EP3719210A1 - Combinaison de moteur oscillant et de changement rapide - Google Patents

Combinaison de moteur oscillant et de changement rapide Download PDF

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Publication number
EP3719210A1
EP3719210A1 EP19020256.4A EP19020256A EP3719210A1 EP 3719210 A1 EP3719210 A1 EP 3719210A1 EP 19020256 A EP19020256 A EP 19020256A EP 3719210 A1 EP3719210 A1 EP 3719210A1
Authority
EP
European Patent Office
Prior art keywords
motor
shaft
hydraulic
quick
swivel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19020256.4A
Other languages
German (de)
English (en)
Other versions
EP3719210B1 (fr
Inventor
Thomas Bogner
Michael Wittmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Raedlinger Maschinen und Stahlbau GmbH
Original Assignee
Raedlinger Maschinen und Stahlbau GmbH
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Publication date
Application filed by Raedlinger Maschinen und Stahlbau GmbH filed Critical Raedlinger Maschinen und Stahlbau GmbH
Priority to EP19020256.4A priority Critical patent/EP3719210B1/fr
Publication of EP3719210A1 publication Critical patent/EP3719210A1/fr
Application granted granted Critical
Publication of EP3719210B1 publication Critical patent/EP3719210B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3663—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat hydraulically-operated
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3627—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat with a hook and a longitudinal locking element
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3654—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat with energy coupler, e.g. coupler for hydraulic or electric lines, to provide energy to drive(s) mounted on the tool
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3677—Devices to connect tools to arms, booms or the like allowing movement, e.g. rotation or translation, of the tool around or along another axis as the movement implied by the boom or arms, e.g. for tilting buckets

Definitions

  • 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 dipperstick 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 located at the other end of the dipper stick in the forward rotation plane.
  • generic quick coupler / swivel motor combinations provide a further degree of freedom of movement for the coupled implement, namely a lateral pivoting around a rotation axis lying in the forward rotation plane, so that with the coupled, laterally pivoted implement, for example a digging bucket Inclined planes, for example ditch slopes, can be worked on to the horizontal.
  • known quick coupler / swivel motor combinations each have a swivel motor and a hydraulically or mechanically operated quick coupler 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.
  • 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 around which the quick hitch can be swiveled out by the swivel motor lies. If the dipper stick with the attached quick coupler / 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 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 so as to be rotatable 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 areas on the inner circumference of the motor housing or 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.
  • 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 front and back of the motor housing, 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 swivel axis plane and serve to hang the quick coupler under the swivel motor.
  • the quick coupler has a frame that includes two side tabs that extend parallel to the pivot axis plane on both sides of the swivel axis plane in the non-swiveled 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 can be locked or unlocked on a second locking axis provided on the attachment by moving the locking claw hydraulically along the direction of the pivot axis.
  • double-acting hydraulic cylinder which can be moved towards the front end or towards the rear end along the direction of the pivot axis by applying pressure to a first pressure chamber or a second pressure chamber.
  • the pressurized hydraulic oil of the earth-moving machine which is provided via hydraulic feed lines from the dipperstick, must be fed into the two pressure chambers in the quick coupler.
  • hose lines outside the housing were provided in order to direct 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.
  • hose lines at the interface between the dipperstick and the attachment are constantly exposed to the risk of damage during rough work.
  • the motor shaft has two rotary feedthroughs at one end, which on the top side are connected to hydraulic connections on the dipperstick side via channels running through the wall of the motor housing and on the bottom side 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.
  • 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 lines could be pinched or torn off; falling stones onto the pipes could not be ruled out either.
  • the quick coupler is a safety-critical component, so that a permanently applied hydraulic pressure must be guaranteed so that the attached attachment cannot become loose and fall, which could otherwise lead to serious injuries for personnel in the immediate vicinity.
  • a quick coupler / swivel motor combination of the generic type which has a corresponding number of internal fluid lines to supply 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.
  • a single-acting linear actuator on the quick coupler in which the hydraulics only work in one direction, counter to the biasing force of a mechanical spring arrangement that actuates the linear actuator in the other direction when the hydraulic pressure is turned 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.
  • the rear end of the shaft has proven to be a suitable location for placing the rotary feedthrough on the sliding 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, in addition, 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.
  • 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 two fluid lines from two oil supply connections to supply the two pressure chambers required for this required on the top of the motor.
  • 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 , the ring-shaped oil guide groove of which leads via a front motor shaft-internal line section into a front suspension sheet-internal line section running internally in the front suspension plate, a rear fluid line having a rear rotary feedthrough on the sliding 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.
  • the rear shaft flange is here also advantageously a bottom bearing flange formed on a bottom 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 further into 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 in a rear line section inside the quick changer frame can open, which continues from there into the other of the two pressure chambers.
  • the quick coupler frame can advantageously comprise a base plate which is welded to the underside end faces of the suspension plates.
  • 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.
  • 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.
  • transverse bore can be designed as a receiving bore into 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 inside 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 running 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 at the top and into a line section 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 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.
  • the quick changer frame internal Line sections of the front and / or rear fluid line then comprise, for example, two oil guide grooves, which open at one end into different connecting bores leading into different pressure chambers and the other end into the same line section emerging from the top of the base plate, which leads up into the same, in the same suspension plate Connection hole opens.
  • 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.
  • a counter-attack arrangement preferably designed as a shaft
  • 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.
  • the engagement arrangement and the locking element of the quick coupler 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.
  • claws and locking bolts would also be included, which are attached to an adapter frame
  • 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.
  • 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.
  • the pivot 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 be connected to the motor housing a coarse thread pairing and, with the motor shaft, a rising thread pairing in opposite directions, 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 hydraulic supply of the earth-moving machine via motor hydraulic inputs on the top of the motor housing, 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.
  • 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
  • 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 slewing motor, which tends to brush against obstacles during work.
  • 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.
  • 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 have to connect the oil guide groove of the front rotating union with the associated quick coupler hydraulic input.
  • a front line section of the front fluid line inside the motor housing consists of a connecting bore leading upwards from the front rotary feedthrough through the motor housing, which opens 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.
  • the deflection line section in the front deflection block can then be connected to a line end section through a rear deflection block via a first hydraulic pipe.
  • 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.
  • 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 to a second line end section through the rear deflection block via a second hydraulic pipe, 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.
  • a rear line section of the rear fluid line inside the motor housing can consist of a connection 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.
  • a bore leading to the rear engine pressure chamber can be up through the engine housing into a further, fourth line end section through the rear Deflection block open out, 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.
  • end stops or milled surfaces can also be attached to the quick coupler base plate. These end stops are to 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 shaft end is connected to the front suspension plate and the floor bearing is axially fixed to the rear suspension plate and transmits torque, with the rear rotary feedthrough being formed on the rear plain bearing of the floor bearing flange, the result is reliable torque transmission from the motor shaft to the quick coupler housing.
  • the motor shaft does not have the necessary play on either side to compensate for heat-induced expansion, this arrangement can lead to problems.
  • 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.
  • the shaft has the smallest cross-sectional area in the rear area, the risk of shaft damage is particularly great there.
  • the bottom bearing in the rear plain bearing surface of the motor housing can easily tilt.
  • a large amount of friction arises in the rear sliding bearing, which is greater than in the front sliding bearing. This puts additional torsional stress on the shaft, which in turn has a strong influence on the service life of the shaft.
  • 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
  • the front shaft end is also axially fixed and axially fixed to the front suspension plate Is connected to transmit torque, but the bottom bracket 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.
  • the rear rotary leadthrough is advantageously connected via a number of internal channels to an additional rotary leadthrough on the plain bearing of the floor bearing on the rear suspension plate, the rear lead section internal to the suspension plate extending from the additional rotary leadthrough.
  • 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 laterally in the coupled state.
  • 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 pivot 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.
  • one or two boom cylinders 4 at the lower boom end 2 are used for raising and lowering in a vertical plane extending forwards 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 attached to the boom 1 for rotating the dipperstick 8 in the same vertically forwardly extending forward rotation plane in which the boom 1 operates.
  • the excavator superstructure 5 is fastened 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.
  • the dipperstick 8 is extended forward by two jointed bucket movement components (deflector 14 and pressure support 15) which can be moved by a bucket cylinder 16 in the forward rotation plane.
  • the bucket cylinder 16 is fastened with a cylinder bottom side 17 on the dipperstick 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.
  • 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 cleaning bucket by using 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.
  • the individually shown quick coupler / swivel motor combination includes a hydraulic swivel motor 23 with attached side brackets 29 serving as an excavator suspension, which have 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 therefore be attached to the dipperstick 8 and the pressure support 15 in a manner similar to a conventional backhoe bucket or comparable tool (see FIG Fig. 3 ).
  • a hydraulic quick coupler 63 is suspended from the suspension plate 55, 80 below the swivel motor 23, with which the tool can then be picked up.
  • 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 transversely to the plane of the forward rotation, and right and left side cutting edges which are arranged almost perpendicular to the main cutting edge.
  • 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. In this way, slope profiles and similar trenches can be created.
  • the side cutting edges are tilted from an almost vertical plane to 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.
  • the rigid trench clearing bucket 22 By pivoting the rigid trench clearing bucket 22, the bulk material can also be dumped out in a better metered manner.
  • 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
  • the swivel or rotary motor 23 shown in detail is attached, while the suspension plates 55, 80 for the quick changer 63 are attached to a motor shaft 32 rotatably arranged in the motor housing 24, so that the quick changer 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.
  • the cavity 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.
  • the motor shaft 32 designed as a splined 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.
  • a seal 112 is inserted between motor shaft 32 and floor bearing 34 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 a plurality of cylinder screws 46 and thereby locked.
  • 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 engages with its internal thread 114.
  • the piston 33 has an internal thread 114 in the first third from the front 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 an opposite pitch.
  • a front annular piston guide 117 is arranged on the outside perpendicular to the axis of rotation 35.
  • 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 to seat a seal 119a, 119b, the other groove to seat a guide band 120a, 120b.
  • Fig. 10 shows, at the front upper end of the swivel motor housing 24 there is a hydraulic fluid connection 123 with a bore 124 which enters an annular oil guide groove 199 in the motor housing 24 opens, with a transverse bore 127 being provided on the front shaft flange 37, which opens from the annular oil guide groove 199 into the front engine pressure chamber 121.
  • 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.
  • 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.
  • 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 double pressure relief valve 132 opens as overload protection against excessive pressure Hydraulic 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.
  • 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.
  • any other overload protection valve can also be used.
  • 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 between the motor housing 24 and the motor shaft 32, each inserted in one of the six circumferential grooves in the motor housing 24.
  • 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.
  • the rear oil guide groove 70 is connected through a connecting bore 72 to the hydraulic connection 73 located on the rear upper side of the engine.
  • a transverse bore 51 is arranged in the direction of the main shaft axis 35 on the sliding bearing 36. 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 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 the 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 machined into the bottom bearing flange 74 on the sliding bearing 69.
  • the position of this transverse bore 79 is aligned with the rear annular oil guide groove 70 of the motor housing 24.
  • At the end of the bottom bearing flange 74 is like 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.
  • the front shaft flange or flange section 37 has a round hole pattern 52a with a plurality of threaded bores 53 on the front end face of the motor shaft 24, see Fig. 7 .
  • an annular groove 136 is machined concentrically to the shaft axis 35 in 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 or 148 in the form of through bores 138 which is identical to the hole pattern 52a on the flange section 37.
  • 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. This absorbs radial forces and relieves the load on the screws 139.
  • 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 and on the floor bearing 74.
  • 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 sealed by a plug 158 of sufficient diameter to protect against ingress of contaminants.
  • a floor bearing flange 74 has a round hole pattern 76a with threaded holes 77, please refer Fig. 8 .
  • 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.
  • a free annular section remains in the annular recess 142 of the bottom bearing 34, which serves 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 lock nut 45 in the floor bracket 34.
  • the rear suspension sheet 80 is screwed to the floor bracket 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 section in the annular recess 142 of the bottom bearing 34, which extends around the lock nut 45 of the bottom bearing 34. As a result, radial forces are intercepted and the screws 145 are relieved.
  • 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 front O-ring holder 58 shown in detail 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.
  • 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 holder 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 fasten a puller for removing the front O-ring holder 58 from the receiving hole 57 of the front suspension plate 55.
  • the rear suspension plate 80 in the area of the hole pattern 76a ( Fig.
  • 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 shape and preferably also in terms of dimensions to the front O-ring holder 58 and 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 relief 61a and rear sealing groove 61b as the front O-ring holder 58.
  • the O-ring holder 83 is on the side of the Longitudinal bore 59 chamfered. This chamfer in turn serves as a sealing seat 66.
  • 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 removing 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 and 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.
  • the cover 154, 155 In the area of the cutouts 159, 160 on the two side covers 137, 143 there is a separate oil duct cover 154, 155 of the oil duct ( Fig. 16 ).
  • the shape and bores of the cover corresponds 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 by means of two screws 139, 145 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.
  • both the front and the rear suspension plate 55, 80 are fastened to the quick coupler base plate 62 by an oil-tight weld 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 guided 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 and fastened to the quick coupler base plate 62 by an oil-tight welded seam 92.
  • the screw plug 100 is 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.
  • the screw plugs 97 and 100 can be opened for maintenance work, e.g. B. for flushing the respective fluid channel.
  • 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.
  • 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 changer 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.
  • the quick changer frame 62, 62a, 62b, 188 is advantageously designed as a closed housing, like in particular the Figures 10 to 13 demonstrate.
  • On the front of the quick coupler 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.
  • the hydraulic linear actuator 102 which comprises 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 a longitudinal actuator axis 192 parallel to the longitudinal motor axis 35 .
  • An elongated piston rod 193 is attached to the piston 190 and is arranged coaxially in the linear actuator housing 107 and 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 of which on its upper side is inclined to one Wedge surface 198a, 198b is flattened.
  • 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 floor 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 bores 59, 60 and the rear connecting bores n 98a
  • the front fluid line comprises a front line section 49 inside the motor housing, a front rotary leadthrough 47, 48a, 48b on the front sliding bearing 36 or on the front shaft flange 37, a front line section 51, 54b inside the motor shaft, a front line section 59, 60, 95 inside the mounting 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 bracket 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.
  • 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.
  • Screw-in fittings 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.
  • 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 bore 124 leading to the front engine pressure chamber 121 opening into the front deflecting block 163a, the rear connecting bore 72 and the bore leading to the rear engine pressure chamber 122 126 on the rear deflection block 163b.
  • the two deflection blocks 163a, 163b are over two Hydraulic pipes 163c, 163d connected to one another, via which the front fluid line and the fluid line leading to the front engine pressure chamber are guided to the rear 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 inside with two horizontal bores 167a, 167b, which are machined into 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 that leads 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 machined 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 tubes 163c, 163d by means of seals 172a, 172b, 172c, 172d at the front and rear ends of the hydraulic tubes 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 side wall. Concentric to these four hydraulic inlets 173a, 173b, 173c and 173d, further horizontal bores 175a, 175b, 175c and 175d are drilled towards the rear of the block.
  • the rear deflection block 163b has two on the lower half horizontal mounting bores 174c, 174d for 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.
  • the two vertical bores 166c, 166d intersect two horizontal bores 175a, 175b in the interior of the rear deflection block 163b, which are assigned to the Lead hydraulic inputs 173a, 173d.
  • the rear deflection block is screwed onto a milled sealing surface 169b between the rear fastening feet 28b of the motor housing 24 by means of screws 168.
  • 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 counterbore 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 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 line 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 inlet 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.
  • a double check valve cartridge or a load holding valve cartridge could be built into the rear deflection block, into which all fluid channels ultimately lead.
  • the valve cartridge must be installed in such a way that it is 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 is positioned.
  • the cartridge When activated, the cartridge lets the hydraulic fluid flow into the corresponding engine pressure chamber and flow out of 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 no movement of the swivel motor is intended, any unforeseen and unwanted movements can be excluded, which reduces the potential risk in the swivel area.
  • the swivel motor 23 has a fixed bearing-fixed bearing design of the motor shaft 32. That is, the motor shaft 32 and the bottom bearing 34 are fixedly mounted in their axial and radial degrees of freedom.
  • the motor shaft 200 is also arranged here with fixed bearings, i. H. Fixed in its axial and radial degrees of freedom, only the rotation is free.
  • the bottom bearing 201 is, however, arranged as a floating bearing; 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.
  • FIG. 11 shows an embodiment of the invention which is largely similar to that in FIGS Figures 17 to 19 embodiment shown corresponds.
  • 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.
  • the quick coupler / swivel motor combination also only has 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.
  • the annular oil guide groove 447 of the front rotary feedthrough 447, 448a, 448b leads via a front line section inside the motor shaft (longitudinal bore 478b, transverse bore 479) into a front suspension sheet-internal line section 59, 60, 495 which runs internally in the front suspension sheet 455 and which in turn leads the bores 59, 60 by an O-ring holder and a vertical connecting bore 495 down to the quick changer base plate 462, or the front quick changer frame-side line section 464, 505 running therein.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Quick-Acting Or Multi-Walled Pipe Joints (AREA)
  • Hydraulic Motors (AREA)
EP19020256.4A 2019-04-04 2019-04-04 Combinaison de moteur oscillant et de changement rapide Active EP3719210B1 (fr)

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EP19020256.4A EP3719210B1 (fr) 2019-04-04 2019-04-04 Combinaison de moteur oscillant et de changement rapide

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021110943A1 (de) 2021-04-28 2022-11-03 Béla Cseri Besitzunternehmung GbR (vertretungsberechtigter Gesellschafter: Béla Cseri, 89129 Langenau) Baugruppe mit einem schwenkantrieb und einem schnellwechsler sowie arbeitsmaschine mit einer solchen baugruppe
DE102022121104A1 (de) 2022-08-22 2024-02-22 emtec Engineering & Maschinentechnik GmbH Ankoppelvorrichtung und mobile Arbeitsmaschine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008109963A1 (fr) * 2007-03-15 2008-09-18 Viewquest Pty Ltd Optimisations de dispositifs de verrouillage ou connexes à ces derniers
EP2327840A1 (fr) 2009-11-25 2011-06-01 Dean R. Weyer Ensemble d'outils inclinable pour une excavatrice

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008109963A1 (fr) * 2007-03-15 2008-09-18 Viewquest Pty Ltd Optimisations de dispositifs de verrouillage ou connexes à ces derniers
EP2327840A1 (fr) 2009-11-25 2011-06-01 Dean R. Weyer Ensemble d'outils inclinable pour une excavatrice

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021110943A1 (de) 2021-04-28 2022-11-03 Béla Cseri Besitzunternehmung GbR (vertretungsberechtigter Gesellschafter: Béla Cseri, 89129 Langenau) Baugruppe mit einem schwenkantrieb und einem schnellwechsler sowie arbeitsmaschine mit einer solchen baugruppe
WO2022228612A1 (fr) * 2021-04-28 2022-11-03 Béla Cseri Besitzunternehmung Gbr Ensemble comprenant un entraînement à pivot et une libération rapide, et engin de chantier équipé d'un tel ensemble
DE102022121104A1 (de) 2022-08-22 2024-02-22 emtec Engineering & Maschinentechnik GmbH Ankoppelvorrichtung und mobile Arbeitsmaschine
EP4328387A1 (fr) * 2022-08-22 2024-02-28 Emtec Engineering & Maschinentechnik GmbH Dispositif d'accouplement et machine de travail mobile

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