JPS58178802A - Turbine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a turbine driven by a work fluid such as steam.

An object of the invention is to provide an efficient turbine, and this object according to the invention comprises a high pressure section with at least one radial impulse turbine stage, a low pressure section with at least one trickle turbine stage,
a reservoir device for introducing a work fluid at one pressure into the high pressure section to drive the radial impulse stage and a work fluid at a lower pressure into the low pressure section to drive the trickle stage; This is achieved by a double-pressure turbine equipped with a device.

This novel combination of radial impulse stages and axial stages has significantly higher efficiency than conventional turbine configurations.

The turbine may include a reservoir k for mixing the work fluid discharged from the high pressure section with further work fluid to produce a lower pressure work fluid that is introduced into the low pressure section. In this case, for example, the steam discharged from the high-pressure section is combined with the steam fed to the low-pressure turbine, and this mixture is fed to the low-pressure turbine stage.

Such a configuration allows maximum use of energy.

Alternatively, the turbine has a single inlet in communication with the radial impulse stage or the first stage thereof, where the work fluid discharged from the radial impulse stage or the last stage thereof is axially It is also possible to provide all of the work fluid supplied to the low pressure section by being sent to the stage or the first stage thereof.

Turbines with this structure are of the “forced flow” type (“onc”).
e-through” type) in which the work fluid is supplied to the turbine all at one pressure, and the work fluid is discharged from the radial impulse stage directly into the first stage of the axial flow stage. Although there is some sacrifice in efficiency, this configuration is less complex, has lower maintenance costs, is more reliable, and has faster response times.Thus, this forced-flow structure has more advantages than efficiency. The advantages prevail, making it suitable for applications such as those provided in the Navy's A111!: The rotors of each radial impulse stage and axis #L cane are coaxially coupled as a single rotating unit. can.

This eliminates the connection between the island and the low pressure section and reduces the associated expense and power loss. In this case one common casing is usually provided which accommodates both the still and low pressure sections.

Radial impulse turbines have been well developed in recent decades. The latest form of the turbine includes a rotor with packets oriented transversely to the direction of wheel rotation and opening at the periphery of the wheel. The elastic working fluid is
For example, the packets are fed through a nozzle ring surrounding the rotor.

The radial impulse stage or at least one stage in the high pressure section can be of such construction that it has several valuable features, particularly the feature of being able to accommodate higher than conventional work fluid velocities. sound.

One feature of the present invention is that a radial oscillation stage or a radial oscillating stage is provided at intervals around the periphery of the rotor and has a tube opening into the periphery of the rotor and into the packet for rotating the rotor. The valley packets have an inlet on one side of the rotor and an outlet on the other side, and the packets are arranged to introduce work fluids at different pressures. The shape is such that the incoming fluid flow vector and the outgoing fluid flow vector 1 are substantially parallel to each other and substantially parallel to a plane perpendicular to the axis of the rotor. be done.

According to a second feature of the invention, the radial impulse stages are spaced around the periphery of the rotor and have packets opening into the periphery of the rotor, and the radial impulse stages are elevated into the backpack for rotating the rotor. The rotor includes an annular array of reservoir nozzles for introducing work fluid at both pressures, the outlets of which communicate with the packet inlet substantially all around the rotor. The work fluid is then injected onto the packet from a location surrounding the wheel and being substantially uninterrupted.

Efficiency is further promoted if the cross section of the packet and nozzle outlet perpendicular to the flow of the work fluid has substantially right angle corners. Such a configuration effectively reduces undesirable shocks and turbulence that waste power.

According to a sixth feature of the invention, the radial impulse stages are arranged in a rotor having a bubbler tractor spaced around the periphery of the rotor and opening at this periphery; It is equipped with a nozzle ring for introducing the work fluid at the same pressure,
To maximize the work obtained from the work fluid, the rotor is completely traversed between the inlet and outlet of the packet by an enclosing canopy, and the nozzle ring is placed against the upstream side of this drop, which The machine forms the upstream wall of the nozzle. Such cores maintain flow characteristics.

Without the drop, the circulation characteristics of the flow become generally uncertain in the vicinity of the packet. The provision of plates eliminates windage losses that occur in conventional coreless or partially shrouded radial impulse turbines.

According to a fourth aspect of the invention, the radial impulse stages are arranged on a rotor having packets spaced apart from and opening at the periphery of the rotor, and for directing the rotor into the packets. a nozzle ring comprising an annular array of nozzles for introducing a work fluid at a higher pressure; The vanes have a surface directed towards the axis of the rotor, which surface is continuous from the edge at the nozzle outlet to a portion located radially outward of the edge of the adjacent vane. bent to

The edges at the nozzle outlet of each vane have a penetrating angle of less than 60. Wedge angles of 11 degrees or more are typical in prior art designs. However, the inventors have found that the efficiency can be significantly increased by reducing the angle to a maximum of 3 degrees.

It also reduces wake and relative flow disturbance.

Reducing the wedge angle also reduces the stress exerted on the rotor by the work fluid distributed from the turbine nozzle to the rotor.

The high-pressure section comprises a rotor having packets spaced around the circumference of the rotor and opening into the circumference l#; 1 and 2 radial impulse stages, each nozzle having an inlet opening at the outer periphery of the ring and an outlet opening at the inner periphery of the ring; It also bends the work fluid discharged radially outwardly from the packets of the first stage rotor axially toward the second stage rotor, and then
A flow director may be included for directing the flow radially inwardly into the inlets of the nozzles of the stage nozzle ring.

j! ! In a practical arrangement, the high pressure section comprises a nozzle ring containing an annular array of work fluid distribution nozzles surrounding the rotor, and a rotor having packets spaced around the circumference of the rotor and opening to this circumference H1. The high pressure section also includes a first and a second radially moving stage, each of which is separate from the others, and the high pressure section also directs the work fluid discharged from the packets of the first stage rotor after the work fluid has passed through the packets of the first stage rotor. and a discharging solinum downstream of the second stage rotor, the packets of the second stage rotor having a device for directing the fluid into the nozzle surrounding the second stage rotor. It is shaped to discharge fluid into a discharge plenum.

Hereinafter, in conjunction with the accompanying drawings, 2 constructed in accordance with the present invention will be described.
Two examples will be described.

The turbine 6 shown in FIGS. 1 to 4 has an elongated outer casing 7 having a generally circular cross section and consisting of a plurality of casing elements assembled together by bolts.
Equipped with

The interior of the cage/gua is divided into a high pressure section 8 and a low pressure section 9 (see Figures 2 and 6).

The high pressure section 8 has two impulse turbine stages 10 and 11. The low pressure section 9 has six conventional trickle turbine stages 12, 13, 14, 15, 16°17.

The high pressure turbine stage and the low pressure turbine stage each include a rotor. These rotors are labeled with the same reference number V and the letter R as the stage in question.

The eight rotors 10R, . The elements of the assembly thus produced are held together by a single tension bolt 19, and the assembly is rotatably supported in suitable bearings within the cage/gua. The upstream (or forward) end of the assembly is provided with splines (not shown) for receiving drive couplings, so that power take-off is provided upstream of the high pressure section.

As shown in FIG. 2, the ratio 1 and first stage rotors IOR and 11B in the lateral pressure section 8 of the turbine 6 are made of steam grade 17-4 stainless steel or equivalent material. Ru.

The second stage rotor IOR is surrounded by an annular nozzle ring 20. The nozzle 21 of this ring has a converging shape as shown in FIG. These nozzles are defined between vanes 21A made of gold cormorant left in the milling of the ring 20 forming the nozzles. The blades have sharp edges 21C and curves 1ti exhibiting wedge angles of less than 6°.
21B. This curved surface faces radially inward toward the rotor axis and extends from edge 21C to a location at 1 at edge 21C of the next blade. The curvature of the surface 21B is similar to the curvature of the outer circumference of the rotor (ie, plus or minus 10%).

Each nozzle has an inlet port 22 that opens on the outer periphery of the nozzle ring.
and a discharge port 23 opening on its inner periphery, and the cross-section in the direction perpendicular to the fluid flow at the discharge end is square. The outlet of the nozzle 21 is the second
As shown, it mates radially Ii with the inlet 24 to the packet 25 at the peripheral 7 flange 26 of the second stage rotor IOH.

The packets Vi are equiangularly spaced and are typically formed by milling with a cutter inclined at an angle of 18° to the radial direction.

A cross-section perpendicular to the fluid flow of the packets 25 has substantially right-angled corners 21 (see FIG. 4), and they have an inlet 24 near the upstream side of the rotor, an outlet 28 near the downstream side of the rotor, as well as? -t'+. A semicircular impulse surface 29 is provided between the inlet and the outlet.

By processing the packets so that the inlet and outlet sides of the packets have transition surfaces,
Maximum efficiency can be obtained. Such a transition surface reduces losses due to the fluid impinging on the rotor when the work fluid changes flow direction fr: in the packet.

Commercial efficiency can be achieved by arranging the profile of the trailing surface 30 of each packet to be a smooth curved surface terminating in sharp edges, as shown in FIG. Its rounded curved surface can be produced on the island by casting. Alternatively, such a curved surface could be fabricated by making a 7-in. This 6: Removes excess metal from the rotor F-1 and also matches well with the relative proboscis velocity of the work fluid discharged from the nozzle ring. In other words, it is made from a flat surface IJ construction V! Along with the sharp leading edge, it helps to reduce irregular flow and improve efficiency.

One groove is milled seven times into the rotor before the packet 25 is milled seven times. This groove extends continuously around the p-tor, opens at the periphery of the rotor, and creates a slot in the front part of the packet.

Although this groove is provided primarily to avoid interfering with the shank of the cutter used to form the back cut, it also eliminates excess metal from the rotor and reduces stress between the rotor and the packet.

The outlet 23 of the nozzle 21 forms an almost continuous circle around the rotor 10RI7)8. This, along with the sharp details between adjacent packets, creates a substantially perfect arc-shaped jet of work fluid to the packet and ensures smooth filling of the packet. This contributes significantly to the efficiency of the turbine.

The nozzle ring 20 is coupled to a radial flange 32 at the downstream end of the plate-side infeed manifold 33 by an H-roll prevention pin 31 . Manifold 33 is the first high pressure section
It is bolted to the curve of the casing elements 34 and 35 on the upstream 0 side of the stage rotor 10H.

Work fluid is supplied to the m1 stage 10 of the turbine 6 from an inlet 38 communicating with the interior of the high pressure inlet manifold 33 . This working fluid is introduced from the manifold 33 into an annular inlet hole 39'f between the outer periphery of the nozzle ring 20 and the inner wall of the manifold 33.
: Flows through in the axial direction.

The fluid then flows radially inwardly into the nozzles 21 of the nozzle ring 20, as shown by arrows 40 in FIG.

The work fluid is ejected from the nozzle 21 and enters the packet 25 of the rotor ion, driving the rotor while flowing within the packet. The fluid then flows radially outward as indicated by arrows 41. The incoming and outgoing flow vectors of the work fluid are parallel.

Efficiency is also enhanced by completely shielding the packet 25 between the inlet 24 and outlet 28 by a shroud 36 that completely surrounds the rotor 10R. This complete shroud reduces power loss and turbulence. Efficiency is also enhanced by maintaining a free surface on the egress side of each packet. Furthermore, since the work fluid flowing out from the packet outlet does not collide with the pattern 36, its outflow moment is maintained. This is %VC
This is an important advantage in multi-stage turbines.

The working fluid exiting the packet of P-10H and flowing outwardly is first axially and then radially inwardly (as indicated by the arrows) by the cooperation of the casing element 37 and the annular disk-shaped flow director plate 43 42) can be bent.

The guide plate 43 is mounted upstream of a radially inwardly extending annular tube 44 on the casing element 37 by a fixing screw 45 .

Flow guide plate 43 and turbine rotor 10R...
Leakage between the 17R assembly and the joint seals 46 and 4
Prevented by 7. These seals connect the inner periphery of the flow director plate and the high pressure section first and second stage rotors 101' (
, 11Fl.

The work fluid discharged from the first stage 10 is transferred to the second stage 0-11.
Nozzle 4 formed in nozzle ring 49 surrounding iR
It flows into 8. Again, the nozzle outlet is aligned with the inlet 50 of the bacut 51, which is similar to the packet 25.

Nozzle ring 49 seats within four portions 52 of flow director plate 43 and is identified upstream of flange 44 by the flow director plate and fasteners 45 .

The upstream side of this 7-line nozzle is the rear or lower #LO of the nozzle.
Ill become a wall.

Although the nozzle 48 is not shown in detail #I, it is preferably the fourth nozzle.
with a convergent shape similar to that shown in the figure.

The sixth stage rotor 17R is completely folded in the same manner as described above. In this case the opening is formed by a circular radial flange 44 of the casing element 370.

After passing through the packet 51 of the second stage turbine rotor 11H, the work fluid is discharged radially outwardly from the outlet 53 of that packet and is directed to the high and low pressure turbine sections 8 and 9.
Enter the concession form Zolinum 54 prepared between. here,
Work fluid discharged from the still pressure section 8 of the turbine is combined with work fluid introduced into the turbine through an inlet 55 and an annular low pressure inlet manifold 56 surrounding the plenum 54.

Communication between manifold 56 and plenum 54 is provided by inwardly directed circular apertures 57. Axially extending circular bosses 58 and 5 which are an integral part of the casing element 37
9, and the manifold 56 and inlet 55 form a nozzle.

The mixed work fluid flows axially, as shown by arrow 60 in FIGS. 2 and 3, into the low pressure section 9 of the turbine 6. This section 9 of the turbine 6 is of an energized trickle configuration υ and is best shown in FIG.

Each turbine stage of the low pressure section includes one rotor as described above, consisting of an annular array of vanes 62 mounted on a disk 661. A conventional annular array of fixed nozzles 63 is provided upstream of each rotor. The nozzles of each stage are attached to an annular nozzle support 64 fixed to the casing element 37.

Leakage passing through the nozzles of each stage is prevented by a circular diaphragm 65.
This is prevented by a seal 66 provided on the inner periphery of this diaphragm and a cooperating seal 67 carried on one adjacent disc.

An axially extending circular flange 68 is secured to the diaphragm 65 of the first axial turbine stage 12 for guiding the mixed work fluid from the annular discharge plenum 54 into the first axial turbine stage 12 .

As shown in FIG. 6, each low pressure axial flow stage preferably includes:
An annular abradable sliding ring 69 is provided which forms part of the nozzle support of the stage and surrounds its rotor. This sliding ring minimizes the blade tip clearance for the work fluid used and reduces work fluid leakage through the blade tips.

The flow of work fluid through the low pressure section is constant and the fluid is discharged from the sixth stage rotor 17R to an annular discharge manifold (not shown).

Work fluid is discharged from the manifold and turbine casing through a discharge duct 70 (see FIG. 1).

1800 shaft horsepower (136872 mh/S) C 600 shaft horsepower (45624 mK2/S) in the high pressure impulse section
)] is shown in FIGS. 2 and 3, one turbine of the characteristics as herein described, designed to produce a power output of

Typically, this turbine has 14 to 2 pots (200p
High pressure steam at 382°C (720oF') at a rate of 9/B (3,231 bs/S) to 1.47 and 4 at 9/an2 (40 psia) to 2,8
0.35 Ky of low pressure steam at 21°0 (790°F)
/S (0,761 bs/S).

The design pressure of the steam discharged from the final stage of the low-pressure axial section of the turbine is 0.046 Ky/Cm2 (0.65
psia).

Two reconnaissance stages 10 in the high pressure section 8 of the turbine 6
and 110 rotors have diameters of 0.60 and 0.35+, respectively.
n (11,75 and 13.875 inches), and the median chord length of the blades 62 in the low pressure axial section of the turbine is:
It ranges from 0.015 m (0.6 inches) at the first stage 12 to 0.13 m (5.16 inches) at the sixth stage 17. The diameter of the disks on which the blades are mounted is all 0.3
4 m (13,5 inches).

The invention is also applicable to once-through turbines that combine radial impulse stages and axial stages. This type of turbine also provides an efficient arrangement for transferring work fluid from one radial impulse stage to the next, and can employ more than one radial impulse stage. This type of turbine is designated at 71 in FIG.

In many respects, turbine 71 is similar to the turbines previously described. Therefore, in order to avoid complicating the description, the turbine 71 will be mainly described with respect to its different features from the turbines described above.

The turbine 71 has an elongated outer casing 72 in which three radial impulse stages are arranged. 3,74° 75 and seven axial stages 76 (of which only one is shown) are accommodated.

Each axial flow stage (which may be of the character previously described in turbine 6) and each impulse turbine stage is designated by the same reference numeral as the stage in question, followed by the letter R.

10 rotors 73h, 74R, 75B, 76R...
... are joined together by curvic fittings 77 and held in this assembled condition by tension bolts 78. Suitable bearings (not shown) rotatably support the assembly within gauging 72.

The rotors 73R, 74R, 75R of the radial impulse stage are similar to those in the turbine 6, and they have the above-mentioned advantages obtained by completely enclosing them. , 79,8
It is surrounded by 0.81.

The first stage rotor 73R is surrounded by an annular nozzle ring 82 having nozzles of the type shown in FIG.

/ l The working fluid is supplied through an inlet 84 that connects with an inlet manifold 83
is supplied to the first stage 73 of the turbine 71. Work fluid enters the nozzles of the nozzle ring from manifold 83 through annular inlet 85.

The work fluid flows into the rotor 73R(7) packet from these nozzles and drives the rotor while flowing through the packet.

Work fluid discharged from the packets of rotor 73H and flowing outwardly is deflected first axially and then radially inwardly by the common fil K between turbine casing 72 and flow director plate 86. The flow guidance board 86 is
It is similar to the flow finger 4 plate used in the turbine 6 shown in FIG. This prevents the work fluid flow from spreading as it exits the packets of the first stage rotor 73R and is directed toward the nozzle ring 87 of the second impulse stage 74. This is a good thing for TL as it reduces energy loss when fluid movement takes place.

The operation of the second and sixth radial stages 74 and 75 and the movement of work fluid between them is essentially the same as in the previous embodiment.

From the rotor of the sixth radial impulse stage 75 the work fluid flows again against the surface of the shroud 81 and is deflected towards the first of the trickle stages 16.

The flow of work fluid through the axial stages is turbulent and the work fluid is discharged from the final stage rotor to a discharge manifold (not shown). Work fluid is discharged from the manifold and turbine casing through a discharge duct similar to that shown in FIG.

It will be appreciated by those skilled in the art that the number of radial impulse stages that can be used in a radial impulse turbine section is not limited to six, and the efficiency increases as the number of stages increases. However, in most cases, the number of stages higher than 6 is simply because the squares are too large.
It is said that the steps are actually y & degree.

[Brief explanation of drawings]

1 is a partial side view of the first turbine; FIG. 2 is a partial axial cross-sectional view of the high pressure section of the first turbine; FIG. 6 is a similar cross-sectional view of the low pressure section of the first turbine; FIG. FIG. 5 is a partial axial cross-sectional view of the rotor and nozzle ring of the radial impulse stage of the high pressure section of the first turbine; FIG. 5 is a partial cross-sectional side view of the axial flow section of the second turbine. 6... Turbi/, 7... Casing, 8... High pressure section, 9... Low pressure section, 10.11...
・Impulsive terpino stage, 10R, IIR...same rotor, 1
2゜13.14, 15, 16.17... Axial flow turbine stage, 12B (...17R... Same rotor, 19
...Tension bolt, 20.49...Nozzle ring, 2
1.48... Nozzle, 23... Nozzle outlet, 24
．． 50... Packet inlet, 25.51... Packet, 28.53... Packet outlet, 33... Pressure feeding manifold, 34, 35.37... Casing support,
36.44... Rotor surrounding handling, 38... High pressure inlet, 43... Flow guidance plate, 541... Plinum, 55... Low pressure inlet, 56... Low pressure inlet manifold, 61...Low pressure axial flow rotor disk, 62...Axial flow rotor blade, 63...Fixed nozzle,
64... Nozzle support, 65... Diaphragm, 69
...Sliding ring, 71...Forced flow turbine, 72...Cage/Guar 3.74.75...Radial impulse stage, 73R974
R, 75R...same rotor, 76...axial flow stage, 76R
...same rotor, 78...tension pole), 79°80.
81... Rotor surrounding rear, 82.87... Nozzle ring, 83... Inlet manifold, 84... Inlet port, 86... Guidance board. Agent Asamura Akigai 4 people 2

Claims (1)

Claims: (11) at least one radial impulse turbine stage (10
), a low pressure section (9) having at least one axial turbine stage (12),
a reservoir device (38) for introducing a work fluid at a pressure into the high pressure section to drive the radial impulse stage;
and a double pressure turbine (6) comprising a device (56) for introducing a lower pressure work fluid into the low pressure section to drive the axial stage. (2. In the turbine of Claim 1 JJ, in order to provide the low-pressure work fluid introduced into the low-pressure section, a device for mixing the work fluid discharged from the high-pressure section with other fluids in a nest) (54). (3)% The turbine of claim 6, wherein the mixing device comprises an I
J [zolinum (54), an annular inlet manifold (56L) surrounding the inlet manifold and the inlet manifold (56L), an annular flow passageway (57) connecting the inlet manifold and the plenum, and a fist through which work fluid can be passed to the inlet manifold. (55)
A turbine equipped with. (4) A turbine according to claim 1, having a single inlet (84), which inlet communicates with the radial impulse stage or the first stage (73) thereof, in which the All of the work fluid supplied to the low pressure section by means of the work fluid discharged from the radial impulse stage or its last stage (75) being sent to the nuclear trickle stage or its first stage (76). The turbine is provided. (5) Turbia VLc according to any one of the claims above
comprising a casing (7) housing both the high and low pressure sections, the radial impulse stage and the axial stage each having a rotor (10R, 17R), all the rotors having a single A turbine that is coaxially coupled as a rotating unit. (6) In the turbine according to claim 5, the 1
A turbine in which an 11-turn unit provides power take-off at the upper part of the high pressure section. (7) Permissible Claim Range In the column of the optional 1 above, the radial V# moving stage (10) is rotor (10R'
) are set at intervals around the periphery! 1 and the baffler that opens on this periphery) (25') Its rotor (10R
), and a device for introducing a working fluid at a higher force pressure into the Bakut to turn the rotor &(2(l)
, the packets have an inlet IC 24) at one side of the rotor and an outlet (28) at the other side, the packets have a fluid flow entering each packet used. vector and the flow vector of the fluid exiting it are shaped so that they are substantially half a line from each other and substantially parallel to a strictly perpendicular 1'F-plane of the rotor; turbine. (8) Claims In the turbine according to any one of the preceding claims, the radial impulse stage (10) has a bucket (25') that is provided at intervals around the periphery of the rotor (10R) and that is open to the periphery. a rotor (10R) and an annular array of nozzles (21) for introducing a working fluid at a higher commercial pressure into the bucket for turning the rotor, the outlet (23) of the nozzle communicates with the lever foot inlet [l (24') substantially all around the rotor;
turbine. (9) In the turbine according to claim 8, the lateral face of the packet (25) that is at a plane angle to the flow of the work fluid and the corner where the cross section of the nozzle outlet (23) is substantially a mountain angle. A whirring turbine. 00) %ff = 0 range In the turbine according to any one of the above items, the radial impulse stage (10) has a rotor (10R
), the rotor (10R) having a bucket ) (25') spaced apart from the periphery of the bucket and opening at the periphery;
and a nozzle ring (20) for introducing higher pressure work fluid into the packet to turn the rotor.
to maximize the work obtained from the work fluid, the rotor is completely evacuated between the inlet (24) and outlet (28) of the packet by a surrounding arbor (36); The nozzle link (20) is connected to the upstream side of the drop.
the turbine, thereby forming the upstream side wall of the nozzle. (11) Claims In the turbine according to any one of the preceding claims, the radial impulse stage (10) is provided at intervals on the periphery of the rotor (10R), and has a bucket (25') that opens on the periphery. M rotor (10R'),
and a reservoir nozzle (21) for introducing higher pressure work fluid into the packet to defeat the rotor.
a nozzle link (20) comprising an annular array of nozzles;
These vanes form the rotor's meticulously directed surface (21
B) has [~, this surface is continuously curved from the edge (21C) located at the brewing nozzle outlet (23) to the part located radially outward of the edge of the adjacent blade,
turbine. 02) % Turbia If(
, the edge (21C) of each blade has a clamping angle of less than 6°. (13j) The turbine according to Claim 11 and Claim 12, wherein the curvature of the blade surface (21B) is similar to that of the outer periphery of the rotor. turbine, in which the high-pressure section (8) is spaced around the periphery of the rotor (10R, 11R) and has packets (25) opening at the periphery of the rotor (10R, 11R).
R, 11R) and a first and second radial impulse stage (10,
11), each nozzle having an inlet (22) opening on the outer periphery of the ring (20) and an outlet opening (23) opening on the inner periphery of the ring, and the high pressure section (8) Further, the work fluid discharged radially outward from the packets of the first stage rotor (IOR) is transferred to the second stage rotor (11R).
Bend axially toward the second stage nozzle ring (4
9) including a flow directing device (37, 43') for feeding radially inwardly into the inlet of the nozzle (48) of the turbine. 05) In the turbine according to claim 14, the flow guiding device is applied to the "second flow side" of the second stage nozzle ring (49), so that the first and second stage rotors (10R, 11R), and includes a radially oriented annular member (43) provided between this portion I' (43
) is spaced inwardly from the casing (37') to form a flow passage therebetween, the member (43)
A seal arrangement k (46° 47) is provided on the inner circumference of the member so that the working fluid discharged from the first stage rotor (10R) leaks around the member to the second stage radial impulse stage (11). The turbine prevents. (]61% Permission 8 Application Range Paragraphs 1 to 13 JJl
In any one of the turbines in the high pressure section (
8) are provided at intervals around the periphery of the rotor (iQR, l iR') and have packets (25
) having a rotor (10R, 11R) and a nozzle ring (20) each comprising an annular array of work fluid distribution nozzles (21) surrounding the rotor.
radial impulse stages (10, 11), the high pressure section also directs the work fluid discharged from the packets of the first stage rotor after the work fluid has passed through the packets of the first stage rotor.
A device (41) for guiding into a nozzle surrounding the second stage rotor (1111()), and a discharge solinum (54) f downstream of the second stage rotor, including a packet of the second stage rotor. The turbine is configured to discharge the work fluid into the discharge plenum after the work fluid passes through the packets of the second stage rotor.