EP0567736B1 - Hydrostatic motor with a braking device - Google Patents

Hydrostatic motor with a braking device Download PDF

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Publication number
EP0567736B1
EP0567736B1 EP93103001A EP93103001A EP0567736B1 EP 0567736 B1 EP0567736 B1 EP 0567736B1 EP 93103001 A EP93103001 A EP 93103001A EP 93103001 A EP93103001 A EP 93103001A EP 0567736 B1 EP0567736 B1 EP 0567736B1
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EP
European Patent Office
Prior art keywords
brake
pressure
hydrostatic motor
motor according
housing
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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
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EP93103001A
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German (de)
French (fr)
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EP0567736A1 (en
Inventor
Rainer Stoelzer
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Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control

Definitions

  • the invention relates to a hydrostatic motor with a braking device according to the preamble of claim 1.
  • Hydrostatic motors of this type are used in particular as so-called plug-in motors for installation in, for example, wheel hubs of vehicle drive wheels.
  • a further reduction in the axial length of the hydrostatic motor can be achieved by arranging the compression spring in an axial material bore in the pressure element.
  • the length of the compression spring in the tensioned state when the brake is released is essentially equal to the length dimension of the axial blind bore.
  • one of the two brake surfaces can be formed, for example, on the housing and the other on a brake disk axially displaceably fastened to the rotor, two brake disks are provided according to a development of the invention, the surfaces of which face one another are the brake surfaces.
  • the hydrostatic motor shown schematically in FIG. 1 is intended for installation in the hub of a wheel for the purpose of driving the same and is designed as an axial piston motor in a swashplate construction with a constant displacement volume. It comprises in a conventional manner a substantially cylindrical and one-sided open housing 1, a connecting plate 2 with a suction and a pressure connection (both not shown) which can be releasably closed off the open end of the same, one by means of cones 3, 4 in the housing 1 and in the Connection plate 2 rotatably mounted output shaft 5, a rotatably arranged on this rotor in the form of a cylinder drum 6, which is supported on a control plate attached to the connection plate 2 (not shown), a swash plate 7 attached to the control disc on the housing 1 and a braking device to be described 8.
  • An annular space 9 is formed between housing 1 and cylinder drum 6.
  • axially extending and evenly distributed over the circumference cylindrical bores 10 are formed in a known manner, which open via cylinder channels 11 on the end face of the cylinder drum 6 facing the control disc.
  • two diametrically opposed control kidneys are formed in a known manner, which produce the connection between the cylinder channels 11 and the suction and the pressure connection when the cylinder drum 6 rotates.
  • Pistons 12, which are displaceably guided in the cylinder bores 10, are supported with their piston ends opposite the cylinder channels 11 by sliding shoes 13 on the swash plate 7.
  • the housing 1 is provided at its open end facing the connection plate 2 with a circumferential, radially outwardly extending housing flange part 14, in which the annular space 9 is expanded radially outwards.
  • the enlarged annulus area formed in this way is over a encircling radial shoulder 15 formed on the housing 1 is connected to the remaining annular area and is stepped twice by a second radial shoulder 16 and a third radial shoulder 17 and thereby divided into three areas of different outside diameters; the largest outside diameter area opens out on the end face of the housing 1 facing the connection plate 2.
  • the braking device 8 is arranged in the enlarged annulus area. It comprises a brake disk package consisting of a first and a second, each annular brake disk 18 or 19, an annular pressure element 20, a plurality of compression springs 21 and a pressure line 22 for a hydraulic pressure medium.
  • the first and the second brake disks 18, 19 are by means of nose-shaped projections 23 (see FIG. 2) and 24 (see FIG. 1), each with an axial toothing in the housing inner wall 25 or the outer surface of the cylinder drum 6 in the area between the first and second shoulder 15, 16 axially displaceable and rotatably arranged. Only the toothing for the first brake disk 18, which is formed in the housing inner wall 25 and is designated by the reference numeral 26, is shown (see FIG. 2).
  • the second brake disk 19 faces the first shoulder 15 and is supported by the latter during the brake intervention with the first brake disk 18, which is still to be described.
  • the first shoulder 15 and the surface of the first brake disk 19 facing it are essentially free of friction.
  • the pressure element 20 is in the expanded annular space on the housing 1 rotatably and axially displaceable with the stroke A and for this purpose has an axial dimension which is correspondingly smaller than the axial distance between the end face of the housing 1 or the connecting plate 2 and the first Shoulder 15 minus the axial dimensions of both brake disks 18,19.
  • the pressure element 20 also has in its outer lateral surface a circumferential, radially extending step 27, which is assigned to the third shoulder 17 and is axially spaced from it in every axial position of the pressure element 20. In this way, the third shoulder 17 and the step 27 define an annular first pressure space 28.
  • the stage 27 divides the pressure element 20 into a section of smaller and a section of larger outside diameter.
  • the latter section is guided on the housing inner wall 25 in the region between the shoulder 17 and the end face of the housing 1 during the axial displacement of the pressure element 20.
  • An annular seal 29 is arranged in a circumferential groove in the outer circumferential surface of the pressure element 20.
  • the smaller outside diameter of the pressure element 20 is somewhat smaller than the outside diameter of the annular space area between the first and second shoulders 15, 16.
  • the axially extending annular gap 30 formed in this way between the housing inner wall 25 in the region between the second and third shoulders 16, 17 and the pressure element section of smaller outer diameter represents a second pressure chamber which is in communication with the first pressure chamber 28 and with it forms a common pressure chamber 28,30.
  • An annular body 32 with play and an annular seal 31 are arranged in the annular gap 30. The latter partially protrudes into the pressure chamber 28 and is supported via the ring body 32 on the second shoulder 16 serving as an abutment.
  • the compression springs 21 are designed as cylindrical helical springs and are integrated in the pressure element 20; for this purpose they are inserted in axially extending blind bores 33 in the pressure element 20 and are supported with a prestress on the connection plate 2; their length when the brake disks 18, 19 have been released from the brake (see FIG. 4) is equal to the length dimension of the axial blind bores 33.
  • the latter are arranged at equal mutual distances on a pitch circle.
  • the pressure line 22 is formed in the area between two adjacent axial blind bores 33 as a through bore which runs axially through the pressure element 20 and opens out at the step 27.
  • a connecting line 34 running axially through the connecting plate 2 (see FIG. 1) is aligned with the pressure line 22.
  • the mutually facing end regions of both lines 22, 34 have a larger diameter than the remaining line regions and are connected to them via a circumferential, radial shoulder connected. Only the one located in the pressure line 22 with the Paragraph designated 35 is shown (see FIG. 2).
  • a lock-up clutch 36 is inserted with play into the line end regions of larger diameter and establishes a connection between the two lines 22, 34.
  • the lock-up clutch 36 is shorter by the dimension B than the two line sections of larger diameter.
  • the dimension B is somewhat larger than the stroke A of the pressure element 20.
  • the connecting line is connected in a manner not shown to the pressure medium circuit of the hydrostatic motor or a pressure medium line connected to it.
  • the function of the above-described hydrostatic motor is described below with reference to the braking device according to the invention:
  • the compression springs 21 constantly press the pressure element 20 in the direction of the brake disc package 18, 19.
  • the pressure element 20 is in the (left) braking position shown in FIGS. 2 and 3, in which it presses the two brake disks 18, 19 against the first shoulder 15 serving as support and thus holding each other in braking.
  • the pressure element 20 is arranged at a distance B corresponding to the stroke A from the connection plate 2 and the bridging bush 36 from the shoulder 35 in the pressure line 22.
  • the compression springs 21 move the pressure element 20 back into the braking position shown in FIGS Shoulder 15 are supported. Because of its rotationally fixed arrangement on the housing 1, the first brake disk 18 is at rest relative to the pressure element 20 even when the cylinder drum 6 is rotating, so that the latter does not absorb any braking torque when the cylinder drum 6 is braked.
  • the pressure chamber 28, 30 can be supplied with hydraulic pressure medium via more than one pressure line 22. Furthermore, it is possible to arrange the second brake disk 19 on the housing 1 in a manner fixed against relative rotation and optionally axially immovable; in this case, the first brake disk 18 is to be fastened to the cylinder drum 6 in an axially displaceable manner. Instead of a loosely inserted ring body 32, it is possible to design the same as part of the housing 1. With a sufficiently stable design of the second brake disc 19, the first shoulder 15 can be omitted. It is also conceivable to design the brake disc package with more than two brake discs.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)
  • Hydraulic Motors (AREA)

Description

Die Erfindung betrifft einen hydrostatischen Motor mit einer Bremseinrichtung nach dem Oberbegriff des Patentanspruches 1. Hydrostatische Motoren dieser Art werden insbesondere als sogenannte Einschubmotoren für den Einbau in beispielsweise Radnaben von Fahrzeug-Antriebsrädern verwendet.The invention relates to a hydrostatic motor with a braking device according to the preamble of claim 1. Hydrostatic motors of this type are used in particular as so-called plug-in motors for installation in, for example, wheel hubs of vehicle drive wheels.

Aus der FR-A-2 143 079 und der DE-OS 29 31 641 ist ein solcher hydrostatischer Motor mit einer Bremseinrichtung bekannt, deren Druckleitung gemäß der erstgenannten Druckschrift in axialer Richtung des Motors und gemäß der letztgenannten Druckschrift unter einem Winkel sowohl zur axialen als auch zur radialen Richtung schräg durch das Gehäuse nach außerhalb desselben verläuft. Dieser schräge Verlauf der Druckleitung ist insofern nachteilig, als die nutzbare radiale Abmessung, d.h. der nutzbare Außendurchmesser des bekannten hydrostatischen Motors um das für den hydraulischen Anschluß an die Druckleitung erforderliche Maß größer als der tatsächliche Außendurchmesser ist. Möglichst geringe nutzbare Abmessungen sowohl in axialer als auch in radialer Richtung sind jedoch mit die wichtigsten Anforderungen an einen zur Verwendung als Einschubmotor vorgesehenen hydrostatischen Motor.From FR-A-2 143 079 and DE-OS 29 31 641 such a hydrostatic motor with a braking device is known, the pressure line according to the first-mentioned document in the axial direction of the motor and according to the latter document at an angle to both the axial and also extends obliquely to the radial direction through the housing outside of the same. This oblique course of the pressure line is disadvantageous in that the usable radial dimension, i.e. the usable outside diameter of the known hydrostatic motor is larger than the actual outside diameter by the amount required for the hydraulic connection to the pressure line. However, the smallest possible usable dimensions in both the axial and radial directions are one of the most important requirements for a hydrostatic motor intended for use as a plug-in motor.

Es ist daher Aufgabe der Erfindung, einen hydrostatischen Motor der eingangs genannten Art so weiterzubilden, daß er zumindest in Radialrichtung geringere nutzbare Abmessungen aufweist.It is therefore an object of the invention to develop a hydrostatic motor of the type mentioned at the outset such that it has smaller usable dimensions, at least in the radial direction.

Diese Aufgabe wird durch die kennzeichnenden Merkmale des Patentanspruches 1 gelöst. Aufgrund des axialen Verlaufs der Druckleitung durch das Druckelement ist der nutzbare Außendurchmesser des hydrostatischen Motors verringert; er entspricht nun dessen tatsächlichem Außendurchmesser. Im Gegensatz zu dem im Stand der Technik über nahezu seine gesamte axiale Länge am Gehäuse geführten Druckelement bietet die Kombination des Ringspaltes und des relativ zum Druckelement beweglichen und somit entweder lose in den Ringspalt eingesetzten oder als Teil des Gehäuses ausgebildeten Ringkörpers die Möglichkeit, den Außendurchmesser des Druckelementes und damit die radiale Abmessung des hydrostatischen Motors maximal um die doppelte Breite des Ringspaltes - bei gleichbleibender Größe der Druckfläche - zu verringern und/oder die für die hydraulische Beaufschlagung zur Verfügung stehende Druckfläche maximal um die Ringfläche des Ringspaltes zu vergrößern. Mit der entsprechend größeren, auf das Druckelement wirkenden Kraft des hydraulischen Druckmittels kann zwecks Lösung des Bremseingriffs der Bremsflächen die Federkraft einer stärkeren Druckfeder überwunden werden, die erforderlich ist, um mit der geringstmöglichen Anzahl von zwei Bremsflächen die gleiche Bremskraft wie mit den aus dem Stand der Technik bekannten Bremseinrichtungen zu erzielen, die eine größere Anzahl von beispielsweise 10 Bremsflächen verwenden. Auf diese Weise wird die axiale Baulänge des hydrostatischen Motors entsprechend der Differenz zwischen der größeren und der geringstmöglichen Anzahl von Bremsflächen reduziert.This object is achieved by the characterizing features of patent claim 1. Due to the axial course of the pressure line through the pressure element, the usable outer diameter of the hydrostatic motor is reduced; it now corresponds to its actual outside diameter. In contrast to the pressure element guided on the housing over almost its entire axial length in the prior art, the combination of the annular gap and the annular body which is movable relative to the pressure element and thus either inserted loosely into the annular gap or formed as part of the housing offers the possibility of determining the outer diameter of the Pressure element and thus the radial dimension of the hydrostatic motor by a maximum of twice the width of the annular gap - with the same size of the pressure area - and / or to reduce the pressure area available for hydraulic loading by a maximum of the ring area of the annular gap. With the correspondingly larger force of the hydraulic pressure medium acting on the pressure element can be overcome in order to solve the braking intervention of the braking surfaces, the spring force of a stronger compression spring, which is required to achieve the same braking force with the smallest possible number of two braking surfaces as with those known from the prior art To achieve braking devices that use a larger number of 10 braking surfaces, for example. In this way, the axial length of the hydrostatic motor is reduced according to the difference between the larger and the smallest possible number of braking surfaces.

Eine weitere Reduzierung der axialen Baulänge des hydrostatischen Motors kann durch Anordnung der Druckfeder in einer axialen Sachbohrung im Druckelement erreicht werden. Im Sinne weiterer Reduzierung der axialen Baulänge ist es hierbei vorteilhaft, wenn die Länge der Druckfeder im gespannten Zustand bei gelöstem Bremseingriff im wesentlichen gleich der Längenabmessung der axialen Sackbohrung ist.A further reduction in the axial length of the hydrostatic motor can be achieved by arranging the compression spring in an axial material bore in the pressure element. In the sense of a further reduction in the axial overall length, it is advantageous here if the length of the compression spring in the tensioned state when the brake is released is essentially equal to the length dimension of the axial blind bore.

Obwohl eine der beiden Bremsflächen beispielsweise am Gehäuse und die andere an einer am Rotor axial verschiebbar befestigten Bremsscheibe ausgebildet sein können, sind gemäß einer Weiterbildung der Erfindung zwei Bremsscheiben vorgesehen, deren einander zugewandten Flächen die Bremsflächen sind.Although one of the two brake surfaces can be formed, for example, on the housing and the other on a brake disk axially displaceably fastened to the rotor, two brake disks are provided according to a development of the invention, the surfaces of which face one another are the brake surfaces.

Bei höherem Druck des hydraulischen Druckmittels ist es vorteilhaft, eine Dichtung im Ringspalt anzuordnen, um einen Druckverlust im Druckraum durch Leckage zu den Bremsflächen hin zu vermeiden.At higher pressure of the hydraulic pressure medium, it is advantageous to arrange a seal in the annular gap in order to avoid a pressure loss in the pressure chamber due to leakage to the braking surfaces.

Nachstehend ist die Erfindung anhand eines bevorzugten Ausführungsbeispiels unter Bezugnahme auf die Zeichnung näher beschrieben. Es zeigen:

Fig. 1
einen Axialschnitt eines hydrostatischen Motors gemäß dem bevorzugten Ausführungsbeispiel der Erfindung mit einer im Bremseingriff befindlichen Bremseinrichtung,
Fig. 2
eine vergrößerte Darstellung des in Figur 1 mit A bezeichneten Ausschnitts,
Fig. 3
eine vergrößerte Darstellung des in Figur 1 mit B bezeichneten Ausschnitts, und
Fig. 4
der Ausschnitt B mit außer Bremseingriff befindlicher Bremseinrichtung.
The invention is described in more detail below on the basis of a preferred exemplary embodiment with reference to the drawing. Show it:
Fig. 1
3 shows an axial section of a hydrostatic motor according to the preferred exemplary embodiment of the invention with a braking device in braking engagement,
Fig. 2
2 shows an enlarged illustration of the detail designated by A in FIG. 1,
Fig. 3
an enlarged view of the section designated by B in Figure 1, and
Fig. 4
the section B with the brake device out of brake engagement.

Der in Figur 1 schematisch dargestellte hydrostatische Motor ist für den Einbau in die Nabe eines Rades zwecks Antrieb desselben vorgesehen und als ein Axialkolbenmotor in Schrägscheibenbauweise mit konstantem Schluckvolumen ausgebildet. Er umfaßt in herkömmlicher Weise ein im wesentlichen zylindrisches und einseitig offenes Gehäuse 1, eine das offene Ende desselben lösbar verschließende Anschlußplatte 2 mit einem Saug- und einem Druckanschluß (beide nicht gezeigt), eine mittels Kegel lagern 3, 4 im Gehäuse 1 und in der Anschlußplatte 2 drehgelagerte Abtriebswelle 5, einen drehfest auf dieser angeordneten Rotor in Form einer Zylindertrommel 6, die an einer an der Anschlußplatte 2 befestigten Steuerscheibe (nicht gezeigt) abgestützt ist, eine gegenüber der Steuerscheibe am Gehäuse 1 befestigte Schrägscheibe 7 sowie eine noch zu beschreibende Bremseinrichtung 8. Zwischen Gehäuse 1 und Zylindertrommel 6 ist ein Ringraum 9 ausgebildet.The hydrostatic motor shown schematically in FIG. 1 is intended for installation in the hub of a wheel for the purpose of driving the same and is designed as an axial piston motor in a swashplate construction with a constant displacement volume. It comprises in a conventional manner a substantially cylindrical and one-sided open housing 1, a connecting plate 2 with a suction and a pressure connection (both not shown) which can be releasably closed off the open end of the same, one by means of cones 3, 4 in the housing 1 and in the Connection plate 2 rotatably mounted output shaft 5, a rotatably arranged on this rotor in the form of a cylinder drum 6, which is supported on a control plate attached to the connection plate 2 (not shown), a swash plate 7 attached to the control disc on the housing 1 and a braking device to be described 8. An annular space 9 is formed between housing 1 and cylinder drum 6.

In der Zylindertrommel 6 sind in bekannter Weise axial verlaufende und gleichmäßig über den Umfang verteilte Zylinderbohrungen 10 ausgebildet, die über Zylinderkanäle 11 an der der Steuerscheibe zugewandten Stirnfläche der Zylindertrommel 6 ausmünden. In der Steuerscheibe sind in bekannter Weise zwei diametral gegenüberliegende Steuernieren ausgebildet, die bei Drehung der Zylindertrommel 6 die Verbindung zwischen den Zylinderkanälen 11 und dem Saug- bzw. dem Druckanschluß herstellen. In den Zylinderbohrungen 10 verschiebbar geführte Kolben 12 stützen sich mit ihren den Zylinderkanälen 11 gegenüberliegenden Kolbenenden über Gleitschuhe 13 an der Schrägscheibe 7 ab.In the cylinder drum 6 axially extending and evenly distributed over the circumference cylindrical bores 10 are formed in a known manner, which open via cylinder channels 11 on the end face of the cylinder drum 6 facing the control disc. In the control disk, two diametrically opposed control kidneys are formed in a known manner, which produce the connection between the cylinder channels 11 and the suction and the pressure connection when the cylinder drum 6 rotates. Pistons 12, which are displaceably guided in the cylinder bores 10, are supported with their piston ends opposite the cylinder channels 11 by sliding shoes 13 on the swash plate 7.

Das Gehäuse 1 ist an seinem offenen, der Anschlußplatte 2 zugewandten Ende mit einem umlaufenden, sich radial nach außen erstreckenden Gehäuseflanschteil 14 versehen, in welchem der Ringraum 9 radial nach außen erweitert ist. Der auf diese Weise ausgebildete erweiterte Ringraumbereich ist über eine umlaufende, am Gehäuse 1 ausgebildete radiale Schulter 15 mit dem verbleibenden Ringraumbereich verbunden und durch eine zweite radiale Schulter 16 sowie eine dritte radiale Schulter 17 zweifach abgestuft und dadurch in drei Bereiche unterschiedlicher Außendurchmesser unterteilt; der größte Außendurchmesserbereich mündet an der der Anschlußplatte 2 zugewandten Stirnfläche des Gehäuses 1 aus.The housing 1 is provided at its open end facing the connection plate 2 with a circumferential, radially outwardly extending housing flange part 14, in which the annular space 9 is expanded radially outwards. The enlarged annulus area formed in this way is over a encircling radial shoulder 15 formed on the housing 1 is connected to the remaining annular area and is stepped twice by a second radial shoulder 16 and a third radial shoulder 17 and thereby divided into three areas of different outside diameters; the largest outside diameter area opens out on the end face of the housing 1 facing the connection plate 2.

Die Bremseinrichtung 8 ist im erweiterten Ringraumbereich angeordnet. Sie umfaßt ein Bremsscheiben-Paket bestehend aus einer ersten und einer zweiten, jeweils ringförmigen Bremsscheibe 18 bzw. 19, ein ringförmiges Druckelement 20, mehrere Druckfedern 21 und eine Druckleitung 22 für ein hydraulisches Druckmittel.The braking device 8 is arranged in the enlarged annulus area. It comprises a brake disk package consisting of a first and a second, each annular brake disk 18 or 19, an annular pressure element 20, a plurality of compression springs 21 and a pressure line 22 for a hydraulic pressure medium.

Die erste und die zweite Bremsscheibe 18,19 sind mittels nasenförmiger Ansätze 23 (siehe Fig. 2) bzw. 24 (siehe Fig. 1) in je einer axialen Verzahnung in der Gehäuseinnenwand 25 bzw. der Mantelfläche der Zylindertrommel 6 im Bereich zwischen der ersten und zweiten Schulter 15,16 axial verschiebbar und drehfest angeordnet. Lediglich die mit dem Bezugszeichen 26 bezeichnete, in der Gehäuseinnenwand 25 ausgebildete Verzahnung für die erste Bremsscheibe 18 ist dargestellt (siehe Figur 2). Die zweite Bremsscheibe 19 ist der ersten Schulter 15 zugewandt und wird von dieser während des noch zu beschreibenden Bremseingriffs mit der ersten Bremsscheibe 18 abgestützt. Die erste Schulter 15 und die ihr zugewandte Fläche der ersten Bremsscheibe 19 sind im wesentlichen reibungsfrei.The first and the second brake disks 18, 19 are by means of nose-shaped projections 23 (see FIG. 2) and 24 (see FIG. 1), each with an axial toothing in the housing inner wall 25 or the outer surface of the cylinder drum 6 in the area between the first and second shoulder 15, 16 axially displaceable and rotatably arranged. Only the toothing for the first brake disk 18, which is formed in the housing inner wall 25 and is designated by the reference numeral 26, is shown (see FIG. 2). The second brake disk 19 faces the first shoulder 15 and is supported by the latter during the brake intervention with the first brake disk 18, which is still to be described. The first shoulder 15 and the surface of the first brake disk 19 facing it are essentially free of friction.

Das Druckelement 20 ist im erweiterten Ringraumbereich am Gehäuse 1 drehfest und mit dem Hub A axial verschiebbar angeordnet und weist zu diesem Zweck eine axiale Abmessung auf, die entsprechend geringer als der axiale Abstand zwischen der Stirnfläche des Gehäuses 1 bzw. der Anschlußplatte 2 und der ersten Schulter 15 minus der axialen Abmessungen beider Bremsscheiben 18,19 ist. Das Druckelement 20 weist ferner in seiner äußeren Mantelfläche eine umlaufende, sich radial erstreckende Stufe 27 auf, die der dritten Schulter 17 zugeordnet ist und dieser gegenüber bei jeder axialen Stellung des Druckelementes 20 einen axialen Abstand aufweist. Die dritte Schulter 17 und die Stufe 27 definieren auf diese Weise einen ringförmigen ersten Druckraum 28. Die Stufe 27 unterteilt das Druckelement 20 in einen Abschnitt kleineren und einen Abschnitt größeren Außendurchmessers. Letzterer Abschnitt ist während der axialen Verschiebung des Druckelementes 20 an der Gehäuseinnenwand 25 im Bereich zwischen der Schulter 17 und der Stirnfläche des Gehäuses 1 geführt. Eine ringförmige Dichtung 29 ist in einer umlaufenden Nut in der äußeren Mantelfläche des Druckelementes 20 angeordnet.The pressure element 20 is in the expanded annular space on the housing 1 rotatably and axially displaceable with the stroke A and for this purpose has an axial dimension which is correspondingly smaller than the axial distance between the end face of the housing 1 or the connecting plate 2 and the first Shoulder 15 minus the axial dimensions of both brake disks 18,19. The pressure element 20 also has in its outer lateral surface a circumferential, radially extending step 27, which is assigned to the third shoulder 17 and is axially spaced from it in every axial position of the pressure element 20. In this way, the third shoulder 17 and the step 27 define an annular first pressure space 28. The stage 27 divides the pressure element 20 into a section of smaller and a section of larger outside diameter. The latter section is guided on the housing inner wall 25 in the region between the shoulder 17 and the end face of the housing 1 during the axial displacement of the pressure element 20. An annular seal 29 is arranged in a circumferential groove in the outer circumferential surface of the pressure element 20.

Der kleinere Außendurchmesser des Druckelementes 20 ist etwas geringer als der Außendurchmesser des Ringraumbereichs zwischen der ersten und zweiten Schulter 15,16. Der auf diese Weise gebildete, axial verlaufende Ringspalt 30 zwischen der Gehäuseinnenwand 25 im Bereich zwischen der zweiten und dritten Schulter 16,17 sowie dem Druckelement-Abschnitt kleineren Außendurchmessers stellt einen zweiten Druckraum dar, der mit dem ersten Druckraum 28 in Verbindung steht und mit diesem einen gemeinsamen Druckraum 28,30 bildet. Im Ringspalt 30 sind ein Ringkörper 32 mit Spiel sowie eine Ringdichtung 31 angeordnet. Letztere ragt teilweise in den Druckraum 28 hinein und stützt sich über den Ringkörper 32 an der als Widerlager dienenden zweiten Schulter 16 ab.The smaller outside diameter of the pressure element 20 is somewhat smaller than the outside diameter of the annular space area between the first and second shoulders 15, 16. The axially extending annular gap 30 formed in this way between the housing inner wall 25 in the region between the second and third shoulders 16, 17 and the pressure element section of smaller outer diameter represents a second pressure chamber which is in communication with the first pressure chamber 28 and with it forms a common pressure chamber 28,30. An annular body 32 with play and an annular seal 31 are arranged in the annular gap 30. The latter partially protrudes into the pressure chamber 28 and is supported via the ring body 32 on the second shoulder 16 serving as an abutment.

Die Druckfedern 21 sind als zylindrische Schraubenfedern ausgebildet und in das Druckelement 20 integriert; sie sind zu diesem Zweck in axial verlaufenden Sackbohrungen 33 im Druckelement 20 eingesetzt und mit Vorspannung an der Anschlußplatte 2 abgestützt; ihre Länge bei gelöstem Bremseingriff der Bremsscheiben 18,19 (siehe Figur 4) ist gleich der Längenabmessung der axialen Sackbohrungen 33. Letztere sind mit gleichen gegenseitigen Abständen auf einem Teilkreis angeordnet.The compression springs 21 are designed as cylindrical helical springs and are integrated in the pressure element 20; for this purpose they are inserted in axially extending blind bores 33 in the pressure element 20 and are supported with a prestress on the connection plate 2; their length when the brake disks 18, 19 have been released from the brake (see FIG. 4) is equal to the length dimension of the axial blind bores 33. The latter are arranged at equal mutual distances on a pitch circle.

Die Druckleitung 22 ist im Bereich zwischen zwei benachbarten axialen Sackbohrungen 33 als axial durch das Druckelement 20 verlaufende, an der Stufe 27 ausmündende Durchgangsbohrung ausgebildet. Eine axial durch die Anschlußplatte 2 verlaufende Anschlußleitung 34 (siehe Fig. 1) fluchtet mit der Druckleitung 22. Die einander zugewandten Endbereiche beider Leitungen 22,34 weisen einen größeren Durchmesser als die verbleibenden Leitungsbereiche auf und sind mit diesen über je einen umlaufenden, radialen Absatz verbunden. Lediglich der in der Druckleitung 22 befindliche, mit dem Bezugszeichen 35 bezeichnete Absatz ist dargestellt (siehe Fig. 2). Eine Überbrückungskupplung 36 ist mit Spiel in die Leitungsendbereiche größerer Durchmesser eingesetzt und stellt eine Verbindung zwischen beiden Leitungen 22,34 her. Zu diesem Zweck ist die Überbrückungskupplung 36 um das Maß B kürzer als die beiden Leitungsabschnitte größeren Durchmessers. Das Maß B ist etwas größer als der Hub A des Druckelementes 20. Die Anschlußleitung ist in nicht gezeigter Weise mit dem Druckmittelkreislauf des hydrostatischen Motors bzw. einer an diesen angeschlossenen Druckmittelleitung verbunden.The pressure line 22 is formed in the area between two adjacent axial blind bores 33 as a through bore which runs axially through the pressure element 20 and opens out at the step 27. A connecting line 34 running axially through the connecting plate 2 (see FIG. 1) is aligned with the pressure line 22. The mutually facing end regions of both lines 22, 34 have a larger diameter than the remaining line regions and are connected to them via a circumferential, radial shoulder connected. Only the one located in the pressure line 22 with the Paragraph designated 35 is shown (see FIG. 2). A lock-up clutch 36 is inserted with play into the line end regions of larger diameter and establishes a connection between the two lines 22, 34. For this purpose, the lock-up clutch 36 is shorter by the dimension B than the two line sections of larger diameter. The dimension B is somewhat larger than the stroke A of the pressure element 20. The connecting line is connected in a manner not shown to the pressure medium circuit of the hydrostatic motor or a pressure medium line connected to it.

Die Funktion des vorbeschriebenen hydrostatischen Motors ist nachstehend mit Bezug auf die erfindungsgemäße Bremseinrichtung beschrieben:
Die Druckfedern 21 beaufschlagen das Druckelement 20 ständig in Richtung Bremsscheiben-Paket 18,19. Bei nicht angetriebenem hydrostatischen Motor und entsprechend drucklosem Druckraum 28,30 befindet sich das Druckelement 20 in der in den Figuren 2 und 3 gezeigten (linken) Bremsstellung, in der es die beiden Bremsscheiben 18,19 gegen die als Abstützung dienende erste Schulter 15 preßt und somit im gegenseitigen Bremseingriff hält. Das Druckelement 20 ist mit dem dem Hub A entsprechenden Abstand von der Anschlußplatte 2 und die Überbrückungsbuchse 36 vom Absatz 35 in der Druckleitung 22 mit einem Abstand B angeordnet.The function of the above-described hydrostatic motor is described below with reference to the braking device according to the invention:
The compression springs 21 constantly press the pressure element 20 in the direction of the brake disc package 18, 19. When the hydrostatic motor is not driven and the pressure chamber 28, 30 is correspondingly depressurized, the pressure element 20 is in the (left) braking position shown in FIGS. 2 and 3, in which it presses the two brake disks 18, 19 against the first shoulder 15 serving as support and thus holding each other in braking. The pressure element 20 is arranged at a distance B corresponding to the stroke A from the connection plate 2 and the bridging bush 36 from the shoulder 35 in the pressure line 22.

Bei angetriebenem hydrostatischen Motor wird über die Leitungen 34,22 dem Druckraum 28,30 hydraulisches Druckmittel zugeführt, dessen hydraulische Kraft die gesamte, als Druckfläche dienende Ringfläche der Stufe 27 des Druckelementes 20 beaufschlagt und letzteres gegen die Kraft der Druckfedern 21 in der Zeichnung nach rechts so weit verschiebt, bis es an der Anschlußplatte 2 anliegt (siehe Figur 4) und der Abstand zwischen dem Absatz 35 und der Überbrückungsbuchse 36 verringert ist (nicht gezeigt). Während dieser Verschiebung des Druckelementes 20 unter der Kraftwirkung des hydraulischen Druckmittels, wobei der Ringkörper 32 die Ringdichtung 31 an der zweiten Schulter 16 abstützt, löst sich die erste Bremsscheibe 18 aus dem Bremseingriff mit der zweiten Bremsscheibe 19 und letztere aus dem Druckeingriff mit der ersten Schulter 15; beide Bremsscheiben befinden sich in der in Figur 4 gezeigten Stellung und drehen nahezu reibungsfrei relativ zueinander.When the hydrostatic motor is driven, hydraulic pressure medium is fed via lines 34, 22 to pressure chamber 28, 30, the hydraulic force of which acts on the entire annular surface of stage 27 of pressure element 20, which serves as the pressure surface, and the latter against the force of compression springs 21 to the right in the drawing until it abuts the connection plate 2 (see Figure 4) and the distance between the shoulder 35 and the bridging bush 36 is reduced (not shown). During this displacement of the pressure element 20 under the action of the hydraulic pressure medium, the ring body 32 supporting the ring seal 31 on the second shoulder 16, the first brake disc 18 releases from the brake engagement with the second brake disc 19 and the latter from the pressure engagement with the first shoulder 15; both brake disks are in the position shown in FIG. 4 and rotate relative to one another with almost no friction.

Sobald der Antrieb des hydrostatischen Motors beendet und damit der Druckraum 28 druckentlastet wird, verschieben die Druckfedern 21 das Druckelement 20 zurück in die in den Figuren 2 und 3 gezeigte Bremsstellung, in der sich beide Bremsscheiben 18,19 im gegenseitigen Bremseingriff befinden sowie an der ersten Schulter 15 abgestützt sind. Aufgrund ihrer drehfesten Anordnung am Gehäuse 1 befindet sich die erste Bremsscheibe 18 auch bei drehender Zylindertrommel 6 in Ruhe relativ zum Druckelement 20, so daß letzteres beim Abbremsen der Zylindertrommel 6 kein Bremsmoment aufnimmt.As soon as the drive of the hydrostatic motor is ended and the pressure chamber 28 is thus relieved of pressure, the compression springs 21 move the pressure element 20 back into the braking position shown in FIGS Shoulder 15 are supported. Because of its rotationally fixed arrangement on the housing 1, the first brake disk 18 is at rest relative to the pressure element 20 even when the cylinder drum 6 is rotating, so that the latter does not absorb any braking torque when the cylinder drum 6 is braked.

Der Druckraum 28,30 kann über mehr als eine Druckleitung 22 mit hydraulischem Druckmittel beaufschlagt werden. Ferner ist es möglich, die zweite Bremsscheibe 19 am Gehäuse 1 drehfest und gegebenenfalls axial unverschiebbar anzuordnen; in diesem Fall ist die erste Bremsscheibe 18 axial verschiebbar an der Zylindertrommel 6 zu befestigen. Statt eines lose eingesetzten Ringkörpers 32 ist es möglich, denselben als Teil des Gehäuses 1 auszubilden. Bei ausreichend stabiler Ausbildung der zweiten Bremsscheibe 19 kann die erste Schulter 15 entfallen. Denkbar ist auch eine Ausbildung des Bremsscheiben-Paketes mit mehr als zwei Bremsscheiben.The pressure chamber 28, 30 can be supplied with hydraulic pressure medium via more than one pressure line 22. Furthermore, it is possible to arrange the second brake disk 19 on the housing 1 in a manner fixed against relative rotation and optionally axially immovable; in this case, the first brake disk 18 is to be fastened to the cylinder drum 6 in an axially displaceable manner. Instead of a loosely inserted ring body 32, it is possible to design the same as part of the housing 1. With a sufficiently stable design of the second brake disc 19, the first shoulder 15 can be omitted. It is also conceivable to design the brake disc package with more than two brake discs.

Claims (12)

  1. Hydrostatic motor having a rotor (6) rotatably mounted in a housing (1) and having a brake device (8) arranged in an annular chamber (9) between housing (1) and rotor (6), which brake device includes at least two brake surfaces (18, 19) fixed respectively on the housing (1) and the rotor (6), for rotation respectively therewith, of which brake surfaces at least one is displaceable in the axial direction of the hydrostatic motor, having at least one pressure line (22) for a hydraulic pressure medium, having an axially displaceable pressure element (20) with a pressure surface which can be acted upon by the hydraulic pressure medium and which bounds a pressure chamber (28, 30), and having at least one compression spring acting upon the pressure element (20) in the direction of the displaceable brake surface (18, 19), whereby the displaceable brake surface (18, 19) is held in braking engagement with the other brake surface (19) by means of the pressure element (20), upon hydraulic relief of the latter, and the displaceable brake surface being releasable from the braking engagement by means of axial displacement of the pressure element (20) under the effect of the force of the hydraulic pressure medium,
    characterized in that,
    the pressure line (22) runs axially through the pressure element (20) up to the height of the pressure surface (27), and in that the pressure chamber (28, 30) includes an axially running annular gap (30) between pressure element (20) and housing (1) and extends up to an annular body (32) , moveable relatively to the pressure element (20), in the annular gap (30).
  2. Hydrostatic motor according to claim 1,
    characterized by two brake disks (18, 19) the mutually confronting surfaces of which are the brake surfaces.
  3. Hydrostatic motor according to claim 2,
    characterized by a support (15) on the housing side, on which the brake disks (18, 19) are supported during their braking engagement.
  4. Hydrostatic motor according to claim 2 or 3,
    characterized in that,
    the brake disks (18, 19) are axially displaceable.
  5. Hydrostatic motor according to claim 3 or 4,
    characterized in that,
    the mutually confronting surfaces of the support (15) and the neighbouring brake disk (19) are substantially frictionless.
  6. Hydrostatic motor according to any of claims 2 to 5,
    characterized in that,
    the pressure element (20) and its neighbouring brake disk (18) are arranged fixed on the housing (1) for rotation therewith.
  7. Hydrostatic motor according to any preceding claim,
    characterized in that,
    a seal (31) is placed in the annular gap (30).
  8. Hydrostatic motor according to any preceding claim,
    characterized in that,
    the annular body (32) is placed loosely in the annular gap (30) and can be supported on an abutment (16) on the housing side.
  9. Hydrostatic motor according to any preceding claim,
    characterized in that,
    the pressure element (20) has an axial blind bore (33) in which the compression spring (21) is arranged.
  10. Hydrostatic motor according to claim 9,
    characterized in that,
    the length of the compression spring (21) in the tensioned condition upon released brake engagement is substantially the same as the longitudinal dimension of the axial blind bore (33).
  11. Hydrostatic motor according to any preceding claim,
    characterized in that,
    the compression spring (21) is supported on a connection plate (2) releasably attached to the housing (1) at an end thereof.
  12. Hydrostatic motor according to claim 11,
    characterized by a connection line (34) extending axially through the connection plate (2) and aligned with the pressure line (22) and by a bridging sleeve (46) which provides a connection between the two lines (22, 34).
EP93103001A 1992-04-30 1993-02-25 Hydrostatic motor with a braking device Expired - Lifetime EP0567736B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4214397A DE4214397C2 (en) 1992-04-30 1992-04-30 Hydrostatic motor with a braking device
DE4214397 1992-04-30

Publications (2)

Publication Number Publication Date
EP0567736A1 EP0567736A1 (en) 1993-11-03
EP0567736B1 true EP0567736B1 (en) 1996-03-20

Family

ID=6457924

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93103001A Expired - Lifetime EP0567736B1 (en) 1992-04-30 1993-02-25 Hydrostatic motor with a braking device

Country Status (2)

Country Link
EP (1) EP0567736B1 (en)
DE (2) DE4214397C2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9249664B2 (en) 2012-04-24 2016-02-02 Komatsu Ltd. Bent axis type axial piston motor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08177899A (en) * 1994-12-27 1996-07-12 Komatsu Ltd Brake device for hydraulic motor
DE10112501B4 (en) * 2001-03-15 2015-11-12 Linde Hydraulics Gmbh & Co. Kg Hydrostatic drive unit
DE102006025969A1 (en) * 2006-06-02 2007-12-06 Robert Bosch Gmbh Hydrostatic piston engine and pressure ring for a braking device of the same
DE102011076581A1 (en) 2010-12-23 2012-06-28 Robert Bosch Gmbh Hydrostatic piston engine with brake device

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1086190B (en) * 1958-08-01 1960-07-28 Kaemper Motoren G M B H Brake device for hydraulic motors
DE2130513A1 (en) * 1971-06-19 1972-12-21 Linde Ag Axial piston machine with an inclined disk
DE2931641A1 (en) * 1979-08-01 1981-02-05 Mannesmann Ag HYDROSTATIC AXIAL PISTON MOTOR IN SLOPED AXLE DESIGN, ESPECIALLY FOR CHASSIS

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9249664B2 (en) 2012-04-24 2016-02-02 Komatsu Ltd. Bent axis type axial piston motor

Also Published As

Publication number Publication date
DE59301926D1 (en) 1996-04-25
DE4214397A1 (en) 1993-11-04
DE4214397C2 (en) 1995-07-06
EP0567736A1 (en) 1993-11-03

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