EP0432287B1

EP0432287B1 - Rotary engine

Info

Publication number: EP0432287B1
Application number: EP89122788A
Authority: EP
Inventors: Waldemar H. Kurherr
Original assignee: Individual
Current assignee: Individual
Priority date: 1989-11-28
Filing date: 1989-12-09
Publication date: 1995-10-25
Anticipated expiration: 2009-12-09
Also published as: AU642132B2; AU4564189A; EP0432287A1

Description

BACKGROUND OF THE INVENTION

The state of the art, in particular DE-A-2 321 639 describes gear-pumps, gear-motors or volume-counters. There is no doubt that the instant invention is basically akin to gear-pumps with two or more shafts but the instant invention is designed as a powerful power-plant turbine with own and different attributes.
The above mentioned Offenlegungsschrift shows no gear-type sealing teeth but accomplishes the sealing by having the rotors and the rotor blades move at close vicinity to each other.
This does definitely not show a continuous dynamic frictionless labyrinth seal between the gear-type teeth of said first rotor outer surface and the gear-type teeth of the outer surface of each of said plurality of groove rotors. Furthermore as a gear-type motor the invention is not self-starting when the rotor blades are in a horizontal position within the groove rotors and that therefore a neutralization of rotary forces with resulting intermittent torque transmission do occur.
The USA-2 956 735 and GB-A-843 675 do also not show a continuous dynamic frictionless labyrinth seal between said first rotor outer surface and the outer surface of each of said plurality of groove rotors.
The state of the art shows a discontinued dynamic labyrinth seal disrupted by the respective rotor-blades, thus resulting in repulsion and neutralization of the rotary forces and therefore in a discontinuous or intermittent torque transmission.
Furthermore, the acting rotation forces on the rotor-blades are thus neutralized and therefore the above shown invention cannot function without the use of valves, as a rotation machine as the instant invention teaches.
Machines as depicted by USA-2 956 735 and GB-A-843 675 are not functional without the extensive use of a multitude of valves.
The instant invention shown has a continuous dynamic frictionless labyrinth seal between the first rotor outer surface and the outer surface of each of said plurality of groove rotors without the disruptive influence of the rotor blades and needs therefore no valves.
In the Offenlegungsschrift 23 30 992 the Figures 1, 2, 3 and 4 show examples of roughly sketched gear-pumps that are only discussed without being part of the inventive matter filed in the said patent application.
If for example, the dimensions of the 35 mm rotor diameter of the gear-pumps are extrapolated or increased by a multiplication-factor of 28,6 to attain the dimensions of a 1000 mm rotor diameter of a power-plant turbine than the gear-type teeth would measure 85 mm and the rotor blades would measure 228 mm.
This clearly shows that there are insurmountable differences, among other, between the constructive dimension of an ordinary gear-pump and a gear-pump-like Turbine and that therefore a continuous dynamic seal that is applicable particularly for large rotary machines, is not shown.
The inventive matter filed for patent, of the above Offenlegungsschrift, is shown in the Figures 2, 3/1 and 3/2.
The Figures 2, 3/1 and 3/2 also show a discontinued dynamic frictionless labyrinth seal, disrupted by the influence of the rotor blades, between the first rotor outer surface and the outer surface of the groove rotor.
It is therefore one of the primary aims of the instant invention to demonstrate a contact-less gear-type labyrinth seal for this large rotary steam engine with very low steam leakage losses and with a therefrom resulting very high volumetric efficiency. Presently, it is not economical to run conventional turbines or any rotary steam engines with steam temperatures much higher than 560°C due to erosion and corrosion effects such as cavitation or pitting of the rotor blades and other parts. Therefore, it is a very important aim of the instant invention to show a large rotary steam engine capable to run with steam temperatures higher than 560°C without the necessity of rotor blade cooling and the employment of expensive special steels. It is presently impossible to build large rotary steam engines to be run with high steam pressures and high revolution due to incomplete internal pressure forces compensation. Therefore, it is an additional aim of the instant invention to show a rotary steam engine with a total internal radial and axial pressure forces compensation. Another important aim of the instant invention is to show a continuous smooth torque power output at the power take-off shaft as necessary for high power energy conversion application. Conventional steam turbines work at their maximum efficiency only at full load and a respective high rate of revolution. Under partial load condition the efficiency of conventional steam turbines deteriorates rapidly. It is therefore a further most important aim to show a rotary steam engine capable to work at all load conditions with an efficiency equal or even higher than at full load condition. It is furthermore the aim of the instant inventions to show a rotary steam engine capable to run with extreme wet steam, undegassed steam as well as steam containing large amounts of impurities.

SUMMARY OF THE INVENTION

The objects of the invention are attained by constructing a displacement-type rotary turbine according to claim 1, i.e. an engine that mainly functions as a displacing-type steam engine that in addition also partially utilizes the kinetic energy generated by the fast flowing steam molecules impinging upon the rotor blades thus functioning also similar to a radial flow turbine. The instant invention comprises an upper half housing and a lower half housing whereby both half's are tightly screwed together with their flange rims. The two-stage turbine without total internal pressure compensation consists preferably of three blades rotor chambers, six grooves rotor chambers and one gear chamber all situated parallel to each other on their respective shaft. Each housing chamber is formed from preferably a set of three aligned and intersecting cylindrical first or second-stage chambers capable to embody one first or second-stage blades rotor and two first or second-stage grooves rotors mounted on the left and right horizontally alongside the said blades rotor. The gear chamber situated at the rear of the housing is up to a certain rotor diameter equipped with gear wheels having the same diameter as the rotors. Rotors of very large diameter and high revolution are preferably equipped with five smaller gear wheels to keep the circumferential velocity of the gear wheels as low as possible. The first-stage, and the two second-stage blades rotors as well as the large gear wheel are all mounted on the same shaft. Each set of grooves rotors and the corresponding small gear wheel are also mounted on a mutual shaft. Each set of blades rotor chambers and the corresponding small gear wheel are also mounted on a mutual shaft. Each set of blades rotor chambers and the respective grooves rotor chambers are sealed from the other sets of chambers and from the gear chamber. On the circumferential surface of the blades rotors and on the surface of the grooves rotors small gear-type teeth are arranged such that a contact-less meshing can be accomplished as said rotors rotate about their respective axis. The large gear wheel and the small gear wheels are precision ground and mesh very exactly thus allowing the synchronization of the rotation of the contact-less meshing said rotors. The housing further comprises for each chamber corresponding inlet ports and outlet ports situated diametrical to each other and leading to the respective blades rotor chamber. Mounted longitudinally on the surface of the said blades rotors thick rotor blades are situated spaced radially equidistant from each other. The grooves rotors possess a corresponding number of blade grooves varying in number respective to the number of rotor blades and the ratio of mutual rotor revolution. To obtain a continuous smooth torque moment at the power take-off shaft the said rotor blades mesh with the said blade grooves without surface contact leaving for the steam a gap large enough to prevent the forming of a one sided pressure build-up between the turbine blade under one sided pressure exerted by the pressurized working medium within said chamber and the next turbine blade on the same blades rotor meshing with the corresponding blade groove of the grooves rotor. An internal pressure compensation between two rotor blades as described would result in a periodic torque cancellation thus being perceptible at the power take-off shaft as an uneven power output which would soon prove detrimental by large power conversion application. Parallel between said rotor blades and said blade grooves comparative small gear-type teeth are situated. Said gear-type teeth mesh contact-less but very tightly with the complementary teeth of the opposing rotor thus establishing a very effective dynamic friction-less labyrinth gear-type sealing action between the meshing rotors thereby attaining a high volumetric efficiency. The rotor blades of the said blades rotors and the said small gear-type teeth of the grooves rotors move as they rotate about their corresponding shaft very close to their respective hollow cylindrical interior chamber wall thus performing with their gear-type teeth a dynamic frictionless labyrinth sealing action thereby sealing that part of the cylindrical interior chamber that embodies the working medium under pressure from that part of the cylindrical interior chamber that embodies the working medium under pressure from that part of the cylindrical interior chamber that embodies the working medium in a state of partial expansion. The sealing action subdivides the said cylindrical interior chamber parts into at least two different and sealed from each other pressure states. The space volume displacing action of the pressurized medium within said chamber parts generates a continuous rotational work condition by continuously exerting a pressure upon that side of the rotor blades facing in the direction of rotation as said rotor blades pass tightly through their respective chamber. The object of attaining a high volumetric efficiency is furthermore reached by utilizing the two sets of second stage chambers situated on each side of the set of the first-stage chamber as partial expansive working medium volume chambers. The pressurized working medium introduced through the inlet ports of the first-stage chamber does work by forcing the said rotor blades in a displacing mode through the said first-stage chamber after which it expands into the interconnected two second-stage chambers. The total chamber volume of the said two second-stage chambers is many times that of the former first-stage chamber. Wherefore the ratio of the leakage rate of the pressure reduced working medium per chamber of the working medium is accordingly much lower. The energy inherent in the partially expanded lost working medium is subsequently much lower. Therefore, as the total volume of the second-stage chambers increase in relation to the first-stage chamber the energy loss through the leakage of the working medium comparatively decreases. Therefore the effective leakage of the working medium is reduced to a proportional fraction thus consequently resulting in a respective considerable additional increase of volumetric efficiency. The erosion and corrosion within a steam turbine increases among other proportionally with the increase of the temperature of the working medium. Thus, the introduction of a rotor cooling means without directly effecting a temperature reduction of the working medium produces an inverse effect on the erosion and corrosion within the turbine. The solution of the problem was achieved by constructing the cylindrical interior chamber wall such that only approximately half of the exterior circumferential blades rotor surface is exposed to the high temperature working medium. The other half of the exterior circumferential blades rotor surface is exposed to the partially expanded and therefore extensively cooler working medium thus subsequently experiencing a respective cooling. The cooling capacity increases approximately linearly with the increase of the surface exposed to the coolant and the temperature difference of the media. The erosion and corrosion effects also rise with the increase of the flow velocity of the working medium. Due to the displacing effect within the instant invention the flow velocity of the working medium exceeds only insignificantly the circumferential velocity of said blades rotors and consequently the erosion and corrosion effect is reduced respectively. Contrary to the thin rotor blades of conventional turbines the rotor blades of the instant invention are designed very thick and short and therefore various types of surface coatings or special materials such as ceramics become applicable thus reducing the erosion and corrosion effects of the rotor blades even further.
A further reduction of erosion and corrosion is accomplished by constructing the blades rotor and the rotor blades hollow and thus perform with the aid of the coolant an internal cooling. The pressure forces compensation of the blades rotor was achieved by arranging an even number of rotor blades on the blades rotor surface and by arranging the inlet ports, the outlet ports within the interior cylindrical chamber diametrical to each other such that the pressure force moments oppose and cancel each other. To cancel the pressure force moments of the grooves rotors completely additional two pressure force compensation rotors are mounted between the first-stage grooves rotors and the second-stage grooves rotors on their respective shaft. The circumferential surface of the two said pressure forces compensation rotors is polished and a surface area equivalent in size times pressure and direction to counter all the opposing pressure force moments is sealed and connected by a tubing to a first-stage inlet port. The pressure force compensation is thus performed automatically for all pressure states. Therefore, all axial forces, radial forces and even the forces exerted by the weight of the rotors can be compensated thus it becomes possible to run each pressure stage of this instant invention with a respective high steam pressure and revolution. The instant invention as constructed reduces high pressure steam similar to a one or two stage radial flow tandem build turbine. A speed control regulates the pressure and the volume of the working medium to be utilized for the displacing process. Thus, a very useful turbine system with excellent attributes, a very high thermal efficiency and very high overall efficiency is provided.
The instant invention can also be used as a combination of a turbine and a pump or compressor.
Further applications of the instant invention are among other: compressors, pumps, motors, etc.
In the instant invention the said pressure blades of the first rotor mesh with the grooves of the groove rotors in a contactless manner throughout the meshing sequence and do thereby define a continuing gap between the pressure blades and the grooves (thereby preventing a rotary pressure-force neutralization by a one-sided pressure buildup between the two pressure blades 13,49);
that furthermore the first rotor gear-type teeth and at least one of the teeth on each side of the groove of said groove rotors, mesh tightly but without contact continuously with the corresponding gear-type teeth (thereby generating the continuous dynamic frictionless labyrinth seal);
that furthermore said arrangement of the meshing of the pressure blades of the first rotor and the grooves of the groove rotors and the said arrangement of the meshing gear-type teeth of the first rotor and the groove rotors establish together, both the continuous dynamic frictionless labryrinth seal and the substantial constant torque output on the center-most shaft.
The seal plates are of great importance for the functioning of a large rotary machine without lubrication between the fast moving rotor blades (at certain instances the steam velocities exceed the velocity of sound) and the chamber walls within the working chamber.
The seal plates should be made of different material than the rotor blades to prevent seizure, corrosion, erosion etc. The use of the seal plates further define a gap due to the increase of the housing diameter relative to the seal plate thickness and thus preventing a positive and a negative pressure buildup within the turbine housing.
A positive pressure buildup within the housing would be formed between the groove rotor, the first rotor, a pressure blade, and that small part of the housing between the groove rotor and the outlet.
A negative pressure buildup or partial vacuum would by generated on the inlet channel side of the housing.
Towards the outlet channels the seal plates are made shorter and oblique thus the gradually slanting end of the seal plates serve to regulate the rate of steam expansion, in particular by high circumferential velocities and high steam pressures, where otherwise within the housing enormous pressure and sound waves occur.

BRIEF DESCRIPTION OF THE DRAWINGS

Other and further object of the instant invention will become more apparent from the following detailed description of the various embodiments thereof when taken with reference to the appended drawings in which like characters refer to like structure and in which:

FIG. 1 shows a front view of a vertical center cut about the set of first-stage rotors of the instant invention.
FIG. 2 shows a front view of a vertical center cut about the compression compensating rotors of the instant invention.
FIG. 3 shows a side view of a vertical cut of the instant invention depicting also the two pressure compensation rotors.
FIG. 4a and 4b shows part of an enlargement of a vertical cut through part of the blades-rotor of the instant invention, with a comparison to a blade-rotor without gear-type teeth.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

The instant invention as illustrated in FIG. 1 and FIG. 3 comprises an upper half housing 1 and a lower half housing 2. The said housing 1 and 2 embody sets of first and second stage chambers with their respective first and second stage rotors. Centrally situated are a large circular blades rotor chamber and one small circular grooves rotor chamber situated parallel at the left and one at the right side horizontally of the said large blades rotor chamber. Both said housing half's are tightly screwed together with their polished flange rimes 7. Both the upper and the lower said housing 1 and 2 embody an inlet port 3 and 5 and an outlet port 4 and 6 whereby the said ports are situated diametrically to each other. To support the housing legs 8 and 9 are rigidly mounted to the lower half housing. Inside the said large circular chamber the first-stage blades rotor 12 is mounted on shaft 14 centrally within the housing. Parallel beside the said first-stage blades rotor 12 the grooves rotors 15 and 16 are mounted on their respective shaft 17 and 18. Mounted longitudinal on the surface of the said blades rotor 12 thick rotor blades 13 are situated spaced radially equidistant from each other. The grooves rotors 15 and 16 possess a corresponding number of blade grooves 19 and 20 varying in number respective to the number of rotor blades 13 and the ratio of the mutual revolution. The rotor blades 13 mesh with the blade grooves 19 and 20 contact-less. The rotor blades 13 move contact-less very close to the adjustable preferably metal insert plates 10 and 11 thus sealing the inlet port 3 and 5 chamber sides from the outlet port 4 and 6 chamber sides wherefore through the introduction of a pressurized medium such as steam through the diametrically opposed inlet ports 3 and 5 a continuous rotational work condition is reached. The said metal rotor chamber seal plates 10 and 11 are preferably to be of such materials that prevent seizure by a possible occurring contact with the rotor blades 13. The side chamber seal plates 38 and 39 are made of such materials that seizure with the rotor blades 13 as well as the blades rotors and the grooves rotors be prevented. Parallel between the said rotor blades 13 and the said blade grooves 19 and 20 comparative small gear- type teeth 21 and 22 are situated. The said gear- type teeth 21 and 22 mesh contact-less but very tightly with the complementary teeth of the opposing rotor thereby establishing a very effective dynamic friction-less labyrinth gear-type sealing action between the said rotors. The gear-type teeth 22 of the grooves rotors 15 and 16 rotate very tightly but contact-less to the seal plates 23 and 24 thus establishing a sealing action between the chamber side close to the inlet ports 3 and 5 and the rotor chamber side close to the outlet ports 6 and 4. The contact-less meshing of all the rotors is accomplished through the synchronization gear wheels 40 shown in FIG. 3. To function as a two stage expansion turbine the second-stage blades rotors 34 and 35 are mounted on the mutual central shaft 14 on each side of the said first-stage blades rotor 12 and the corresponding second-stage grooves rotors are mounted on shaft 17 and 18. The total volume between two successive rotor blades of the blades rotors 34 and 35 are many times that of the volume of the blades rotor 12 thus permitting a respective second-stage internal steam expansion. Between the blades rotors 34, 12 and 35 are the pressure compensation rotors 25a, 25b, and 26a, 26b are mounted on the shaft 17 and 18 respectively. FIG. 2 shows the pressure compensation rotors 25a and 25b mounted on their respective shaft 17 and 18. The labyrinth seals 27, 28, 29 and 30 seal contact-less part of the polished surface of the pressure compensating rotors 25a and 25b from the chamber 50. The inlet ports 3 and 5 are interconnected with the inlet ports 31 and 32 thus automatically producing an equal pressure exertion diametrically on the surfaces of the pressure compensating rotors 25a, 25b and 26a, 26b and the grooves rotors 15 and 16 whereby a total pressure compensation is attained. Contrary to the grooves rotors the blades rotors 12, 34 and 35 are always fully pressure compensated due to the fact that the steam pressure forces always occur diametrically wherefore the counter directed forces cancel each other. The outlet ports 4 and 6 of the chamber of the blades rotor 12 and outlet port 33 of the pressure compensating rotors are interconnected with the inlet ports of the chamber of the blades rotors 34 and 35 thus transforming leakage steam into additional working medium thereby improving the volumetric efficiency of the instant invention.
FIG.4 the two contact-less revolving rotor surfaces 51 and 52 without the gear- type teeth 21 and 22 have although with equal pitch circles 47 and 48 extreme large steam leakages through the gap 43a and 44a about the contact-less meshing rotor blade 49 and the corresponding rotor groove 20. The gap 43b and 44b shows with equal pitch circles 47 and 48 a far lesser steam leakage due to the sealing ability of the contact-less meshing gear- type teeth 21 and 22 thus producing a considerable increase in the volumetric efficiency. The gap 43 and 44 prevents a steam pressure build-up as shown between the rotor blades 13 and 49 whereby otherwise an internal pressure compensation between said rotor blades would occur thus resulting in a periodic torque cancellation thus being perceptible as an uneven power output at the power take-off shaft. The rotor blades are mounted within t-grooves 41 and possess at their tip grooves 42 to enhance their labyrinth sealing ability. At the sides of all rotors seizure preventive seal plates 38 and 39 are installed. Due to the pressure compensation of the rotors only minimal forces act on the rotor shafts 14, 17 and 18 thus permitting among other the application of fast turning ball bearings 45 and 46. The seal 36 and 37 seal between all respective chambers.
The instant invention is used as a combination of turbine and pump or compressor by using the two blades rotors 34 and 35 to compress a medium such as air by using the inlet ports as outlet ports and the outlet ports as inlet ports for that medium and by furthermore using the blades rotor 12 to do work in a displacing fashion as described. It will be manifestly appreciated by those skilled in the art that the instant invention can be employed in various form such as compressor, pump, motor, etc..

Claims

A displacing gear-pump or gear-motor like rotary-type machine with a housing (1,2) having means defining at least one hollow inner space divided into a plurality of aligned and partially intersecting cylindrical chambers, said plurality of cylindrical chambers together comprising one chamber set and a like plurality of adjacent shafts (14,17,18) rotatably connected to said housing (1,2) each of said plurality of shafts extending parallel with one another and positioned substantially at the center of one of said plurality of chambers respectively and having a housing (1,2) including means defining at least two inlet (3,5) and at least two outlet (4,6) channels for entry and exit respectively of a working medium to said chamber set;
said chamber set having a first rotor (12) mounted on a center-most shaft (14) of said plurality of shafts; first rotor (12) including an outer surface having a plurality of pressure blades (13,49) mounted so as to extend longitudinally thereon and at radially spaced apart positions; said chamber set further including a plurality of groove rotors (15,16) mounted on the shafts (17,18) adjacent to said center-most shaft (14) and each of said groove rotors (15,16) disposed in close proximity to said first rotor (12) and having an outer surface including a plurality of grooves (19,20) spaced radially thereon in a manner corresponding to the spacing of said pressure blades (13,49) and that each of said grooves (19,20) being shaped to receive one of said plurality of pressure blades (13,49) to permit the meshing of said pressure blades with said grooves during rotation of said first rotor and said groove rotor;
means for synchronizing the rotation of the respective shafts and power take-off means operatively associated with said first rotor (12) for connecting said turbine to a utility device;
the machine being a
displacement-type rotary turbine characterized by having inlet (3,5) and outlet (4,6) channels arranged in parallel such that inlet channels (3,5) face outlet channels (4,6) thus providing a high velocity steam passage and the partial utilization of kinetic energy and that said inlet and outlet channel means being arranged on and in said housing such that the respective inlet channels and the respective outlet channels and the inside of the housing are diametrically opposed from each other to permit the pressure force moments created by passage of the working medium there through to oppose and cancel each other;
that pressure blades (13,49) mesh with grooves (19,20) in a contact-less manner throughout the meshing sequence so as to define a continuing gap (43b,44b,13,20) therebetween and said groove thereby preventing intermittent torque transmissions and that furthermore first rotor gear-type teeth (21) mesh tightly and contact-less with gear-type teeth (22) of the groove rotors whereby a continuous dynamic frictionless labyrinth seal between said first rotors (12) outer surface and the outer surface of each of said plurality of groove rotors (15,16) is established whereby first rotors gear-type teeth (21) mesh such that at least two gear-type teeth (22) one on each side of the grooves of said groove rotors mesh tightly but without contact with the corresponding gear-type teeth (21) of the blades rotor (12) whereby together both a continuous dynamic frictionless labyrinth seal and a substantially constant torque output on the center-most shaft (14) is provided;
that means for seal plates (10,11) being mounted to said housing (1,2) and disposed in said chamber set so as to be in close proximity to said first rotor (12) so that said pressure blades (13,49) move relatively to each said seal plate so that a dynamic frictionless seal is created thereby isolating the chamber part containing the working medium in a state of expansion from the chamber part containing the pressurized working medium and wherein the seal plates (10;11) extend across only a portion of the circumferential distance between said inlet (3,5) and outlet (4,6) channel and that the shortened ends of the seal plates facing the outlets are made oblique such that the working medium gradually expands prior to entering said outlet channel (4,6) means.
A displacement type rotary turbine as in claim 1, wherein said pressure seal means comprises a circular pressure ring (38,39) disposed between said housing and said plurality of shafts on both sides of the chamber set and that the two circular side chamber seal plates (38,39) are mounted to said housing and being disposed on the inside walls of said chamber set so as to be in close proximity to said first rotor (12) and a groove seal plate mounted to said housing so as to be in close proximity to each of said plurality of groove rotors.
A displacement type rotary turbine as in claim 1, wherein said synchronizing means comprises a plurality of gear wheels (40) with one mounted to the end of each of said plurality of shafts with said plurality of gear wheels being drivingly connected to one another.
A displacement type rotary turbine as in claim 1, wherein an ever number of pressure blades (13,49) are mounted on said first rotors (12).
A displacement type rotary turbine as in claim 1, wherein the tip of said pressure blades (13,49) are provided with a plurality of lengthwise extending grooves (42) so that the seal established between said pressure blades and the curved interior chamber seal plates (10,11) is enhanced.
A displacement type rotary turbine as in claim 1, wherein the first rotor-gear-type teeth (21) and the groove rotor gear type teeth (22) are arranged and formed so as to serve as the synchronizing gear for a period of time during which said synchronizing means (40) is malfunctioning.
A displacement type rotary turbine as in claim 1, wherein said housing further includes means defining at least one groove disposed in the portion of said housing with a curvature in close proximity to said plurality of pressure blades (13,49) thereby defining a gap between said housing (1,2) curvature and said pressure blades, said groove in the housing curvature disposed such that said groove reaches from the groove rotors (15,16) to the inlet port (3,5) adjacent thereto and from the outlet port (4,6) to the groove rotors (15,16) adjacent thereto.
A displacement type rotary turbine as in claim 1, wherein said pressure blades (13,49) are mounted with a T-groove (41) in said first rotor (12) so as to facilitate ease of replacement of said pressure blades (13,49).
A displacement type rotary turbine as in claim 1, wherein said gear-type teeth (21,22) formed on said outer surfaces of both said plurality of first rotors (12;49) and said plurality of groove rotors (15,16) are constructed with angled side walls sufficient to compensate for any differences in rotor diameter which might occur as a result of variations in rotor temperatures.
A displacement type rotary turbine as in claim 1, wherein said housing further includes means defining a plurality of additional chamber sets through which said plurality of shafts (14,17,18) extend, said additional chamber sets being spaced apart from one another axially within said housing, said housing further including a means defining additional inlet (31,32) and two outlet (33) channel means for allowing entry and exit of a working medium to each of said additional chamber sets and that said additional inlet and outlet channel means being arranged on said housing at diametrically opposed positions so as to permit the pressure force moments created by passage of the working medium there through to oppose and cancel each other.
A displacement type rotary turbine as in claim 10, wherein said first rotor (12) in one of said chamber sets functions in the displacing fashion while said first rotor in another chamber set functions by pumping or compressing a medium thereby providing pressure force compensation.
A displacement type rotary turbine as in claim 10, wherein said housing further includes means defining at least one pressure compensating chamber formed from a plurality of aligned partially intersecting cylindrical chambers and that said pressure compensation chamber is disposed axially along said plurality of shafts and positioned between and spaced from each of two said chamber sets and that said pressure compensation chamber having one pressure compensating rotor (25,26) mounted on each of said plurality of shafts having groove rotors mounted thereon and that said housing further including means defining at least one inlet (31,32) for each pressure compensating rotor (25,26) and at least one outlet (33) for each pressure compensating chamber for entry and exit respectively of a working medium to each of said pressure compensation chambers and a means for establishing a labyrinth pressure seal to isolate the working medium within the pressure compensating chambers.
A displacement type rotary turbine as in claim 12, wherein said labyrinth pressure seal means comprises two curved compensating rotor seal plates mounted on said housing in close proximity to said compensating rotors (25,26).
A displacement type rotary turbine as in claim 12, wherein said first rotor (12) in one of said chamber sets is adapted for working with a high pressure medium while said first rotor (34,35) in another of said chamber sets is adapted for working with a low pressure medium.
A displacement type rotary turbine as in claim 14, wherein the outlet channels (4,6) of the chamber set provided with said first rotor (12) designed to operate with the relative high pressure working medium commutes with the outlet (33) channel for the pressure compensating chamber and are further connected to the inlet channels for the chamber sets designed to operate with the working medium at relative low pressures.
A displacement type rotary turbine as in claim 2, wherein the circular side chamber seal plates (23,24) of the groove rotors (15,16) have a sealing surface of at least twice the width of said rotor grooves (19,20).
A displacement type rotary turbine as in claim 2, wherein all of the seal plates are comprised of a material other than the material of said first and grooves rotors and of said pressure blades.
A displacement type rotary turbine as in claim 2, wherein all of the plates are comprised of materials which minimize the possibility of a seizure caused by contact with said first and groove rotors.
A displacement type rotary turbine as in claim 2, wherein said groove rotor seal plate (23,24) is disposed on said housing adjacent said inlet means.
A displacement type rotary turbine as in claim 3, wherein the number of gear wheels (40) exceeds the number of said plurality of parallel shafts.
A displacement type rotary turbine as in claim 7, wherein at all times at least two of said first rotor gear-type teeth (21) mesh with a like number of said groove rotor gear-type teeth (22) in establishing the continuous dynamic labyrinth seal.