EP4101592A1 - Dispositif de presse et système de presse - Google Patents

Dispositif de presse et système de presse Download PDF

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Publication number
EP4101592A1
EP4101592A1 EP21179007.6A EP21179007A EP4101592A1 EP 4101592 A1 EP4101592 A1 EP 4101592A1 EP 21179007 A EP21179007 A EP 21179007A EP 4101592 A1 EP4101592 A1 EP 4101592A1
Authority
EP
European Patent Office
Prior art keywords
spindle
wheel
drive wheel
pressing
drive
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.)
Granted
Application number
EP21179007.6A
Other languages
German (de)
English (en)
Other versions
EP4101592B1 (fr
Inventor
Valentin STALDER
Roger Dejakum
Albert Loichinger
Peter Eichenberger
Raphael JUD
Rudolf Kamber
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.)
Geberit International AG
Original Assignee
Geberit International AG
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 Geberit International AG filed Critical Geberit International AG
Priority to EP21179007.6A priority Critical patent/EP4101592B1/fr
Publication of EP4101592A1 publication Critical patent/EP4101592A1/fr
Application granted granted Critical
Publication of EP4101592B1 publication Critical patent/EP4101592B1/fr
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Anticipated expiration legal-status Critical

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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
    • B25B27/00—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for
    • B25B27/02—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same
    • B25B27/10—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same inserting fittings into hoses

Definitions

  • the present invention relates to a pressing device according to claim 1 and a pressing system according to claim 14.
  • press fittings When connecting drinking water pipes, press fittings are often used, which are pressed with a press tool.
  • Such pressing tools comprise a pressing device and a pressing tool, such as a pressing jaw or a pressing sling, which is exchangeably attached to the pressing device.
  • a pressing force can be applied to the press jaws and the press fitting is pressed with the press jaws.
  • a piston in the pressing device is extended with great force and acts on the pressing jaws.
  • Such pressing devices are designed electrohydraulically, with an oil pressure being built up with a pump, which then causes a force on the piston, which in turn acts on the pressing jaws.
  • the hydraulic mode of operation has various disadvantages. Manufacturing technology very precise tolerances are required, which makes production expensive.
  • the handling of the oil when filling it for the first time and also during maintenance work is complex. The oil also diffuses over time, which leads to a loss of pressing force.
  • the DE 203 05 473 U1 proposes a hydraulic oil-free pressing device, with a planetary gear being provided between a press ram and a drive.
  • the use of such planetary gears is disadvantageous because the planetary gears are very complex and therefore prone to failure.
  • the planetary gears are usually very bulky, which makes them difficult to use in tight spaces.
  • the invention is based on the object of specifying a pressing device which overcomes the disadvantages of the prior art.
  • it is an object of the present invention to specify a pressing device which is compact and which can apply high pressing forces.
  • a pressing device comprises an electric motor with an output shaft, a gear driven by the output shaft, a spindle driven by the gear and defining a central axis, a plunger driven by the spindle, and a tool holder for receiving a pressing tool.
  • the gear has a first gear part acting on the spindle and a second gear part acting on the spindle.
  • the first transmission part has a first drive wheel and spindle wheel, with the spindle being mounted in the spindle wheel in a rotationally fixed and longitudinally displaceable manner.
  • the spindle wheel is rotatable with respect to a rotation about the central axis and fixed with respect to a movement along the central axis, that is to say it is mounted immovably.
  • the second transmission part has a second drive wheel and a spindle nut driven by the second drive wheel.
  • the spindle nut is rotatable with respect to a rotation about the central axis and fixed with respect to a movement along the central axis, that is to say it is mounted immovably.
  • the spindle wheel and the spindle nut are set in rotation in such a way that the spindle undergoes an axial advance in relation to the spindle wheel and in relation to the spindle nut, with this axial advance of the spindle causing the plunger to undergo an advance movement in the direction of the tool holder, so that a pressing movement can be performed by the plunger.
  • the spindle is moved in the axial direction relative to the spindle wheel and the spindle nut as well as to the two drive wheels.
  • the spindle is moved forward from an initial position in the direction of the central axis moved to an end position.
  • the movement from the end position to the starting position is effected by reverse drive of the electric motor.
  • the outer diameter of the spindle essentially defines the buckling strength of the spindle. At the same time, the outer diameter of the spindle has only a very small influence on the compactness of the pressing device. Thus, a pressing device can be specified which can apply large forces under the stipulation of a compact design.
  • the first drive wheel and the second drive wheel are preferably arranged on a common drive shaft. This has the advantage of a simple construction, because only one drive shaft has to be driven by the output shaft of the electric motor.
  • the output shaft of the electric motor preferably acts indirectly on the drive shaft via a drive gear. This has the advantage that a transmission or reduction stage can be provided in the drive housing. Alternatively, the output shaft of the electric motor acts directly on the input shaft, which can simplify the mechanical design. The input shaft can also be provided by the output shaft from the electric motor.
  • the first drive wheel and the spindle wheel each have a toothing, with the toothing of the first drive wheel engaging in the toothing of the spindle wheel.
  • the second drive wheel and the spindle wheel each have teeth, the teeth of the second drive wheel engaging in the teeth of the spindle wheel.
  • the design of the elements mentioned as gears has the advantage that large forces can be efficiently transmitted.
  • the teeth are preferably external teeth.
  • the toothing can be of any design, in particular with regard to the number and shape of the teeth.
  • toothing instead of the toothing, other elements that can transmit a rotational movement and a torque can also be provided.
  • the distance between the first drive wheel and the second drive wheel is fixed.
  • the distance between the spindle wheel and the spindle nut is also fixed.
  • the spindle wheel and the spindle nut are set in rotation.
  • the transmission ratios between the first drive wheel and the spindle wheel and between the second drive wheel and the spindle nut are preferably such that the spindle nut rotates at a lower speed than the spindle, so that said propulsion can be provided, and that a greater torque is preferably generated via the spindle nut can be provided on the spindle than on the spindle wheel.
  • the transmission ratio between the first drive wheel and the spindle wheel is preferably smaller than the transmission ratio between the second drive wheel and the spindle nut.
  • the transmission ratio between the first drive wheel and the spindle wheel is preferably between 1:2 and 1:10, in particular at 1:5.13.
  • the transmission ratio between the second drive wheel and the spindle nut is preferably between 1% and 50%, in particular 9% higher than between the first drive wheel and the spindle wheel.
  • the overall transmission ratio of the gearbox is preferably between 1:20 and 1:200, in particular at 1:65.
  • the speed of the drive shaft and thus of the first drive wheel and the second drive wheel is preferably in the range from 500 revolutions per minute to 15,000 revolutions per minute, in particular in the range from 1,500 revolutions per minute to 5,000 revolutions per minute.
  • the differential speed between the spindle and the spindle nut is preferably in the range from 60 to 3,000 revolutions per minute.
  • the spindle and the spindle nut preferably rotate in the same direction of rotation.
  • the pressing device preferably also has a support structure, the first drive wheel and the spindle wheel being rotatably mounted at a bearing point of the support structure, and the second drive wheel and the spindle nut being rotatably mounted at another bearing point in the support structure.
  • the two bearing points are at a fixed distance from one another and are preferably firmly connected to one another.
  • the drive wheels, the spindle wheel and the spindle nut are preferably mounted on the bearing point via roller bearings, with the bearing point having correspondingly designed receptacles.
  • the electric motor and/or the drive shaft of the drive gear is also mounted on the support structure.
  • the tool holder is preferably also mounted on the support structure.
  • the non-rotatable and longitudinally displaceable connection between the spindle wheel and the spindle is preferably provided by a splined shaft connection, in particular by a multi-splined shaft connection.
  • a mechanically simple mounting can be provided, which can easily fulfill the two functions of being non-rotatable and longitudinally displaceable.
  • the spindle is preferably connected to the plunger via an axial bearing.
  • the plunger is preferably mounted in a longitudinal guide in the direction of the central axis of the spindle so that it can be displaced longitudinally but is non-rotatably mounted on the tool holder.
  • the first drive wheel and the second drive wheel are axially offset from the central axis of the spindle.
  • the elements of the two gear parts are therefore next to the spindle.
  • the pitch of the spindle is preferably in the range from 1.5 to 10, in particular from 5 to 7 millimeters and/or that the spindle and the spindle nut are designed as ball screws.
  • the diameter of the spindle is in the range from 10 to 30 millimeters, in particular from 18 to 22 millimeters.
  • the spindle can also be designed as a spindle with a metric thread or as a spindle with a trapezoidal thread.
  • the pitch of the metric thread or the trapezoidal thread is preferably in the range from 1.5 to 10 millimeters.
  • the power of the motor is in the range of 200 to 1500 watts.
  • the engine's torque ranges from 0.5 to 4.5 Newton meters.
  • the pressing piston preferably has a pair of rollers on the front side, which can be moved against a pressing tool fastened in the tool holder.
  • the pressing force provided by the pressing piston is applied to the pressing tool via the pair of rollers.
  • the information given here with regard to the parameters can also be selected to be larger or smaller when the pressing device is scaled.
  • a pressing system includes a pressing device according to the above description and a pressing tool inserted into the tool holder, such as a pressing jaw or a pressing sling.
  • the pressing device 1 comprises an electric motor 2 with an output shaft 3, a gear 4 driven by the output shaft 3, a spindle 5 which is driven by the gear 4 and defines a central axis M, a pressing piston 6 which is driven by the spindle 5, and a tool holder 7 for Recording of a pressing tool.
  • the pressing device further comprises a drive gear 11 which is arranged between the output shaft 3 and the gear 4 .
  • the pressing tool is, for example, a pressing jaw or pressing tongs, a pressing sling or another pressing tool. A fitting of a pipe connection can be pressed with the pressing tool.
  • the pressing device 1 and the pressing tool not shown in the figures, form a pressing system.
  • the electric motor 2 acts on the transmission 4 with its output shaft 3 .
  • said drive gear is arranged between the gear 4 .
  • a gearwheel 11a of the drive gear 11 is arranged on the output shaft 3 of the electric motor 2 .
  • the gear 11a acts on a gear 10a of a drive shaft 10 of the transmission 4 .
  • the output shaft 3 is connected to the rotor shaft of the electric motor by a shaft coupling 25 .
  • the output shaft 3 can also be provided directly by the rotor shaft.
  • the tool holder 7 has a jaw-like receiving section 16 and a bearing opening 17 in which the plunger 6 is mounted.
  • the pressing tool is mounted in the jaw-like receiving section 16 .
  • Various pressing tools can be used in the receiving section 16 .
  • the gear 4 has a first gear part 8 and a second gear part 9 . Both the first gear part 8 and the second gear part 9 act on the spindle.
  • the first transmission part 8 has a first drive wheel 8a and a spindle wheel 8b.
  • the second transmission part 9 has a second drive wheel 9a and a spindle nut 9b.
  • the two drive wheels 8a, 9a are mounted on the drive shaft 10, which, as described above, is driven directly or indirectly via the drive gear 11 by the electric motor 2.
  • the figures also show that there is a support structure 12 in which the individual parts are mounted.
  • the support structure 12 according to the present embodiment essentially comprises a first bearing point 13 and a second bearing point 14.
  • the two bearing points 13, 14 are firmly connected to one another. For example via a housing or a similar structure.
  • the first bearing point 13 provides a bearing for the drive gear 11 and the electric motor 2 . Furthermore, the first bearing point provides a bearing for the drive shaft 10 and the spindle wheel 8b.
  • the first bearing point 13 has corresponding bearing openings for the storage of the elements mentioned, in which the elements mentioned are stored.
  • the spindle wheel 8b is rotatable, but axially immovable, mounted in the corresponding bearing opening.
  • the second bearing point 14 provides storage for the drive shaft 10 and the spindle nut 9b.
  • the drive shaft 10 is mounted on the first bearing point 13 and the second bearing point 14 .
  • the second bearing point 14 has corresponding bearing openings for the storage of the elements mentioned, in which the elements mentioned are stored.
  • the spindle nut 9b is rotatable, but axially immovable, mounted in the corresponding bearing opening.
  • the tool holder 7 is also firmly connected to the support structure.
  • the spindle 5 is non-rotatably mounted with a spindle end 18 and is longitudinally displaceable in the spindle wheel 8b.
  • the mounting is such that a rotary movement acting on the spindle wheel 8b can be transmitted to the spindle 5, the spindle 5 being rotated, and that the spindle 5 can be displaced in the direction of its central axis M relative to the spindle wheel 8b. This displacement is the result of the action of the second Transmission part 9, as will be described below.
  • the spindle 5 is connected to the spindle wheel 8b via a splined connection 19 .
  • Other types of connection are also conceivable.
  • the spindle nut 9b engages in the external thread 20 on the spindle 5 .
  • the spindle nut has an internal thread 21 for this purpose.
  • the spindle nut 9b is rotated about the central axis M of the spindle 5 via the second drive wheel 9a.
  • the speed of the spindle nut 9b is lower than the speed of the spindle wheel 8b. This means that the spindle 5 rotates faster than the spindle nut 9b.
  • This provides a spindle drive and the compressive force can also be applied to the press block 6 through this spindle drive.
  • the spindle nut 9b is rotatable with respect to rotation about the central axis M and fixed with respect to a movement along the central axis M.
  • the spindle nut 9b is fixed with respect to an axial movement.
  • the drive wheel 8a drives the spindle wheel 8b and the drive wheel 9a drives the spindle nut 9b.
  • the gear ratios between the first drive wheel 8a and the spindle wheel 8b and between the second drive wheel 9a and the spindle nut 9b are such that the spindle nut 9b rotates at a lower speed than the spindle 5, so that said propulsion can be provided, and that via the Spindle nut 9b, a greater torque can be applied to the spindle 5 than via the spindle wheel 8b.
  • the speed difference between the spindle wheel 8b and the spindle nut 9b forms the speed relevant for the spindle feed. In other words, the spindle wheel 8b rotates at a higher speed than the spindle nut 9b.
  • the transmission ratio between the first drive wheel 8a and the spindle wheel 8b is between 1:2 and 1:10, in particular at 1:5.13, and the transmission ratio between the second drive wheel 9a and the spindle nut 9b is between 1% and 50%, in particular around 9%, higher than between the first drive wheel and the spindle wheel.
  • the overall transmission ratio of the transmission 4 is preferably between 1:20 and 1:200, in particular at 1:65.
  • the Figure 4a shows a sectional view through the section line BB figure 3 .
  • the output shaft 3 of the electric motor 2 engages in the gear 10a of the drive shaft 10.
  • the Figure 4b shows a sectional view through the section line CC figure 3 .
  • the first drive wheel 8a engages in the spindle wheel 8b.
  • the Figure 4c shows a sectional view through the section line DD figure 3 .
  • the second drive wheel 9a engages in the spindle nut 9b.
  • the first drive wheel 8a and the spindle wheel 8b each have a toothing, the toothing of the first drive wheel 8a engaging in the toothing of the spindle wheel 8b.
  • the second drive wheel 9a and the spindle nut 9b each have teeth, the teeth of the second drive wheel 9a engaging in the teeth of the spindle wheel 9b.
  • the toothing is an integral part of the spindle wheel 8b.
  • the toothing is formed separately from the actual nut and is connected to the nut with a wedge connection 26. An integral training would also be conceivable.
  • An axial bearing 15 which acts on the plunger 6 is arranged on the front side of the spindle 5 .
  • the spindle 5 has a shoulder-shaped receptacle 22 on which the axial bearing 15 rests.
  • the plunger has a receptacle 23, which also serves to accommodate the axial bearing.
  • the plunger 6 further has a pair of rollers 24 which acts on the pressing tool.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
EP21179007.6A 2021-06-11 2021-06-11 Dispositif de presse et système de presse Active EP4101592B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21179007.6A EP4101592B1 (fr) 2021-06-11 2021-06-11 Dispositif de presse et système de presse

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21179007.6A EP4101592B1 (fr) 2021-06-11 2021-06-11 Dispositif de presse et système de presse

Publications (2)

Publication Number Publication Date
EP4101592A1 true EP4101592A1 (fr) 2022-12-14
EP4101592B1 EP4101592B1 (fr) 2023-11-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP21179007.6A Active EP4101592B1 (fr) 2021-06-11 2021-06-11 Dispositif de presse et système de presse

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EP (1) EP4101592B1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29919604U1 (de) * 1999-11-09 2000-01-05 Karlsruhe Forschzent Vorschubgetriebe zum gleichzeitigen Antrieb und Vorschub einer Spindel
US6240626B1 (en) * 1997-02-21 2001-06-05 Novopress Gmbh Pressen Und Presswerkzauge & Co. Kg Pressing device
DE20305473U1 (de) 2003-04-03 2003-06-12 Novopress Gmbh Handgeführtes Preßgerät

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6240626B1 (en) * 1997-02-21 2001-06-05 Novopress Gmbh Pressen Und Presswerkzauge & Co. Kg Pressing device
DE29919604U1 (de) * 1999-11-09 2000-01-05 Karlsruhe Forschzent Vorschubgetriebe zum gleichzeitigen Antrieb und Vorschub einer Spindel
DE20305473U1 (de) 2003-04-03 2003-06-12 Novopress Gmbh Handgeführtes Preßgerät

Also Published As

Publication number Publication date
EP4101592B1 (fr) 2023-11-29

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