the delivery body 20, narrows toward the rear, and is formed to a width (or narrow width, wide width) that corresponds to the guide groove 20a near the guide groove 20a. The width between the step portions 20c1, 20c1 is formed into a generally triangular inclined surface or wedge shape (see FIG. 10(d)). Adjacent guide portions 20c may overlap at the front end edge or may be spaced apart (there may be a space between the step portions 20c1 or they may be formed from a portion recessed from the front end edge).

[0057] During assembly, the transmission cam body 18 is attached from the front into the delivery body 20. In this case, since the transmission cam body 18 has no front or back, no front or back positioning is required, and the workload is reduced. When the transmission cam body 18 is inserted into the delivery body 20, the pair of protruding projections 18b come into contact with the step portions 20c1, 20c1 and are guided to fit into the pair of guide portions 20c. Then, as the transmission cam body 18 moves backward, the projections 18b come into contact with the step portions 20c1, 20c1 and are guided by the guide portions 20c and slide into the guide grooves 20a.

[0058] Therefore, simply by inserting the transmission cam body 18 into the payout body 20, the protrusion 18b is guided and fits into the guide groove 20a, eliminating the need to position the protrusion 18b circumferentially in the guide groove 20a. This eliminates the need for positioning, reduces the amount of work required, and is extremely efficient. Also,

[0059] (Front and rear symmetrical parts) Of the components of the applicator, 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 to be symmetrical in the front-rear direction. These components will be explained below.

[0060] (Rotating cam body 16) As shown in FIG. 11, the rotating cam body (delivery cam) 16 alone has a front side 16F and a rear side 16R that are symmetrical in shape, and has a generally cylindrical shape having a hollow portion.

[0061] An outer cam portion 16o and an inner cam portion 16i are formed on the front side 16F and the rear side 16R, respectively. The same function is achieved regardless of whether the front side 16F or the rear side 16R is facing when the screw is mounted in the threaded body 22.

[0062] The rotating cam body 16 is involved in the payout mechanism A shown in FIG. 5, and has a front cam portion 16a serving as an outer circumferential cam portion 16o and a rear cam portion 16b serving as an inner circumferential cam portion 16i.

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

[0064] As shown in Fig. 11, a protrusion for preventing rotation is formed on the inner peripheral surface of the internal through hole 16c. This protrusion 16c1 engages with a flat cutout portion 14c on the outer peripheral surface of the screw shaft 14 (see Fig. 13) and has the function of restricting the relative rotation between the rotating cam body 16 and the screw shaft 14 and enabling relative forward and backward movement in the axial direction.

[0065] (Transmission cam body 18) As shown in Fig. 12, the transmission cam body 18, when taken alone, has a large diameter at the center, and front and rear portions that are slightly smaller in diameter than the center, extend in a cylindrical manner in the front and rear directions, forming a cam portion (18a) with cams formed on the front and rear end faces. A pair of protrusions 18b protrude from the opposing outer circumferential faces of the center. A pair of notches 18b1 are formed in the center, penetrating the inner and outer circumferential faces, sandwiching the location where the protrusions 18b are formed. In the center, the portion sandwiched between the notches 18b1, 18b1 is formed to be elastically deformable.

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

[0067] The cam portion 18a of the transmission cam body 18 and the rearward 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, the meshing can be easily disengaged when the transmission cam body 18 rotates in the other direction.

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

[0069] The forward cam portion 16a of the rotating cam body 16 and the rearward cam portion 22c in the cylindrical portion 22a of the screw body 22 are formed in a sawtooth shape that, when they are in contact with each other, meshes with each other when the rotating cam body 16 rotates in the other direction, and conversely, the meshing is easily released when the rotating cam body 16 rotates in one direction. Specifically, as shown generally in Fig. 17 described later, the forward cam portion 16a of the rotating cam body 16 has a plurality of sawtooth triangular peaks inclined in one direction (e.g., clockwise rotation direction) on the slope, and the rearward cam portion 22c in the cylindrical portion 22a of the screw body 22 has a plurality of sawtooth triangular peaks inclined in the other direction (e.g., counterclockwise rotation direction) on the slope.

[0070] The payout body 20 disposed within the cylindrical portion 22a of the threaded body 22 is structured so as to be movable within a certain range in the axial direction while its relative rotation with respect to the threaded body 22 is restricted.

[0071] Specifically, the structure that allows axial movement by restricting relative rotation is such that a protrusion 20b is formed on the outside of a cantilever-like arm that is elastically deformable on the side of the payout body 20, and the protrusion 20b fits into an axially long window 22a1 of the cylindrical portion 22a so as to be movable back and forth, as shown in Figures 5 and 6. In addition, the protrusion 18b of the transmission cam body 18 fits into the guide groove 20a, and a spring 18c is interposed between the payout body 20 and the transmission cam body 18, so that they resiliently bias against each other. The spring 18c is preferably a coil spring made of metal, resin, or the like.

[0072] In addition, in the assembled state, the cam formed on the outer periphery 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 the cam operation.

[0073] (Screw shaft 14) As shown in Fig. 13, when viewed from the axial direction, the screw shaft 14 has male screw threads 14a, 14a formed in a pair of arc-shaped portions on the outer circumferential surface, and flat notches 14c, 14c are formed between the screw threads 14a, 14a. The screw shaft 14 is symmetrical in the axial direction, and fitting portions 14b are formed at the front and rear ends to fit into the main body 12a of the piston 12 (see Fig. 15) to rotate and to prevent it from coming off. The fitting portions 14b are formed by forming flange-like ribs on the outer circumferential surface of columnar portions extending to the front and rear ends of the screw shaft 14.

[0074] When mounting the screw shaft 14 on the rotating cam body 16, as shown in Fig. 14, the front or rear end of the screw shaft 14 is inserted into the internal through-hole 16c toward the axial direction of the rotating cam body 16. During assembly, the flat cutout portion 14c of the screw shaft 14 engages with the protrusion 16c1 of the rotating cam body 16 due to the insertion. Note that since the screw shaft 14 has a front-to-rear symmetrical shape, there is no need to consider the front-to-rear position during insertion, and therefore no positioning in the front-to-rear direction is required, making the work easier.

[0075] (Piston 12) As shown in Fig. 15, the piston 12 has a shape that is symmetrical in the front-rear direction and axially symmetrical. The piston 12 has a main body 12a with a hole into which the fitting portion 14b (see Fig. 13) of the screw shaft 14 fits, and a seal portion 12b that expands in diameter in the front-rear direction and surrounds the main body 12a. An uneven portion is formed inside the hole of the main body 12a with which the fitting portion 14b can rotate and whose front-rear movement is restricted. The seal portion 12b comes into sliding contact with the inner surface of the shaft tube 10 to make the accommodation portion 10b liquid-tight (see Fig. 3).

[0076] (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 a protrusion 36c extends rearward to prevent the agitator 10d or the seal ball 36a from blocking the seal joint 36. The front end is formed with an enlarged flange portion 36d. The flange portion 36d abuts against the end face of the front end portion 10a of the barrel 10 to prevent it from slipping into the front end portion 10a (see Fig. 1).

[0077] Next, the propelling action (knocking action) of the applicator of the above-described embodiment will be described with reference to FIGS. 2, 3, 17 to 18. FIG.

[0078] Fig. 2 shows the state of the applicator when not knocking (original position), and Fig. 3 shows the state when knocking. In addition, Fig. 5 shows the state when not knocking and Fig. 6 shows the state when knocking in the propelling mechanism A. Figs. 17 and 18 are operation explanatory diagrams using schematic diagrams of the screw body 22, the rotating cam body 16, the transmission cam body 18, and the propelling body 20 in the propelling mechanism. Fig. 17(a) is an explanatory diagram of each part, (b) is a diagram of the initial state, and (c) is a diagram of the state when knocking starts, and Fig. 18(a) is a diagram of the state when knocking has been completed, (b) is a diagram of the state when knocking has been released and return has begun, and (c) is a diagram of the initial state when knocking has been completely returned.

[0079] In the knock-type applicator, when a user knocks on the outer periphery of the rear end surface of the propelling body 20, the propelling body 20 is caused to move forward as shown in FIG.

[0080] 17(a), during the extension operation, the guide groove 20a and the protrusion 18b on the side surface of the transmission cam body 18 convert the forward movement into a rotational movement (one direction: indicated by the symbol F) of the transmission cam body 18. The rotation angle of the transmission cam body 18 is indicated by θ in the figure, and the knock stroke of the extension body 20 is indicated by the symbol L.

[0081] The rotation of the transmission cam body 18 rotates the rotating cam body 16 in one direction, moving the screw shaft 14 forward and advancing the piston 12. On the other hand, by releasing the pressure, the delivery 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 Fig. 17(b)-(c) to Fig. 18(a), first, when the propelling body 20 is pressed forward, the propelling body 20 moves forward against the elastic force of the spring 18c (see Fig. 3). This causes the protrusion 18b to slide along the guide groove 20a, and the transmission cam body 18 rotates in one direction (the direction of the arrow F). As shown in Fig. 17(b)-(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 with each other, and the rotating cam body 16 starts to rotate.

[0083] After Figure 17(c), when the protrusion 18b slides rearward along the guide groove 20a until the feed body 20 reaches the bottom dead center and the rotating cam body 16 rotates, the teeth of the forward-facing cam portion 16a of the rotating cam body 16 overcome the teeth of the rear-facing cam portion 22c in the cylindrical portion 22a after moving one pitch or more, and then, as shown in Figure 18(a), fit into the teeth of the next pitch when the bottom dead center is reached.

[0084] 17(b)-(c) and 18(a), the knock operation of the delivery body 20 is transmitted from the rotation of the transmission cam body 18 to the rotation of the rotating cam body 16, and the rotation of the rotating cam body 16 rotates the screw shaft 14 (not shown), which advances due to the action of the female screw (female thread) 22b2 of the screw portion 22b. The advance of the screw shaft 14 advances the piston 12 within the storage portion 10b and delivers the application liquid toward the applicator body 24.

[0085] On the other hand, when the pressing operation of the payout body 20 is released, as shown in the order of Figures 18(a) to (c), the elastic force of the spring 18c moves the payout body 20 backward, causing the protrusion 18b to slide forward along the guide groove 20a and causing the transmission cam body 18 to rotate in the other direction (the opposite direction to F). The teeth of the forward-facing cam portion of the rotating cam body 16 and the backward-facing cam portion in the cylindrical portion 22a of the screw body 22 mesh with each other, restricting the rotation of the rotating cam body 16, and 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 moving forward by one pitch or more, the teeth move over and engage with the teeth of the next pitch, so that the rotation of the transmission cam body 18 in the other direction is not transmitted to the rotating cam body 16, and the transmission cam body 18 engages with the teeth one pitch away on the rotating cam body 16. At that time, the transmission cam body 18 returns to the initial state one pitch back as shown in Figure 18(c).

[0087] As an example of the knock mechanism, the knock stroke is set to 2 mm. When the user knocks to operate the extension, the extension body 20 advances 1 mm for each 1 mm knock, causing the protrusion 18b of the transmission cam body 18 to move (rotate) along the guide groove 20a that opens diagonally in the extension body 20. When the knock reaches 2 mm, the knock limit is reached and the protrusion 18b of the transmission cam body 18 rotates completely. During this time, the rotating cam body 16 rotates (see Figures 17(b)-(c) and Figure 18(a)).

[0088] When the knock operation is released, the extension body 20 returns to the rear and the protrusion 18b of the transmission cam body 18 rotates reversely along the guide groove 20a, but the cam of the transmission cam body 18 and the cam of the rotating cam body 16 are released from engagement, and only the transmission cam body 18 rotates in the reverse direction, and the rotating cam body 16 does not rotate (Figures 18(a) to (c)).

[0089] Consider the conditions for the rotation angle θ. When the delivery body 20 is knocked by the knock stroke L, the transmission cam body 18 rotates by a rotation angle of θ degrees. If the rotation angle of one peak of the transmission cam body 18 and the rotating cam body 16 (rear cam portion 16b) is B, then the relationship "θ>B" is required.

[0090] In other words, if the rotation angle θ is larger than the rotation angle B of one crest, it is not possible to go over the crest of the cam portion.

[0091] In addition, when the knock is fully completed, the angle by which the forward cam portion 16a of the rotating cam body 16 passes over the cam portion 22c of the screw body 22 is defined as C, and similarly, when the knock is returned to its original position, the angle by which the rotating cam body 16 passes over the transmission cam body 18 and then further advances is defined as A. θ=A+B+C, and by appropriately setting the extra rotations A and C, it is possible to make "θ>B".

[0092] If A or C is small (few), it may not be possible to overcome the cam due to component tolerances and variations, and if they are too large, the knock stroke will have to be increased unnecessarily, which is not efficient.

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

[0094] According to the knock type applicator of the embodiment, the guide groove 20a of the propelling body 20 is formed at an angle to the axial direction, and when the propelling body 20 is advanced by a knock operation, the guide groove 20a and the protrusion 18b convert the advancement motion into a rotational motion of the transmission cam body 18 in one direction, and the cam portion of the transmission cam body 18 meshes with the cam portion at the rear of the rotating cam body 16, and the rotation of the transmission cam body 18 rotates the rotating cam body 16, and the advancement of the screw shaft 14 advances the piston 12, and on the other hand, when the knock operation is released, the resilient force of the spring 18c causes the propelling body 20 to rotate in one direction. When the dispensing body 20 is retracted, the guide groove 20a and the protrusion 18b convert the retracting motion into a rotational motion of the transmission cam body 18 in the other direction, returning it to its original position, and 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 restricting the operation of the screw shaft 14 and the piston 12. Therefore, the force generated when knocking the dispensing body 20 can be transmitted to the pressing force of the piston 12 without any loss of force, and when dispensing highly viscous contents, the feeling of operation can be made even lighter while preventing loss of knocking force.

[0095] At the same time, since the screw body 22 is provided with a cylindrical portion 22a having a rearward-facing cam portion 22c integrally formed therein, this cam portion is not provided separately, and therefore the number of parts can be reduced and manufacturing can be simplified compared to a case in which the cam portion is provided separately.

[0096] In addition, when the payout body 20 is pressed forward, the protrusion 18b slides along the guide groove 20a, causing the transmission cam body 18 to rotate in one direction, causing the opposing cam portions of the transmission cam body 18 and the rotating cam body 16 to mesh with each other, and the forward-facing cam portion of the rotating cam body 16 and the rearward-facing cam portion within the cylindrical portion 22a to disengage from each other, thereby transmitting the rotation of the rotating cam body 16. The rotation of the rotating cam body 16 causes the screw shaft 14 to rotate, and moves forward due to the action of the female thread of the screw portion 22b. When the pressing operation of the delivery body 20 is released, the elastic force of the spring 18c causes the delivery body 20 to move rearward, causing the protrusion 18b to slide along the guide groove 20a and the transmission cam body 18 to rotate in the other direction, causing the abutting cam portions of the transmission cam body 18 and the rotating cam body 16 to disengage from each other, and the forward-facing cam portion of the rotating cam body 16 and the rear-facing cam portion within the cylindrical portion 22a of the screw body 22 to engage with each other, preventing the rotation of the transmission cam body 18 in the other direction from being transmitted to the rotating cam body 16. By repeating the above pressing operation of the delivery body 20, the piston 12 can be smoothly pushed out.

[0097] In addition, if the tooth pitch of the rearward cam portion of the transmission cam body 18 and the rotating cam body 16 is the same as that of the forward cam portion of the rotating cam body 16 and the rearward cam portion in the cylindrical portion 22a of the screw body 22, and the phase of the teeth of the rearward cam portion of the rotating cam body 16 and the forward cam portion are shifted, the cam teeth of the rotating cam body 16 are engaged with the cam teeth of the cylindrical portion 22a before the knock operation of the feeding body 20, and the cam portion of the transmission cam body 18 is out of phase with the rearward teeth of the rotating cam body 16 when the feeding body 20 is knocked, so that the transmission cam body 18 rotates as the feeding body 20 advances. Then, when the knock of the feeding 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 rotating cam body 16 can be reliably prevented from rotating back.

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

[0099] In the applicator of the embodiment, as shown in Figure 3, front barrel 26 is provided at front end 10a of barrel tube 10 covering the periphery of applicator body 24, and front barrel 26 and barrel tube 10 are each formed with a permanent fitting portion and a temporary fitting portion, and front barrel 26 and barrel tube 10 each have an anti-rotation rib (reference number 46 in Figure 19, reference number 38 in Figure 20), and in the initial fitted state (see Figure 23) where the temporary fitting portions of barrel 10 and front barrel 26 engage with each other, the anti-rotation ribs do not engage with each other, while in the permanent fitted state (see Figure 22) where the permanent fitting portions engage with each other, the anti-rotation ribs engage with each other.

[0100] The full fitting and the provisional fitting will be explained with reference to FIG. 19, a parts diagram of the barrel 10, and FIG. 20, a parts diagram of the front barrel 26.

[0101] (Shaft tube 10) The barrel 10 will now be described.

[0102] As shown in Fig. 19, the barrel 10 is generally cylindrical. The front end 10a of the barrel 10 is located in front of the main body where the storage portion 10b is located, and is formed with a smaller diameter than the main body. As shown in Fig. 19(c), the front end 10a has two spaced ribs (front main fitting portion 42F and rear main fitting portion 42R) formed in an annular shape on the outer periphery as the main fitting portion 42.

[0103] In the permanent fitting portion 42, the rib on the application portion side, i.e., the front side of the permanent fitting portion 42F, has a stepped diameter enlarged at its front side to form a temporary fitting portion 44. Specifically, at the front end portion 10a of the barrel 10, the outer diameter at the front of the permanent fitting portion 42F is smaller than the outer diameter at the rear side to form a step that is nearly right-angled, and the front step of the permanent fitting portion 42F forms the step of the temporary fitting portion 44.

[0104] A rattle prevention portion 50 that supports the front barrel from the inside in the radial direction during temporary fitting is formed on the outer circumferential surface of the front end portion 10a of the barrel tube 10. Specifically, the rattle prevention portion 50, which is made of a rib during temporary fitting, is formed along the axial direction between the front main fitting portion 42F and the rear main fitting portion 42R.

[0105] Further, the outer diameter of front full fitting portion 42F is different from that of rear full fitting portion 42R. In front of temporary fitting portion 44, a rotation prevention rib 46 that prevents front barrel 26 from rotating relative to barrel tube 10 is formed.

[0106] As shown in Fig. 19, the front end 10a of the barrel 10 is reduced in diameter, but the inner peripheral surface of the rear end is formed with a stepped fitting portion 10e. Also, slightly rearward of the center portion, a vertical rib 10f is formed, protruding inward and extending in the axial direction.

[0107] When attaching the threaded body 22 (see FIG. 1) to the barrel 10, the threaded body 22 is inserted forward from the open rear end of the barrel 10, and then moved forward while attaching the outer periphery of the threaded body 22 to the vertical rib 10f until it is fitted in place.

[0108] The screw body 22, to which the cylindrical extension body 20 with a closed rear end is attached and restricted from rotating, is fitted into the fitting portion 10e, and the rear end of the extension body 20 is exposed from the rear end of the barrel 10 (see Figure 1).

[0109] (front axis 26) FIG. 20 is a parts drawing of the front barrel 26.

[0110] As shown in Fig. 20, front barrel 26 is generally cone-shaped with a tip that is tapered from the rear. On the inner circumference of front barrel 26, a stepped rear end side surface of front rib 54, which is a temporary fitting portion for temporarily fitting with temporary fitting portion 44 (see Fig. 19) of front end 10a of barrel tube 10, and front rib 54 and rear rib 56 that properly fit with proper fitting portion 42 (42F, 42R) (see Fig. 19) of front end 10a are formed over substantially the entire circumference. Forming front rib 54 and rear rib 56 over substantially the entire circumference improves the temporary pull-out force between front barrel 26 and barrel tube 10 in the initial fitting state, and prevents front barrel 26 from falling off barrel 10 during transportation, etc.

[0111] The front rib 54 and the rear rib 56 have a generally trapezoidal cross-sectional shape along the axial direction. Note that the cross-sectional shape of the ribs 54, 56 is not limited to a trapezoidal shape with sharp edges at the corners, and may be one in which the corners are chamfered or in which the corners are arc-shaped.

[0112] In front barrel 26, the inner periphery of the front portion is formed into a cylindrical inner periphery shape that houses applicator body 24, and the inner periphery of the central portion is formed with engaging step portion 26a for fitting in pipe joint 30. In addition, the outer circumferential surface of front barrel 26 is formed with annular uneven portion 26b for fixing cap 28 in place.

[0113] The portion of front barrel 26 in front of engaging stepped portion 26a is the rear inner periphery, and a plurality of anti-rotation ribs 38 in the form of vertical grooves for preventing rotation are formed on the inside of uneven portion 26b.

[0114] On the inner periphery of front barrel 26, a stepped locking portion 26c is formed forward of engagement step 26a, against which flange 24a of applicator body 24 abuts. A triangular groove is formed in locking portion 26c before and after the step. The groove guides the hairs at the tip of the brush when applicator body 24 is attached, preventing the tip of the brush from turning over (facing the opposite direction).

[0115] When the applicator of the embodiment is used from an unused state, it goes into an initial fitted state shown in FIG. 21, a full fitted state shown in FIG. 22, and a provisionally fitted state in which the applicator is slightly pushed in as shown in FIG.

[0116] When the applicator is unused, it maintains an initial fitted state in which front barrel 26 is held via stopper ring 34 and provisionally fitted into barrel tube 10 (see FIG. 1).

[0117] To start using the product, the user first removes stopper ring 34 to place front barrel 26 in a state where it is not pressed into barrel tube 10 (initial fitting state). In this case, as shown in FIG. 21, front rib 54 of front barrel 26 abuts against or is located forward of temporary fitting portion 44 of barrel tube 10, and rear rib 56 is located depressed between front and rear full fitting portions 42 (full fitting portions 42F, 42R). Seal ball 36a is fitted into seal joint 36. Anti-rotation rib 46 of barrel tube 10 is not engaged with anti-rotation rib 38 of front barrel 26. Therefore, front barrel 26 is freely rotatable relative to barrel tube 10. Rear rib 56 of front barrel 26 is positioned between front and rear main fitting portions 42 (main fitting portions 42F, 42R), but rattle prevention portion 50 consisting of a rattle prevention rib between main fitting portions 42F, 42R supports rear rib 56 of front barrel 26, preventing rattle of front barrel 26.

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

[0119] Then, when front barrel 26 is pushed in from the temporary fitting state of Fig. 23, front rib 54 moves from temporary fitting portion 44 over front full fitting portion 42F and engages with full fitting portion 42F. Also, rear rib 56 moves over full fitting portion 42R and engages. This results in the full fitting state shown in Fig. 22. Front barrel 26 moves axially by approximately the length of stopper ring 34, and reaches the full fitting state in which it fits directly into barrel tube 10. At the same time, anti-rotation rib 38 of front barrel 26 is completely inserted into anti-rotation rib 46 of barrel tube 10, making it possible to more reliably prevent rotation of barrel tube 10 relative to front barrel 26.

[0120] According to the applicator of the embodiment, barrel 10 is formed with full fitting portion 42 (42F, 42R) and temporary fitting portion 44, and front rib 54 for temporary fitting with temporary fitting portion 44 of front end portion 10a of barrel 10, and front rib 54 and rear rib 56 for full fitting with full fitting portion 42 (42F, 42R) of front end portion 10a are formed around substantially the entire inner circumference of front barrel 26. Barrel 10 has anti-rotation rib 46, and front barrel 26 has anti-rotation rib 38.

[0121] 21, in the initial fitted state before the barrel tube 10 and the front barrel 26 are provisionally fitted (before the provisionally fitted portion 44 and the front rib 54 engage with each other), the anti-rotation ribs 46, 38 are not engaged with each other. This is a relatively rotatable state.

[0122] On the other hand, as shown in FIG. 23, in the provisionally fitted state (the provisionally fitted portion 44 and the front rib 54 are engaged with each other), the anti-rotation ribs 46, 38 are engaged with each other, resulting in an anti-rotation state.

[0123] Furthermore, as shown in FIG. 22, when the fully fitted state (fully fitted portions 42 (42F, 42R) and front ribs 54 and rear ribs 56) is reached, front barrel 26 and barrel tube 10 are connected and ready for use.

[0124] Therefore, if the user removes front barrel 26 in addition to stopper ring 34 when starting use, even if front barrel 26 is reinstalled and fully fitted, anti-rotation ribs 46, 38 will be in engagement with each other, allowing press-fitting without misalignment. This makes it possible to prevent liquid leakage due to insufficient press-fitting.

[0125] In addition, anti-rotation rib 46 of barrel 10 and anti-rotation rib 38 of tip shaft 26 engage with each other to prevent barrel 10 and tip shaft 26 from rotating, thereby preventing applicator body 24, which is made up of the bundled brush tip and fibers, from twisting when the user turns tip shaft 26.

[0126] Furthermore, since the provisional removal force in the initial fitting state (the removal force when the stopper ring 34 is present) can be made strong, it is possible to prevent the front barrel 26 from falling off the barrel tube 10 during transportation or the like. [Industrial Applicability]

[0127] The applicator of the present invention can be used as a cosmetic applicator for cosmetic products and the like. [Explanation of symbols]

[0128] 10 shaft cylinder 10a Front end 10b Storage section 10c Step 10d stirring body 10e Fitting part 10f Vertical rib 12 Piston 12a Main unit 12b Seal part 14 Screw shaft 14a Threaded part 14b Fitting part 14c Cutout 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 Extension body 20a Guide groove 20b protrusion 20b1 Arm 20c induction part 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 Threaded part 22d flange 22e unevenness 22f guide groove 24 Applied body 24a flange 26 Tip axis 28 Cap 30 Pipe Fittings 32 Pipe 34 Stopper ring 36 Seal joint 36a Seal Ball 36b Narrow diameter part 36c Convex 36d Flange part 38 Anti-rotation rib of shaft tube 42 Main fitting part 44 Temporary fitting part 46 Anti-rotation rib of the front shaft 50 Anti-rattle part 54 Front rib 56 Rear rib A. Feeding mechanism

Claims

1. an applicator comprising a storage section for storing a coating liquid, a piston that slides within the storage section, a screw shaft having a thread formed on its circumferential surface, an advancing body for advancing operation, a rotating cam body, and a transmission cam body, a screw portion that screws onto the screw shaft is provided at the rear of the storage section, and an advancing operation on the advancing body rotates the rotating cam body to rotate the screw shaft and the screw portion relatively to each other to advance the screw shaft, and the piston is advanced by the screw shaft to supply the coating liquid stored in the storage section to the applicator body, At least one of the screw shaft, the rotating cam body, and the transmission cam body is formed in a front-rear symmetrical shape, A front barrel is provided at the front end of the barrel so as to cover the applicator body; A permanent fitting portion and a temporary fitting portion are formed on each of the front barrel and the barrel tube, The front barrel and the barrel tube each have a rotation-preventing rib, This applicator is characterized in that, in an initial engagement state in which the temporary engagement portions of the barrel and the front barrel engage with each other, the respective anti-rotation ribs do not engage with each other, and, on the other hand, in a main engagement state in which the main engagement portions engage with each other, the respective anti-rotation ribs engage with each other.

2. an applicator comprising a storage section for storing a coating liquid, a piston that slides within the storage section, a screw shaft having a thread formed on its circumferential surface, an advancing body for advancing operation, a rotating cam body, and a transmission cam body, a screw portion that screws onto the screw shaft is provided at the rear of the storage section, and an advancing operation on the advancing body rotates the rotating cam body to rotate the screw shaft and the screw portion relatively to each other to advance the screw shaft, and the piston is advanced by the screw shaft to supply the coating liquid stored in the storage section to the applicator body, At least one of the screw shaft, the rotating cam body, and the transmission cam body is formed in a front-rear symmetrical shape, The relative rotation between the rotating cam body and the screw shaft is regulated, the transmission cam body rotates the rotating cam body by operating the feeding body, a screw body having a threaded portion that screws onto the screw shaft is provided at the rear of the storage section, and when the feeding body is operated, the rotating cam body rotates via the transmission cam body, causing a piston to advance so as to supply the coating liquid contained in the storage section to the applicator body.

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