EP0328767A1 - Vibrating roller - Google Patents

Vibrating roller Download PDF

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Publication number
EP0328767A1
EP0328767A1 EP88120969A EP88120969A EP0328767A1 EP 0328767 A1 EP0328767 A1 EP 0328767A1 EP 88120969 A EP88120969 A EP 88120969A EP 88120969 A EP88120969 A EP 88120969A EP 0328767 A1 EP0328767 A1 EP 0328767A1
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EP
European Patent Office
Prior art keywords
pump
clutch
pressure
filling
pump unit
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
EP88120969A
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German (de)
French (fr)
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EP0328767B1 (en
Inventor
Manfred Polacek
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Wacker Werke GmbH and Co KG
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Wacker Werke GmbH and Co KG
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Publication of EP0328767A1 publication Critical patent/EP0328767A1/en
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Publication of EP0328767B1 publication Critical patent/EP0328767B1/en
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    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll

Definitions

  • the invention relates to a vibratory roller according to the preamble of patent claim 1.
  • Vibratory rollers of this type are known. They are manufactured and distributed by the applicant and are described in their prospectus (W 680 / 12-10-10.87 from October 1987).
  • the clutch is operated mechanically.
  • the mechanical actuation device and the clutch equipped for mechanical actuation are bulky, so that a second output on the internal combustion engine was required on the opposite side of the variable displacement pump and the motor shaft also had to be brought out there.
  • the shift clutches which can be actuated mechanically directly by the operator via the shift linkage have the disadvantage that it is not guaranteed that they are actuated gently, ie in particular largely without slippage.
  • the invention has for its object to provide a vibrating roller according to the preamble of claim, in which the clutch is arranged in a space-saving manner in a compact structure on the same side as the variable displacement pump, in particular without the need for the motor shaft to be led out, and moreover is set up that operating errors are excluded.
  • Hydraulically actuated clutches are known per se. They take up less space than mechanically actuated couplings and can be easily operated from any desired location on the vibrating roller using space-saving pressure medium lines.
  • the disadvantage is that they require a hydraulic pressure transducer, for which the existing pressure medium circuit of the variable displacement pump is not suitable because of the special pressure conditions prevailing in it, in particular the operational pressure fluctuations down to idle pressure, so that the use of hydraulically actuated clutches has so far been avoided.
  • the invention is based on the knowledge that the filling pump combined with the variable pump in a pump unit can be used as a pressure transmitter for the clutch if it is made accessible from the outside to the integrated pressure medium circuit in the pump unit.
  • the vibrating roller shown in FIGS. 1 and 2 has a rigid machine frame 1, in which a front and a rear roller drum 2a or 2b are non-steerably but rotatably mounted.
  • an internal combustion engine 3 here a diesel engine, is attached off-center with a motor shaft 3a arranged parallel to the Bendagen axes so that it does not protrude beyond the remaining parts of the vibratory roller on the left-hand side for the viewer of FIG.
  • the motor 3 extends approximately over half the roll width, so that on the right-hand side of the viewer of FIG. 2 there is a free space also extending over approximately half the roll width up to the right-hand side roll limitation.
  • the motor shaft 3a is led out of the motor 3 only on this right-hand side and drives a pump unit 4 there with a shaft 4a coaxial with it, which comprises a variable displacement pump 5 with variable displacement and reversible conveying direction and a filling pump 6.
  • the pump unit 4 is flanged directly to the motor 3.
  • the shaft 4a of the pump unit is led out of it and drives the input member 7a of a hydraulically actuated clutch 7, which has an output member 7b designed as a drum and in turn to the pumps unit 4 is flanged.
  • the outer main connections of the variable displacement pump 5, which form the pressure connection and the suction connection of the pressure medium circuit acted upon by them, are designated A and B.
  • the clutch 7 has a single pressure medium connection D '; when this is pressurized hydraulically, the clutch 7 switches through, so that then and only then is the input member 7a of the clutch 7 rotatably connected to its output member 7b.
  • the drum-shaped output member 7b of the hydraulically actuated clutch 7 is provided with V-grooves in which V-belts 8 run, which drive a V-belt pulley 9 at the end of an intermediate shaft 10 which runs parallel to the motor shaft 3a under the motor 3 from that for the viewer of FIG. 2 extends right side of the vibrating roller to the left and is rotatably supported in the roller frame 1 near its ends.
  • V-belts 8 run, which drive a V-belt pulley 9 at the end of an intermediate shaft 10 which runs parallel to the motor shaft 3a under the motor 3 from that for the viewer of FIG. 2 extends right side of the vibrating roller to the left and is rotatably supported in the roller frame 1 near its ends.
  • the output torque of the clutch 7 is transmitted to the other side of the vibrating roller and drives the unbalance vibrators 12a located in the bandages 2a and 2b via a V-belt transmission 11, which is only schematically indicated in the drawing.
  • the rotary drive of the drums 2a and 2b is provided by a gear mechanism 13, which is also only schematically indicated in FIG. 2 of the drawing, a hydraulic drive motor 14 fixed displacement between the drums under the diesel engine 3 on the roller frame 1 and which, in the usual way, has two main pressure medium connections A ' and B ', which, as can be seen in Fig. 3, with the main connections A and B of the variable pump 5 in the 1 and 2 pressure medium lines, not shown, are connected.
  • the speed and the direction of rotation of the hydraulic motor 14 depend on the respectively set delivery volume or the respectively selected delivery direction of the variable pump 5 and determine the driving speed or the driving direction of the vibrating roller.
  • FIG. 3 shows the circuit diagram of the hydraulic circuits in the vibrating roller according to FIGS. 1 and 2.
  • the hydraulic connections on the pump unit 4, the clutch 7 and the drive motor 14, which are designated with capital letters in FIG. 2, are given the same letters in FIG. 3 designated.
  • variable displacement pump 5 and the filling pump 6 are interconnected in the usual way.
  • the suction side of the filling pump 6 is connected to an oil reservoir 15. Its pressure side is in each case connected via a check valve 16a or 16b to one or the other of the two connecting lines leading from the variable pump 5 to the connections A and B and integrated into the pump unit 4.
  • the check valves 16a and 16b open in the direction of these connecting lines, so that a permanent filling of the pressure medium main circuit via the connections A, A ', B' and B between the variable displacement pump 5 and the hydraulic drive motor 14 is ensured and the piston heads of the variable displacement pump are always held under a certain pressure in contact with their swashplate.
  • Pressure limiting valves 17a, 17b limit the maximum pressure that can occur in the respective pressure branch of the main hydraulic circuit between the variable displacement pump 5 and the travel drive motor 14.
  • the maximum pressure in the pressure circuit of the filling pump 6 is limited by a pressure relief valve 18.
  • the connecting lines shown in broken lines in FIG. 3 are Ent load or leakage oil lines leading back to the sump 15.
  • the branch going through connection B represents the pressure branch and the branch going through connection A represents the suction branch or vice versa.
  • the speed of travel motor 14 depends on the delivery volume of variable displacement pump 5, which is via the Tilt angle of the swash plate is selectable.
  • the pressure in the pressure branch of the main pressure medium circuit depends up to the permitted maximum value on the driving resistance, which acts on the shaft of the drive motor 14, is therefore subject to considerable fluctuations, which are above the pressure of the filling pump 6 by the check valves 16a predetermined by the limiting valve 18 and 16b are kept away from the latter so that the fill pump pressure has a substantially constant value.
  • the connections A and B and a connection F for an external relief and leakage oil line are the previously discussed connection paths with the built-in valves in the pump unit 4 integrated.
  • an outlet channel is also provided in the pump unit 4, which connects the pressure side of the filling pump 6 to the external pressure medium connection C.
  • a switching valve 19 having two switching positions, which has a second pressure medium connection E, which is connected to the sump 15 via a pressure medium line.
  • a third pressure medium connection D of the switching valve 19 is connected via a pressure medium line to the pressure medium connection D 'of the clutch 7.
  • the two switching positions of the switching valve 19 can be selected by means of a lever 20 which, like the switching valve 19, is attached to the vibrating roller and is located in the access area of the roller operator. In one Switching position, the switching valve 19 blocks the pressure medium connection C 'and connects the connections D and E, while in the other switching position it blocks the connection E and connects the connections C' and D.
  • connection D ' is relieved of pressure and thus the clutch 7 is disconnected, and in the latter switching position, the connection D' is under pressure from the filling pump 6, so that the clutch 7 is switched through and a rotationally fixed connection between the Input member 7a and the output member 7b is produced and the diesel engine 3 then also drives the unbalance vibrators 12 in the bandages 2a and 2b.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The invention relates to a vibrating roller having a hydrostatic driving mechanism, in which the internal-combustion engine (3) drives a pump unit (4) which includes a variable-displacement swash plate pump and a filling pump, and the driving mechanism is served by at least one hydraulic motor which is supplied with pressure means by the swash plate pump. The unbalance vibrators (12) situated in the tyres are driven by means of a mechanical power-transmission path which is derived from the internal-combustion engine (3) and has a built-in clutch (7). According to the invention, the clutch (7) is flanged onto the pump unit (4) and provided with a hydrostatically actuable switching mechanism which can be connected by means of a switching valve to the delivery side of the filling pump in order to engage the clutch (7). In this manner, a space-saving compact design of the drive for the unbalance vibrators (12), including the means for its control, with optimum conditions for the clutch actuation is achieved. …<IMAGE>…

Description

Die Erfindung bezieht sich auf eine Vibrationswalze nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a vibratory roller according to the preamble of patent claim 1.

Vibrationswalzen dieser Art sind bekannt. Sie werden von der Anmelderin hergestellt und vertrieben und sind in deren Prospekt ( W 680/12-10-10.87 vom Oktober 1987 be­schrieben).Vibratory rollers of this type are known. They are manufactured and distributed by the applicant and are described in their prospectus (W 680 / 12-10-10.87 from October 1987).

Bei den bekannten Vibrationswalzen wird die Schaltkupplung mechanisch betätigt. Die mechanische Betätigungsvorrich­tung und die für mechanische Betätigung ausgerüstete Kupp­lung sind sperrig, so daß ein zweiter Abtrieb am Ver­brennungsmotor auf der der Verstellpumpe entgegenge­setzten Seite erforderlich war und die Motorwelle auch dort herausgeführt werden mußte. Darüber hinaus haben die über das Schaltgestänge vom Bedienungsmann mechanisch direkt betätigbaren Schaltkupplungen den Nachteil, daß nicht gewährleistet ist, daß sie schonend, d.h. insbeson­dere weitgehend schlupffrei , betätigt werden.In the known vibratory rollers, the clutch is operated mechanically. The mechanical actuation device and the clutch equipped for mechanical actuation are bulky, so that a second output on the internal combustion engine was required on the opposite side of the variable displacement pump and the motor shaft also had to be brought out there. In addition, the shift clutches which can be actuated mechanically directly by the operator via the shift linkage have the disadvantage that it is not guaranteed that they are actuated gently, ie in particular largely without slippage.

Der Erfindung liegt die Aufgabe zugrunde, eine Vibra­tionswalze gemäß dem Oberbegriff des Patentanspruchs zu schaffen, bei der die Schaltkupplung insbesondere ohne die Notwendigkeit einer Herausführung der Motorwelle auf bei­den Seiten der Brennkraftmaschine raumsparend in einem kompakten Gefüge auf der gleichen Seite wie die Verstell­pumpe angeordnet und überdies so eingerichtet ist, daß Fehlbedienungen ausgeschlossen sind.The invention has for its object to provide a vibrating roller according to the preamble of claim, in which the clutch is arranged in a space-saving manner in a compact structure on the same side as the variable displacement pump, in particular without the need for the motor shaft to be led out, and moreover is set up that operating errors are excluded.

Die vorstehende Aufgabe wird durch die im Kennzeichnungs­teil des Patentanspruchs 1 genannten Merkmale gelöst.The above object is achieved by the features mentioned in the characterizing part of patent claim 1.

Hydraulisch betätigbare Schaltkupplungen sind für sich bekannt. Sie haben einen kleineren Raumbedarf als mecha­nisch betätigbare Kupplungen und können über raumsparend verlegbare Druckmittelleitungen praktisch von jeder gewünschten Stelle an der Vibrationswalze her leicht be­dient werden. Nachteilig ist, daß sie einen hydraulischen Druckgeber erfordern, wofür sich der vorhandene Druckmit­telkreis der Verstellpumpe wegen der besonderen , in ihm vorherrschenden Druckverhältnisse , insbesondere der be­triebsbedingten Druckschwankungen bis herunter zum Leer­laufdruck nicht eignet, so daß bisher vom Einsatz hydrau­lisch betätigbarer Schaltkupplungen Abstand genommen wur­de. Die Erfindung beruht auf der Erkenntnis, daß die mit der Verstellpumpe in einer Pumpeneinheit zusammengeschlos­sene Füllpumpe als Druckgeber für die Schaltkupplung herangezogen werden kann, wenn ihr in die Pumpeneinheit integrierter Druckmittelkreis von außen zugänglich gemacht wird.Hydraulically actuated clutches are known per se. They take up less space than mechanically actuated couplings and can be easily operated from any desired location on the vibrating roller using space-saving pressure medium lines. The disadvantage is that they require a hydraulic pressure transducer, for which the existing pressure medium circuit of the variable displacement pump is not suitable because of the special pressure conditions prevailing in it, in particular the operational pressure fluctuations down to idle pressure, so that the use of hydraulically actuated clutches has so far been avoided. The invention is based on the knowledge that the filling pump combined with the variable pump in a pump unit can be used as a pressure transmitter for the clutch if it is made accessible from the outside to the integrated pressure medium circuit in the pump unit.

Die Erfindung wird nachstehend anhand der Zeichnung an einem Ausführungsbeispiel noch näher erläutert.The invention is explained in more detail below with reference to the drawing using an exemplary embodiment.

In der Zeichnung zeigt jeweils in schematischer Darstellung:

  • Fig. 1 eine Vibrationswalze gemäß der Erfindung in Seitenansicht, wobei die über die Bandagen parallel zur Fahrtrichtung vorstehenden Teile weggelassen sind,
  • Fig. 2 die Vibrationswalze nach Fig. 1 im Querschnitt ent­lang der Schnittlinie II-II in Fig. 1, und
  • Fig. 3 das Schaltschema der Hydraulikkreisläufe bei der Vibrationswalze nach Fig. 1 und 2.
The drawing shows in a schematic representation:
  • 1 is a side view of a vibratory roller according to the invention, the parts projecting beyond the bandages parallel to the direction of travel being omitted,
  • Fig. 2 shows the vibratory roller according to Fig. 1 in cross section along the section line II-II in Fig. 1, and
  • 3 shows the circuit diagram of the hydraulic circuits in the vibrating roller according to FIGS. 1 and 2.

Die in Fig. 1 und 2 dargestellte Vibrationswalze weist einen starren Maschinenrahmen 1 auf, in dem eine vordere und eine hintere Walzenbandage 2a bzw. 2b unlenkbar aber drehbar gelagert sind. Auf dem Rahmen 4 ist eine Brenn­kraftmaschine 3, hier ein Dieselmotor, mit parallel zu den Bendagenachsen angeordneter Motorwelle 3a außermittig so befestigt, daß er auf der für den Betrachter der Fig.2 linken Seite nicht über die übrigen Teile der Vibrations­walze vorsteht. Der Motor 3 erstreckt sich etwa über die halbe Walzenbreite, so daß auf der für den Betrachter der Fig. 2 rechten Seite von ihm ein sich ebenfalls über etwa die halbe Walzenbreite erstreckender freier Raum bis zur rechten seitlichen Walzenbegrenzung vorhanden ist. Die Motorwelle 3a ist nur auf dieser rechten Seite aus dem Motor 3 herausgeführt und treibt dort eine Pumpenein­heit 4 mit zu ihr koaxialer Welle 4a an, die eine Ver­stellpumpe 5 mit veränderlicher Verdrängung und umsteuer­barer Förderrichtung sowie eine Füllpumpe 6 umfaßt. Die Pumpeneinheit 4 ist unmittelbar an den Motor 3 ange­flanscht. Auf der von dem Motor 3 entfernten Seite ist die Welle 4a der Pumpeneinheit aus dieser herausgeführt und treibt das Eingangsglied 7a einer hydraulisch betätigbaren Schaltkupplung 7 an, die ein als Trommel ausgeführtes Ausgangsglied 7b aufweist und ihrerseits an die Pumpenein­ heit 4 angeflanscht ist. In der Zeichnung sind die außen­liegenden Hauptanschlüsse der Verstellpumpe 5, die in ver­tauschbarer Weise den Druckanschluß und den Sauganschluß des von ihr beaufschlagten Druckmittelkreises bilden, mit A und B bezeichnet. Ein weiterer , aus der Pumpeneinheit 4 herausgeführter Druckmittelanschluß ist mit der perma­nenten Druckseite der Füllpumpe verbunden. Die Schalt­kupplung 7 hat einen einzigen Druckmittelanschluß D′; wenn dieser hydraulisch mit Druck beaufschlagt wird, schaltet die Schaltkupplung 7 durch, so daß dann und nur dann das Eingangsglied 7a der Schaltkupplung 7 mit deren Ausgangs­glied 7b drehfest verbunden ist.The vibrating roller shown in FIGS. 1 and 2 has a rigid machine frame 1, in which a front and a rear roller drum 2a or 2b are non-steerably but rotatably mounted. On the frame 4, an internal combustion engine 3, here a diesel engine, is attached off-center with a motor shaft 3a arranged parallel to the Bendagen axes so that it does not protrude beyond the remaining parts of the vibratory roller on the left-hand side for the viewer of FIG. The motor 3 extends approximately over half the roll width, so that on the right-hand side of the viewer of FIG. 2 there is a free space also extending over approximately half the roll width up to the right-hand side roll limitation. The motor shaft 3a is led out of the motor 3 only on this right-hand side and drives a pump unit 4 there with a shaft 4a coaxial with it, which comprises a variable displacement pump 5 with variable displacement and reversible conveying direction and a filling pump 6. The pump unit 4 is flanged directly to the motor 3. On the side remote from the motor 3, the shaft 4a of the pump unit is led out of it and drives the input member 7a of a hydraulically actuated clutch 7, which has an output member 7b designed as a drum and in turn to the pumps unit 4 is flanged. In the drawing, the outer main connections of the variable displacement pump 5, which form the pressure connection and the suction connection of the pressure medium circuit acted upon by them, are designated A and B. Another pressure medium connection led out of the pump unit 4 is connected to the permanent pressure side of the filling pump. The clutch 7 has a single pressure medium connection D '; when this is pressurized hydraulically, the clutch 7 switches through, so that then and only then is the input member 7a of the clutch 7 rotatably connected to its output member 7b.

Das trommelförmige Ausgangsglied 7b der hydraulisch be­tätigbaren Schaltkupplung 7 ist mit Keilnuten versehen, in denen Keilriemen 8 laufen, die eine Keilriemenscheibe 9 am Ende einer Zwischenwelle 10 antreiben, die sich parallel zur Motorwelle 3a unter dem Motor 3 von der für den Betrachter der Fig. 2 rechten Seite der Vibrations­walze zur linken erstreckt und im Walzenrahmen 1 jeweils in der Nähe ihrer Enden drehbar gelagert ist. Auf diese Weise wird das Abtriebsmoment der Schaltkupplung 7 zur anderen Seite der Vibrationswalze übertragen und treibt dort über ein in der Zeichnung nur schematisch angedeute­tes Keilriemengetriebe 11 die in den Bandagen 2a und 2b befindlichen Unwuchtvibratoren 12a an.The drum-shaped output member 7b of the hydraulically actuated clutch 7 is provided with V-grooves in which V-belts 8 run, which drive a V-belt pulley 9 at the end of an intermediate shaft 10 which runs parallel to the motor shaft 3a under the motor 3 from that for the viewer of FIG. 2 extends right side of the vibrating roller to the left and is rotatably supported in the roller frame 1 near its ends. In this way, the output torque of the clutch 7 is transmitted to the other side of the vibrating roller and drives the unbalance vibrators 12a located in the bandages 2a and 2b via a V-belt transmission 11, which is only schematically indicated in the drawing.

Den Drehantrieb der Bandagen 2a und 2b besorgt über ein in Fig. 2 der Zeichnung ebenfalls nur schematisch ange­deutetes Zahnradgetriebe 13 ein zwischen den Bandagen un­ter dem Dieselmotor 3 am Walzenrahmen 1 befestigter hy­draulischer Fahrantriebsmotor 14 fester Verdrängung, der in üblicher Weise zwei Druckmittel-Hauptanschlüsse A′ und B′ aufweist, die, wie in Fig. 3 zu sehen, mit den Haupt­anschlüssen A bzw. B der Verstellpumpe 5 über in den Fig. 1 und 2 nicht dargestellte Druckmittelleitungen ver­bunden sind. Die Drehzahl und die Drehrichtung des Hy­draulikmotors 14 hängen von dem jeweils eingestellten Fördervolumen bzw. der jeweils gewählten Förderrichtung der Verstellpumpe 5 ab und bestimmen die Fahrgeschwindig­keit bzw. die Fahrtrichtung der Vibrationswalze.The rotary drive of the drums 2a and 2b is provided by a gear mechanism 13, which is also only schematically indicated in FIG. 2 of the drawing, a hydraulic drive motor 14 fixed displacement between the drums under the diesel engine 3 on the roller frame 1 and which, in the usual way, has two main pressure medium connections A ' and B ', which, as can be seen in Fig. 3, with the main connections A and B of the variable pump 5 in the 1 and 2 pressure medium lines, not shown, are connected. The speed and the direction of rotation of the hydraulic motor 14 depend on the respectively set delivery volume or the respectively selected delivery direction of the variable pump 5 and determine the driving speed or the driving direction of the vibrating roller.

Die Fig. 3 zeigt das Schaltschema der Hydraulikkreise bei der Vibrationswalze nach Fig. 1 und 2. Die in Fig. 2 mit Großbuchstaben bezeichneten hydraulischen Anschlüsse an der Pumpeneinheit 4, der Schaltkupplung 7 und dem Fahran­triebsmotor 14 sind in Fig. 3 mit den gleichen Buchstaben bezeichnet.3 shows the circuit diagram of the hydraulic circuits in the vibrating roller according to FIGS. 1 and 2. The hydraulic connections on the pump unit 4, the clutch 7 and the drive motor 14, which are designated with capital letters in FIG. 2, are given the same letters in FIG. 3 designated.

Die Verstellpumpe 5 und die Füllpumpe 6 sind in der üblichen Weise zusammengeschaltet. Die Saugseite der Füllpumpe 6 ist mit einem Ölvorratsbehälter (Sumpf) 15 verbunden. Ihre Druckseite ist jeweils über ein Rückschlagventil 16a bzw. 16b an die eine bzw. andere der beiden von der Verstell­pumpe 5 zu den Anschlüssen A und B führenden, in die Pumpeneinheit 4 integrierten Verbindungsleitungen ange­schlossen. Die Rückschlagventile 16a und 16b öffnen in Richtung zu diesen Verbindungsleitungen, so daß eine permanente Füllung des über die Anschlüsse A, A′, B′ und B gehenden Druckmittel-Hauptkreises zwischen der Verstell­pumpe 5 und dem hydraulischen Fahrantriebsmotor 14 ge­währleistet ist und die Kolbenköpfe der Verstellpumpe stets unter einem gewissen Druck in Anlage an deren Schräg­scheibe gehalten werden. Druckbegrenzungsventile 17a, 17b begrenzen den maximalen Druck, der im jeweiligen Druck­zweig des Hydraulik-Hauptkreises zwischen der Verstell­pumpe 5 und dem Fahrantriebsmotor 14 auftreten kann. Der Maximaldruck im Druckkreis der Füllpumpe 6 wird durch ein Druckbegrenzungsventil 18 begrenzt. Die in Fig. 3 ge­strichelt eingetragenen Verbindungsleitungen sind Ent­ lastungs- bzw. Leckölleitungen, die zum Sumpf 15 zurück­führen. Je nach Einstellung der Neigungsrichtung der Schrägscheibe der Verstellpumpe 5 stellt der über den Anschluß B gehende Zweig den Druckzweig und der über den Anschluß A gehende Zweig den Saugzweig oder umgekehrt dar. Die Drehzahl des Fahrantriebsmotors 14 hängt vom Fördervolumen der Verstellpumpe 5 ab, das über den Neigungswinkel der Schrägscheibe wählbar ist. Der Druck im Druckzweig des Haupt-Druckmittelkreises richtet sich bis zum zugelassenen Höchstwert nach dem Fahrwiderstand , der auf die Welle des Fahrantriebsmotors 14 einwirkt, unterliegt also erheb­lichen Schwankungen, die oberhalb des durch das Begren­zungsventil 18 vorgegebenen Druckes der Füllpumpe 6 durch die Rückschlag-ventile 16a und 16b von der letzteren fern­gehalten werden, so daß der Füllpumpendruck einen im we­sentlichen konstanten Wert hat. Bis zu den Anschlüssen A und B und einem Anschluß F für eine äußere Entlastungs- und Leckölleitung sind die bisher besprochenen Verbin­dungswege mit den eingebauten Ventilen in die Pumpenein­heit 4
integriert. Darüber hinaus ist in der Pumpenein­heit 4 zusätzlich noch ein Austrittskanal vorgesehen, der die Druckseite der Füllpumpe 6 mit dem äußeren Druckmit­telanschluß C verbindet. Dieser ist über eine außenliegen­de Verbindungsleitung an den einen Eingang C′ eines zwei Schaltpositionen aufweisenden Schaltventils 19 angeschlos­sen, das einen zweiten Druckmittelanschluß E aufweist, der über eine Druckmittelleitung mit dem Sumpf 15 in Verbin­dung steht. Ein dritter Druckmittelanschluß D des Schalt­ventils 19 ist über eine Druckmittelleitung mit dem Druck­mittelanschluß D′ der Schaltkupplung 7 verbunden. Die bei­den Schaltpositionen des Schaltventils 19 sind mittels eines Hebels 20 wählbar, der, ebenso wie das Schaltventil 19, an der Vibrationswalze angebracht ist und sich im Zu­griffsbereich des Walzenführers befindet. In der einen Schaltposition sperrt das Schaltventil 19 den Druckmittel­anschluß C′ und verbindet die Anschlüsse D und E, während es in der anderen Schaltstellung den Anschluß E sperrt und die Anschlüsse C′ und D verbindet. In der erstgenannten Schaltposition ist demgemäß der Anschluß D′ vom Druck ent­lastet und damit die Schaltkupplung 7 getrennt, und in der letztgenannten Schaltposition steht der Anschluß D′ von der Füllpumpe 6 her unter Druck , so daß die Schalt­kupplung 7 durchschaltet und eine drehfeste Verbindung zwischen dem Eingangsglied 7a und dem Ausgangsglied 7b hergestellt wird und der Dieselmotor 3 dann auch die Un­wuchtvibratoren 12 in den Bandagen 2a und 2b antreibt.The variable displacement pump 5 and the filling pump 6 are interconnected in the usual way. The suction side of the filling pump 6 is connected to an oil reservoir 15. Its pressure side is in each case connected via a check valve 16a or 16b to one or the other of the two connecting lines leading from the variable pump 5 to the connections A and B and integrated into the pump unit 4. The check valves 16a and 16b open in the direction of these connecting lines, so that a permanent filling of the pressure medium main circuit via the connections A, A ', B' and B between the variable displacement pump 5 and the hydraulic drive motor 14 is ensured and the piston heads of the variable displacement pump are always held under a certain pressure in contact with their swashplate. Pressure limiting valves 17a, 17b limit the maximum pressure that can occur in the respective pressure branch of the main hydraulic circuit between the variable displacement pump 5 and the travel drive motor 14. The maximum pressure in the pressure circuit of the filling pump 6 is limited by a pressure relief valve 18. The connecting lines shown in broken lines in FIG. 3 are Ent load or leakage oil lines leading back to the sump 15. Depending on the setting of the direction of inclination of the swash plate of the variable displacement pump 5, the branch going through connection B represents the pressure branch and the branch going through connection A represents the suction branch or vice versa. The speed of travel motor 14 depends on the delivery volume of variable displacement pump 5, which is via the Tilt angle of the swash plate is selectable. The pressure in the pressure branch of the main pressure medium circuit depends up to the permitted maximum value on the driving resistance, which acts on the shaft of the drive motor 14, is therefore subject to considerable fluctuations, which are above the pressure of the filling pump 6 by the check valves 16a predetermined by the limiting valve 18 and 16b are kept away from the latter so that the fill pump pressure has a substantially constant value. Up to the connections A and B and a connection F for an external relief and leakage oil line are the previously discussed connection paths with the built-in valves in the pump unit 4
integrated. In addition, an outlet channel is also provided in the pump unit 4, which connects the pressure side of the filling pump 6 to the external pressure medium connection C. This is connected via an external connecting line to the one input C 'of a switching valve 19 having two switching positions, which has a second pressure medium connection E, which is connected to the sump 15 via a pressure medium line. A third pressure medium connection D of the switching valve 19 is connected via a pressure medium line to the pressure medium connection D 'of the clutch 7. The two switching positions of the switching valve 19 can be selected by means of a lever 20 which, like the switching valve 19, is attached to the vibrating roller and is located in the access area of the roller operator. In one Switching position, the switching valve 19 blocks the pressure medium connection C 'and connects the connections D and E, while in the other switching position it blocks the connection E and connects the connections C' and D. Accordingly, in the first-mentioned switching position, the connection D 'is relieved of pressure and thus the clutch 7 is disconnected, and in the latter switching position, the connection D' is under pressure from the filling pump 6, so that the clutch 7 is switched through and a rotationally fixed connection between the Input member 7a and the output member 7b is produced and the diesel engine 3 then also drives the unbalance vibrators 12 in the bandages 2a and 2b.

Das unmittelbare Aneinanderflanschen des Motors 3, der Pumpeneinheit 4 und der Schaltkupplung 7 , das durch den Einsatz einer hydraulisch betätigbaren Schaltkupplung unter Heranziehung der Füllpumpe als Druckmittelquelle für diese ermöglicht ist, ergibt einen geschützten, kompakten Aufbau von geringer Störanfälligkeit bei optimaler Funk­tionstüchtigkeit, dessen Raumbedarf nur so groß ist, daß er leicht innerhalb der verfügbaren Walzenbreite stirnsei­tig vor dem Dieselmotor 3 untergebracht werden kann, wenn dieser seitlich gegen die Walzenmitte versetzt ange­ordnet wird, was wegen der unverbauten Stirnseite des Motors auf der anderen Seite von diesem optimal ermöglicht ist.The direct flanging of the motor 3, the pump unit 4 and the clutch 7, which is made possible by the use of a hydraulically actuated clutch using the filling pump as a pressure medium source for this, results in a protected, compact structure with low susceptibility to malfunction with optimal functionality, the space requirement of which is only is so large that it can easily be accommodated in front of the diesel engine 3 within the available roller width if this is laterally offset from the center of the roller, which is optimally possible because of the unobstructed end face of the engine on the other side of the latter.

Claims (1)

Vibrationswalze mit hydrostatischem Bandagen-Fahrantrieb mittels mindestens eines Hydromotors , der an eine vom Bedienungsmann steuerbare, von einer Brennkraftmaschine 3, insbesondere einen Dieselmotor, angetriebene Verstell­pumpe veränderbarer Verdrängung angeschlossen ist, die als Schrägscheibenpumpe mit Füllpumpe 6 für den Saughub der Verdrängerkolben ausgeführt ist, und bei der die Unwucht­rüttler (12) über einen von der Antriebswelle 3a der Brennkraftmaschine 3 abgeleiteten , gesonderten mecha­nischen Kraftübertragungsweg mit eingebauter, vom Be­dienungsmann betätigbarer Schaltkupplung 7 angetrieben sind, dadurch gekennzeichnet, daß die Schaltkupp­lung (7) a) an die die Verstellpumpe (5) und die Füllpumpe (6) umfassende Pumpeneinheit (4) angeflanscht und ihr Eingangsglied (7a) mit der Pumpenwelle (4a) gekup­pelt ist, und b) einen hydrostatisch betätigbaren Schaltmechanismus aufweist, der über ein vom Bedienungsmann betätig­bares Schaltventil wahlweise mit der Druckseite der Füllpumpe (6) oder mit dem Sumpf (15) der Pumpen­einheit (4) verbindbar ist. Vibration roller with hydrostatic drum drive by means of at least one hydraulic motor, which is connected to a variable displacement pump which is controllable by the operator and driven by an internal combustion engine 3, in particular a diesel engine, and which is designed as a swash plate pump with filling pump 6 for the suction stroke of the displacement piston, and at of the unbalanced mass vibration generator (12), separate mechanical transmission are driven by built-actuated by the operator shift clutch 7 discharged via one of the input shaft 3a of the engine 3, characterized in that the clutch (7) a) flanged to the pump unit (4) comprising the variable displacement pump (5) and the filling pump (6) and its input member (7a) is coupled to the pump shaft (4a), and b) has a hydrostatically actuated switching mechanism which can be connected to the pressure side of the filling pump (6) or to the sump (15) of the pump unit (4) via a switching valve which can be actuated by the operator.
EP88120969A 1988-02-13 1988-12-15 Vibrating roller Expired - Lifetime EP0328767B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3804620A DE3804620A1 (en) 1988-02-13 1988-02-13 VIBRATION ROLLER
DE3804620 1988-02-13

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EP0328767A1 true EP0328767A1 (en) 1989-08-23
EP0328767B1 EP0328767B1 (en) 1991-09-04

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EP88120969A Expired - Lifetime EP0328767B1 (en) 1988-02-13 1988-12-15 Vibrating roller

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US (1) US4962644A (en)
EP (1) EP0328767B1 (en)
JP (1) JPH0649961B2 (en)
DE (2) DE3804620A1 (en)
ES (1) ES2026629T3 (en)

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CN101824792A (en) * 2010-03-01 2010-09-08 江阴柳工道路机械有限公司 Constant speed device for tandem vibratory roller
CN101824793A (en) * 2010-03-01 2010-09-08 江阴柳工道路机械有限公司 Shifting device for tandem vibratory roller

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JPH0732221Y2 (en) * 1989-12-05 1995-07-26 株式会社神崎高級工機製作所 Hydraulic supply for work vehicles
US5513438A (en) * 1994-08-29 1996-05-07 Emmons; J. Bruce Vehicle wheel alignment system
US5938224A (en) * 1996-04-08 1999-08-17 Brackett; Douglas C. Hydraulic bicycle with conjugate drive motors and variable stroke crankshaft
US5772225A (en) * 1996-04-08 1998-06-30 Brackett; Douglas C. Hydraulic bicycle with conjugate drive motors

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Publication number Priority date Publication date Assignee Title
CN101824792A (en) * 2010-03-01 2010-09-08 江阴柳工道路机械有限公司 Constant speed device for tandem vibratory roller
CN101824793A (en) * 2010-03-01 2010-09-08 江阴柳工道路机械有限公司 Shifting device for tandem vibratory roller

Also Published As

Publication number Publication date
DE3804620A1 (en) 1989-08-24
JPH0649961B2 (en) 1994-06-29
EP0328767B1 (en) 1991-09-04
ES2026629T3 (en) 1992-05-01
US4962644A (en) 1990-10-16
DE3864678D1 (en) 1991-10-10
JPH01315504A (en) 1989-12-20

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