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WO2021182184A1 - Instrument résistant à la pression et cylindre à pression de fluide - Google Patents

Instrument résistant à la pression et cylindre à pression de fluide 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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English (en)
Japanese (ja)
Inventor
小林　俊雄
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KYB Corp
Original Assignee
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/fr
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)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Actuator (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

L'invention concerne un cylindre (100) qui comprend : un fond de cylindre (120) qui a une section de paroi annulaire (122) s'étendant à partir d'une section de base (121) et qui ferme une ouverture d'un tube cylindrique (110) ; une bague arrière (140) qui est disposée de façon à faire face à la surface périphérique interne (110b, 122b) du tube cylindrique (110) et/ou à la section de paroi (122) ; et une section de rainure (124) qui est formée dans la surface interne du fond de cylindre (120), la section de rainure (124) ayant une première sous-section de rainure (124a) qui est formée dans la surface périphérique interne (122b) de la section de paroi (122) et une seconde sous-section de rainure (124b) qui est formée dans une surface inférieure (121a) de la section de base (121) de manière contiguë avec la première sous-section de rainure (124a).
PCT/JP2021/007947 2020-03-13 2021-03-02 Instrument résistant à la pression et cylindre à pression de fluide Ceased WO2021182184A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020044381A JP2021143748A (ja) 2020-03-13 2020-03-13 耐圧機器及び流体圧シリンダ
JP2020-044381 2020-03-13

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WO2021182184A1 true WO2021182184A1 (fr) 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 (fr) * 1988-01-29 1989-08-04
JPH0362216U (fr) * 1989-10-23 1991-06-18
WO2008105005A1 (fr) * 2007-03-01 2008-09-04 Toscotec S.P.A. Cylindre yankee de machine à papier
JP2012127433A (ja) * 2010-12-16 2012-07-05 Ud Trucks Corp 構造体の応力集中緩和構造
JP2016539006A (ja) * 2013-11-19 2016-12-15 バルメット、アクチボラグＶａｌｍｅｔ Ａｋｔｉｅｂｏｌａｇ スチールヤンキーシリンダを作製する方法
JP2019063853A (ja) * 2017-10-05 2019-04-25 Ｋｙｂ株式会社 耐圧機器及び流体圧シリンダ

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01116204U (fr) * 1988-01-29 1989-08-04
JPH0362216U (fr) * 1989-10-23 1991-06-18
WO2008105005A1 (fr) * 2007-03-01 2008-09-04 Toscotec S.P.A. Cylindre yankee de machine à papier
JP2012127433A (ja) * 2010-12-16 2012-07-05 Ud Trucks Corp 構造体の応力集中緩和構造
JP2016539006A (ja) * 2013-11-19 2016-12-15 バルメット、アクチボラグＶａｌｍｅｔ Ａｋｔｉｅｂｏｌａｇ スチールヤンキーシリンダを作製する方法
JP2019063853A (ja) * 2017-10-05 2019-04-25 Ｋｙｂ株式会社 耐圧機器及び流体圧シリンダ

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