CA2704349A1 - Fluid flow machine - Google Patents
Fluid flow machine Download PDFInfo
- Publication number
- CA2704349A1 CA2704349A1 CA2704349A CA2704349A CA2704349A1 CA 2704349 A1 CA2704349 A1 CA 2704349A1 CA 2704349 A CA2704349 A CA 2704349A CA 2704349 A CA2704349 A CA 2704349A CA 2704349 A1 CA2704349 A1 CA 2704349A1
- Authority
- CA
- Canada
- Prior art keywords
- fluid flow
- intermediate sleeve
- rotor
- flow machine
- stator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
- F16J15/3288—Filamentary structures, e.g. brush seals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/55—Seals
- F05D2240/56—Brush seals
Abstract
A fluid flow machine has a stator, a rotor which is supported so as to be rotatable relative to the stator, and a brush seal which seals a gap formed between the stator and rotor in a radial direction to prevent the passage of fluid. The brush seal has a brush holder and a plurality of sealing bristles, each of which has a first end that is fastened to the brush holder and a second end that contacts a sealing surface. The sealing surface is rotationally displaceable relative to the second ends of the respective sealing bristles. The fluid flow machine is characterized in that the sealing surface is formed by a circumferential surface of an intermediate sleeve which is arranged between the stator and rotor and which radially divides the gap.
Description
FLUID FLOW MACHINE
The invention is directed to a fluid flow machine according to the preamble of patent claim 1.
A fluid flow machine of the type mentioned above is known, e.g., from EP 0 834 688 Al. A brush seal according to the preamble of patent claim I is also known, e.g., from DE 601 24 204 T2.
Fluid flow machines include, for example, propellers and repellers, centrifugal pumps and turbo machinery of any kind such as gas turbines, steam turbines and rotary compressors such as, e.g., radial compressors and axial compressors.
The rotor in fluid flow machines such as turbo machines can be sealed by means of labyrinth tip seals, mechanical seals or brush seals to prevent the leakage of fluid. In brush seals, sealing bristles (also known as brush wires) of the brush seal make direct contact with the rotor of the turbo machine, this rotor being constructed, e.g., as a shaft. The brush seal limits the amount of work fluid, e.g., the amount of compressor air, flowing out of a flow part of the turbo machine into a bearing periphery of the turbo machine, for example.
Figures 1 and 2 show a fluid flow machine 1 according to the preamble of patent claim 1 which is constructed as a gas turbine. As can be seen from Fig.
I and Fig. 2, the fluid flow machine I has a stator 10 which is constructed in this instance as a gas turbine housing, a rotor 20 which is supported so as to be rotatable relative to the stator 10 and which is constructed in this instance as a shaft, rotational bearings 30, 40 which carry out the rotatable bearing support of the rotor 20 in the stator 10, and two brush seals 50 which seal a gap S formed in radial direction RR
between the stator 10 and rotor 20 to prevent the passage of fluid.
As can be seen particularly from Fig. 2, every brush seal 50 has a brush holder 51 and a plurality of sealing bristles 5, each of which has a first end which is fastened to the brush holder 51 and a second end which contacts a sealing surface D
which is formed in this case by an outer circumferential surface 21 of the rotor 20, so that a sealing bristle-on-sealing surface contact zone is formed. The sealing surface D is
The invention is directed to a fluid flow machine according to the preamble of patent claim 1.
A fluid flow machine of the type mentioned above is known, e.g., from EP 0 834 688 Al. A brush seal according to the preamble of patent claim I is also known, e.g., from DE 601 24 204 T2.
Fluid flow machines include, for example, propellers and repellers, centrifugal pumps and turbo machinery of any kind such as gas turbines, steam turbines and rotary compressors such as, e.g., radial compressors and axial compressors.
The rotor in fluid flow machines such as turbo machines can be sealed by means of labyrinth tip seals, mechanical seals or brush seals to prevent the leakage of fluid. In brush seals, sealing bristles (also known as brush wires) of the brush seal make direct contact with the rotor of the turbo machine, this rotor being constructed, e.g., as a shaft. The brush seal limits the amount of work fluid, e.g., the amount of compressor air, flowing out of a flow part of the turbo machine into a bearing periphery of the turbo machine, for example.
Figures 1 and 2 show a fluid flow machine 1 according to the preamble of patent claim 1 which is constructed as a gas turbine. As can be seen from Fig.
I and Fig. 2, the fluid flow machine I has a stator 10 which is constructed in this instance as a gas turbine housing, a rotor 20 which is supported so as to be rotatable relative to the stator 10 and which is constructed in this instance as a shaft, rotational bearings 30, 40 which carry out the rotatable bearing support of the rotor 20 in the stator 10, and two brush seals 50 which seal a gap S formed in radial direction RR
between the stator 10 and rotor 20 to prevent the passage of fluid.
As can be seen particularly from Fig. 2, every brush seal 50 has a brush holder 51 and a plurality of sealing bristles 5, each of which has a first end which is fastened to the brush holder 51 and a second end which contacts a sealing surface D
which is formed in this case by an outer circumferential surface 21 of the rotor 20, so that a sealing bristle-on-sealing surface contact zone is formed. The sealing surface D is
-2-rotationally displaceable, particularly rotatable in this case, relative to the second ends of the respective sealing bristles 52.
During operation of the fluid flow machine 1, the relative movement between the rotating rotor 20 and the brush seal 50, which is static in this case, leads to heating of the sealing surface D of the rotor 20 and sealing bristles 52 due to the friction between the sealing bristles 52 and the outer circumferential surface 21 of the rotor 20.
However, problems arise in this conventional seal in that an uneven heating of the sealing surface D is brought about in the absence of a state of true in the contact zone of the sealing surface D and sealing bristles 52. This uneven heating can exacerbate the out-of-true state and lead to a deformation of the rotor 20 (manifesting itself in this case as sagging between the rotational bearings 30 and 40 of the shaft) which impairs continued operation of the fluid flow machine I owing to impermissibly strong rotor vibrations.
It is the object of the invention to provide a fluid flow machine according to the preamble of patent claim 1 in which the sealing bristle-on-sealing surface contact zone is thermally decoupled in order to prevent a deformation in the fluid flow machine which is brought about by introduced heat and which impairs the operation of the fluid flow machine.
The above-stated object is met by a fluid flow machine according to patent claim 1. Further developments of the invention are defined in the dependent patent claims.
According to the invention, a fluid flow machine has a stator, a rotor which is supported so as to be rotatable relative to the stator, and a brush seal which seals a gap formed between the stator and rotor in a radial direction of the rotor to prevent the passage of fluid. The brush seal has a brush holder and a plurality of sealing bristles, each of which has a first end that is fastened to the brush holder and a second end that contacts a sealing surface so that a sealing bristle-on-sealing surface contact zone is formed. The sealing surface is rotationally displaceable relative to the second ends of the respective sealing bristles.
The fluid flow machine according to the invention is characterized in that the sealing surface is formed by a circumferential surface of an intermediate sleeve or
During operation of the fluid flow machine 1, the relative movement between the rotating rotor 20 and the brush seal 50, which is static in this case, leads to heating of the sealing surface D of the rotor 20 and sealing bristles 52 due to the friction between the sealing bristles 52 and the outer circumferential surface 21 of the rotor 20.
However, problems arise in this conventional seal in that an uneven heating of the sealing surface D is brought about in the absence of a state of true in the contact zone of the sealing surface D and sealing bristles 52. This uneven heating can exacerbate the out-of-true state and lead to a deformation of the rotor 20 (manifesting itself in this case as sagging between the rotational bearings 30 and 40 of the shaft) which impairs continued operation of the fluid flow machine I owing to impermissibly strong rotor vibrations.
It is the object of the invention to provide a fluid flow machine according to the preamble of patent claim 1 in which the sealing bristle-on-sealing surface contact zone is thermally decoupled in order to prevent a deformation in the fluid flow machine which is brought about by introduced heat and which impairs the operation of the fluid flow machine.
The above-stated object is met by a fluid flow machine according to patent claim 1. Further developments of the invention are defined in the dependent patent claims.
According to the invention, a fluid flow machine has a stator, a rotor which is supported so as to be rotatable relative to the stator, and a brush seal which seals a gap formed between the stator and rotor in a radial direction of the rotor to prevent the passage of fluid. The brush seal has a brush holder and a plurality of sealing bristles, each of which has a first end that is fastened to the brush holder and a second end that contacts a sealing surface so that a sealing bristle-on-sealing surface contact zone is formed. The sealing surface is rotationally displaceable relative to the second ends of the respective sealing bristles.
The fluid flow machine according to the invention is characterized in that the sealing surface is formed by a circumferential surface of an intermediate sleeve or
-3-intermediate bushing which is arranged between the stator and rotor and which radially divides the gap.
By moving the sealing surface to an intermediate sleeve, the sealing bristle-on-sealing surface contact zone is thermally decoupled so as to prevent a deformation in the fluid flow machine which is brought about by introduced heat and which impairs the operation of the fluid flow machine.
According to the invention, the intermediate sleeve is fastened either to a rotating part or to a stationary part of the brush seal. This fastening is advantageously carried out in such a way that, on the one hand, sufficient stability is achieved and, on the other hand, a heat transfer between the intermediate sleeve and the part to which the intermediate sleeve is fastened is as small as possible. The small heat transfer can be achieved, e.g., by means of the smallest possible contact surfaces and/or by providing an insulating layer between the contact surfaces of the intermediate sleeve and the part fastening the latter.
According to the invention, the brush holder can be arranged at the stator and the intermediate sleeve can be arranged at the rotor so as to rotate along with the latter. In this case, the circumferential surface of the intermediate sleeve forming the sealing surface would be an outer circumferential surface. However, it is also possible according to the invention that the brush holder is arranged at the rotor and the intermediate sleeve is arranged in a stationary manner at the stator so that the circumferential surface of the intermediate sleeve forming the sealing surface would be an inner circumferential surface in this case. The respective solution can be determined depending on the desired operating characteristics and design factors.
Further, according to the invention, the rotor can be formed, e.g., by a shaft rotating in a stator (e.g., in a housing) and, e.g., by a housing rotating around a stator (e.g., around an axle). The respective solution can be determined depending on the desired operating characteristics and the design factors.
According to an embodiment form of the invention, the intermediate sleeve divides the gap radially into a first gap portion adjoining the sealing surface and a second gap portion adjoining a circumferential surface of the intermediate sleeve remote of the sealing surface, wherein a radial extension of the second gap portion is greater than zero.
By moving the sealing surface to an intermediate sleeve, the sealing bristle-on-sealing surface contact zone is thermally decoupled so as to prevent a deformation in the fluid flow machine which is brought about by introduced heat and which impairs the operation of the fluid flow machine.
According to the invention, the intermediate sleeve is fastened either to a rotating part or to a stationary part of the brush seal. This fastening is advantageously carried out in such a way that, on the one hand, sufficient stability is achieved and, on the other hand, a heat transfer between the intermediate sleeve and the part to which the intermediate sleeve is fastened is as small as possible. The small heat transfer can be achieved, e.g., by means of the smallest possible contact surfaces and/or by providing an insulating layer between the contact surfaces of the intermediate sleeve and the part fastening the latter.
According to the invention, the brush holder can be arranged at the stator and the intermediate sleeve can be arranged at the rotor so as to rotate along with the latter. In this case, the circumferential surface of the intermediate sleeve forming the sealing surface would be an outer circumferential surface. However, it is also possible according to the invention that the brush holder is arranged at the rotor and the intermediate sleeve is arranged in a stationary manner at the stator so that the circumferential surface of the intermediate sleeve forming the sealing surface would be an inner circumferential surface in this case. The respective solution can be determined depending on the desired operating characteristics and design factors.
Further, according to the invention, the rotor can be formed, e.g., by a shaft rotating in a stator (e.g., in a housing) and, e.g., by a housing rotating around a stator (e.g., around an axle). The respective solution can be determined depending on the desired operating characteristics and the design factors.
According to an embodiment form of the invention, the intermediate sleeve divides the gap radially into a first gap portion adjoining the sealing surface and a second gap portion adjoining a circumferential surface of the intermediate sleeve remote of the sealing surface, wherein a radial extension of the second gap portion is greater than zero.
-4-In other words, there is an air gap between the intermediate sleeve and the part (e.g., the rotor or the stator) fastening this intermediate sleeve, and this air gap advantageously ensures additional thermal insulation between the intermediate sleeve and the part fastening the latter. This makes it even more difficult for heat to transfer from the sealing surface and the part fastening the intermediate sleeve so that a deformation of the part fastening the intermediate sleeve that is brought about by introduced heat is prevented in an even more reliable manner.
According to an embodiment form of the invention, the intermediate sleeve has a flange by means of which the intermediate sleeve is mounted at a flange mounting portion of the stator or rotor so as to be fixed with respect to rotation relative to it.
This construction of the invention is advantageous particularly with respect to ensuring the smallest possible contact surfaces between the intermediate sleeve and the part (in this case, particularly the stator or the rotor) fastening this intermediate sleeve, while at the same time ensuring that the fastening is sufficiently stable.
According to another embodiment form of the invention, the flange is mounted at the flange mounting portion by detachable fastening means. Such fastening means can be, for example, screw connections, rivet connections, clamping connections, etc. In particular, the detachable connection facilitates the changing of worn intermediate sleeves, for example.
Further, the flange connection makes it possible to introduce a thermal insulation layer between the flange and the flange mounting portion in a simple manner.
According to another embodiment form of the invention, the flange is arranged at an axial end of the intermediate sleeve so that the flange has, at the axial end, an annular flange surface which contacts a mounting surface of the flange mounting portion so as to be tight against fluid.
This construction of the invention reliably ensures a seal between the intermediate sleeve and the part fastening this intermediate sleeve to prevent the passage of fluid.
According to another embodiment form of the invention, the rotor is formed by a shaft and the intermediate sleeve is mounted on the rotor so as to be fixed with
According to an embodiment form of the invention, the intermediate sleeve has a flange by means of which the intermediate sleeve is mounted at a flange mounting portion of the stator or rotor so as to be fixed with respect to rotation relative to it.
This construction of the invention is advantageous particularly with respect to ensuring the smallest possible contact surfaces between the intermediate sleeve and the part (in this case, particularly the stator or the rotor) fastening this intermediate sleeve, while at the same time ensuring that the fastening is sufficiently stable.
According to another embodiment form of the invention, the flange is mounted at the flange mounting portion by detachable fastening means. Such fastening means can be, for example, screw connections, rivet connections, clamping connections, etc. In particular, the detachable connection facilitates the changing of worn intermediate sleeves, for example.
Further, the flange connection makes it possible to introduce a thermal insulation layer between the flange and the flange mounting portion in a simple manner.
According to another embodiment form of the invention, the flange is arranged at an axial end of the intermediate sleeve so that the flange has, at the axial end, an annular flange surface which contacts a mounting surface of the flange mounting portion so as to be tight against fluid.
This construction of the invention reliably ensures a seal between the intermediate sleeve and the part fastening this intermediate sleeve to prevent the passage of fluid.
According to another embodiment form of the invention, the rotor is formed by a shaft and the intermediate sleeve is mounted on the rotor so as to be fixed with
-5-respect to rotation relative to it so that the sealing surface is formed by an outer circumferential surface of the intermediate sleeve, wherein the brush holder is arranged at the stator so as to be fixed with respect to rotation relative to it.
An embodiment of the invention of the kind mentioned above can be produced in a particularly simple and dependably operating manner.
According to another embodiment form of the invention, an inner diameter of the intermediate sleeve is greater than an outer diameter of the shaft so that an annular gap is formed between an inner circumferential surface of the intermediate sleeve and an outer circumferential surface of the shaft.
This construction of the invention achieves a thermally insulating air gap between the intermediate sleeve and the part fastening this intermediate sleeve in a simple and robust manner, this part being formed in this case by the rotor which is constructed as a shaft.
According to embodiment forms of the invention, the fluid flow machine is formed by a turbo machine, particularly a gas turbine or a turbo compressor.
The invention will be described in more detail in the following with reference to preferred embodiment forms and the accompanying drawings. The drawings show:
Fig. 1 a schematic sectional view of the basic construction of a fluid flow machine constructed as a gas turbine;
Fig. 2 an enlarged section A from Fig. 1 showing a brush seal of a fluid flow machine according to the prior art; and Fig. 3 an enlarged section A' from Fig. 1 showing a brush seal of a fluid flow machine according to an embodiment form of the invention.
As is shown in Figs. 1 and 3, a fluid flow machine 1 which is constructed in this instance as a gas turbine has a stator 10 which is constructed in this instance as a gas turbine housing, a rotor 20 which is constructed in this instance as a shaft which is mounted so as to be rotatable relative to the stator 10, two rotational bearings 30, 40 which form the rotatable bearing support of the rotor 20 in the stator 10, and two brush seals 50' which seal a gap S which is formed in a radial direction RR
between the stator 10 and rotor 20 so as to be prevent the passage of fluid.
An embodiment of the invention of the kind mentioned above can be produced in a particularly simple and dependably operating manner.
According to another embodiment form of the invention, an inner diameter of the intermediate sleeve is greater than an outer diameter of the shaft so that an annular gap is formed between an inner circumferential surface of the intermediate sleeve and an outer circumferential surface of the shaft.
This construction of the invention achieves a thermally insulating air gap between the intermediate sleeve and the part fastening this intermediate sleeve in a simple and robust manner, this part being formed in this case by the rotor which is constructed as a shaft.
According to embodiment forms of the invention, the fluid flow machine is formed by a turbo machine, particularly a gas turbine or a turbo compressor.
The invention will be described in more detail in the following with reference to preferred embodiment forms and the accompanying drawings. The drawings show:
Fig. 1 a schematic sectional view of the basic construction of a fluid flow machine constructed as a gas turbine;
Fig. 2 an enlarged section A from Fig. 1 showing a brush seal of a fluid flow machine according to the prior art; and Fig. 3 an enlarged section A' from Fig. 1 showing a brush seal of a fluid flow machine according to an embodiment form of the invention.
As is shown in Figs. 1 and 3, a fluid flow machine 1 which is constructed in this instance as a gas turbine has a stator 10 which is constructed in this instance as a gas turbine housing, a rotor 20 which is constructed in this instance as a shaft which is mounted so as to be rotatable relative to the stator 10, two rotational bearings 30, 40 which form the rotatable bearing support of the rotor 20 in the stator 10, and two brush seals 50' which seal a gap S which is formed in a radial direction RR
between the stator 10 and rotor 20 so as to be prevent the passage of fluid.
-6-As can be seen particularly from Fig. 3, every brush seal 50' has a brush holder 51 and a plurality of sealing bristles 52 each of which has a first end fastened to the brush holder 51 and a second end contacting a sealing surface D' so as to form a sealing bristle-on-sealing surface contact zone, the sealing surface D' being displaceable with respect to rotation, particularly rotatable in this instance, relative to the second ends of the respective sealing bristles 52.
As can be seen from Fig. 3, the sealing surface D' is formed by an outer circumferential surface 61 of an intermediate sleeve 60 which is arranged between the stator 10 and rotor 20 and which is mounted on the rotor 20 so as to be fixed with respect to rotation relative to it and so as to divide the gap S radially. The brush holder 51 is arranged at the stator 10 so as to be fixed with respect to rotation relative to it.
The intermediate sleeve 60 divides the gap S radially into a first gap portion adjoining the sealing surface D' and a second gap portion adjoining an inner circumferential surface (not shown) of the intermediate sleeve 60 remote of the sealing surface D'. A radial extension of the second gap portion is greater than zero.
This means that an inner diameter of the intermediate sleeve 60 is greater than an outer diameter of the rotor (shaft) 20 so that an annular gap is formed between the inner circumferential surface of the intermediate sleeve 60 and an outer circumferential surface 21 of the rotor 20.
In other words, an air gap (annular gap) is provided between the intermediate sleeve 60 and the rotor 20 fastening the latter, which air gap advantageously ensures a thermal insulation between the intermediate sleeve 60 and the rotor 20. This makes it more difficult for heat to be transferred from the sealing surface D' to the rotor 20, which prevents a deformation of the rotor 20 fastening the intermediate sleeve 60 due to introduced heat.
Further, as can be seen from Fig. 3, the intermediate sleeve 60 has a flange by means of which the intermediate sleeve 60 is mounted at the flange mounting portion 22 of the rotor 20 so as to be fixed with respect to rotation relative to it. The flange 62 is arranged at an axial end of the intermediate sleeve 60 so that the flange 62 has, at the axial end, an annular flange surface (not designated separately) which contacts a recessed mounting surface (not designated separately) of the flange
As can be seen from Fig. 3, the sealing surface D' is formed by an outer circumferential surface 61 of an intermediate sleeve 60 which is arranged between the stator 10 and rotor 20 and which is mounted on the rotor 20 so as to be fixed with respect to rotation relative to it and so as to divide the gap S radially. The brush holder 51 is arranged at the stator 10 so as to be fixed with respect to rotation relative to it.
The intermediate sleeve 60 divides the gap S radially into a first gap portion adjoining the sealing surface D' and a second gap portion adjoining an inner circumferential surface (not shown) of the intermediate sleeve 60 remote of the sealing surface D'. A radial extension of the second gap portion is greater than zero.
This means that an inner diameter of the intermediate sleeve 60 is greater than an outer diameter of the rotor (shaft) 20 so that an annular gap is formed between the inner circumferential surface of the intermediate sleeve 60 and an outer circumferential surface 21 of the rotor 20.
In other words, an air gap (annular gap) is provided between the intermediate sleeve 60 and the rotor 20 fastening the latter, which air gap advantageously ensures a thermal insulation between the intermediate sleeve 60 and the rotor 20. This makes it more difficult for heat to be transferred from the sealing surface D' to the rotor 20, which prevents a deformation of the rotor 20 fastening the intermediate sleeve 60 due to introduced heat.
Further, as can be seen from Fig. 3, the intermediate sleeve 60 has a flange by means of which the intermediate sleeve 60 is mounted at the flange mounting portion 22 of the rotor 20 so as to be fixed with respect to rotation relative to it. The flange 62 is arranged at an axial end of the intermediate sleeve 60 so that the flange 62 has, at the axial end, an annular flange surface (not designated separately) which contacts a recessed mounting surface (not designated separately) of the flange
-7-mounting portion 22 in a fluid-tight manner. Although not shown in Fig. 3, a flat seal can be provided for achieving the fluid tightness and a thermal insulation between the annular flange surface of the flange 62 and the recessed mounting surface of the flange mounting portion 22.
As is shown in Fig. 3, the flange 62 is mounted at the flange mounting portion 22 of the rotor 20 by detachable fastening means which are realized in this instance in the form of a screw connection.
In conclusion, the rotor 20 which is constructed in this instance as a shaft is provided with an intermediate sleeve or intermediate bushing 60 according to an embodiment form of the invention. The intermediate sleeve 60 is connected to the rotor 20 by means of an axial flange 62 and detachable fastening means. There is an annular gap between the intermediate sleeve 60 and the rotor 20. The sealing bristles or brush wires 52 of the brush seal 50' contact the sealing surface D' formed by the outer circumferential surface 61 of the intermediate sleeve 60.
Accordingly, in the event of an out-of-true state of the intermediate sleeve 60, an uneven deformation of the intermediate sleeve 60 may only aggravate the out-of-true state of the intermediate sleeve 60 because the rotor 20 is only connected to the intermediate sleeve 60 by the connection of its flange mounting portion 22 to the flange 62 so that a direct heating of the rotor 20 caused by heat entering the area of the brush seal 50' is prevented.
The solution according to the invention can be applied wherever a fluid flow machine, e.g., a gas turbine, is to be sealed with brush seals. According to embodiment forms of the invention, the invention can be applied, e.g., in disk rotor units, full rotor units and welded rotor units.
The solution according to the invention can be used to seal a bearing periphery of a fluid flow machine and to seal between individual stages of the fluid flow machine, e.g., compressor stages or turbine stages.
Apart from the flange connection described above, fastening of the intermediate sleeve to the part which fastens or holds it can also be carried out by means of shrinking or welding or by means of other fastening elements.
As is shown in Fig. 3, the flange 62 is mounted at the flange mounting portion 22 of the rotor 20 by detachable fastening means which are realized in this instance in the form of a screw connection.
In conclusion, the rotor 20 which is constructed in this instance as a shaft is provided with an intermediate sleeve or intermediate bushing 60 according to an embodiment form of the invention. The intermediate sleeve 60 is connected to the rotor 20 by means of an axial flange 62 and detachable fastening means. There is an annular gap between the intermediate sleeve 60 and the rotor 20. The sealing bristles or brush wires 52 of the brush seal 50' contact the sealing surface D' formed by the outer circumferential surface 61 of the intermediate sleeve 60.
Accordingly, in the event of an out-of-true state of the intermediate sleeve 60, an uneven deformation of the intermediate sleeve 60 may only aggravate the out-of-true state of the intermediate sleeve 60 because the rotor 20 is only connected to the intermediate sleeve 60 by the connection of its flange mounting portion 22 to the flange 62 so that a direct heating of the rotor 20 caused by heat entering the area of the brush seal 50' is prevented.
The solution according to the invention can be applied wherever a fluid flow machine, e.g., a gas turbine, is to be sealed with brush seals. According to embodiment forms of the invention, the invention can be applied, e.g., in disk rotor units, full rotor units and welded rotor units.
The solution according to the invention can be used to seal a bearing periphery of a fluid flow machine and to seal between individual stages of the fluid flow machine, e.g., compressor stages or turbine stages.
Apart from the flange connection described above, fastening of the intermediate sleeve to the part which fastens or holds it can also be carried out by means of shrinking or welding or by means of other fastening elements.
-8-List of Reference Numbers 1 fluid flow machine stator rotor 21 outer circumferential surface 22 flange mounting portion rotational bearing rotational bearing brush seal 50' brush seal 51 brush holder 52 sealing bristles intermediate sleeve 61 outer circumferential surface 62 flange D sealing surface D' sealing surface S gap RR radial direction
Claims (9)
1. Fluid flow machine (1) with a stator (10), a rotor (20) which is supported so as to be rotatable relative to the stator (10), and a brush seal (50') which seals a gap (S) formed between the stator (10) and rotor (20) in a radial direction (RR) to prevent the passage of fluid, wherein the brush seal (50') has a brush holder (51) and a plurality of sealing bristles (52), each of which has a first end that is fastened to the brush holder (51) and a second end that contacts a sealing surface (D'), wherein the sealing surface (D') is rotationally displaceable relative to the second ends of the respective sealing bristles (52), characterized in that the sealing surface (D') is formed by a circumferential surface of an intermediate sleeve (60) which is arranged between the stator (10) and rotor (20) and which radially divides the gap (S).
2. Fluid flow machine (1) according to claim 1, wherein the intermediate sleeve (60) divides the gap (S) radially into a first gap portion adjoining the sealing surface (D') and a second gap portion adjoining a circumferential surface of the intermediate sleeve (60) remote of the sealing surface (D'), and wherein a radial extension of the second gap portion is greater than zero.
3. Fluid flow machine (1) according to claim 1 or 2, wherein the intermediate sleeve (60) has a flange (62) by means of which the intermediate sleeve (60) is mounted at a flange mounting portion (22) of the stator (10) or rotor (20) so as to be fixed with respect to rotation relative to it.
4. Fluid flow machine (1) according to claim 3, wherein the flange (62) is mounted at the flange mounting portion (22) by detachable fastening means.
5. Fluid flow machine (1) according to claim 3 or 4, wherein the flange (62) is arranged at an axial end of the intermediate sleeve (60) so that the flange (62) has, at the axial end, an annular flange surface which contacts a mounting surface of the flange mounting portion (22) so as to be tight against fluid.
6. Fluid flow machine (1) according to one of claims 1 to 5, wherein the rotor (20) is formed by a shaft, and the intermediate sleeve (60) is mounted on the rotor (20) so as to be fixed with respect to rotation relative to it so that the sealing surface (D') is formed by an outer circumferential surface (61) of the intermediate sleeve (60), and wherein the brush holder (51) is arranged at the stator (10) so as to be fixed with respect to rotation relative to it.
7. Fluid flow machine (1) according to claim 6, wherein an inner diameter of the intermediate sleeve (60) is greater than an outer diameter of the shaft so that an annular gap is formed between an inner circumferential surface of the intermediate sleeve (60) and an outer circumferential surface (21) of the shaft.
8. Fluid flow machine (1) according to one of claims 1 to 7, wherein the fluid flow machine (1) is formed by a turbo machine.
9. Fluid flow machine (1) according to claim 8, wherein the fluid flow machine (1) is formed by a gas turbine or a turbo compressor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009037393A DE102009037393A1 (en) | 2009-08-13 | 2009-08-13 | flow machine |
| DE102009037393.4-13 | 2009-08-13 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2704349A1 true CA2704349A1 (en) | 2011-02-13 |
| CA2704349C CA2704349C (en) | 2014-07-15 |
Family
ID=42989218
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2704349A Active CA2704349C (en) | 2009-08-13 | 2010-05-17 | Fluid flow machine |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20110038718A1 (en) |
| EP (1) | EP2284426B1 (en) |
| JP (1) | JP5568365B2 (en) |
| CA (1) | CA2704349C (en) |
| DE (1) | DE102009037393A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9793782B2 (en) | 2014-12-12 | 2017-10-17 | Hamilton Sundstrand Corporation | Electrical machine with reduced windage |
| EP3293360A1 (en) * | 2016-09-13 | 2018-03-14 | United Technologies Corporation | Seal system with primary and secondary seal arrangement |
| US10669873B2 (en) * | 2017-04-06 | 2020-06-02 | Raytheon Technologies Corporation | Insulated seal seat |
| US11415062B2 (en) | 2020-11-18 | 2022-08-16 | Raytheon Technologies Corporation | Rotating sleeve controlling clearance of seal assembly of gas turbine engine |
| CN114033500B (en) * | 2021-11-10 | 2024-04-02 | 北京动力机械研究所 | Rotor sealing structure of self-adaptive radial-flow turbocharging system |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3143866A1 (en) * | 1981-11-05 | 1983-05-11 | Howaldtswerke-Deutsche Werft Ag Hamburg Und Kiel, 2300 Kiel | SEALING ARRANGEMENT WITH A RADIAL SLIDING RING |
| JPH0417840Y2 (en) * | 1987-01-22 | 1992-04-21 | ||
| DE3828363A1 (en) * | 1988-08-20 | 1990-02-22 | Mtu Muenchen Gmbh | SEALING DEVICE |
| US5181728A (en) * | 1991-09-23 | 1993-01-26 | General Electric Company | Trenched brush seal |
| DE59710884D1 (en) | 1996-10-02 | 2003-11-27 | Mtu Aero Engines Gmbh | brush seal |
| US6168377B1 (en) * | 1999-01-27 | 2001-01-02 | General Electric Co. | Method and apparatus for eliminating thermal bowing of steam turbine rotors |
| JP4067709B2 (en) * | 1999-08-23 | 2008-03-26 | 三菱重工業株式会社 | Rotor cooling air supply device |
| US6435514B1 (en) | 2000-12-15 | 2002-08-20 | General Electric Company | Brush seal with positive adjustable clearance control |
| US6669228B2 (en) * | 2001-07-02 | 2003-12-30 | Delphi Technologies, Inc. | Air bag cover of polymeric foam having weakened region |
| US6575703B2 (en) * | 2001-07-20 | 2003-06-10 | General Electric Company | Turbine disk side plate |
| DE50206223D1 (en) * | 2001-10-22 | 2006-05-18 | Sulzer Pumpen Ag | Shaft sealing arrangement for a pump for conveying hot fluids |
| US6811374B2 (en) * | 2002-10-31 | 2004-11-02 | General Electric Company | Raised rotor platform with an internal breech ring locking mechanism for brush seal application in a turbine and methods of installation |
| US7410173B2 (en) * | 2003-05-01 | 2008-08-12 | Justak John F | Hydrodynamic brush seal |
| US6976679B2 (en) * | 2003-11-07 | 2005-12-20 | The Boeing Company | Inter-fluid seal assembly and method therefor |
-
2009
- 2009-08-13 DE DE102009037393A patent/DE102009037393A1/en not_active Withdrawn
-
2010
- 2010-04-13 EP EP10159701.1A patent/EP2284426B1/en active Active
- 2010-04-28 JP JP2010103660A patent/JP5568365B2/en active Active
- 2010-05-17 CA CA2704349A patent/CA2704349C/en active Active
- 2010-07-22 US US12/841,317 patent/US20110038718A1/en not_active Abandoned
Also Published As
| Publication number | Publication date |
|---|---|
| EP2284426A2 (en) | 2011-02-16 |
| CA2704349C (en) | 2014-07-15 |
| DE102009037393A1 (en) | 2011-02-17 |
| EP2284426A3 (en) | 2014-03-12 |
| JP2011038509A (en) | 2011-02-24 |
| EP2284426B1 (en) | 2018-10-24 |
| JP5568365B2 (en) | 2014-08-06 |
| US20110038718A1 (en) | 2011-02-17 |
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| EEER | Examination request |