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WO2021182184A1 - Pressure resistant instrument and fluid pressure cylinder - Google Patents

Pressure resistant instrument and fluid pressure cylinder Download PDF

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Publication number
WO2021182184A1
WO2021182184A1 PCT/JP2021/007947 JP2021007947W WO2021182184A1 WO 2021182184 A1 WO2021182184 A1 WO 2021182184A1 JP 2021007947 W JP2021007947 W JP 2021007947W WO 2021182184 A1 WO2021182184 A1 WO 2021182184A1
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WO
WIPO (PCT)
Prior art keywords
cylinder
groove portion
groove
pressure
main body
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2021/007947
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French (fr)
Japanese (ja)
Inventor
小林　俊雄
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KYB Corp
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KYB Corp
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Filing date
Publication date
Application filed by KYB Corp filed Critical KYB Corp
Publication of WO2021182184A1 publication Critical patent/WO2021182184A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general

Definitions

  • the present invention relates to a pressure resistant device and a fluid pressure cylinder.
  • JPS60-196003U discloses a hydraulic cylinder in which a peripheral wall of a rear lid provided with a peripheral wall protruding in a tubular shape and a cylinder tube are joined by welding.
  • the peripheral wall of the cylinder tube and the rear lid is fitted onto an annular backing plate, and the butt portions of the two are joined by welding.
  • An object of the present invention is to improve the durability of a pressure resistant device and a fluid pressure cylinder.
  • the pressure-resistant device has a tubular main body portion, a base portion, and an annular wall portion protruding from the base portion, and the wall portion is joined to the main body portion.
  • a lid portion that closes the opening of the main body portion, and a positioning portion that is provided so as to face the inner peripheral surface of at least one of the main body portion and the wall portion and determines a relative position between the main body portion and the lid portion.
  • a groove portion formed on the inner surface of the lid portion is provided, and the groove portion is formed on the bottom surface of the base portion continuously with the first groove portion formed on the inner peripheral surface of the wall portion and the first groove portion. It has a second groove and a second groove.
  • FIG. 1 is a partial cross-sectional view of a hydraulic cylinder provided with a cylinder according to an embodiment of the present invention.
  • FIG. 2 is an enlarged view of A shown in FIG.
  • FIG. 3 is a diagram showing a modified example of the cylinder according to the embodiment of the present invention, and is shown corresponding to FIG.
  • FIG. 4 is a diagram showing a modified example of the groove portion, and is shown corresponding to FIG.
  • FIG. 5 is a diagram showing a flow of force (force line) transmitted from the cylinder bottom to the cylinder tube, and is shown corresponding to FIG.
  • FIG. 6 is a diagram showing stress (force line) generated in the cylinder of the comparative example, and is shown corresponding to FIG.
  • FIG. 7 is a diagram showing stress (force line) generated in the cylinder according to the embodiment of the present invention, and is shown corresponding to FIG.
  • the pressure resistant device is formed so that the fluid can be stored, and receives the pressure of the fluid from the inside.
  • the pressure resistant device is a cylinder 100 used for a fluid pressure cylinder will be described.
  • the hydraulic cylinder 1 as a fluid pressure cylinder includes a hollow cylinder 100, a piston rod 20 inserted into the cylinder 100, and an inner peripheral surface of the cylinder 100 provided at the end of the piston rod 20. It is provided with a piston 30 that slides along the above.
  • the piston 30 divides the inside of the cylinder 100 into a rod side chamber 4 and an anti-rod side chamber 5.
  • the rod side chamber 4 and the anti-rod side chamber 5 are filled with hydraulic oil as a hydraulic fluid.
  • the piston rod 20 extends from the cylinder 100, and the hydraulic cylinder 1 expands and contracts due to the hydraulic oil supplied and discharged to the cylinder 100. Specifically, when the hydraulic oil is supplied to the anti-rod side chamber 5 and the hydraulic oil is discharged from the rod side chamber 4, the hydraulic cylinder 1 is extended. Further, when the hydraulic oil is supplied to the rod side chamber 4 and the hydraulic oil is discharged from the anti-rod side chamber 5, the hydraulic cylinder 1 contracts.
  • the cylinder 100 includes a cylinder tube 110 as a tubular main body and a cylinder bottom 120 as a lid for closing the opening of the cylinder tube 110.
  • a cylinder tube 110 as a tubular main body and a cylinder bottom 120 as a lid for closing the opening of the cylinder tube 110.
  • One opening of the cylinder tube 110 is closed by the cylinder bottom 120, and the other opening of the cylinder tube 110 is closed by the cylinder head 50 that slidably supports the piston rod 20.
  • a mounting portion 123 for mounting the hydraulic cylinder 1 to another device is formed on the cylinder bottom 120.
  • the direction along the central axis of the cylinder tube 110 is referred to as "axial direction”
  • the radial direction centered on the central axis of the cylinder tube 110 is referred to as “diameter direction”
  • the direction is referred to as “circumferential direction”.
  • FIG. 2 is an enlarged view of part A in FIG.
  • the cylinder bottom 120 has a base portion 121 and an annular wall portion 122 projecting from the base portion 121, and the wall portion 122 is joined to the cylinder tube 110.
  • the base 121 covers the opening of the cylinder tube 110
  • the wall 122 projects axially from the bottom surface 121a of the base 121.
  • the tip portion 122a of the wall portion 122 is joined to the open end portion 110a of the cylinder tube 110 by welding.
  • the cylinder tube 110 and the cylinder bottom 120 are joined to each other via a joint 130 formed between the tip 122a of the wall 122 and the open end 110a of the cylinder tube 110.
  • any method such as arc welding including plasma welding and TIG welding, gas welding, laser welding, electron beam welding, resistance welding, and friction welding can be used.
  • the cylinder 100 is provided so as to face the inner peripheral surface 110b of the cylinder tube 110 and the inner peripheral surface 122b of the wall portion 122, and the buckling 140 as a positioning portion that determines the relative position between the cylinder tube 110 and the cylinder bottom 120. To be equipped.
  • the buck ring 140 is formed separately from the cylinder tube 110 and the wall portion 122 when the cylinder tube 110 and the wall portion 122 are not joined. At the time of joining the cylinder tube 110 and the wall portion 122, the buckling 140 fits over both the cylinder tube 110 and the wall portion 122. As a result, the relative movement of the cylinder tube 110 and the cylinder bottom 120 can be prevented at the time of joining, and the cylinder tube 110 and the wall portion 122 can be joined with their axes aligned.
  • the cylinder tube 110 and the wall portion 122 are welded to each other so that the joint portion 130 reaches the inner peripheral surfaces 110b and 122b of the cylinder tube 110 and the wall portion 122. Therefore, the outer peripheral surface 140a of the buck ring 140 is joined to the joint portion 130.
  • the outer peripheral surface 140a of the buck ring 140 is joined to the joint portion 130, but the entire outer peripheral surface 140a of the back ring 140 may be joined to the joint portion 130.
  • the buck ring 140 may be integrally formed with the wall portion 122 of the cylinder bottom 120.
  • the buck ring 140 is provided so as to face only the inner peripheral surface 110b of the cylinder tube 110. Since the buck ring 140 fits into the cylinder tube 110, it is possible to prevent the relative movement between the cylinder tube 110 and the cylinder bottom 120 at the time of joining. Therefore, the cylinder tube 110 and the wall portion 122 can be joined in a state where their axes are aligned. Further, since the buck ring 140 is integrally formed with the wall portion 122, it is possible to prevent the buck ring 140 from moving with respect to the wall portion 122 when the buck ring 140 is fitted to the cylinder tube 110. can. Therefore, the cylinder tube 110 and the wall portion 122 can be easily joined, and the cylinder 100 can be easily manufactured.
  • the buck ring 140 may be formed integrally with the cylinder tube 110.
  • the buck ring 140 is provided so as to face only the inner peripheral surface 122b of the wall portion 122. That is, the buck ring 140 may be provided so as to face at least one inner peripheral surface 110b, 122b of the cylinder tube 110 and the wall portion 122.
  • stress concentration tends to occur at the boundary between the joint portion 130 and the buckling 140. Specifically, stress concentration may occur at the boundary portions 110c and 122c between the joint portion 130 and the outer peripheral surface 140a of the buckling 140, which may adversely affect the durability of the hydraulic cylinder 1.
  • the cylinder 100 includes a groove portion 124 formed on the inner surface of the cylinder bottom 120 in order to reduce stress at the boundary portions 110c and 122c.
  • the groove portion 124 has a first groove portion 124a formed on the inner peripheral surface 122b of the wall portion 122, and a second groove portion 124b formed on the bottom surface 121a of the base portion 121 continuously with the first groove portion 124a.
  • the first groove portion 124a and the second groove portion 124b are continuous via the curved surface portion 124c.
  • the groove portion 124 is formed in an annular shape over the entire circumference of the inner surface of the cylinder bottom 120.
  • the first groove portion 124a is formed so as to be recessed in the radial direction from the inner peripheral surface 122b of the wall portion 122 and have an arcuate cross section along the axial direction.
  • the second groove portion 124b is formed so as to be recessed in the axial direction from the bottom surface 121a of the base portion 121 and have an arcuate cross section along the axial direction.
  • the curved surface portion 124c is provided between the end portion 124e of the first groove portion 124a and the end portion 124f of the second groove portion 124b.
  • the axial width of the first groove portion 124a is larger than the radial width of the second groove portion 124b, and the radial depth of the first groove portion 124a is that of the second groove portion 124b. It is formed so as to be larger than the axial depth.
  • the relationship between the width and depth of the first groove portion 124a and the second groove portion 124b may be the reverse of the above. Further, the width and depth of the first groove portion 124a and the second groove portion 124b may be the same.
  • the groove portion 124 may be formed so that the curved surface portion 124c is not provided and the first groove portion 124a and the second groove portion 124b are directly continuous. In this case, the end portion 124e of the first groove portion 124a and the end portion 124f of the second groove portion 124b are directly continuous. Even if the end portion 124e of the first groove portion 124a and the end portion 124f of the second groove portion 124b are directly continuous, the radius of curvature of the entire groove portion 124 can be increased.
  • FIG. 5 is a diagram showing a flow of force (force line) transmitted from the cylinder bottom 120 to the cylinder tube 110 when the cylinder 100 receives a tensile load in the axial direction, and corresponds to FIG. 2.
  • the force line is shown by a broken line, and the diagonal line showing the cross section of the cylinder tube 110, the cylinder bottom 120, and the joint portion 130 is omitted.
  • the tensile load acts on the cylinder 100 by, for example, the pressure of the hydraulic oil in the cylinder 100 and the load connected to the hydraulic cylinder 1.
  • the force acting on the cylinder bottom 120 is transmitted to the cylinder tube 110 through the joint 130.
  • the force path is narrowed by the first groove portion 124a recessed in the radial direction from the inner peripheral surface 122b of the wall portion 122. Therefore, the force is transmitted to the cylinder tube 110 mainly through the radial outer region of the joint 130. Therefore, the force transmitted to the inner peripheral side of the joint portion 130 can be reduced, and the stress acting on the boundary portions 110c and 122c can be reduced. Therefore, the durability of the cylinder 100 can be improved.
  • the first groove portion 124a is preferably formed near the joint portion 130.
  • the force acting on the cylinder bottom 120 passes between the outer circumference of the wall portion 122 and the first groove portion 124a, and then is transmitted to the cylinder tube 110 through the joint portion 130 while spreading inward in the radial direction. Therefore, the closer the first groove portion 124a is formed to the joint portion 130, the more the force transmitted to the inner peripheral side of the joint portion 130 can be reduced, and the stress acting on the boundary portions 110c and 122c can be reduced. can.
  • FIGS. 6 and 7 are views showing the stress (force line) generated in the cylinder 100 due to the pressure of the hydraulic oil in the anti-rod side chamber 5, and correspond to FIG. 2.
  • FIG. 6 is a diagram showing a case where the groove portion 124 is not provided as a comparative example of the present embodiment
  • FIG. 7 is a diagram showing a case where the second groove portion 124b of the present embodiment is provided.
  • the force lines are shown by broken lines, and the diagonal lines showing the cross sections of the cylinder tube 110, the cylinder bottom 120, and the joint portion 130 are omitted.
  • the first groove portion 124a and the curved surface portion 124c are not shown.
  • the second groove portion 124b is provided so as to be recessed in the axial direction from the bottom surface 121a of the base portion 121 of the cylinder bottom 120. Therefore, the axial distance D between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is larger than that in the case where the second groove portion 124b is not provided in the cylinder bottom 120 (FIG. 6). As a result, the influence of the stress generated in the vicinity of the corner portion of the cylinder bottom 120 on the boundary portions 110c and 122c is reduced, so that the stress generated in the boundary portions 110c and 122c is reduced. Therefore, the durability of the cylinder 100 can be improved.
  • the joint portion 130 is moved away from the corner portion of the cylinder bottom 120, that is, moved to the cylinder head 50 side. Is also possible. However, in this case, the buckling 140 narrows the slidable region of the piston 30.
  • the cylinder 100 of the present embodiment by providing the second groove portion 124b, the axial distance D between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is increased without changing the position of the joint portion 130.
  • the durability of the cylinder 100 can be improved. That is, the durability of the cylinder 100 can be improved without changing the stroke amount of the piston 30.
  • the first groove portion 124a and the second groove portion 124b are continuously formed, the radius of curvature of the entire groove portion 124 can be increased. Therefore, the stress concentration on the groove 124 can be reduced. Therefore, the durability of the cylinder 100 can be improved.
  • the first groove portion 124a and the second groove portion 124b are continuously formed via the curved surface portion 124c, so that the curved surface portion 124c as shown in FIG. 4 is not provided.
  • the radius of curvature of the entire groove portion 124 can be increased. Therefore, the stress concentration in the groove 124 can be further reduced, and the durability of the cylinder 100 can be further improved.
  • the force transmitted to the inner circumference of the joint 130 between the cylinder tube 110 and the wall 122 of the cylinder bottom 120 is reduced by the first groove 124a, and the boundary 110c and 122c between the joint 130 and the buckling 140 are reduced.
  • the resulting stress is reduced.
  • the distance D in the axial direction between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is increased by the second groove portion 124b, the stress generated at the boundary portions 110c and 122c is reduced. Therefore, the durability of the cylinder 100 can be improved.
  • the radius of curvature of the entire groove portion 124 can be increased by continuously forming the first groove portion 124a and the second groove portion 124b. Therefore, the stress concentration on the groove 124 can be reduced. Therefore, the durability of the cylinder 100 can be improved. Further, since the first groove portion 124a and the second groove portion 124b are continuously formed via the curved surface portion 124c, the radius of curvature of the entire groove portion 124 can be increased as compared with the case where the curved surface portion 124c is not provided. can. Therefore, the stress concentration in the groove 124 can be further reduced, and the durability of the cylinder 100 can be further improved.
  • the cylinder 100 has a cylindrical cylinder tube 110, a base portion 121, and an annular wall portion 122 protruding from the base portion 121, and the wall portion 122 is joined to the cylinder tube 110 to close the opening of the cylinder tube 110.
  • a buckling 140 provided facing the cylinder bottom 120, at least one inner peripheral surface 110b, 122b of the cylinder tube 110 and the wall portion 122, and determining a relative position between the cylinder tube 110 and the cylinder bottom 120, and a cylinder bottom 120.
  • the groove portion 124 is provided on the inner surface of the wall portion 122, and the groove portion 124 is formed on the bottom surface 121a of the base portion 121 continuously with the first groove portion 124a formed on the inner peripheral surface 122b of the wall portion 122 and the first groove portion 124a. It has a second groove portion 124b to be formed.
  • the force transmitted to the inner circumference of the joint portion 130 between the cylinder tube 110 and the wall portion 122 of the cylinder bottom 120 is reduced by the first groove portion 124a, and the boundary portions 110c and 122c between the joint portion 130 and the buckling 140 are formed.
  • the resulting stress is reduced.
  • the distance D in the axial direction between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is increased by the second groove portion 124b, the stress generated at the boundary portions 110c and 122c is reduced. Therefore, the durability of the cylinder 100 can be improved.
  • the first groove portion 124a and the second groove portion 124b are continuous via the curved surface portion 124c.
  • the first groove portion 124a and the second groove portion 124b are continuously formed via the curved surface portion 124c, so that the radius of curvature of the entire groove portion 124 is increased as compared with the case where the curved surface portion 124c is not provided. be able to. Therefore, the stress concentration on the groove 124 can be reduced. Therefore, the durability of the cylinder 100 can be improved.
  • the cylinder 100 is formed so that the first groove portion 124a and the second groove portion 124b have an arcuate cross section along the axial direction of the cylinder tube 110.
  • the axial width of the first groove portion 124a is larger than the radial width of the cylinder tube 110 of the second groove portion 124b.
  • the present embodiment relates to a hydraulic cylinder 1 that expands and contracts when hydraulic oil is supplied to and discharged from the cylinder.
  • the cylinder is a cylinder 100.
  • the cylinder since the cylinder is the cylinder 100 described above, the cylinder has high durability. Therefore, the durability of the hydraulic cylinder 1 can be improved.
  • the groove portion 124 is formed all around in the circumferential direction, but the groove portion 124 may be formed in a part in the circumferential direction.
  • the cross section of the first groove portion 124a and the second groove portion 124b may have a shape other than an arc shape, for example, a shape such as a triangle or a quadrangle.
  • the cylinder 100 used for the hydraulic cylinder 1 has been described as the pressure resistant device.
  • the pressure-resistant device is not limited to this, and may be a pressure vessel such as a cylinder for storing a liquid or gas.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Actuator (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

A cylinder (100) comprises: a cylinder bottom (120) that has an annular wall section (122) extending from a base section (121) and closes an opening of a cylinder tube (110); a back ring (140) that is provided so as to face the inner circumferential surface (110b, 122b) of the cylinder tube (110) and/or the wall section (122); and a groove section (124) that is formed in the inner surface of the cylinder bottom (120), wherein the groove section (124) has a first groove subsection (124a) that is formed in the inner circumferential surface (122b) of the wall section (122) and a second groove subsection (124b) that is formed in a bottom surface (121a) of the base section (121) contiguously with the first groove subsection (124a).

Description

耐圧機器及び流体圧シリンダPressure-resistant equipment and fluid pressure cylinder

　本発明は、耐圧機器及び流体圧シリンダに関する。 The present invention relates to a pressure resistant device and a fluid pressure cylinder.

　ＪＰＳ６０－１９６００３Ｕには、管状に突出する周壁を備えた後蓋の周壁とシリンダチューブとが溶接により接合されてなる油圧シリンダが開示されている。シリンダチューブと後蓋の周壁が環状の当て板に外嵌され、両者の突き合わせ部が溶接により接合されている。 JPS60-196003U discloses a hydraulic cylinder in which a peripheral wall of a rear lid provided with a peripheral wall protruding in a tubular shape and a cylinder tube are joined by welding. The peripheral wall of the cylinder tube and the rear lid is fitted onto an annular backing plate, and the butt portions of the two are joined by welding.

　ＪＰＳ６０－１９６００３Ｕに開示される油圧シリンダでは、溶接による接合部と当て板の境界部に応力集中が生じ、油圧シリンダの耐久性に悪影響を及ぼすおそれがある。 In the hydraulic cylinder disclosed in JPS60-196003U, stress concentration occurs at the boundary between the joint and the backing plate due to welding, which may adversely affect the durability of the hydraulic cylinder.

　本発明は、耐圧機器及び流体圧シリンダの耐久性を向上させることを目的とする。 An object of the present invention is to improve the durability of a pressure resistant device and a fluid pressure cylinder.

　本発明のある態様によれば、耐圧機器であって、筒状の本体部と、基部と、前記基部から突出する環状の壁部とを有し、前記壁部が前記本体部に接合されて前記本体部の開口を閉塞する蓋部と、前記本体部及び前記壁部の少なくとも一方の内周面に対向して設けられ、前記本体部と前記蓋部との相対位置を定める位置決め部と、前記蓋部の内面に形成される溝部と、を備え、前記溝部は、前記壁部の内周面に形成される第一溝部と、前記第一溝部と連続して前記基部の底面に形成される第二溝部と、を有する。 According to an aspect of the present invention, the pressure-resistant device has a tubular main body portion, a base portion, and an annular wall portion protruding from the base portion, and the wall portion is joined to the main body portion. A lid portion that closes the opening of the main body portion, and a positioning portion that is provided so as to face the inner peripheral surface of at least one of the main body portion and the wall portion and determines a relative position between the main body portion and the lid portion. A groove portion formed on the inner surface of the lid portion is provided, and the groove portion is formed on the bottom surface of the base portion continuously with the first groove portion formed on the inner peripheral surface of the wall portion and the first groove portion. It has a second groove and a second groove.

図１は本発明の実施形態に係るシリンダを備えた油圧シリンダの部分断面図である。FIG. 1 is a partial cross-sectional view of a hydraulic cylinder provided with a cylinder according to an embodiment of the present invention. 図２は図１に示すＡの拡大図である。FIG. 2 is an enlarged view of A shown in FIG. 図３は本発明の実施形態に係るシリンダの変形例を示す図であり、図２に対応して示す。FIG. 3 is a diagram showing a modified example of the cylinder according to the embodiment of the present invention, and is shown corresponding to FIG. 図４は溝部の変形例を示す図であり、図２に対応して示す。FIG. 4 is a diagram showing a modified example of the groove portion, and is shown corresponding to FIG. 図５はシリンダボトムからシリンダチューブに伝わる力の流れ（力線）を示す図であり、図２に対応して示す。FIG. 5 is a diagram showing a flow of force (force line) transmitted from the cylinder bottom to the cylinder tube, and is shown corresponding to FIG. 図６は比較例のシリンダに生じる応力（力線）を示す図であり、図２に対応して示す。FIG. 6 is a diagram showing stress (force line) generated in the cylinder of the comparative example, and is shown corresponding to FIG. 図７は本発明の実施形態に係るシリンダに生じる応力（力線）を示す図であり、図２に対応して示す。FIG. 7 is a diagram showing stress (force line) generated in the cylinder according to the embodiment of the present invention, and is shown corresponding to FIG.

　以下、図面を参照して、本発明の実施形態に係る耐圧機器について説明する。耐圧機器は流体を貯留可能に形成され、流体の圧力を内側から受ける。以下では、耐圧機器が、流体圧シリンダに用いられるシリンダ１００である場合について説明する。 Hereinafter, the pressure-resistant device according to the embodiment of the present invention will be described with reference to the drawings. The pressure resistant device is formed so that the fluid can be stored, and receives the pressure of the fluid from the inside. Hereinafter, a case where the pressure resistant device is a cylinder 100 used for a fluid pressure cylinder will be described.

　図１に示すように、流体圧シリンダとしての油圧シリンダ１は、中空のシリンダ１００と、シリンダ１００内に挿入されるピストンロッド２０と、ピストンロッド２０の端部に設けられシリンダ１００の内周面に沿って摺動するピストン３０と、を備える。ピストン３０によって、シリンダ１００の内部がロッド側室４と反ロッド側室５とに区画される。ロッド側室４及び反ロッド側室５には、作動流体としての作動油が封入される。 As shown in FIG. 1, the hydraulic cylinder 1 as a fluid pressure cylinder includes a hollow cylinder 100, a piston rod 20 inserted into the cylinder 100, and an inner peripheral surface of the cylinder 100 provided at the end of the piston rod 20. It is provided with a piston 30 that slides along the above. The piston 30 divides the inside of the cylinder 100 into a rod side chamber 4 and an anti-rod side chamber 5. The rod side chamber 4 and the anti-rod side chamber 5 are filled with hydraulic oil as a hydraulic fluid.

　ピストンロッド２０はシリンダ１００から延出し、シリンダ１００に給排される作動油によって油圧シリンダ１は伸縮作動する。具体的には、作動油が反ロッド側室５に供給されロッド側室４から作動油が排出されると、油圧シリンダ１は伸長作動する。また、作動油がロッド側室４に供給され反ロッド側室５から作動油が排出されると、油圧シリンダ１は収縮作動する。 The piston rod 20 extends from the cylinder 100, and the hydraulic cylinder 1 expands and contracts due to the hydraulic oil supplied and discharged to the cylinder 100. Specifically, when the hydraulic oil is supplied to the anti-rod side chamber 5 and the hydraulic oil is discharged from the rod side chamber 4, the hydraulic cylinder 1 is extended. Further, when the hydraulic oil is supplied to the rod side chamber 4 and the hydraulic oil is discharged from the anti-rod side chamber 5, the hydraulic cylinder 1 contracts.

　シリンダ１００は、筒状の本体部としてのシリンダチューブ１１０と、シリンダチューブ１１０の開口を閉塞する蓋部としてのシリンダボトム１２０と、を備える。シリンダチューブ１１０の一方の開口は、シリンダボトム１２０によって閉塞され、シリンダチューブ１１０の他方の開口は、ピストンロッド２０を摺動自在に支持するシリンダヘッド５０によって閉塞される。シリンダボトム１２０には、油圧シリンダ１を他の機器に取り付けるための取付部１２３が形成される。 The cylinder 100 includes a cylinder tube 110 as a tubular main body and a cylinder bottom 120 as a lid for closing the opening of the cylinder tube 110. One opening of the cylinder tube 110 is closed by the cylinder bottom 120, and the other opening of the cylinder tube 110 is closed by the cylinder head 50 that slidably supports the piston rod 20. A mounting portion 123 for mounting the hydraulic cylinder 1 to another device is formed on the cylinder bottom 120.

　以下において、シリンダチューブ１１０の中心軸に沿う方向を「軸方向」と称し、シリンダチューブ１１０の中心軸を中心とする放射方向を「径方向」と称し、シリンダチューブ１１０の中心軸の周りに沿う方向を「周方向」と称する。 In the following, the direction along the central axis of the cylinder tube 110 is referred to as "axial direction", the radial direction centered on the central axis of the cylinder tube 110 is referred to as "diameter direction", and is along the circumference of the central axis of the cylinder tube 110. The direction is referred to as "circumferential direction".

　図２は、図１におけるＡ部の拡大図である。図２に示すように、シリンダボトム１２０は、基部１２１と、基部１２１から突出する環状の壁部１２２と、を有し、壁部１２２がシリンダチューブ１１０に接合される。具体的には、基部１２１はシリンダチューブ１１０の開口を覆い、壁部１２２は基部１２１の底面１２１ａから軸方向に突出する。壁部１２２の先端部１２２ａは、シリンダチューブ１１０の開口端部１１０ａと溶接によって接合される。言い換えれば、シリンダチューブ１１０とシリンダボトム１２０とは、壁部１２２の先端部１２２ａとシリンダチューブ１１０の開口端部１１０ａとの間に形成される接合部１３０を介して互いに接合される。この溶接には、プラズマ溶接及びＴＩＧ溶接を含むアーク溶接、ガス溶接、レーザー溶接、電子ビーム溶接、抵抗溶接、並びに摩擦圧接など任意の方法を用いることができる。 FIG. 2 is an enlarged view of part A in FIG. As shown in FIG. 2, the cylinder bottom 120 has a base portion 121 and an annular wall portion 122 projecting from the base portion 121, and the wall portion 122 is joined to the cylinder tube 110. Specifically, the base 121 covers the opening of the cylinder tube 110, and the wall 122 projects axially from the bottom surface 121a of the base 121. The tip portion 122a of the wall portion 122 is joined to the open end portion 110a of the cylinder tube 110 by welding. In other words, the cylinder tube 110 and the cylinder bottom 120 are joined to each other via a joint 130 formed between the tip 122a of the wall 122 and the open end 110a of the cylinder tube 110. For this welding, any method such as arc welding including plasma welding and TIG welding, gas welding, laser welding, electron beam welding, resistance welding, and friction welding can be used.

　また、シリンダ１００は、シリンダチューブ１１０の内周面１１０ｂ及び壁部１２２の内周面１２２ｂに対向して設けられ、シリンダチューブ１１０とシリンダボトム１２０との相対位置を定める位置決め部としてのバックリング１４０を備える。 Further, the cylinder 100 is provided so as to face the inner peripheral surface 110b of the cylinder tube 110 and the inner peripheral surface 122b of the wall portion 122, and the buckling 140 as a positioning portion that determines the relative position between the cylinder tube 110 and the cylinder bottom 120. To be equipped.

　バックリング１４０は、シリンダチューブ１１０と壁部１２２とが接合されていない状態では、シリンダチューブ１１０及び壁部１２２と別体に形成される。シリンダチューブ１１０と壁部１２２との接合時には、バックリング１４０は、シリンダチューブ１１０と壁部１２２との両方にわたって嵌合する。これにより、接合時にシリンダチューブ１１０とシリンダボトム１２０との相対移動を防止することができ、シリンダチューブ１１０と壁部１２２とを、これらの軸心を合わせた状態で接合することができる。 The buck ring 140 is formed separately from the cylinder tube 110 and the wall portion 122 when the cylinder tube 110 and the wall portion 122 are not joined. At the time of joining the cylinder tube 110 and the wall portion 122, the buckling 140 fits over both the cylinder tube 110 and the wall portion 122. As a result, the relative movement of the cylinder tube 110 and the cylinder bottom 120 can be prevented at the time of joining, and the cylinder tube 110 and the wall portion 122 can be joined with their axes aligned.

　また、シリンダチューブ１１０と壁部１２２とは、接合部１３０がシリンダチューブ１１０及び壁部１２２の内周面１１０ｂ、１２２ｂにまで達するようにして互いに溶接される。そのため、バックリング１４０の外周面１４０ａが接合部１３０と接合される。図２に示す例では、バックリング１４０の外周面１４０ａの一部のみが接合部１３０と接合されるが、バックリング１４０の外周面１４０ａの全体が接合部１３０と接合されていてもよい。 Further, the cylinder tube 110 and the wall portion 122 are welded to each other so that the joint portion 130 reaches the inner peripheral surfaces 110b and 122b of the cylinder tube 110 and the wall portion 122. Therefore, the outer peripheral surface 140a of the buck ring 140 is joined to the joint portion 130. In the example shown in FIG. 2, only a part of the outer peripheral surface 140a of the buck ring 140 is joined to the joint portion 130, but the entire outer peripheral surface 140a of the back ring 140 may be joined to the joint portion 130.

　なお、図３に示すように、バックリング１４０は、シリンダボトム１２０の壁部１２２と一体に形成されてもよい。この場合、バックリング１４０は、シリンダチューブ１１０の内周面１１０ｂのみに対向して設けられる。バックリング１４０は、シリンダチューブ１１０に嵌合するため、接合時にシリンダチューブ１１０とシリンダボトム１２０との相対移動を防止することができる。よって、シリンダチューブ１１０と壁部１２２とを、これらの軸心を合わせた状態で接合することができる。また、バックリング１４０が壁部１２２と一体的に形成されるので、バックリング１４０をシリンダチューブ１１０に嵌合する際に、壁部１２２に対してバックリング１４０が移動することを防止することができる。したがって、シリンダチューブ１１０と壁部１２２とを容易に接合することができ、シリンダ１００を容易に製造することができる。 As shown in FIG. 3, the buck ring 140 may be integrally formed with the wall portion 122 of the cylinder bottom 120. In this case, the buck ring 140 is provided so as to face only the inner peripheral surface 110b of the cylinder tube 110. Since the buck ring 140 fits into the cylinder tube 110, it is possible to prevent the relative movement between the cylinder tube 110 and the cylinder bottom 120 at the time of joining. Therefore, the cylinder tube 110 and the wall portion 122 can be joined in a state where their axes are aligned. Further, since the buck ring 140 is integrally formed with the wall portion 122, it is possible to prevent the buck ring 140 from moving with respect to the wall portion 122 when the buck ring 140 is fitted to the cylinder tube 110. can. Therefore, the cylinder tube 110 and the wall portion 122 can be easily joined, and the cylinder 100 can be easily manufactured.

　また、バックリング１４０は、シリンダチューブ１１０と一体に形成されてもよい。この場合、バックリング１４０は、壁部１２２の内周面１２２ｂのみに対向して設けられる。つまり、バックリング１４０は、シリンダチューブ１１０及び壁部１２２の少なくとも一方の内周面１１０ｂ,１２２ｂに対向して設けられればよい。 Further, the buck ring 140 may be formed integrally with the cylinder tube 110. In this case, the buck ring 140 is provided so as to face only the inner peripheral surface 122b of the wall portion 122. That is, the buck ring 140 may be provided so as to face at least one inner peripheral surface 110b, 122b of the cylinder tube 110 and the wall portion 122.

　シリンダチューブ１１０とシリンダボトム１２０とが接合されたシリンダ１００においては、接合部１３０とバックリング１４０との境界部に応力集中が生じやすい。具体的には、接合部１３０とバックリング１４０の外周面１４０ａとの境界部１１０ｃ，１２２ｃに応力集中が生じ、油圧シリンダ１の耐久性に悪影響を及ぼすおそれがある。 In the cylinder 100 in which the cylinder tube 110 and the cylinder bottom 120 are joined, stress concentration tends to occur at the boundary between the joint portion 130 and the buckling 140. Specifically, stress concentration may occur at the boundary portions 110c and 122c between the joint portion 130 and the outer peripheral surface 140a of the buckling 140, which may adversely affect the durability of the hydraulic cylinder 1.

　シリンダ１００は、境界部１１０ｃ，１２２ｃにおける応力を軽減するために、シリンダボトム１２０の内面に形成される溝部１２４を備える。溝部１２４は、壁部１２２の内周面１２２ｂに形成される第一溝部１２４ａと、第一溝部１２４ａと連続して基部１２１の底面１２１ａに形成される第二溝部１２４ｂと、を有する。第一溝部１２４ａと第二溝部１２４ｂは、曲面部１２４ｃを介して連続する。曲面部１２４ｃを介して第一溝部１２４ａと第二溝部１２４ｂが連続して形成されることにより、溝部１２４全体の曲率半径を大きくすることができる。 The cylinder 100 includes a groove portion 124 formed on the inner surface of the cylinder bottom 120 in order to reduce stress at the boundary portions 110c and 122c. The groove portion 124 has a first groove portion 124a formed on the inner peripheral surface 122b of the wall portion 122, and a second groove portion 124b formed on the bottom surface 121a of the base portion 121 continuously with the first groove portion 124a. The first groove portion 124a and the second groove portion 124b are continuous via the curved surface portion 124c. By continuously forming the first groove portion 124a and the second groove portion 124b via the curved surface portion 124c, the radius of curvature of the entire groove portion 124 can be increased.

　溝部１２４は、シリンダボトム１２０の内面の全周にわたって環状に形成される。第一溝部１２４ａは、壁部１２２の内周面１２２ｂから径方向に窪んで、軸方向に沿った断面が円弧状となるように形成される。第二溝部１２４ｂは、基部１２１の底面１２１ａから軸方向に窪んで、軸方向に沿った断面が円弧状となるように形成される。曲面部１２４ｃは、第一溝部１２４ａの端部１２４ｅと第二溝部１２４ｂの端部１２４ｆとの間にわたって設けられる。 The groove portion 124 is formed in an annular shape over the entire circumference of the inner surface of the cylinder bottom 120. The first groove portion 124a is formed so as to be recessed in the radial direction from the inner peripheral surface 122b of the wall portion 122 and have an arcuate cross section along the axial direction. The second groove portion 124b is formed so as to be recessed in the axial direction from the bottom surface 121a of the base portion 121 and have an arcuate cross section along the axial direction. The curved surface portion 124c is provided between the end portion 124e of the first groove portion 124a and the end portion 124f of the second groove portion 124b.

　第一溝部１２４ａと第二溝部１２４ｂは、第一溝部１２４ａの軸方向の幅が第二溝部１２４ｂの径方向の幅よりも大きく、第一溝部１２４ａの径方向の深さが第二溝部１２４ｂの軸方向の深さよりも大きくなるように形成される。なお、第一溝部１２４ａと第二溝部１２４ｂの幅及び深さの関係は、上記と逆であってもよい。また、第一溝部１２４ａと第二溝部１２４ｂの幅及び深さが同じであってもよい。 In the first groove portion 124a and the second groove portion 124b, the axial width of the first groove portion 124a is larger than the radial width of the second groove portion 124b, and the radial depth of the first groove portion 124a is that of the second groove portion 124b. It is formed so as to be larger than the axial depth. The relationship between the width and depth of the first groove portion 124a and the second groove portion 124b may be the reverse of the above. Further, the width and depth of the first groove portion 124a and the second groove portion 124b may be the same.

　なお、図４に示すように、溝部１２４は、曲面部１２４ｃが設けられず、第一溝部１２４ａと第二溝部１２４ｂが直接連続するように形成されてもよい。この場合は、第一溝部１２４ａの端部１２４ｅと第二溝部１２４ｂの端部１２４ｆが直接連続する。第一溝部１２４ａの端部１２４ｅと第二溝部１２４ｂの端部１２４ｆが直接連続する構成であっても、溝部１２４全体の曲率半径を大きくすることができる。 As shown in FIG. 4, the groove portion 124 may be formed so that the curved surface portion 124c is not provided and the first groove portion 124a and the second groove portion 124b are directly continuous. In this case, the end portion 124e of the first groove portion 124a and the end portion 124f of the second groove portion 124b are directly continuous. Even if the end portion 124e of the first groove portion 124a and the end portion 124f of the second groove portion 124b are directly continuous, the radius of curvature of the entire groove portion 124 can be increased.

　図５は、シリンダ１００が軸方向に引張荷重を受けたときにシリンダボトム１２０からシリンダチューブ１１０に伝わる力の流れ（力線）を示す図であり、図２に対応する。図５では、力線を破線で示し、シリンダチューブ１１０、シリンダボトム１２０及び接合部１３０の断面を示す斜線を省略している。引張荷重は、例えば、シリンダ１００内の作動油の圧力、及び油圧シリンダ１に連結される負荷によって、シリンダ１００に作用する。 FIG. 5 is a diagram showing a flow of force (force line) transmitted from the cylinder bottom 120 to the cylinder tube 110 when the cylinder 100 receives a tensile load in the axial direction, and corresponds to FIG. 2. In FIG. 5, the force line is shown by a broken line, and the diagonal line showing the cross section of the cylinder tube 110, the cylinder bottom 120, and the joint portion 130 is omitted. The tensile load acts on the cylinder 100 by, for example, the pressure of the hydraulic oil in the cylinder 100 and the load connected to the hydraulic cylinder 1.

　シリンダ１００が軸方向に引張荷重を受けたとき、シリンダボトム１２０に作用する力は、接合部１３０を通じてシリンダチューブ１１０に伝わる。このとき、力の経路は、壁部１２２の内周面１２２ｂから径方向に窪んだ第一溝部１２４ａによって狭められる。よって、力は、接合部１３０における径方向外側の領域を主に経てシリンダチューブ１１０に伝わる。したがって、接合部１３０の内周側に伝わる力を低減することができ、境界部１１０ｃ，１２２ｃに作用する応力を軽減することができる。よって、シリンダ１００の耐久性を向上させることができる。 When the cylinder 100 receives a tensile load in the axial direction, the force acting on the cylinder bottom 120 is transmitted to the cylinder tube 110 through the joint 130. At this time, the force path is narrowed by the first groove portion 124a recessed in the radial direction from the inner peripheral surface 122b of the wall portion 122. Therefore, the force is transmitted to the cylinder tube 110 mainly through the radial outer region of the joint 130. Therefore, the force transmitted to the inner peripheral side of the joint portion 130 can be reduced, and the stress acting on the boundary portions 110c and 122c can be reduced. Therefore, the durability of the cylinder 100 can be improved.

　なお、第一溝部１２４ａは、接合部１３０の近くに形成されるのが好ましい。シリンダボトム１２０に作用する力は、壁部１２２における外周と第一溝部１２４ａとの間を通過後、径方向内側に広がりながら接合部１３０を経てシリンダチューブ１１０に伝わる。このため、第一溝部１２４ａが接合部１３０の近くに形成されるほど、接合部１３０の内周側に伝わる力を低減することができ、境界部１１０ｃ，１２２ｃに作用する応力を軽減することができる。 The first groove portion 124a is preferably formed near the joint portion 130. The force acting on the cylinder bottom 120 passes between the outer circumference of the wall portion 122 and the first groove portion 124a, and then is transmitted to the cylinder tube 110 through the joint portion 130 while spreading inward in the radial direction. Therefore, the closer the first groove portion 124a is formed to the joint portion 130, the more the force transmitted to the inner peripheral side of the joint portion 130 can be reduced, and the stress acting on the boundary portions 110c and 122c can be reduced. can.

　また、シリンダ１００では、反ロッド側室５内の作動油の圧力により、シリンダ１００内部から力が作用し、シリンダ１００に応力が生じる。図６，７は、反ロッド側室５内の作動油の圧力により、シリンダ１００に生じる応力（力線）を示す図であり、図２に対応する。図６は、本実施形態の比較例として溝部１２４が設けられない場合を示した図であり、図７は、本実施形態の第二溝部１２４ｂが設けられる場合を示した図である。図６，７では、力線を破線で示し、シリンダチューブ１１０、シリンダボトム１２０及び接合部１３０の断面を示す斜線を省略している。図７では、第一溝部１２４ａ及び曲面部１２４ｃの図示を省略している。 Further, in the cylinder 100, a force acts from the inside of the cylinder 100 due to the pressure of the hydraulic oil in the anti-rod side chamber 5, and stress is generated in the cylinder 100. 6 and 7 are views showing the stress (force line) generated in the cylinder 100 due to the pressure of the hydraulic oil in the anti-rod side chamber 5, and correspond to FIG. 2. FIG. 6 is a diagram showing a case where the groove portion 124 is not provided as a comparative example of the present embodiment, and FIG. 7 is a diagram showing a case where the second groove portion 124b of the present embodiment is provided. In FIGS. 6 and 7, the force lines are shown by broken lines, and the diagonal lines showing the cross sections of the cylinder tube 110, the cylinder bottom 120, and the joint portion 130 are omitted. In FIG. 7, the first groove portion 124a and the curved surface portion 124c are not shown.

　図６に示すように、反ロッド側室５内の作動油の圧力により、壁部１２２の内周面１２２ｂと基部１２１の底面１２１ａとの間の角部近傍には、大きな応力が生じる。よって、接合部１３０がシリンダボトム１２０の角部に近いと、境界部１１０ｃ，１２２ｃには大きな応力が作用する。つまり、接合部１３０とシリンダボトム１２０の底面Ａとの軸方向の距離Ｄが小さいほど、境界部１１０ｃ，１２２ｃには大きな応力が作用してしまう。 As shown in FIG. 6, due to the pressure of the hydraulic oil in the anti-rod side chamber 5, a large stress is generated in the vicinity of the corner portion between the inner peripheral surface 122b of the wall portion 122 and the bottom surface 121a of the base portion 121. Therefore, when the joint portion 130 is close to the corner portion of the cylinder bottom 120, a large stress acts on the boundary portions 110c and 122c. That is, the smaller the axial distance D between the joint portion 130 and the bottom surface A of the cylinder bottom 120, the greater stress acts on the boundary portions 110c and 122c.

　図７に示すように、本実施形態のシリンダ１００では、第二溝部１２４ｂがシリンダボトム１２０の基部１２１の底面１２１ａから軸方向に窪んで設けられる。よって、シリンダボトム１２０に第二溝部１２４ｂが設けられない場合（図６）と比較して、接合部１３０とシリンダボトム１２０の底面Ａとの軸方向の距離Ｄが大きくなる。これにより、シリンダボトム１２０の角部近傍に生じる応力が境界部１１０ｃ，１２２ｃに及ぼす影響が小さくなるため、境界部１１０ｃ，１２２ｃに生じる応力が低減される。よって、シリンダ１００の耐久性を向上させることができる。 As shown in FIG. 7, in the cylinder 100 of the present embodiment, the second groove portion 124b is provided so as to be recessed in the axial direction from the bottom surface 121a of the base portion 121 of the cylinder bottom 120. Therefore, the axial distance D between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is larger than that in the case where the second groove portion 124b is not provided in the cylinder bottom 120 (FIG. 6). As a result, the influence of the stress generated in the vicinity of the corner portion of the cylinder bottom 120 on the boundary portions 110c and 122c is reduced, so that the stress generated in the boundary portions 110c and 122c is reduced. Therefore, the durability of the cylinder 100 can be improved.

　なお、接合部１３０とシリンダボトム１２０の底面Ａとの軸方向の距離Ｄを大きくする別の方法として、接合部１３０をシリンダボトム１２０の角部から遠ざける、つまり、シリンダヘッド５０側に移動させることも考えられる。しかし、この場合、バックリング１４０によりピストン３０が摺動可能な領域が狭められてしまう。これに対して、本実施形態のシリンダ１００では、第二溝部１２４ｂを設けることで、接合部１３０の位置を変えずに接合部１３０とシリンダボトム１２０の底面Ａとの軸方向の距離Ｄを大きくし、シリンダ１００の耐久性を向上させることができる。つまり、ピストン３０のストローク量を変えずに、シリンダ１００の耐久性を向上させることができる。 As another method of increasing the axial distance D between the joint portion 130 and the bottom surface A of the cylinder bottom 120, the joint portion 130 is moved away from the corner portion of the cylinder bottom 120, that is, moved to the cylinder head 50 side. Is also possible. However, in this case, the buckling 140 narrows the slidable region of the piston 30. On the other hand, in the cylinder 100 of the present embodiment, by providing the second groove portion 124b, the axial distance D between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is increased without changing the position of the joint portion 130. However, the durability of the cylinder 100 can be improved. That is, the durability of the cylinder 100 can be improved without changing the stroke amount of the piston 30.

　また、第一溝部１２４ａと第二溝部１２４ｂが連続して形成されることにより、溝部１２４全体の曲率半径を大きくすることができる。そのため、溝部１２４への応力集中を低減することができる。よって、シリンダ１００の耐久性を向上させることができる。さらに、図２に示すように、曲面部１２４ｃを介して第一溝部１２４ａと第二溝部１２４ｂが連続して形成されることにより、図４に示すような、曲面部１２４ｃが設けられずに第一溝部１２４ａと第二溝部１２４ｂが直接連続して形成される場合と比較して、溝部１２４全体の曲率半径を大きくすることができる。そのため、溝部１２４への応力集中をさらに低減することができ、シリンダ１００の耐久性をさらに向上させることができる。 Further, since the first groove portion 124a and the second groove portion 124b are continuously formed, the radius of curvature of the entire groove portion 124 can be increased. Therefore, the stress concentration on the groove 124 can be reduced. Therefore, the durability of the cylinder 100 can be improved. Further, as shown in FIG. 2, the first groove portion 124a and the second groove portion 124b are continuously formed via the curved surface portion 124c, so that the curved surface portion 124c as shown in FIG. 4 is not provided. Compared with the case where the one groove portion 124a and the second groove portion 124b are directly and continuously formed, the radius of curvature of the entire groove portion 124 can be increased. Therefore, the stress concentration in the groove 124 can be further reduced, and the durability of the cylinder 100 can be further improved.

　以上の本実施形態によれば、以下の効果を奏する。 According to the above embodiment, the following effects are obtained.

　シリンダ１００では、第一溝部１２４ａによりシリンダチューブ１１０とシリンダボトム１２０の壁部１２２との接合部１３０の内周に伝わる力が低減され、接合部１３０とバックリング１４０との境界部１１０ｃ，１２２ｃに生じる応力が低減される。また、第二溝部１２４ｂにより接合部１３０とシリンダボトム１２０の底面Ａとの軸方向の距離Ｄが長くなるため、境界部１１０ｃ，１２２ｃに生じる応力が低減される。よって、シリンダ１００の耐久性を向上させることができる。 In the cylinder 100, the force transmitted to the inner circumference of the joint 130 between the cylinder tube 110 and the wall 122 of the cylinder bottom 120 is reduced by the first groove 124a, and the boundary 110c and 122c between the joint 130 and the buckling 140 are reduced. The resulting stress is reduced. Further, since the distance D in the axial direction between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is increased by the second groove portion 124b, the stress generated at the boundary portions 110c and 122c is reduced. Therefore, the durability of the cylinder 100 can be improved.

　シリンダ１００では、第一溝部１２４ａと第二溝部１２４ｂが連続して形成されることにより、溝部１２４全体の曲率半径を大きくすることができる。そのため、溝部１２４への応力集中を低減することができる。よって、シリンダ１００の耐久性を向上させることができる。さらに、曲面部１２４ｃを介して第一溝部１２４ａと第二溝部１２４ｂが連続して形成されることにより、曲面部１２４ｃが設けられない場合と比較し、溝部１２４全体の曲率半径を大きくすることができる。そのため、溝部１２４への応力集中をさらに低減することができ、シリンダ１００の耐久性をさらに向上させることができる。 In the cylinder 100, the radius of curvature of the entire groove portion 124 can be increased by continuously forming the first groove portion 124a and the second groove portion 124b. Therefore, the stress concentration on the groove 124 can be reduced. Therefore, the durability of the cylinder 100 can be improved. Further, since the first groove portion 124a and the second groove portion 124b are continuously formed via the curved surface portion 124c, the radius of curvature of the entire groove portion 124 can be increased as compared with the case where the curved surface portion 124c is not provided. can. Therefore, the stress concentration in the groove 124 can be further reduced, and the durability of the cylinder 100 can be further improved.

　以下、本発明の実施形態の構成、作用、及び効果をまとめて説明する。 Hereinafter, the configurations, actions, and effects of the embodiments of the present invention will be collectively described.

　シリンダ１００は、筒状のシリンダチューブ１１０と、基部１２１と、基部１２１から突出する環状の壁部１２２とを有し、壁部１２２がシリンダチューブ１１０に接合されてシリンダチューブ１１０の開口を閉塞するシリンダボトム１２０と、シリンダチューブ１１０及び壁部１２２の少なくとも一方の内周面１１０ｂ、１２２ｂに対向して設けられ、シリンダチューブ１１０とシリンダボトム１２０との相対位置を定めるバックリング１４０と、シリンダボトム１２０の内面に形成される溝部１２４と、を備え、溝部１２４は、壁部１２２の内周面１２２ｂに形成される第一溝部１２４ａと、第一溝部１２４ａと連続して基部１２１の底面１２１ａに形成される第二溝部１２４ｂと、を有する。 The cylinder 100 has a cylindrical cylinder tube 110, a base portion 121, and an annular wall portion 122 protruding from the base portion 121, and the wall portion 122 is joined to the cylinder tube 110 to close the opening of the cylinder tube 110. A buckling 140 provided facing the cylinder bottom 120, at least one inner peripheral surface 110b, 122b of the cylinder tube 110 and the wall portion 122, and determining a relative position between the cylinder tube 110 and the cylinder bottom 120, and a cylinder bottom 120. The groove portion 124 is provided on the inner surface of the wall portion 122, and the groove portion 124 is formed on the bottom surface 121a of the base portion 121 continuously with the first groove portion 124a formed on the inner peripheral surface 122b of the wall portion 122 and the first groove portion 124a. It has a second groove portion 124b to be formed.

　この構成では、第一溝部１２４ａによりシリンダチューブ１１０とシリンダボトム１２０の壁部１２２との接合部１３０の内周に伝わる力が低減され、接合部１３０とバックリング１４０との境界部１１０ｃ，１２２ｃに生じる応力が低減される。また、第二溝部１２４ｂにより接合部１３０とシリンダボトム１２０の底面Ａとの軸方向の距離Ｄが長くなるため、境界部１１０ｃ，１２２ｃに生じる応力が低減される。よって、シリンダ１００の耐久性を向上させることができる。 In this configuration, the force transmitted to the inner circumference of the joint portion 130 between the cylinder tube 110 and the wall portion 122 of the cylinder bottom 120 is reduced by the first groove portion 124a, and the boundary portions 110c and 122c between the joint portion 130 and the buckling 140 are formed. The resulting stress is reduced. Further, since the distance D in the axial direction between the joint portion 130 and the bottom surface A of the cylinder bottom 120 is increased by the second groove portion 124b, the stress generated at the boundary portions 110c and 122c is reduced. Therefore, the durability of the cylinder 100 can be improved.

　シリンダ１００は、第一溝部１２４ａと第二溝部１２４ｂは、曲面部１２４ｃを介して連続する。 In the cylinder 100, the first groove portion 124a and the second groove portion 124b are continuous via the curved surface portion 124c.

　この構成では、曲面部１２４ｃを介して第一溝部１２４ａと第二溝部１２４ｂが連続して形成されることにより、曲面部１２４ｃが設けられない場合と比較し、溝部１２４全体の曲率半径を大きくすることができる。そのため、溝部１２４への応力集中を低減することができる。よって、シリンダ１００の耐久性を向上させることができる。 In this configuration, the first groove portion 124a and the second groove portion 124b are continuously formed via the curved surface portion 124c, so that the radius of curvature of the entire groove portion 124 is increased as compared with the case where the curved surface portion 124c is not provided. be able to. Therefore, the stress concentration on the groove 124 can be reduced. Therefore, the durability of the cylinder 100 can be improved.

　シリンダ１００は、第一溝部１２４ａ及び第二溝部１２４ｂは、シリンダチューブ１１０の軸方向に沿った断面が円弧状となるように形成される。 The cylinder 100 is formed so that the first groove portion 124a and the second groove portion 124b have an arcuate cross section along the axial direction of the cylinder tube 110.

　この構成では、第一溝部１２４ａ及び第二溝部１２４ｂへの応力集中を低減することができる。 With this configuration, stress concentration on the first groove portion 124a and the second groove portion 124b can be reduced.

　シリンダ１００は、第一溝部１２４ａの軸方向の幅は、第二溝部１２４ｂのシリンダチューブ１１０の径方向の幅よりも大きい。 In the cylinder 100, the axial width of the first groove portion 124a is larger than the radial width of the cylinder tube 110 of the second groove portion 124b.

　この構成では、第一溝部１２４ａの軸方向の幅が大きいことにより、接合部１３０とシリンダボトム１２０の底面Ａとの軸方向の距離Ｄが長くなるため、境界部１１０ｃ，１２２ｃに生じる応力が低減される。 In this configuration, since the axial width of the first groove portion 124a is large, the axial distance D between the joint portion 130 and the bottom surface A of the cylinder bottom 120 becomes long, so that the stress generated at the boundary portions 110c and 122c is reduced. Will be done.

　本実施形態は、シリンダに作動油が給排されることによって伸縮作動する油圧シリンダ１に係る。シリンダは、シリンダ１００である。 The present embodiment relates to a hydraulic cylinder 1 that expands and contracts when hydraulic oil is supplied to and discharged from the cylinder. The cylinder is a cylinder 100.

　この構成では、シリンダが前述のシリンダ１００であるので、シリンダは高い耐久性を有する。したがって、油圧シリンダ１の耐久性を向上させることができる。 In this configuration, since the cylinder is the cylinder 100 described above, the cylinder has high durability. Therefore, the durability of the hydraulic cylinder 1 can be improved.

　以上、本発明の実施形態について説明したが、上記実施形態は本発明の適用例の一部を示したに過ぎず、本発明の技術的範囲を上記実施形態の具体的構成に限定する趣旨ではない。 Although the embodiments of the present invention have been described above, the above embodiments are only a part of the application examples of the present invention, and the technical scope of the present invention is limited to the specific configurations of the above embodiments. No.

　（１）本実施形態では、溝部１２４は、周方向に全周に形成されるが、溝部１２４は、周方向における一部に形成される構成であってもよい。 (1) In the present embodiment, the groove portion 124 is formed all around in the circumferential direction, but the groove portion 124 may be formed in a part in the circumferential direction.

　（２）第一溝部１２４ａ、第二溝部１２４ｂの断面は、円弧状以外の形状、例えば三角形、四角形等の形状であってもよい。 (2) The cross section of the first groove portion 124a and the second groove portion 124b may have a shape other than an arc shape, for example, a shape such as a triangle or a quadrangle.

　（３）上記実施形態では、耐圧機器として、油圧シリンダ１に用いられるシリンダ１００について説明した。耐圧機器は、これに限らず、液体や気体を保管するためのボンベなどの圧力容器でもよい。 (3) In the above embodiment, the cylinder 100 used for the hydraulic cylinder 1 has been described as the pressure resistant device. The pressure-resistant device is not limited to this, and may be a pressure vessel such as a cylinder for storing a liquid or gas.

　本願は２０２０年３月１３日に日本国特許庁に出願された特願２０２０－４４３８１に基づく優先権を主張し、この出願の全ての内容は参照により本明細書に組み込まれる。 This application claims priority based on Japanese Patent Application No. 2020-44381 filed with the Japan Patent Office on March 13, 2020, and the entire contents of this application are incorporated herein by reference.

Claims (5)

　耐圧機器であって、
　筒状の本体部と、
　基部と、前記基部から突出する環状の壁部とを有し、前記壁部が前記本体部に接合されて前記本体部の開口を閉塞する蓋部と、
　前記本体部及び前記壁部の少なくとも一方の内周面に対向して設けられ、前記本体部と前記蓋部との相対位置を定める位置決め部と、
　前記蓋部の内面に形成される溝部と、を備え、
　前記溝部は、
　前記壁部の内周面に形成される第一溝部と、
　前記第一溝部と連続して前記基部の底面に形成される第二溝部と、を有する耐圧機器。 It is a pressure resistant device
Cylindrical body and
A lid portion having a base portion and an annular wall portion protruding from the base portion, and the wall portion is joined to the main body portion to close the opening of the main body portion.
A positioning portion provided so as to face at least one inner peripheral surface of the main body portion and the wall portion and determining a relative position between the main body portion and the lid portion.
A groove portion formed on the inner surface of the lid portion is provided.
The groove is
The first groove formed on the inner peripheral surface of the wall and
A pressure-resistant device having a second groove portion formed on the bottom surface of the base portion continuously with the first groove portion. 　請求項１に記載の耐圧機器であって、
　前記第一溝部と前記第二溝部は、曲面部を介して連続する耐圧機器。 The pressure-resistant device according to claim 1.
The first groove portion and the second groove portion are pressure-resistant devices that are continuous via a curved surface portion. 　請求項１または２に記載の耐圧機器であって、
　前記第一溝部及び前記第二溝部は、前記本体部の軸方向に沿った断面が円弧状となるように形成される耐圧機器。 The pressure-resistant device according to claim 1 or 2.
The first groove portion and the second groove portion are pressure-resistant devices formed so that the cross section of the main body portion along the axial direction is arcuate. 　請求項１から３のいずれか一つに記載の耐圧機器であって、
　前記第一溝部の前記軸方向の幅は、前記第二溝部の前記本体部の径方向の幅よりも大きい耐圧機器。 The pressure-resistant device according to any one of claims 1 to 3.
A pressure-resistant device in which the axial width of the first groove portion is larger than the radial width of the main body portion of the second groove portion. 　シリンダに作動流体が給排されることによって伸縮作動する流体圧シリンダであって、
　前記シリンダは、請求項１から４のいずれか一つに記載の耐圧機器である流体圧シリンダ。 A fluid pressure cylinder that expands and contracts when working fluid is supplied to and discharged from the cylinder.
The cylinder is a fluid pressure cylinder which is a pressure resistant device according to any one of claims 1 to 4.
PCT/JP2021/007947 2020-03-13 2021-03-02 Pressure resistant instrument and fluid pressure cylinder Ceased WO2021182184A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020-044381 2020-03-13
JP2020044381A JP2021143748A (en) 2020-03-13 2020-03-13 Pressure-resistant device and fluid pressure cylinder

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WO2021182184A1 true WO2021182184A1 (en) 2021-09-16

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01116204U (en) * 1988-01-29 1989-08-04
JPH0362216U (en) * 1989-10-23 1991-06-18
WO2008105005A1 (en) * 2007-03-01 2008-09-04 Toscotec S.P.A. Yankee cylinder for paper producing machine
JP2012127433A (en) * 2010-12-16 2012-07-05 Ud Trucks Corp Structure for relaxing stress concentration of structured body
JP2016539006A (en) * 2013-11-19 2016-12-15 バルメット、アクチボラグＶａｌｍｅｔ Ａｋｔｉｅｂｏｌａｇ How to make a steel Yankee cylinder
JP2019063853A (en) * 2017-10-05 2019-04-25 Ｋｙｂ株式会社 Pressure proof device and fluid pressure cylinder

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01116204U (en) * 1988-01-29 1989-08-04
JPH0362216U (en) * 1989-10-23 1991-06-18
WO2008105005A1 (en) * 2007-03-01 2008-09-04 Toscotec S.P.A. Yankee cylinder for paper producing machine
JP2012127433A (en) * 2010-12-16 2012-07-05 Ud Trucks Corp Structure for relaxing stress concentration of structured body
JP2016539006A (en) * 2013-11-19 2016-12-15 バルメット、アクチボラグＶａｌｍｅｔ Ａｋｔｉｅｂｏｌａｇ How to make a steel Yankee cylinder
JP2019063853A (en) * 2017-10-05 2019-04-25 Ｋｙｂ株式会社 Pressure proof device and fluid pressure cylinder

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