EP0536233B1 - Vorrichtung zum antrieb eines in axialer richtung hin- und herbewegbaren werkzeuges - Google Patents

Vorrichtung zum antrieb eines in axialer richtung hin- und herbewegbaren werkzeuges Download PDF

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Publication number
EP0536233B1
EP0536233B1 EP91912127A EP91912127A EP0536233B1 EP 0536233 B1 EP0536233 B1 EP 0536233B1 EP 91912127 A EP91912127 A EP 91912127A EP 91912127 A EP91912127 A EP 91912127A EP 0536233 B1 EP0536233 B1 EP 0536233B1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
working
master cylinder
pressure
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.)
Expired - Lifetime
Application number
EP91912127A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0536233A1 (de
Inventor
Hans-Werner Meixner
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.)
Pi-Patente (gmbh) Entwicklung und Verwertung GmbH
Pi Patente GmbH
Original Assignee
Pi-Patente (gmbh) Entwicklung und Verwertung GmbH
Pi Patente 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 Pi-Patente (gmbh) Entwicklung und Verwertung GmbH, Pi Patente GmbH filed Critical Pi-Patente (gmbh) Entwicklung und Verwertung GmbH
Publication of EP0536233A1 publication Critical patent/EP0536233A1/de
Application granted granted Critical
Publication of EP0536233B1 publication Critical patent/EP0536233B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/02—Systems with continuously-operating input and output apparatus

Definitions

  • the invention relates to a device for driving a tool that can be moved back and forth in the axial direction.
  • Such tools and drives are known, for example as pneumatic hammers, pneumatic knives and the like, which operate according to this principle. These drives make a lot of noise even when idling, even if you only want a small amount of power for the drive. In the known drives, the weight and volume of the tool in relation to the power also leaves something to be desired, and the tool therefore requires a large amount of manual effort to operate.
  • a telemotor system in which a drive unit moves a piston in a cylinder, which acts on an oil column which acts on a piston acts in a cylinder of an implement and, for example, moves the cutting edge of a hedge trimmer.
  • the return of the master cylinder piston against the force-exerting cam disc is done by the springs acting on the piston. Since springs work too slowly, such drives can only be used for tools with a low stroke frequency. Otherwise, lifting and knocking occur between the piston and the cam disk. At a faster stroke frequency, for example greater than 12 Hz, there is also outgassing in the oil. As a result, the efficiency of the power transmission between the driving motor and the driven tool is greatly impaired.
  • an eccentric disc acts via a ball bearing ring on a piston which actuates an oil column against the pressure of a spring in the working cylinder, or two counter-rotating drive devices are acted upon by the eccentric disc in accordance with FIG. 5 such that two oil columns on the opposite sides of the drive piston for the Tool work.
  • Such a drive has the disadvantage that the oil column or the oil columns are briefly subjected to an undesired negative pressure with each work cycle, in particular if a rapid oscillation of the working cylinder piston is desired, so that cavitation phenomena occur.
  • the object of the invention is to provide a drive with a rapidly oscillating stroke frequency and high efficiency between drive (motor) and output (tool), which is designed such that the tool is advantageous to handle as a light, small in volume, but very powerful handheld device.
  • Sub-task a) is a prerequisite for an economically and economically sensible drive that can be designed so that it works with the greatest possible efficiency.
  • the drive according to the invention is supposed to have the reverse effect that the handling of the tool is made considerably easier.
  • the solution to sub-task d) has the effect that cavitations are to be avoided in every hydraulic transmission system and because cavitations, in particular in the drive according to the invention, would have a performance-reducing effect on the handheld device, so that these phenomena do not occur.
  • the solution to sub-task h) is expedient because, for example, a knife, including the drive, must be cleaned and such cleaning is expediently carried out by immersing it in the cleaning liquid (water) during the run.
  • the drive is the prerequisite for creating a rapidly oscillating handheld device with high efficiency, which is of significant economic importance and which is particularly user-friendly.
  • an electric motor for driving the piston of the master cylinder, this advantageously acts on the at least one eccentric disk in order to set it in rotation.
  • the eccentric disk then expediently carries the ball bearing on its circumference, the inner shell of which is connected to the eccentric disk, is advantageously shrunk onto the circumference of the disk, that is to say it rotates with the eccentric disk, and the outer shell of which is non-rotatable but can carry out a linear movement, such that the piston of the master cylinder articulated on it executes a reciprocating as well as a forced movement by the eccentric disk.
  • the piston of the master cylinder can also be articulated laterally with its piston rod on the eccentric disk.
  • the drive according to the invention has the advantage that both the force and the frequency and the stroke of the piston of the working cylinder can be easily regulated.
  • the frequency is determined by the speed of the drive motor.
  • the maximum stroke is predetermined by the design of the eccentric disc. Precise regulation and lowering of the stroke is possible through the measures described on the basis of the drawing.
  • the force primarily determines the pressure of the displaced liquid. This force can be regulated by a pressure relief valve. This makes the drive extremely versatile. Details on this can be found in the subclaims and the description of exemplary embodiments.
  • the master cylinder can not only drive the piston of a working cylinder, but can also act on a plurality of pistons, each of which drives a tool, by branching the transmission lines.
  • an automatic oil refill device with a venting device is provided between the master cylinder and the working cylinder or connected to the working cylinder itself.
  • the connecting hoses between master cylinder and working cylinder are useful with easily detachable plug-in couplings for the desired connection provided so that a tool without oil loss with its special drive is easily interchangeable with another.
  • each working piston has at least one counter-pressure spring, which counteracts the oil pressure when the piston is displaced in the master cylinder.
  • the outside air pressure continues to act on the piston of the working cylinder and increases the effect of the counter pressure spring.
  • the oil column is thus moved back and forth between the piston of the master cylinder and the piston of the working cylinder, without the oil ever falling below a predetermined minimum pressure during a work cycle and thereby causing cavitation phenomena. This measure makes a significant contribution to enabling a rapidly oscillating frequency of the oil column.
  • the counter-pressure spring can also be used, for example, to couple the tool to the working cylinder piston, which makes it easy to replace the tool.
  • an electric motor 1 which drives a shaft 2 which runs in ball bearings 3, 4.
  • an eccentric 5 is fixed, which rotates about the drive axis A-A of the shaft.
  • the eccentric 5 carries a ball bearing 6, the inner shell 6a of which is advantageously shrunk onto the eccentric disk 5.
  • the balls run between the shell 6a and an outer shell 7, which is not rotatable. However, the shell 7 can be moved back and forth in the direction of the line B-B. It is articulated to a piston rod 7a.
  • the piston rod 7a carries a piston 8 and moves it back and forth in a master cylinder 9.
  • the oil refill device 11 has a ventilation device 12 in its cover.
  • the working space 10 also has an outlet opening 12a for the oil.
  • a media pre-pressure screw 40 acts on the cylinder volume to compensate for a minimal pressure loss due to expansion of the hose.
  • the transmission medium oil is fed to a working cylinder 20 when the piston 8 moves forward.
  • a quick coupling 15 is provided in the line 14 in order to be able to produce different connections to different work tools.
  • the quick coupling is sensitive to pressure and prevents oil loss when changing the connection of another tool.
  • the working cylinder 20 has a piston 22, on which the oil acts when the piston 8 advances, in such a way that the piston 22 moves in the direction of the arrow 24. If the piston 8 moves back in the master cylinder 9, that is towards the eccentric, the oil pressure in the line 14 is reduced. A negative pressure is created in the working space 23 of the cylinder 20 so that it moves back, that is to the right in FIG. 1.
  • the tool to be moved (not shown) is fastened to the piston 22 with the aid of a spring 25.
  • the spring simultaneously acts as a counter-pressure spring on the working piston 22.
  • the force of the spring is such that it does not hinder the forward movement of the piston and thus the tool, but on the other hand ensures that the piston 22 is returned sufficiently quickly.
  • the volume of the compressed oil is changed at the same time, so that a greater or lesser amount of oil is pressed into the line 14 with each forward movement of the piston 8 and stroke control is thus possible.
  • the reciprocable piston 8 in FIG. 1 is replaced by a piston 41 which has an inclined surface 42.
  • the piston 41 closes the inlet opening 43 for the refill device 11, depending on the inclination of the inclined surface sooner or later.
  • the set screw 40a is additionally connected to the piston 41 in such a way that the piston can be rotated about its axis B-B, so that the inclination of the inclined surface 42 to the oil inlet opening 43 changes. That is, when the piston is reciprocated, the inlet opening 43 is opened or closed depending on the inclination of the inclined surface.
  • the adjusting screw 40a for adjusting the inclination of the inclined surface has two cams 50, 51 which lie in corresponding recesses in the piston and which rotate the screw 40a about the axis B-B. The set screw is locked in the desired position.
  • a plurality of inlet openings 43a, 43b, 43c can be provided one behind the other, which the piston closes one after the other as it moves. This allows the Liquid displacement and thus the stroke movement of the working piston 22 can also be regulated by the adjusting screw now successively closing one or more of the inlet openings.
  • the inclined surface of the piston need not be provided for this. In any case, one of the inlet openings provided must always be open.
  • the system is designed simultaneously for several working cylinders, for example for working cylinders 31 to 36, as shown schematically by branching the connecting lines at points 52 to 57.
  • the mode of action is the same.
  • Fig. 5 shows an embodiment in which two master cylinders 9 and 65 are provided.
  • the piston 8 of the master cylinder 9 is in turn moved back and forth by the eccentric disc 5.
  • the piston 66 of the master cylinder 65 is driven accordingly by an eccentric disk 64.
  • the disk 5, like the disk 64, is connected to an associated piston 8, 66.
  • the eccentric discs 5 and 66 are arranged on the shaft 2 of the electric motor 1 offset by 180 °, so that when the piston 8 is in the right position in the cylinder, the piston 66 is in the left position of the cylinder 65, that is , Pistons 8 and 66 work in opposite directions.
  • the piston 8 presses oil through the line 14 into the working space 23 of the cylinder 27.
  • the piston 66 presses oil via the line 67 into the space 68 in front of the piston 22 (complementary working space).
  • the opposing oil pressure in rooms 23 and 68 now pushes the piston 22 back and forth.
  • the spring for returning the piston can thus be omitted.
  • Fig. 7 shows a modified embodiment.
  • the master cylinders 9 and 65 of FIG. 5 are connected to two working cylinders 20 and 70 via lines 14 and 67.
  • One line 14, 67 is assigned to one of the working cylinders 20, 70.
  • the pistons 22, 71 of the working cylinders 20, 70 act on a plate 72 or a lever which can be moved back and forth about an axis 73 in the direction of the arrow 76.
  • the plate 72 acts on the tool so that it executes the oscillating movement again. 5, which has the same effect that the oil supply lines on the side facing away from the tool open into the working cylinder.
  • the master cylinder 9 acts via the line 14 on the working cylinder 20 with the interposition of a pressure-sensitive changeover valve 75.
  • a line 74 leads from the valve 75, which leads into the refill device 11. This device works as follows: If the piston of the cylinder 9 moves to the right, it presses the oil flowing in from the refill container 11 via the line 14, the now open valve 75 into the cylinder 20 and also moves its piston to the right. If the piston in cylinder 9 moves to the left, a negative pressure is created in line 14. The valve 75 now connects the cylinder 20 to a line 74 which opens into the oil refill container 11.
  • the training according to the invention shows the further advantages: Due to the selected drive, the weight and volume can be in an extremely favorable ratio to the transmitted force. If the weight of the working cylinder with piston is around 40 grams with a stroke length of 12 to 13 millimeters and the piston is moved at a frequency of ten Hertz, a force of 100 kilograms is generated per stroke, by driving an electric motor of 750 Watt.
  • the drive works with an extraordinarily high degree of efficiency. This is due to the fact that the power output of the drive motor is transmitted almost uniformly as both forward and backward movement to the piston of the master cylinder by the non-positive transmission of the rotary movement of the motor shaft during an entire revolution.
  • the drive works almost silently.
  • the coupling of a work unit is easily possible through the quick coupling 15 in the transmission line 14.
  • the connection is subject to virtually no wear.
  • the coupling enables the implement to be quickly replaced with another implement.
  • the vibration in the oscillating implement which is normally transmitted to the implement in conventional systems, for example in the case of a drive with compressed air, is derived here from the work unit by the oil pressure column as the drive means.
  • the implement itself is almost vibration-free.
  • the actual drive that is, the master cylinder unit and the working cylinder unit is not rigid, but is connected to one another by a flexible hose, so that the loads and in particular the weight of the transmitter unit are not transferred to the working unit.
  • Even for the highest power transmission only small hose cross-sections are necessary for the transmission line.
  • a hose with an outer diameter of five millimeters is required. Due to the low weight and the thin, flexible supply hose, excellent handling of each work unit is possible, as already mentioned above.
  • the drive unit is sealed, it can also be used with devices that run under water or at least can be cleaned with liquid.
  • the entire system is almost maintenance-free and has a very long life expectancy.
  • the system is easy to manufacture. The manufacturing costs are low, and much cheaper than a compressed air system or the like in the same performance size.
  • the work unit is not directly connected to electrical power, so that underwater operation is also possible. Even with high power transmission, the working cylinder, which is directly connected to the tool, is still very small. Another advantage is that the stroke frequency, the stroke height and the force of the tool unit can be regulated continuously and independently of one another, even during operation. Any liquid can be used as a transfer medium for simple applications.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Measurement Of Resistance Or Impedance (AREA)
  • Actuator (AREA)
  • Sawing (AREA)
  • Vehicle Body Suspensions (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Turning (AREA)
EP91912127A 1990-06-29 1991-06-20 Vorrichtung zum antrieb eines in axialer richtung hin- und herbewegbaren werkzeuges Expired - Lifetime EP0536233B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4020776 1990-06-29
DE4020776A DE4020776A1 (de) 1990-06-29 1990-06-29 Vorrichtung zum antrieb eines werkzeuges fuer eine axiale hin- und herbewegung des werkzeuges
PCT/EP1991/001146 WO1992000460A1 (de) 1990-06-29 1991-06-20 Vorrichtung zum antrieb eines in axialer richtung hin- und herbewegbaren werkzeuges

Publications (2)

Publication Number Publication Date
EP0536233A1 EP0536233A1 (de) 1993-04-14
EP0536233B1 true EP0536233B1 (de) 1995-02-22

Family

ID=6409359

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91912127A Expired - Lifetime EP0536233B1 (de) 1990-06-29 1991-06-20 Vorrichtung zum antrieb eines in axialer richtung hin- und herbewegbaren werkzeuges

Country Status (9)

Country Link
US (1) US5337565A (enrdf_load_stackoverflow)
EP (1) EP0536233B1 (enrdf_load_stackoverflow)
JP (1) JP2534420B2 (enrdf_load_stackoverflow)
AT (1) ATE118860T1 (enrdf_load_stackoverflow)
AU (1) AU8069191A (enrdf_load_stackoverflow)
CA (1) CA2086431C (enrdf_load_stackoverflow)
DE (2) DE4020776A1 (enrdf_load_stackoverflow)
DK (1) DK0536233T3 (enrdf_load_stackoverflow)
WO (1) WO1992000460A1 (enrdf_load_stackoverflow)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1256093B (it) * 1992-11-04 1995-11-27 Gruppo di comando per carrelli di tiro,in particolare per banchi di trafilatura
US6193476B1 (en) * 1999-09-13 2001-02-27 Gerald T. Sweeney 1½ Piston force pump
US9115710B2 (en) 2004-01-29 2015-08-25 Richard F. McNichol Coaxial pumping apparatus with internal power fluid column
US8454325B2 (en) * 2007-01-30 2013-06-04 Richard F. McNichol Coaxial pumping apparatus with internal power fluid column
US20050169776A1 (en) * 2004-01-29 2005-08-04 Mcnichol Richard F. Hydraulic gravity ram pump
GB0412810D0 (en) * 2004-06-09 2004-07-14 Imi Norgren Ltd Actuator assembly
EP3670095A1 (de) * 2018-12-20 2020-06-24 Hilti Aktiengesellschaft Handwerkzeugmaschine
EP4239218A1 (en) * 2022-03-03 2023-09-06 FNF Innovation SH.P.K. Power transmission device
CN117512826A (zh) * 2023-12-22 2024-02-06 安徽翰联色纺股份有限公司 一种转杯纺排杂装置

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DE3928873C1 (enrdf_load_stackoverflow) * 1989-08-31 1991-02-21 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De

Also Published As

Publication number Publication date
JPH05507428A (ja) 1993-10-28
CA2086431C (en) 1999-02-02
CA2086431A1 (en) 1991-12-30
AU8069191A (en) 1992-01-23
DE59104721D1 (de) 1995-03-30
ATE118860T1 (de) 1995-03-15
DK0536233T3 (da) 1995-06-26
WO1992000460A1 (de) 1992-01-09
EP0536233A1 (de) 1993-04-14
DE4020776A1 (de) 1992-01-09
US5337565A (en) 1994-08-16
DE4020776C2 (enrdf_load_stackoverflow) 1992-05-21
JP2534420B2 (ja) 1996-09-18

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