EP0442842B1 - Vérin hydraulique avec multiplicateur de pression - Google Patents

Vérin hydraulique avec multiplicateur de pression Download PDF

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Publication number
EP0442842B1
EP0442842B1 EP91810039A EP91810039A EP0442842B1 EP 0442842 B1 EP0442842 B1 EP 0442842B1 EP 91810039 A EP91810039 A EP 91810039A EP 91810039 A EP91810039 A EP 91810039A EP 0442842 B1 EP0442842 B1 EP 0442842B1
Authority
EP
European Patent Office
Prior art keywords
piston
primary
duct
primary piston
secondary piston
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
EP91810039A
Other languages
German (de)
English (en)
Other versions
EP0442842A1 (fr
Inventor
Dionizy Simson
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.)
Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT91810039T priority Critical patent/ATE104023T1/de
Publication of EP0442842A1 publication Critical patent/EP0442842A1/fr
Application granted granted Critical
Publication of EP0442842B1 publication Critical patent/EP0442842B1/fr
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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the present invention relates to a hydraulic cylinder according to the preamble of patent claim 1 and according to the preamble of patent claim 2.
  • Hydraulic cylinders are needed, which generate large forces with small dimensions and weight. Such cylinders are used in piling technology in civil engineering as well as in stamping technology and as clamping elements in machine tools and in robotics.
  • either a shoulder is attached to the circumference of the primary piston or the cylinder tube has a step, or a ring is arranged inside the cylinder tube, which has the advantage that supply bores are not run over by seals and are thereby destroyed.
  • a cylinder 1 is closed on the one hand with a piston rod guide flange 2 and on the other hand with a cylinder base 3.
  • a primary piston 4 is provided with two bores 5 and 6, into which two plungers 7 and 8 penetrate.
  • the holes 5 and 6 are provided with seals 9 and 10.
  • the plungers 7 and 8 are rigidly connected to a secondary piston 11 in a ring shape.
  • the secondary piston 11 is on the piston rod 12 of the primary piston 4 and is movably sealed with respect to the cylinder 1 and the piston rod 12 with seals 13 and 14.
  • In the piston rod guide flange 2 there is also a seal 15 for sealing the piston rod 12 from the flange.
  • the primary piston 4 is also provided with a seal 16 at its end remote from the piston rod 12.
  • the primary and secondary pistons are shown in the upper half of FIG. 1 in a first position and in the lower half in a second position.
  • the cylinder base 3 contains two unlockable check valves 17 and 18, the check valve 17 being biased by a strong spring 19 and the check valve 18 by a weak spring 20.
  • the check valves 17 and 18 are unlocked by two unlocking pistons 21 and 22 designed as balls.
  • a supply line 23 for the fluid opens into the two narrower areas 24 and 25 of the check valve chambers 26 and 27.
  • the line 23 opens into the narrow areas 28 and 29, which are located between the check valves 17 and 18 and the release pistons 21 and 22 Parts 24 and 25 of the chambers 26 and 27.
  • a further supply line for the fluid opens at points 31 and 32 into the areas 33 and 34 of the check valve chambers, which are located behind the unlocking pistons, and connects the two chambers.
  • Another line 35 connects the check valve chamber 26 with the space 36 between the secondary piston 11 and the piston rod guide flange 2.
  • Another line 37 connects the part 34 of the check valve chamber 27 with a junction 38 in the cylinder barrel.
  • Another line 39 connects the check valve chamber 27 to the space 40, which is located between the cylinder base 3 and the primary piston 4.
  • bores 41 and 42 which connect the front to the rear of the valves.
  • Both pistons 4 and 11 are in their initial positions, as shown in the upper half of FIG. 1.
  • the check valve 18 opens with the weak spring 20, and thus the pressure fluid can flow through the bore 42 and the line 39 into the chamber 40.
  • the primary piston 4 moves until it encounters hard resistance.
  • the flow of the pressure fluid is interrupted for a short time, the check valve 18 closes with the weak spring 20 and the check valve 17 with the strong spring 19 is opened by the pressure building up.
  • the pressure fluid flows via the line 35 into the chamber 36, which has the consequence that the secondary piston 11 begins to move and the plungers 7 and 8 penetrate into the bores 5 and 6 of the primary piston 4.
  • the ratio between the pressurized areas of the secondary piston 11 and the plungers 7 and 8 are dimensioned in such a way that a hydraulic transmission occurs.
  • the pressure of the pressure fluid in the chamber 40 increases in accordance with the hydraulic translation.
  • the primary piston 4 moves forward with increased force until the resistance reaches the same size as the force generated. In this case, both the primary piston 4 and the secondary piston 11 do not reach their end position.
  • the pressure in the supply line is equalized, the check valve 17 closes, and the inflow of the hydraulic fluid can be interrupted. The pressure reached is retained.
  • the pressure in the line 30 is increased, the unlocking pistons 21 and 22 unlocking the two check valves 17 and 18.
  • the pressure fluid flows through the line 37 into the chamber 45 and forces the primary piston 4 and the secondary piston 11 back into their starting positions.
  • the pressure fluid can escape from the chambers 36 and 40 without pressure via the lines 35, 39 and 23.
  • the primary piston 4 does not encounter any fixed resistance in its forward movement, it comes to a stop with the secondary piston 11, in which case the latter cannot move and the pressure increase is not initiated. In this case, only the primary force acts on the piston rod guide flange 2 and the same cannot be torn off.
  • the shoulder 43 on the primary piston 4 or on the secondary piston 11 ensures that the mouth 38 of the line 37 is not is covered by a seal, and that through the shoulder 43 a hydraulic connection with the chamber 45 is constantly maintained. If the primary piston 4 encounters a resilient resistance during its forward movement, the translation process is initiated, but the maximum force is not reached because the secondary piston 11, after executing its stroke with the plungers 7 and 8, comes into contact with the cylinder base 3. The mouth 38 of the line 37 is not run over, and the seals are not destroyed. This situation is shown in the lower part of FIG. 1.
  • the cylinder tube 46 has a gradation 47, as a result of which a fixed stop 48 is formed for the primary piston.
  • the stop for the primary piston is formed by a split ring 49 within the cylinder tube 50, which ring is spread by a spring ring 51.
  • the solutions according to FIGS. 2 and 3 are less advantageous than those according to FIG. 1, since the translated force nevertheless arises when the stroke is carried out and then has to be absorbed with considerable effort. Also in the embodiments according to FIGS. 2 and 3, different positions of the pistons are shown in the drawing in the upper and lower halves. 2 and 3 is the same as that in FIG. 1.
  • the primary piston 52 has no axial bores and the secondary piston 53 has no plungers.
  • the primary piston is designed in three stages and has an axial line 54, which connects the chamber 55 to the chamber 56.
  • the secondary piston 53 has a two-stage bore 57, which is provided with seals 58, 59 at both ends.
  • a step 61 on the secondary piston ensures that there is always a hydraulic connection between the line mouth 62 and the chamber 63.
  • the function is the same as in the embodiment according to FIG. 1, ie when the primary piston 53 is maximally extended, a hydraulic transmission cannot occur at all. 4, different positions of the pistons are shown in the drawing in the upper and lower half.
  • the exemplary embodiments according to FIGS. 1 and 4 make it impossible to generate high internal forces which have to be absorbed afterwards.
  • the possibility of using commercially available stepless cylinder tubes in the exemplary embodiments according to FIGS. 1, 3 and 4 allows the manufacturing costs to be reduced considerably.
  • the check valves in the cylinder bottom By placing the check valves in the cylinder bottom, the high pressure area is limited to only one room and its size is only determined by the stroke of the primary piston.
  • the cylinder tube can be tapered, which is particularly desirable when used as a clamping cylinder in civil engineering, since the clamping body can then be made more solid.
  • the embodiment according to FIG. 4 is suitable especially for cylinders with small diameters for robotics.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Vehicle Body Suspensions (AREA)
  • Glass Compositions (AREA)
  • Paper (AREA)

Claims (4)

  1. Vérin hydraulique avec multiplicateur de pression constitué d'un tube de vérin (1), d'une bride de guidage de tige de piston (2), d'un fond de vérin (3), d'un piston primaire (4) pourvu d'une tige de piston (12) et d'un piston secondaire (11), le piston primaire (4) et le piston secondaire (11) étant disposés axialement l'un derrière l'autre et réciproquement mobiles, le piston secondaire l'étant entre le piston primaire et la bride de guidage et deux clapets anti-retour (17, 18) déverrouillables, préchargés par deux ressorts (19, 20) étant disposés dans le fond du vérin (3), les caractéristiques des deux ressorts (19, 20) étant différentes et la chambre (26) d'un des clapets anti-retour (17) étant reliée par une première conduite (35) à la chambre (36) se trouvant entre la bride de guidage de la tige de piston (2) et le piston secondaire (11), la chambre (27) de l'autre clapet anti-retour (18) étant reliée par une seconde conduite (39) à la chambre (40) se trouvant entre le fond du vérin (3) et le piston primaire (4), les parties arrière (24, 25) des deux chambres (26, 27) présentant respectivement un piston de déverrouillage (21, 22) et les parties arrière étant reliées entre elles par une troisième conduite (37), laquelle troisième conduite débouche dans la chambre (44) entre le piston primaire (4) et le piston secondaire (11) caractérisée en ce que le piston primaire (4) est pourvu d'au minimum deux trous (5, 6) dans lesquels pénètrent au minimum deux plongeurs (7, 8) reliés par le piston secondaire (11) et dont le rapport entre la surface sollicitée par la pression du piston secondaire et du plongeur est dimensionné de manière qu'apparaisse une multiplication hydraulique.
  2. Vérin hydraulique avec multiplicateur de pression constitué d'un tube de vérin (1), d'une bride de guidage de tige de piston (2), d'un fond de vérin (3), d'un piston primaire (52) pourvu d'une tige de piston (12) et d'un piston secondaire (53), le piston primaire (52) et le piston secondaire (53) étant disposés axialement l'un derrière l'autre et réciproquement mobiles, le piston secondaire l'étant entre le piston primaire et la bride de guidage et deux clapets anti-retour (17, 18) déverrouillables, préchargés par deux ressorts (19, 20) étant disposés dans le fond du vérin (3), les caractéristiques des deux ressorts (19, 20) étant différentes et la chambre (26) d'un des clapets anti-retour (17) étant reliée par une première conduite (35) à la chambre (36) se trouvant entre la bride de guidage de la tige de piston (2) et le piston secondaire (53), la chambre (27) de l'autre clapet anti-retour (18) étant reliée par une seconde conduite (39) à la chambre (55) se trouvant entre le fond du vérin (3) et le piston primaire (4), les parties arrière (24, 25) des deux chambres (26, 27) présentant respectivement un piston de déverrouillage (21, 22) et les parties arrière étant reliées entre elles par une troisième conduite (37), laquelle troisième conduite débouche dans la chambre (63) entre le piston primaire (52) et le piston secondaire (53) caractérisée en ce que le piston secondaire (53) est pourvu d'un trou axial à deux étages (57) lequel présente aux deux extrémités des joints (58, 59) et une chambre (56) est constituée entre la afce frontale intérieure du piston primaire (52) constitué de plusiseurs étages et du trou axial (57) du piston seconadire (53) et le piston primaire (52) est traversé par une conduite axiale (54) qui relie la chambre (56) et la chambre (55) entre elles.
  3. Vérin hydraulique selon la revendication 1 du brevet caractérisé en ce qu'un décrochement (43) est prévu sur la périphérie du piston primaire (4).
  4. Vérin hydraulique selon l'une des revendications précédentes du brevet caractérisé en ce qu'un passage (41, 42) se trouve dans les clapets anti-retour (17, 18) lequel relie les faces avant et arrière des clapets (17, 18).
EP91810039A 1990-02-14 1991-01-17 Vérin hydraulique avec multiplicateur de pression Expired - Lifetime EP0442842B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91810039T ATE104023T1 (de) 1990-02-14 1991-01-17 Hydraulikzylinder mit druckuebersetzung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH476/90 1990-02-14
CH47690 1990-02-14

Publications (2)

Publication Number Publication Date
EP0442842A1 EP0442842A1 (fr) 1991-08-21
EP0442842B1 true EP0442842B1 (fr) 1994-04-06

Family

ID=4187877

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91810039A Expired - Lifetime EP0442842B1 (fr) 1990-02-14 1991-01-17 Vérin hydraulique avec multiplicateur de pression

Country Status (5)

Country Link
EP (1) EP0442842B1 (fr)
JP (1) JPH051703A (fr)
AT (1) ATE104023T1 (fr)
DE (1) DE59101302D1 (fr)
PL (1) PL165086B1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06342623A (ja) * 1993-06-01 1994-12-13 S O C Kk チップヒューズ
DE102006029523B4 (de) * 2006-06-27 2014-10-23 Damcos A/S Stellvorrichtung
CN108561446B (zh) * 2018-01-18 2024-03-15 申科滑动轴承股份有限公司 一种推力头液压锁紧装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1296522B (de) * 1958-05-22 1969-05-29 Glas Maurus Hydraulische Druckeinheit mit Druckuebersetzung
US3410089A (en) * 1967-03-08 1968-11-12 Joseph D. Snitgen Fluid operated device
CH665007A5 (de) * 1984-05-11 1988-04-15 Enfo Grundlagen Forschungs Ag Hydraulischer zylinder mit kraftmultiplikation.

Also Published As

Publication number Publication date
ATE104023T1 (de) 1994-04-15
PL165086B1 (pl) 1994-11-30
JPH051703A (ja) 1993-01-08
PL288948A1 (en) 1992-01-27
DE59101302D1 (de) 1994-05-11
EP0442842A1 (fr) 1991-08-21

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