EP3719210B1 - Quick change pivot motor combination - Google Patents

Description

The invention relates to a quick coupler / swivel motor combination according to the preamble of claim 1.

Generic quick coupler / swivel motor combinations are used to couple and uncouple attachments to or from a dipper stick of an earth-moving machine, such as an excavator. The dipper stick can be pivoted in a forward rotation plane by means of the excavator hydraulics, so that the attached attachment, for example a backhoe or the like, can be pivoted about a rotation axis at the other end of the dipper stick in the forward rotation plane.

In addition to the mobility in the forward rotation plane, generic quick coupler / swivel motor combinations provide a further degree of freedom of movement for the coupled implement, namely lateral pivoting about an axis of rotation lying in the forward rotation plane, so that the coupled, laterally pivoted implement, for example a digging bucket, starts Inclined planes, for example ditch embankments, can be worked on to the horizontal.

For this purpose, known quick coupler / swivel motor combinations each have a swivel motor and a hydraulically or mechanically operated quick changer which is suspended below the swivel motor and which can be swiveled laterally out of the forward rotation plane by means of the swivel motor. When the quick coupler is not swiveled out, the forward rotation plane of the dipper stick corresponds to a swivel axis plane extending vertically through the quick hitch swivel motor combination, in which the swivel axis about which the quick hitch can be swiveled out by the swivel motor is located. If the dipper stick with the attached quick hitch swivel motor combination is held accordingly, the forward rotation plane and thus the swivel axis plane is aligned perpendicular to the surface of the earth.

The international patent application WO2008 / 109963 A1 shows a quick hitch swivel motor combination with a swivel motor and a swivel motor under the swivel motor suspended, hydraulically operated quick coupler.

The European patent specification EP 2 327 840 B1 shows a generic quick hitch swivel motor combination with a hydraulically operated quick hitch. The swivel motor has a motor housing in which a motor shaft is arranged rotatably by hydraulics about a swivel axis lying horizontally in the swivel axis plane. A piston arranged coaxially around the motor shaft is used to rotate the motor shaft, which engages with helical toothing in assigned helical toothing areas on the inner circumference of the motor housing or on the outer circumference of the motor shaft and a translational movement induced by hydraulic pressure on its front or rear end by means of the helical toothing in a rotary movement the motor shaft translated.

At the top of the motor housing, two side tabs extending parallel to the plane of the pivot axis are welded, each of which has two hinge eyes, to which they can be attached by means of mounting bolts on the free end of the dipperstick and another actuator of the excavator kinematics.

The motor shaft penetrates the motor housing on its front and back, with a front suspension plate being non-rotatably attached to a front end of the motor shaft, which protrudes from the front end of the motor housing and a rear suspension plate is non-rotatably attached to a rear end of the motor shaft, wherein the rear end of the motor shaft protrudes from the rear end of the motor housing. The two suspension plates thus extend downwards transversely to the plane of the swivel axis and serve to hang the quick coupler under the swivel motor.

The quick coupler has a frame that includes two side tabs extending parallel to the pivot axis plane on both sides of the swivel axis plane in the non-swiveled-out state, with a receiving claw being provided at the front end of the two side tabs so that an associated shaft or axis on the attachment is gripped can be. Facing away from the claws, a hydraulically movable locking claw is received on the frame of the quick coupler, so that the quick coupler is attached to a second locking axis provided on the attachment can be locked or unlocked by moving the locking claw hydraulically along the direction of the pivot axis.

This is done by a double-acting hydraulic cylinder held between the two side plates of the quick coupler frame, which can be moved towards the front end or the rear end along the direction of the pivot axis by pressurizing a first pressure chamber or a second pressure chamber.

For the hydraulic actuation of the double-acting hydraulic cylinder on the quick coupler, the pressurized hydraulic oil of the earth-moving machine, which is made available via hydraulic feed lines from the dipperstick, must be fed into the two pressure chambers in the quick coupler. In earlier quick coupler / swivel motor combinations, including those made by the local applicant, hose lines outside the housing were provided to guide the hydraulic oil from the connection above the swivel motor into the two pressure chambers in the quick coupler, i.e. below the swivel motor.

These hose lines at the interface between the dipperstick and the attachment are constantly exposed to the risk of damage during rough work. According to the EP 2 327 840 B1 Therefore, hydraulic lines inside the housing are provided from the top of the engine into the pressure chambers of the quick coupler. For this purpose, the motor shaft has two rotary feedthroughs at one end, which on the top are connected to hydraulic connections on the dipperstick side via channels running through the wall of the motor housing, and on the bottom via themselves in the motor shaft and the associated suspension plate up to the quick coupler and there into the pressure chambers extending hydraulic channels.

Without the housing-internal routing of the two rotary feed-through channels, hydraulic lines would be necessary outside the swivel motor to the quick coupler. These hydraulic lines would then be exposed to the risk of being pinched or torn off during the pivoting movement. Even during normal work, such as digging, such cables could be jammed or torn off; falling stones on the lines could not be ruled out either.

However, the quick coupler is a safety-critical component, so that a permanent hydraulic pressure must be guaranteed so that the attached attachment cannot become loose and fall down, which could otherwise lead to serious injuries for personnel in the immediate vicinity.

While the housing-internal fluid channel guide according to the EP 2 327 840 B1 remedies this weak point in earlier quick coupler / swivel motor combinations, there is a need for further improvement in terms of service life, response behavior and energy consumption.

It is therefore the object of the present invention to develop a quick coupler / swivel motor combination of the generic type in such a way that service life, response behavior and the energy consumption required for operation are improved.

This object is achieved with the features of claim 1.

According to the invention, in a quick coupler / swivel motor combination of the generic type, which has a corresponding number of internal fluid lines for supplying the number of pressure chambers provided on the quick coupler with hydraulic oil, which connects the number of pressure chambers to a corresponding number of quick coupler hydraulic inputs on the top of the motor housing, proposed to provide at most a single rotary leadthrough for the number of fluid lines on each of the two sliding bearings, that is to say in the region of each shaft end.

Because with generic quick coupler / swivel motor combinations, premature failure of the swivel motor has occurred again and again, which, as costly tests have shown, is generally due to the torsional load on the shaft and in particular to the torsional load on the shaft end provided with sealing ring packs for both oil passages was. If only one rotary feedthrough is provided for each shaft end or sliding bearing provided there, the torsional load generated by this is distributed evenly over the shaft, which leads to a significantly longer service life and better service life of the swivel motor. At the same time, lower torque losses than before are achieved and, above all, a better response behavior of the swivel motor is achieved, in particular when the hydraulically triggered swivel movement is started, because the motor shaft is gentler starts up. In addition, two oil supply connections are no longer required in the area of the shaft end provided with the two rotary feedthroughs for the hydraulic quick coupler or the sliding bearing of the shaft there on the motor housing, so that the length of the swivel motor can be reduced, the improved load distribution on the motor shaft being smaller overall Components on the swivel motor allows.

According to a first aspect of the invention, which is particularly suitable for the small excavator segment, it is proposed to implement the inventive measures to use a single-acting linear actuator on the quick coupler, in which the hydraulics only work in one direction, namely against the biasing force of a mechanical spring arrangement which actuates the linear actuator in the other direction when the hydraulic pressure is switched off and holds it in this position after reaching the desired position until the linear actuator is actuated again in one direction by hydraulic pressure, for example in the unlocking direction.

This means that the use of a second fluid line can be dispensed with, so that only one fluid line with a single rotary feedthrough is required and thus not only the overall torsional load on the shaft of the swivel motor is reduced, but also the structural complexity compared to two fluid lines inside the housing and, in particular, to the two rotary feedthroughs required for this on the motor shaft is halved.

In particular, the rear end of the shaft has proven to be a suitable location for placing the rotary feedthrough on the plain bearing there, because the hydraulic hose coming from the excavator arm or dipperstick can be better protected against damage in rough work if the oil supply connection is provided there. The rotary feedthrough is therefore advantageously formed on the sliding bearing on the rear shaft flange. This is because there is less risk of damage at the rear of the motor housing than at the front, and a hose guide with a large radius for the hydraulic hose coming from the dipperstick can be achieved.

The rear shaft flange is advantageously a bottom bearing flange formed on a bottom bearing screwed onto the shaft.

According to a second aspect of the invention, on the other hand, as usual, a double-acting linear actuator is provided on the quick coupler, which is operated in both directions - locking and unlocking - by hydraulic pressure and therefore also requires two fluid lines from two oil supply connections on the top of the motor to supply the two pressure chambers required for this .

The two rotary feedthroughs required for this are now distributed to the two available shaft ends or the slide bearings provided there on the motor shaft of the swivel motor, in that a front fluid line has a front rotary feedthrough on the slide bearing located in the area of the front shaft end or on the front shaft flange , whose annular oil guide groove leads via a front motor shaft-internal line section into a front suspension plate internal line section running internally in the front suspension plate, a rear fluid line having a rear rotary feedthrough on the plain bearing located in the area of the rear shaft end or on the rear shaft flange, the annular oil guide groove of which via a rear engine shaft-internal line section leads into an internally running in the rear suspension plate, rear suspension plate-internal line section.

Here, too, the rear shaft flange is advantageously a floor bearing flange formed on a floor bearing screwed onto the shaft.

The front line section inside the suspension plate can then open out on the front of the quick changer into a front line section inside the quick changer frame, which leads from there to one of the two pressure chambers required for operating the double-acting linear actuator, the rear line section inside the suspension plate on the rear of the quick changer into a rear line section inside the quick changer frame can open, which continues from there into the other of the two pressure chambers.

This enables the oil to be supplied to the two pressure chambers of the quick coupler via the rotary feedthroughs at the opposite ends of the motor shaft without the need for structurally complex ducts inside the motor shaft from the rotary feedthrough on the rear of the motor shaft to the front suspension plate. In the further development of the invention according to the first aspect, on the other hand, only the front or preferably only the rear fluid line is advantageously provided.
The quick coupler frame can advantageously comprise a base plate which is welded to the underside end faces of the suspension plates. As a result, the duct routing through the suspension plates down to the quick coupler can be constructed very simply and thus inexpensively. All that is required is a connecting bore leading upwards from the underside of the end face of the respective suspension plate, which is connected at the bottom to a respective quick changer frame-internal line section, which in turn can be incorporated into the base plate. At the upper end of the connecting bore, a further bore can then establish the connection to the associated, motor-shaft-internal line section transversely to the connecting bore in the direction of the motor shaft or the shaft flange. This further, transverse bore can be designed as a receiving bore, in which an O-ring holder with a number of corresponding sealing rings can advantageously be inserted, which is penetrated by channels that connect the respective motor shaft-internal line section and the associated mounting sheet-internal sheet metal section and at the same time seals the front or rear fluid line against oil loss at the interface between the mounting plate and the motor shaft.

The line sections within the quick changer frame can include a number of horizontally running oil guide grooves built into the base plate, which open at one end into a connecting bore that runs transversely to the oil guide groove and into the associated pressure chamber and, at the other end, into a line section emerging from the base plate on the top side, which into one in the associated suspension plate connecting hole leading upwards opens. The number of line sections inside the quick changer frame is thus completely formed on the base plate, so that a short and structurally simple line routing in the quick changer frame results, be it in a further development of the invention with a front and a rear fluid line for feeding two pressure chambers of a double-acting linear actuator or in a further development of the invention with only one front or one rear fluid line for charging a pressure chamber of a single-acting linear actuator.

Within the scope of the invention, it would also be conceivable to use two or more single or double-acting linear actuators for locking or unlocking the one or more locking elements of the quick changer. The quick changer frame-internal line sections of the front and / or rear fluid line could then include, for example, two oil guide grooves that open at one end into different connection bores leading into different pressure chambers and the other end into the same line section emerging from the top of the base plate, the same into the same Suspension plate leads upwards connecting hole opens.

Furthermore, according to the invention, the quick changer has an engagement arrangement with claws that can attack a counter-attack arrangement, preferably designed as a shaft, on the attachment to be received, as well as a locking element actuated via your linear actuator for locking and unlocking an associated counter-locking element on the attachment, for example a number Locking bolts displaceable by a linear actuator for sliding in and out of corresponding recesses in a wall of the attachment parallel to the shaft. Of course, the engagement arrangement and the locking element of the quick changer can also be designed differently, depending on how the counter-attack arrangement and the counter-locking element are designed on the attachment to be accommodated. For example, claws and locking bolts would also be included, which are attached to an adapter frame of an attachment according to FIG DE 19 2005 037 105 C5 can attack.

The horizontally running oil guide groove or the horizontally running oil guide grooves can each have two steps in cross section, a groove cover being arranged in the upper step and welded to the base plate, so that the lower step of the oil guide groove forms an oil-tight channel inside the base plate, which is sealed oil-tight towards the top by the groove cover. Of course, it would also be conceivable to work the respective oil guide groove into the base plate from below and then weld a groove bottom into the first stage of the respective oil guide groove instead of a groove cover.

To rotate the motor shaft in relation to the motor housing and thus to pivot the quick coupler suspended below with the one received on it As an attachment, the swivel motor can advantageously have a piston arranged radially between the motor housing and the motor shaft and axially between the front shaft flange and the rear shaft flange. The piston can form a coarse thread pairing with the motor housing and a rising thread pairing in opposite directions with the motor shaft, whereby a front motor pressure chamber can be arranged on the front side of the piston and a rear pressure chamber can be arranged on the rear side of the piston, which can be connected to the motor hydraulic inlets on the top of the motor housing Hydraulic supply of the earth-moving machine can be connected in order to bring about a translational movement of the piston by hydraulic pressure on the front or rear side of the piston and thus a rotary movement of the motor shaft via the coarse thread pairings.

In the context of the invention, however, designs of the swivel motor with other designs, e.g. oval piston swivel motors, are also conceivable.

The number of hydraulic inputs used to connect the number of fluid lines to the hydraulic supply of the earth-moving machine, referred to as quick coupler hydraulic inputs, and preferably also the number of hydraulic inputs used to connect the two motor pressure chambers to the hydraulic supply of the earth-moving machine, referred to as motor-hydraulic inputs, is advantageous in the rear arranged at the top of the motor housing. Because there the hydraulic hoses coming from the dipperstick are much better protected against damage than at the front end of the swivel motor, which tends to brush against obstacles during work. In addition, it is advantageous if the hydraulic hoses routed from the hydraulic supply of the earth-moving machine along the dipper arm to the quick coupler / swivel motor combination can be routed in a package to a connection point for all hoses. If all hydraulic inputs for supplying the pressure chamber (s) of the quick coupler and the motor pressure chambers are arranged in the rear upper area on the motor housing and each have an opening direction that is at least one directional component towards the front, the corresponding hydraulic hose package can be connected to these hydraulic inputs in an arc with a large radius connected and is therefore much less prone to kinking or tearing off than a straight hose guide.

Around the front fluid line to the rear upper area on the motor housing To guide arranged quick coupler hydraulic input, a front motor housing-internal line section of the front fluid line can have a line section leading backwards along the motor shaft through a wall of the motor housing in order to connect the oil guide groove of the front rotary union with the assigned quick coupler hydraulic input.

It is preferred, however, if a front line section of the front fluid line inside the motor housing consists of a connecting bore leading upwards from the front rotary leadthrough through the motor housing and opening into a deflection line section through a front deflection block. The front deflection block can be screwed onto the motor housing above the front shaft flange. However, it would also be conceivable to form it in one piece with the motor housing. The deflection line section in the front deflection block can then be connected via a first hydraulic pipe to a line end section through a rear deflection block. The rear deflection block can in turn be screwed onto the motor housing above the floor bearing flange or rear shaft flange, the line end section opening out at the quick coupler hydraulic inlet for connecting the front fluid line to the hydraulic supply of the earth-moving machine, which is formed on the rear deflection block.

Correspondingly, a bore through the engine housing leading to the front engine pressure chamber can open into a second deflection line section through the front deflection block, wherein the second deflection line section can be connected via a second hydraulic pipe to a second line end section through the rear deflection block, the second line end section being connected to the engine hydraulic input for connection the front engine pressure chamber leads to the hydraulic supply of the earth-moving machine.

Furthermore, a rear line section of the rear fluid line inside the motor housing can consist of a connecting bore leading upwards from the rear rotary feedthrough through the motor housing, which is connected to a further, third line end section through the rear deflection block, which is connected to the quick coupler hydraulic input for connecting the rear fluid line the hydraulic supply of the earth-moving machine ends.

Furthermore, a bore leading to the rear engine pressure chamber through the engine housing can open up into a further, fourth line end section through the rear deflection block, wherein the further line end section can open into the engine hydraulic input for connecting the rear engine pressure chamber to the hydraulic supply of the earth-moving machine.

In this way, all hydraulic inputs for operating the quick coupler / swivel motor combination can be configured at the upper rear end of the swivel motor housing on a deflection block, so that the connection of the hydraulic hoses, which are routed downwards in the hose package on the dipper stick, from the hydraulic supply of the earth-moving machine, is easy and kink-proof and protected as best as possible can be used against damage during work.

For an external swivel angle limitation of the swivel motor, four mechanical end stops or milled surfaces can also be attached to the quick coupler base plate. These end stops must be placed in such a way that they limit the swivel movement of the swivel motor and, when the maximum swivel angle is reached, the front and rear fastening feet for the side walls of the excavator suspension are in contact with side surfaces from above on the motor housing.

A bottom bearing can be pushed or screwed onto the rear shaft end of the motor shaft, which is axially fixed there while rotating. The rear shaft flange can then be formed on the floor bearing, that is to say as a floor bearing flange. If the front end of the shaft is connected to the front mounting plate and the bottom bracket is axially fixed to the rear mounting plate and transmits torque, the rear rotary feedthrough being formed on the rear plain bearing of the bottom bearing flange, the result is reliable torque transmission from the motor shaft to the quick coupler housing. However, since the motor shaft does not have the necessary play on either side to compensate for heat-induced expansion, this arrangement can lead to problems.

Because by the application of one of the two engine pressure chambers of the swivel engine With hydraulic pressure, enormous tensile forces arise, which stress the shaft, especially in the rear shaft area, and damage the shaft.

In the above-explained further development of the invention with a fixed bearing-fixed bearing arrangement, the shaft expansion has a negative effect on the service life of the motor shaft. Due to the fixed connection of the front end of the shaft with the front suspension plate and the floor bearing with the rear suspension plate, the expansion of the shaft cannot be compensated for. When the motor shaft is stretched, bending stress is generated on the shaft via the front mounting plate and the front shaft end, as well as the rear mounting plate and the bottom bearing, which can be particularly critical at the rear shaft area.

Because the shaft has the smallest cross-sectional area in the rear area, the risk of shaft damage is particularly great there. In addition, when the motor shaft bends, the bottom bearing in the rear plain bearing surface of the motor housing can easily tilt. As a result, when the motor shaft rotates, a large amount of friction arises in the rear sliding bearing, which is greater than in the front sliding bearing. As a result, the shaft is additionally subjected to torsion, which in turn has a strong influence on the service life of the shaft.

A further development of the invention is therefore preferred in which the rear shaft flange is also designed as a floor bearing flange on a floor bearing that is pushed or screwed onto the rear shaft end of the motor shaft and is axially fixed there in a rotating manner, and the front shaft end is also axially fixed and axially fixed to the front suspension plate Is connected to transmit torque, but the floor bearing is axially loose on the rear suspension plate and not torque-transmitting radially sliding bearings.

The expansion of the motor shaft can be compensated for by the floating bearing arrangement of the floor bearing in the rear suspension plate. The floor bearing or a rear side cover screwed onto the floor bearing can slide axially in a bearing seat in the rear suspension plate. This axial degree of freedom means that there is no longer any bending stress on the rear shaft area. The bottom bearing can no longer tilt in the plain bearing in the swivel motor-motor housing and the torsional stress on the shaft is eliminated.

In order to connect the rear rotary leadthrough on the rear sliding bearing of the floor bearing flange to the rear line section of the rear fluid line inside the suspension plate, the rear rotary leadthrough is advantageously connected via a number of internal channels to an additional rotary leadthrough on the sliding bearing of the floor bearing on the rear suspension plate, the rear suspension plate internal line section from the additional rotary feedthrough goes off. It has been shown that in spite of the axial displacement of the additional rotary leadthrough, which in turn is equipped with an annular oil guide groove in the rear suspension plate or the floor bracket or the side cover connected to the floor bracket and two sealing rings, oil tightness can be established on the auxiliary rotary leadthrough, while at the same time ensuring that oil is fed into the rear line section inside the suspension plate, since the axial displacement of the rear end of the motor shaft due to thermal expansion is not so great that the annular oil guide groove loses contact with the connected line sections.

The above-explained development of the invention with fixed bearing-floating bearing arrangement can of course be used both in a quick changer swivel motor combination with a front fluid line and rear fluid line, and in a quick changer swivel motor combination with only one fluid line front fluid line is provided as the only fluid line, no additional rotary feedthrough on the floor bearing side is necessary. Therefore, a front fluid line with a rotary feedthrough on the front shaft flange and a fluid line in the front suspension plate is preferred for a quick coupler with a single-acting linear actuator and a fixed bearing-floating bearing arrangement with floating support for the rear shaft flange or the floor bearing in the rear suspension plate.

Fig. 1

eine Erdbaumaschine mit einer angeschlossener Schnellwechsler-Schwenkmotor-Kombination gemäß einer Ausführungsform der Erfindung und daran aufgenommenem Grabenräumlöffel;

Fig. 2

eine Löffelstielkinematik des in Fig. 1 gezeigten Baggers mit Montagebolzen;

Fig. 3

den Löffelstiel aus Fig. 2 mit angebauter Schnellwechsler-Schwenkmotor-Kombination;

Fig. 4

die in Fig. 1 und 3 gezeigte Schnellwechsler-Schwenkmotor-Kombination seitlich von vorne und seitlich von hinten;

Fig. 5

einen Schwenkmotor der in den vorherigen Figuren gezeigten Schnellwechsler-Schwenkmotor-Kombination schräg von oben;

Fig. 6a

einen Querschnitt durch den in Fig. 5 gezeigten Schwenkmotor mit allen Fluidkanälen auf einer Ebene;

Fig. 6b

eines weiteren Querschnitt durch den in Fig. 5 und 6a gezeigten Schwenkmotors;

Fig. 7

eine Vorderansicht des in den vorherigen Figuren gezeigten Schwenkmotors;

Fig. 8

eine Rückansicht des in den vorherigen Figuren gezeigten Schwenkmotors;

Fig. 9

eine Schnittansicht eines O-Ring-Halters des in den vorherigen Figuren gezeigten Schwenkmotors;

Fig. 10

eine Schnittansicht der Schnellwechsler-Schwenkmotor-Kombination gemäß der in den vorherigen Figuren gezeigten Ausführungsform der Erfindung mit allen Fluidkanälen auf einer Ebene;

Fig. 11

eine perspektivische Ansicht des Schnellwechslers mit Aufhängungsblechen zum Anbau an den Schwenkmotor der in den vorherigen Figuren gezeigten Ausführungsform der Erfindung;

Fig. 12

weitere Ansichten des in Fig. 11 gezeigten Schnellwechslers mit Aufhängblechen zur Veranschaulichung von Anordnung und Details von Ölführungsnuten im Schnellwechsler und den Schwenkmotor-Aufhängungsblechen;

Fig. 13

einen Querschnitt durch den in den Figuren 11 und 12 gezeigten Schnellwechsler mit Aufhängungsblechen zum Anbau an den Schwenkmotor und mit allen Fluidkanälen in einer Ebene;

Fig. 14

einen vorderen Seitendeckel von vorne und in seitlicher Schnittansicht;

Fig. 15

einen hinteren Seitendeckel von vorne und in seitlicher Schnittansicht;

Fig. 16

eine Öldurchführungs-Abdeckung von vorne, seitlich und von unten;

Fig. 17

einen Querschnitt durch eine Schnellwechsler-Schwenkmotor-Kombination mit Axialausgleich gemäß einer weiteren Ausführungsform der Erfindung, wobei der Schwenkmotor mit allen Fluidkanälen auf einer Ebene gezeigt ist;

Fig. 18

einen hinteren Seitendeckel für den Schwenkmotor der in Fig. 17 gezeigten Schnellwechsler-Schwenkmotor-Kombination von vorne und in seitlicher Schnittansicht;

Fig. 19

den Schwenkmotor für den Schwenkmotor der in Fig. 17 gezeigten Schnellwechsler-Schwenkmotor-Kombination mit allen Fluidkanälen auf einer Ebene im Querschnitt und von hinten; und

Fig. 20

eine der Fig. 10 entsprechende Schnittansicht einer weiteren Ausführungsform der Erfindung.

Further advantageous developments are explained in more detail with reference to the embodiments of the invention shown in the accompanying drawings. Show it:

Fig. 1

an earth-moving machine with a connected quick coupler / swivel motor combination according to an embodiment of the invention and a trench clearing bucket received thereon;

Fig. 2

a dipperstick kinematics of the in Fig. 1 shown excavator with Mounting bolts;

Fig. 3

the dipper stick out Fig. 2 with attached quick coupler / swivel motor combination;

Fig. 4

in the Fig. 1 and 3 Quick coupler / swivel motor combination shown laterally from the front and laterally from the rear;

Fig. 5

a swivel motor of the quick coupler swivel motor combination shown in the previous figures obliquely from above;

Figure 6a

a cross section through the in Fig. 5 Swivel motor shown with all fluid channels on one level;

Figure 6b

another cross-section through the in Fig. 5 and 6a swing motor shown;

Fig. 7

a front view of the swing motor shown in the previous figures;

Fig. 8

a rear view of the swing motor shown in the previous figures;

Fig. 9

a sectional view of an O-ring holder of the swing motor shown in the previous figures;

Fig. 10

a sectional view of the quick changer swivel motor combination according to the embodiment of the invention shown in the previous figures with all fluid channels on one plane;

Fig. 11

a perspective view of the quick changer with suspension plates for attachment to the swivel motor of the embodiment of the invention shown in the previous figures;

Fig. 12

further views of the in Fig. 11 shown quick coupler with suspension plates to illustrate the arrangement and details of oil guide grooves in the quick coupler and the swivel motor suspension plates;

Fig. 13

a cross section through the in the Figures 11 and 12th Quick coupler shown with suspension plates for attachment to the swivel motor and with all fluid channels in one plane;

Fig. 14

a front side cover from the front and in a side sectional view;

Fig. 15

a rear side cover from the front and in a side sectional view;

Fig. 16

an oil passage cover from the front, side and from below;

Fig. 17

a cross section through a quick coupler swivel motor combination with axial compensation according to a further embodiment of the invention, wherein the swivel motor is shown with all fluid channels on one plane;

Fig. 18

a rear side cover for the swivel motor of the in Fig. 17 Quick coupler swivel motor combination shown from the front and in a side sectional view;

Fig. 19

the swivel motor for the swivel motor of the in Fig. 17 Quick coupler swivel motor combination shown with all fluid channels on one plane in cross section and from the rear; and

Fig. 20

one of the Fig. 10 corresponding sectional view of a further embodiment of the invention.

The present invention relates to a quick coupler swivel motor combination for the fluid-driven coupling of attachments to earth-moving machines, which should be able to be swiveled out to the side in the coupled state. Such a quick coupler / swivel motor combination according to an embodiment of the invention is shown in FIG Fig. 4 shown.

This quick coupler / swivel motor combination can be used with an earth-moving machine such as an in Fig. 1 illustrated excavator or other suitable vehicle types are used, which is equipped with a kinematics for the use of attachments.

The excavator has a boom 1 which is attached at the lower end 2 to be pivotable about a horizontal axis on the excavator superstructure 5, which forms part of the platform of the earth-moving machine. The boom 1 can also, as in Fig. 1 shown, be rotatably attached to a vertical axis 12 on an axle receptacle 3 at the front of the excavator superstructure 5, which allows an additional rotary movement of the boom 1 to the left and right. Depending on the size of the earth-moving machine, one or two boom cylinders 4 at the lower boom end 2 are used for raising and lowering in a forward-extending vertical plane in relation to the excavator superstructure 5.

An upper end 9 of a dipperstick 8 is pivotally attached to the upper end 6 of the boom. An arm cylinder 7 is for rotating the dipperstick 8 on the boom 1 in the same vertically forwardly extending forward rotation plane in which the Boom 1 works, attached.

The excavator superstructure 5 is attached to a chassis 10 and can be rotated about a vertical axis 11. This enables a simultaneous movement of the boom 1 and dipperstick 8 by 360 ° and thus a greater range in all directions while the boom 1 and the dipperstick 8 remain in the forward rotation plane as seen from the excavator uppercarriage 5.

Even if the movement is described as extending forward in order to simplify the description, it must be noted that the forward rotation plane, when the excavator superstructure 5 is rotated in relation to the chassis 10, rotates about the vertical axis of rotation 11 of the chassis and therefore to a certain extent loses its front-to-rear alignment, the plane actually extending laterally with respect to the chassis 10 when the excavator superstructure 5 is rotated.

Slightly above a lower end 13 of the dipperstick, the dipperstick 8 is extended forward by two jointed bucket movement components (deflector 14 and pressure support 15), which can be moved in the forward rotation plane by a bucket cylinder 16. The bucket cylinder 16 is fastened with a cylinder bottom side 17 on the dipper stick 8 and with a cylinder piston rod 18 on the joint between the deflector 14 and the pressure support 15. A four-bar chain with two free ends is formed by the dipperstick 8, the deflector 14 and the pressure support 15.

How Fig. 2 shows the free ends on the dipperstick 8 and the pressure support 15 are each provided with a transverse bore 19 and 20, which can hold exchangeable tools, such as a backhoe or a ditch-clearing bucket, through the use of mounting bolts 21. The tool can then be moved in the forward rotation plane by three different controls, namely by controlling the boom cylinder 4, the stick cylinder 7 and the bucket cylinder 16.

In the Fig. 4 The separately shown quick coupler / swivel motor combination includes a hydraulic swivel motor 23 with attached side brackets 29 serving as an excavator suspension, which fastening eyes for the in Fig. 2 have mounting bolts 21 shown. The swivel motor 23 and thus the entire quick coupler-swivel motor combination can thus in a similar manner as a conventional backhoe bucket or comparable tool can be attached to the dipperstick 8 and the pressure support 15 (see Fig. 3 ). By means of a front and a rear suspension plate 55, 80, a hydraulic quick coupler 63 is suspended below the swivel motor 23, with which the tool can then be picked up.

In the illustrated embodiment of the invention, a rigid ditch cleaning bucket 22 is used in combination with the quick coupler 63. The rigid ditch clearing bucket 22 has a main cutting edge which extends laterally, generally transverse to the plane of the forward rotation, and right and left side cutting edges which are arranged almost perpendicularly to the main cutting edge.

By using the swivel motor 23, the main cutting edge can be swiveled, which means that digging can be carried out in the tilted position in addition to its main function. This enables embankment profiles and similar trenches to be created. When the rigid ditch cleaning bucket is pivoted through 90 °, the side cutting edges are tilted from an almost vertical plane into an almost horizontal plane. In this way, one of the side cutting edges can take over the function of the main cutting edge, which means that work can be carried out particularly in confined spaces. By pivoting the rigid ditch clearing spoon 22, the bulk material can also be dumped out in a better dosed manner.

In order to be able to pick up the trench clearing bucket 22 or another tool with the quick coupler 63, an adapter frame 181 is attached to the top of the trench clearing bucket 22. This adapter frame 181 consists of an inclined rear plate 183, on the narrow sides of which on the right and left side plates are attached parallel and at the same height to one another, which in turn are connected on their side opposite the rear plate 183 by an adapter shaft. The adapter shaft has a suitable diameter for gripping by the quick changer 63. The rear plate 183 has two identical, semicircular cutouts 187a, 187b into which the quick changer 63 can lock and unlock.

The excavator suspension of the in Fig. 4 The quick coupler / swivel motor combination shown individually is attached to a cylindrical motor housing 24 of the in the Figures 5 to 8 in detail shown swivel or rotary motor 23 attached, the suspension plates 55, 80 for the quick coupler 63, on the other hand, on a motor shaft 32 that is rotatably arranged in the motor housing 24, so that the quick coupler 63 and thus a ditch cleaning bucket 22 ( Fig. 1 ) relative to the motor housing 24 or the dipperstick 8 attached to it can be pivoted out of the forward rotation plane.

The cylindrical motor housing 24 of the swivel motor 23 has a front 26 and a rear end face 27. Above the front and rear end faces 26 and 27 there are fastening feet 28a, 28b for welding the side brackets 29 serving as excavator suspensions.

The motor housing 24 is hollowed out around its longitudinal axis 35. The cylindrical cavity has the largest diameter in a first housing section 30 and in an opposite, fourth housing section. In a second housing section adjoining the first housing section, the cavity has a smaller diameter and in a third section 31 next to it the diameter is smallest. These gradations serve to provide the components inside with the necessary accommodation and storage.

The motor shaft 32 designed as a toothed shaft, a piston 33 and a bottom bearing 34 of the motor shaft 32 are arranged in combination coaxially in the motor housing 24 and can rotate about their common longitudinal axis 35.

The motor shaft 32 is mounted near its front shaft end 38 on a front shaft flange 37 with a slide bearing 36 in the motor housing 24. The motor shaft 32 extends over the entire length of the motor housing 24 and has the front shaft end 38 on the front end face 26 and a rear shaft end 39 on the rear end face 27. The annular bottom bearing 34 of the motor shaft 32 is screwed onto the rear shaft end 39.

The bottom bearing 34 has a thread 40 inside, which is screwed to a corresponding circumferential thread section 41 of the motor shaft 32. The bottom bearing 34 and thus the rear shaft end 39 of the motor shaft 32 is mounted in the motor housing 24 in the form of a sliding bearing 69 with a bottom bearing flange 74 that forms a rear shaft flange 74 and is formed on the bottom bearing 34. Between motor shaft 32 and Bottom bearing 34, a seal 112 is used for a fluid-tight connection, see Figure 6b .
A support ring 42 is arranged on an axial contact surface 128a of the housing 31 between the motor shaft 32 and the second inner section of the motor housing 24. The support ring 42 serves to stabilize the thrust washer 43, which is arranged between the motor shaft 32 and the support ring 42. A thrust washer 44 is arranged on an axial contact surface 128b between the floor bearing 34 and the third inner section of the motor housing 31. The thrust washers 43 and 44 serve to minimize friction, prevent jerky starting, limit torque losses and reduce the torsional stress on motor shaft 32.

The bottom bearing 34 is secured by a locking nut 45 screwed onto the motor shaft 32 with the opposite screwing direction. The locking nut 45 is clamped to the floor bearing 34 by several cylinder screws 46 and thereby locked. As a result, the front shaft end 38 and the bottom bracket 34 rotate synchronously in one direction. The floor bearing 34 rotates with the motor shaft 32.

An external thread 113 in the form of a coarse thread is arranged over the second and third sixths of the motor shaft 32 from the front. With this external thread 113, the piston 33 is in engagement with its internal thread 114. The piston 33 has an internal thread 114 in the first third from the front side and an external thread 115 in the second and third third. The external thread 115 of the piston 33 engages in the internal thread 116 of the swivel motor housing 24. The two coarse thread pairs have a pitch in opposite directions. In the first third of the piston 33, a front annular piston guide 117 is arranged on the outside perpendicular to the axis of rotation 35. On the last third of the piston 33, a rear annular piston guide 118 is arranged inwardly perpendicular to the axis of rotation 35. In these piston guides 117, 118, two grooves are machined around the axis of rotation 35. One groove is used for the seat of a seal 119a, 119b, the other groove for the seat of a guide band 120a, 120b.

The piston 33 and its seals 119a and 119b thus create a front motor pressure chamber 121 and a rear motor pressure chamber 122 between the motor shaft 32, the motor housing 24 and the bottom bearing 34. How Fig. 10 shows is located on The front upper end of the swivel motor housing 24 has a hydraulic fluid connection 123 with a bore 124 which opens into an annular oil guide groove 199 in the motor housing 24, a transverse bore 127 being provided on the front shaft flange 37, which opens from the annular oil guide groove 199 into the front motor pressure chamber 121. When pressure is applied to the front hydraulic fluid connection 123, the hydraulic fluid passes through the bore 124 of the motor housing 24, via the oil guide groove 199 circumferentially around the shaft flange 37 and through the transverse bore 127 in the shaft flange 37 into the front pressure chamber 121 Hydraulic fluid connection 125 with a bore 126 which leads into the rear pressure chamber 122. Hydraulic fluid can be pumped into one of the two motor pressure chambers 121, 122 through these fluid channels and fed back from the opposite one to the tank of the machine.

The piston 33 is held displaceably in the body for reciprocal movement by the piston guide bands 120a and 120b and experiences a longitudinal and rotational movement in relation to the motor housing 24. By screwing the motor shaft 32 to the bottom bearing 34 against the axial swivel motor housing contact surfaces 128a and 128b there are no axial degrees of freedom of the shaft 32 and the bottom bearing 34. Due to the sliding bearing of the shaft 36 and the bottom bearing 69 in the swivel motor housing 24, the shaft 32 and the bottom bearing 34 no longer have any radial degrees of freedom. The movement of the motor shaft 32 and the bottom bearing 34 is thus restricted to rotation, whereby any movement of the piston 33 is converted into a rotational movement of the shaft 32. The application of fluid pressure to the first hydraulic fluid connection 123 in the front pressure chamber 121 creates an axial movement of the piston 33 in the direction of the rear end face 27. The application of fluid pressure to the second hydraulic fluid connection 125 in the rear pressure chamber 122 creates an axial movement of the piston 33 in the direction of the front face 26.

At the rear end of the motor shaft 39 is an end-face, stepped bore 129 with several steps along the axis of rotation 35, which, like the Figure 6a , 6b show by way of example, extends to approximately the middle of the shaft. Two transverse bores 130, 131 lead from this stepped bore 129 to the outer circumference of the motor shaft 32. The first transverse bore 131 creates a channel into the front engine pressure chamber 121, the second transverse bore 130 creates a channel into the rear engine pressure chamber 122. This creates a connection between the two engine pressure chambers 121 and 122, through a double pressure relief valve 132 is interrupted in the central stepped bore 129. This double pressure relief valve 132 opens as overload protection against excessively high hydraulic pressure. If the pressure in one of the two engine pressure chambers 121, 122 rises above the permissible operating pressure, the double pressure relief valve 132 opens and allows the hydraulic fluid to flow into the other, thus reducing the pressure. The double pressure relief valve 132 is held in position by a screw plug 133 in the bore of the shaft 129. The screw plug 133 also closes the shaft end 39. It should be noted that the double pressure relief valve 132 can also be installed at a different location in the shaft 32, the swivel motor housing 24 or other external components. The prerequisite is that it fulfills its function: Under normal conditions, it separates both pressure chambers from one another through its closed state. If the pressure is too high, it opens and the front and rear pressure chambers are connected to one another. Instead of a double pressure relief valve, any other overload protection valve can also be used.

On the front and rear slide bearings 36, 69, six grooves are machined in the swivel motor housing 23 around the axis of rotation 35 concentrically. In the two grooves arranged near the two end faces 26, 27, wiper rings 48c, 71c are arranged to protect against contamination from the outside.

A front, annular oil guide groove 47 is machined into the motor housing 24 on the sliding bearing 36 of the motor shaft 32, coaxially to the main shaft axis 35 and running around the motor housing 24. The front oil guide groove 47 is sealed by two sealing rings 48a and 48b, each inserted into one of the six circumferential grooves in the motor housing 24, between the motor housing 24 and the motor shaft 32. The front oil guide groove 47 is connected by a connecting bore 49 to the hydraulic connection 50 located on the front top of the engine.

A rear annular oil guide groove 70 is machined into the motor housing 24 coaxially to the main shaft axis 35 in the motor housing 24 on the rear end face 27 in the area of the sliding bearing 69 of the bottom bearing 34. The rear oil guide groove 70 is sealed between the motor housing 24 and the motor shaft 32 by two sealing rings 71a and 71b each inserted into one of the six circumferential grooves in the motor housing 24. In addition, the rear oil guide groove 70 is through a communication hole 72 is connected to the hydraulic connection 73 located on the rear top of the engine.

A transverse bore 51 is arranged in the direction of the main shaft axis 35 on the sliding bearing 36 on the front shaft flange 37. The position of this hole is aligned with the front oil guide groove 47 of the motor housing 24. Shown in the Figure 6a and Fig. 7 is on the end face of the front shaft flange 37 in the area of the pitch circle diameter 52b between two threaded bores 53, a longitudinal bore 54b with an opening 54a, which is arranged parallel to the main shaft axis 35. This longitudinal bore 54b is connected to the transverse bore 51. The hydraulic fluid thus passes from the hydraulic connection 50 located on the front top side of the engine through the connecting bore 49 to the front oil guide groove 47 in the motor housing 24. The hydraulic fluid is guided around the front shaft flange 37 through the front oil guide groove 47. The hydraulic fluid in the interior of the motor shaft 32 is deflected through the transverse bore 51 and longitudinal bore 54b and continues to the end-side longitudinal bore opening 54a on the front shaft flange 37.

A transverse bore 79 running transversely to the direction of the main shaft axis 35 is incorporated in the plain bearing 69 on the bottom bearing flange 74. The position of this transverse bore 79 is aligned with the rear annular oil guide groove 70 of the motor housing 24. On the front side of the bottom bearing flange 74 is how that Figure 6a and 8th show, in the area of a pitch circle diameter 76b of the threaded bores 77 between two threaded bores 77, a further longitudinal bore 78b is arranged parallel to the main shaft axis 35. This longitudinal bore 78b is connected to the transverse bore 79. The hydraulic fluid thus passes from the hydraulic connection 73 located on the rear top side of the engine through the connecting bore 72 to the rear oil guide groove 70 in the motor housing 24. The hydraulic fluid is guided around the bottom bearing flange 74 through the rear oil guide groove 70. The hydraulic fluid is deflected through the transverse bore 79 and the longitudinal bore 78b in the floor bearing flange 74 and continues to the opening 78a of the longitudinal bore on the end face of the floor bearing 34.

In the following, reference is made to the Figures 10 to 15 . The front shaft flange or flange section 37 has a round hole pattern 52a with several threaded bores 53 on the front end face of the motor shaft 24, see FIG Fig. 7 . With a smaller diameter than this hole pattern 52a, an annular groove 136 is concentric to the Shaft axis 35 incorporated into the front flange section 37. The threaded bores 53 and the groove 136 are used to connect the shaft 32 to the front suspension plate 55.
A front side cover 137 is individually in the Fig. 14 shown. The front side cover 137 and the front swivel motor mounting plate 55 have a hole pattern 52a and 148, which is identical to the hole pattern 52a on the flange section 37, in the form of through bores 138. The front side cover 137 is pushed through the front suspension plate 55 and protrudes into the annular groove 136 of the flange section or front shaft flange 37. The front suspension plate 55 is screwed to the shaft flange 37 by means of screws 139. The screws 139 are additionally secured against loosening by means of screw locking washers 140. The front side cover 137 has contact with the front shaft flange 37 only on an outer groove ring surface 141 of the shaft flange 37. As a result, radial forces are absorbed and the screws 139 are relieved.

The front side cover 137 and the rear side cover 143 each have a flat cylindrical shaped section 25a, 75a, on the flat underside of which there is a cylindrical fitting section 25b, 75b with a smaller diameter. Its diameter corresponds to the diameter of circular cutouts in the suspension plates 150, 151. A cylindrical recess 25c, 75c is machined inwardly on the underside of the cylindrical fitting section 25b, 75b. The outer diameter of the smaller cylinder 25b, 75b corresponds to the diameter of the outer groove ring surface 141, 147 in the shaft flange 37 or bottom bearing flange 74.

The side covers 137, 143 are pushed through the suspension plates 55, 80 and protrude into the annular sections 136, 142 on the shaft flange 37 or on the floor bearing 74.

If a double pressure relief valve 132 is inserted in the shaft 32, the rear side cover 143, which blocks access to said double pressure relief valve 132 and its screw plug 133, has a circular cutout 157 with a sufficient diameter to allow access to screw plug 133 and valve 132 if necessary guarantee. This circular cutout 157 is provided with a plug 158 of sufficient diameter to protect against the ingress of Impurities sealed.

A floor bearing flange 74 has a round hole pattern 76a with threaded bores 77, see Fig. 8 . With a smaller diameter than this hole pattern 76a, an annular recess 142 is machined concentrically to the shaft axis 35 in the end face of the bottom bearing 34. The locking nut 45 is screwed into this recess 142. Due to the smaller diameter of the locking nut 45, a free annular section remains in the annular recess 142 of the bottom bearing 34, which fulfills an identical purpose as the groove 136 in the front shaft flange. The threaded bores 77 and the free section in the annular recess 142 around the lock nut 45 are used to connect the bottom bracket 34 to the rear swing motor mounting plate 80.

A rear side cover 143 is individually in the Fig. 15 shown. The rear side cover 143 and the rear suspension plate 80 have a hole pattern 76a and 149 in the form of through holes 144 that are identical to the outer threaded holes 77 of the floor bearing 34. The rear side cover 143 is pushed through the rear swivel motor mounting plate 80 and protrudes into the free section 142 around the locking nut 45 in the floor bearing 34. The rear suspension plate 80 is screwed to the floor bearing 34 by means of screws 145. The screws 145 are additionally secured against loosening by means of screw locking washers 146. The rear side cover 143 is in contact with an outer groove ring surface 147 of the free portion in the annular recess 142 of the bottom bracket 34, which extends around the lock nut 45 of the bottom bracket 34. As a result, radial forces are intercepted and the screws 145 are relieved.
In the front suspension plate 55, in the area of the hole pattern 52a ( Fig. 7 ) a receiving bore 57 for the seat of a front O-ring holder 58 is arranged between two fastening bores 56. This receiving bore 57 is arranged concentrically to the longitudinal bore 54b of the oil guide in the front shaft flange 37. The front O-ring holder 58 inserted into the receiving bore 57 and a sealing O-ring 68 held by it have the task of sealing the front end face 26 of the motor shaft 32 against escaping hydraulic fluid between the motor shaft 32 and the front suspension plate 55.

The in Fig. 9 The detailed front O-ring retainer 58 is a small cylinder, the length of which corresponds to the thickness of the area around the receiving bore 57 in the front suspension plate 55. The O-ring holder 58 has a longitudinal bore 59, one or more transverse bores 60, a front free rotation 61a and a rear sealing groove 61b.

The O-ring holder 58 is chamfered on the side of the longitudinal bore 59. This chamfer serves as a sealing seat 66. By inserting the O-ring holder 58 into the front swivel motor suspension plate 55, a triangular groove is created between the front shaft flange 37, the O-ring holder 58 and the front suspension plate 55 Seal 67 is inserted. A fluid-tight connection between the front shaft flange 37 and the O-ring holder 58 is thus established. A sealing O-ring 68 is mounted in the sealing groove 61b to establish a fluid-tight connection between the O-ring retainer 58 and the front suspension plate 55.

The hydraulic fluid is diverted from a horizontal oil guide from the motor shaft 32 via the front O-ring holder 58 into a vertical oil guide down into the front suspension plate 55 and further to a base plate 62 of the quick changer 63 and into a front fluid channel 64 located therein . A threaded hole 65 on the rear side of the front O-ring holder 58 is used to attach a puller for removing the front O-ring holder 58 from the receiving hole 57 of the front suspension plate 55.
In the rear suspension plate 80 in the area of the hole pattern 76a ( Fig. 8 ) a receiving bore 82 for the seat of a rear O-ring holder 83 is arranged between two fastening bores 81, analogous to the above-mentioned receiving bore 57 on the front suspension plate 55, see Fig. 11 . The receiving bore 82 is arranged concentrically to the longitudinal bore 78b of the rear oil guide in the bottom bearing flange 74.

The rear O-ring holder 83 inserted into the receiving bore 82 corresponds in terms of shape and preferably also in terms of dimensions to the front O-ring holder 58 and, together with it, is in FIG Fig. 9 shown individually. Together with the sealing O-ring 86 carried by it, it has the task of sealing the face between the floor bearing 34 and the rear suspension plate 80 against escaping hydraulic fluid. The rear O-ring holder 83 has the same longitudinal bore 59, the same or more transverse bores 60 and the same front free rotation 61a and rear Sealing groove 61b like the front O-ring holder 58. The O-ring holder 83 is chamfered on the side of the longitudinal bore 59. This chamfer in turn serves as a sealing seat 66.

By inserting the rear O-ring holder 83 into the rear swivel motor mounting plate 80, a triangular groove is created between the bottom bracket flange 74, the rear O-ring holder 83 and the rear suspension plate 80, in which a further seal 85 ( Fig. 10 ) is used. A fluid-tight connection between the bottom bearing flange 74 and the rear O-ring holder 83 is thus established. The sealing O-ring 86 is mounted in the sealing groove 61b to establish a fluid-tight connection between the rear O-ring holder 83 and the rear suspension plate 80.

The hydraulic fluid is diverted from a horizontal oil guide from the bottom bracket 34 via the rear O-ring holder 83 into a vertical oil guide down into the rear suspension plate 80 and further to the base plate 62 of the quick changer 63 and into the rear fluid channel 84 located therein. The threaded bore 65 on the rear side of the O-ring holder 83 is in turn used to fasten a puller for dismantling the O-ring holder 83 from the receiving bore 82 of the rear suspension plate 80.

The side covers 137, 143 each have a cutout 159, 160 in the radial circumference in order to provide access to the O-ring holder 58 and 83 and its seals 67, 68, 85 and 86. The cutout 159, 160 has the shape of a rectangle bent around the center point of the side cover. The rectangle extends over the receiving bore 57, 82 as well as the two directly adjacent through bores 144, 138. The cutout is somewhat smaller than a milled recess 152, 153 in the associated suspension plate 55, 80.

In the area of the cutouts 159, 160 on the two side covers 137, 143, a separate oil duct cover 154, 155 of the oil duct is arranged in each case ( Fig. 16 ). The shape and bores of the cover correspond to the shape of the associated cutout 159, 160, but it is slightly smaller at the contours that touch the side cover 137, 143 in order to ensure a fitting fit. The cover 154, 155 serves to ensure that the O-ring holder 58, 83 cannot be pushed out of its receiving bore 57, 82 and to reliably seal the area. The Cover 154, 155 is screwed to the respective suspension plate 55, 80 on the milled contact surface 152, 153 and to the shaft flange 37 or floor bearing flange 74 by means of two screws 139, 145.
How in particular Fig. 13 shows, both the front and the rear suspension plate 55, 80 are attached to the quick coupler base plate 62 by an oil-tight welded seam 87 and 88, respectively. A front and a rear oil guide groove are milled into the quick coupler base plate 62.

Each oil guide groove has two incorporated steps, see Fig. 12 , bottom left. The hydraulic fluid is conducted in the lower stage 89. The lower steps of the two oil guide grooves thus serve as the front and rear fluid ducts 64, 84. A groove cover 91 is arranged in the step 90 above and is attached to the quick coupler base plate 62 by an oil-tight welded seam 92.

From the front area 93 of the quick changer base plate 62, namely from the front fluid channel 64, through the oil-tight weld joint 87 between the quick changer base plate 62 and the front suspension plate 55, there is a vertical or inclined front connecting hole 95 upwards to the receiving hole 57 of the front O-ring holder 58 out, see Fig. 13 . Through this front connecting bore 95 a connection of the oil-carrying bores 59, 60 of the front O-ring holder 58 ( Fig. 9 ) and the horizontally running front fluid channel 64 in the quick changer base plate 62. A threaded hole 96 is machined into the bottom of the quick changer base plate 62. A screw plug 97 is mounted in this threaded hole 96. The screw plug 97 creates a fluid-tight connection between the seat 57 of the front O-ring holder 58 in the front suspension plate 55 and the front fluid channel 64 in the base plate 62.

From the rear area 94 of the quick changer base plate 62, namely from the rear fluid channel 84, through the oil-tight weld seam connection 88 between the quick changer base plate 62 and the rear suspension plate 80, there is a vertical or inclined rear connecting bore 98a, 98b upwards to the receiving bore 82 of the rear O-ring holder 83 out. Through this connecting bore 98a, 98b a connection of the oil-carrying bores 59, 60 of the rear O-ring holder 83 ( Fig. 9 ) to the horizontally running, rear fluid channel 84 in the quick coupler base plate 62 created. A threaded hole 99 is machined into the bottom of the quick coupler base plate 62. A screw plug 100 is mounted in this threaded hole 99. The screw plug 100 creates a fluid-tight connection between the receiving bore 82 for the rear O-ring holder 83 in the rear suspension plate 80 and the rear fluid channel 84. In addition, the screw plugs 97 and 100 can be opened for maintenance work, e.g. B. for flushing the respective fluid channel.

How Fig. 13 shows, a flat surface 101 is incorporated on the underside of the quick changer base plate 62. This plane surface 101 serves to support a double-acting linear actuator 102. In the area of the linear actuator connections 103 and 104, a vertical connecting bore 105, 106 is drilled into the quick coupler base plate 62 upwards to the corresponding fluid channel 64, 84. Flat countersinks 108, 109, which serve as seats for a seal 110, 111, are attached to a linear actuator housing 107 or in the quick-change base plate 62. These seals 110, 111 ensure a fluid-tight connection between the corresponding fluid channel 64, 84 of the quick changer base plate 62 and the associated linear actuator connection 103, 104 of the linear actuator 102.

Thus, a connection from the front hydraulic connection 50 or rear hydraulic connection 73 through the swivel motor 23 and a quick coupler frame 62, 62a, 62b, 188 formed by the base plate 62 and further walls 62a, 62b, 188 welded to it, to a respective front or rear hydraulic connection is possible. rear pressure chamber 103a, 104a made in the quick coupler linear actuator 102.

The quick changer frame 62, 62a, 62b, 188 is advantageously designed as a closed housing, such as in particular the Figures 10 to 13 demonstrate. On the front of the quick changer housing are immovable, mutually parallel claws 186a, 186b with opening to the front, which form an engagement element for gripping the adapter shaft of the adapter frame 181.

Inside the quick coupler frame 62, 62a, 62b, 188 is the hydraulic linear actuator 102, which the linear actuator housing 107 and a hydraulic piston 190 arranged therein for reciprocating linear movement between the rear 191a and front housing end 191b and along one to the Motor longitudinal axis 35 includes parallel actuator longitudinal axis 192. An elongated piston rod 193 is attached to the piston 190 and is arranged coaxially in the linear actuator housing 107 and is supported thereon for linear longitudinal movement. The piston rod 193 extends forward out of the linear actuator housing 107 toward the front body end 191b and has a piston rod eye 194 at the front end.

The piston rod eye 194 is connected to a transversely aligned bridge. A locking wedge 196a, 196b aligned parallel to the actuator axis 192 is attached to both ends of the bridge. The two locking wedges 196a, 196b can penetrate the rear wall 188 of the quick coupler frame 62, 62a, 62b, 188 at two openings and have a cylindrical shape, the rear end of which is attached to the bridge and the front end on its upper side at an angle to one Wedge surface 198a, 198b is flattened. By means of these wedge surfaces 198a, 198b, the rear wall 188 of the quick coupler frame 62, 62a, 62b, 188 can be clamped against the rear plate 183 of the adapter frame 181, while at the same time the claws 186a, 186b are pressed against the adapter shaft.

The two oil supply connections 50, 73 on the top of the motor housing 24 are connected to the two pressure chambers 103a, 104a of the linear actuator 102 via internal fluid lines leading through the swivel motor 23, the suspension plates 55, 80 and the quick-change frame 62, 62a, 62b, 188 .

The fluid lines inside the housing include line sections 49, 72 inside the motor housing, namely the connection bore 49 between the front oil guide groove 47 and the front oil supply connection 50 and the connection bore 72 between the rear oil guide groove 70 and the rear oil supply connection 73, the two rotary feedthroughs 47, 48a, 48b, 70 , 71a, 71b on the motor shaft 32 or its bottom bearing 34, motor shaft-internal line sections 51, 54b, 78b, 79, namely the transverse bore 51 connected to the longitudinal bore 54b on the shaft flange 37 and the transverse bore 79 connected to the longitudinal bore 78b on the base bearing flange 74, internal to the suspension plate Line sections 59, 60, 95, 59, 60, 98a, 98b, namely the longitudinal and transverse bore 59, 60 passing through the front O-ring holder 58 and the front connecting bore 95 on the one hand and the one through the rear O-ring holder 83 longitudinal and transverse bore 59, 60 and the rear connection bores 98a, 98b on the other hand, as well as line sections 64, 105, 84, 106 inside the quick changer frame, namely the front fluid channel 64 in the quick changer base plate 62 with the front connecting bore 105 to the linear actuator 102 and the rear fluid channel 84 in the quick changer base plate 62 with the rear connecting bore 106 for Linear actuator 102.

This not only ensures the oil supply to the quick changer 63 and controls its linear actuator 102, but also ensures that the fluid lines are not damaged during work due to the line routing inside the housing.

One of the two fluid lines is arranged at the front and one of the two fluid lines is arranged at the rear on the one on the quick-change swivel motor combination. The front fluid line comprises a front motor housing-internal line section 49, a front rotary leadthrough 47, 48a, 48b on the front sliding bearing 36 or on the front shaft flange 37, a front motor shaft-internal line section 51, 54b, a front line section 59, 60, 95 inside the suspension plate and a front quick changer frame internal line section 64, 105. The rear fluid line comprises a rear motor housing internal line section 72, a rear rotary feedthrough 70, 71a, 71b on the rear sliding bearing 39 or on the bottom bearing 34, a rear internal motor shaft line section 78b, 79, a rear internal mounting plate line section 59 , 60, 98a, 98b and a rear quick changer frame-internal line section 84, 106.

As a result, the friction due to the annular seals 48a, 48b or 71a, 71b and oil guide grooves 47 and 70 required on the rotary unions 47, 48a, 48b, 70, 71a, 71b, is uniform on the front and rear sliding bearings 36 and 69 distributed and the torsional stress on the motor shaft 32 is reduced. This increases the service life of the swivel motor 23. The motor shaft 32 starts more smoothly and torque losses are limited.

Even if the quick changer / swivel motor combination of the present embodiment has the quick changer 63 described above, other common quick changers could also be installed on the present quick changer / swivel motor combination, which are operated by a double-acting linear actuator can be operated. However, it would also be conceivable to hang a hydraulic quick coupler with a single-acting linear actuator under the swivel motor, which in this case only takes up one of the two fluid lines.
The motor housing 24 has, on the one hand, the connecting bores 49, 72 leading from the annular oil guide grooves 47, 70 to the oil supply connections 50, 73 and, on the other hand, the bores 124, 126 leading to the motor pressure chambers 121, 122.

From the outside, threaded holes could now be attached to the end of these holes. Screw-in screw connections could in turn be screwed into these threaded bores, which as hydraulic inputs enable a direct connection to hydraulic lines coming from the dipperstick and thus the hydraulic supply of the earth-moving machine.

Preferred and at the in the Figures 1 to 16 shown embodiment shown (see in particular Fig. 5 ) it is, however, the hydraulic inputs 173a, 173b, 173c, 173d of the swivel motor 23 which are used for connection to the hydraulic lines coming from the dipperstick 8 and thus for connection to the hydraulic supply of the earth-moving machine, namely two quick-changer hydraulic inputs 173b, 173c and two motor hydraulic inputs 173a, 173d provided for the swivel motor operation, in the rear upper area of the motor housing 24.

By redirecting to the rear swing motor side, a more curved hose guide 164 and the hydraulic hoses 165 rolling up and down when the bucket cylinder 16 is actuated are achieved, see FIG Fig. 3 . This significantly reduces the risk of the hydraulic hoses kinking and tearing off.

However, a diversion into the front upper area of the motor housing would also be conceivable. In view of a common structure of earth-moving machine kinematics, however, a second, unnecessary hose bend would then be generated.

Like in particular the Fig. 5 , 6a and 6b show, a front deflection block 163a and a rear deflection block 163b are screwed onto the motor housing 24, the front connecting bore 49 and the one leading to the front motor pressure chamber 121 Bore 124 open into the front deflection block 163a, the rear connecting bore 72 and the bore 126 leading to the rear engine pressure chamber 122 on the rear deflection block 163b. The two deflection blocks 163a, 163b are connected to one another via two hydraulic pipes 163c, 163d, via which the front fluid line and the fluid line leading to the front engine pressure chamber are guided backwards to the rear deflection block 163b.

The front deflection block 163a has two vertical bores 166a and 166b on the lower contact surface. These two vertical bores 166a, 166b are connected on the inside with two horizontal bores 167a, 167b, which are incorporated in its rear side wall, and thus form a first deflection line section 166a, 167a of the front fluid line and a second deflection line section 166b, 167b of the one leading to the front engine pressure chamber 121 Fluid line.

The front deflection block 163a is screwed by means of screws 168 onto a milled sealing surface 169a between the front fastening feet 28a of the motor housing 24. Flat countersinks 170 around the bores 166a, 166b or 49, 72 are incorporated either in the sealing surface 169a of the motor housing 24 or in a lower contact surface of the deflection block 163a. A seal 171 is inserted in each of these flat countersinks 170 and thus a fluid-tight connection is established between the bore 124 and the connecting bore 49 in the motor housing 24 and the vertical bores 166a, 166b in the deflection block 163a. The front deflection block 163a has, coaxially to the horizontal bores 167a, 167b, two horizontal receiving bores 174a, 174b on the inner side wall for the two hydraulic pipes 163c, 163d.

The two deflection blocks 163a, 163b are sealed fluid-tight on the two hydraulic pipes 163c, 163d by means of seals 172a, 172b, 172c, 172d at the front and rear ends of the hydraulic pipes 163c, 163d. Fluid-tight connections are thus established between the front 163a and rear block 163b.

The rear deflection block has the four hydraulic inputs 173a, 173b, 173c, 173d, namely the two quick-changer hydraulic inputs 173b, 173c intended for quick-change operation and the two motor-hydraulic inputs 173a, 173d intended for swivel motor operation on the upper half of its front Sidewall on. Concentric to these four hydraulic inlets 173a, 173b, 173c and 173d, further horizontal bores 175a, 175b, 175c and 175d are drilled in the direction of the rear of the block. The rear deflection block 163b has two horizontal receiving bores 174c, 174d for the two hydraulic pipes 163c, 163d on the lower half.

Concentric to the bores of the two hydraulic pipes 163c, 163d, horizontal bores 176a, 176b are drilled in the direction of the back of the block up to approximately the middle. Two hydraulic inlets 173b, 173c of the four hydraulic inlets 173a, 173b, 173c, 173d are connected to the horizontal bores 176a, 176b by an inclined or preferably vertical bore 177a, 177b. The opening of these bores 177a, 177b is closed in a fluid-tight manner with a screw plug or an expander 178a, 178b.

The rear deflection block 163b also has two further vertical bores 166c, 166d penetrating its lower contact surface. One of these two vertical bores 166c, 166d is used to connect the rear fluid line to the quick changer, the other to connect the fluid line to the rear engine pressure chamber 122 Lead hydraulic inputs 173a, 173d. The rear deflection block is screwed by means of screws 168 onto a milled sealing surface 169b between the rear fastening feet 28b of the motor housing 24. Flat countersinks 170 around the bores 166c, 166d in the rear deflection block 163b or the opening bores 126, 72 in the motor housing 24 are machined either in the sealing surface of the swivel motor housing or in the lower contact surface of the rear deflection block 163b. A seal 171 is inserted into this countersink 170 and thus a fluid-tight connection is established between the bores in the swivel motor housing 24 and the two vertical bores 166c, 166d in the rear deflection block 163b.

The four hydraulic inlets 173a, 173b, 173c, 173d are provided with threads into which, as Figure 6b shows that screw connections for connection to the hydraulic system of the earth-moving machine are screwed in.

A first quick coupler hydraulic input 173b is used to connect the front fluid line to the hydraulic supply of the earth-moving machine. A second Quick coupler hydraulic input 173c is used to connect the rear fluid line to the hydraulic supply of the earth-moving machine. A first engine hydraulic input 173a is used to connect the front engine pressure chamber 121 to the hydraulic supply of the earth-moving machine. A second engine hydraulic input 173d is used to connect the rear engine pressure chamber 122 to the hydraulic supply of the earth-moving machine.

The horizontal bore 176a coming from the assigned, first hydraulic pipe 163c, the subsequent vertical bore 177a and the horizontal bore 175b finally leading to the assigned first quick coupler hydraulic input 173b thus form a second conduit end section 175b, 176a, 177a of the front fluid line leading through the rear deflection block 163b.

The vertical bore 166c coming from the outlet 73 of the connecting bore 72 in the motor housing 24 forms, with the horizontal bore 175c leading to the assigned second quick coupler hydraulic input 173c, a third line end section 166c, 175c of the rear fluid line leading through the rear deflection block 163b.

The horizontal bore 176b coming from the assigned, second hydraulic pipe 163d, the subsequent vertical bore 177b and the horizontal bore 175a finally leading to the assigned first engine hydraulic input 173a thus form a first line end section 176b, 177b, 175a leading through the rear deflection block 163b for connecting the front engine pressure chamber 121 to the hydraulic supply.

The vertical bore 166d leading to the rear engine pressure chamber 122 in the engine housing 24 forms, with the horizontal bore 175d leading to the assigned second engine hydraulic input 173d, a fourth line end section 166d, 175d leading through the rear deflection block 163b for connecting the rear engine pressure chamber 122 to the hydraulic supply.

Furthermore, a double check valve cartridge or a load holding valve cartridge could be installed in the rear deflection block, into which all fluid channels ultimately lead.

The valve cartridge must be installed in such a way that it is positioned between the hydraulic connection of the front engine pressure chamber and the front engine pressure chamber, and at the same time between the hydraulic connection of the rear engine pressure chamber and the rear engine pressure chamber. When activated, the cartridge allows the hydraulic fluid to flow into the corresponding engine pressure chamber and drain from the opposite engine pressure chamber. If the swivel motor is not actuated, the valve cartridge locks the hydraulic fluid in the two motor pressure chambers. This valve cartridge keeps the hydraulic pressure locked in the front and rear engine pressure chambers, the piston remains preloaded and the engine is in a stable position. If the aim is not to move the swivel motor, any unforeseen and unwanted movements can be excluded, which reduces the potential risk in the swivel area.

In the previous embodiment of the invention with front and rear rotary feedthroughs, the swivel motor 23 has a fixed bearing-fixed bearing design of the motor shaft 32. That is to say, the motor shaft 32 and the bottom bearing 34 are fixedly mounted in their axial and radial degrees of freedom.

Another swivel motor variant with front and rear rotary feedthrough and with a fixed bearing / floating bearing arrangement is in the Figures 17 to 19 shown.

The motor shaft 200 is also arranged here with fixed bearings, i. H. Fixedly mounted in their axial and radial degrees of freedom, only the rotation is free. The bottom bearing 201 is, however, arranged as a floating bearing, i. H. Although radially fixed, but with an axial degree of freedom and with a degree of freedom of rotation with respect to the motor shaft 200. A torque is thus only transmitted from the motor or toothed shaft 200 to the front suspension plate 202. The swivel motor 203 can only be supported radially via the rear side cover 204 in the rear suspension plate 205. This means that only radial forces are transmitted via the rear connection, but no torque.

• Das Bodenlager 201 wird auf die Zahnwelle 200 geschraubt und mittels Stiften 206 gegen Lösen gesichert. Die Sicherung des Bodenlagers 201 kann jedoch auch mittels einer Sicherungsmutter oder ähnlich bekannten Sicherungsmethoden gesichert werden.
• Das Bodenlager 201 besitzt an seiner Flanschseite 207 eine ringförmige Nut 208 für den Sitz des hinteren Seitendeckels 204. In dieser Nut sind umlaufend Gewindebohrungen 209 angebracht.
• Die Ausführung des hinteren Seitendeckels (Fig. 18): Der hintere Seitendeckel 204 ist in einer zylindrischen Form ausgeführt und weist drei verschiedene Durchmesserstufen auf. Die zweite Durchmesserstufe 215 dient für den Sitz eines Schmutzabstreifers 216. Die dritte Durchmesserstufe 217 ist am vorderen Ende 218 angefast und weist zwei ringförmige Nuten für Dichtungen 219a und 219b konzentrisch zur Wellenhauptachse 211 auf. Zwischen den beiden Nuten 219a und 219b ist eine ringförmige Ölführungsnut 220 angebracht. Falls das Doppeldruckbegrenzungsventil am hinteren Ende der Zahnwelle 200 positioniert ist, weist der hintere Seitendeckel 204 einen zweistufigen kreisförmigen Innenausschnitt 221a und 221b mit ausreichendem Durchmesser auf, um im Bedarfsfall Zugang zu Verschlussschraube 222 und Ventil 223 zu gewährleisten. Dieser kreisförmige Ausschnitt 221a wird durch einen Stöpsel 224 mit ausreichendem Durchmesser zum Schutz vor dem Eintritt von Verunreinigungen versiegelt. Die zweite Stufe des Innenausschnitts 221b dient zur Freigängigkeit des Bodenlagers 201 und der Zahnwelle 200. Der hintere Seitendeckel 204 weist Durchgangsbohrungen mit Flachsenkungen 227 mit einem Lochbild 225 und einem Lochkreisdurchmesser 226 auf. Dieses Lochbild 225 und der Lochkreisdurchmesser 226 sind identisch zu Lochbild und Lochkreisdurchmesser der Gewindebohrungen 209 des Bodenlagers 201. Von der vorderen Stirnseite 228 des hinteren Seitendeckels 204 ist eine Horizontalbohrung 229 bis zur Höhe der Ölführungsnut 220 ausgeführt. Von der radialen Mantelfläche der Ölführungsnut 220 ist eine vertikale Bohrung 230 in Richtung Wellenhauptachse 211 ausgeführt und schneidet sich mit der Horizontalbohrung 229. Die Position der Horizontalbohrung 229 bzw. des Dichtungssitz 231 ist auf dem Lochkreisdurchmesser 226 zwischen zwei der Durchgangsbohrungen 227.
• Für den Sitz einer Dichtung 232 ist konzentrisch zur Horizontalbohrung 229 eine Flachsenkung 231 ausgeführt. Diese Flachsenkung kann jedoch statt im hinteren Seitendeckel 204 auch im Bodenlager 201 um den entsprechenden Fluidkanalanschluss ausgeführt sein.
• Der hintere Seitendeckel 204 wird auf das Bodenlager 201 geschraubt und ist mit der radialen Außenfläche der Nut 208, aber auch stirnseitig in Kontakt.
• An der radialen Mantelfläche des Bodenlagers ist eine Vertikalbohrung 210 in Richtung Wellenhauptachse 211 angebracht. Die Vertikalbohrung 210 ist zur hinteren ringförmigen Ölführungsnut 212 im Motorengehäuse 213 ausgerichtet. In der ringförmigen Nut 208 des Bodenlagers ist zwischen zwei Gewindebohrungen 209 eine Horizontalbohrung 214 angeordnet und mit der Vertikalbohrung 210 verbunden.
• Der hintere, herausragende Teil des Bodenlagers ist mit einem Absatz 233 versehen, auf dem ein Schmutzabstreifer 234 montiert ist. Deshalb sind in der hinteren Gleitlagerfläche 235 des Motorengehäuses nur noch zwei Dichtungsnuten 236a und 236b angeordnet, die der Abdichtung der hinteren Ölführungsnut 214 dienen. Die Aufteilung der Dichtungen in und am Schwenkmotorgehäuse ist auch bei dieser Variante gleichmäßig in der vorderen Gleitlagerung und hinteren Gleitlagerung verteilt. Hierdurch werden einseitige Reibung und Torsionsbeanspruchung reduziert.
• Am Schwenkmotorgehäuse 213 auf der hinteren Stirnseite ist eine Planfläche 237 gefräst an der die Dichtlippe des Schmutzabstreifers 234 anliegt und abdichtet.
• Das hintere Aufhängungsblech weist nur noch eine große Aufnahmebohrung 238 für den Sitz des hinteren Seitendeckels 204 auf. Die vordere und hintere Stirnseite 241a und 241b des hinteren Aufhängungsblechs weist um die Aufnahmebohrung jeweils eine abgefräste Planfläche auf, auf der die Dichtlippen der Schmutzabstreifer 216 und 234 eingreifen. Die Schmutzabstreifer 216 und 234 sorgen dafür, dass kein Schmutz in die Aufnahmebohrung des hinteren Aufhängungsblechs eindringen kann und das axiale Gleiten des Seitendeckels nicht eingeschränkt wird. Der innere Schmutzabstreifer 234 dichtet außerdem das Innere des Schwenkmotorgehäuses ab und verhindert das Eindringen von Schmutz.
• Eine vertikale Bohrung 239a und 239b von der Schnellwechsler-Grundplatte 240 führt bis zur Aufnahmebohrung 238 des hinteren Seitendeckels 204. Diese Vertikalbohrung 239a ist auf Höhe der Ölführungsnut 220 des hinteren Seitendeckels positioniert. Durch die Dichtungen 219a und 219b im hinteren Seitendeckel 204 ist die Ölführungsnut 220 fluiddicht mit der Vertikalbohrung 239a und b verbunden.
• Das Bodenlager und das hintere Schnellwechsler-Aufhängungsblech werden nicht mit dem hinteren Seitendeckel verspannt (Loslageranordnung).
• Der Seitendeckel wird nur noch radial im hinteren Aufhängungsblech abgestützt und kann axial gleiten (Loslager).
• Ein Spalt ist zwischen Bodenlager und hinterem Schwenkmotor-Aufhängungsblech angeordnet, für den Axialausgleich des Bodenlagers, das als Loslager angeordnet ist.
• Ein Spalt ist zwischen Absatz 215 des hinteren Seitendeckels und Schwenkmotor-Aufhängungsblech 205 vorhanden, um ein axiales Wandern des Bodenlagers und des hinteren Seitendeckels zu gewährleisten (Loslageranordnung).
• die restliche Anordnung der Ölführung im Schnellwechsler ist identisch wie zuvor in der Festlager-Festlager-Anordnung beschriebenen Ausführungsform der Erfindung.
• Somit ist eine fluiddichte Verbindung vom DD1-Motorenanschluss, durch den Schwenkmotor bis hin zum Linearaktuator des Schnellwechslers hergestellt.

The swivel motor 203 with a fixed bearing / floating bearing design is constructed similarly to the swivel motor 24 with a fixed bearing / fixed bearing design. A distinction must be made between the two solutions at the following points:

• The floor bearing 201 is screwed onto the splined shaft 200 and secured against loosening by means of pins 206. The securing of the floor bearing 201 can however, they can also be secured by means of a locking nut or similar known locking methods.
• The bottom bearing 201 has an annular groove 208 on its flange side 207 for the seat of the rear side cover 204. In this groove, threaded bores 209 are made all around.
• The design of the rear side cover ( Fig. 18 ): The rear side cover 204 is designed in a cylindrical shape and has three different diameter stages. The second diameter step 215 serves to seat a dirt scraper 216. The third diameter step 217 is chamfered at the front end 218 and has two annular grooves for seals 219a and 219b concentric to the main shaft axis 211. An annular oil guide groove 220 is provided between the two grooves 219a and 219b. If the double pressure relief valve is positioned at the rear end of the splined shaft 200, the rear side cover 204 has a two-stage circular inner cutout 221a and 221b with a sufficient diameter to ensure access to screw plug 222 and valve 223 if necessary. This circular cutout 221a is sealed by a plug 224 of sufficient diameter to prevent the ingress of contaminants. The second step of the inner cutout 221b is used to allow the floor bearing 201 and the splined shaft 200 to move freely. The rear side cover 204 has through bores with flat countersinks 227 with a hole pattern 225 and a hole circle diameter 226. This hole pattern 225 and the hole circle diameter 226 are identical to the hole pattern and hole circle diameter of the threaded holes 209 of the floor bearing 201. A horizontal hole 229 is made from the front end 228 of the rear side cover 204 up to the level of the oil guide groove 220. A vertical bore 230 is made in the direction of the main shaft axis 211 from the radial outer surface of the oil guide groove 220 and intersects with the horizontal bore 229. The position of the horizontal bore 229 or the seal seat 231 is on the pitch circle diameter 226 between two of the through bores 227.
• For the seat of a seal 232, a countersink 231 is made concentric to the horizontal bore 229. However, instead of in the rear side cover 204, this flat countersink can also be implemented in the floor bearing 201 around the corresponding fluid channel connection.
• The rear side cover 204 is screwed onto the floor bearing 201 and is in contact with the radial outer surface of the groove 208, but also on the face side.
• A vertical bore 210 in the direction of the main shaft axis 211 is made on the radial jacket surface of the floor bearing. The vertical bore 210 is aligned with the rear annular oil guide groove 212 in the motor housing 213. In the annular groove 208 of the floor bearing, a horizontal bore 214 is arranged between two threaded bores 209 and is connected to the vertical bore 210.
• The rear, protruding part of the floor bracket is provided with a shoulder 233 on which a dirt scraper 234 is mounted. Therefore, only two sealing grooves 236a and 236b are arranged in the rear sliding bearing surface 235 of the motor housing, which are used to seal the rear oil guide groove 214. The division of the seals in and on the swivel motor housing is evenly distributed in this variant in the front plain bearing and rear plain bearing. This reduces one-sided friction and torsional stress.
• A flat surface 237 is milled on the swivel motor housing 213 on the rear face, on which the sealing lip of the dirt scraper 234 rests and seals.
• The rear suspension plate now only has one large receiving bore 238 for the seat of the rear side cover 204. The front and rear end faces 241a and 241b of the rear suspension plate each have a milled flat surface around the receiving bore, on which the sealing lips of the dirt scrapers 216 and 234 engage. The dirt wipers 216 and 234 ensure that no dirt can penetrate into the mounting hole of the rear suspension plate and that the axial sliding of the side cover is not restricted. The inner dirt wiper 234 also seals the interior of the swing motor housing and prevents dirt from entering.
• A vertical bore 239a and 239b from the quick coupler base plate 240 leads to the receiving bore 238 of the rear side cover 204. This vertical bore 239a is positioned at the level of the oil guide groove 220 of the rear side cover. The oil guide groove 220 is connected in a fluid-tight manner to the vertical bore 239a and b through the seals 219a and 219b in the rear side cover 204.
• The bottom bracket and the rear quick hitch mounting plate will not braced with the rear side cover (floating bearing arrangement).
• The side cover is only supported radially in the rear suspension plate and can slide axially (floating bearing).
• A gap is arranged between the floor bearing and the rear swivel motor mounting plate, for the axial compensation of the floor bearing, which is arranged as a floating bearing.
• A gap is provided between the shoulder 215 of the rear side cover and the swivel motor mounting plate 205 in order to ensure that the bottom bearing and the rear side cover can move axially (floating bearing arrangement).
• the remaining arrangement of the oil guide in the quick coupler is identical to the embodiment of the invention described above in the fixed bearing-fixed bearing arrangement.
• This creates a fluid-tight connection from the DD1 motor connection through the swivel motor to the linear actuator of the quick coupler.

Figure 20 FIG. 4 shows an embodiment of the invention which is largely similar to that shown in FIGS Figures 17 to 19 embodiment shown corresponds. However, the quick coupler / swivel motor combination shown here has a quick coupler with a single-acting linear actuator 402, the quick coupler being locked by means of spring force of a compression spring 402a placed around the piston of the linear actuator and only the quick coupler being unlocked hydraulically via hydraulic pressure in a pressure chamber 402b of the Linear actuator 402.

Accordingly, the quick coupler / swivel motor combination also has only a single fluid line which connects the quick coupler pressure chamber 402b to a single, assigned quick coupler hydraulic input on the rear deflection block 463b. A front rotary leadthrough 447, 448a, 448b for this is formed on the front shaft flange 437 and has an annular oil guide groove 447 which is sealed by two. A rear rotary feedthrough, however, is missing.

The annular oil guide groove 447 of the front rotary feedthrough 447, 448a, 448b leads via a front motor shaft-internal line section (longitudinal bore 478b, transverse bore 479) into a front suspension sheet-internal line section 59, 60, 495 running internally in the front suspension sheet 455, which in turn leads the bores 59, 60 through an O-ring holder and a vertical connecting hole 495 down to the quick changer base plate 462 or the front quick changer frame-side line section 464, 505 running therein.

Accordingly, only the front line section 464, 505 on the quick changer frame side is present in the quick changer. A rear line section on the quick changer frame side is missing. A rear rotary leadthrough and a rear suspension plate-internal line section in a rear suspension plate 480 are also missing.

Deviations and variations of the embodiments shown are conceivable without departing from the scope of the invention.
For example, it would be conceivable to use a quick changer with a single-acting linear actuator on a quick changer / swivel motor combination with a front and a rear fluid line and to place one of the two fluid lines blind.

List of reference symbols

1

Boom of the excavator

2

lower end of the excavator boom

3

Axle mount on the front of the excavator truck

4th

Boom cylinder

5

Excavator superstructure

6th

upper end of the boom

7th

Stick cylinder

8th

Dipperstick

9

upper end of dipperstick 8

10

Undercarriage of the excavator

11

vertical axis around which the excavator superstructure can be rotated

12th

vertical axis around which the boom is rotatably attached to the excavator superstructure

13th

lower end of dipperstick 8

14th

Deflector

15th

Pressure support

14.15

Bucket motion components

16

Bucket cylinder

17th

Cylinder bottom side of the bucket cylinder

18th

Cylinder piston rod

19th

Cross hole at the bottom of the dipperstick

20th

Cross hole at the lower end of the pressure support

21

Mounting bolts

22nd

Ditch cleaning bucket

23

Rotary motor

24

Motor housing

25a

Flat cylindrical shaped section of the front side cover

25b

cylindrical fitting portion of the front side cover

25c

cylindrical recess on the front side cover

26th

front face of the swivel motor housing

27

rear face of the swivel motor housing

28a, 28b

Fastening feet for fastening the excavator suspension to the swing motor housing

29

Side brackets (excavator suspension)

30th

first housing section

31

third housing section

32

Motor shaft

33

Swivel motor piston

34

Bottom bearing of the swivel motor

35

Longitudinal axis of the swivel motor

36

Plain bearing of the shaft

37

front shaft flange or flange section of the shaft

38

front shaft end

39

rear shaft end

40

Thread inside the bottom bracket

41

Thread circumferential section of the shaft

42

Support ring

43

Thrust washer between shaft and support ring

44

Thrust washer between floor bearing and housing

45

Locknut bottom bracket / shaft

46

Cylinder screw for countering the lock nut

47

front annular oil guide groove

48a, 48b

Sealing rings for the front oil guide groove

48c

front wiper ring

49

Connection hole between the front oil guide groove and hydraulic connection 50

50

Hydraulic connection on the front top of the engine

51

Cross hole to the front oil guide groove

52a

Hole pattern on the front end of the shaft

52b

Hole circle diameter at the front end of the shaft

53

Threaded holes of the bolt circle

54a

Opening of the longitudinal bore 54b

54b

Longitudinal bore that leads to the transverse bore 51

55

front suspension plate

56

Mounting hole on the front suspension plate

57

Location hole as a seat for the front O-ring holder

58

front O-ring holder

59

Longitudinal hole in the O-ring holder

60

Cross holes in the O-ring holder

61a

front free rotation in the O-ring holder

61b

rear sealing groove in the O-ring holder

62

Base plate of the quick coupler frame

62a

front side wall of the quick hitch frame

62b

Bottom wall of the quick coupler frame

63

Quick coupler

64

front fluid channel in the quick coupler base plate

65

Threaded hole on the back of the O-ring holder

66

Sealing seat on the O-ring holder

67

Seal on the front O-ring holder

68

Sealing O-ring on the front O-ring holder

69

Plain bearing of the floor bearing

70

rear annular oil guide groove

71a, 71b

Sealing rings for the rear oil guide groove

71c

rear wiper ring

72

Connecting hole between the rear oil guide groove and hydraulic connection 73

73

Hydraulic connection on the rear top of the engine

74

rear shaft flange or bottom bearing flange

75a

flat cylindrical shaped section of the rear side cover

75b

cylindrical fitting portion of the rear side cover

75c

cylindrical recess on the rear side cover

76a

Hole pattern on the bottom bracket

76b

Bolt circle diameter on the bottom bracket

77

Threaded holes of the bolt circle

78a

Opening of the longitudinal bore 78b

78b

Longitudinal bore connected to transverse bore 79

79

Cross hole to the rear oil guide groove

80

rear suspension plate

81

Mounting holes on the rear suspension plate

82

Location hole for rear O-ring holder

83

rear O-ring holder

84

rear fluid channel

85

Seal on the rear O-ring holder

86

Sealing O-ring on the rear O-ring holder

87

front weld

88

rear weld

89

lower tier

90

level above

91

Groove cover

92

Weld seam on the groove cover

93

front area of the quick coupler base plate

94

rear area of the quick coupler base plate

95

front connecting hole

96

front threaded hole on the quick coupler base plate

97

Locking screw for the front threaded hole

98a, 98b

Sections of the rear connecting hole

99

rear threaded hole on the quick coupler base plate

100

Locking screw for the rear threaded hole

101

Flat surface on the underside of the quick coupler base plate

102

Linear actuator

103

front linear actuator connection

103a

front pressure chamber

104

rear linear actuator connection

104a

rear pressure chamber

105

front connection hole to the linear actuator

106

rear connection hole to the linear actuator

107

Linear actuator housing

108

front flange countersink

109

rear flange countersink

110

front seal on the linear actuator housing

111

rear seal on the linear actuator housing

112

Seal motor shaft-bottom bearing

113

External thread of the motor shaft

114

Internal thread of the piston

115

External thread of the piston

116

Internal thread of the motor housing

117

front annular piston guide

118

rear annular piston guide

119a, 199b

Seals on the piston guides

120a, 120b

Guide straps on the piston guides

121

front engine pressure chamber

122

rear engine pressure chamber

123

Hydraulic fluid connection for the front engine pressure chamber

124

Hole for the front engine pressure chamber

125

Hydraulic fluid connection for rear engine pressure chamber

126

Hole for rear engine pressure chamber

127

Cross hole on the front shaft flange

128a

axial contact surface of the swivel motor housing

128b

axial contact surface of the swivel motor housing

129

stepped bore on the face

130

first cross hole

131

second cross hole

132

Double pressure relief valve

133

Screw plug of the double pressure relief valve

136

annular groove of the front shaft flange

137

front side cover

138

Through holes on the front side cover / front suspension plate

139

Screws

140

Screw lock washers

141

outer grooved surface at the front

142

annular recess on the floor bearing

143

rear side cover

144

Through holes on the rear side cover / rear suspension plate

145

Screws

146

Screw lock washers

147

outer groove ring surface at the rear

148

Hole pattern on the front suspension plate

149

Hole pattern on the rear suspension plate

150

circular cutout on the front suspension plate

151

circular cutout on the rear suspension plate

152

Milled recess on the front suspension plate

153

Milled recess on the rear suspension plate

154

Oil feed-through cover on the front side cover

155

Oil feed-through cover on the rear side cover

157

circular cutout on the rear side cover

158

Plug on the rear side cover

159

Cutout on the front side cover

160

Cutout on the rear side cover

163a

front conduit turning block

163b

rear conduit turning block

163c

first hydraulic pipe to the front rotating union

163d

second hydraulic pipe to the front engine pressure chamber

164

curved hose guide

165

Hydraulic hoses

166a, 166b

Vertical holes on the front deflection block

166c, 166d

Vertical holes on the rear deflector block

167a, 167b

Horizontal bores on the front deflection block

168

Screws for front / rear deflection block

169a

Sealing surface for front deflection block

170

Flat countersinks on the front deflection block

171

Seals on the engine side on the front deflection block

172a, 172b

Seals at the front end of the hydraulic pipes

172c, 172d

Seals at the rear of the hydraulic pipes

173a

first motor hydraulic input

173b

first quick coupler hydraulic input

173c

second quick coupler hydraulic input

173d

second motor hydraulic input

174a, 174b

Mounting holes for hydraulic pipes on the front deflection block

174c, 174d

Mounting holes for hydraulic pipes on the rear deflection block

175a, 175b, 175c, 175d

Horizontal drilling at the hydraulic inputs

176a, 176b

Vertical holes in the rear deflector block

181

Adapter frame

183

Back plate of the adapter frame

187a, 187b

semicircular cutouts in the rear panel

188

Rear wall of the quick-change frame

190

Hydraulic piston

191a, 191b

Housing end of the linear actuator housing

192

Actuator longitudinal axis

193

Piston rod

194

Piston rod eye

196a, 196b

Latch wedges

198a, 198b

Wedge surface of the locking wedges

199

annular oil guide groove to the front engine pressure chamber

402

single-acting linear actuator

402a

Compression spring

402b

Pressure chamber

463b

rear turning block

447, 448a, 448b

front rotating union

447

annular oil guide groove

448a, 448b

Sealing rings

478b, 479

front motor shaft internal line section

478b

Longitudinal bore

479

Cross hole

59, 60, 495

Line section inside the front suspension plate

464, 505

Line section on the quick changer frame side

464

Fluid channel in the quick coupler base plate

480

rear suspension plate

505

front connection hole to the linear actuator

Claims (15)

1. Quick change pivot motor combination for coupling and uncoupling attachments (22) to and from a dipper arm (8) of an earth-moving machine, wherein the coupled attachment (22) can be pivoted out laterally relative to a forward plane of rotation of the dipper arm (8), wherein the forward plane of rotation corresponds to a pivot axis plane extending vertically through the quick change pivot motor combination when the attachment (22) is coupled and not pivoted out, having:

   a pivot motor (23) and a hydraulically actuatable quick coupler (63) suspended below the pivot motor (23) and laterally pivotable out by means of the pivot motor (23), wherein

   the pivot motor (23) has a preferably cylindrical motor housing (24), in which a motor shaft (32), which can be rotated by hydraulic pressure, is mounted with a front shaft flange (37) and a rear shaft flange (74) on a front and a rear plain bearing (36, 69) so as to be rotatable about a pivot axis (35) which is preferably horizontal in the pivot axis plane, and wherein

   as excavator suspension on both sides of the pivot axis plane, side plates (29) extending along the pivot axis plane and upwardly are attached, preferably welded, to the motor housing (24), and wherein

   a front suspension plate (55) is attached to the front shaft end (38) of the motor shaft (32) and a rear suspension plate (80) is attached to the rear shaft end (39) of the motor shaft (32), so that the two suspension plates (55, 80) each extend downwardly transversely to the pivot axis plane, wherein the quick coupler (63) comprises a quick coupler frame (62, 62a, 62b, 188) to which the front and rear suspension plates (55, 80) are fastened, preferably welded on, so that a torque can be transmitted from the motor shaft (32) to the quick coupler (63) and the quick coupler (63) can be pivoted out laterally with respect to the motor housing (24) about the pivot axis (35) out of the pivot axis plane, and wherein

   the quick coupler frame (62, 62a, 62b, 188) has a linear actuator (102) which can be hydraulically actuated via a number of pressure chambers (103a, 104a), and on a front side of the quick coupler frame (62, 62a, 62b, 188) an engagement arrangement preferably provided with claws (186a, 186b) for engaging a counter-engagement arrangement, which is preferably in the form of a shaft, is provided on the attachment (22), and on a rear side of the quick coupler frame (62, 62a, 62b, 188) a locking element (196a, 196b), which is actuated via the linear actuator (102) and is accommodated in a displaceable manner for locking or unlocking on an associated counter-engagement arrangement on the attachment (22), is provided, and wherein

   a number of fluid lines corresponding to the number of pressure chambers (103a, 104a) are provided, which connect the number of pressure chambers (103a, 104a) to a corresponding number of quick coupler hydraulic inlets (173b, 173c) for connection to a hydraulic supply of the earth-moving machine on an upper side of the motor housing (24), and wherein

   the number of fluid lines comprises a corresponding number of rotary unions (47, 48a, 48b, 70, 71a, 71b), wherein each of the number of rotary unions (47, 70) is provided on one of the plain bearings (36, 69) and comprises an annular oil guide groove (47, 70) formed in the motor housing (24) on an inner circumferential side and/or in the motor shaft (32) on an outer circumferential side, which is sealed with sealing rings (48a, 48b, 71a, 71b), wherein a line section (49, 72) inside the motor housing leads from the annular oil guide groove (47, 70) in the direction of one of the quick coupler hydraulic inlets (173b, 173c) and one of a number of engine-shaft-internal line sections (51, 54b, 78b, 79) into one of a number of suspension-plate-internal line sections (59, 60, 95, 59, 60, 98a, 98b), and from there further into one of a number of quick-coupler-frame-internal line sections (64,105, 84, 106), which opens into one of the number of pressure chambers (103a, 104a),

   characterized in that

   the number of fluid lines both at the front plain bearing (36) and at the rear plain bearing (69) each comprises at most a single one of the number of rotary unions (47, 48a, 48b, 70, 71a, 71b).
2. Quick change pivot motor combination according to claim 1, characterized in that a single-acting linear actuator having a single pressure chamber is provided, said actuator being locked by mechanical spring pretension and being unlockable by hydraulic pressure from the pressure chamber against the spring pretension, wherein a single fluid line is provided for connecting the pressure chamber to a single quick coupler hydraulic inlet, wherein the fluid line comprises either
   only a front rotary union (447, 448a, 448b) at the plain bearing (436) located in the area of the front shaft flange (437), and the annular oil guide groove (447) of the front rotary union (447, 448a, 448b) leads via a front engine-shaft-internal line section (478b, 479) into a front suspension-plate-internal line section (59, 60, 495) extending internally in the front suspension plate (455), or
   preferably comprises only one rear rotary union at the plain bearing located in the region of the rear shaft flange, and the annular oil guide groove of the rear rotary union leads via a rear engine-shaft-internal line section into a rear suspension-plate-internal line section extending internally in the rear suspension plate.
3. Quick change pivot motor combination according to claim 1, characterized in that a double-acting linear actuator (102) having two pressure chambers (103a, 104a) is provided, which can be locked and unlocked by hydraulic pressure from the respective pressure chamber (103a, 104a), wherein two fluid lines are provided for connecting the two pressure chambers (103a, 104a) to two quick coupler hydraulic inlets (173b, 173c), wherein
   a front one of the two fluid lines connects a front rotary union (47, 48a, 48b) at the plain bearing (36) located in the area of the front shaft flange (37), and the annular oil guide groove (47) of the front rotary union (47, 48a, 48b) leads via a front engine-shaft-internal line section (78b, 79) into a front suspension-plate-internal line section (59, 60, 95) extending internally in the front suspension plate (55), and wherein
   a rear one of the two fluid lines has a rear rotary union (70, 71a, 71b) on the plain bearing (69) located in the region of the rear shaft flange (74), and the annular oil guide groove (70) of the rear rotary union (70, 71a, 71b) leads via a rear engine-shaft-internal line section (78b, 79) into a rear suspension-plate-internal line section (59, 60, 98a, 98b) extending internally in the rear suspension plate (80).
4. Quick change pivot motor combination according to claim 1, 2 or 3, characterized in that the front suspension-plate-internal line section (59, 60, 95) on the front side of the quick coupler (63) opens into a front quick-coupler-frame-internal line section (64, 105), which from there leads further into one of the two pressure chambers (103a, 104a), and/or the rear suspension-plate-internal line section (59, 60, 98a, 98b) on the rear side of the quick coupler (63) opens into a rear quick-coupler-frame-internal line section (84, 106), which leads from there further into the other of the two pressure chambers (103a, 104a).
5. Quick change pivot motor combination according to one of the preceding claims, characterized in that the quick coupler frame (62, 62a, 62b, 188) comprises a base plate (62) which is welded to the underside end faces of the suspension plates (55, 80) and into which the number of quick-coupler-frame-internal line sections (64, 105, 84, 106) is incorporated, wherein in at least one of the two suspension plates (55, 80), a connecting bore (95, 98a, 98b) leads upwards from its underside end face, wherein each connecting bore (95, 98a, 98b) is connected at the bottom to one of the number of quick-coupler-frame-internal line sections (64, 105, 84, 106) and at the top via a transversely extending receiving bore (57, 82) to one of the number of engine-shaft-internal line sections (58, 95, 83, 98a, 98b).
6. Quick change pivot motor combination according to claim 5, characterized in that a number of horizontally extending oil guide grooves is incorporated into the base plate (62), wherein each of the number of oil guide grooves has two steps (89, 90) in cross-section and a groove cover (91) is arranged in the upper step (90) and welded to the base plate (62), and wherein each of the number of horizontally extending oil guide grooves opens at one end with its lower step (89) into a connecting bore (105, 106) extending transversely to the oil guide groove and leading into the associated pressure chamber (103a, 104a), and at the other end into a line section which emerges from the base plate (62) at the top and which opens into a connecting bore (95, 98a, 98b) leading upwards into the associated suspension plate (55, 80), so that the number of quick-coupler-frame-internal line sections (64, 105, 84, 106) is formed completely on the base plate (62).
7. Quick change pivot motor combination according to one of the preceding claims, characterized in that the pivot motor comprises a piston (33) arranged radially between the motor housing (24) and the motor shaft (32) and axially between the front shaft flange (37) and the rear shaft flange (74), which piston forms a steep threaded pairing with the motor housing (24) and a steep threaded pairing in the opposite direction thereto with the motor shaft (32), wherein a front engine pressure chamber (121) is arranged on a front side of the piston (33) and a rear engine pressure chamber (122) is arranged on a rear side of the piston (33), which are connected via engine hydraulic inlets (173a, 173d) on the upper side of the motor housing (24) to the hydraulic supply of the earth-moving machine in order to effect a translational movement of the piston (33) by hydraulic pressure on the front or rear side of the piston (33) and a rotary movement of the engine shaft (24) via the steep thread pairings.
8. Quick change pivot motor combination according to one of the preceding claims, characterized in that the number of quick coupler hydraulic inlets (173b, 173c) serving to connect the number of fluid lines to the hydraulic supply of the earth-moving machine and preferably also the number of engine hydraulic inlets (173a, 173d) serving to connect the two motor pressure chambers (121, 122) of the pivot motor (23) to the hydraulic supply of the earth-moving machine is arranged in the rear upper region on the motor housing (24) and preferably has an opening direction directed forwards in each case at least with a directional component along the pivot axis.
9. Quick change pivot motor combination according to claim 8, characterized in that a front motor-housing-internal line section of the front fluid line has a line section extending rearwardly along the engine shaft through a wall of the motor housing to connect the oil guide groove of the front rotary union to the associated quick coupler hydraulic inlet for connecting the front fluid line to the hydraulic supply of the earth-moving machine.
10. Quick change pivot motor combination according to claim 8, characterized in that a front motor-housing-internal line section (49) of the front fluid line consists of a connecting bore (49) leading upwardly from the front rotary union (47, 48a, 48b) through the motor housing (24), which opens into a first deflection line section (166a, 167a) leading through a front deflection block (163a), wherein the front deflection block (163a) is screwed onto the motor housing (24) above the front shaft flange (37), and wherein the first deflection line section (166a, 167a) is connected via a hydraulic tube (163c) to a first line end section (175a, 176a, 177a) leading through a rear deflection block (163b) to the associated quick coupler hydraulic inlet (173b), wherein the rear deflection block (163b) is screwed onto the motor housing (24) above the rear shaft flange (74), and wherein the associated quick coupler hydraulic inlet (173b) is configured for connecting the front fluid line to the hydraulic supply of the earth-moving machine at the rear deflection block (163b).
11. Quick change pivot motor combination according to one of claims 8 to 11, characterized in that a rear motor-housing-internal line section (72) of the rear fluid line consists of a connecting bore (72) leading upwardly from the rear rotary union (70, 71a, 71b) through the motor housing (24), which connecting bore (72) is connected to a third line end section (166c, 175c) leading through the rear deflection block (163b), wherein the rear deflection block (163b) is screwed onto the motor housing (24) above the rear shaft flange (74), and the associated quick coupler hydraulic inlet (173c) is designed for connecting the rear fluid line to the hydraulic supply of the earth-moving machine at the rear deflection block (163b).
12. Quick change pivot motor combination according to one of claims 8 to 10, characterized in that a bore (124) leading to the front motor pressure chamber (121) opens through the motor housing (24) into a second deflection line section (166b, 167b) leading through the front deflection block (163a), wherein the second deflection line section (166b, 167b) is connected via a second hydraulic tube (163d) to a first line end section (175a, 175b, 177b) leading through the rear deflection block (163b) to the associated engine hydraulic inlet (173a), wherein the rear deflection block (163b) is screwed onto the motor housing (24) above the rear shaft flange (74) and the associated engine hydraulic inlet (173a) is formed for connecting the front motor pressure chamber (121) to the hydraulic supply of the earth-moving machine at the rear deflection block (163b).
13. Quick change pivot motor combination according to one of claims 7 to 12, characterized in that a bore (126) leading to the rear motor pressure chamber (122) upwardly through the motor housing (24) opens into a fourth line end section (166d, 175d) leading through rear deflection block (163b) to the associated engine hydraulic inlet (173d), wherein the rear deflection block (163b) is screwed above the bottom bearing flange (74) onto the motor housing (24) and the associated engine hydraulic inlet (173d) is formed for connecting the rear motor pressure chamber (122) to the hydraulic supply of the earth-moving machine at the rear deflection block (163b).
14. Quick change pivot motor combination according to one of the preceding claims, characterized in that the rear shaft flange (74) is formed as a bottom bearing flange (74) on a bottom bearing (34) pushed onto the rear shaft end (39) of the motor shaft (32) and fixed there in an axially fixed manner in co-rotation, wherein the front shaft end (38) is connected to the front suspension plate (55) and the bottom bearing (34) is connected to the rear suspension plate (80) in an axially fixed and torque-transmitting manner, and wherein the rear rotary union (70, 71a, 71b) is formed on the rear plain bearing (69) of the bottom bearing flange (74).
15. Quick change pivot motor combination according to one of the preceding claims 1 to 14, characterized in that the rear shaft flange is formed as a bottom bearing flange on a bottom bearing (201) which is pushed onto the rear shaft end of the motor shaft and is axially fixed there in a co-rotating manner, wherein the front shaft end is connected to the front suspension plate (202) in an axially fixed and torque-transmitting manner, and the bottom bearing (201) is mounted on the rear suspension plate (205) in an axially loose and non-torque-transmitting radially sliding manner, and wherein the rear rotary union (212, 236a, 236b) is formed on the rear plain bearing of the bottom bearing flange and an auxiliary rotary union (219a, 219b, 220) is connected via a number of engine-shaft-internal line sections (210, 214, 229, 230) to the plain bearing of the bottom bearing or a side cover (204), which is connected to the bottom bearing (201) in a co-rotating manner, is connected to the rear suspension plate (205), wherein the rear suspension-plate-internal line section (239a, 239b) extends from the auxiliary rotary union (219a, 219b, 220).

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