EP0428574B1 - Moteur hydraulique a piston axial - Google Patents

Moteur hydraulique a piston axial Download PDF

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Publication number
EP0428574B1
EP0428574B1 EP89908962A EP89908962A EP0428574B1 EP 0428574 B1 EP0428574 B1 EP 0428574B1 EP 89908962 A EP89908962 A EP 89908962A EP 89908962 A EP89908962 A EP 89908962A EP 0428574 B1 EP0428574 B1 EP 0428574B1
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EP
European Patent Office
Prior art keywords
axial
control
rotor
housing
piston motor
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Expired - Lifetime
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EP89908962A
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German (de)
English (en)
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EP0428574A1 (fr
Inventor
Eckehart Schulze
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Individual
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Individual
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Priority to AT89908962T priority Critical patent/ATE81892T1/de
Publication of EP0428574A1 publication Critical patent/EP0428574A1/fr
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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
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0676—Arrangement for pressing the cylinder barrel against the valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0668—Swash or actuated plate
    • F03C1/0671—Swash or actuated plate bearing means or driven axis bearing means

Definitions

  • the invention relates to a hydraulic axial piston motor as a rotary drive motor for tools or positioning or feed drives on machine tools or processing machines, with a rotatably mounted in a housing with the drive shaft of the motor rotatably and displaceably connected, axially play-free, rotor, which is axially symmetrical Distribution around the axis of rotation has bores in which a piston can be displaced in a pressure-tight manner in the axial direction - parallel to the axis of rotation - which forms the axially movable boundary of a drive pressure space, through the controllable application of which to the outlet pressure of a pressure supply unit, the piston in system with a housing-fixed , With the axis of rotation concentric cam track can be urged, which, likewise in a group that is axially symmetrical with respect to the axis of rotation, but with less multiplicity than that of the bores of the motor, indicates projections un d has depressions arranged between them, which, with a smooth curvature
  • Such axial piston motors are known from FR-A 1 452 275.
  • the closure elements are the metal sealing connection of the drive pressure spaces of the individual linear cylinders of the rotor with the control channels of the control disk End elements achieved in the bores mentioned, so that they are not subject to any significant wear, however, in order to keep the end elements in sealing contact with the control disk, additional spring elements - corrugated ring springs - must be provided, which in turn are located in the internal grooves of the cylinder bores of the rotor support the more or less elastic washers axially.
  • a disadvantage is the not inconsiderable technical outlay which is associated with the insertion of internal grooves into the cylinder bores, the arrangement of internal support rings and the spring washers axially supported on these.
  • FR-A 1 452 275 also mentions the possibility of pressing the end elements against the control disk by means of elastic sealing rings clamped between the end faces of the same and the rotor of the axial piston motor, in which case, however, a centering effect cannot be achieved by the sealing rings and therefore the centering of the end elements must be achieved by a particularly precise adaptation of their shape to the bore cross-sections of the cylinder bores - exact, section-wise spherical shape of their outer lateral surfaces - which in turn is associated with considerable production expenditure and, since in this case the end elements in a sliding system with the Cylinder bore can come, can also be subject to wear.
  • the end elements Due to the design of the bores of the rotor as stepped bores, the end elements as stepped piston-shaped plugs and the arrangement of a prestressed elastic ring seal between an annular shoulder of the cylinder bores and the radial flange of the plugs, this seal also the cylinder jacket-shaped, smaller step of the plug, under tension , encloses, the seal conveys three essential functions, namely on the one hand the sealing of the respective drive pressure space against the housing space containing the rotor, and on the other hand the Pressing the respective closure element onto the control disk and thirdly centering the closure element with respect to the central bore axis, with the favorable consequence that, apart from the good planarity of their metallic sealing surfaces, the plugs otherwise do not require any particularly precise machining and can therefore be produced as simple turned parts which do not require a particularly precise adaptation to the bore diameter, so that relatively large gap widths between the flange-shaped steps of the stopper and these surrounding bore walls are possible, for which particularly favorable minimum values are indicated by the
  • the plugs end at a small distance e from the inner annular shoulder of the cylinder bores, which in any case prevents the plugs from striking the bore walls and minimizing wear.
  • claims 4 to 7 indicate advantageous designs of the sealing elements of the rotor, the control disk of the rotor and the housing parts of the axial piston motor according to the invention which delimit the control spaces, both from a functional point of view and also from the point of view of the inexpensive manufacturability.
  • claims 8 to 12 provide structurally simple measures for realizing a play-free and low-wear mounting of the motor shaft and the rotor of the axial piston motor according to the invention.
  • the - known per se - measure according to claim 13 provides the lubricant for the rotor bearing from the pressure medium supply circuit in a simple manner.
  • the features of claim 14 indicate - using the axial piston motor according to the invention - a hydraulic drive unit which is suitable for a large number of uses and is distinguished by a particularly space-saving overall structure.
  • a hydraulic axial piston motor according to the invention is shown in the context of a hydraulic drive unit, which in turn is generally designated by 11, which itself and as a control element for the latter is designated by 12 includes electrohydraulic overrun control valve that works with electrically controlled rotation angle or rotation frequency specification and mechanical rotation angle feedback.
  • a pulse-controlled stepper motor 13 is provided, the rotor of which - for the sake of simplicity - not shown - when driven with a sequence of electrical pulses per pulse, each rotation by a defined angle of z. B. experiences 4 °, wherein the stepper motor can be controlled in start-stop mode with a pulse train whose pulse train frequency can be up to 5 kHz.
  • the follow-up control valve 12 and the stepper motor 13 provided for its control can be assumed to be known in terms of structure and function and are therefore only to be explained below to the extent necessary for understanding the invention.
  • the axial piston motor 10, the follow-up control valve 12 and the stepper motor 13 are arranged along a common central longitudinal axis 14 of their respective housings, which also marks the axis of rotation of the shaft 16 of the axial piston motor 10 and the control shaft 17 of the stepper motor 13.
  • the rotor, designated overall by 18, of the axial piston motor 10 comprises a thick-walled, ring-cylindrical drive part 19 which is designed in the manner of the drum of a drum turret and is connected to the motor shaft 16 of the axial piston motor 10 in a rotationally fixed and non-displaceable manner. In principle, it could be made in one piece with the motor shaft 16, but for manufacturing reasons it is designed as a "separate" structural element of the rotor, which is connected in a manner not shown in detail to a control valve-side section 21 of the motor shaft, which is connected by a central one Bore 22 of the drive part 19 of the rotor 18 passes through and projects out of the central bore 22 on the valve side with a free end section 23 of its length.
  • these bores 24 pass into a bore step 28 of slightly larger diameter, which is only slightly extended in the axial direction and which are offset against the somewhat smaller bores 24 by a radial annular shoulder 29.
  • Step-shaped plugs 31 are inserted into the stepped through bores 24, 28, as can best be seen in the illustration in FIG. 1a), the details of which are also expressly referred to.
  • These plugs 31 have a cylinder-shaped step 32, the outer diameter of which is equal to or approximately the same as the diameter d 1 of the bore 24 of the drive part 19 and an outer diameter larger, annular flange-shaped piston step 33, the outer diameter of which is slightly smaller than the diameter d 2 of the larger bore step 28 of the Drive part 19.
  • the peripheral lateral surface 33 'of this ring flange 33 has a flat-convex curvature.
  • the plugs 31 are centered by rubber-elastic O-rings 34 and sealed against the drive part 19, these O-rings 34 being axially supported on the one hand on the ring shoulders 29, which separate the - spatially - further bore steps 28 against the bores 24 of the drive part 19, and, on the other hand, are supported by a thin washer 35 on the inside of the ring-flange-shaped step 33 of the plug 31, as a result of which they are held in the position shown, in which the inner end faces of the plug 31 are still at a small axial distance e from that of the bore steps 28 and 24 opposing annular shoulders 29 are arranged.
  • the sealing disk 35 provided as an additional sealing element consists of an elastomer, e.g. B.
  • a piston 36 is guided in a pressure-tight manner, which forms the axially movable limitation of one of the drive pressure spaces 37 - 37a to 37h - of the rotor 18, through the alternative pressurization thereof and relief the drive control of the hydraulic motor 10 takes place.
  • the pistons 36 are axially supported on a housing-fixed, coaxial with the central longitudinal axis 14 of the axial piston motor 10, with respect to this axially symmetrical cam 38, which in the particular embodiment shown, in which the rotor 18 is equipped with eight drive pistons 36 - 36a to 36h is in the form of a three-pronged "crown", the prongs 39 - 39a, 39b, 39c - are arranged pointing to the drive part 19 of the rotor 18.
  • the prongs 39 of the curved rib 38 which is circular at its base have the shape of flat, isosceles-obtuse-angled triangles, the limbs 41 - 41a, 41b and 41c - as well as 42 - 42a, 42b and 42c - include an obtuse angle ⁇ which in practice has a value between 120 ° and 150 °, in the preferred configuration of the axial piston motor 10 a value around 140 °, especially a value of 138 °.
  • These support balls 47 are freely rotatably mounted in concave bearing pans 48 of the pistons 36 and can therefore roll on the ramp-shaped running surfaces 41 and 42 of the curved rib 38, as a result of which friction losses are kept very low.
  • the curved rib 38 is made in one piece with a sleeve-shaped housing part 51 of the motor housing, within which the motor shaft 16 is mounted free of play by means of two angular ball bearings 52 and 53 braced axially against one another.
  • the bearing section 54 of the motor shaft 16, on which the inner rings 56 and 57 of the two angular contact ball bearings 52 and 53 are seated, is through a central section 58, the diameter of which is somewhat larger than that of the bearing section 54, against which the drive part 19 of the rotor is rotationally and displaceably fixed connected drive section 21 of the motor shaft 16, the diameter of which in turn is somewhat smaller than that of the central section and is the same as that of the bearing section 54 in the special embodiment shown.
  • the inner rings 56 and 57 of the two angular contact ball bearings 52 and 53 are held axially displaceably between the radial step 61 of the motor shaft 16, which sets off the central section 58 against the bearing section 54 of the motor shaft 16, and a snap ring 62 which is inserted into an outer groove 63 of the motor shaft 16 , wherein the inner bearing rings 56 and 57 of the two angular contact ball bearings 52 and 53 directly abut each other with their mutually facing annular end faces.
  • the outer bearing rings 64 and 66 of the angular contact ball bearings 52 and 53 are somewhat “narrower” in the axial direction than the inner bearing rings 56 and 57 in order to be able to brace them against one another, such that a gap 69 between the facing ring end faces 67 and 68, respectively with only a small axial gap width remains in the illustrated embodiment, which is sufficient to be able to brace the angular contact ball bearings against each other.
  • the outer ring 64 of the inner angular contact ball bearing 52 whose inner bearing ring 56 is supported or can be supported on the radial step 61 of the motor shaft 16, is axially supported on a radially outward-pointing support flange 71 of a slide bearing bush 72, in the central bore 73 of which the motor shaft 16 is also supported its central section 58 is additionally rotatably and slidably mounted.
  • This slide bearing bush 72 is supported with its radially outward-pointing support flange 72 axially on a radially inward-facing ring flange 74 of the housing part 51 provided for the mounting of the motor shaft 16, the curved rib on the inside of this ring flange 74 of the sleeve-shaped housing part 51 facing the drive part 19 38 is arranged.
  • the slide bearing bush 72 has a cylindrical jacket-shaped centering extension 76 which passes through the opening which is circular and coaxial with the central axis 14 and which is delimited by the radially inward-pointing flange 74 of the sleeve-shaped housing part 71.
  • the support flange 71 of the slide bearing bush 72 has a somewhat larger - axial - thickness in its radially outer region 77 than in its central region 78. This difference in thickness is dimensioned in the special embodiment shown so that the annular surface of the thicker, radially outer region 77 is on which the outer bearing ring 64 of the inner angular contact ball bearing 52 can be axially supported, runs in the plane in which the radial section 61 of the motor shaft 16 which separates the central section 58 from the bearing section 54 of the motor shaft 16 also lies, while the plane in which the bearing-side ring end face of the Central area 78 of the plain bearing bush 72 is located at a small axial distance from this "within" the area of the central portion 58 of the motor shaft 16.
  • axial bracing of the two angular contact ball bearings 52 and 53 against one another takes place by means of a clamping ring 79, which can only be axially supported on the outer, ring end face 81 of the outer bearing ring 66 of the outer angular contact ball bearing 53, as seen in the axial direction.
  • axial clamping screws 82 are provided in an axially symmetrical distribution about the central longitudinal axis 14 of the motor which are tightened using a torque wrench.
  • the circular central opening 83 of the clamping ring 79 is - by means of a sealing ring 84 firmly connected to the outer, adjoining the bearing section 54 of the motor shaft 16 - free end section 86 of the motor shaft 16 - slidingly - the output shaft with the - not specifically shown - rotating or possibly only pivotally driven part, z. B. a gear or an articulated arm is rotatably coupled.
  • the plugs 31, which each form an - essentially rotor-fixed - axial limitation of the drive pressure spaces 37 of the drive part 19 of the rotor 18 have, as can best be seen in FIG. 1 a), central through bores 87, via which the supply and discharge from pressure medium to or from the drive pressure chambers 37, through their appropriately controlled pressurization or relief, the axially movable boundaries of the drive pressure chambers 37 forming piston 36 experience axial displacements, which result from the fact that the pistons 36 via the support balls 47 on the cam rib 38 are supported axially, the support balls 47 being able to roll on the running surface 49 of the curved rib 38, are converted into rotational movements of the drive part 19 of the rotor 18 and with it the motor shaft 16.
  • a first control disk 88 executing the rotational movements of the rotor 18 and in this respect itself forming an element of the rotor 18 and a second control disk 89 are provided, which support the regulator-side support element of the whole with 91 designated motor housing or stator of the axial piston motor 10 forms.
  • the rotor-side, first control disk 88 is connected in a rotationally fixed manner to the rotor 18 by means of a driving pin 92 (FIG. 2b) which is fixedly connected to the drum-shaped drive part 19 of the rotor 18 and engages in a driving bore 93 of the first control disk 88.
  • the first control disk 88 has a centering hole 94, through which the controller-side, free end section 23 of the motor shaft 16 passes as a centering piece.
  • the clear diameter d z of the centering hole 94 of the control disk 88 is larger by a positive minimum tolerance of 0.02 mm than the diameter d of the controller-side section 21 or of the free end section 23 of the motor shaft 16.
  • the first control disk 88 is provided with axial control channels 96, the number and symmetry of the arrangement of which corresponds to that of the drive pressure chambers 37 and drive pistons 36 of the drive part 19 of the rotor 18.
  • control channels 96 have, on the consumer side, that is to say on the side of the control disk 88 facing the plug 31 of the drive part 19, orifices 97 which are arranged coaxially with the central axes 26 of the through bores 87 of the plugs 31 and have the same diameter as these through bores 87.
  • control channels 96 On the supply side, that is to say on the side facing the second control disk 89 fixed to the housing, the control channels 96 have orifices 98, the diameter of which is somewhat smaller than that of the orifices 97 on the consumer side and, in the special embodiment shown, the radial inside width w from in the view of FIG. 2a, the details of which are now also referred to, corresponds to kidney-shaped control grooves 99 of the housing-fixed, second control disk 89, which are arranged on the side facing the first control disk 88.
  • the control channels 96 of the first control disk 88 are realized by merging bore sections of different diameters, the central axes 101 of the bore sections 102, which have the smaller diameter, being arranged along a bore circle 103, the diameter of which is slightly larger than that of the bore circle 27 of which the central axes 26 of the larger diameter sections 106 of the Control channels 97 of the first control disk 88 are arranged, the diameter of the smaller bore sections 102 being matched to that of the larger bore sections 106 of the control channels 96 such that the bore sections 102 and 106 seen in the illustration in FIG. 2b, the same outer, through the circle 107 represented envelope, which is also the outer envelope of the kidney-shaped control grooves 99 of the control disk 89 fixed to the housing. Accordingly, the inner envelope, represented by the circle 108, of the smaller diameter bore sections 102 of the control channels 96 of the first control disk 88 also coincides with the inner envelope of the kidney-shaped control grooves 99 of the second control disk 89 fixed to the housing.
  • the consumer-side orifices 97 of the control channels 96 of the first control disk 88 lie within a flat end face 109 of a flat, first annular rib 111 of the first control disk 88, which runs at right angles to the central longitudinal axis 14 of the axial piston motor 10, as shown in FIGS. 1 and 1a).
  • the supply-side orifices 98 of the control channels 96 of the first control disk 88 also lie within an end face 112, parallel to the end face 109 of the first annular rib 111, of a second flat annular rib 113, pointing towards the second control disk 89, of the first control disk 88.
  • kidney-shaped control grooves 99 are within an annular shape End face 114 of a flat annular rib 116, pointing toward the first control disk 88, of the second control disk 89, which is fixed to the housing.
  • the outer diameters of the flat annular ribs 113 and 116 facing one another of the first control disk 88 and the second control disk 89 have the same value. The same applies, in the special exemplary embodiment shown, with regard to the inner diameter of these two ring ribs 113 and 116.
  • the stepped piston-shaped plugs 31, which form the one-sided - “rotor-fixed” - axial boundaries of the drive pressure chambers 37 of the rotor 18, are on their side facing the first control disk 88 with the central longitudinal axis 26 of their through bores 87 are provided with coaxial ring ribs 117, which have ring-shaped end end faces 118 which are parallel to the ring end face 109 of the first flat ring rib 111 of the first control disk 88 facing them and with which they, with a metallic seal on the annular end end face 109 first control disk 88 - are held in contact by the elastic prestressing of the rubber-elastic ring seals 34.
  • the first disk 88 - with the end face 112 of its second flat annular rib 113 is held in metallic sealing contact with the end face 114 of the annular rib 116 of the second control disk 89 fixed to the housing.
  • the clear diameters d 1 and d 2 of the bore stages 24 and 28 in which the cylinder-shaped piston stage 32 and the annular flange-shaped piston stage 33 are Plugs 31 are arranged, with positive tolerances of at least 0.02 mm, that is to say somewhat coarser in diameter than the above-mentioned steps 32 or 33 of the plugs 31, so that both these and the first control disk 88 have sufficient play "in order to be able to contact one another with their ring ribs 117 and 111 or 113 and 116, each with a metallic seal, the ring seals 34 acting as a buffer body, as it were, which" axial "manufacturing tolerances of the parts which lie tightly against one another - the first control disk 88 and the housing-fixed control disk 89 on the one hand and the plug 31 on the first S control disc 88 on the other hand - to
  • the first control disk 88 could be made in one piece with the plugs 31 delimiting the drive pressure chambers 37 of the drive part 19 of the motor 10, but this would be more complex in terms of production technology than the design of the first control disk 88 and the plugs 31 of the rotor 18 described using the special exemplary embodiment.
  • a possible leakage oil flow in this configuration of the control disk 88 and the plug 31, which flows into the rotor via the sealing joint 119, along which the plug 31 and the first control disk 88 bear against one another with the annular surfaces 118 and 109 of their annular ribs 117 and 111 18 surrounding leakage oil chamber 121 can pass, a sufficient elastic Preload the buffer body 34 provided, are easily kept so low that it does not interfere.
  • This leakage oil space is delimited in the radial direction by a tubular housing part 122 which extends between a radial ring flange 123 of the control disk 89 fixed to the housing and a radial ring flange 124 of the sleeve-shaped housing part 51 (FIG. 1) and is fixedly connected to the latter by means of housing fastening screws 126.
  • the tubular housing part 122 is sealed against these housing parts by means of an annular seal 127 and 128, respectively, which are attached in the outer grooves of the control disk 89 or the sleeve-shaped housing part 51, which are fixed to the housing.
  • control grooves 99 - 99a to 99f - which are arranged with the 6-digit, axially symmetrical grouping with respect to the central axis 14 of the axial piston motor 10, are arranged in the circumferential direction, with the grouping which can be seen best from FIG. 2a, to the details of which express reference is made , that is, seen in the azimuthal direction represented by the arrow 43 ⁇ of FIG. 2 a) or the arrow 43 of FIG.
  • the overrun control valve 12 passes into its functional position II, in which the B control connection 132 of the overrun control valve 12 via a flow-through flow path 139 with the high-pressure connection 133 and the A control connection 131 are connected via a flow-through flow path 141 to the return connection 134 of the follow-up control valve 12.
  • control grooves of the control disk 89 fixed to the housing in the development illustration of FIG. 3 are designated 99a, 99c and 99e via the flow path 137 of the run-on control valve 12 with its high-pressure connection 133 connected, while the control grooves designated 99b, 99d and 99f are connected via the flow flow path 138 of the overflow control valve 12 to the return connection 134 thereof.
  • K ⁇ P ⁇ F ⁇ tg ⁇ is given, with ⁇ being the "pitch angle" which the "rising” sections 41a, 41b and 41c of the curved rib 38 enclose with their base line 40, which, seen in the circumferential direction of the curved rib 38, the envelope of the "valleys” 46 forms, in which the sloping sections 42a, 42b and 42c and the rising sections 41a, 41b and 41c of the crown prongs 39a, 39b and 39c of the curved rib 38 adjoin each other with a smooth curvature. 3 in FIG.
  • pistons 36b, 36d, 36e and 36g are involved in the torque development until the next piston, in the selected explanatory example, the piston 36d in the Valley 46 between the rib sections 42a and 41b reaches its outer dead center, and, if this is the case, is shut off against the control groove 99c of the control disk 89 fixed to the housing, etc.
  • the radius of curvature with which rising sections 41 and falling sections 42 of the cam rib 38 connect to one another is somewhat larger than the radius of the piston support balls 47, which roll on the running surface of the cam rib 38 can, wherein the support balls 47 are slidably mounted in the bearing pans 48 of the pistons 36.
  • Continuous, axial piston bores 144 open into the bearing troughs 48 of the pistons 36, via which pressure medium is pressed into the bearing pans 48 for lubricating the support balls.
  • the overrun control valve 12 reaches its functional position II, with which the direction of rotation of the axial piston motor 10 is linked in the counterclockwise direction.
  • the control of the rotational speed of the axial piston motor 10 and thus also of its output takes place by regulating the swallowing volume Q e by means of the run-on control valve 12, which can be assumed to be known in terms of structure and function.
  • the overflow control valve 12 shown in FIG. B. in DE 37 29 564 A1 described in detail, to which extent reference is expressly made.
  • Such a follow-up control valve works with an electrically controlled setpoint specification of the angle of rotation ⁇ of the rotor 18 and mechanical feedback of this angle of rotation, the opening cross-section of each of the alternatives being proportional to and in the same direction as the follow-up error Direction of rotation - clockwise or counterclockwise - of the axial piston motor 10 used flow path 137 and 138 or 139 and 141 varies, that is coarsened with increasing tracking error and reduced with decreasing tracking error.
  • the overrun control valve 12 is designed as a 4/3-way slide valve, which assumes its basic position 0, in which the setpoint and actual values of the rotor angle of rotation are the same, in which the control connections 131 and 132 against the supply connections 133 and 134 of the follow-up control valve 12 are blocked.
  • the steady-state operation of the engine 10 - constant speed - corresponds to a passage state (I or II) of the follow-up control valve 12 which is linked to a defined flow resistance.
  • the central axis 14 simultaneously marks the axis of rotation of the output shaft 17 of the stepping motor 13 and the axial piston motor 10 as well as a (rotational angle) setpoint specification spindle 147 and an actual value feedback spindle 148.
  • the setpoint specification spindle 147 is designed as a hollow spindle with an internal thread, which is connected in a rotationally fixed manner to the output shaft 17 of the stepping motor 13, but is arranged so that it can be axially pushed back and forth.
  • the output shaft of the stepping motor 17 is provided with an external axial toothing with which an axial internal toothing of the spindle end meshes.
  • the feedback spindle 148 is non-rotatably and non-displaceably connected to the motor shaft 16 and has an external thread in meshing engagement with the internal thread of the setpoint input spindle 147.
  • the total of 149 slide valve of the follow-up control valve 12 comprises a total of four valve bodies 151 to 154, by moving them together in the direction of arrow 156, to the left according to FIG. 1, the follow-up control valve reaches its functional position I and by moving them together in the opposite direction, represented by the arrow 157, the overflow control valve 12 reaches its functional position 11, the flow cross sections of the flow paths 137 and 138 in both cases with increasing displacement from the blocking position of the overflow control valve 12 corresponding to the basic position 0 or 139 and 141 increase steadily, as already mentioned.
  • valve bodies 151 to 154 are clamped in pairs between stop rings 158 and 159, through which the setpoint specification spindle passes axially, with axial ball bearings 161 and 162, which each between one of the stop rings 158 and 159 and a radial end flange 163 and 164 respectively
  • Setpoint specification spindle 147 are arranged, allow relative rotational movements of the same with respect to stop rings 158 and 159, such that they execute - axial - displacement movements of setpoint specification spindle 147, but do not rotate, but are supported on valve bodies 151 to 154 in a rotationally fixed manner stay.
  • the follow-up control valve 12 which is explained in summary in terms of its basic structure, operates as follows in the context of the hydraulic drive unit 11:
  • stepper motor 13 with a z. B. a first output 166 of an electronic control unit 167 delivered sequence of control pulses clockwise, the setpoint input spindle 147 rotates, so this leads, because of the thread engagement between setpoint input spindle 147 and actual value feedback spindle 148, initially "Stops", for an axial displacement of the setpoint input spindle 147 and with this of the valve spool 149 in the direction of arrow 156 - to the left, that is to say into the functional position I of the follow-up control valve 12.
  • the resultant pressurization of the drive pressure spaces 37b, 37d and 37g and pressure relief of the drive pressure chambers 37c, 37f and 37h of the rotor 18 (FIG.
  • valve body 159 of the follow-up control valve 12 “remains” in a position that corresponds to a specific one, with the predetermined engine speed linked value of the effective swallowing volume of the axial piston motor 10 and thus also corresponds to a certain useful output of the same.
  • a level-controlled electric motor e.g. B. a DC motor can be used, especially when it is primarily important that the axial piston motor 10 with a certain minimum useful power - continuously - is driven and the "exact" number of revolutions of the rotor 18 is irrelevant.
  • an axial piston motor 10 falling within the scope of the invention also with a different number of drive pistons 36 and control grooves 99, e.g. B. seven pistons and six control grooves can be realized.

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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
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  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Abstract

Le rotor (18) d'un moteur hydraulique à piston axial (10) est relié de manière solidaire en rotation et en coulissement à l'arbre du moteur (16) et supporté dans le carter du moteur (91) sans jeu dans la direction axiale. Le chevauchement alterné des sections transversales de conduits de commande (96) avec les chambres de commande (99) pressurisées ou détendues du carter du moteur (91) provoque l'alternance entre mise sous pression et détente des chambres de pression d'entraînement (37) du rotor (18). Lesdites chambres de commande sont agencées sur un disque de commande (88), qui est relié de manière solidaire en rotation à la partie entraînement (19) du rotor (18) délimitant les chambres de pression d'entraînement (37), mais peut effectuer des mouvements de compensation de balancement ou de décalage axial par rapport à ladite partie. Le disque de commande (88) comporte une surface d'étanchéité métallique (118), dans laquelle sont situées les ouvertures (98) de ses conduits de commande (96) et par laquelle elle est en contact coulissant et étanche avec une surface d'étanchéité située du côté carter, dans laquelle sont situées les ouvertures (98) des chambres de commande (99). Ledit disque est poussé en contact avec la surface d'étanchéité (114) située du côté carter par des éléments d'étanchéité élastiques (34), qui assurent l'étanchéification des chambres de pression d'entraînement (37) par rapport à la chambre de carter qui contient le rotor (18); les éléments d'étanchéité (34) sont ainsi maintenus sous une forte prétension axiale.

Claims (14)

1. - Moteur hydraulique à pistons axiaux utilisé comme moteur d'entraînement rotatoire pour des outils ou comme système de positionnement ou d'avancement sur des machines-outils ou des machines d'usinage, comprenant un rotor monté de manière tournante et sans jeu axial dans un carter et couplé de manière rigide en rotation et en translation avec l'arbre primaire du moteur, qui comporte des alésages répartis de manière axisymétrique autour de l'axe de rotation, dans chacun desquels est guidé axialement - parallèlement à l'axe de rotation - un piston qui peut être déplacé de manière étanche à la pression et constitue la délimitation axialement mobile d'une chambre de compression d'entraînement dont l'alimentation contrôlable sous la pression de sortie d'un groupe d'alimentation en pression permet de pousser le piston contre un chemin incurvé solidaire du carter,concentrique par rapport à l'axe de rotation, qui présente, également avec un groupement axisymétrique par rapport à l'axe de rotation mais avec une multiplicité moins grande que celle des alésages du moteur, des saillies orientées vers ledit moteur et des dépressions disposées entre celles-ci lesquelles se raccordent entre elles avec une courbure lisse et forment une surface de roulement pour des billes d'appui montées aux extrémités libres des pistons de manière à pouvoir tourner librement, l'arrivée et l'évacuation de fluide sous pression vers les et hors des chambres de compression d'entraînement du rotor s'effectuant par l'intermédiaire de canaux pilotes disposés du côté rotor sur un plateau de distribution couplé de manière rigide en rotation avec le rotor, et de volumes de commande situés du côté carter et communiquant alternativement avec lesdits canaux pilotes, lesquels volumes de commande sont groupés dans une symétrie correspondant à la symétrie axiale du chemin incurvé, avec une répartition azimutale équidistante autour de l'axe central du moteur à pistons axiaux et, vu dans le sens de rotation, peuvent être raccordés alternativement à la sortie de la pression de service et au réservoir du groupe d'alimentation en pression, les canaux pilotes étant disposés sur un plateau de distribution qui, au moyen d'une surface d'étanchéité métallique à l'intérieur de laquelle se situent les orifices côté carter de ses canaux pilotes, est appliqué de manière coulissante et étanche contre une surface d'étanchéité côté carter à l'intérieur de laquelle se situent les orifices des volumes de commande côté carter, et qui, pour permettre, à l'intérieur d'une petite plage angulaire ou de déplacement axial, des mouvements de compensation en nutation et respectivement en déplacement axial par rapport au rotor, prend élastiquement appui sur le rotor par l'intermédiaire d'éléments de fermeture munis d'ouvertures de passage centrales lesquels sont insérés dans les alésages du rotor et maintenus axialement sur le rotor par l'intermédiaire d'éléments d'étanchéité élastiques sous précontrainte qui assurent l'étanchéité de ces alésages par rapport au volume du carter contenant le rotor et s'appliquent à leur tour avec une surface d'étanchéité de manière étanche contre le plateau de distribution, caractérisé en ce que les alésages (24, 28) dans lesquels les pistons (36) sont guidés de manière étanche et coulissante, sont conformés en alésages étagés dont les échelons (24, 28) sont séparés l'un de l'autre par un épaulement annulaire (29); que les éléments de fermeture (31) sont réalisés sous la forme de bouchons en forme de pistons différentiels insérés dans les alésages étagés (24, 28) et munis des ouvertures de passage centrales (87), avec un échelon (32) plus petit en forme de corps de cylindre et un échelon (33) en forme de bride d'un diamètre plus grand, l'échelon (33) en forme de bride étant placé dans la section d'alésage (28) plus grande dirigée vers le plateau de distribution (88) et présentant un diamètre qui est légèrement inférieur au diamètre d₂ de la section d'alésage (28) plus grande; et que les éléments d'étanchéité mis sous précontrainte élastique sont conformés en joints toriques (34) qui sont disposés entre l'échelon (33) en forme de bride des bouchons (31) et l'épaulement annulaire (29) séparant les sections d'alésage (28 et 24), et assurent le centrage des bouchons (31).
2. - Moteur à piston axial selon la revendication 1, caractérisé en ce que le diamètre d₂ des sections d'alésages (28) plus grandes est supérieur d'au moins 2/100 mm au diamètre de l'échelon en forme de bride annulaire (33) des bouchons (31), et que le diamètre extérieur de l'échelon cylindrique (32) des bouchons (31) est inférieur d'au moins 2/100 mm au diamètre d₁ de la section d'alésage (24) plus petite.
3. - Moteur à piston axial selon l'une des revendications 1 ou 2, caractérisé en ce que les surfaces frontales terminales intérieures des bouchons (31) se situent à une faible distance axiale (e) de l'épaulement annulaire (29) qui sépare les sections d'alésage (24 et 28).
4. - Moteur à piston axial selon la revendication 3, caractérisé en ce que les surfaces d'étanchéité (118) des bouchons (31) situées du côté plateau de distribution sont constituées par les surfaces frontales terminales de nervures annulaires (117) qui entourent les orifices côté plateau de distribution des ouvertures de passage (87) des bouchons (31).
5. - Moteur à piston axial selon la revendication 4, caractérisé en ce que la surface d'étanchéité à l'intérieur de laquelle se situent les orifices des canaux pilotes (96) du plateau de distribution (88) dirigés vers les bouchons (31) du rotor (18, 19), est constituée par la surface frontale terminale libre (109) d'une nervure annulaire plate (111) du plateau de distribution (88).
6. - Moteur à piston axial selon l'une des revendications précédentes, caractérisé en ce que la surface d'étanchéité (112) par laquelle le plateau de distribution (88) est appliqué de manière coulissante contre la surface d'étanchéité (114) solidaire du carter à l'intérieur de laquelle débouchent les sections transversales des volumes de commande (99) et/ou la surface d'étanchéité (114) solidaire du carter est constituée par la surface frontale terminale (112 et respectivement 114) de respectivement une nervures annulaire plate (113 et respectivement 116) du plateau de distribution (88) et respectivement de l'élément de carter (89) qui délimitent de manière solidaire du carter les volumes de commande (99).
7. - Moteur à piston axial selon l'une des revendications précédentes, caractérisé en ce que l'élément de carter (89) qui délimite de manière solidaire du carter les volumes de commande (99) est à son tour constitué par un élément de fermeture du carter du moteur (919) conformé en disque annulaire.
8. - Moteur à piston axial selon l'une des revendications précédentes, caractérisé en ce que deux roulements inclinés (52 et 53) bloqués axialement l'un contre l'autre sont prévus pour assurer le montage sans jeu du rotor (18) du moteur à piston axial (10).
9. - Moteur à piston axial selon la revendication 8, caractérisé en ce que la section de palier (54) de l'arbre (16) du moteur sur laquelle sont montés les roulements inclinés (52 et 53), est disposée entre la section terminale (86) de l'arbre (16) du moteur qui sort du carter (91) en tant qu'arbre mené, et la section d'entraînement (59) de l'arbre (16) du moteur qui porte l'élément d'entraînement (19) du rotor (18).
10. - Moteur à piston axial selon la revendication 9, caractérisé en ce que les roulements inclinés (52 et 53) sont logés dans un élément de carter (51) en forme de douille qui présente, du côté dirigé vers l'élément d'entraînement (19) du rotor (18), une bride (74) dirigée radialement vers l'intérieur à partir de laquelle part une nervure curviligne (38) dont la face frontale dirigée vers l'élément d'entraînement (19) et axialement en saillie et en retrait, forme le chemin incurvé sur lequel les pistons (36) du rotor (18) peuvent s'appuyer dans le sens axial.
11. - Moteur à piston axial selon la revendication 10, caractérisé en ce que l'élément de carter (71) en forme de douille est muni d'une bride (74) dirigée radialement vers l'intérieur et entourant à distance radiale une section médiane (58) de l'arbre (16) du moteur, et que dans l'élément de carter (71) en forme de douille est inséré un coussinet lisse (72) dans lequel la section médiane (58) de l'arbre (16) est montée de manière coulissante.
12. - Moteur à piston axial selon la revendication 11, caractérisé en ce que la section médiane (58) de l'arbre (16) du moteur montée dans le coussinet lisse (72) est munie de gorges de lubrification (146) par lesquelles l'huile de fuite peut également passer du volume d'huile de fuite (121) contenant l'élément d'entraînement (19) du rotor (18) dans l'espace du carter contenant les roulements inclinés (52 et 53) pour assurer la lubrification.
13. - Moteur à piston axial selon l'une des revendications précédentes, caractérisé en ce que les billes d'appui (47) des pistons (36) du rotor (18, 19) pouvant rouler sur le chemin incurvé sont montées dans des coussinets (48) dans lesquels débouchent des ouvertures de passage des pistons (36) qui communiquent avec les chambres de compression d'entraînement (37).
14. - Unité d'entraînement hydraulique avec utilisation d'un moteur à piston axial selon l'une quelconque des revendications 1 à 13, comprenant une vanne-pilote asservie prévue pour la commande des mouvements du moteur à piston axial et fonctionnant avec prédétermination commandée électriquement de la valeur de consigne de l'angle de rotation et répétition mécanique de la valeur effective de l'angle, une broche déplaçable axialement et pouvant être entraînée par un moteur pilote étant prévu pour la prédétermination de la valeur de consigne et une broche répétitrice couplée de manière rigide en rotation et non déplaçable avec l'arbre du moteur assurant la répétition de la valeur effective, lesdites broches coopérant par l'intermédiaire d'un filetage intérieur et d'un filetage extérieur, caractérisée en ce que l'arbre mené (17) du moteur électrique (13) prévu pour la prédétermination de la valeur de consigne, la broche (147) pouvant être entraînée avec celui-ci, la broche répétitrice (148) et l'arbre (16) du moteur à piston axial (10) sont disposés coaxialement le long de l'axe longitudinal central (14) du moteur à piston axial (10).
EP89908962A 1988-08-12 1989-08-09 Moteur hydraulique a piston axial Expired - Lifetime EP0428574B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89908962T ATE81892T1 (de) 1988-08-12 1989-08-09 Hydraulischer axialkolbenmotor.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3827365A DE3827365A1 (de) 1988-08-12 1988-08-12 Hydraulischer axialkolbenmotor
DE3827365 1988-08-12

Publications (2)

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EP0428574A1 EP0428574A1 (fr) 1991-05-29
EP0428574B1 true EP0428574B1 (fr) 1992-10-28

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Family Applications (1)

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EP89908962A Expired - Lifetime EP0428574B1 (fr) 1988-08-12 1989-08-09 Moteur hydraulique a piston axial

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EP (1) EP0428574B1 (fr)
DE (2) DE3827365A1 (fr)
WO (1) WO1990001637A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4015101A1 (de) * 1990-05-11 1991-11-14 Eckehart Schulze Hydraulische antriebsvorrichtung
DE10355172B3 (de) * 2003-11-26 2005-06-02 MTS Gesellschaft für Maschinentechnik und Sonderbauten mbH Verdichtervorrichtung eines Baggers

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1006262B (de) * 1954-11-24 1957-04-11 Georg Wiggermann Einrichtung bei mehrzylindrigen OElpumpen mit umlaufendem Zylinderkoerper
US3228346A (en) * 1963-02-27 1966-01-11 Trw Inc Hydraulic apparatuses
US3277835A (en) * 1964-07-07 1966-10-11 Gunnar A Wahlmark Fluid device
FR1416863A (fr) * 1964-12-08 1965-11-05 Serck R & D Ltd Machine hydraulique
FR1452275A (fr) * 1965-08-04 1966-02-25 Soupape de commande à tiroir rotatif pour groupes hydrostatiques à pistons axiaux hydrauliques
FR2386699A1 (fr) * 1977-04-08 1978-11-03 Affouard Robert Perfectionnements aux moteurs hydrauliques a pistons axiaux
DE2857567C2 (de) * 1978-11-04 1984-02-23 Mannesmann Rexroth GmbH, 8770 Lohr Mehrhubiger hydraulischer Axialkolbenmotor
DE3729564A1 (de) * 1986-09-04 1988-04-07 Eckehart Schulze Hydraulisches nachlauf-regelventil

Also Published As

Publication number Publication date
WO1990001637A1 (fr) 1990-02-22
DE58902574D1 (de) 1992-12-03
EP0428574A1 (fr) 1991-05-29
DE3827365A1 (de) 1990-04-12

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