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 cosmetic liquid, 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 has been proposed that converts a knocking operation into a rotational operation to feed out a coating liquid (see Patent Document 1).

[0003] Since this applicator has a cam surface on the end face of a cylindrical rotating body, there is a limit value to 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, Patent Document 2 proposes an applicator capable of increasing the feeding force by a guide groove and a protrusion.

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 such a 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 a coating tool provided with a storage part for storing a coating liquid, a piston that slides within the storage part, a screw shaft having a screw formed on its circumferential surface, a feeding body for performing a feeding operation, a rotating cam body, and a transmission cam body. A screw part that engages with the screw shaft is provided behind the storage part. By rotating the rotating cam body through the feeding operation on the feeding body, the screw shaft and the screw part are relatively rotated to advance the screw shaft, and the piston is advanced by the screw shaft to supply the coating liquid stored in the storage part to the coating body. In the coating tool, at least one of the screw shaft, the rotating cam body, and the transmission cam body is formed in a bilaterally symmetric shape.

[0009] In the present invention, it is preferable that the piston is formed in a bilaterally symmetric shape.

[0010] In the present invention, it is preferable that the screw part is formed, and an inclined surface that expands in diameter from the rear to the front is formed on the inner surface of the screw body that houses the rotating cam body, the transmission cam body, and the feeding body.

[0011] In the present invention, a tip shaft is provided to cover the periphery of the coating body at the front end of the shaft cylinder. A main fitting part and a temporary fitting part are formed on the tip shaft and the shaft cylinder respectively. The tip shaft and the shaft cylinder each have an anti-rotation rib. When the temporary fitting parts of the shaft cylinder and the tip shaft are engaged in the initial fitting state, the anti-rotation ribs do not engage with each other. On the other hand, when the main fitting parts are engaged in the main fitting state, the anti-rotation ribs engage with each other.

[0012] In the present invention, the relative rotation between the rotating cam body and the screw shaft is restricted. The transmission cam body rotates the rotating cam body by the feeding operation on the feeding body. The screw body having the screw part that engages with the screw shaft is provided behind the storage part. By operating the feeding body, the rotating cam body rotates to advance the piston and supply the coating liquid stored in the storage part to the coating body.

Advantages of the Invention

[0013] According to the applicator of the present invention, since at least one of the screw shaft, the rotary cam body, and the transmission cam body is formed in a bilaterally symmetric shape, alignment in the front-back direction can be omitted, and excellent effects such that the assemblability during manufacturing is improved can be achieved.

Brief Description of the Drawings

[0014]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

Figure 19

Figure 20

Figure 21

Figure 22

Figure 23

Embodiments for Carrying Out the Invention

[0015] Hereinafter, embodiments of the present invention will be described with reference to Figs. 1 to 23.

[0016] Fig. 1 shows the unused state of the applicator, Fig. 2 shows the start of use, Fig. 3 shows the state of knocking and pressing, and Fig. 4 shows the end of use.

[0017] As shown in Figs. 1 to 4, the applicator according to the embodiment includes a housing portion 10b for storing the coating liquid, a piston 12 that slides within the housing portion 10b, and a screw shaft 14 having a male screw thread portion 14a formed on its peripheral surface, which are provided within a shaft cylinder 10. A feeding body 20 for performing a feeding operation is provided, 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 by a feeding operation on the feeding body 20, and a screw body 22 having a screw portion 22b that is screwed onto the screw shaft 14 are provided behind the housing portion 10b. In the applicator configured such that when the feeding body 20 is operated, the rotating cam body 16 rotates to advance the piston 12 and supply the coating liquid stored in the housing portion 10b to the coating body 24, at least one example of the screw shaft 14, the rotating cam body 16, and the transmission cam body 18 (contained inside the screw body 22) is formed in a front-back symmetric shape.

[0018] In the applicator, a feeding mechanism A including a screw body 22, a screw shaft 14, a rotating cam body 16, a transmission cam body 18, a spring 18c, and a feeding body 20 is disposed within the shaft cylinder 10.

[0019] When the applicator is in an unused state, as shown in FIG. 1, the cap 28 and the stopper ring 34 are attached, and the stopper ring 34 positions the front shaft 26 forward so that the seal ball 36a fits in. At the start of use, as shown in FIG. 2, the stopper ring 34 is removed and the seal ball 36a falls into the accommodating portion 10b. During knocking, as shown in FIG. 3, the piston 12 is pressed by the extending body 20. At the end of use, as shown in FIG. 4, the piston 12 is positioned at the front end of the accommodating portion 10b.

[0020] FIGS. 5 and 6 are part drawings of the feeding mechanism A, where FIG. 5 shows the non-knocking state and FIG. 6 shows the knocking state. FIGS. 7 and 8 are part drawings of the state where the screw body 22 is removed from the feeding mechanism A, where FIG. 7 shows the non-knocking state and FIG. 8 shows the knocking state. FIG. 9 is a drawing of the screw body 22, FIG. 10 is a drawing of the extending body 20, FIG. 11 is a drawing of the rotating cam body 16, FIG. 12 is a drawing of the transmission cam body 18, FIG. 13 is a drawing of the screw shaft 14, FIG. 14 is a drawing of the state where the screw shaft 14 is axially directed to the rotating cam body 16, FIG. 15 is a drawing of the piston 12, and FIG. 16 is a part drawing of each part of the joint 36.

[0021] (Feeding mechanism A) As shown in FIGS. 5 and 6, the feeding mechanism A includes a rotating cam body 16 whose relative rotation with the screw shaft 14 is restricted and which has cam portions 16a and 16b formed at the front and rear portions respectively, a transmission cam body 18 having a cam portion 18a formed at the front portion for engaging with the cam portion 16b at the rear portion of the rotating cam body 16 and having a protrusion 18b formed on the side surface, an extending body 20 having a guide groove 20a for guiding the protrusion 18b of the transmission cam body 18 and rotating the transmission cam body 18 through the guide groove 20a and the protrusion 18b by forward and backward movement, a spring 18c for elastically ejecting the extending body 20 backward and the transmission cam body 18 forward, and a screw body (corresponding to a "fixed cam body") 22 having a cylindrical portion 22a containing the transmission cam body 18, the rotating cam body 16, the spring 18c, the screw shaft 14, and the extending body 20 and having a rearward cam portion 22c integrally formed inside and a screw portion 22b screwed to the screw shaft 14 at the front portion.

[0022] In addition to the above-described configurations of the screw body 22, the rotary cam body 16, and the screw shaft 14, the screw portion of the screw body 22 may be formed into a non-circular hole to regulate relative rotation with the screw shaft 14 according to the cross-section of the screw shaft 14, and a female screw portion may be formed on the inner circumference of the rotary cam body 16 so that the screw portion is screwed with a male screw on the outer peripheral surface of the screw shaft 14 to form a feeding mechanism.

[0023] And the guide groove 20a of the feeding body 20 is formed obliquely at an angle with respect to the axial direction (the front-rear direction of the applicator).

[0024] In the above-described knock-type applicator, when the feeding body 20 is advanced by a knock operation with respect to the feeding mechanism A, the forward movement is converted into a rotational movement of the transmission cam body 18 in one direction (the right-rotating direction in the axial forward direction in the embodiment) by the guide groove 20a and the protrusion 18b. The cam portion 18a of the transmission cam body 18 meshes with the cam portion 16b at the rear portion of the rotary cam body 16, and the rotary cam body 16 is rotationally operated by the rotation of the transmission cam body 18 to advance the piston 12 by the advancement of the screw shaft 14. On the other hand, when the feeding body 20 is retracted by the elastic force of the spring 18c by releasing the knock operation, the backward movement is converted into a rotational movement of the transmission cam body 18 in the other direction (the left-rotating direction in the axial forward direction in the embodiment) by the guide groove 20a and the protrusion 18b to return to the original position. Further, the cam portion 16a at the front portion of the rotary cam body 16 meshes with the cam portion 22c of the cylindrical portion 22a, and the rotational operation of the rotary cam body 16 is restricted to restrict the operations of the screw shaft 14 and the piston 12.

[0025] (Coating body 24) As shown in FIGS. 1 to 3, in the applicator, the coating body 24 is attached to the front end portion 10a of the shaft cylinder (rear shaft) 10 by the front shaft 26. The coating body 24 is not particularly specified as long as it is a material capable of impregnating and applying a coating liquid such as a resin fiber bundle or a porous body. In the embodiment, the rear end portion thereof is bundled by melting and has a flange shape.

[0026] (Coating liquid) The coating liquid to be accommodated in the accommodation part 10b of the shaft cylinder 10 is a cosmetic liquid, an ink for writing instruments, or a chemical solution. In particular, in the case of a cosmetic liquid having a high viscosity (preferably a viscosity of 300 mPa·s or more), the feeding can be facilitated.

[0027] In the embodiment, a liquid oily cosmetic can be accommodated and used in the accommodation part 10b. Suitable as the liquid oily cosmetic in this embodiment is at least (a) 5 to 40% by weight of hydrofluoroether, (b) 20 to 60% by weight of a low-boiling silicone oil, (c) 2 to 10% by weight of a silicone resin, (d) 2 to 10% by weight of one or more thickeners selected from the group consisting of crosslinked methylpolysiloxane, inulin stearate, and sucrose fatty acid ester, and (e) 10 to 40% by weight of a powder, and contains a volatile hydrocarbon.

[0028] Also, suitable as another liquid oily cosmetic is at least (a) 20 to 75% by weight of isododecane, (b) 2 to 25% by weight of one or more of trimethylsiloxysilicic acid, an alkyl acrylate, and an alkyl acrylate copolymer, and (c) 2 to 25% by weight of one or more powders selected from carbon black, iron oxide, and ultramarine.

[0029] Moreover, 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 the average initial evaporation rate within 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. If the viscosity exceeds 400 mPa·s, the feel of use deteriorates due to the increase in the viscosity of the cosmetic, which is not preferable. If the viscosity is less than 40 mPa·s, it is likely to ooze on the skin, which is not preferable for use. If the initial evaporation rate exceeds 2.00 mg / sec, the evaporation rate is too fast, so the "spread" of the cosmetic becomes extremely poor, which is not preferable for use. Also, when the initial evaporation rate is less than 0.15 mg / sec, the stickiness of the cosmetic after coating remains for a long time, or the makeup retention deteriorates, which is not preferable for use. The initial evaporation rate is calculated as follows under the environment of 25°C and 65% RH. Approximately 1 g of the cosmetic is accurately weighed on a filter paper with a diameter of φ90 mm. The weight is measured again 1 minute after the weighing, and the initial evaporation rate is calculated from the weight difference before and after the measurement using the following formula. Initial evaporation rate (mg / sec) = (W 0 - W 1 ) ÷ 60 × 1000 Here, W 0 , W 1 are as follows. W 0 : The weight (g) of the cosmetic weighed on the filter paper immediately after the start of the measurement W 1 : The weight (g) of the cosmetic on the filter paper 1 minute after the start of the measurement

[0030] When the liquid oily cosmetic is accommodated in the accommodating portion 10b, it is preferable to use polybutylene terephthalate resin (PBT resin) for the material of the shaft cylinder 10.

[0031] (The whole applicator) In the applicator, as shown in FIG. 1, the front end portion 10a of the shaft cylinder (rear shaft) 10 is formed to have a smaller diameter in a stepped shape than the portion of the accommodating portion 10b inside the shaft cylinder 10. A cap 28 is detachably and freely fitted onto the front end portion 10a of the shaft cylinder 10 so as to cover the tip shaft 26 and the coating body 24. Inside the portion of the tip shaft 26 fitted inside the front end portion 10a of the shaft cylinder 10, there is a pipe joint 30. The flange at the rear end portion of the coating body 24 is sandwiched between the tip end portion of the pipe joint 30 and the inner surface portion of the tip shaft 26 to fix the coating body 24. A pipe 32 made of SUS or resin extends from the central hole of the pipe joint 30 into the coating body 24 and is arranged so that the coating liquid can flow toward the tip end portion of the coating body 24 through the pipe 32.

[0032] On the outer peripheral surface side of the portion (step portion 10c) of the front end portion 10a of the shaft cylinder 10 that has a smaller diameter in a stepped shape, the cap 28 abuts against the forward-facing surface (see FIG. 1). Also, on the inner peripheral surface side of the step portion 10c, it faces the accommodating portion 10b of the coating liquid in the rearward direction, and the piston 12 abuts against the rearward-facing surface at the forward end position to restrict the position (see FIG. 4). The front part inside the shaft cylinder 10 serves as the storage part 10b for the coating liquid. Inside the rear part, a feeding mechanism A is disposed, which consists of a threaded body 22, a threaded shaft 14, a rotating cam body 16, a transmission cam body 18, a spring 18c, and a feeding body 20, and has the function of advancing the piston 12 in the storage part 10b to feed the coating liquid toward the coating body 24. In the shaft cylinder 10, a stirring body 10d for stirring the coating liquid together with the coating liquid is accommodated in the storage part 10b. The stirring body 10d may be a ball made of metal or resin or a rod-shaped body.

[0033] In the coating tool, as shown in FIG. 1, when not in use, a stopper ring 34 for maintaining the front shaft 26 in an unused state is interposed between the front end surface of the stepped part 10c of the shaft cylinder 10 and the rear end surface of the front shaft 26. A cylindrical seal joint 36 is fitted into the front end part 10a of the shaft cylinder 10. This seal joint 36 has a seal ball 36a fitted therein for sealing the storage part 10b when the coating tool is in an unused state.

[0034] When the user starts using it, as shown in FIG. 2, by removing the stopper ring 34 and pressing the front shaft 26 backward against the front end part 10a of the shaft cylinder 10, the rear end part of the pipe joint 30 is pushed into the seal joint 36, dropping the seal ball 36a into the storage part 10b to open the storage part 10b. By operating the feeding mechanism A, the piston 12 advances and the coating liquid is supplied to the coating body 24 through the seal joint 36, the pipe joint 30, and the pipe 32.

[0035] Note that, as shown in FIGS. 1 and 2, the cap 28 has an inner cap 28a and a biasing spring 28b disposed inside. The coating tool has a structure in which the inner cap 28a biased by the spring 28b abuts airtightly against the outer peripheral surface of the front shaft 26 when the coating tool is not in use or not being used. Therefore, drying of the coating body 24 is prevented.

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

[0037] As shown in FIGS. 5 to 6, the feeding mechanism A is composed of a screw shaft 14, a feeding body 20, a rotating cam body 16, a transmission cam body 18, and a spring 18c mounted in a screw body 22. FIGS. 7 to 8 show the state where the screw body 22 is removed. Each component of the feeding mechanism A is shown in FIGS. 9 to 16. Each part will be described below.

[0038] (Screw body 22) The screw body 22, when viewed alone, has a generally cylindrical shape with open front and rear ends as shown in FIG. 9. The front screw portion (corresponding to the "female screw portion") 22b has a smaller diameter in a stepped manner than 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 screw portion 22b extends from the front end of the cylindrical portion 22a in a generally cylindrical shape, but is bifurcated by a split portion 22b1 cut in the axial direction, and is elastically deformable in the radial direction. A plurality of (for example, 1 to 3) female screw threads 22b2 that can be screwed onto the screw shaft 14 protrude inwardly on the inner peripheral portion of the screw portion 22b. Further, a flange-like blade portion 22b3 for contacting the inner peripheral surface of the shaft cylinder 10 is formed on the outer peripheral portion of the screw portion 22b.

[0039] On the outer peripheral portion of the cylindrical portion 22a, convex ribs 22a2 are formed so as to extend in the axial direction in plurality to prevent rotation with respect to the inner surface of the shaft cylinder 10. A window portion 22a1 is formed behind the rib 22a2. The rib 22a2 is structured to engage with the longitudinal rib 10f (see FIG. 19) on the inner surface of the shaft cylinder 10, preventing rotational malfunction during knocking by preventing the rotation of the screw body 22.

[0040] On the inner surface of the cylindrical portion 22a, as shown in FIG. 9, a thin-walled portion 22a3 is formed with an inclined surface that expands in diameter from the rear to the front on the inner surface. Specifically, on the inner surface of the cylindrical portion 22a, the thin-walled portion 22a3 is formed in a state where two portions are notched in a semi-circular shape and thinned from the rear end surface of the cylindrical portion 22a toward the window portion 22a1. The other part of the cylindrical portion 22a and the thin-walled portion 22a3 are continuous via a semi-circular step 22a31.

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

[0042] Since the thin-wall portion 22a3 is formed, when the piston 12, the screw shaft 14, the rotary cam body 16, the transmission cam body 18, the spring 18c, and the feeding body 20 are assembled (see FIGS. 7 and 8) and mounted in the cylindrical portion 22a of the screw body 22, the feeding body 20 is pushed in. At this time, the protrusion 20b of the feeding body 20 abuts against the step 22a31 of the thin-wall portion 22a3 and is guided to rotate and be positioned, and heads toward the window portion 22a1 so that the protrusion 20b slides into the window portion 22a1.

[0043] Therefore, when the feeding body 20 is mounted on the cylindrical portion 22a, the protrusion 20b can be fitted into the window portion 22a1 only by inserting the feeding body 20 into the cylindrical portion 22a without aligning the protrusion 20b in the circumferential direction with respect to the window portion 22a1. Since alignment is not required, the working efficiency can be increased.

[0044] Also, since the screw portion 22b bifurcates at the pre-cracked portion 22b1, when the screw shaft 14 is assembled, if the screw shaft 14 is pushed into the screw portion 22b, the screw portion 22b elastically deforms and can be mounted. Therefore, the assembly can be performed without the need to turn the screw shaft 14 and screw it into the screw portion 22b, enabling easy and reliable mounting in the manufacturing line and significantly reducing the working load.

[0045] Also, in the screw body 22, a cam portion 22c having a plurality of rearward inclined surfaces is formed in the cylindrical portion 22a behind the screw portion 22b, and the forward cam portion 16a of the rotary cam body 16 is disposed to face the rearward cam portion 22c (see FIG. 5).

[0046] As shown in FIG. 9, since the rearward cam portion 22c is integrally formed inside the cylindrical portion 22a of the screw body 22 by an inclined surface, the number of parts can be reduced as compared with the case where the cam portion 22c is provided separately. Further, at the time of assembly, the screw portion 22b has an internal female thread 22b2 that engages with the screw shaft 14. The blade portions 22b3 on the outer peripheral portion abut against the contact portion with the inside of the shaft cylinder 10, and by forming the blade portions 22b3 that are partially thin-walled, it is possible to prevent the screw body 22 from opening due to sink marks during molding. The blade portions 22b3 are assembled so as to abut against the vertical ribs 10f (see FIG. 19) on the inner surface of the shaft cylinder 10. The number of the blade portions 22b3 is preferably two in order to satisfy the filling amount of the coating liquid and prevent opening at the same time. Further, due to the formation of the pre-crack portion 22b1, the degree of freedom in the design of the molding die is improved, which can lead to cost reduction.

[0047] The window portion 22a1 of the cylindrical portion 22a has a structure that engages with the protrusion 20b of the feeding body 20, and when the feeding body 20 is pressed, the feeding body 20 is prevented from rotating. Discharge defects can be prevented (see FIGS. 5 and 6). As shown in FIGS. 5 and 9, a flange 22d for abutting against and positioning at the rear end of the shaft cylinder 10 (see FIG. 1) is formed with an enlarged diameter at the rear end portion of the cylindrical portion 22a. Further, a plurality of uneven portions 22e for engaging with the inner surface of the rear end portion of the shaft cylinder 10 are formed on the outer periphery at a front position adjacent to the flange 22d of the cylindrical portion 22a. The window portion 22a1 is formed so as to penetrate the uneven portion 22e in the radial direction. Since the formation positions of the uneven portion 22e and the window portion 22a1 are substantially the same in the axial direction of the screw body 22, resin easily flows into the uneven portion 22e and the flange 22d because the inside of the window portion 22a1 is a space in injection molding. Therefore, the screw body 22 has a shape in which molding defects such as sink marks are less likely to occur.

[0048] Also, on the inner surface of the threaded body 22, as shown in FIG. 9, the thin-walled portion 22a3 extends to the position of the window portion 22a1. The step 22a31 of the thin-walled portion 22a3 is positioned such that the triangular front-end top portion overlaps the window portion 22a1. On the inner surface of the threaded body 22, a guide groove 22f is formed along the axial direction from the window portion 22a1 to the central portion of the axis. The guide groove 22f slides and guides a guide protrusion 20d (see FIG. 10) 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 feeding body 20 is assembled to the threaded body 22, the guide protrusion 20d abuts against the step 22a31 and is guided into the guide groove 22f.

[0049] (Feeding body 20) The feeding body 20 (knocking body), when alone, as shown in FIG. 10, presents a generally cylindrical shape with a closed rear end, and a pair of guide grooves 20a penetrating the inner and outer circumferential surfaces are formed obliquely at an angle with respect to the axial direction at its front portion.

[0050] When the user performs a knocking operation on the outer circumference of the closed rear end surface of the feeding body 20, when the feeding body 20 is advanced, the forward movement is converted into a rotational movement of the transmission cam body 18 by the guide groove 20a and the protrusion 18b on the side surface of the transmission cam body 18, and the rotation of the transmission cam body 18 rotates the rotary cam body 16 to advance the screw shaft 14 and advance the piston 12 (see FIGS. 5 and 6).

[0051] Also, as shown in FIGS. 7, 8, and 10, a cantilever-like arm portion 20b1 that can be elastically deformed by a U-shaped notch is formed on the side portion on the rear side of the feeding body 20, and a protrusion 20b is formed on the outside of the arm portion 20b1. Also, on the outer circumferential surface at the front position of the arm portion 20b1, a guide protrusion 20d is formed to protrude outward in a direction corresponding to the circumferential direction of the protrusion 20b.

[0052] Here, as shown in FIG. 9, on the screw body 22, 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 forward from the window portion 22a1. 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 assembling the screw body 22 to the feeding body 20, the feeding body 20 is pushed into the screw body 22 from its rear for assembly. When the feeding body 20 advances relative to the screw body 22 by being pushed in for assembly, the guide protrusion 20d first abuts against the step 22a31 and rotates so that the circumferential position faces the window portion 22a1, and the relative angle is determined. When the feeding body 20 is further pushed in, the guide protrusion 20d passes through the window portion 22a1 and is guided into the guide groove 22f, and advances along the guide groove 22f. Since the protrusion 20b is in the same circumferential position as the guide protrusion 20d, as the guide protrusion 20d advances along the guide groove 22f, the protrusion 20b smoothly fits into the window portion 22a1 without being displaced.

[0053] Therefore, it is possible to assemble by simply pushing the feeding body 20 into the screw body 22 from the rear without positioning the feeding body 20 (see FIGS. 5 and 6 for the fitted state). Therefore, the guide protrusion 20d has a function of fitting into and guiding the guide groove 22f in the circumferential position, and a function of positioning the rear protrusion 20b so that it smoothly fits into the window portion 22a1.

[0054] Also, as shown in FIGS. 7, 8, and 10, on the outer peripheral surface of the rear portion of the feeding body 20, the portion behind the step 20f is formed to have a slightly larger diameter than the front portion over the entire circumference. The thickened portion behind the step 20f on the inner peripheral surface of the cylindrical portion 22a of the screw body 22 is in contact to maintain airtightness between the feeding body 20 and the cylindrical portion 22a (see FIGS. 5 and 6).

[0055] Also, on the outer peripheral surface of the portion behind the step 20f, a pair of second protrusions 20e protrude in the radial direction in a rib shape. The second protrusions 20e protrude from the outer peripheral surface of the feeding body 20 in a pair at the same circumferential position as the protrusion 20b and the guide protrusion 20d. The second protrusion 20e abuts (or is close to) and supports the inner peripheral surface (the thin-walled portion 22a3) of the cylindrical portion 22a when the feeding body 20 is mounted in the threaded body 22, thus preventing the feeding body 20 from rattling with respect to the cylindrical portion 22a (see FIGS. 5 and 6).

[0056] Also, as shown in FIG. 10, in the inner peripheral portion at the front of the feeding body 20, a guiding portion 20c for guiding the protrusion 18b (see FIG. 12) into the guide groove 20a when the transmission cam body 18 is assembled is formed. This guiding portion 20c is a thin-walled portion formed by hollowing out the inner periphery from the front edge of the feeding body 20 to around the guide groove 20a, and is formed at two locations corresponding to the guide groove 20a. Step portions 20c1 that connect to other thick-walled portions in a stepped manner are formed from the thin-walled guiding portion 20c. Two guiding portions 20c are formed. The widths of the step portions 20c1, 20c1 sandwiching each guiding portion 20c are approximately half of the peripheral edge at the front edge of the feeding body 20, and become narrower towards the rear, and are formed to have a width corresponding to the guide groove 20a (or narrower or wider) near the guide groove 20a. The widths of the step portions 20c1, 20c1 are formed in a substantially triangular slope or wedge shape (see FIG. 10(d)). The adjacent guiding portions 20c may overlap or be spaced apart at the front edge (a space may be provided between the step portions 20c1, or it may be formed from a portion that has entered from the front edge).

[0057] Upon assembly, the transmission cam body 18 is mounted into the feeding body 20 from the front. In this case, since the transmission cam body 18 has no front and rear, there is no need for front and rear positioning, and the working load is small. When the transmission cam body 18 is inserted into the feeding body 20, the protruding protrusions 18b in a pair hit the step portions 20c1, 20c1 and are guided to fit into the pair of guiding portions 20c. Then, as the transmission cam body 18 enters rearward, the protrusions 18b hit the step portions 20c1, 20c1, are guided by the guiding portions 20c, and slide to fit into the guide groove 20a.

[0058] Therefore, just by inserting the transmission cam body 18 into the feeding body 20, the protrusion 18b is guided and fitted into the guide groove 20a. Thus, it is not necessary to position the protrusion 18b in the circumferential direction in the guide groove 20a, eliminating the need for positioning, reducing the number of working steps, and being extremely efficient.

[0059] (Front-back symmetric shaped part) In the applicator, among the component parts, as shown in FIG. 11, the rotary cam body 16, as shown in FIG. 12, the transmission cam body 18, and as shown in FIG. 13, the screw shaft 14 are formed in a front-back symmetric shape. These parts will be described.

[0060] (Rotary cam body 16) The rotary cam body (feeding cam) 16, when alone, as shown in FIG. 11, has a front side 16F and a rear side 16R that are symmetric in shape, and presents a substantially cylindrical shape with a hollow part.

[0061] On each of the front side 16F and the rear side 16R, an outer peripheral cam part 16o and an inner peripheral cam part 16i are formed. Whether the front side 16F or the rear side 16R is facing inward when mounted in the screw body 22, it exhibits the same function.

[0062] The rotary cam body 16 is involved in the feeding mechanism A shown in FIG. 5, where the front cam part 16a of the front part is the outer peripheral cam part 16o, and the rear cam part 16b of the rear part is the inner peripheral cam part 16i.

[0063] As shown in FIG. 5, on the rotary cam body 16, forward and backward cam parts 16a and 16b are respectively formed at the front and rear parts in the axial direction. At the same time, the cam part 18a formed at the front part of the transmission cam body 18 is disposed opposite to the backward cam part 16b of the rotary cam body 16.

[0064] As shown in FIG. 11, a protrusion is formed around the inner peripheral surface of the internal through hole 16c to prevent rotation. This protrusion 16c1 engages with the flat surface notch 14c on the outer peripheral surface of the screw shaft 14 (see FIG. 13), has the function of restricting the relative rotation between the rotary cam body 16 and the screw shaft 14, and enabling relative axial movement of the shinchiji (unclear term, might be a misspelling).

[0065] (Transmission cam body 18) As shown in Fig. 12, the transmission cam body 18, when alone, has a thick diameter at the central portion, and front and rear portions slightly thinner than the central portion extend cylindrically forward and backward, and cam portions (18a) with cams formed on the front end face and the rear end face. Protrusions 18b project in pairs from the opposing outer peripheral surfaces of the central portion. In the central portion, notches 18b1 that penetrate the inner and outer peripheral surfaces are formed in pairs with the formation locations of the protrusions 18b interposed therebetween. In the central portion, the portion sandwiched by the notches 18b1, 18b1 is formed to be elastically deformable.

[0066] In the assembled state, as shown in Figs. 5 and 6, the front portion of the transmission cam body 18 has a slightly thinner diameter than the central portion and is inserted into the cylindrical rear portion of the rotary cam body 16, and the cam portion 18a of the front portion 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 rotary cam body 16 are formed in a sawtooth shape such that when they are in contact with each other, they mesh when the transmission cam body 18 rotates in one direction, and conversely, they are easily disengaged when the transmission cam body 18 rotates in the other direction.

[0068] Specifically, as schematically shown in Fig. 17 to be described later, the cam portion 18a of the transmission cam body 18 is a sawtooth formed with a plurality of triangular ridges inclined in one direction (e.g., the clockwise rotation direction) of the slope, and the rearward-facing cam portion 16b of the rotary cam body 16 is a sawtooth formed with a plurality of triangular ridges inclined in the other direction (e.g., the counterclockwise rotation direction) of the slope.

[0069] When the forward cam portion 16a of the rotary cam body 16 and the rearward cam portion 22c within the cylindrical portion 22a of the screw body 22 are in contact with each other, they engage when the rotary cam body 16 rotates in the other direction, and conversely, they are easily disengaged when the rotary cam body 16 rotates in one direction. Specifically, as schematically shown in FIG. 17 described later, it is a sawtooth shape formed with a plurality of triangular ridges inclined in one direction (e.g., the right rotation direction) of the slope of the forward cam portion 16a of the rotary cam body 16, and the rearward cam portion 22c within the cylindrical portion 22a of the screw body 22 is a sawtooth shape formed with a plurality of triangular ridges inclined in the other direction (e.g., the left rotation direction) of the slope.

[0070] The feeding body 20 disposed within the cylindrical portion 22a of the screw body 22 has a structure that is movable within a certain range in the axial direction while being restricted in relative rotation with respect to the screw body 22.

[0071] Specifically, as shown in FIGS. 5 and 6, this structure that is axially movable with the restriction of relative rotation is such that a protrusion 20b is formed on the outer side of an elastic deformable cantilever-like arm portion on the side portion of the feeding body 20, and the protrusion 20b is fitted into a window portion 22a1 that is long in the axial direction of the cylindrical portion 22a so as to be able to move back and forth. Also, the protrusion portion 18b of the transmission cam body 18 is fitted into the guide groove 20a, and a spring 18c is interposed between the feeding body 20 and the transmission cam body 18 to elastically repel each other. The spring 18c is preferably a coil spring made of metal, resin, or the like.

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

[0073] (Screw shaft 14) As shown in FIG. 13, in the axial direction view, on the outer peripheral surface of the screw shaft 14, male screw portions 14a, 14a are formed on arc-shaped portions that are diametrically opposite to each other, and flat notch portions 14c, 14c are formed between the male screw portions 14a, 14a. Also, the screw shaft 14 is axially symmetric, and at the front end portion and the rear end portion, fitting portions 14b are formed that can be inserted into and rotatably engaged within the main body 12a (see FIG. 15) of the piston 12 to prevent them from coming off. The fitting portion 14b is formed with flange-shaped ribs on the outer peripheral surface of a cylindrical portion that extends to the front end portion and the rear end portion of the screw shaft 14.

[0074] When mounting the screw shaft 14 onto the rotary cam body 16, as shown in FIG. 14, the front end portion or the rear end portion of the screw shaft 14 is axially directed towards the rotary cam body 16 and inserted into the internal through-hole 16c. During assembly, the flat notch portion 14c of the screw shaft 14 engages with the protrusion 16c1 of the rotary cam body 16 due to the insertion. Since the screw shaft 14 has a front-back symmetric shape during insertion, there is no need to consider the front-back position, so front-back positioning is not required and the operation is simple.

[0075] (Piston 12) As shown in FIG. 15, the piston 12 has a front-back symmetric and axisymmetric shape. The piston 12 is formed with a main body 12a having a hole into which the fitting portion 14b (see FIG. 13) of the screw shaft 14 is inserted, and a seal portion 12b that expands in diameter front and back so as to surround the main body 12a. In the hole of the main body 12a, uneven portions are formed for engaging the fitting portion 14b in a rotatable manner while restricting front-back movement. Also, the seal portion 12b is in sliding contact with the inner surface of the shaft cylinder 10 to make the accommodating portion 10b liquid-tight (see FIG. 3).

[0076] (Seal joint 36) As shown in Fig. 16, the seal joint 36, when considered as a single part, has a small-diameter portion 36b formed inside for receiving a seal ball 36a (see Fig. 1), and a convex portion 36c extending rearward to prevent the agitating body 10d and the seal ball 36a from closing the seal joint 36. The front end portion forms a flange portion 36d with an enlarged diameter. The flange portion 36d abuts against the end face of the front end portion 10a of the shaft cylinder 10 to restrict its intrusion into the front end portion 10a (see Fig. 1).

[0077] Next, the feeding operation (knock operation) of the applicator according to the above-described embodiment will be described with reference to Figs. 2, 3, 17 to 18.

[0078] Fig. 2 shows the state of the applicator when not knocking (original position), and Fig. 3 shows the state when knocking. In the feeding mechanism A, Fig. 5 shows the state when not knocking, and Fig. 6 shows the state when knocking. Figs. 17 to 18 are operation explanatory diagrams by schematic diagrams of the screw body 22, the rotary cam body 16, the transmission cam body 18, and the feeding body 20 in the feeding mechanism. Fig. 17(a) shows an explanatory diagram of each part, (b) shows the initial state diagram, and (c) shows the state diagram at the start of knocking. Fig. 18(a) shows the state diagram when knocking is completed, (b) shows the state diagram when starting to return after knocking is released, and (c) shows the state diagram of the initial state when knocking is completely returned.

[0079] In the knock-type applicator, when the user knocks on the outer periphery of the rear end face of the feeding body 20, the feeding body 20 is advanced as shown in Fig. 3.

[0080] As shown in Fig. 17(a), during the feeding operation, the forward movement is converted into a rotational movement (in one direction: indicated by the symbol F) of the transmission cam body 18 by the guide groove 20a and the protrusion 18b on the side surface of the transmission cam body 18. 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] When the transmission cam body 18 rotates, the rotary cam body 16 is rotated in one direction, the screw shaft 14 is advanced, and the piston 12 is advanced. On the other hand, when the pressing is released, the feeding body 20 returns rearward, and the transmission cam body 18 rotates in the other direction and returns to the original position.

[0082] Specifically, as shown in FIGS. 17(b) to (c) and FIG. 18(a), first, when the feeding body 20 is pressed forward, the feeding body 20 moves forward against the elastic force of the spring 18c (see FIG. 3). As a result, the protrusion 18b slides along the guide groove 20a, and the transmission cam body 18 rotates in one direction (the direction of arrow F). As shown in FIGS. 17(b) to (c), the rotation of the transmission cam body 18 in one direction causes the teeth of the cam portions 18a and 16b of the transmission cam body 18 and the rotary cam body 16 that are in contact with each other to mesh, and the rotary cam body 16 starts to rotate.

[0083] After FIG. 17(c), when the protrusion 18b slides rearward along the guide groove 20a until the feeding body 20 reaches the bottom dead center and the rotary cam body 16 rotates, when the teeth of the forward-facing cam portion 16a of the rotary cam body 16 cross over the teeth of the rearward-facing cam portion 22c in the cylindrical portion 22a by one pitch or more and reach the bottom dead center as shown in FIG. 18(a), they fit into the teeth of the next pitch.

[0084] By the operations shown in FIGS. 17(b) to (c) and FIG. 18(a), the knocking operation of the feeding body 20 is transmitted from the rotation of the transmission cam body 18 to the rotation of the rotary cam body 16. By the rotation of the rotary cam body 16, the screw shaft 14 (not shown) rotates and advances by the action of the female screw (female thread) 22b2 of the screw portion 22b. By the advancement of the screw shaft 14, the piston 12 advances in the housing portion 10b and feeds the coating liquid toward the coating body 24.

[0085] On the one hand, when the pressing operation of the feeding body 20 is released, as shown in FIGS. 18(a) to 18(c) in sequence, the feeding body 20 moves backward by the elastic force of the spring 18c, and thus the protrusion 18b slides forward along the guide groove 20a, causing the transmission cam body 18 to rotate in the other direction (the direction opposite to F). The teeth of the forward cam portion of the rotating cam body 16 and the teeth of the backward 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. Therefore, only the transmission cam body 18 rotates (see FIGS. 18(b) to 18(c)).

[0086] Then, when the meshing of 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 disengages, and after advancing by one pitch or more of the teeth and getting over it to fit into the teeth of the next pitch, the rotation of the transmission cam body 18 in the other direction is not transmitted to the rotating cam body 16, but fits into the teeth adjacent by one pitch in the rotating cam body 16. At that time, it becomes the initial state returned by one pitch shown in FIG. 18(c).

[0087] As an example of the knocking mechanism, the knock stroke is set to 2 mm. When the user knocks and performs the feeding operation, when the knock is 1 mm, the feeding body 20 advances 1 mm, and along the guide groove 20a that is obliquely opened in the feeding body 20, the protrusion 18b of the transmission cam body 18 moves (rotates). When the knock reaches 2 mm, it reaches the knock limit and the protrusion 18b of the transmission cam body 18 rotates completely. During that time, the rotating cam body 16 rotates (see FIGS. 17(b) to 17(c), FIGS. 18(a)).

[0088] When the knocking operation is released, the feeding body 20 returns backward and the protrusion 18b of the transmission cam body 18 rotates reversely along the guide groove 20a. However, the meshing between the cam of the transmission cam body 18 and the cam of the rotating cam body 16 is released, and only the transmission cam body 18 rotates in the reverse direction, while the rotating cam body 16 does not rotate (see FIGS. 18(a) to 18(c)).

[0089] Consider the conditions for the above rotation angle θ. When knocking only during the knock stroke L of the feeding body 20, the transmission cam body 18 rotates by a rotation angle of θ degrees. If the rotation angle of one crest between the transmission cam body 18 and the rotating cam body 16 (rear cam portion 16b) is B, the relationship of "θ > B" is necessary.

[0090] That is, if the rotation angle θ is not larger than the rotation angle B of one crest, the crest of the cam portion cannot be overcome.

[0091] Also, when knocking until the end, let the angle by which the forward cam portion 16a of the rotating cam body 16 advances over the cam portion 22c of the screw body 22 be C, and similarly, when returning the knock, let the angle by which the rotating cam body 16 further advances after overcoming the transmission cam body 18 be A. Then θ = A + B + C, and by appropriately setting A and C that rotate excessively, "θ > B" can be achieved.

[0092] If A and C are small (if they are small), there may be cases where the cam cannot be overcome due to component tolerances and variations. If they are made too large, the knock stroke has to be increased unnecessarily, which is not efficient.

[0093] Considering one embodiment, if the cam is equally divided into 12 parts, B = 360 / 12 = 30 degrees. If A and C are set to 7.05 degrees, the rotation angle due to knocking is θ = 30 + 7.05 + 7.05 = 44.1 degrees. That is, the rotation angle due to knocking becomes 44.1 degrees.

[0094] According to the knock-type applicator of the embodiment, the guide groove 20a of the feeding body 20 is formed obliquely with an angle with respect to the axial direction. When the feeding body 20 is advanced by a knock operation, the guide groove 20a and the protrusion 18b convert the forward movement into a rotational movement of the transmission cam body 18 in one direction. The cam portion of the transmission cam body 18 meshes with the cam portion at the rear of the rotary cam body 16, and the rotation of the transmission cam body 18 rotates the rotary cam body 16 to advance the piston 12 by the advancement of the screw shaft 14. On the other hand, when the feeding body 20 is retracted by the elastic force of the spring 18c by releasing the knock operation, the guide groove 20a and the protrusion 18b convert the backward movement into a rotational movement of the transmission cam body 18 in the other direction to return to the original position. Moreover, the cam portion at the front of the rotary cam body 16 meshes with the cam portion of the cylindrical portion 22a, and the rotational operation of the rotary cam body 16 is restricted, so that the operations of the screw shaft 14 and the piston 12 are restricted. Therefore, the force when the feeding body 20 is knocked can be transmitted to the pressing force of the piston 12 without loss of force, and in the case of feeding a high-viscosity content, the operation feeling can be further lightened while preventing loss of the knock force.

[0095] At the same time, since the screw body 22 is provided with the cylindrical portion 22a integrally formed with the rearward cam portion 22c inside, since this cam portion is not provided separately, the number of parts can be reduced and the manufacturing can be facilitated as compared with the case where it is provided separately.

[0096] Also, when the feeding 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. 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 cam portion of the rotating cam body 16 and the rearward cam portion within the cylindrical portion 22a disengages. As a result, the rotation of the rotating cam body 16 is transmitted, and the rotation of the rotating cam body 16 causes the screw shaft 14 to rotate and advance due to the action of the female screw of the screw portion 22b. When the pressing operation of the feeding body 20 is released, the elastic force of the spring 18c causes the feeding body 20 to move rearward. This causes the protrusion 18b to slide along the guide groove 20a, causing the transmission cam body 18 to rotate in the other direction. The engagement between the contacting cam portions of the transmission cam body 18 and the rotating cam body 16 disengages, and the forward cam portion of the rotating cam body 16 and the rearward cam portion within 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 pressing the feeding body 20 as described above, the piston 12 can be smoothly pushed out.

[0097] In addition, if the tooth pitch of each cam portion in the rearward cam portions of the transmission cam body 18 and the rotating cam body 16, the forward cam portion of the rotating cam body 16, and the rearward cam portion within the cylindrical portion 22a of the screw body 22 is the same, and the tooth phases of the rearward and forward cam portions of the rotating cam body 16 are offset, then before the knocking operation of the feeding body 20, the cam teeth of the rotating cam body 16 are engaged with the cam teeth of the cylindrical portion 22a. During the knocking operation of the feeding body 20, the phase of the cam portion of the transmission cam body 18 is offset from the rearward teeth of the rotating cam body 16, so the transmission cam body 18 rotates as the feeding body 20 advances. Then, when the knocking of the feeding body 20 is released, the cam portions of the rotating cam body 16 and the cylindrical portion 22a can be reliably engaged, and the reverse rotation of the rotating cam body 16 can be reliably prevented.

[0098] In addition, if a ring-shaped sealing body (elastic body such as rubber or elastomer) is circumferentially positioned between the outer periphery of the feeding body 20 and the inner periphery of the cylindrical portion 22a of the threaded body 22, the ring-shaped sealing body can ensure airtightness from the feeding body 20 to the rear and reliably prevent drying and deterioration of the contents.

[0099] In the applicator of the embodiment, as shown in FIG. 3, a tip shaft 26 is provided to cover the periphery of the application body 24 at the front end portion 10a of the shaft cylinder 10. A main fitting portion and a temporary fitting portion are formed on each of the tip shaft 26 and the shaft cylinder 10. The tip shaft 26 and the shaft cylinder 10 each have a rotation prevention rib (reference numeral 46 in FIG. 19 and reference numeral 38 in FIG. 20). When in the initial fitting state where the temporary fitting portions of the shaft cylinder 10 and the tip shaft 26 are engaged (see FIG. 23), the rotation prevention ribs of each other are not engaged. On the other hand, when in the main fitting state where the main fitting portions are engaged with each other (see FIG. 22), the rotation prevention ribs of each other are engaged.

[0100] The main fitting and the temporary fitting will be described with reference to the part drawing of the shaft cylinder 10 in FIG. 19 and the part drawing of the tip shaft 26 in FIG. 20.

[0101] (Shaft cylinder 10) The shaft cylinder 10 will be described.

[0102] As shown in FIG. 19, the shaft cylinder 10 is generally cylindrical. The front end portion 10a of the shaft cylinder 10 is on the front side of the main body having the accommodating portion 10b and is formed with a reduced diameter compared to the main body. As shown in FIG. 19(c), on the front end portion 10a, two ribs (front main fitting portion 42F and rear main fitting portion 42R) with a gap are annularly formed on the outer periphery as the main fitting portion 42.

[0103] In the main fitting portion 42, the rib on the application portion side, that is, the rib of the front main fitting portion 42F, is a temporary fitting portion 44 with a stepped enlarged diameter on its front side. Specifically, at the front end portion 10a of the shaft cylinder 10, with the main fitting portion 42F as a boundary, the outer diameter in the front is formed to be smaller than the outer diameter in the rear and is a stepped portion close to a right angle. The stepped portion on the front side of the main fitting portion 42F is the stepped portion of the temporary fitting portion 44.

[0104] On the outer peripheral surface of the front end portion 10a of the shaft cylinder 10, a backlash prevention portion 50 is formed that supports the tip shaft from the inner side in the radial direction during temporary fitting. Specifically, between the front main fitting portion 42F and the rear main fitting portion 42R, a backlash prevention portion 50 in the form of a rib during temporary fitting is formed along the axial direction.

[0105] Also, the outer diameters of the front main fitting portion 42F and the rear main fitting portion 42R are different. In front of the temporary fitting portion 44, a rotation prevention rib 46 that prevents the rotation of the tip shaft 26 with respect to the shaft cylinder 10 is formed.

[0106] As shown in FIG. 19, the front end portion 10a of the shaft cylinder 10 has a reduced diameter, but a fitting portion 10e with an uneven stepped shape is formed on the inner peripheral surface of the rear end portion. Also, from slightly behind the central portion, a vertical rib 10f protrudes inward and extends in the axial direction.

[0107] When mounting the screw body 22 (see FIG. 1) on the shaft cylinder 10, the screw body 22 is inserted forward from the open rear end portion of the shaft cylinder 10, and while being mounted on the outer periphery of the screw body 22 on the vertical rib 10f, it is advanced and fitted.

[0108] A feeding body 20 having a cylindrical shape with a closed rear end is rotatably restricted, and the mounted screw body 22 is fitted within the fitting portion 10e, and the rear end of the feeding body 20 is exposed from the rear end of the shaft cylinder 10 (see FIG. 1).

[0109] (Tip shaft 26) FIG. 20 is a component drawing of the tip shaft 26.

[0110] As shown in FIG. 20, the front shaft 26 has a generally conical shape with a tapered front end compared to the rear end. On the inner circumference of the front shaft 26, there are a stepped rear end side surface of the front rib 54, which is a temporary fitting portion for temporarily fitting with the temporary fitting portion 44 (see FIG. 19) of the front end portion 10a of the shaft cylinder 10, and a front rib 54 and a rear rib 56 that are permanently fitted with the permanent fitting portions 42 (42F, 42R) (see FIG. 19) of the front end portion 10a, formed over substantially the entire circumference. The fact that the front rib 54 and the rear rib 56 are formed over substantially the entire circumference improves the temporary pulling force between the front shaft 26 and the shaft cylinder 10 in the initial fitting state, and can prevent the front shaft 26 from falling off the shaft cylinder 10 during transportation or the like.

[0111] The front rib 54 and the rear rib 56 have a substantially trapezoidal shape in cross-section along the axial direction. Note that the cross-sectional shape of the ribs 54 and 56 is not limited to a trapezoidal shape with corners becoming edges, and may be a trapezoidal shape with chamfered corners or an arc shape.

[0112] In the front shaft 26, the inner circumference of the front portion is formed into a cylindrical inner circumference shape for accommodating the coating body 24, and an engaging step portion 26a for inserting the pipe joint 30 is formed on the inner circumference of the central portion. Further, an annular uneven portion 26b for fitting and fixing the cap 28 is formed on the outer peripheral surface of the front shaft 26.

[0113] The front side of the engaging step portion 26a of the front shaft 26 is the inner circumference of the rear portion, and a plurality of anti-rotation ribs 38 for preventing rotation around a vertical groove are formed inside the uneven portion 26b.

[0114] On the inner circumference of the front shaft 26, in front of the engaging step portion 26a, a stepped locking portion 26c against which the flange 24a of the coating body 24 abuts is formed. A groove with a triangular shape before and after the step is formed in the locking portion 26c. The groove guides the hairs of the spikelet head when the coating body 24 is attached, so that the spikelet head can be prevented from turning over (becoming reverse).

[0115] When starting to use the applicator of the embodiment from the unused state, it becomes the initial fitting state shown in FIG. 21, the permanent fitting state shown in FIG. 22, and the temporarily pushed-in temporary fitting state shown in FIG. 22.

[0116] In the unused state, the applicator maintains an initial fitting state in which the front shaft 26 is held via the stopper ring 34 and temporarily fitted into the shaft cylinder 10 (see Fig. 1).

[0117] For starting use, first, the user removes the stopper ring 34 and sets the front shaft 26 in a state where it is not pushed into the shaft cylinder 10 side (initial fitting state). In this case, as shown in Fig. 21, the front rib 54 of the front shaft 26 abuts or is positioned forward of the temporary fitting portion 44 of the shaft cylinder 10, and the rear rib 56 falls and 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 46 of the shaft cylinder 10 is not engaged with the anti-rotation rib 38 of the front shaft 26. Therefore, the front shaft 26 can rotate freely with respect to the shaft cylinder 10. Although the rear rib 56 of the front shaft 26 falls and is positioned between the front and rear main fitting portions 42 (main fitting portions 42F, 42R), the anti-play portion 50 composed of ribs for preventing play between the main fitting portions 42F, 42R supports the rear rib 56 of the front shaft 26, so that play of the front shaft 26 can be prevented.

[0118] When preparing for use, the front shaft 26 is slightly pushed into the shaft cylinder 10 from the initial fitting state to reach the temporary fitting state shown in Fig. 23. Also in this case, the front rib 54 of the front shaft 26 abuts against the temporary fitting portion 44 of the shaft cylinder 10 and is positioned. 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 engaged with the anti-rotation rib 46 of the shaft cylinder 10, whereby the front shaft 26 and the shaft cylinder 10 are prevented from rotating.

[0119] Then, when the front shaft 26 is pushed in from the temporary fitting state of Fig. 23, the front rib 54 gets over the temporary fitting portion 44 and engages with the front main fitting portion 42F. Also, the rear rib 56 gets over the main fitting portion 42R and engages. The main fitting state shown in Fig. 22 is reached. The front shaft 26 moves in the axial direction by approximately the length of the stopper ring 34 and reaches a state of direct fitting into the shaft cylinder 10, which is the main fitting state. At the same time, the anti-rotation rib 38 of the front shaft 26 is completely inserted into the anti-rotation rib 46 of the shaft cylinder 10, and the shaft cylinder 10 can be more reliably prevented from rotating with respect to the front shaft 26.

[0120] According to the applicator of the embodiment, the main fitting portion 42 (42F, 42R) and the temporary fitting portion 44 are formed on the shaft cylinder 10, and on the inner periphery of the tip shaft 26, there are a front rib 54 for temporarily fitting with the temporary fitting portion 44 of the front end portion 10a of the shaft cylinder 10, and a front rib 54 and a rear rib 56 for main fitting with the main fitting portion 42 (42F, 42R) of the front end portion 10a are formed over substantially the entire circumference. The shaft cylinder 10 has an anti-rotation rib 46, and the tip shaft 26 has an anti-rotation rib 38.

[0121] As shown in FIG. 21, in the initial fitting state before the temporary fitting of the shaft cylinder 10 and the tip shaft 26 (before the temporary fitting portion 44 and the front rib 54 engage with each other), the anti-rotation ribs 46 and 38 of each other are not engaged with each other. It is in a state where relative rotation is possible.

[0122] On the other hand, as shown in FIG. 23, in the state of temporary fitting (where the temporary fitting portion 44 and the front rib 54 engage with each other), the anti-rotation ribs 46 and 38 of each other engage with each other, and it becomes a state of being prevented from rotating.

[0123] Furthermore, as shown in FIG. 22, in the state of main fitting (where the main fitting portion 42 (42F, 42R) and the front rib 54 and the rear rib 56 engage with each other), the tip shaft 26 and the shaft cylinder 10 are connected and can be used.

[0124] Therefore, when the user removes the tip shaft 26 in addition to the stopper ring 34 at the start of use, even if the tip shaft 26 is refitted and main-fitted, the anti-rotation ribs 46 and 38 engage with each other, so that it can be press-fitted without displacement. Therefore, liquid leakage due to insufficient press-fitting can be prevented.

[0125] In addition, since the anti-rotation rib 46 of the shaft cylinder 10 and the anti-rotation rib 38 of the tip shaft 26 engage with each other and the shaft cylinder 10 and the tip shaft 26 are in a state of being prevented from rotating, it is possible to prevent the coating body 24 formed by bundling the pen tip and fibers from being twisted when the user rotates the tip shaft 26.

[0126] In addition, since the temporary pulling-out force in the initial fitting state (the pulling-out force when the stopper ring 34 is present) can be increased, the front shaft 26 can be prevented from falling off from the shaft cylinder 10 during transportation or the like.

Industrial Applicability

[0127] The applicator of the present invention can be used for cosmetic applicators such as cosmetic products.

Explanation of Reference Numerals

[0128] 10 Shaft cylinder 10a Front end portion 10b Accommodating portion 10c Step portion 10d Stirring body 10e Fitting portion 10f Vertical rib 12 Piston 12a Body 12b Sealing portion 14 Screw shaft 14a Threaded portion 14b Fitting portion 14c Notch portion 16 Rotating cam body 16a Cam portion 16b Cam portion 16c Internal through hole 16c1 Projection 18 Transmission cam body 18a Cam portion 18b Projection portion 18c Spring 20 Pay-out body 20a Guide groove 20b Projection 20b1 Arm portion 20c Guide portion 20c1 Step portion 20d Guide projection 20e Second projection 20f Step portion 22 Screw body 22a Cylindrical portion 22a1 Window portion 22a2 Rib 22a3 Thin-walled part (inclined surface) 22a31 Step 22b Thread part 22d Flange 22e Concavo-convex 22f Guide groove 24 Coating body 24a Flange 26 Front shaft 28 Cap 30 Pipe joint 32 Pipe 34 Stopper ring 36 Seal joint 36a Seal ball 36b Small-diameter part 36c Convex part 36d Flange part 38 Anti-rotation rib around the shaft cylinder 42 Main fitting part 44 Temporary fitting part 46 Anti-rotation rib around the front shaft 50 Anti-play part 54 Front rib 56 Rear rib A Pay-out mechanism

Claims

[Claim 1] The invention described herein.

Images