JP2009150412A - Helical gear and power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a helical gear which realizes weight reduction while maintaining rigidity and strength, and a power transmission device equipped with the helical gear. <P>SOLUTION: In a second driven gear 43 or the like consisting of a helical gear equipped with a minor diameter annular part 81, a plurality of columns 82 radially extending from the outer peripheral part of the minor diameter annular part 81, a major diameter annular part 83 provided to a radial outer end of the column 82 surrounding the periphery of the minor diameter annular part 81, a tooth part 84 formed in the radial outer peripheral surface of the major diameter annular part 83 and provided with a tooth trace 84a inclined with respect to the axial direction of the minor diameter annular part 81, the column 82 is inclined around a radial shaft so that both outer peripheral surfaces of the column 82 extend in the same direction as a normal direction of the tooth trace 84a. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a helical gear and a power transmission device, and in particular, a through-hole between a small-diameter annular portion and a large-diameter annular portion by connecting a small-diameter annular portion and a large-diameter annular portion having a tooth portion with a support column. The present invention relates to a helical gear and a power transmission device.

  Helical gears are cylindrical gears whose tooth traces are slanted in a spiral shape with respect to the rotation axis, and differ in the direction of the tooth traces from spur gears whose tooth traces are cut parallel to the rotation axis. It has become. The helical gears are respectively fixed to two shafts arranged in parallel, and these helical gears mesh with each other to transmit rotational motion between the two shafts. This helical gear has a higher meshing ratio than a spur gear, and is therefore an advantageous gear for transmitting a large torque.

  As a transmission equipped with this helical gear, for example, a helical gear is fitted to each of the input shaft, the output shaft, and the final shaft. The rotary motion input from the internal combustion engine to the shaft is transmitted to the final shaft via the output shaft, and the rotary motion input to the final shaft is output to the drive shaft that drives the wheels.

  By the way, the noise generated in the transmission is generated when the helical gears, shafts, bearings, etc. rotate, and when these vibrations propagate to the transmission case etc. and the transmission case etc. resonates. It is roughly divided into noise.

  Conventionally, attempts have been made to reduce the noise generated in this transmission by preventing the resonance of the transmission case or the like by taking measures such as adding ribs to the transmission case or the like.

  However, in recent years, the reduction in noise of internal combustion engines, the reduction of noise generated by the rotation of tires, and reduction of wind noise due to improvement of the body have been reliably realized. It is becoming impossible to ignore the noise.

  In addition, in recent years, restrictions on the space for mounting a transmission on a vehicle and restrictions on the weight of the transmission itself have become more severe, making it very difficult to implement countermeasures for transmission cases and the like. ing. For this reason, it is necessary to develop a noise reduction technique other than measures for the transmission case and the like.

  In response to such demands, there is a structure in which the structure of a helical gear is devised so as to suppress noise and reduce the weight of the transmission, as shown in FIG. 11 (see, for example, Patent Document 1). . In FIG. 11, the helical gear 1 includes a hub portion 2 as a small-diameter annular portion fitted to an input shaft and an output shaft, and a plurality of struts 3 extending radially from the outer peripheral portion of the hub portion 2; A large-diameter annular portion 4 provided at the radially outer end of the support column 3 so as to surround the periphery of the hub portion 2, a radial outer peripheral surface of the large-diameter annular portion 4, and the axial direction of the hub portion 2 And a tooth portion 5 (a part of which is shown in FIG. 11). The through hole 6 is formed between the pillars 3 so as to be thinned.

  In this helical gear 1, since the elastic deformation in the radial direction and the tangential direction when the tooth portion 5 of the helical gear 1 is engaged can be allowed, the tooth portion 5 of the helical gear 1. The timing of meshing of the tooth portion 5 varies due to fluctuations in the noise applied when the tooth portions 5 collide with each other and vibration is generated when the teeth mesh with each other, or the load applied to the helical gear 1 varies. Therefore, it is possible to reduce the noise caused by the vibrations generated and suppress the vibrations from propagating to the transmission case and the like to resonate.

Moreover, since the helical gear 1 is thinned by forming the through hole 6 between the support columns 3, the helical gear 1 can be reduced in weight, and as a result, the transmission can be reduced in weight. Can be achieved.
JP 2005-69401 A

  However, in such a conventional helical gear 1, the hub portion 2 and the large-diameter annular portion 4 are connected by the column 3 and the through hole 6 is formed between the columns 3. Although the weight can be reduced, there is room for further weight reduction of the helical gear 1 because the shape of the support column 3 is not devised for the load applied in the rotation direction of the helical gear 1. .

  That is, when the helical gear 1 is rotated by meshing the teeth 5 of the helical gear 1, the helical gear 1 has a helical gear as shown in FIGS. 12 (a) and 12 (b). The component force a in the normal direction perpendicular to the tooth trace 5a of the tooth portion 5 and the component force b in the direction parallel to the tooth trace 5a are applied to the load F applied in the rotation direction 1.

  Here, as shown in FIGS. 12A and 12B, both side surfaces 3a of the column 3 are extended in a direction orthogonal to the axial direction of the helical gear 1, and both side surfaces 3b of the column 3 are connected to the hub. Consider a structure in which the column 3 is made thin so as to extend in parallel with the axial direction of the portion 2.

At this time, the distribution of the internal stress of the support column 3 varies with respect to the component force a and the component force b applied to the support column 3. In particular, the distribution of the internal stress distribution of the support column 3 with respect to the component force a increases. End up.
For this reason, if the plate thickness of the column 3 is reduced, the rigidity and strength of the helical gear 1 are reduced, and the component force a and component force b applied to the column 3 by increasing the plate thickness of the column 3 are increased. On the other hand, it is necessary to prevent a decrease in rigidity and strength. Therefore, it is difficult to reduce the weight while maintaining the rigidity and strength of the conventional helical gear 1, and there is still an improvement.

  The present invention has been made in order to solve the conventional problems as described above, and can achieve reduction in weight while maintaining rigidity and strength, and a power transmission device including a helical gear. The purpose is to provide.

  In order to achieve the above object, the helical gear according to the present invention includes (1) a small-diameter annular portion fitted to the outer peripheral portion of the rotating shaft, and a plurality of radially extending portions from the outer peripheral portion of the small-diameter annular portion. And a large-diameter annular portion provided to surround the periphery of the small-diameter annular portion at the radially outer end of the post, and the small-diameter annular portion formed on the radially outer peripheral surface of the large-diameter annular portion. In the helical gear having a tooth portion having a tooth trace inclined with respect to the axial direction of the post, the outer peripheral side surfaces of the support pillar extend in the same direction as the normal direction of the tooth trace. Is tilted around the radial axis.

  With this configuration, the struts are tilted around the radial axis so that the outer peripheral side surfaces of the struts extend in the same direction as the normal line of the tooth traces. On the other hand, when a component force in a direction perpendicular to the tooth part and a component force in a direction parallel to the tooth trace are applied to the column, the component force in a direction parallel to the component force in the direction perpendicular to the tooth trace is applied. The distribution of the internal stress of the support can be made uniform.

  For this reason, the thickness of the column can be reduced to the minimum necessary for maintaining the strength and rigidity against the load in the rotating direction of the helical gear, and the column can be reduced in weight. .

  The helical gear described in (1) above is configured such that (2) the support column has both outer peripheral side surfaces extending in the same direction as the axial direction of the small-diameter annular portion.

  With this configuration, the support column has both outer peripheral side surfaces that extend in the same direction as the axial direction of the small-diameter annular portion, so by forming a through hole between the small-diameter annular portion and the large-diameter annular portion by punching or the like, When forming a support | pillar between an annular part and a large diameter annular part, the punching direction and the direction of the outer peripheral both sides of a support | pillar can be made into the same direction, and a support | pillar can be formed easily.

  In the helical gear described in (1) and (2) above, (3) a radial inner end portion of the support column is connected so as to surround the small diameter cylindrical portion.

  With this configuration, the radial inner end of the column is connected so as to surround the small-diameter cylindrical portion, so that when the moment is applied to the radial outer end of the column in the rotational direction of the helical gear, The rigidity of the inner end of the direction can be increased, and the thickness of the strut can be made the minimum necessary to maintain the strength and rigidity against the load in the rotation direction of the helical gear. The weight of the support can be reduced.

  The power transmission device according to the present invention is (4) a power transmission device having the above-mentioned helical gear, wherein the case, the input shaft and the output shaft housed in the case, the input shaft and the output shaft The helical gear is engaged with the small-diameter annular portion, and the teeth of the large-diameter annular portion are engaged with each other, and a bearing that rotatably supports the input shaft and the output shaft on the case, The lubricating oil stored on the bottom surface of the case is made up of the helical gear provided on the input shaft or the output shaft.

  With this configuration, the struts are tilted around the radial axis so that the outer peripheral side surfaces of the struts extend in the same direction as the normal direction of the tooth trace, so the helical gear of the input shaft and the output shaft On the meshing surface of the helical gear, a component force in a direction perpendicular to the tooth trace of the tooth portion and a component force in a direction parallel to the tooth trace are applied to the support column with respect to the load applied in the rotation direction of the helical gear. In this case, it is possible to make the distribution of the internal stress of the support column uniform with respect to the component force in the direction parallel to the component force perpendicular to the tooth trace.

  For this reason, the thickness of the column can be reduced to the minimum necessary for maintaining the strength and rigidity against the load in the rotating direction of the helical gear, and the column can be reduced in weight. . As a result, the power transmission device can be reduced in weight.

  In addition, since the struts are tilted around the radial axis so that both outer peripheral sides of the struts extend in the same direction as the normal direction of the tooth traces, the struts can function as propellers, and the bottom of the case When the lubricating oil stored in the cylinder is scraped up by a helical gear provided on the input shaft or the output shaft, directivity can be given to the flow of the lubricating oil by the support.

  For this reason, when the bearing that supports the input shaft or the output shaft is located in the vicinity of the helical gear, the bearing can be lubricated by forcibly supplying lubricating oil to the bearing by the support column, The lubrication performance of the power transmission device can be improved.

  (5) The power transmission device according to (4), wherein (5) a breather is provided in the case and allows air to flow between the inside and outside of the case in accordance with a pressure difference inside the case and a pressure outside the case. It is comprised from what has an apparatus.

  With this configuration, the support column can function as a propeller, so that an air flow can be generated when the helical gear rotates, and the atmospheric pressure in the case can be optimized.

  For this reason, when the amount of lubricating oil scooped up by the helical gear increases, it is possible to prevent the air pressure in one part of the case from becoming higher than the other part with respect to the outside air. Therefore, it is possible to prevent the lubricating oil from being blown out.

  ADVANTAGE OF THE INVENTION According to this invention, the power transmission device provided with the helical gear which can achieve weight reduction, maintaining a rigidity and intensity | strength, and a helical gear can be provided.

  Hereinafter, embodiments of a helical gear and a power transmission device according to the present invention will be described with reference to the drawings.

(First embodiment)
1 to 9 are views showing a first embodiment of a helical gear and a power transmission device according to the present invention, and the present invention is applied to a transaxle having a manual transmission as a power transmission device. An example is shown.

First, the configuration will be described.
FIG. 1 is a view showing a transaxle provided with a manual transmission. In FIG. 1, the transaxle 20 includes a transmission 21. The transmission 21 includes an input shaft and a rotation accommodated in a space defined by a first case 22 and a second case 23 as cases. An input shaft 32 as a shaft, and a first drive gear 33, a second drive gear 34, a third drive gear 35, a force drive gear 36, a fifth drive gear 37, and a reverse drive gear 38 attached to the input shaft 32 are provided.

The first drive gear 33 and the second drive gear 34 are fixed to the input shaft 32 and are rotated together with the input shaft 32.
Further, the third drive gear 35, the force drive gear 36 and the fifth drive gear 37 can idle with respect to the input shaft 32, and sleeves 39 and 40 of a predetermined sync mechanism are moved in the axial direction of the input shaft 32 (hereinafter simply referred to as “synchronization mechanism”). By being slid in the axial direction), it is coupled with the input shaft 32 and rotates together with the input shaft 32.
Further, the input shaft 32 is connected to an engine which is an internal combustion engine via a clutch, and the input shaft 32 is rotated by a driving force from the engine.

  The transmission 21 includes an output shaft 41 as an output shaft and a rotation shaft. The output shaft 41 extends substantially in parallel with the input shaft 32. The output shaft 41 includes a first driven gear 42 and a second driven gear 42. A driven gear 43, a third driven gear 44, a force driven gear 45, a fifth driven gear 46, and an output gear 47 are provided.

  The output gear 47, the third driven gear 44, and the force driven gear 45 are fixed to the output shaft 41 and rotate together with the output shaft 41.

  Further, the first driven gear 42 and the second driven gear 43 can idle with respect to the output shaft 41, and are engaged with the output shaft 41 by rotating the sleeve 48 in the axial direction so as to rotate together with the output shaft 41.

  A reverse driven gear 49 is attached to the outer periphery of the sleeve 48, and a reverse idler gear 50 is interposed between the reverse drive gear 38 and the reverse driven gear 49.

  The reverse idler gear 50 does not mesh with either the reverse drive gear 38 or the reverse driven gear 49 when the vehicle is traveling forward. Further, when the vehicle moves backward, the reverse idler gear 50 meshes with the reverse drive gear 38 and the reverse driven gear 49, and the rotation of the input shaft 32 passes through the reverse drive gear 38, the reverse idler gear 50, and the reverse driven gear 49 to the output shaft 41. Communicated.

  The first drive gear 33 and the first driven gear 42 constitute the first speed, the second drive gear 34 and the second driven gear 43 constitute the second speed, the third drive gear 35 and the third driven gear 44 constitute the third speed, and the force drive gear. 36 and the force driven gear 45 constitute the fourth speed, and the fifth drive gear 37 and the fifth driven gear 46 constitute the fifth speed.

  The first drive gear 33, the second drive gear 34, the third drive gear 35, the force drive gear 36, the fifth drive gear 37, the reverse drive gear 38, the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 45. 46 is composed of a helical gear, and the drive gears 33 to 38 and the driven gears 42 to 46 have a twist angle of 45 ° which is a predetermined angle with respect to the axial direction of the input shaft 32 and the output shaft 41. Are engaged.

  Further, the fork shaft 51 is connected to the sleeve 40 and the reverse idler gear 50 of the fifth speed synchro mechanism by the shift fork 52 and the shift fork 53. By sliding in the longitudinal direction, the sleeve 40 is moved to the fifth speed. The Fifth drive gear 37 is connected to the input shaft 32 by operating the synchro mechanism, or the reverse idler gear 50 is engaged with the reverse drive gear 38 and the reverse driven gear 49.

  Further, the fork shaft 54 is connected to the sleeve 39 of the sync mechanism for the third speed and the fourth speed by the shift fork 55, and the sleeve 39 can be used for the third speed or the fourth speed by sliding the fork shaft 54 in the longitudinal direction. Activate the synchro mechanism. As a result, either the third drive gear 35 or the force drive gear 36 rotates together with the input shaft 32.

  The fork shaft 56 is connected to the sleeve 48 of the first-speed and second-speed sync mechanism by the shift fork 57. When the fork shaft 56 slides in the longitudinal direction, the sleeve 48 becomes the first-speed or second-speed sync mechanism. Mesh. As a result, either the first driven gear 42 or the second driven gear 43 rotates together with the output shaft 41.

  These fork shafts 51, 54, and 56 transmit the operating force accompanying the shift operation of a shift lever (not shown) to the sleeves 39, 40, and 48 through the fork shafts 51, 54, and 56, and the sleeves 39, 40, and 48 are It is slid in the axial direction and meshed with the third drive gear 35, the force drive gear 36, the fifth drive gear 37, the first driven gear 42 and the second driven gear 43 in accordance with the shift position.

  The output gear 47 meshes with the ring gear 58 of the differential, and this ring gear 58 is fixed to the differential case 59 so that both the differential case 59 and the ring gear 58 rotate.

  The output gear 47 and the ring gear 58 are helical gears, and the output gear 47 and the ring gear 58 have a twist angle of 45 °, which is a predetermined angle with respect to the axial direction of the input shaft 32 and the output shaft 41. Are engaged.

  The differential case 59 holds a pinion gear 61 that can rotate and revolve by a pinion shaft 60, and the pinion gear 61 meshes with a pair of side gears 62. An output member 63 is connected to the side gear 62 by a spline, and the rotational force output from the output member 63 is transmitted to the wheel through the drive shaft.

  On the other hand, one axial end portion of the input shaft 32 and the output shaft 41 is rotatably attached to the first case 22 of the transaxle 20 via ball bearings 71 and 72 as bearings. The other axial end of the shaft 41 is rotatably attached to the second case 23 of the transaxle 20 via cylindrical roller bearings 73 and 74 as bearings.

  One end portion of the differential case 59 is rotatably attached to the first case 22 of the transaxle 20 via a tapered roller bearing 75 as a bearing, and the other end portion of the differential case 59 is a tapered roller as a bearing. It is rotatably attached to the second case 23 of the transaxle 20 via a bearing 76.

  In addition, lubricating oil O (see FIG. 2) is stored on the bottom surface of the first case 22, and this lubricating oil contains the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46. The bottom is immersed.

  A separate plate 65 is provided below the first case 22, and the separate plate 65 provides a slight gap in the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46. Are facing each other.

  As shown in FIG. 2, the separate plate 65 is curved along the circumferential direction of the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46. In FIG. 2, the shape of the separate plate 65 below the second driven gear 43 is shown.

  In the separate plate 65, the lubricant stored in the bottom surface of the first case 22 is separated from the separate plate 65 and the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45 and the fifth driven gear 46. In order to reduce the amount of lubricating oil, the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46 reduce the amount of lubricating oil, and the first driven gear 42, The stirring resistance of the driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46 is prevented from increasing.

  Further, the lubricant driven up by the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45 and the fifth driven gear 46 is used as the first drive gear 33, the second drive gear 34, the third drive gear 35, the force drive gear 36, The fifth drive gear 37, the reverse drive gear 38 and the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46 are supplied to the respective meshing surfaces. 38 and the driven gears 42 to 46 are lubricated by lubricating oil.

  Further, lubricating oil is stored on the bottom surface of the second case 23, and this lubrication immerses the ring gear 58 below. The lubricating oil is scraped up by the ring gear 58 and supplied to the meshing surfaces of the ring gear 58 and the output gear 47 to lubricate the meshing surfaces of the ring gear 58 and the output gear 47.

  The second case 23 is provided with a catch tank (not shown), and the lubricating oil scraped up by the ring gear 58 is temporarily stored in the catch tank, so that the bottom surface of the second case 23 is lubricated. The stirring level of the ring gear 58 is reduced by lowering the oil level.

  The first drive gear 33, the second drive gear 34, the third drive gear 35, the force drive gear 36, the fifth drive gear 37, the reverse drive gear 38, the first driven gear 42, the second driven gear 43, the third driven gear 44, which are helical gears, The force driven gear 45, the fifth driven gear 46, the output gear 47, and the ring gear 58 are shown as shown in FIGS. In addition, although the magnitude | size of each gear differs, since the basic composition is the same, the structure of the second driven gear 43 is demonstrated.

  Hereinafter, the first drive gear 33, the second drive gear 34, the third drive gear 35, the force drive gear 36, the fifth drive gear 37, the reverse drive gear 38, the first driven gear 42, the third driven gear 44, the force driven gear 45, the fifth driven gear 46, In the description of each part of the output gear 47 and the ring gear 58, the same reference numerals as those of the second driven gear 43 are used.

  3 and 4, the second driven gear 43 includes a small-diameter annular portion 81 that is spline-fitted to the output shaft 41, a plurality of struts 82 that extend radially from the outer periphery of the small-diameter annular portion 81, A large-diameter annular portion 83 provided so as to surround the periphery of the small-diameter annular portion 81 at the radially outer end, and an axial direction of the small-diameter annular portion 81 formed on the radial outer peripheral surface of the large-diameter annular portion 83, that is, And a tooth portion 84 having tooth traces 84a inclined at an angle of 45 ° with respect to the axial direction of the output shaft 41.

  Further, as shown in FIG. 5, the column 82 is tilted around the radial axis of the column 82 so that the outer peripheral side surfaces 82a of the column 82 extend in the same direction as the normal direction of the tooth trace 84a. The outer peripheral side surfaces 82b orthogonal to the outer peripheral side surfaces 82a of the support 82 extend in the same direction as the tooth traces 84a. Accordingly, a through hole 85 is formed between the support columns 82.

  When the material of the second driven gear 43 is made of resin, the support 82 may be formed by thinning the through hole 85 using a mold, and the material of the second driven gear 43 is made of metal. In this case, the through hole 85 may be cut out by cutting.

  Further, as shown in FIG. 1, a breather device 77 as a breather means is provided on the upper portion of the first case 22, and the breather device 77 includes a hose 78 protruding from above the first case 22. A plug 79 for closing the end of the hose 78 is provided, and a gap is formed between the hose 78 and the plug 79 to allow passage of air and prevent passage of lubricating oil.

  The breather device 77 is provided in the first case according to the pressure in the space defined by the first case 22 and the second case 23 and the pressure difference outside the first case 22 and the second case 23. Air is circulated between the space defined by the second case 23 and the outside and the outside.

Next, the operation will be described.
When driving the vehicle, a first drive gear 33, a second drive gear 34, a third drive gear 35, a force drive gear 36, a fifth drive gear 37, a reverse drive gear 38, a first driven gear 42, a helical gear having a through hole 85, When the third driven gear 44, the force driven gear 45, the fifth driven gear 46, the ring gear 58 and the output gear 47 mesh with each other, the first drive gear 33, the second drive gear 34, the third drive gear 35, the force drive gear 36, the fifth drive gear 37, Radiation of reverse drive gear 38, first driven gear 42, third driven gear 44, force driven gear 45, fifth driven gear 46, output gear 47 and ring gear 58 It can be tolerated elastic deformation of the direction and the tangential direction.

  For this reason, the noise generated when the tooth portions 84 such as the third drive gear 35 and the third driven gear 44 collide with each other and the vibration is generated, and the load applied to the third drive gear 35 and the third driven gear 44 is changed. Noise caused by vibrations caused by fluctuations in the timing of meshing is reduced, and these vibrations propagate to the first case 22 and the second case 23 so that the first case 22 and the second case 23 are Resonance can be suppressed.

  A small amount of lubricating oil separated by the separate plate 65 is scraped up by the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46, and the first drive gear 33, the second drive gear 34, the third The drive gear 35, the force drive gear 36, the fifth drive gear 37, the reverse drive gear 38 and the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 46 are supplied to the meshing surfaces of the gears. Lubricated.

  Further, the lubricating oil stored on the bottom surface of the second case 23 is scraped up by the ring gear 58 and supplied to the meshing surfaces of the ring gear 58 and the output gear 47, and the meshing surfaces of the ring gear 58 and the output gear 47 are lubricated. The

Here, the first drive gear 33, the second drive gear 34, the third drive gear 35, the force drive gear 36, the fifth drive gear 37, the reverse drive gear 38, the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45 and the fifth gear. Since the outer peripheral side surfaces 82a of the prop 82 of the driven gear 46 are inclined around the radial axis of the prop 82 so as to extend in the same direction as the normal direction of the tooth trace 84a, the prop 82 is a propeller. The function of will be demonstrated.
That is, since the support column 82 is inclined, the lubricating oil that has collided with the front side of the outer peripheral side surface 82a of the support column 82 moves from the front side of the outer peripheral side surface 82a to the back side along the outer peripheral side surface 82a.

  For this reason, the flow of the lubricating oil scraped up by the force driven gear 45 and the fifth driven gear 46 and the first driven gear 42 and the force drive gear 36 has directivity by the support 82, and the lubricating oil The ball bearing 72 is lubricated by being supplied to the ball bearing 72 adjacent to the fifth driven gear 46, the first driven gear 42 and the force drive gear 36.

  Further, the lubricating oil scraped up from the force driven gear 45 and the fifth driven gear 46 to the force drive gear 36 and the fifth drive gear 37 is transferred to the force drive gear 36 and the fifth drive gear 37 by the support 82 of the force drive gear 36 and the fifth drive gear 37. It is supplied to the adjacent ball bearing 71 and the ball bearing 71 is lubricated.

  Further, the lubricating oil scraped up by the first driven gear 42 is supplied to the cylindrical roller bearing 73 adjacent to the first drive gear 33 by the support 82 of the first drive gear 33, and the cylindrical roller bearing 73 is lubricated.

  Further, the lubricating oil scraped up by the first driven gear 42 is supplied to the cylindrical roller bearing 74 adjacent to the output gear 47 by the support 82 of the output gear 47, and the cylindrical roller bearing 74 is lubricated.

  Further, the lubricating oil scraped up by the ring gear 58 is supplied to the tapered roller bearing 75 adjacent to the ring gear 58 by the support 82 of the ring gear 58, and the tapered roller bearing 75 is lubricated.

  Thus, in the present embodiment, the support 82 can function as a propeller, and when the lubricating oil stored on the bottom surface of the first case 22 is scraped up by the Fifth drive gear 37 or the like, the support 82 is lubricated. Bearings 71, 72, 73 adjacent to the fifth driven gear 46, the fifth drive gear 37, the first driven gear 42, the force drive gear 36, the first driven gear 42, and the ring gear 58, which can give directivity to the flow of oil; By forcibly supplying the lubricant oil 74 and 75 from the support 82, the lubricating oil can be efficiently lubricated and the lubricating performance of the transaxle 20 can be improved.

  The first drive gear 33, the second drive gear 34, the third drive gear 35, the force drive gear 36, the fifth drive gear 37, the reverse drive gear 38, the first driven gear 42, the second driven gear 43, the third driven gear 44, the force driven gear 45, and the fifth driven gear 45. 46 supports 82 can generate a flow of airflow in the space defined by the first case 22 and the second case 23, and the pressure in the space can be optimized. It can prevent becoming higher than the pressure of other parts.

  Therefore, when the pressure in the space defined by the first case 22 and the second case in the vicinity of the breather device 77 is increased and the amount of lubricating oil circulating in the space is increased, the breather is increased. It is possible to prevent so-called breather blowing, in which lubricating oil is blown out from the device 77.

  On the other hand, as shown in FIG. 5, the second driven gear 43 or the like having the support 82 of the present embodiment is in a direction orthogonal to the tooth trace 84a of the tooth portion 84 with respect to the load F applied in the rotation direction of the second driven gear 43 or the like. A component force a and a component force b in a direction parallel to the tooth trace 84a are applied.

  In the present embodiment, as shown in FIG. 5, the outer peripheral side surfaces 82a of the support column 82 extend in the normal direction of the tooth trace 84a of the tooth portion 84, and the outer peripheral side surfaces 82b of the support column 82 are parallel to the tooth trace 84a. Therefore, the distribution of internal stress of the column 82 with respect to the component force in the direction b parallel to the component force a in the direction orthogonal to the tooth trace 84a can be made uniform.

  For this reason, the thickness of the column 82 can be reduced to the minimum necessary for maintaining the strength and rigidity against the load F in the rotational direction of the second driven gear 43 and the like, and the column 82 can be reduced in weight. be able to. Therefore, the second driven gear 43 and the like can be reduced in weight, and as a result, the transaxle 20 can be reduced in weight.

  In this embodiment, the outer peripheral side surfaces 82b orthogonal to the outer peripheral both side surfaces 82a of the support 82 are extended in the same direction as the tooth traces 84a. However, as shown in FIG. You may make it extend the outer peripheral both sides | surfaces 82b orthogonal to 82a to the same direction as the axial direction of the small diameter annular part 81. FIG. In this case, when the through-hole 85 is formed between the small-diameter annular portion 81 and the large-diameter annular portion 83 by punching or the like, the column 82 is formed between the small-diameter annular portion 81 and the large-diameter annular portion 83. In addition, the punching direction and the direction of the outer peripheral side surfaces 82b of the support 82 can be made the same direction, and the support 82 can be easily formed.

  Further, as shown in FIGS. 7 and 8, the radial inner end of the column 91 is connected so as to surround the small-diameter annular portion 81, and the small-diameter annular portion 81 and the large-diameter annular except for the radial inner end of the column 91. A through hole 92 may be formed between the portions 83.

  In this way, since the radially inner end of the column 91 can be connected, when the moment is applied to the radially outer end of the column 91 in the rotational direction of the second driven gear 43 or the like, the radiation of the column 91 is emitted. The rigidity of the inner end portion in the direction can be increased, and the thickness of the support column 91 can be set to the minimum necessary thickness for maintaining the strength and rigidity against the load in the rotation direction of the second driven gear 43 and the like. It is possible to reduce the weight of the column 91.

(Second Embodiment)
9 and 10 are views showing a second embodiment of the helical gear and the power transmission device according to the present invention, and the present invention is applied to a transaxle having an automatic transmission as a power transmission device. An example is shown. Since the configuration of the helical gear is the same as that of the first embodiment, the description of the helical gear will be made using the drawings describing the helical gear of the first embodiment.
Further, in the automatic transmission according to the present embodiment, the helical gear is applied to the output gear and the differential device. Therefore, the configuration of the differential device will be specifically described, and the configuration of the automatic transmission. Will be described using a skeleton diagram.

  In FIG. 9, a transaxle 110 is rotatably fixed to a case 111 and has an input shaft 112 and a second shaft center 120c that are centered on a first shaft 112c that is disposed in parallel to each other. The counter shaft 120 includes a third shaft center 130c that is the center of rotation of the left and right axles 131 and is parallel to the first shaft center 112c and the second shaft center 120c. Yes.

  On the first shaft center 112c, there are a first speed changer 114 and a second planetary gear unit 117 which are mainly composed of a torque converter 108 with a lock-up clutch coupled to the input shaft 112, and a first planetary gear unit 115. And the third planetary gear unit 118, and an output gear 119 is concentrically provided between the first transmission unit 114 and the second transmission unit 116.

  A driven gear is disposed on the counter shaft 120 so as to be rotatable on the second axis 120c, and has a diameter larger than that of the output gear 119 and meshes with the output gear 119 to constitute the counter gear pair 121. A differential drive gear 124 having a diameter smaller than that of the driven gear 122 and the driven gear 122 is provided.

  A bevel gear type differential gear device 132 connected to the axle 131 is disposed on the third shaft center 130c. The differential gear device 132 is provided with a differential ring gear 134 having a diameter larger than that of the differential drive gear 124 meshed with the differential drive gear 124 and being fixed to the differential case 133 and having a third shaft center 130c as a rotation center. .

  The transaxle 110 configured as described above is provided between the engine 106 that is an internal combustion engine and the drive wheels 136, and transmits the output of the engine 106 to the left and right drive wheels 136. Specifically, the output of the engine 106 is transmitted to the input shaft 112 via the torque converter 108 connected to the crankshaft 107 of the engine 106, and the input shaft 112 is rotated around the first axis 112c by the engine 106. The rotation is driven, and the rotation is transmitted to the output gear 119 rotating around the first axis 112c via the first transmission unit 114 and the second transmission unit 116.

  The power from the output gear 119, that is, the rotation of the output gear 119 is decelerated through the driven gear 122, the differential drive gear 124 and the differential ring gear 134, and the left and right drives are driven through the differential gear device 132 and the axle 131. The left and right drive wheels 136 are rotationally driven by the engine 106 by being transmitted to the wheels 136.

  The first transmission unit 114 includes a double pinion type first planetary gear unit 115. The first planetary gear device 115 includes a first sun gear S1, a plurality of pairs of first planetary gears P1 that mesh with each other, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first planetary gear P1. Is provided with a first ring gear R1 meshing with the first sun gear S1.

  The first carrier CA1 is connected to the input shaft 112 via a transmission member M1 constituting the first intermediate output path, and the rotational speed of the input shaft 112 is from the transmission member M1 at a gear ratio “1.0”. It is output to the second transmission unit 116 side.

  The first sun gear S1 is integrally fixed to the case 111 so as not to rotate, and the first ring gear R1 is connected to a transmission member M2 constituting a second intermediate output path that decelerates and outputs the rotation of the input shaft 112. The first transmission unit 114 rotates the input shaft 112 through a first intermediate output path and a second intermediate output path that is rotated at a reduced speed because the transmission ratio is large with respect to the first intermediate output path. Output to the transmission 116.

  The second transmission unit 116 includes a single pinion type second planetary gear unit 117 and a double pinion type third planetary gear unit 118. The second planetary gear device 117 includes a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second sun gear via the second planetary gear P2. A second ring gear R2 meshing with S2 is provided.

  The third planetary gear unit 118 includes a third sun gear S3, a plurality of pairs of third planetary gears P3 that mesh with each other, a third carrier CA3 that supports the third planetary gear P3 so as to rotate and revolve, and a third planetary gear P3. And a third ring gear R3 that meshes with the third sun gear S3.

  Further, the second planetary gear device 117 and the third planetary gear device 118 are configured such that the second carrier CA2 and the third carrier CA3 are constituted by common parts, and the second ring gear R2 and the third ring gear R3 are common parts. And a Ravigneaux type planetary gear train that also serves as one of a pair of third planetary gears P3 meshing with each other.

  In the second transmission unit 116, the second sun gear S2 is selectively connected to the first carrier CA1 corresponding to the first intermediate output path via the fourth clutch C4, and is connected to the second sun gear S2 via the third clutch C3. 2 selectively connected to the first ring gear R1 corresponding to the intermediate output path, and further selectively connected to the case 111 via the first brake B1, and the second carrier CA2 and the third carrier CA3 are integrally connected. And selectively connected to the input shaft 112 corresponding to the first intermediate output path via the second clutch C2, and selectively connected to the case 111 via the second brake B2, and the second ring gear R2 The third ring gear R3 is integrally connected to the output gear 119, and the third sun gear S3 is connected to the first intermediate output path corresponding to the second intermediate output path via the first clutch C1. Is selectively connected to the ring gear R1.

  In addition, the one-way clutch F1 is provided in parallel with the second brake B2, and the second carrier CA2 and the third carrier CA3 are only in the case of power-on running in which the driving wheels 136 are rotationally driven by the power of the engine 106. The one-way clutch F1 is automatically engaged with the case 111.

  On the other hand, as shown in FIG. 10, a driven gear 122 and a differential drive gear 124 are provided in a case portion 141 as a case that is positioned below the case 111 and constitutes a part of the case 111 and has a space independent of the case 111. The differential gear 134 is housed, and the output gear 119 is engaged with the driven gear 122. The driven gear 122, the differential drive gear 124, and the differential ring gear 134 are composed of helical gears as in the first embodiment.

  That is, the driven gear 122, the differential drive gear 124, and the differential ring gear 134 include a small-diameter annular portion 81 that is spline-fitted to the counter shaft 120 and the differential case 133, and a plurality of struts that extend radially from the outer peripheral portion of the small-diameter annular portion 81. 82, a large-diameter annular portion 83 provided to surround the periphery of the small-diameter annular portion 81 at the radially outer end of the support 82, and a small-diameter annular portion 81 formed on the radially outer peripheral surface of the large-diameter annular portion 83. , That is, a tooth portion 84 having tooth traces 84a inclined at an angle of 45 ° with respect to the axial direction of the counter shaft 120 and the differential case 133 (see FIGS. 3 and 4).

  Further, the support column 82 is tilted around the radial axis of the support column 82 so that the outer peripheral side surfaces 82a of the support column 82 extend in the same direction as the normal direction of the tooth trace 84a. The outer peripheral side surfaces 82b orthogonal to the both side surfaces 82a extend in the same direction as the tooth traces 84a. Therefore, a through hole 85 is formed between the columns 82 (see FIG. 5).

  Lubricating oil is stored on the bottom surface of the case portion 141, and the lubricating oil immerses the driven gear 122 and the diff ring gear 134 below. The lubricating oil is scraped up by the differential ring gear 134 to lubricate the meshing surfaces of the differential drive gear 124 and the differential ring gear 134, and is also scraped up by the driven gear 122, so that the meshing surface of the driven gear 122 and the output gear 119 is It is designed to lubricate.

  The counter shaft 120 and the differential case 133 are rotatably attached to the case portion 141 by a bearing (not shown), and this bearing is provided so as to sandwich the differential ring gear 134, the differential drive gear 124, and the driven gear 122.

  Also, a breather device 142 as a breather means is attached to the case portion 141. The breather device 142 includes a hose protruding from above the case portion 141 and a plug for closing the end of the hose. The air is allowed to pass through a gap provided between the plug and the plug and the lubricating oil is prevented from passing therethrough.

  A catch tank (not shown) is provided above the case portion 141, and the bottom surface of the case portion 141 is obtained by temporarily storing the lubricating oil scraped up by the diff ring gear 134 and the driven gear 122 in the catch tank. By lowering the level of the lubricating oil, the stirring resistance of the differential ring gear 134 and the driven gear 122 is reduced.

  In the transaxle 110 having such a configuration, the diff ring gear 134 and the diff drive gear 124, the diff ring gear 134 and the output gear 119, which are helical gears having the through holes 85, are engaged with each other when the vehicle is operated. In this case, the elastic deformation in the radial direction and the tangential direction of the differential ring gear 134, the differential drive gear 124, and the differential ring gear 134 can be allowed.

  For this reason, the noise generated when the tooth portions 84 such as the differential ring gear 134 and the differential drive gear 124 collide with each other generate vibrations, and the load applied to the differential ring gear 134 and the differential drive gear 124 varies. It is possible to reduce noise caused by vibrations caused by fluctuations in the meshing timing, and to suppress the propagation of these vibrations to the case part 141 and the case part 141 to resonate.

  Further, the lubricating oil is scraped up by the differential ring gear 134 and the driven gear 122, and this lubricating oil is supplied to the meshing surfaces of the differential ring gear 134 and the differential drive gear 124 and the meshing surfaces of the driven gear 122 and the output gear 119, thereby lubricating each gear. The

  Here, both outer peripheral side surfaces 82a of the post 82 of the differential ring gear 134, the differential drive gear 124 and the driven gear 122 extend around the radial axis of the post 82 so as to extend in the same direction as the normal line direction of the tooth trace 84a. Since it is tilted, the support column 82 exhibits a function as a propeller.

  For this reason, the flow of the lubricating oil scraped up by the differential ring gear 134 and the differential drive gear 124 has directivity by the support 82, and this lubricating oil is applied to the differential ring gear 134, the differential drive gear 124 and the driven gear 122. Supply to adjacent bearings to lubricate the bearings.

  As described above, in this embodiment, the support 82 can function as a propeller. When the lubricating oil stored on the bottom surface of the case portion 141 is scraped up by the diff ring gear 134 and the driven gear 122, the support oil is used by the support 82. The bearing can be lubricated efficiently by forcibly supplying the lubricating oil from the support 82 to the bearing adjacent to the differential ring gear 134, the differential drive gear 124 and the driven gear 122 having the support 82. The lubricating performance of the transaxle 20 can be improved.

  Further, the support 82 of the differential ring gear 134, the differential drive gear 124, and the driven gear 122 can generate an air flow in the space defined by the case portion 141, so that the atmospheric pressure in the space can be optimized. It is possible to prevent the pressure in a part of the space from becoming higher than the pressure in the other part. For this reason, when the pressure in the vicinity of the breather device 142 increases and the amount of lubricating oil circulating in the space increases, the so-called breather blow occurs in which the lubricant oil blows out from the breather device 142. Can be prevented.

  Further, the component force a in the direction orthogonal to the tooth trace 84a of the tooth portion 84 and the component force b in the direction parallel to the tooth trace 84a with respect to the load F applied in the rotational direction of the differential ring gear 134, the differential drive gear 124 and the driven gear 122. However, in the present embodiment, both side surfaces 82a of the support column 82 extend in the normal direction of the tooth trace 84a of the tooth portion 84, and the outer peripheral side surfaces 82b of the support column 82 extend in parallel with the tooth trace 84a. Since this is done, the distribution of the internal stress of the column 82 with respect to the component force in the direction b parallel to the component force a in the direction orthogonal to the tooth trace 84a can be made uniform, and as in the first embodiment, The thickness of the support 82 can be set to the minimum thickness necessary for maintaining the strength and rigidity against the load F in the rotational direction of the differential ring gear 134, the differential drive gear 124, and the driven gear 122. It is possible to reduce the weight of the pillar 82.

  Therefore, it is possible to reduce the weight of the differential ring gear 134, the differential drive gear 124, and the driven gear 122. As a result, it is possible to reduce the weight of the transaxle 110.

  The embodiment disclosed this time is illustrative in all respects and is not limited to this embodiment. The scope of the present invention is shown not by the above description of the embodiments but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.

  As described above, the helical gear and the power transmission device according to the present invention have an effect that the weight can be reduced while maintaining rigidity and strength, and a large-diameter ring having a small-diameter annular portion and a tooth portion. It is useful as a helical gear, a power transmission device, or the like in which a through hole is formed between the small-diameter annular portion and the large-diameter annular portion by connecting the portions to each other with a support column.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, and is sectional drawing of a power transmission device. It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, and is sectional drawing which shows the vicinity of a second driven gear and a separate plate. It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, and is a perspective view of a second driven gear. It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, and is a front view of a second driven gear. It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, (a) is the part added to the direction orthogonal to a tooth trace with respect to the positional relationship of a tooth trace and a support | pillar, and the rotation direction of a support | pillar. The figure which shows force a, (b) is a figure which shows the component force b added to the direction parallel to a tooth trace with respect to the rotation direction of the support | pillar of the figure (a). BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, (a) is orthogonal to a tooth trace with respect to the positional relationship of a tooth trace and another shape support | pillar, and the rotation direction of a support | pillar. The figure which shows the component force a added to a direction, (b) is a figure which shows the component force b added to a direction parallel to a tooth trace with respect to the rotation direction of the support | pillar of the figure (a). It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, and is a perspective view of the second driven gear which has another support | pillar shape. It is a figure which shows 1st Embodiment of the power transmission device which concerns on this invention, and is a front view of the second driven gear which has another support | pillar shape. It is a figure which shows 2nd Embodiment of the power transmission device which concerns on this invention, and is a skeleton figure of a power transmission device. It is a figure which shows 2nd Embodiment of the power transmission device which concerns on this invention, and is a figure which shows the positional relationship of a differential ring gear, a differential drive gear, and a differential ring gear. It is a perspective view of the conventional helical gear. (A) is the figure which shows the component force a added to the direction orthogonal to a tooth trace with respect to the positional relationship of the conventional support | pillar and a tooth trace, and the rotation direction of a support | pillar, (b) is the support | pillar of the figure (a) It is a figure which shows the component force b added to a direction parallel to a tooth trace with respect to this rotation direction.

Explanation of symbols

22 First case (case part)
23 Second case (case part)
32 Input shaft (rotary shaft, input shaft)
33 First drive gear (helical gear)
34 Second drive gear (helical gear)
35 Third drive gear (helical gear)
36 Force drive gear (helical gear)
37 Fifth drive gear 38 Reverse drive gear (helical gear)
41 Output shaft (rotary shaft, output shaft)
42 First driven gear (helical gear)
43 Second driven gear (helical gear)
44 Third driven gear (helical gear)
45 Force driven gear (helical gear)
46 Fifth driven gear (helical gear)
47 Output gear (helical gear)
81 Small-diameter annular portion 82, 91 Post 82a, 82b Both sides of outer periphery 83 Large-diameter annular portion 84 Tooth portion 84a Tooth trace 71, 72 Ball bearing (bearing)
73, 74, cylindrical roller bearings (bearings)
75, 76 Tapered roller bearing (bearing)
77, 142 Breather device (breather means)
122 Driven gear (helical gear)
124 Differential drive gear (helical gear)
134 Defring gear (helical gear)
141 Case part (case)

Claims (5)

A small-diameter annular portion fitted to the outer peripheral portion of the rotating shaft, a plurality of struts extending in a radial direction from the outer peripheral portion of the small-diameter annular portion, and a periphery of the small-diameter annular portion at a radial outer end portion of the post. A lotus provided with a large-diameter annular portion provided so as to surround, and a tooth portion having a tooth trace formed on the radial outer peripheral surface of the large-diameter annular portion and inclined with respect to the axial direction of the small-diameter annular portion. In the case of gears,
A helical gear characterized in that the struts are tilted around the radial axis so that both outer peripheral side surfaces of the struts extend in the same direction as the normal direction of the tooth traces. The helical gear according to claim 1, wherein the strut has outer peripheral side surfaces extending in the same direction as the axial direction of the small-diameter annular portion. The helical gear according to claim 1 or 2, wherein a radially inner end portion of the support column is connected so as to surround the small-diameter cylindrical portion. A power transmission device having a helical gear according to any one of claims 1 to 3,
A helical gear in which the small-diameter annular portion is fitted to the case, the input shaft and the output shaft accommodated in the case, and the teeth of the large-diameter annular portion are engaged with each other. And a bearing that rotatably supports the input shaft and the output shaft on the case,
A power transmission device characterized in that the lubricating oil stored on the bottom surface of the case is scraped up by the helical gear provided on the input shaft or the output shaft. 5. The power according to claim 4, further comprising a breather unit that is provided in the case and circulates air between the inside and outside of the case in accordance with a pressure difference between the pressure inside the case and the pressure outside the case. Transmission device.

Images