DE1528615A1 - Hydrostatic radial piston unit - Google Patents

Description

A 2739 Voith Getriebe KG

"Self-sealing hydraulic pump" Heidenheim (Brenz)

Hydrostatic radial piston unit

The invention relates to a hydrostatic radial piston unit (Pump or motor) in double design with two essentially each in one of two axially adjacent Axially perpendicular planes in a set of radially acting displacers arranged with the drive or output shaft rotating (Piston and cylinder), in which the connected to the rotating cylinders Channels for the supply or discharge of the working medium to the fixed channels in the housing in one of the two or in open on both side surfaces of the rotor and are continued from there in the housing, and in the case of the means for sealing off the flow of working medium at the transition points from the rotor to the housing by pressing sealing surfaces against one another by means of the working medium pressure are provided.

In known hydrostatic units of this type, there is a separate pressure piece mounted in the housing or rotating with the rotor also provided with channels, which on the one hand with the stationary suction or pressure line of the unit, on the other hand with are connected to the flow channels arranged in the rotor. The runner must close at the transition points of the circumferential channels the channels arranged in the housing or the non-rotatably connected parts are sealed well, so that at these transition points no leakage losses occur. This is achieved in known hydrostatic units in that the pressure piece in the area the mouths of the housing channels in the axial direction against that on the housing or on the rotor, which forms a single piece with the shaft, arranged so-called. Control plate pressed by pressure medium is, so that a reliable seal is achieved on these sliding surfaces between rotating and stationary parts. The pressure piece is with on its side surface remote from the control plate

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from the working medium pressure; applied pressure surfaces.

The arrangement of such pressure pieces results in a special one Disadvantage that the axial extent of the pressure pieces to be arranged in the immediate vicinity of the rotor is a the axial width of the rotor is considerably larger than the bearing position requires, which makes vibration-free operation of the pump at high speeds difficult or a considerable Reinforcement of the drive shaft forces. This in turn has a corresponding increase in the radial outer dimensions of the pump housing and thus additional expenditure in terms of material, weight and construction volume. In addition, these are thrust pads quite complicated components that cause considerable costs for their production.

The object of the invention is to provide a hydrostatic radial piston pump designed in such a way that the disadvantages mentioned are reduced, i.e. that the axial space requirement as well as the structural and Manufacturing effort for the sealing of the working medium flow at the transition points from the rotor to the housing is lower than before. This object is achieved according to the invention thereby achieves that the runner carrying the displacer consists exclusively of two axially juxtaposed, against the approach or The output shaft is non-rotatable and axially movable with respect to one another, each with a set of displacer parts, and that between the two rotor parts at least one sealed gap which is connected to the respective pressure line is provided in such a way that the working medium pressure introduced into the gap space is at least one of the rotor parts of the two The rotor halves are pressed directly against the associated sealing surface (control plate) on the housing.

By designing the hydrostatic unit in this way, there is a perfect seal at the transition point between the suction and pressure lines from the stationary housing part to the rotating rotor and vice versa, the manufacturing costs for the unit, in particular

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an expensive production of the pressure pieces avoided; also become the dimensions of the pump are reduced, in particular in the axial direction, and the mounting of the drive shaft is improved. Of the for pressing the runner parts against the axial side surfaces of the fixed housing parts is filled with pressure medium gap space (or if necessary several such gap spaces are) now between the rotor parts receiving the displacer. No other parts are necessary either on the housing or on the rotor. Even with one that only has a single row of cylinders Pump in which the cylinders are arranged in one rotor part, while the other rotor part is only as Disc formed and possibly even rigidly connected to the shaft or formed from one piece, is the axial space requirement for this last-mentioned additional runner part a little smaller compared to the space required for the pressure piece. at one provided with a number of cylinders in each rotor part, so-called double unit, only those parts are provided that are absolutely necessary anyway and cannot be replaced. One of the rotor parts of a double unit can be fixed axially rigidly on the rotor shaft, but then muli the rotor shaft have a certain axial play themselves. Furthermore, in the case of a double unit, a control plate can only be arranged on one side be. Then one of the rotor parts without its own control unit must axially feed through the other rotor part; also mu3 he is supported axially.

According to a further concept of the invention, the or each gap space is expediently essentially as a ni-Lr.deotens one of the facing Jeiter.flächer, -the rotor parts arranged annular recess formed, at the Auier.umfanö and on the inner circumference each one ar. known piston seal,

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for example, a highly elastic sealing ring is provided.

According to a further idea of the invention, the gap space is axially via a preferably narrow bore with one on the outer rare surface of at least one of the rotor parts arranged, Concentric to the axis of rotation, connected to the pressure line adjoining annular groove. This design is also used in a A large number of cylinders in one or each rotor part ensures that the gap is always with the highest one Pressure of the medium generating cylinder is connected. In order to avoid the failure of the print medium - for example when starting the Pump against an unpressurized consumer - there is sufficient pressure on the axially outer side surfaces of the rotor parts to ensure the corresponding side surfaces of the housing parts are - according to a further concept of the invention - between the two rotor parts arranged compression springs.

In a further embodiment of the invention, between the or each axially displaceable rotor part and the associated side surface of the housing is provided a fitting piece having passage openings, the side surface of which is flat and on the rotor side whose side surface on the housing side is spherical. Due to the arrangement of these adapters - without significant Enlargement of the axial length of the pump - on the one hand the Tightness of the sealing surfaces ensured even with unfavorable installation conditions, on the other hand an easily replaceable one Wear member created, welciies contains the sliding surface that is most exposed to wear.

According to a further idea of the invention, the two are axially displaceable on a splined shaft profile of the drive shaft Rotor parts in the axial area of the spline profile near their axially outer side surfaces, each with a cylindrical recess provided, which is paired with a cylindrical groove arranged at the corresponding points on the drive shaft, and in Each of these pairings has a highly elastic sealing ring and axially outside a transversely divided support ring that supports it

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This design makes it a very reliable, convenient to use radially inner sealing of the gap is achieved. Advantageously the recess receives a greater axial width than the groove, because such a training is effortless Removal and installation of the sealing rings and the support rings allows.

A double pump designed in the manner described according to the invention works completely satisfactorily when the pressure channels and the suction channels of the two rows of cylinders are brought together in the housing and the common pressure line is connected to a single one Consumption point is connected. In many applications of such double pumps, however, it is very desirable to have each row of cylinders to be connected to its own consumption point.

When operating one in such a way at two different consumption points connected double pump, it is inevitable that the two rows of cylinders occasionally with significantly different Pressure work. Since both rows of cylinders are now in If there are line connections with the common gap space, undesirable effects occur if the cylinder rows are unevenly loaded Compensating flows from the pressure line connected to the cylinder bank with the higher pressure via the annular grooves, the narrow ones Bores and the gap space to the pressure line connected to the cylinder bank with the lower pressure. These equalizing currents cause greater losses, the greater the pressure difference in the two pressure lines.

There is also the fact that in such a case the pressure in the gap adjusts itself to a mean value between the pressures in the two pressure lines. It can happen that with strong Relief of one row of cylinders, the mean pressure that is established in the gap is no longer necessary to keep the Oleitflachen on the pump side having the higher pressure sufficient. This disadvantage can be explained according to another thought the invention by eliminating each of the bores between a Hingnut and the gap space with one against the latter opening, preferably in an axially parallel sack

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bore arranged check valve provides. As a result, the pressure in the gap is always on the one in each of the Both pressure lines maintained the highest pressure, but the flow of pressure medium after the pressure line with the prevented lower pressure.

When operating a double pump designed in this way the pressure in both pressure lines decreases, the pressure prevailing before the pressure decrease remains in the gap space; with others In other words, the check valves prevent the automatic pressure equalization between the gap space and the higher pressure having pressure line. This is usually harmless. However, if the working pressures vary greatly, it can happen that that the higher energy consumption caused by the high pressure in the gap due to friction on the sliding surfaces between the rotor parts and the housing parts in relation becomes too high for useful power. This disadvantage can be countered by - a further idea of the invention according to - one in the or each rotor part provided with a check valve in the bore leading to the gap space the cylinder spaces of this rotor part with the gap space, preferably via one of the blind bores, directly connecting compensation bore arranges. This compensation hole only needs to have a very small cross-section, since it is only used for pressure compensation Vanishing amounts of pressure medium have to pass through. By this compensating bore becomes a direct one when the working pressure in the cylinder rows of the two rotor parts drops Pressure equalization between the gap and the pressure line achieved with the higher working pressure.

The design of the double pump continues to be expedient in such a way that that each of the rotor parts by means of a common splined shaft profile extending over the axial extent of the two rotor parts the drive shaft is rotatably fixed with this, but axially displaceable on it. To avoid such Arrangement the use of combined axial-radial bearings for the Requires storage of the drive shaft - according to a

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Another idea of the invention - the spline of the drive shaft in the area of the parting line between the two Runner parts through a recess for inserting a cross-cut, preferably the same outside diameter as the spline having the fitting ring interrupted. Against the axial end faces of this fitting ring then lay the axial end faces of the facing towards the gap space projecting parts of the spline profile located on the rotor parts. As a result, the rotor parts move axially prevented.

In a further embodiment of the invention, the gap is sealed on the radially inner side by a highly elastic sealing ring, which rests directly on the outer surface of the transversely divided fitting ring. Since this sealing ring is under external overpressure stands, it also prevents the two halves of the transversely split fitting ring from giving way radially under the influence of the centrifugal forces occurring during the rotation of the rotor.

To a designed according to the invention double pump in any Way to be able to use, i.e. not only with bell-biger direction of rotation and equally as a pump or as a motor, but also with any flow direction, adjustable on both sides Eccentricity and separate connection of the two rows of cylinders at different consumption points, has become a training with two concentrically arranged gap spaces proved to be advantageous, one of which to the two pressure-side, whose the other connected to the two suction-side flow channels of the pump is. With such a design it is easily possible to interchange pressure channels and suction channels. To this Purposes are - according to a further idea of the invention, the two rotor parts on the axial side surfaces facing one another provided with a recess and / or a projection, both in the radial direction by coaxial cylinder surfaces are limited and wherein the turning of one rotor part is located at the same mean distance from the axis of rotation Is assigned to the projection of the other rotor part

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and the radial extent of the projection is smaller than that of the associated recess such that a highly elastic sealing ring can be arranged between each two facing cylindrical boundary surfaces of the recess and the associated projection. In order to reduce the radial space requirement of these gap spaces and to securely hold the transversely divided fitting ring in the recess of the splined shaft profile, the radially inner sealing ring rests snugly on the fitting ring. On its outside, this sealing ring is then enclosed by the radially inner cylindrical boundary surface of the projection of the one rotor part.

The invention is shown in several exemplary embodiments in the accompanying drawings shown. The same parts are provided with the same reference symbols in the drawings.

Fig. 1 shows the guided in the direction of eccentricity between rotor and housing through a longitudinal section designed according to the invention double pump with two axially adjacent rows of Cylinders;

2 shows a section through a perpendicular to the eccentricity between the rotor and the housing another type of double pump designed according to the invention;

Fig. 5 and 4 show two further embodiments of the gap space or the ¹ grant gap spaces between the two barrel.

On the drive shaft 1 of the double pump geir & sb 'Fig. 1, with the aid of a splined shaft profile 2, a pump rotor consisting of two axially juxtaposed runners is arranged in a rotationally fixed but axially somewhat displaceable manner. The rotor parts 5 and 4 have radially aligned cylinders 5 and 6, in which pistons 7 and 8 engage, A;> the pistons 7, 8, guide pieces 9 are articulated, which are in contact with the inner surface of a race 10. The race 10 is, more crazy side parts II in the ιλε-'Ό arranged in the housing 19 v _e l hat fixed or adjustable eccentricity geiage ·· - ^f - ¹ · ■ ^ - <· * -. ♦ er-rc-e- ie-M ;, -rlas. * with ο <? 2? Drive shaft 1 of the

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Rotate the race 10 and the side parts 11 so that the guide pieces 9 on the race 10 only have a slight eccentricity . Carry out a corresponding sliding movement.

Flow channels 15 and 20 are connected to cylinders 5 and 6, respectively; these are connected to the suction or pressure side of the pump, depending on the point at which each cylinder is located during one revolution of the drive shaft 1. Between the stationary housing 19 of the pump and the rotor parts 3 * 4 fitting pieces 17 and 22 are arranged in the axial direction, each of which is provided with passage openings 16 and 21, respectively. These passage openings 16, 21 establish the connection between the flow channels 15 and 20 and the suction lines 18, 18 'and the pressure lines 23, 23 '. In a simplified version of the Punipe, the fitting pieces can be omitted and the rotor parts can be pressed directly against the axially inwardly directed side surfaces of the housing 19. Furthermore, the fitting pieces can either be connected to the housing or to the rotor in a rotationally fixed manner.

For the purpose of sealing the sliding surfaces between the rotating rotor parts and the fitting pieces assumed below as "non-rotating" as well as the facing outer side surfaces of the fitting pieces and inner side surfaces of the housing, the rotor parts 3, 4 are attached to the fitting pieces 17 and 22 and these to the associated axially inner side surfaces of the housing 19 pressed by means of pressure medium. For this purpose, an annular gap space 24 is provided between the rotor parts 3 * 4 in their radially inner area adjacent to the drive shaft 1, which pressure medium flows from the passage opening 21 of the fitting piece 22 leading to the pressure line 23 'via a recess 25 made there and via the recess 25 in the rotor part attached annular groove 26 is fed by means of the bore 28. As a result, a high pressure builds up in the gap 24 , by means of which the rotor parts 3, 4 are pressed apart and the associated fitting pieces 17, 22 are pressed. The gap 24 is radially outward through a highly elastic sealing ring 30 and on the radially inner one Side of each rotor part is sealed by a highly elastic sealing ring 34. The sealing rings 34 are in grooves 31 of the drive shaft 1 in the axial area of the spline shaft

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Profils 2 near the axially outer side surfaces of the rotor parts 5, 4 and inserted into recesses 52 paired with these in the rotor parts 5, 4 and held on their axially outer side by a support ring 55 which is divided transversely.

Only a small amount of pressure medium is required to maintain a pressure in the gap 24 corresponding to the operating pressure of the medium in order to achieve good sealing of the flow channels at the sliding points. The bore 28 can therefore be narrow.

The fitting pieces 17, 22 connected in a rotationally fixed manner to the housing 19 have flat inner, the rotor parts 5s4 facing and spherical outer, the housing 19 facing side surfaces. The latter causes installation inaccuracies, in particular misalignment and deformation influences balanced, whereas the radial deflection of the central part of the drive shaft 1 as a result of radial forces is received in the axially perpendicular flat sealing surfaces without the sealing effect, for example by tilting, to affect or the friction on the sliding surface !! to increase because sliding occurs anyway on these Diohtungsflächen when the pump is in operation.

Inserted into axial bores 36,37 of the runner parts 3 and 4, respectively Compression springs 35 press the rotor parts in the absence of pressure, im Gap 24, for example when starting the pump, against the Sealing surfaces.

The construction according to FIG. 2 has a more extensive application possibility than the construction according to FIG. 1, without having to forego its advantageous, space-saving overall arrangement or having to accept these restrictive conditions. This construction of a hydrostatic radial piston pump shown in FIG. 2 differs from the exemplary embodiment according to FIG. 1 only with regard to the design of the two-part rotor 3 * 4. It is enough, therefore, just this and üi-? to represent and describe in each case immediately adjacent parts of the housing 19 in the axial direction, because the other housing parts with

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those of the embodiment of FIG. 1 match. In contrast to the representation according to FIG. 1, in FIG. 2 the sectional plane is perpendicular to the eccentricity between the housing and runner guided so that the pistons 7, 8 are in the cylinders 5, 6 in the middle position of their stroke.

Each cylinder 5, 6 has a side face of the associated rotor part 3 * 4 which is axially guided towards the housing 19 facing Flow channel 15, 20, the mouth of which when the rotor rotates over the mouths of the fittings 17 * 22 attached, connected to the housing channels 18,18 'and 25,23' Passage openings 16, 21 slide away so that a line connection between the rotor channels over a short period of time and the housing channels. Radially outside and radially inside the mouths of the rotor channels 15, 20 are on the axial outer side surfaces of the rotor parts 3 * 4 two to the axis of rotation arranged concentric annular grooves 26,27. Depending on the setting of the eccentricity between the rotor and the housing, one of these is 26 with the pressure-side, the other 27 with the suction-side passage opening l6 or 21 of the fitting pieces 17, 22 or vice versa in connection, each through a recess 25 * 25 *.

As in the exemplary embodiment according to FIG. 1, one of the drive shaft 1 is radial between the two rotor parts 3 »4 An annular gap 24 extending outwards to approximately the radial distance between the cylinder bases and the axis of rotation is arranged, which is formed by facing indentations in the two rotor parts 3, 4. Instead of this training of the Gap space 24, as shown in Fig. 2, this gap space can also be produced in that only in one of the a recess is provided for both rotor parts, while the other rotor part is designed with a smooth inner side wall is.

The gap space 24 is opposite the separating slot which extends in the radial direction to the outer edge of the two rotor parts sealed by an inserted, highly elastic sealing ring 30.

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Radially within the sealing ring 30 are in the axial direction Blind bores 36,37 incorporated into the facing end faces of the rotor parts, from the bottom of which are relatively narrow bores 28,29 to the annular grooves 26,27 in the axially * outer side surfaces of the rotor parts 3 # ^ are guided. These narrow bores 28,29 are closed against the gap 24 by check valves, which in the illustrated embodiment are designed as balls 40. These balls are pushed to the bottom of the blind bores by compression springs 35 ' pressed. The compression springs 35 'serve at the same time to press the rotor parts 3, 4 against the fitting pieces 17, 22 and against the rotor-side Side surfaces of the housing 19 in the absence of pressure from the medium in the gap 24.

On the radially inner side, the gap space 24 is the same Sealed way as in the embodiment according to FIG. 1 by sealing rings 34, which are in grooves 3I in the drive shaft 1 and inserted into corresponding recesses 32 in the rotor parts 3, 4 and are trimmed outward in the axial direction by transversely divided support rings 33. For immediate pressure equalization in the gap 24 when the pressure drops in the pressure line 23 'leading to the point of use is between that of the gap 24 outgoing blind bore 37 and the cylinder space 6 a narrow compensating bore 42 is provided. A similar compensating bore 41 is located between the cylinder space 5 of the rotor part 3 and the blind hole 36 is present.

This construction of the rotor of the hydrostatic radial piston pump according to FIG. 2 ensures that with this double pump not only the cylinders of one rotor part can be connected to a different point of consumption than the cylinders of the other rotor part, without leakage loss when the two consumption points are subjected to different loads occurs between the cylinders of one row and those of the other row, but in this design the pressure side and suction side can also be interchanged, the eccentricity of the rotor relative to the housing thus ν ση aer sentmic position in both directions

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settings and the pump with any delivery direction can be used. Of course, this pump can also be used as a motor.

The need to insert check valves in the bores 36,37 in order to avoid the occurrence of leakage currents between the two rows of cylinders with different loads, however, has the undesirable effect that the pressure prevailing in the gap space 24 is the highest in one of the connecting openings 16,21 of the fitting pieces 17 * 22 and thus corresponds to the highest pressure generated in the cylinders 5 »6. If the pressure in the pressure line or in one of the pressure lines is reduced, the pressure present there before the pressure reduction is maintained in the gap 24, since the check valves prevent automatic pressure equalization when the working pressure in the ducts leading to the point of consumption or points of use is reduced. As a result, however, a greater force is exerted on the side surfaces of the rotor parts acting as sealing surfaces than is necessary to maintain the sealing effect between these surfaces and the adjacent side surfaces of the fitting pieces. As a result, the friction losses occurring on these sealing surfaces when the rotor rotates become too high in relation to the pump output, so that the pump efficiency is impaired in an undesirable manner. This disadvantage can be eliminated by the compensating bores 41, 42, through which the gap space 24 is directly connected to one of the cylinder spaces 5 or 6 of each cylinder row.

For the axial guidance of the two rotor parts 3 * 4 axially displaceable in the spline 2 of the drive shaft 1, the spline at the parting line of the two rotor parts is interrupted by a recess 38 of rectangular cross-section extending to the base of the spline. In this recess a transversely divided Paasring 39 of approximately the same outer diameter as the wedge wave profile 2 is inserted.

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Instead of the embodiment shown in FIG. 1, the radial Outer sealing of the gap space 24 it is - because of the more convenient installation - advantageous, the sealing according to Pig. 3 train. In this design, one of the rotor parts (for example rotor part 3) is provided with one that is concentric to the axis of rotation Recess 43, the other rotor part (in the illustrated embodiment, rotor part 4) has an annular projection 44, which in the assembled state of the telden rotor parts 3 * 4 with axial and radial play in the Einö; Exercise 43 of the runner part 3 dips.

Between the opposing radially outer cylindrical Boundary surfaces of the recess 43 and the projection 44, a highly elastic sealing ring 45 is inserted between the two rotor parts 3, 4. Another highly elastic sealing ring is between the cylindrical outer surface of the transversely divided in the recess 38 of the spline shaft profile 2 of the drive shaft 1 inserted fitting ring 39 and the radially inwardly directed cylindrical boundary surface of the projection 44.

The gap 49 between the two sealing rings 45,46 has an annular surface which is dimensioned in such a way that a sealing force corresponding to the prevailing highest working pressure is exerted there the axially outer side surfaces of the rotor parts on the fitting pieces and the associated side surfaces of the rotor Housing is exercised, and is via holes 28,29 with the Annular grooves, not shown, in the axially outer side surfaces of the rotor parts 3, 4 in connection.

These bores 28, 29 are, as in the exemplary embodiment, according to FIG Fig. 2, secured by check valves, which are made of compression spring-loaded, in axial blind bores 4 ″, 48 arranged balls are formed. The gap 49 is included for pressure equalization when the working pressure drops in one or both rows of cylinders connected to a cylinder space of each row by a compensating bore. In FIG. 3 is that of the axial blind bore 48 Planned compensation bore 42 leading to the cylinder chamber 6.

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In the design of the seal according to FIG. 4, they are axial Outer side surfaces of the rotor parts 3, 4 are each provided with two annular grooves 26, 27, between which the from the cylinders to the Housing lines leading connection channels in the side surfaces flow out. Of these connection channels, ″ in FIG. 4 is the connection channel 15 leading from cylinder 5 to the outside drawn.

The rotor part 3 is turned on its side face facing the rotor part 4 in its radially inner region for receiving a sealing ring 50, connecting radially outwards with a projection 44 and a further recess 43, the Rotor part 4 on its rare surface facing rotor part 3 in its radially inner area in a recess 4jJ 'and then radially outwardly provided with a projection 44 '. Projections and indentations of the same rotor part are through coaxial cylindrical surfaces separated from each other, against which the sealing rings 50,51 * 52 are supported. Every lead of the one Runner part is assigned a turning of the other runner part in such a way that both are at the same mean distance of the axis of rotation are located and the radial extent of each projection by a caused by the sealing rings resting on this Dimension is smaller than the radial extent of the associated recess. Also the height of the projections or the depth of the indentations corresponds to the thickness of the adjacent sealing rings.

From the space between the two rotor parts 3 * 4 Thus, by means of a total of three highly elastic sealing rings 50, 51 * 52 arranged concentrically to the drive shaft 1, two gap spaces 53 * 54 separated, the outer one over the one with a valve ball provided check valve 55 and a bore 57 is connected to the radially outer annular groove 26, while the inner gap space Via a similar check valve 56 and a bore 58 with the radially inner annular groove 27 is in communication. The radially innermost sealing ring 50 is supported against with its inner sealing surface a transversely divided fitting ring 39 inserted on the drive shaft 1 in a recess 38 interrupting the spline 2,

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with its radially outer sealing surface against the radially inner cylindrical boundary surface of the projection 44 of the rotor part. The two rotor parts J, k are held in the axial direction by the fitting ring 59 in the same way as in the previous exemplary embodiments. To compensate for pressure when the working pressure in the cylinders falls, the gap spaces 53 * 5 ^ are connected to a cylinder of the respectively assigned row via equalization bores, of which in FIG is. The bores 57,58, which connect the blind bores 47,48 with the annular grooves 26 and 27, are made relatively wide in this embodiment and only have a considerably smaller clear width in the part directly adjoining the entry into the blind bore in order to allow the flow of the To limit the print medium.

August 4, 1966 009832/0161

Sha / DrBi / EBi.

Claims (1)

A 2759 Λ% Voith Getriebe KG "Self-sealing hydraulic pump" Heidenheim (Brenz) Claims 1) Hydrostatic radial piston unit (pump or rotor) in double design with two sets of radially acting displacers (piston and cylinder) arranged essentially in one of two axially adjacent axially perpendicular planes in a rotor rotating with the drive or output shaft which the channels connected to the rotating cylinders for the supply and discharge of the working fluid to the fixed channels in the housing open in one of the two or both side surfaces of the rotor and are continued from there in the housing and at the means for sealing the working fluid flow the transition points from the rotor to the housing are provided by pressing sealing surfaces against each other by means of the working pressure, characterized in that the rotor carrying the displacement body consists of two axially juxtaposed, rotationally fixed against the input and output shaft (1) and axially movable against each other, each with one set from displacement organs armed parts (J>, 4) is formed and that between the two rotor parts (5,4) at least one with the respective pressure line (2; 5,2j5 ') in connection sealed gap space (24,49,53,54) is provided is such that the working medium pressure directed into the gap presses at least one of the rotor parts of the two rotor halves directly against the respectively assigned sealing surface (control plate) on the housing (I9). 2) Unit according to claim 1, characterized in that the or each gap space (24,49,53,54) essentially as a min- BATH ORIGINAL 009832/0161 ι in »nfiiinfln (am. 11 1 Ab · .2 No. 1 sentenceIdaiΧτβϋυηΐΜαΜ. ν. 4. y. at least one of the mutually facing side surfaces of the rotor parts (3 * ² O arranged annular recess is formed, on the outer circumference and on the inner circumference of which a piston seal known per se, for example a highly elastic sealing ring (30,34,45,46,50,51, 52) is provided. 3 «unit according to claim 1 or 2, characterized in that the Gap space (24,49,53 * 54) via a preferably narrow bore (28,29,57,58) with one on the axially outer side surface at least one of the rotor parts (3, 4) arranged relative to the axis of rotation concentric annular groove (26,27) connected to the pressure line. 4.EinheStnach claim 1 to 3 * characterized by between the two rotor parts (3 * 4) arranged compression springs (35) for Pressing the rotor part or parts against the sealing surfaces if the pressure medium fails. 5 «unit according to one of claims 1 to 4, characterized in that between the or Jv. / In the axially displaceable rotor part (3 * 4) and the associated side surface of the housing (19) a fitting piece (17, 22) is provided which has openings (16,21) and whose side surface on the rotor side is flat and whose side surface on the housing side is spherical. _y 6. Unit according to one of claims 1 to 5, characterized in that that the two rotor parts (3, 4) axially displaceable on a splined shaft profile (2) of the drive shaft (1) Area of the spline close to their axially outer side 009832/0161 bathroom tenflachen each have a cylindrical recess (32) which each paired with a cylindrical groove (31) arranged at the corresponding points on the drive shaft (1), and that in each of these pairings has a highly elastic sealing ring (34) and axially outside a transversely divided support ring that supports it (33) are inserted. 7. Unit according to claim 6, characterized in that the recess (32) has a greater axial width than the groove (31). 8. Unit according to claim 3, characterized in that each of the Bores (28,29,57,58) between an annular groove (26,27) and the gap (24,49,53,54) with one facing the latter opening check valve (40,55,56) preferably arranged in an axially parallel blind bore (36,37,47,48) is. 9. Unit according to claim 8, characterized in that in the or each provided with a check valve (40,55,56) in the bore (28,29,57,58) leading to the gap (24,49,53,54) Runner part (3, 4) one of the cylinder spaces (5, 6) of this runner part with the gap space, preferably via one of the blind bores (36,37,47,48) directly connecting compensating bore (41,42) is arranged. 10 »Unit according to one of claims 1 to 9, characterized in that the Kellwellenprofil (2) of the drive shaft (1) in the area of the joint between the two rotor parts (3, 4) by a 009832/0161 BATH ORIGINAL Turning (38) for inserting a transversely divided, preferably the same outer diameter as the spline having fitting ring (39) for the purpose of axial guidance of the rotor parts is interrupted. 11. Unit according to claim 10, characterized in that the radially inner sealing ring ( 46, 50) rests directly on the outer surface of the transversely divided barrel ring (39). 12.2 unit according to one of claims 1 to 11, characterized in that the two runner parts (3, 4) are provided with a recess (43, 43 ') and / or a projection ( 44, 44') on the axial side surfaces facing one another, both of which are in each case delimited in the radial direction by coaxial cylindrical surfaces and wherein the recess of the one rotor part a medium on an equal • distance from the rotational axis befindlicher projection is associated with the other rotor part and the radial extent of the projection is smaller than that of the associated recess such that A highly elastic sealing ring (45,51,52) is arranged between each two facing cylindrical boundary surfaces of the recess and the associated projection. August 4th, 1966 Sha / DrBi / EBi. BATH 009832/0161 Blank page