US3269371A

US3269371A - Rotary vane unit

Info

Publication number: US3269371A
Application number: US322724A
Authority: US
Inventors: Eickmann Karl
Original assignee: Individual
Current assignee: Individual
Priority date: 1962-11-09
Filing date: 1963-11-12
Publication date: 1966-08-30
Anticipated expiration: 1983-08-30
Also published as: DE1401403A1

Description

Aug. 30, 9 I K. EICKMANN 3,

ROTARY VANE UNIT Filed Nov. 3.2, 1963 '7 Sheets-Sheet 1 Aug. 3%, 1966 K. EICKMANN 3,2693% ROTARY VANE UNI T Filed Nov. 12, 1963 7 Sheets-Sheet 2 INVENTOR karfi 15mm OTARY VANL] UNI l '7 Sheets Sheet 3 Filed Nov.

ZNVENTOR ATTORNEY A 25m mew Filed Nov. 12 1963 ROTARY VAN]? UNIT '7 Sheets-Sheet 4.

INVENTOR a a x Jww ATTORNEY ROTARY JANE UNIT Aug. 236% ii M. Emmmwm 3,26%,3711

ROTARY VANE UNIT Filed Nov. .122, 1.965 '7 Sheets-Sheet 6 INVENTOR 72mm x fi z-$6,

ATTORNEY Aug, 3% w m. EEQKMANN 3,269,371

ROTARY VANE UNI T Filed Nov. 12; 1963 '7 Sheets-Sheet v INVENTOR A arf 50671400 ATTORNEY United States Patent 20 Claims. (Cl. 1238) The present invention relates to a rotary vane unit, and more particularly to a rotary unit of the type including a rotor having vanes and a casing ring surrounding the rotor and being eccentrically mounted for performing during rotation of the unit, a movement transverse to the rotor axis. Due to the eccentric arrangement of the casing ring in relation to the rotor, vanes guided in slots of the rotor and engaging the inner surface of the casing ring, perform a reciprocating motion while forming expanding and contracting working chambers in the inner space between the casing ring and the rotor.

It is one object of the invention to use the relative movement between the casing ring and the rotor for additional functions particularly for increasing the output and economy of the machine, for providing an additional compression stage, or for equalizing the pressures acting in the working chambers.

Another object of the invention is to use the fluid filling the working chambers, or the fluid which produces the equalization of the pressure, for additional functions which take place outside of the main working chambers.

Another object of the invention is to provide a rotary vane-type machine which is particularly suited for high working pressures.

Another object of the invention is to provide a rotary vane machine which can be economically operated as a combustion engine.

With these objects in view, the present invention relates to a rotary machine of the vane-type, and more particularly to a rotary unit for a machine of this type. In accordance with one embodiment of the invention, a rotary unit comprises a rotor mounted for rotation about a first axis; a casing ring eccentrically surrounding the rotor and defining with the rotor an inner space; vanes preferably mounted on the rotor for radial movement and being in contact with the casing ring so as to divide the inner space into a plurality of first working chambers for a fluid; and piston means mounted on the casing ring movably disposed in a cavity of the rotor and defining therein second working chambers for a fluid.

' During rotation of the rotor with the casing ring, the

first and second working chambers expand and contract in accordance with the eccentric movement of the casing ring relative to the rotor. Since both, the first and second Working chambers expand and contract, fluid is supplied to, and discharged from the working chambers. While the first working chambers expand and contract in accordance with the angular displacement of the rotor, the second working chambers formed by the piston means, expand and contract in accordance with the eccentric movement of the casing ring which takes place in substantially radial direction with respect to the axis of rotation of the rotor unit.

In a preferred embodiment of the invention, the rotor has two axially spaced walls and -a central portion surrounded by the casing ring. Pistons located in cavities of the rotor walls are mounted on opposite sides of the casing ring, preferably supported by a shaft passing through the casing ring in axial direction. The fluid is supplied to, and discharged from the working chambers of the rotary unit by means of ducts and passages provided in the rotor unit and communicating with a valve disposed in the interior of the rotor shaft. In one embodiment of the invention, parts of the second working chambers communicate with the open air, and in another embodiment of the machine, a fuel is supplied to part of the second working chambers for driving the pistons in an expansion stroke, when ignited.

The novel features which are considered as characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construction and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings, in which:

FIG. 1 is an axial sectional view taken on line 11 in FIG. 2 and illustrating a first embodiment of the invention;

FIG. 2 is a fragmentary cross sectional view taken on line 22 in FIG. 1;

FIG. 3 is a fragmentary cross sectional view taken on line 33 in FIG. 1;

FIG. 4 is an axial sectional view illustrating a second embodiment of the invention;

FIG. 5 is a fragmentary sectional view taken on line 5-5 in FIG. 4;

FIG. 6 is an axial sectional view taken on line 6-6 in FIG. 7, and illustrating a third embodiment;

FIG. 7 is a cross sectional view taken on line 7-7 in FIG. 6;

FIG. 8 is an axial sectional view taken on line 88 in FIG. 9 and illustrating a fourth embodiment of the invention; and

FIG. 9 is a cross sectional view taken on line 9-9 in FIG. 8.

Referring now to the drawings, and more particularly to the embodiment illustrated in FIGS. 1-3, a rotor unit is mounted in a stator housing 10 and comprises a rotor shaft 11 having a journal and coupling portion 12 at one end, and an elongated hollow portion 13 on which a rotor 14 which includes two axially spaced walls 15 and 16 and a central portion, is mounted. The arrangement is such that rotor 14 can slide onto shaft 13 until abutting rotor end part 18, whereupon rotor end part 17 is placed on the opposite side of rotor 14 to hold the same in place. Rotor end parts 17 and 18 form caps abutting the end faces of rotor walls 15 and 16 in axial direction, and the peripheral surfaces of rotor walls 15 and 16 in radial direction.

Rotor end part 18 abuts a flange 19 of rotor shaft 11, while portion 17a of rotor end part 17 abuts an annular member 20 on shaft portion 13. Bolts, not shown preferably extend in axial direction through the rotor parts 17, 14, 18 and hold the rotor parts together. The tubular end portions 17a of rotor end part 17 abuts an annular member 20 which surrounds the hollow shaft portion 13. One or several chambers 21 are provided in member 20 to receive piston means 22 which abuts a resilient split ring 23 mounted in an annular groove of shaft portion 13. When a pressure fluid is supplied to chamber 21, the rotor unit is urged to the right as viewed in FIG. 1 into abutment with flange 19. The above described rotor means is mounted for rotation in a casing 10. A tubular portion 17a is mounted in a bearing portion 24 of casing 10, and shaft portion 12 is mounted in a bearing portion 25 of casing 10.

As best seen in FIG. 2, the central portion of rotor 14 has a smaller diameter than the walls 15 and 16 of the rotor which are best seen in FIG. 3. An annular space is thus formed between the central rotor portion and the axially spaced rotor walls 15 and 16, and a casing ring 27 is mounted in this space as best seen in FIGS. 1 and 2. The casing ring 27 defines with a central rotor portion an inner space 28, best seen in FIG. 2. The lateral faces of the casing ring 26 slidingly engage corresponding faces of the rotor end parts 17 and 18, and also the inner confronting faces of rotor walls and 16-.

Casing ring 23 includes an inner part 27 and an outer part 27a which has a curved peripheral surface abutting an outer stationary ring 30 which is mounted within a tubular casing portion 31.

Flange portions

32 and 33 support the tubular part 31 in the outer casing 10.

As best seen in FIGS. 2 and 3, the circular inner and outer surfaces of the inner casing ring 27 have a center located eccentric with respect to the axis of shaft 11 and of rotor 14. The outer casing ring 27a has an inner surface concentric with the inner casing ring 27, and an outer circular surface concentric with the rotor unit. Casing ring 27 rotates wit-h the rotor unit, but has an axis parallel to the axis of the rotor unit and spaced from the same the distance e.

The central part of rotor 14 has a plurality of radial slots 34 which are continued in the rotor walls 15 and 16, as best seen in FIGS. 2 and 3. Vanes 37 are mounted in slots 34, 35, 36 for radial movement. In the illustrated embodiment six vanes and six slots 34 are provided. The central portions of vanes 34, which are guided in the slots of the central portion of the rotor, slidingly engage the inner surface of easing ring 27, and form a plurality of working chambers in the inner space 28. When rotor 14 rotates together with casing ring 27, any working chamber between two adjacent vanes 34 first expands and then contracts. This causes radial movement of vanes 34 in slots 34, 35, 36. The working chambers formed by the vanes are bounded in axial direction by the inner surfaces of the rotor walls 15 and 16. Due to the fact that the axial end portions of vanes 37 project into slots 35, 36 of the rotor walls 15 and 16, the working chambers are sealed from each other, and the vanes are reliably supported against the pressure of the fluid in the working chambers. The position of the end portions of vanes 37 in slots 36 of rotor wall 16 is best seen in FIG. 3. The vanes are guided along the walls of the slot in fluid-tight engagement so that the chambers formed in slots and 36 inwardly and outwardly of the vanes are separated from the working chambers 28. However, the inner chamber in each slot communicates with the outer chamber in the respective slot.

The sealing achieved by the vanes between the slots and working chambers 28 is furthed improved by the construction of the vanes inasmuch as the vane end portions 38 and 39 are longer in radial direction than the central vane portions 34 and have outwardly projecting portions 38a and 39a which are in sliding engagement with the lateral faces of the inner casing ring 27 as best seen in the lower portion of FIG. 1. The central vane portions 34 have slide shoes 40 slidably engaging the inner surface of the inner casing ring 27 and being mounted on the main central portion of the vane by a pin 41.

As explained above, the casing ring 26 has lateral faces engaged by the rotor end parts 17 and 18, and by the inner faces of rotor walls 15 and 16. The walls 15 and 16 of the rotor have cavities 44, which open on the inner faces of walls 15 and 16. A plurality of shafts 46 pass through the inner casing ring 27 and have end portions projecting into the cavities 44, 45 of rotor walls 15 and 16, as best seen in FIGS. 1 and 2. A piston means 42, 43 is mounted on each end portion of each shaft 46, and has a substantially rectangular cross section corresponding to the cross section of the cavities 44, 45. Each shaft end portion of shaft 46 is located in a circumferential slot of the respective piston, as best seen in FIG. 3. Pistons 42 form an inner chamber 48 and an outer chamber 50 in the cavity 44, and piston 43 forms an inner chamber 49 and an outer chamber 51 in the cavity 45. The bore in casing ring 27 in which shaft 46 is mounted has a diameter corresponding to the diameter of shaft 46.

When the rotor unit including rotor 14 with walls 15 and 16 rotates, the casing ring 27 rotates with the rotor unit with which it is coupled by pistons 42, 43 and shaft 46. However, since the axis of easing ring 27 is eccentric to the axis of the rotor shaft 11, the casing ring is forced to perform a motion transverse to the axis of the rotor whereby pistons 42, 43 are reciprocated in radial direction in cavities 44, 45 whereby inner chambers 48, 49 and outer chambers 50, 51 alternately expand and contract in timed relation with the expansion and contraction of the working chambers in the inner space 28.

A control valve 52 is disposed in the interior of the l'lOllOlW shaft portion 13, and is provided with an inlet passage 54 and an outlet passage 53, assuming that the :machine is operated as a pump. Segment-shaped control grooves 55 to 62 communicate with

passages

53 and 54 and supply and discharge, respectively, an operating fluid to the ducts 63, 64, 65 and 66 which lead to chambers 50, 58, 34, and 51.

As clearly shown in FIG. 1, duct 63 is provided in rotor end part 17 and communicates with the outer chamber 50, duct 66 is provided in end part 18 and comm-unicates with the outer chamber 51, duct 64 communicates with the working chambers 28, and duct 65 communicates with the inner chamber in slot 34. Ducts 67 and 68 are provided in the rotor end parts .17 and 18 and connect the inner chambers 48, 49 of cavities 44, 45 with an outer space in the casing communicating with the open The embodiment illustrated in FIGS. 1 to 3 operates as follows:

Main working chambers in inner space 28 If the machine is operated as a pump requiring rotation of the rotor in the direction of the arrow 1 in FIG. 2, pressure fluid flows through inlet passage 34 and is sucked through groove 57 and some of ducts 64 into those working chambers 28 which expand as indicated by minus signs in FIG. 2. At the same time, the (WOIking chambers 28 indicated by plus signs contract so that liquid is discharged through other ducts 64 and groove 58 to the outlet passage 53.

In the position illustrated in FIG. 2, the main working chamber 28 which has the maximum volume has just been connected with the discharge passage 53 so that the fluid is discharged from passage 53 when during further rotation the respective working chamber contracts.

Slots 34, 35, 36

The chambers in slots 34 of the central portion of the rotor, and slots 35, 36 in the rotor walls 15, 16, are either connected through groove 59 with the discharge passage 54, or through groove 60 with the inlet passage 53, ducts establishing the connection. The change of volume of these chambers is caused by the fact that vanes 37 approach the rotor axis and move away from the rotor axis during each revolution of the rotor so that the vanes act like pistons in chambers 34. In the illustrated embodiment it is assumed that vanes 37 are controlled in substantially the same manner as the main working chambers '28.

Chambers 50, 51

These chambers, which are located outwardly of pistons 42, 43, are either connected through grooves 55, 61 with the inlet passage 54, or through grooves 56, 62 with a discharge passage 53, ducts 63 and 66, respectively, establishing the connection. Chambers 50, 51 are preferably controlled in such a manner that they are filled with pressure fluid when the respective radially associated main chamber 28 is subjected to high pressure, and vice versa. Pistons 42, 43 are operated as pistons since they are moved in radial direction in the radial chambers 44, 45 of the rotor :walls 15 and 16 by the reciprocating motion of the eccentric casing ring 27.

Chambers 48 and 49 These chambers which are located radially outwardly of pistons 42 and 43 communicate with the outer air through ducts 67 and 68 in the cap-shaped rotor end parts 17 and 18. However, the inner chambers 48 and 49 may also be used in the same manner as the outer chambers 50, 51 as working chambers if the pressure fluid is supplied thereto in such a manner that the pressure in the inner chambers is negative when the pressure in the outer chambers 50, 51 is positive which can be accomplished by the rotor shaft 11 and the control valve 52 by suitable ducts.

Balancing chambers 69:: are provided in the bearing region of the rotor unit in the bearing portions 24, of the casing, and balancing chambers 6911 are provided on the bearing portions of tubular casing member 31. These balancing chambers are provided with pressure fluid to oppose one-sided forces acting on the bearings resulting in excellent pressure compensation.

The construction of the embodiment illustrated in FIGS. 4 and 5 is similar to the embodiment of FIG. 1, and corresponding parts are indicated by corresponding reference numerals to which 100 was added.

The main working chambers 128 are connected by ducts 164, grooves 157, 158 which respectively cornmunicate with the supply and discharge passages in control valve 152. These passages are not shown in FIG. 4, and correspond to

passages

53 and 54 in FIG. 1. Pistons 142 and 143 form inner chambers 148 and 149 and outer chambers 1511 and 151 in the cavities in the rotor walls 115 and 116. The outer chambers 151) and 151 are connected by ducts 163 and 166 in the rotor end parts .117 and 118, and in the tubular shaft portion 113a to control

grooves

155, 156. In contrast to the embodiment of FIG. 1, the inner working chambers 148 and 149 are not connected to the outer air, but are connected by ducts 184, 185 to control

grooves

180, 181 and 182, 183 which are respectively connected to the supply and discharge passages in control valve 152.

While in the embodiment of FIG. 1, the inner and outer chambers formed in slots and 36 communicate with each other due to the fact that vanes 37 have a lesser axial length than the rotor 14, the embodiment of FIG. 5 provides inner and outer chambers in the slots 135, 136 which do not communicate with each other, but which are separated by the vanes.

Consequently, passage 165 connects only the inner chamber 134 through control grooves 159, 160 to the supply and discharge passages in control valve 152. The outer chambers 135 and 136 are connected to passages 190 and 191, control grooves 186, 187 and 188, 189 and to the supply and discharge passages.

Another improvement of the embodiments of FIGS. 4 and 5 is the pressure balancing of shaft 146 which supports and connects the pistons 142 and 143. The end portions 146a of shaft 146 are mounted without play in corresponding bores in pistons 142 and 143 while the center portion 146!) of shaft 146 is mounted in a corresponding cutout of casing ring 127 movable in circumferential direction to a limited extent. Recesses 192 and 193 are provided in the central portion 146]; and connected through corresponding ducts in center portion 146b, and in the casing ring, not shown, to a source of pressure fluid, for example to working chambers.

The rotor unit of the embodiment of FIGS. 4 and 5 has a shaft 111 which is mounted in an anti-friction hearing 194, while a journal portion of end part 117 is mounted in an anti-friction bearing 195 in part 124 of casing 110. The bearing parts 124 and 125 are constructed as outer races for the rollers of the anti-friction bearings.

A pressure chamber 121 counterbalances axial pressures as explained with reference to FIG. 1.

By suitably dimensioning the respective pressure chambers, and by controlling the pressure fluid supplied thereto depending on the angular position of the rotor, a complete pressure compensation can be achieved for the rotor unit including the rotor 111, 114, 117, 118 and 115, 116 and casing ring 126. The pressure equalization is complete in radial as well as axial direction.

The construction of the embodiment of FIGS. 6 and 7 corresponds in principle to the construction of the above described two embodiments, and corresponding parts are indicated by like reference numerals increased by 200.

The rotor unit is mounted in bearings 211 and 212 of the stationary casing 211 The rotor unit includes a hollow rotor shaft 213, a rotor 214 having

rotor walls

215 and 216 of greater diameter and a center portion of smaller diameter, and two

rotor end parts

217 and 218. The several parts of the rotor are held together in axial direction by a flange 219 and an annular member 220. A spring ring 221 secures member 221) to shaft 213. Bolts, not shown, extending in axial direction through corresponding bores in the rotor parts are provided for preventing relative angular displacement between the rotor parts.

The center portion of rotor 214 is surrounded by a casing ring 222 which forms with the central rotor portion and with rotor vanes 231, working chambers 223 which exp-and and contract during the synchronous rotation of rotor 114 and easing ring 222. Casing ring 222 has an outer curved peripheral surface supported in a correspondingly shaped stationary supporting ring 224 secured to tubular member 225 which is mounted on casing 216 by means of bearings 226 and 227.

Slots 228 in the central portion of rotor 214 are extended to form slots 229 and 230 in the

rotor walls

215 and 216. Vanes 231 are mounted for radial movement in slots 228, 229, 231? and form expanding and contracting working chambers 223 between the inner circular surface of casing ring 222 and the outer circular surface of the central portion of the rotor. The

rotor walls

215 and 216 bound working chambers 223 in axial direction. As explained with reference to FIGS. 4 and 5, the chambers formed by the vanes 231 in the slots 229 and 230 may be used as working chambers since they expand and contract as the vanes move along the inner surface of the eccentric casing ring 223.

Pistons

232 and 233 are located in cavities 234, 235 of the

rotor walls

215 and 216, and are guided therein for movement in radial direction as best seen in FIG. 7. Pairs of

pistons

232, 233

are mounted on a shaft 236 which is disposed in a bore of casing ring 222. Slide members 237, 238 are mounted on the ends of shafts 236 and are mounted for sliding movement in slots 239 of

pistons

232, 233 for movement in circumferential direction.

Pistons

232, 233 form outer working chambers 240, 241 and inner Working chambers 242, 243 in the cavities 234, 235. The inner and outer chambers expand and contract in accordance with the relative radial movement between casing ring 222 and rotor 214 which is caused by the eccentricity of casing ring 222. The arrangement is such that the inner chambers 242 and 243 expand at the same time as the working chambers 223 located in the same radial planes, while the respective outer chambers contract when the inner chambers expand, and vice versa.

Similar to the embodiment of FIG. 1, the inner chambers 242, 243 are connected by ducts 244 and 245 to a space in the outer casing communicating with the outer air. The outer chambers 240, 241 are connected by ducts 246 and 247 with the respective main. working chambers 223 which are located in the same radial planes so that the same pressure prevails in the outer chambers 240, 241 as in the corresponding Working chambers 223.

The working chambers 223 on the left side of FIG. 7 are connected with the supply passage for the fluid, and the working chambers 223 on the right side are connected with the discharge passage for the fluid in a control valve member corresponding to control

valves

52 and 152, but not shown in FIG. 6.

Substantially radial ducts 248 in rotor 214 and rotor shaft 213 communicate with the working chambers 223 and with the control grooves of the control valve, not shown. As explained above, liquid is supplied to the expanding working chambers 233, and discharged from the contracting working chambers 223.

As indicated by arrows, the pressure in the main working chambers 223 acts inwardly on rotor 214 and rotor shaft 213, and outwardly on casing ring 222. In the outer chambers 240 and 241 in which

pistons

232, 233 of easing ring 222 are located, the pressure forces are reversed and act in outward direction on the peripheral tubular portions 217a, 218a of the

rotor end parts

217 and 218, and in radially inward direction on the

pistons

232 and 233, and thus on shafts 236 and casing ring 222.

Consequently, the pressures in the main working chambers 223, and in the outer chambers 240, 241 oppose each other in the action on rotor 214 and casing ring 220 so that chambers 240, 241 constitute balancing and pressure compensating chambers.

The axial dimensions of chambers 2'40, 241, corresponding to the axial thickness of

rotor walls

215, 216 influences the total force acting on rotor and casing ring in end chambers 240 and 241. When the axial thickness of

rotor walls

215, 216 is substantially half the axial width of the center portion of the rotor, the radial pressures are completely compensated. In the event that the inner chambers 242, 243 are provided with pressure fluid, as explained with reference to FIG. 4, corresponding corrections of dimensions of the chambers have to be carried out.

According to a modified construction, the

outer chambers

240, 24 1 and the inner chambers 242, 243 are connected by ducts in

rotor walls

217, 218 so that the pressure is further equalized. Due to the symmetric arrangement of the chambers 24%, 24d with respect to the central portion of the rotor, no tilting moments about an axis transverse to the rotor am's are produced by the action of the pressure fluid in the chambers of the rotor.

The general arrangement of the embodiment illustrated in FIGS. 8 and 9 corresponds to the construction of the above described embodiments. A stationary casing 3'10 includes a tubular wall 311 supported on end members 313 and 3 14 which are mounted in

end plates

312 and 315. The rotor unit is mounted in roller bearings 3116 and 3117 in bearing portions of

end plates

312 and 315. A rotor shaft 318 has concentric tubular rotor portions 319 and 320 and supports a rotor 321 which has a central portion of smaller diameter and two walls 322 and 323 of greater diameter. Rotor 321 is mounted between I a [flange 326 of rotor shaft 318 and an annular member 327 on which bearing 316 is mounted. An annular member 328 abuts member 327 and is formed with a cylinder chamber 330 in which an annular piston 329 is located. Piston 329 is axially secured by a split ring 331 so that when pressure fluid is supplied to cylinder member 30, the parts of the rotor unit are pressed together in axial direction and abut flange 32 6.

The central portion of rotor 321 is surrounded by a casing ring 332 which includes an inner casing ring 333 and a divided outer casing ring 334 which has a curved outer surface supported on a corresponding surface of an outer supporting ring 336 which is secured to the tubular casing member 367 which is secured to a pair of end members 338, 339 mounted in

casing portions

313 and 314 in bearings 340 and 341.

Between the inner surface of the casing ring, the outer surface of the central part of the rotor, the lateral inner confronting surfaces of the rotor walls 322 and 323, and the ends 343, working chambers 335 are formed which expand and contract during rotation of the rotor unit, due to the eccentricity of casing ring 232.

Rotor 321 has radial slots 342 which extend in axial direction int-o the rotor walls 322 and 323, and slidingly receive the vanes 343.

As explained with reference to the other embodiments of the invention, the working chambers 335 expand and contract during rotation of the rotor unit since relative movement between the rotor and the eccentric casing ring takes place. Working chambers 335 may be provided with igniting means, or injection devices for injecting fuel so that the machine can be operated as a combustion engine.

Rotor walls 322, 323 have cavities 344 in which pistons .345 and 346 are mounted and guided for radial movement. Pistons 345 and 34-6 are supported on shafts 347 which (fit into corresponding bores of the pistons, but are guided for movement in circumferential direction in corresponding slots of casing ring 333, similar to the embodiment of FIGS. 4 and 5. The construction described with reference to the embodiment of FIGS. 6 and 7 could be substituted for this construction. Due to the eccentric radial movement of casing ring 3 32, pistons 34-5 and 346 will perform a radial reciprocating stroke causing expansion and contraction of the inner chambers 350, 351 and outer chambers 348, 349 during rotation of the rotor unit, and in synchronism with the expansion and contraction of the main working chamber-s 335. The inner chambers 350, 351 will expand and contract together with the main working chambers 335, which are located in the same radial planes. The expansion and contraction of the outer chambers 348 and 349' will take place in the opposite sense.

In the embodiment illustrated in FIGS. 8 and 9, the outer chambers are connected by ducts 352 and 353 to a chanrber communicating with the outer air, while the inner chambers are used as additional working chambers. Ducts 354 are provided in the casing ring to connect corresponding inner chambers 351i and 3.51 so that each pair of inner chambers forms a working chamber which expands and contracts in synchronism with the main working chambers 335.

Chambers 350, 354, 35 1 are used as working or suction chambers for the main working chambers 335 which are operated as combustion chambers.

Chambers 351, and thereby also chambers 350, are each connected by a duct 355 in rotor shaft parts 319, 326 and in rotor end part 325 to the chamber of a valve 356 which is spring-loaded to normally assume a closed position. Each valve 356 opens when due to the expansion of the respective inner working chambers 350, 351, fresh air for a fuel air mixture is sucked into chambers 350, 351.

When chambers 350, 351 contract, compressed air, or a compressed fuel air mixture, is pressed through ducts 358 through ducts 360 into the main working chambers 335, the control valve 359 being automatically placed in a corresponding control position in which duct 358 communicates the valve chamber with duct 360 while duct 351 is separated by control valve 359 from duct 361).

The fuel air mixture is burnt in the main working chambers 3'35, and during the expansion of the respective working chambers 335 during the rotation of the rotary unit, the combustion gases expand and provide a turning moment. When working .chambers 335 contract, the exhaust gases are discharged through ducts 361 into a discharge passage 362 in the tubular rotor shaft portion 320.

In the illustrated embodiment, the outward movement of control valve 359 takes place due to the action of the centrifugal force during the rotation of the rotor unit. The control valves are shifted to .the inner position by pressure fluid supplied through ducts 363. The pressure fluid is supplied in accordance with the angular position of the rotor shaft by means which are not illustrated in FIG. 8 and are known to those skilled in the art. It is also possible to operate the control valve 359 by mechanical operating means in which event duct 363 can be omitted.

Each of the main working chambers 335 and the corresponding additional working chambers 350, 351 cooperate independently of the other groups of corresponding chambers. Consequently, each group of chambers has a control valve 359 and inlet valve 356, and corresponding ducts. However, it is possible to connect several of the chambers 50, 51 and provide a common control valve and a common inlet valve for a group of such chambers. Other valve arrangements may be substituted for the illustrated valve construction, and may include a turnable valve or a slide valve controlling slots.

Control valve 359 is constructed in such a manner that ducts 358 and 360 on one hand, and ducts 361 and 362 on the other hand are connected with each other in the radially outer position of control valve 359, while the communication between these ducts is interrupted in the inner position of the control valve. It is, however, also possible to control ducts 358 and 361 independently of the other ducts.

In a modified arrangement, the ducts 354 in casing ring 333 are omitted, and separate valve arrangements are provided for each of the inner chambers 350 and 351, permitting independent operations of these chambers.

While in the embodiment illustrated in FIGS. 8 and 9, the outer chambers 348, 349 are connected to the outer air, and have no influence on the operations, it is contemplated to connect chambers 348 and 349 by ducts to the pressure medium which is supplied through a valve in rotor shaft 318, as described with reference to FIGS. 1 and 4. A pressure equalization may be obtained in this manner. On the other hand, chambers 348, 349 may be used as suction chambers for receiving the fuel air mixture as described with reference to chambers 350 and 351. It is also possible to connect the outer chambers 348 and 349 to inlet and outlet passages independent of the main inlet and outlet, and to use these chambers as pump chambers to pump another fluid.

As explained with reference to the embodiment of FIGS. 4 and 5, the chambers formed by vanes 343 in rotor slots 342 my be connected by suitable ducts to inlet and outlet passages and serve as working chambers for pumping a fluid, or for equalizing and compensating transverse pressure forces.

The output of the machine can be regulated by varying the distance e between the axis of the casing ring and the axis of the rotor. When this distance is increased, the volume variations of each working chamber 335, and of the additional working chambers 350, 351 or 348, 349 is increased, and when the eccentricity is reduced, the volume change is also reduced, resulting in a decreased output. When the casing ring is shifted in the direction of the arrows x1 and x2 in FIG. 9, the output of the machine is correspondingly adjusted.

The balancing chamber 330 is preferably connected by a duct, not shown, to working chambers 335 in which a suitable pressure prevails which may be achieved by suitable ports in a control valve within the hollow shaft 318 corresponding to the arrangement described with reference to FIGS. 1 and 4. It is also possible to provide a check valve in a duct between balancing chamber 330 and ducts 358, 360. The pressure exerted on the rotor walls 322 and 323 in the working chambers 335 can be compensated by suitable pressure in balancing chamber 330 so that no play develops between the rotor walls 322, 323 and the cap-shaped end parts 324 and 325 of the rotor. Since the annular cylinder member 328 is independent of the annular member 327, annular cylinder member 328 can be made of a special high test material, and member 327 can be made of a less expensive material.

Two machines according to the present invention may be combined in an arrangement wherein one machine is used as a combustion motor driving another machine which operates as pump, blower, or compressor.

Due to the fact that the several embodiments of the invention are modifications of the same basic concept, it is possible to provide certain features which were described With reference to one embodiment in one or several of the other embodiments.

It will be understood that each of the elements described above, or two or more together, may also find a useful application in other types of rotary machines of the vane type differing from the types described above.

While the invention has been illustrated and described as embodied in a rotary vane-type machine including an eccentric casing ring operating pistons in working chambers of a rotor surrounded by the casing ring, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can by applying current knowledge readily adapt it for vari ous applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the following claims.

What is claimed as new and desired to be secured by Letters Patent is:

1. In a rotary machine, in combination, a rotary unit comprising rotor means mounted for rotation about an axis; a casing ring means eccentrically surrounding said rotor means and mounted for rotation so that said casing ring means moves during rotation transverse to said axis, said casing ring means defining with said rotor means an inner space; vanes mounted on one of said means for radial movement and being in contact with the respective other means so as to divide said inner space into a plurality of first working chambers for a fluid, said first working chambers expanding and contracting during transverse movement of said casing ring means; piston means mounted on one of said means movably disposed in a cavity of the respective other means and defining therein second working chambers for a fluid so that during rotation of said rotor means, said casing ring means rotates therewith and moves transverse to said axis with said piston means whereby said second working chambers expand and contract; and means for supplying a fluid to said working chambers and for exhausting fluid from the same.

2. In a rotary machine, in combination, a rotary unit comprising rotor means mounted for rotation about an axis and including two axially spaced walls of greater diameter and a central portion of smaller diameter, at least one of said walls being formed with cavities; casing ring means eccentrically surrounding said central portion of said rotor means and being located between said walls, said casing ring means being mounted for rotation so that said casing ring means moves during rotation transverse to said axis, said casing ring means defining with said central portion of said rotor means an inner space; vanes mounted on one of said means for radial movement and being in contact with the respective other means so as to divide said inner space into a plurality of first Working chambers for a fluid, said first working chambers, expanding and contracting during transverse movement of said casing ring means; piston means mounted on said casing ring means and being movably disposed in said cavities of said walls and defining therein second working chambers for a fluid so that during rotation of said rotor means, said casing ring means rotates therewith and moves transverse to said axis with said piston means whereby said second working chambers expand and contract; and means for supplying a fluid to said working chambers and for exhausting fluid from the same.

3. In a rotary machine, in combination, a rotary unit comprising rotor means mounted for rotation about an axis and including two axially spaced walls of greater diameter and a central portion of smaller diameter, at least one of said walls being formed with cavities; casing ring means eccentrically surrounding said central portion of said rotor means and being located between said walls, said casing ring means being mounted for rotation so that said casing ring means moves during rotation transverse to said axis, said casing ring means defining with said central portion of said rotor means an inner space; vanes mounted on one of said means for radial movement and being in contact with the respective other means so as to divide said inner space into a plurality of first working chambers for a fluid, said first working chambers expanding and contracting during transverse movement of said casing ring means; piston means including shaft means mounted on said casing ring means and axially projecting from the same into said cavities, and pistons mounted on said shafts, respectively, and respectively movably disposed in said cavities and defining therein second working chambers for a fluid so that during rotation of said rotor means, said casing ring means rotates therewith and moves transverse to said axis with said piston means whereby said second working chambers expand and contract; and means for supplying a fluid to said working chambers and for exhausting fluid from the same.

4. In a rotary machine, in combination, a rotary unit comprising rotor means mounted for rotation about an axis; a casing ring means eccentrically surrounding said rotor means and mounted for rotation so that said casing rin-g means moves during rotation transverse to said axis, said casing ring means defining with said rotor means an inner space; vanes mounted on one of said means for radial movement and being in contact with the respective other means so as to divide said inner space into a plurality of first working chambers for a fluid, said first working chambers expanding and contracting during transverse movement of said casing ring means; piston means including shaft means mounted on said casing ring means and axially projecting from the same, and pistons mounted on said shafts, respectively, and respectively movably disposed in a cavity of the respective other means and defining therein second working chambers for a fluid so that during rotation of said rotor means, said casing ring means rotates therewith and moves transverse to said axis with said piston means whereby said second working chambers expand and contract; and means for supplying a fluid to said working chambers and for exhausting fluid from the same.

5. A rotary machine as set forth in claim 1 wherein at least one of said means is formed with ducts communicating with said working chambers for supplying and discharging a fluid; and wherein said means for supplying and exhausting fluid includes a stationary valve having a supply passage and a discharge passage communicating with said ducts.

6. A rotary machine as set forth in claim 1 and including stationary casing means enveloping said rotor unit; a carrier ring supporting said casing ring means for turning movement; said casing ring means being supported on said carrier ring for radial movement and said casing ring means and said carrier ring have a common axis parallel to said axis.

7. A rotary machine as set forth in claim 6 wherein said casing ring means and said carrier ring each have a peripheral surface curved in axial planes, said curved surfaces contacting each other,

8. A rotary machine as set forth in claim 1 and including means for supplying at least to said first Working chambers a combustible fuel air mixture.

9. A rotary machine as set forth in claim 1 including means for supplying a fluid to said second working chambers; means for controlling the supply of the fluid; duct means formed in said rotor means for connecting said first working chambers with said second working chambers; control means in said duct means; means for burning a fuel air mixture in said first working chambers and for discharging burned gases therefrom; and control means for controlling the supply and discharge of gases to and from said first working chambers.

10. In a rotary machine, in combination, a rotary unit comprising a rotor means mounted for rotation about an axis and being formed with radial slots and radially extending cavities; a casing ring means eccentrically surrounding said rotor means and mounted for rotation so that said casing ring means moves during rotation transverse to said axis, said casing ring means having an inner annular surface defining with said rotor means an inner space; vanes mounted in said radial slo'tsfo'r radial movement and having end faces in contact with said annular surface so as to divide said inner space into a plurality of first working chambers expanding and contracting during transverse movement of said casing ring means and adapted to receive and discharge a fluid; a plurality of piston means mounted on said casing ring means and movably disposed in said cavities and defining in the same second working chambers for a fluid so that during rotation of said rotor means, said casing ring means rotates therewith and moves transverse to said axis with said piston means whereby said second working chambers expand and contract; and means including a valve having inlet and outlet passages for a fluid, and ducts formed in said rotor means and communicating with said working chambers for supplying and discharging fluid from the same.

11. A rotary unit as set forth in claim 10 wherein said piston means includes shaft means mounted on said casing ring, and pistons disposed in said cavities and defining within the same outer and inner second working chambers located respectively radially outward and radially inward of the respective piston, said cavities having substantially radial walls for guiding said pistons.

12. A rotary unit as set forth in claim 10 wherein said vanes define in said slots third working chambers, and wherein said rotor means is formed with ducts communicating with said third working chambers.

13. A rotary unit as set forth in claim 11 wherein some of said ducts communicate with said outer second working chambers, and wherein said rotor means is formed with other ducts connecting said inner second working chambers with the open air.

14. A rotary unit as set forth in claim 10 and including means for supplying a fuel air mixture to said second working chambers, said rotor means being formed with other ducts for connecting said second working chambers with said first working chambers; control valve means in said ducts; means for causing combustion of said fuel air mixture in said first working chambers; and wherein said rotor means is formed with discharge ducts communicating with said first working chambers.

15. A rotary unit as set forth in claim 10 wherein said rotor means is formed with ducts connecting said second Working chambers with said first working chambers; and including control valve means in said ducts, said control valve means being mounted for radial movement and adapted to move outwardly to a first control position under the action of the centrifugal force; and means for moving said control valve means inwardly to a second control position whereby the supply and discharge of fluid to said first working chambers is controlled.

16. A rotary unit as set forth in claim 15 wherein said rotor means is formed with ducts communicating with said second working chambers for supplying a fuel air mixture to the same, and check valve means in said last mentioned ducts adapted to open when said piston means cause expansion of said second working chambers whereby suction is applied to said check valve means for opening the same.

17. In a rotary machine, in combination, a rotary unit comprising a rotor means mounted for rotation about an axis, said rotor means including two axially spaced walls of eater d ameter and a central portion of smaller diam- 13 eter, each of said walls being formed with a plurality of cavities extending in radial direction, said rotor means being formed with a plurality of radial slots formed in said central portion and in said walls; a casing ring means eccentrically surrounding said central portion of said rotor means and being mounted for rotation so that said casing ring means moves during rotation transverse to said axis, said casing ring means having an inner annular surface defining with said rotor means an inner space between said walls; vanes mounted in said radial slots for radial movement and having end faces in contact with said annular surface so as to divide said inner space into a plurality of first working chambers expanding and contracting during transverse movement of said casing ring means and adapted to receive and discharge a fluid, said vanes defining in the portions of said radial slots located in said walls other chambers expanding and contracting during transverse movement of said casing ring means and corresponding radial movement of said vanes; a plurality of piston means mounted on said casing ring means and movably disposed in said cavities and defining in the same second working chambers for a fluid so that during rotation of said rotor means, said casing ring means rotates therewith and moves transverse to said axis with said piston means whereby said second working chambers expand and contract; and means including a valve having inlet and outlet passages for a fluid, and ducts formed in said rotor means and communicating with said working vanes have end faces in contact with said walls of said rotor means whereby said other chambers are divided into outer chamber portions and inner chamber portions separated from each other; and wherein said rotor means is formed with duct means for supplying and discharging a fluid at least to said outer chamber portions.

19. A rotary unit as set forth in claim 17 wherein said cavities are formed in said walls adjacent the outer peripheral surfaces of said walls and open on the same, and wherein said rotor means includes cap-shaped end parts on opposite sides of said walls, and having tubular portions surrounding and abutting said outer peripheral surfaces of said walls to close said cavities.

20. A rotary unit as set forth in claim 11 wherein said rotor means is formed with ducts connecting said outer second working chambers with said first working chambers, and formed with other ducts connecting said inner second working chambers with the outer air whereby transverse pressure forces acting on said rotor are compensated.

No references cited.

MARK NEWMAN, Primary Examiner.

SAMUEL LEVINE, Examiner.

F. T. SADLER, Assistant Examiner.

Claims

1. IN A ROTARY MACHINE, IN COMBINATION, A ROTARY UNIT COMPRISING ROTOR MEANS MOUNTED FOR ROTATION ABOUT AN AXIS; A CASING RING MEANS ECCENTRICALLY SURROUNDING SAID ROTOR MEANS AND MOUNTED FOR ROTATION SO THAT SAID CASING RING MEANS MOUNTED FOR ROTATION TRANSVERSE TO SAID AXIS, SAID CASING RING MEANS DEFINING WITH SAID ROTOR MEANS AN INNER SPACE; VANES MOUNTED ON ONE OF SAID MEANS FOR RADIAL MOVEMENT AND BEING IN CONTACT WITH THE RESPECTIVE OTHER MEANS SO AS TO DIVIDE SAID INNER SPACE INTO A PLURALITY OF FIRST WORKING CHAMBERS FOR A FLUID, SAID FIRST WORKING CHAMBERS EXPANDING AND CONTRACTING DURING TRANSVERSE MOVEMENT OF SAID CASING RING MEANS; PISTON MEANS MOUNTED ON ONE OF SAID MEANS MOVABLY DISPOSED IN A CAVITY OF THE RESPECTIVE OTHER MEANS FOR DEFINING THEREIN SECOND WORKING CHAMBERS FOR A FLUID SO THAT DURING ROTATION OF SAID MEANS, SAID CASING RING MEANS ROTATES THEREWITH AND MOVES TRANSVERSE TO SAID AXIS WITH SAID PISTON MEANS WHEREBY SAID SECOND WORKING CHAMBERS EXPAND AND CONTRACT; AND MEANS FOR SUPPLYING A FLUID TO SAID WORKING CHAMBERS AND FOR EXHAUSTING FLUID FROM THE SAME.