EP1466092B1 - Radialkolbenhydraulikmotor - Google Patents

Radialkolbenhydraulikmotor Download PDF

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Publication number
EP1466092B1
EP1466092B1 EP02799840A EP02799840A EP1466092B1 EP 1466092 B1 EP1466092 B1 EP 1466092B1 EP 02799840 A EP02799840 A EP 02799840A EP 02799840 A EP02799840 A EP 02799840A EP 1466092 B1 EP1466092 B1 EP 1466092B1
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EP
European Patent Office
Prior art keywords
orifice
orifices
distribution
communication
notch
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EP02799840A
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English (en)
French (fr)
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EP1466092A1 (de
Inventor
Bernard Allart
Louis Bigo
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Poclain Hydraulics Industrie
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Poclain Hydraulics Industrie
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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
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel
    • 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
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0444—Particularities relating to the distribution members to plate-like distribution members

Definitions

  • the present invention relates to a radial piston hydraulic motor as defined in the preamble of claim 1.
  • a radial piston hydraulic motor as defined in the preamble of claim 1.
  • Such an engine is known from each of US-A-4522110 or DE-C-829553 or DE-A-2634065 or FR-A -2587761.
  • each communication orifice is successively opposite a dispensing orifice connected to the fluid supply and facing a dispensing orifice connected to the fluid outlet.
  • the connection to the dispensing orifice which is connected to the supply has the effect of pushing radially outwardly the piston contained in the cylinder connected to the communication port in question, while the connection of the same communication port to a dispensing orifice connected to the fluid outlet makes it possible to retract this piston in its cylinder, towards the axis of the engine.
  • each piston cooperates successively with the different parts of the lobes of the cam to allow the relative rotation of the cylinder block and the cam.
  • the spacings between the dispensing orifices and the spacings between the communication orifices are such that a communication orifice is not simultaneously connected to two dispensing orifices respectively connected to the fluid supply and to the fluid outlet.
  • the engine components in particular the crankcase, are subjected to load variation which causes noise-generating vibrations, the intensity of the noise produced being mainly dependent on the speed of the increase and the pressure drops in the crankcase. working rooms.
  • the pressure difference between the fluid supply and the fluid outlet is important.
  • a piston contributing to the engine torque reaches the end of its stroke, towards its position farthest from the axis of the engine (top dead center), because of the connection of the port of communication of its cylinder to an orifice
  • the same communication port is isolated from the dispensing port connected to the fluid supply, and is then connected to another dispensing orifice which, this time, is itself connected to the fluid outlet.
  • the detents that occur are generating shock or shock sensations, and noises such as clicks.
  • the present invention aims to limit the relaxation phenomena and the impact effects that result, tending to allow operation of the engine substantially smoothly.
  • edge arrangements of a dispensing orifice are different, the edge arrangement of a dispensing orifice which is arranged in angular correspondence with the convex region of the ramp of the cam corresponding to the dispensing orifice considered being able to allow the passage of a volume of pressure compensation fluid between a communication orifice and the dispensing orifice smaller than the volume of pressure compensation fluid whose edge arrangement the same dispensing orifice which is arranged in angular correspondence with the concave region of said ramp is adapted to allow passage.
  • These volumes of compensation fluid are the volumes of fluid capable of passing through the notches of these edge arrangements as long as the communication between the dispensing orifice and a communication orifice is made only by the cut or notches of the arrangement. considered.
  • the invention proposes to equip the leading portion and the separation portion of the edge of at least some dispensing orifices each of an edge arrangement having at least one notch.
  • the communication port of the cylinder of this piston leaves the separation portion of a dispensing orifice or approaches the attack portion of the next dispensing orifice by an edge arrangement having at least one notch adapted to pass a small volume of pressure compensation fluid between the orifices.
  • the communication port of the cylinder of this piston leaves the separation portion of a dispensing orifice or approaches the leading portion of the neighboring dispensing orifice by an edge arrangement having at least one notch capable of passing a greater volume of pressure compensation fluid between the orifices.
  • the invention allows the connection between each communication orifice and each dispensing orifice to be progressive, or by means of the cut or notches of the edge arrangement allowing the passage of a small volume arranged on one of the edges of the dispensing orifice, said arrangement "small section notched” or by means of the notch or notches of the edge arrangement allowing the passage of a large volume disposed on the other edge, arrangement said "large section notched". This limits the relaxation phenomena mentioned above.
  • connection between a communication orifice and the small section edge arrangement notched with a dispensing orifice is made when the volume of the working chamber of the cylinder connected to the communication orifice in question is minimal, while that the connection between the same communication port and the large-section edge arrangement notched with a dispensing orifice takes place when the volume of the working chamber of the cylinder associated with the same communication port is at a maximum.
  • the edge arrangement of the leading portion of at least one dispensing orifice comprises at least one notch which, with respect to a notch of the edge arrangement of the separation portion of said dispensing orifice. , is disposed at a radial distance different from the axis of rotation.
  • the period of time during which the notch furthest from the axis of rotation belonging to the notched-section edge arrangement communicates with a communication orifice is generally greater since, for a given relative angle of rotation between the cylinder block and the distributor, the distance to be traveled by a point distant from the axis of rotation is greater than that which is traversed by a point closer to this axis.
  • Another use of the length of the notch is, for a notch of great length, to limit the communication of this notch with a communication orifice, to a small part only of the length of the notch (ie ie on a small angular sector of relative rotation between the cylinder block and the distributor), before the clear communication with the edge of the dispensing orifice is established.
  • this long notch constitutes a restriction of great length which authorizes, on the small part considered, only the passage of a small volume of pressure compensation fluid. This long cut therefore corresponds to the small notched section defined previously.
  • the notch on the other edge of the dispensing orifice arranged at a smaller radial distance from the axis of rotation, has a shorter length but is used throughout its length on an angular sector substantially identical to that of the limited communication of the long notch with the communication port before the frank communication is established with the very edge of the dispensing orifice.
  • This short cut thus allows the passage of a greater volume of pressure compensation and corresponds to the large notched section defined above.
  • the distance of a notch of short length to the axis of rotation is less than the distance of a notch of great length to the rotation axis.
  • the edge arrangement which is arranged in angular correspondence with the concave region of the cam ramp corresponding to the dispensing orifice in question comprises at least one notch which extends over a sector angular, measured between two radii extending from the axis of rotation, which is larger than the angular sector, measured in the same manner, over which the notch extends, which is arranged in angular correspondence with the convex region of the ramp .
  • the edge arrangement which is arranged in angular correspondence with the concave region of the cam ramp corresponding to said orifice has a notched section larger than that of the edge arrangement which is arranged in angular correspondence with the convex region of the ramp.
  • the edge arrangements of at least one dispensing orifice each have the same number of notches (advantageously a single notch), the cut or notches of one of these arrangements being different (s) from the one (s) of the other edge arrangement.
  • the edge arrangements of at least one dispensing orifice each have similar notches, the number of notches of one of these edge arrangements being different from the number of notches of the other edge arrangement.
  • similar notches is meant notches having substantially the same section and can be made with the same tool.
  • two similar notches respectively present on the leading portion and on the separation portion of a dispensing orifice are such that the image of one of these notches obtained by symmetry with respect to a plane of symmetry the dispensing orifice has a conformation identical or almost identical to that of the other notch.
  • the same tool can thus be used to machine all the cuts and to choose the number of notches on each edge to allow the passage of the desired pressure compensation volume.
  • An advantageous variant is defined by the fact that two adjacent ramps of the cam are interconnected either by a cam crown zone extending between their respective convex regions, or by a cam bottom zone extending between their regions. respective cams, and said cam and cam bottom regions are substantially circular arcs centered on the axis of rotation, so that when the pistons cooperate with said zones, their radial strokes are substantially zero and by the fact that the dispensing orifices and the communication orifices have dimensions such that, during the relative rotation of the cylinder block and the distributor, each dispensing orifice remains momentarily isolated from any communication orifice.
  • cam plates These cam top areas and these cam bottom areas are referred to as "cam plates". It is advantageous to coincide the substantially zero stroke of a piston which cooperates with a cam plate with an insulation of the communication port of the cylinder of this piston, relative to any dispensing orifice. Any compression or significant decompression of fluid in the working chamber of the cylinder block whose piston is in contact with a cam crown zone or a cam bottom zone is then avoided.
  • FIG. 1 shows a hydraulic motor comprising a fixed casing in three parts, 2A, 2B and 2C, assembled by screws 3.
  • the invention is not limited to hydraulic motors with fixed housing, but it also applies to hydraulic motors with rotating housing which are well known to those skilled in the art.
  • Part 2C of the housing is closed axially by a 2D radial plate also fixed by screws.
  • a corrugated reaction cam 4 is formed on the part 2B of the housing.
  • the engine comprises a cylinder block 6 which is rotatably mounted around an axis of rotation 10 with respect to the cam 4 and which comprises a plurality of radial cylinders, which can be supplied with fluid under pressure and at the same time. inside which the radial pistons 14 are slidably mounted.
  • the cylinder block 6 rotates a shaft 5 which cooperates with it by splines 7.
  • This shaft carries an outlet flange 9.
  • the engine further comprises an internal fluid distributor 16 which is secured to the casing with respect to the rotation about the axis 10. Between the distributor 16 and the inner axial face of the portion 2C of the casing are formed distribution grooves, respectively a first groove 18, a second groove 19 and a third groove 20.
  • the dispenser distribution ducts 16 are distributed in a first group of conduits which, like the duct 21, are all connected to the groove 18, a second group of ducts (not shown) which are connected to the groove 19 and a third group of ducts which, like the duct 22, are connected to the throat 20.
  • the first groove 18 is connected to a first main duct 24 to which are thus connected all the dispensing orifices of the distribution ducts of the first group, such as the orifice 21A.
  • the third groove 20 is connected to a second main duct 26 to which are thus connected all the distribution orifices of the ducts of the third group, such as the orifice 22A of the duct 22.
  • the main ducts 24 and 26 are respectively an exhaust duct and a fluid supply duct, or the converse.
  • the distribution ducts open into a distribution face 28 of the distributor 16, which bears against a communication face 30 of the cylinder block.
  • Each cylinder 12 has a cylinder duct 32 which opens into this communication face so that, during the relative rotation of the cylinder block and the cam, the cylinder ducts are alternately in communication with the distribution ducts of the different groups.
  • the engine of FIG. 1 further comprises a device for selecting the displacement, which in this case comprises a bore 40 which extends axially in the part 2C of the casing and in which is disposed an axially movable selection slide 42 .
  • the bore 40 comprises three communication channels, respectively 44, 46 and 48, which are respectively connected to the grooves 18, 19 and 20, by connecting conduits, respectively 44 ', 46' and 48 '.
  • the drawer 42 is movable between two extreme positions inside the bore 40 in which it makes the channels 44 and 46 communicate or the channels 46 and 48 through its groove 43.
  • the distribution orifices successively considered in the direction of relative rotation between the cylinder block and the distributor, comprise a pair of orifices 21A, 23A, respectively connected to the grooves 18 and 19, and a pair of orifices 21A, 22A respectively connected to the grooves 18 and 20.
  • the grooves 19 and 20 communicate with each other. with the fluid supply.
  • a communication port 32A is successively set to high and low pressure by communicating with the orifices of the two aforementioned pairs.
  • the selector 42 When, on the other hand, the selector 42 is moved in the direction of the arrow F so as to make the grooves 18 and 19 communicate with each other, then the two distribution orifices 21A, 23A of the first pair mentioned above are both set the same pressure. This pair is therefore inactivated since, when a communication port passes from one to the other of the two distribution orifices of this pair, the pressure in the cylinder duct connected to said communication port does not change. On the other hand, the next pair is active, since a communication orifice communicating respectively with the two orifices 21A, 22A of this pair is successively placed at high and at low pressure.
  • the situation shown in Figure 1 is a situation of large displacement, while that in which the selector 42 is moved in the direction of the arrow F to communicate the grooves 18 and 19 is a small displacement situation.
  • the pairs of orifices 21A and 23A are inactive, while the pairs of orifices 21A and 22A are active.
  • the portions B1 of the edges of the dispensing orifices constitute driving portions, through which the opening of an orifice communicating with a dispensing orifice, while the portions B2 of the edges of the dispensing orifices are separating portions, through which the placing in communication ceases.
  • the portions B2 which constitute the leading portions and the portions B1 which constitute the portions of separation are the portions B2 which constitute the leading portions and the portions B1 which constitute the portions of separation.
  • the leading portions B1 and the separating portions B2 of each distribution orifice each have an edge arrangement, comprising a notch. It can be seen that these cuts are of different sizes, the notches 54A of the edge arrangements 53A of the edges B1 of the distribution orifices 23A and 22A, as well as the notches 54A of the edge arrangements 53A of the edges B2 of the orifices 21A being small notches these edges thus having small notched sections, while the notches 54B of the edge arrangements 53B of the edges B2 of the distribution orifices 23A and 22A, as well as the notches 54B of the arrangements of FIG. edge 53B edges B1 orifices 21A being large notches, these edges thus having large notched sections.
  • Each lobe of the cam comprises two ramps, each having a convex region and a concave region.
  • FIG. 4 shows one of these ramps 50, whose convex region, closer to the axis of rotation 10, is designated by the reference 51, and whose concave region, less close to this axis, is designated by the reference 52.
  • a cam lobe is constituted by this ramp 50, and by another symmetrical ramp of the ramp 50 relative to the radius R passing through the axis of rotation of the motor.
  • the adjacent cam lobe has a ramp 50 ', symmetrical with the ramp 50 relative to the radius RS.
  • a dispensing orifice is associated with each ramp of the cam. There is therefore an angular correspondence between each dispensing orifice and a ramp of the cam. Although the dispensing orifices are not in the same radial plane as the cam, FIG. 4 shows the angular correspondence between a dispensing orifice 23A and the ramp 50 of the cam. Moreover, for the clarity of the drawing, the proportions were not respected, the communication and distribution orifices being represented closer to the cam than in reality.
  • the orifice 23A is arranged so that the inscribed circle passing through the end of the notches is substantially symmetrical with respect to a radius RC of the cam which intersects the latter substantially in a zone of inflection between its convex regions 51 and concave 52.
  • the notch 54A of the portion B1 of the edge of the orifice 23A is a small cut, while the notch 54B of the portion B2 of the edge of the orifice 23A is a large cut.
  • the small notch 54A is in angular correspondence with the convex portion 51 of the cam, i.e. a radius of the cam, extending radially from the axis of rotation of the motor and passing through the notch 54A cuts the ramp 50 in the convex region 51 thereof.
  • FIG. 4 also shows the different positions of a communication orifice with respect to the dispensing orifice 23A during the relative rotation of the cylinder block and the distributor.
  • the cylinder block rotates in the direction R2 with respect to the cam, in which direction the portions B2 and B1 of the edge of the orifice 23A respectively constitute the leading portion and the separating portion.
  • a position 32A1 of the communication port 32A in which this communication port is isolated from any dispensing orifice. It can be seen that, in this position, the orifice 32A is separated from the tip of the notch 54B of the orifice 23A by an angular distance ⁇ 1, for example of the order of 1 °, and that it is also isolated from the notch 54B of the previous dispensing orifice 21A.
  • the communication orifice gradually covers the notch 54B of the orifice 23A and, on an angular displacement ⁇ 2, for example of the order 2 °, it communicates with the dispensing orifice 23A only by this notch 54B, to occupy a position 32A2.
  • the communication orifice gradually covers the entire orifice 23A, and there is a position 32A3, in which the dispensing orifice 23A is completely covered by the communication port, the communication section between the dispensing orifice and the communication port then being maximum.
  • the communication section decreases and the communication orifice reaches a position 32A4 in which it communicates with the distribution orifice 23A only via the notch 54A of the edge of this orifice. He then has to go through an angular stroke ⁇ 3, for example of the order of 1 °, so that the communication with the dispensing orifice 23A ceases completely. It then remains to the communication port to go through an angular stroke ⁇ 4, for example of the order of 1 °, before it begins its communication with the dispensing orifice 21A which is located after the dispensing orifice 23A in the direction of rotation R2, by the notch 54A of this orifice 21A.
  • the total section of the communication passage between this orifice and the dispensing orifice 23A is greater than the section of the communication passage which is established, by the small notch 54A, between the same dispensing orifice and the communication orifice when it occupies its position 32A4.
  • the ratio between these passage sections is advantageously chosen as a function of the ratio between the volumes of the working chamber of the cylinder 12 fed by the communication port 32A considered when the communication orifice occupies respectively its positions 32A2 and 32A4.
  • the ratio between the communication sections authorized by the cuts 54B and 54A is proportional to the ratio between the volume that the working chamber of the cylinder fed by the orifice 32A when this orifice is in its position 32A2 and the volume of the the same working chamber when the orifice 32A is in its position 32A4.
  • the large cut 54B extends over an angular sector ⁇ 2, measured between two radii extending from the axis of the motor, which is greater than the angular sector ⁇ 3, also measured between two radii originating from the axis of the motor, on which extends the small cut 54A.
  • the ramp 50 of the cam is connected to the adjacent ramp 50 'by a cam-top zone 56, which extends between the convex region 51 of the ramp 50 and the convex region of the ramp 50', and is connected to at the other ramp adjacent thereto, namely the ramp 50 ", a cam bottom area 58 which extends between the concave region 52 of the ramp 50 and the concave region of the ramp 50".
  • the cam vertex areas are those in which the radial distance from the cam to the axis of rotation is minimal, while the cam bottom areas are those in which the radial distance from the cam to the axis of rotation is Max.
  • the cam bottom area 58 When a piston cooperates with the cam bottom area 58, its radial stroke is zero or substantially zero. For example, it is at most substantially equal to 0.5% of the amplitude of the piston stroke between its top and bottom dead spots.
  • the cam bottom area 58 is substantially an arc of a circle centered on the axis of rotation. This means that this cam bottom area is either an arc centered on the axis of rotation, or a region which, over the entire angular distance 2 ⁇ '1 that it covers, has a radial distance to the axis of rotation. rotation of the motor which is substantially equal to the maximum radial distance from the cam to the axis of rotation 10.
  • the angle ⁇ '2 on which the portion of the cam-top region 56 situated on one side of the radius of symmetry RS extends corresponds to the path described by the communication orifice 32A between its position 32A4 and its position. 32A5, in which it is ready to approach the dispensing orifice 21A which follows the orifice 23A in the direction R2, by the small notch 54A of this dispensing orifice 21A.
  • the communication orifice moves between its positions 32A4 and 32A5 while the piston of the cylinder fed by this orifice cooperates with the cam crown zone 56.
  • the cam crown region 56 substantially describes an arc of a circle centered on the axis of rotation. It can either actually form such an arc, or present, over the entire angular distance 2 ⁇ '2 that it covers, a radial distance from the axis of rotation of the motor which is substantially equal to the minimum radial distance from the cam to the axis of rotation 10, for example by deviating of this radial distance at most of about 0.5%.
  • Figure 5 shows a communication port 32A which is circular, disposed between two dispensing orifices, respectively 123A and 121A, which are non-circular.
  • the leading portion (B2, if the cylinder block rotates in the direction R2 relative to the distributor and B1, if the direction of this relative rotation is R1), as well as the portion separation (B1 if the relative direction of rotation is R2 and B2 if the relative direction of rotation is R1) are both generally convex, seen from inside the orifice.
  • the leading portions and the separation portions form arcs of circles which, during the relative movement of the distributor and the cylinder block, cover the edge of a communication port, when the latter occupies a position corresponding to the position 32A2 or position 32A4 shown in Figure 4.
  • dispensing orifices generally have the forms described in patent application FR-A-2 587 761.
  • the communication orifice 32A has a substantially circular section, and the aforementioned convex shape of the edges of the orifices of the distributions 121A and 123A is the one that makes it possible to increase the communication between the communication orifice and the the dispensing orifices, after a first communication via the notches 54A and 54B.
  • leading portion and the separation portion of the dispensing orifices are formed that are substantially complementary to the shapes that form the edges of the communication orifices through which the communication between the orifices opens or closes. distribution and communication ports.
  • FIG. 6 shows a dispensing orifice 221A disposed, during the relative rotation of the cylinder block and the distributor, between two communication orifices 32A and 32'A respectively, while being simultaneously isolated from these two orifices.
  • the arcs C1 and C2 between which the communication and distribution orifices are delimited are indicated. If the relative direction of rotation of the cylinder block and the distributor is such that the cylinder block rotates in the direction R1 relative to the distributor, then the notch 254A is disposed on the leading portion B1 of the edge of the orifice 221A distribution, while the notch 254B is disposed on the separation portion B2 of the edge of this orifice. It can be seen that the notches 254A and 254B of the edge arrangements 253A and 253B are disposed at different radial distances from the axis of rotation.
  • the distance from the small notch 254A to the axis of rotation of the motor is less than the distance of the large notch 254B to this axis and the angular sector on which the large notch limits the communication between the orifices is larger than the angular sector of the small cut.
  • This allows, during the relative rotation between the distributor cylinder block, to ensure that the time period during which the dispensing orifice 221A communicates with the communication port 32A only by the notch 254B is larger. than that during which the dispensing orifice communicates with the communication port 32'A only by the notch 254A.
  • the length of the notch 254B measured tangentially relative to the axis of rotation of the motor, is greater than that of the notch 254A.
  • the notches 254A and 254B both have substantially the same thickness e, measured along a radius passing through the axis of rotation of the motor.
  • Figure 7 differs from Figure 6 only in that the notch 254'B of the separation portion B2 of the dispensing orifice 221A is slightly different from the notch 254B.
  • the notch 254'B of the edge arrangement 253'B has a maximum thickness e1, measured along a radius passing through the axis of rotation, which is greater than the thickness e, also measured along a radius passing through the axis of rotation, of the notch 254A of the edge arrangement 253A.
  • the thickness e1 is substantially equal to twice the thickness e.
  • the large cut 254'B forms an opening larger than the small cut 254A.
  • the dispensing orifice 221A is oblong, its largest dimension being measured along a radius passing through the axis of rotation.
  • the distribution orifice 321A has, considering that the cylinder block rotates in the direction R1 with respect to the cam, a separation portion B2 whose edge arrangement 353B comprises a notch 354B of upper section to that of the notch 354A of the edge arrangement 353A of the leading portion B1.
  • the partition portion B2 of the dispensing orifice has substantially the shape of an arc whose center is located inside this orifice.
  • the notch 354A is for example similar to the notch 254A of Figures 6 and 7.
  • This leading portion B1 has a shape substantially complementary to that of the edge C of the communication port 32'A by which the communication between the communication port and the dispensing orifice opens when the cylinder block rotates in the direction of rotation R1 relative to the distributor. It is also through this edge C that closes the communication between the dispensing orifice and the communication port 32'A when the cylinder block rotates relative to the distributor in the R2 direction opposite to the direction R1.
  • the leading portion B1 is convex, when considered from within the dispensing orifice 321A. It has substantially the shape of an arc capable of covering the arc formed by the portion C1 of the communication port 32'A.
  • the communication between the distribution orifice 321A and the communication port 32'A is first of all a very small section, due to the notch 354A, then it increases very rapidly because of the shape of the attacking portion B1.
  • dispensing orifices having generally the same shape as the opening 321A similar notches to any of the notches 54A, 54B, or 254A, 254B previously mentioned.
  • the dispensing orifice 421A is generally in the form of a circle except for its notches. It can be seen that the notches 454A of the edge arrangement 453A of its leading portion B1 and 454B of the edge arrangement 453B of its separating portion B2 (in the direction of rotation R1) are located at different radial distances. the axis of rotation of the motor.
  • the small notch 254A or 354A is substantially located on an arc of a circle, centered on the axis of rotation of the motor and passing through the geometric centers of the communication orifices 32A and 32'A, while the large notch 2548, 254'B or 354B is located beyond this arc, away from the axis of rotation.
  • the "small" notch 454A is the cut of greater length and is located beyond an arc A, passing through the geometric centers of the communication orifices 32A and 32'A and centered on the axis of rotation, while the "large” 454B notch is the shortest notch and is located below this arc.
  • Notches 454A and 454B have identical sections.
  • This arrangement of the notch 454A of greater length makes it possible to limit the volume of fluid passing through the notch over the small part of its length in communication with the communication orifice, before the frank communication with the edge is established. even of the dispensing orifice.
  • This limitation of the volume is due to the loss of load generated by the great length of restriction that makes this notch.
  • the cut 454B of smaller length is used throughout its length on the same angular sector centered on the axis of rotation as that of the limited communication of the long notch 454A with the communication port before the establishment of the open communication with the very edge of the dispensing orifice.
  • the notch 454B therefore allows the passage of a greater volume of pressure compensation.
  • the advantage of this arrangement is to keep the circular communication and distribution orifices of the standard dispensers (without cuts) and to achieve in addition the notches defined for each application as a function of the working pressures, the rotation speeds and the volumes of the valves. working rooms at the top and bottom dead spots.
  • edges of all the dispensing orifices have notches, respectively on their leading portions and on their separation portions.
  • the large notches 54B are all the same size, while the small cuts 54A are all the same size.
  • the motor shown comprises two active operating displacements, ie a large displacement in which each pair of consecutive distribution orifices (21A, 23A, 21A, 22A) comprises an orifice (22A or 23A) connected to the fluid supply and an orifice (21A) connected to the fluid outlet.
  • this large displacement is obtained when the selector 42 is in the position shown.
  • the engine also includes a small active operating displacement in which certain pairs of consecutive dispensing ports (21A, 22A) are active and include an orifice (22A) connected to the fluid supply and an orifice (21A) connected to the fluid exhaust, while other pairs of distribution ports (21A, 23A) are inactive and include two orifices at the same pressure.
  • the edges of the distribution orifices of the active pairs in small displacement have edge arrangements having notched sections larger than those of the edge arrangements of the inactive pairs of distribution ports in small displacement.
  • the edge arrangements of the distribution orifices of the active pairs in small displacement comprise a small notch and a large notch respectively arranged in angular correspondence with a convex zone and with a concave zone of the cam
  • the edge arrangements of the orifices inactive pairs in small displacement also comprise a small notch and a large notch respectively located opposite a convex zone and a concave zone of the cam, but these notches of inactive orifices in small displacement are smaller than those of the orifices active in small displacement.
  • each edge arrangement of a dispensing orifice has a single notch and the small or large notched sections are obtained by the choice of a small or large notch.
  • the edge arrangements 553A and 553B of the dispensing orifice 521A comprise similar but different numbers of notches.
  • the edge arrangement 553A thus includes a notch 554A, while the edge arrangement 553B includes two notches 554B and 554'B.
  • the single notch 554A therefore defines, for the arrangement 553A, a smaller notched section than that defined for the arrangement 553B, the two notches 554B and 554'B.

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

Claims (13)

  1. Hydraulischer Radialkolbenmotor mit einer Nockenscheibe (4) und einem Zylinderblock (6), die sich bezüglich einander um eine Drehachse (10) zu drehen vermögen, wobei der Zylinderblock Radialzylinder (12) umfasst, die durch Zylinderleitungen (32) mit Verbindungsöffnungen (32A) verbunden sind, welche in einer Verbindungsseite (30) des Zylinderblocks angeordnet sind, die senkrecht zur Drehachse ist, wobei die in den Zylindern gleitend montierten Kolben (14) mit der Nockenscheibe (4) zusammenzuwirken vermögen, wobei Letztere mehrere Bögen mit jeweils zwei Rampen (50) aufweist, die jeweils einen konvexen (51) und einen konkaven (52) Bereich umfassen, wobei der Motor ferner einen Fluidverteiler (16) umfasst, der eine Verteilerseite (28) aufweist, die senkrecht zur Drehachse verläuft und an der Verbindungsseite (30) des Zylinderblocks anzuliegen vermag, wobei diese Verteilerseite Verteileröffnungen (21A, 22A, 23A) mit an einen Fluidzulauf (24) anschließbaren Öffnungen und mit an einen Fluidauslass (26) anschließbaren Öffnungen aufweist, wobei der Fluidverteiler mit der Nockenscheibe solchermaßen drehfest verbunden ist, dass jeder Verteileröffnung eine Rampe der Nockenscheibe entspricht, wobei die Verteileröffnungen während der relativen Drehung des Zylinderblocks (6) und des Verteilers (16) nacheinander mit den Verbindungsöffnungen verbunden zu werden vermögen, wobei der Rand jeder Verteileröffnung ein Eingriffsstück (B1) hat, durch das sich die Verbindung zwischen der Verteileröffnung und den Verbindungsöffnungen während der relativen Drehung zwischen dem Zylinderblock und dem Verteiler in einer gegebenen relativen Drehrichtung (R1) öffnet, sowie ein Trennstück (B2), durch das sich die Verbindung zwischen der Verteileröffnung und den Verbindungsöffnungen während der relativen Drehung zwischen dem Zylinderblock und dem Verteiler in derselben relativen Drehrichtung (R1) schließt, wobei das Eingriffsstück und das Trennstück (B1, B2) des Rands wenigstens einiger Verteileröffnungen (21A, 22A, 23A) jeweils eine Randanordnung (53A, 53B; 53'A, 53'B; 253A, 253B; 253'A, 253'B; 353A, 353B; 453A, 453B; 553A, 553B) mit wenigstens einem Einschnitt aufweisen,
    dadurch gekennzeichnet, dass die Randanordnungen einer Verteileröffnung unterschiedlich sind, wobei die Randanordnung einer Verteileröffnung, die in Winkelübereinstimmung mit dem der betreffenden Verteileröffnung (21A) entsprechenden konvexen Bereich (51) der Rampe (50) der Nockenscheibe (4) angeordnet ist, den Durchlass eines Fluidvolumens zum Druckausgleich zwischen einer Verbindungsöffnung und der Verteileröffnung zu gestatten vermag, das geringer ist als das Druckausgleichsfluidvolumen, dessen Durchlass die Randanordnung derselben Verteileröffnung, die in Winkelübereinstimmung mit dem konkaven Bereich (52) der Rampe (50) angeordnet ist, zu gestatten vermag.
  2. Motor nach Anspruch 1,
    dadurch gekennzeichnet, dass das Eingriffsstück und das Trennstück bei wenigstens einigen Verteileröffnungen (121A, 123A) Formen aufweisen, die zu den Formen, welche die Ränder der Verbindungsöffnungen (32A) haben, durch die sich die Verbindung zwischen den Verteileröffnungen und den Verbindungsöffnungen öffnet oder schließt, im Wesentlichen komplementär sind.
  3. Motor nach Anspruch 2,
    dadurch gekennzeichnet, dass das Eingriffsstück und das Trennstück (B1, B2) bei jeder Verteileröffnung (121A, 123A) vom Inneren der Öffnung aus betrachtet allgemein konvex sind.
  4. Hydraulikmotor nach einem der Ansprüche 1 bis 3,
    dadurch gekennzeichnet, dass die Randanordnung (253A; 353A; 453A; 553A) des Eingriffsstücks (B1) wenigstens einer Verteileröffnung (221A; 321A; 421A; 521A) wenigstens einen Einschnitt (254A; 354A, 454A; 554A) aufweist, der bezogen auf einen Einschnitt (254B; 254'B; 354B; 454B; 554B) der Randanordnung (253B; 353B; 453B; 553B) des Trennstücks (B2) des Verteileröffnungsrands mit einem anderen radialen Abstand zur Drehachse angeordnet ist.
  5. Motor nach Anspruch 4,
    dadurch gekennzeichnet, dass bei den Randanordnungen wenigstens einer Verteileröffnung (221A; 321A; 421A) der Abstand eines kurzen Einschnitts (254A; 354A; 454B) zur Drehachse kleiner ist als der Abstand eines langen Einschnitts (254B; 254'B; 354B; 454B) zur Drehachse.
  6. Motor nach einem der Ansprüche 1 bis 5,
    dadurch gekennzeichnet, dass bei wenigstens einer Verteileröffnung (21A; 123A; 221A; 321A) die Randanordnung (53B; 53'B; 253B; 253'B; 353B), die in Winkelübereinstimmung mit dem konkaven Bereich (52) der Rampe (50) angeordnet ist, wenigstens einen Einschnitt (54B; 254B; 254'B; 354B) aufweist, der sich in einem zwischen zwei von der Drehachse (10) ausgehenden Radien gemessenen Winkelsektor (α2) erstreckt, der größer ist als der in gleicher Weise gemessene Winkelsektor (α3), in dem der Einschnitt (54A; 254A; 354A) verläuft, der in Winkelübereinstimmung mit dem konvexen Bereich (51) der Rampe (50) angeordnet ist.
  7. Motor nach einem der Ansprüche 1 bis 6,
    dadurch gekennzeichnet, dass die Randanordnung (253'B; 353B; 553B), die in Winkelübereinstimmung mit dem konkaven Bereich (52) der Rampe (50) angeordnet ist, bei wenigstens einer Verteileröffnung einen eingeschnittenen Abschnitt hat, der größer ist als der der Randanordnung (253A; 353A; 553A), die in Winkelübereinstimmung mit dem konvexen Bereich (51) der Rampe (50) angeordnet ist.
  8. Motor nach einem der Ansprüche 1 bis 7,
    dadurch gekennzeichnet, dass die Randanordnungen (53A; 53B; 253A; 253B; 253'A; 253'B; 353A; 353B; 453A; 453B) wenigstens einer Verteileröffnung jeweils die gleiche Anzahl Einschnitte aufweisen, wobei sich der bzw. die Einschnitte einer dieser Randanordnungen von dem bzw. denen der anderen Randanordnung unterscheidet bzw. unterscheiden.
  9. Motor nach einem der Ansprüche 1 bis 7,
    dadurch gekennzeichnet, dass die Randanordnungen (553A; 553B) wenigstens einer Verteileröffnung (521A) jeweils ähnliche Einschnitte aufweisen, wobei sich die Anzahl der Einschnitte (554A) einer dieser Randanordnungen (553A) von der Anzahl der Einschnitte (554B; 554'B) der anderen Randanordnung (553B) unterscheidet.
  10. Motor nach einem der Ansprüche 1 bis 9,
    dadurch gekennzeichnet, dass zwei benachbarte Rampen (50, 50'; 50, 50") der Nockenscheibe entweder durch einen Nockenscheibenscheitelbereich (56), der zwischen ihren jeweiligen konvexen Bereichen (51) verläuft, oder durch einen Nockenscheibensohlenbereich (58), der zwischen ihren jeweiligen konkaven Bereichen (52) verläuft, miteinander verbunden sind, dass der Nockenscheibenscheitel- und der Nockenscheibensohlenbereich im Wesentlichen auf die Drehachse zentrierte Kreisbögen sind, so dass beim Zusammenwirken der Kolben mit diesen Bereichen deren radiale Hübe im Wesentlichen Null sind, und dass die Verteileröffnungen (21A, 22A, 23A) und die Verbindungsöffnungen (32A) solche Abmessungen aufweisen, dass jede Verteileröffnung während der relativen Drehung des Zylinderblocks (6) und des Verteilers (16) zeitweilig von jeder Verbindungsöffnung abgesperrt bleibt.
  11. Motor nach Anspruch 10,
    dadurch gekennzeichnet, dass die Nockenscheibenscheitelbereiche (56) in jeweils zwischen zwei von der Drehachse (10) ausgehenden Radien gemessenen Winkelsektoren (α'2 + α'2) verlaufen, die kleiner sind als die in gleicher Weise gemessenen Winkelsektoren (α'1 + α'1), in denen die Nockenscheibensohlenbereiche (58) verlaufen.
  12. Motor nach einem der Ansprüche 1 bis 11, mit zwei aktiven Arbeitshubräumen, das heißt einem großen Hubraum, in dem jedes Paar aufeinanderfolgender Verteileröffnungen (21A, 22A; 21A, 23A) eine mit dem Fluidzulauf (26) verbundene Öffnung (22A, 23A) und eine mit dem Fluidauslass (24) verbundene Öffnung (21A) aufweist, sowie einem kleinen Hubraum, in dem bestimmte Paare aufeinanderfolgender Verteileröffnungen (21A, 22A) aktiv sind und eine mit dem Fluidzulauf (26) verbundene Öffnung (22A) und eine mit dem Fluidauslass (24) verbundene Öffnung (21A) aufweisen, während andere Verteileröffnungspaare inaktiv sind und zwei unter demselben Druck stehende Öffnungen (21A, 23A) aufweisen,
    dadurch gekennzeichnet, dass nur die Ränder der Verteileröffnungen der im kleinen Hubraum aktiven Paare Einschnitte aufweisen.
  13. Motor nach einem der Ansprüche 1 bis 11, mit zwei aktiven Arbeitshubräumen, das heißt einem großen Hubraum, in dem jedes Paar aufeinanderfolgender Verteileröffnungen (21A, 22A; 21A, 23A) eine mit dem Fluidzulauf (26) verbundene Öffnung (22A, 23A) und eine mit dem Fluidauslass (24) verbundene Öffnung (21A) aufweist, sowie einem kleinen Hubraum, in dem bestimmte Paare aufeinanderfolgender Verteileröffnungen (21A, 22A) aktiv sind und eine mit dem Fluidzulauf (26) verbundene Öffnung (22A) und eine mit dem Fluidauslass (24) verbundene Öffnung (21A) aufweisen, während andere Verteileröffnungspaare inaktiv sind und zwei unter demselben Druck stehende Öffnungen (21A, 23A) aufweisen,
    dadurch gekennzeichnet, dass die Ränder der Verteileröffnungen der im kleinen Hubraum aktiven Paare Randanordnungen aufweisen, die eingeschnittene Abschnitte haben, die größer sind als die der Randanordnungen der Verteileröffnungen der im kleinen Hubraum inaktiven Paare.
EP02799840A 2001-12-24 2002-12-20 Radialkolbenhydraulikmotor Expired - Lifetime EP1466092B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0116815A FR2834011B1 (fr) 2001-12-24 2001-12-24 Moteur hydraulique a pistons radiaux
FR0116815 2001-12-24
PCT/FR2002/004494 WO2003056172A1 (fr) 2001-12-24 2002-12-20 Moteur hydraulique a pistons radiaux

Publications (2)

Publication Number Publication Date
EP1466092A1 EP1466092A1 (de) 2004-10-13
EP1466092B1 true EP1466092B1 (de) 2007-02-21

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EP02799840A Expired - Lifetime EP1466092B1 (de) 2001-12-24 2002-12-20 Radialkolbenhydraulikmotor

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US (1) US6978713B2 (de)
EP (1) EP1466092B1 (de)
JP (1) JP4133828B2 (de)
AU (1) AU2002364477A1 (de)
DE (1) DE60218351T2 (de)
FR (1) FR2834011B1 (de)
WO (1) WO2003056172A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2834012B1 (fr) * 2001-12-24 2004-03-19 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
DE102006058076A1 (de) * 2006-12-07 2008-06-19 Zf Friedrichshafen Ag Hydraulischer Radialkolbenmotor
FI122115B (fi) * 2007-01-26 2011-08-31 Sampo Hydraulics Oy Mäntähydraulimoottori
FI125367B (fi) * 2007-01-26 2015-09-15 Sampo Hydraulics Oy Ajovoimansiirron ohjausjärjestelmä
US9003954B2 (en) * 2010-02-23 2015-04-14 Artemis Intelligent Power Limited Variable displacement radial piston fluid working machine
EP2436918A1 (de) 2010-09-29 2012-04-04 Salzgitter Maschinenbau AG, Hydraulischer Radialkolbenmotor
FR3038348B1 (fr) * 2015-07-01 2019-08-23 Poclain Hydraulics Industrie Machine hydraulique a pistons radiaux a distribution en harmonique

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Publication number Priority date Publication date Assignee Title
GB604117A (en) * 1944-08-15 1948-06-29 Vickers Armstrongs Ltd Improvements in radial pumps or hydraulic motors
DE2634065A1 (de) * 1976-07-29 1978-02-02 Duesterloh Gmbh Reversierbare, hydrostatische radial- oder axialkolbenmaschine
SE456517B (sv) * 1982-09-08 1988-10-10 Hegglund & Soner Ab Hydraulisk radialkolvmotor
FR2587761B1 (fr) 1985-09-20 1988-01-15 Poclain Hydraulics Sa Mecanisme hydraulique comportant des glace et contre-glace de distribution du fluide
FR2679963B1 (fr) * 1991-08-01 1993-11-12 Poclain Hydraulics Mecanisme a fluide sous pression muni d'enceintes d'equilibrage particulieres.
DE19804374B4 (de) * 1998-02-04 2004-09-30 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit Mitteldrucköffnung

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DE60218351T2 (de) 2007-10-31
AU2002364477A1 (en) 2003-07-15
JP4133828B2 (ja) 2008-08-13
FR2834011A1 (fr) 2003-06-27
US20050126387A1 (en) 2005-06-16
WO2003056172A1 (fr) 2003-07-10
EP1466092A1 (de) 2004-10-13
JP2005513351A (ja) 2005-05-12
DE60218351D1 (de) 2007-04-05
US6978713B2 (en) 2005-12-27
FR2834011B1 (fr) 2004-03-19

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