JPH03189301A - Volume type rotary turbine - Google Patents

Abstract

PURPOSE: To reduce leak of vapor and provide high volumetric efficiency by providing relatively small gear-type teeth on the outer peripheries of a blade rotor and a groove rotor to make non-contact engagement. CONSTITUTION: A blade rotor 12 and groove rotors 15, 16 are respectively adhered on a shaft 14 and shafts 17, 18 journalled in parallel with housings 1, 2. A rotor blade 13 arranged on the blade rotor 12 is almost non-contactly engaged with blade grooves 19, 20 provided on the groove rotors 15, 16. Relatively small gear-type teeth 21, 22 are provided on the outer peripheries of the blade rotor 12 and the groove rotors 15, 16, and perform almost-non-contact engagement motion with a synchronous gear wheel. Thus, clearance between the rotor blade 13 and the blade grooves 19, 20 is sealed by the teeth 21, 22 to extremely reduce leak of vapor. Therefore, an engine with very high volumetric efficiency can be provided.

Description

[Detailed Description of the Invention] (Background of the Invention) In the past, many types of rotary steam engines have been made, some of which were developed by famous engineers such as Watt, Murdoch, Hornblower, Trevisic, Erickson, and Moseley. done by people. However, all of these IN cabinets had some kind of drawback, and in the end, they were not successfully put into practical use. The earliest large rotary steam engines encountered severe sealing problems and failed. That is, there was uncontrollably high steam leakage, resulting in low volumetric efficiency. Therefore, one of the main objects of the present invention is to provide a non-contact gear type labyrinth seal for this large rotary steam connection, which has extremely low steam leakage and therefore extremely high volumetric efficiency. The goal is to realize the above-mentioned institutions that have. Currently, it is not economical to operate conventional turbines or any rotary steam engine at steam temperatures significantly higher than 560°C. This is because rotor blades and other parts can cavitate and pit due to erosion and corrosion. It is therefore an important object of the present invention to develop a large rotary steam system capable of operating with steam temperatures higher than 560°C without the need for cooling the rotor blades or employing expensive special steel.
The goal is to provide the following. At present it is not possible to build large rotary steam engines to be operated at high steam pressures due to insufficient internal pressure compensation. It is thus an additional object of the invention to indicate a rotary steam engine whose internal radial and axial pressures are compensated as a whole. Another important object of the present invention is the provision of continuous and smooth torque power extraction in the power extraction shaft required for field output energy conversion applications. Conventional steam turbines reach maximum efficiency only at full load and correspondingly high rotational speeds. At part-load conditions, the efficiency of conventional steam turbines deteriorates rapidly. A further important objective, therefore, is to demonstrate a rotary steam engine capable of operating at all load conditions with efficiency equal to or greater than full load conditions. A further object of the invention is to provide a rotary steam engine which can be operated not only with moderately moist steam, non-degassed steam, but also with steam containing a large amount of impurities.

(Summary of the Invention) The object of the present invention is to function primarily as a volumetric steam turbine, but also to utilize in part the kinetic energy generated by rapid steam molecules impinging on the rotor blades, similar to the radial flow turbines of the past. This is achieved by constructing a volumetric type rotary system steam turbine engine that also performs the functions of The present invention has an upper housing half and a lower housing half, such that the halves are screwed snugly together with their flange rims. Said two-stage turbine without full pressure compensation preferably consists of three blade rotor chambers, a 6I11 groove rotor chamber and one gear chamber, all arranged parallel to each other on their respective shafts. has been done. Preferably, each housing chamber is formed from a set of three aligned and intersecting cylindrical first or second stage chambers, each set of chambers having one first or second stage blade rotor;
The blade rotor may include two first or second stage groove rotors arranged on the left and right sides of the blade rotor in the horizontal direction.

The gear chamber located at the rear of the housing is equipped with a gear wheel with the same diameter as the rotor and extends to the rotor diameter. Preferably, a rotor with a very large diameter and high rotational speed is equipped with five smaller gear wheels in order to keep the circumferential speed of said gear wheels as low as possible.

The first stage and two second stage blade rotors and large gear wheels are all mounted on the same shaft. Each set of grooved rotors and corresponding small gear wheels are also mounted on a common shaft. Each red's plaid rotor chamber and corresponding small gear wheel are also mounted on the common shaft. Each set of plate rotor chambers and each groove rotor chamber are sealed from the other sets of chambers and from the gear chambers. On the circumferential surface of the bladed rotor and on the surface of the grooved rotor, small gear-type teeth are arranged in a manner that provides non-contact meshing as the rotors rotate about their respective axes. is achieved. The large gear wheel as well as the small gear wheel are precisely ground and mesh very precisely, so that non-contact meshing rotation with the rotor can be synchronized.

The housing further has a corresponding inlet boat and outlet boat for each chamber, which are arranged diametrically opposite each other and which communicate with the respective plate rotor chamber. Thick-walled rotor blades are arranged longitudinally on the surface of the blade rotor and spaced equidistantly from each other in the radial direction.

The grooved rotor has a corresponding number of blade grooves, which number also varies depending on the number of rotor blades and the relative rotor rotation ratio. In order to obtain a continuous and smooth torque moment on the movement take-off shaft, the rotor blades mesh with the blade grooves without surface contact, so that the torque induced by the pressurized working medium in the chamber is Prevents biased pressure being induced between a turbine blade under pressure on one side and the next turbine blade on the same blade rotor meshing with the corresponding blade groove of the groove rotor. A large enough gap is left for the steam to flow. The internal pressure compensation effect between the two rotor blades, as described above, can result in a periodic torque canceling effect, thus detecting uneven power output at the power take-off shaft, which is detrimental in high power conversion applications. will be done. Parallel small gear-type teeth are disposed between the rotor blade and the blade groove. Although the teeth of this gear dive are non-contact, they mesh extremely tightly with the complementary teeth of the opposing rotor, so
A highly effective dynamic frictionless labyrinth gear type sealing action is obtained between the meshing rotors, resulting in high volumetric efficiency. The rotor blades of the bladed rotor as well as the small gear type teeth of the grooved rotor move in close proximity to their respective hollow cylindrical internal chamber walls as they rotate about their respective shafts, thus Together with their gear type teeth, they exhibit a dynamic frictionless labyrinth sealing effect. The portion of the cylindrical internal chamber containing the pressurized non-working medium is thus sealed from the portion of the cylindrical internal chamber containing the working medium which is under partially expanded conditions. This sealing action subdivides the cylindrical inner chamber portion into at least two different and mutually sealed pressure states.

When the pressurized medium acts to change the spatial volume within the chamber section, it exerts a continuous pressure on the steel in the direction of rotation of the rotor blade as the rotor blade passes tightly through the respective chamber. A continuous rotating work state can be obtained by inducing a continuous rotational work state. The objective of achieving high volumetric efficiency is further achieved by utilizing two sets of second stage chambers disposed on each steel of said set of first stage chambers as partially fat-swollen working medium volume chambers. I can do it. a pressurized working medium introduced into the intake boat of the first stage chamber performs work by forcing the rotor blades into the first stage chamber in a displacement mode;
The same working medium then engraves into two connected second stage chambers. The total chamber volume of the two second stage chambers is much larger than the volume of the former first stage chamber. The leakage rate of the reduced pressure working medium per relevant chamber is therefore much smaller. The energy inherent in the media lost in partially engraving is therefore much smaller. Therefore, as the total volume of the second stage chamber increases with respect to the first stage chamber, energy losses due to working medium leakage decrease relatively.

The effective leakage of the working medium is therefore proportionally reduced, thus resulting in a significant additional increase in the respective volumetric efficiency. Erosion and corrosion in steam turbines increase proportionally, inter alia, with increasing temperature of the working medium. Thus, introducing a rotor cooling medium without directly affecting the temperature reduction of the working medium has an adverse effect on erosion and corrosion within the turbine.

A solution to this problem has been achieved by configuring the cylindrical inner chamber wall so that only approximately half of the outer circumferential blade rotor surface is exposed to the hot working medium. The other half of the outer peripheral blade rotor surface is partially i
Expanded and therefore exposed to an increasingly cold working medium, it is then subjected to a corresponding cooling effect. Cooling capacity increases approximately linearly with increasing surface area exposed to the refrigerant and temperature difference of the medium. The effects of erosion and corrosion also increase with increasing flow rate of the working medium. Due to the displacement effect in the present invention, the flow rate of the working medium only slightly exceeds the peripheral speed of the blade rotor, thus also reducing the erosion and corrosion effects.

In contrast to the thin-walled rotor blades of conventional turbines, the rotor blades of the present invention are made extremely thick and short, thus allowing the use of various types of surface coatings or special materials such as ceramics, thus making the rotor blades more flexible. Erosion and corrosion effects are further reduced.

A further reduction in erosion and corrosion is achieved by constructing the blade rotor and rotor blades hollow, thus providing internal cooling with the aid of a refrigerant. The pressure compensating action of a bladed rotor is achieved by having an even number of rotor blades on the bladed rotor surface, with the inlet and outlet boats oriented diametrically to each other in an inner cylindrical chamber, so that the pressure moments oppose and cancel each other. This was achieved by working together. In order to completely cancel the pressure moments of the groove rotors, two additional pressure compensating rotors are mounted on the respective shafts between the first stage groove rotor and the second stage groove. The circumferential surfaces of the two pressure compensating rotors are ground and sealed with surfaces equal in dimension x pressure and orientation opposing all opposing pressure moments, and are connected to the first stage intake robot via a duplex. ing. Pressure compensation is thus carried out automatically for all pressure conditions. Therefore, all axial forces, radial forces and even the forces induced by the weight of the rotor are compensated, making it possible to operate each pressure surge section of the invention with its respective high steam pressure and rotational speed. Become.

Thus constructed, the present invention reduces high pressure steam in a manner similar to a one to two stage radial flow tandem turbine.

A speed control device regulates the pressure and volume of the working medium utilized for the displacement process. Thus, a highly useful turbine system with superior attributes, very high thermal efficiency and very high overall efficiency is provided.

The invention can also be used as a turbine and pump or compressor combination.

Another application of the invention is in compressors, pumps, prime movers, etc., among others.

(Detailed Description of Preferred Embodiments) The present invention illustrated in FIGS. 1 and 3 includes ten upper half housings 1 and one half ζ side housing 2. The housings 1 and 2 constitute a set of first and second stage chambers, which chambers are provided with respective first and second stage rotors. In the center there is a large circular blade rotor chamber, and to the horizontal left and right of the rotor, parallel to the rotor, there are two small circular groove rotor chambers. Both housing halves are securely screwed together with their polished 7-lange rims together.

The upper and lower housings 1 and 2 have inlet boats 3 and 5 and outlet ports 4 and 6, which are located diametrically opposite each other. Legs 8 and 9 are rigidly attached to the lower housing half to support the housing. Inside the large circular chamber is the blade rotor 12 of the first stage.
is mounted on a shaft 14 provided centrally within the housing. Parallel with this rotor 12 are mounted the above-mentioned 15 and 16 on their respective shafts 17 and 18. On the surface of the blade rotor 12, the rotor blades 13 within the thickness are arranged radially at equal distances from each other in the longitudinal direction. The grooved rotors 15 and 16 have a corresponding number of blade grooves 19 and 20, which number varies depending on the number of rotor blades 13 and their relative rotation ratio. Rotor blade 13 meshes with blades 119 and 20 almost without contact. The rotor blades 13 are fitted with adjustable insert plates 10 and 1, preferably metal.
1 in close proximity and contact-free, thus sealing the chamber side of the inlet boats 3 and 5 from the chamber side of the outlet boats 4 and 6. Thus, when a pressurized medium such as steam is introduced via the diametrically opposed intake boats 3 and 5, a continuous rotational operating condition is achieved.

The metal rotor chamber seals the plates 1o and 11 and is preferably made of a material that prevents seizure in the unlikely event of contact with the rotor blades 13. The side chamber seal plates 38 and 39 are made of a material that prevents seizure not only with the rotor blades 13 but also with the blade rotor and the grooves. Relatively small gear-type teeth 21 and 22 are provided between and parallel to the rotor blade 13 and the blade grooves 19 and 20. The gear type teeth perform meshing motion without contact, but they firmly mesh with the complementary teeth of the opposing rotor, so the dynamic non-am labyrinth gear type is extremely effective for the U-torter. A sealing effect is established. The gear type teeth 22 of the groove rows 915 and 16 rotate in close proximity to the seal plates 23 and 24 but without contact, so that the chamber side close to the intake boats 3 and 5 and the outlet boats 6 and 4 are close to each other. A sealing effect is established between the 0 and the chamber sides. Said non-contact meshing of all rotors is achieved via synchronous gear wheels 40 shown in FIG.

To act as a two-stage expansion turbine, the second stage blade rotors 34 and 35 are mounted on each other's central shaft 14 in each strip of the first stage blade rotor 12, and the corresponding second stage blade rotors 34 and 35 Two stage groove rotors are mounted on shafts 17 and 18. Since the total volume between two successive rotor blades of bladed rotors 34 and 35 is several times greater than the volume of bladed rotor 12, each second stage internal steam expansion is possible. Blade rotor 34.12 and 35@
Pressure supplement @0-even 25a, 25b and 26a, 26b
are provided, which are mounted on shafts 17 and 18, respectively.

FIG. 2 shows IC pressure compensators 25a and 25b mounted on respective shafts 17 and 18.

Labyrinth seals 27, 28, 29 and 30 seal the non-contacting portions of the abrasive surfaces of pressure compensating rotors 25a and 25b from chamber 50. Inlet ports 3 and 5 are connected to inlet boats 31 and 32 and thus pressure compensating rotors 25a, 25b and 26a, 26b.
Also, a diametrically equal pressure effect is automatically induced on the surfaces of the grooved rotors 15 and 16, resulting in an overall pressure compensation effect. As opposed to a groove rotor, a blade rotor 12
, 34 and 35, the steam pressure always acts in the diametrical direction,
Due to the fact that these opposing forces cancel each other out, there is always perfect pressure compensation. The outlet boats 4 and 6 of the chambers of the blade rotor 12 and the outlet boats 33 of the pressure compensating coater are connected to the inlet boats of the chambers of the blade rotors 34 and 35, thus diverting leakage steam to additional working medium. conversion, thereby improving the volumetric efficiency of the present invention.

In FIG. 4, gear type 2 without teeth 21 and 22 is shown.
The two non-contact rotating rotor surfaces 51 and 52 have equal pitch circles 47 and 48, but around the non-contact meshing rotor blades 49 and the corresponding rotor grooves 20, the extremes through gaps 43a and 44a A large amount of steam leakage is occurring. Although the gaps 43b and 44b have equal pitch circles 47 and 48, due to the sealing ability of the non-contact meshing gear type teeth 21 and 22, they exhibit much less steam leakage, thus allowing for a significant increase in volumetric efficiency. It is.

Gaps 43 and 44 are located between rotor blades 13 as shown.
and 49, preventing steam pressure from being induced between
Since internal pressure compensation between the rotor blades otherwise occurs, a periodic torque cancellation effect is obtained and a non-uniform power take-off effect is detected at the power take-off shaft 17. The rotor blade is mounted in a T-slot 41, and has a groove 42 at its tip to enhance labyrinth sealing ability. Anti-seizure seal plates 38 and 39 are fitted on all rotor sides. Due to the pressure compensation effect of the rotor, the rotor shaft 1
4. Only the minimum force is acting on 17 and 18,
Thus, inter alia, high speed rotating ball bearings 45 and 4
6 can be used. Seals 36 and 37 seal between all chambers.

The invention is used as a combination turbine and pump or compressor by using two bladed rotors 34 and 35 to compress a medium such as air.

In that case, the inlet boat for the medium is used as an outlet boat, the take-off boat is used as an inlet boat, and in addition the blade rotor 12 is used to perform displacement displacement work as described above. Those skilled in the art will readily appreciate that the present invention can be implemented in a variety of forms, including compressors, pumps, motors, and the like.

It is therefore understood that the various embodiments described and disclosed herein are merely illustrative and that further modifications of the invention may be devised without departing from the spirit or scope of the invention. should be understood.

[Brief explanation of drawings]

FIG. 1 is a front view of a set of first stage rotors of the present invention in a vertical center cross section; FIG. 2 is a front view of a compressive force compensating rotor of the present invention in a vertical center cross section; FIG. 3 is a front view of a set of first stage rotors of the present invention; Figures 4a and 4b are enlarged vertical cross-sectional side views of a portion of the blade rotor of the invention showing a compensating rotor, the blades having no gear-type teeth; Comparison with rotor is shown. 1.2...Housing, 3.5...Intake boat,
4.6... Outlet boat, 12... First stage blade rotor, 15.16... Groove rotor, 17.18
...Shaft, 14...Central shaft, 13.49
...Rotor blade, 19.20...Blade groove,
10°11...Plate, 38.39...Side chamber seal plate, 21.22...Small gear type tooth, 23.24...Seal plate, 40...Saki period gear wheel, 34. 35...Second stage blade rotor, 25a, 25b, 26a, 26b--Pressure compensation rotor, 27.28.29.30...Labyrinth seal, 43a, 44a...Gap.

Claims (24)

[Claims] (1) a turbine comprising a plurality of aligned and partially intersecting cylindrical chambers, the plurality of cylindrical chambers together forming a chamber set; a housing with means for defining at least one divided hollow inner space; and a plurality of similarly adjacent shafts rotationally connected to said housing, said shafts extending parallel to each other and substantially each having a shaft disposed centrally in one of said plurality of chambers, said housing including means means defining an inlet and an outlet for respectively introducing and removing working medium from said set of chambers. and the inlet and outlet channel devices are arranged on the housing at diametrically opposed positions to allow pressure moments induced by passage of the working fluid therethrough to oppose and cancel each other. and the chamber set includes a first rotor mounted on the centralmost shaft of the plurality of shafts, the first rotor extending longitudinally on the shaft and being spaced from each other. an outer surface with a plurality of pressure blades mounted at radially spaced locations; the chamber set further includes a plurality of groove rotors mounted on the shaft proximate the centralmost shaft; contains,
Each of the groove rotors is disposed proximate the first rotor and has an outer surface including a plurality of radially spaced grooves corresponding to the spacing of the pressure blades. each groove receives one of the plurality of pressure blades to allow the pressure blade to engage the groove during rotation of the first rotor and the groove rotor; producing a substantially constant torque output on the centralmost shaft, and the turbine further includes a continuous dynamic torque output between the first rotor outer surface and the outer surface of each of the plurality of grooved rotors. means for establishing a friction labyrinth seal; means for establishing a pressure seal between the housing and the chamber to isolate the working medium; a sealing plate for each inlet arrangement; Seal plates are mounted to the housing and disposed within the chamber set proximate the first rotor, and the pressure blades move relative to each seal plate to create a dynamic frictionless labyrinth. for synchronizing the rotation of the respective shafts with a sealing plate arranged such that a seal is induced and thus isolates the portion of the chamber containing the working fluid in an expanded state from the portion of the chamber containing the pressurized medium; and a power take-off device operatively coupled to the first rotor to connect the turbine to a utility device. (2) The turbine according to claim 1, wherein the pressure seal device is attached to the housing and includes a circular pressure ring disposed between the housing and the plurality of shafts on both sides of the chamber set; two circular side chamber seal plates disposed on an inner wall of the chamber set proximate the first rotor and mounted to the housing proximate each of the plurality of grooved rotors; A positive displacement rotary turbine having a grooved rotor seal plate. (3) In the turbine according to claim 1, the synchronizer has a plurality of gear wheels, the gear is attached to an end of each of the plurality of shafts, and the gear is attached to an end of each of the plurality of shafts. Volume type rotary turbine characterized in that the gear wheels are drivingly connected to each other. (4) In the turbine according to claim 1, the plurality of pressure blades and the plurality of rotor grooves are engaged with each other in a non-contact state, and no repulsive or unilateral pressure is generated between them. 1. A positive displacement rotary turbine, wherein said substantially constant torque output results from said substantially constant torque output being arranged to define such a gap. (5) The positive displacement rotary turbine according to claim 1, wherein an even number of pressure blades are mounted on the first rotor. 6. The turbine of claim 1, wherein the pressure blade has a plurality of longitudinally extending grooves at its distal end, thus creating an induced seal between the pressure blade and the curved inner chamber seal plate. Displacement type rotary turbine characterized by enhanced action. 7. The turbine of claim 1, wherein said means for establishing a continuous dynamic frictionless labyrinth seal comprises gear-type teeth formed on an outer surface of said first rotor. teeth extending along the outer surface between the pressure blades, the labyrinth seal further including gear-type teeth formed on the outer surface of each of the plurality of grooved rotors; is configured to mesh closely but without contact with corresponding gear type teeth formed on the first rotor. (8) The turbine according to claim 7, wherein the first rotor gear type teeth and the grooved rotor gear type teeth are arranged and formed so as to act as periodic gears only during the time when the synchronizer is in error movement. A displacement type rotary turbine characterized by: 9. The turbine of claim 1, wherein the housing further defines at least one groove disposed within the housing portion having a curved portion proximate the plurality of pressure blades; means for defining a gap between said housing curvature and said pressure blade, said groove in said housing curvature extending from said grooved rotor to an intake boat adjacent thereto; A positive displacement rotary turbine, characterized in that the turbine is arranged to reach a grooved rotor from an outlet port in the vicinity thereof. 10. The turbine of claim 1, wherein the pressure blades are mounted with T-grooves in the first rotor to facilitate their replacement. turbine. 11. The turbine of claim 1, wherein the gear-type teeth formed on the outer surfaces of both the plurality of first rotors and the plurality of grooved rotors are provided as a result of variations in rotor temperature. A positive displacement type rotary turbine characterized in that it is constructed with angled sidewalls sufficient to compensate for differences in rotor diameter that may occur as a result. 12. The turbine of claim 1, wherein the curved inner chamber seal plate is located between the inlet and outlet channel devices such that the working medium gradually expands before entering the outlet channel device. Volume type rotary turbine characterized in that it extends across only a part of the radial distance. 13. The turbine of claim 1, wherein the housing further includes a device defining a plurality of additional chamber sets through which the plurality of shafts extend;
The additional chamber sets are axially spaced apart from each other within the housing, and the housing further defines additional inlets for allowing entry and exit of a working medium into each of the additional chamber sets. means device and 2
and an additional inlet and outlet channel arrangement, said additional inlet and outlet channel arrangements being arranged at diametrically opposite positions on said housing, said pressure moment induced by the working medium passing therethrough being A positive displacement rotary turbine, characterized in that it is adapted to allow mutual cancellation in opposition. (14) The turbine according to claim 13, wherein the first rotor provided in one of the chamber sets operates in a displacement manner, while the first rotor provided in another chamber set operates in a displacement manner. Volumetric rotary turbine, characterized in that it functions by pumping or compressing a medium, thereby providing pressure compensation. 15. The turbine of claim 13, wherein the housing further includes means for defining at least one compensation chamber formed from a plurality of aligned, partially intersecting cylindrical chambers; the pressure compensation chambers are disposed axially along the plurality of shafts and spaced between each of two of the chamber sets, the pressure compensation chambers having a grooved rotor mounted thereon; one pressure-compensating rotor mounted on each of the plurality of shafts, the housing further comprising at least one pressure-compensating rotor for each pressure-compensating rotor for respectively entering and discharging a working medium into each of the pressure-compensating chambers; means for defining at least one inlet and at least one outlet for each pressure compensation chamber; and means for establishing a labyrinth pressure seal to isolate working medium within said pressure compensation chamber. A displacement type rotary turbine featuring: 16. The turbine of claim 15, wherein the labyrinth pressure seal device includes two curved compensating rotor seal plates mounted on the housing proximate the compensating rotor. Volume type rotary turbine. (17) The turbine according to claim 15, wherein the first rotor in one of the chamber sets is adapted to operate with a high pressure medium, and the first rotor in the other chamber set is adapted to operate with a low pressure medium. Volumetric rotary turbine, characterized in that it is adapted to work with a medium. (18) The turbine of claim 17, wherein the outlet channel of the chamber set provided with the first rotor is configured to operate with a relatively high pressure working medium. Volume type rotary turbine, characterized in that it communicates with an outlet channel and is further connected to an inlet channel for a set of chambers made to operate with a working medium at a relatively low pressure. 19. A positive displacement rotary turbine according to claim 2, wherein the circular side chamber sealing plate of the grooved rotor has a sealing surface at least twice the width of the rotor groove. (20) The turbine according to claim 2, wherein all the seal plates are made of a different material from the material forming the first and groove rotors and the pressure blades. rotating turbine. 21. The turbine of claim 2, wherein all said seal plates are made of a material that minimizes the possibility of seizure caused by contact with said first and groove rotors. Type rotating turbine. 22. The positive displacement rotary turbine according to claim 2, wherein the grooved rotor seal plate is disposed on the housing near the intake device. (23) The positive displacement rotary turbine according to claim 3, wherein the number of gear wheels is greater than the number of the plurality of parallel shafts. (24) The turbine of claim 7, characterized in that at any given time, at least two of the first rotor gear type teeth mesh with a similar number of the grooved rotor gear type teeth to establish a continuous dynamic labyrinth seal. A volumetric type rotary turbine.