GB2235502A - Differential gear apparatus and limiting mechanism having altered spline spacing - Google Patents
Differential gear apparatus and limiting mechanism having altered spline spacing Download PDFInfo
- Publication number
- GB2235502A GB2235502A GB9016930A GB9016930A GB2235502A GB 2235502 A GB2235502 A GB 2235502A GB 9016930 A GB9016930 A GB 9016930A GB 9016930 A GB9016930 A GB 9016930A GB 2235502 A GB2235502 A GB 2235502A
- Authority
- GB
- United Kingdom
- Prior art keywords
- spline
- differential gearing
- output shaft
- limiting
- differential
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D35/00—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion
- F16D35/005—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with multiple lamellae
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/26—Arrangements for suppressing or influencing the differential action, e.g. locking devices using fluid action, e.g. viscous clutches
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H2048/382—Methods for manufacturing differential gearings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
A differential gear apparatus comprises a differential gearing limiting mechanism and a differential gearing mechanism (2) including an input element (5) and an output element (8a), an output shaft (9a) spline-connected (S1 and S2) at an end of the output shaft to the output element (8a), and a differential gearing limiting mechanism (3) including a first (10) and a second differential gearing limiting element (11). The first differential gearing limiting element (10) is spline-connected (S3 and S4) to an intermediate portion of the output shaft (9a), and the second differential gearing limiting element (11) is spline-connected (S5 and S6) to the input element (5), both or either one of following two relationships is established: distances between a position of a tip end of a spline at an end of the output shaft and the tip end of splines of the second gearing limiting element (A) and the intermediate portion of the output shaft (C) are set larger than distances between a position of rear end of a spline of the output shaft and positions of splines of the input element (B) and the first differential gearing limiting element (D). This is to overcome disadvantages in assembling of the differential gear apparatus owing to the cocurrent rotation of the output shaft (9a) and the output element (8a). <IMAGE>
Description
DIFFERENTIAL GEAR APPARATUS WITH DIFFERENTIAL
GEARING LIMITING MECHANISM
The present invention relates to a differential gearing apparatus for an automobile- and trove particularly to a differential gear apparatus with a differential gearing limiting mechanism,. catising a differential gearing mechanism including an input element and an output element coaxially disposed within the input element, an output shaft extended through the input element of the differential gearing mechanism and spline-connected at an end of the output shaft to the output element, and a differential gearing limiting mechanism including a first and a second differential gearing limiting element which are rotated relative to each other with a predetermined braking force, the first differential gearing limiting element being spline-connected to an intermediate portion of the output shaft, and the second differential gearing limiting element being spline-connected to the input element of the differential gearing mechanism.
In the accompanying drawings, Figs.1 to 3 illustrate a differential gear apparatus with a differential gearing limiting mechanism according to one embodiment of the present invention, wherein Fig.1 is a longitudinal sectional view of the differential gear apparatus;
Fig.2 is a view for illustrating a procedure of assembling the differential gear apparatus;
Fig.3 is a view for illustrating another procedure of assembling the differential gear apparatus;
Figs.4 to 6 illustrate a prior art differential gear apparatus with a differential gearing limiting mechanism, wherein Fig.4 is a longitudinal sectional view of the prior art differential gear apparatus; Fig.5 is a view for illustrating a procedure of assembling the prior art differential gear apparatus; and
Fig.6 is a view for illustrating another procedure of assembling the prior art differential gear apparatus.
There is a conventionally known differential gear apparatus of the above described type with a differential gearing limiting mechanism, for example, as described in
Japanese Patent Application Laid-open No.186051/88.
The prior art differential gear apparatus shown in
Fig.4 is comprised of a differential gearing mechanism 2 disposed within a casing 1, and a differential gearing limiting mechanism 3 disposed outside the casing 1. The mechanism 2 comprises a housing 5 as an input element including at an outer periphery thereof an input gear 4 which is connected to a transmission and is driven therethrough, a pair of planetary gears 7a and 7b carried on the housing 5 through a planetary gear shaft 6, a pair of output shafts 9a and 9b rotatably carried on the housing 5- and carrying a pair of sun gears 8a and 8b as output elements meshed with the planetary gears 7a and 7b.On the other hand, the differential gearing limiting mechanism 3 comprises a first drum-like differential gearing limiting element 10 coupled to one of the output shafts 9a, and a second differential gearing limiting element 11 extended inside the first differential gearing limiting element 10 and coupled to an extension 5a of the housing 5 which extends outwardly to pass through the.casing 1, A large number of disks 12 and 13 coupled respectively to the first and second differential gearing limiting elements 10 and 11 are opposed within the first differential gearing limiting element 10 filled with a viscous fluid, thereby providing a given braking force between the differential gearing limiting elements 10 and 11, i.e., between the output shaft 9a and the housing 5.
An end of the rotary shaft 9a and the sun gear 8a are coupled to each other through an outer tooth spline S1 and inner tooth spline S2, and an intermediate portion of the rotary shaft 9a and the first differential gearing limiting element 10 are coupled to each other through an outer tooth spline S3 and an inner tooth spline S4. In addition, the extension 5a of the housing 5 and the second differential gearing limiting element 11 are coupled to each other through an outer tooth spline 55 and an inner tooth spline
S6.
Thus, the above described differential gear apparatus has characteristics of an ability to add a differential gearing limiting mechanism to the prior art differential gear apparatus without any large modification, an ease to repair the differential gearing limiting mechanism, and an ease to change properties of the differential gearing limiting mechanism in accordance with travelling purposes.
In the above differential gear apparatus, however, following disadvantages may be encountered in assembling the differential gearing limiting mechanism 3:
(1) Employment of a procedure of previously connecting the output shaft 9a and the differential gearing limiting mechanism 3 to each other through the outer tooth spline 53 and the inner tooth spline S4 to constitute a single unit and integrally coupling this unit to the side of the differential gearing mechanism 2 through the splines S1 and S2 and the splines S5 and S6*as shown in Fig.5.
In this case, in the prior art differential gear apparatus, a distance A between a position aO of a tip end of the spline S1 at the end of the output shaft 9a and a position a1 of a tip end of the spline S6 of the second differential gearing limiting element 11 is set smaller than a distance B between a position b of a rear end of the spline S2 of the output element 8a and a position bl of a rear end of the spline S5 of the input element 5 (i.e., A < B).For this reason, if the unit is brought close to the differential gearing mechanism 2, the splines S5 and 56 are first engaged with each other (see the state of Fig.5), and then, the splines S1 and S2 are engaged with each other. Therefore, the unit comprised of the output shaft 9a and the differential gearing limiting mechanism 3 is first rotated, thereby aligning the phases of the splines S5 and S6 to achieve the engagement thereof. Then*, the unit is further moved toward the differential gearing mechanism 2 to bring the splines S1 and 52 into engagement with each other. Even in this case, alignment in phase of the splines is required. In this case, however, the unit comprised of the output shaft 9a and the differential gearing limiting mechanism 3 have been connected to each other through the splines S5 and 56 already engaged with each other and moreover, the differential gearing limiting mechanism 3 has exhibited a braking force. Therefore, even if the output shaft 9a is rotated for alignment in phase1 such rotation is transmitted to the housing 5 to cause the sun gear 8s supported within the housing 5 to be rotated in the same phase, so that the alignment in phase of the splines S1 and S2 cannot be achieved for ever.Accordingly, in this case, it is required that the other output shaft 9b be previously connected to the sun gear 8b, so that the output shaft 9a and the sun gear 8a are relatively rotated by temporarily applying a load to the output shaft 9b, or the housing 5 is fixed and prevented from being rotated, so that the output shaft 9a and the sun gear 8a are relatively rotated, thus providing alignment of their phases.For this reason, the prior art apparatus has disadvantages that in the former case, not only the assembling procedure is limited, but also an extra operation is required and in the latter case, not only an extra operaiton is required, but also a great amount of force is required to rotate the output shaft 9a against the braking force of the differential gearing limiting mechanism 3.
(2) Employment of a procedure of previously connecting the housing 5 and'the differential gearing limiting mechanism 3 to each other through the outer tooth spline 5.5 and the inner tooth spline S6 to constitute a single unit and inserting the output shaft 9a into the unit, thereby bringing the splines S1 and 52 and the splines S3 and S4 into engagement with each other as shown in Fig. 6.
In this case, in the above-described prior art differential gear apparatus, a distance C between the position aO of the tip end of the spline S1 at the end of the output shaft 9a and a position a2 of a tip end of the spline S3 at the intermediate portion of the output shaft 9a is set smaller than a distance D between the position b of the tip end of the spline S2 of the output element 8a and a position b2 of a rear end of the spline 54 of the first differential gearing limiting element 10 (i.e., C < D).For this reason, if the output shaft 9a is inserted, the splines S3 and S4 are first engaged with each other (see the state of Fig.6) and then, the splines S1 and S2 are engaged with each other. Therefore, the output shaft 9a is first rotated, thereby aligning the phases of the splines 53 and 54 to achieve the engagement thereof and then, the rotary shaft 9a is further inserted to bring the splines S1 and S2 into engagement with each other. Even in this case, alignment of the splines S1 and S2 is required.
However, because the output shaft 9a and the housing 5 have been already connected to each other through the splines S3 and S4 as well as splines S5 and S6 as in the above case, even if the output shaft 9a is rotated for alignment, such rotation is transmitted to the housing 5 to cause the sun gear 8a carried within the housing 5 to be rotated in the same phase, so that the alignment of the splines S1 and 52 cannot be achieved for ever.Therefore, even in this case, it is required that the other output shaft 9b be previously connected to the sun gear 8b, so that the output shaft 9a and the sun gear 8a are relatively rotated by temporarily applying a load to the output shaft 9b, or the housing 5 is fixed and prevented from being rotated, in order that the output shaft 9a and the sun gear 8a are relatively rotated, thus providing alignment of their phases. This results in an extremely complicated assembling thereof.
The present invention has been accomplished with the above circumstances in view, and it is an object of the present invention to improve the assemblability of a differential gear apparatus of the type described above only by providing a slight modification to the construction of the above described prior art differential gear apparatus.
To achieve the above object, a first feature of the present invention resides in that a distance between a position of a tip end of a spline at an end of the output shaft and a position of a tip end of a spline of the second differential gearing limiting element is set larger than a distance between a position of a rear end of a spline of the output element and a position of a rear end of a spline of the input element.
Owing to the first feature of the present invention, when a unit comprised of the output shaft and the differential gearing limiting mechanism coupled to each other is assembled to the differential gearing mechanism, the spline at the tip end of the output shaft is first engaged with the spline of the output element of the differential gearing mechanism and then, the spline of the second differential gearing limiting element of the differential gearing limiting mechanism is engaged with the spline of the input element of the differential gearing mechanism.Therefore, the unit is rotated, whereby the spline at the tip end of the output shaft is first aligned in phase with the spline of the output element of the differential gearing mechanism for engagement with each other and then, the spline of the second differential gearing limiting element of the differential gearing limiting mechanism is aligned in phase with the spline of the input element of the differential gearing mechanism. In the latter alignment in phase, the input element,of the differential gearing mechanism cannot be rotated with the rotation of the unit. This makes it possible to easily achieve the alignment in phase and the engagement of the splines.
In addition, a second feature of the present invention resides in that a distance between a position of a tip end of a spline at an end of the output shaft and a position of a tip end of a spline at the intermediate portion of the output shaft is set larger-than a distance between a position of a rear end of the output element and a position of a rear end of a spline of the first differential gearing limiting element.
Owing to the second feature of the present invention, when the output shaft is inserted into and assembled to the unit comprised of the differential gearing mechanism and the differential gearing limiting mechanism coupled to each other, the spline at the tip end of the output shaft is first engaged with the spline of the output element of the differential gearing mechanism and then, the spline at the intermediate poriton of the output shaft is engaged with the spline of the first differential gearing limiting element of the differential gearing limiting mechanism.
Therefore, the output shaft is rotated, whereby the spline at the tip end of the output shaft is first aligned in phase and engaged with the spline of the output element of the differential gearing mechanism and then, the spline of the intermediate poriton of the output shaft is aligned in phase with the spline on the first differential gearing limiting element of the differential gearing mechanism. In the latter alignment, the spline of the first differential gearing limiting element of the differential gearing limiting mechanism cannot be rotated with the rotation of the output shaft. This permits the alignment in phase and the engagement of the splines to be easily achieved.
Further, a third feature of the present invention resides in that a distance between a position of a tip end of a spline at an end of the output shaft panda position of a tip end of a spline of the second differential gearing limiting element is set larger than a distance between a position of a rear end of a spline of the output element and a position of a rear end of a spline of the input element, and a distance between the position of the tip end of the spline at the end of the output shaft and a position of a tip end of a spline at the intermediate portion of the output shaft is set larger than a distance between the position of the rear end of the spline of the output element and a position of a rear end of a spline of the first differential gearing limiting element.
Owing to the third feature, even if any of the above-described assembling procedures is employed, the rotation of the splines to be engaged can be regulated, permitting the alignment in phase and the engagement of the splines to be easily achieved.
The present invention will now be described by way of one embodiment with refernce to Figs.1 to 3.
In this embodiment, parts or components corresponding to those in the prior art differential gearing apparatus previously described in detail with reference to Figs.4 to 6 are designated by the same reference numerals and characters.
Referring to Fig.11 a differential gear apparatus of the embodiment comprises a differential gearing mechanism 2 and a differential gearing limiting mechanism 3 both having the substantially same constructions as of the above described prior art differential gearing apparatus. As in the prior art differential gearing apparatus, one of output shafts 9a is engaged at an end thereof with a sun gear 8a as an output element of the differential gearing mechanism 2 through an outer tooth spline S1 and an inner tooth spline 52 and is connected at an intermediate portion thereof to a first differential gearing limiting element 10 of the differential gearing limiting mechanism 3 through an outer tooth spline S3 and an inner tooth spline 54.Further, an extension 5a of a housing 5 which is an input element of the differential gearing mechanism 2 is connected to a second differential gearing limiting element 11 of the differential gearing limiting mechanism 3 through an inner tooth spline 55 and an outer tooth spline 56.
Thus, the differential gear apparatus is characterized in that a distance A between a position a of a tip end of the spline S1 at the end of the output shaft 9a and a position a1 of a tip end of the spline S6 of the second differential gearing limiting element 11 is set larger than a distance B between a position b of a rear end of the spline 52 of the sun gear 8a and a position b1 of a rear end of the spline S5 of the housing 5, and in that a distance C between the position aO of the tip end of the spline S1 at the end of the output shaft 9a and a position a2 of a tip end of the spline S3 at the intermediate portion of the output shaft 9a is set larger than a distance D between the position bo of the rear end of the spline 52 of the sun gear 8a and a position b of a rear end of the spline S4 of
2 the first differential gearing limiting element 10.
The operation of the embodiment of the present invention having the above construction will be described below.
(3) Employment of a procedure of previously connecting the output shaft 9a with the differential gearing limiting mechanism 3 through the outer tooth spline S3 and the inner tooth spline S4 to constitute a single unit and integrally coupling this unit to the side of the differential gearing mechanism 2 through the splines S1 and S2 and the spline S5 and 56, as shown in Fig.2.
In this case, because the distance A between the position a of the tip end of the spline S1 and the
0 position a1 of the tip end of the spline S6 is set larger than the distance B between the position b of the rear end of the spline S2 and the position b1 of the rear end of the spline 55 (i.e., A > B), if the unit is brought close to the differential gearing mechanism 2 as shown in
Fig.2, the splines S1 and S2 are first engaged (see the state shown in Fig.2), and subsequently, the splines S5 and S6 are engaged.Therefore, the unit comprised of the output shaft 9a and the differential gearing limiting mechanism 3 is first rotated to align the phases of the splines S1. and
S2, thus achieving their mutual engagement.
At this time, the splines S5 and S6 are still not engaged and hence, the rotation of the unit is not transmitted to the sun gear 8a through the housing 5. Accordingly, the engagement of the splines Sl and S2 is easily achieved. Then, the unit is further moved toward the differential gearing mechanism 2, thereby allowing the spline S5 to be engaged with the spline 56. In this case, if the unit, i.e., the output shaft 9a is rotated, the sun gear 8a is rotated by the splines S1 and 52 already engaged with each other. However, such rotation only causes a planetary gear 7a and another sun gear 8b to be rotated, and the housing 5 is maintained stationary. Therefore, the inner tooth spline S5 formed on the extension 5a of the housing 5 and the outer tooth spline S6 formed on the second differential gearing element 11 are relatively rotated and aligned in phases and thus, the engagement of the splines S5 ans S6 is achieved.
(4) Employment of a procedure of previously connecting the differential gearing limiting mechanism 3 with the housing 5 through the inner tooth spline S5 and the outer tooth spline S6 to constitute a single unit and inserting this unit into the output shaft 9a for their engagement through the splines S1 and 52 and the splines S3 and S4, as shown in
Fig.3.
In this case, because the distance C between the position aO of the tip end of the spline S1 and the position a2 of the tip end of the spline S3 is set larger than the distance D between the position b of the rear end of the spline S2 and the position b2 of the rear end of the spline 54 (i.e., C > D), if the output shaft 9a is inserted as shown in Fig. 3, the splines S1 and S2 are first engaged with each other (see the state of Fig.3) and then, the splines S3 and 54 are engaged with each other.Therefore1 the output shaft 9a is first rotated, thereby allowing the splines S1 and S2 to be aligned in phase and engaged with each other. Then, the rotary shaft 9a is further inserted to provide the engagement of the splines 53 and S4. Even in this case, the alignment in phases of the splines S3 and S4 is required. However, the rotation of the output shaft 9a is absorbed by the sun gears 8a and 8b and the planetary gears 7a and 7b without transmission toward the differential gearing mechanism 3 and hence, the alignment in phases and the engagement of the splines 53 and S4 are easily per formed.
It should be noted that because A > B and C > D in the above embodiment, the two types of assembling procedures can be used for the same arrangement. More specifically,. the former assembling procedure can be employed in the first assembling and thereafter, the output shaft 9a can be easily removed by the latter assembling procedure for repair or replacement of the output shaft 9a.
Claims (4)
1. A differential gear apparatus with a differential gearing limiting mechanism, comprising a differential gearing mechanism including an input element and an output element coaxially disposed within the input element, an output shaft extended through the input element of the differential gearing mechanism and spline-connected at an end thereof to the output element, and a differential gearing limiting mechanism including a first and a second differential gearing limiting element which are rotatable relative to each other with a predetermined braking force1 the first differential gearing limiting element being spline-connected to an intermediate portion of the output shaft, the second differential gearing limiting element being spline-connected to the input element of the differential gearing mechanism, wherein
a distance between a position of a tip end of a spline at the end of the output shaft and a position of a tip end of a spline of the second differential gearing limiting element is set larger than a distance between a position of a rear end of a spline of the output element and a position of a rear end of a spline of the input element.
2. A differential gear apparatus with a differential gearing limiting mechanism, comprising a differential gearing mechanism including an input element and an output element coaxially disposed within the input element, an output shaft extended through the input element of the differential gearing mechanism and spline-connected at an end thereof to the output element, and a differential gearing limiting mechanism including a first and a second differential gearing limiting element which are rotatable relative to each other with a predetermined braking force, the first differential gearing limiting element being spline-connected to an intermediate portion of the output shaft, the second differential gearing limiting element being spline-connected to the input element of the differential gearing mechanism, wherein
a distance between a position of a tip end of a spline at the end of the output shaft and a position of a tip end of a spline at the intermediate portion of the output shaft is set larger than a distance between a position of a rear end of a spline of the output element and a position of a rear end of a spline of the first differential gearing limiting element.
3. A differential gear apparatus with a differential gearing limiting mechanism, comprising a differential gearing mechanism including an input element and an output element coaxially disposed within the input element, an output shaft extended through the input element of the differential gearing mechanism and spline-connected at an end thereof to the output element, and a differential gearing limiting mechanism including a first and a second differential gearing limiting element which are rotatable relative to each other with a predetermined braking force, the first differential gearing limiting element being spline-connected to an intermediate portion of the output shaft, the second differential gearing limiting element being spline-connected to the input element of the differential gearing mechanism, wherein
a distance between a position of a tip end of a spline at the end of the output shaft and a position of a tip end of a spline of the second differential gearing limiting element is set larger than a distance between a position of a rear end of a spline of the output element and a position of a rear end of a spline of the input element, and a distance between the position of the tip end of the spline at the end of the output shaft and a position of a tip end of a spline at the intermediate portion of the output shaft is set larger than a distance between the position of the rear end of the spline of the output element and a position of a rear end of a spline of the first differential gearing limiting element.
4. A differential gear apparatus substantially as hereinbefore described with reference to Figures 1 & 3 of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989091965U JPH083735Y2 (en) | 1989-08-04 | 1989-08-04 | Differential device with differential limiting mechanism |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB9016930D0 GB9016930D0 (en) | 1990-09-19 |
| GB2235502A true GB2235502A (en) | 1991-03-06 |
| GB2235502B GB2235502B (en) | 1993-06-16 |
Family
ID=14041263
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB9016930A Expired - Fee Related GB2235502B (en) | 1989-08-04 | 1990-08-02 | Differential gear apparatus with differential gearing limiting mechanism |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH083735Y2 (en) |
| GB (1) | GB2235502B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0511068A1 (en) * | 1991-04-26 | 1992-10-28 | Glaenzer Spicer | Differential and viscous clutch transmission device particularly for motor vehicles |
| DE102005004290A1 (en) * | 2005-01-28 | 2006-08-10 | Gkn Driveline International Gmbh | Transmission module for variable torque distribution |
| WO2007133418A3 (en) * | 2006-05-01 | 2008-01-31 | Getrag Corp | Independently mounted electronic limited slip device for vehicle |
| EP1927498A1 (en) * | 2006-12-01 | 2008-06-04 | GKN Driveline International GmbH | Drive assembly with intermediate shaft and coupling unit |
| US7713159B2 (en) | 2006-04-10 | 2010-05-11 | Gkn Driveline Torque Technology Kk | Power transmitting apparatus |
| US10113629B2 (en) * | 2016-12-02 | 2018-10-30 | Caterpillar Inc. | Side pinion differential locking mechanism |
| EP3412934A4 (en) * | 2016-09-28 | 2019-08-28 | Komatsu Ltd. | Power transmission device |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4976577B1 (en) * | 2011-08-03 | 2012-07-18 | 藤田 啓一 | Ventilation equipment |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0265297A1 (en) * | 1986-09-19 | 1988-04-27 | Glaenzer Spicer | Differential transmission device, particularly for motor vehicles |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61136043A (en) * | 1984-12-04 | 1986-06-23 | Tochigi Fuji Ind Co Ltd | Power distributing device |
-
1989
- 1989-08-04 JP JP1989091965U patent/JPH083735Y2/en not_active Expired - Fee Related
-
1990
- 1990-08-02 GB GB9016930A patent/GB2235502B/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0265297A1 (en) * | 1986-09-19 | 1988-04-27 | Glaenzer Spicer | Differential transmission device, particularly for motor vehicles |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0511068A1 (en) * | 1991-04-26 | 1992-10-28 | Glaenzer Spicer | Differential and viscous clutch transmission device particularly for motor vehicles |
| US5338266A (en) * | 1991-04-26 | 1994-08-16 | Glaenzer Spicer | Differential transmission device and viscous coupler, especially for a motor vehicle |
| DE102005004290A1 (en) * | 2005-01-28 | 2006-08-10 | Gkn Driveline International Gmbh | Transmission module for variable torque distribution |
| DE102005004290B4 (en) * | 2005-01-28 | 2006-11-02 | Gkn Driveline International Gmbh | Transmission module for variable torque distribution |
| US7713159B2 (en) | 2006-04-10 | 2010-05-11 | Gkn Driveline Torque Technology Kk | Power transmitting apparatus |
| DE102007016599B4 (en) * | 2006-04-10 | 2012-09-20 | Gkn Driveline Torque Technology Kk | Power transmission device |
| WO2007133418A3 (en) * | 2006-05-01 | 2008-01-31 | Getrag Corp | Independently mounted electronic limited slip device for vehicle |
| US7815538B2 (en) | 2006-05-01 | 2010-10-19 | Getrag Corporation | Independently mounted electronic limited slip device for vehicle |
| US8105197B2 (en) | 2006-05-01 | 2012-01-31 | GKN Driveline Newton, LLC | Independently mounted electronic limited slip device for vehicle |
| EP1927498A1 (en) * | 2006-12-01 | 2008-06-04 | GKN Driveline International GmbH | Drive assembly with intermediate shaft and coupling unit |
| US7846056B2 (en) | 2006-12-01 | 2010-12-07 | Gkn Driveline International Gmbh | Drive assembly with intermediate shaft and coupling unit |
| EP3412934A4 (en) * | 2016-09-28 | 2019-08-28 | Komatsu Ltd. | Power transmission device |
| US10113629B2 (en) * | 2016-12-02 | 2018-10-30 | Caterpillar Inc. | Side pinion differential locking mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH083735Y2 (en) | 1996-01-31 |
| GB2235502B (en) | 1993-06-16 |
| JPH0330642U (en) | 1991-03-26 |
| GB9016930D0 (en) | 1990-09-19 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 20000802 |