Torque divider

Abstract: A torque divider for distributing the engine torque in a determined torque dividing ratio includes a case (3) which is driven and rotated by an engine and which has first and second supporting holes (53,55). In the torque divider first and second side gears (11,13) are arranged side by side. The second side gear (13) has a predetermined radius (R₂) larger than that (R₁) of the first side gear (11). First and second pinion gears (57,59) are housed inside the first and second supporting holes (53,55), respectively. The first and second pinion gears (57,59), respectively, have first and second gear parts (61,63). The first gear parts (61) of the first and second pinion gears (57,59) are meshed with each other; the second gear part (63) of the first pinion gear (57) is meshed with the first side gear (11); and the second gear part (63) of the second pinion gear (59) is meshed with the second side gear (13).

Description: BACKGROUND OF THE INVENTION This invention relates to a torque divider for distributing the engine torque in a determined torque dividing ratio according to the preamble portion of claim 1 and claim 2 respectively. Such a torque divider can be employed in a center differential limiting device which serves to distribute the engine torque to the front wheels and the rear wheels in a four wheel drive motor vehicle. A torque divider of this type is known from DE-A-39 06 650 which discloses a conventional torque divider 201 as shown in Fig. 1. This torque divider 201 includes a pair of pinion gears 205, 207 which are housed inside and supported by a differential-gear case 203, and a pair of side gears 209, 211 which are connected to front and rear axle shafts, respectively. The pair of pinion gears 205, 207 mesh with each other. The first side gear 209 is meshed with the first pinion gear 205, and the second side gear 211 is meshed with the second pinion gear 207. The torque of the engine which rotatively drives the differential-gear case 203 is distributed to each front and rear axle shaft through the pinion gears 205, 207 and the side gears 209, 211. The number of gear teeth of the second side gear 211 (N2) is greater than that of the first side gear 209 (N1). Accordingly, the torque dividing ratio between the side gears 209, 211 is N1: N2. Thus, when this mechanism is employed in the center differential limiting device of a four wheel drive motor vehicle, it is possible to distribute a greater proportion of the total torque to the rear axle shaft than to the front axle shaft. However, if the radius of the second side gear 211 is enlarged to enhance the torque dividing ratio, the radial size of the torque divider 201 also becomes larger. The limiting factor of the size of the radius of the shaft around which the first side gear 209 is secured, deters decreasing the radius of the first side gear 209 to enhance the torque dividing ratio in the torque divider 201. Thus, it is difficult to enhance the torque dividing ratio in the torque divider 201. Further, since the gear parts of the pinion gears 205, 207 which are meshed with the side gears 209, 211 are spaced apart from each other while the gear parts of the pinion gears meshing with each other are arranged between said side gears, it is necessary to fill the axial space between the first side gear 209 and the second side gear 211 with a filling member so that the member can receive the thrust force generated by the meshing of the gears 205, 207, 209, 211. SUMMARY OF THE INVENTION The object of the present invention, therefore, is to provide a torque divider of the type as mentioned above wherein it is possible to enlarge the torque dividing ratio without enlarging the radial size of the divider while reducing the number of parts in the divider. In order to achieve the above-mentioned object, this invention provides a torque divider, comprising the features of claim 1 and claim 2 respectively. Thus, it is possible to enlarge the torque dividing ratio without enlarging either side gears; namely, without enlarging the size of the torque divider, thereby facilitating the possibility of employing this torque divider in various types of motor vehicles. Further, since the enhancement of the torque dividing ratio depends on the number of gear teeth or the pitch radius of the pinion gears, the second side gear with a larger pitch radius than that of the first side gear can, more easily, be made relatively smaller, thereby enhancing minimization of the torque divider's size. Moreover, since the second side gear is located adjacent to the first side gear, it is not necessary to provide a member to receive the thrust force, thereby reducing the number of members in the torque divider. In a preferred embodiment, the first and second gear parts of the first pinion gear are connected by and rotatable around the shaft. The shaft is located around the second side gear, and the second side gear is located axially between the first side gear and the first gear parts. Thus the second gear part of the first pinion gear is meshed with the smaller first side gear and therefore may have a large radius. The second gear part of the second pinion gear which is meshed with the second side gear which has a radius larger than that of the first side gear, may have a small radius. In the above-mentioned configuration, while the number of gear teeth of the first side gear (N1) is predetermined smaller than that of the second side gear (N2) and the inequality, n2'/n1'< n2/n1 is satisfied, where n1' and n2' are the number of gear teeth of the first and second gear parts of the second pinion gear, respectively, and n1 and n2 are the number of gear teeth of the first and second gear parts of the first pinion gear, respectively; since X= N2/N1 · n2/n1 · n1'/n2' is given, where X is the torque dividing ratio, a large torque ratio is obtained by, for example, setting the number of second gear part gear teeth of the first pinion gear (n2) to be greater than that of first gear part gear teeth of the first pinion gear (n1) (i.e. n2> n1) and by setting the number of first and second gear part gear teeth of the second pinion gear (n1', n2') to be equal (i.e. n1'=n2'). Meanwhile, while the size of pitch radius of the first side gear (R1) is predetermined smaller than that of the second side gear (R2) and r2'/r1'< r2/r1 is satisfied, where r1' and r2' are the sizes of pitch radii of the first and second gear parts of the second pinion gear, respectively, and r1 and r2 are the sizes of pitch radii of the first and second gear parts of the first pinion gear, respectively; since X= R2/R1 · r2/r1 · r1'/r2' is given, where X is the torque dividing ratio, a large torque ratio is obtained, for example, by selecting a larger pitch radius of the second gear part of the first pinion gear (r2), a smaller pitch radius of the first gear part of the first pinion gear (r1) and an equal pitch radii of first and second gear parts of the second pinion gear (r1', r2'). Further advantagous embodiments of the invention are set out in the subclaims. BRIEF DESCRIPTION OF THE DRAWING Fig. 1 is a cross-sectional view of a conventional torque divider. Fig. 2 is a cross-sectional view of a torque divider according to a first embodiment of the present invention. Fig. 3 is a cross-sectional view of the torque divider, taken in a direction shown by arrow III - III of Fig. 2. Fig. 4 is a cross-sectional view of a torque divider according to a second embodiment of the present invention. Fig. 5 is a cross-sectional view of a torque divider according to a third embodiment of the present invention. DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to Figs. 1 and 2, the first embodiment will be described. A torque divider according to this embodiment is employed in a center differential limiting device 1 which distributes torque generated in an internal combustion engine of a four wheel drive motor vehicle to the front wheels and the rear wheels. The below-described front and rear sides or directions correspond to the left and right sides or directions in Fig. 2. As shown in Fig. 2, the front end of an inner case 3 is supported inside a transfer case 7 through a bearing 5. The inner case 3 is connected to output members of a transmission through a hollow shaft 9 which is spline connected to the inner case 3, so as to be rotatively driven by the engine. A first side gear 11 and a second side gear 13 have the same axis and are arranged at the front and rear side, respectively, inside the inner case 3. The second side gear 13 has a predetermined size of pitch radius larger than that of the first side gear 11. The front end of the first side gear 11 is supported along the inner periphery of the inner case 3 through a bearing 15. The rear end of the second side gear 13 is supported by a shaft support portion 17 inside the inner case 3. A shaft support member 19 is provided between the side gears 11, 13. Through the shaft support member 19, each opposite end of the side gears 11, 13 are firmly maintained and the centering for the side gears 11, 13 are executed. A washer 21 is provided between the first side gear 11 and the inner case 3 and a washer 23 between the second side gear 13 and the inner case 3. The first side gear 11 is connected to a transmission shaft 27 for the front wheels through a coupling sleeve 25. The transmission shaft 27 is supported along the inner periphery of the hollow shaft 9 through a bearing 29. A bearing 31 is provided between the rear end of the hollow shaft 9 and the front ends of the coupling sleeve 25 and the first side gear 11. A threaded nut 33 is fastened at the rear end of the transmission shaft 27 so as to prevent the coupling sleeve 25 from slipping off. The torque of the first side gear 11 is distributed to the right and left front wheels through the transmission shaft 27 and a front differential device. The second side gear 13 located behind the first side gear 11 is spline connected to a transmission shaft 35 for the rear wheels. The transmission shaft 35 is supported by the first side gear 11, the inner case 3, and the transfer case 7 through bearings 37, 39, 41, respectively. A gear portion 43 provided on the transmission shaft 35 is meshed with a gear portion 47 provided on a parallel shaft 45 which is supported by the transfer case 7 through bearings 49, 51. A washer 52 is provided between the gear portion 43 and the inner case 3. The torque of the side gear 13 is distributed to the right and left rear wheels through the transmission shaft 35, the parallel shaft 45, and a rear differential device. Four sets of pairs of supporting holes 53, 55 are provided in the inner case 3 as shown in Figs. 2 and 3. First and second pinion gears 57, 59 are housed inside the supporting holes 53, 55, respectively. The first pinion gear 57 has a length along the axis thereof larger than that of the second pinion gear 59 and consists of a first gear part 61, a second gear part 63, and a shaft part 65 which connects the first and second gear parts 61, 63 to each other. The first gear part 61 has a radius smaller than that of the second gear part 63. The second pinion gear 59 consists of a second gear part 69 and a first gear part 67 which is located behind the second gear part 69. The first gear part 61 of the first pinion gear 57 is meshed with the first gear part 67 of the second pinion gear 59 and the second gear part 63 of the first pinion gear 57 is meshed with the first side gear 11. Further, the second gear part 69 of the second pinion gear 59 is meshed with the second side gear 13. The driving force of the engine which rotates the inner case 3 is transmitted to the pinion gears 57, 59 through the inner case 3 and to the side gears 11, 13 through the pinion gears 57, 59 and is distributed to the front and rear wheel sides. Even if differences of driving resistance between the front and rear wheels occur, the driving force of the engine is differentially distributed to both front and rear wheel sides due to the self rotation of the pinion gears 57, 59. Further, while the driving force or torque is distributed, since the pinion gears 57, 59 are pressed to the walls of the supporting holes 53, 55, respectively, due to the meshing reaction force generated between the side gears 11, 13, the generated frictional torque serves to limit the differential distribution of the torque. In the above-explained configuration, there are two methods to enhance the torque dividing ratio. In the first method, in order to increase the torque dividing ratio (i.e. the ratio of the torque distributed to the front wheels to the torque distributed to the rear wheels) higher than the ratio of the number N2 of gear teeth on the second side gear 13 to the number N1 of gear teeth of the first side gear 11, i.e. N2/N1, the number of gear teeth of the first and second gear parts 61, 63 of the first pinion gear 57, i.e n1, n2, and the number of gear teeth of the first and second gear parts 67, 69 of the second pinion gear 59, i.e n1', n2', is determined, respectively, using the following conditional expressions: N1< N2 N2/N1< N2/N1· n2/n1 · n1'/n2'. Solving the conditional expression (2) results in n2'/n1'< n2/n1. Thus, the number of gear teeth of the pinion gears 57, 59 is determined so as to satisfy the expressions (1) and (3). For example, the number of gear teeth for the side gears 11, 13 is determined as N1=15, N2=18; the number of gear teeth for the first and second gear parts 61, 63 of the pinion gear 57 as n1=6, n2=8; and the number of gear teeth for the first and second gear parts 67, 69 of the pinion gear 59 as n1'=n2'=6. Accordingly, the ratio of the torque distributed to the front wheels to the torque distributed to the rear wheels can be calculated as N2/N1 · n2/n1 = 1.2 × 8/6= 1.6, which is greater than N2/N1= 18/15= 1.2; this latter value is the ratio obtained in a conventional torque divider which considers only the gear teeth ratio for the side gears 11, 13. In this situation, the torque dividing ratio does not only depend on the gear teeth ratio for the side gears 11, 13, but can also depend on the gear teeth ratio of the second and first gear parts 63, 61, i.e n2/n1, of the first pinion gear 57. In other words, if the gear teeth ratio of the second and first gear parts 63, 61, i.e n2/n1, is determined to be large when the number of gear teeth for the first and second gear parts 67, 69, i.e n1' and n2', of the second pinion gear 59 is equal, the torque dividing ratio will in turn be large. In this situation, since the second gear part 63 is meshed with the first side gear 11, which has a radial size smaller than that of the second side gear 13, even when the radial size of the second gear part 63 is larger than that of the first gear part 61, it is possible to prevent the inner case 3 from being enlarged. Thus, without enlarging the radial size of the second side gear 13 with a radial size larger than that of the first side gear 11, namely without enlarging the radial size of the inner case 3 and without making the whole center differential limiting device 1 large and heavy, the torque dividing ratio for the front and rear wheel sides can easily be enhanced, thereby improving the acceleration performance of the vehicle. In other words, it is possible to minimizing the size of the center differential limiting device 1 by reducing the size of the second side gear 13 which has a radial size larger than that of the first side gear 11 within the limit of the radial size thereof. Moreover, it is possible to further enhance the torque dividing ratio by changing the ratio of the number pf gear teeth for the first and second gear parts 67, 69, i.e n1'/n2', in addition to the ratio of the number of gear teeth for the second and first gear parts 63, 61, i.e. n2/n1. In the second method to enhance the torque dividing ratio, the sizes of pitch radii of the gears or the gear parts are determined, respectively. This is done as an alternative to determining the number of gear teeth on the gears or the gear parts as in the first method, so as to satisfy the following conditional expressions: R1< R2 r2'/r1'< r2/r1 where R1 and R2 are the sizes of the pitch radii of the side gears 11, 13, respectively; r1' and r2' are the sizes of pitch radii of the first and second gear parts 67, 69 of the second pinion gear 59, respectively; and r1 and r2 are the sizes of pitch radii of the first and second gear parts 61, 63 of the first pinion gear 57, respectively, as shown in Fig. 2. In this second method, the torque dividing ratio does not only depend on the pitch radius ratio for the side gears 11, 13, but can also depend on the pitch radius ratio of the second and first gear parts 63, 61 (r2/r1) of the first pinion gear 57 and the pitch radius ratio of the first and second gear parts 67, 69 (r1'/r2') of the second pinion gear 59. In other words, if the pitch radius ratio of the second and first gear parts 63, 61 (r2/r1) (or the pitch radius ratio of the first and second gear parts 67, 69 (r1'/r2')) is determined to be large, the torque dividing ratio will in turn be large. Thus, it is possible to prevent the inner case 3 from being enlarged, as explained in connection with the first method. Accordingly, the same effects are obtained by the second method. As in both methods the side gears 11, 13 are arranged parallel to each other and the meshing contact between the pinion gears 57, 59 is executed behind the side gears 11, 13, it is not necessary to provide a member to receive the thrust force between the side gears 11, 13, which is needed in the prior art device, thereby reducing the number of parts in the center differential limiting device 1. Next, referring now to Fig. 4, the second embodiment of the present invention will be described. A torque divider according to this second embodiment is also employed in a center differential limiting device 71 as in the first embodiment. The below-described front and rear sides or directions correspond to the left and right sides or directions in Fig. 4. A boss 75 is spline connected with a case 73, while being prevented from slipping off by a locating snap ring 77. The boss 75 is connected to output members of a transmission. The case 73 is rotatively driven by the engine. First and second side gears 79, 81 have the same axis and are arranged in the front and rear sides, respectively, inside the case 73. The rear end of the second side gear 81 is supported by a shaft support portion 83 inside the case 73. The opposite ends of the side gears 79, 81 support each other and center each other by use of a shaft support member 85 provided therein. Washers 87, 89 are provided between the side gears 79, 81 and between the second side gear 81 and the case 73, respectively. The first side gear 79 is spline coupled with a hollow shaft 91 for the front wheel side. The hollow shaft 91 is supported along the inner periphery of the boss 75 through bearings 93, 95. The torque of the first side gear 79 is distributed to the right and left front wheels through the hollow shaft 91 and a front differential device. The second side gear 81 located behind the first side gear 79 is spline coupled with a transmission shaft 97 for the rear wheel side. The transmission shaft 97 is supported by the hollow shaft 91 through a bearing 99 and by the case 73 through a bearing 101. A gear portion 103 of the transmission shaft 97 is meshed with a gear portion of a parallel shaft, which is connected to a propeller shaft for the rear wheels. The torque of the second side gear 81 is distributed to the right and left rear wheels through a rear differential device. A washer 105 is provided between the gear portion 103 and the case 73. Four sets of pairs of supporting holes 107, 109 are provided in the case 73. First and second pinion gears 111, 113 are housed inside the supporting holes 107, 109, respectively. The first pinion gear 111 has a length along the axis thereof larger than that of the second pinion gear 113 and consists of a first gear part 115, a second gear part 117, and shaft part 119 which connects the first and second gear parts 115, 117 to each other. The first gear part 115 has a radius smaller than that of the second gear part 117. The second pinion gear 113 consists of a second gear part 123 and a first gear part 121 which is located behind the second gear part 123. The first gear part 115 of the first pinion gear 111 is meshed with the first gear part 121 of the second pinion gear 113 and the second gear part 117 is meshed with the first side gear 79. Further, the second gear part 123 of the second pinion gear 113 is meshed with the second side gear 81, which has a radius larger than that of the first side gear 79. A supporting member 125 is provided at the rear end of the case 73 which is retained by a locating snap ring 127 so as to prevent the supporting member 125 from slipping off. The number of gear teeth for the side gears 79, 81, i.e N1 and N2, is determined as 15, 18; and the number of gear teeth of the first and second gear parts 115, 117, 121, 123, i.e. n1, n2, n1', n2', as 6, 8, 6, 6, respectively. Thus, the ratio of the front wheels side torque to the rear wheels side torque is enhanced to 1.6 from 1.2; the latter value being the torque ratio obtained in the prior art which considers only the side gears 79, 81, as explained in connection with the first embodiment. The meshing reaction force of the pinion gears 111, 113 to the side gears 79, 81, which occurs when torque is transmitted, is proportional to the transmitted torque. Accordingly, the differential limiting function depends on the frictional force between the supporting holes 107, 109 and the pinion gears 111, 113. Thus the function may be called a "torque proportional" type function. The center differential limiting device 71 includes two types of differential limiting devices, a rotational speed proportional type 129 and the torque proportional type. One side of the differential limiting device 129 includes a rear-end portion 131 provided in the boss 75 which is spline coupled with the case 73. The other side of the differential limiting device 129 includes a member 133 which is spline coupled with the outer periphery of the hollow shaft 91, which is arranged in the front wheels side. The rear-end portion 131 contacts the first side gear 79 and the first pinion gear 111 through a bearing 135. The rotational speed proportional type of differential limiting device 129 is exemplified by a "pump" type of coupling device and a "multiplate" type of viscosity coupling device, etc. By utilizing both types of differential limiting function (i.e. the rotational speed proportional type and the torque proportional type), even if one front wheel on the vehicle idles, a relatively large amount of power can be transmitted to the rear wheels. The same result holds true if a rear wheel idles; thereby improving driving performance through bad road conditions. Thus, the center differential limiting device 71 can facilitate steady driving or operating performance. Also, in the center differential limiting device 71, it is possible to enhance the torque dividing ratio by changing the number of gear teeth of the pinion gears 111, 113 without enlarging and making the whole device heavy, as is also accomplished in the first embodiment. Further, it is not necessary to provide a member to receive the thrust force between the side gears 79, 81. Next, referring now to Fig. 5, the third embodiment of the present invention will be described. In this embodiment, a second pinion gear 137 includes a first gear part 143 and a second gear part 139 which has a radius smaller than that of the first gear part 143. The second gear part 139 is meshed with a second side gear 141 which has a radius larger than that of a first side gear 151 located adjacent to the second side gear 141. Further, the first gear part 143 is meshed with a first gear part 147, which is provided on a first pinion gear 145. Since a second gear part 149 provided on the first pinion gear 145 is meshed with the second side gear 151 the first pinion gear 145 is located relatively close to a shaft 153 around which the first side gear 151 is arranged. Accordingly, even when the first gear part 143 of the second pinion gear 137 has a relatively large radius, it is possible to avoid enlarging the whole device, as explained in connection with the first and second embodiments. Where N1 is the number of gear teeth of the first side gear 151; N2 is the number of gear teeth of the second side gear 141; n1 and n2 are the numbers of gear teeth of the first and second gear parts 147, 149 of the first pinion gear 145, respectively; n1' and n2' are the numbers of gear teeth of the first and second gear parts 143, 139 of the second pinion gear 137, respectively; if each number of gear teeth is selected to satisfy n2'/n1'< n2/n1, the torque dividing ratio for the front and rear wheel sides can be larger than the torque dividing ratio which depends only on the ratio of the number of gear teeth of the second side gear 141 to the number of gear teeth of the first side gear 151, namely N2/N1, as in the prior art device.

Claims: A torque divider for distributing engine torque in a determined torque dividing ratio, comprising: a case (3; 73) being driven and rotated by an engine; first and second supporting holes (53, 55; 107, 109) being provided in said case; a first side gear (11; 79); a second side gear (13; 81) being located adjacent to the first side gear, said second side gear having a predetermined radius larger than a predetermined radius of the first side gear; and first and second pinion gears (57, 59; 111, 113), respectively, being housed inside the first supporting hole (53; 107) and the second supporting hole (55; 109), said first and second pinion gears, respectively, having a first gear part (61, 67; 115, 121) and a second gear part (63, 69; 117, 123), said first gear parts (61, 67; 115, 121) of the first and second pinion gears being meshed with each other, said second gear part (63; 117) of the first pinion gear (57; 111) being meshed with the first side gear (11; 79), and said second gear part (69; 123) of the second pinion gear (59; 113) being meshed with the second side gear (13; 81), characterized in that the second gear part (63; 117) of the first pinion gear (57; 111) has a larger pitch radius than the first gear part (61; 115) to which it is connected by a shaft (65; 119). A torque divider for distributing engine torque in a determined torque dividing ratio, comprising: a case (3) being driven and rotated by an engine; first and second supporting holes (53, 55) being provided in said case; a first side gear (151); a second side gear (141) being located adjacent to the first side gear, said second side gear having a predetermined radius larger than a predetermined radius of the first side gear; and first and second pinion gears (145, 137), respectively, being housed inside the first supporting hole (53) and the second supporting hole (55), said first and second pinion gears, respectively, having a first gear part (147, 143) and a second gear part (149, 139), said first gear parts (147, 143) of the first and second pinion gears being meshed with each other, said second gear part (149) of the first pinion gear (145) being meshed with the first side gear (151), and said second gear part (139) of the second pinion gear (137) being meshed with the second side gear (141), characterized in that the second gear part (139) of the second pinion gear (137) has a smaller pitch radius than the first gear part (143) to which it is connected by a shaft. A torque divider as claimed in claim 1 or claim 2, wherein in the first side gear (11; 79; 151) the number N1 of the gear teeth is smaller than the number N2 of the gear teeth in the second side gear (13; 81; 141), and in the second pinion gear (59; 113; 137) the ratio of the number n2 of gear teeth of the second gear part (69; 123; 139) to the number n1 of gear teeth of the first gear part (67; 121; 143) is smaller than the ratio of the number n2 of gear teeth of the second gear part (63; 117; 149) to the number n1 of gear teeth in the first gear part (61; 115; 147) in the first pinion gear (57; 111; 145). A torque divider as claimed in claim 1 or in claim 2, wherein in the first side gear (11; 79; 151) the pitch radius R1 is smaller than the pitch radius R2 of the second side gear (13; 81; 141), and in the second pinion gear (59; 113; 137) the ratio of the pitch radius r2 of the second gear part (69; 123; 139) to the pitch radius r1 of the first gear part (67; 121; 143) is smaller than the ratio of the pitch radius r2 of the second gear part (63; 117; 149) to the pitch radius r1 of the first gear part (61; 115; 147) in the first pinion gear (57; 111; 145). A torque divider as claimed in claim 1, wherein the shaft (65; 119) is located around the second side gear (13; 81), and the second side gear (13; 81) is located axially between the first side gear (11; 79) and the first gear parts (61, 67; 115, 121). A torque divider as claimed in claim 5, wherein the first and second gear parts (67, 69; 121, 123) of the second pinion gear (59; 113) have the same number of gear teeth. A torque divider as claimed in claim 2, wherein the shaft is located around the first side gear (151), and the first side gear (151) is located axially between the second side gear (141) and the first gear parts (143, 147). A torque divider as claimed in claim 7, wherein the first and second gear parts (147,149) of the first pinion gear (145) have the same number of gear teeth. A torque divider as claimed in claim 1 or claim 2, wherein the frictional force generated between the first and second supporting holes (53, 55; 107, 109) and the first and second pinion gears provide a torque proportional differential limiting function. A torque divider as claimed in claim 9 which further comprises a rotational speed proportion type differential limiting device inside the case.

Inventors: TERAOKA MASAO, TERAOKA, MASAO, TERAOKA, MASAO, C/O TOCHIGIFUJISANGYO K.K.
Applicants: TOCHIGI FUJI SANGYO KK, TOCHIGIFUJISANGYO KABUSHIKI KAISHA
Application year: 1993
Main classification: F16H48
IPC codes: F16H1, F16H48