US2699319A

US2699319A - Power conversion machine

Info

Publication number: US2699319A
Application number: US130732A
Authority: US
Inventors: Jr George J Huebner; David M Borden
Original assignee: Chrysler Corp
Current assignee: Old Carco LLC
Priority date: 1949-12-02
Filing date: 1949-12-02
Publication date: 1955-01-11
Anticipated expiration: 1972-01-11

Description

Jan 11, 1955 G.'J. HUEBNER, JR., ETAL POWER CONVERSION MACHINE Filed DSC. 2, 1949 WEL/Al /777'aFA/EKS,

United States Patent O 2,699,319 POWER CONVERSION MACHINE George J. Huebner, Jr., Bloomfield Hills, and David M. Borden9 Huntington Woods, Mich., assignors to Chrysler Corporation, Highland Park, Mich., a corporation of Delaware Application December 2, 1949, Serial No. 130,732 4 Claims. (Cl. 253-69) The present invention relates to compressors, pumps, turbines and similar bladed, rotary power conversion machines utilizing compressible fluids for powering the same. More particularly, this invention relates to a means for controlling the direction of iiow of the compressible fluids through concentric bladed stages of the machine to obtain optimum performance thereof.

It is known that the effect of the working gases upon the blading for such power conversion machines may be altered by providing a means for individually pivoting the blades as desired about an axis extending lengthwise of the blades. A suitable locking means may be provided for such pivoted blades for fixing the same at some desired blade angle. However, such constructions are usually accompanied by serious design difliculties which have no practical solution. The lack of uniformity of the movement of the blades about their pivots, erosion and the difliculty in mounting a pivoted blade assembly upon a rotor component have prevented such pivoted blade machines from obtaining widespread acceptance.

According to a feature of the present invention a relatively simple and uniform blading arrangement is provided by which different blading effects may be achieved merely by adjustably controlling appropriate portions of the blading system.

According to a further feature of the invention, means are provided for changing the power rating and operating characteristics of the machine as desired for a specilied motive liuid ow or shaft torque. Portions of this means are disposed within the blading of the machine.

According to still a further feature of the invention a nozzle section is provided which has a plurality of effective discharge angles made possible by causing auxiliary blade sets therein to freewheel or to be fixed in a stationary position.

According to another feature of the invention a rotor section having a plurality of effective blade angles is provided for selectively achieving different degrees of energy interchange between the rotor and the motive fluid, all other conditions being the same.

According to still another feature, relatively rotative parts are provided of which the relative movement one to the other is readily controlled and positively and uniformly changed to suit various conditions.

According to yet another feature a releasable machine part is provided which, when not needed to ac commodate the change in some external operating factor of the machine, may be allowed to yield and free wheel without substantial effect on the machine.

Various other features and objects and advantages will become apparent from the following detailed description and the accompanying drawing through which the invention is illustrated by way of example and in which:

Figure 1 is a longitudinal view in section of' a machine to which the instant invention has been applied;

Figure 2 is a section through the blading of the machine of Figure 1;

Figure 3 is an enlarged diagrammatic view of the blading of Figure 2;

Figure 4 is a modified form of blading; and

Figure 5 illustrates a further modification of the blad- 1n gIn regard to Figures l and 2 particularly, a turbine selected as illustrative of an application of the present invention is shown and it includes outer and inner walls and 12 defining an annular passage for accommodating the ow of compressible energy fluids.

Engaging walls 10 and 12 are

flanges

15 and 16. Flange 5 1s carried by a Wall 18 in which is received the tip portions of a plurality of nozzle vanes or blades in the nozzle section of the turbine. A rib 22 formed on the wall 18 is joined to an end wall 24 for the turbine. The base of each vane 20 is mounted to a stationary carrier portion 26 which may be provided with inwardly directed lugs as shown at 28.

Other blading 30 is also disposed in the nozzle section, the tip 32 of which is positioned close to wall 18 but in a non-contacting relation therewith. The base 34 of blade 30 is mounted in a carrier portion 36. Outer wall 18 is provided with a radially extending flange 3S which marks the end of the nozzle section of the turbine and mates with a companion flange 39.

The rotor section of the turbine beginning at flange 39 contains a rotor blade 40, the tip 42 of which is disposed adjacent to wall 44 of the turbine outer housing but in non-contacting relation therewith. The base of blade is shown at 46 mounted in a carrier portion 48, the rotor section additionally having another blade which is adapted to rotate within and in spaced relationship with wall 44. A flange 52 provided on wall 44 and a mating flange 54 join to connect an outer wall 56 in registry with the gas passage. Inner wall 58 cooperates with wall 56 to confine the gases to a selected path. Blade 50 is carried by a carrier portion 60 which is rotatably mounted adjacent to wall 58. lt is to be noted that a slight clearance is provided between the aforesaid carrier portions and between each carrier portion and the wall 98 to provide a means for obtaining a controlled leakage into the combustion gas path in a fashion more fully described later.

An end wall 64 of the turbine has a portion 62 forming a gastight connection with wall 58 and a reinforcing bracket is provided for the end wall at 66. At the forward end of the turbine is a wall 68 provided with a radial rib 70 and peripheral flange 72. Flange '/"2 is connected with lug 28 by means of a fastener 74. A fastener 76 on wall 68 serves to secure its inner margin to a lug 78 formed on the main casing 80 of the turbine. Oil fitting 82 is threadably received in casing S0 and cornmunicates through passage 34 and branch 86 with an oil chamber 88. Oil chamber 88 serves to lubricate a bearing 90, the inner race of which is retained in place in casing by a ring segment 92. The outer race of bearing 90 is held in position by a similar ring segment 94 in a hub 96 rotatably mounted on bearing 90. Engageable parts 98 and 100 are formed in association adjacent hub to provide a brake for the hub. An opening 103 formed in the wall of casing 80 receives an automatically controlled or operator-controlled member 102 which may be utilized to cause engagement between braking parts 98 and 100 and which may be op erated by a shifter yoke lever generally indicated at 101. A sealing ring 104 is provided between casing 80 and the hub 96 rotatably mounted therein for the purpose of conning the oil to passages devoted to lubrication.

An opening 108 is provided in casing 80 for the introduction of air or other coolant which may be under suitable pressure and led into a chamber defined by end wall 68 and the web 110 of the wheel mounted on hub 96. The entering coolant may pass along a rib 112 formed on web and into the compressible combustion gas passage by the controlled leak mentioned and may also pass through a communication 114 formed in web 110. Hub 96 has a closing plate 116 in attachment adjacent bearing 90.

Disposed along axis 117 of the turbine is main shaft 113 journalled in

outboard bearings

120 and 122 which latter are firmly held in casing portion 124. The inner end 126 of the main shaft is secured to a hub 128 of a wheel 130, Coolant which passes through described pas' sage 114 rnay enter the chamber between web 110 and wheel 130 and pass therealong into the motive gas passage. Coolant may also pass through an opening 132 formed in wheel 13d and enter into a chamber between wheel 13@ and another wheel 134. Blades itl and 50 are mounted for rotation with these respective wheels.

An opening 136 formed in wheel 134 allows passage of coolant into the chamber between end wall 64 and wheel 134. Wheel 134 has a hub 138 firmly secured as by splines to a shaft 140 coaxial with and surrounding main shaft 118. A seal 142 for the coolant, which may be of the labyrinth type, cooperates with an end of shaft 140 to confine the coolant within end Wall 64 and is provided with a connection at 144 sealing it to end wall Intermediate coaxial shafts 118 and 140 is disposed a pair of

pilot bearings

146 and 148. Mounted in turn in bearings 150 and 152, the shaft 140 is effectively supported in portion 154 of the turbine casing. Forme on shaft 118 is a guide member 156 formed with a guide opening 157. Adjacent this guide opening are disposed

engageable parts

158 and 160 which constitute a clutch. The member 160 of the clutch is operated to eiect engagement between the clutch parts by an operator-controlled member 162 which may in turn be operated by a shifter yoke lever generally indicated at 163.

As to operation of the construction shown in Figures 1 and 2, let it be assumed that braking parts 98 and 100 are mutually engaged, and that

clutching parts

158 and 160 are mutually engaged. Therefore, the compressible energy gases will be passed along the passage 14 and upon introduction into the nozzle section will be deected so as to acquire tangential velocity. This tangential velocity becomes manifest upon the gases entering the rotor section of the turbine, and by virtue of their deection and the change in tangential velocity in passing along

blades

40 and 50 will apply force to the blades of the rotor section thereby tending to rotate them in a clockwise direction as when viewed from an upstream position. When engageable parts 98 and 100 are released, the torque reaction on blades 30 is no longer exerted on the casing therethrough and instead of serving effectively in their nozzle vane capacity these blades 30 and the associated wheel assembly will rotate freely upon bearing 90 in a direction opposite to rotor rotation, or in other words, counterclockwise. As a result, the tangential velocity of the energy gases in passing through the nozzle section will be reduced and blades 30 will offer substantially no interference with the turbine processes. Regardless of the particular tangential velocity of thc gases on entering the rotor section the gases will tend to be turned while transferring their energy to blades 40 and will lose some of their tangential velocity.

lf clutching parts

158 and 160 are disengaged the blades 50 will tend to freewheel in their

bearings

150, 152, 146, and 148 and will not interfere to any appreciable extent with the turbine processes.

Reference may be had to Figure 3 for a more complete understanding of the operating principles applicable to the above discussion. It will be observed that widths wz and W4 between blades are less than either Width w1 or w3. Blades 20 may be considered xedly mounted in the turbine casing in a disposition such that their zero lift line 21 is at an angle of lift L1 to the axis 117 of the machine. With respect to the row of blades 20, the individual blades are of a height h1, and the distance between them as respects the included passage is of width w1. While passing through blades 20, the compressible gases must pass through a passage of the dimensions h1, w1 and submit to a turning effect in a clockwise sense in accordance with the angle of lift L1. The machine described being of a single pass, single-stage axial flow type, the inward velocity v1 to blades 20 in vector form is parallel to the axis 117 of the machine and the exit velocity of the gases may be represented by a vector vz making an angle p2 thus producing a tangential velocity component vt.

If blades 30 are allowed to rotate freely in the casing, then the gases would enter the rotor section of the machine with a velocity v2 and at an angle Q52. Blading 30 is effectively disposed in the machine so that the Zero lift line 31 effects an angle of lift L2 with the axis 117 of the machine. Angle L2 exceeds the previously considered angle of lift L1 of blades 20 and hence when blades 30 are held against movement an additional turning effect is given the motive fluid. Owing to the increased angularity of blades 30, the width wz of the passage defined therebetween is narrower than the width wi previously considered and inasmuch as the heights h1, h2 of respective blades 20 and 30 are nearly the same, the passage dened by blades 30 is of a more restricted character than the passages defined by blades 20. As a result of holding blades 30 against rotation, the velocity vector of its discharging gases will be of the order of vector v3 having a greater angle 3 to the axis of the machine than angle qbz just considered and the tangential velocity vt of vector v3 will also be in excess of the tangential component vr of velocity v2. The compressible energy gases are therefore subjected to an additional turning effect in a clockwise sense.

When blading 40 and 50 is held nized rotation, the bucket speed may value u. Blading 40 is effectively disposed in the machine such that its zero lift line 41 is at an angle L3 with the axis of the machine. The energy gases are introduced into blading 40 and as they are turned thereby in a counterclockwise sense in passing along the passage of dimensions ha, w3 they deliect and accordingly impart energy to blading 40. The tangential velocity component vr of the velocity v4 of the gases discharged from blading 40 is of lesser magnitude than the velocity component in the tangential direction of the entering gases and the angle gbr made by vector velocity v4 is of lesser magnitude than angle p3 made by the entering iiuid. The lift angle L3 is of an opposite sense to lift angle L2. In the event that blading 50 is allowed to freewheel, the gases will leave the rotor section with a velocity having a magnitude and direction substantially the same as velocity v4 and angle p4 respectively. That is, the net change will be a turning in a counterclockwise sense as produced solely by blading 40. It will be noted, however, that blading 50 is effectively set in the machine such that its zero lift line 51 makes an angle L4, relative to the axis of the machine, which is greater than angle L3 but of the same sense. Passages W4 of blading 50 are narrower in magnitude than w3, the width of the passages of blading V40, and since the height of these blades, that is h3 and h4, is of the same order, a more restricted iiow must pass through blades S0. Further turning of the energy tiuid results in a counterclockwise whirl sense and the exit velocity v5 of the tiuids may be reduced in angularity to a small value s lying on either side of the axis of the machine and of relatively minor tangential component vr. Situations are readily conceivable in which it would be desirable to allow blades 30 and 50 both to freewheel, both to be held against rotation to its

complernentary member

20 or 40, or either allowed to freewheel as the other is held against such unrestrained rotation.

In the modification of Figure 4 is shown a section through the blading of a turbine having only one set of blading 220 in the nozzle section and two sets of blading 240 and 250 in the rotor section. The effect of blades 220 is much the same as the elfect which would be obtained if both sets of blades in the nozzle section of the first embodiment were permanently locked together. Rotor blading 240 and its auxiliary component 250 are arranged either for independent rotation, one on the main shaft and one freewheeling, or for synchronized rotation as in the irst embodiment wherein they are indexed together.

In the modification of Figure 5, a turbine appears which has a nozzle section comprising blades 320 and blades 330. One or the other of these groups of blades is permanently held in the turbine casing, and the other is either held against rotation or allowed to freewheel as desired. The rotor section of the embodiment of Figure 5 is composed of a row of single blades 340 which have much the same effect in operation as a conventional turbine or much the same operation as the first embodiment if the

engageable parts

158 and 160 thereof were permanently locked together.

It will be apparent that though the blading effect in the machine above described may be varied through use of automatically controlled or operator-controlled parts, still, non-uniformity in blade lift angles cannot result as between blades of the same row since blades of the same row do not have to be adjusted relative to one another. The freewheeling sets are either effectively in use or not in use and the blade angles are not physically changed at all but rather are merely changed as to their eiectiveness for the particular ends and purposes sought.

While the invention has been described with respect to certain preferred examples selected to give satisfactory results, it will be understood by those skilled in the art, after understanding the invention, that various changes and modifications may be made without departing from the spirit and scope of the invention.

together for synchrobe of the designated What is claimed is: 1. A single pass axial flow fluid turbine comprising a casing, a pair of concentric shafts supported by a portion of said casing and journalled one within another for relative rotation, a vvheel hub including a third blade arranged in series in that order behind said fluid nozzle vane, the respective wheel means being carried by said Wheel hub member, by one shaft of said pair of shafts, and by the other shaft of said pair of shafts, said first blade being curved and set for an angle of lift greater than said predetermined angle of lift of the nozzle vane, said second blade being curved and set for a preselected angle of lift relative to the axes of said shafts and said third blade being curved and set for an angle of lift greater than said preselected angle of lift of the second blade, brake portions connected to said wheel hub member and said other casing portion and engageable to hold the wheel hub member and the Wheel means including the first blade against rotation for increasing the tangential velocity of the fluid leaving the nozzle vane, and a clutch portion connected to each of said shafts and engageable to lock the shafts and the second and third blades and their respective associated wheel means for rotation together whereby the second blade decreases the tangential velocity of the passing uid and derives energy therefrom and the third blade further decreases the tangential velocity of the passing fluid and derives further energy therefrom.

2. A single pass axial flow fluid turbine comprising a casing, a pair of concentric shafts supported by a portion of said casing and journalled one within another for relative rotation, a vvheel hub to each of said shafts, a fixed fluid nozzle including a vane curved and set at a predetermined angle of lift relative to the axes of said shafts, said bearing means and said Xed fluid nozzle being supported by another portion of said casing, wheel means including a first blade and wheel means including a second blade and Wheel means including a third blade arranged in series in that order behind said shafts and frictionally engageable to lock the shafts and the second and third blades and their respective associated Wheel means for rotation together whereby the second blade decreases the tangential velocity of the passing fluid and derives energy therefrom and the third blade further decreases the tangential velocity of the passing fluid and derives further energy therefrom.

3. A single pass axial flow fluid turbine comprising a casing, a p air of concentric shafts supported by a portion porting said hub member for independent rotation relative to each of said shafts, a fixed uid nozzle including a vane curved and set at a predetermined angle of lift relative to the axes of said shafts, said bearing means and said fixed fluid nozzle being supported by another portion of said casing, wheel means including a first blade shaft of said pair of shafts, and by the other shaft of said first blade being curved and set for an angle of lift greater than said predetermined angle of lift of the nozzle vane, said second blade being curved and set for a preselected angle of lift 1n an opposite sense to said predetermined angle relative to the axes of said shafts and said third blade being curved and set for an angle of lift greater than said preselected angle of lift of the second blade, brake portions connected to said wheel hub member and said other casing portion and engageable to hold the wheel hub member and a clutch portion connected to each of said shafts and engageable to lock the shafts and the second and third energy therefrom.

4. A single pass axial flow fluid turbine comprising a casing, a pair of concentric shafts supported by a portion of said casing and journalled one Within another for relative rotation, member coaxially disposed with respect to said pair of shafts bearing means for supporting said hub member for independent rotation relative to each of said shafts, a fixed fluid nozzle including a vane curved and set at a predetermined angle of lift relative carried by said Wheel hub member, by one shaft of said pair of shafts, and by the other shaft of said pair of shafts,

of lift greater than said preselected angle of lift of the second blade, a turbine housing member adjacent the bearing means contained in said wheel hub member secured to said other casing portion and being adapted to contain pressurized cooling air for the Wheel means, brake portions connected to said wheel hub member and said other casing portion and engageable to hold the wheel hub member and the wheel means including the first blade against rotation for increasing the tangential nozzle vane, and a clutch therefrom, there being a slight clearance provided between said wheel means each with respect to the other and with respect to the housing member so as to provide a path for the controlled leakage of said coollng air into the path of said fluid as it passes said blades.

References Cited in the tile of this patent UNITED STATES PATENTS