DE2037429A1 - Hvdrauhk radial motor and pump - Google Patents

Description

PATENT ADVOCATE
DR. HANS ULRICH MAY 2037429

D θ MÖNCHEN 2, OTTOSTRASSE 1 a TELEGRAMS: MAYPATENT MONKS TELEPHONE COS11> 093082

D ~ 7-P _r i / 8'79 Munich, July 28, 1970

Dr, .Ii. / ng

Kenneth Raymond Dixon in Kingston Beach, Tasmania / Australia

Hydraulic radial motor and pump

Background of the invention :

Known hydraulic radial motors or pumps are the radial piston motors or pumps, which have a cylinder block rotatable about a first axis, pistons running in the cylinders with radially inwardly lying working surfaces and a rotor which rotates around a second axis parallel to the first axis and at a distance therefrom is rotatable second axis and has chordal surfaces against which the radially outwardly lying ends of the pistons are slidably supported.

Theoretically, the forces acting on or through the pistons are all radial to the first axis and go through the central axes of the Cylinder and piston, so that no torque whatsoever around the central axes should act on the pistons. In practice, however, it is found that torques acting on the piston even with the largest cylinder volume can occur, which cause a plague seizure, if the parts are not machined to very low tolerances and / or the pistons and cylinders have a significant overlap

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Because machining to close tolerances is avoided as much as possible and the diameter of the motor or pump in general should be kept as small as possible are those given above Solutions to the seizure problem are not always practical.

The invention is therefore based on the object of motors or pumps of the kind specified, in which the problem of plague eating is at least partially solved.

It has been found that the pistons can, in principle, be essentially omitted as far as their function of accommodating Power from hydraulic medium and the transmission of power to this medium is concerned, and that the rotor can be used as an equivalent of the piston working surfaces.

For the description of the invention it is necessary to be clear understand how pumps and motors are similar and how they work in general. To facilitate this understanding, be pointed out that, in the case of an engine, work is done when the flow medium (hydraulic fluid) is introduced under pressure into cylinders, while in the case of a pump work is done when the flow medium is under pressure is pushed out of cylinders. This work is always done during the working strokes, and it should be emphasized that the working stroke of an engine during intake and that of a pump during the discharge of the medium. Conversely, the non-working cycle of an engine results during of venting and that of a pump during intake. The fluid which, in the case of an engine, is used to perform work is determined and on which work has been done in the case of a pump, is appropriately referred to as the working medium,

00 98 87/1623 ^:

that in the case of a motor and in the case of a Fluid sucked in (introduced) by the pump is expediently referred to as non-working medium.

Summary of the invention:

4h To solve the problem posed vßrd / according to the invention a hydraulic radial motor or pump with a cylinder block relatively rotatable about a first axis, reciprocating parts in or on the cylinders and one about a second axis that is parallel to the first axis and in one Distance from it runs, relatively rotatable rotor with chordal planes forming inner surfaces, against which the ™ radially outwardly lying ends of the reciprocating parts slide and seal, proposed, velche are characterized in that the reciprocating parts

KanHU
running passages are provided for the fluid, how do you establish a fluid connection between the rotor chord surfaces and the cylinders in such a way that the fluid in the cylinders during the working cycle "? generated are taken outwardly directed forces hydraulically venigstens in vesentlichen completely and vesentlichen up directly from the tendons surfaces μ.

Because these tendon surfaces the forces hydraulically and at least absorb essentially completely and directly, the forces acting on the reciprocating parts are compared to the pistons of the known radial piston engines or. -pump at least significantly reduced and thus the risk of seizure also reduced in comparison with the known machines. According to the invention, therefore, motors or pumps can be manufactured with parts are not machined to close tolerances, and Eolclie motors and pumps can be made with relatively small

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Diameters built for a given capacity.

Preferably, the radially outward ends of the reciprocating parts carry seals that are attached to the tendon surfaces make a tight fit in order to prevent the loss of flow medium from the cylinders.

According to the invention, devices are also provided which reduce unwanted unbalance forces, and for this purpose had the motor or the pump, preferably a second flow

channel
middle passage which establishes a connection of the fluid with the rotor in such a way that, during operation, a force acts thereon which is essentially equal to and generally opposite to the radially outwardly directed forces which are exerted on the chordal surfaces by the fluid in the cylinders by exercising at least a substantial part of the work cycle during a year.

In a preferred embodiment, the motor or the pump has a bearing, the one first cylindrical section on the first axis and a second cylindrical portion on the second axis, in use the cylinder block relative to the first section and the rotor rotates relative to the second section. In this construction, the second passage has / preferably a passage in the bearing, which is in operation with working medium in connection and to the periphery of the second section is open, whereby the working medium exerts on the rotor / a force that is essentially equal and opposite to the radially outwardly directed forces acting on the chordal surfaces through the flow medium in the cylinders at least a considerable part of the work cycles ^ are carried out.

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In a particularly preferred embodiment, the second

channel i _e ; l

Passage 'two groups of passages in the camp / which open diametrically opposite to each other to the periphery of the second section and in operation with the working or non-working medium or. the non-working or working medium, whereby the machine can be operated both as a pump and as a motor with any direction of relative rotation and, under all such circumstances, enables working medium to communicate with the Rotor is brought, whereby this / a force is exerted, which is essentially equal and on the whole opposite to the radially outwardly acting forces, which act through hydraulic medium in the cylinder during at least a considerable part of the work cycle> on the surfaces. In a special embodiment of the last-mentioned embodiment, the rotor is provided with recesses which are open towards the periphery of the second section and have effective working surfaces such that a force is exerted on the rotor during operation by interacting with the opening of the second passage to the periphery of the second section is exerted, which ^ is substantially equal and on the whole opposite to the forces acting radially outward on the surfaces, which act through the hydraulic medium in the cylinders ^ uring at least a considerable part of the working cycle ^.

fax * The recesses preferably extend in the shape of a ring / an angle of the second sections, so that, during operation, they interact with the opening of the second passage to the circumference of the second section for at least a considerable part of the work cycles. As a further measure to reduce undesired unbalance forces, it is preferred that the effective working surface of the cylinder block, which is to be used during the working

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working medium acts radially inwards and radially outwards, is essentially the same.

Devices are preferably provided in order to change the distance between the axes.

In a preferred embodiment, the motor or pump has a shaft which has an intermediate cylindrical outer surface which forms the first cylindrical portion and two cylindrical parts, each of which has a cylindrical outer surface with surfaces which together form the second Form cylindrical section, wherein the cylindrical parts are held non-rotatably on the shaft at opposite ends axially opposite to the first section. The shaft and the two cylindrical parts are movable relative to each other in a direction which runs diametrically to the axes _t in a continuous through the axes imaginary plane - to ä © n spacing of the axes to vary from one another. Preferably, a chamber can be provided which is at least partially limited by the shaft and one of the two cylindrical parts and into which the flow medium was introduced under pressure in order to exert a force between the shaft and the mentioned one of the two cylindrical parts to reduce the mentioned Generate relative movement sbu. Even more preferred is the arrangement of two groups of brackets, which are at least partially limited by the shaft and the two cylindrical parts and are arranged in the plane diametrically at a distance from each other, and in dlez * channels are provided for pressure medium, whereby pressure medium - each d @ i> can be fed to both groups in order to produce the specified relative movement.

In a further preferred embodiment, the motor has

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or the pump forms a first shaft with a cylindrical outer surface, velche the first cylindrical section »and a Rotor holder with a cylindrical bore which defines the second cylindrical section and a second relative therein rotatable shaft connected to the rotor and at least partially held non-rotatably within the first shaft is, wherein the first shaft and the rotor holder relative to each other in a direction diametrically to the axes in a through the axes going imaginary plane is movable to change the distance between the axes from each other. Preferably is a chamber is provided which is at least partially through the first

ift

Shaft and the rotor holder is limited and / the pressure medium can be introduced to exert a force between the first shaft and the rotor holder, which the specified relative movement causes. Even more preferred is the arrangement of two chambers which are at least partially delimited by the first shaft and the rotor holder and are arranged in the plane diametrically at a distance from one another, with pressure medium channels being provided, through which print media can be directed into each of the cameras to produce the specified relative motion.

Detailed description

To further explain the invention, a Number of devices according to the invention and modifications thereof are described with reference to the accompanying drawings.

1 shows a cross section of a device according to the invention; FIG. A shows a section along 2-2 of FIG. I; 3 shows a section along 3-3 of FIG. 1; Figure 4 is a cross-section along 4-4 of Figure 2; being parts

are shown schematically;

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5 shows a detail of the device in section; 6 shows another detail of the device in section; 7 shows a modification of the part shown in FIG. 6 in section;

FIG. BA shows a modification of the part shown in FIG. 5 in section, as well as pressure gradients and resultants and

FIG. 8B shows a modification of another part shown in FIG. 5 on average;

fig. Sfl another part of the device in section and the

9B and 9C pressure gradients and resultants; Fig. 10 is a view of a further part of the device;

11 shows a cross section corresponding to Pig.1 of a modified one Contraption;

Figure 12 is a section taken approximately along 12-12 of Figure 11;

13 shows a cross section corresponding to FIG. 1 of another modified device;

14 shows a section / 14-14 of FIG. 13 and 15 shows a section approximately along 15-15 of FIG.

The device shown in Figures 1b; Ls 4 is for use intended as a motor or pump. Rs first becomes the arrangement of its-main parts while specific details of certain parts and modifications thereof are given below.

The device according to the invention has a (stationary) shaft with a first cylindrical section 2 having an axis 3. A cylinder block 4, which has five cylinders 6, is rotatable on the section 2. In each cylinder 6 there is a reciprocating part 7 # which is hereinafter referred to as a piston-like part.

The shaft 7 also has cylindrical portions 8 with a

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Axis 11 on. On the sections 8 there is a rotor 12 around the axis 11 rotatable,. And it should be noted that the axes 3 and 11 parallel to each other but at a distance E - the eccentricity - run from each other.

Each of the piston-like parts 7 has a through hole 13 and at the radially outer ends depressions 14, which are limited by seals, ring seals and shoulders 19. The effective area of each of the recesses 14 is substantially the same but slightly smaller than the effective working area of the cylinders 6.

The shaft 1 has two fluid chambers 21 and 22 which are in communication with bores 23 and 24, respectively. More holes or channels 26 and 27, which are in communication with the bores 23 and 24, open into depressions 31 and 32, respectively, in the jacket surface Further sections 8 diametrically opposite the chambers 21 and 22, respectively.

The cylinder block 4 has ring seals 33A and 33B and transverse seals 36, recesses 37 and bores 38 which connect the recesses to the cylinders 6. The effective work surface each of the areas delimited by the ring seals 33 and transverse seals 36, i.e. practically the effective working area each of the recesses 37 'is essentially equal to the effective working area of each of the cylinders 6.

The cylinder block 4 also has arms 39 'which drive pins 41 wear. The ends of the driving pins are circular Recesses 40 are arranged, the diameter of which is equal to twice the E plus the diameter of the driver pin 41.

The rotor 12 has five circular chord surfaces 42 and abutments 43

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which under the shoulders 19 of the piston-like parts 7 grip and press the radially outer ends of the same tightly against the chordal surfaces 42.

The rotor 12 veist bearing surfaces 44, which on the other Indentations Sections 8 of the shaft 1 are rotatable. Dif / 31 and 32

are open to these storage areas. It's king seals that are formed by sealing rings 47 and the abutment of the sides 49 of the rotor 12 against shoulders 52 on the shaft 1, and transverse seals 54 are provided.

P The bearing surfaces 44 each have five depressions 56. the effective areas bounded by adjacent transverse seals 54 and the ring seals, i.e. practically the effective The area of each of the recesses 56 are substantially equal to half the effective area of a cylinder on each bearing surface 6, so that recesses 56 arranged at a similar angle have an effective area essentially equal to that of a cylinder 6 on the bearing surfaces together.

How it works as a motor

In the following, the operation of the device described above as a motor for rotating the rotor 12 clockwise, as seen in Fig. 2, described.

Flow medium {hydraulic medium} under pressure (working medium) is the bore 24 and enters the chamber 22.

If now a cylinder 6A, which is approximately in the position X is located, is moved slightly in a clockwise direction, the transverse seal 36A no longer presses against the part of the shaft between A and B "so that work" raedium von der KaMftev 22 in di "

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Recess 37A and pass through the bore 38A in the cylinder 6A can. Since the effective areas of the recess 37A and of the cylinder 6A are substantially the same, there will be substantially no radially outward or inward directed on the cylinder block Force exerted.

In the cylinder 6A, the working medium passes through the bore 13 into the recess "14A, the effective area of which is essentially the same but slightly smaller than that of the cylinder 6A, so that the forces directed radially inwards and outwards at the radially inward and outward-lying ends of the piston-like part are substantially balanced, etc., but a small force remains, which keeps the piston-like part 7A sealingly pressed against the chordal surface 42A It is also noted that even the pressure of the shoulders 19 serves by the stop 43, the piston-like parts. 7 in close sealing contact with the tendon surfaces 42.

In the recess 14A, the working medium acts on the tendon surface 42A and exerts a force directed radially to the axis 3 and in the direction of the center line of the cylinder 6A on the surface 42A.

So you can see that the hydraulic medium in the Zy ™

alleviate 6 induced, radially outwardly directed forces hydraulically at least substantially completely and immediately are picked up by the surfaces 42, which should be compared with the known devices, where such forces hydraulically directly on the piston and mechanically directly on the piston the surfaces are transferred.

The force acting radially outward on the surface 42A is radial to the axis 3, but eccentric to the axis 11, so that a torque acts on the rotor 12 which makes it easier with respect to the

009887/1523

sees the Fig. 2 strives to rotate clockwise.

Bs should be noted, however, that the working medium on the cylinder block 4 exerts no direct torque and that the force required to rotate it is only that required to overcome the friction is. Since the piston-like parts 7 are pressed against the surfaces 42 and are in operative connection with them, the Block 4 inevitably rotated with the rotor 12. In addition, the engagement of the driving pins 41 also forces the circular recesses 40 the cylinder block 4 rotates together with the rotor 12 and serves to reduce the risk of seizure, since the block 4 is not only driven by the piston-like parts 7.

The cylinder block 4 and rotor 12 therefore rotate with the same Angular velocity, and it can be seen that the cylinder 6A between X and Y passes through a work stroke which is ended when the transverse seal 36D reaches point B on section 2.

Further movement of the cylinder 6A beyond Y causes the transverse seal 36A is moved beyond the point C onto the section 2 and the cylinder 6A begins a non-power stroke, meanwhile, medium is discharged through the chamber 21 and the bore 23

occurs.

It should also be noted that the medium, while on the surfaces 42 of the rotor 12 acts, also acts on the bearing surfaces 44 from the fact that the passage channels 27 are in communication with the bore 24 (and passage channels 26 in communication with the Bokrang 23), ' and therefore working medium in the well '32 up ** well 56 where it acts on the bearing surfaces · 44. As "mentioned above, is the effective area of each of the wells 36 is half as large as that

0Q9887 / 1S23

of a cylinder 6, so that a radially outwardly directed force acts on the bearing parts, which on the whole are just opposite and is substantially equal to the outward forces acting on surfaces 42.

(It should be noted that the direction is not entirely opposite to those radially outwardly directed forces, since the direction is radial to the axis 11 because of the eccentricity E. That is, however, of little importance.) So a balance is achieved.

To reverse the direction of rotation of the rotor 12 only needs. the " To be connected to the bore 23 with the working medium, the bore 24 then serves as an outlet for the non-working medium. In In this case, the wells 31 receive working medium, and a compensation is achieved as described above.

When operated as a pump, the rotor 12 is assumed to be clockwise rotated with respect to Fig. 2, and the medium to be conveyed is generally under a slightly higher pressure than the ambient pressure the bore 24 carried out. A cylinder 6 A sucks in non-working medium during a non- ^ during the rotation from X to Y work cycle and pumps this out through the bore 23 during the further rotation from Y to X during one work cycle «

It should be noted in particular that the radially outwardly directed forces caused by the hydraulic medium in the cylinders 6 during the working cycles are hydraulically at least substantially completely and directly absorbed by the surfaces 42, while in the known star piston machines these forces are directly applied hydraulically to the Pistons are transferred, which in turn mechanically transfer them directly to the surfaces ». Q _09887n 533

When operating as a pump and rotating in the direction indicated above receive the depressions 31 working medium, so that a compensation, as described above for use as a motor, is obtained.

If the direction of rotation of the rotor 12 is counterclockwise with reference to FIG. In this case, the depressions 32 receive working medium, and there is a compensation _{y as} described above «.

Individual description of parts

In Fig. 5 there are suitable seals 17 for delimiting the depressions 14 and ring seals 18 of the piston-like parts are shown, each consisting of a Q-ring 1? A or, 18A and a ring 17B bzv. 18B with an L-shaped radial cross section. Bine Modified ring seal 18 (without O-Riiig) is together with pressure gradients and resultant shown in Figs. 8 &, while an alternative to seal 17 (without O-ring) is shown in Fig. 8B is.

The cylinder block transverse seals 36 can _; 6 and in this case each have a ring 36E with a square radial cross-section, an O-ring 36G and a ring 36F with a U-shaped radial cross-section * FIG. 7 shows an alternative with a ring 36H and O. Ring 36J, and the two FIGS. 6 and 7 also show the state in which the working medium is on the right and the weighting medium is on the left.

The cylinder block ring seals 33A and 33B are shaped as in Fig. 1 shown, be formed. The shown seal 33B consists of an annular shoulder 66 and a ring 67 against which the Cylinder block 4 presses. The seal 33A can have a similar »

009887/1523

however, be an adjustable arrangement comprising a ring 68 and a threaded ring 69 screwed onto the shaft 1 fulfills the same task as the ring shoulder 66. In the gap between the rings 68 and 69wir4 during assembly plastic Metal 65 is introduced and the ring 69 is screwed onto the shaft 1 so that the king 68 is pressed against the cylinder block 4 will. The use of plastic metal avoids the need for machining to close tolerances. .

A modified cylinder block ring seal shown in Fig. 9A has rings 71 and 72 which are arranged in a groove 73 in the cylinder block. Fig. To shows how one of these ring seals with a r transverse seal 36 meets. Pressure gradient and Resultant of these ring seals are shown in Figs. 9B and 9C,

Ball or roller bearings 74 can also be provided to to absorb external loads. QueMeals 54 in the storage areas 44 are preferably constructed similarly to those shown in FIG. 6, and an annular seal results from the interaction of Sides 49 of the rotor 12 ait shoulders 52 on the shaft 1 or through the ring seals 47, the rings 76, plastic metal 77 and threaded rings 78 have cylinder block ring seals similar to that described above with reference to FIG. 1.

Modifications

In the modifications described below are parts that the parts of the device shown in Figs. 1 to 10 essentially are the same, old denoted by the same one- or two-digit reference numbers - three-digit reference numbers, both of which last numbers in Figs. 1 to 10 and / or, in the case of Fig. 13 to 15 * used the last two in Figs. 11 and 12

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Numbers correspond to, on the other hand, designate parts of a different construction, but similar function.

The modification shown in Figs. 11 and 12 is constructed similarly and operates similarly to the device shown in Figs.

The main difference is that the eccentricity E thereby changed verden that the rotor 12 by means of bearings 179 in the Housing 181 is rotatable about axis 11 and devices for changing the relative position of the axis 3, about which the cylinder block 4 rotates, to the axis 11, i.e. the eccentricity E. are.

The device for changing the relative position of the axes exists in that the shaft 1 is composed of parts 102 and 108, of which the part 102, the cylindrical portion 2 and the part 108 has the cylindrical sections 8.

The shaft part 102 has parallel sides 182 and is displaceable in a guide 183 of similar shape in the housing 181. The shaft part 102 also has parallel sides 184 and is displaceable in similarly shaped guides 186 in the shaft parts 108. As a result of the engagement of the parallel sides 182 and 184 in guides 183 and 186, the shaft part 102 can be displaced vertically with respect to FIG. 11, ie the axis 3 can be displaced vertically while the axis 11 is immovable. As a result, the eccentricity can be changed ο Mechanical connections can be used to. to adjust and determine the relative disengagement of the axles, but it is advisable to do so as a precaution. channels 187 and 188 are planned, which open sicti wl Eamiiarn 189 and 191 . The eccentricity can be changed by feeding hydraulic medium under pressure into the quays 189 and 191, respectively

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The chambers 189 and 191 are sealed by the fact that the side 193 of the shaft part 108 and the side 194 of the shaft part 102 as well the side 196 of the shaft part 102 and in turn against the Page 199 of the cylinder block. abutting plate 197 and plates 109 with one side against the sides 128 of the Press shaft parts 108 and insert them from the other side of plastic metal 134 from rings 110 and against them screwed rings 129 are pressed.

As a result of the devices for changing the eccentricity, devices must be provided, whereby channels 426 and "/ 27 are permanently in communication with chambers 131 and 132. That will 12 achieved in that 102 depressions 146 are provided in the shaft part, each of which for all relative positions of the Axes 3 and 11 to each other with one of the channels 157 in the shaft part 108 is in connection. The device with the in Fig. 11 and The construction shown can be used as a motor or pump with variable Working capacity, and the rotor is provided with a shaft, which acts in the former case as an output shaft and in the latter case as a drive shaft.

The modification shown in FIGS. 13 to 15 is constructed similarly like the device shown in Figs. 1 to 10 and operates similarly like these.

However, the following main differences should be noted » ·.

The shape of the shaft 1 and the arrangement of the cylindrical sections 2 and 8;

Devices for changing the eccentricity; the arrangement of devices that enable the exercise of a

009887 / 1S23

essentially the same and on the whole opposite Force to the radially outwardly directed, during the work cycles cause forces acting on the tendon surfaces, and

the construction of the cylinder block.

In the device shown in FIGS. 13 to 15, there is VeIIe 1 consists of a first outer cylindrical part 202 on the Axis 3, the outer jacket of which is functionally equivalent to the cylindrical section 2, and a second inner part 208 »with a through cylindrical bore 251 along the axis 11, the circumference of which is functionally equivalent to the cylindrical section 8 is.

The rotor has a shaft 253 that rotates in the bore 251, and the circumference 244 of this shaft is functionally equivalent to the bearing surfaces 44.

A bore 248 through the part 202 mat parallel surfaces which form guides 283 for the part 208 provided with similar parallel surfaces 282, whereby the part 202 is vertically displaceable as shown in FIG. In this way, the relative position of the axes 3 and 11 and thus the eccentricity E can be changed. As mechanical connections can soaped provided \ m ISND to change the desired relative position of the axes to determine the in Fig. 11 and 12 apparatus. However, for this purpose, hydraulic medium under pressure is again preferably used, which can be pressed through channels 287 or 288 into chambers 289 or 291.

The arrangement of the devices "which" seed-host, around one essentially the same and, in the whole, eat-in-time force to *

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radially on the tendon surfaces during the work cycles outwardly directed forces su generate is substantially different from that shown in Fig. 1 to 4 or 11 and 12, mechanically but equivalent.

In this case, the dumbbell surface 244 of the shaft 253 has recesses 256, which correspond to the depressions 56, while

The part 208 has recesses 231 and 232, like the recesses 31 and 32, and channels 226 and 227 are provided with bores 223 and 223, respectively. 224 through the depressions 2H-6 in connection, which ensure that the connection is maintained for all relative positions of the μ axes 3 and 11 to one another. The effective area of each of the depressions 256 is the same as that of a cylinder, 6. These devices operate in an equivalent manner to the corresponding devices in FIGS. 1 to 4.

Bores 223 and 224 in part SOP extend into a Bushing 216, which can be formed in one piece with part 202, to establish fluid communication with chambers 221 and 222, and telescopic tubes 264 are provided to allow the Medium can flow to and from Xamners 221 and 222 «^

Between the socket 216 and the housing 281 is an Oldhara coupling 257 is provided so that the part 202 cannot rotate.

The axial ends of the chambers 289 and 289 lying on the left in FIG 291 are tightly closed by a plate 209, which with the one or the other of the two parts 202 and 208. can be firmly connected, while the axial ends lying on the right in FIG. 13 the chambers 289 and 231 are tightly closed by the bushing 216 which may be attached to part 202 or part 208, but preferably with the Qldham coupling 257 in mind

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Part 202 is attached or formed integrally therewith.

The cylinder block 204 consists of a number of parts, viz Ring 258, cylinders 206 and two cylinder connecting rings 259.

The ring 258 is provided with through bores 238, which the
Bores 38 correspond, and recesses 237, which correspond to the recesses 37, provided. The effective area of each of the recesses 237 is equal to that of a cylinder 206, which is the
has the same effect as described with reference to FIGS.

The radially outer surface of the ring 258 is designed as a spherical surface and the radially inner ends of the cylinders 206 are shaped accordingly. The cylinders 206 have shoulders 261 with outer surfaces also spherical, and the cylinder connecting rings 259 together form seats 262 which correspond to the same spherical surface "The cylinder connecting rings' 259 are connected to one another by bolts," according to Malten
Cylinder 206 in their relative »position sueinand @ r. At the de? radially outer surface of the ring 2 ^ 8 siM äsiscliüAge 263 provided to the rotation exerts cylinöes? and ZyliffiöeweÄiadmgsi'iisge on this surface to foegreaseuu

This construction of the Sj lungstecfeaiscfeoi © rttedea

204 is off

The swisefee seal "gives way" because 202 strikes wad de "ring

SS? I:

At the so f

Fig. 1 to 4 »11 and 12 dl ©

g 1st mm

piston-like part 7 is essentially the same, but somewhat is smaller than that of a cylinder 206 and so that of the hydraulic Medium in the cylinders during the work cycles caused radially outward forces hydraulically at least be received substantially entirely and substantially directly by the surfaces 42 of the rotor.

In the devices described above, the axes 3 and 11 are non-rotating while the cylinder blocks and rotors revolve around them rotate * It should be noted, however, that the invention is based on the relative Rotation extends and so includes constructions in which the shaft rotates about axis 3 or about axis 11, as, for example, in the device of FIGS. 1 to 4 »

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Claims (18)

Claims Hydraulic ' , ■ / Machine for use as a radial rotor or radial pump with a cylinder block rotatable relative to a first axis, parts reciprocating in or on the cylinders, and a around a second axis, which is parallel to the first axis and in one Distance from it runs, relatively rotatable rotor with inner surfaces of the circular chord, against which the radially outer ends of the reciprocating parts press displaceably and sealingly, marked through a hole through each of the reciprocating parts, create a medium connection between the circular tendon and the cylinders
inner surfaces / manufacture in such a way that radially outwardly directed forces generated by the hydraulic medium in the cylinders during work cycles are absorbed hydraulically at least substantially completely and essentially directly from the inner surfaces of the circular chord. 2. Motor or pump according to claim 1, characterized in that further channels are provided for the medium, velche the medium Bring in connection with the rotor in such a way that it exerts a force on the rotor during operation which at least during operation a considerable part of the work cycles essentially the same and generally opposite to the radially outwardly directed, through the flow medium in the cylinders on the inner surfaces of the circular chord acting forces is. 3 · Motor or pump according to claim 1 or 2, characterized in that the motor or the pismp have a bearing / having a first cylindrical section mxi of the first axis and a second cylindrical section on the second axis, and that in operation the Cylinder block relatively »around 003887 / 1S23 -as- 2037A29 first section and the rotor in operation relative to the second Rotate section. 4. Motor or pump according to claim 2 and 3, characterized in that that the second channel for the medium has a passage channel in the camp has, which is in operation with the working medium in connection and is open to the periphery of the second section, whereby Ar-. working medium exerts a force on the rotor that is essentially equal and on the whole opposite to that during at least a considerable part of the work cycles by the hydraulic Medium in the cylinders exerted on the inner tendons, | forces directed radially outwards is 5. Motor or pump according to claim % ^ d 3 »characterized in that the second passage channel has two groups of passage openings in the bearing / which open diametrically opposite to each other to the circumference of the two section feia and in operation each with work or NlchtarbeitBrnedlum or «Not * -. Put working or working medium in connection »by means of which the operation both as a pump and as a motor is possible with every direction of relative rotation and under all such circumstances one or the other of the passage openings brings the working medium into connection with the rotor so that it moves onto it exerts a force which is substantially equal to and generally opposite to the radially outwardly directed forces exerted on the rotor surfaces by the hydraulic medium in the cylinders during at least a substantial part of the work strokes. 6. Motor or pump according to claim 4 or 5 » characterized in that the rotor« is stranded with recesses, the sun circumference 009887/1523 ~ 24 " of the second section are open and such effective work surfaces have that in operation on the rotor by interacting with the opening of the second D ^ ctilaßkanals to the circumference of the second section a force is exerted »which substantially during at least a substantial part of the work cycles equal and on the whole opposite south through the hydraulic Medium in the cylinders acting on the Rptorflachen after external forces. 7. Motor or pump according to claim 6, characterized in that that the wells are annular over angular ranges of the second Sections extend so that they are in operation during at least one A significant part of the work cycles cooperate with the opening of the second passage channel to the periphery of the second section. 8. Motor or pump according to one of the preceding claims, characterized in that the effective working surface of the cylinder block, acts on the working medium during work cycles radially inward and radially outward, essentially the same is. 9. Motor or pump according to claim 3, or one of the claims 4 to 8 in conjunction with claim 3, characterized in that the second cylindrical section is arranged at an axial "distance from the first cylindrical section" 10. Motor or pump according to Aasprmcl 3 to 8 in connection with Aaspwieli 3 ₉ äaetaeii gutamsiaietaet that / the second cylindrical Afectaifi awei zylta & diigte parts at axially opposite booths »ö @ s first syliastedsetea Absctoitts, on which the red is relatively 11. Motor or pump according to claim 3 or one of the claims 4 to. 8 in conjunction with claim 3 _t characterized in that the cylindrical portion to V aweite a cylindrical bore / eist in which a connected to the rotor shaft is relatively rotatable. 12. Motor odcü ¹ pump according to one of the preceding claims, characterized by devices for changing the distance between the first and second axis « 13. Motor or pump according to claim 3 or one of claims 4 up to 8 in connection with claim 3, characterized by a shaft with a cylindrical outer surface lying between its ends, which forms the first cylindrical section, and two cylindrical parts that are non-rotatable on the shaft axially opposite ends to the first cylindrical portion and each having an outer cylindrical surface have, which together form the second cylindrical portion, the shaft and the two cylindrical parts for Change in the distance between the axes relative to one another in an imaginary plane passing through the axes in a direction diametrically opposite are movable to the axes 14. Motor or pump according to claim 13, characterized by a Chamber which is at least partially bounded by the shaft and one of the two cylindrical parts and in. The pressure medium. can be introduced in order to exert a force between the shaft and one of the two cylindrical parts, which the in Claim 13 causes specified relative movement. 15 * motor or pump according to claim 13, characterized by two Groups of chambers at least partially through the shaft and 009887/1523 the two, in the plane diametrically arranged cylindrical parts are limited, and autdi channels for the medium, causing this under pressure in one or the other of the Both groups are led by Jcannjna the ia claim 13 stated To show relative movement " 16. Motor or pump after
4 gekemssiehraet to 8 in conjunction with Äasprucfe 3 ", represented by a first shaft having a cylindrical AnBeafläcfee _e which CTEA first cylindrical Abschiaitt ₉ forms" ad © iiaea lotoAalter sweiten having a cylindrical bore "ii © de» cylindrical portion and a second "dayia contains relatively rotatable shaft connected to the rotor, which at least in part is not drcMbas »if necessary realtea in the first shaft, wöfe @ i di @ e ^ ste shaft β and the rotor holder relative zn eimasekn "sms ¥ <^ äsidiOiif prior axes in a direction äiaseteal on ä @ a in a movable by the axes geteafea gdiaeJateii Bhmi®. 17. Motor or pump nac & Aiispratglj, t§ _e g © & @ Mi ^ © isteiet € nrch a chamber which is at least partially limited diwcli aim tis-sf © shaft mid the rotor holder isid ia welete Mddii «iaate ^ Drsek can be initiated mmd "to zwiseße" of the first shaft to the lotorhalter a teaft exert ^ which causes the specified in -laspFixeM 16 relative movement " 18. Motor or pump according to Aaspraefe 16 ₀ gekesinzeictöaet two chambers, the smallest & s partially oimek ä ± Q «s> ste Velle and attached to the rotor holder limited nai in the / Elbeae äiassetval ia distance from each other are ₀ mmd thru limülm & zsAElms dvsck the medium under bridge in which one © der aafe ⁵ © ä & Kami ^ pa can be directed to the in claim 16
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