EP3052813B1 - Turbo engine with torsional coupling integrated to the driving and the driven shaft - Google Patents
Turbo engine with torsional coupling integrated to the driving and the driven shaft Download PDFInfo
- Publication number
- EP3052813B1 EP3052813B1 EP14780832.3A EP14780832A EP3052813B1 EP 3052813 B1 EP3052813 B1 EP 3052813B1 EP 14780832 A EP14780832 A EP 14780832A EP 3052813 B1 EP3052813 B1 EP 3052813B1
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- EP
- European Patent Office
- Prior art keywords
- shaft
- driving
- driven
- coupling
- torsional
- 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.)
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Links
- 230000008878 coupling Effects 0.000 title claims description 50
- 238000010168 coupling process Methods 0.000 title claims description 50
- 238000005859 coupling reaction Methods 0.000 title claims description 50
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 6
- 239000007789 gas Substances 0.000 description 5
- 238000003754 machining Methods 0.000 description 5
- 238000005242 forging Methods 0.000 description 3
- 230000007547 defect Effects 0.000 description 2
- 238000009760 electrical discharge machining Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000000112 cooling gas Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
- F04D29/054—Arrangements for joining or assembling shafts
-
- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/026—Shaft to shaft connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/022—Units comprising pumps and their driving means comprising a yielding coupling, e.g. hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/043—Shafts
- F04D29/044—Arrangements for joining or assembling shafts
Definitions
- the invention relates to turbo engines, for example integrated motor-driven compressors.
- turbo engines for example integrated motor-driven compressors.
- a turbo alternator for example a turbo alternator.
- US 3 368 743 A discloses a shaft construction in which two rigid shafts are interconnected by a relatively flexible intermediately located shaft part.
- An integrated motor-driven compressor group comprises a leakproof housing which contains an engine, for example an electric motor, and a compressor group, for example a multi-stage unit, which comprises one or several wheels with blades for compression carried by a driven driven shaft and actuated by a driving driving shaft consisting of the rotor of the motor or actuated by the latter.
- an engine for example an electric motor
- a compressor group for example a multi-stage unit, which comprises one or several wheels with blades for compression carried by a driven driven shaft and actuated by a driving driving shaft consisting of the rotor of the motor or actuated by the latter.
- One coupling solution for the driving shaft and the driven shaft consists in a coupling of the driven shaft and the driving shaft by means of a rigid coupling, with bearings provided for supporting the ends of the line of shafts of the motor-driven compressor group, as well as its median portion.
- the currently used flexible couplings which are generally of the type with a membrane, increase the axial dimension of the motor-driven compressor group, typically of the order of 35 to 40 cm, compared to a rigid coupling with a flange.
- they present a fragility zone because they can be subjected, for example, only to tensile or compression forces that are limited in the axial direction.
- the gas feeding the compressor is extracted in full or in part after the compression stage and is used for cooling the motor.
- the flow of the cooling gas in the motor takes place in the direction of the compressor.
- the motor-driven compressor has a single abutment on the rotor of the compressor, on the opposite side of the coupling. Due to this fact, an axial thrust is generated in the motor and is absorbed by the coupling prior to being taken over by the axial abutment. Therefore, in order to alleviate these inconveniences, it has been proposed to use a torsional coupling placed in a hollow shaft of the compressor. Such a layout is described in the document FR 2 969 722 . Although it is effective in alleviating the inconveniences related to the use of a flexible coupling between the driving shaft and the driven shaft, such a layout complicates the structure of the shaft assembly.
- the aim of the invention is to mitigate the inconveniences related to the layouts according to the state of the art and, in particular, to enable the axial efforts generated during the functioning of the levels of compression to be supported and this in a simple layout.
- the object of the invention is a turbo engine comprising a driving shaft and a driven shaft actuated by the driving shaft being coupled driven to this driving shaft by means of a torsional coupling.
- the torsional coupling is integrated into the driven and driving shafts which comprise a flexible zone in torsion so as to form the said torsional coupling.
- This can be, for example, a motor-driven compressor group comprising a motor driving a compressor, comprising a set of wheels with blades for compression mounted on the driven shaft.
- the set is mounted in a common housing which is impermeable to the gas generated by the motor-driven compressor group.
- the shaft in which the torsional coupling is integrated, comprises, in addition, preferably, an external peripheral zone which constitutes a means for supporting the functions performed by the rotor.
- This torsional zone existing in the driving and driven shafts, is formed by a cylindric part with a diameter that is smaller than the remaining part of the shaft in which the torsional coupling is integrated.
- the shaft assembly comprises an internal shaft with reduced dimensions, through which the driving and driven shafts are coupled, permitting a localized deformation of the shaft assembly by the torsion.
- the torsional cylindrical part can be entirely in projection starting from the shaft, into which the coupling is integrated, or can be partially or totally situated in the interior of a hollow part, in the form of a hollow shaft, enabling the hollow shaft to support one or several functions carried out by the rotor.
- the torsional cylindrical part is located inside the hollow shaft, it is thus in cantilever around the torsional part. This solution can be realized eventually by means of a throat or by reducing the diameter and of the assembly.
- the realization of the torsional part partially or completely inside a hollow part enables the length of the shaft assembly to be limited and thereby the dimensions, the weight and the cost of the turbo engine.
- cylindrical part(s) can be obtained by using various techniques.
- One embodiment comprises an axial cylindrical throat, which delimits in the said shaft another internal shaft which is coupled to the other driving or driven shaft and one external shaft.
- the axial cylindrical throat is formed by means of electroerosion.
- this torsional coupling is obtained by providing at the manufacturing stage a reduction of the diameter (for example by means of forging and by machining) in the driven and/or driving shaft.
- At least one of the driven and driving shafts comprises in its torsional coupling zone one axial cylindrical throat delimited by an internal shaft and one external shaft assembled around the internal shaft.
- the external shaft is extending till the connection zone of the driving and driven shafts.
- the free end of the shaft, into which the torsional coupling is integrated at a diameter that is greater than the diameter of its median part forms a coupling zone of the said internal shaft with the other driving or driven shaft.
- the free end of the shaft, to which the torsional coupling is integrated has a diameter that is less than those of the coupling zone corresponding to the other driving or driven shaft, with which it is coupled, forming a flange that ensures the coupling of the said driving or driven shafts.
- a motor-driven compressor designated by the general reference G, comprises essentially a motor 1, for example an electric motor with high rotational speed, for example between 6,000 and 16,000 revolutions/minute, powered by a frequency converter and comprising a stator 2 and a rotor 3 forming a driving shaft for the motor-driven compressor group, and a compressor group 4 comprising a set of wheels with blades 5, 6 and 7, here three in number, mounted on the driven shaft 8.
- the driven shaft 8 is supported by the radial bearings 9.
- the arrangement is mounted on a base (not shown) and is located in a common casing 10, which is impermeable to the gas generated by the motor-driven compressor group.
- the casing 10 comprises an input "INPUT”, through which the gas to be generated is drawn by suction into the compressor and an output "OUTPUT”, through which the compressed gas is delivered when it exits from the compressor group 4.
- the compressor group 4 comprises three wheels with blades mounted on the driven shaft 8.
- the compressor group 4 can comprise any number of such wheels with blades or comprise a different layout of wheels with blades.
- the driven shaft 8 is equipped, at the level of its end zone, with a shoulder E, with which this shaft is bolted on the one end with respect to the driving shaft 3 of the motor 1.
- the coupling between the driven shaft and the driving shaft consists of a torsional coupling.
- This torsional coupling is obtained by the implementation in both the driven and driving shafts of a torsional zone, i.e. flexible in the rotation.
- a torsional coupling is obtained by machining an axial cylindrical throat 11 in the driven shaft 8, in order to form in the driven shaft 8 an internal shaft 12, through which the driven shaft 8 is coupled to the driving shaft 3, and an external shaft 13, through which the driven shaft 8 is guided by the radial bearing 9.
- the length of the throat will be selected in relation to the diameter of the shaft, in which it is mounted, with a length chosen in such a way as to confer to the coupling a torsional character.
- the useful diameter of the shaft 8, which transmits the actuation efforts is locally reduced, and its resistance to torsional and radial deformations can be reduced, while retaining an important radial rigidity.
- the driven shaft and in particular the internal shaft 12 remain notably capable of withstanding the axial force created during the operation of the wheels with compression blades 5, 6 and 7.
- the presence of the torsional part enables because of the localized reduction of the useful section of the shaft assembly, the driven shaft 8 to be endowed with the characteristic that it can be deformed by bending and by elastic torsion so that on the one hand, defects in the angular alignment, on the one hand, and on the other lateral defects, on the other, between the driven shaft and the driving shaft can be compensated, either during the installation of the motor-driven compressor or while it is in operation.
- This flexibility also enables the flexural vibrations between the driving shaft and the driven shaft to be filtered.
- the torsional zone enables a gradation to be achieved of the efforts transmitted during the rapid changes of the torque transmitted by the motor or the resistive torque produced by the compressor.
- the mounting is largely simplified since the shaft assembly is constituted simply by two portions of the shafts, namely the driving shaft and the driven shaft.
- the torsional part is mounted in the driven shaft 8.
- the driven shaft 8 comprises an external shaft 13, whose end is behind in relation to the free end of the internal shaft 12, with which this shaft 12 was fixed to the driving shaft 3.
- the internal shaft 12 has a diameter that is smaller than the diameter of the end formed by the shoulder E.
- the torsional coupling is obtained, as can be seen in figures 1 and 2 , by obtaining, at the manufacturing stage, for example by means of forging and by machining of the driven shaft 8, a localized reduction of the diameter in order to form the end zone 12 of the driven shaft of reduced diameter, the cylindrical throat being then realized in order to form the external shaft 13.
- the torsional coupling obtained as shown in figures 1 and 2 , by arranging a throat in the driving shaft is - according to the invention - also formed by arranging this throat in the driving shaft, i.e. in the two shafts - driving and driven.
- the external shaft 13 extends over a substantial part of the internal shaft 12, which here does not have an end shoulder. Therefore, the mounting of the internal shaft 12 on the end of the driving shaft 3 employs a flange 14 fixed by being bolted onto the free end of the driving shaft 3 and connected in rotation to the internal shaft 12.
- Axial throat could be provided, for example, in the internal peripheral surface of the flange 14, destined to engage with the corresponding ribs mounted at the free end of the internal shaft 12.
- a flange with a general conical form or endowed with an end shoulder as can be seen in figure 3 can be used.
- the driving shaft 3 and the driven shaft 4 both have an axial cylindrical throat 11 and 11a.
- the throat 11 is similar to the throat used in the embodiment in figure 3 .
- the axial cylindrical throat 11 creates an internal shaft 12 and an external shaft 13 which are extended along a substantial part of the internal shaft 12, with this internal shaft 12 extending in a projection starting from the external shaft 13 along a length that is sufficient for the mounting of a flange 15.
- the axial cylindrical throat 11a creates in this shaft 3, an internal shaft 16 and an external shaft 17 which are extended along a substantial part of the internal shaft 16, with the latter extending in a projection beyond the free end of the external shaft 17 along a length that is sufficient for the mounting of the flange 15.
- the torsional zone of the shaft assembly is formed in the driving shaft 3 and in the driven shaft 8.
- the shaft assembly comprises a torsional zone with increased length.
- the implementation of the torsional zone consists, in particular, in the realization of the internal shaft within the driven shaft 8, through which the driven shaft 8 is coupled driven to the driving shaft 3, and of an external shaft 13, which is then assembled to the driven shaft 8 and through which the latter is guided by the radial bearing 9 in a way as to form a cylindrical throat between the two internal and external shafts.
- the external shaft is assembled around the zone of the shaft which has a reduced diameter.
- the hollow part can be assembled on the rotor, for example close to the torsional zone, for example by bolting and/or through the diameter of the abutment and/or by means of a toothed hirth and/or by using many other assembly modes.
- the driven shaft comprises an internal shaft 12 and an external shaft 13
- the external shaft can then be used for the implementation of functions carried out by the rotor.
- a bearing support and/or a support of one or several wheel(s) with blade(s) can be realized ( figure 3 ).
- the invention is not limited to what is described above. It is also possible, according to the invention, to arrange the axial cylindrical throat in the driving shaft and in the driven shaft and to make sure, regarding both the driving shaft and the driven shaft, that the distance between the ends of the shafts, namely between the ends of the two exterior shafts 13 and 17, is equal to half of the torsional length or, in other terms, to ensure that the length of the interior shaft, which extends outside the exterior shaft, is equal to the length of the exterior shaft, as described in the reference to figure 2 , both as regards the driving shaft and the driven shaft.
- the torsional zone can be formed by the realization, during the manufacture of the driven shaft, of a zone 18 with diameter that is reduced in a such a way as to confer on the coupling a torsional character.
- the coupling with the driving shaft can be realized both by providing a shoulder E at the end, as shown, or by using a fitted flange.
- the reduced diameter zone can also be realized independently from the rest of the driven shaft and can be assembled, as previously indicated in the reference to the figures 2 to 4 , to the driven shaft.
- the reduced diameter zone can be formed in the driving shaft or in the two driven and driving shafts. It is to be noted that, as shown in figures 1 to 4 , the length of the reduced diameter zone is chosen in relation to the diameter of this zone in a way as to confer a torsional character on the shaft.
- the torsional zone can be realized over a length between 600 and 700 mm.
- the axial cylindrical throat produced in the driven shaft and/or in the driving shaft can be formed by means of electroerosion or by EDM ("Electrical Discharge Machining" ), which is a machining procedure consisting in the removal of material in one piece by using electric discharges.
- EDM Electro Discharge Machining
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Description
- The invention relates to turbo engines, for example integrated motor-driven compressors. However, of course one does not go outside the framework of the present invention merely because it relates to another type of turbo engine, namely a turbo alternator.
-
US 3 368 743 A discloses a shaft construction in which two rigid shafts are interconnected by a relatively flexible intermediately located shaft part. - An integrated motor-driven compressor group comprises a leakproof housing which contains an engine, for example an electric motor, and a compressor group, for example a multi-stage unit, which comprises one or several wheels with blades for compression carried by a driven driven shaft and actuated by a driving driving shaft consisting of the rotor of the motor or actuated by the latter.
- One coupling solution for the driving shaft and the driven shaft consists in a coupling of the driven shaft and the driving shaft by means of a rigid coupling, with bearings provided for supporting the ends of the line of shafts of the motor-driven compressor group, as well as its median portion.
- This solution poses in a certain number of cases manufacturing problems and problems related to the dynamic of the rotor.
- Therefore, it is proposed to couple the driving shaft and the driven shaft by means of a flexible coupling in order to avoid the problems related to the alignment. In this respect, one can refer to the document
WO 2004/083644 which describes such a layout. - The currently used flexible couplings, which are generally of the type with a membrane, increase the axial dimension of the motor-driven compressor group, typically of the order of 35 to 40 cm, compared to a rigid coupling with a flange. In addition, they present a fragility zone because they can be subjected, for example, only to tensile or compression forces that are limited in the axial direction.
- However, during the functioning of the layout described by the document
WO 2004/083644 , the gas feeding the compressor is extracted in full or in part after the compression stage and is used for cooling the motor. The flow of the cooling gas in the motor takes place in the direction of the compressor. - The motor-driven compressor has a single abutment on the rotor of the compressor, on the opposite side of the coupling. Due to this fact, an axial thrust is generated in the motor and is absorbed by the coupling prior to being taken over by the axial abutment. Therefore, in order to alleviate these inconveniences, it has been proposed to use a torsional coupling placed in a hollow shaft of the compressor. Such a layout is described in the
document FR 2 969 722 - In view of the preceding discussion, the aim of the invention is to mitigate the inconveniences related to the layouts according to the state of the art and, in particular, to enable the axial efforts generated during the functioning of the levels of compression to be supported and this in a simple layout.
- Therefore, the object of the invention is a turbo engine comprising a driving shaft and a driven shaft actuated by the driving shaft being coupled driven to this driving shaft by means of a torsional coupling.
- The present invention is defined in the accompanying claims.
- Accordingly, the torsional coupling is integrated into the driven and driving shafts which comprise a flexible zone in torsion so as to form the said torsional coupling.
- This can be, for example, a motor-driven compressor group comprising a motor driving a compressor, comprising a set of wheels with blades for compression mounted on the driven shaft.
- The set is mounted in a common housing which is impermeable to the gas generated by the motor-driven compressor group.
- Because the torsional coupling is integrated in the driving and the driven shaft, the problems, namely in terms of design and manufacturing, in the assembly, which exist in the case of a torsional coupling assembled to a driving or driven shaft, such as described in the above-quoted
document FR 2 969 722 - The shaft, in which the torsional coupling is integrated, comprises, in addition, preferably, an external peripheral zone which constitutes a means for supporting the functions performed by the rotor.
- This torsional zone, existing in the driving and driven shafts, is formed by a cylindric part with a diameter that is smaller than the remaining part of the shaft in which the torsional coupling is integrated.
- It has, advantageously, a length selected in relation to the diameter in a way to confer to the coupling a torsional capability. Thanks to the presence of this reduction of the diameter, the shaft assembly comprises an internal shaft with reduced dimensions, through which the driving and driven shafts are coupled, permitting a localized deformation of the shaft assembly by the torsion.
- The torsional cylindrical part can be entirely in projection starting from the shaft, into which the coupling is integrated, or can be partially or totally situated in the interior of a hollow part, in the form of a hollow shaft, enabling the hollow shaft to support one or several functions carried out by the rotor. When the torsional cylindrical part is located inside the hollow shaft, it is thus in cantilever around the torsional part. This solution can be realized eventually by means of a throat or by reducing the diameter and of the assembly.
- The realization of the torsional part partially or completely inside a hollow part enables the length of the shaft assembly to be limited and thereby the dimensions, the weight and the cost of the turbo engine.
- This can have also a beneficial effect on the dynamics of the rotor.
- It has to be noted that the cylindrical part(s) can be obtained by using various techniques.
- One embodiment, comprises an axial cylindrical throat, which delimits in the said shaft another internal shaft which is coupled to the other driving or driven shaft and one external shaft. For example, the axial cylindrical throat is formed by means of electroerosion.
- Alternatively, this torsional coupling is obtained by providing at the manufacturing stage a reduction of the diameter (for example by means of forging and by machining) in the driven and/or driving shaft.
- In this case, at least one of the driven and driving shafts comprises in its torsional coupling zone one axial cylindrical throat delimited by an internal shaft and one external shaft assembled around the internal shaft.
- In one embodiment mode, the external shaft is extending till the connection zone of the driving and driven shafts.
- According to another embodiment, the free end of the shaft, into which the torsional coupling is integrated at a diameter that is greater than the diameter of its median part, forms a coupling zone of the said internal shaft with the other driving or driven shaft. Alternatively, it is also possible to ensure that that the free end of the shaft, to which the torsional coupling is integrated, has a diameter that is less than those of the coupling zone corresponding to the other driving or driven shaft, with which it is coupled, forming a flange that ensures the coupling of the said driving or driven shafts. Other objectives, characteristics and advantages of the invention will become apparent from a reading of the following description, which is provided solely as an example without limitations and refers to the attached drawings in which:
-
Figure 1 is a synoptic diagram illustrating the general structure of a motor-driven compressor group; -
Figure 2 illustrates a first example of the motor-driven compressor group according tofigure 1 ; -
Figure 3 illustrates another example of a motor-driven compressor group; -
Figure 4 illustrates an embodiment according to the invention; and -
Figure 5 illustrates another implementation mode of the torsional zone. - Referring first to
figure 1 , a motor-driven compressor, designated by the general reference G, comprises essentially amotor 1, for example an electric motor with high rotational speed, for example between 6,000 and 16,000 revolutions/minute, powered by a frequency converter and comprising astator 2 and arotor 3 forming a driving shaft for the motor-driven compressor group, and acompressor group 4 comprising a set of wheels withblades shaft 8. As it can be seen, the drivenshaft 8 is supported by the radial bearings 9. - The arrangement is mounted on a base (not shown) and is located in a
common casing 10, which is impermeable to the gas generated by the motor-driven compressor group. Thecasing 10 comprises an input "INPUT", through which the gas to be generated is drawn by suction into the compressor and an output "OUTPUT", through which the compressed gas is delivered when it exits from thecompressor group 4. - In the example shown, the
compressor group 4 comprises three wheels with blades mounted on the drivenshaft 8. Obviously, thecompressor group 4 can comprise any number of such wheels with blades or comprise a different layout of wheels with blades. - As illustrated in
figures 1 and 2 , the drivenshaft 8 is equipped, at the level of its end zone, with a shoulder E, with which this shaft is bolted on the one end with respect to the drivingshaft 3 of themotor 1. - In any case, the coupling between the driven shaft and the driving shaft consists of a torsional coupling.
- This torsional coupling is obtained by the implementation in both the driven and driving shafts of a torsional zone, i.e. flexible in the rotation.
- As shown in
figures 1 to 4 , a torsional coupling is obtained by machining an axialcylindrical throat 11 in the drivenshaft 8, in order to form in the drivenshaft 8 aninternal shaft 12, through which the drivenshaft 8 is coupled to thedriving shaft 3, and anexternal shaft 13, through which the drivenshaft 8 is guided by the radial bearing 9. The length of the throat will be selected in relation to the diameter of the shaft, in which it is mounted, with a length chosen in such a way as to confer to the coupling a torsional character. - In this way, by mounting the cylindrical throat in the driven
shaft 8, the useful diameter of theshaft 8, which transmits the actuation efforts is locally reduced, and its resistance to torsional and radial deformations can be reduced, while retaining an important radial rigidity. The driven shaft and in particular theinternal shaft 12 remain notably capable of withstanding the axial force created during the operation of the wheels withcompression blades - The presence of the torsional part enables because of the localized reduction of the useful section of the shaft assembly, the driven
shaft 8 to be endowed with the characteristic that it can be deformed by bending and by elastic torsion so that on the one hand, defects in the angular alignment, on the one hand, and on the other lateral defects, on the other, between the driven shaft and the driving shaft can be compensated, either during the installation of the motor-driven compressor or while it is in operation. - This flexibility also enables the flexural vibrations between the driving shaft and the driven shaft to be filtered.
- Furthermore, the torsional zone enables a gradation to be achieved of the efforts transmitted during the rapid changes of the torque transmitted by the motor or the resistive torque produced by the compressor.
- In addition, the mounting is largely simplified since the shaft assembly is constituted simply by two portions of the shafts, namely the driving shaft and the driven shaft.
- It is to be noted that in the example illustrated in
figures 1 and 2 , the torsional part is mounted in the drivenshaft 8. In addition, the drivenshaft 8 comprises anexternal shaft 13, whose end is behind in relation to the free end of theinternal shaft 12, with which thisshaft 12 was fixed to the drivingshaft 3. In other terms, theinternal shaft 12 has a diameter that is smaller than the diameter of the end formed by the shoulder E. - In addition, the torsional coupling is obtained, as can be seen in
figures 1 and 2 , by obtaining, at the manufacturing stage, for example by means of forging and by machining of the drivenshaft 8, a localized reduction of the diameter in order to form theend zone 12 of the driven shaft of reduced diameter, the cylindrical throat being then realized in order to form theexternal shaft 13. - The torsional coupling obtained as shown in
figures 1 and 2 , by arranging a throat in the driving shaft is - according to the invention - also formed by arranging this throat in the driving shaft, i.e. in the two shafts - driving and driven. - In another example, which can be seen in
figure 3 , theexternal shaft 13 extends over a substantial part of theinternal shaft 12, which here does not have an end shoulder. Therefore, the mounting of theinternal shaft 12 on the end of the drivingshaft 3 employs a flange 14 fixed by being bolted onto the free end of the drivingshaft 3 and connected in rotation to theinternal shaft 12. Axial throat could be provided, for example, in the internal peripheral surface of the flange 14, destined to engage with the corresponding ribs mounted at the free end of theinternal shaft 12. - In this respect, a flange with a general conical form or endowed with an end shoulder as can be seen in
figure 3 can be used. - This is advantageous insofar as it enables the distance between the ends of the shafts to be reduced, i.e. the distance between the free end of the
external shaft 13 and the free end with respect to the drivingshaft 3, this distance being fixed by the length of the flange 14. - According to an embodiment of the invention, shown in
figure 4 , the drivingshaft 3 and the drivenshaft 4 both have an axialcylindrical throat 11 and 11a. Thethroat 11 is similar to the throat used in the embodiment infigure 3 . - As in the examples described above, as regards the driven shaft, the axial
cylindrical throat 11 creates aninternal shaft 12 and anexternal shaft 13 which are extended along a substantial part of theinternal shaft 12, with thisinternal shaft 12 extending in a projection starting from theexternal shaft 13 along a length that is sufficient for the mounting of aflange 15. - As regards the driving
shaft 3, the axial cylindrical throat 11a creates in thisshaft 3, aninternal shaft 16 and anexternal shaft 17 which are extended along a substantial part of theinternal shaft 16, with the latter extending in a projection beyond the free end of theexternal shaft 17 along a length that is sufficient for the mounting of theflange 15. Thus, in this embodiment, the torsional zone of the shaft assembly is formed in the drivingshaft 3 and in the drivenshaft 8. - In other terms, with respect to the previously described examples, the shaft assembly comprises a torsional zone with increased length.
- It is to be noted that the example resp. embodiment shown in
figures 3 and 4 , in which the mounting of the driven shaft and the driving shaft is performed by means of a fitted flange, enabling the torsional zone to be created at the manufacturing stage namely by means of forging and then by machining. - The implementation of the torsional zone consists, in particular, in the realization of the internal shaft within the driven
shaft 8, through which the drivenshaft 8 is coupled driven to the drivingshaft 3, and of anexternal shaft 13, which is then assembled to the drivenshaft 8 and through which the latter is guided by the radial bearing 9 in a way as to form a cylindrical throat between the two internal and external shafts. In other terms, and as this is illustrated with a dotted line in the figures, the external shaft is assembled around the zone of the shaft which has a reduced diameter. - Such an assembly can be obtained with various means. The hollow part can be assembled on the rotor, for example close to the torsional zone, for example by bolting and/or through the diameter of the abutment and/or by means of a toothed hirth and/or by using many other assembly modes.
- The example resp. embodiment shown in the
figures 3 and 4 , in which the driven shaft comprises aninternal shaft 12 and anexternal shaft 13, are also advantageous since the external shaft can then be used for the implementation of functions carried out by the rotor. - In particular, a bearing support and/or a support of one or several wheel(s) with blade(s) can be realized (
figure 3 ). - Obviously, the invention is not limited to what is described above. It is also possible, according to the invention, to arrange the axial cylindrical throat in the driving shaft and in the driven shaft and to make sure, regarding both the driving shaft and the driven shaft, that the distance between the ends of the shafts, namely between the ends of the two
exterior shafts figure 2 , both as regards the driving shaft and the driven shaft. - Therefore, as shown in
figure 5 , the torsional zone can be formed by the realization, during the manufacture of the driven shaft, of a zone 18 with diameter that is reduced in a such a way as to confer on the coupling a torsional character. As previously described, the coupling with the driving shaft can be realized both by providing a shoulder E at the end, as shown, or by using a fitted flange. - The reduced diameter zone can also be realized independently from the rest of the driven shaft and can be assembled, as previously indicated in the reference to the
figures 2 to 4 , to the driven shaft. - Obviously, as it was previously indicated, as an alternative the reduced diameter zone can be formed in the driving shaft or in the two driven and driving shafts. It is to be noted that, as shown in
figures 1 to 4 , the length of the reduced diameter zone is chosen in relation to the diameter of this zone in a way as to confer a torsional character on the shaft. - For example, for a shaft diameter of the order of 50 mm, the torsional zone can be realized over a length between 600 and 700 mm.
- And finally, it is to be noted that the axial cylindrical throat produced in the driven shaft and/or in the driving shaft, can be formed by means of electroerosion or by EDM ("Electrical Discharge Machining" ), which is a machining procedure consisting in the removal of material in one piece by using electric discharges.
Claims (12)
- A turbo engine, comprising a driving shaft (3) and a driven shaft (8) actuated by the driving shaft, which is coupled to this driving shaft by means of a torsional coupling, wherein the torsional coupling is integrated in at least one of the driven and driving shafts which comprises a zone that is flexible in rotation, in a manner to constitute the said torsional coupling, wherein the flexible zone comprises a cylindrical part (12, 16) with a diameter that is smaller than the rest of the shaft (3, 8) into which the flexible coupling is integrated, characterized in that the cylindrical part (12, 16) is mounted in the driven shaft (8) and in the driving shaft (3).
- A turbo engine according to claim 1, wherein the shaft, into which the torsional coupling is integrated, additionally comprises an external peripheral zone (13, 17), which constitutes a means of support to the functions carried out by the rotor.
- A turbo engine according to claim 1 or claim 2, wherein the length of the cylindrical part (12, 16) is selected in relation to the diameter in such a way as to confer a torsional character to the coupling.
- A turbo engine according to any one of the preceding claims, wherein the torsional cylindrical part is entirely in projection starting from the shaft (3, 8) into which the coupling is integrated.
- A turbo engine according to any one of the preceding claims, wherein the torsional cylindrical part is partially or completely located inside a hollow part (13).
- A turbo engine according to any of the preceding claims, wherein at least one of the driven and driving shafts (3; 8) comprises in its torsional coupling zone an axial cylindrical throat (11, 11a) delimiting in the said shaft an internal shaft (12), which is coupled to the other driving or driven shaft, and an external shaft (13).
- A turbo engine according to claim 6, wherein the axial cylindrical throat (11; 11a) is formed by means of electroerosion.
- A turbo engine according to any of the claims 1 to 5, wherein at least one of the driven and driving shafts comprises in its torsional coupling zone an axial cylindrical throat (11, 11a) delimited by an internal shaft (12) and an external shaft (13) assembled around the internal shaft (12).
- A turbo engine according to any of the claims 6, 7 and 8, depending on claim 2, wherein the external shaft (13) constitutes the said means of support for the functions carried out by the rotor.
- A turbo engine according to any of the claims 6, 7 and 8, wherein the external shaft (13) is extended as far as the zone of the connection of the driving and driven shafts.
- A turbo engine according to any of the claims 1 to 10, wherein the free end of the shaft (12), into which the torsional coupling is integrated, has a diameter that is greater than that of its median part and forms a coupling zone of the said internal shaft with the other driving or driven shaft.
- A turbo engine according to any of the claims 1 to 10, wherein the free end of the shaft, into which the torsional coupling is integrated, has a diameter that is smaller than that of the coupling zone corresponding to the other driving or driven shaft, with which it is coupled and in which a flange (15) ensures the coupling of the said shafts.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1359553A FR3011291B1 (en) | 2013-10-02 | 2013-10-02 | TURBOMACHINE WITH TORSIBLE COUPLING INTEGRATED WITH AT LEAST ONE SHAFT AND / OR LEAD |
PCT/EP2014/071057 WO2015049295A1 (en) | 2013-10-02 | 2014-10-01 | Turbo engine with torsional coupling integrated to at least one driving or driven shaft driving |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3052813A1 EP3052813A1 (en) | 2016-08-10 |
EP3052813B1 true EP3052813B1 (en) | 2023-07-19 |
Family
ID=49911669
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14780832.3A Active EP3052813B1 (en) | 2013-10-02 | 2014-10-01 | Turbo engine with torsional coupling integrated to the driving and the driven shaft |
Country Status (10)
Country | Link |
---|---|
US (1) | US20160245088A1 (en) |
EP (1) | EP3052813B1 (en) |
JP (2) | JP2016532805A (en) |
KR (1) | KR102266201B1 (en) |
CN (1) | CN105593530A (en) |
BR (1) | BR112016005995B1 (en) |
CA (1) | CA2925413C (en) |
FR (1) | FR3011291B1 (en) |
MX (1) | MX2016004281A (en) |
WO (1) | WO2015049295A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7429541B2 (en) * | 2020-01-06 | 2024-02-08 | 三菱重工コンプレッサ株式会社 | compressor system |
US11454140B1 (en) | 2021-11-09 | 2022-09-27 | Borgwarner Inc. | Torque-limiting rotor coupling for an electrically-actuated camshaft phaser |
US11454141B1 (en) | 2021-11-09 | 2022-09-27 | Borgwarner Inc. | Torque limited variable camshaft timing assembly |
US11940030B1 (en) | 2022-10-24 | 2024-03-26 | Borgwarner Inc. | Torque-limiting torsion gimbal |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1440721A (en) * | 1965-04-12 | 1966-06-03 | Cem Comp Electro Mec | Improvement in shafts for rotating machines |
DE1628779A1 (en) * | 1966-05-11 | 1970-07-02 | Siemens Elektrogeraete Gmbh | Drain pump, especially for washing machines or dishwashers |
JP3116233B2 (en) * | 1990-05-17 | 2000-12-11 | 三信工業株式会社 | Thrust receiving structure of ship propulsion machine |
ITMI20051518A1 (en) * | 2005-08-02 | 2007-02-03 | Nuovo Pignone Spa | SYSTEM FOR ELECTROEROSION FOR THE CONSTRUCTION OF A HOLLOW OR I A SHAPED HOLE IN A PARTICULAR |
JP5150346B2 (en) * | 2008-04-16 | 2013-02-20 | 泉陽興業株式会社 | Ferris wheel |
CN201236832Y (en) * | 2008-08-06 | 2009-05-13 | 杨怀庆 | Household miniature flexible shaft pump |
JP5660803B2 (en) * | 2009-08-17 | 2015-01-28 | Jfeシビル株式会社 | Steel pipe pole joint structure and steel pipe pole joined thereby |
CN201739213U (en) * | 2010-07-16 | 2011-02-09 | 潘海龙 | Flexible shaft centrifugal submersible pump |
FR2966528B1 (en) * | 2010-10-25 | 2016-12-30 | Thermodyn | CENTRIFUGAL COMPRESSOR GROUP |
FR2969722B1 (en) * | 2010-12-22 | 2013-01-04 | Thermodyn | TORSIBLE COUPLING MOTORCOMPRESSOR UNIT LOCATED IN A HOLLOW COMPRESSOR SHAFT |
-
2013
- 2013-10-02 FR FR1359553A patent/FR3011291B1/en active Active
-
2014
- 2014-10-01 EP EP14780832.3A patent/EP3052813B1/en active Active
- 2014-10-01 US US15/026,464 patent/US20160245088A1/en not_active Abandoned
- 2014-10-01 MX MX2016004281A patent/MX2016004281A/en unknown
- 2014-10-01 JP JP2016518684A patent/JP2016532805A/en active Pending
- 2014-10-01 CN CN201480054645.1A patent/CN105593530A/en active Pending
- 2014-10-01 BR BR112016005995-6A patent/BR112016005995B1/en active IP Right Grant
- 2014-10-01 CA CA2925413A patent/CA2925413C/en active Active
- 2014-10-01 KR KR1020167010970A patent/KR102266201B1/en active IP Right Grant
- 2014-10-01 WO PCT/EP2014/071057 patent/WO2015049295A1/en active Application Filing
-
2020
- 2020-03-02 JP JP2020035290A patent/JP2020112161A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
JP2020112161A (en) | 2020-07-27 |
BR112016005995B1 (en) | 2022-03-03 |
CA2925413A1 (en) | 2015-04-09 |
FR3011291A1 (en) | 2015-04-03 |
KR20160060752A (en) | 2016-05-30 |
BR112016005995A2 (en) | 2017-08-01 |
CA2925413C (en) | 2022-08-02 |
EP3052813A1 (en) | 2016-08-10 |
WO2015049295A1 (en) | 2015-04-09 |
FR3011291B1 (en) | 2015-10-16 |
KR102266201B1 (en) | 2021-06-18 |
MX2016004281A (en) | 2016-10-12 |
JP2016532805A (en) | 2016-10-20 |
CN105593530A (en) | 2016-05-18 |
US20160245088A1 (en) | 2016-08-25 |
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