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EP0766010A2 - Outil à main à commande hydraulique - Google Patents

Outil à main à commande hydraulique Download PDF

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Publication number
EP0766010A2
EP0766010A2 EP96114779A EP96114779A EP0766010A2 EP 0766010 A2 EP0766010 A2 EP 0766010A2 EP 96114779 A EP96114779 A EP 96114779A EP 96114779 A EP96114779 A EP 96114779A EP 0766010 A2 EP0766010 A2 EP 0766010A2
Authority
EP
European Patent Office
Prior art keywords
piston
valve
control
pressure
control valve
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.)
Withdrawn
Application number
EP96114779A
Other languages
German (de)
English (en)
Other versions
EP0766010A3 (fr
Inventor
Rudolf Herrgen
Gerhard Hellebrandt
Thilo Weber
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.)
Rothenberger Werkzeugemaschinen GmbH
Original Assignee
Rothenberger Werkzeugemaschinen GmbH
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 Rothenberger Werkzeugemaschinen GmbH filed Critical Rothenberger Werkzeugemaschinen GmbH
Publication of EP0766010A2 publication Critical patent/EP0766010A2/fr
Publication of EP0766010A3 publication Critical patent/EP0766010A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/005—Hydraulic driving means

Definitions

  • Devices of this type which are also referred to as electro-hydraulic devices, are known. They are preferably - but not exclusively - used for the radial pressing of so-called pipe connections by means of exchangeable press heads which are adapted to the pipe diameter and the shape of the pipe connection.
  • exchangeable press heads which are adapted to the pipe diameter and the shape of the pipe connection.
  • Such a press head and a pipe connection produced with it as well as the pressing process itself are described in DE 27 25 280 A1. This also shows that the pressing process must be carried out extremely precisely. In particular, it is necessary to continuously complete a pressing process once it has started, i.e. the press jaws, which are adapted to the pipe connection, must close completely.
  • Pressing operations of this type require an extremely precise chronological sequence of the individual control processes in the hydraulic control block, in particular rapid advancement and retraction of the piston in order to enable largely fatigue-free work.
  • the invention is therefore based on the object of specifying a hydraulically driven hand tool of the type described in the introduction, which contains hydraulic control elements which respond quickly and precisely to the hydraulic control block.
  • control valve check valve which is kept closed in the feed phase of the piston by the pressure of the hydraulic pump, ensures that after relieving pressure by stopping the pump motor, the hydraulic oil can flow from the pressure side of the control valve without great resistance. It should be noted here that the control body of the control valve at the end of the push-back movement of the piston is pushed back to the last millimeter by the piston itself over the plunger, ultimately by the return spring of the piston. This is a small portion of the hydraulic oil that is used as the control fluid for the control valve.
  • the annular channel in the control body into which the channels open radially, creates a very large cross section for the backflow of the hydraulic oil from the piston chamber into the tank chamber. It is the main amount of hydraulic oil that is displaced only by the return spring of the piston. It should be noted here that the design of the return spring has to be based on a compromise: a strong return spring favors a quick return movement of the piston when the hydraulic oil has to flow through narrow channels, but on the other hand consumes a considerable part of the forces when the piston is advanced. Conversely, a weak return spring favors the advance of the piston and the piston rod, but delays the backflow of the hydraulic fluid.
  • the special design of the sensor valve is also advantageous:
  • the pressure in the piston chamber always acts on a precisely defined surface of the sensor body, namely on its circular end face.
  • the solution according to the invention thus results in a chronologically exact sequence of the individual valve movements with simultaneous release of large opening cross sections, the workflow taking place more precisely and more quickly.
  • control body and the plunger projecting into the piston chamber are designed as separate components and if the plunger is guided at least largely tightly in the control block by means of a guide bushing.
  • control body is located in the piston-side section of a stepped bore and if there is an insert body with at least one first reflux channel on the pressure side of the control body in the widened section of the stepped bore remote from the piston Check valve is connected.
  • the sensor body of the sensor valve is located in the piston-side section of a stepped bore and has an annular flange which is supported against a compression spring which is held in the section of the stepped bore remote from the piston by means of an insert body.
  • a housing 1 is shown in which a pump motor 2 is housed with a motor shaft 3.
  • the housing 1 continues in a pistol-shaped handle 4, which is provided with a cable entry 5 and from which a switch button 6 protrudes.
  • a gear part 7 is screwed to the housing 1, the spur gear 8 cooperating with the end of the motor shaft 3, which is designed as a pinion.
  • a locking piston 11 with a plunger 12 (see also FIGS. 2 and 3), which acts on a locking device 13.
  • the locking device 13 is designed as a push rod which, by means of an angular extension 14, into a recess 15 protrudes between the gear part 7 and the control block 9 and against which the plunger 12 of the locking piston 11 rests.
  • the locking device 13 is held by a protective bracket 16, which forms a guide 17 for the locking device 13 on its side facing the gear part 7 and the housing 1.
  • the locking device 13 By mounting the protective bracket 16, the locking device 13 is held longitudinally displaceably in the guide 17. As long as the plunger 12 of the locking piston 11 is extended (FIG. 3), the locking device 13 is pressed against the switch button 6 and keeps the associated switch closed, so that the tool is kept in operation until the operation has been completed.
  • the piston 21 has a piston rod 22 which is surrounded by a prestressed return spring 23. Beyond the piston 21, a tank space 24 is formed, which is connected to the suction side of the pump 10 and into which the hydraulic fluid flows back when the piston 21 is pushed back. Under a screw cap 25 there is an elastomeric membrane 26 which serves to compensate for changes in volume of the hydraulic fluid.
  • the piston rod 22 has two rollers 27 at its end, only one of which is visible. These rollers interact with a press head, not shown here, which has two press jaws with inclined planes on which the rollers 27 act.
  • the press head can be fastened by means of a bolt which is held in a fork-shaped extension 29 of the cylinder 20 by a bore 28. Further explanations are unnecessary, since the working of such press heads is known.
  • a control valve 30 is arranged in the control block 9, via which the pressure side of the piston chamber 19 can be connected to the tank chamber 24.
  • This control valve 30 is shot in FIGS. 2 and 4, but is opened in FIGS. 3 and 5.
  • Of the Return flow channel 31 to the tank space 24 is shown broken off.
  • control block 9 there is also a sensor valve 32 which responds to a limit pressure for the hydraulic actuation of the control valve 30 via a control line 33. Further details of this sensor valve 32 are explained in more detail with reference to FIGS. 6 and 7.
  • control block 9 there is also a reflux valve 34 which is connected upstream of the control valve 30 via a reflux channel 35 on the pressure side. Further details are explained in more detail below with reference to FIGS. 4 and 5.
  • the pump 10 supplies the hydraulic oil in the direction of arrow 36 into the pressure channel 18 and from here into the piston chamber 19.
  • An emergency valve 37 is provided for emergencies, which is shown pulled out for the sake of clarity.
  • the emergency valve 37 is opened by a pushbutton 38, so that the oil in the pressure channel 18 and in the piston chamber 19 can flow off to the tank chamber 24 via a channel 39 and the return flow channel 31, the piston 21 moving back into its starting position according to FIG.
  • Within the channel 39 there is still a residual oil valve 40 with a tappet 41 which projects into the piston chamber 19 by approximately 2 mm, so that the residual oil valve 40 passes through at the end of the return movement of the piston 20 this is opened so that any excess pressure on the pressure side of the piston can be reduced.
  • the control block 9 has, on its end facing the piston 21, a circular disc-shaped recess 42, which to a certain extent also has a distributor function.
  • a pressure generated by the pump 10 in the pressure channel 18 does not only propagate onto the piston 21, but is also present in the main control line 43, which has branch lines (not shown here in more detail) with the locking piston 11, the sensor valve 32 and the reflux valve 34 communicates.
  • the control valve 30 has a control body 45, which has an annular channel 46, via which the piston chamber 19 can be connected to the tank chamber 24.
  • the return channel 31 already described, which leads to the tank space 24, serves this purpose.
  • the control body 45 has a pressure side 47 and an unpressurized side 48, on which a tappet 49 acts, which is guided in the control block 9 at least largely oil-tight by means of a guide bushing 50. This results in a mechanically perfect guidance of control body 45 and plunger 49 because there are no mechanical overdeterminations.
  • the oil displaced by the control body 45 during its displacement passes via the already described channel 39 and the connecting channel 51 into the already pressure-free return flow channel 31 and from there to the tank 24.
  • the control body 45 is located in the piston-side section 52 of a stepped bore 53 Pressure side 47 of the control body 45 is a widened portion remote from the piston 54 of the stepped bore 53.
  • an insert body 55 is arranged in a sealed manner and has an axial return flow channel 56, which is connected to the return flow valve 34 via the return flow channel 35 already described.
  • the reflux valve 34 has a spring-loaded cylindrical valve body 57 which is connected to the piston chamber 19 on the spring-loaded side via a channel 58 and the main control line 43.
  • the valve body 57 has a return bore 59 leading to the piston chamber 19, with which the valve body 57 is supported on a sealing body 60 in order to interrupt the connection to the control valve 30.
  • valve body 57 of the reflux valve 34 is arranged in the piston-side section 61 of a stepped bore 62.
  • a sealed insert body 64 which carries the sealing body 60.
  • FIG. 5 shows a position of the control body 45 in which the tappet 49 is pushed into the piston chamber 19 by approximately 7 mm.
  • the ring channel 46 is aligned with the main return flow channel 44 and the unpressurized return flow channel 31 leading to the tank 24.
  • This displacement has arisen under the influence of the opening of the sensor valve 32, which causes the pressure of the pump 10 via the control line 33 to the pressure side 47 of the control body 45 has passed.
  • the pump pressure is also present on the valve body 57 of the return valve 34 via the main control line 43 and the channel 58, the valve body remains closed, so that the control pressure cannot escape via the return flow channel 56.
  • the oil displaced during the forward movement of the control body 45 on its depressurized side 48 has in this case drained off via the channel 39 in the direction of the arrow 65.
  • FIGS. 6 and 7 now show the sensor valve 32 in its two alternative positions.
  • Its sensor body 67 is arranged in a stepped bore 68 which has a portion 69 on the piston side and a portion 70 remote from the piston.
  • the sensor body 67 has an annular flange 71 which is supported against a precisely prestressed compression spring 72 which determines the response pressure of the sensor valve 32.
  • This compression spring is also sealed in the control block 9 by means of an insert body 73.
  • the insert body 73 is located in the section 70 of the stepped bore 68 remote from the piston.
  • the piston-side section 69 is a cylinder bore 69a
  • the sensor body 67 has at the end of a cylinder surface 67a a circularly delimited end surface 74 which can be acted upon by the pump pressure against the force of the compression spring 72 .
  • the end face 74 need not be absolutely flat, it could also be designed as a conical surface or a truncated cone surface, but the sensor body 69 is not a ball.
  • the control line 33 opens radially into the cylinder bore 69a, which is thereby connected to the pressure side 47 of the control valve 30.
  • the sensor valve 32 is actuated by the main control line 43 in the manner already described above.
  • the oil flowing in via the main control line 43 shifts the sensor body 67 from the position shown in FIG. 6 to the position shown in FIG. this happens very defined, since the end face 74 has a precisely defined size, so that the forces arising here compress the prestressed compression spring 72 accordingly.
  • the relatively large cross-section of the control line 33 is released extremely quickly, so that the control valve 30 is also brought into its open position.
  • the sensor valve 32 thus represents, as it were, a hydraulic monostable switch which has a very clear, pressure-dependent changeover characteristic.
  • the entire hydraulic control has the following mode of operation: As soon as the pump 10 starts up from the initially depressurized state according to FIG. 2, the pump pressure acts on the piston 21, the sensor valve 32, the locking piston 11 and the reflux valve 34. With the exception of pushing out the plunger 12 to lock the switch, this initially does not trigger any further activities in the hydraulics.
  • the residual oil valve 40 is initially still in its open position. As soon as the pressure rises further and displaces the piston 21, the residual oil valve 40 is first closed by releasing its tappet 41. After overcoming an empty stroke of the connected tool, the pressure now rises steeply, as a result of which the closing force of the reflux valve 34 is increased.
  • the piston rod 22 is increasingly extended until it has reached its end position, which is dependent on the geometry of the tool, which means when connecting a press head of the type described at the outset that the press jaws are absolutely closed. At this moment the piston 21 comes to a standstill and the pressure on the pressure side of the piston 21 increases further, for example by an additional 10 to 40%.
  • the pressure increase can be influenced by adjusting the sensor valve 32. As soon as its response pressure has been reached, the sensor valve 32 opens into a position according to FIGS. 3 and 7, so that the pressure side 47 of the control valve 30 is now acted upon and its control body 45 is advanced, to a position shown in FIGS. 3 and 5 is shown.
  • the function of the emergency valve 37 certainly does not need to be explained in more detail, since this results automatically from the hydraulic circuit diagram for the person skilled in the art.
  • the plunger 12 is pushed back by the drop in the oil pressure, so that the switch button 6 is also unlocked and the pump motor comes to a standstill.
  • the hand tool according to the invention can also be used in conjunction with attachment tools other than for pressing heads, for example for actuating cutting tools (scissors) and pushing tools for the axial pushing together of Pipe connections that consist of a sleeve and two sliding sleeves that are pressed onto hoses that are pushed onto two pipe sockets of the sleeve.
  • actuating cutting tools sinissors
  • pushing tools for the axial pushing together of Pipe connections that consist of a sleeve and two sliding sleeves that are pressed onto hoses that are pushed onto two pipe sockets of the sleeve.
  • the hydraulic control element referred to as sensor valve 32 is a type of pressure relief valve which can also be referred to as a connecting valve. However, it does not serve to control the entire hydraulic oil when the pressure is exceeded, but rather as a series valve for the actual control valve 30.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
EP96114779A 1995-09-26 1996-09-16 Outil à main à commande hydraulique Withdrawn EP0766010A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19535691 1995-09-26
DE1995135691 DE19535691C1 (de) 1995-09-26 1995-09-26 Hydraulisch angetriebenes Handwerkzeug

Publications (2)

Publication Number Publication Date
EP0766010A2 true EP0766010A2 (fr) 1997-04-02
EP0766010A3 EP0766010A3 (fr) 1999-05-06

Family

ID=7773164

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96114779A Withdrawn EP0766010A3 (fr) 1995-09-26 1996-09-16 Outil à main à commande hydraulique

Country Status (2)

Country Link
EP (1) EP0766010A3 (fr)
DE (1) DE19535691C1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6276186B1 (en) 1997-10-15 2001-08-21 Gustav Klauke Gmbh Hydraulic pressing device and method for operating the same
DE10013194B4 (de) 2000-03-17 2005-02-24 Festo Ag & Co.Kg Antriebsvorrichtung
DE10106360C1 (de) * 2001-02-12 2002-07-11 Rothenberger Werkzeuge Ag Verfahren zum automatischen Steuern von elektro-hydraulischen Handwerkzeugen und Anordnung hierfür
DE20113238U1 (de) 2001-08-09 2001-11-22 Rothenberger Werkzeuge AG, 65779 Kelkheim Handwerkzeug mit einem elektrohydraulischen Antriebsteil und einem Arbeitskopf
DE102008023719A1 (de) 2007-12-14 2009-06-18 Gustav Klauke Gmbh Hydraulisches Pressgerät
EP2070660B1 (fr) 2007-12-14 2012-09-26 Gustav Klauke GmbH Appareil de presse hydraulique
DE202008015574U1 (de) * 2008-11-24 2009-12-31 Novopress Gmbh Pressen Und Presswerkzeuge & Co. Kg Antriebseinrichtung für ein Pressgerät sowie Pressgerät mit einer solchen Antriebseinrichtung
CN101825078A (zh) * 2010-03-30 2010-09-08 西安燎原液压有限责任公司 手动电动泵

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2729994A (en) * 1951-05-29 1956-01-10 Westinghouse Air Brake Co Hose clamp applying machine
DE2136782C2 (de) * 1971-07-23 1982-12-02 Novopress GmbH Pressen und Presswerkzeuge & Co KG, 4000 Düsseldorf Tragbares druckmittelbetriebenes Klemmwerkzeug
GB1535927A (en) * 1975-04-08 1978-12-13 Secretary Industry Brit Hydraulic impactors
DE2725280A1 (de) * 1977-06-01 1978-12-14 Mannesmann Roehren Werke Ag Rohrverbindung fuer leitungsrohre
US4583388A (en) * 1983-09-30 1986-04-22 West Coast Industries, Inc. Method and apparatus for hole coldworking
US4594030A (en) * 1984-01-30 1986-06-10 The Boeing Company Pneumatic-hydraulic drill unit
GB2171948B (en) * 1985-02-26 1988-07-06 Coal Ind Hydraulic impact tool
US5125324A (en) * 1988-02-10 1992-06-30 Daia Industry Co. Ltd. Portable hydraulically operated device incorporating automatic drain valve
CH681380A5 (fr) * 1990-04-09 1993-03-15 Asea Brown Boveri
DE4207764C2 (de) * 1992-03-11 1994-08-25 Hugo Junkers Werke Gmbh Hydraulik-Werkzeug mit vollständig integriertem Hydraulik-Kreislauf

Also Published As

Publication number Publication date
DE19535691C1 (de) 1997-01-23
EP0766010A3 (fr) 1999-05-06

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