WO2007043143A1 - Dispositif de pression hydraulique - Google Patents

Dispositif de pression hydraulique Download PDF

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Publication number
WO2007043143A1
WO2007043143A1 PCT/JP2005/018425 JP2005018425W WO2007043143A1 WO 2007043143 A1 WO2007043143 A1 WO 2007043143A1 JP 2005018425 W JP2005018425 W JP 2005018425W WO 2007043143 A1 WO2007043143 A1 WO 2007043143A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure chamber
pressure
bolt
load receiving
piston
Prior art date
Application number
PCT/JP2005/018425
Other languages
English (en)
Japanese (ja)
Inventor
Atsushi Imai
Original Assignee
Imai, Akira
Imai, Tooru
Imai, Yutaka
Imai, Satoshi
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Imai, Akira, Imai, Tooru, Imai, Yutaka, Imai, Satoshi filed Critical Imai, Akira
Priority to PCT/JP2005/018425 priority Critical patent/WO2007043143A1/fr
Priority to JP2007539764A priority patent/JP4839317B2/ja
Publication of WO2007043143A1 publication Critical patent/WO2007043143A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B29/00—Accessories
    • B25B29/02—Bolt tensioners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/243—Flange connections; Bolting arrangements
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B31/00—Screwed connections specially modified in view of tensile load; Break-bolts
    • F16B31/04—Screwed connections specially modified in view of tensile load; Break-bolts for maintaining a tensile load
    • F16B31/043—Prestressed connections tensioned by means of liquid, grease, rubber, explosive charge, or the like

Definitions

  • the present invention relates to a fluid pressure device in which a bolt passed through a through hole of a member to be fastened is screw-coupled in a state where a pulling force is previously held.
  • the hydraulic nut includes an annular cylinder disposed on the turbine case and a piston mounted so as to be movable in the axial direction with respect to the cylinder.
  • a pressure chamber is provided between the cylinder and the piston.
  • a compartment is formed, and an oil supply port for supplying hydraulic pressure to the pressure chamber is formed in the cylinder or piston.
  • a screw hole is formed in the axial center of the piston, and a bolt passed through the through hole of the turbine bin case is screwed into this screw hole, and the piston is screwed to the bolt.
  • a lock ring is attached to the outer periphery of the piston by screw connection.
  • a fastening direction using a bolt tensioner is known in order to screw-connect a nut in a state in which a tensile force is previously applied to the bolt.
  • the bolt tensioner has a cylinder, and a nut accommodating chamber is provided on the lower side of the cylinder, and the cylinder is placed on the turbine case so that the tip of the bolt with the nut loosely tightened is covered with the nut accommodating chamber. Be placed.
  • a piston is assembled in the cylinder so as to be movable in the axial direction, and a pressure chamber is defined by the piston and the cylinder.
  • a screw hole is formed in the axial center of the piston, and this screw hole is detachably screwed to the tip of the bolt housed in the nut housing chamber. Then, the hydraulic pressure was supplied to the pressure chamber with the piston screwed to the bolt, the nut was tightened with the tensile force applied to the bolt, and the hydraulic pressure in the pressure chamber was released to generate axial force on the bolt. In this state, the nut can be fastened to the bolt. After the fastening operation is completed, the screw connection between the piston and the bolt is released, and the bolt tensioner is removed from the turbine case. When removing the fastened nut from the bolt, the bolt tensioner is again placed on the turbine case, and the screw is screwed to the bolt to supply hydraulic pressure to the pressure chamber. The nut can be removed from the bolt by releasing the hydraulic pressure by sufficiently loosening the nut and releasing the hydraulic pressure while the piston is operated until the nut leaves the turbine case force.
  • An object of the present invention is to provide a liquid pressure device that can easily continue operation even if a pressure chamber seal failure occurs.
  • the liquid pressure device is a liquid pressure device that is screw-coupled in a state where a tensile force is applied to a bolt threaded through a through hole of the fastened member, and is disposed on the fastened member.
  • a pressure chamber is defined by the first load receiving member and a screw hole that is screw-coupled to the bolt and is assembled to the first load receiving member so as to be movable in the axial direction.
  • a second load receiving member to be formed; an intermediate piston which is assembled in the pressure chamber so as to be movable in the axial direction; and divides the pressure chamber into a first pressure chamber and a second pressure chamber; Formed in the first load chamber, and is formed in the second load receiving member.
  • the liquid pressure is applied to the second pressure chamber.
  • a second liquid pressure supply port to be supplied, and one of the first and second load receiving members.
  • a lock ring that is screw-coupled to a peripheral portion and that is in contact with the other axial end surface of the first and second load receiving members to support the axial force of the bolt, the first and second The second load receiving member can be operated even if the liquid pressure is supplied from a deviation of the liquid pressure supply port.
  • the liquid pressure device of the present invention is previously pulled by a bolt passed through the through hole of the fastening member.
  • a hydraulic device for screwing a nut in a state where force is applied comprising: a first load receiving member that is detachably arranged on the fastened member; and a screw hole that is detachably screwed to the bolt.
  • a second load receiving member that is assembled to the first load receiving member so as to be movable in the axial direction, and defines a pressure chamber by the first load receiving member; and an axial direction in the pressure chamber.
  • An intermediate piston that is movably assembled and divides the pressure chamber into a first pressure chamber and a second pressure chamber, and the first load receiving member, and guides the liquid pressure to the first pressure chamber.
  • a second liquid pressure supply port that is formed in the second load receiving member and guides the liquid pressure to the second pressure chamber. Even if the liquid pressure is supplied from the deviation of the second liquid pressure supply port, the second load receiving member is not removed. It is possible to operate.
  • the liquid pressure device includes a first seal member that prevents leakage of liquid pressure from the first pressure chamber and a second pressure that prevents leakage of liquid pressure from the second pressure chamber.
  • a sealing member is attached to the intermediate piston.
  • the second load receiving member can be operated regardless of the supply of liquid pressure from either the first or second liquid pressure supply port. Even if liquid pressure leaks from one of the pressure chambers, the liquid pressure can be supplied to the other pressure chamber and the second load receiving member can be operated to continue the fastening operation with the bolt. Thereby, the workability of the liquid pressure device can be improved. Even if a seal failure occurs in one of the first and second pressure chambers, the second load receiving member can be operated by supplying liquid pressure to the other pressure chamber without repairing it. Therefore, it is possible to work quickly in an emergency.
  • FIG. 1 is a cross-sectional view showing a part of a gas turbine using a hydraulic nut according to an embodiment of the present invention.
  • FIG. 2 is a perspective view showing details of the hydraulic nut shown in FIG. 1.
  • FIG. 3 is a cross-sectional view showing a usage state (before supplying hydraulic pressure) of the hydraulic nut shown in FIG.
  • FIG. 4 is a cross-sectional view showing a usage state of a hydraulic nut when a second lubricating oil pressure is supplied.
  • FIG. 5 is a cross-sectional view showing a usage state of the hydraulic nut when the first oil supply loca hydraulic pressure is supplied.
  • FIG. 6 is a sectional view showing details of a bolt tensioner according to another embodiment of the present invention.
  • a gas turbine 11 shown in FIG. 1 is used in a power plant such as a power plant.
  • a heat energy of a gas having a high temperature and a high pressure is converted into mechanical energy.
  • the turbine shaft is housed.
  • the turbine case 12 which is a member to be fastened, is formed to be separable into an upper case 13 and an under case 14, and is inserted into through holes 13b, 14b formed in the flanges 13a, 14a of the cases 13, 14, respectively.
  • Bolt 15 is passed through.
  • the bolt 15 is inserted from one flange 14a side, and its tip protrudes from the other flange 13a side.
  • a hydraulic nut 21 as a fluid pressure device is screwed to the threaded portion 15a.
  • the flanges 13a and 14a are sandwiched between the head 15b of the bolt 15 and the hydraulic nut 21, and the turbine case 12 is assembled.
  • the hydraulic nut 21 is screw-coupled in a state where a tensile force is applied to the bolt 15, and the turbine case 12 is firmly fastened with the bolt 15 after fastening being in a state where an axial force is generated.
  • FIG. 2 is a perspective view showing details of the hydraulic nut shown in FIG. 1
  • FIG. 3 is a sectional view showing a usage state (before supplying hydraulic pressure) of the hydraulic nut shown in FIG. 2
  • FIG. FIG. 2 is a cross-sectional view showing a usage state of a hydraulic nut when a two-fuel supply rocker hydraulic pressure is supplied.
  • the hydraulic nut 21 includes a cylinder 22 as a first load receiving member and a pin as a second load receiving member.
  • the outer shape is formed in a substantially cylindrical shape.
  • the cylinder 22 is formed in a bottomed cylindrical shape in which a disk-shaped bottom wall portion 22a and a cylindrical side wall portion 22b are integrated by cutting a steel material.
  • the fastening surface 22c formed on the lower surface of the bottom wall portion 22a is arranged on the flange 13a of the turbine case 12.
  • a cylinder chamber 24 is formed inside the side wall portion 22b, and the screw portion 15a of the bolt 15 protruding from the flange 13a is inserted through a through hole 22d provided in the shaft center of the bottom wall portion 22a. Projects inside 24.
  • the piston 23 is formed in a substantially annular shape in which the large-diameter cylindrical portion 23a and the small-diameter cylindrical portion 23b are integrated by cutting a steel material, and the outer peripheral surface of the large-diameter cylindrical portion 23a is formed.
  • the piston 23 is assembled to the cylinder 22 so as to be movable in the axial direction by being in sliding contact with the inner peripheral surface of the cylinder chamber 24 and the outer peripheral surface of the small diameter cylindrical portion 23b being in sliding contact with the inner peripheral surface of the through hole 22d.
  • a screw hole 25 is formed in the shaft center of the piston 23, and the piston 23 is screwed to the screw portion 15 a of the bolt 15 in the screw hole 25. Therefore, when the piston 23 moves in the direction away from the cylinder 22 (upward in FIG. 2) with the bolt 15 screwed to the screw hole 25 of the piston 23, the bolt 15 is pulled by the piston 23. That's true.
  • An annular pressure chamber 26 is defined by these members between the cylinder 22 and the piston 23.
  • the piston 23 moves in the direction away from the cylinder 22, that is, away from the flange 13a, the pressure is increased.
  • the volume of chamber 26 is increased.
  • An intermediate piston 27 is assembled in the pressure chamber 26 so as to be movable in the axial direction with respect to the cylinder 22 and the piston 23.
  • the intermediate piston 27 is formed in an annular shape in sliding contact with the inner peripheral surface of the cylinder chamber 24 at the outer peripheral portion and in sliding contact with the outer peripheral surface of the piston 23 at the inner peripheral portion, and the pressure chamber 26 is connected to the first pressure chamber 26a.
  • the second pressure chamber 26b are divided into two in the axial direction.
  • the cylinder 22 is provided with a first oil supply port 31 as a first liquid pressure supply port in order to supply liquid pressure, that is, hydraulic pressure using hydraulic oil as a working medium, into the first pressure chamber 26a. It has been done.
  • the first oil supply port 31 has a connection portion 31a that opens to the side surface of the cylinder 22, and a guide hole 31b that penetrates from the connection portion 31a to the first pressure chamber 26a. It is connected to a hydraulic pump (not shown), and hydraulic pressure can be supplied to the inside of the first pressure chamber 26a via the hydraulic pump force guide hole 31b.
  • the piston 23 has three second oil supply ports 32 as second liquid pressure supply ports for supplying liquid pressure, that is, hydraulic pressure, into the second pressure chamber 26b. Yes.
  • Each of these second oil supply ports 32 has a connection portion 32a that opens to the axial end surface of the piston 23, and a guide hole 32b that penetrates from the connection portion 32a to the second pressure chamber 26b.
  • the hydraulic pump 32a is connected to a hydraulic pump (not shown) so that the hydraulic pump can also supply hydraulic pressure to the inside of the second pressure chamber 26b through the guide hole 32b.
  • one of the second oil supply ports 32 is opened for air venting, and after the inside of the second pressure chamber 26b is filled with hydraulic oil, the connection portion 32a is not shown in the figure. Even if it is blocked with ⁇ .
  • the force by which the piston 23 has three second oil supply ports 32 for supplying hydraulic pressure to the second pressure chamber 26b is not limited thereto, and the number thereof is not limited to this. It can be set arbitrarily. Also, form a port for venting air separately from the second oil filler port 32.
  • a seal member 33a that is in sliding contact with the outer peripheral surface of the small-diameter cylindrical portion 23b is attached to the bottom wall portion 22a of the cylinder 22, and the intermediate piston
  • a first seal member 34 slidably in contact with the inner peripheral surface of the cylinder chamber 24 is attached to the axial end of the outer peripheral portion of the intermediate piston 27 on the first pressure chamber 26a side.
  • a first seal member 35 slidably in contact with the outer peripheral surface of the small-diameter cylindrical portion 23b is attached to the axial end on the pressure chamber 26a side.
  • a seal member 33b slidably contacting the inner peripheral surface of the cylinder chamber 24 is attached to the outer peripheral portion of the large-diameter cylindrical portion 23a of the piston
  • a second seal member 36 slidably contacting the inner peripheral surface of the cylinder chamber 24 is attached to the axial end of the outer peripheral portion of the intermediate piston 27 on the second pressure chamber 26b side, and the inner peripheral portion of the intermediate piston 27 is attached.
  • a second seal member 37 that is in sliding contact with the outer peripheral surface of the small-diameter cylindrical portion 23b is attached to the axial end of the second pressure chamber 26b.
  • a lock ring 41 is attached to the outer peripheral portion of the piston 23 in order to support the axial force of the bolt 15 applied to the piston 23.
  • the lock ring 41 is formed in an annular shape from a steel material, and as shown in FIG. 3, a female thread portion 41a is formed on the inner peripheral surface of the lock ring 41, and the lock ring 41 has a large diameter of the piston 23 at the female thread portion 41a. It is screwed to a male screw portion 23c formed on the outer peripheral portion of the cylindrical portion 23a. Therefore, the lock ring 41 can be moved in the axial direction with respect to the piston 23 by rotating the lock ring 41. Further, the axial end surface (the lower end surface in FIG.
  • a load support surface 41b perpendicular to the axial direction of the lock ring 41 is a load support surface 41b, and this load support surface 41b is the opening side of the side wall portion 22b of the cylinder 22. It faces the axial end face 22e. Then, by rotating the lock ring 41 in the circumferential direction, the load supporting surface 41b of the lock ring 41 and the axial end surface 22e of the cylinder 22 can be brought into contact with each other.
  • the hydraulic nut 21 is arranged so that the cylinder 22 is arranged in the upper case 13, and the threaded portion 15a of the bolt 15 passed through the through hole 22d is connected to the piston 23. Screwed into screw hole 25. At this time, no hydraulic pressure is supplied to the first pressure chamber 26 a and the second pressure chamber 26 b, and the piston 23 is close to the cylinder 22.
  • a hydraulic pump (not shown) is connected to the second oil supply port 32, and hydraulic oil is supplied from the second oil supply port 32 to the inside of the second pressure chamber 26b with a predetermined pressure by the hydraulic pump.
  • the hydraulic pressure supplied to the second pressure chamber 26b is, for example, an ultra-high pressure of about 250 Mpa.
  • the piston 23 moves in a direction to increase the volume of the second pressure chamber 26b, that is, away from the cylinder 22, and as shown in FIG.
  • the threaded portion 15 a moves in the axial direction together with the piston 23 and a tensile force is applied, and the bolt 15 extends in the axial direction due to the tensile force.
  • the mouth ring 41 moves together with the piston 23 and moves to a position where a gap L is formed between the load supporting surface 41b and the axial end surface 22e of the cylinder 22 as shown by a one-dot chain line in FIG. To do.
  • the lock ring 41 is rotated and moved to a position where the load supporting surface 21b abuts against the axial end surface 22e of the cylinder 22 (a position indicated by a solid line in FIG. 4).
  • the supply of hydraulic pressure to the pressure chamber 26b of 2 is stopped.
  • the hydraulic pressure in the second pressure chamber 26b is reduced, and the axial force due to the elastic force of the bolt 15, that is, the force applied in the direction approaching the cylinder 22 is applied to the piston 23.
  • FIG. 5 is a cross-sectional view showing a usage state of the hydraulic nut when the first oil supply rocker hydraulic pressure is supplied.
  • the hydraulic pressure is supplied from the first oil supply port 31 instead of the second oil supply port 32.
  • the piston 23 can be operated in the axial direction.
  • the intermediate piston 27 reduces the volume of the second pressure chamber 26b and the first pressure chamber 26a by the hydraulic pressure. After the intermediate piston 27 comes into contact with the axial end surface of the piston 23, the piston 23 is operated in the axial direction by being pushed by the intermediate piston 27.
  • the second oil supply port 32 also maintains the airtightness of the second pressure chamber 26b. Even if the sealing members 33b, 36, and 37 cannot be able to withstand the high pressure and are damaged and the second pressure chamber 26b cannot be raised to the specified hydraulic pressure, By supplying hydraulic pressure to the pressure chamber 26a, the piston 23 can be operated to pull the tension force on the bolt 15. That is, in this hydraulic nut 21, the pressure chamber 26 is divided into two by the intermediate piston 27. Therefore, when one of the second pressure chambers 26b generates a hydraulic leak, the second oil supply port 32 is replaced. The piston 23 can be operated in the axial direction by supplying hydraulic pressure from the first oil supply port 31 to the first pressure chamber 26a.
  • the piston 23 can be operated regardless of whether the oil pressure is supplied from either the first oil supply port 31 or the second oil supply port 32, so the second pressure chamber 26b Even if hydraulic pressure leaks from the piston 23, the piston 23 can be operated by supplying hydraulic pressure to the first pressure chamber 26a. Therefore, even if hydraulic pressure leaks from the pressure chamber 26, it is possible to continue the fastening operation and the removing operation of the hydraulic nut 21 with the bolt 15, thereby improving the working efficiency of the hydraulic nut 21. be able to.
  • the piston 23 can be operated by supplying hydraulic pressure to the other pressure chamber 26a, so that work can be performed quickly in an emergency. Furthermore, even if a hydraulic leak occurs from the pressure chamber 26, it is not necessary to cut the lock ring 41, etc., so that work at the time of trouble avoidance is facilitated and safety of the work is improved.
  • FIG. 6 is a sectional view showing details of a bolt tensioner according to another embodiment of the present invention.
  • members corresponding to those described above are denoted by the same reference numerals. ing.
  • a bolt tensioner 51 as a fluid pressure device shown in FIG. 6 is used for screwing a nut 52 in a state in which a tension force is previously held on a bolt 15 for fastening a turbine case 12.
  • a nut 52 is screwed together with an axial force applied to the bolt 15 to obtain a large fastening force.
  • the cylinder 22 of the bolt tensioner 51 is formed with a cylindrical nut receiving portion 53 on the flange 13a side of the pressure chamber 26.
  • the cylinder 22 of the bolt tensioner 51 has a bolt 15 that receives the nut. It is arranged on the upper case 13 so as to be detachable so as to be located inside the portion 53. Note that a nut 52 is lightly screwed to the bolt 15 in advance, and the nut 52 is disposed in the nut accommodating portion 53 together with the bolt 15.
  • a window portion 54 is formed in the nut accommodating portion 53, and a nut 52 is tightened from the window portion 54.
  • a nut adapter 55 is fitted into the nut 52.
  • the nut adapter 55 has an engagement hole 55a on the outer peripheral surface and is inserted from the window portion 54.
  • the bolt tensioner 51 is arranged on the bolt 15 that is lightly screw-coupled with the nut 52, and is inserted into the screw hole 25 of the piston 23. Screw bolt 15 together.
  • hydraulic pressure is supplied from the second oil supply port 32, the hydraulic pressure in the second pressure chamber 26 b is increased, the piston 23 is moved away from the cylinder 22, and a tensile force is applied to the bolt 15.
  • a tensile force is applied, the bolt 15
  • the nut 52 moves along with the bolt 15 in a direction away from the flange 13a of the upper case 13, and a gap is formed between the nut 52 and the upper case 13.
  • the pressure chamber 26 defined by the cylinder 22 and the piston 23 is divided into two axially by the intermediate piston 27, and is supplied from the second oil supply port 32.
  • the pressure chamber 26b is divided into two axially by the intermediate piston 27, and is supplied from the second oil supply port 32.
  • the nut 52 can be fastened or removed. Therefore, even if the second pressure chamber 26b leaks during the fastening operation of the large number of bolts 15, the hydraulic pressure can be supplied from the first oil supply port 31 and the operation can be continued.
  • the workability is improved because it is not necessary to suspend the work to prepare another bolt tensioner. In this case, maintenance such as replacement of the seal member is required after the work is completed.
  • the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention.
  • the force used for assembling the hydraulic case 21 for the assembly of the turbine case 12 is not limited to this, but may be used for fastening other members to be fastened.
  • the hydraulic pressure is supplied to the pressure chamber 26.
  • the present invention is not limited to this.
  • the liquid is incompressible and fluid, such as water.
  • Other liquid pressures may be supplied.
  • the second oil supply port 32 mainly leads to the second pressure chamber 26b.
  • the hydraulic pressure is supplied to operate the piston 23, and when the second pressure chamber 26b leaks, the hydraulic pressure is supplied from the first oil supply port 31 to the first pressure chamber 26a.
  • the first oil filler 31 may be mainly used, and the second oil filler 32 may be used as a spare.
  • the force in which the cylinder 22 is provided as the first load receiving member and the piston 23 is provided as the second load receiving member is not limited to this, and the first load A piston portion may be provided on the receiving member, and a cylinder portion may be provided on the second load receiving member.
  • the lock ring 41 is mounted on the outer peripheral surface of the piston 23, but the present invention is not limited to this, and the lock ring 41 may be mounted on the outer peripheral surface of the cylinder 22. Good.
  • the piston 23 is formed with an axial end surface that can come into contact with the load support surface 41 b of the lock ring 41.
  • the present invention can be applied when a strong fastening structure is required, such as assembly of a steam turbine or a gas turbine turbine case used in a power plant such as a power plant.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Connection Of Plates (AREA)
  • Actuator (AREA)

Abstract

La présente invention concerne un écrou hydraulique (21) utilisé pour assembler un carter de turbine (12) en joignant par filetage un carter de turbine (12) à un boulon (15) qui est inséré dans un orifice d’insertion (13b) du carter de turbine (12) avec une force de traction auparavant appliquée sur le boulon (15). L’écrou hydraulique (21) possède un vérin (22) et un piston (23) qui sont agencés au niveau du carter de turbine (12). Un piston intermédiaire (27) est installé de façon axialement mobile dans une chambre de pression (26) définie et formée entre le vérin (22) et le piston (23), et la chambre de pression (26) est divisée par le piston intermédiaire (27) en deux chambres qui sont une première chambre de pression (26a) et une seconde chambre de pression (26b). Dans le vérin (22) est formée une première ouverture d’alimentation en huile (31) destinée à distribuer une pression hydraulique à la première chambre de pression (26a), et dans le piston (23) est formée une seconde ouverture d’alimentation en huile (32) destinée à distribuer une pression hydraulique à la seconde chambre de pression (26b). Le piston (23) peut être actionné lorsque la pression hydraulique est distribuée à partir de l’une quelconque de la première ouverture d’alimentation en huile (31) et de la seconde ouverture d’alimentation en huile (32).
PCT/JP2005/018425 2005-10-05 2005-10-05 Dispositif de pression hydraulique WO2007043143A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2005/018425 WO2007043143A1 (fr) 2005-10-05 2005-10-05 Dispositif de pression hydraulique
JP2007539764A JP4839317B2 (ja) 2005-10-05 2005-10-05 液体圧装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2005/018425 WO2007043143A1 (fr) 2005-10-05 2005-10-05 Dispositif de pression hydraulique

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WO2007043143A1 true WO2007043143A1 (fr) 2007-04-19

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Cited By (7)

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Publication number Priority date Publication date Assignee Title
JP2010065720A (ja) * 2008-09-09 2010-03-25 Toa Valve Engineering Inc 流体圧ナット
WO2014178092A1 (fr) * 2013-04-30 2014-11-06 株式会社 日本製鋼所 Ensemble couvercle pour contenant sous pression, et amortisseur hydraulique
WO2015066504A1 (fr) * 2013-10-31 2015-05-07 Hennessy Industries, Inc. Appareil de serrage de pneu pour une machine d'entretien de roues
CN108708899A (zh) * 2018-08-13 2018-10-26 上海宝骜工业技术服务有限公司 一种改进液压螺母及其应用的液压螺母组件
WO2019126426A1 (fr) 2017-12-20 2019-06-27 Superbolt, Inc. Tendeurs multi-boulons hydrauliques à chambres multiples
EP3471920A4 (fr) * 2016-06-16 2020-03-04 Superbolt, Inc. Améliorations apportées à des tensionneurs à vérins multiples
WO2020077396A1 (fr) * 2018-10-15 2020-04-23 Nord-Lock Switzerland Gmbh Outil de mise sous tension et de libération hydraulique pour éléments de fixation à expansion

Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
CN114083490B (zh) * 2022-01-25 2022-04-12 江苏华恩机械科技有限公司 具有智能校准功能的液压拉伸器及其方法

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JPS59155315U (ja) * 1983-04-05 1984-10-18 三菱重工業株式会社 ボルト締付装置
JPS6298815U (fr) * 1985-12-13 1987-06-24
JPH11347857A (ja) * 1998-06-10 1999-12-21 Toshiba Corp 油圧式テンショナーおよびテンショナー装置

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JPS6298815A (ja) * 1985-10-25 1987-05-08 Hitachi Ltd 半導体集積回路装置

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Publication number Priority date Publication date Assignee Title
JPS59155315U (ja) * 1983-04-05 1984-10-18 三菱重工業株式会社 ボルト締付装置
JPS6298815U (fr) * 1985-12-13 1987-06-24
JPH11347857A (ja) * 1998-06-10 1999-12-21 Toshiba Corp 油圧式テンショナーおよびテンショナー装置

Cited By (15)

* Cited by examiner, † Cited by third party
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JP2010065720A (ja) * 2008-09-09 2010-03-25 Toa Valve Engineering Inc 流体圧ナット
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