• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to an upstream fan rotor (16) with a hub (18) with an axis of rotation (X), and a cone (22) mounted on the hub (18) of the fan (16), characterized in that the cone (22) comprises an air sampling orifice (34) which opens into an air line (32) of which an upstream end section (32A) passes through the fan rotor (27), said section ( 32A) comprising mechanical means for driving the air. The invention also relates to an upstream turbomachine axial body equipped with such a fan rotor (16).
    公开号:FR3018094A1
    申请号:FR1451626
    申请日:2014-02-28
    公开日:2015-09-04
    发明作者:Christian Vessot；Matthieu Leyko
    申请人:SNECMA SAS；
    IPC主号:
    专利说明:

    [0001] TECHNICAL FIELD OF THE INVENTION The field of the present invention is that of aeronautical turbomachines and, more particularly that of multi-flow turbojets or turboprops, comprising a gearbox for driving the fan, or respectively the propeller.
    [0002] BACKGROUND OF THE INVENTION Conventionally, the turbomachines firstly comprise, starting from upstream, one or more compressor modules arranged in series, which compress air sucked into an air inlet. The air is then introduced into a combustion chamber where it is mixed with fuel and burned. The combustion gases pass through one or more turbine modules that drive the compressor (s). The gases are finally ejected either in a nozzle to produce a propulsive force or on a free turbine to produce power that is recovered on a transmission shaft. The current high-dilution turbofan jet turbofan engines comprise a fan rotor and several compressor stages, including a low pressure (LP) compressor and a high pressure (HP) compressor which belong to the primary body of the engine. Upstream of the low pressure compressor is disposed a large blade impeller, or blower, which feeds both a primary stream in primary flow through the compressors BP and HP and a secondary stream in cold flow, or secondary flow, which is directed directly to a cold flow nozzle, called secondary nozzle. The blower is driven by the rotation shaft of the BP body and generally rotates at the same speed as it. However, it may be advantageous to rotate the fan at a lower rotational speed than the LP shaft, especially when it is of very large size, in order to better adapt aerodynamically. For this we have a gearbox between the BP shaft and a fan shaft, which is carrying the fan. Such a configuration is particularly described in patent applications FR 20120051655 and 20120051656 filed February 23, 2012.
    [0003] The turbojet engine has obvious advantages but some difficulties have yet to be overcome. In particular, this reducer must be lubricated and cooled to ensure proper operation without being damaged. It is estimated today that the amount of oil required to operate a turbojet engine equipped with a speed reducer is twice as high as in the case of a turbojet without a speed reducer. This oil makes it possible in particular to fulfill the lubrication and cooling functions of the mobile components of the turbomachine. It is known to cool this oil by means of an air / oil surface exchanger, also known under the name "SACOC", acronym for the term "Surface Air-Cooled Oil-Cooler". The exchange surface is generally formed in an air flow line of the turbojet engine. In this exchanger are formed a multitude of channels in which circulates the oil to be cooled. The heat exchange is carried out by thermal conduction through the walls of the channels. Thus, air and oil are not mixed. In known heat exchangers, the heat exchanger is arranged in the secondary vein of the turbojet, downstream of the fan. In jet engines designed without speed reducer, the air flow required to cool the oil is low enough not to cause significant pressure losses in the secondary vein. However, turbojets equipped with a speed reducer require a much higher air flow, for example twice the air flow of a turbojet without a speed reducer. FR-B1-2.965.299 relates to the lubrication of rolling bearings, in which the oil is contained in lubrication chambers held in overpressure with respect to the surrounding cavities to ensure the preservation of the oil to the oil. inside the lubrication chambers. This overpressure is achieved by injecting compressed air into the chamber. This compressed air also makes it possible to produce an oil mist allowing a homogeneous distribution of the oil on the components of the turbomachine to be lubricated. To prevent the compressed air from having a temperature that is too high to allow effective cooling of the components, this document proposes to take air upstream of the blower. Nevertheless, the collected air is not cold enough to ensure efficient cooling of the lubricating and cooling oil alone. In addition, the air is drawn into the oil chambers by means of a jet pump requiring the collection of air in the primary vein. The operation of such a device is therefore likely to disturb the flow of air into the primary vein, especially when the amount of air to be taken is important. BRIEF SUMMARY OF THE INVENTION To solve these problems, the invention proposes a turbomachine fan rotor intended to be rotatably mounted about an axis of rotation, the rotor comprising: a hub, and a cone mounted upstream hub; characterized in that the cone comprises an air bleed port which opens into an air line of which an upstream end section comprises mechanical means for driving the air. According to the invention, the drive means make it possible to drive air into the air duct, for example in the manner of a bailer. They can be configured to induce a gyration of the air flow entering the pipe.
    [0004] According to other characteristics of the fan rotor: the upstream end section of the air duct has an annular section that is coaxial with the axis of rotation of the fan rotor, a crown of radial vanes being interposed in the upstream end section, the vanes being integral in rotation with the hub; the blade crown is disposed in said cone; the air sampling orifice has an annular shape coaxial with the axis of rotation of the fan rotor, the cone being divided by the sampling orifice into a leading end section and a rear frustoconical section; - The upper section is fixed with the frustoconical section of the cone by the blades, the latter thus ensuring the connection between these sections of the cone, the blades having a structural role. The summit section makes it possible to divert foreign bodies capable of impacting this section in flight; the air duct is centered on the axis of rotation of the rotor. The invention also relates to an upstream axial body of a turbomachine, in particular a multi-flow turbojet, comprising a compressor shaft, in particular the low-pressure compressor shaft, which drives a fan rotor of the type described above, characterized in that the air duct extends into the upstream axial body beyond the rotor, the air duct having at least one oil cooling wall which is intended to cool oil by heat exchange through said wall with the flow of air flowing in the air duct. According to other characteristics of the turbomachine: the cooling wall is located downstream of the drive means; the torque of rotation of the compressor shaft is transmitted to the rotor of the fan via a speed reducer, the speed reducer being lubricated by cooled oil in contact with said cooling wall; the air duct is centered on the axis of rotation of the body; the flow of air flowing in the air duct is evacuated backwards in a hollow central shaft; the air duct has a generally rectilinear axis parallel to the axis of rotation of the body; - the air line is supplied with air exclusively through the annular sampling port.
    [0005] BRIEF DESCRIPTION OF THE FIGURES Other features and advantages of the invention will emerge during the reading of the following detailed description for the understanding of which reference will be made to the appended drawings in which: FIG. 1 is a sectional view axial which schematically represents a turbomachine; FIG. 2 is a view in half axial section showing a front end section of a turbojet engine which is equipped with a speed reducer and which is equipped with a cooling wall arranged according to the teachings of the invention; ; - Figure 3 is a perspective view showing the front end portion of Figure 2 which is provided with a rotary cone having air bleed holes for supplying the cooling wall. DETAILED DESCRIPTION OF THE FIGURES In the remainder of the description, there will be adopted in a nonlimiting manner an axial orientation "A" directed along the axis "X" of rotation of the turbomachine 10, and radial directions directed from the axis "X" rotation of the turbomachine 10 to the outside. The axial orientation "A" is directed from the rear, on the right in FIG. 1, towards the front, on the left in FIG. 1, the air entering through the front of the turbomachine 10 to emerge from it. 'back. The terms "upstream" and "downstream" are used with reference to the direction of flow of air in the air line 32 and in the veins of the turbomachine. FIG. 1 shows a turbomachine 10. This is a turbofan engine used for the propulsion of an aircraft.
    [0006] The engine 14 is double-body with a first low-pressure body and a second high-pressure body. Both bodies are rotatably mounted coaxially around the central "X" axis. Such an architecture is well known from the state of the art.
    [0007] The low pressure body comprises a front compressor 15A and a rear turbine 15B which are rotatably connected about the "X" axis via a first common central axial shaft 15C. Likewise, the high-pressure body comprises a front compressor 17A and a rear turbine 17B which are connected in rotation around the axis "X" via a second common central axial shaft 17C which is hollow. The shaft 15C of the low pressure body is here arranged concentrically inside the hollow shaft 17C of the high pressure body.
    [0008] A blower 16 is rotatably mounted about the central axis "X" on the engine 14, upstream of the low pressure compressor 15A and in an annular housing. Blower 16, also known by the name "fan", has a central hub 18 bearing a blade ring 20 which extend radially outwardly. The fan 16 compresses the incident air F1 which is distributed downstream between a secondary vein 21 and a primary stream 23. The flow of air flowing axially in the primary stream 23 is compressed by the successive compressor stages 15A, 17A of the turbomachine 10 before entering a combustion chamber. The combustion energy is converted into mechanical energy through the turbines 17B, 15B which drive the compressors 15A, 17A and the fan 16. The flow of air flowing in the secondary vein 21, for its part, contributes to the thrust of the 10. The front of the engine 14 has been shown in more detail in FIG. 2. The front end of the engine 14 is provided with a cone 22 or conical end-end piece which is mounted to rotate with the hub 18 of the fan 16. The cone 22 has an axisymmetric shape of central axis "X", its top being directed upstream. The front end cone 22 and the blower hub 18 thus form a rotatable blower rotor 27 about the "X" axis. The fan 16 is rotated by the low pressure turbine 15B. To allow the blower 16 to turn more slowly than the low pressure body, the rotational torque of the low pressure turbine 15B is transmitted to the blower 16, via the low pressure compressor shaft 15C, via a speed reducer 24, for example with an epicyclic gear train. The speed reducer 24 is arranged axially between the fan 16 and the low pressure compressor 15A. In the embodiment shown in FIGS. 2 and 3, an upstream end axial body 29 comprising the fan 16, the speed reducer 24 and at least one section of the shaft 15C of the low pressure compressor 15A forms a module which is preassembled independently of the rest of the engine 14 and which is intended to be subsequently assembled with other modules of the engine 14 comprising in particular the low and high pressure rotary assemblies and the combustion chamber 25. The speed reducer 24 is solicited at very high speed. This causes very significant heating of its various components. It is therefore expected to cool these components by oil spraying which also allows to lubricate the gearbox 24 speed. In the example shown in the figures, said oil is also used for the lubrication and cooling of other elements of the turbomachine 10, in particular for bearings 26 supporting a front end portion of the drive shaft of the fan 16, as shown in FIG. 2. The various components to be lubricated, in particular those of the speed reducer 24, are contained in an enclosure 28 of the turbomachine 10. This enclosure 28 is designed to contain the oil in a sealed manner, thus preventing any oil leakage in the rest of the turbomachine 10. The oil chamber 28 is here interposed axially between the hub 18 of the fan and the speed reducer 24. This enclosure 28 is partly delimited by a wall 30, said cooling wall 30, which forms a partition wall between the inside of the enclosure 28 and a pipe 32 of air called "pipe 32 cooling". The cooling pipe 32 is arranged inside the gas turbine engine 14. The cooling pipe 32 is for example formed inside the drive shaft of the rotor 27 and / or inside the shaft 15C of the low pressure compressor 15A. The cooling wall 30 is intended to cool the oil by thermal conduction between a cold air flow circulating in the cooling pipe 32 in contact with a first face of said cooling wall, and the oil contained in the enclosure 28 in contact with a second opposite face of said cooling wall 30, as illustrated by the double-arrows "F2" of Figure 2.
    [0009] To increase the heat exchange surface with the air, the face of the cooling wall which forms the inside of the cooling pipe 32 is bristled with fins (not shown). The cooling wall 30 is arranged axially behind the cone 22. The cooling of the oil requires a high air flow in the cooling pipe 32. To avoid causing losses in the primary stream 12, the invention proposes to take air upstream of the blower 16.
    [0010] Thus, as shown in FIG. 2, the cooling duct 32 is supplied with air by at least one upstream air intake orifice 34 which is arranged in front of the hub of the blower 16. An upstream end section 32A is the cooling pipe 32 passes through the fan rotor 27, thus passing through the end cone 22 and then through the hub 18 of the fan 16 to guide the flow of air to the cooling wall 30. The upstream end section 32A thus extends axially in the upstream axial body 29 beyond the rotor 27.
    [0011] The upstream end section 32A of the cooling pipe 32 is thus delimited radially by a rotatable wall around the "X" axis of the gas turbine engine 14.
    [0012] The section 32A upstream end of the pipe is equipped with mechanical means for air entrainment. The drive means are located upstream of the cooling wall 30 to accelerate the flow of air before it comes into contact with the cooling wall. In the example shown in the figures, the cooling pipe 32 is fed with air exclusively through the air sampling orifice 34. In a variant not shown of the invention, the cooling duct is supplied with air taken in front of the hub of the blower, on the one hand, and with air taken from the primary vein, on the other hand. In the example shown in FIGS. 2 and 3, the cooling duct 32 more particularly comprises a single air sampling orifice 34 which opens axially forwards into the end cone 22 of the gas turbine engine 14. . The air sampling orifice 34 here has an annular shape coaxial with the axis "X" of rotation of the fan 16.
    [0013] Thus, the cone 22 is divided by the sampling orifice 34 into a front upper section 22A and into a rear frustoconical section 22B. In a nonlimiting embodiment of the invention, it has been estimated that for a 10 MW turbine engine equipped with a gearbox for driving the fan, the air flow required to effectively cool the oil is about 2 kg.s-1. In order for this flow rate to be obtained during take-off of the aircraft, that is to say at a relatively low backward air displacement speed with respect to the turbomachine 10, it has been calculated that the area of the aircraft air sampling port 34 in cross section should be less than 10% of the surface of the front end cone 22.
    [0014] As illustrated in Figure 3, the air drive means are here formed by a ring of 36 radial drive blades which are interposed in the section 32A upstream end of the pipe. The blades 36 are integral in rotation with the fan rotor 27 to allow the entrainment of the incoming air during the rotation of the fan 16. The drive blades 36 are here arranged in the cone 22, directly ahead of the annular sampling orifice 34, for driving air into the cooling pipe 32 during the rotation of the fan 16. The inclination of the blades 36 is determined as a function of the minimum flow rate of air required for a satisfactory cooling of oil by heat exchange through the cooling wall.
    [0015] For example, the blades 36 are dimensioned to have an effect as neutral as possible vis-à-vis the flow of the air flow at a cruising speed of the aircraft, conferring at most a gyration of the air. For lower speeds of movement of the aircraft, the blades 36 can cause the flow of air inside the pipe 32 cooling, giving it however a greater gyration. This gyration of the air in the cooling duct 32 advantageously enables greater convection to be produced which improves the cooling of the oil through the cooling wall. However, this gyration must be controlled to limit the pressure losses in the pipe 32 cooling. This arrangement of the blades 36 makes it possible to fix the upper section 22A with the frustoconical section 22B of the cone 22. This configuration is advantageous because the upper section 22A of the cone 22 makes it possible to prevent foreign bodies from entering through the orifice 34. deviating them.
    [0016] In a variant not shown of the invention, the air bleed orifice is arranged at the top of the front end cone. This configuration, however, does not allow to obtain the suction effect of the configuration shown in Figures 2 and 3.
    [0017] The upstream end section 32A of the cooling pipe 32 thus has an upstream end section of annular section coaxial with the "X" axis of the turbomachine 10. The upstream end portion 32A converges axially downstream to open into a downstream end section 32B having a circular section. In the example shown in Figure 2, the cooling wall 30 is arranged in the downstream end section 32B of the pipe 32 cooling. The upstream end section 32A of the cooling pipe 32 between the sampling orifice 34 and the cooling wall 30 is short and generally straight. The flow of air flowing in the cooling pipe 32 thus undergoes very little pressure drop between its entry into the cooling pipe 32 and its passage at the level of the cooling wall 30.
    [0018] The downstream end section 32B of the cooling pipe 32 is rectilinear with a circular section centered on the "X" axis. Thus, after its passage in contact with the cooling wall 30, the cooling air is evacuated axially rearwards in a hollow central shaft of the turbomachine 10 to a downstream orifice (not shown) at the outlet. outdoors. This maintains a high airflow rate at the cooling wall. The flow of air flowing in the cooling pipe 32 thus flows axially from upstream to downstream, as indicated by the arrows "F3" of FIG. 2. During the operation of the turbomachine 10, the fan 16 is driven in rotation. The cold air entering the cooling line 32 is driven by the drive blades 36. The flow of cold air thus driven by the drive vanes 36 flows axially downstream in the cooling line 32 to the cooling wall 30. The heat of the hot oil is transferred to the cold air flow through the cooling wall. Then, the heated air stream and continues its flow in the cooling pipe 32 axially rearward to its evacuation to the open air. The turbomachine 10 produced according to the teachings of the invention makes it possible to circulate a high air flow rate in the cooling pipe 32 without disturbing the flow of air in the secondary vein 21. This makes it possible to cool the oil very effectively. The arrangement of the air sampling orifice 34 on the front end cone 22 notably makes it possible to benefit from air flowing at a high axial speed, for example between 0.5 and 0.6 Mach, when it enters the the orifice 34 for sampling air. In addition, the cone 22 rotates the vanes 36 to suck air entering the pipe 32 cooling. The high air inlet velocity makes it possible to obtain a high air flow rate in the cooling duct 32. In addition, the upstream section of the cooling pipe 32 is short and almost straight, which makes it possible to avoid the losses in the flow of air between the inlet orifice 34 and the cooling wall 30.
    权利要求:
    Claims (10)
    [0001]
    REVENDICATIONS1. A turbomachine blower (16) rotor (27) adapted to be rotatably mounted about an axis of rotation (X), the rotor (27) comprising: - a hub (18), and - a cone (22) ) mounted upstream of the hub (18); characterized in that the cone (22) has an air bleed port (34) which opens into an air line (32) of which an upstream end section (32A) comprises mechanical drive means 'air.
    [0002]
    2. rotor (27) blower (16) according to the preceding claim, characterized in that the section (32A) of upstream end of the pipe (32) of air has a ring-shaped section coaxial with the axis ( X) of rotation of the rotor (27) of a fan (16), a ring of radial blades (36) being interposed in the section (32A) of upstream end, the vanes (36) being integral in rotation with the hub ( 18).
    [0003]
    3. Fan rotor (16) according to the preceding claim, characterized in that the blade ring (36) is disposed in said cone (22).
    [0004]
    4. Fan rotor (16) according to any one of the preceding claims, characterized in that the orifice (34) of air sampling has an annular shape coaxial with the axis (X) of rotation of the rotor (27). ) of the fan (16), the cone (22) being divided by the sampling orifice (34) into a front end section (22A) and a rear frustoconical section (22B).
    [0005]
    5. Blower rotor (16) according to the preceding claim, characterized in that the upper portion (22A) is fixed with the frustoconical section (22B) of the cone (22) by the vanes (36).
    [0006]
    6. blower rotor (16) according to any one of the preceding claims, characterized in that the duct (32) of air is centered on the axis (X) of rotation of the rotor (27).
    [0007]
    7. The upstream axial body of a turbomachine (10), in particular a multi-flow turbojet engine, comprising a compressor shaft (15C), in particular the low-pressure compressor shaft, which drives a fan rotor (16) produced according to FIG. any of the preceding claims, characterized in that the air duct (32) extends into the upstream axial body beyond the rotor (27), the air duct (32) having at least one wall (30). ) for cooling oil which is intended to cool oil by exchanging heat through said wall with the flow of air flowing in the air duct (32).
    [0008]
    8. upstream axial body according to the preceding claim, characterized in that the wall (30) of cooling is located downstream of the means (36) for driving.
    [0009]
    9. upstream axial body according to the preceding claim, characterized in that the torque of the compressor shaft (15C) is transmitted to the rotor (27) of the fan (16) via a gearbox (24). ), the speed reducer (24) being lubricated by cooled oil in contact with said cooling wall (30).
    [0010]
    10. upstream axial body according to any one of claims 7 to 9, characterized in that the duct (32) of air opens downstream in a hollow central shaft, the air flow flowing in the pipe (32) d air being discharged downstream into this hollow central shaft.
    类似技术:
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    同族专利:
    公开号 | 公开日
    US10082080B2|2018-09-25|
    CN106460726B|2018-03-09|
    EP3111077A1|2017-01-04|
    FR3018094B1|2021-12-03|
    JP2017507279A|2017-03-16|
    JP6556157B2|2019-08-07|
    CN106460726A|2017-02-22|
    WO2015128563A1|2015-09-03|
    EP3111077B1|2018-01-31|
    US20170009656A1|2017-01-12|
    CA2940978A1|2015-09-03|
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    法律状态:
    2015-02-24| PLFP| Fee payment|Year of fee payment: 2 |
    2016-02-03| PLFP| Fee payment|Year of fee payment: 3 |
    2016-05-06| RM| Correction of a material error|Effective date: 20160404 |
    2017-02-07| PLFP| Fee payment|Year of fee payment: 4 |
    2017-11-10| CD| Change of name or company name|Owner name: SNECMA, FR Effective date: 20170713 |
    2018-01-23| PLFP| Fee payment|Year of fee payment: 5 |
    2019-01-23| PLFP| Fee payment|Year of fee payment: 6 |
    2020-01-22| PLFP| Fee payment|Year of fee payment: 7 |
    2021-01-20| PLFP| Fee payment|Year of fee payment: 8 |
    2022-01-19| PLFP| Fee payment|Year of fee payment: 9 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1451626A|FR3018094B1|2014-02-28|2014-02-28|BLOWER ROTOR FOR A TURBOMACHINE SUCH AS A MULTIFLUX TURBOREACTOR DRIVEN BY REDUCER|FR1451626A| FR3018094B1|2014-02-28|2014-02-28|BLOWER ROTOR FOR A TURBOMACHINE SUCH AS A MULTIFLUX TURBOREACTOR DRIVEN BY REDUCER|
    US15/120,679| US10082080B2|2014-02-28|2015-02-19|Fan rotor for a turbo machine such as a multiple flow turbojet engine driven by a reduction gear|
    JP2016553636A| JP6556157B2|2014-02-28|2015-02-19|Fan rotor for turbomachines such as multi-stream turbojet engines driven by reduction gears|
    EP15709282.6A| EP3111077B1|2014-02-28|2015-02-19|Fan rotor for a turbo machine such as a multiple flow turbojet engine driven by a reduction gear|
    PCT/FR2015/050407| WO2015128563A1|2014-02-28|2015-02-19|Fan rotor for a turbo machine such as a multiple flow turbojet engine driven by a reduction gear|
    CN201580010019.7A| CN106460726B|2014-02-28|2015-02-19|The fan propeller driven by reduction gearing for such as turbine of multithread turbojet|
    CA2940978A| CA2940978A1|2014-02-28|2015-02-19|Fan rotor for a turbo machine such as a multiple flow turbojet engine driven by a reduction gear|
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