EP2647793A1 - Moteur hydraulique - Google Patents

Moteur hydraulique Download PDF

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Publication number
EP2647793A1
EP2647793A1 EP12006750.9A EP12006750A EP2647793A1 EP 2647793 A1 EP2647793 A1 EP 2647793A1 EP 12006750 A EP12006750 A EP 12006750A EP 2647793 A1 EP2647793 A1 EP 2647793A1
Authority
EP
European Patent Office
Prior art keywords
rotor
shaft
housing
fluid
rolling bearing
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
EP12006750.9A
Other languages
German (de)
English (en)
Other versions
EP2647793B1 (fr
Inventor
Alexandros Voulgaris
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.)
AVS Hydraulikmotorenbau GmbH
Original Assignee
AVS Hydraulikmotorenbau GmbH
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Publication date
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Publication of EP2647793A1 publication Critical patent/EP2647793A1/fr
Application granted granted Critical
Publication of EP2647793B1 publication Critical patent/EP2647793B1/fr
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Anticipated expiration legal-status Critical

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to a hydraulic motor according to the preamble of claim 1.
  • Hydraulic motors of this kind are from the DE 295 21 598 U1 known. They are for example for rotary actuators of. Excavator buckets or grabs from loading cranes successfully used, where they are characterized by noise immunity, robustness and long life.
  • the shaft is usually rotatably supported by means of rolling bearings in the form of two tapered roller bearings in the housing of the hydraulic motor.
  • the two bearings are, viewed in the axial direction, relatively far apart in the two end portions of the housing and arranged on opposite sides of the rotor set, which consists of the rotatably connected to the shaft rotor and the rotor ring surrounding the rotor.
  • the housing space in which the rolling bearings are arranged, is subject to substantially the same fluid pressure, which also prevails in the fluid working chambers between the rotor and the rotor ring.
  • the invention is based on the object, a hydraulic motor of the type mentioned above, which is both compact and subject to a lower load by pressure peaks and thus less wear.
  • the roller bearing space is sealed fluid-tight with respect to the rotor space.
  • connection pressures which may often be more than 300 bar, for example, in the case of dredgers
  • additional devices in particular by means of corresponding limiting valves, in order to protect the hydraulic motor.
  • hydraulic motors according to the prior art often can withstand only hydraulic pressures of 200 bar to 250 bar
  • the hydraulic motors according to the invention can be charged with significantly higher pressures. The manufacturers of excavators or grapples do not have to worry about overpressure protection in the hydraulic motor.
  • the substantially reduced pressure peaks make it possible to size the bearings smaller, whereby the size of the hydraulic motor can be reduced.
  • the hydraulic motor can thus be made very compact, especially at a lower height, which strongly meets the demands of the market.
  • a first, outer seal arrangement is provided between the side disk arranged between the rotor space and the rolling bearing space and the housing, and a second, inner seal arrangement for fluid sealing of the rotor space relative to the rolling bearing space is provided between this side disk and the shaft.
  • the rolling bearing space in which all rolling bearings of the rolling bearing arrangement are arranged, with which the shaft is rotatably mounted in the housing, between the rotor space and one end of the housing, which is adjacent to a flange or coupling portion of the shaft.
  • the two rolling bearings in particular the tapered roller bearings, exclusively on one side of the rotor space, near that end of the housing where the shaft exits the housing.
  • the rolling bearing assembly may consist of two tapered roller bearings, which are arranged close to each other so that their axial distance is only 0.1 to 2 times the length of the tapered rollers. This hydraulic motors can be designed in a very compact form.
  • the shaft has an end portion disposed within the housing, which is radially mounted in the housing by means of at least one sliding bearing.
  • the hydraulic motor comprises a housing 1, a shaft 2, which is rotatably supported by two tapered roller bearings 3, 4 in the housing 1, a shaft 2 surrounding the rotor 5, which is rotatably connected by means of a spline 6 with the shaft 2 and an external toothing 7 ( FIG.
  • the housing 1 is divided into two in the present embodiment and consists of an upper housing part 14 and a lower housing part 15.
  • the upper housing part 14 is lid-shaped or cap-shaped and fitted accurately on the hollow cylindrical lower housing part 15.
  • the two housing parts 14, 15 are fixedly connected to each other by means of screws 16 which extend in the vicinity of the outer periphery of the lower housing part 15 from below through corresponding axial through holes and are screwed into threaded holes 17 of the upper housing part 14.
  • screws 16 which extend in the vicinity of the outer periphery of the lower housing part 15 from below through corresponding axial through holes and are screwed into threaded holes 17 of the upper housing part 14.
  • Upper housing part 14 and lower housing part 15 together enclose a cavity, which is closed at the top by the upper housing part 14 and open at the bottom.
  • the shaft 2 is inserted from below and mounted by means of the tapered roller bearings 3, 4 so centrally within the housing 1, that axial and radial forces can be transmitted from the shaft 2 to the housing 1.
  • the lower part of the shaft 2 projects axially downward slightly over the housing part 15 and has in this axially projecting end region a flange section 18 which extends radially outwards beyond the outer circumference of the lower housing part 15.
  • a flange section 18 which extends radially outwards beyond the outer circumference of the lower housing part 15.
  • In the outer edge region of this flange portion 18 are regularly distributed over the circumference axial through holes 19th provided, can be passed through the screws, not shown, to tighten the device to be held, such as a bucket or grapple bucket at the bottom of the shaft 18.
  • One or more, provided in the flange 18 centering holes 20 are used for accurate fitting of the device to be fastened to the shaft 2.
  • At least one axial through hole 21 is provided in the flange portion 18, which is aligned in a certain rotational position of the shaft 2 with the through holes 22 and has such a diameter, so that the screws 16 can be passed including the screw head.
  • access to the screws 16 is provided from below, that the upper housing part 14 can be detached from the lower housing part 15 and screwed onto this without having to separate the shaft 2 from the lower housing part 15.
  • an outer Aufsetzring 23 is further provided, which is mounted from above on the radially projecting portion of the flange portion 18 and screwed thereto is. The screwing is done by means of screws 24, which are passed from below through the flange portion 18 and screwed into blind holes 25 of the Aufsetzrings 23.
  • the through holes through which the screws 24 are passed lie on the same bolt circle as the through holes 19, which serve to fasten the device.
  • axial through holes 26 are present in the Aufsetzring 23, which are aligned with the through holes 19 of the flange portion 18.
  • the Aufsetzring 23 is guided around the lower housing part 15 around and carries on its inner peripheral wall a sealing ring 27 which provides a seal against the outer peripheral wall of the lower housing part 15.
  • FIG. 1 It can also be seen that through the central portion of the shaft 2 fluid channels 28, 29 extending axially therethrough. Through these fluid channels 28, 29, hydraulic fluid, which is supplied via the upper housing part 14 in a manner not shown, are forwarded to the device attached to the hydraulic motor, such as excavator or grapple bucket to perform additional functions on the device, such as opening and Close the excavator or grapple blades to effect.
  • hydraulic motor such as excavator or grapple bucket
  • the rotation of the shaft 2 takes place by means of a rotor set which surrounds the rotor 5 and the rotor ring 8 in the vicinity of the upper end of the shaft 2.
  • This rotor set is preferably arranged within the cavity, which surrounds the upper housing part 14.
  • the rotor 5 is rotatably connected via the keyway 6, but axially slidably connected to the shaft 2. Instead of the keyway 6, another positive connection can be used. Furthermore, the rotor 5 is in the region of that end of the shaft 2, which has the smallest outer diameter. The upper end of the shaft 2 and the keyway 6 are designed such that the rotor 5 can be pushed from above onto the keyways of the shaft 2.
  • the outer teeth 7 of the rotor 5, as shown FIG. 2 Obvious, rounded teeth on.
  • the rotor ring 8 surrounds the rotor 5, wherein the internal toothing 9 of the rotor ring 8 cooperates with the external toothing 10 of the rotor 5 in a manner known per se.
  • the internal toothing 9 of the rotor ring 8 also has rounded teeth, wherein the number of teeth of the internal toothing 9 is larger by one than the number of teeth of the rotor 5.
  • working chambers 30 are formed, which in the circumferential direction by the contact surfaces or . - lines of the external toothing 7 and the internal toothing 9 are sealed.
  • hydraulic fluid is supplied and removed in a manner known per se, whereby a rotational movement of the rotor 5 is generated, while the rotor ring 8 performs a wobbling motion in the circumferential direction and in the radial direction.
  • the external toothing 10 of the rotor ring 8 also has rounded teeth whose number corresponds to the internal toothing 9. This external toothing 10 cooperates in a known manner with the circumferential internal toothing 11 of the upper housing part 14.
  • the supply and discharge of hydraulic fluid into and from the working chambers 30 takes place in a controlled manner via the first side window 12 and the second side window 13.
  • the side windows 12, 13 can therefore also be used as distributor plates be designated.
  • the two rotationally fixed side windows 12, 13 are, viewed axially, arranged on opposite sides of the rotor 5 and the rotor ring 8, formed annularly and abut against the corresponding end faces of the rotor 5 and the rotor ring 8.
  • the hydraulic fluid used to rotate the hydraulic motor as shown in FIGS. 1 and 3 can be seen, supplied via a radial fluid passage 31 in the upper housing part 14 provided in the outer peripheral wall of the first side window 12, circumferential annular channel 32. From this annular channel 32, a plurality of radially inwardly extending fluid channels 33 extend to a corresponding number of FluidzuWORKö réelleen 34, which open into that end face of the first side plate 12, which faces the rotor 5 and the rotor ring 8. If a working chamber 30 is located below such a fluid feed opening 34, hydraulic fluid can thus be introduced into the working chamber 30.
  • the first side window 12 has a plurality of continuous axial bores 63. These serve to allow leakage oil, which is located in the rotor chamber 46, to flow off faster, so that no undesirably high pressure forms in the rotor region.
  • the first side window 12 is inserted in an upper, inner stepped recess of the upper housing part 14.
  • the outer peripheral wall of the first side window 12 is fluid-tightly sealed from the adjacent peripheral wall of this step recess by means of two sealing rings 35, 36, which, in axial Direction, both sides of the annular channel 32 are located.
  • the second side window 13 is seated in a stepped recess of the lower housing part 15 and is supported axially downwards by a diameter step 42 of the lower housing part 15.
  • a radially outwardly projecting, circumferential radial projection 64 of the side plate 13 protrudes radially outward beyond the outer circumference of the rotor ring 8 and is located in a front side introduced into the lower housing part 15 recess.
  • the outer circumference of the side window 13 is thus larger than that of the rotor ring 8.
  • the second side window 13 by means of two sealing rings 43, 44, which are arranged in corresponding circumferential recesses in the outer peripheral wall of the second side window 13 on opposite sides of the annular channel 39, fluid-tight against the adjacent inner peripheral wall of the lower housing part 15 sealed. Another a fluid-tight seal between the second side plate 13 and the shaft 2 via a sealing ring 45 which is inserted into a corresponding stepped recess of the second side window 13.
  • sealing rings 43, 44, 45 thus takes place a fluid-tight seal between a rotor chamber 46, in the axial direction through the two side windows 12, 13, radially inwardly through the shaft 2 and radially outwardly through the housing 1, in particular the upper housing part 14, is limited, and adjacent to the second side window 13 cavity of the housing 1, in which the two tapered roller bearings 3, 4 are located and which is therefore hereinafter referred to as rolling bearing 47.
  • the outer ring of the tapered roller bearing 3 is fixed axially downwardly by a radially inwardly projecting diameter step 48 of the lower housing part 15.
  • the inner ring of the tapered roller bearing 3 is axially fixed by a threaded ring 49 which can be screwed on a threaded portion 50 of the shaft 2 from above until the threaded ring 49 abuts against a radially outwardly projecting diameter stage 51 of the shaft 2.
  • the outer ring of the second tapered roller bearing 4 is fixed axially upwards by a diameter step 52 of the upper housing part 15.
  • the inner ring of the tapered roller bearing 4 abuts against the upper end face of the flange portion 18 of the shaft 2 and is thereby fixed axially downwards.
  • the two tapered roller bearings 3, 4 are arranged close to each other on the same side of the rotor chamber 46 and the second side plate 13 between the housing 1 and shaft 2.
  • the mutual distance a of the two tapered roller bearings 3, 4 is about 0.5 times the length 1 of the tapered rollers.
  • this distance a may vary to a relatively large extent and in particular be 0.1 to 2 times the length 1 of the tapered rollers.
  • the tapered roller bearing 4 is arranged at the lower end or near the lower end of the lower housing part 15.
  • one or more radial bearings for example two slide bearings 53, can be provided in the upper end region of the shaft 2 , 54, between shaft 2 and housing 1, in particular in the upper housing part 14, are provided.
  • the sliding bearing 53 can be formed in that a stepped cylindrical section 62 projecting centrally downwards from the cover plate of the upper housing part 14 with a diameter step having an outer circumferential wall 55 fits snugly into a central axial bore 56 of the shaft 2.
  • the second sliding bearing 54 can be formed by a further, reduced diameter diameter step of the cylindrical portion 62 with an outer peripheral wall 57 fits accurately into a diameter-adapted axial bore 58 of the shaft 2.
  • the plain bearings 53, 54 thus represent pivot bearings, via which the shaft 2 is supported radially in its upper end region with respect to the housing 1.
  • slide bearings 53, 54 are only optional.
  • the shaft 2 is sealed in a fluid-tight manner with respect to the housing 1 by means of two sealing rings 59, 60.
  • the sealing ring 59 is arranged such that no fluid flow between the fluid channel 29 and the rotor chamber 46 can take place.
  • the sealing ring 60 is arranged such that no fluid flow between the fluid channel 28 and the fluid channel 29 or the rotor chamber 46 can take place.
  • the sealing rings 59, 60 also act as radial bearings, with which the upper end portion of the shaft 2 is supported radially relative to the housing 1, so that often additional radial bearings, for example in the form of the sliding bearings 53, 54 described above, can be dispensed with.
  • the tapered roller bearings 3, 4 are no longer automatically lubricated by the hydraulic fluid that passes from the rotor space into the rolling bearing space in hydraulic motors according to the prior art. Instead, the tapered roller bearings 3, 4 are self-lubricated in the hydraulic motor according to the invention by the rolling bearing chamber 47 is filled with grease. This can be done by means of a lubricant which is attached to the outside of the lower housing part 15. In order to prevent the lubricant from escaping downwards out of the roller bearing space 47, a sealing ring 61 is provided between the lower end wall of the lower housing part 15 and the adjacent end wall of the flange section 18 of the shaft 2 ( FIG. 1 ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
EP20120006750 2012-04-03 2012-09-27 Moteur hydraulique Active EP2647793B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201220003347 DE202012003347U1 (de) 2012-04-03 2012-04-03 Hydraulikmotor

Publications (2)

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EP2647793A1 true EP2647793A1 (fr) 2013-10-09
EP2647793B1 EP2647793B1 (fr) 2015-01-07

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ID=46511733

Family Applications (1)

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EP20120006750 Active EP2647793B1 (fr) 2012-04-03 2012-09-27 Moteur hydraulique

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EP (1) EP2647793B1 (fr)
DE (1) DE202012003347U1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3490383A (en) * 1969-01-29 1970-01-20 Koehring Co Hydraulic pump or motor
DE3346519A1 (de) * 1982-12-24 1984-07-05 Mannesmann Rexroth GmbH, 8770 Lohr Verdraenger-, insbesondere kreiskolbenmaschine
DE4202466A1 (de) * 1992-01-29 1993-08-05 Andres Voulgaris Hydraulischer motor
DE19536060A1 (de) * 1995-09-28 1997-04-03 Danfoss As Hydraulische Maschine
DE29521598U1 (de) 1995-07-31 1998-01-22 Voulgaris, Alexander, 83734 Hausham Hydraulische Maschine in Zahnring-Bauweise

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3490383A (en) * 1969-01-29 1970-01-20 Koehring Co Hydraulic pump or motor
DE3346519A1 (de) * 1982-12-24 1984-07-05 Mannesmann Rexroth GmbH, 8770 Lohr Verdraenger-, insbesondere kreiskolbenmaschine
DE4202466A1 (de) * 1992-01-29 1993-08-05 Andres Voulgaris Hydraulischer motor
DE29521598U1 (de) 1995-07-31 1998-01-22 Voulgaris, Alexander, 83734 Hausham Hydraulische Maschine in Zahnring-Bauweise
DE19536060A1 (de) * 1995-09-28 1997-04-03 Danfoss As Hydraulische Maschine

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Publication number Publication date
EP2647793B1 (fr) 2015-01-07
DE202012003347U1 (de) 2012-06-12

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