US2430183A

US2430183A - Double rotation elastic fluid turbine

Info

Publication number: US2430183A
Application number: US628682A
Authority: US
Inventors: Moller Ragnar Olov Jacob
Original assignee: Individual
Current assignee: Individual
Priority date: 1944-12-16
Filing date: 1945-11-15
Publication date: 1947-11-04
Anticipated expiration: 1964-11-04

Description

' Nov; 4, 1947. R. o. J. MOLLERY 9 09 DOUBLE ROTATION ELASTIC FLUID TURBINE Filed Nov. 15, 1945 2 Sheets-Sheet l 2 Sheets-Sheet 2 R. o. J. MULLER DOUBLE ROTATION ELASTIC FLUID TURBINE Filed Nov. 15 1945 Nov. 4, 194 7.

Patented Nov. 4, 1947 DOUBLE ROTATION ELASTIC FLUID TURBINE Ragnar Olov .lacob Miiller, Finspong, Sweden Application November 15, 1945, Serial No. 628,682 In Sweden December 16, 1944 This invention relates to double rotation elastic fluid turbines of the radial or axial flow type, and more particularly to turbines of said class which are provided with an auxiliary impulse blade system adapted to convert, at a high efficiency, the highest pressure stage into work.

An example of the turbine of this class is described in the British Patent No. 570,624 where it is disclosed as a driving mechanism for vessels, especially torpedoes. For such purposes the double rotation reaction type of turbine is a preferred driving motor, as the torques of the oppositely moving turbine rotors are equal to each other, so that the reaction moments maybalance each other. If, however, as the case may be in respect of the driving mechanism disclosed in said patent, the double rotation reaction type of turbine is provided with an auxiliary set of impulse turbine blades, reaction forces are produced in the stationary expansion nozzles belonging to the impulse blade system which produce torques appearing as a tendency of the torpedo body to heel over. In case of torpedoes it is, however, of great importance to avoid heeling over.

The object of this invention is to suppress to the largest extent possible the heeling over tendency and, should a heeling over nevertheless occur, to restore the normal state of balance.

In order to avoid the formation of torques, that may give rise to heeling over, the auxiliary impulse blade system according to a feature of this invention is provided with two axially spaced sets of stationary expansion nozzles with the nozzles of one set directed oppositely to those of the other set as far as the peripheral direction is concerned. By this means the reaction forces as produced in the expansion nozzles of one set may be balanced by the oppositely directed reaction forces produced in the nozzles of the other set.

According to a further feature of the invention means are provided to restore the equilibrium of the vessel if in spite of the above said arrangement of the expansion nozzles a heeling over should appear. To this end a member unaffected by the heeling over movement is provided which is adapted to control, either directly or by means of a servomotor, the distribution of the driving fluid to the expansion nozzles of the impulse blade system so that the counteracting reaction forces above referred to become different in such a way that the prevailing reaction may restore the vessel to its normal position.

6 Claims. (01 253-) In the accompanying drawings a form of the invention is illustrated. Fig. 1 is an axial section of a portion of a torpedo turbine according to the invention. Fig. 2 is an axial section on a larger scale of an impulse section of a somewhat modified structure. Fig. 3 is a cross section on the line III--III of Fig. 2 of a portion or one group of expansion nozzles. Fig. l is an axial section of an impulse section of another modified form. Figs. 5-7 illustrate a control mechanism according to the invention. Fig. 5 is a section on the line V-V of Fig. 6, and Fig. 6 is a section on the line VIVI of Fig. 5 and Fig. 7. llhe quadrant k of Fig. 6 represents a section on the line k-k of Fig. 5. Fig. '7 shows a portion of the groups of nozzles shown in Fig. 6, as seen from above. Fig. 8 shows a modified form of this portion.

With reference to Fig. 1, the numeral 1 designates the body of the vessel, which may be assumed to be a torpedo, 2 is the turbine casing, 3 is one turbine shaft and 4 the other turbine shaft. Shaft 4 is concentrically surrounded by the tubular shaft 3 and may itself be tubular, as shown. Shafts 3 and A may represent the propeller shafts of the torpedo or shafts coupled thereto. 5 is a turbine disc supported by the

other shaft

3, and 6 is a turbine disc supported by the inner shaft 4. The

turbine discs

5 and 6 carry the oppositely rotating blades of the radial flow reaction system I. Formed in the wall of shaft 4 in register with the blade system I are ports 8 to allow the driving fluid to enter the shaft 4 that serves as a distance pipe. Connected to the turbine disc 5 by means of a drumlike wall 9 is an inwardly extending turbine disc ill which carries in conjunction with the opposite surface of turbine disc 6 a set of impulse blades il -AI for double rotation. In addition, discs 6 and It] carry

reaction blades

20, 2| situated on a larger radius than said impulse blades. Inserted between the turbine disc l0 and a radially extending wall l2 of the turbine casing is a labyrinth packing i3. Provided inside the impulse blade system are two annular sets of expansion nozzles l4, l5 adaptedto admit the driving fiuid to the impulse blades from a central passage H6.

The innermost impulse blade ring H situated next to said nozzles which is attached to the turbine disc 5 is adapted to be impelled by the driving fluid admitted from the set of nozzles i4 only, whereas the second impulse blade ring I l which is carried by the turbine disc 10 comprises two axially spaced sets of blades, one of action forces emanating from the expansion nozzles become therefore oppositely directed and, since they are equal, they may balance each other.

Since part of the driving fiuid as delivered by the nozzles acts directly on the second blade ring I R, an increased amount of power maybe yielded by this blade ring. By this means a power balance may be obtained within the impulse-blade system proper which is not obtainable in conventional double rotation impulse turbines having but one passage forthe driving fluid, in which the rotor half to which the blade ring first impolled by the driving fluid belongs, receives and deliversmore power than the other half of the rotor. In certain kinds of turbines, especially those adapted to drive electric dynamos, 'itmay be desired to distribute the power in some appropriate way and this may be done by means of an impulse turbine modified as above described.

In Fig. 2 is shown an impulse turbine in which the-driving fluid is supplied at the outer periphe'ry of th'eturbine to then pass inwardly, the design being for the rest similar to that above described. The reference numerals l4 and i5 designiate as before two annular expansion nozzles and It isthe'common fluid supply passage there-- for. 6 and H! are the two oppositely rotating turbine discs carrying the impulse blades. The innermost impulse blade ring 'I I comprises a single set of blades situated right opposite the nozzle ring Hi, whereas each of the remaining blade rings H and H is provided with two sets of blades, separated by a partition ll and each situated right opposite an individual one of the nozzle rings M and 15. If desired, the partition Il may be dispensed with.

'Fig. 3 shows the position of guide blades I t and 16 provided in the nozzle rings to divide each of them into a plurality of separate orifices. As shown, the direction of the orifices of one nozzle cross the direction of those of the other nozzle under very obtuse angles looking from the inside or the outside of the nozzle rings, so that the fluid will leave the two nozzle sets in nearly tangential, opposed directions.

As shown in Figs. 1 and 2, there may be a compar'atively wide radial gap between the nozzle ring '55 and the second blade ring i I The width of this gap maybe reduced so as to agree with the width 'Of the radial space between each two adjacent blade rings by placing the set of nozzles nearer to said second blade ring. as illustrated in Fig. 4. Here, the same reference numerals are used as in Fig. 2. Another way in which to obtain the same efiect is to increase the radial thick ness of the second blade ring H right opposite the nozzle ring l5.

In the structures above described with. reference to Figs. l3, those reaction forces which emanate from one nozzle ring will be balanced by those emanating from the other nozzle ring. In the embodiment shown in Fig. 4 the balancing efiec is not equally perfect owing to the placing of the two nozzle rings on difierentradii. Evidently, a

4 certain tendency towards heeling over cannot be avoided in this case.

In order to avoid any tendency towards heeling over that may appear from the one reason or the other, a member that cannot be affected by the heeling over movements may be provided which may either be constructed to act as a fluid distributor for the expansion nozzles or adapted to control such a distributor via a servo motor. Figs. 5-! illustrate an example of the said first mentioned arrangement and Fig 8 illustrates a modification thereof.

Mounted on an edge It coinciding with the axis ofgthe turbine is a pendulum [9 the lower the end of which forms a valve body 2D, the

operative surface of which is concentric with the turbine'axis and situated in close proximity to the inner cylindrical surface of the nozzle rings. Below said valve surface the nozzles I4 and I5 are replaced by a solid ring segment 21 the profile of'which lookingfrom the centre of the turbii'ie may be as'shown in Fig. 7 or Fig. 8. In these illustrations the outline of the valve body is indicated'by'dotted lines, as shown at 20.

In Fig. 7 a steplike form of ring segment 2| is shown, the solid segments of the nozzle rings l4 and I5 being in staggered relation to each other, inasmuch as the solid segment of nozzle ring 14 is displaced to the left in relation to the solid segment of nozzle ring i5. In Fig. 8 the solid segments of the two nozzle rings are located in axial alinement. In the first mentioned case the profile of the valve body 20 is square-shaped, in the last-mentioned case steplike. In both cases the valve body extends normally slightly over the nozzle ring H; to the right of the solid segment 21 and to acorresponding extent over the nozzle ring 2'5 to the left of the solid segment 21. By this means'the reaction force emanating from one nozzle ring becomes equal to that emanating from the'other nozzle ring. In case of a heeling over, for instance, to the right in the drawing, so that the solid segment 2! moves to the left in Figs. 'iaridB, the pendulum 19 due to its remaining in vertical position will cover by its valve body 29 more orifices of the nozzle ring [4 to the right of the solid segment El, while at the same time completely uncovering the nozzle ring 15 to the left of said segment. As a result, the admission of driving fluid to the nozzle ring 14 will be re duced, allowing the reaction forces emanating from the nozzle ring iii to preponderate over those emanating from the nozzle ring i4 and effect a turning of the casing of the turbine, correspending in the example under consideration to a heeling over to the left sufficient for restoring the normal equilibrium As already mentioned, the pendulum need not necessarily act as a valve, but may be arranged to control a valve, as for instance, via a servomotor. The controlling device may, furthermore, be constructed so as to effectan increase (or decrease) of the impulse produced by the he eling over movement, for instance, so that a heeling over by one degree may efiect a turning of the valve by several degrees or by a fraction of a degree only, according as it is desired to efiecta more rapid or a more slow restoration of the normal position.

what I clean is: k a p 1. Adriving mechanism forvessels comprising in combination, .acasing rigidly connected to the vessel, two rotatable driven elements, a reaction type of turbine having two oppositely rotatable main systems of reaction blades, each system being drivingly connected to rotate one of the delivering driving fluid to said blade auxiliary system, an inlet positioned at the common axis of the driven elements for admitting driving fluid directly to said nozzles, means to direct the exhaust fluid from said auxiliary blade system to the main blade system, said nozzles being stationary with respect to the casing so that the oppositely acting turning moments resulting from the reaction forces produced in said sets of nozzles may balance each other for preventing heeling over of the casing and the vessel rigidly connected thereto.

2. A driving mechanism for vessels as claimed in claim 1, in which the impulse blade system comprises more than one blade ring, and in which the impulse blade ring situated next to the sets of expansion nozzles is arranged so as to be impelled by the fluid admitted from one of said sets of nozzles only, the next succeeding blade ring being arranged so as to be impelled, in part, directly by the fluid admitted from the other set of nozzles and, in part, by fluid that has already passed the said first-mentioned impulse blade ring.

3. A driving mechanism for vessels as claimed in claim 1, in which the impulse blade system comprises concentric blade rings and in which the innermost one of these blade rings is arranged to receive driving fluid from one set of nozzles only, while the blade ring next succeeding is arranged to be impelled, in part, directly by the fluid admitted from the other set of nozzles and, in part, by fluid that has already passed said first-mentioned impulse blade ring, said other set of expansion nozzles being displaced With relation to the first-mentioned set so as to extend nearly to the said last-mentioned blade ring.

4. A driving set for vessels as claimed in claim 1, in which the impulse blade system comprises concentric blade rings, and in which the innermost one of these blade rings is arranged to receive driving fluid from one set of nozzles only, while the blade ring next succeeding is arranged to be impelled, in part, directly by the fluid admitted from the other set of nozzles and, in part, by fluid that has already passed said firstmentioned impulse blade ring, said last-mentioned impulse blade ring, which is arranged to be directly impelled by the fluid delivered from said other set of expansion nozzles, being extended into close proximity to said set of nozzles.

5. A driving system for the propelling Olf vessels comprising in combination, a vessel, an elastic fluid turbine having a main system of reaction blades for rotating a propeller shaft in one direction, a casing stationary with respect to said vessel, another main system of reaction blades for rotating another propeller shaft in the opposite direction, an auxiliary impulse blade system for converting the highest pressure stage of the driving fluid into work, two annular sets of expansion nozzles situated side by side for delivering driving fluid to said impulse blade system, the nozzles of the two sets being directed in opposite peripheral directions and being rigidly connected to the casing for allowing the oppositely acting turning moments resulting from the reaction forces produced in the two sets of nozzles to balance each other in order not to impart any turning tendency to the casing, and

means responsive to heeling of the casing for controlling the admission of driving fluid through said sets of nozzles for maintaining the normal position of the casing with respect to its axis.

6. A driving mechanism for the propelling of vessels comprising in combination with the body of the vessel, an elastic fluid turbine of the double rotation type including a casing rigidly connected to said vessel and a pair of oppositely rotatable shafts, a main system of reaction blades for rotating a propeller shaft in one direction, another main system of reaction blades for rotating another propeller shaft in the opposite direction, and an auxiliary impulse blade system for converting the highest pressure stage of the driving fluid into work, two annular sets of expansion nozzles situated side by side for delivering driving fluid to said impulse blade system, the nozzles of the two sets being directed in opposite peripheral directions and being rigidly connected to the casing for allowing the oppositely acting turning moments resulting from the reaction forces produced in the two sets of nozzles to balance each other in order not to impart any turning tendency to the casing, and a valve mounted so as to be responsive to heeling of the turbine as a whole and the vessel body rigidly connected therewith about the axis of the turbine or another axis parallel thereto, which is adapted, to cover and uncover parts of the sets of expansion nozzles under the action of a turning moment, in order thereby to adjust the distribution of driving fluid to both sets of nozzles with a view to restoring the normal position of the turbine and the vessel.

RAGNAR oLov JACOB MCSLLER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,273,633 Ljungstrom July 23, 1918 2,276,695 Lavarello Mar. 17, 1942 FOREIGN PATENTS Number Country Date 357,019 Great Britain Sept. 17, 1931 386,853 Great Britain Jan. 26, 1933 572,458 Germany Mar. 16, 1933 611,741 Germany Apr. 5, 1935 621,436 Germany Nov. 7, 1935 768,464 France May 14, 1934 768,465 France May 14, 1934 768,466 France May 14, 1934