DE3134239C2 - Capsule pump or motor for fluids - Google Patents

Abstract

The invention provides a capsule pump or a capsule motor for fluids, in particular hydraulic fluids. The pump or motor comprises in a housing (1) with a cylindrical inner surface, which has an inlet-outlet channel pair (2, 3) running through a housing end face, a circular disk-shaped rotary valve (4) mounted concentrically therein with two diametrically offset rotary valves -Inlet-outlet slot pairs (5, 6) in radial alignment with the inlet-outlet channel pair of the housing. A diametrical sliding groove (8) for receiving a cuboid control piston (9) at part of its height is provided in the central parallel of one rotary slide control slot pair (5). A circular running disk (11) is mounted eccentrically on the housing (1) and lies flat against the rotary valve. This eccentric running disk (11) has an axially continuous slot track (12) running perpendicular to the sliding groove of the rotary valve, in which the control piston (9) is tightly received over the remainder of its height. This allows the sliding grooves and slot tracks (8, 12, 15) to be easily produced by milling.

Description

45 disk (14) is provided with a sliding groove (15) which takes up the remaining quarter of the height of the control piston (9) and which runs parallel to the sliding groove (8) of the rotary valve (4) and that the running disk (11) on both sides of it Slotted track (12) has two compensation passages (16) which open into the end sections of the sliding groove (15) of the compensation disk (14).

8. Pump / motor according to claim 7, characterized in that the compensating pulley (14) has a drive or output pin (17).

The invention relates to a capsule pump or a capsule motor according to the preamble of claim 1.

Such a pump or such a motor is already known from US-PS 16 22 816 and comprises a housing with a cylindrical inner surface. About an axially parallel through a housing face The inlet-outlet channel pair running into the interior of the housing is used for the inflow and outflow of the fluid. In the housing itself a rotary valve is mounted concentrically as well as one which is influenced by an eccentric Control piston. The control piston itself sits in a sliding groove in the rotary valve. However, this device has the disadvantage that the flow rate fluctuations of the pump or the fluctuations of the delivered Torque in the engine are not sufficiently damped. They also need to be given a predetermined Power the dimensions of the capsule pump or motor should be relatively large, so over the associated Drive pin the corresponding torques can be absorbed.

In the device known from US Pat. No. 1,867,198 for a capsule pump or a capsule motor are from the embodiment according to FIGS. 3 to 5, two more mutually acting Pressure chambers provided to the flow rate fluctuations of the pump or the fluctuations of the output torque at the engine to dampen a little. Due to the specific design, however are the torques to be transmitted due to the small cross-sectional thickness of the pivot pin used and the control slide limited. In addition, additional problems arise due to the specific Formation of the control piston with the intended circular arc surfaces on a partial circumferential area.

The capsule pump known from US Pat. No. 4,090,817 also has the aforementioned disadvantages a high flow rate fluctuation with a comparably low power transfer.

In contrast, it is the object of the invention to provide a capsule pump (motor) of this type to improve that with a comparably high output the flow rate fluctuations of the pump (or at Motor of the output torque).

The object is according to the invention in accordance with the characterizing part of claim 1 specified features solved. Advantageous configurations of the invention are in the I 'ni. claims specified.

The underlying invention makes it extremely achieved in an advantageous and simple manner, dal) at Maximum torque transmission and thus high performance are responsible for fluctuations in the pump's flow rate

or the fluctuations in the torque output in the engine are extremely dampened and this at simplest manufacturing possibility

This follows in particular from the fact that the pressure spaces acting against one another on both sides of the> Control pistons are provided in two different axially offset areas, so that the Control piston itself can be cuboid and with the rotary valve via a straight line Sliding groove or slot track interacts Furthermore, i "the control piston does not require any special oscillating bearings, it is simply inserted into the sliding groove in the rotary valve and the one perpendicular to it Slot track used in the running disc

The development according to claim 2 practically fully utilizes the stroke of the Control piston allows

Through the further development according to claim 3, advantages of the invention can be produced by a very simple, for example by - achieve ^i] milling producible slide groove.

Through the development according to claim 4 it is achieved that the control piston on the running disk interspersed with their full strength.

The development according to claim 6 produces a 2 => radial mass balance and a particularly uniformly damped flow rate fluctuation or a particularly uniformly delivered torque.

Through the development according to claim 7 wire a w achieved even more extensive torque compensation, so that in addition still vibrating moments perpendicular to the Housing axis are largely switched off.

Through the development according to claim 8 it is achieved that the drive or output pin can have a relatively large diameter, so that maximum with small dimensions Torque transmissions are possible.

The invention is explained in more detail below with reference to the drawings. It shows in detail

1 shows an embodiment of a capsule pump according to the invention in axial section;

Fig. 2, 3, 5, 6 sections along the lines H-II, resp. III-III or V-V or VI-VI from Fig. 1;

F i g. 4 shows a section along the line IV-IV from FIG. 3;

FIG. 5a shows a sectional view analogous to FIG. 5 in contrast reduced representation, with one compared to FIG. 5 illustrates the operating position offset by 90 ° is.

The capsule pump illustrated in the drawing comprises a housing 1 with a cylindrical inner surface, a diametrically opposed pair of inlet and outlet channels through a lower housing end face 2.3 runs into the interior of the housing. In the case 1 a cylindrical rotary valve 4 «is mounted concentrically, which two offset from each other by 90 °, Rotary slide inlet / outlet control slot pairs located diametrically to the central axis 5, 6 in radial alignment with the inlet-outlet channel pair 2, 3.

As can be seen from FIG. 2 shows each inlet-off opens ^b0 laßkanal 2, 3 of the housing 1 at the bearing against the rotary slide valve end face 4 of the housing 1 in an associated nearly semicircular channel groove T and 8 '.

As can best be seen from FIG. 3 and 4 he ^ .Dt, the *> ■> Rotary valve 4 in the middle between the one pair of control slots 5, a transverse to the connecting line running slide groove 8 for tightly receiving a

^{4 (1}

45

5o cuboid control piston 9 on part of its height. The one rotary slide control slot pair 5 penetrates the rotary slide 4 in a direction parallel to the axis. The other pair of control slots 6 is connected to each end of the sliding groove 8 facing away from the extension of the pair of control slots 6 via a cranked control slot channel 7 running in the rotary slide 4 and opens there.

An eccentric ring disk 10 is placed on the upper ring face of the housing 1, the cylindrical inner surface of which runs with its axis eccentric to the axis AG of the housing 1 (see FIG. 5, 5a). In the eccentric ring disk 10, a circular running disk 11 is mounted eccentrically with respect to the housing 1, which rests flush against the rotary valve 4 (see FIG. 1). The running disk 11 is provided with a continuous slot track 12 set perpendicular to the slide groove 8 of the rotary valve 4, this perpendicular alignment being brought about by the engagement of the control piston 9 in both the slide groove 8 and the slot track 12. As can also best be seen from FIG. 5 results, the axially parallel rotary slide control slot pair 5 opens into the end sections of the slot track 12.

As can best be seen from FIG. 1 results, in the illustrated embodiment, the sliding groove 8 of the Rotary valve 4 half the axial depth of the slot track 12 of the running disk. The control piston 9 dips into the Rotary valve 4 with a quarter and in the running disk 11 with half of its height. The tight plant against the running disk U on its side facing away from the rotary valve 4 is in one Housing cover 13 a circular compensating pulley 14 with a the remaining quarter of the height of the Control piston 9 receiving sliding groove 15 is provided, which is provided parallel to the sliding groove 15, which runs parallel to the sliding groove 8 of the rotary valve 4 ″. This setting is fixed by the control piston 9, which is in the sliding groove 15 with a quarter of its height immersed. As can best be seen from FIG. 5 and 6 results, the running disk 11 has on both sides transversely to the longitudinal extent their slot track 12, that is, transversely to the direction of movement of the control piston 9, two compensation passages 16, which open into the end sections of the sliding groove 15 of the compensating pulley 14. the Compensating pulley 14 is provided with a drive pin 17 formed in one piece therewith.

As shown in FIG. 1 can be seen, the housing 1, the eccentric washer 10 and the housing cover 13 held together tightly and tightly by four tension bolts 18 evenly distributed over the circumference.

To explain the operating mode, the position according to FIGS. 1 to 3, 5 and 6 is assumed as the starting position, and a rotation is transmitted via the drive pin 17 according to the curved arrows PfX in FIGS. 3, 5 and 6. The axis AK of the control piston 9 is offset from the housing axis AG. The Einlaß-Auslaßkar.alpaar 2, 3 is either directly or indirectly via the channel grooves T, 8 'in connection with the inlet-Auslaßsteuerschlitzpaar 5 in the rotary valve 4 and thus also with the slot track 12 of the eccentric disk 11. In addition, there is initially over the channel grooves T, 8 ', the inlet-outlet control slot pair 5 in the rotary valve 4 and thus also with the slot track 12 of the eccentric running disk 11. In addition, it initially looks over the channel grooves 7', 8 '. the inlet-outlet control slot pair 6 and the cranked control slot

Näle 7 a connection to the two end portions of the sliding groove 8, which in turn via the Compensating passages 16 are connected to the sliding groove 15 in the compensating pulley 14. All in all are therefore in the assumed basic position within the slot path 12 by the control piston 9 two equally sized "cylinder spaces" are divided, while in the sliding grooves 8 and 15 by the control piston 9 a in FIG. 3 and F i g. 6 larger "cylinder space" located at the bottom and a smaller "cylinder space" at the top will.

If the drive pin 17 is rotated in the direction of the arrow PfX, the control piston 9 performs a radial movement according to a straight arrow Pf2 from FIG. 5 from (indicated schematically in FIG. 1 by a small crossed ring R ). This movement of the control piston 9, after passing through a right angle, leads to the position according to FIG. 5a, where the "axis" AK of the control piston 9 coincides with the housing axis AG . In the course of this rotation, the control piston sucks in over one part of the slot track 12 and compresses it on the opposite “cylinder pressure chamber”. With regard to the sliding grooves 8 and 15, the control piston 9 moves from an eccentric position into a central position.

So it is the control piston 9 via the inlet-outlet

laßkanalpaar 2, 3 together with channel grooves 7 ', 8' both over the rotary valve inlet outlet control slot pair 5 (via the slot track 12), as well as via the rotary valve inlet outlet control slot pair 7 (with respect to the sliding grooves 8 and 15) acted upon. This gives sL-h an extensive torque compensation, since pressures on the control piston 9 are largely compensated, as a consideration in particular of FIG. 1 results.

However, it is also possible to use the compensating pulley at the expense of less good torque compensation 14 omit and close the housing immediately above the eccentric washer 10. The piston 9 would in this case with its half height in the sliding groove 8 and with the other half of its Immerse height in the contactor track 12. In this case, the drive should have a dashed line Drive pin 17a take place, which is either formed with the rotary valve 4 in one piece or in it engages positively.

According to a further embodiment, to achieve a continuous change in the stroke of the piston 9, the eccentric ring disk 10 can be mounted adjustably displaceably relative to the housing 1 perpendicular to its axis on a straight line running perpendicularly through the axes AC and AK (FIG. 5).

For this purpose 3 sheets of drawings

Claims (1)

Patent claims: IO 1. Capsule pump or motor for fluids, in particular hydraulic fluids, comprising a housing with a cylindrical inner surface, one through a housing face approximately axially parallel into the housing interior running inlet-outlet channel pair and one mounted concentrically in the housing circular disk-shaped rotary valve together with a control piston influenced by an eccentric, the is arranged in a sliding groove in the rotary valve, characterized in that the rotary valve (4) with two pairs of rotary valve inlet and outlet control slots (5, 6) is provided that the sliding groove (8) on the side of the spool valve (4) facing the control piston (1) perpendicular to the connecting plane of the axially parallel pair of control slots (5) for receiving the cuboid control slot pair (5) for receiving the parallelepiped-shaped control piston (9) is provided on a part of its height and the other control slot pair (6) each off via a respective extending in the rotary valve cranked control slot channel (7) in which from the extension of the control slot pair (6) - ⁵ turned end of the slide groove (8) opens, that a circular drive disc (11) is eccentrically mounted in the housing (1) and rests flat tightly against the rotary slide valve (4) and extending to the slide groove (8) of the latter perpendicular axially carried ⁱⁿ rising slot path ( 12), in which the control piston (9) is received tightly on a remaining part of its height and that the axially parallel rotary slide control slot pair (5) in the end sections of the Sch Litzbahn (12) of the running disc (11) ^J1 > opens. 2. Pump / motor according to claim I, characterized in that each inlet-outlet channel (2, 3) of the housing (1) on the end face of the housing resting against the rotary valve (4) into a associated, almost semicircular channel groove (7 'or 8') opens. 3. Pump / motor according to claim 1, characterized in that the sliding groove (8) of the rotary valve (4) is diametrically continuous. 4. Pump / motor according to claim 1, characterized in that the slot track (12) of the Running disk (U) has a shorter length than its diameter. 5. Pump / motor according to claim 1, characterized in that the control piston (9) as a cube is trained. 6. Pump / motor according to claim I, characterized in that the sliding groove or slot track (8 or 12) of the rotary valve (4) and the running disk (U) each have the same axial depth and that the control piston (9) is immersed therein at half its height. 7. Pump / motor according to one of claims 1-5, characterized in that the sliding groove (8) of the Rotary valve (4) half the axial depth of that (12) of the running disc (II) that the One quarter of the control piston (9) into the rotary valve (4) and one half of it into the running disk (II) its height is immersed that in close contact against the running disk (11) on the one of the rotary valve (4) facing away a zenirisch in that Housing (I) mounted circular compensating barrel 40