EP0301230B1 - Machine à pistons radiaux ou axiaux avec un aménagement des soupapes comprenant une bague de soupapes - Google Patents

Machine à pistons radiaux ou axiaux avec un aménagement des soupapes comprenant une bague de soupapes Download PDF

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Publication number
EP0301230B1
EP0301230B1 EP88109856A EP88109856A EP0301230B1 EP 0301230 B1 EP0301230 B1 EP 0301230B1 EP 88109856 A EP88109856 A EP 88109856A EP 88109856 A EP88109856 A EP 88109856A EP 0301230 B1 EP0301230 B1 EP 0301230B1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
piston machine
machine according
valve ring
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
EP88109856A
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German (de)
English (en)
Other versions
EP0301230A2 (fr
EP0301230A3 (en
Inventor
Manfred Lotter
Rainer Stölzer
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.)
Hydromatik GmbH
Original Assignee
Hydromatik GmbH
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Filing date
Publication date
Application filed by Hydromatik GmbH filed Critical Hydromatik GmbH
Publication of EP0301230A2 publication Critical patent/EP0301230A2/fr
Publication of EP0301230A3 publication Critical patent/EP0301230A3/de
Application granted granted Critical
Publication of EP0301230B1 publication Critical patent/EP0301230B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate

Definitions

  • the invention relates to a piston machine according to the preamble of claim 1.
  • Control valve arrangements with a valve ring and a valve seat in the form of an annular surface, on which a plurality of valve openings open are used, for example, in hydraulic power steering systems for motor vehicles.
  • FR-A-2193152 describes such a steering system, the control valve arrangement of which comprises two valve openings opening diametrically on the annular surface of a control body and a rigid, closed valve ring which loosely surrounds the control body and protects it from radial movements in order to close one and release the other Can perform valve opening; the valve ring lies against the control body or its ring surface with a comparatively small peripheral section in the region of the valve opening to be closed in each case.
  • the valve ring is fixed on the latter by means of a pin which is arranged offset by 90 ° with respect to both valve openings.
  • valve ring in this known control valve arrangement is not suitable for radial or axial piston machines because of its comparatively small circumferential section, which is available for contacting the control body, since more than two, generally seven to 9 valve openings each open out on the annular surfaces of their control valve arrangements each of which must be about half closed or open.
  • a valve ring is required, which with a correspondingly larger circumferential section can rest against the control body or its annular surface.
  • Such a Valve ring is known from DE-OS 3623797.
  • the valve ring surrounds the annular surface with radial movement play and it is made of a material, such as spring steel, which is not subject to any expansion deformation when the high pressure occurs and cannot be destroyed, for example pierced, by the high pressure due to the corresponding high strength.
  • the valve ring has a comparatively low bending stiffness, so that it can bend in its plane under the effect of the high pressure that occurs and consequently can assume different radii of curvature, with no stresses affecting the fatigue strength occurring.
  • valve openings due to high pressure will move the valve ring as a whole by releasing the valve openings to be opened by the amount of its radial play; then it is bent under the action of the high pressure in such a way that it conforms to the entire circumferential portion of the annular surface, on which the valve openings to be closed open and which is usually about 180 ° in axial piston machines.
  • the distance between the opposite circumferential section of the valve ring and the ring surface is increased somewhat, thereby creating the required flow cross section.
  • both the opening and the closing function of the valve ring are continuous, whereby it continuously lies against the ring surface in the circumferential direction and lifts again. There is no need to fix the valve ring in the circumferential direction, so that it can roll on the ring surface while avoiding wear.
  • the essential individual parts of the axial piston pump, generally designated 1 in FIG. 1, are a housing 4 consisting of a cup-shaped housing part 2 and a housing cover 3, a drive shaft 7 passing through the cup-shaped housing part 2 or the cavity 5 of the housing 4 along the central axis 6
  • a plurality, in the present case seven, of pistons 9 arranged on a pitch circle 8, correspondingly by means of a swash plate 11 arranged on the drive shaft 7 in a rotationally fixed manner dimensioned and assigned piston bores 12 of a cylinder block 13 arranged on the inside of the housing cover 3 are displaceable and generally designated 14 and 15 inlet and outlet valves for controlling the axial piston pump.
  • the swash plate 11 is mounted with its circumferential surface and with its end surface facing away from the cylinder block 13 in a radial and an axial slide bearing 16, 17.
  • the pistons 9 are held in contact with the slant surface 19 of the swash plate 11 by a retraction plate 18, the slant plate 11 being in contact through a ball head bearing 20 with a sleeve 21 arranged on the drive shaft 7, which - and thus also the retraction plate 18 - a spring 22 supported on the housing cover 3 is acted upon in the direction of the skew surface 19.
  • the pistons 9 have spherical piston heads with which they are mounted in an articulated but axially fixed manner in sliding shoes 23 which slide on the inclined surface 19.
  • the inlet valves 14 are formed by a channel connection running inside the piston 9 and emerging radially at a specific point on the piston jacket 24.
  • the arrangement is such that this point, designated 25, is exposed in the retracted position of the respective piston 9 to the cavity 5 of the housing 4, but is covered by the wall of the associated piston bore 12 in the advanced position of the respective piston 9.
  • the distance a of this point 25 from the edge 26 of the associated piston bore 12 in the retracted position of the piston 9 is to be adapted to the functional requirements of the axial piston pump 1 and is approximately 2 mm in the present exemplary embodiment.
  • the piston bore 12 is filled by negative pressure from the cavity 5 of the housing 4, which is filled with fluid during operation.
  • pistons 9 with a bore 27 (hollow piston) extending from their end face are used.
  • the opening to the cavity 5 is formed by at least one, preferably four radial bores 28.
  • the exhaust valves 15 have a common valve ring 31, which is arranged with radial movement play S 1 and lateral movement play S 2 in an annular groove 32 which, in the present exemplary embodiment, surrounds all existing piston bores 12 and - seen radially - is arranged in the region of the inner ends of the piston bores 12 .
  • the outlet valves 15 are further formed by delivery channels 33 with valve openings 34, starting from the piston bores 12 and opening radially into an annular groove 32, the diameter d of which is smaller than the width b of the valve ring 31.
  • a further delivery channel 35 extends radially outward from the annular groove 32 from which opens into a radial connection 36 for a delivery line, not shown.
  • the cylinder block 13 protrudes by the dimension denoted by c into the cylindrical section 37 of the cup-shaped housing 2, an annular body 41 being inserted between the outer lateral surface 38 of the cylinder block 13 and the cylindrical inner lateral surface 39 of the section 37 (see distance B) is axially fixed at its end facing the swash plate 11 to a shoulder 42 of the housing part 2 and at its other end to a shoulder 43 of the cylinder block 13, and the ring channel 32 limited on its side facing the swash plate 11.
  • the ring channel 32 is delimited by the housing cover 3 or its flange-shaped extension. The housing cover 3 is thus centered indirectly via the ring body 41 in the cylindrical recess of the housing part 2.
  • the ring body 41 fits with a fine fit on the cylinder block 13 and in the housing part 2.
  • O-rings 40 can be provided in ring grooves between the ring body 41 and adjoining parts (housing part 2) and the housing part 2 and the housing cover 3.
  • the housing cover 3 is fastened to the housing part 2 by screws 44.
  • the fluid is sucked through an indicated suction line, which can be connected to a radial line connection 45, and a flow channel 46, which connects to the line connection 45, into the cavity 5 of the housing 4 and further into the piston bores 12 as described above.
  • the pistons 9 are fed, in which essentially half of the number of pistons 9 present, in the present exemplary embodiment seven, participates, the fluid flows out of the piston bores 12 in the direction of the flow arrows designated 47 in FIG. 2 into the annular channel 32 and further pushed laterally through the gaps 48 between the valve ring 31 and the radial walls of the ring channel 32 past the valve ring 31, the fluid passing through the delivery channel 34 to the indicated delivery line.
  • the existing valve openings 34 are each opened or closed by a radial displacement of the valve ring 31, as can best be seen in FIG. 2.
  • the valve ring 31 is due to the the flow pressure of the fluid exiting through the valve openings 34 automatically moves him into the position in which he opens the valve openings 34 discharging the pressurized fluid (left side).
  • the diametrically opposed valve openings 34 (right side) are closed at the same time, the negative pressure contained in the associated piston bores 12 and possibly the pressure on this side of the valve ring 31, the tight contact of the valve ring 31 on the annular surface containing the valve openings 34 49 of the ring channel 32 causes.
  • the valve ring 31 is able to contact the ring surface 49 of the ring channel 32 by approximately 180 °, ie to deform or bend in such a way that it consists of a flexible, preferably elastically flexible material such as metal or plastic.
  • the size of the movement s1, s2 or column depends on the throughput or delivery volume of the axial piston pump 1. The arrangement must be such that the fluid can be conveyed out of the piston bores 12 without significant throttling losses.
  • the size of the movement s1, s2 or column 48 is thus also dependent on the number of pistons 9, because with a larger number of pistons 9, the delivery volume is also larger.
  • the movement play s 1, s 2 or the column 48 can be dimensioned relatively small.
  • the size of the movement s1, s2 or gap widths depend on the throughput or delivery volume of the axial piston machine 1. With a diameter of the valve ring 31 of about 50 mm, about 0.3 to 1 mm should be aimed for. In experiments, good results were achieved with a movement clearance or a gap width of approximately 0.5 mm. This makes it clear that the Elasticity of the valve ring can be relatively low.
  • the embodiment according to the invention can also be used for piston machines with an adjustable throughput quantity, since the above-described relationship allows deviations of certain sizes.
  • valve arrangement according to the invention in contrast to the previously described valve ring 31 as an outer ring, it is also possible to design the valve arrangement according to the invention with a valve ring as an inner ring.
  • configuration according to the invention can also be implemented on a radial piston machine (pump).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Claims (9)

1. Machine à pistons axiaux ou radiaux avec un bloc à cylindres qui présente plusieurs cylindres à pistons dans chacun desquels un piston est guidé de manière coulissante et qui débouchent par des ouvertures de soupapes sur une surface annulaire qui coopère, en tant que siège de soupapes, pour un agencement de soupapes de commande, avec une bague de soupapes fermée sur elle-même, caractérisée en ce qu'il est prévu entre la surface annulaire (49) et la bague de soupapes (31) un jeu (S₁) de mouvement radial, et en ce que la bague de soupapes (31) présente une rigidité à la flexion telle que, sous l'effet de la pression hydraulique régnant dans au moins une ouverture de soupape (34), elle s'applique étroitement, sans déformation par allongement, contre la surface annulaire (49) dans la région de celle-ci contenant les autres ouvertures de soupapes (34) destinées à être fermées.
2. Machine à pistons selon la revendication 1, caractérisée en ce que la bague de soupapes (31) est flexible élastiquement.
3. Machine à pistons selon la revendication 1 ou 2, caractérisée en ce que la bague de soupapes (31) est constituée de métal, en particulier d'acier, ou de matière plastique.
4. Machine à pistons selon une des revendications 1 à 3, caractérisée en ce que le canal annulaire (32) est disposé dans la région des extrémités intérieures des cylindres à pistons (12), de préférence radialement à l'extérieur des cylindres à pistons (12).
5. Machine à pistons selon une des revendications 1 à 4, caractérisée en ce que, dans le cas d'une machine à pistons axiaux, le canal annulaire (32) est disposé entre un bloc à cylindres (13) fixé au boîtier et contenant les cylindres(12) à pistons et une paroi (37) du boîtier (4) entourant ce dernier.
6. Machine à pistons selon la revendication 5, caractérisée en ce qu'un corps annulaire (41) est interposé entre la surface extérieure de la jupe (38) du bloc à cylindres (13) et la paroi (37), ce corps annulaire délimitant axialement le canal annulaire (32).
7. Machine à pistons selon la revendication 6, caractérisée en ce que le corps annulaire (41) est fixé axialement entre un épaulement (42) sur la paroi (37) du boîtier (4) et un épaulement (43) sur le bloc à cylindres (13).
8. Machine à pistons selon une des revendications 5 à 7, caractérisée en ce que le bloc à cylindres (13) est disposé sur le côté intérieur d'un couvercle de boîtier (3) en forme de flasque délimitant axialement le canal annulaire (32), en étant de préférence fait d'une seule pièce avec ce couvercle.
9. Machine à pistons selon une des revendications 1 à 8, caractérisée en ce qu'un canal de refoulement radial (46) va du canal annulaire (32) jusqu'à un raccord (36) pour une conduite qui est de préférence radial.
EP88109856A 1987-07-28 1988-06-21 Machine à pistons radiaux ou axiaux avec un aménagement des soupapes comprenant une bague de soupapes Expired - Lifetime EP0301230B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3724967 1987-07-28
DE19873724967 DE3724967A1 (de) 1987-07-28 1987-07-28 Axial- oder radialkolbenmaschine mit einer einen ventilring aufweisenden steuerventilanordnung

Publications (3)

Publication Number Publication Date
EP0301230A2 EP0301230A2 (fr) 1989-02-01
EP0301230A3 EP0301230A3 (en) 1989-09-06
EP0301230B1 true EP0301230B1 (fr) 1991-09-25

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ID=6332528

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88109856A Expired - Lifetime EP0301230B1 (fr) 1987-07-28 1988-06-21 Machine à pistons radiaux ou axiaux avec un aménagement des soupapes comprenant une bague de soupapes

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EP (1) EP0301230B1 (fr)
DE (2) DE3724967A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3841382C1 (fr) * 1988-12-08 1990-03-15 Hydromatik Gmbh, 7915 Elchingen, De
DE4238376A1 (de) * 1992-11-13 1993-12-02 Bosch Gmbh Robert Kolbenpumpe
DE19740436A1 (de) 1997-09-15 1999-03-18 Schaeffler Waelzlager Ohg Taumellager
DE102005060957B4 (de) * 2005-12-20 2012-08-23 Industriehansa Consulting & Engineering Gmbh Hochdruckpumpe mit mehreren Kolben pro Zylinder

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB541295A (en) * 1940-02-09 1941-11-20 Browett Lindley 1931 Ltd J Improvements in and relating to air compressors
GB1431437A (en) * 1972-07-19 1976-04-07 Bendix Westinghouse Ltd Power assistance control device
DE3623797A1 (de) * 1985-07-24 1987-03-19 Barmag Barmer Maschf Radialkolbenpumpe

Also Published As

Publication number Publication date
DE3724967A1 (de) 1989-02-09
EP0301230A2 (fr) 1989-02-01
EP0301230A3 (en) 1989-09-06
DE3865140D1 (de) 1991-10-31

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