WO2016142037A1 - Disposition de paliers à balancier d'une machine à pistons axiaux - Google Patents

Disposition de paliers à balancier d'une machine à pistons axiaux Download PDF

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Publication number
WO2016142037A1
WO2016142037A1 PCT/EP2016/000333 EP2016000333W WO2016142037A1 WO 2016142037 A1 WO2016142037 A1 WO 2016142037A1 EP 2016000333 W EP2016000333 W EP 2016000333W WO 2016142037 A1 WO2016142037 A1 WO 2016142037A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
axial piston
piston machine
pivoting
pivoting cradle
Prior art date
Application number
PCT/EP2016/000333
Other languages
German (de)
English (en)
Inventor
Pascal Progin
Andreas Kurzen
Erwin Feusi
Original Assignee
Liebherr Machines Bulle Sa
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Liebherr Machines Bulle Sa filed Critical Liebherr Machines Bulle Sa
Priority to EP16706532.5A priority Critical patent/EP3265679B1/fr
Publication of WO2016142037A1 publication Critical patent/WO2016142037A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles

Definitions

  • the present invention relates to a pivotal support of an axial piston machine.
  • An axial piston machine is an energy converter which, in the axial piston pump design, can convert the mechanical power resulting from rotational speed and torque into hydraulic energy. Hydraulic energy is known to result from pressure and flow.
  • axial piston machine as axial piston motor
  • the operating principle of an axial piston pump is reversed so that correspondingly hydraulic power is converted into mechanical energy.
  • axial piston machines There are basically three different types of axial piston machines. Namely swashplate machines, oblique axis machines and swashplate machines.
  • the axis of rotation is surrounded by revolver-like cylinders arranged. This means, the cylinders are arranged substantially parallel to the axis of rotation of an axial piston machine and rotate during operation of the axial piston machine about the longitudinal axis of the axis of rotation around.
  • the cylinder liners which together with the respective cylinder pistons represent important elements of the cylinders, are not displaced along their own axis of symmetry during operation of the axial piston engine, ie they are stationary with respect to the axis of rotation of the axial piston engine.
  • the respective cylinder pistons are forced to move in the direction of the longitudinal axis of the rotation axis apart from the possible case of an idling operation of the axial piston machine. This is done by the various cylinder pistons are fixedly connected to the projecting out of the cylinder sleeve end with a pivot axis to the axis of rotation, so that when tilting the plate with respect to the axis of rotation a cylinder, the cylinder liner is indeed fixed to the axis of rotation, at a Drehachsenumwebung a complete stroke.
  • the pivotable plate which is connected to the projecting from the respective cylinder liners ends of the cylinder piston, variable in position to To tilt the axis of rotation. This is done by means of a so-called pivoting cradle, on which the side of the plate facing away from the cylinders is mounted.
  • the claimed pivoting journalling comprises a housing and a pivoting cradle which is arranged in the housing and has a through-hole for a drive shaft, wherein a bearing surface is formed on two opposite sides to the through-hole.
  • the pivotal pivot bearing comprises two bearing shells in the housing for pivotally mounting the corresponding two bearing surfaces of the pivoting cradle.
  • the pivotal pivot bearing is characterized in that the two bearing surfaces of the pivoting cradle are hydrostatically supported in the two bearing shells, and in a storage area between the bearing surface and the bearing shell, the two bearing surfaces and / or the two bearing shells each have a groove.
  • the component is referred to in an axial piston machine whose inclination to a plane passing through the longitudinal axis of the axis of rotation of the axial piston plane controls an axial stroke of the axial piston. This is done as explained in the introductory part of the description in interaction with the plate, which is connected to the cylinder piston.
  • the Swivel cradle on the side facing away from the cylinders on two bearing surfaces which are formed point-symmetrical to a center of the through hole of the pivoting cradle. These two bearing surfaces touch the bearing surface facing side of a respective bearing shell and can slide in this, to allow pivoting of the pivoting cradle.
  • the axial force FA resulting from the piston stroke of the cylinder acts against the respective bearing shell through the pivoting cradle.
  • the force between the bearing shells and the pivoting cradle is hydrostatically relieved. This also means that the tilting of the pivoting cradle by an adjustment hysteresis is possible.
  • the groove corresponds to a recess, which is discontinued in contrast to the surrounding level, that is reduced in height.
  • a cavity formed by the respective groove is connected to a liquid from a high-pressure side of an axial piston machine in order to hydrostatically relieve the respective bearing shell with a specific pressure.
  • a high pressure side of the set by the axial piston machine in the operating condition under pressure side of the liquid is considered. Accordingly, there is a gravure side, which corresponds to the side of the liquid that is sucked in by the axial piston machine.
  • both sides of the liquid interacting with an axial piston machine have identical pressure ratios. In this case, a hydrostatic discharge is not necessary due to a non-existent force that could act on the pivotal pivot bearing.
  • a channel which leads from the high pressure side of an axial piston machine to the cavity formed by the respective groove.
  • the channel which forms the connection of the cavity formed by the groove and one of the groove opposite the boundary surface to the high pressure side of an axial piston machine can pass through the pivoting cradle or through the bearing shell.
  • the purpose of this channel, or the connection with the high-pressure side of the axial piston machine is the supply of a highly pressurized liquid in the cavity characterized by the groove to relieve the frictional force acting between pivoting cradle and bearing shells.
  • the pressures formed by the liquid of the high-pressure side in the various cavities of the respective grooves which are preferably arranged point-symmetrical to the center of the through hole, are different in size.
  • the axial force F A emitted by the axial piston machine onto the pivoting cradle is offset from the longitudinal direction of the through-hole and consequently also acts with different force on the two bearing shells.
  • the wrapping angle ⁇ of the two bearing shells is about 150 °, preferably about 165 °, and particularly preferably about 180 °.
  • the wrap angle is the angle at which the bearing shell surrounds the pivoting cradle in the pivoting direction of the pivoting cradle.
  • An angle of wrap of 180 ° thus corresponds to a semicircle in a plane spanned by the pivoting angle. This is advantageous, since thus enough pressure field surface is available to ensure a good support and centering even at a maximum deflection of the pivot angle ⁇ .
  • the swivel angle ⁇ is zero degrees.
  • the system includes a first nozzle located downstream of the first check valve providing liquid for the cavity formed by the first groove, and a second nozzle located downstream of the second check valve and liquid for the second groove formed by the second Cavity provides.
  • a connection nozzle is provided which connects a point between the first check valve and the first nozzle and a point between the second check valve and the second nozzle.
  • the passage of liquid through the nozzle changes its pressure level.
  • connection side of the axial piston machine one of the two supply / discharge lines of an axial piston machine is designated for a liquid, of which one is the high-pressure side and the other the low-pressure side during operation. Since, depending on the position of the pivoting weighing plate, the two connections of the axial piston machine can be used both as a supply line and as a discharge line, these are referred to below as the first connection side and the second connection side of the axial piston machine.
  • there is a channel which connects the first connection side with a first check valve and a channel which connects the second connection side with a check valve. The check valve allows only a flow away from the connection side, thus preventing flow in the direction of the connection side.
  • a further channel which connects the side facing away from the first connection side of the first check valve with a first nozzle, which creates on its side facing away from the non-return valve a connection to the cavity created by the groove.
  • a second nozzle on the side of the check valve, which faces away from the second connection point, wherein the second Nozzle has a channel to the other characterized by the groove cavity.
  • This arrangement ensures that the pivoting cradle receives different weighing pressures in its two storage areas.
  • the bearing shell is loaded on the low pressure side with only half the force of the bearing shell on the high pressure impact.
  • a lower weighing pressure P W 2 builds up on the bearing shell of the low-pressure side than Pwi.
  • the connecting channel which is supplied by the high pressure side and supplies through suitable nozzles a liquid with suitable pressure, exists between the low pressure side of the pivoting pivot bearing.
  • the low-pressure side with a corresponding position of the pivoting cradle can also represent a high-pressure side
  • the symmetrical design of the liquid supply from the first and the second connection point of the axial piston machine is advantageous.
  • the two grooves are supplied with different pressures by a liquid of the high pressure side.
  • the various nozzles are provided, and leakage loss between the swing cradle and the bearing shell flows into the housing.
  • the distance of the closest points of the two bearing surfaces is approximately equal to the outer diameter of a roller bearing of a through-hole extending drive shaft.
  • the bearing distance DL is an important factor in increasing the rigidity of a pivoting cradle. This contributes to keeping the gap heights that occur between a bearing shell and a bearing surface as small as possible. Since under load, deformation of the pivoting cradle can not be prevented, the size of a gap height must be kept as small as possible. In fact, the gap height ensures correspondingly high leakage values, which are equivalent to a power loss of the pump. This is because the leakage values are fed from the high pressure side of the pump. The smallest possible distance between the two bearing surfaces thus results if they are directly adjacent to the through hole. This corresponds to the outer diameter of a roller bearing of an extending through the through-hole drive shaft of the axial piston machine.
  • the bearing surface and / or the bearing shell are provided with two mutually independent grooves in at least one of the two storage areas between the bearing surface and the bearing shell.
  • the pivotal pivot bearing thus has at least three grooves.
  • This arrangement helps to compensate for a radially acting force Fsteii.
  • a radial movement of the pivoting cradle within a bearing clearance is automatically reduced by the gap height difference between the bearing shell and the bearing surface.
  • this embodiment has for each of the two mutually independent grooves in at least one of the plurality of storage areas separate or separate connections to a pressure fluid to a specific process for the respective groove hydrostatic discharge at a setting operation of the pivoting cradle gain.
  • the specific relief of the groove is advantageously achieved by means of a liquid flowing through a nozzle, wherein the liquid is supplied from the high pressure side of the axial piston machine.
  • the fluid communication includes a further connection with the outside of the bearing surface of the pivoting cradle, which is disposed in an area substantially in an idle position of the pivoting cradle with a liquid inlet from a high pressure side of an axial piston machine through the bearing shell substantially.
  • the pressure supply of the grooves which are formed independently of each other, via directly introduced in the pivoting cradle channels.
  • an associated nozzle is also arranged in the channels for each of the separate grooves.
  • the further connection to the outside of the bearing surface of the pivoting cradle extends from a channel connecting the two nozzles to the outside.
  • the result is a substantially T-shaped line, wherein at two ends of the grooves are arranged and at the third end, the outside of the bearing surface is located.
  • the channel leading to the outside of the bearing surface is in an idle position of the pivoting cradle, i. in a position in which an axial piston machine does not pump liquid, with a liquid supply from a high pressure side passing through the bearing cup.
  • the two different grooves are supplied with different pressures.
  • a gap which widens in the direction of the through-hole is present between a bearing surface and an associated bearing shell. This is one way to reduce the leakage losses occurring during hydrostatic discharge to a low level. In the unloaded or lightly loaded state of the pivoting cradle, this creates a gap, which, however, causes only a slight increase in the absolute leakage losses at the prevailing relatively low pressures.
  • the widening in the direction of the through hole gap may be provided by a bevel of the respective bearing shells and / or a chamfer of a housing portion on which the respective bearing shell is arranged.
  • the gap results from a bevel of the bearing surface.
  • At least one of the existing grooves is configured in a staircase, that has at least two different depth levels.
  • This embodiment is advantageous in terms of a lower local deformation of the pivoting cradle in the region of the groove, since this is loaded laterally with high pressure.
  • At least one of the existing grooves comprises a plurality of parallel subslubs and a transverse subslot connecting them.
  • the invention further comprises an axial piston machine with a pivoting pivot bearing according to one of the preceding claims.
  • the invention comprises an axial piston machine with a pivoting pivot bearing according to one of the preceding claims, wherein the pistons of the axial piston machine are designed as solid pistons. This implies the advantage that any bearing clearance between the bearing shell and the bearing surface is reduced, so that a particularly effective bearing of the pivoting cradle is achieved.
  • FIG. 1 shows a section through an axial piston machine with a pivoting pivot bearing according to the invention
  • FIG. 3 shows a further sectional view through an axial piston machine with a pivoting pivot bearing according to the invention
  • Fig. 4 is a partial sectional view through an axial piston machine, in which a
  • Pivoting cradle can be seen in a deflected state
  • FIG. 7 shows a view of a pivoting cradle, in which the position of an axial force of an axial piston machine is indicated
  • FIG. 11 shows a further embodiment of the pivoting pivot bearing
  • FIG. 12 shows another form of pivoting pivot bearing
  • FIG. 13 shows various side views of the pivoting cradle, in which a groove is formed in a staircase shape
  • FIG. 15 shows a further embodiment of a pivoting cradle according to the invention in a perspective view
  • Fig. 16 two axial piston machines, once with hollow piston and once with solid piston.
  • FIG. 1 shows a sectional view of an axial piston machine 2 with a pivoting pivot bearing 1 according to the invention.
  • the reference numeral 6 denotes the drive shaft of the axial piston machine 2, with which the cylinder liners 14 and the cylinder pistons 13 received therein are firmly connected. Upon rotation of the drive shaft 6, therefore, the fixed thereto cylinders are rotated. The stroke of the cylinder piston 13 depends on such a rotation, depending on the position of the pivoting cradle 4. In an idle state of the axial piston machine finds no Axialhub the cylinder piston 13 at a complete rotation of the drive shaft 6 instead. In an idling operation, the surface of the pivoting cradle facing the cylinders forms a bearing surface on a plane which is essentially characterized by a normal vector parallel to the longitudinal direction of the drive shaft.
  • the axial force FA which results from the axial piston machine in this process and when pushing back a cylinder piston 13 in the cylinder liner 14 acts on the pivoting cradle 4, presses the pivoting cradle 4 against the bearing shell 8.
  • This contact force which arises between the bearing shell and the pivoting cradle 4 is hydrostatically relieved to the mechanical friction existing in the gap there to eliminate as much as possible.
  • the hydrostatic bearing via the construction of a pressure field between the bearing shell 8 and the bearing surface 7 of the pivoting cradle 4.
  • a groove 9 which communicates with the high pressure side of the PH Axial piston machine 2 via a channel 16 is in communication.
  • a pressure field specified in more detail below is constructed, whose effectiveness is determined by the size and shape of the groove 9.
  • the effect of the force acting in the groove 9 pressure field should be large enough to completely relieve the axial force F A of the axial piston machine can.
  • the groove 9 is designed such that there sets up a desired action force with a pressure Pwi slightly lower than the system pressure of the axial piston machine on the high pressure side PH there.
  • FIG. 2 shows a sectional view, indicated along the straight line AA in FIG. 1, in which the pivotability of the pivoting cradle in the bearing shell 8 provided therefor, which is arranged in the housing 3, can be better understood.
  • the half-circular in this sectional view formed bearing shell. 8 and the pivoting cradle 4 received therein can change its position relative to the bearing shell 8, whereby the axial stroke of the corresponding cylinder can be adjusted.
  • a groove 9 introduced into the pivoting cradle or into the bearing surface 7 of the pivoting cradle 4 forms a cavity with the bearing shell 8, which is connected to a connection side A via a channel 16. This ensures that the pressurized remplisstechniksleit necessary for hydrostatic discharge can be supplied via the high pressure side of the axial piston machine 2.
  • connection side A of the axial piston machine 2 does not necessarily have to coincide with the high pressure side of the axial piston machine 2, since the high pressure side can be changed depending on the position of the pivoting cradle 4, a system 10 for connection to the high pressure side of the axial piston machine (connection point A or connection point B ) supplied the liquid with the correspondingly high pressure.
  • FIG. 3 shows, in a section through B-B indicated in FIG. 2, a part of the system that supplies the two grooves 9 via respective channels 16 with a liquid from the high-pressure side of the axial piston machine 2 (connection point A or connection point B).
  • connection point A connection point
  • connection point B connection point
  • the groove is not shown in the drawing and lies outside the image plane.
  • connection nozzle 105 the downstream of the check valves 101, 102, the respective compounds of the check valve and groove 9 interconnects.
  • the connection nozzle 105 arranged in this connecting line ensures a certain pressure difference, so that different pressures act on the two grooves 9 or on the two pivoting vanes.
  • FIG. 4 shows a partial view of FIG. 2, which shows that the wrap angle ⁇ must exceed a certain extent in order to have enough pressure field surface in order to ensure good support and centering even at a maximum pressure field area. ximalen deflection of the pivoting cradle ⁇ to ensure. In this oblique position of the pivoting cradle by the angle ⁇ , one also recognizes the Axialhub good, run the cylinder heads 13a, 13b and 13c.
  • the groove 9 of the pivoting cradle 4 forms a cavity with the bearing shell 8, which at each pivoting angle ⁇ via a channel 16 and a system 10 for connecting the formed by the groove 9 Cavity with a liquid of the high pressure side of the axial piston machine 2 is in communication. This ensures that even with a maximum pivoting angle ⁇ , the hydrostatic bearing of the pivoting cradle 4 can be performed.
  • Fig. 5 shows a schematic diagram of the system 10, with which the grooves 9 are supplied with a liquid for generating the hydrostatic bearing.
  • the components shown here can already be found partially in the description of FIG. 3.
  • the bearing shell lying on the low pressure side (the bearing shell, acts on the less force by the movement of the piston) is loaded in the present embodiment, only with half the force, as the high pressure side bearing shell 8.
  • a lower weighing pressure Pw2 builds up as Pwi, which also requires a respectively adapted hydrostatic discharge with a corresponding backpressure.
  • Another ratio of the force distribution tion of the two pressures Pwi and Pw2 such as 1: 2, 1: 3, 1: 4, 2: 3, 2: 5, 3: 4 or 3: 5 can also be implemented.
  • the corresponding pressures for hydrostatic bearing are generated via nozzles 103, 104, 105 by a loss of leakage, which flows between the pivoting cradle and the bearing shell into the housing.
  • the necessary pressure P W i is generated from the high pressure side PH of the reciprocating engine 2 via a pressure drop at the nozzle 104.
  • a check valve 101 is also installed on the low pressure side. Since the low-pressure side can change from the connection point A to the connection point B depending on the position of the pivoting cradle 4 in an axial piston machine, a further check valve 102 is necessary in the system 10, so that no fluid is transferred to the low-pressure and high-pressure side. pressure side flows. Overall, thus obtaining a symmetrical structure of the system 10, which supplies the grooves with pressurized fluid.
  • Fig. 6 shows the interaction between pivoting cradle 4 and bearing shell 8 and the effects of the axial force F A , which is not arranged centrally to the through hole 5 of the pivoting cradle 4.
  • the left-hand drawing shows, with an offset axial force FA, by way of example the optimum bearing force which is offset by an angle ⁇ from the axis of symmetry of the pivoting cradle 4.
  • the right-hand drawing of FIG. 6 shows that the non-symmetrical impact of the force FA causes the pivoting cradle 4 inside the bearing shell 8 to rotate in a manner that varies along the bearing shell 8, which is illustrated by the values S 1 and S 2 of FIG Bearing game e is displayed.
  • FIG. 7 shows a perspective view of a pivoting cradle in which the axial force F A caused by the pistons is drawn at a specific pivoting of the pivoting cradle 4. It can be seen that the axial force FA is offset from the axis of symmetry or the center of the through hole 5 and is arranged closer to one of the two bearing shells.
  • Fig. 8 shows an advantageous countermeasure to relieve the axial force F A , which acts on the pivoting cradle 4, as effectively as possible hydrostatically.
  • the grooves 9a, 9b are arranged so as to communicate with a liquid supply from the high-pressure side of the axial piston machine 2, respectively. This liquid feed is formed via the bearing shell 8 into the groove formed by the groove 9a, 9b with the bearing shell 8. th cavity supplied.
  • FIG. 9 shows a further embodiment with which the resultant bearing force can be offset by an angle ⁇ , although the supply line of the high-pressure side of the axial piston machine 2 is arranged centrally to the axis of symmetry of the bearing shell 8. That is, the supply line is orthogonal to the pivotal wobble surface on which the axial pistons act, provided that the axial piston machine is in an idling state.
  • the pivoting cradle 4 is provided with a conduit system 11, which supplies the mutually independent grooves 9a, 9b with liquid.
  • corresponding nozzles 111, 112 are provided in the supply lines to the respective grooves 9a, 9b.
  • connection 12 extends to the bearing surface 7 of the pivoting cradle.
  • this connection 12 is in alignment with the supply line which extends through the bearing shell 8 from the high-pressure side of the axial piston machine 2.
  • Fig. 10 shows a schematic diagram indicating the leakage losses in a hydrostatic bearing of Schwenkwiegeunterlasses.
  • An important point in the hydrostatic pivot bearing is the achievement of a high rigidity of the pivoting cradle 4.
  • the undesirable but not completely avoidable deformation of the pivoting cradle 4 under the axial force FA is exemplified in Fig. 10.
  • the sum of the leakage values QLi and QL 2 is taken from the high-pressure side of the pump and accordingly represents a power loss of the pump.
  • the gap heights 21, 22 must be made as small as possible. It is advantageous that the pivoting cradle 4 is made very stiff.
  • the bearing distance D L shown in FIG. 1 is an important factor in increasing the rigidity. It is advantageous if the distance DL is as low as possible. The smallest possible distance corresponds to the outer diameter of a roller bearing, which is therefore selected without inner ring. The rolling elements of the bearing run directly on the drive shaft 6 of the axial piston machine.
  • FIG. 11 Such an embodiment is shown in FIG. 11.
  • an enlarged view of the pivotal pivot bearing is shown, in which a in the direction of Through hole widening gap ⁇ between the housing 3 and the bearing shell 8 is present.
  • Fig. 12 shows a similar area as Fig. 11, but in this case the widening in the direction of the through hole gap ⁇ is formed by a taper of the bearing surface 7 of the pivoting cradle 4, whereby a gap between the bearing surface 7 and bearing shell 8 is formed.
  • the leakage losses QLi and QL 2 are lowered to a low level.
  • the gap between the bearing surface 7 and the bearing shell 8 is caused by a chamfering of the bearing surface 7 or a chamfering of the bearing surface 8 or even by a chamfering of the bearing surface 7 and the bearing surface 8.
  • the housing 3 is beveled in an area on which the bearing shell 8 is located. The gap then arises here between the housing and the bearing shell and is reduced in a deformation of the pivoting cradle 4 in the direction of the beveled housing surface.
  • Fig. 13 shows a further embodiment of the pivoting cradle 4 in which the groove 9 is formed in a staircase shape.
  • the step-shaped configuration of the groove 9 leads to a greater material thickness of the pivoting cradle 4 and is advantageous in terms of a lower local deformation of the pivoting cradle 4 in the region of the groove 9, since this is loaded laterally with a liquid under high pressure.
  • Fig. 14 shows a perspective view of the pivoting cradle 4 in which the groove 9 is present directly in a blank of the pivoting cradle 4.
  • Fig. 15 shows again a perspective view of the pivoting cradle according to another embodiment and an enlarged part of the pivoting cradle, which shows the groove in a slightly enlarged view.
  • a plurality of small, preferably parallel, sublets 91 are provided, which can be supplied with pressure by means of a subduct 92 transverse thereto.
  • the plurality of parallel subsleads 91 are spaced apart from each other and are connected to the transverse sublude 92 in a state received by a bearing cup 8 so that liquids can flow between them.
  • the advantage of this is that between the Unternuten 91, 92 additional contact surfaces against the bearing shell 8 are available.
  • This particular embodiment of the grooves can be combined with any disclosed embodiment of the pivoting cradle and / or the pivoting pivot bearing.
  • the invention further comprises an axial piston machine with one of the above-described pivoting pivot bearings.
  • the swivel bearing according to one of the embodiments described above if the axial piston machine 2 is operated with solid pistons, as shown in FIG. 16b, instead of the hollow pistons (see FIG , In this case, the bearing clearance e between the bearing shell 8 and the bearing surface 7 of the pivoting cradle 4 decreases, whereby the additional design effort for displacing the bearing force F L does not necessarily have to be performed.
  • the pivoting cradle 4 may be made of a nitriding steel to achieve the necessary tensile strengths. The forming is done by forging.
  • the pivoting dimensions are so great that forging of the blank can not be performed, an alternative is the use of nodular cast iron or the use of nitridable materials.
  • the machined component is nitrided or nitrocarburized, with other methods of increasing surface hardness, such as case hardening, to be included.
  • the bonding layer is removed or polished after nitriding.
  • the hardness difference between the weighing surface (bearing surface 7) and the sliding bearing (bearing shell 8) should be at least 4 factor to ensure a wear-free function.
  • 8 brass alloys are used for the bearing shells.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

La présente invention concerne une disposition de paliers à balancier d'une machine à pistons axiaux, qui prévoit, au moyen d'une décharge hydrostatique en conjonction avec une gorge apportée dans la surface de palier d'un balancier, une disposition de paliers à balancier présentant particulièrement peu d'usure ou même sans usure. Selon l'invention, le balancier d'une machine à pistons axiaux est pourvu d'une gorge dans une zone de la surface de palier du balancier, la cavité formée par la coquille de coussinet et la gorge étant en liaison avec un côté sous forte pression d'un liquide de la machine à pistons axiaux. De cette façon, il est possible d'utiliser la pression régnant sur le côté sous forte pression pour décharger de manière hydrostatique la pression agissant sur le balancier par la machine à pistons axiaux.
PCT/EP2016/000333 2015-03-06 2016-02-26 Disposition de paliers à balancier d'une machine à pistons axiaux WO2016142037A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16706532.5A EP3265679B1 (fr) 2015-03-06 2016-02-26 Montage à berceau pivotant de machine à pistons axiaux

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH00316/15 2015-03-06
CH00316/15A CH710829A1 (de) 2015-03-06 2015-03-06 Schwenkwiegenlagerung einer Axialkolbenmaschine.

Publications (1)

Publication Number Publication Date
WO2016142037A1 true WO2016142037A1 (fr) 2016-09-15

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PCT/EP2016/000333 WO2016142037A1 (fr) 2015-03-06 2016-02-26 Disposition de paliers à balancier d'une machine à pistons axiaux

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EP (1) EP3265679B1 (fr)
CH (1) CH710829A1 (fr)
WO (1) WO2016142037A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109611448A (zh) * 2018-12-21 2019-04-12 成都利君实业股份有限公司 一种可调心滑动轴承
US10760683B2 (en) 2017-01-31 2020-09-01 Parker-Hannifin Corporation Cradle-mounted swash with trunnion-mounted positioning arms

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US10760683B2 (en) 2017-01-31 2020-09-01 Parker-Hannifin Corporation Cradle-mounted swash with trunnion-mounted positioning arms
CN109611448A (zh) * 2018-12-21 2019-04-12 成都利君实业股份有限公司 一种可调心滑动轴承
CN109611448B (zh) * 2018-12-21 2023-11-14 成都利君实业股份有限公司 一种可调心滑动轴承

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