JP2010216592A - Planetary gear device of transmission for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a planetary gear device of the transmission for a vehicle capable of alleviating an impact sound generated at the connection portion between a carrier (non-rotation member) and a case without the aging deterioration of the performance. <P>SOLUTION: The planetary gear device is provided with a cylindrical external circumferential surface 46 and a cylindrical internal circumferential surface 48 which are respectively provided on a metallic internal ring 26 fitted to a carrier CA1 and on a metallic external ring 38 fitted in the fitting hole 36 of a case 12 and opposite to each other across a circular annular clearance, and a plurality of metallic rollers 56 rollably housed in the clearance between the cylindrical external circumferential surface 46 and the cylindrical internal circumferential surface 48 and biting into the clearance between the cylindrical external circumferential surface 46 and the cylindrical internal circumferential surface 48 as the carrier CA1 and the case 12 relatively rotates therebetween in one and the other circumferential directions to inhibit further relative rotation. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a technology for connecting any one of the components as a non-rotating member to the case so as not to be relatively rotatable in a planetary gear device housed in a case as part of a transmission for a vehicle. is there.

  A sun gear, a carrier that rotatably supports a plurality of pinion gears that mesh with the sun gear, and a ring gear that meshes with the plurality of pinion gears, and is housed in a case as part of a vehicle transmission, and the sun gear, the carrier, and There is known a planetary gear device for a vehicle transmission in which any one of the ring gears is fitted as a non-rotating member to the case so as not to rotate relative to the case. For example, it is described in Patent Document 1. In Patent Document 1, the ring gear is fixed to the case so as not to rotate relative to the case.

Japanese Utility Model Publication No. 3-72144

  By the way, in the conventional planetary gear device for a vehicle transmission, when the non-rotating member and the case are completely fixed, the durability and vibration are adversely affected. They are connected in a state having a predetermined play in the rotation direction. However, the spline teeth of the non-rotating member and the case collide with each other when the vehicle suddenly starts up or suddenly accelerates or decelerates, causing a problem that an impact sound (tooth rattling sound) is generated. Although it may be possible to reduce the impact sound by reducing the predetermined play, the fixing member and the case are manufactured with predetermined crossing dimensions for mass production. There are limits to reducing it.

  On the other hand, in Patent Document 1, the impact sound is generated by the coating of an elastic member on the spline teeth of the ring gear as the non-rotating member and the play is filled, and it is generated in the planetary gear device. A technique is described in which meshing vibration is prevented from being transmitted to a case or a meshing portion of another planetary gear device through a spline fitting portion. However, since the spline fitting portion between the non-rotating member and the case is a part that always receives driving force, the impact noise suppression and meshing vibration transmission suppression effects disappear due to the deterioration of the durability of the elastic member over time. There was a problem to do.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is that one of the constituent elements of the planetary gear device is connected to the case as a non-rotating member so as not to be relatively rotatable. Therefore, it is an object of the present invention to provide a planetary gear device for a transmission device for a vehicle that can suppress an impact sound generated at a connecting portion between the non-rotating member and a case without deterioration in performance over time.

  To achieve this object, the gist of the invention according to claim 1 is as follows: (1) a sun gear, a carrier that rotatably supports a plurality of pinion gears that mesh with the sun gear, and a ring gear that meshes with the plurality of pinion gears. And a planetary of the vehicle transmission device, wherein the sun gear, the carrier, and the ring gear are fitted as non-rotating members so as not to rotate relative to the case. (2) provided on the outer peripheral surface of the non-rotating member or the outer peripheral surface of the inner shaft fitted to the non-rotating member and the inner peripheral surface of the fitting ring of the case or the outer ring fitted thereto; Rolling into a cylindrical outer peripheral surface and a cylindrical inner peripheral surface facing each other across an annular clearance, and (3) a clearance between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface And further biting into the gap between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface in accordance with the relative rotation in any direction between the non-rotating member and the case, thereby suppressing further relative rotation. A plurality of rolling elements are provided.

  According to the planetary gear unit of the vehicle transmission of the invention of claim 1, the outer peripheral surface of the non-rotating member or the outer peripheral surface of the inner shaft fitted to the non-rotating member and the fitting hole of the case or the fitting hole. A cylindrical outer peripheral surface and a cylindrical inner peripheral surface that are provided on the inner peripheral surface of the outer ring and face each other with an annular gap therebetween, and are transferred into the clearance between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface. It is accommodated in a movable manner, and further relative rotation is suppressed by biting into the gap between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface according to the relative rotation in any direction of the non-rotating member and the case. A cylindrical outer peripheral surface and a cylinder provided on the inner shaft and the outer ring fitted to them or according to the relative rotation between the non-rotating member and the case at the time of torque transmission. Contact between the inner circumferential surface and the rolling element The cylindrical outer peripheral surface and the frictional force between the cylindrical inner peripheral surface and the rolling element, which continuously increase with the force, are continuously increased as the torque input to the non-rotating member increases. Since this acts as a reaction force torque that increases to the relative rotation between the non-rotating member and the case, it is possible to suppress the generation of an impact sound at the connecting portion between the non-rotating member and the case in the relative rotation section. it can. In addition, when the rolling element and the member on which the cylindrical outer peripheral surface and the cylindrical inner peripheral surface are formed are made of a member that is relatively less likely to undergo a change over time, such as a metal such as steel, a non-rotating member and a case It is possible to suppress the generation of impact sound at the connecting portion with no deterioration in performance over time.

  Here, preferably, the present invention is applied to a planetary gear device of a vehicle transmission device in which the carrier is fitted to the case so as not to be relatively rotatable relative to a predetermined amount. The planetary gear device has a cylindrical outer peripheral surface at the outer peripheral portion and is opposed to the cylindrical outer peripheral surface of the inner shaft with an annular gap interposed between the inner shaft fitted on the outer peripheral surface of the carrier. A carrier and a case, which are rotatably accommodated in a gap between an outer ring having a cylindrical inner peripheral surface and fitted in a fitting hole of the case, and the cylindrical outer peripheral surface and the cylindrical inner peripheral surface. And a plurality of rolling elements that suppress further relative rotation by biting into the gap between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface according to relative rotation in one direction and the other direction in the circumferential direction. Is done.

  Preferably, at least one of the cylindrical outer peripheral surface and the cylindrical inner peripheral surface has a radial interval between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface in one circumferential direction. And a plurality of first recesses and second recesses formed to become smaller toward the other direction, and the plurality of rolling elements are the cylinders corresponding to the plurality of first recesses and the second recesses. Is accommodated in a gap between the outer peripheral surface and the cylindrical inner peripheral surface in a rollable manner.

  Preferably, the plurality of first recesses and the second recesses are formed by a plurality of grooves parallel to the axis of the outer ring formed in the cylindrical inner peripheral surface, The plurality of rolling elements are cylindrical members respectively disposed in gaps between the plurality of first recesses and second recesses and the cylindrical outer peripheral surface. In this way, the rolling element and the cylindrical outer peripheral surface and the cylindrical inner peripheral surface are in line contact. For example, when the rolling element, the cylindrical outer peripheral surface, and the cylindrical inner peripheral surface wear, Aged deterioration in performance due to the formation of more than a predetermined amount of play can be suppressed.

It is a figure which shows a part of planetary gear apparatus of the transmission for vehicles of this invention, Comprising: It is the II sectional view taken on the line of FIG. It is a partial cross section figure which shows the planetary gear apparatus containing the II-II arrow part cross section of FIG. In the conventional planetary gear set for a vehicle transmission, it is a view showing a connection portion between a carrier and a case with a part cut away.

  Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a cross-sectional view showing a part of a planetary gear unit 10 of a vehicle transmission according to the present invention. In FIG. 1, the lower half of the axis C, which is the center of rotation, is omitted. FIG. 2 is a partial cross-sectional view showing the planetary gear device 10 including a cross section taken along the line II-II in FIG. 1 and 2, the planetary gear device 10 is housed in a case 12 as a part of a vehicle transmission. In the present embodiment, the planetary gear device 10 can rotate, for example, a sun gear S1 rotatably provided around the axis C and a plurality of pinion gears P1 meshing with the sun gear S1 via a plurality of pinion shafts 14, respectively. A carrier CA1 to be supported and a ring gear R1 meshing with the plurality of pinion gears P1 are provided. The sun gear S1 is supported by the case 12 via a bearing 16 so as to be rotatable around the axis C, and is fitted on the outer peripheral portion of the rotating shaft 18 to which torque of an electric motor (not shown) is transmitted by, for example, spline fitting. ing. Further, the carrier CA1 is fitted to the case 12 as a non-rotating member so as not to be relatively rotatable more than a predetermined amount. The ring gear R1 is supported by the case 12 via a bearing 20 so as to be rotatable around the axis C. An output gear 22 connected to, for example, a differential gear device on the drive wheel side is integrally provided on the outer peripheral portion of the ring gear R1.

  Hereinafter, a connection structure between the carrier CA1 as a non-rotating member and the case 12 will be described in detail.

  The carrier CA1 is provided on both sides in the direction of the axis C of the pinion gear P1, and a pair of annular carrier body portions 24 that support both ends of the pinion shaft 14 inserted through the pinion gear P1, and the pair of carrier body portions. 24 and a connecting portion (not shown) that connects the two integrally with each other.

  A cylindrical inner ring (inner shaft) 26 made of metal such as steel is provided on the outer peripheral portion of one of the pair of carrier body portions 24 on the bearing 16 side (hereinafter referred to as one of the carrier body portions 24). For example, it is fitted by press fitting. A plurality of concave portions 32 and convex portions 34 are respectively provided on the inner peripheral surface 28 of the inner ring 26 and one outer peripheral surface 30 of the carrier main body 24 toward the radially outer side. One of the inner ring 26 and the carrier main body 24 is fixed so as not to be relatively rotatable by fitting the convex portion 32 and the concave portion 34 together.

  A part of the inner peripheral surface of the case 12 is formed with a fitting hole 36 having a cylindrical inner peripheral surface. The fitting hole 36 has a cylindrical outer ring 38 made of metal such as steel. Are fitted by press-fitting, for example. A plurality of convex portions 42 and concave portions 44 are respectively provided on the outer peripheral surface 40 and the fitting hole 36 of the outer ring 38 toward the radially outer side. The outer ring 38 and the case 12 are fixed so that they cannot rotate relative to each other by fitting the convex portion 42 and the concave portion 44 together.

  On the outer peripheral portion (outer peripheral surface) of the inner ring 26 and the inner peripheral portion (inner peripheral surface) of the outer ring 38, there are a cylindrical outer peripheral surface 46 and a cylindrical inner peripheral surface 48 that are opposed to each other in the radial direction with an annular gap interposed therebetween. Is formed. The cylindrical inner peripheral surface 48 is circumferentially arranged so that the gap in the radial direction between the cylindrical inner peripheral surface 46 and the cylindrical outer peripheral surface 46 gradually decreases toward one direction in the circumferential direction, that is, the direction A in FIG. The radial spacing of the gaps between the plurality of first recesses 50 formed at a plurality of positions (three positions in the present embodiment) at predetermined intervals and the cylindrical outer peripheral surface 46 is the other direction in the circumferential direction, that is, B in FIG. And a plurality of second recesses 52 formed at a plurality of positions (three positions in the present embodiment) at predetermined intervals in the circumferential direction so as to gradually become smaller toward the direction. The plurality of first recesses 50 and the second recesses 52 are formed by a plurality of grooves 54 that are parallel to the axis C formed in the cylindrical inner peripheral surface 48.

  A cylindrical roller 56 made of a metal such as steel that can roll within the gaps is accommodated in the gaps between the plurality of first recesses 50 and the second recesses 52 and the cylindrical outer peripheral surface 46. ing. The roller 56 accommodated in the gap between the first recess 50 and the cylindrical outer peripheral surface 46 is in response to the relative rotation in one direction in the circumferential direction between the inner ring 26 and the outer ring 26, and the first recess 50 and the cylindrical outer peripheral surface. Further relative rotation is suppressed by biting into the gap with 46. Also, the roller 56 accommodated in the gap between the second recess 52 and the cylindrical outer peripheral surface 46 is in contact with the second recess 52 and the cylindrical shape in accordance with the relative rotation of the inner ring 26 and the outer ring in the circumferential direction. By biting into the gap with the outer peripheral surface 46, further relative rotation is suppressed.

  In the planetary gear device 10 configured as described above, the torque input to the rotary shaft 18 from the electric motor or the like is amplified and transmitted before being input to the ring gear R1 through the sun gear S1 and the pinion gear P1. Yes. At this time, a predetermined torque is also input to the carrier CA1, but when the carrier CA1 and the inner ring 26 connected thereto are going to rotate relative to the outer ring 38, as described above, the roller 56 is moved to the inner ring. Since the inner ring 26 and the carrier CA1 are prevented from further rotation by biting into the gap between the cylindrical outer circumferential surface 46 of the inner ring 26 and the cylindrical inner circumferential circle 48 of the outer ring 38, the carrier CA1 is a case. 12 is fixed so as not to be rotatable relative to a predetermined amount. That is, the contact pressure between the inner ring 26 and outer ring 38 provided between the carrier CA1 and the case 12 and the roller 56 increases continuously according to the relative rotation between the carrier CA1 and the case 12, and the inner ring 26 and the inner ring 26 continuously increase accordingly. The tangential component of the frictional force between the outer ring 38 and the roller 56 acts as a reaction torque that continuously increases as the torque input to the carrier CA and the inner ring 26 increases. Thus, the relative rotation between the carrier CA1 and the case 12 is suppressed by the reaction torque that continuously increases when the roller 56 is sandwiched in the gap between the inner ring 26 and the outer ring 38. No impact noise such as rattling noise is generated unlike the case of fixing the carrier CA1 and the case 12 by spline fitting as shown in FIG.

  Here, the carrier CA1 and the case 12 slightly rotate relative to each other until the roller 56 bites into the gap between the cylindrical outer peripheral surface 46 of the inner ring 26 and the cylindrical inner peripheral surface 48 of the outer ring 38 as described above. The meshing vibration generated in the planetary gear device 10 is absorbed without being transmitted to the case 12 in the process in which the reaction torque continuously increases in the predetermined relative rotation section. Note that the relative rotation amount of the carrier CA1 and the case 12 until the roller 56 bites into the gap and the shapes of the first recess 50 and the second recess 52 are transmitted to the case 12, for example, meshing vibration generated in the planetary gear device 10 is transmitted. It is experimentally obtained in advance and set so as to be effectively absorbed without being.

  Incidentally, FIG. 3 is a diagram showing a part of the connecting portion between the carrier CA1 and the case 12 in the planetary gear device of the conventional vehicle transmission, with a part cut away. In FIG. 3, in the conventional planetary gear device, the carrier CA1 and the case 12 are connected to each other in a state having predetermined play in the radial direction and the rotational direction by spline fitting. The backlash is provided to eliminate adverse effects on durability and vibration when completely fixed, that is, to absorb the meshing vibration generated in the planetary gear unit 10 before being transmitted to the case 12. However, the spline teeth of the carrier CA1 and the case 12 collide with each other when the vehicle suddenly starts or suddenly accelerates or decelerates.

  As described above, according to the planetary gear device 10 of the vehicle transmission of the present embodiment, the outer peripheral surface of the inner ring (inner shaft) 26 fitted to the outer peripheral portion of the carrier CA1 as a non-rotating member and the case 12 A cylindrical outer peripheral surface 46 and a cylindrical inner peripheral surface 48 which are provided on the inner peripheral surface of the outer ring 38 fitted in the fitting hole 36 and face each other across an annular gap, and the cylindrical outer peripheral surface 46 Rollably accommodated in a gap between the cylindrical inner peripheral surface 48 and the cylindrical outer peripheral surface 46 and the cylindrical inner surface according to relative rotation in one direction in the circumferential direction and the other direction between the carrier CA1 and the case 12. Since a plurality of rollers (rolling elements) 56 that suppress further relative rotation by biting into the gap with the peripheral surface 48 are provided, these torques are transmitted according to the relative rotation between the carrier CA1 and the case 12 during torque transmission. Inner ring provided between 6 and the contact pressure between the outer ring 38 and the roller 56 continuously increase, and the inner ring 26 and the tangential component of the frictional force between the outer ring 38 and the roller 56 that continuously increase with the contact pressure are the carrier CA1 and the inner ring 26. Since it acts as a reaction torque that continuously increases with an increase in the torque inputted to the carrier CA1 to suppress the relative rotation between the carrier CA1 and the case 12, the connecting portion between the carrier CA1 and the case 12 in the relative rotation section. It is possible to suppress the generation of impact sound. In addition, since the roller 56, the inner ring 26, and the outer ring 38 are made of a material that is relatively difficult to change with time, for example, a metal such as steel, it is known that an impact sound is generated at the connecting portion between the carrier CA1 and the case 12. Can be suppressed without degrading the performance.

  Further, according to the planetary gear unit 10 of the vehicle transmission of the present embodiment, the cylindrical inner peripheral surface 48 has a gap in the radial direction between the cylindrical outer peripheral surface 46 and one direction in the circumferential direction. The plurality of first recesses 50 and the second recesses 52 are formed so as to become smaller toward the direction, and the plurality of rollers 56 are cylinders corresponding to the plurality of first recesses 50 and the second recesses 52. Is accommodated in a gap between the cylindrical inner peripheral surface 48 and the cylindrical outer peripheral surface 46 so as to be able to roll, and in response to relative rotation in one direction and the other direction between the carrier CA1 and the case 12 during torque transmission. The contact force between the inner ring 26 and the outer ring 38 provided between them and the roller 56 increases, and the tangential component of the frictional force between the inner ring 26 and the outer ring 38 and the roller 56 that increases with the contact force is increased by the carrier CA. And inner ring 26 Since so as to act as a reaction torque anticaries in one direction and the other direction torque is input, it is possible to prevent the shock sound is generated at the junction of the carrier CA1 and the case 12.

  Further, according to the planetary gear device 10 of the vehicle transmission of the present embodiment, the plurality of first recesses 50 and the second recesses 52 are parallel to the axis C formed in the cylindrical inner peripheral surface 48. The plurality of rollers 56 are formed in a cylindrical shape and are respectively disposed in the gaps between the plurality of first recesses 50 and second recesses 52 and the cylindrical outer peripheral surface 46. Since the roller 56 and the cylindrical outer peripheral surface 46 and the cylindrical inner peripheral surface 48 are in line contact with each other, for example, the roller 56, the cylindrical outer peripheral surface 46, and the cylindrical inner peripheral surface 48 are worn. Aged performance deterioration due to the formation of a predetermined or larger backlash between them can be suppressed.

  As mentioned above, although one Example of this invention was described in detail with reference to drawings, this invention is not limited to this Example, It can implement in another aspect.

  For example, in the above-described embodiment, the planetary gear device 10 is of a type in which the carrier CA1 is coupled to the case 12 as a non-rotating member. However, the sun gear S1 or the ring gear R1 is coupled to the case 12 without being limited thereto. May be of the form At that time, a connecting device including an inner ring 26, an outer ring 38, and a plurality of rollers 56 may be used for the connecting portion.

  In the above-described embodiment, the cylindrical outer peripheral surface 46 and the cylindrical inner peripheral surface 48 are the outer peripheral surface of the inner ring 26 fitted on the outer peripheral portion of the carrier CA1 and the inner circumference of the outer ring 38 fitted on the case 12. Although it was formed in the surface, it is not restricted to this. For example, the cylindrical outer peripheral surface 46 may be formed on the outer peripheral portion of the carrier CA1, and the cylindrical inner peripheral surface 48 may be formed in the fitting hole 36 of the case. Therefore, the inner ring 26 and the outer ring 38 are not necessarily provided.

  In the above-described embodiment, the first recess 50 and the second recess 52 are provided on the cylindrical inner peripheral surface 48, but not limited thereto, the cylindrical outer peripheral surface 46 and the cylindrical inner peripheral surface 48 are not limited to this. Either one or both may be provided.

  In the above-described embodiment, the roller 56 is formed of a cylindrical member. However, the roller 56 is not limited thereto, and may be a rolling element such as a spherical member or an elliptic cylindrical member.

  In the above-described embodiment, the plurality of rollers 56 are accommodated in the gap between the first concave portion 50 and the second concave portion 52 formed on the cylindrical inner peripheral surface 48 and the cylindrical outer peripheral surface 46. The plurality of rollers 56 bite into the gaps between the first concave portion 50 and the second concave portion 52 and the cylindrical outer peripheral surface 46 at the time of relative rotation between the outer ring 38 and the outer ring 38, thereby suppressing further relative rotation. However, it is not limited to this. For example, the first recess 50 and the second recess 52 are not formed, and the gap between the cylindrical inner peripheral surface 48 and the cylindrical outer peripheral surface 46 is a non-circular shape such as an elliptical shape or a polygonal shape with rounded corners, or A plurality of cylindrical members (rolling elements) having a combined cross section are accommodated, and when the inner ring 26 and the outer ring 38 are rotated relative to each other, the plurality of cylindrical members are cylindrical inner peripheral surface 48 and cylindrical outer periphery. It may be configured to suppress further relative rotation by biting into the gap with the surface 46.

  It should be noted that the above description is merely an embodiment, and other examples are not illustrated. However, the present invention is implemented in variously modified and improved modes based on the knowledge of those skilled in the art without departing from the gist of the present invention. Can do.

10 planetary gear unit 12 case 26 inner ring (inner shaft)
36 fitting hole 38 outer ring 46 cylindrical outer peripheral surface 48 cylindrical inner peripheral surface 50 first concave portion 52 second concave portion 56 roller (rolling element)
CA1 carrier P1 pinion gear R1 ring gear S1 sun gear

Claims (1)

A sun gear, a carrier that rotatably supports a plurality of pinion gears that mesh with the sun gear, and a ring gear that meshes with the plurality of pinion gears. Any one of the ring gears is a planetary gear device of a vehicle transmission device that is fitted to the case as a non-rotating member so as not to be relatively rotatable,
Provided on the outer peripheral surface of the non-rotating member or the inner peripheral surface of the inner shaft fitted to the non-rotating member and the inner peripheral surface of the outer ring fitted to the fitting hole of the case or the case, and facing each other with an annular gap interposed therebetween A cylindrical outer peripheral surface and a cylindrical inner peripheral surface;
The cylindrical outer peripheral surface and the cylindrical inner peripheral surface are rotatably accommodated in a gap between the cylindrical outer peripheral surface and the cylindrical outer peripheral surface according to the relative rotation in any direction of the non-rotating member and the case. A planetary gear device for a vehicle transmission, comprising: a plurality of rolling elements that bite into a gap between the cylindrical inner peripheral surface and suppress further relative rotation.

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