JPH0571509U - Vehicle worm differential gear unit - Google Patents

Abstract

(57) [Summary] [Purpose] To stabilize the torque bias ratio. [Structure] Washers 8b, 10b contacting the differential case 1
Is fixed to the differential case 1, and the washers 8c, 9b, 9c and 10c which are in contact with the worm gears 2 and 3 are attached to the worm gear 2 and
Fix to 3. As a result, the washers 8b, 8c, 9
b, 9c, 10b, 10c are bearing members 8a, 9
The worm gear 2 is prevented from rotating together with the a and 10a.
3 stabilizes the torque bias ratio by suppressing the variation in the frictional state during driving.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a vehicle differential gear device, and more particularly to a vehicle worm differential gear device using a worm gear coupling.

[0002]

[Prior Art]

 As a vehicle differential gear device, a diff case that is rotationally driven, a pair of rotatable worm gears that are arranged in series within the diff case and that are respectively coupled to two output shafts, and a worm wheel and both sides of the worm wheel are provided. A plurality of sets of elements arranged in the opening for mounting the element gears of the differential case, with one pair of the spur gears meshing with each other and the worm wheels meshing with each of the worm gears as a set. A vehicular worm differential gear unit having a gear is known.

In such a conventional worm differential gear device for a vehicle, for example, as disclosed in Japanese Patent Laid-Open No. 49-50625, a bearing member and this bearing member are provided between a worm gear and a differential case. By interposing a thrust ring assembly for adjusting the frictional force, which comprises a pair of washers that sandwich the worm, a desired frictional state is given to the worm gear. Recently, instead of a bearing member and a pair of washers sandwiching the bearing member between the differential case and the worm gear, a friction force adjusting washer member that is slippery on one side and slippery on the other side is used to prevent slipping. The surface is in contact with the differential case, and the slippery surface is on the worm gear side, so that the worm gear is given a desired friction state.

As is well known, such a differential gear device not only corrects the rotation difference between both output shafts like a normal bevel gear differential device, but also distributes torque to both output shafts. There is a function to do. That is, depending on the torque bias ratio that is determined by the lead angle of the worm gear and the frictional state in the drive of the worm gear, the output shaft with the higher resistance than the output shaft with the lower resistance is Distribute even larger torque.

[0005]

[Problems to be solved by the device]

 With a configuration in which a thrust ring assembly consisting of a bearing member and a pair of washers sandwiching this bearing member is interposed between the worm gear and the differential case, the washer and the washer rotate due to the thrust force from the worm gear, and the bearing member However, there is a problem that the torque bias ratio becomes unstable because the frictional state in driving the worm gear varies and the torque bias ratio becomes unstable. In addition, if a washer member for frictional force adjustment is installed between the worm gear and the differential case, with one side slippery and the other side less slippery, it is not only between the friction force adjusting washer member and the worm gear side. , The thrust force from the worm gear causes a slip between the friction force adjusting washer member and the differential case, which similarly causes the friction state in the drive of the worm gear to vary and the torque bias ratio to become unstable. There was a problem of becoming.

The present invention has been made based on the above viewpoint, and an object thereof is to provide a worm differential gear device for a vehicle which is effective in stabilizing the torque bias ratio.

[0007]

[Means for Solving the Problems]

 In the present invention, a diff case that is driven to rotate, a pair of rotatable worm gears that are arranged in series in the diff case and that are respectively coupled to two output shafts, a worm wheel, and an engagement member provided on both sides of the worm wheel. A plurality of sets of the element gears rotatably provided in the differential case, wherein the pair of element gears are composed of a combination gear and engagement gears mesh with each other and a worm wheel meshes with each of the worm gears. And a thrust ring assembly for frictional force adjustment, which includes a bearing member and a washer interposed between the pair of worm gears and between the worm gear and the differential case. , The washer of the thrust ring assembly in contact with the differential case The differential case the fixed and the by the slide string assembly of a vehicle worm differential gear device a washer fixed to said worm gear in contact with the worm gear, to achieve the above object.

Further, in the present invention, a diff case that is rotationally driven, a pair of rotatable worm gears that are arranged in series in the diff case and that are respectively coupled to two output shafts, a worm wheel and both sides of the worm wheel. A plurality of rotatably provided on the differential case, each of which is a pair of element gears, each of which is formed by engaging the engaging gears with each other and engaging the worm wheel with each of the worm gears. A pair of the element gears and the friction force adjusting washer that is interposed between the worm gear and the differential case such that one surface is configured to be slippery and the surface configured to be slippery is the worm gear side. A worm differential gear unit for a vehicle having a member, the friction force adjusting washer member The above purpose is achieved by the vehicle worm differential gear unit fixed to the differential case.

[0009]

[Action]

 The washer of the thrust ring assembly that contacts the diff case is fixed to the diff case, and the washer of the thrust ring assembly that contacts the worm gear is fixed to the worm gear. Therefore, the washer does not rotate together with the bearing member, slip occurs only between the bearing member and the washer, and the torque bias ratio is stabilized.

The frictional force adjusting washer member is fixed to the differential case. Therefore, no slip occurs between the friction force adjusting washer member and the differential case, and the torque bias ratio is stabilized.

[0011]

Embodiment FIG. 1 is a block diagram showing an embodiment of the present invention, and FIG. 2 is a sectional view taken along line AA of FIG.

In these drawings, 1 is a differential case, 2 and 3 are worm gears, 4,5, 6, and 7 are element gears, and 8, 9 and 10 are thrust ring assemblies for frictional force adjustment.

The differential case 1 has three element gear mounting openings 1 a formed on the outer surface at angular intervals of 120 ° with respect to the central axis, and is provided with a flange 11, and the flange 11 has a ring gear. 12 is fixed. The differential case 1 is rotationally driven through engagement of a ring gear 12 and a hypoid gear (not shown).

The worm gears 2 and 3 are rotatably arranged in series in the differential case 1, and are spline-coupled to the output shafts 13 and 14, respectively.

The element gears 4 to 7 are composed of worm wheels 4a, 5a, 6a, 7a and spur gears (engaging gears) 4b, 5b, 6b, 7b provided on both sides of the worm wheel, respectively, and a pair of element gears. As a set, three sets are arranged around the circumference of the worm gears 2 and 3 at an angular interval of 120 degrees, and are rotatably attached to the element gear attachment opening 1a of the differential case 1 through the journal pins 15, 16, 17, and 18. It is included. In this example, the element gears 4 and 5 are paired, and the element gears 6 and 7 are paired with an element gear (not shown), respectively. In the element gears 4 and 5, the respective spur gears 4b and 5b mesh with each other, the worm wheel 4a of the element gear 4 meshes with one worm gear 2, and the worm wheel 5a of the element gear 5 meshes with the other worm gear 3. is doing. The other element gear pairs have the same structure.

The thrust ring assembly 8 includes a bearing member 8 a and a pair of washers 8 b and 8 c sandwiching the bearing member 8 a, and is provided between the differential case 1 and one worm gear 2. The washer 8b contacting the differential case 1 is fixed to the differential case 1, and the washer 8c contacting the worm gear 2 is fixed to the worm gear 2. The thrust ring assembly 9 includes a bearing member 9a and a pair of washers 9b and 9c sandwiching the bearing member 9a, and is provided between the pair of worm gears 2 and 3. The washer 9b that contacts one worm gear 2 is fixed to the one worm gear 2, and the washer 9c that contacts the other worm gear 3 is fixed to the other worm gear 3. The thrust ring assembly 10 includes a bearing member 10a and a pair of washers 10b and 10c sandwiching the bearing member 10a, and is provided between the differential case 1 and the other worm gear 3. The washer 10b in contact with the differential case 1 is fixed to the differential case 1, and the washer 10c in contact with the worm gear 3 is fixed to the worm gear 3.

FIG. 3 is an example showing a fixing means of the washer 8b (10b) to the differential case 1. In FIG. 3, 19 is a pin hole, 20 is a through hole, 21 is a detent pin, and 22 is a bolt. The pin hole 19 is formed on the surface of the washer 8b (10b) on the side of the differential case 1. The through hole 20 is formed in the output shaft holding portion 24 of the differential case 1 in parallel with the holding hole 23 of the output shaft 13 (14) and communicates with the pin hole 19 of the washer 8b (10b). There is. The detent pin 21 is inserted into the through hole 20 so that one end engages with the pin hole 19 of the washer 8b (10b), and the other end is retained and retained by the bolt 22 screwed into the through hole 20. The washer 8b (10b) is thereby fixed to the differential case 1.

FIG. 4 shows another example of the fixing means of the washer 8b (10b) to the differential case 1. In FIG. 4, 25 is a washer side pin hole, 26 is a differential case side pin hole, and 27 is a rotation stop pin. The washer-side pin hole 25 is formed on the surface of the washer 8b (10b) on the side of the differential case 1. The differential case side pin hole 26 is formed on the inner surface of the differential case 1 facing the washer 8a (10b) so as to correspond to the washer side pin hole 25. The rotation stopper pin 27 has one end engaged with the washer-side pin hole 25 and the other end engaged with the differential case-side pin hole 26, whereby the washer 8b (10b) is fixed to the differential case 1. It has become so.

FIG. 5 is a first example showing a fixing means of the washer 8c (9b, 9c, 10c) to the worm gear 2 (3). In FIG. 5, reference numeral 28 denotes a pawl provided on the side of the worm gear 2 (3) of the washer 8c (9b, 9c, 10c), and by engaging the pawl 28 with the worm gear groove on the surface of the worm gear 2 (3), 8c (9b, 9c, 10c) is fixed to the worm gear 2 (3).

FIG. 6 shows a second example of the fixing means of the washer 8c (9b, 9c, 10c) to the worm gear 2 (3). In FIG. 6, 29 is a pin and 30 is a pin hole. The pin 29 is provided on the worm gear 2 (3) side of the washer 8c (9b, 9c, 10c). The pin hole 30 is formed on the end surface of the worm gear 2 (3) facing the washer 8c (9b, 9c, 10c) so as to correspond to the position of the pin hole 29. The washer 8c (9b, 9c, 10c) is fixed to the worm gear 2 (3) by engaging the pin 29 with the pin hole 30.

7 and 8 are a third example showing the fixing means of the washer 8c (9b, 9c, 10c) to the worm gear 2 (3), and FIG. 8 is a plan view of the washer holding member in FIG. .. 7 and 8, 31 is a washer holding member, which has a washer holding claw 32 on the washer 8c (9b, 9c, 10c) side and a fixing claw 33 on the worm gear 2 (3) side. The washer holding member 31 fixedly holds the washer 8c (9b, 9c, 10c) on the washer holding member 31 by the spring force of the washer holding claw 32 that tries to move inward of the washer holding member 31, and the fixing claw 33 The washer 8c (9b, 9c, 10c) is fixed to the worm gear 2 (3) by engaging with the worm gear groove on the surface of the worm gear 2 (3). A groove that engages with the washer holding claw 32 may be formed at a portion of the washer 8c (9b, 9c, 10c) with which the washer holding claw 32 of the washer holding member 31 is in pressure contact. The washer 8c (9b, 9c, 10c) can be more securely fixed and held by the engagement of the groove with the groove.

FIG. 9 is a fourth example showing a fixing means for fixing the washer 8c (9b, 9c, 10c) to the worm gear 2 (3). In FIG. 9, 34 is a washer side pin hole, 35 is a worm gear side pin hole, and 36 is a rotation stop pin. The washer-side pin hole 34 is formed on the surface of the 8c (9b, 9c, 10c) on the worm gear 2 (3) side. The worm gear side pin hole 35 is formed at the end face of the worm gear 2 (3) facing the washer 8c (9b, 9c, 10c) so as to correspond to the washer side pin hole 34. One end of the anti-rotation pin 36 is engaged with the washer-side pin hole 34, and the other end is engaged with the worm gear-side pin hole 35, whereby the washer 8c (9b, 9c, 10c) is secured. It is designed to be fixed to the worm gear 2 (3).

According to the above-mentioned configuration, the washers 8a of the thrust ring assemblies 8 and 10 contacting the differential case 1 are fixed to the differential case 1, and the washers 8c of the thrust ring assemblies 8, 9 and 10 contacting the worm gears 2 and 3 are fixed. , 9b, 9c, 10c are fixed to the worm gears 2, 3, so that the washers 8b, 8c, 9b, 9c, 10b, 10c do not rotate together with the bearing members 8a, 9a, 10a, and the bearing members 8a, 9a. A slip occurs only between 9a, 10a and the washers 8b, 8c, 9b, 9c, 10b, 10c, and the torque bias ratio is stabilized by suppressing the variation in the friction state when the worm gears 2, 3 are driven. be able to.

FIG. 10 is a schematic view of a main part of another embodiment of the present invention, in which the thrust ring assembly 8 (10) in the previous embodiment is provided between the differential case 1 and the worm gear 2 (3). A washer member 37 for adjusting the frictional force, one surface 37a of which is slippery, is interposed. The friction force adjusting washer member 37 has a slippery surface 37a on the worm gear 2 (3) side, and a washer-side pin hole 38 is formed on the opposite surface to the differential case 1 side. A differential case side pin hole 39 is formed in a portion of the differential case 1 corresponding to the position of the washer side pin hole 38. One end engages with the washer side pin hole 38 and the other end engages with the differential case side pin hole 39. The anti-rotation pin 40 fixes the frictional force adjusting washer member 37 to the differential case 1. Reference numeral 41 is an ordinary washer, which is fixed to the end surface of the worm gear 2 (3) by the fixing means described above. With such a configuration, slippage does not occur between the friction force adjusting washer member 37 and the differential case 1, the torque bias ratio can be stabilized, and the friction force adjusting washer can be stabilized. The surface of the member 37 on the side of the differential case 1 does not need to be made slippery, and the roughness of the joint surface of the differential case 1 with the washer member 37 for adjusting the frictional force can be simplified. It is needless to say that the structure shown in FIG. 3 can be applied as the fixing means of the frictional force adjusting washer member 37. Other configurations are as described in the previous embodiment.

[0025]

[Effect of the device]

 As described above, according to the present invention, the washer of the thrust ring assembly that contacts the differential case is fixed to the differential case, and the washer of the thrust ring assembly that contacts the worm gear is fixed to the worm gear. It does not rotate, slip occurs only between the bearing member and the washer, and the torque bias ratio can be stabilized. In addition, instead of the thrust ring assembly consisting of the bearing member and the washer between the differential case and the worm gear, if a washer member for frictional force adjustment that has one surface slippery is interposed, Since the washer member is fixed to the differential case, no slip occurs between the friction force adjusting washer member and the differential case, and the torque bias ratio can be stabilized.

[Brief description of drawings]

FIG. 1 is a block diagram showing an embodiment of the present invention.

FIG. 2 is a cross-sectional view taken along the line AA of the configuration of FIG.

FIG. 3 is an example showing a fixing means of a washer to a differential case.

FIG. 4 is another example showing the fixing means of the washer to the differential case.

FIG. 5 is a first example showing a fixing means of a washer to a worm gear.

FIG. 6 is a second example showing the fixing means of the washer to the worm gear.

FIG. 7 is a third example showing the fixing means of the washer to the worm gear.

FIG. 8 is a plan view of the washer holding member in FIG.

FIG. 9 is a fourth example showing the fixing means of the washer to the worm gear.

FIG. 10 is a configuration diagram of a main part showing another embodiment of the present invention.

[Explanation of symbols]

 1 differential case 2,3 worm gear 4,5,6,7 element gear 4a, 5a, 6a, 7a worm wheel 4b, 5b, 6b, 7b spur gear 8,9,10 thrust ring assembly 8a, 9a, 10a bearing member 8b, 8c , 9b, 9c, 10b, 10c Washer 13, 14 Output shaft 19 Pin hole 20 Through hole 21 Non-rotating pin 22 Bolt 25 Washer side pin hole 26 Differential case side pin hole 27 Non-rotating pin 28 Claw 29 pin 30 Pin hole 31 Washer retention Member 32 Washer holding claw 33 Fixed claw 34 Washer side pin hole 35 Worm gear side pin hole 36 Whirl-stop pin 37 Friction force adjustment washer member 38 Washer side pin hole 39 Differential case side pin hole 40 Non-rotating pin

Claims (2)

[Scope of utility model registration request] 1. A rotationally driven differential case, a pair of rotatable worm gears arranged in series in the differential case and coupled to two output shafts respectively, a worm wheel and a pair of engagement members provided on both sides of the worm wheel. A plurality of sets of element gears rotatably provided on the differential case, wherein the pair of element gears are composed of a combination gear and engagement gears mesh with each other and a worm wheel meshes with each of the worm gears. And a thrust ring assembly for frictional force adjustment, which includes a bearing member and a washer interposed between the pair of worm gears and between the worm gear and the differential case, the worm differential gear device for a vehicle comprising: The washer of the thrust ring assembly contacting the A worm differential gear device for a vehicle, wherein a washer of the thrust ring assembly that is fixed to the worm gear and is in contact with the worm gear is fixed to the worm gear. 2. A rotationally driven differential case, a pair of rotatable worm gears arranged in series inside the differential case and respectively coupled to two output shafts, a worm wheel, and an engagement member provided on both sides of the worm wheel. A plurality of sets of element gears rotatably provided on the differential case, wherein the pair of element gears are composed of a combination gear and engagement gears mesh with each other and a worm wheel meshes with each of the worm gears. And a frictional force adjusting washer member interposed between the worm gear and the differential case such that one surface is configured to be slippery and the surface configured to be slippery is on the worm gear side. In a worm differential gear device, a vehicle washer in which the washer member for adjusting the frictional force is fixed to the differential case. Ohmic differential gearing.