• 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 a method of manufacturing a helical gearbox comprising the following steps: - Measurement of crankcase manufacturing defects (Yav,? Zav,? Yar,? Zar); - Calculation of a first angular clearance (δmanufacture) induced at each intermediate gear (2a, 2b) from the measured manufacturing defects (Yav,? Zav,? Yar,? Zar); - Estimation of a second angular clearance (δdeformation) induced at each intermediate gear (2a, 2b) by deformations of the housing (12) during the transmission of a threshold torque by the gearbox; - Calculation of a total angular clearance (δtotal) from the first angular clearance and the second angular clearance; - Choice of two intermediate gears with a phasing difference (-dototal) compensating for this total angular clearance.
    公开号:FR3031562A1
    申请号:FR1550246
    申请日:2015-01-13
    公开日:2016-07-15
    发明作者:Antoine Mathieu；Benjamin Feraud
    申请人:Hispano Suiza SA；
    IPC主号:
    专利说明:

    [0001] TECHNICAL FIELD The present invention relates to a method of manufacturing a helical reducer and a helical reducer obtained by this method.
    [0002] STATE OF THE PRIOR ART Prior art propeller turbomachines generally comprise a propeller drive box, also called PGB or "propeller gearbox" or "propeller reducer", which transmits a rotational movement of the propeller. a motor shaft, generally driven by a gas turbine, to a propeller, with a selected reduction ratio. Such a helical gearbox rotates the propeller with a speed lower than the rotational speed of the motor shaft. Such a helical gearbox is for example described in the document W000 / 17540.
    [0003] Among the various helical gearboxes that can be used, the prior art knows "compound" type reducers. Such a reducer is also called transmission line reducer. Such a gearbox is shown in Figure 1. It generally comprises: - an input pinion 1; - 2 intermediate gears 2, each intermediate gear having a first stage 3 meshing with the input pinion 1 and a second stage 4; an output wheel meshing with the second stage 4 of each of the intermediate gears.
    [0004] The input gear is intended to be connected to a motor shaft. The output wheel is intended to be connected to the propeller to rotate. However, as shown in FIG. 2, such a helical gearbox is hyperstatic. Therefore, a game 6 at one of the intermediate gears 2 can cause a poor distribution of loads so that the other intermediate gear then passes the majority of the engine power while the first intermediate gear is almost no power. However, when the gearbox 5 transmits the maximum torque for which it is dimensioned, this poor distribution of the torque transmitted by the two intermediate gears may cause damage to the helical gear and premature wear of said gear. To remedy this problem, the prior art has proposed a helical gearbox provided with a spring system as shown in FIGS. 3a, 3b and 4. This spring system 7 comprises a spring 7 fixed to the input pinion. 1. The spring system 7 also has a swivel spline at the axis of the input gear and a keel 9 supported by bearings. The spring system adds a degree of freedom by allowing the input gear 1 to move vertically so that the two intermediate gears transmit the same power. Indeed, the spring system is dimensioned so that the input pinion finds its equilibrium position when the tangential forces exerted on either side of the input pinion, and therefore the couples transmitted by both intermediate gears 2, are equal. Thus, for example, when the torque transmitted by the intermediate gear 2a is greater than the torque transmitted by the intermediate gear 2b, the input gear will move upwards, as shown in FIGS. 2a and 2b, by to equalize the torque transmitted by the two intermediate gears. This spring system is effective, but it forces the gear teeth of the helical gearbox to work in a non-aligned manner, which damages them in the long run. In addition, the fact of introducing a spring in the helical gearbox is detrimental to the dynamic behavior and reliability of said helical gear.
    [0005] The dynamic load distribution systems in the prior art helical gearboxes are therefore effective, but they have a negative impact in terms of bulk, mass and complexity of the helical gearboxes.
    [0006] SUMMARY OF THE INVENTION The object of the invention is to remedy the drawbacks of the state of the art by proposing a solution allowing a good distribution of the torque transmitted by the intermediate gears of a helical gear reducer, which does not weigh down not the propeller reducer, which is not bulky and not complicated. To do this, is proposed according to a first aspect of the invention, a method of manufacturing a helical gear comprising: - a casing having at least two bearing bearing surfaces and two rear bearing bearing surfaces; - an input gear; at least two intermediate gears, each intermediate gear having a first stage meshing with the input gear and a second stage, each intermediate gear being fixed to the housing via at least one front bearing and one rear bearing, each forward bearing being supported by one of the front bearing seats, each rear bearing being supported by one of the rear bearing seats; an output wheel meshing with the second stage of each of the intermediate gears; the method comprising the following steps: a) Measuring crankcase manufacturing defects; b) Calculation of a first induced angular clearance at each intermediate gear from the measured manufacturing defects; C) Estimation of a second angular clearance induced at each intermediate gear by deformations of the casing during transmission of a threshold torque by the gearbox; d) calculating a total angular clearance from the first angular clearance and the second angular clearance; E) Choice of two intermediate gears having a phasing difference compensating for this total angular clearance. In this document, the term "phasing difference" refers to the relative angle between a first stage toothing and a second stage toothing on each intermediate gear. In this document, the term "angular clearance" refers to a possible angular deflection on an intermediate gear when the other idler gear is in contact with both the input gear and the output gear. The angular clearance can be measured by contacting the teeth on one side of the gearbox and measuring the possible angular displacement on the other side of the gearbox.
    [0007] The manufacturing process therefore makes it possible to produce a helical gearbox in which the torque transmitted by the two intermediate gears is balanced, while dispensing with the load distribution systems used in the prior art. To do this, the method proposes to use a pairing of the intermediate gears so as to improve the distribution of the charges between these two gears. Thus, instead of using dynamic load distribution systems as in the prior art, in order to balance the loads between the intermediate gears over the entire range of use of the gearbox, the method proposes to choose the intermediate gears. in order to compensate for the manufacturing defects of the housing and its deformation when the gearbox transmits a threshold torque. This threshold torque is preferably the maximum torque for which the gearbox has been dimensioned. A gearbox is thus obtained in which the transmitted torque is equitably distributed between the two intermediate gears when the gearbox transmits a maximum torque, which limits the risk of damage and wear of the gearbox, without increasing the complexity or the complexity of the gearbox. In addition, the prior art load balancing systems with moving parts, which jeopardize the reliability of the gearbox, are dispensed with. The method according to the first aspect of the invention may also have one or more of the following features taken independently or in any technically possible combination. Advantageously, the step (a) for measuring defects comprises a step of measuring a real position of each bearing surface.
    [0008] Advantageously, step (b) of calculating the first angular clearance comprises the following steps: for each bearing surface, calculating a difference between the actual position of the bearing surface and a reference position of to obtain a bearing range offset; for each intermediate gear: calculating an offset of the intermediate gear from the shifts of the bearing surfaces supporting the bearings of this intermediate gear; calculating the first angular clearance from the shifting of the intermediate gear. Advantageously, the step (c) of estimating the second angular clearance comprises the following steps: estimating a displacement of each bearing surface during the transmission of a threshold torque by the gearbox; for each intermediate gear: calculation of a displacement of the first stage from the displacements of the bearing surfaces supporting the bearings of this intermediate gear; calculation of the second angular clearance from the calculated displacements; A second aspect of the invention relates to a helical gearbox obtained by the method according to the first aspect of the invention. BRIEF DESCRIPTION OF THE FIGURES Other features and advantages of the invention will emerge on reading the detailed description which follows, with reference to the appended figures, which illustrate: FIG. 1 is a perspective view of a gear reducer; helix to which the method according to the first aspect of the invention applies; - Figure 2, a front view of a helical gearbox manufactured according to a manufacturing method of the prior art; FIGS. 3a, 3b and 4 are diagrammatic representations of a prior art helical gearbox provided with a spring load distribution system; Figure 5 is a view of the face of a helical gearbox according to an embodiment of the invention; Figure 6, a top view of a portion of a helical gear according to one embodiment of the invention; Figure 7, a front view of the casing of the helical gear of Figure 6; Figure 8 is an enlarged view of a portion of the housing of Figure 7; Figure 9 is a schematic representation of the method for calculating the meshing offset; Figures 10a to 10c, schematic representations of the teeth of an intermediate gear used in the context of a method according to one embodiment of the invention; FIG. 11, a field of displacement of the bearing seats of the casing of FIG. 7 in the case of a loading at the threshold torque; Figure 12, a field of displacement of an intermediate gear of the helical gear of Figure 5; Figure 13 is a view of the first stage of the helical gear of Figure 5; Fig. 14 is a view of the second stage of the helical gearbox of Fig. 5; Figure 15 is a view of a tooth of an intermediate gear meshing with a tooth of the impeller wheel of Figure 5; Figures 16a, a schematic representation of the torque transmitted by each of the intermediate gears of a helical gear in the absence of use of a method according to the invention; FIG. 16b is a diagrammatic representation of the torque transmitted by each of the intermediate gears of a helical gearbox manufactured by a method according to one embodiment of the invention.
    [0009] For the sake of clarity, identical or similar elements are marked with identical reference signs throughout the figures. DETAILED DESCRIPTION OF AT LEAST ONE EMBODIMENT The method aims to manufacture a helical gear as shown in the figures. This helical gearbox comprises a casing 12. The casing 12 comprises two front bearing bearing surfaces 13 and two bearing rear bearing surfaces 14. The casing 12 surrounds a chain of gears enabling a propeller to be rotated in rotation at a difference speed. the speed of rotation of a motor shaft. To do this, the gear chain comprises an input pinion 1 intended to be fixed to a drive shaft and an output wheel 5 intended to be secured to a propeller to drive in rotation. The gear chain also comprises at least two intermediate gears 2. Each intermediate gear 2 comprises a first stage 3 which meshes with the input gear 10 and a second stage 4 which meshes with the output wheel 5. Each intermediate gear is secured to the housing by: - a front bearing 15 supported by one of the front bearing seats 13 of the housing and - a rear bearing 16 supported by one of the rear bearing seats 14 of the housing. A method of manufacturing such a reducer will now be described. It first comprises a step (a) for measuring crankcase manufacturing defects. More precisely, during this step, the actual position of each bearing surface 20 is measured. The method then comprises a step of comparison between the actual position of each bearing surface and a reference position. Thus, with reference to FIGS. 7 and 8, the method includes a step of measuring the difference between a reference position 17 specified by the planes and the actual position 18 of each bearing surface. This results in a bearing span offset (AYav, AZav) for each front bearing seat and (AYar, AZar) for each rear bearing seat. The method then comprises a step (b) of calculating a first angular clearance 30 induced at each intermediate gear from the measured manufacturing defects. This step comprises a step of calculating a shift of the first stage of each intermediate gear from the offsets of the calculated bearing staves. Thus, the intermediate gear 2b for example is fixed to the housing via the front bearing seat 13 and via the rear bearing seat 14. Referring to FIG. 13, knowing the shift of the front bearing seat 13 (AYav, AZav), the offset of the rear bearing bearing 14 (AYar, AZar), the total length of the intermediate gear L, and the distance between the intermediate gear and one of the bearing surfaces L1, the offset is calculated (AY, AZ ) of the first stage of the intermediate gear 2b: AYar * (L-L1) + L1 * AYav AZ = L The method then comprises a step of calculating the first angular clearance from the offset (AY, AZ) of the first gear stage intermediate 2b. This first angular clearance is given by the following equations: EI = AZ / r + Artan (a) / r Where r is the pitch radius of the intermediate gear in mm The first angular clearance, 52, is calculated in the same way for the other intermediate gear 2a. The method then comprises a step of calculating the first total angular clearance of manufacture = El + δ 2. The method also comprises a step of estimating a second angular clearance induced at each intermediate gear by deformations of the casing during the transmission of power. a threshold torque by the reducer. For this, with reference to FIGS. 11 and 12, it is possible, for example, to perform a finite element calculation to know the displacement of each bearing surface due to the deformations of the casing during the transmission of a threshold torque by the gearbox. This threshold torque is preferably the maximum torque for which the gearbox has been dimensioned. Thus, the displacements (AY'av, AZ'av) of the front bearing seats and the displacements (AY'ar, AZ'ar) of the rear bearing seats are thus obtained. The method then comprises a step of calculating the displacement (AY ', AZ') of the first stage of the intermediate gear 2b in case of transmission of the threshold torque: Aral- The method then comprises a step of calculating the second angular clearance from the offset (AY ', AZ') of the first stage of the intermediate gear 2b. This second angular clearance is given by the following equations: E1 '= AZ7r + AY' * tan (a) / r Where r is the pitch radius of the intermediate gear in mm 10 The second angular clearance Ô2 'is calculated in the same way for the other intermediate gear 2a.
    [0010] The method then comprises a step of calculating the second total angular clearance ôdeformation = E '+ Ô2' The method then comprises a step of calculating a total angular clearance: ôtotal = fabrication + ôdeformation 20 The method then comprises a step of choice a pair of intermediate gears causing a phase shift equal to - ôtotal as shown in Figure 15.
    [0011] The described method therefore makes it possible to compensate for manufacturing and deformation defects by choosing an appropriate pair of intermediate gears. It thus makes it possible to obtain a balanced load distribution between the two intermediate gears. Thus, FIG. 16a shows the evolution of the torque transmitted by each of the intermediate gears 2a and 2b as a function of the torque Ce at the input of the gearbox when the gearbox is not manufactured by a method according to the invention. As can be seen in this figure, the two intermediate gears transmit very different pairs. FIG. 16b shows the evolution of the torque transmitted by each of the intermediate gears 2a and 2b as a function of the torque Ce at the input of the gearbox when the gearbox has was manufactured by a method according to an embodiment of the invention. As can be seen in this figure, the transmitted torque is then equitably distributed between the two intermediate gears. Naturally, the invention is not limited to the embodiments described with reference to the figures and variants could be envisaged without departing from the scope of the invention. In particular, the method could be used to manufacture helical reducers having more than two intermediate gears.
    权利要求:
    Claims (5)
    [0001]
    REVENDICATIONS1. A method of manufacturing a helical gearbox comprising: - a housing (12) having at least two bearing bearing surfaces (13) and two rear bearing bearing surfaces (14); - an input gear (1); at least two intermediate gears (2, 2a, 2b), each intermediate gear (2, 2a, 2b) comprising a first stage (3) meshing with the input pinion (1) and a second stage (4), each intermediate gear (2, 2a, 2b) being fixed to the housing (12) via at least one front bearing (15) and one rear bearing (16), each front bearing (15) being supported by one of the bearings front bearing (13), each rear bearing (16) being supported by one of the rear bearing seats (14); an output wheel (5) meshing with the second stage (4) of each of the intermediate gears; the method comprising the following steps: - (a) Measuring crankcase manufacturing defects (3, Yav, 3, Zav, 4Yar, AZar); (b) calculating a first induced angular clearance (fabrication) at each intermediate gear (2a, 2b) from the measured manufacturing defects (3, Yav, 3, Zav, 4Yar, 32ar); - (c) estimating a second angular clearance (deformation) induced at each intermediate gear (2a, 2b) by deformations of the housing (12) during the transmission of a threshold torque by the gearbox; - (d) Calculation of a total angular clearance (ôtotal) from the first angular clearance and the second angular clearance; - (e) Choice of two intermediate gears having a phasing difference (-OTotal) compensating for this total angular clearance. 3031562 12
    [0002]
    2. Method according to the preceding claim, wherein the step (a) for measuring defects comprises a step of measuring a real position (18) of each bearing surface (13, 14). 5
    [0003]
    3. Method according to the preceding claim, wherein the step (b) of calculating the first angular clearance comprises the following steps: - for each bearing surface (13, 14), calculating a difference between the actual position (18) ) of the bearing bearing and a reference position (17) so as to obtain a bearing span shift (AYav, AZav, AYar, AZar); for each intermediate gear (2a, 2b): calculating an offset (AY, AZ) of the intermediate gear from the shifts of the bearing seats (AYav, AZav, AYar, AZar) supporting the bearings of this intermediate gear ; calculating the first angular clearance (fabrication) from the offset (AY, AZ) of the intermediate gear. 20
    [0004]
    4. Method according to one of the preceding claims, wherein the step (c) for estimating the second angular clearance comprises the following steps: - estimation of a displacement (AY'av, AZ'av, AY'ar, AZ'ar) of each bearing surface (13, 14) during transmission of a threshold torque by the gearbox; for each intermediate gear (2a, 2b): calculating a displacement (AY ', AZ') of the first stage from the displacements (AY'av, AZ'av, AY'ar, AZ'ar) of the staves bearings bearing the bearings of this intermediate gear; o Calculation of the second angular clearance (odeformation) from the calculated displacements. 3031562 13
    [0005]
    5. Helical gearbox manufactured by a method according to one of the preceding claims.
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    法律状态:
    2016-01-22| PLFP| Fee payment|Year of fee payment: 2 |
    2016-07-15| PLSC| Publication of the preliminary search report|Effective date: 20160715 |
    2017-01-05| PLFP| Fee payment|Year of fee payment: 3 |
    2017-08-25| CD| Change of name or company name|Owner name: HISPANO SUIZA, FR Effective date: 20170725 |
    2017-12-21| PLFP| Fee payment|Year of fee payment: 4 |
    2019-12-19| PLFP| Fee payment|Year of fee payment: 6 |
    2020-12-17| PLFP| Fee payment|Year of fee payment: 7 |
    2021-12-15| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1550246A|FR3031562B1|2015-01-13|2015-01-13|METHOD FOR MANUFACTURING A PROPELLER REDUCER|FR1550246A| FR3031562B1|2015-01-13|2015-01-13|METHOD FOR MANUFACTURING A PROPELLER REDUCER|
    PCT/FR2016/050046| WO2016113494A1|2015-01-13|2016-01-12|Method for manufacturing a propeller reduction gear|
    RU2017128570A| RU2697164C2|2015-01-13|2016-01-12|Method for manufacturing a propeller reduction gear|
    US15/543,106| US10047849B2|2015-01-13|2016-01-12|Method for manufacturing a propeller reduction gear|
    CA2973533A| CA2973533A1|2015-01-13|2016-01-12|Method for manufacturing a propeller reduction gear|
    CN201680007450.0A| CN107208776B|2015-01-13|2016-01-12|Method for manufacturing a propeller reduction gear|
    JP2017536940A| JP6636029B2|2015-01-13|2016-01-12|Manufacturing method of propeller speed reducer|
    EP16703339.8A| EP3245427B1|2015-01-13|2016-01-12|Method for manufacturing a propeller reduction gear|
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