EP0567736A1 - Moteur hydrostatique avec un dispositif de freinage - Google Patents

Moteur hydrostatique avec un dispositif de freinage Download PDF

Info

Publication number
EP0567736A1
EP0567736A1 EP93103001A EP93103001A EP0567736A1 EP 0567736 A1 EP0567736 A1 EP 0567736A1 EP 93103001 A EP93103001 A EP 93103001A EP 93103001 A EP93103001 A EP 93103001A EP 0567736 A1 EP0567736 A1 EP 0567736A1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydrostatic motor
pressure element
braking
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP93103001A
Other languages
German (de)
English (en)
Other versions
EP0567736B1 (fr
Inventor
Rainer Stoelzer
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
Hydromatik GmbH
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 Brueninghaus Hydromatik GmbH, Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0567736A1 publication Critical patent/EP0567736A1/fr
Application granted granted Critical
Publication of EP0567736B1 publication Critical patent/EP0567736B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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.
  • Such a hydrostatic motor with a braking device is known from DE-OS 29 31 641, the pressure line of which runs obliquely at an angle both to the axial and to the radial direction through the housing to the outside thereof.
  • 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.
  • 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.
  • 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 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 at the open end thereof, one by means of tapered bearings 3, 4 in the housing 1 and in the connecting plate 2 rotatably mounted output shaft 5, a rotatably arranged rotor in the form of a cylinder drum 6, which is supported on a control disk (not shown) attached to the connecting plate 2, a swash plate 7 attached to the control disk on the housing 1, and a braking device 8 to be described An annular space 9 is formed between the housing 1 and the cylinder drum 6.
  • cylinder bores 10 are formed in a known manner, which open out via cylinder channels 11 on the end face of the cylinder drum 6 facing the control disk.
  • 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.
  • the housing 1 is provided at its open end facing the connecting plate 2 with a circumferential, radially outwardly extending housing flange part 14, in which the annular space 9 is expanded radially outwards.
  • the enlarged annular space 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 inner wall 25 of the housing and 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 disc 19 faces the first shoulder 15 and is supported by it during the brake intervention with the first brake disc 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 enlarged 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.
  • the third shoulder 17 and the step 27 thus 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 lateral 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 region 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 area 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 prestress on the connection plate 2; their length when the brake disks 18, 19 are released (see FIG. 4) is equal to the length dimension of the axial blind bores 33.
  • the latter are arranged on a pitch circle with the same mutual spacing.
  • 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 lockup 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 lockup 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 hydrostatic motor described above 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 connecting 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. If the second brake disk 19 is made sufficiently stable, the first shoulder 15 can be omitted. It is also conceivable to design the brake disc package with more than two brake discs.

Landscapes

  • 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)
EP93103001A 1992-04-30 1993-02-25 Moteur hydrostatique avec un dispositif de freinage Expired - Lifetime EP0567736B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4214397A DE4214397C2 (de) 1992-04-30 1992-04-30 Hydrostatischer Motor mit einer Bremseinrichtung
DE4214397 1992-04-30

Publications (2)

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

Family

ID=6457924

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93103001A Expired - Lifetime EP0567736B1 (fr) 1992-04-30 1993-02-25 Moteur hydrostatique avec un dispositif de freinage

Country Status (2)

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0797020A1 (fr) * 1994-12-27 1997-09-24 Komatsu Ltd. Dispositif de frein pour moteur hydraulique
JP2009531620A (ja) * 2006-06-02 2009-09-03 ブルーニンガウス ハイドロマティック ゲゼルシャフト ミット ベシュレンクテル ハフツンク 液圧ピストンマシンとそのブレーキ装置のためのスラストリング
DE10112501B4 (de) * 2001-03-15 2015-11-12 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Antriebseinheit

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011076581A1 (de) 2010-12-23 2012-06-28 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit Bremsvorrichtung
JP5174260B1 (ja) * 2012-04-24 2013-04-03 株式会社小松製作所 斜軸式アキシャルピストンモータ

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1086190B (de) * 1958-08-01 1960-07-28 Kaemper Motoren G M B H Bremsvorrichtung fuer hydraulische Motoren
FR2143079A1 (fr) * 1971-06-19 1973-02-02 Linde Ag
DE2931641A1 (de) * 1979-08-01 1981-02-05 Mannesmann Ag Hydrostatischer axialkolbenmotor in schraegachsenbauweise, insbesondere fuer fahrgetriebe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1086190B (de) * 1958-08-01 1960-07-28 Kaemper Motoren G M B H Bremsvorrichtung fuer hydraulische Motoren
FR2143079A1 (fr) * 1971-06-19 1973-02-02 Linde Ag
DE2931641A1 (de) * 1979-08-01 1981-02-05 Mannesmann Ag Hydrostatischer axialkolbenmotor in schraegachsenbauweise, insbesondere fuer fahrgetriebe

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0797020A1 (fr) * 1994-12-27 1997-09-24 Komatsu Ltd. Dispositif de frein pour moteur hydraulique
EP0797020A4 (fr) * 1994-12-27 1998-10-07 Komatsu Mfg Co Ltd Dispositif de frein pour moteur hydraulique
US6006872A (en) * 1994-12-27 1999-12-28 Komatsu Ltd. Braking apparatus for a hydraulic motor
DE10112501B4 (de) * 2001-03-15 2015-11-12 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Antriebseinheit
JP2009531620A (ja) * 2006-06-02 2009-09-03 ブルーニンガウス ハイドロマティック ゲゼルシャフト ミット ベシュレンクテル ハフツンク 液圧ピストンマシンとそのブレーキ装置のためのスラストリング

Also Published As

Publication number Publication date
DE59301926D1 (de) 1996-04-25
DE4214397A1 (de) 1993-11-04
DE4214397C2 (de) 1995-07-06
EP0567736B1 (fr) 1996-03-20

Similar Documents

Publication Publication Date Title
DE2430069C2 (de) Hydraulisch lösbare Lamellenbremse
DE3815225C2 (fr)
DE69826657T2 (de) Flache freilaufkupplungeinheit
DE4237075C1 (de) Druckmittelbetätigte Reibscheibenkupplung
DE60124075T2 (de) Kombinierte park- und betriebsbremse
DE3211366C2 (de) Federspeicherbremse mit druckmittelbetätigbarer Lüfteinrichtung
DE4311997C2 (de) Hydraulikmotor
DE2835558C2 (fr)
DE1655256A1 (de) Hydraulisch betaetigte Bremse fuer Kraftfahrzeuge
DE4206101C2 (de) Hydromechanisches Antriebssystem
DE69205468T2 (de) Anordnung zur Drehmomentübertragung eines Vierradgetriebenen Fahrzeuges.
DE3325523A1 (de) Stufenlos einstellbares kegelscheiben-umschlingungsgetriebe
DE19504451B4 (de) Antriebseinrichtung für mobile Arbeitsgeräte
DE3911427C2 (fr)
DE60029425T2 (de) Motor mit symmetrischem bremssystem
DE3025282A1 (de) Sperrdifferential fuer fahrzeuge
DE10306850A1 (de) Hydraulisch betätigte Reibungskupplung
EP0599870B1 (fr) Moteur hydrostatique a pistons axiaux pour le montage dans le moyeu d'une roue a entrainer
EP0567736B1 (fr) Moteur hydrostatique avec un dispositif de freinage
DE4432134C2 (de) Antriebsaggregat mit koaxialer Anordnung von Motor, Planetengetriebe und Endabtriebswelle
EP0809736B1 (fr) Mecanisme vireur pour benne preneuse
DE3720280A1 (de) Selbstsperrdifferential
DE102007018158A1 (de) Wälzlager mit einer Bremseinrichtung
DE3220492C2 (de) Hydraulischer Radialkolbenmotor
WO1999030030A1 (fr) Moteur a pistons radiaux avec frein a friction

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19940119

17Q First examination report despatched

Effective date: 19941010

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BRUENINGHAUS HYDROMATIK GMBH

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

REF Corresponds to:

Ref document number: 59301926

Country of ref document: DE

Date of ref document: 19960425

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19960621

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20090223

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20090223

Year of fee payment: 17

Ref country code: IT

Payment date: 20090227

Year of fee payment: 17

Ref country code: DE

Payment date: 20090417

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20090217

Year of fee payment: 17

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20100225

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20101029

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100225

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100225

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100226