EP0751294A1 - Hydraulic motor with flushing valve - Google Patents

Hydraulic motor with flushing valve Download PDF

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Publication number
EP0751294A1
EP0751294A1 EP96109648A EP96109648A EP0751294A1 EP 0751294 A1 EP0751294 A1 EP 0751294A1 EP 96109648 A EP96109648 A EP 96109648A EP 96109648 A EP96109648 A EP 96109648A EP 0751294 A1 EP0751294 A1 EP 0751294A1
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EP
European Patent Office
Prior art keywords
pressure
housing
valve
chamber
hydraulic motor
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Granted
Application number
EP96109648A
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German (de)
French (fr)
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EP0751294B1 (en
Inventor
Sinclair Cunningham
Peter Dr. Wüsthof
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Bosch Rexroth AG
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Mannesmann Rexroth AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0431—Draining of the engine housing; arrangements dealing with leakage fluid
    • 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
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F03C1/24—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders
    • F03C1/2407—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders

Definitions

  • the invention relates to a hydraulic motor, in particular to a radial piston motor with flushing valve according to DE patent 39 26 354 C2.
  • the task of a flushing valve is to supply the heat-generating parts of the hydraulic motor with a constant cooling flow in order to reduce the temperature of the heat-generating parts.
  • the low-pressure control side of the hydraulic motor is connected to the housing space by the flushing valve, the two outlets of the flushing valve having throttle bodies to limit the amount of coolant.
  • a partial flow of the working fluid always flows via the flush valve to the housing space and from there to the tank.
  • This partial flow must be supplemented by a feed pump on the low-pressure side, mixing the hydraulic motor and hydraulic pump, together with the leakage losses in the hydraulic motor and the hydraulic pump supplying the working fluid.
  • the feed pump must deliver such a flow rate that compensates for the leakage losses to maintain the low pressure. Since the feed pump must simultaneously supply the control liquid for its own adjustment and for the adjustment of the hydraulic pump for the hydraulic motor and possibly also for the adjustment of the hydraulic motor, these additional consumers must also be taken into account for their dimensioning.
  • the object of the invention is to relieve the feed pump with respect to its delivery rate as soon as the pressure set on the feed pump drops due to the actuation of the consumer or torque torque fluctuations of the hydraulic motor, so that the required low pressure can be restored as quickly as possible is. According to the invention this is achieved with the characterizing features of claim 1.
  • the setting of the switching pressure for the valve for connecting the low-pressure chamber to the housing chamber is kept slightly lower than the pressure setting of the feed pump, so that when the low pressure drops below this set value, the valve closes and the flushing liquid flow through the housing to the tank is interrupted.
  • the associated relief of the feed pump in terms of its delivery volume ensures a quick build-up of pressure on the low pressure side to the required value and thus a rapid stabilization of the entire drive and control system without having to use a feed pump of larger nominal size.
  • FIG. 1 The only figure in the drawing shows an axial section of a multi-stroke hydraulic motor, the housing of which is formed by a first housing half 1 and a second housing half 2.
  • the two housing halves 1, 2 are combined with the lifting disk 3 to form a fixed unit by means of fastening screws.
  • the shaft 5 is supported in the first housing half 1 by roller bearings 6, 7.
  • the housing end 8 of the shaft 5 is designed as a splined shaft and supports the rotor via a corresponding recess 9.
  • the rotor 10 is designed as a cylinder block and has bores 11 which are uniformly distributed over its circumference and serve to receive the pistons 12.
  • the pistons 12 are provided in their radial outer region with a recess for receiving a bearing shell 13 and a cylindrical roller 14.
  • rollers 14 are supported on a curved path 17 of the lifting disc 3. In the radially lower region of the piston 12, this has a piston ring 20 as a sealing element in a circumferential groove.
  • the piston spaces formed by the bores 11 are operatively connected via axially extending bores 21 and likewise axially extending control bores 22 in a fixed control sleeve 24 accommodated in the housing half 2.
  • the control sleeve 24 is pressed in axial direction onto the rotor 10, i.e. axially displaceable in the housing, but otherwise arranged non-rotatably as mentioned.
  • the control sleeve 24 delimits non-running control spaces 25, 26, which are connected via connections (shown at 125, 126 (also designated A and B)) for the supply and discharge of the working medium.
  • the working medium applies either high or low pressure to them and thus generates a torque on the rotor 10 which transmits it to the outside via a splined connection to the drive shaft or output shaft 5.
  • the flush valve 50 integrated in the control sleeve 24 ensures that a metered amount of operating medium is fed from the respective low-pressure working line into the inner spaces 66 of the housing parts 1, 2 for cooling the heat-generating parts of the hydraulic motor. From there, the limited amount of operating fluid continues to flow to an external leak connection 53.
  • the purge valve 50 is generally arranged parallel to the longitudinal axis 48 of the hydraulic motor.
  • the flushing valve 50 has a control piston 56 which is arranged to move back and forth in a bore 57 in the control sleeve 24.
  • the control piston 56 is delimited at the end by control spaces 85, 86, which are connected to the circumferential control spaces 25, 26 via control bores 90, 91 via flats 87 on the piston collars 88, 89 which serve to guide the control piston.
  • the control rooms 85, 86 are formed by hollow screw bodies 92, 93, which in corresponding lateral recesses 94, 95 of the Control sleeve 24 are screwed.
  • Centering springs 96, 97 for the control piston are simultaneously accommodated in the control chambers 85, 86.
  • the centering springs are supported at one end on the bottom 92a, 93a of the hollow screw body and at the other end via a disk 98, 99 and piston collars 100, 101 on the control piston 56 as soon as it is moved from the central position into a switching position.
  • the disks 98, 99 are supported on the bottom surfaces of the recesses 94, 95 for the hollow screw bodies 92, 93 and thus fix the control piston in its central position or starting position.
  • the control piston When the hydraulic machine is started up, the control piston is released from the starting position defined by the centering springs 96, 97, in which the control piston collars 102, 103 interrupt the connection of the control bores 90, 91 to the control chamber 104 in the guide bore 57 delimited by the control collars 102, 103 High pressure is shifted into a control position producing the connection of the low-pressure circumferential control chamber 25, 26 with the control chamber 104 between the two control piston assemblies 102, 103 and thus via the connecting bore 60 and the axial bore 64 from the front face 61 of the control sleeve and from the end wall 62 the housing half 2 formed space 63 connected to the low pressure side of the hydraulic machine.
  • This space 63 can be connected to the housing space 66 via a seat valve 65 arranged in the housing half 2.
  • the seat body 67 of the seat valve interacts with a seat 68 of a bore 69 connected to the space 63.
  • This bore serves at the same time for guiding a sleeve-shaped extension 70 of the seat body 67.
  • a disk 72 with a throttle bore 73 is pressed in.
  • the extension 70 has radial bores 74 which, when the seat body 67 is open, connect the cavity 75 of the extension 70 with the valve space 76 accommodating the seat body 67.
  • the valve chamber 76 is connected to the housing chamber 66 via a bore 77 in the housing half 2.
  • valve chamber 76 is a hollow cylindrical screw plug 78 completed, which at the same time receives the compression spring 79 pressing the seat body 67 onto the seat surface 68.
  • the prestress of the compression spring 79 is selected so that the seat body 67 only releases the connection of the space 63 to the housing space 66 when the pressure prevailing in the space 63 has approximately reached the value set on the feed pump (not shown). As a rule, this is approx. 2 bar difference to the set value of the low pressure.
  • the detergent branched off from the low-pressure side of the hydraulic machine through the flush valve 50 flows from the space 63 via the throttle bore 73 of the disk 72 delimiting the cavity 75 of the extension 70 the cavity 75 and from there via the radial bores 74 of the extension 70 into the valve space 76 and finally further via the bore 77 to the housing space 66, from where it flows back to the tank via the housing outlet 53 after flushing or cooling of the parts affected by the temperature .
  • the throttle bore 73 in the disk 72 defines the amount of flushing liquid which is branched off from the working liquid flowing back via the flushing valve 50 on the low-pressure side to the input of the working medium source.
  • the revolving control chamber 26 acts via the control line 91 and the flattened area 87 on the piston collar 89 in the control chamber 86 and shifts the control piston 56 against the force of the centering spring 90 in the direction of the control chamber 85 which is under low pressure
  • the rotating control chamber 25, which is under low pressure is connected to the chamber 63 via the control line 90, the control edge 102a of the control piston collar 102, the control chamber 104, the connecting bore 60 and via the axial bore 64.
  • the closing body is displaced in the opening direction, so that the flushing fluid can flow through the throttle point 73 into the housing space 66, where the heat-generating parts washed around and the absorbed heat transported back into the tank via the leakage liquid connection 53.
  • the amount of flushing liquid is determined by the pressure difference acting at the throttle point. If the low pressure drops below the value determined by the pretensioning of the closing spring 79, the valve 65 closes and interrupts the flow of flushing liquid from the low pressure side to the housing space 66 until this set pressure is restored by the feed pump. With a relatively small, constant delivery rate of the feed pump, a rapid build-up of the desired low pressure is to be ensured if this breaks down as a result of occurring control processes or torque fluctuations.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Multiple-Way Valves (AREA)

Abstract

The motor is particularly of the radial-piston type, having a non-rotating control member in the housing connecting the working chambers to high- and low-pressure unions. The valve (50) discharges into a pressure chamber (63) separate from the housing chamber (66). A valve (65) operated by the pressure in the pressure chamber connects the latter to the housing chamber. The fluid from the pressure chamber to the housing chamber flows via a device (73) restricting the flow rate. The valve connecting the pressure and housing chambers can be of type with seat, the pressure in the pressure chamber acting on it in the opening direction, its plug (67) being spring-loaded (79) shut.

Description

Die Erfindung bezieht sich auf einen Hydromotor, insbesondere auf einen Radialkolbenmotor mit Spülventil nach dem DE-Patent 39 26 354 C2.The invention relates to a hydraulic motor, in particular to a radial piston motor with flushing valve according to DE patent 39 26 354 C2.

Die Aufgabe eines Spülventils besteht darin, den wärmeerzeugenden Teilen des Hydromotors einen ständigen Kühlstrom zuzuführen, um die Temperatur der wärmeerzeugenden Teile zu mindern. Nach dem bekannten Stand der Technik wird durch das Spülventil die niederdruckführende Steuerseite des Hydromotors mit dem Gehäuseraum verbunden, wobei zur Begrenzung der Kühlflüssigkeitsmenge die beiden Austritte des Spülventils Drosselkörper aufweisen. Bei Betrieb des Hydromotors strömt also immer ein Teilstrom der Arbeitsflüssigkeit über das Spülventil zum Gehäuseraum und von dort weiter zum Tank. Dieser Teilstrom muß gemeinsam mit den anfallenden Leckverlusten im Hydromotor und der das Arbeitsmittel liefernden im geschlossenen Kreislauf arbeitenden Hydraulikpumpe durch eine Speisepumpe auf der Niederdruckseite mischen Hydromotor und Hydraulikpumpe ergänzt werden. Die Speisepumpe muß eine solche Fördermenge liefern, die zur Aufrechterhaltung des Niederdrucks die Leckverluste ausgleicht. Da die Speisepumpe gleichzeitig die steuerflüssigkeit für ihre eigene Verstellung sowie für die Verstellung der Hydraulikpumpe für den Hydromotor und gegebenenfalls auch für die Verstellung des Hydromotors liefern muß, müssen für deren Bemessung auch noch diese zusätzlichen Verbraucher berücksichtigt werden.The task of a flushing valve is to supply the heat-generating parts of the hydraulic motor with a constant cooling flow in order to reduce the temperature of the heat-generating parts. According to the known prior art, the low-pressure control side of the hydraulic motor is connected to the housing space by the flushing valve, the two outlets of the flushing valve having throttle bodies to limit the amount of coolant. When the hydraulic motor is in operation, a partial flow of the working fluid always flows via the flush valve to the housing space and from there to the tank. This partial flow must be supplemented by a feed pump on the low-pressure side, mixing the hydraulic motor and hydraulic pump, together with the leakage losses in the hydraulic motor and the hydraulic pump supplying the working fluid. The feed pump must deliver such a flow rate that compensates for the leakage losses to maintain the low pressure. Since the feed pump must simultaneously supply the control liquid for its own adjustment and for the adjustment of the hydraulic pump for the hydraulic motor and possibly also for the adjustment of the hydraulic motor, these additional consumers must also be taken into account for their dimensioning.

Die Aufgabe der Erfindung besteht nun darin, die Speisepumpe hinsichtlich ihrer Fördermenge zu entlasten, sobald durch Betätigung der Verbraucher oder durch auftretende Drehmomentschwankungen des Hydromotors ein Absinken des an der Speisepumpe eingestellten Niederdruckes auftritt, damit eine möglichst schnelle Wiederherstellung des geforderten Niederdruckes zu erreichen ist. Nach der Erfindung wird dies mit den kennzeichnenden Merkmalen des Anspruches 1 erzielt.The object of the invention is to relieve the feed pump with respect to its delivery rate as soon as the pressure set on the feed pump drops due to the actuation of the consumer or torque torque fluctuations of the hydraulic motor, so that the required low pressure can be restored as quickly as possible is. According to the invention this is achieved with the characterizing features of claim 1.

Die Einstellung des Umschaltdruckes für das Ventil zur Verbindung des Niederdruckraumes mit dem Gehäuseraum wird geringfügig kleiner gehalten als die Druckeinstellung der Speisepumpe, so daß beim Absinken des Niederdruckes unter diesem eingestellten Wert das Ventil schließt und damit der Spülflüssigkeitsstrom durch das Gehäuse zum Tank unterbrochen ist. Die damit verbundene Entlastung der Speisepumpe hinsichtlich ihrer Fördermenge gewährleistet einen schnellen Druckaufbau auf der Niederdruckseite auf den geforderten Wert und damit eine schnelle Stabilisierung des gesamten Antriebs- und Steuerungssystems, ohne eine Speisepumpe größerer Nennweite einsetzen zu müssen.The setting of the switching pressure for the valve for connecting the low-pressure chamber to the housing chamber is kept slightly lower than the pressure setting of the feed pump, so that when the low pressure drops below this set value, the valve closes and the flushing liquid flow through the housing to the tank is interrupted. The associated relief of the feed pump in terms of its delivery volume ensures a quick build-up of pressure on the low pressure side to the required value and thus a rapid stabilization of the entire drive and control system without having to use a feed pump of larger nominal size.

Weitere Einzelheiten der Erfindung ergeben sich aus den Ansprüchen und werden nachfolgend anhand eines in der Zeichnung dargestellten Ausführungsbeispiels beschrieben.Further details of the invention result from the claims and are described below with reference to an embodiment shown in the drawing.

Die einzige Figur der Zeichnung zeigt einen Axialschnitt eines Mehrhubhydromotors, dessen Gehäuse durch eine erste Gehäusehälfte 1 und eine zweite Gehäusehälfte 2 gebildet ist. Mittels Befestigungsschrauben sind die beiden Gehäusehälften 1, 2 mit der Hubscheibe 3 zu einer festen Einheit vereinigt.The only figure in the drawing shows an axial section of a multi-stroke hydraulic motor, the housing of which is formed by a first housing half 1 and a second housing half 2. The two housing halves 1, 2 are combined with the lifting disk 3 to form a fixed unit by means of fastening screws.

In der ersten Gehäusehälfte 1 ist die Welle 5 durch Wälzlager 6, 7 gelagert. Das gehäuseseitige Ende 8 der Welle 5 ist als Vielkeilwelle ausgebildet und trägt über eine entsprechende Ausnehmung 9 den Rotor. Der Rotor 10 ist als Zylinderblock ausgebildet und weist über seinen Umfang gleichmäßig verteilte Bohrungen 11 auf, die zur Aufnahme der Kolben 12 dienen. Die Kolben 12 sind in ihrem radialen äußeren Bereich mit einer Ausnehmung zur Aufnahme einer Lagerschale 13 und einer zylindrischen Rolle 14 versehen.The shaft 5 is supported in the first housing half 1 by roller bearings 6, 7. The housing end 8 of the shaft 5 is designed as a splined shaft and supports the rotor via a corresponding recess 9. The rotor 10 is designed as a cylinder block and has bores 11 which are uniformly distributed over its circumference and serve to receive the pistons 12. The pistons 12 are provided in their radial outer region with a recess for receiving a bearing shell 13 and a cylindrical roller 14.

Die Rollen 14 stützen sich an einer Kurvenbahn 17 der Hubscheibe 3 ab. Im radial unteren Bereich des Kolbens 12 weist dieser in einer umlaufenden Nut einen Kolbenring 20 als Dichtelement auf.The rollers 14 are supported on a curved path 17 of the lifting disc 3. In the radially lower region of the piston 12, this has a piston ring 20 as a sealing element in a circumferential groove.

Die von den Bohrungen 11 gebildeten Kolbenräume stehen über axial verlaufende Bohrungen 21 und ebenfalls axial verlaufenden Steuerbohrungen 22 in einer feststehenden, in der Gehäusehälfte 2 untergebrachten Steuerhülse 24 in Wirkverbindung. Die Steuerhülse 24 ist in Axialrichutng an den Rotor 10 angedrückt, d.h. axial verschiebbar im Gehäuse, aber ansonsten wie erwähnt drehfest angeordnet. Die Steuerhülse 24 begrenzt unlaufende Steuerräume 25, 26, die über bei 125, 126 dargestellten Anschlüssen (auch mit A und B bezeichnet), zur Zu- und Abführung des Arbeitsmittels in Verbindung stehen. Je nach Stellung der Kolbenräume 11 zu den Steuerbohrungen 22 werden diese vom Arbeitsmittel entweder mit Hoch- oder Niederdruck beaufschlagt und damit ein Drehmoment auf den Rotor 10 erzeugt, der dieses über Vielkeilverbindung auf die Antriebswelle bzw. Abtriebswelle 5 nach außen weiterleitet.The piston spaces formed by the bores 11 are operatively connected via axially extending bores 21 and likewise axially extending control bores 22 in a fixed control sleeve 24 accommodated in the housing half 2. The control sleeve 24 is pressed in axial direction onto the rotor 10, i.e. axially displaceable in the housing, but otherwise arranged non-rotatably as mentioned. The control sleeve 24 delimits non-running control spaces 25, 26, which are connected via connections (shown at 125, 126 (also designated A and B)) for the supply and discharge of the working medium. Depending on the position of the piston chambers 11 relative to the control bores 22, the working medium applies either high or low pressure to them and thus generates a torque on the rotor 10 which transmits it to the outside via a splined connection to the drive shaft or output shaft 5.

Insbesondere dann, wenn der Hydraulikmotor mit großer Leistung gefahren wird, entsteht ein erhöhter Wärmeanfall zwischen den Rollen 14 und den Gleitlagern 13, wodurch die Gleitlager durch örtlich hohe Temperaturen gefährdet sind. Das in der Steuerhülse 24 integrierte Spülventil 50 sorgt dafür, aus der jeweiligen Niederdruckarbeitsleitung eine dosierte Menge Betriebsmittel in die inneren Räume 66 der Gehäuseteile 1, 2 zum Kühlen der wärmeerzeugenden Teile des Hydraulikmotors zu leiten. Von dort fließt die begrenzte Menge Betriebsmittel weiter zu einem äußeren Leckanschluß 53.In particular, when the hydraulic motor is operated at high power, there is an increased heat build-up between the rollers 14 and the slide bearings 13, as a result of which the slide bearings are endangered by locally high temperatures. The flush valve 50 integrated in the control sleeve 24 ensures that a metered amount of operating medium is fed from the respective low-pressure working line into the inner spaces 66 of the housing parts 1, 2 for cooling the heat-generating parts of the hydraulic motor. From there, the limited amount of operating fluid continues to flow to an external leak connection 53.

Das Spülventil 50 ist im ganzen parallel zur Längsachse 48 des Hydraulikmotors angeordnet. Im einzelnen weist das Spülventil 50 einen Steuerkolben 56 auf, der in einer Bohrung 57 der Steuerhülse 24 hin und her beweglich angeordnet ist. Der Steuerkolben 56 wird endseitig von Steuerräumen 85, 86 begrenzt, die über Abflachungen 87 an den der Führung des Steuerkolbens dienenden Kolbenbunden 88, 89 mit dem umlaufenden Steuerräumen 25, 26 über Steuerbohrungen 90, 91 in hydraulischer Verbindung stehen. Die Steuerräume 85, 86 werden von hohlen Schraubkörpern 92, 93, gebildet, die in entsprechende seitliche Ausnehmungen 94, 95 der Steuerhülse 24 eingeschraubt sind. In den Steuerräuemn 85, 86 sind gleichzeitig Zentrierfedern 96, 97 für den Steuerkolben untergebracht. Die Zentrierfedern stützen sich mit dem einen Ende am Boden 92a, 93a der hohlen Schraubkörper und mit ihren anderen Ende über eine Scheibe 98, 99 und Kolbenbunde 100, 101 am Steuerkolben 56 ab, sobald dieser aus der Mittelstellung in eine Schaltstellung verschoben wird. In der Mittelstellung des Steuerkolbens stützen sich die Scheiben 98, 99 an den Bodenflächen der Ausnehmungen 94, 95 für die hohlen Schraubkörper 92, 93 ab und fixieren damit den Steuerkolben in seiner Mittelstellung bzw. Ausgangsstellung.The purge valve 50 is generally arranged parallel to the longitudinal axis 48 of the hydraulic motor. In particular, the flushing valve 50 has a control piston 56 which is arranged to move back and forth in a bore 57 in the control sleeve 24. The control piston 56 is delimited at the end by control spaces 85, 86, which are connected to the circumferential control spaces 25, 26 via control bores 90, 91 via flats 87 on the piston collars 88, 89 which serve to guide the control piston. The control rooms 85, 86 are formed by hollow screw bodies 92, 93, which in corresponding lateral recesses 94, 95 of the Control sleeve 24 are screwed. Centering springs 96, 97 for the control piston are simultaneously accommodated in the control chambers 85, 86. The centering springs are supported at one end on the bottom 92a, 93a of the hollow screw body and at the other end via a disk 98, 99 and piston collars 100, 101 on the control piston 56 as soon as it is moved from the central position into a switching position. In the central position of the control piston, the disks 98, 99 are supported on the bottom surfaces of the recesses 94, 95 for the hollow screw bodies 92, 93 and thus fix the control piston in its central position or starting position.

Bei Inbetriebnahme der Hydromaschine wird der Steuerkolben aus der von den Zentrierfedern 96, 97 festgelegten Ausgangsstellung, in der die Steuerkolbenbunde 102, 103 die Verbindung der Steuerbohrungen 90, 91 zu dem von den Steuerbunden 102, 103 begrenzten Steuerraum 104 in der Führungsbohrung 57 unterbrechen, vom Hochdruck in eine die Verbindung des den Niederdruck führenden umlaufenden Steuerraumes 25, 26 mit dem Steuerraum 104 zwischen den beiden Steuerkolbenbunden 102, 103 herstellende Steuerstellung verschoben und damit über die Verbindungsbohrung 60 und die Axialbohrung 64 der von der Stirnseite 61 der Steuerhülse und von der Abschlußwand 62 der Gehäusehälfte 2 gebildete Raum 63 mit der Niederdruckseite der Hydromaschine verbunden. Dieser Raum 63 ist über ein in der Gehäusehälfte 2 angeordnetes Sitzventil 65 mit dem Gehäuseraum 66 verbindbar. Der Sitzkörper 67 des Sitzventils wirkt mit einer Sitzfläche 68 einer mit dem Raum 63 verbundenen Bohrung 69 zusammen. Diese Bohrung dient gleichzeitig zur Führung einer hülsenförmigen Verlängerung 70 des Sitzkörpers 67. Am dem Raum 63 zugekehrten Ende 71 der Verlängerung 70 ist eine Scheibe 72 mit einer Drosselbohrung 73 eingepreßt. Sitzkörperseitig weist die Verlängerung 70 Radialbohrungen 74 auf, die bei geöffnetem Sitzkörper 67 den Hohlraum 75 der Verlängerung 70 mit dem den Sitzkörper 67 aufnehmenen Ventilraum 76 verbinden. Der Ventilraum 76 ist über eine Bohrung 77 in der Gehäusehälfte 2 mit dem Gehäuseraum 66 verbunden. Nach außen ist der Ventilraum 76 von einer hohlzylindrischen Verschlußschraube 78 abgeschlossen, die gleichzeitig die den Sitzkörper 67 auf die Sitzfläche 68 drückende Druckfeder 79 aufnimmt. Die Vorspannung der Druckfeder 79 ist so gewählt, daß der Sitzkörper 67 die Verbindung des Raumes 63 mit dem Gehäuseraum 66 erst freigibt, wenn der im Raum 63 herrschende Druck annähernd den an der nicht dargestellten Speisepumpe eingestellten Wert erreicht hat. In der Regel sind dies ca. 2 bar Differenz zum eingestellten Wert des Niederdruckes. Bei geöffnetem Sitzkörper 67 dessen Öffnungshub von Anschlagflächen 80, 81 des Sitzkörpers und Verschlußschraube 78 begrenzt ist, strömt das von der Niederdruckseite der Hydromaschine durch das Spülventil 50 abgezweigte Spülmittel vom Raum 63 über die Drosselbohrung 73 der den Hohlraum 75 der Verlängerung 70 begrenzenden Scheibe 72 in den Hohlraum 75 und von dort über die Radialbohrungen 74 der Verlängerung 70 in den Ventilraum 76 und schließlich weiter über die Bohrung 77 zum Gehäuseraum 66, von wo es nach Spülung bzw. Kühlung der von der Temperatur betroffenen Teile über den Gehäuseauslaß 53 zurück zum Tank strömt. Die Drosselbohrung 73 in der Scheibe 72 legt die Spülflüssigkeitsmenge fest, die von der über das Spülventil 50 auf der Niederdruckseite zum Eingang der Arbeitsmittelquelle zurückströmenden Arbeitsflüssigkeit abgezweigt wird.When the hydraulic machine is started up, the control piston is released from the starting position defined by the centering springs 96, 97, in which the control piston collars 102, 103 interrupt the connection of the control bores 90, 91 to the control chamber 104 in the guide bore 57 delimited by the control collars 102, 103 High pressure is shifted into a control position producing the connection of the low-pressure circumferential control chamber 25, 26 with the control chamber 104 between the two control piston assemblies 102, 103 and thus via the connecting bore 60 and the axial bore 64 from the front face 61 of the control sleeve and from the end wall 62 the housing half 2 formed space 63 connected to the low pressure side of the hydraulic machine. This space 63 can be connected to the housing space 66 via a seat valve 65 arranged in the housing half 2. The seat body 67 of the seat valve interacts with a seat 68 of a bore 69 connected to the space 63. This bore serves at the same time for guiding a sleeve-shaped extension 70 of the seat body 67. At the end 71 of the extension 70 facing the space 63, a disk 72 with a throttle bore 73 is pressed in. On the seat body side, the extension 70 has radial bores 74 which, when the seat body 67 is open, connect the cavity 75 of the extension 70 with the valve space 76 accommodating the seat body 67. The valve chamber 76 is connected to the housing chamber 66 via a bore 77 in the housing half 2. To the outside, the valve chamber 76 is a hollow cylindrical screw plug 78 completed, which at the same time receives the compression spring 79 pressing the seat body 67 onto the seat surface 68. The prestress of the compression spring 79 is selected so that the seat body 67 only releases the connection of the space 63 to the housing space 66 when the pressure prevailing in the space 63 has approximately reached the value set on the feed pump (not shown). As a rule, this is approx. 2 bar difference to the set value of the low pressure. When the seat body 67 is open, the opening stroke of which is limited by stop surfaces 80, 81 of the seat body and locking screw 78, the detergent branched off from the low-pressure side of the hydraulic machine through the flush valve 50 flows from the space 63 via the throttle bore 73 of the disk 72 delimiting the cavity 75 of the extension 70 the cavity 75 and from there via the radial bores 74 of the extension 70 into the valve space 76 and finally further via the bore 77 to the housing space 66, from where it flows back to the tank via the housing outlet 53 after flushing or cooling of the parts affected by the temperature . The throttle bore 73 in the disk 72 defines the amount of flushing liquid which is branched off from the working liquid flowing back via the flushing valve 50 on the low-pressure side to the input of the working medium source.

Führt beispielsweise der umlaufende Steuerraum 26 Hochdruck, wirkt dieser über die Steuerleitung 91 und die Abflachung 87 am Kolbenbund 89 auch im Steuerraum 86 und verschiebt dort den Steuerkolben 56 gegen die Kraft der Zentrierfeder 90 in Richtung des unter Niederdruck stehenden Steuerraumes 85. In dieser Schaltstellung des Steuerkolben ist der unter Niederdruck stehende umlaufende Steuerraum 25 über die Steuerleitung 90, die Steuerkante 102a des Steuerkolbenbundes 102, den Steuerraum 104, die Verbindungsbohrung 60 und über die Axialbohrung 64 mit dem Raum 63 verbunden. Erreicht der auch im Raum 63 wirkende Niederdruck der Steuerflüssigkeit einen Wert, der der Vorspannkraft der Feder 79 des Ventils 65 entspricht, wird der Schließkörper in Öffnungsrichtung verschoben, so daß die Spülflüssigkeit über die Drosselstelle 73 in den Gehäuseraum 66 strömen kann, dort die wärmeerzeugenden Teile umspült und die aufgenommene Wärme über den Leckflüssigkeitsanschluß 53 zurück in den Tank transportiert. Die Spülflüssigkeitsmenge wird neben dem freien Durchflußquerschnitt der Drosselstelle 73 von der an der Drosselstelle wirkenden Druckdifferenz festgelegt. Sinkt der Niederdruck unter den von der Vorspannung der Schließfeder 79 festgelegten Wert, schließt das Ventil 65 und unterbricht den Spülflüssigkeitsstrom von der Niederdruckseite zum Gehäuseraum 66 solange, bis durch die Speisepumpe dieser eingestellte Druck wieder hergestellt ist. Damit ist mit einer verhältnismäßig kleinzuhaltenden konstanten Fördermenge der Speisepumpe ein schneller Aufbau des gewünschten Niederdruckes zu gewährleisten, wenn dieser infolge auftretender Regelvorgänge oder Drehmomentschwankungen einbricht.If, for example, the revolving control chamber 26 is at high pressure, it acts via the control line 91 and the flattened area 87 on the piston collar 89 in the control chamber 86 and shifts the control piston 56 against the force of the centering spring 90 in the direction of the control chamber 85 which is under low pressure Control piston, the rotating control chamber 25, which is under low pressure, is connected to the chamber 63 via the control line 90, the control edge 102a of the control piston collar 102, the control chamber 104, the connecting bore 60 and via the axial bore 64. If the low pressure of the control fluid, which also acts in the space 63, reaches a value which corresponds to the pretensioning force of the spring 79 of the valve 65, the closing body is displaced in the opening direction, so that the flushing fluid can flow through the throttle point 73 into the housing space 66, where the heat-generating parts washed around and the absorbed heat transported back into the tank via the leakage liquid connection 53. In addition to the free flow cross section of the throttle point 73, the amount of flushing liquid is determined by the pressure difference acting at the throttle point. If the low pressure drops below the value determined by the pretensioning of the closing spring 79, the valve 65 closes and interrupts the flow of flushing liquid from the low pressure side to the housing space 66 until this set pressure is restored by the feed pump. With a relatively small, constant delivery rate of the feed pump, a rapid build-up of the desired low pressure is to be ensured if this breaks down as a result of occurring control processes or torque fluctuations.

Claims (5)

Hydromotor, insbesondere Radialkolbenmotor, mit einem innerhalb von diesem angeordneten Spülventil, mit einem Gehäuse, in dem ein Rotor drehbar angeordnet ist, sowie mit einem drehfest im Gehäuse angeordneten Steuerteil, welches die Arbeitsräume mit Hochdruck- und Niederdruckanschlüssen verbindet, dadurch gekennzeichnet, daß der Ausgang des Spülventils (50) in einen vom Gehäuseraum (66) getrennten Druckraum (63) mündet, der über ein vom in diesem Druckraum herrschenden Druck betätigbares Ventil (65) mit dem Gehäuseraum (66) verbindbar ist, und daß die vom Druckraum (63) zum Gehäuseraum (66) strömende Spülflüssigkeit über eine die Spülflüssigkeitsmenge begrenzende Einrichtung (73) strömt.Hydraulic motor, in particular radial piston motor, with a flush valve arranged inside it, with a housing in which a rotor is rotatably arranged, and with a control part arranged in a rotationally fixed manner in the housing and connecting the working spaces with high-pressure and low-pressure connections, characterized in that the outlet of the flushing valve (50) opens into a pressure chamber (63) which is separate from the housing chamber (66) and which can be connected to the housing chamber (66) via a valve (65) which can be actuated by the pressure prevailing in this pressure chamber, and that the pressure chamber (63) Flushing liquid flowing to the housing space (66) flows through a device (73) limiting the amount of flushing liquid. Hydromotor nach Anspruch 1, dadurch gekennzeichnet, daß das den Druckraum (63) mit dem Gehäuseraum (66) verbindende Ventil (65) von einem vom im Druckraum (63) herrschenden Druck in Öffnungsrichtung beaufschlagten Sitzventil gebildet ist, dessen Schließkörper (67) von einer Feder (79) in Schließrichtung beaufschlagt ist.Hydraulic motor according to claim 1, characterized in that the valve (65) connecting the pressure chamber (63) to the housing chamber (66) is formed by a seat valve acted upon by the pressure in the pressure chamber (63) in the opening direction, the closing body (67) of which is one Spring (79) is acted upon in the closing direction. Hydromotor nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die den Schließkörper (67) in Schließrichtung beaufschlagende Feder (79) eine Vorspannung aufweist, deren Druckentsprechung geringfügig kleiner ist als der an einer Speisepumpe eingestellte Niederdruck.Hydraulic motor according to Claim 1 or 2, characterized in that the spring (79) acting on the closing body (67) in the closing direction has a pretension, the pressure of which is slightly less than the low pressure set on a feed pump. Hydromotor nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß der Schließkörper (67) eine in einer Führungsbohrung (69) geführte hülsenförmige Verlängerung (70) mit Drosselbohrung (73) aufweist.Hydraulic motor according to Claim 2 or 3, characterized in that the closing body (67) has a sleeve-shaped extension (70) with a throttle bore (73) which is guided in a guide bore (69). Hydromotor nach Anspruch 4, dadurch gekennzeichnet, daß die hülsenförmige Verlängerung (70) einen einen Hohlraum (75) begrenzenden Boden (72) mit einer Drosselbohrung (73) zur Begrenzung der Spülflüssigkeitsmenge und unterhalb der Sitzfläche (68) des Schließkörpers (67) Radialbohrungen (74) aufweist, die in geöffneter Lage des Schließkörpers (67) die über die Drosselbohrung (73) in den Hohlraum (75) einströmende Spülflüssigkeit in den Gehäuseraum (66) weiterleiten.Hydraulic motor according to claim 4, characterized in that the sleeve-shaped extension (70) has a bottom (72) defining a cavity (75) with a throttle bore (73) for limiting the amount of flushing liquid and below the seat surface (68) of the closing body (67) radial bores ( 74) which In the open position of the closing body (67), pass the flushing liquid flowing into the cavity (75) via the throttle bore (73) into the housing space (66).
EP19960109648 1995-06-21 1996-06-15 Hydraulic motor with flushing valve Expired - Lifetime EP0751294B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19522448A DE19522448C1 (en) 1995-06-21 1995-06-21 Hydraulic motor with flushing valve, esp. radial piston motor
DE19522448 1995-06-21

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EP0751294A1 true EP0751294A1 (en) 1997-01-02
EP0751294B1 EP0751294B1 (en) 2001-07-25

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19733911C1 (en) * 1997-08-05 1998-07-16 Mannesmann Rexroth Ltd Hydrostatic motor with fluid circulation in housing

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2820186B1 (en) 2001-01-31 2004-03-12 Poclain Hydraulics Ind EXCHANGE DEVICE FOR A CLOSED CIRCUIT

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2168436A (en) * 1984-12-18 1986-06-18 Duesterloh Gmbh Reversible hydraulic machine
DE3926354A1 (en) * 1989-08-09 1991-02-14 Rexroth Mannesmann Gmbh PURGE VALVE

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2168436A (en) * 1984-12-18 1986-06-18 Duesterloh Gmbh Reversible hydraulic machine
DE3926354A1 (en) * 1989-08-09 1991-02-14 Rexroth Mannesmann Gmbh PURGE VALVE

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19733911C1 (en) * 1997-08-05 1998-07-16 Mannesmann Rexroth Ltd Hydrostatic motor with fluid circulation in housing
EP0896150A2 (en) 1997-08-05 1999-02-10 Brueninghaus Hydromatik Gmbh Hydraulic machine with flushing valve for housing
EP0896150A3 (en) * 1997-08-05 1999-10-13 Brueninghaus Hydromatik Gmbh Hydraulic machine with flushing valve for housing

Also Published As

Publication number Publication date
EP0751294B1 (en) 2001-07-25
DE19522448C1 (en) 1996-09-12

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