DE2010033A1 - Rotary vane piston machine - Google Patents

Description

PATENT Attorney DIPL-INQ. JOACHIM STREET

«45 HANAU · RÖMERSTR. 1 »· POST BOX 7» J · TEL. 20β03 · TELEQRAMME: HANAUPATENT · TELEX: 4184782p «t

Dalsaku Odawara March 3, 1970 Sakal-shi, Osaka, Japan Zo / Jg - 10 435 Rotary vane piston machine

The present invention relates to rotary valve piston machines in which a rotor is eccentric in a housing is arranged, and sliders are attached to the rotor, which move radially on the rotor so that the volume of the working chambers can be varied with the movement of the rotor.

Known machines of this type have the disadvantage that it is impossible above a certain size, the To increase the eccentricity of the rotor in relation to the housing, there increasing difficulties in the mastery of firmness the rotor including the slider and the one for the intake the slider provided grooves in the rotor and when sealing of the working medium occur. It has already been suggested To use slides of a predetermined length, which are guided through the center of the rotor to perform a sliding movement, and to construct the housing so that its inner surface coincides with the geometrical location of the forward ends of the slider. The design has the disadvantage that the inner

009839/1426

the slide surfaces almost always have a circular shape have a slightly different shape, so that it is impossible to keep the front ends of the blades in the immediate vicinity Maintain contact with the interior surface of the housing. In addition, in the event of a collision, the front ends of the Slide with the inner surface of the housing the working medium compresses and exerts such strong forces on the slides that they break easily. The sliders must be tight and be stably constructed so that they can be used before the work withstand applied forces and keep their forward ends in close contact with the inner surface of the housing. The known Sliders tend to graze the inside surface of the housing, inevitably destroying the front ends of the Slider and the inner surface of the housing leads. To improve the rotary valve piston machine, it has been proposed to Each side of the rotor has a disc to be mounted firmly and airtight rotors as a closed unit with the discs associate. The disks have radially arranged grooves for receiving the slides and for guiding them during the sliding movements on. Hold the rotors sealed airtight close contact with the front ends of the slide and rotate concentrically with the housing, with which it is supported by roller bearings (Ant I friktions I agar) Keep in contact so that the airtight encapsulated Rotate rotors depending on the main rotor. With this arrangement, the slides are from the grooves in the Discs received in such a way that those forces are eliminated, which by the slide on the slide grooves of the rotor be exercised. This arrangement enables the use of telescopic slides, with the washers providing the axial compressive force record on the working chamber, so that the disadvantages which could arise from the direct action of this compressive force on the housing, are canceled.

The improved construction described above has many advantages. Due to the possibility of the exact design of the housing in the form of a ball, the machining

009839 / U26

management processes ν / it is neces- sarily correct. When assembling the slide .wercQii ciese first. Their front ends are hooked so that it is not possible to make sure that the leaves are in place. radial positions on the circumferential circle and the front ends of the slide in the. be in close contact with the inner surface of the housing. Furthermore, the use of special Isskoparttgen slides in the grooves of the cams makes it possible to increase the eccentricity of the rotor. An increase in the eccentricity causes an increase in the delivery or in the compression ratio, thereby expanding the range of application of the rotary vane piston machine.

It is an object of the present invention to provide a rotary piston engine to create an improvement over known embodiments for the application of the machine as Represents I nnjanyer internal combustion engine. .

Another object of the invention is to provide a Machine with a high relative to the eccentricity of the rotor Compression recovery, in the means for the improvement of the Cooling of the slide and the rotor are provided. These The object is according to the invention by means of a rotary valve piston machine solved, in which at least one telescope-like design Slide of the one extending through the rotor Groove is.t-, a multitude of intertwined te I eskopart i g having displaceable slide parts, mlt on the opposite-lying EndfI Already the rotor arranged disks with Grooves for receiving and guiding the telescopic slide, the housing, the rotor, the disks and the telescopic Form slide working chambers, their volumes change during the rotation of the rotor and that in two ' Rows of supports for the 'Po.sl.tionierung' on the outside of the panes the sliding parts are provided, and the supports parallel to each other, rotatable and concentric to the cyto-

BATH ORIGINAL

-A-

's inner surface of the housing are eordnet by roller bearings (Ant I fr 1ktIonslager) to ^ ^'.

Wei + ero advantages, features and details of the present Invention are based on the drawings shown embodiments described:

Show it:

Flg. 1 shows a to M section of an embodiment of the elements of the invention Crehschi eber kc I benmasch i rie, trained as an Innon combustion engine,

FIG. 2 shows a partial section along the line II-II from FIG Fig. 1 with two different embodiments the machine arranged side by side,

3 shows a perspective view of the rotor with the omission of the annular parts of the disks,

Figure 4 is a perspective view of the invention Slide with section-wise partial development,

Flg. 5 is a plan view of the supports for the plate-shaped I shivered,

FIG. 6 shows a partial section along the line VI - VI from FIG. 5,

FIg. 7 is a perspective view of a slide pack d i caution,

Flg. 0 is a top view of the supports for the S-shaped Slider parts,

Flg. 9 an overview of the operating cyclone used as an internal combustion machine i ne used inventions Rotary valve piston machine,

009839/1426

BATH ORIGINAL

.Flg. 10 is a partial view of a further embodiment of the present invention,

Fig. 11 is a close-up view of the sliding packing seals on the front ends of the slide according to the embodiment according to Fig. 10,

FIG. 12 shows an axial partial section similar to FIG. 2 along the line X- X of Fig. 10,

13 is a perspective view of the rotor of the embodiment 10 with the omission of the annular Parts of the discs,

14 is a perspective view of the slide packs and packs the sliding pieces arranged on one side of the slide and

15 shows a plan view of a rotatable support element for the embodiment according to FIG. 10.

In FIG. 1, a rotor 2 is arranged eccentrically and rotatably in a housing 1. A slider groove 10 extends through the rotor 2, in which two slides 6 which are designed in the manner of a telescope and which have an angle of 180 ° relative to one another are arranged. Each telescopic slide 6 consists of two slide parts 6a and 6b. The slide parts 6b of the two, slide 6 are U-shaped and are disposed side by "page that it bi an S-shaped unit I to. The front end of the plate member 6A -is on a slider 6 supporting shaft 36 attached, which is surrounded by a rotatable Gleltpakkungsdichtung 7, - This arrangement ensures a seal of the working chamber and prevents the outflow of the medium. The concave instead of zyI Indian training of the

009839/1426 " ⁶ "

ORIGINAL

inner surface of the housing 1, to increase the working volume, like that shown in Fig. 2 on the right Embodiment is the case, the sliding packing seals 7 are designed correspondingly complementary convex to be on the concave inner surface of the housing (see. Fig. 7) lying down without play.

The sliding packing 7 are each with their ends Sliders 56 are provided which maintain close contact with airtight rotors 15. These are fastened concentrically with the help of roller bearings (Antifr i kt i onsm i tte I) on the opposite sides of the working chamber in the housing 1, so that the sliding ^ packing seals 7 are radially displaceable at any time. Of the ^ Rotor 2 has recesses 20 in its surface (see. Fig. and 3) on. The lining 64 of the housing 1 and the rotor 2 touch each other at a support point 65. That behind the Support point 65 located working medium, starting from the Direction of rotation of the rotor 2, is very strongly compressed, so that damage due to the high forces can very easily occur. Serves to prevent such damage the recess 20 as a bypass through which the medium from rear part can flow into the front part of the working chamber.

A spark plug 63 is arranged on the support point 65. That ■ Housing has an inlet channel 18 and an outlet channel 19 on. Further parts of the embodiment according to FIG. 1 are will be described below.

FIg. 2 shows two different embodiments of the rotary valve piston machine according to the invention. In every embodiment connect disks 8 to the sides of the rotor 2, at right angles to the axis of the rotor 2.

Flg. 3 shows that each of the disks 8 has a radial cylindrical cavity 13 with a Radlolnut 17. The grooves

009839 / U26 - 7 -

BATH

17 are above the slide slot 10: in _; Rotor. 2 i η connection so that the. S-shaped sliding elements 6b can execute a sliding movement in the radial grooves 17 and in the slide groove 10. ¹ The cylindrical cavities 13 in the disks 8 have slots 14a running parallel to the cavity axes. The longitudinal extension of the slots 14a agrees with the range of movement of the slide parts 6a. Another slot 14b along the space 13 adjoins the slot 14a and extends through the middle piece of the disk 8. The slots 14b will be described in detail below

A ring-shaped part I 8 'of the disk 8 is on their Arranged outside surface (see Fig. 2). A V-shaped circular groove 47 and a gear 48 are arranged on the outer circumference of the surface of each ring-shaped part 8 '. In Fig. 3 are for enlargement of the parts 8 'of the view are omitted.

The well-known rotary valve piston machines are usually successful. Kfp ftTransmission and power take-off through a shaft coupled to the rotor. The combination of rotor and the associated shaft for power transmission brings difficulties with the rotary valve piston machine according to the invention, since the eccentricity of the rotor in relation to the housing is very large and the valve groove 10 extends through the center piece of the rotor 2 . To remedy this disadvantage, three parallel shafts 491, 4? C and 49R connected to the rotor 2 are arranged on the outside of the disk 8 at equal intervals of 120 ° around the rotor 2 (see Fig. 1). The letters L, C, R assigned to the reference number 49 mean left, central and right shafts.

A drive wheel 43 and a fractionation wheel 44 are on each of the) mutually parallel shafts, "within" the range of each

BATH

Disc 8, as shown in FIG. 2, is provided. The drive wheel 43 is in mesh with the gear 48 on the annular Part 8 ', while the friction wheel 44 in the V-shaped, on Circumferentially arranged groove 47 of the annular part 8 'engages. A print IagermetaI I is in a central support section 52 of the drive wheels 43 are arranged.

With the help of the pressure IagermetaI Is each drive wheel 43 and Each friction wheel 44 is just as accurate as with a spacer sleeve can be set. This arrangement is provided for all three shafts 49C, 49L and 49R. The sections of the central Bearing parts 52 of the shafts 49C, 49L and 49R are in the same place Normal plane to the shafts so that the friction wheels 44 and the V-shaped circumferential grooves 47 formed in Are engaged with the friction wheels 44, also in a Normal plane to the shafts are arranged. Since the disks lie in a normal plane to the shafts, the rotor is 2 ml + the disks 8 arranged along its central axis. the Transmission 43 on the one hand transmit the In the working chamber generated force to the outside and on the other hand force from the outside to the slides 6 and the rotor 2. Since the gear 43 with the Right and left disks 8 of the rotor 2 are engaged in three positions, a rotation of the disks 8 as a result uneven power transmission from the working chamber to the Disks 8 or in the opposite direction prevented. The friction wheels 44 and the grooves 47 arranged on the circumference in the Disks 8 have the task of supporting the disks 8 in three positions and absorbing axial compressive forces. In this It goes without saying that the training of the Grooves and the circumference of the friction wheels in no way, as shown, Must be V-shaped. The friction wheels and the grooves can have any shape as long as they are the above fulfill the function described.

009839 / U26

BATH

Fig. 2 shows that the support 52 of the central shaft 49C from a removable bearing shell connected to the housing 1 e 51 and consists of an upper bearing part 50. The supports 5 2 of the left and right sheep 49, the clarity Because they are not shown, have bearing shells 51 which are part of the housing 1. The arrangement of one with the Housing 1 detachably connected bearing shell 51 enables a gap between the friction wheels 44 and those on the circumference arranged grooves 47, "the wheels by worn Frikt1 ons by inserting or removing washers or other shims to compensate.

In Fig. 2, a gear 46 is at the right end of each of the shafts 49G, 49L and 49R, which meshes with a gear 53, is mounted. This I st - constancy of a shaft. 54, the rotatable is arranged in a support part 55 of the housing 1, wherein the power transmission can take place to the outside or from the outside. By selecting the diameter of the gears 46 and 53 will be the desired speed of the shaft 54 is clear.

As shown in FIGS. 2 and 4, the shafts 36 which carry the slide 6 are fixedly connected to sliders 11b which are displaceable in concave parts of the main sliding pieces 11a,. 1 la arranged are. With each of the joint pieces 11b there is a further shaft 39 fixedly connected, which runs coaxially to the shaft 36 and extends through an axial slot '12 in the main sliding pieces 11a and the slot 14a in one of the disks 8 extends. Of the concave part Each main slider 11a is as a cylindrical one Inner surface formed with a FU H te I I 62, which serves as a guide groove for the slider 11b. The main sliding pieces TTa, which are arranged displaceably in the cylindrical cavities 13 of the disks 8, are in each case with their middle pieces with the opposite sides of the S-shaped porthole I es 6b firmly connected, so that the main interface pieces 11a and the> Slide part 6b form an H-shaped unit,

- 10 009839/1426

BATH

On the outside of the middle piece of each main piece 11a a support shaft 3 is arranged, which extends through the Slot 14b, in one of the cylindrical cavities 13 of the Washer 0 extends and its end shaft offset and one has a smaller diameter than the main shaft. The end shaft is supported by a bearing part 16a of a rotatable support 16 added, which on a hub 9. Of the housing 1 (cf. Fig. 2) is arranged. The Tragschiifte 3 are through the Bearing parts 16a set in rotation via the support 16 as soon as the rotor 2 begins to threaten, the position of the S-shaped slide part 6b, which with the shafts is connected, is influenced by the rotor 2 radially. The Tragscha'fte 3 can with the help of before, bearing elements with the supports 16a are connected.

The Scha'fto 39 shown in Fig. 5 are supported by bearing parts 4a and 4b of the bearings 5a and 5b supported, which are rotatable within the Geha'uses 1 and concentric to its cylindrical Inner surface are arranged. The bearings 5a and 5b are arranged side by side. The shafts 39 with the slide parts 6a connected, move in opposite directions telescopically in the S-shaped Schlebertei len 6b and are replaced by the, camped! Ie 4a and 4b of the bearings 5a, 5b added. For this reason, two shafts 39 of different lengths are provided for the bearings 5a, 5b. Because of the eccentric arrangement of the rotors 2 in With respect to the inner surface of the housing 1, the front ends of the two sliding parts Ie 6a, telescopically from the S-shaped Sch leborte M en 6b are performed or the shafts connected to the front ends of the slider barrel 6a 36 and 39 different ones, varying from time to time Circumferential speed! GkoI ton on. For no reason it is not possible, the two villains 39 of the Sch IobertoI Ie 6a with the to pre-bind the same camp. The arrangement in which the villains 39 are supported by the bearings 5a and 5b, allows maintaining close contact between the front

- 11 -

009839 / U26

SAD OftfGINAL

Ends of the slide parts 6a and ″ of the inner surface of the working chamber to achieve an airtight seal.

In the embodiment shown in FIG and by WIi Ί ζ I ager are arranged rotatably to the inner surface of the housing -T, they rotate at substantially the same speed as the - "sliding pack seals 7. Because of the very small difference between the relative speeds of the sliding pack seals 7 and the airtight rotors 15 occurs only a very slight wear of the sliding packing seals 7. In the embodiment shown on the left-hand side of FIG of a little over 180 °, so that a detachment caused by the centrifugal forces of the Sliding packing twisting 7 is prevented by the shaft 36. D read embodiment α therefore does not require any airtight rotors. 15. The two slides 6 are arranged at an angle of 180 ° relative to one another and are operated as described with reference to FIGS. 1 and 4, each slide being formed from the plate-shaped slide part 6a and the U-shaped slide part 6b. The two U-shaped slider parts 6b are joined together to form an S-shaped unit, so that the two plate-like parts 6a can move simultaneously into and out of the U-shaped plate parts 6b. This arrangement is mainly used for embodiments in which the eccentricity of the rotor is great. If the eccentricity is low, it is not necessary to design the two U-shaped plate parts as a coherent S-shaped unit.

009839 / U26

bath

The present invention can be used for internal combustion engines, Pumps, compressors and similar machines are used. When using a non-compressible liquid as Both the suction and the discharge side must be used for the medium be left open. When using a compressIbI It is necessary to have a valve in each of the liquid Provide suction and drainage openings. The present invention is in the following with reference to an embodiment, which as Internal combustion engine operated with electrical ignition is described in more detail. Figs. 1 and 2 show that the lining 64 of the inner surface of the housing 1 can be applied at any time as desired can be replaced. The lining 64 is applied without play to the rotor 2 at the support point 65. To enlarge the sealing effect at point 65 is either on the surface of the rotor 2 or a sealing means is provided on the surface of the liner.

Inlet and outflow openings 27 and 30 with the inlet channel and the drainage channel 19 are provided in the housing 1 in the lining on the side opposite the support point 65. Support brackets 21 and 22 are between the housing 1 and the lining 64 for the suction and discharge openings 27 or 30 are provided and open and close these openings synchronous with the operating status of the machine. The operation when opening and closing the openings 27, 30 is subsequently described in more detail.

A worm 42 (see Fig. 1) is on the left power transmitting Shank 49L, which meshes with a worm wheel 41, is arranged. This is through a bearing part 40 of the Housing 1 connected to one end of a shaft 38. At the other end of the shaft 38 a screw gear 37 is provided, which is in engagement with a gear 35, which in turn engages in a gear 34. The speed of the transmission 34 is half that of rotor 2. On the

009839/1426

BAD ORJGINAL.

Gear 34 is a pin 23 attached, which is in a slot a lever 25 engages. The lever 25 is rotatable with a attached to the housing Γ pin 24 connected so that it is a Carry out sliding movement within the area of the slot 26 can. At the free end of the lever 25 is a drive pin 29 attached, the one groove in a holder 28 of the storage support 21 records. This arrangement enables the reversal of the circular Rotary movement of the gear 34 into a rotary movement of the Lever 25 over the pin 24 and then in a sliding movement of the sluice gate 21 for opening and closing the suction port 27. The moving speed of the sluice gate 21 is not constant. The opening speed is slower than the closing speed. Should it be necessary it is possible to close the suction opening 27 until the end of the suction stroke to leave open, whereby the intake volume 11 is increased,

The execution and the sequence of movements of the for da.s opening and Closing the outflow opening 30 provided mechanism (See right side of Fig. 1) Is similar to the one just now described mechanism for the suction port 27 and is therefore not described in detail.

Instead of back-up supports 21 and 22, throttle valves can also be used can be used as suction and discharge valves. Likewise, instead of one spark plug, two spark plugs on each side of the support point 65 between the rotor 2 and the Inner surface of the housing 1 is provided so that each one of the spark plugs in the same tone as the direction of rotation of the Rotor 2 for reversing the drive on the machine Can be used.

Optionally, one or more fuel injection valves can be provided in the positions. In which spark plugs are usually arranged as a reading machine when driving a boat.

- 14 -

009839/1426

-M-

Due to the close contact without any play between the rotor 2 and the liner divides the working chamber into two parts. The medium in the part that is related to the direction of movement of the rotor 2 is backwards, it is strongly compressed as the volume is reduced. To prevent this a fold 20 is provided on the surface of the rotor 2, which creates a connection between the front and dome rear part of the working chamber.

With this arrangement, the working medium moves out of the Rear part in the form of a jet in the front part of the Working chamber after the ρ slat-shaped slide part 6a the ^ Passed position 65. The resulting turbulent Flow provides a homogeneous mixture of air and fuel. This advantage not only has a positive effect on the electrical ignition, but also enables the machine to be operated like a I operate this aggregate because the air-fuel mixture is homogeneous allows spontaneous ignition at a later point in time. Instead of the folds 20, two or more folds can be provided in order to prevent the turbulent flow align so that an additional turbulent flow arises.

The ignition will preferably take place when the slides 6 are horizontal or only deviate slightly, as in FIG P Fig. 1 gozoigt, have from the horizontal position. Since the Burning time is constant regardless of the speed it is necessary in proportion to the increase in Speed, the position of the ignition point or the point for the gas injection nozzle to change so that the ignition occurs regardless of the increase in speed when the slide take a horizontal position. In the one for an internal combustion machine provided embodiment of the rotary valve piston machine are two working chambers offset by 180 ° to each other

0Q9839 / M26

on opposite sides of two axially aligned Arranged sliders. The suction, compression, explosion and discharge stroke take place in each of the working chambers as in Case of a four-stroke piston engine during two complete ones Revolutions of the rotor 2. This operational sequence is referred to with reference on Fig. 9 described in more detail. In operating level Γ, the Chamber A the suction tube and the. Chamber B the discharge stroke through .. In stage II, the compression takes place in chamber A, while chamber B performs the suction stroke. In the stage IM ignition and explosion takes place in chamber A, while there is compression in chamber B. in the final stage IV, the chamber A carries out its discharge stroke, währond the explosion takes place in chamber B. The work cycles of the working chamber A lead those of chamber B by 180 °.

Optionally, the working chamber B can also be used instead of the discharge stroke Perform the compression stroke in stage I. In this In case I, the chamber B. carries out the exposure, the outflow and the Intake stroke in stage II, III or IV. The work cycles the Chamber hurry In this case the working cycle of the Chamber A forward by 180.

In the embodiment described, the suction angle follows from 180 of the chamber A the suction angle from 180th of the Kanmer 3, so that the suction opening during one complete revolution of the rotor 2 can remain open. The same goes for that Outlet opening. , The discharge opening opens after a Rotation of the rotor by 180 ° after the suction opening has been closed. This starts after opening the rotor has rotated another 180 °. -Then stay with both the Inlet and outflow openings during the Welter -..., turning the rotor by 180 °. opened. The closing and opening process , the suction and discharge openings are reversible. This means that cl & ß in the event of a reversal, the direction of rotation of the invention Machine to open and close the suction

- 16 -

0098 ^ / 1426 "

and outflow openings run off in the manner described above, without a switchover having to be carried out with the help of a kecke. Known ', usführunnsformen know only in the form of two-link machines a I π reversible machines are operated. The poor flushing effect of such machines is a disadvantage. It was only due to animal present invention, it is possible to operate machines as reversible Viortekt machines. FCr use animal present invention as a reversible machine it is necessary to dispose not only the electrical ignition parts or the fuel injection nozzles symmetrical to the support point 65 but also the Ansaugi: nd provide outflow openings symmetrical with respect to the position 65th As seen from Fig. 9, is only tei each second Umdrehurg of the rotor a Exp I osicnstakt instead, se that the supply of additional energy is needed for example, by a flywheel for maintaining the rotation of the rotor during animal cxpIosionsfreien work cycles. This problem can be circumvented shown two machines side by side, as shown in Fig. 2 daP are ancecrrinet in which the opening and closing animal valves is adjusted so that at any time in one of the working chambers an explosion takes place. This arrangement ensures that the machine runs smoothly and develops a high level of performance.

Optionally, three cylinders can also be arranged side by side, so that an explosion stroke takes place in one of the cylinders at any time. With every third revolution an explosion occurs in a tier cylinder and the operating cycle comprising six work cycles includes suction, compression, discharge, cooling (suction) and flushing (discharge) during three rotations. The cooling efficiency and the efficiency of the machine are increased by the corresponding work cycles, so that the known cooling problems at high speed and high output where the usual

- 17 009839 / U26

BATH

Air or water cooling systems or cooling by means of lubricants fail, are resolved.

Instead of three parallel shafts for power transmission can have more shafts, the same distance to each other, wise to be used. The arrangement of a bearing part in the rotor shaft there can be one or two for the transfer of forces para I e I e shaf te be provided.:

F ig. · 1 0 shows a further f ührungsf ortr the vcrl laying invention extend in two parallel vane grooves 10a and 10b by the opposite sides of the rotor 2 in parallel to the rotor 2 · dor Zentralaehse. One telescopic J

like slide 6 is slidable in each of the slide grooves 10a and IOb arranged. The telescopic slide 6 consists of two sliders i J en 6a and 6b, where the ρ I attenf 8-rm i ge slider part 6a is telescopically displaceable in the U-shaped slide part ob. One carrying the slide Shaft. 36a is each plate-shaped with the free end Slider part 6a connected, while a slide-carrying Shank 36b with the free end of each U-shaped slide part 6b, as shown in FIG. 11, is connected. Each of the shafts 36a is covered by a sliding packing 7a which surrounds the shaft 36 is rotatable, enclosed. A rotatable sliding packing seal 7b surrounds each of the shafts 36b. Dio adjoining each other G Ie i tpackungsd I cn ttingen 7a and 7b show a match the fold and a projection so that they are telescopic are connected to each other. A viol number of axially extending Grooves 31 on the surface of the GI packing seals 7 a and 7b abuts in contact with the liner 64 on the inner surface of the housing 1. A sealing tape 32 is in each of the axially provided on grooves 31. This arrangement gov / ühr l-e i rj ^ ot a seal there at the Arbo i tskammorn- A and i3 to the fore-. Change of S i cko rvor I ur> ton dos work mode i urns and bi i dot in addition a no Arbo I tsrned I um ontha I toncJo- Zw i already konmer C between the two arbors' chambers A and B.

- 18 -0098397 U26

^BATH

The arrangement in which sliding packing seals 7a, 7b the Shafts 36a, 36b enclose, prevents pressing of the, Sliding packing seals 7a, 7b against the liner 64 the inner surface of the housing 1 due to the centrifugal forces high pressures occurring during the rotation of the rotor 2. With a concave inner surface of the housing 1, for Increase in stroke volume, as in the one on the right of the embodiment shown in FIG. 12, the sliding pack seals 7a and 7b have a corresponding convex shape so that they fit into the concave inner surface of the housing 1 fit.

In Fig. 12, two embodiments of the throttle piston machine, corresponding to the embodiment of the invention shown in Fig. 10, arranged side by side are. The arrangement in Flg. 12 points in comparison to the arrangement 2 in that a shaft forms an extension of the rotor 2. The disks 8 have in each case two parallel cylindrical cavities 13, which in turn are parallel to the slide grooves 10a and 10b in rotor 2 are. Stepped grooves 60 and 61 represent the Connection between the slide grooves 10a and 10b and the Cavities 13 (see Fig. 13). The stepped grooves 60 and 61 consist of axial wall parts 60a, 61a and normal extending walls I I e ^ 60b and 61b. Preceding the U-shaped slide parts described are inserted slidably in these grooves. Each of the U-shaped slide parts 6b is passed through the wall parts 60a, 60b and 61a, 61b of the grooves 60 and 61, so that radial and axial forces from these Wall parts are included. The plate-shaped slide parts 6a slid into and out of the U-shaped slide parts 6b. Run parallel to the cylindrical cavities 13 Slots 14 through the discs 8. The main dimension of the slots 14 corresponds to the range of movement of the plate-shaped Slider part 6a. FIg. 12 shows that each of the disks 8

- 19 0098 3 9 / U26

a ring-shaped part 8 'on the outer periphery having.

The shafts 36 a and 36 b carrying the slide 6 are connected at their ends to sliding pieces 57 a and 57 b, which slide in the cylindrical cavities 13 of the disks 8. On the sliders 57a and 57b, shafts 39 are voi—. seen, which represent the coaxial extensions (see FIGS. 12 and 14) of the shafts 36a and 36b and extend through the slots 14. ^ "'iSrd ^ SxWäf -τΐΓ39 are given by reference ¹ ■ parts 58a, 59a and 58b, the rotary bearing 5a and 5b supported 59b, which are arranged concentrically in the housing 1 (see. Fig. 15). the fixed to the shafts 36a slide 'ä pieces 57a are longer than the costs associated with the shafts 36b sliders 57b . the arranged at one end of the two slides sets 6 shafts 39 support the bearing parts ^58a: 59a of a Lagers'5a, while arranged at the other end of the two slides sets 6 shafts 39, the bearing portions 58b, 59b of the second bearing 5b take '. The distance between the two shafts 39, which are supported by the same support 5a (or 5b), is not constant, but varies 1π with respect to the circumferential direction of the support The shafts 36a, 36b and 39 provide the necessary close contact to achieve an airtight seal between the front ends of the slide parts 6a and 6b and the inner surface of the working chamber. that only a single rotatable support 5b is used instead of the two sets of rotatable supports 5a, 5b, which simplifies the design effort and reduces the size of the machine 60 and 61. Ln the combined with the rotor 2 ben ticket 8 so on _taken> that the slide · * - bertej Ie 6b is a Gl eitbewegung.ausführen, while the side

■■ "..- 20 -

009839 / U26

union surfaces and end surfaces of the axially extended side parts with the axial wall parts 60a and 61a and the peripheral wall parts 60b and 61b of the grooves 60 and 61 airtight i eat.

In addition, means are provided to prevent damage caused by the interruption of the grooves 60 and 61 and working chambers connected to the cylindrical cavities 13 A, B and the intermediate chamber C. The sliders 57a and 57b, which are connected to the shafts 36a and 36b, have a slider 45 that slides back and forth in the stepped grooves 60 and 61 and at the same time causes their sealing. The slider 45 comprises a part I 45a, which is in the narrow part I and a toi I 45b, which slides in the wider part of the grooves 60,61. The part 45a has the same length as the sliders 57a and 57b, while the part 45b is shorter than the part 45a. the Sliders 57a and the sliders 45a, which with the slide parts 6a are connected, have a length that prevent an interruption between the working chambers A, B and the intermediate chamber C, even with the maximum length of the slide 6, d. H. so when fully extended from the slide parts 6b Sliding instruments 6a.

The preceding statements show that with the inventive Doppe I valve piston machine is a particularly large one Compression ratio in relation to the eccentricity of the Rotor can be achieved. The machine enables adjustment a predetermined compression ratio even with a relatively large diameter of the rotor. The use of a rotor with a large diameter can increase the Strength of the rotor and thus an increase in Ürehzah sources.

Another advantage of the present invention is the arrangement of the sliding packing seals 7a and 7b, which are telescopic

009839 / U26

1 -

BATH

■ - 21 -

for sealing the intermediate channel C against the working medium are connected to each other. Since the intermediate chamber C no Contains working medium, can solve the difficult cooling problem When the machine is used as an internal combustion machine, cooling means are provided via feedthroughs in the rotor and in the rotor shaft are fed.

Expectations

009839 / U26

Claims (11)

Expectations .) Rotary vane piston machine with a housing, an in this housing rotatably and eccentrically with respect to the cylindrical inner surface of the housing rotor, characterized in that at least a telescopic slide (6), which in a groove (10) extending through the rotor (2) is arranged, a plurality of telescoping into one another has displaceable slide parts (6a, 6b), with to the opposite end faces of the rotor (2) arranged fc, washers (Θ) with grooves (17) for receiving and guiding the telescopic slide (6), the housing (1), the rotor (2), the discs (8) and the telescopic Form slides (6) working chambers (A, B), their volumes change during the rotation of the rotor (2) and that in two rows on the outside of the discs (8) supports (16) intended for positioning the sliver parts (6a, 6b) and the supports (16) are mutually parallel, rotatable and concentric to the cylindrical inner surface of the housing (1) arranged by roller bearings (AntifriktIons Jager) are. 2. Rotary valve piston machine according to claim 1, characterized in that two telescopic slides (6) are provided which are arranged in two mutually parallel slide grooves (10a, 10b) extending through the rotor (2), the two being arranged The slide (6) delimits an intermediate chamber (C) which is sealed against the working medium. 3. DrohschleberkoIbenmaschIne according to claims 1 and 2, characterized in that a gear (48) and a circular and V-shaped groove (47) on the outer 009839 / U26 . Circumferential area each. Disc (8) 'and a Multiple shafts (49) parallel to the rotor axis with connected to a gear (43) and provided with a drive wheel (44) are, which with the gear (48) and the hat 047), on the outer circumferential surface of the disks (8) "to" r power transmission be engaged via the shafts (49) 4. Rotary vane piston machine according to * the claims'T'bfs"3,^v;'thereby ge ke ή η ζ ei ch η et, ' · '' that the" rotor (2) is eccentric with respect to the housing (1) in such a way " , is arranged that seepage losses of the 'arbe i tsmdd'i around i η a position in which the "rotor (2) is in" contact with the inner surface of the housing (1) always occur, and that a fold ( 20) 'on. of ¹ Oberf times the r rotor '*' ( '■!) zv) isehen the sliders (6) provided' is / the eiή DurchfIfcßen of the working medium from a working chamber (A) ¹ iTi allows * the other 'working chamber (B). '''-.<■ -: ··· -..., - ..,. '' ■ '■ -'.- ; -. : -. - .. κ ^v ■ -. ^; -. T 5. Rotary vane piston machine according to one or more 'the'. Claims T to 4, because by C h "g ο k ^: " c η η ζ e Λ- c h η et, 'that "ring-shaped, mass-density ROtörcnMi5) arranged co-centrically to the outer cylindrical five-flat housing (10') and are connected to this via "ViS I ζ I ager (Antifri fci ions-. · - ,; lager), whereby on the side surfaces of the airtight, opposite one another stand ^; nden '^; * Ro'toTen (Ί5 ^ν ) - Disks 8 ...> provided sfrvd 'and' the rotors (15) in close contact with the tips' of the slides (6) or the slides provided on the sliders (6) pieces (7). ^ · = · ':. ■ ...., - · .., -. 6. Rotary luerRöIbenmaschIne "according to" einörn or several of claims 1 to 5, d ad u ~ fch - ge 'k' o. η, -η-ζ β. I need the means (34, 25, 24, 21, 22) for setting the opening and closing! leßens - the "intake and outflow.möffhüngeh (27, 30) and - the installation of the ignition point of the - see - ZU'ndvorr ^ chit'ungen · _: · (63} or" the fuel - 24 - 3 t% '·''· f S 6> fe · ■' · '' -P- 00 9839 / T4Ä ^Ä BATH ORIGINAL Injection through the fuel injectors are provided, with a four-stroke or six-stroke operation is possible. 7. Rotary vane piston machine according to claim 6, characterized g e k e η η ζ e i c h η e t that two ignition devices (63) or two fuel injectors are provided and the suction and discharge valves (21, 22) are synmetrical to the support point (65) between the rotor (2) and Inner surface of the housing (1) are arranged, whereby c'ie Machine independently reverses its sequence of movements. 8. Rotary vane machine according to one or more of the Claims 1 to 5 and according to Claim 7, characterized in that two machines are side by side Side are arranged, with each of the machines in four-stroke operation works, see that always in one of the working chambers (A, D) of the two machines during each work cycle an explosion takes place. 9. Rotary valve piston machine or one or more of the Claims 1 to 5 and according to Claim 7, d a d u r c h g e k e η η ζ e i c h η e t that three machines side by side Side are arranged, each of which in six-stroke operation works with the inclusion of the cooling and rinsing process, so that always in one of the working chambers (A, B) the three machines an explosion during each work cycle takes place. 10. rotary valve piston machine according to claims 1 to 9, characterized in that sliding packing seals (7a, 7b) telescopically with one another at the tips of the two parallel slides (6) are connected so that slo each of the working chambers (A, D) and seal the intermediate chamber (G). - 25 - 009839 / U26 BATH ORIGINAL 11. Rotary vane piston machine according to claims 1 to 10, characterized in that a Coolant is provided in the intermediate chamber (C). 009839 / U26