DE1453675A1 - Power transmission device - Google Patents

Description

The invention relates to power transmission devices and particularly orbiting pressure energy conversion devices of high speed. "

Such rotating fluid energy conversion devices have a rotatably mounted drive element, a number of cylinders in which pistons are reciprocable and motion conversion means which Connect the piston and the drive element to one another. ivi with one end of each cylinder becomes consecutive an inlet and an outlet in communication. V / erm such a provision. thereby operated as a motor

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is that the inlet pressure medium is supplied, the motion conversion means change the reciprocating Movement of the piston into a rotary movement of the drive element. If such a device is operated as a pump in that the drive element to Rotation is driven, change the motion conversion means the rotary movement of the drive element in a reciprocating movement of the piston to a Pump fluid from inlet to outlet.

Ylewi such a device either as a motor or as ^? Pump is operated, the pressure inside the housing corresponds to the gate direction, ie the pressure at the other ends of the cylinders, usually the tank or container pressure. This leads to unbalanced and high bearing loads in the door direction and, as a result of the pressures of the fluid on the ends of the pistons in the cylinders, there is leakage of the fluid at the -; Pistons past and take place at the interface between the cylinder block and control plate. This leakage leads '- ..' ■■ not only to a reduced degree of efficiency, but also to. Heat Loss "Such loss" becomes quite critical in the applications where. heat dissipation is a problem "for example" when operating missiles and other spacecraft at high altitudes.

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When such a pressure energy converting device is used as a Motor used with a four-way servovalve conventional type, the high pressures require both on the inlet as well as on the outlet of the engine, a high breakaway torque to initiate the Operation of the engine. In addition, very high forces are exerted on the motor, which causes wear on the surface the cylinder and chafing of the piston walls. The control plate on which the cylinders cylinder block forming is also exposed to excessive wear.

Another problem encountered with such raw energy conversion devices is present, is that if it is not practical from a constructive point of view is, the center of the bearing of the cylinder block in the plane of the joints of the connecting rods or To arrange the handlebars of the pistons, tilting forces or moments occur in diametrical planes, v / which the inlet and Cut exhaust ports. These tilting moments tend to out of alignment with the cylinder block To move the control plate, which leads to a pressure loss, heat and a consequent reduced efficiency leads.

In addition, when pressure energy conversion devices

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lines of the type mentioned are operated at high speeds either as motors or pumps that Centrifugal force considerable tilting forces or moments in a diametrical plane between the inlet and outlet channels. It is therefore advantageous to eliminate these forces in order to minimize leakage and heat loss and ensure more efficient operation.

An object of the invention is to provide a rotary pressure energy conversion device in which the the aforementioned difficulties have been eliminated, the inclination ' to compensate for the bearing load, which simplifies the bearing construction, and in which the Leakage is decreased, which puts the heat problems on one To be reduced to a minimum.

Another object of the invention is to provide a pressure energy conversion device which is used in the ' Use as a motor has a low breakaway torque, in Connection with a four-way servo valve.

Another object of the invention is to provide a pressure energy conversion device that is equipped with a requires less space and is less dedicated can be produced ».

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Another aim of the invention is creation a device of the type mentioned, which has an improved efficiency and in which the lowest possible Change in torque takes place.

Another object of the invention is to provide one Pressure energy conversion device in which the overturning moments as a result of the arrangement of the center of the bearing outside the plane of the joints of the handlebars to the pistons are essentially off.

Another object of the invention is to provide a pressure energy conversion device, in which the overturning moments under the effect of the leaning force essentially are turned off.

According to the invention - it is therefore provided that the housing the rotating pressure energy converting device with is loaded at a pressure intermediate between the inlet and outlet pressures at which the device is operated will. This pressure is preferably substantially equal to half the sum of the inlet and outlet pressures. According to the invention, this pressure load enables the Housing a better balance on the parts of the device - and increases the forces on the main bearing substantially on. By exerting a force on the floors of the

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Piston, the resulting force on the piston on the high pressure side of the gate direction is reduced and on the Bottoms of the pistons exerted a force on the low pressure side. If the pressure load has the preferred level, namely half the sum of the inlet pressure and the outlet pressure corresponds, the forces on one side of the cylinder block are equal and opposite to the Forces on the other side of the cylinder bioekes. This enables a device to be built more compactly Design and lower weight, because of the bearing loads are lower. In addition, significantly less leakage can be achieved when the device is used as a motor becomes ,, only a small breakaway or starting force is required. The device has a higher efficiency than the conventional devices and a more uniform one Torque.

According to the invention, to compensate for the tilting moment, caused by the placement of the center of the bearing outside the plane of the joint of the handlebars to the pistons are provided, the device in addition to the pressure load with a counteracting moment, which is caused by a change the base of the cylinder block or, if necessary, by changing the size of the inlet and exhaust ports is introduced into the cylinder block, whereby the contact area of the cylinder bio with the

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Control plate is changed.

In addition, the pressure load on the housing compensates for centrifugal forces on the various parts. To the Compensation for the torque that can be generated by centrifugal forces at a given speed is the Arrangement made so that the cylinder block is loaded to the control plate. This can be achieved by that cavities or pillows, in one or more places be provided between the cylinder block and the control plate and a high or low pressure on the Kiesen is exerted to the cylinder block in the right sighting for the compensation of the centrifugal moment to press «

The invention relates generally to fluid pumps or motors of the rotating axial piston type. hereinafter the invention for a fluid pump described, however, when the term "pump" is used in the following, it is also a fluid motor to understand.

Bs has already been proposed to change the performance of a device of the type mentioned in that a movable valve or control plate with an inlet and an outlet opening is used, which on-

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consecutively with one of the ends of each cylinder in Connection comes »by twisting the valve resp. Control plate, the phase relationship between the basket stroke and the interacting control openings can be changed

Both fixed displacement pumps and pumps with variable displacement of the type described there is always the problem of providing sufficient fluid to the inlet to ensure effective operation. Rotating the control plate on a variable displacement pump increases the size of the Inlet opening changed, resulting in considerable loss of heat and friction, * -

An object of the invention is to provide an improved orbiting pressure energy conversion device, in which the problem of the supply of fluid to the Inlet is traced back to the lowest possible i <xass.

Another object of the invention is to provide an improved fluid energy conversion device with variable displacement, in which the problem of adequate supply of fluid to the inlet is minimized.

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According to the invention, the cylinder openings are also with Running a substantially constant diameter over its full length, the housing is the circumferential Pressure converting device is loaded with a pressure which is between the inlet and outlet pressures which the device is operated, and preferably, substantially equal to half the sum of the inlet and outlet Outlet pressures are, and are voids adjacent to the inlet and outlet ports of the control plate between this and the cylinder block provided, the the Inlet opening adjacent cavity is connected to the outlet opening, while that of the outlet opening adjacent Cavity is connected to the inlet port, so that the cylinder block is held against the control plate. Through this it is achieved that ax large opening in the end of each cylinder adjacent to the control plate a slight Forms access of the fluid to the inlet. In addition, in the variable displacement device, in which the control plate is rotated to the area ratio to change between the piston stroke and the cooperating control ports, by a slight Movement of the movable control plate exposed a fairly large area of the cylinder, reducing the inlet pressure is made less critical and the throttling forces on the fluid flowing to the cylinders be reduced to a minimum.

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In the accompanying drawings show no

Fig * 1 is a schematic flow diagram of a engine according to the invention;

2 shows a partial view in section and in a schematic representation of a bridge control valve;

ig. 3 is a view, partly in section, of an invention non-volatile fluid pressure energy conversion device;

FIG. 4 is a partial view in section of part of FIG

door direction shown in Fig. 3, on an enlarged scale;

5 is a schematic flow diagram of a another embodiment of the invention;

FIG. 6 is a partial view in section of part of FIG

in Fig. 3 shown device in an enlarged. Scale, with the section following the line 6-6 is guided in Fig. 7;

7 - a view of the cylinder block in section along line 7-7 in Fig. 6;

FIG. 8 is a view of the control plate along the line 8-8 in FIG. 6; ■

Fig. 9 is a view of a portion of the cylinder bioclave shown in Fig. 7;

10 is a partial view in section along the line 10-10 in FIG. 9;
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11 is a partially schematic sectional view similar to FIG. 6 along the line 11-11 in FIG Fig. 8, which shows the tilting moments in the device with the bearing element in a certain Position represents;

FIG. 12 is a view similar to FIG. 11, with the bearing is in a different position;

Fig. 13 is a partially schematic sectional view taken along line 13-13 in Fig. 8 showing the. Represents centrifugal moment on the device;

Figure 14 is a view similar to Figure 13 taken along line 14-14 in Figure 8;

Fig. 15 is a view, partly in longitudinal section, of a fluid pressure energy conversion device according to the invention;

FIG. 16 is a partial view in section along the line 16-16 in FIG. 1; FIG.

FIG. 17 is a view in section along line 17-17 in FIG. 15; FIG.

Fig. 18 is a view in section along the line 18-18 in Fig. 15 showing one side of the Control plate shows;

-Fig. 19 is a partial view in section along line 19-19 in FIG. 15 showing the other side the oteuerplatte shows;

FIG. 20 shows a partial view in section along the line 20-20 in FIG. 19?

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21 is a partial view in section along the line 21-21 in Pig. 15th

Referring to Figs. 3 and 6, there is a rotary fluid pressure energy conversion device according to the present invention 10, a housing 11 and a rotatable cylinder block 12 has, in which the latter a number of cylinders 13 are provided, in which pistons 14 can be reciprocated are arranged. Connecting rods or links 15 have a universal joint connection at one end with the pistons 14 and are connected at their other ends to a drive element 16 by universal joints 17. The drive element 16 is on a drive element ■

18 attached. A double cardan universal joint extends between the drive member 18 and the cylinder block for proper angular alignment therebetween to maintain both parts.

The cylinder block 12 rests against a control plate 19, which is provided with two openings 20, 21, which are consecutive with the ends of the cylinders 13 (Fig. 8) in Be connected .. When the pressure energy conversion device 10 is operated as a pump, the drive element 18 is driven to rotate and the Openings 20, 21 with a liquid supply and a device connected, which is to be supplied with liquid. By rotating the drive element 18

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the piston 14 reciprocates and is fluid through the inlet opening 20 is sucked in and displaced through the outlet opening 21. When the device 10 is operated as a motor is, pressure medium is supplied to one opening 20 or 21 and through the other opening 20 or 21 to exit brought. This drives the piston 14, which in turn rotates the drive element 18. The direction of rotation of the engine depends on which of the openings 20, 21 form the inlet. The arrangement described so far is conventional.

According to the invention, the chamber, which is through the housing 11 is bounded adjacent those ends of the cylinders 13 which are furthest from the inlet and outlet ends remote, filled with hydraulic fluid and pressurized, which is preferably essentially half the sum of the pressures at the openings 20, 21 corresponds.

As shown in FIG. 1, when the pressure energy conversion device is operated as a motor, fluid via a line L, a / ierweg servo valve 30 is supplied and returned via a line Lp. The Yierwege servo valve has two channels, which can optionally be connected to the inlet line L-. and the outlet pipe Lp thereby be connected that the control element in the valve, for example

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wise a piston valve, is set so that the ^ inlet pressure and the outlet pressure either in the channels or lines 31, 32 v / becomes ineffective. Channel 31 is with the one opening 20 or 21 of the pressure energy conversion device 10 connected, while the channel 32 is connected to the other of the two openings. In this way can the motor 10 in 'one or the other rotation

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operated depending on the position of the control element in the four-way valve 30.

According to the invention, pressure is applied to the inside of the chamber 35 located hydraulic work equipment exercised. As shown in FIG. 1, this is done with the aid of a pressure control valve 35, the lines 36, 37 with the channels 31 and 32 is connected and serves to maintain a pressure which is substantially equal to half the sum of the pressures in the lines 31, 32, to the chamber 25 via a channel 38

exercise. .

The pressure control valve can be of any suitable type be, with which essentially half the sum of the pressures can be achieved. For example, as in tfig. 2 shown, the valve has a body 40 with channels 41,42 which are connected to lines 36 and 37. The channels 41, 42 extend to connecting chambers 43, 44. The piston 45 has a stepped part 46 on, which extends into the chamber 43, and a

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enlarged part 47 which extends into the chamber 44. The pressure in the channel 41 acts on the surface 50 at the end of the stepped section 46, while the pressure in the channel 42 acts on the surface 49 at one end of the enlarged section 47. The area 49 'on which the pressure from the channel 42 is effective is related to the surface 50 on which the pressure from the channel 41 is effective, * and to the surface 51 at the free end of the widened section 47, that the outlet pressure through the outlet channel 52, which is in communication with the line 38, is equal to half the sum of the pressures in the channels 41, 42. This is achieved in that the area 49 becomes equal to the area 50 and each of these areas is in turn half the size of the area 51. Pressure control valves of this type are known ^{per se, but other types of valves or the like can also be used for} can be used to achieve a similar result.

Since on both sides of the cylinder block 12 essentially a balance is achieved, the exertion of a small force is expedient, which tends to the cylinder block 12 to keep in contact with the oteuerplatte 19. This can be achieved by removing a spring from the * common in rotating pressure energy converters used type. -. ·. . ■

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As Fig. 8 shows, a preferred method is through which the cylinder block 12 against the control plate 19 can be held in that a light pressure on a cutout or cushion surface 57, 58 in the control plate 19 is exerted below the cylinder block 12, which causes sufficient pressure asymmetry to to keep the cylinder block 12 in contact with the control plate 19. Λ / ie in Pig. 1, this is done with the help of Lines 55, 56 reached, which are connected to the lines 31, 32 and to the cushion 571 58 via a Line 59 extend. In the lines 55, 56 one-way or check valves 60, 61 are provided so that ' there is only a low pressure in the cushions 57, 58, while the high pressure tends to do the job To close the check valve. The cushions 57 »58 are provided in the control plate adjacent the cylinder block and serve to form areas of lower pressure, so that the higher pressure on the cylinder block 12 loaded this in contact with the control plate.

When the motor shown in Fig. 1 by an operation of the four-way valve 30 is put into operation, the Chamber within the engine adjacent to the other ends of the cylinders, which is indicated in Figures 3 and 6 by 25, put under a pressure that is essentially the same is half the sum of the inlet and outlet pressures. By

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this arrangement essentially balances the forces acting on the cylinder block 12. Through this becomes the use of bearings of lighter weight and the engine can be built separately.

Since the same in the neutral position of the four-way valve Pressures are exerted on both channels 20, 21 of the motor, and since the pressure load on the housing is equal to that half the sum of the two pressures, the breakout force which is required to turn the motor on with a slight movement of the servo valve in one way or the other To put the Hearing in operation, significantly reduced, This can be clearly seen from Table I below.

Table I.

Testing conventional engine with

Motor pressure equalization

Weight (dry) 0.907 feg 0.771 kg

Hand torque with Q kg / cm

at both openings 0.576 cmkg 0.829 omkg

Hand torque at 105kg / cm

at both openings 10.368 cmkg 1.440 cmkg

Breakaway pressure difference η ■ 9

(clockwise) 37.80 kg / cm 5.11 kg / cm

Operating pressure difference 2 2

(clockwise) 26.04 kg / cm 3.08 kg / cm

Breakaway pressure difference 2 2

(counterclockwise) 39.20 kg / cm 4.90 kg / cm

Operating pressure difference q 2

(clockwise) 25.41 kg / cm 2.94 kg / cm

Tightening torque

Maximum value 48.1536 cmkg 49.3056 cmkg

Minimum value 45.8496 cmkg 47.6928 cmkg

Mean 46.73664cmkg 48.32640cmkg,

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From the preceding ^ table it follows that not only the breakaway pressure difference is significantly reduced, d. H. the · pressure required to start the motor ■ is required, but also a higher torque by the motor according to the invention in contrast to a Conventional engine design having pistons and cylinders of substantially the same size is achieved.

It was also found that in üervoventilbetrieb the motor of the invention has higher efficiency and effective torque over a full range of pressure differences of 24.50 to 211 kg / cm between has the inlet and outlet ports. If-the pressure energy converting device is used as a pump, the four-way valve is of course omitted and has .,the. Flow diagram essentially that in! Fig. 5 shown. Arrangement on. Ba the pump only in one If the direction is turned, only line 56 is used. Otherwise the cycle is essentially the same as shown in]? ig .. '1.

If a device with the in H ¹ Ig. 5 is operated by the pump, the advantages of a practical balance of forces are achieved as in the case of engine operation. In this way, the bearing loads are eliminated and a more compact design and a device of much lighter weight is made possible.

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If the bearing is not in the same plane as the plane which connects the joints of the connecting rods with the pistons, the forces have a tendency to produce tilting moments in the plane Χ-λ which intersect the inlet and outlet. '.Like in Pig. 11 have shown when the bearing 30 is with. its center E is above plane B, which connects the joints of the connecting rods with the pistons, the tilting moments in the plane λ-λ on the connecting rods tend to cause a torque in the counter-clockwise direction. This torque can be compensated for by generating a clockwise torque in the plane λ-Χ by either reducing the base area F of the cylinder block or by reducing the radial xireite G of the kidney-shaped inlet and outlet slots 20, 21 in the control plate 19 (Fig 7, 9) is enlarged. The üeite of the slots 20, 21 tapers, as in -e ⁿ ig. 10 shown.

Similarly, if the bearing at H is below level B, as in i ^A ig. 12, the tilting moments in plane XX are directed in a clockwise direction and an equal moment can be generated in that the base area F is increased or the width G of the kidney-shaped slot C is reduced.

The centrifugal moment that occurs at high speeds in the plane

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occurs which intersects the inlet and outlet, is best from the partially schematic representation in ^ 'ig. 13 understandable, which is a sectional view after the line 13-13 in Pig. 8 is. When the camp with its center at A above level B, which is the joints of the connecting rods to the pistons connects, then the forces generated by the centrifugal force tend to produce a torque in the counter-clockwise direction to evoke. This can be overridden by providing a pillow as shown at C, and Inlet pressure is directed to the cushion so that the right part of the cylinder block is pressed towards the control plate. ' Another cushion D can be provided on the left side of the cylinder block and this cushion higher up Pressure can be supplied to load the cylinder block further clockwise with the aim of reducing the centrifugal torque counter-balance. In one level, which is the inlet and. Outlet canals after line 14-14 in Fig. 8 intersects, a similar torque is applied generated the section shown in Fig. 14, which in similar ■ Vfeise can be offset by cushions C and D. the Channels to the pillows are not shown, but can can easily be provided in the control plate 19 extending to the inlet or outlet.

It follows from this that both the centrifugal overturning moments

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and the overturning moments due to the displacement of the bearing out of the plane that connects the joints of the connecting rods to the pistons, duroh a combination from housing pressure load and regulation of the forces between the cylinder block and the control plate can be balanced »resulting in a more efficient pressure energy conversion device leads.

In Fig. 15 is a fluid pressure energy conversion device 110, which includes a housing 11 and a rotatable cylinder block 112 "The block 112 is with multiple circumferentially from each other in Spaced cylinders 113 of constant diameter Provided over their full length, in soft pistons 114 are arranged reciprocally * connecting rods 115 are articulated to pistons 114 at one end and are at their other end with a drive element 116 by means of a universal joint 117 connected. The drive element 116 is in turn firmly connected to a drive element 118. Between the Aiittriebselement 118 and the cylinder block 112 is a Double cardan universal joint 119 is provided to hold the two parts in the correct angular alignment.

The cylinder block 112 has a control surface 120,

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the aii of the surface 121 of a control plate 122 rests, the is arranged in a head 12-3 which is attached to the housing 111 is fastened by screws 124 '"

The Öteuerplatte 122 is on a rotatable BlociE 125 iü Any suitable way, for example by means of fl uid pins attached} so that their angular position with respect to the housing can be changed. The movement'der Control plate for changing the displacement of the pressure energy conversion device can be done in a known manner with the help of a handle 126 or hydraulically, for example As in the patent (patent application V 17 872 'XiI 47h from 13 * Jan * 1960) described *

The device is provided with a bolt 127 * which is attached to the head 125 and extends through the control plate 122 and also serves to rotate the cylinder block 112 *

As can be seen in FIG. 16, the block 125 is provided with an arcuate or kidney-shaped inlet opening 130 as well as with an arcuate or kidney-shaped outlet opening 131 is provided * Channels 132, 133 connect the openings 130, 131 with one Bore 134 in which a pressure control valve, for example, of the type shown in Mg »2, which in turn serves to supply the hydraulic fluid in the ·

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Cavity 135 of the housing surrounding the cylinder block 112 Apply pressure. The pressure supplied is in the range between the oil inlet and outlet pressures and is substantial equal to half the sum of the inlet and outlet pressures.

In FIGS. 18 and 19, the control plate 122 is kidney-shaped -Inlet and outlet ports 136, 137, which with the Linlaß and the outlet 130, 131 in ülock 125 cooperate to the cylinders 113 in the cylinder block 112 to supply or to divert fluid from this. By rotating the control plate 122, the phase relationship can be achieved between the cylinder block and the control plate.

As shown in FIG. 18, the control plate 122 is with an arc-shaped groove 138 in aer surface 121 adjacent the inlet port 136 and an arcuate groove 139 in the surface 121 adjacent the outlet port, üin channel 140 connects the iiut 138 with the outlet opening 137, which has a bore 141 which extends from the bottom of the groove 138 to the opposite surface 142 of the control plate extends, while a connecting groove 143 extends from the bore 141 along the surface 142 to the outlet port 137 extends. Similarly, the groove 139 with the inlet opening 136 is through a channel

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connected, which has a bore 145 extending from the bottom of the groove to the opposite surface 142 of the Control plate extends. A connecting groove 146 extends from the bore 145 along the surface 142 to the inlet opening 136.

This Vifeise is carried out as a result of the inlet pressure the hydraulic pressure in the groove 138 exerted a force which tends to pull the cylinder block 112 from the To push away inlet 136, and is due to the inlet pressure by the hydraulic pressure in the groove 139 exerted a reduced force tending to pull the cylinder block towards the control plate. this is best shown in FIG. 15, from which it can be seen is that the pressure exerted in cavity 135, what pressure equal to half the sum of entry and exit - pressure is, a force on the cylinder block and simultaneously generated along the circumference of the cylinder block, which tends to press the cylinder block against the control plate. The force of the outlet pressure in the However, the outlet side of the cylinder block is larger and tends to have an unbalanced upward movement cause «when the inlet pressure is adjacent to the outlet side of the cylinder block and the outlet pressure becomes effective adjacent to the inlet side of the cylinder block, a torque is generated which tends to

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the unbalanced force of the outlet pressure in to counteract the outlet ends of the cylinders.

An additional compensation or an additional hold down can be adjacent by radial grooves 147, 148 the ends of the groove 138 and grooves 149, 150 adjacent the Achieve ends of the groove 139.

To compensate for additional torques, which either as a result of unbalanced forces that are conditioned by operation, or, for example, by The centrifugal force caused, hold-down cushions can be provided in the surface 121 of the riteuer plate to which hydraulic fluid is supplied. So can channels 151, 152 in the control plate with the outlet opening 137 and the surface 121 in connection stand to hydraulic fluid through an annular groove 153 in face 120 of the cylinder block to feed. This in turn can reach the surface of the cylinder block through openings 153, 154.

Patent claims:

BAD ORiQlNAL. 909885/0335

Claims (1)

-.26 - Claims 1. Rotary fluid pressure energy conversion device for a hydraulic power transmission arrangement, characterized by a housing with a number Cylinder, pistons can be moved back and forth in multiple pairs, a rotatable drive element and motion conversion elements, which connect the reciprocating pistons to the rotatable drive element, wherein the device has an inlet and an outlet, the sequential with one end of each cylinder come into connection, means which delimit a chamber adjacent to the other ends of the cylinders, and means connected to the inlet and the outlet and are in communication with the mentioned chamber for hydraulic fluid in . the mentioned chamber to exert a pressure, the size of which in the range between the pressure at the inlet and the Pressure at the outlet. 2. .Device according to claim 1, characterized in that that the latter means pressurize the hydraulic fluid in the mentioned chamber exercise the size of which is substantially equal to half that Sum of the pressure at the inlet and the pressure at the outlet is" 909885/033 3. Device according to claims 1 and 2, characterized in that the cylinders are formed in a cylinder block and an oteuerplatte is provided which rests against the end of the cylinder block and has an inlet and an outlet opening. 4 · Device according to claim 3, characterized by Means which limit spaces between the cylinder block and the control plate, which trees with the inlet are in communication to generate a pressure difference by which the cylinder block against the Control plate is printed. 5. Device according to claims 1 to 3 »with a Control plate, characterized in that the cylinders form part of a single cylinder block and at least one cushion defined by a cavity between the cylinder block and the control plate is provided, as well as a channel for the supply of pressurized fluid to the cushion are. 6. Apparatus according to claim 5, characterized by that the area of the contact surface of the cylinder block with the oteuerplatte and the radial width of the inlet and ^ outlet channels in the oteuerplatte so to each other 909885/0335 'BAD OHKIlHAL stand in the ratio * that the overturning moment ;, that through the relocation of the camp out of the common level is conditioned * is compensated., - 7. The device according to claim 3, characterized by means for the supply of forces to the cylinder block * to load it against the control plate » 8. Device according to claims 1 to 7, characterized by a four-way servo valve having an inlet port and an outlet port, the Inlet opening is in communication with a pressure medium source, the four-way valve is provided with two channels connected to said inlet and outlet ports, the pressure energy converting device is connected with its inlet and outlet with the channels of the servo valve. 9. Device according to claims 1 to 8, characterized in that each cylinder has a bore one that is essentially constant over its full length Has diameter. ■ 10. Device according to claims 3 to 9, -marked by means defining a cavity between the cylinder block and each of the inlet and outlet ports 903885/0335 limit the control panel, and; Means that the Outlet »it connect the cavity adjacent to the inlet opening and means connecting the inlet to the aforementioned Connect the cavity adjacent to the outlet opening » 11. Device according to claims 3 to 9, characterized by means which have a cavity in the control plate between this and the ZyI in α erb look; limit ¹ · ¹ » ¹¹¹¹ Ct mean _% connecting the last-mentioned cavity with the outlet. 12. The device according to claim 11, characterized in that that the cavities with the inlet opening or with the outlet opening connecting means are formed by channels in the control plate. 15. Device according to claims 3 to 9, characterized by an arcuate one. Mut in the area of the control plate '!, Enachbart the cylinder block and each adjacent to the inlet and outlet ports and a first channel ,, ± 13 _»r dteuerplatte of which the outlet opening in the latter with the arcuate groove adjacent the connecting irinlaßöffnung, as well as a second kajasal in the control plate _r which adjoins the inlet opening in the other with the arched hat S 0 9 8 a 5 / ® 3 3 5. ^ß AD • - ■ 50.- the outlet opening in the control plate connects " 14. Apparatus according to claim. f3> marked by this, that each of the channels mentioned has a courage in the opposite Has surface of the control plate, which with an opening; is in communication in a bore, which extends aurch the control plate and with the last mentioned hat in the arched lutln. Yer- - there is a bond » Method for operating a hydraulic power transmission arrangement with a rotating fluid pressure energy conversion device comprising a housing having a plurality of cylinders into which pistons extend. and moveable are * a rotatable drive element and motion _{conversion elements i:} which connect the reciprocating pistons to the rotatable drive element, the aforesaid conversion device having an inlet and an outlet: P which is connected in succession to the one of each of the Cylinder in ■ connection; the housing delimits a chamber adjacent the other ends of the cylinders, characterized in that; hydraulic fluid is supplied from the inlet of the chamber mentioned at a pressure whose size is in the range between the pressure at the inlet and the pressure at the outlet. '■' - ■ ■ ORIGINAL BATHROOM 16. The method according to claim 15, characterized in that the pressure in said chamber is substantially equal to half the sum of the pressure at the inlet and the Pressure at the outlet. 17 · Procedure for balancing the centrifugal tilting moments in a high-speed pressure energy conversion device, comprising a rotatable drive element, a cylinder block rotatably mounted in the housing with several axially arranged cylinders, a bearing for the rotatable mounting of the cylinder block in the housing, pistons reciprocable in said cylinders and motion converting elements which the reciprocating piston connect to the rotatable drive element and through to the piston articulated connecting rods are formed, which are located in a substantially common level, a control plate arranged in the housing having an inlet and an outlet which are consecutive communicating with one end of each of the cylinders with the housing adjacent the other ends the cylinder defines a chamber, characterized in that a pressure on the hydraulic fluid is exerted in the mentioned chamber, the size in the range between the inlet pressure and the outlet pressure lies and between the cylinder block and the 9 0 9 8 8 5 / Q 3 3 B BAD ORaSlNAL Control plate. Area, provided wild, the fluid can be supplied under pressure in order to exert forces on the cylinder block, which load it to the control plate. 18. Procedure for balancing the overturning moments in one high-speed pressure energy conversion device comprising a rotatable drive element, a cylinder block, which is rotatably mounted in the housing and has a plurality of axially arranged cylinders Bearing for the rotatable mounting of the cylinder block in the housing, reciprocable in the cylinders mentioned Pistons, and motion converting elements, 'which the reciprocating pistons with the connect rotatable drive element and are formed by connecting rods that are connected to the piston are articulated in a substantially common plane, a control plate arranged in the housing having an inlet and an outlet which are consecutive communicating with one end of each cylinder, the housing being adjacent the other ends of the cylinder bounded a chamber and with the mentioned tilting moments by the displacement the center of the camp from the mentioned common plane are conditioned out, characterized in that a pressure on the hydraulic fluid in the er ---. mentioned chamber is exercised, its size in the 309885/0336 / _{ßAD ommmL} Range between the inlet pressure and the outlet pressure and the contact area between the cylinder block and the control plate is regulated by that the contact surface of the cylinder block and the radial width of the inlet and outlet channels to generate be changed by balancing forces. 19. A method for the operation of a high-speed pressure energy conversion device comprising a rotatable drive element, a cylinder block rotatably mounted in the housing with a number of axially arranged cylinders, a bearing for rotatably mounting the cylinder biook, pistons reciprocable in said cylinders, and motion conversion elements , which connect the reciprocating pistons to the rotatable drive element and are formed by connecting rods which are hinged to the pistons in a substantially common plane, the housing containing a control plate with an inlet and an outlet, ' the sequential with one end of each of the cylinders is in communication, and the housing adjacent to the other ends of the cylinder delimits a chamber, characterized in that the tilting moments which are caused by the displacement of the center of the bearing out of the mentioned common plane out in §09885 / 0338. BATHROOM 0FS6INAL in de'r ./eise more balanced, that a compensating moment is created in that the contact area between the cylinder block and the inlet and outlet ports is reduced when the center of the bearing is above the mentioned level, and the contact area between the cylinder block and the control plate is enlarged when the center of the bearing is below the common plane. 9Q.9885 / 0 335 55 blank page