WO2010051913A1 - Convertisseur de forces hydraulique - Google Patents

Convertisseur de forces hydraulique Download PDF

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Publication number
WO2010051913A1
WO2010051913A1 PCT/EP2009/007617 EP2009007617W WO2010051913A1 WO 2010051913 A1 WO2010051913 A1 WO 2010051913A1 EP 2009007617 W EP2009007617 W EP 2009007617W WO 2010051913 A1 WO2010051913 A1 WO 2010051913A1
Authority
WO
WIPO (PCT)
Prior art keywords
primary
pressure chamber
cylinder
piston
main
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.)
Ceased
Application number
PCT/EP2009/007617
Other languages
German (de)
English (en)
Inventor
Robert Eckert
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to CN2009801540521A priority Critical patent/CN102272460A/zh
Publication of WO2010051913A1 publication Critical patent/WO2010051913A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • F15B7/06—Details
    • F15B7/08—Input units; Master units

Definitions

  • the invention relates to a hydraulic power transmission according to the
  • the publication DE 101 57 373 A1 discloses a drive unit with a hydraulic power booster for a plastic injection molding machine, which generates a linear output movement with different partial strokes from a rotational movement of an electric motor via a spindle drive and three different cylinder-piston combinations.
  • the drive unit can meet two important different requirements that occur in plastic injection molding machines at different locations.
  • the mold clamping plate for closing and opening the mold are moved as quickly as possible, so that the cycle time for the production of a molding can be kept small.
  • the mold clamping plate and thus the whole shape against the high injection pressure can be kept with great force.
  • the power translator has three relatively movable and differing in the size of their active surfaces piston and an intermediate part.
  • the output motion is divided into a first high-speed portion by activating and deactivating individual cylinder-piston combinations via a clutch, a blocker, and a 2/2 way valve, a middle speed middle section thereafter, and a low speed last section Speed.
  • the applied output forces behave in this case In contrast to the speeds, the maximum output force that can be applied is therefore greatest at the last partial stroke.
  • a disadvantage of such hydraulic power boosters are the large number of cylinder-piston combinations and the device-technical effort (intermediate part, valve, clutch and blocking device).
  • the object of the invention is to provide a hydraulic force translator, e.g. to create for the jig of machine tools, which generates a linear movement with minimal device complexity, having different sections at different speeds.
  • the hydraulic power booster according to the invention has a primary unit that moves one of a drive unit in a stationary primary cylinder
  • Primary piston has, and a secondary unit, which has at least one secondary cylinder and at least one secondary piston, wherein the primary unit and the secondary unit together define a pressure medium space.
  • the primary cylinder and the primary piston are stepped, so that during a first partial stroke of the primary piston, a comparatively large end face of the primary piston limits a main pressure chamber of the primary cylinder, and limits a fine control pressure chamber of the primary cylinder during a second partial stroke of the primary piston a comparatively small end face of the primary piston.
  • a hydraulic power booster is provided with a primary unit, which has only a cylinder-piston combination, and in which with minimal device complexity, a combination of a rapid traverse and a single operation or Creep speed (with comparatively high maximum force) can be generated, which is suitable for example for clamping devices.
  • a circular-cylindrical fine control section and a frusto-conical transition section are arranged between the comparatively small end face and the Rihgstirn preparation of the primary piston. It is preferred if a frusto-conical transition pressure space is arranged between the main pressure chamber and the fine control pressure chamber of the primary cylinder, which has a similar shape as the frusto-conical transition portion of the primary piston.
  • the power booster has a main line which connects the fine control pressure chamber of the primary cylinder with the at least one secondary cylinder.
  • the drive unit is essentially formed by a spindle drive and by an electric motor with a parking brake.
  • the force translator has a pressure sensor which generates a control signal as a function of the pressure in the main line, wherein a torque of the electric motor is controllable with the control signal.
  • Plunger cylinder with integrated return springs which are directed against each other, so that the force translator is used in a machine tool and between the two secondary pistons, an object can be clamped.
  • the secondary piston move back independently with a discharge of the secondary unit and displaces the pressure medium from the secondary unit.
  • this advantageously has a bypass line which connects the main pressure chamber of the primary cylinder to the main line.
  • the force translator has a spill valve which is arranged in a line which connects the main pressure chamber of the primary cylinder with a surge tank, wherein the spill valve releases a passage from the main pressure chamber to the expansion tank in a spring-biased position and closes this passage in a switching position.
  • This overflow valve is switchable in a transitional position of the primary piston with respect to the primary cylinder by a mother of the spindle drive. As a result, excess pressure medium can be displaced from the main pressure chamber of the primary cylinder during operation or creep speed of the force translator.
  • the mouth of the bypass line in the main pressure chamber of the primary cylinder from the primary piston can be closed by driving over.
  • the force translator according to the invention in the bypass line has a 3/2-way valve which releases a passage from the main pressure chamber to the main line in a spring-biased position and interrupts the passage from the main pressure chamber of the primary cylinder to the main line in a switching position and instead with the main pressure chamber connects to a surge tank.
  • the 3/2-way valve is in a transition position of the primary piston with respect to the primary cylinder of a Mother of the spindle drive switchable.
  • the force translator advantageously has a pressure relief valve which is arranged in a line which connects the main pressure chamber with the expansion tank.
  • the pressure relief valve is acted upon in the opening direction by the pressure in the main pressure chamber and relieved this to the expansion tank.
  • the fine control section can enter the fine control pressure space, even if previously the secondary unit has encountered great resistance.
  • both variants of the power booster have a check valve which is arranged in a line which connects the expansion tank to the main line.
  • the opening direction of the check valve is directed from the expansion tank to the main line.
  • Figure 1 shows a first embodiment of a hydraulic power transmission according to the invention in a schematic representation
  • FIG. 2 shows a second embodiment of a hydraulic power transmission according to the invention in a schematic representation.
  • Figure 1 shows a first embodiment of a hydraulic power transmission according to the invention in a schematic representation. It essentially consists of a primary unit 1 and a secondary unit 2. ,
  • the primary unit 1 comprises a stationary primary cylinder 4 and a primary piston 6 guided therein, which is connected via e.g. four connecting portions 8, two of which are shown in Figure 1, is fixedly connected to a nut 10 of a spindle drive.
  • the spindle drive further has a spindle 12 which is set in rotational motion by a fixed electric motor 14.
  • the nut 10 moves in a known manner in a straight line to the primary cylinder 4 to or from it (see arrow), whereby the stroke of the primary piston 6 is achieved in the primary cylinder 4.
  • the primary piston 6 has on its primary cylinder 4 facing end face an annular end face 6d and a substantially cylindrical fine control section 6b, which is arranged concentrically to the annular end face 6d of the primary piston 6 and the opposite has a significantly reduced diameter.
  • the primary cylinder 4 has a main pressure space 4a and a fine control pressure space 4b arranged concentrically therewith, wherein the diameter of the main pressure space 4a corresponds to that of the annular end surface 6d and the diameter of the fine control pressure space 4b corresponds to that of the fine control portion 6b of the primary piston 6.
  • a transitional pressure chamber 4e is arranged between the main pressure chamber 4a and the fine control pressure chamber 4b of the primary cylinder 4, while between the fine control section 6b and the annular end face 6d of the primary piston 6, a corresponding transition section 6e is arranged.
  • the transitional pressure chamber 4e and the transition section 6e are formed approximately frusto-conical.
  • the force translator has a main line 16 which is connected to the end face of the fine control pressure chamber 4b of the primary cylinder 4, wherein the main line 16 is connected via a branch to two secondary cylinders 18.
  • the secondary cylinders 18 are designed as clamping cylinders or plunger cylinders and each have a secondary piston 20, both Secondary cylinder 18 and both secondary pistons 20 lie on a common clamping axis.
  • compression springs 22 are arranged, which press the secondary piston 20 from the clamping area to the outside at a relief of the secondary cylinder 18.
  • connection or bypass line 24 is arranged between the main pressure chamber 4a of the primary cylinder 4 and the main line 16.
  • an overflow line 26 is connected to the main pressure chamber 4 a of the primary cylinder 4, which connects the main pressure chamber 4 a via an overflow valve 30 with a surge tank 28.
  • the overflow valve 30 is formed by a 2/2-way valve which shuts off the overflow line 26 in a spring-biased basic position while it releases the connection between the main pressure chamber 4a and the expansion tank 28 in its switching position marked a.
  • the overflow valve 30 is switched as a function of the position of the primary piston by the nut 10 of the spindle drive, this circuit will be explained below in connection with the functional description of the force translator according to the invention.
  • a pressure limiting valve 32 is arranged parallel to the overflow valve 30, which is acted upon in the closing direction by a spring, while it is acted upon in the opening direction by the pressure in the overflow line 26 and in the main pressure chamber 4a of the primary cylinder 4.
  • the Pressure relief valve 32 relieves the main pressure chamber 4a to the expansion tank 28th
  • a compensation line 34 is provided with a check valve 36 between the surge tank 28 and the main line 16, the opening direction of the surge tank 28 is directed to the main line 16.
  • This working stroke of the primary piston 6 is divided into two partial strokes. First, a partial stroke, which is temporally before or spatially below the position of the primary piston 6 shown in Figure 1 and is displaced in the comparatively much pressure medium from the primary cylinder 4. Thereafter, a second partial stroke, which is temporally after or spatially above the position shown in Figure 1, and in which comparatively little pressure medium (at relatively high pressure applied) is displaced from the fine control pressure chamber 4b.
  • an end face of the primary piston 6 is operative, which is composed of the end face 6c of the fine control section 6b and the annular end face 6d of the primary piston 6.
  • the pressure medium from the main pressure chamber 4a of the primary cylinder 4 is partially conveyed through the bypass line 24 and partly through the fine control pressure chamber 4b to the main line 16.
  • the pressure medium reaches the two with a comparatively large volume flow Secondary cylinder 18, whereby the secondary piston 20 are moved toward each other in rapid traverse.
  • the primary piston 6 closes the cylinder-side mouth of the bypass line 24 by driving over.
  • the fine control section 6b of the primary piston 6 enters the fine control pressure space 4b of the primary cylinder 4.
  • the overflow valve 30 is adjusted at its time by the switching device 38 in its marked with a switching position, so that the overflow 26 is released from the main pressure chamber 4a of the primary cylinder 4 to the expansion tank 28.
  • the counterpressure of the secondary unit 2 can already become comparatively high before the fine control section 6b enters the fine control pressure chamber 4b of the primary cylinder 4 dips. Then the pressure medium compressed in the main pressure chamber 4a of the primary cylinder 4 can flow out via the pressure limiting valve 32 to the expansion tank 28 until the fine control section 6b enters the fine control Pressure chamber 4b is immersed and the spill valve 30 opens. Up to this opening, the pressure limiting valve 32 is opened in a known manner by the rising pressure in the main pressure chamber 4a against the spring force.
  • a pressure sensor 40 is arranged, the measurement result is adjusted with a preset system pressure.
  • the power supply of the electric motor 14 is controlled so that it outputs a variable torque.
  • the power supply of the electric motor 14 is reduced or interrupted, and a Festestellbremse (not shown) is activated. In this way, the achieved predetermined contact pressure of the secondary piston 20 can be maintained even without further power supply to the electric motor 14.
  • 36 pressure fluid from the surge tank 28 can be sucked at any time from the main line 16 via the equalization line 34 and the check valve.
  • Figure 2 shows a second embodiment of the hydraulic power transmission according to the invention in a schematic representation. This embodiment largely corresponds to the first embodiment of Figure 1; Therefore, only the differences of the second embodiment from the first embodiment will be described below.
  • bypass line and the overflow line are laid together in sections.
  • a 3/2-way valve 130 is provided, which is likewise adjusted in a transition position (shown in FIG. 2) from a spring-biased basic position into a switching position marked a.
  • a bypass line 124th opened In the spring-biased basic position of the 3/2-way valve 130 during the first partial stroke is a bypass line 124th opened, which leads from the main pressure chamber 4a of the primary cylinder 4 to the main line 16.
  • Main pressure chamber 4 a via a compensation line 134 connected to the surge tank 28.
  • Check valve 36 is provided, which opens in the direction of the expansion tank 28 to the main line 16.
  • a pressure relief valve 32 is provided between the section of the bypass line 124, which connects the main pressure chamber 4a and the 3/2-way valve 130, and the compensation line 134.
  • a pressure relief valve 32 is provided between the section of the bypass line 124, which connects the main pressure chamber 4a and the 3/2-way valve 130, and the compensation line 134.
  • the 3/2-way valve 130 is in its spring-biased basic position, whereby a second flow path from the main pressure chamber 4a to the main line 16 and to the secondary unit 2 is created via the bypass line 124.
  • the 3/2-way valve 130 is adjusted by the switching device 38 in its switching position marked a, so that in the second partial stroke, the pressure medium from the main pressure chamber 4a through the compensation line 134 to the surge tank 28 can flow.
  • pressure medium can be sucked into the main line 16 at any time from the expansion tank 28 via the equalization line 134, the check valve 36 and the bypass line 124.
  • Secondary unit also be designed differently, in particular, the number of secondary cylinders may deviate from two.
  • a hydraulic power booster having a primary unit having a movable from a drive unit in a stationary primary cylinder primary piston, and having a secondary unit having at least one secondary cylinder and at least one secondary piston, wherein the primary unit and the secondary unit together define a pressure medium space.
  • the primary cylinder and the primary piston are stepped, wherein during a first partial stroke of the primary piston a comparatively large end face of the
  • Primary piston limits a main pressure chamber of the primary cylinder, and during a second partial stroke of the primary piston, a comparatively small end face of the primary piston limits a fine control pressure chamber of the primary cylinder.
  • a hydraulic power booster is provided with a primary unit, which has only a cylinder-piston combination, and in which with minimal device complexity, a combination of a rapid traverse and a single pass or creep speed (with relatively high maximum force) can be generated, the eg suitable for clamping devices.

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

L'invention concerne un convertisseur de forces hydraulique avec une unité primaire qui possède un piston primaire pouvant être déplacé dans un cylindre primaire fixe par une unité d'entraînement et avec une unité secondaire qui possède au moins un cylindre secondaire et au moins un piston secondaire. L'unité primaire et l'unité secondaire délimitent ensemble une chambre de fluide sous pression. Le cylindre primaire et le piston primaire sont étagés, si bien que, pendant une première course partielle du piston primaire, une surface frontale relativement grande du piston primaire délimite un chambre sous pression principale du cylindre primaire, tandis que, pendant une deuxième course partielle du piston primaire, une surface frontale relativement petite du piston primaire délimite une chambre sous pression de commande fine du cylindre primaire. On obtient ainsi un convertisseur de forces hydraulique avec une unité primaire qui ne possède qu'une seule unité à cylindre et piston et avec laquelle, pour un coût d'aménagement technique minimal, on peut réaliser une combinaison d'une vitesse rapide et d'une vitesse de travail ou d'une vitesse lente (avec une force maximale comparativement supérieure), ce qui convient par exemple pour des dispositifs de serrage.
PCT/EP2009/007617 2008-11-08 2009-10-24 Convertisseur de forces hydraulique Ceased WO2010051913A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2009801540521A CN102272460A (zh) 2008-11-08 2009-10-24 液压的力转换器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810056378 DE102008056378A1 (de) 2008-11-08 2008-11-08 Hydraulischer Kraftübersetzer
DE102008056378.1 2008-11-08

Publications (1)

Publication Number Publication Date
WO2010051913A1 true WO2010051913A1 (fr) 2010-05-14

Family

ID=41560400

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/007617 Ceased WO2010051913A1 (fr) 2008-11-08 2009-10-24 Convertisseur de forces hydraulique

Country Status (3)

Country Link
CN (1) CN102272460A (fr)
DE (1) DE102008056378A1 (fr)
WO (1) WO2010051913A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109185239A (zh) * 2018-09-10 2019-01-11 深圳市中粤海洋能源科技有限公司 一种潮汐发电增压系统

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011121271B4 (de) * 2011-12-15 2023-12-21 Robert Bosch Gmbh Hydrostatischer Kreis mit Sekundärregelung
CN106523442B (zh) * 2016-11-10 2018-03-06 郑州磨料磨具磨削研究所有限公司 超高压螺旋式伺服加压器
DE102017211871A1 (de) * 2017-07-12 2019-01-17 Robert Bosch Gmbh Steuervorrichtung und Verfahren zum Ausführen einer Haltefunktion mittels eines hydraulischen Bremssystems eines Fahrzeugs
DE102018120000A1 (de) * 2018-08-16 2020-02-20 Moog Gmbh Elektrohydrostatisches Aktuatorsystem mit Nachsaugbehälter

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09151903A (ja) * 1995-11-28 1997-06-10 Mitsubishi Heavy Ind Ltd 増圧ピストン式加圧試験装置
EP1138872A1 (fr) * 2000-03-30 2001-10-04 Halliburton Energy Services, Inc. Actionneurs d'un outil de puits et procédé
WO2002029254A2 (fr) * 2000-10-04 2002-04-11 Robert Bosch Gmbh Soupape pour reguler des liquides
DE10157373A1 (de) * 2001-11-22 2003-05-28 Bosch Rexroth Ag Antriebsvorrichtung, insbesondere für die Schließeinheit, die Einspritzeinheit oder die Auswerfer einer Kunstoffspritzgießmaschine
US20040216600A1 (en) * 2001-05-19 2004-11-04 Jorg Dantlgraber Drive mechanism, particularly for a moveable part of a closing unit or the injection unit of a plastic injection moulding machine
WO2004102010A1 (fr) * 2003-05-13 2004-11-25 Rang Jiao Verin electrique multiplicateur de pression hydraulique

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09151903A (ja) * 1995-11-28 1997-06-10 Mitsubishi Heavy Ind Ltd 増圧ピストン式加圧試験装置
EP1138872A1 (fr) * 2000-03-30 2001-10-04 Halliburton Energy Services, Inc. Actionneurs d'un outil de puits et procédé
WO2002029254A2 (fr) * 2000-10-04 2002-04-11 Robert Bosch Gmbh Soupape pour reguler des liquides
US20040216600A1 (en) * 2001-05-19 2004-11-04 Jorg Dantlgraber Drive mechanism, particularly for a moveable part of a closing unit or the injection unit of a plastic injection moulding machine
DE10157373A1 (de) * 2001-11-22 2003-05-28 Bosch Rexroth Ag Antriebsvorrichtung, insbesondere für die Schließeinheit, die Einspritzeinheit oder die Auswerfer einer Kunstoffspritzgießmaschine
WO2004102010A1 (fr) * 2003-05-13 2004-11-25 Rang Jiao Verin electrique multiplicateur de pression hydraulique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109185239A (zh) * 2018-09-10 2019-01-11 深圳市中粤海洋能源科技有限公司 一种潮汐发电增压系统

Also Published As

Publication number Publication date
CN102272460A (zh) 2011-12-07
DE102008056378A1 (de) 2010-05-12

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