WO2006066521A1 - Entrainement lineaire a convertisseur de force - Google Patents

Entrainement lineaire a convertisseur de force Download PDF

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Publication number
WO2006066521A1
WO2006066521A1 PCT/DE2005/001965 DE2005001965W WO2006066521A1 WO 2006066521 A1 WO2006066521 A1 WO 2006066521A1 DE 2005001965 W DE2005001965 W DE 2005001965W WO 2006066521 A1 WO2006066521 A1 WO 2006066521A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
linear drive
piston
force
drive according
Prior art date
Application number
PCT/DE2005/001965
Other languages
German (de)
English (en)
Inventor
Michael Robohm
Original Assignee
Bosch Rexroth 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 Bosch Rexroth Ag filed Critical Bosch Rexroth Ag
Publication of WO2006066521A1 publication Critical patent/WO2006066521A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B2015/1495—Characterised by the construction of the motor unit of the straight-cylinder type with screw mechanism attached to the piston

Definitions

  • the invention relates to a linear drive according to the preamble of patent claim 1.
  • Such linear drives are used for example in flanging machines, in which flanged jaws are moved by means of a working cylinder. These are initially moved into certain stroke positions with a relatively high speed and low force, the actual cylinder then has to apply a large traction over a relatively small stroke the actual flanging. This can be applied for example via a hydraulic power booster.
  • Such linear drives designed with hydraulic force translators are also used to actuate a closing unit, an injection unit or an ejector of plastic injection molding machines or for clamping tools on machine tools.
  • a generic linear actuator in which a force translator piston is axially displaceable via a spindle drive.
  • the power booster piston and a working piston of a working cylinder bound together in sections a pressure chamber, wherein the adjacent to the pressure chamber effective surfaces of the working piston are larger than the corresponding surfaces of the pressure booster piston, so that adjusts a corresponding pressure transmission ratio.
  • rapid feed for example, injection process during injection molding
  • the axial movement of the pressure booster piston is transmitted directly to the working piston without force transmission.
  • a pressure chamber also limiting intermediate part and the working piston according to the effective area ratio applied with a large force.
  • the pressure medium flow paths between the limited areas of the active surfaces of the power booster are designed so that the force transmission acts in both directions of movement of this known linear drive.
  • a change in direction of the spindle drive is required.
  • the clamping of the above-mentioned intermediate part for initiating the power transmission can take place only in predetermined positions.
  • the object of the invention is to provide a linear drive which makes it possible to adapt the force and speed curves comparatively easily to different requirements.
  • the power booster has a power booster piston with a comparatively small active surface, which separates two power booster chambers, one of which reduces in axial displacement of the power booster piston and the other increases accordingly.
  • Each of these power booster chambers can be hydraulically connected to one of two pressure chambers delimited by a drive piston of the linear drive, wherein the drive piston has a larger effective area than the power booster piston.
  • a directional control valve is arranged, via which in both directions of movement of the working piston, the reducing power booster chamber in a position of the directional control valve with the first and in another position of the directional valve with the second of the working piston Pressure chambers is connectable. Ie. , By reversing this directional valve, the direction of movement of the working piston can be reversed without the drive of the power booster is reversed. In this way, relatively complex speed and pressure curves can be traced - such a process control is not possible in the solutions described above.
  • check valves are provided in connecting lines between the two force booster chambers and / or the two pressure chambers, which can be brought from a blocking position in which the two pressure chambers / force booster chambers are separated from each other in a passage position, so that the pressure medium of a pressure - room / power booster room flows into the other pressure chamber / power booster room.
  • the directional control valve according to the invention preferably has a blocking position into which the connection between the pressure - A -
  • the feed during the express operation without power transmission is particularly simple when the working piston has a stop shoulder on which the power booster piston runs to take the working piston.
  • the drive of the power booster preferably takes place via a spindle arrangement with axially displaceable spindle nut and driven spindle.
  • This variant is characterized by a short design, as the spindle does not extend in the axial direction.
  • the working piston and the power booster piston must in each case be designed with an anti-twist device.
  • the pressure chambers / force translator chambers which in each case increase, can be connected to a low-pressure accumulator via a valve arrangement.
  • the valves of this valve arrangement are preferably switched by the pressure in the pressure chamber / force booster chamber, which reduces in each case.
  • the linear drive can be performed without moving lines when the directional control valve, at least the associated the pressure booster piston switching valve and, if necessary. the low-pressure accumulator are integrated in the working piston.
  • Figure 1 is a schematic sectional view of a linear drive according to the invention in a basic position.
  • FIG. 2 shows the linear drive from FIG. 1 in an opening
  • Figure 3 shows the linear drive of Figure 1 at the end of the rapid traverse
  • Figure 4 shows the linear drive of Figure 1 wherein the working piston is retracted after extension with high tensile force.
  • FIG. 1 shows a linear drive 1 which can be used, for example, for actuating the crimping jaws of a crimping machine.
  • This crimping jaws are guided linearly in the crimping machine and are moved by means of the linear drive. At certain positions, the sheet is crimped, including then the crimping jaws are acted upon by the linear drive with a large tensile force along a relatively small stroke range.
  • the suitable for such a kinematics linear drive 1 has an electrically driven spindle drive 2, via which a power booster piston 4 of a power booster 6 is displaceable in the axial direction.
  • the power booster piston 6 is mounted in a working piston 8 of a working cylinder 10 of the hemming machine.
  • Working piston 8 actuates the aforementioned crimping jaws of the crimping machine.
  • the spindle drive one of an electric motor (not shown) driven spindle 12 which is mounted on a bearing 14 on a machine frame 16.
  • the spindle 12 is in engagement with a movable in the axial direction of the spindle nut 18 which is rotatably mounted on the spindle 12.
  • This spindle nut 18 is connected to the power booster piston 4, so that the AxialVerschiebung the spindle nut 18 is transmitted to the power booster piston 4.
  • This is axially displaceably guided in an axial bore 20 which is widened in the radial direction to an annular space which is divided by a radial collar 22 of the power booster piston 4 in a front and a rear power booster chamber 24, 26.
  • These are connected to each other by means of a force translator connection line 28, in which an electrically operated force translator check valve 30 is arranged, which can be brought by means of a solenoid from a spring-biased locking position in a passage position (b).
  • a cylinder bore 32 of the working cylinder 10 is likewise set back radially and the resulting annular space is divided by a piston collar 34 of the working piston 8 into a front pressure chamber 36 and a rear pressure chamber 38.
  • These two annular pressure chambers 36, 38 are - similar to the Kraftübersetzersammlung 24, 26 - connected via a connection 40 with a check valve 42 which is switchable by means of a solenoid from a blocking position into a passage position (b), in which the two pressure chambers 36th , 38 are interconnected.
  • the four pressure chambers 36, 38; 24, 26 is associated with a directional control valve 44, which in the dargestellen execution- example is designed as a 4/3-way valve.
  • the directional control valve 44 and the above-described channels 46, 48, 50, 52 are integrated into the jacket of the working piston 8, so that no external flexible lines are required for the connection of these pressure chambers.
  • the front pressure chamber 36 and the rear pressure chamber 38 are connected via low-pressure lines 54, 56 and a storage valve 58 with a low-pressure accumulator 60.
  • This accumulator valve 58 is switched over the higher pressure in the low pressure lines 54, 56, so that by the higher pressure in the low pressure line 56 of the low pressure accumulator 60 with the low pressure line 54 (switching position (b)) and vice versa at a higher pressure in the low pressure line 54 of Low-pressure accumulator 60 is connected to the low pressure line 56 (switch position a).
  • the front power transmission duct 46 and the rear power transmission duct 48 are connected by lines 62, 64 to a switching valve 66 which is switchable by either higher pressure in the lines 62, 64 to either a position (a) or a position (b).
  • a switching valve 66 which is switchable by either higher pressure in the lines 62, 64 to either a position (a) or a position (b).
  • the respective lower pressure leading line 62, 64 is connected via a connecting line with a further switching valve 70, whose inputs via line sections 72, 74 are connected to the low pressure lines 54 and 56 respectively.
  • This further switching valve 70 can be switched by the higher of the pressures in the line sections 72, 74, so that the connecting line 68 is then connected to the line leading to the lower pressure. Ie.
  • the switching valves 58, 66, 70 are adjusted by the respectively effective higher pressure so that the low-pressure accumulator 60 is connected to the respective force translator chamber 24, 26 and pressure chamber 36, 38, which has the lower pressure in the operation of the linear drive.
  • the cascade connection of these switching valves 66, 70, 58 is designed so that the number of flexible, movable lines is low, so that the piping costs for this linear drive 1 is minimal and damage due to breakage of flexible lines can practically not occur.
  • the circuit can be further simplified if the low-pressure accumulator 60 is also integrated with the associated switching valves in the working piston 8.
  • the function of the linear drive 1 will be explained with reference to the following drawings.
  • This relative movement of the power booster piston 4 with respect to the working piston 8 from the position shown in Figure 1 in the position shown in Figure 2 (abutment on the shoulder 76) can be effected, for example, that the power transmission lock valve 30 is brought into its passage position (a) and the Spindle drive 2 is driven so that the power booster piston 4 is moved in the direction of arrow to the right.
  • the pressure medium displaced from the front power transmission chamber 24 then flows via the power transmission connection line 28 into the increasing power transmission chamber 26, the working piston 8 stops until the power transmission piston 4 runs onto the shoulder 76.
  • the check valve 42 is switched to its passage position (b), so that the pressure chambers 36, 38 of the working cylinder 10 are connected to each other.
  • the working piston 8 is then taken by the power booster piston 4 at a comparatively high speed, wherein the force transmitted from the spindle drive 2 must be low.
  • the directional control valve 44 remains in its illustrated blocking position.
  • the spindle drive 2 is stopped in the illustrated embodiment and the check valve 42 is switched to its blocking position (a), so that the connection between the two pressure chambers 36, 38 of the working cylinder 10 is shut off -
  • the working cylinder 10 is then locked. Accordingly, then the force translator check valve 30 is switched to its blocking position (a), so that the connection between the two power transmission chambers 24, 26 is shut off.
  • the working piston 8 For the actual flanging operation, the working piston 8 must then be moved with great force in the opposite direction (to the left in FIG. 4), with only a small stroke being required.
  • the direction of rotation of the spindle drive 2 is reversed and the directional control valve 44 is switched to its (b) marked position in which the front power transmission channel 46 is connected to the rear channel 52 and the front channel 50 to the rear power transmission channel 48.
  • the power booster piston 4 moves to the left, so that the rear power booster chamber 26 is reduced in size and corresponding to the front power booster chamber 24 is increased.
  • the displaced from the rear power transmission chamber 26 pressure fluid flows through the directional control valve 44 in the front pressure chamber 36, so that the working piston 10 is moved with great force and relatively low speed to the left.
  • the thereby displaced from the rear pressure chamber 38 pressure fluid flows through the directional control valve 44 in the increasing front power transmission chamber 24.
  • Embodiment is a spindle drive with electric drive used.
  • other drives for example, pneumatic or hydraulic drives can be used.
  • a linear drive with a hydraulic power booster the power booster piston separates two power booster chambers, one of which decreases in an axial displacement of the power booster and the other increases accordingly.
  • These force translator chambers are hydraulically connectable to two pressure chambers delimited by the working piston, wherein this pressure medium connection takes place according to the invention via a directional control valve via which the force transmission chambers can be selectively connected to one or the other pressure chamber of the working piston.

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)
  • Fluid-Pressure Circuits (AREA)

Abstract

La présente invention concerne un entraînement linéaire (1) comprenant un convertisseur de force hydraulique dont le piston de convertisseur de force (22) sépare deux chambres de convertisseur de force (24,26), la taille de l'une des chambre diminuant lors d'un déplacement axial du convertisseur de force, alors que la taille de l'autre augmente en correspondance. Ces chambres de convertisseur de force peuvent être reliées d'un point de vue hydraulique à deux chambres de pression (36,38) délimitées par le piston de travail (8), cette liaison d'agent sous pression s'effectuant selon l'invention par une soupape de distribution (44) par laquelle les chambres de convertisseur de force peuvent être reliées de manière sélective à l'une ou l'autre chambre de pression du piston de travail.
PCT/DE2005/001965 2004-12-20 2005-11-02 Entrainement lineaire a convertisseur de force WO2006066521A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410061298 DE102004061298A1 (de) 2004-12-20 2004-12-20 Linearantrieb
DE102004061298.6 2004-12-20

Publications (1)

Publication Number Publication Date
WO2006066521A1 true WO2006066521A1 (fr) 2006-06-29

Family

ID=35759252

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2005/001965 WO2006066521A1 (fr) 2004-12-20 2005-11-02 Entrainement lineaire a convertisseur de force

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DE (1) DE102004061298A1 (fr)
WO (1) WO2006066521A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMO20090161A1 (it) * 2009-06-17 2010-12-18 Rozzi De Hieronymis Carlo Maria Intensificatore di forza idraulica a riarmo
ITMO20100044A1 (it) * 2010-02-26 2011-08-27 De Hieronymis Carlo Maria Rozzi Intensificatore di forza idraulica a riarmo con mantenimento della posizione raggiunta e della forza di spinta ottenuta durante ogni fase di riarmo
DK3318767T3 (da) 2016-11-04 2021-07-26 Pistonpower Aps Hydraulisk aktuator med trykforstærker
EP3318768B1 (fr) 2016-11-04 2021-09-08 PistonPower ApS Actionneur hydraulique à amplificateur de pression de cartouche

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982002423A1 (fr) * 1981-01-12 1982-07-22 Mccormack Wallace Dispositif d'actionnement de vanne
DE3937448A1 (de) 1989-10-06 1991-04-11 Gedib Ingbuero Innovation Spanneinrichtung fuer werkzeugmaschinen
DE10121024A1 (de) 2000-05-23 2001-11-29 Mannesmann Rexroth Ag Antriebsvorrichtung, insbesondere für die Schließeinheit, die Einspritzeinheit oder die Auswerfer einer Kunststoffspritzgießmaschine
WO2002036968A1 (fr) * 2000-10-31 2002-05-10 Halliburton Energy Services, Inc. Actionneur hydraulique miniature a faible puissance
EP1310346A1 (fr) * 2001-11-08 2003-05-14 Bosch Rexroth AG Dispositif de fermeture du moule pour une machine à injecter de matières plastiques

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982002423A1 (fr) * 1981-01-12 1982-07-22 Mccormack Wallace Dispositif d'actionnement de vanne
DE3937448A1 (de) 1989-10-06 1991-04-11 Gedib Ingbuero Innovation Spanneinrichtung fuer werkzeugmaschinen
DE10121024A1 (de) 2000-05-23 2001-11-29 Mannesmann Rexroth Ag Antriebsvorrichtung, insbesondere für die Schließeinheit, die Einspritzeinheit oder die Auswerfer einer Kunststoffspritzgießmaschine
WO2002036968A1 (fr) * 2000-10-31 2002-05-10 Halliburton Energy Services, Inc. Actionneur hydraulique miniature a faible puissance
EP1310346A1 (fr) * 2001-11-08 2003-05-14 Bosch Rexroth AG Dispositif de fermeture du moule pour une machine à injecter de matières plastiques

Also Published As

Publication number Publication date
DE102004061298A1 (de) 2006-06-22

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