EP0283694A1 - Dispositif de verrouillage pour vérin à fluide - Google Patents

Dispositif de verrouillage pour vérin à fluide Download PDF

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Publication number
EP0283694A1
EP0283694A1 EP88101899A EP88101899A EP0283694A1 EP 0283694 A1 EP0283694 A1 EP 0283694A1 EP 88101899 A EP88101899 A EP 88101899A EP 88101899 A EP88101899 A EP 88101899A EP 0283694 A1 EP0283694 A1 EP 0283694A1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure medium
braking
cylinder
spring
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
EP88101899A
Other languages
German (de)
English (en)
Other versions
EP0283694B1 (fr
Inventor
Peter Pick
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.)
Knorr Bremse AG
Original Assignee
Knorr Bremse 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 Knorr Bremse AG filed Critical Knorr Bremse AG
Priority to AT88101899T priority Critical patent/ATE45012T1/de
Publication of EP0283694A1 publication Critical patent/EP0283694A1/fr
Application granted granted Critical
Publication of EP0283694B1 publication Critical patent/EP0283694B1/fr
Expired 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
    • 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
    • F15B15/082—Characterised by the construction of the motor unit the motor being of the slotted cylinder type
    • 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/261—Locking mechanisms using positive interengagement, e.g. balls and grooves, for locking in the end positions
    • 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads
    • 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/265—Locking mechanisms specially adapted for rodless pistons or slotted cylinders

Definitions

  • the invention relates to a braking device for pressure medium cylinders, in particular rodless cylinders, with a brake element which can be tightened by means of pressure medium application and whose pressure medium application is monitored by a switching valve.
  • Such braking devices are shown, for example, in EP-A 104 364 for rodless cylinders, the braking member being arranged integrated in the power take-off member.
  • the known brake devices mentioned have the defect to solve in the event of an undesired loss of pressure, which often cannot be permitted for safety reasons.
  • spring-loaded brakes that is to say to apply them with spring force and to release them by means of pressure medium.
  • a pressure medium accumulator which can be charged via a check valve from a pressure medium source is arranged in such a way that the pressure of the pressure medium source acts on a pressure switch which, when the pressure falls below a first, high Pressure threshold switches the switching valve to open an otherwise closed connection from the pressure medium store to the brake member, that a spring-loaded cylinder from the pressure medium store is provided, which activates a mechanical movement block arranged parallel to the brake member when a pressure exceeding a second, medium pressure threshold is applied, and that Braking member is designed to hold the nominal load of the pressure medium cylinder until it falls below a third, low pressure threshold of its pressure.
  • a pressure medium connection 2 leads from a pressure medium source 1, here a compressed air source, through a check valve 3 to a pressure medium reservoir 4 designed as a container.
  • a pressure switch 5 is connected to the pressure medium connection 2, which is above a relatively high spring 6 by an adjustable spring 6 adjustable pressure threshold in the pressure medium connection 2 closes a switch 7 and keeps it open below this pressure threshold.
  • a switching valve designed as a solenoid valve 8 and representing a 3/2-way valve, is connected to the pressure medium accumulator and connects the pressure medium accumulator 4 with a pressure medium connection 10 leading to braking elements 9 in the de-energized state; in the de-energized state, the solenoid valve 8 blocks this connection and keeps the pressure medium connection 10 depressurized, for example in the illustrated pneumatic system, vented to the atmosphere.
  • the switch 7 is arranged in an electrical connection 11 from a current source symbolized only by a plus sign to the excitation coil of the solenoid valve 8.
  • the pressure chamber 12 of a spring-loaded cylinder 13 is connected to the pressure medium reservoir 4, the piston rod 14 of the spring rod 15 when the force falls below a second, average pressure threshold in the pressure chamber 12 extends.
  • the piston rod 14 which represents a locking pin, ends in front of a perforated strip 16 located in front of the spring-loaded cylinder 13; in the extended state, the piston rod 14 can engage in the holes 17 in the perforated strip 16.
  • the piston rod 14 thus forms, together with the perforated strip 16, a mechanical, switchable movement lock 14, 16.
  • the braking device described above is arranged on a pressure medium cylinder (not shown in FIG. 1) with at least one fixed part and one part that is movable under pressure medium in such a way that the check valve 3, the pressure monitor 5, the pressure medium accumulator 4, the solenoid valve 8, the braking members 9 and the Spring cylinder 13 on one and the perforated strip 16 on the other of the two parts.
  • the perforated strip 16 is expediently fixed, and in the case of a conventional piston rod cylinder, the perforated strip 16 can be arranged in a movable manner with the piston rod.
  • the braking members 9 are constructed in the usual way as a friction brake; they can, as can be seen from the above-mentioned EP-A 104 364, each have a cylinder or bellows which can be pressurized by the pressure medium connection 10 and which, when pressurized, has a friction element, in particular a brake shoe or presses a brake lining onto the other part of the pressure cylinder which is relatively displaceable for this purpose.
  • the pressure medium cylinder can be equipped with a further, customary brake, for example according to EP-A 104 364 mentioned, which is used as a service brake in normal operation of the pressure medium cylinder.
  • the braking device according to Fig. 1 acts as follows:
  • the switch 7 is closed and, if the power source is functioning, that Solenoid valve 8 thus excited.
  • the pressure medium reservoir 4 is filled by the check valve 3 from the pressure medium source 1, but the energized solenoid valve 8 keeps the braking members 9 depressurized and thus released.
  • the spring-loaded cylinder 13 is acted upon from the pressure medium reservoir 4, so that its piston rod 14 is retracted and out of engagement with the perforated strip 16. If the pressure at the pressure medium source 1 drops due to any damage, the switch 7 of the pressure switch 5 opens when the pressure falls below a first, still relatively high pressure threshold and thus interrupts the excitation of the solenoid valve 8.
  • the solenoid valve 8 therefore switches to the switch position shown um, whereby it separates the braking members 9 from the atmosphere and instead connects to the pressure medium accumulator 4.
  • the braking elements 9 are therefore pressurized from the pressure medium store 4 and tighten, so that the pressure medium cylinder is braked in its current position. Since the pressure drop in the pressure medium source 1 via the check valve 3 means that there is no further pressure make-up in the pressure medium reservoir 4, a compensating pressure is established between the pressure medium reservoir 4 and the pressurized spaces of the braking members 9, which, however, is considerably higher than the pressure level by appropriately dimensioning the volume of the pressure medium reservoir 4 which is required to safely brake the pressure medium cylinder under its nominal load.
  • the spring-loaded cylinder 13 remains in its tensioned position, the piston rod 14 thus remains out of engagement with the perforated strip 16.
  • the compensating pressure prevailing in these rooms gradually drops. If the pressure falls below a second, medium pressure threshold, the storage spring 15 of the spring-loaded cylinder 13 pushes out the piston rod 14 so that it engages with the perforated strip 16. In general, the piston rod 14 will not yet engage in one of the holes 17 of the perforated strip 16, but rather on that Spring surface 13 facing surface 18 of perforated strip 16 stand up. At this medium pressure threshold mentioned, the application pressure is still sufficient to securely apply the braking elements 9. If the leak continues, the pressure in the pressure medium reservoir 4 and the spaces connected to it further decreases.
  • the pressure medium cylinder is thus locked in a form-fitting manner, so no further movement can take place. If, by chance, the piston rod 14 immediately engages in one of the holes 17 when it is extended, the aforementioned slipping of the pressure medium cylinder is of course not required; the pressure medium cylinder is locked in a form-fitting manner immediately without slipping.
  • the storage spring 15 is only slightly loaded when the piston of the spring storage cylinder 13 is suitably dimensioned, and can therefore be designed to be fatigue-free and unbreakable.
  • a further switch 19 indicated only by dashed lines, in the electrical connection between the current source and the switch 7, possibly also in the connection 11:
  • this switch 19 can be used for operational actuation of the braking members 9 serve, it is in this So if no further service brake is required.
  • the switch 19 is to be closed, the excitation of the solenoid valve 8 keeps the brake members 9 depressurized and thus released, while when the switch 19 is opened the excitation of the solenoid valve 8 is interrupted and the brake members are pressurized to brake will.
  • the switch 19, as is customary for service brakes, can be switched by any stops or a control program for the pressure medium cylinder.
  • FIG. 2 shows a braking device corresponding to that of FIG. 1, but the braking members are designed as a dual-circuit brake with the braking members 9 and 9 ⁇ for one braking circuit each, this dual-circuiting serves to further increase operational safety.
  • the parts corresponding to FIG. 1 are given the same reference numerals in FIG. 2 and therefore require no further explanation.
  • a pressure medium connection 20 leads from the solenoid valve 8 to an inlet of a 5/3-way valve 21, which is stabilized in its middle switching position by two springs 22.
  • the two output connections of the directional valve 21 are each connected to the braking members 9 and 9 ⁇ via a pressure medium connection 10 ⁇ or 23.
  • the directional control valve 21 is therefore pressurized on one side via the branch channels and switches to one of its lateral limit switch positions in which it connects the pressure medium connection 20 connects alone with the intact brake circuit for the braking elements 9 or 9 ⁇ , while the other, defective brake circuit is kept depressurized.
  • the function of the braking device is thus ensured even in the case of a defective brake circuit. Otherwise, the function of the braking device according to FIG. 2 corresponds to that according to FIG. 1.
  • FIG. 3 To use the braking elements provided for the braking device also for the service braking of the pressure medium cylinder required in normal operation, an arrangement according to FIG. 3 can be provided in a further modification:
  • the check valve 3, the pressure switch 5, the air container 4 and the spring accumulator 13 combined into a structural unit, which is symbolized by a square 24, to which on the one hand the pressure medium source 1 and on the other hand a solenoid valve 8 'is connected.
  • the line 10 or 20 extends from the solenoid valve 8 ⁇ according to FIG. 1 or 2. 1 and 2, the solenoid valve 8 ⁇ in the excited state does not connect the pressure medium connection 10 or 20 to the atmosphere, but to a further solenoid valve 25; in the de-energized state, the connections and functions described in FIGS.
  • the solenoid valve 25 is designed as a 3/2-way valve, in the unexcited state it connects a pressure medium source 1 ⁇ , which can correspond to the pressure medium source 1, to the solenoid valve 8 ⁇ , in the excited state it keeps the connection to the solenoid valve 8 ⁇ unpressurized. It thus follows that with an intact pressure medium source and power supply by means of the solenoid valve 25 direct control of the pressurization of the braking members is possible, the braking members being actuated when the solenoid valve 25 is not energized and the braking members released when the solenoid valve 25 is energized.
  • p3 means the pressure applied to the braking elements, that is to say the pressure prevailing in the pressure medium connection 10 or 20, p2 the pressure in the pressure medium reservoir 4, p v the pressure of the pressure medium source 1 and I the excitation current for the solenoid valve 8 or 8 ⁇ .
  • T the time lapse is plotted.
  • T the pressure medium and the current source are intact.
  • T takes place during the period between the times t1 and t2 a controlled by closing the switch 19 release process, the solenoid valve 8 picks up during this period, so that the pressure p3 drops and the braking members 9 release.
  • the pressure medium source 1 fails, its pressure drops rapidly according to p v and the switch 7 of the pressure monitor 5 opens immediately.
  • the solenoid valve 8 drops and acts on the braking elements 9 from the pressure medium accumulator 4, so that its pressure, as can be seen from the pressure curve of the p2, drops slightly; the drop in pressure is sufficient for safe braking.
  • the braking members 9 should also leak, so that their pressurization pressure together with the pressure of the pressure medium reservoir 4, as can be seen from the pressure profiles p3 and p2, begins to drop.
  • the pressure in the pressure medium reservoir 4 has dropped to a value at which the spring-loaded cylinder 13 responds and the piston rod 14 extends; however, the braking members 9 are still securely applied. If there is a further loss of pressure, the pressure drops below the pressure in the braking elements 9 at which they begin to slip under load with the nominal load of the pressure medium cylinder, at the latest immediately after this point in time, the piston rod 14 engages in a hole 17 in the perforated strip 16 and positively locks the pressure medium cylinder . It can thus be seen that if the pressure medium source fails, the frictional braking elements 9 are actuated and if there is a subsequent pressure loss due to leakage, a positive locking takes place.
  • a rodless cylinder 26 is indicated in front view, top view and side view with dashed lines, which cylinder is provided with a slide or force output element 27 shown in solid lines.
  • the force output element 27 includes a braking element, as is known, for example, from EP-A mentioned at the beginning. From FIG. 5 B, which shows a section along line AB in FIG. 5 A, it can be seen that the force output element 27 contains cavities 28 which serve as pressure medium stores. Furthermore, a recess 29 for receiving a check valve and a further recess 30 for receiving a pressure switch 31 are provided, the pressure switch 31, in contrast to FIG.
  • the solenoid valve 8 Fig. 1 is designed as a 3/2-way valve without a switch 7 and thus also fulfills the function of the solenoid valve 8 Fig. 1.
  • the spring-loaded cylinder 13 with the storage spring 15 and the piston rod 14 is arranged in the center of the force-output member 27, the piston rod 14 extends transversely to the longitudinal direction of the cylinder 26.
  • a solenoid valve 32 is provided, which corresponds to the solenoid valve 25 according to FIG.
  • the above-mentioned functional parts are connected by means of bores and channels running in the walls of the power output member 27.
  • On the outside of the cylinder 26 there are clamping grooves 33, one of which is clamped with a stop 35 by means of a clamping device 34.
  • the stop 35 protrudes only when the piston rod is extended in its path of motion when the force output element 27 is moving. Overall, this results in a rodless cylinder which, with little additional effort and little enlargement of the required Installation space in addition to a service brake has a frictional braking device, which acts in emergencies, with a form-fitting emergency stop held adjustably by the clamping device 34.
  • the braking device is also suitable for hydraulic pressure medium cylinders, the pressure medium accumulator must be designed accordingly and return lines must be provided instead of venting.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Braking Arrangements (AREA)
  • Lock And Its Accessories (AREA)
  • Braking Systems And Boosters (AREA)
EP88101899A 1987-03-20 1988-02-10 Dispositif de verrouillage pour vérin à fluide Expired EP0283694B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88101899T ATE45012T1 (de) 1987-03-20 1988-02-10 Bremseinrichtung fuer druckmittelzylinder.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3709164 1987-03-20
DE19873709164 DE3709164A1 (de) 1987-03-20 1987-03-20 Bremseinrichtung fuer druckmittelzylinder

Publications (2)

Publication Number Publication Date
EP0283694A1 true EP0283694A1 (fr) 1988-09-28
EP0283694B1 EP0283694B1 (fr) 1989-07-26

Family

ID=6323573

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88101899A Expired EP0283694B1 (fr) 1987-03-20 1988-02-10 Dispositif de verrouillage pour vérin à fluide

Country Status (3)

Country Link
EP (1) EP0283694B1 (fr)
AT (1) ATE45012T1 (fr)
DE (2) DE3709164A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0442859A1 (fr) * 1990-02-09 1991-08-21 Hygrama Ag Arrangement pour fixer un rail à un piston pilote
CN102392845A (zh) * 2011-11-28 2012-03-28 巨力索具股份有限公司 无源锁紧液压系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009034721A1 (de) 2009-07-24 2011-01-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pneumatikanlage

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2932282A (en) * 1957-07-08 1960-04-12 Roe L Mckinley Fluid actuated systems for operating and locking control elements
US3033171A (en) * 1960-09-07 1962-05-08 Sperry Rand Corp Interlocking means for hydraulic servomotor systems
US3654833A (en) * 1970-06-29 1972-04-11 Eaton Yale & Towne Hydraulic control circuit

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2610692C2 (de) * 1976-03-13 1986-11-27 L. Schuler GmbH, 7320 Göppingen Antriebseinrichtung für eine mechanisch angetriebene Presse
DE2633322C2 (de) * 1976-07-24 1985-07-18 L. Schuler GmbH, 7320 Göppingen Sicherheitssteuerung
DE2814163A1 (de) * 1978-04-01 1979-10-11 Teves Gmbh Alfred Notversorgungssystem
DE3363754D1 (en) * 1982-08-05 1986-07-03 Knorr Bremse Gmbh Rodless fluidic motor with brake means
DE3328292A1 (de) * 1983-08-05 1985-02-21 Robert Bosch Gmbh, 7000 Stuttgart Arbeitszylinder mit bremseinrichtung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2932282A (en) * 1957-07-08 1960-04-12 Roe L Mckinley Fluid actuated systems for operating and locking control elements
US3033171A (en) * 1960-09-07 1962-05-08 Sperry Rand Corp Interlocking means for hydraulic servomotor systems
US3654833A (en) * 1970-06-29 1972-04-11 Eaton Yale & Towne Hydraulic control circuit

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0442859A1 (fr) * 1990-02-09 1991-08-21 Hygrama Ag Arrangement pour fixer un rail à un piston pilote
CN102392845A (zh) * 2011-11-28 2012-03-28 巨力索具股份有限公司 无源锁紧液压系统
CN102392845B (zh) * 2011-11-28 2014-08-20 巨力索具股份有限公司 无源锁紧液压系统

Also Published As

Publication number Publication date
DE3860001D1 (en) 1989-08-31
ATE45012T1 (de) 1989-08-15
EP0283694B1 (fr) 1989-07-26
DE3709164A1 (de) 1988-09-29

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