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
  • F04B1/20—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
• • 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
  • F04B1/2035—Cylinder barrels
• • 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
  • F04B1/22—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 having two or more sets of cylinders or pistons
  • F04B1/24—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 having two or more sets of cylinders or pistons inclined to the main shaft axis
• • 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
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/14—Pistons, piston-rods or piston-rod connections

Definitions

• the invention relates to a hydrostatic axial piston machine with individual cylinder sleeves according to the preamble of patent claim 1.
• Hydrostatic axial piston machines are known from the prior art, in which a plurality of cylinders is formed in a cylinder drum.
• the cylinder drum for example, obliquely to a shaft (in motors to the output shaft and pumps to the drive shaft) and employed to a disc of the shaft.
• the cylinder are inclined to the shaft, whereby a Schrägachsenbauweise is defined.
• a piston is guided, which is pivotally coupled via a piston foot to the disc.
• the shaft rotate with the disc and the employed, "oblique" cylinder drum, so that the pistons rotate with each and make a total stroke (stroke in one direction and stroke in the opposite direction).
• a disadvantage of such axial piston machines with cylindrical drum is that due to the uneven distribution of solid material over the cylinder drum uneven, radial expansion of the cylinder bores can be done under working pressure.
• An original, in particular circular, cross-section of the cylinder bores is thus distorted under working pressure, or has a deviating from its original shape. Since the piston is not subject to the same distortion of its cross-section, sealing of the piston against the cylinder bore is worsened with increasing pressure.
• axial piston machines are known from the state of the art, in which the cylinders are formed as individual cylinder tubes or sleeves, that is to say not in solid material.
• the cross-section of the cylinder bore remains substantially undistorted under working pressure, or the expansion takes place uniformly.
• the document DE 10 2007 01 1 441 A1 shows such an axial piston machine with individual cylinder sleeves.
• the cylinder sleeves are in one piece and one end portion of each piston is slidably and sealingly received in the associated cylinder sleeve to perform the lifting movement during operation.
• each end portion must additionally be pivotally received in the cylinder sleeve to allow a resulting from the Schrägachsenbauweise, approximately elliptical orbit of the piston.
• each cylinder sleeve At an opposite end portion of the piston each cylinder sleeve this is pivotally mounted on a spherical bearing head. About this pivoting the employment of the cylinder sleeves is realized against the drive shaft of the axial piston machine.
• the bearing heads are in turn attached to a drum shaft rotating with the drive shaft.
• the cylinder sleeves are each supported via a tension spring and a spring plate on a drum ring comprehensive circlip. In this way, the cylinder sleeves are held down on a contact surface of the drum disc.
• the invention is based on the object to provide an axial piston machine, in which a backup of the cylinder sleeve is simplified in terms of device technology against removal from the bearing head.
• An axial piston machine has a plurality of individual cylinder sleeves, each of which is pivotally mounted on a radially enlarged, in particular crowned or at least partially spherical head or bearing head.
• each cylinder sleeve is coupled against removal from the bearing head via a first securing means with the bearing head.
• each of the cylinder sleeves is also coupled against being pushed onto the bearing head via a second securing means with the bearing head.
• the bearing head is fixed relative to the cylinder sleeve at a specific axial position or at least in a specific axial region of the cylinder sleeve, while maintaining its pivotability.
• the cylinder sleeve is thus neither deductible from the bearing head nor pushed on a proper way out on the bearing head. In this way, a collision of the cylinder sleeve with other components, in particular plates, disks or similar components to which the bearing heads are mounted avoided.
• the first and / or second securing means is preferably designed such that the bearing head of the corresponding securing means at least in sections
• one of the two securing means is preferably arranged on a first side and the respective other of the two securing means on a second side of an equator or a largest diameter of the bearing head.
• the securing means is formed integrally with the cylinder sleeve, which represents a device-technically particularly simple solution with few components.
• the securing means is preferably formed via a radial tapering section of an inner circumferential surface of the cylinder sleeve.
• This radial tapering section is preferably formed over an at least partially circumferential shoulder and / or over at least one approximately radially externally applied embossing point of the cylinder sleeve and / or about an approximately radially applied from the outside crimping or rolling of the cylinder sleeve.
• the securing means has at least one securing element which, at least in sections, dips into a recess of the cylinder sleeve.
• the securing element and the cylinder sleeve each represent a part. This variant proves to be advantageous in the assembly of the bearing head in the cylinder sleeve.
• the recess is formed in an inner circumferential surface or in an outer lateral surface of the cylinder sleeve.
• the securing element is substantially annular in this case and the recess is formed correspondingly annular groove on the inner circumferential surface of the cylinder sleeve.
• the securing element is a round wire snap ring, which is inserted in particular after installation of the bearing head in the cylinder sleeve with radial bias in a recess formed as a circumferential groove, so that it rests against a bottom of the groove with pressure.
• the round wire snap ring without radial preload tion in the circumferential groove or recess used so that it is not or only selectively applied to the bottom of the groove.
• the round wire snap ring can preferably be expanded so far in the groove that a largest diameter of the bearing head is released by a widened inner diameter of the snap ring.
• the securing element is a spring plate with a bore which has a diameter which is smaller than an inner diameter of the cylinder sleeve or as a largest diameter of the bearing head.
• the spring plate is inserted into a arranged on an outer circumferential surface of the cylinder sleeve groove and thus engages around an edge of the cylinder sleeve.
• the spring plate is inserted into a groove arranged on the inner circumferential surface of the cylinder sleeve.
• the securing means is a pin which passes through the cylinder sleeve approximately radially and also projects beyond an inner circumferential surface of the cylinder sleeve.
• the recess is formed in this case as NaturalgangsausEnglishung or bore. It is also possible to use two, three or more pins as securing means.
• the pin is preferably pressed into the recess or screwed as a stud in this.
• the securing means is at least partially joined to the cylinder sleeve, in particular by pressing, welding, gluing or the like.
• an annular securing means with a cylindrical outer circumferential surface is suitable, which is arranged at least partially on an inner circumferential surface of the cylinder sleeve.
• the securing means may in principle be formed in one piece or in several parts.
• the securing means in a preferred embodiment is an at least two-part segmented ring, which is inserted into a particular groove-shaped recess of an inner circumferential surface of the cylinder sleeve.
• the ring segments are held by the latter after mounting the bearing head in the groove of the cylinder sleeve.
• the cylinder sleeve may be formed either in one piece or in several parts. In the case of multi-part, a stroke of the piston in the cylinder sleeve can be increased by the fact that the several parts of the cylinder sleeve are telescopically slidable.
• the axial piston machine is preferably designed in bent-axis or swash-plate design.
• the bearing head is preferably fastened to a rotor coupled to a drive shaft, wherein the piston is fastened to a rotatable cylinder base with an end portion arranged opposite its head.
• the cylinder bottom can be pivoted via an adjustment lens supported on a housing.
• a particularly simple embodiment of the axial piston machine has a through-hole in the bearing head, via which a hydrostatic working space, which is at least partially delimited over an outer surface of the head of the piston and an inner surface of the cylinder sleeve, can be connected to a high-pressure and / or low-pressure connection.
• the head of the piston on the end face a recess, on the surface together with an inner circumferential surface of the cylinder sleeve at least partially a hydrostatic working space is limited.
• the working pressure prevailing in the hydrostatic working space can widen the head of the piston and keep or reduce a gap between an outer circumferential surface of the head of the piston and the inner circumferential surface of the cylinder sleeve constant. In this way, the tightness is consistently stable or even increased with increasing pressure.
• FIG. 1 shows a first embodiment of a hydrostatic axial piston machine in a schematic longitudinal section
• FIG. 2 shows a detailed view of a securing means of a second embodiment of a hydrostatic axial piston machine in a longitudinal section and the securing means in a plan view
• FIG. 3 shows a detailed view of a securing means of a third exemplary embodiment of a hydrostatic axial piston machine in a longitudinal section and the securing means in a plan view
• FIG. 4 shows a detail view of a securing means of a fourth exemplary embodiment of a hydrostatic axial piston machine in a longitudinal section and the securing means in a plan view
• Figure 5 is a detail view of a securing means of a fifth embodiment of a hydrostatic axial piston machine in a longitudinal section
• Figure 6 is a detail view of a securing means of a sixth embodiment of a hydrostatic axial piston machine in a longitudinal section
• Figure 7 is a detail view of a securing means of a seventh embodiment of a hydrostatic axial piston machine in a longitudinal section
• FIG. 8 shows a detailed view of a securing means of an eighth embodiment of a hydrostatic axial piston machine in a longitudinal section
• FIG. 9 shows a detailed view of a securing means of a ninth embodiment of a hydrostatic axial piston machine in a longitudinal section
• Figure 10 is a detail view of a securing means of a tenth embodiment of a hydrostatic axial piston machine in a longitudinal section.
• FIG. 1 shows a first exemplary embodiment of an axial piston machine according to the invention in a bent-axis design in a side-cut schematic representation.
• a housing 1 In the interior of a housing 1 is a plurality of cylinder-piston unit th (for example, six cylinder-piston units) arranged on a circular path, of which only two cylinder-piston units are shown in the figure.
• a high pressure port HD and a low pressure port ND are formed in the housing 1, each with a circular arc-shaped connection kidney (not shown in detail), of which one connecting kidney is above the plane of the drawing and the other connecting kidney is below the plane of the drawing.
• the two connecting kidneys are connected to a number of cylinder-piston units corresponding number of through holes 2 in pressure medium connection, which are arranged distributed uniformly on a circular path of a rotor 4, and pass in operation at the two Anschlußnieren.
• the rotor 4 is disc-like and mounted on a rolling bearing 6 in the housing 1.
• a bearing head 9 is fastened via a connecting sleeve 8.
• the connecting sleeves 8 have compared to the respective bearing head 9 has a slightly reduced diameter.
• a corresponding plurality of passage recesses 12 is provided on a cylinder base 10 attached to the rotor 4, adjacent to each passage recess 12 on the cylinder base 10, a hollow piston 14 is fixed, at the end portion of a substantially spherical head 16 is arranged.
• the pistons 14 also have a slightly reduced diameter relative to their respective head 16.
• To the bearing head 9 and the head 16 of the piston 14 each have a cylinder sleeve 18 is arranged as a boundary of a working space 20.
• the spherical shape of the head 16 of the piston 14 makes it possible to compensate for a kinematic nonuniformity of the movement of the heads resulting from the oblique axis design. These do not run on a circular path but on a slightly elliptical path.
• the spherical shape allows for compensating a pivoting movement of the sleeve on the head 16.
• the spherical shape of the bearing head 9 ensures buckling of the cylinder sleeve 18 according to a set via an adjustment lens 28 Anstellwinkel.
• the cylinder sleeve 18 is according to the invention via a first securing means 22, which engages behind the bearing head 9 on one side adjacent to the drive shaft 24 coupled to the rotor 4, against removal from the bearing head 9.
• the cylinder the sleeve 18 via a second securing means 23 which engages behind the bearing head 9 on a side facing away from the rotor 4 side of the bearing head 9, secured against an inadmissibly wide sliding onto the bearing head 9. In this way, a collision of the cylinder sleeve 18 with the rotor 10 is prevented.
• Both securing means 22, 23 are designed as a round wire snap ring and are each inserted into a circumferential in an inner circumferential surface 25 of the cylinder sleeve 18 groove with bias.
• a detailed illustration of this first exemplary embodiment of the first securing means 22 and further exemplary embodiments are described in the following FIGS. 2 to 10.
• the bearing head 9 and the head 16 have the same diameter, which corresponds to the inner diameter of the cylinder sleeve 18, so that no share of the hydraulic force has to be absorbed by the securing element 22, but only frictional forces of the piston head 16 in the cylinder sleeve 18th
• the commutation so the alternate connection of the working spaces 20 to the high pressure and low pressure port HD, ND of the axial piston machine, carried by the rotor-side connecting kidneys and the rotor-side bearing heads 9.
• the rotor 4 is slidably mounted on a drive shaft 24 and radially mounted.
• the axial bearing of the rotor 4 relative to the housing 1 assumes a hydrostatic discharge, which is advantageously combined with the commutation.
• the separation of radial and axial load allows a very precise adjustment of the axial relief to 100% degree of relief and thus a very low-friction support.
• the cylinder bottom 10 is taken from a drive flange or from a drive shaft 4 via a gimbal 26.
• the non-uniform rotational transmission which is inherent in a universal joint, is compensated by the bearing head 9 and the head 16 of the piston 14 of the single-cylinder piston units. Also compensated is the elliptical path of the center points of the piston-side heads 16, which is related to the cylinder bottom 10.
• the cylinder bottom 10 is also decoupled via a hydrostatic discharge from the adjusting lens 28.
• the cylinder bottom 10 can be pivoted on the adjusting lens 28 geometrically in both directions.
• the adjustment of the adjusting lens 28 can be made mechanically, hydraulically or electrically via a longitudinal or transverse adjustment. Due to the large surface of the adjusting lens 28 without breakthrough it is stored in low-friction plastic composite bearings relative to the housing 1. Lubrication or relief may be via the cylinder bottom 10 (or the hydraulic actuator, if selected).
• Figure 2 shows the conditions on the bearing head 9 according to a second embodiment of a hydrostatic axial piston machine in a longitudinal section. For reasons of clarity, only a detailed detail in the region of the bearing head 9 is shown. This form of presentation is also chosen for the sake of simplicity for all subsequent embodiments.
• a plan view of a first securing means 22 is furthermore depicted. This representation is also selected for the embodiments according to FIGS. 3 and 4.
• the second exemplary embodiment of the hydrostatic axial piston machine corresponds predominantly to the first exemplary embodiment according to FIG. 1.
• a representation of the second securing means 23 according to FIG. 1 was dispensed with for a simplified illustration.
• the bearing head 9 is shown with a comparatively small diameter, so that it does not appear to abut against the inner circumferential surface 25 of the cylinder sleeve 18.
• the bearing head 9 is fixed to the respective inner lateral surface 25,. 825 sealing.
• a further difference from the illustration according to FIG. 1 consists in the sectional guide in FIG. 2, in which the rotor 4 and the bearing head 9 are excluded from the cut.
• the rotor 4 and the bearing head 9 correspond in the embodiment according to Figure 2 and in all the following those of the first embodiment of Figure 1.
• the cylinder sleeve 18 has an encircling recess 30 formed as a groove at an end section adjacent to the rotor 4 in the inner lateral surface 25.
• recess 30 designed as a round wire snap ring first fuse element 22 is inserted.
• the outer diameter of the round wire snap ring and the groove are matched to one another such that the round wire snap ring is to be pressed together for assembly so that it can be inserted from the left into the groove or into the recess 30 in FIG. It should be noted during assembly that the cylinder sleeve 18 is postponed before inserting the round wire snap ring on the bearing head 9.
• FIG. 2 shows on the right the plan view of the insulated first fuse element 22 or the round wire snap ring. It can be seen clearly that the first securing element 22 has a gap 36, which allows the above-described assembly.
• the third exemplary embodiment of an axial piston machine shown in FIG. 3 has a certain similarity to the second exemplary embodiment according to FIG. Again, a round wire snap ring is used as a first securing means 122.
• the difference from the embodiment of Figure 2 is now that the round wire snap ring is inserted in the assembled state without radial bias and instead with a game in a trained as a circumferential groove recess 130 of a cylinder sleeve 1 18.
• An outer diameter of the groove is dimensioned such that for mounting the bearing head 9 in the cylinder sleeve 1 18 of the already pre-assembled in the groove round wire snap ring is expandable to the extent that the outer diameter of the bearing head 9 is released by the expanded inner diameter of the snap ring.
• the bearing head 9 can be mounted in a very simple manner in the cylinder sleeve 1 18, since the round wire snap ring in the cylinder sleeve 1 18 can be pre-assembled.
• Also designed as a round wire snap ring first fuse element 122 according to Figure 3 has a gap 136. This allows the Expansion of the round wire snap ring for mounting the bearing head 9 in the cylinder sleeve 1 18.
• the fourth exemplary embodiment of an axial piston machine according to FIG. 4 shows a first securing means 222, which is designed as a segmented ring. As shown in Figure 4 right, the segmented ring has a pitch 238, so that two ring segments are formed.
• both ring segments rest against the bottom of the recess 230 formed as a circumferential groove. In this way, on the one hand prevents the segmented ring pulling a cylinder sleeve 218 from the bearing head 9 and on the other hand, the bearing head 9, the two ring segments radially fixed in the recess 230.
• the round wire snap ring according to the first to fourth embodiments is supported via a line or cam contact on the bearing head 9 and the surfaces forming this contact are convexly rounded, is for the cylinder sleeves 18; 1 18; 218 realized a low-wear trigger guard.
• the fifth exemplary embodiment according to FIG. 5 has a ring with a flat, approximately rectangular cross-section, which is inserted into a cylindrical sleeve 318 at its left-hand end section in FIG.
• the ring is joined to the cylinder sleeve 318.
• the ring is pressed into the cylinder sleeve 318.
• the first securing means 322 or the ring has a chamfer 334.
• a spring plate 422 is proposed as the first securing means, which engages around an end portion of a cylinder sleeve 418 adjacent to the bearing head 9 from the outside.
• the spring plate is essentially plate-shaped formed and immersed with an edge 442 in a formed in an outer circumferential surface 432 as a circumferential groove recess 430 of the cylinder sleeve 418 a.
• the spring plate has a through-passage 444 with a diameter which is smaller than the largest diameter of the bearing head 9.
• the seventh embodiment according to FIG. 7 shows a device-technically simple solution for securing a cylinder sleeve 518.
• the cylinder sleeve 518 has a recess 530 in the form of a through-hole or bore into which a pin 522 is inserted or pressed.
• the pin has a chamfer 534 to reduce wear on the bearing head 9.
• only one pin is used.
• a stud can also be screwed into the cylinder sleeve 518.
• the recess 530 is then designed as a threaded bore.
• the eighth exemplary embodiment according to FIG. 8 shows a cylinder sleeve 618 which, as the first securing means 622, has an embossing point in the region of an end section of the cylinder sleeve 618. Due to the embossing of the cylinder sleeve 618 in this area, the bearing head 9 is engaged behind by a convex protuberance of an inner circumferential surface 625 of the cylinder sleeve 618. In contrast to the exemplary embodiment according to FIG. 8, more than one embossing point, for example two, three or four embossing points, can also be introduced into the cylinder sleeve 618. A similar solution is shown by the ninth exemplary embodiment according to FIG. 9.
• an end section of a cylinder sleeve 718 adjacent to the bearing head 9 has a first securing means as a curling. This is formed circumferentially on the cylinder sleeve 718, so that a radial tapering portion of the inner circumferential surface 725, over which the first securing element 722 is formed, is circumferential
• the tenth embodiment according to FIG. 10 likewise shows a first securing means 822 formed integrally with a cylinder sleeve 818.
• the first securing means 822 is not embossed, rolled or crimped but formed on the cylinder sleeve 818 by a forming or machining process.
• the first securing means 822 is formed via an annular circumferential, radial taper of the cylinder sleeve 818 formed on an inner circumferential surface 825 of the cylinder sleeve 818. This taper or shoulder has a chamfer 834 to reduce friction between the bearing head 9 and the cylinder sleeve 818.
• the cylinder sleeve can also be secured against being pushed onto the bearing head 9 by means of a second securing means.
• the second securing means differs from the first at least in that it engages behind the bearing head 9 on a side of an equator of the bearing head 9 arranged opposite the first securing means.
• the second securing means may be formed in its geometric configuration and / or its anchoring coupling with the cylinder sleeve equal to the first securing means of the above-described ten embodiments.
• the ten embodiments of the first securing means can be combined as desired with the ten embodiments of the second securing means.
• each cylinder-piston unit shown so the bearing head, the head and the cylinder sleeve, each matched in their stiffness so that the expansion of the gap between the respective head and the inner circumferential surface of the cylinder sleeve, resulting from the pressure in the working space , is compensated.
• This tuning can be achieved by the appropriate choice of material properties or mechanical stiffnesses.
• a hydrostatic axial piston machine with a plurality of individual cylinder sleeves, which are each mounted pivotably on a radially enlarged bearing head.
• a radially extended head of a piston is displaceably guided.
• each of the cylinder sleeves is coupled to the bearing head at least against removal from the bearing head via a first securing means.

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

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Citations (3)

• 2012
  • 2012-03-29 DE DE201210006288 patent/DE102012006288A1/de not_active Withdrawn
• 2013
  • 2013-03-19 WO PCT/EP2013/055598 patent/WO2013143906A1/fr not_active Ceased

Patent Citations (3)

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