Fittings

Abstract

To provide a joint which can be easily mounted to a gas bomb.SOLUTION: A joint 1 includes a cylindrical retainer 2 opened to both ends, a nut 3 provided at one end of the retainer 2 rotatably in the peripheral direction, a linear mover 4 provided at the other end of the retainer 2 movably in the axial direction, a shaft member 5 provided in the retainer 2 so that a spiral groove 51 is formed in the outer peripheral face, a drum 6 on the inner peripheral face of which drum inner teeth 611 are formed, a guide ring 7 provided between the shaft member 5 and the drum 6 so as to mesh with both of the spiral groove 51 and the drum inner teeth 611 for converting the linear motion of the linear mover 4 into rotary motion to be transmitted to the drum 6, and a planetary gear mechanism 8 for transmitting the rotary motion transmitted to the drum 6 by the guide ring 7, to the nut 3.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The present invention relates to a joint.

Background Art

[0002] Patent Document 1 discloses attaching a joint to a gas cylinder by screwing.

Prior Art Document

Patent Document

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, with the joint described in Patent Document 1, after attaching the joint to the gas cylinder by hand tightening, it was necessary to tighten the joint on the gas cylinder with a tool such as a wrench. For this reason, there was a problem that the attachment of the joint to the gas cylinder could not be easily performed.

[0005] The present invention has been made paying attention to this problem, and an object thereof is to provide a joint that can be easily attached to a gas cylinder.

Means for Solving the Problems

[0006] According to one aspect of the present invention, a coupling for attachment to a gas cylinder is provided, comprising: a cylindrical retainer with openings at both ends; a nut provided at one end of the retainer so as to be rotatable in the circumferential direction of the retainer; a cylindrical linear mover provided at the other end of the retainer so as to be movable along the axial direction of the retainer; a shaft member provided inside the retainer, located on the inner circumference side of the linear mover and having a helical guide formed on its outer circumference; a drum provided between the retainer and the shaft member so as to be rotatable in the circumferential direction, having drum internal teeth and drum gears formed on its inner circumference and outer circumference at its tip, respectively; a linear-to-rotational motion conversion member provided between the shaft member and the drum so as to mesh with both the helical guide and the drum internal teeth, and converting the linear motion of the linear mover into rotational motion and transmitting it to the drum; and a planetary gear mechanism that transmits the rotational motion transmitted to the drum by the linear-to-rotational motion conversion member to the nut. [Effects of the Invention]

[0007] According to this embodiment, the fitting can be easily attached to the gas cylinder. [Brief explanation of the drawing]

[0008] [Figure 1] Figure 1 is a side view showing a joint according to the first embodiment. [Figure 2] Figure 2 is a cross-sectional view taken along the line II-II in Figure 1. [Figure 3A] Figure 3A is a cross-sectional view along the line IIIA-IIIA in Figure 2. [Figure 3B] Figure 3B is a cross-sectional view along the line IIIB-IIIB in Figure 2. [Figure 3C] Figure 3C is a cross-sectional view along the line IIIC-IIIC in Figure 2. [Figure 3D] Figure 3D is a cross-sectional view along the IIID-IIID line in Figure 2. [Figure 3E] Figure 3E is a cross-sectional view along the line IIIE-IIIE in Figure 2. [Figure 3F]FIG. 3F is a cross-sectional view taken along line IIIF-IIIF in FIG. 2. [Figure 4A] FIG. 4A is a partial longitudinal cross-sectional view showing the unlocked state of the linear mover of the joint according to the first modification. [Figure 4B] FIG. 4B is a partial longitudinal cross-sectional view showing the locked state of the linear mover of the joint according to the first modification. [Figure 5] FIG. 5 is a longitudinal cross-sectional view showing the joint according to the second modification. [Figure 6A] FIG. 6A is a cross-sectional view taken along line VIA-VIA in FIG. 5. [Figure 6B] FIG. 6B is a cross-sectional view taken along line VIB-VIB in FIG. 5. [Figure 7] FIG. 7 is a side view showing the joint according to the second embodiment. [Figure 8] FIG. 8 is a cross-sectional view taken along line VIII-VIII in FIG. 7. [Figure 9A] FIG. 9A is a cross-sectional view taken along line IXA-IXA in FIG. 8. [Figure 9B] FIG. 9B is a cross-sectional view taken along line IXB-IXB in FIG. 8. [Figure 9C] FIG. 9C is a cross-sectional view taken along line IXC-IXC in FIG. 8. [Figure 9D] FIG. 9D is a cross-sectional view taken along line IXD-IXD in FIG. 8.

BEST MODE FOR CARRYING OUT THE INVENTION

[0009] Hereinafter, embodiments of the present invention (hereinafter referred to as the present embodiments) will be described with reference to the accompanying drawings. In this specification, the same reference numerals are given to the same elements throughout.

[0010] (First Embodiment) [Configuration of Joint] First, the configuration of the joint 1 according to the first embodiment will be described with reference to FIGS. 1 to 3F.

[0011] FIG. 1 is a side view showing the joint 1 according to the first embodiment. FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1. FIG. 3A is a cross-sectional view taken along line IIIA-IIIA in FIG. 2. FIG. 3B is a cross-sectional view taken along line IIIB-IIIB in FIG. 2. FIG. 3C is a cross-sectional view taken along line IIIC-IIIC in FIG. 2. FIG. 3D is a cross-sectional view taken along line IIID-IIID in FIG. 2. FIG. 3E is a cross-sectional view taken along line IIIE-IIIE in FIG. 2. FIG. 3F is a cross-sectional view taken along line IIIF-IIIF in FIG. 2.

[0012] As shown in FIGS. 1 and 2, the joint 1 according to the first embodiment is a joint that connects a gas cylinder (specifically, the gas supply port of the gas cylinder) (not shown) and the pipe P (specifically, the end portion P1 of the pipe P) by being attached to the gas supply port of the gas cylinder. A male thread is formed on the outer peripheral surface of the gas supply port of the gas cylinder. A flange P2 is provided at the end portion P1 of the pipe P, and a gasket (not shown) is provided at the tip of the flange P2. The male thread of the gas supply port is formed so as to be capable of being screwed with the female thread 311 of the nut 3 described later.

[0013] Then, in a state where a gasket is provided on the flange P2 of the pipe P through which the joint 1 is inserted, the male thread of the gas supply port of the gas cylinder and the female thread 311 of the nut 3 are screwed together, and by crushing the gasket, the gap between the pipe P and the gas supply port of the gas cylinder is sealed with the gasket, and the gas cylinder and the pipe P can be joined together.

[0014] As shown in FIGS. 1 to 3F, the joint 1 includes a retainer 2, a nut 3, a linear mover 4, a cylindrical (specifically, a cylindrical) shaft member 5, a drum 6, a guide ring 7 as a linear-rotary motion conversion member, an annular (specifically, an annular) bearing O, and a planetary gear mechanism 8. A part of the retainer 2, the nut 3, the linear mover 4, the shaft member 5, the drum 6, the guide ring 7, the bearing O, and the planetary gear mechanism 8 are provided coaxially. Further, the retainer 2, the nut 3, the linear mover 4, the shaft member 5, the drum 6, the guide ring 7, the planetary gear mechanism 8, and the bearing O are made of metal.

[0015] As shown in Figure 2, the retainer 2 is a housing that accommodates a part of the nut 3, a part of the linear slider 4, a shaft member 5, a drum 6, a guide ring 7, a bearing O, and a planetary gear mechanism 8. Specifically, as shown in Figure 2, the retainer 2 has a cylindrical portion 21 extending in the vertical direction (i.e., the axial direction of the retainer 2), a ring portion 22 integrally formed with the cylindrical portion 21 so as to be located on the inner circumference side of the upper end as one end of the cylindrical portion 21, an internal gear 23 (which constitutes the planetary gear mechanism 8) formed on the inner circumference surface of the cylindrical portion 21 adjacent to the ring portion 22, and an annular (specifically, circular) cover portion 24 detachably provided at the lower end as the other end of the cylindrical portion 21.

[0016] A first opening 221 is formed on the inner circumference of the ring portion 22, and a second opening 241 is formed on the inner circumference of the annular lid portion 24. In other words, the retainer 2 is formed in a cylindrical shape (specifically, a cylindrical shape) with openings at both ends. Also, as shown in Figure 1, a guide groove (not shown) is formed on the inner circumference of the lid portion 24 to guide the linear projection 42 of the linear mover 4, which will be described later, so that it can move along the vertical direction.

[0017] As shown in Figure 2, nut 3 is a nut that screws onto the gas supply port of the gas cylinder, as described above. Nut 3 is provided on the upper end of retainer 2 so as to be rotatable in the circumferential direction (hereinafter also simply referred to as the circumferential direction) of retainer 2.

[0018] Specifically, the nut 3 has a cylindrical nut body 31 that protrudes from the first opening 221 of the ring portion 22, and a planetary gear housing portion 32 (which constitutes the planetary gear mechanism 8) that houses a plurality (four in this case) of planetary gears 85, which will be described later in the planetary gear mechanism 8, and guides them so that they can revolve around the sun gear 84, which will be described later in the planetary gear mechanism 8. The nut body 31 and the planetary gear housing portion 32 are integrally formed.

[0019] As shown in Figure 2, the lower end of the ring portion 22 abuts against the upper end of the planetary gear housing portion 32, thereby restricting the upward movement of the nut 3. In other words, the ring portion 22 functions to restrict the upward movement of the nut 3. This reliably prevents the nut 3 from falling off the upper end of the retainer 2.

[0020] As shown in Figure 2, a female thread 311 is formed on the inner circumferential surface of the nut body 31, which engages with the male thread of the gas supply port. A shaft member insertion hole 321 is formed in the center of the planetary gear housing section 32, through which the shaft member 5 is inserted. In addition, a plurality of (in this case, four) housing chambers 322 are formed in the portion of the planetary gear housing section 322 located on the outer circumferential side of the shaft member insertion hole 321, each housing a plurality of planetary gears 85.

[0021] As shown in Figure 2, the linear movable element 4 is a cylindrical linear movable element provided at the lower end of the retainer 2 so as to be movable in the vertical direction. The linear movable element 4 has an insertion portion 41 that passes through the second opening 241 of the lid portion 24, a straight projection 42 (see Figure 1) provided on the outer circumferential surface of the insertion portion 41 so as to engage with the guide groove of the lid portion 24 and extend in the vertical direction, and an annular (specifically, circular) flange portion 43 provided at the upper end as the tip of the insertion portion 41. The insertion portion 41, the straight projection 42, and the flange portion 43 are integrally formed.

[0022] The insertion portion 41 is provided so that its inner circumferential surface can slide against the outer circumferential surface of the shaft member 5 when it moves along the vertical direction. Since the linear projection 42 is engaged with the guide groove, the linear mover 4 can move linearly along the vertical direction relative to the retainer 2 (or shaft member 5) without rotating relative to the retainer 2 (or shaft member 5). The flange portion 43 has a flange body 431 that protrudes radially from the retainer 2 and a press-fit portion 432 that extends upward (towards the nut 3 side) at the outer circumferential edge of the flange body 431.

[0023] As shown in Figure 2, the shaft member 5 is provided (fixed) within the retainer 2 via a disc 81 of the planetary gear mechanism 8, which will be described later, so as to be located on the inner circumference side of the linear mover 4 (specifically, the insertion portion 41 and the flange portion 43). The shaft member 5 has a lower section 5A located below the disc 81 and an upper section 5B located above the disc 81. A helical groove 51 is formed on the outer circumferential surface of the lower section 5A to serve as a helical guide. The upper section 5B is formed to abut against the lower end of the flange P2 of the pipe P. The pipe P is inserted through the inner circumference side of the cylindrical shaft member 5. The shaft member 5 and the disc 81 are integrally formed.

[0024] As shown in Figure 2, the drum 6 is a covered cylindrical member provided between the retainer 2 and the shaft member 5 so as to be circumferentially rotatable. The drum 6 has a drum body 61 extending in the vertical direction, an annular drum cover 62 (i.e., the tip of the drum 6) provided at the upper end of the drum body 61 as one end, and a drum gear 63 extending upward on the inner circumferential edge of the drum cover 62. The drum body 61, drum cover 62, and drum gear 63 are integrally formed.

[0025] Internal drum teeth 611 are formed on the inner circumferential surface of the drum body 61. The lower end of the drum body 61 abuts against the upper end of the cover portion 24 of the retainer 2, thereby restricting the downward movement of the drum 6. In other words, the cover portion 24 performs the function of restricting the downward movement of the drum 6. This reliably prevents the drum 6 from falling off the lower end of the retainer 2. The drum gear 63 is rotatably mounted around the shaft member 5 (specifically, the lower portion 5A).

[0026] As shown in Figure 2, the guide ring 7 is a guide ring that converts the linear motion of the linear mover 4 into rotational motion and transmits it to the drum 6. The guide ring 7 is housed on the inner circumference side of the drum 6. The guide ring 7 has an annular guide ring body 71 and an annular bearing holding portion 72 that extends from the lower end of the guide ring body 71 such that its outer diameter is smaller than the outer diameter of the guide ring body 71. The guide ring body 71 and the bearing holding portion 72 are integrally formed.

[0027] As shown in Figure 3A, the inner circumferential surface of the guide ring body 71 is provided with a plurality (in this case, three) of protrusions 711 that engage with the helical groove 51, spaced at predetermined intervals in the circumferential direction. As a result, the guide ring 7 can move along the vertical direction while rotating circumferentially, guided by the helical groove 51.

[0028] In the first embodiment, the projection 711 is provided on the inner circumferential surface of the guide ring body 71, but is not limited to this. For example, it may be provided on the inner circumferential surface of the bearing retaining portion 72, or it may be provided on both the guide ring body 71 and the bearing retaining portion 72.

[0029] External guide ring teeth 712 that mesh with the internal drum teeth 611 are formed on the outer circumferential surface of the guide ring body 71. This allows the rotation (rotational motion) of the guide ring 7 to be transmitted to the drum 6.

[0030] The bearing O is a radial bearing, in which the outer ring is fixed so as to be press-fitted into the inner circumference of the flange portion 43 (specifically, the press-fitted portion 432), and the inner ring is fitted to the outer circumference of the bearing holding portion 72 of the guide ring 7. As a result, the inner ring of the bearing O rotates circumferentially together with the guide ring 7, but the flange portion 43 can move only vertically together with the outer ring of the bearing O. Furthermore, when the linear mover 4 is moved linearly downward relative to the shaft member 5 (i.e., when the linear mover 4 is pulled from the retainer 2), the outer ring of the bearing O is press-fitted into the inner circumference of the flange portion 43 of the linear mover 4, so the guide ring 7 can move downward while rotating circumferentially relative to the linear mover 4.

[0031] Specifically, the bearing O is press-fitted between the inner side of the flange portion 43 and the outer side of the bearing retaining portion 72 such that the inner ring (inner circumferential surface) and outer ring (outer circumferential surface) contact the outer circumferential surface of the bearing retaining portion 72 and the inner circumferential surface of the press-fitted portion 432, respectively. As a result, the linear mover 4 moves linearly along the vertical direction relative to the retainer 2 (or shaft member 5) without rotating relative to the retainer 2 (or shaft member 5), while the guide ring 7 can rotate and move smoothly.

[0032] Furthermore, it is preferable that the lower end surface of the guide ring body 71 and the upper end surface of the flange portion 43 do not come into contact. By preventing these surfaces from coming into contact, the guide ring 7 can rotate and move smoothly.

[0033] The planetary gear mechanism 8 is a planetary gear mechanism that transmits the rotational motion transmitted to the drum 6 by the guide ring 7 to the nut 3. The planetary gear mechanism 8 is composed of a disc 81 as a plate material, a plurality (four in this case) of first transmission gears 82, a plurality (four in this case) of second transmission gears 83, a sun gear 84, an internal gear 23, a plurality (four in this case) of planetary gears 85, and a planetary gear housing 32. The configuration of the internal gear 23 and the planetary gear housing 32 has been explained, so their explanations will be omitted here.

[0034] As shown in Figures 2 and 3C, the disc 81 is provided between the drum 6 and the nut 3. The outer edge of the disc 81 is provided so as to be connected (fixed) to the cylindrical portion 21 of the retainer 2 by, for example, screw fastening. A through hole 811 through which the pipe P is inserted is formed in the center of the disc 81. In addition, in the portion of the disc 81 located on the outer circumference of the through hole 811, a plurality of (in this case, four) through holes 812 are formed at predetermined intervals in the circumferential direction to support a common rotation shaft 86 which serves as the rotation axis for a plurality of (in this case, four) first transmission gears 82 and second transmission gears 83.

[0035] Furthermore, by integrating the member connecting the shaft member 5 and the retainer 2, and the member supporting the multiple common rotating shafts 86 of the multiple first transmission gears 82 and the multiple second transmission gears 83, into the disc 81, the coupling 1 can be simplified.

[0036] Each of the multiple first transmission gears 82 is meshed with the drum gear 63 located in the center of them. This allows the rotation (rotational motion) of the drum 6 to be transmitted to the multiple first transmission gears 82. Furthermore, the multiple first transmission gears 82 are positioned between the drum 6 (specifically, the drum body 61) and the disc 81.

[0037] Each of the multiple second transmission gears 83 is meshed with the sun gear 84 located in the center. Furthermore, the multiple second transmission gears 83 are positioned between the disc 81 and the nut 3.

[0038] The first transmission gear 82 and the second transmission gear 83 share a common rotating shaft 86. That is, the common rotating shaft 86 protrudes from both ends of the disc 81. The first transmission gear 82 and the second transmission gear 83 are supported at the upper and lower ends of the disc 81, respectively, via the common rotating shaft 86, so as to be rotatable in the circumferential direction. As a result, the first transmission gear 82 and the second transmission gear 83 can rotate at the same angular velocity. Consequently, the rotation (rotational motion) of multiple first transmission gears 82 can be transmitted to multiple second transmission gears 83 via multiple common rotating shafts 86.

[0039] The sun gear 84 is mounted on the outer circumference of the upper part 5B of the shaft member 5 (specifically, the upper part 5B) so as to be rotatable about the axis of the shaft member 5. In contrast, the drum gear 63 is mounted below the disc 81. By mounting the sun gear 84 and the drum gear 63 above and below the disc 81, respectively (i.e., mounting the sun gear 84 and the drum gear 63 spaced apart), rotational interference between the sun gear 84 and the drum gear 63 can be reliably prevented. The sun gear 84 and the nut 3 are mounted coaxially. The rotation (rotational motion) of the drum 6 is transmitted to the sun gear 84 via a plurality of first transmission gears 82 and a plurality of second transmission gears 83.

[0040] As shown in Figures 3E and 3F, the multiple planetary gears 85 are connected to the nut 3 via multiple planetary gear rotation shafts 851 so as to mesh with both the sun gear 84 and the internal gear 23. This allows the rotation (rotational motion) of the sun gear 84 to be transmitted to the multiple planetary gears 85. As a result, the multiple planetary gears 85 can rotate on their own axis around the multiple planetary gear rotation shafts 851 while revolving around the sun gear 84.

[0041] Furthermore, each of the multiple planetary gears 85 is connected to the nut 3 (specifically, the planetary gear housing 32) via multiple planetary gear rotating shafts 851, so that each of them is housed in one of the multiple housing chambers 322 of the planetary gear housing 32. The multiple planetary gear rotating shafts 851 are supported by the planetary gear housing 32. As a result, the revolution (rotational motion) of the multiple planetary gears 85 is transmitted to the nut 3 via the multiple planetary gear rotating shafts 851.

[0042] According to the planetary gear mechanism 8 described above, the rotation (rotational motion) transmitted from the linear mover 4 to the drum 6 by the guide ring 7 is transmitted to the nut 3 via a plurality of first transmission gears 82, a plurality of second transmission gears 83, a sun gear 84, and a plurality of planetary gears 85, thereby amplifying the rotational force of the drum 6 and transmitting it to the nut 3.

[0043] Furthermore, the planetary gear mechanism 8 does not use the drum gear 63 as the sun gear, but instead provides a separate sun gear 84 that meshes with multiple planetary gears 85, as well as multiple first transmission gears 82 and multiple second transmission gears 83 that connect the drum gear 63 and the sun gear 84. Therefore, compared to a configuration in which the drum gear 63 is simply the sun gear (i.e., a configuration without multiple first transmission gears 82, multiple second transmission gears 83, and sun gear 84), the rotational force of the drum 6 can be further amplified and transmitted to the nut 3.

[0044] Furthermore, since the planetary gear mechanism 8 does not have a restricting part that restricts the rotation of the nut 3, the planetary gear mechanism 8 allows the nut 3 to rotate without restriction.

[0045] [Attaching and detaching fittings to gas cylinders] Next, the operation of attaching and detaching the connector 1 to the gas cylinder in the first embodiment will be described with reference to Figures 2 to 3F.

[0046] First, we will explain the procedure for attaching fitting 1 to the gas cylinder.

[0047] As shown in Figure 2, when the linear mover 4 is moved linearly upward relative to the shaft member 5 (i.e., when the linear mover 4 is pressed against the guide ring 7), the guide ring 7 moves upward while rotating counterclockwise, guided by the spiral groove 51, as indicated by the arrow in Figure 3A.

[0048] The counterclockwise rotation (rotational motion) of the guide ring 7 is transmitted to the drum 6 through the meshing of the external teeth 712 of the guide ring and the internal teeth 611 of the drum. In other words, the linear motion of the linear mover 4 is converted into rotational motion by the guide ring 7 and transmitted to the drum 6. Then, as shown by the arrows in Figure 3B, the clockwise rotation (rotational motion) transmitted to the drum 6 by the guide ring 7 is transmitted to the multiple first transmission gears 82 through the meshing of the drum gear 63 and the multiple first transmission gears 82.

[0049] Then, as shown by the arrows in Figure 3C, the clockwise rotation (rotational motion) of the multiple first transmission gears 82 is transmitted to the multiple second transmission gears 83 via the multiple common rotating shafts 86. Then, as shown by the arrows in Figure 3D, the clockwise rotation (rotational motion) of the multiple second transmission gears 83 is transmitted to the sun gear 84 through the meshing of the multiple second transmission gears 83 with the sun gear 84.

[0050] As shown by the arrows in Figure 3E, the counterclockwise rotation (rotational motion) of the sun gear 84 is transmitted to the multiple planetary gears 85 through the meshing of the sun gear 84 with the multiple planetary gears 85. In this case, each of the multiple planetary gears 85 rotates clockwise around the multiple planetary gear rotation axes 851 while revolving counterclockwise around the sun gear 84. As shown by the arrows in Figure 3F, the counterclockwise revolution (rotational motion) of the multiple planetary gears 85 is transmitted to the nut 3 via the multiple planetary gear rotation axes 851. Therefore, the counterclockwise rotation of the nut 3 allows the female thread 311 of the nut 3 to be tightened against the male thread of the gas supply port of the gas cylinder.

[0051] As described above, simply by moving the linear slider 4 upward relative to the shaft member 5, the linear motion of the linear slider 4 is converted into counterclockwise rotational motion by the guide ring 7 and transmitted to the drum 6. The counterclockwise rotational force transmitted to the drum 6 is amplified by the planetary gear mechanism 8 and transmitted to the nut 3. Therefore, the fitting 1 can be easily attached to the gas cylinder without using tools such as a wrench. In other words, the fitting 1 can be attached to the gas cylinder with a single touch.

[0052] Next, we will explain the operation of detaching fitting 1 from the gas cylinder. Note that the operation of detaching fitting 1 from the gas cylinder is the exact opposite of the operation of attaching fitting 1 to the gas cylinder, so we will omit the details.

[0053] By simply moving the linear slider 4 downwards relative to the shaft member 5 (i.e., pulling the linear slider 4 away from the retainer 2), the linear motion of the linear slider 4 is converted into clockwise rotational motion by the guide ring 7 and transmitted to the drum 6. The clockwise rotational force transmitted to the drum 6 is amplified by the planetary gear mechanism 8 and transmitted to the nut 3. As a result, the fitting 1 can be easily detached from the gas cylinder without using tools such as a wrench. In other words, the fitting 1 can be detached from the gas cylinder with a single touch.

[0054] [Effects and Effects] Next, the effects and benefits of the first embodiment will be described.

[0055] The joint 1 according to the first embodiment is a joint 1 for attachment to a gas cylinder, and comprises: a cylindrical retainer 2 with openings at both ends; a nut 3 provided at the upper end of the retainer 2 so as to be rotatable in the circumferential direction of the retainer 2; a cylindrical linear mover 4 provided at the lower end of the retainer 2 so as to be movable along the axial direction of the retainer 2; a cylindrical shaft member 5 provided inside the retainer 2, located on the inner circumference side of the linear mover 4 and having a helical groove 51 formed on its outer circumference; a drum 6 provided between the retainer 2 and the shaft member 5 so as to be rotatable in the circumferential direction, having drum internal teeth 611 formed on its inner circumference; a guide ring 7 provided between the shaft member 5 and the drum 6 so as to mesh with both the helical groove 51 and the drum internal teeth 611, which converts the linear motion of the linear mover 4 into rotational motion and transmits it to the drum 6; and a planetary gear mechanism 8 which transmits the rotational motion transmitted to the drum 6 by the guide ring 7 to the nut 3.

[0056] With this configuration, simply by moving the linear slider 4 upward relative to the shaft member 5, the linear motion of the linear slider 4 is converted into counterclockwise rotational motion by the guide ring 7 and transmitted to the drum 6. The counterclockwise rotational force transmitted to the drum 6 is amplified by the planetary gear mechanism 8 and transmitted to the nut 3. As a result, the fitting 1 can be easily attached to the gas cylinder without using tools such as a wrench. In other words, the fitting 1 can be attached to the gas cylinder with a single touch.

[0057] Furthermore, in the first embodiment, the inner and outer circumferential surfaces of the guide ring 7 are formed with projections 711 that engage with the helical grooves 511 and external guide ring teeth 712 that mesh with the internal drum teeth 611, respectively. The guide ring 7 rotates in the circumferential direction while moving upward due to the pressure exerted by the linear motion of the linear mover 4.

[0058] With this configuration, the unidirectional linear motion of the linear moving element 4 can be easily converted into rotational motion and transmitted to the drum 6, making it easy to attach the fitting 1 to the gas cylinder.

[0059] Furthermore, in the first embodiment, an annular flange portion 43 is provided at the tip of the linear slider 4, and the joint 1 further includes a bearing O in which the outer ring is press-fitted into the inner circumference of the flange portion 43 and the inner ring is fitted into the outer circumference of the bearing holding portion 72.

[0060] In this configuration, the inner ring of bearing O rotates circumferentially together with the guide ring 7, but the flange portion 43 can only move vertically together with the outer ring of bearing O. Furthermore, when the linear mover 4 is moved linearly downward relative to the shaft member 5 (i.e., when the linear mover 4 is pulled from the retainer 2), the outer ring of bearing O is press-fitted to the inner circumference of the flange portion 43 of the linear mover 4, so the guide ring 7 can move downward while rotating circumferentially relative to the linear mover 4.

[0061] Therefore, simply by moving the linear slider 4 downwards relative to the shaft member 5 (i.e., pulling the linear slider 4 from the retainer 2), the linear motion of the linear slider 4 is converted into clockwise rotational motion by the guide ring 7 and transmitted to the drum 6. The clockwise rotational force transmitted to the drum 6 is amplified by the planetary gear mechanism 8 and transmitted to the nut 3. As a result, the fitting 1 can be easily detached from the gas cylinder without using tools such as a wrench. In other words, the fitting 1 can be detached from the gas cylinder with a single touch.

[0062] In the first embodiment, a drum gear 63 is provided at the tip of the drum 6, and the planetary gear mechanism 8 includes a first transmission gear 82 that meshes with the drum gear 63, a second transmission gear 83 having a common rotation axis 86 that is common to the common rotation axis 86 of the first transmission gear 82, a sun gear 84 that meshes with the second transmission gear 83, an internal gear 23 formed on the inner circumferential surface of the retainer 2, and a planetary gear 85 connected to the nut 3 so as to mesh with both the sun gear 84 and the internal gear 23.

[0063] With this configuration, the planetary gear mechanism 8 does not use the drum gear 63 as the sun gear, but instead provides a separate sun gear 84 that meshes with the planetary gear 85, and also provides a first transmission gear 82 and a second transmission gear 83 that connect the drum gear 63 and the sun gear 84. Therefore, compared to a configuration in which the drum gear 63 is simply the sun gear (i.e., a configuration without the first transmission gear 82, the second transmission gear 83, and the sun gear 84), the rotational force of the drum 6 can be further amplified and transmitted to the nut 3.

[0064] In the first embodiment, the planetary gear mechanism 8 further includes a disc 81 provided between the drum 6 and the nut 3 to support a common rotating shaft 86 of the first transmission gear 82 and the second transmission gear 83, and the shaft member 5 is connected to the retainer 2 via the disc 81.

[0065] With this configuration, the member connecting the shaft member 5 and the retainer 2, and the member supporting the common rotating shaft 86 of the first transmission gear 82 and the second transmission gear 83 are integrated into the disc 81, thereby simplifying the coupling 1.

[0066] (First variation) Next, the joint 1 according to the first modified example will be described with reference to Figures 4A and 4B. In this first modified example, points similar to those of the first embodiment described above will be omitted, and the points that differ mainly from the first embodiment described above will be explained.

[0067] Figure 4A is a partial longitudinal cross-sectional view showing the unlocked state of the linear mover 4 of the joint 1 according to the first modified example. Figure 4B is a partial longitudinal cross-sectional view showing the locked state of the linear mover 4 of the joint 1 according to the first modified example.

[0068] In the first embodiment described above, the coupling 1 comprises a retainer 2, a nut 3, a linear slider 4, a shaft member 5, a drum 6, a guide ring 7, a bearing O, and a planetary gear mechanism 8. However, it is not limited to this, and for example, in addition to the retainer 2, nut 3, linear slider 4, shaft member 5, drum 6, guide ring 7, bearing O, and planetary gear mechanism 8, it may further include a locking mechanism 9 (see Figures 4A and 4B) as in the first modified example.

[0069] As shown in Figures 4A and 4B, in the first modified example, the locking mechanism 9 is a locking mechanism that restricts the movement of the linear mover 4 when the nut 3 is tightened to the gas cylinder. The locking mechanism 9 has a claw 44 as the locked part, a claw housing recess 243, a locking part 91, a coil spring 92 as the biasing part, and a support part 93.

[0070] The claws 44 are provided on the outer circumferential surface of the insertion portion 41 that is exposed from the retainer 2. The claws 44 also have a taper 441 that decreases in diameter from bottom to top.

[0071] The claw-receiving recess 243 is located on the outer circumference of the second opening 241 and is formed in the lid portion 24 so as to be recessed from bottom to top.

[0072] The locking portion 91 is supported by the support portion 93 via a coil spring 92 so as to be movable along the radial direction of the retainer 2. The locking portion 91 is also provided with a sliding portion 911 that can slide against the taper 441 of the claw 44 when the linear mover 4 moves. The coil spring 92 is housed in the support portion 93. The coil spring 92 also biases the sliding portion 911 to move toward the insertion portion 41.

[0073] As shown by the arrow in Figure 4A, when the linear mover 4 is moved linearly upward relative to the shaft member 5, the taper 441 presses against the biasing force of the coil spring 92, causing the sliding portion 911 to move away from the insertion portion 41.

[0074] As shown in Figure 4B, when the linear movement of the linear mover 4 occurs and the claw 44 is engaged in the claw housing recess 243 (i.e., the nut 3 is tightened to the gas cylinder), the pressure on the sliding part 911 by the taper 441 is released, and the sliding part 911 moves towards the insertion part 41 due to the biasing force of the coil spring 92 (see arrow in Figure 4B). Then, the downward movement of the linear mover 4 is restricted by the sliding part 911, and the linear mover 4 is locked. As a result, loosening of the nut 3 on the gas cylinder can be suppressed.

[0075] In the first modified example, the joint 1 further includes a locking mechanism 9 that restricts the movement of the linear slider 4 when the nut 3 is tightened onto the gas cylinder.

[0076] This configuration makes it possible to suppress the loosening of the nut 3 on the gas cylinder.

[0077] (Second variation) Next, the joint 1 according to the second modified example will be described with reference to Figures 5 to 6B. In the second modified example, points similar to those of the first embodiment described above will be omitted, and the points that differ mainly from the first embodiment described above will be explained.

[0078] Figure 5 is a longitudinal cross-sectional view showing joint 1 according to the second modified example. Figure 6A is a cross-sectional view along the VIA-VIA line in Figure 5. Figure 6B is a cross-sectional view along the VIB-VIB line in Figure 5.

[0079] In the first embodiment described above, the planetary gear mechanism 8 is configured to have a disc 81, a plurality of first transmission gears 82, a plurality of second transmission gears 83, a sun gear 84, an internal gear 23, a plurality of planetary gears 85, and a planetary gear housing 32. However, it is not limited to this configuration, and for example, as in the second modified example, it may be configured to have an internal gear 23, a plurality (in this case, three) of planetary gears 85, and a planetary guide 87 (see Figures 5 to 6B).

[0080] In the second modified example, as shown in Figure 5, the nut 3 comprises a nut body 31, a nut flange 33 provided on the outer circumference of the lower end of the nut body 31, and a plurality (in this case, three) of protruding poles 34 as connecting parts that protrude from the lower end of the nut flange 33. The nut body 31, the nut flange 33, and the plurality of protruding poles 34 are integrally formed.

[0081] As shown in Figures 5 and 6B, the multiple protruding poles 34 are provided on the nut flange 33 at predetermined intervals in the circumferential direction. The multiple protruding poles 34 connect the nut 3 (specifically, the nut flange 33) to the multiple planetary gears 85. In addition, each of the multiple protruding poles 34 also serves as the axis of rotation for the multiple planetary gears 85.

[0082] As shown in Figures 5 and 6B, the upper end of the retainer 2 (specifically, the cylindrical portion 21) is provided with a disc portion 25 as a plate portion, instead of the ring portion 22 of the first embodiment described above. A central hole 251 is formed in the center of the disc portion 25 through which the pipe P is inserted. The disc portion 25 also has multiple (in this case, three) elongated holes 252 through which multiple protruding poles 34 pass. The multiple elongated holes 252 are formed to be spaced at predetermined intervals in the circumferential direction and to extend along the circumferential direction. The multiple elongated holes 252 restrict the rotation range of the nut 3.

[0083] As shown in Figures 5 and 6B, the disc portion 25 has a connecting region 253 located on the inner circumference side of the multiple elongated holes 252, an outer circumference region 254 located on the outer circumference side of the multiple elongated holes 252, and a plurality (in this case, three) of communication regions 255 formed between adjacent elongated holes 252 and connecting the connecting region 253 and the outer circumference region 254.

[0084] The connecting region 253 is held in the outer peripheral region 254 by multiple communication regions 255. The shaft member 5 and the disc portion 25 are connected in the held connecting region 253 such that the central hole 251 and the inner circumference of the shaft member 5 are in communication. The shaft member 5, the disc portion 25, and the cylindrical portion 21 are integrally formed.

[0085] In this way, since the shaft member 5 is connected to the cylindrical portion 21 via the disc portion 25 provided at the upper end of the retainer 2, the degree of freedom in the layout within the retainer 2 for other members (for example, the planetary gear mechanism 8, etc.) is improved, and the assembly of other members (for example, the planetary gear mechanism 8, etc.) becomes easier.

[0086] Furthermore, since the shaft member 5 and the disc portion 25 are connected in the connecting region 253, the radial size of the connection point on the shaft member 5 can be reduced compared to a configuration in which the shaft member 5 and the disc portion 25 are connected in the outer peripheral region 254. As a result, the radial size reduction of the shaft member 5 improves the freedom of layout for providing the planetary gear mechanism 8.

[0087] As shown in Figures 5 and 6A, the multiple planetary gears 85 are connected to the nut 3 via multiple protruding poles 34, each having multiple elongated holes 252 through them, so as to mesh with both the drum gear 63, which acts as the sun gear, and the internal gear 23. In this way, the orbital (rotational) motion of the multiple planetary gears 85 is transmitted to the nut 3 via the multiple protruding poles 34.

[0088] As shown in Figures 5 and 6A, the planetary guide 87 accommodates multiple planetary gears 85 and guides them so that they can revolve around the drum gear 63. The planetary guide 87 is provided between the drum lid 62 and the disc portion 25 of the drum 6. The planetary guide 87 is also provided on the outer circumference of the shaft member 5 so as to be rotatable in the circumferential direction. A shaft member insertion hole 871 is formed in the center of the planetary guide 87 through which the shaft member 5 is inserted. In addition, multiple (in this case, three) planetary gear housing chambers 872 are formed in the portion of the planetary guide 87 located on the outer circumference side of the shaft member insertion hole 821, each housing multiple planetary gears 85. Multiple protruding poles 34 are supported by the planetary guide 87. As a result, the planetary guide 87 can rotate circumferentially together with the nut 3 as the multiple planetary gears 85 revolve.

[0089] The rotation (rotational motion) transmitted to the drum 6 by the guide ring 7 is then transmitted to the multiple planetary gears 85 through the meshing of the drum gear 63 with the multiple planetary gears 85. In this case, the multiple planetary gears 85 each rotate on their own axis around the multiple protruding poles 34 while revolving around the drum gear 63. The revolving (rotational motion) of the multiple planetary gears 85 is then transmitted to the nut 3 and the planetary guide 87 via the multiple protruding poles 34.

[0090] In the second modified example, a drum gear 63 is provided at the tip of the drum 6, and the planetary gear mechanism 8 includes an internal gear 23 formed on the inner circumferential surface of the retainer 2, and a planetary gear 85 connected to a nut 3 so as to mesh with both the drum gear 63 and the internal gear 23.

[0091] With this configuration, the planetary gear mechanism 8 is composed of an internal gear 23 and planetary gears 85, so the number of parts constituting the planetary gear mechanism 8 can be reduced compared to the planetary gear mechanism 8 of the first embodiment described above. As a result, the coupling 1 can be simplified and miniaturized.

[0092] In the second modified example, a disc portion 25 is provided at the upper end of the retainer 2, and multiple elongated holes 252 are formed in the disc portion 25, through which multiple protruding poles 34 connecting the nut 3 and multiple planetary gears 85 pass, and which extend along the circumferential direction. The disc portion 25 has a connecting region 253 located on the inner circumference side of the multiple elongated holes 252, and the shaft member 5 and the disc portion 25 are connected in the connecting region 253.

[0093] With this configuration, the shaft member 5 is connected to the cylindrical portion 21 via the disc portion 25 provided at the upper end of the retainer 2, which improves the freedom of layout within the retainer 2 for other components (e.g., planetary gear mechanism 8) and makes it easier to assemble other components (e.g., planetary gear mechanism 8).

[0094] Furthermore, since the shaft member 5 and the disc portion 25 are connected in the connecting region 253, the radial size of the connection point on the shaft member 5 can be reduced compared to a configuration in which the shaft member 5 and the disc portion 25 are connected in the outer peripheral region 254. As a result, the radial size reduction of the shaft member 5 improves the freedom of layout for providing the planetary gear mechanism 8.

[0095] (Second Embodiment) Next, the joint 1 according to the second embodiment will be described with reference to Figures 7 to 9D. In the second embodiment, points similar to those of the first embodiment described above will be omitted, and the differences from the first embodiment will be mainly described.

[0096] Figure 7 is a side view showing the joint 1 according to the second embodiment. Figure 8 is a cross-sectional view along the line VIII-VIII in Figure 7. Figure 9A is a cross-sectional view along the line IXA-IXA in Figure 8. Figure 9B is a cross-sectional view along the line IXB-IXB in Figure 8. Figure 9C is a cross-sectional view along the line IXC-IXC in Figure 8. Figure 9D is a cross-sectional view along the line IXD-IXD in Figure 8.

[0097] In the first embodiment described above, the helical guide and the linear rotational motion conversion member are composed of a helical groove 51 and a guide ring 7, respectively, but are not limited to this. For example, as in the second embodiment, they may be composed of a male screw 52 and a plurality (in this case, three) helical gears 7A (see Figures 7 to 9A).

[0098] In this case, as shown in Figures 7 to 9A, the linear moving element 4 is not the linear moving element 4 of the first embodiment described above, but rather has a cylindrical linear moving element body 41A provided on the outer circumference of the shaft member 5, a plurality of (in this case, three) straight-through holes 42A formed at predetermined intervals in the circumferential direction on the circumferential wall of the linear moving element body 41A so as to extend along the vertical direction, and a plurality of (in this case, three) notches 43A formed at predetermined intervals in the circumferential direction on the upper end of the linear moving element body 41A as the tip.

[0099] In the second embodiment, the lower end of the cylindrical portion 21 of the retainer 2 does not have a cover portion 24 (see Figure 2). Instead, as shown in Figure 8, multiple (in this case, three) engagement pins 26 are mounted on the inner circumferential surface of the lower end of the cylindrical portion 21 at predetermined intervals in the circumferential direction, each engaging with a plurality of straight holes 42A. In this way, since the multiple engagement pins 26 each engage with a plurality of straight holes 42A, the linear mover 4 can move linearly along the vertical direction relative to the retainer 2 (or shaft member 5) without rotating relative to the retainer 2 (or shaft member 5).

[0100] Furthermore, the lower end of the drum body 61 contacts the engagement pin 26, thereby restricting the downward movement of the drum 6. In other words, the engagement pin 26 functions to restrict the downward movement of the drum 6. This eliminates the need for a cover portion 24 and reliably prevents the drum 6 from falling off the lower end of the retainer 2.

[0101] As shown in Figure 8, each of the multiple notches 43A houses a plurality of screw gears 7A, each rotatably supported via a rotating shaft 71A. This allows the linear mover 4 to move linearly along the vertical direction together with the plurality of screw gears 7A supported in each of the multiple notches 43A.

[0102] The male screw 52 is formed on the outer circumferential surface of the shaft member 5.

[0103] Each of the multiple screw gears 7A is meshed with both the male screw 52 and the internal teeth 611 of the drum. As a result, as the linear movement of the linear mover 4 occurs, the multiple screw gears 7A can move vertically while rotating through their meshing with the male screw 52. In this process, the meshing of the rotating multiple screw gears 7A with the internal teeth 611 of the drum causes the drum 6 to rotate.

[0104] Thus, similar to the first embodiment described above, the multiple screw gears 7A can easily convert the two-directional linear motion of the linear slider 4 into rotational motion and transmit it to the drum 6, making it easy to attach and detach the coupling 1 to the gas cylinder.

[0105] Furthermore, since the retainer 2, nut 3, and shaft member 5 (excluding the male screw 52) of the second embodiment are the same as the retainer 2 and nut 3 of the second modified example described above, a detailed explanation of the retainer 2, nut 3, and shaft member 5 (excluding the helical groove 51) will be omitted.

[0106] Furthermore, in the first embodiment described above, the planetary gear mechanism 8 is configured to have a disc 81, a plurality of first transmission gears 82, a plurality of second transmission gears 83, a sun gear 84, an internal gear 23, a plurality of planetary gears 85, and a planetary gear housing 32. However, it is not limited to this configuration, and for example, as in the second embodiment, it may be configured to have an internal gear 23, a plurality (in this case, three) of first planetary gears 81A, a first planetary guide 82A as a planetary guide, a sun gear 83A, a plurality (in this case, three) of second planetary gears 84A and second planetary guide 85A (see Figures 7 and 9B to 9D).

[0107] As shown in Figures 8 and 9B, the multiple first planetary gears 81A mesh with both the drum gear 63 and the internal gear 23.

[0108] The first planetary guide 82A houses a plurality of first planetary gears 81A and guides them so that they can revolve around the drum gear 63. The first planetary guide 82A is provided between the drum cover 62 of the drum 6 and the second planetary guide 85A. The first planetary guide 82A is also provided on the outer circumference of the shaft member 5 so as to be rotatable in the circumferential direction.

[0109] A first through-hole 821A is formed in the center of the first planetary guide 82A, through which the shaft member 5 is inserted. In addition, a plurality of (in this case, three) first planetary gear housing chambers 822A are formed in the portion of the first planetary guide 82A located on the outer circumference side of the first through-hole 821A, each housing a plurality of first planetary gears 81A. The first rotation axes 811A of the plurality of first planetary gears 81A are supported by the first planetary guide 82A. As a result, the first planetary guide 82A can rotate in the circumferential direction in accordance with the revolution of the plurality of first planetary gears 81A.

[0110] As shown in Figure 8, the sun gear 83A is located at the tip of the first planetary guide 82A.

[0111] As shown in Figures 8, 9C, and 9D, the multiple second planetary gears 84A are connected to the nut 3 via multiple protruding poles 34 so as to mesh with both the sun gear 83A and the internal gear 23. In this way, the orbital (rotational) motion of the multiple second planetary gears 84A is transmitted to the nut 3 via the multiple protruding poles 34.

[0112] The second planetary guide 85A houses a plurality of second planetary gears 84A and guides them so that they can orbit around the sun gear 83A. The second planetary guide 85A is provided between the first planetary guide 82A and the disc portion 25. The second planetary guide 85A is also provided on the outer circumference of the shaft member 5 so as to be rotatable in the circumferential direction.

[0113] A second through-hole 851A is formed in the center of the second planetary guide 85A, through which the shaft member 5 is inserted. In addition, a plurality (in this case, three) second planetary gear housing chambers 852A are formed in the portion of the second planetary guide 85A located on the outer circumference side of the second through-hole 851A, each housing a plurality of second planetary gears 84A. The protruding poles 34, which serve as the second rotation axes of the plurality of second planetary gears 84A, are supported by the second planetary guide 85A. As a result, the second planetary guide 85A can rotate circumferentially together with the nut 3 as the plurality of second planetary gears 84A orbit.

[0114] The rotation (rotational motion) transmitted to the drum 6 by the screw gear 7A is then transmitted to the multiple first planetary gears 81A and the first planetary guide 82A through the meshing of the drum gear 63 with the multiple first planetary gears 81A. In this case, each of the multiple first planetary gears 81A rotates on its own axis around the multiple first rotation axes 811A while revolving around the drum gear 63. The first planetary guide 82A rotates circumferentially in accordance with the revolving of the multiple first planetary gears 81A.

[0115] The rotation (rotational motion) of the first planetary guide 82A is transmitted to the multiple second planetary gears 84A through the meshing of the sun gear 83A and the multiple second planetary gears 84A. In this case, the multiple second planetary gears 84A each rotate on their own axis around the multiple protruding poles 34 while revolving around the sun gear 83A. The revolving (rotational motion) of the multiple second planetary gears 84A is then transmitted to the nut 3 and the second planetary guide 85A via the multiple protruding poles 34.

[0116] Thus, since the planetary gear mechanism 8 employs a two-stage planetary gear structure having multiple first planetary gears 81A and multiple second planetary gears 84A, the rotational force of the drum 6 can be further amplified and transmitted to the nut 3.

[0117] In the second embodiment, the helical guide is composed of a male screw 52, ​​and the linear-to-rotational motion conversion member is composed of a screw gear 7A rotatably supported on the linear mover 4 so as to mesh with both the male screw 52 and the internal teeth 611 of the drum.

[0118] With this configuration, the screw gear 7A can easily convert the two-directional linear motion of the linear slider 4 into rotational motion and transmit it to the drum 6, thus facilitating the attachment and detachment of the coupling 1 to the gas cylinder.

[0119] In the second embodiment, a drum gear 63 is provided at the tip of the drum 6, and the planetary gear mechanism 8 includes an internal gear 23 formed on the inner circumferential surface of the retainer 2, a first planetary gear 81A that meshes with both the drum gear 63 and the internal gear 23, a first planetary guide 82A provided on the outer circumference of the shaft member 5 so as to be rotatable in the circumferential direction and to be guided so as to be rotatable about the drum gear 63 by the first planetary gear 81A, a sun gear 83A provided at the tip of the first planetary guide 82A, and a second planetary gear 84A connected to the nut 3 so as to mesh with both the sun gear 83A and the internal gear 23.

[0120] With this configuration, the planetary gear mechanism 8 employs a two-stage planetary gear structure having multiple first planetary gears 81A and multiple second planetary gears 84A, thereby further amplifying the rotational force of the drum 6 and transmitting it to the nut 3.

[0121] Furthermore, in the second embodiment, the planetary gear mechanism 8 is configured to include an internal gear 23, a plurality of first planetary gears 81A, a first planetary guide 82A, a sun gear 83A, a plurality of second planetary gears 84A, and a second planetary guide 85A, but is not limited to this, and may be configured similarly to, for example, the planetary gear mechanism 8 of the second modified example.

[0122] Although this embodiment has been described above, the above-described embodiment only illustrates a part of the application of the present invention, and is not intended to limit the technical scope of the present invention to the specific configurations of the above-described embodiment. [Explanation of Symbols]

[0123] 1. Fitting 2 retainers 3 nuts 4 Linear moving element 5 Shaft member 6 drums 7. Guide ring (linear-to-rotational motion conversion member) 8 Planetary gear mechanism 9. Locking mechanism O bearing 23 Internal gear 43 Flange section 52 Spiral groove (spiral guide) 64 Drum Gear 82 First transmission gear 83 Second transmission gear 84 Sun Gear 85 Planetary gear 86 Common rotation axis 611 Drum internal teeth 711 Protrusion 712 Guide ring for external teeth

Claims

1. A fitting for attaching to a gas cylinder, A cylindrical retainer with openings at both ends, A nut is provided at one end of the retainer so as to be rotatable in the circumferential direction of the retainer, A cylindrical linear movable element is provided at the other end of the retainer so as to be movable along the axial direction of the retainer, A cylindrical shaft member is provided within the retainer, located on the inner circumference side of the linear moving element and having a spiral guide formed on its outer surface, A drum is provided between the retainer and the shaft member so as to be rotatable in the circumferential direction, with internal teeth formed on the inner circumferential surface of the drum. A linear-to-rotational motion conversion member is provided between the shaft member and the drum so as to mesh with both the helical guide and the internal teeth of the drum, and converts the linear motion of the linear moving element into rotational motion and transmits it to the drum. The system includes a planetary gear mechanism that transmits the rotational motion transmitted to the drum by the linear-to-rotational motion conversion member to the nut. Fittings.

2. The joint according to claim 1, The aforementioned spiral guide is composed of spiral grooves, The linear rotational motion conversion member is composed of a guide ring having projections that engage with the helical grooves and guide ring external teeth that mesh with the drum's internal teeth formed on its inner and outer circumferential surfaces, respectively. The guide ring rotates in the circumferential direction while moving toward the nut side along the axial direction due to the pressing force of the linear motion of the linear moving element. Fittings.

3. The joint according to claim 2, The tip of the linear moving element is provided with an annular flange portion. The guide ring has an annular bearing holding portion, The bearing further comprises an outer ring fixed so as to be press-fitted into the inner circumference of the flange portion, and an inner ring fitted to the outer circumference of the bearing holding portion. Fittings.

4. The joint according to claim 1, A drum gear is provided at the tip of the drum. The aforementioned planetary gear mechanism is, A first transmission gear that meshes with the drum gear, A second transmission gear having a rotation axis common to the rotation axis of the first transmission gear, The sun gear meshes with the second transmission gear, An internal gear formed on the inner circumferential surface of the retainer, A planetary gear connected to the nut so as to mesh with both the sun gear and the internal gear, Fittings.

5. The joint according to claim 4, The planetary gear mechanism further includes a plate provided between the drum and the nut to support the rotational axes of the first and second transmission gears, The shaft member is connected to the retainer via the plate material. Fittings.

6. The joint according to claim 1, A drum gear is provided at the tip of the drum. The aforementioned planetary gear mechanism is, An internal gear formed on the inner circumferential surface of the retainer, It has a plurality of planetary gears connected to the nut so as to mesh with both the drum gear and the internal gear, which serve as the sun gear, Fittings.

7. The joint according to claim 6, A plate portion is provided at one end of the retainer. The plate portion has multiple connecting portions through which the nuts and multiple planetary gears are connected, and multiple elongated holes extending along the circumferential direction are formed. The plate portion has a connecting region located on the inner circumference side of the plurality of elongated holes, The shaft member and the plate portion are connected in the connecting region. Fittings.

8. The joint according to claim 1, The aforementioned spiral guide is composed of a male screw, The linear rotational motion conversion member consists of a screw gear supported on the linear mover so as to be rotatable in meshing with both the male screw and the internal teeth of the drum. Fittings.

9. The joint according to claim 1, A drum gear is provided at the tip of the drum. The aforementioned planetary gear mechanism is, An internal gear formed on the inner circumferential surface of the retainer, A first planetary gear that meshes with both the drum gear and the internal gear, The first planetary gear is guided so as to be rotatable around the drum gear, and a planetary guide is provided on the outer circumference of the shaft member so as to be rotatable in the circumferential direction, The solar gear is provided at the tip of the aforementioned planetary guide, A second planetary gear is connected to the nut so as to mesh with both the sun gear and the internal gear, Fittings.

10. The joint according to claim 1, The system further includes a locking mechanism that restricts the movement of the linear moving element when the nut is tightened to the gas cylinder. Fittings.

Images