EP0161237B1 - Distributeur à commande hydraulique - Google Patents

Distributeur à commande hydraulique Download PDF

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Publication number
EP0161237B1
EP0161237B1 EP85890104A EP85890104A EP0161237B1 EP 0161237 B1 EP0161237 B1 EP 0161237B1 EP 85890104 A EP85890104 A EP 85890104A EP 85890104 A EP85890104 A EP 85890104A EP 0161237 B1 EP0161237 B1 EP 0161237B1
Authority
EP
European Patent Office
Prior art keywords
switching
bores
index
bore
medium
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
Application number
EP85890104A
Other languages
German (de)
English (en)
Other versions
EP0161237A1 (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.)
Hoerbiger Ventilwerke GmbH and Co KG
Original Assignee
ENFO Grundlagen Forschungs 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 ENFO Grundlagen Forschungs AG filed Critical ENFO Grundlagen Forschungs AG
Priority to AT85890104T priority Critical patent/ATE32624T1/de
Publication of EP0161237A1 publication Critical patent/EP0161237A1/fr
Application granted granted Critical
Publication of EP0161237B1 publication Critical patent/EP0161237B1/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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/12—Fluid oscillators or pulse generators
    • F15B21/125—Fluid oscillators or pulse generators by means of a rotating valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86389—Programmer or timer
    • Y10T137/86405—Repeating cycle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86389—Programmer or timer
    • Y10T137/86405—Repeating cycle
    • Y10T137/86413—Self-cycling
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/877—With flow control means for branched passages
    • Y10T137/87708—With common valve operator
    • Y10T137/87732—With gearing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/877—With flow control means for branched passages
    • Y10T137/87708—With common valve operator
    • Y10T137/87764—Having fluid actuator

Definitions

  • the invention relates to a rotary slide valve with a hydraulic rotary drive, which has a valve housing with bores for supplying and carrying away a working medium and at least one consumer channel, the consumer channel being able to be connected alternately with the bores for supplying and carrying away the working medium.
  • Such a rotary slide valve is known from US-A-2 807 141.
  • the known embodiment consists of an elongated housing with an axial bore in which a shaft designed as a rotary slide valve is mounted. At an axial distance from each other two through holes intersecting at right angles are provided in the shaft, one of which controls the connection of the hole for the supply of the working medium and the other controls the connection of the hole for guiding the working medium away from the forked consumer channel.
  • a turbine is provided for driving the rotary slide valve, the turbine wheel of which is attached to one end of the shaft and pressurized drive medium is applied via a nozzle.
  • the invention has for its object to provide a rotary slide valve of the type mentioned, which has a compact housing and is insensitive to mechanical stresses, so that it is particularly suitable for installation in hydraulic devices, with a secure seal should be easily possible.
  • this object is achieved in that two switching disks are provided, which are provided on their circumference with toothings which are in constant engagement with one another, that the switching disks are provided with at least one axial switching bore, which alternately with rotation of the switching disks the consumer channel can be connected, and that in each switching disc a radially extending slot is provided which constantly connects the switching bore of the one switching disc with the bore for supplying the working medium and the switching bore of the other switching disc with the bore for guiding the working medium away.
  • the use of switching disks for the control of the working medium not only results in a flat valve housing, but also the bores required for the supply and removal of the working medium and the consumer ducts can be easily formed without the need for exposed lines.
  • the switching holes in the switching disks open into flat surfaces, so that the sealing is correspondingly simple.
  • the rotary slide valve according to the invention is characterized by robustness, in particular by resistance to external mechanical influences, and by simple manufacture.
  • two switching bores which are arranged symmetrically to the center and which are connected to the slot can advantageously be provided per switching disk.
  • the rotating speed of the discs can be reduced by half while the number of pulses remains the same.
  • the housing has an upper housing part and a lower housing part and an intermediate plate arranged between them for receiving the switching disks, it can be manufactured and assembled particularly easily.
  • the switching disks can be provided with pressure compensation bores, which they axially penetrate parallel to the switching bores at a lateral distance from them. This avoids one-sided pressure loads on the switching disks caused by the working medium and the associated higher frictional forces.
  • a preferred embodiment of the rotary slide valve according to the invention consists in the fact that the rotary drive is formed by the toothing of the switching disks and bores are provided in the valve housing for supplying and removing a drive medium for actuating the rotary drive.
  • the switch disks themselves are also used as rotary actuators, so that further design measures for them can be omitted.
  • the rotary movement of the switching disks can be further improved and facilitated according to the invention in that in the edge areas of the switching disks, which are diametrically opposed to the edge areas which are acted upon by the supply or removal of drive medium for actuating the rotary drive, diametrically opposite relief grooves are provided, which are provided via Relief channels are connected to the edge areas exposed to the drive medium. It will this also avoids one-sided pressurization of the switching disks acting in the radial direction.
  • the rotary slide valve according to the invention is particularly suitable for a hydraulic vibrating ram due to its compact design, its mechanical insensitivity and due to the high switching frequencies that can be achieved.
  • valve housing 1 to 3 is a 4/2-way valve and comprises a valve housing 1 with an upper housing part 2 and a lower housing part 3. Between the upper housing part 2 and the lower housing part 3 is an intermediate plate 4 with an eyeglass-shaped seat for two switching disks 6 and 7 arranged.
  • the upper housing part 2, the lower housing part 3 and the intermediate plate 4 are provided with seals, not shown, and connected to one another by screws and centering pins, also not shown.
  • the switching disks 6 and 7 are arranged in the sealed valve housing 1 with play. Both switching disks 6, 7 each have two switching bores 8 and 9 or 10 and 11, which are arranged axially in the switching disks 6, 7. Only one or more switching bores per switching disk could also be provided.
  • the switching bores 8 and 9 or 10 and 11 are connected to a slot 12 or 13 which is guided over the center of the switching disks 6, 7. On their circumference, the switching disks 6, 7 are provided with involute teeth 14 and 15, respectively.
  • an axial inlet bore P is arranged above the center of the switching disc 6 and an axial return bore T is arranged above the center of the switching disc 7.
  • axial bores 16, 17, 18 and 19 are incorporated in the upper housing part 2 and in the lower housing part 3.
  • the bores 16 and 17 are located in the area of the switching disk 6 shown on the left in the drawings and the bores 18 and 19 are located in the area of the switching disk 7 shown on the right in the drawings.
  • the axial bores 16 and 18 are horizontal in the lower part 3 of the housing Channel A and the axial bores 17 and 19 are each connected to one another by a horizontal channel B also provided in the lower housing part 3.
  • the vertical bores 16, 17, 18 and 19 start from the respective horizontal channel A and B and are provided both in the lower housing part 3 and in the upper housing part 2.
  • the vertical bores 16, 17, 18 and 19 end blind, wherein they have the same diameter as the sections running in the lower housing part 3 and are flush with them.
  • the blindly ending sections of the bores 16, 17, 18 and 19 bring about pressure equalization.
  • axial pressure compensation bores 20 are also left free. These are arranged in each switching disk 6, 7 in two rows parallel to the slots 12 and 13. Each switching disk 6 and 7 has a total of six axial pressure compensation bores 20. If the switching bores 8 and 9 in the switching disks 6 and 7 are located outside the area of the vertical bores 16, 17, 18 and 19 provided in the housing 1, at least one pressure compensation bore 20 is provided in the area of the vertical bores 16, 17, 18 and 19, whereby the partial sections of the bores located in the upper housing part 2 and in the lower housing part 3 are connected to one another.
  • the drive medium for the rotary drive is supplied and carried away via two bores Z1 and Z2 provided in the upper housing part 2.
  • FIG. 4 shows the position of a switching bore 8, 10 relative to an axial bore 16, 18 cooperating with it.
  • the axial bore 16, 18 is shown in dashed lines.
  • Below devon the upper half of the switching bore 8, 10 together with the subsequent radial slot 12, 13 is shown fully extended. In this position there is just yet no connection between the switching bore 8, 10 and the vertical bore 16, 18.
  • the switching bore 8, 10 gets more and more into the area of the axial bore 16, 18 until it is aligned with it after pivoting through 45 °. After a swivel path of 90 ° clockwise, the connection is interrupted again.
  • the switching bore 8, 10 is then in the position shown in broken lines in FIG. 4.
  • FIGS. 5a, 5b, 5c and 5d four different positions of the switching disks with the switching bores 8, 9, 10 and 11 are shown.
  • the slots 12 and 13 are each in a different position.
  • the inlet bore P and the return bore T are not connected to the consumer channels A and B.
  • the inlet bore P is connected to the channel A via the left switching disc and the return bore T is connected to the channel B via the right switching disc.
  • the inlet bore P is connected to the channel B via the left switching disc and the return bore T is connected to the channel A via the right switching disc.
  • the working medium for the rotary drive of the rotary slide valve enters through one of the bores Z1 or Z2 into the area of the toothings 14, 15 of the two switching disks 6, 7 and flows back through the other bore Z1, Z2 to a container located outside the rotary slide valve.
  • the speed of the switching discs 6 and 7 depends on the flow rate of the drive medium and can be influenced from the outside. Both switching disks 6 and 7 rotate synchronously as a result of the toothing 14 and 15 attached to their circumference, the switching bores 8, 9, 10 and 11 in the switching disks 6 and 7 the bores 16, 17 located in the upper housing part 2 and in the lower housing part 3, Roam 18 and 19.
  • the points drawn in bold in FIGS. 5a to 5d represent any two points on the circumference of the respective switching disk and illustrate the synchronous rotary movement of the switching disks under the influence of the rotary drive.
  • the slots 12 and 13 in the switching disks 6 and 7 each connect both switching bores 8 and 9 or 10 and 11 provided in the disks permanently with the inlet bore P for the working medium or with the return bore T. With a full revolution of the switching disks 6 and 7 there are two switching cycles.
  • the working pressure supplied is completely balanced axially and radially in each switching disc. All active surfaces are symmetrical, the pressure from both sides being compensated for by the pressure compensation holes 20 in the switching disks 6 and 7 during the closing process in the switching bores.
  • each switching disk 6 and 7 is equipped with a hollow bearing journal 21 or 22, which transmits the radial forces to bearing bushes 23 and 24 provided in the upper housing part 2 and in the lower housing part 3.
  • the radial forces can be largely reduced by means of relief grooves 25 and relief channels 26 shown in FIG. 7, which are provided in the intermediate plate 4.
  • only one switching bore is provided for each switching disk, in which case the slot in the switching disk connecting the switching bore with the inlet bore or with the return bore in the valve housing can be formed only on one side.
  • the channels A and B provided in the lower housing part 3 are connected to lines which lead to a vibration cylinder, where alternately one side of the piston and then the other side of the piston are pressurized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)

Claims (8)

1. Distributeur à tiroir rotatif, comportant un dispositif hydraulique (Z1, Z2) pour l'entraînement en rotation, distributeur qui possède un corps (1) pourvu d'orifices (P, T) pour l'amenée et l'évacuation d'un fluide de travail et d'au moins un canal utilisateur (A, B) qui peut être relié alternativement aux orifices (P, T) pour l'amenée et l'évaucation du fluide de travail, caractérisé en ce qu'il comprend deux disques rotatifs de commutation (6, 7) dont les périphéries portent des dentures qui sont constamment en prises l'une avec l'autre, que les disques (6, 7) présentent chacun au moins un perçage axial de commutation (8, 9 ; 10, 11), les perçages des disques (6, 7) pouvant être reliés alternativement au canal utilisateur (A, B) pendant la rotation des disques (6, 7), et que chaque disque (6, 7) est pourvu d'une fente (12, 13) orientée radialement et qui, sur un disque (6), relie le perçage (8, 9) en permanence à l'orifice (P) pour l'amenée du fluide de travail, tandis que, sur l'autre disque (7), elle relie le perçage (10, 11) en permanence à l'orifice (T) pour l'évacuation du fluide de travail.
2. Distributeur selon la revendication 1, caractérisé en ce que chaque disque (6, 7) présente deux perçages de commutation (8, 9 ; 10, 11) disposés symétriquement par rapport au centre et communiquant avec la fente (12, 13).
3. Distributeur selon la revendication 1 ou 2, caractérisé en ce que le corps (1) comporte une partie supérieure (2), une partie inférieure (3) et une plaque intermédiaire (4) interposée entre elles et destinée à recevoir les disques (6, 7).
4. Distributeur selon la revendication 1, 2 ou 3, caractérisé en ce que les disques (6, 7) présentent des trous d'égalisation de pression (20) qui traversent les disques axialement, parallèlement aux perçages de commutation (8, 9; 10, 11) et latéralement à distance de ceux-ci.
5. Distributeur selon une des revendications 1 à 4, caractérisé en ce que le dispositif d'entraînement en rotation est constitué par les dentures des disques (6, 7) et que des orifices (Z1, Z2) pour l'amenée et l'évacuation d'un fluide d'entraînement, sont prévus dans le corps (1) du distributeur pour l'actionnement du dispositif d'entraînement.
6. Distributeur selon une des revendications 1 à 5, caractérisé en ce que les disques (6, 7) sont munis de tourillons (21, 22) et que des coussinets (23, 24) sont prévus dans le corps (1).
7. Distributeur selon une des revendications 1 à 6, caractérisé en ce que des rainures de décharge (25) sont prévues dans des zones périphériques des disques (6, 7) situées diamétralement à l'opposé des zones périphériques, du même disque, sur lesquelles agit le fluide d'entraînement amené ou évacué, en vue de l'actionnement du dispositif d'entraînement en rotation, les rainures (25) étant reliées par des canaux de décharge (26) aux zones périphériques sur lesquelles agit le fluide d'entraînement.
8. Vibrofonceur hydraulique équipé d'un distributeur selon une des revendications précédentes.
EP85890104A 1984-05-11 1985-05-03 Distributeur à commande hydraulique Expired EP0161237B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85890104T ATE32624T1 (de) 1984-05-11 1985-05-03 Wegeventil mit hydraulischer betaetigung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2356/84A CH666091A5 (de) 1984-05-11 1984-05-11 Drehschieberventil mit hydraulischem drehantrieb.
CH2356/84 1984-05-11

Publications (2)

Publication Number Publication Date
EP0161237A1 EP0161237A1 (fr) 1985-11-13
EP0161237B1 true EP0161237B1 (fr) 1988-02-24

Family

ID=4231874

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85890104A Expired EP0161237B1 (fr) 1984-05-11 1985-05-03 Distributeur à commande hydraulique

Country Status (5)

Country Link
US (1) US4633903A (fr)
EP (1) EP0161237B1 (fr)
AT (1) ATE32624T1 (fr)
CH (1) CH666091A5 (fr)
DE (1) DE3561671D1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5241733A (en) * 1991-09-10 1993-09-07 Geber Garment Technology, Inc. Method of making a cloth cutter bristle bed from elongate support members
FR2685944B1 (fr) * 1992-01-08 1995-05-19 Snecma Valve rotative de distribution de fluide et ensemble de valves en faisant application.

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB298935A (en) * 1927-07-14 1928-10-15 Arthur Treve Holman Improvements in or relating to fluid-actuated rock-drills and similar tools
US2178182A (en) * 1939-03-31 1939-10-31 Harry F Morgan Valve structure
US2807141A (en) * 1953-06-02 1957-09-24 Don S Strader Pulsator for a hydraulic system
US2837115A (en) * 1956-10-09 1958-06-03 Howard S Bancroft Fluid pressure controlling valve
US3296874A (en) * 1964-12-16 1967-01-10 Gen Motors Corp Vibration generator
US3499465A (en) * 1967-02-08 1970-03-10 Maurice Rhodes Zent Milking machines
US3654961A (en) * 1969-03-14 1972-04-11 Albert Phillips Rotary percussion drill having a hydraulically actuated percussion device
GB1316261A (en) * 1969-06-27 1973-05-09 Howard Ltd C A E C Fluid flow control valves
DE2819404A1 (de) * 1978-05-03 1979-11-08 Wildfang Dieter Kg Fluessigkeits-impulsgeber
US4373874A (en) * 1979-07-30 1983-02-15 Albert Phillips Fluid actuated pump system
US4478248A (en) * 1983-01-20 1984-10-23 Devall Donald L Rotary valve

Also Published As

Publication number Publication date
DE3561671D1 (en) 1988-03-31
CH666091A5 (de) 1988-06-30
ATE32624T1 (de) 1988-03-15
EP0161237A1 (fr) 1985-11-13
US4633903A (en) 1987-01-06

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