WO2003014603A2 - Systeme de buse d'amortissement - Google Patents

Systeme de buse d'amortissement Download PDF

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Publication number
WO2003014603A2
WO2003014603A2 PCT/DE2002/002664 DE0202664W WO03014603A2 WO 2003014603 A2 WO2003014603 A2 WO 2003014603A2 DE 0202664 W DE0202664 W DE 0202664W WO 03014603 A2 WO03014603 A2 WO 03014603A2
Authority
WO
WIPO (PCT)
Prior art keywords
nozzle body
pressure medium
nozzle
medium channel
nozzle arrangement
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/DE2002/002664
Other languages
German (de)
English (en)
Other versions
WO2003014603A3 (fr
Inventor
Peter Lauer
Karl Meyer
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.)
Bosch Rexroth AG
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 WO2003014603A2 publication Critical patent/WO2003014603A2/fr
Publication of WO2003014603A3 publication Critical patent/WO2003014603A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths

Definitions

  • the invention relates to a damping nozzle arrangement for hydraulic pressure medium according to the preamble of claim 1.
  • damping nozzles usually consist of a nozzle body provided with a longitudinal bore running through it, which can be inserted into a bore of a housing accommodating the nozzle body.
  • the damping effect is greater the smaller the passage cross section of the damping nozzle and the longer the bore.
  • the manufacture of damping nozzles with a small passage cross-section is difficult since this requires drills with a very small diameter.
  • DE 43 27 825 C2 discloses a steaming nozzle arrangement according to the preamble of claim 1.
  • a nozzle body is mounted in an axially displaceable manner in a pressure medium channel of a hydraulic device between a working position and a cleaning position.
  • the nozzle body is designed as a non-return element.
  • Like the pressure medium channel it has a circular cross section.
  • the pressure medium channel has three sections with different diameters.
  • the first section of the pressure medium channel serves as a slide bearing for the nozzle body. In this section, the inside diameter of the pressure medium channel is practically equal to the outside diameter of the nozzle body.
  • the inside diameter of the pressure medium channel is chosen to be larger than the outside diameter of the nozzle body, so that this section forms an annular groove.
  • This section is followed by a third section, in which the inside diameter of the pressure medium channel is smaller than the outside diameter of the nozzle body.
  • the transition region between the second and the third section forms a step with an annular surface facing the nozzle body.
  • the face of the nozzle body lies against this surface in the working position.
  • the end face of the nozzle body, which lies against the step is provided with a slot.
  • the slot together with the circular surface of the step, forms two nozzles with a rectangular cross section.
  • the pressure medium flows over the two Nozzles from the annular groove in the third section of the pressure medium channel.
  • the flow cross section of the two nozzles is determined by the width and the depth of the slot in the end face of the nozzle body.
  • the other end face of the nozzle body is provided with an axial bore which does not completely penetrate the nozzle body. This bore opens into a radial bore that connects the axial bore with the annular groove.
  • the pressure medium flows from one side of the nozzle body via the axial and the radial bore into the annular groove and from there through the slot in the end face to the other side of the nozzle body.
  • the cleaning position of the nozzle body is provided.
  • the nozzle body is acted upon with pressure medium such that the end face provided with the slot lifts off the step.
  • a substantially larger cross-section is available for the pressure medium flow, which makes it possible to wash away dirt particles that have accumulated in the area of the slot through the annular groove, the radial bore and the axial bore.
  • the length of the annular groove is selected so that the radial bore opens into the annular groove both in the working position of the nozzle body and in its cleaning position. Since the width of the front slot of the nozzle body is determined by the thickness of the tool required to produce the slot, not reduce the throttle cross section of the known damping arrangement arbitrarily.
  • the invention has for its object to provide a damping nozzle arrangement for hydraulic pressure medium, which is easy to manufacture even when a high damping is required.
  • the throttling of the pressure medium flow takes place in the area of the annular gap, whereby an additional throttling basically occurs due to the deflection of the pressure medium flow. Since the annular gap is formed from two interlocking parts, a very narrow gap can be realized in a simple manner. Since the annular gap extends over the entire circumference of the nozzle body, the risk that the nozzle arrangement is clogged with dirt particles is low even in the case of nozzle arrangements with a large damping effect. As far as individual dirt particles reach the area of the annular gap, they always cover only a very small part of the entire passage cross section. This reduces the requirements for filtering the pressure medium, so that the effort required for the filter is reduced.
  • FIG. 1 shows a longitudinal section through a first steaming nozzle arrangement according to the invention
  • FIG. 2 shows a section through the steam nozzle arrangement shown in FIG. 1 along the line A - B
  • FIG. 3 shows a longitudinal section through a second steaming nozzle arrangement according to the invention
  • Figure 4 shows a longitudinal section through a third steam nozzle arrangement according to the invention.
  • FIG. 1 shows a longitudinal section through a first steam nozzle arrangement according to the invention.
  • a nozzle body 11 is in a pressure medium channel 12 of a hydraulic device 13, for. B. a hydraulic valve, screwed.
  • the nozzle body 11 and the pressure medium channel 12 are coaxially arranged one another.
  • a first section 14 of the nozzle body 11 is provided with an external thread 15 which engages in an internal thread 16 of the pressure medium channel 12.
  • the internal thread 16 extends only over part of the pressure medium channel 12.
  • the outlet of the internal thread 16 forms a stop which limits the screw-in depth of the nozzle body 11.
  • the core hole diameter of the internal thread 16 is denoted by di.
  • the second section of the nozzle body 11 which is provided with the reference symbol 17, it forms the outer boundary of an annular gap 18.
  • the width of the annular gap 18 is denoted by s.
  • the end faces of the nozzle body 11 are designated 19 and 20.
  • the second section 17 of the nozzle body 11 is provided with two radial bores 21a and 21b which lead from the circumference of the section 17 of the nozzle body 11 to its central axis.
  • the radial bores 21a and 21b form a through bore 21 with the diameter d 3 .
  • a single radial bore or a plurality of radial bores leading from the periphery to the central axis can be provided.
  • An axial bore 22 opens into the through bore 21, which leads from the end face 19 of the nozzle body 11 into the through bore 21, but does not completely penetrate the nozzle body 11.
  • the diameter of the axial bore 22 is denoted by d 4 .
  • the axial bore 22 and the through hole 21 are perpendicular to each other. The angle between the axial bore 22 and that from the circumference to the central axis of the Nozzle body 11 leading radial bores can deviate from 90 °.
  • the damping effect is greater than at an angle of 90 °.
  • the damping effect is smaller than at an angle of 90 °.
  • the width s of the annular gap 18 is both smaller than the diameter d ⁇ of the through hole 21 and smaller than the diameter d 4 of the axial bore 22, the diameter d 4 being advantageously larger than the diameter d3.
  • the hydraulic pressure medium flows from the end face 19 through the axial bore 22 into the radial bores 21a and 21b and from there into the annular gap 18. This takes place both at the transition from the axial bore 22 into the radial bores 21a, 21b and at the transition from these bores in the annular gap 18 a deflection of the pressure medium flow increasing the damping effect.
  • the hydraulic pressure medium can also flow through the steaming nozzle arrangement in the opposite direction.
  • the annular gap 18 has a significant part in the damping effect in connection with the deflection from the radial bores 21a, 21b to the annular gap 18.
  • the nozzle body 11 is provided on the end face with six engagement surfaces, which are receptacles for form an Allen key. Because of the sectional view, only two contact surfaces 25 and 26 are visible in FIG. The recess formed by the engagement surfaces is arranged in the extension of the axial bore 22.
  • FIG. 2 shows a section through the steam nozzle arrangement shown in FIG. 1 along the line A - B at the level of the through bore 21. Between the housing 13 and the nozzle body 11, the annular gap 18 extends, which also extends over the radial bores 21a and 21b the axial bore 22 is connected.
  • FIG. 3 shows a longitudinal section through a second steaming nozzle arrangement according to the invention.
  • a nozzle body 31 provided with an external thread 30 is screwed into a pressure medium channel 33 of the housing 13 of a hydraulic device provided with an internal thread 32.
  • the outer diameter of the external thread 30 is denoted by ds.
  • the internal thread 30 extends in the section designated 35.
  • the outlet of the internal thread 32 forms a stop which limits the screw-in depth of the nozzle body 31.
  • the nozzle body 31 is provided in the section denoted by 36 with an annular groove 37 with a rectangular cross section.
  • the annular gap designated 38 extends here between the nozzle body 31, the outer diameter of which in the region of the annular groove 37 is designated d 2 , and the passages of the external thread 32 of the pressure medium channel 33, which extend between the diameters di and ds.
  • the hydraulic pressure medium flows from the end face 19 via the axial bore 22 and the radial bores 21a, 21b into the annular gap 38. From there, the hydraulic pressure medium flows through two further radial bores 40a and 40b in the form of a through bore 40 with the diameter dg and a further axial bore 41 with the diameter d 7 to the end face 20 of the nozzle body 31.
  • Diameters d3 and dg and the diameters d 4 and d 7 are chosen to be the same size.
  • FIG. 4 shows a longitudinal section through a third steam nozzle arrangement according to the invention.
  • a nozzle body 51 provided with an external thread 50 is screwed into a pressure medium channel 53 of the housing 13 of a hydraulic device provided with an internal thread 52.
  • the nozzle body 51 is designed here as a hollow screw with a cylindrical head 55.
  • the head 55 is provided on the end face with a receiving slot 56 for a screwdriver, the engagement surfaces for the screwdriver are denoted by 56a and 56b.
  • the annular gap designated 57 is located between the head 55 of the nozzle body 51 and the pressure medium channel . 53.
  • a through bore 58 forming two radial bores runs in the cylinder head 55 and opens into the annular gap 57, the length of which is determined by the distance between the outlet openings of the through bore 58 and the end face of the head 55 is determined.
  • an axial bore 59 runs, which opens into the through bore 58.
  • the hydraulic pressure medium can also flow through this steaming nozzle arrangement in both flow directions.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Nozzles (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)

Abstract

Dans un système de buse d'amortissement destiné à un fluide hydraulique sous pression, un corps de buse est disposé dans un canal à fluide sous pression. Ce corps de buse comprend un alésage axial partant d'un côté frontal, cet alésage ne traversant pas complètement le corps de buse. Le corps de buse comprend également un alésage radial qui relie l'alésage axial à un espace annulaire formé entre le corps de buse et le canal à fluide sous pression. Entre cet espace annulaire et le canal à fluide sous pression sont disposées deux buses de section rectangulaire qui déterminent l'effet d'étranglement du système de buse d'amortissement. L'invention concerne un système de buse d'amortissement qui peut être produit facilement même si l'effet d'étranglement recherché est important. A la place des deux buses de section rectangulaire, on utilise pour le diamètre extérieur du corps de buse et pour le diamètre intérieur du canal à fluide sous pression qui l'entoure des dimensions telles qu'un interstice annulaire délimité dans le sens axial soit formé entre le corps de buse et le canal à fluide sous pression, le corps de buse étant fermement maintenu dans le canal à fluide sous pression. Ce type de système de buse est employé pour amortir des systèmes hydrauliques enclins aux vibrations.
PCT/DE2002/002664 2001-07-25 2002-07-19 Systeme de buse d'amortissement Ceased WO2003014603A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10136135 2001-07-25
DE10136135.1 2001-07-25

Publications (2)

Publication Number Publication Date
WO2003014603A2 true WO2003014603A2 (fr) 2003-02-20
WO2003014603A3 WO2003014603A3 (fr) 2003-05-30

Family

ID=7692986

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/002664 Ceased WO2003014603A2 (fr) 2001-07-25 2002-07-19 Systeme de buse d'amortissement

Country Status (2)

Country Link
DE (1) DE10232822A1 (fr)
WO (1) WO2003014603A2 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4327825C2 (de) 1992-11-24 1996-10-02 Mannesmann Ag Drosselrückschlagelement

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2409214A1 (de) * 1974-02-26 1975-09-11 Samson Apparatebau Ag Ventil mit vorrichtung zur geraeuschdaempfung
US5118075A (en) * 1991-02-12 1992-06-02 Allied-Signal Inc. Seal arrangement for a metering valve
DE4334607A1 (de) * 1993-10-11 1995-04-13 Rexroth Mannesmann Gmbh 2-Wege-Einbauventil mit Druckbegrenzungsfunktion

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4327825C2 (de) 1992-11-24 1996-10-02 Mannesmann Ag Drosselrückschlagelement

Also Published As

Publication number Publication date
WO2003014603A3 (fr) 2003-05-30
DE10232822A1 (de) 2003-02-06

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