CN103133632A - Spur gear differential and manufacturing method thereof - Google Patents
Spur gear differential and manufacturing method thereof Download PDFInfo
- Publication number
- CN103133632A CN103133632A CN2012105101936A CN201210510193A CN103133632A CN 103133632 A CN103133632 A CN 103133632A CN 2012105101936 A CN2012105101936 A CN 2012105101936A CN 201210510193 A CN201210510193 A CN 201210510193A CN 103133632 A CN103133632 A CN 103133632A
- Authority
- CN
- China
- Prior art keywords
- planetary
- gear
- planetary carrier
- spur
- 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.)
- Pending
Links
Images
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
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet 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
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun 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
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H2048/382—Methods for manufacturing differential gearings
Abstract
The invention relates to a cylindrical gear differential (1) for a vehicle drive train. The differential (1) has a planetary carrier (3), and sun wheels (5, 6) comprising respective external teeth and arranged at the planetary carrier. The sun wheels are combed with respective input wheels that are designed as planetary wheels. The planetary wheels are connected with one another, and an axial drive wheel (14) is arranged radially at an outer side of the carrier. A rotational torque-transferring connection (17) e.g. force-fit connection and/or welded connection, is formed between an inner surface (15) of the drive wheel and a radial peripheral surface (13) of the carrier. An independent claim is also included for a method for manufacturing a spur gear differential.
Description
Technical field
The present invention relates to a kind of spur-gear differential of the power train for automobile, this spur-gear differential has planetary carrier, be furnished with two sun gears that have separately external tooth in this planetary carrier, this sun gear separately be constituted as the engagement of planetary differential gear, wherein these two mutual shapes of planetary pinion are sealed, and are provided with in addition the shaft drive wheel that roughly radially is arranged in outside planetary carrier.
Background technique
The known spur-gear differential that One's name is legion is arranged in the prior art:
DE102007004709A1 discloses for example a kind of spur-gear differential, this spur-gear differential has at least one main shaft, this main shaft be used for by at least three each free the first row star gears and the second planetary pinion form to torque distribution to the first differential member and the second differential member, wherein a pair of planetary pinion opposed and effective connection mutually.In this case, planetary pinion and sun gear are configured and are arranged by the following stated.
Each planetary pinion of a is to having two planetary pinions, and these two planetary pinions preferably are designed to similar in the same manner.
The b planetary pinion has separately the non-engaging piece section of Outer cylindrical and longitudinally has in addition the engaging piece section.
The radially outside dimension of the non-engaging piece section of c for example outer radius is for example compared little than the minimum as far as possible radially outermost dimension of engaging piece section with Outside radius.In this case, the external diameter of non-engaging piece section is less than the tooth top diameter of engaging piece section, the preferred root diameter that still is equal to or less than the engaging piece section.
The planetary engaging piece section that d is concerned is constituted as cylindrical gears, spur gear, helical gear, wedge shape gear or spiral gear.
The planetary each side of e or sit on independent planetary bolt, or be incorporated on two axle journals or self have two axle journals that axially stretch out from planetary pinion.
F planetary bolt and with the planetary pinion of axle journal or the planetary pinion on axle journal in both sides are placed in housing or on housing.
The axle journal that each planetary pinion of g alternately is contained therewith or single part ground is configured together with the sheet material housing, or be incorporated in this sheet material housing as independent member.
H is as to the substituting of the above-mentioned enforcement of planetary bearing, and single part or multipart axle journal list material ground are configured or are fixed on individually the element on separately planetary pinion together with planetary pinion.
The i planetary pinion is placed in this case or rotatably on axle journal or around bolt axis or together with bolt and is placed on planetary bolt.
The planetary non-engaging piece section of j is longitudinally directed in opposite directions, makes the end face of non-engaging piece section longitudinally point to separately the outside, is preferably used for planetary bolt is placed in housing.
The a pair of planetary each side of k separately with the opposing party's on longitudinal direction, outside branch's section of placing is engaged on two differential members of differential mechanism on planetary pinion of its engaging piece section gear in.
L also can be called as section's section of the outside of outer branch section placing and be concerned ground on planetary longitudinal direction, that is to say with bolt axis aligning ground all the way move forward to of gear branch's section placed in the middle on longitudinal direction from a planetary end.
M planetary pinion separately is engaged with half of width that scope in the internal tooth of differential member or the outer branch section in external tooth preferably is equivalent to the gear on the longitudinal direction of engaging piece section.
The gear of that the differential member in two differential members of n contactlessly is embedded in the circumference space of a pair of planetary pinion each side that is configured around non-engaging piece section separately diametrically and in the axial direction, that differential member and outer branch section engagement with a pair of other planetary gear.
Branch's paragraph qualification placed in the middle that o circumference space is axially placed by vertical inside of gear on a longitudinal direction, and for example limit by housing or by being used for planetary another axial stop on another longitudinal direction.
Keep intermeshing on branch's section placed in the middle of each comfortable engaging piece section of a pair of planetary pinion of p.
Q branch's section placed in the middle is between the outer branch section that is formed in gear on longitudinal direction and non-engaging piece section.
The type selecting of the gear of r outer portion part and size can continue on section's section placed in the middle, substitute but can be also other.
The s planetary pinion is width second half of width of the gear on the longitudinal direction of engaging piece section preferably of branch's section placed in the middle at engaged place mutually.
The every differential mechanism of t is furnished with at least three but preferably four or five planetary pinions pair.
In this case, longitudinal direction is consistent with bolt axis.Draw from this feature:
The required overall width of the engaging piece section of u planetary pinion each side preferably with planetary pinion keep the tooth engagement differential member width and with a pair of planetary pinion width sum of branch's section of pitch wheel with it, also comprise making, installing or be designed at most interval, stage, spacing holder of condition and the like.
The required width of the planetary non-engaging piece section of v preferably is equivalent to and width with the gear of the differential member of a pair of other planetary pinion engagement, also comprises making, installing or be designed at most interval, stage, spacing holder of condition and the like.
The gear of the differential member of w is as far as possible so wide is embedded in the circumference space, makes differential member and the planetary pinion of being correlated with does not just in time also contact.
The facewidth degree of the tooth of the intermeshing member of the differential mechanism of introducing in DE102007004709A1 engagement use is than common outside dimensions is wide thitherto, because planetary pinion is mutually and with differential member not have further axial air gap ground nested in couples.Higher moment of torsion is transferable.Planetary pinion is not on the vertical planetary carrier that medially is disposed in differential mechanism that is placed in separately, but is placed in the both sides of just carrying out the housing of function as planetary carrier.Replace only axle journal by two axle journals, structure is more rigid and more little easy overturning and so more little shortcoming that easily has because of the overturning generation.
Epicyclic transmission mechanism is to can more closely being moved each other at circumference, because on the one hand the load of each planet wheel is distributed in housing or two bearing portions separately on housing, and shell construction itself is that the discoidal planetary carrier of the layout placed in the middle that is made of sheet material is more stable than it on the other hand.Must circumference between each bearing portion for blocking materials for structure space few.The axial arrangement space that needs for the planetary carrier of arranging placed in the middle is because the bearing in housing is cancelled.Gear can be implemented around this quantity is additional widelyr.Therefore also can dwindle again contact radius and can employ than the layout of rigidity and the structure that therefore not too easily produces distortion.The manufacturing of this epicyclic transmission mechanism is lower-cost, because cancelled the manufacturing of the high ring gear of cost.For example the interior processing of internal gear is that cost is high.
DE102007004712A1 discloses a kind of spur-gear differential equally, this spur-gear differential have a two-part at least housing and have one be fixed on this housing and together with this housing for the concentric drive wheel of the rotatingshaft of spur-gear differential, wherein the fixing part section of the first shell part and the second shell part and drive wheel axially is fixed each other by fixed mechanism, and in this case in a circumferential direction mutually antagonism be directed into rotationally on shell part and drive wheel, and be fixed each other for rotatingshaft.
WO2011/003747A2 also discloses a kind of spur-gear differential, this spur-gear differential has the first sun gear and the second sun gear, wherein distribute first group of planetary pinion and distribute second group of planetary pinion to the second sun gear to the first sun gear, and first group of planetary pinion and second group of planetary pinion engagement, and in this case, the number of teeth of the first sun gear equates with the number of teeth of the second sun gear, the tooth that wherein is shifted the first sun gear by profile of tooth is arranged on the top circle with tip diameter, this tip diameter is different from the tip diameter that the tooth of the second sun gear is arranged the top circle on it, wherein first group of planetary pinion only with the first sun gear engagement and wherein second group of planetary pinion only with the second sun gear engagement, wherein the tip diameter of the top circle of the tooth of the first sun gear is implemented by positive profile of tooth displacement in addition, and the tip diameter of the top circle of the tooth of the second sun gear is implemented by negative profile of tooth displacement.
DE102007040475A1 also discloses a kind of spur-gear differential, spur-gear differential especially for automobile, this spur-gear differential has transmission component, this transmission component is anti-to be connected with planetary carrier rotationally, wherein be furnished with rotationally at least one pair of intermeshing planetary carrier in planetary carrier, wherein planetary carrier separately with the engagement of the follower of an engagement.In order to be used for planetary enough structure spaces in the situation that this spur-gear differential forms one, what DE102007040475A1 stipulated is, planetary carrier by two at a certain distance a) the discoidal carrier of arranging that is parallel to each other form, these two carriers are connected with transmission component.Disclosedly be, two followers have a corrugated part section separately, and this corrugated part section is axially outstanding from the protuberance of the sleeve shape of discoidal carrier.
The special nature of spur-gear differential as from known the document of above-mentioned discussion, is also the basis of the present invention that proposes here.
Be used for having lay in it differential gear for example the connection solution of the shaft drive wheel of the shell of bevel gear be also known.
therefore DE10013429C5 discloses a kind of differential mechanism, this differential mechanism has the differential casing that is made of cast iron and the disk gear that is made of case-hardened steel, wherein differential casing has one with the supporting shoulder of outer side surface on the pressurized circumference on it of disk gear, this supporting shoulder radially is arranged in the symmetry axis of disk gear, wherein differential casing and disk gear are made under the application of nickeliferous additional materials by one, weld seam with respect to the same radial arrangement of symmetry axis of disk gear is connected between supporting shoulder and disk gear mutually, wherein disk gear is not to be produced by peeling off at least in part the face that is used for welding to be welded specially.
In addition from the application of the known longitudinal ream of DE102004034736A1, but be in the situation that bevel differential.The there has proposed a kind of differential mechanism for axletree, and this differential mechanism comprises differential carrier and differential cover, and this differential carrier is connected with disk gear with differential cover, and in this differential mechanism, differential carrier is connected by longitudinal ream with disk gear with differential cover.
Also known a kind of for the method with the welding of the differential casing of disk gear and speed changer from DE102005023230A1.the there discloses a kind of method for the differential casing of disk gear and speed changer is welded, carry out in the method following steps: make disk gear, wherein disk gear has one with the disk gear flange of flange surface, surface sclerosis disk gear, the differential casing that casting is made of cast iron materials, wherein differential casing has the flange shoulder, process flange by rotation and take on to make the differential casing flange, bond pad generating gear and differential casing, wherein disk gear is pressed against the flange shoulder with its flange surface, by high energy beam, disk gear flange and flange shoulder are welded, wherein supply with a kind of nickeliferous additional materials during the welding process of welding zone.The flange shoulder has following flange scope: the web that extends on the circumferencial direction of flange shoulder, and its end face is attached on the flange surface of disk gear flange after engaging; Radially be positioned at the flange surface outside web, this flange surface occurs from the end face of web, is positioned at the back of end face of web and this flange surface and is forming the first gap after engaging together with the flange surface of disk gear flange; And radially being positioned at groove within web, that extend on the circumferencial direction of flange shoulder, this groove is forming the second gap after engaging together with the flange surface of disk gear flange.
Unfortunately, the shortcoming that bevel differential has is that bevel differential has large structure space demand.The lightweight differential mechanism of being submitted to by the applicant provides a kind of solution at this.This lightweight differential mechanism that is constituted as spur-gear differential should be in the situation that only need a small amount of structure space that effective engagement is provided.And so-called
The shortcoming that design is in known situation, particularly in the situation that spin and be riveted on this design of using in the scope of standard pitch circle of planetary gear bearing should be eliminated.And be different from so-called
In the situation of differential mechanism, should use the sun gear of outer gearing.Should avoid planetary pinion is placed in frame sheet material.
Summary of the invention
This task a kind of such spur-gear differential used according to the invention is completed like this,, is provided with the link of transmitting torque between the circular radial side face of the inner face of shaft drive wheel and planetary carrier that is.
So can use two discoidal housing structures to consist of planetary carrier, wherein the reprocessing of welding is preset.Can use thus the planetary pinion pair more than three, because no longer need be used to the structure space that is applied between planetary pinion.Also can employ if possible known bolt and use, to realize the add-on security between planet gear mesh and planetary carrier, exist but a kind of ratio occurs
The design of weakness slightly in the situation of design.
Preferred embodiment advocated in the dependent claims and further set forth at following quilt.
Therefore tool is advantageous is that link is constituted as the link of material and/or shape and/or force closure.Spur-gear differential have only a small amount of torque capability design conditions under, only wherein a kind of scheme is just enough, and in the situation that the combination of the design requirement of higher load is that tool is advantageous.
Therefore for example tool is advantageous is, link be designed to punching press connection piece and/or ca(u)lk connection piece and/. or be welded to connect part.And, in the time should transmitting extra high moment of torsion, can use the combination with the sealed link of shape.
The advantageous embodiment of tool is characterised in that, planetary carrier partly is comprised of at least two planetary carriers, this planetary carrier part preferably is constituted as half planetary carrier, wherein in two planetary carriers parts only one or two planetary carriers partly have the link of transmitting torque.
Can abandon riveted joint, wherein particularly the sealed link of shape and joint filling combination is particularly well suited to axial safety.
What meet especially purpose is that two planetary carriers partly have the radially extension of different sizes.So spur-gear differential is designed with can meeting specific (special) requirements.
Have if only have the link that the large planetary carrier that radially extends partly has transmitting torque, can reduce costs so.Also have yet tool is advantageous, two planetary carrier parts all have the link of transmitting torque, because can keep so symmetrical power to import, this is to producing positive influences working life.
In order to transmit extra high moment of torsion, tool is advantageous is, the link of transmitting torque extends on total circumference of at least one planetary carrier part, and namely 360 ° of extensions are preferably extended on total circumference of two planetary carrier parts.Just welding and extruding to be combined in this be that tool is advantageous.
The invention still further relates to a kind of method for the manufacture of this spur-gear differential, the method comprises the step of planetary carrier in the inner face welding of its circumference and shaft drive wheel.
Tool is advantageous in this case is, before welding, with respect to bearing support preferably by the external tooth of grinding process machining shaft drive wheel.And in principle can be with respect to the external tooth of bearing support machining shaft drive wheel after welding.The general construction assembly can be installed thus and lapping gears externally after welding.
If particularly after concentrating cleaning, the member that is in planetary carrier is installed after grinding process, also complete thus differential mechanism, can employ so especially effectively installation procedure.
Also will should be mentioned that, tool is advantageous is, there is interval more closely in differential planetary gear train namely planetary top circle apart from the root diameter of the gear of shaft drive wheel, namely the modulus of five times or maximum six times for example.
Half planetary carrier also can be called as the housing halfliner.
Tool is advantageous in addition is, the top circle of differential planetary gear train has the modulus of more than times apart from the largest interval of the root diameter of shaft drive wheel.
Tool is advantageous in addition is, differential gear obtain one 〉=3.0 value in the excircle of millimeter divided by the overall width in millimeter of differential mechanism.Differential axle is that tool is advantageous in the inner space of staying shaft drive wheel, in any case because the differential design assembly is designed to be all narrow than drive wheel in view of its axial arrangement space in a preferred version.
Description of drawings
And following by accompanying drawing elaboration the present invention, illustrate in greater detail in the accompanying drawings two embodiments.In the accompanying drawings:
Fig. 1 is the spur-gear differential that has discoidal housing parts according to of the present invention, and wherein planetary carrier is made of two-part, and these two-part have same radially extension; And
Fig. 2 be spur-gear differential second embodiment of the invention, one of them planetary carrier partly has the radially extension larger than another planetary carrier part.
Embodiment
Accompanying drawing is only illustrative nature and only is used for understanding the present invention.Similar elements is had same reference character.
With the longitudinal section, almost complete spur-gear differential is shown in Fig. 1, and with the longitudinal section, only cross section according to spur-gear differential of the present invention is shown in Fig. 2.
The first mode of execution according to spur-gear differential 1 of the present invention shown in Figure 1.This spur-gear differential 1 is used in the power train of automobile, for example car, truck, bus or box car.Such automobile has internal-combustion engine usually, but also can be used as alternative or have as a supplement motor.
Spur-gear differential 1 has planetary carrier 2, and this planetary carrier 2 has the first row gear rack part 3 and the second planetary carrier part 4, and they consist of planetary carrier together.In embodiment shown here, two planetary carrier parts 3 and 4 consist of along mold joint symmetrically.Also be furnished with respectively sun gear 5 and 6 within planetary carrier on the both sides of mold joint.Two sun gears 5 and 6 have external tooth 7 separately.Also lay rotationally planetary gear set 9 by bolt 8 in planetary carrier 2, this planetary gear set 9 has the first planetary pinion 10 and the second not shown planetary pinion separately.Observe on the direction perpendicular to the longitudinal axis 11 of radial plane, a planetary pinion is designed to shorter than another planetary pinion.
In the embodiment shown in fig. 1, two planetary carrier parts 3 and 4 have and samely radially extend.This means, their circular radial side face is equidistant with longitudinal axis 11 on maximum diameter.
Outside circular radial side face 13, be provided with contiguously shaft drive wheel 14 with two circular radial side faces 13 of planetary carrier 2, this shaft drive wheel 14 has inner face 15, and this inner face 15 is in the state that contacts with 4 circular radial side face 13 with two planetary carrier parts 3.The side formation that deviates from the planetary carrier part at shaft drive wheel 14 has external tooth 16.This external tooth 16 can be spur gear, helical gear or gear on worm.
Consist of the link 17 that material and/or shape and/or force closure are arranged in the contact area of circular radial side face 13 and inner face 15, wherein this link 17 consists of and can be for example the combination of the sealed combination of ca(u)lk and shape or punching press connection piece and welding towards shaft drive wheel 14 on two planetary carrier parts 3 and 4.Each link assembly is also possible, but according to the applicable cases independent assortment mutually of expectation.
Seeming in the radial direction longer than the second planetary carrier part 4 in the first row gear rack part 3 shown in the right side in Fig. 2.Be provided with the gap between the inner face 15 of the circular radial side face 13 of the second planetary carrier part 4 and shaft drive wheel 14, and do not have the gap on another planetary carrier part 3 between the inner face 15 of circular radial side face 13 and shaft drive wheel 14, but for it unshowned welding on the circular radial side face, this welding extends to the inside of shaft drive wheel 14.
But in a kind of scheme also possible that, not welding in the scope of link 17, but shape is sealed or punching press links.Mark with reference character 18 towards the gap of shaft drive wheel 14 on the second planetary carrier part 4.
Reference numerals list
1 spur-gear differential
2 planetary carriers
3 the first row gear rack parts
4 second planetary carrier parts
5 sun gears
6 sun gears
7 external tooths
8 bolts
9 planetary gear set
10 first planetary pinions
11 longitudinal axis
12 supporting and spacer sleeves
13 circular radial side faces
14 shaft drive wheels
The inner face of 15 shaft drive wheels
16 external tooths
17 links
18 gaps
Claims (10)
1. be used for the spur-gear differential (1) of the power train of automobile, described spur-gear differential (1) has planetary carrier (3), be furnished with two sun gears (5 that have separately external tooth in described planetary carrier (3), 6), described sun gear (5, 6) mesh with a differential gear that is constituted as planetary pinion (10) separately, shape is sealed mutually for wherein said two planetary pinions (9), and described spur-gear differential (1) also is provided with the shaft drive wheel (14) that substantially is arranged in described planetary carrier (2) radially outer, it is characterized in that, be provided with the link (17) of transmitting torque between the circular radial side face (13) of the inner face (15) of described shaft drive wheel (14) and described planetary carrier (2).
2. spur-gear differential according to claim 1 (1), is characterized in that, described link (17) is constituted as the link of material and/or shape and/or force closure.
3. spur-gear differential according to claim 1 and 2 (1), is characterized in that, described link (17) is designed to punching press connection piece and/or ca(u)lk connection piece and/or is welded to connect part.
4. the described spur-gear differential of any one (1) according to claim 1 to 3, it is characterized in that, described planetary carrier (2) is comprised of at least two planetary carrier parts (3 and 4), described planetary carrier part (3 and 4) is half planetary carrier preferably, and in wherein said two planetary carriers part, only one (3 or 4) have the link (17) of described transmitting torque or the link (17) that two described planetary carrier parts (3,4) all have described transmitting torque.
5. spur-gear differential according to claim 4 (1), is characterized in that, described two planetary carriers parts (3,4) have the radially extension of different sizes.
6. spur-gear differential according to claim 5 (1), is characterized in that, only has the link (17) that the larger planetary carrier that radially extends part (3) has described transmitting torque.
7. the described spur-gear differential of any one (1) according to claim 4 to 6, it is characterized in that, the link of described transmitting torque (17) extends on total circumference of at least one planetary carrier part (3 or 4), preferably extends on total circumference of two planetary carrier parts (3,4).
8. for the manufacture of the method for spur-gear differential described according to any one in the claims (1), comprise the step of described planetary carrier (2) in described inner face (15) welding of its circumference and described shaft drive wheel (14).
9. method according to claim 8, is characterized in that, after described welding, preferably by a kind of making method that produces smear metal, with respect to the external tooth (16) of the bearing support described shaft drive wheel of processing (14).
10. method according to claim 9, is characterized in that, the member that is in described planetary carrier (2) was installed before described welding process.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201110087579 DE102011087579A1 (en) | 2011-12-01 | 2011-12-01 | Spur gear differential for use in drive train of e.g. motor vehicle, has sun wheels, and rotational torque-transferring connection formed between inner surface of axial drive wheel and radial peripheral surface of planetary carrier |
| DE102011087579.4 | 2011-12-01 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103133632A true CN103133632A (en) | 2013-06-05 |
Family
ID=48431167
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012105101936A Pending CN103133632A (en) | 2011-12-01 | 2012-12-03 | Spur gear differential and manufacturing method thereof |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103133632A (en) |
| DE (1) | DE102011087579A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107921852A (en) * | 2015-09-04 | 2018-04-17 | 舍弗勒技术股份两合公司 | Independent transmission device and the electric drive unit with independent transmission device |
| CN112424009A (en) * | 2018-07-24 | 2021-02-26 | 沃尔沃卡车集团 | Powertrain system for driving at least one wheel of a vehicle |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20150105212A1 (en) * | 2013-10-14 | 2015-04-16 | Caterpillar Inc. | System and method for salvaging a pin-bore assembly |
| WO2015067247A1 (en) * | 2013-11-08 | 2015-05-14 | Schaeffler Technologies AG & Co. KG | Planetary transmission with cohesively connected planet carrier |
| DE102016214015B4 (en) * | 2016-07-29 | 2022-03-31 | Schaeffler Technologies AG & Co. KG | Planetary differential device and method of manufacturing the planetary differential device |
| RU171000U1 (en) * | 2017-01-23 | 2017-05-17 | Публичное акционерное общество "КАМАЗ" | CYLINDER TRANSFER BOX DIFFERENTIAL |
| DE102017114431A1 (en) | 2017-06-29 | 2019-01-03 | Schaeffler Technologies AG & Co. KG | planetary gear |
| DE102018220105B4 (en) * | 2018-11-22 | 2021-01-21 | Audi Ag | Differential gear for a motor vehicle with an output gear pressed onto the housing through two press fits |
| DE102021110608B3 (en) | 2021-04-26 | 2022-08-18 | Schaeffler Technologies AG & Co. KG | Fastening a cover of a transmission housing; Bevel gear differential and method of assembling a gear case |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2060831U (en) * | 1989-11-16 | 1990-08-22 | 河北省冶金设计研究院 | Inter-tooth planet differential gearing |
| WO2008092526A1 (en) * | 2007-01-31 | 2008-08-07 | Schaeffler Kg | Spur-gear differential |
| DE102007040475A1 (en) * | 2007-08-28 | 2009-03-05 | Schaeffler Kg | spur gear |
| WO2011089706A1 (en) * | 2010-01-22 | 2011-07-28 | トヨタ自動車株式会社 | Welded structure and welding method |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10013429C5 (en) | 2000-03-17 | 2009-10-01 | Daimler Ag | differential |
| DE102004034736A1 (en) | 2004-07-17 | 2006-02-02 | Zf Friedrichshafen Ag | Differential for a vehicle axle |
| DE102005023230B4 (en) | 2005-05-04 | 2010-10-07 | Bayerische Motoren Werke Aktiengesellschaft | Method for welding a ring gear with a differential housing of a transmission |
| DE102007004712B4 (en) | 2007-01-31 | 2012-09-27 | Schaeffler Technologies Gmbh & Co. Kg | Spur gear |
| EP2452099B1 (en) | 2009-07-09 | 2013-03-20 | Schaeffler Technologies AG & Co. KG | Spur gear differential |
-
2011
- 2011-12-01 DE DE201110087579 patent/DE102011087579A1/en active Pending
-
2012
- 2012-12-03 CN CN2012105101936A patent/CN103133632A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2060831U (en) * | 1989-11-16 | 1990-08-22 | 河北省冶金设计研究院 | Inter-tooth planet differential gearing |
| WO2008092526A1 (en) * | 2007-01-31 | 2008-08-07 | Schaeffler Kg | Spur-gear differential |
| DE102007040475A1 (en) * | 2007-08-28 | 2009-03-05 | Schaeffler Kg | spur gear |
| WO2011089706A1 (en) * | 2010-01-22 | 2011-07-28 | トヨタ自動車株式会社 | Welded structure and welding method |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107921852A (en) * | 2015-09-04 | 2018-04-17 | 舍弗勒技术股份两合公司 | Independent transmission device and the electric drive unit with independent transmission device |
| US10760670B2 (en) | 2015-09-04 | 2020-09-01 | Schaeffler Technologies AG & Co. KG | Distribution gearing and electric drive unit having a distribution gearing |
| CN112424009A (en) * | 2018-07-24 | 2021-02-26 | 沃尔沃卡车集团 | Powertrain system for driving at least one wheel of a vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102011087579A1 (en) | 2013-06-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103133632A (en) | Spur gear differential and manufacturing method thereof | |
| CN101611243B (en) | Spur gear differential | |
| US8007391B2 (en) | Differential apparatus for vehicle | |
| US9488265B2 (en) | Compact planetary differential gear set arrangement | |
| CN102388238B (en) | Differential gear and vehicle provided with differential gear | |
| CN102818002B (en) | Compliant carrier wall for improved gearbox load sharing | |
| US9341251B2 (en) | Supporting and guiding disk in a planetary gear train | |
| CN104169612B (en) | There is the planetary gear mechanism of differential mechanism | |
| US7470207B2 (en) | Differential assembly for a machine | |
| CN101573247B (en) | Torque transmission unit | |
| US20150377334A1 (en) | Integrated gear assembly | |
| CN101821532B (en) | Differential gearing having light-weight carrier parts and visco-coupling | |
| CN100462586C (en) | Main speed reducing device having dynamic branch off structure | |
| CN103221717A (en) | Planetary gear for transmitting a driving torque in a vehicle and drive unit comprising the planetary gear | |
| US20050193851A1 (en) | Angle drive with power distribution | |
| CN101025220B (en) | Internal ring gear with integral hub portion and method of manufacture | |
| CN103573961A (en) | Cylindrical gear differential | |
| EP2843139B1 (en) | Drive device for construction machine | |
| US9939056B2 (en) | Final drive system for a machine | |
| KR102279964B1 (en) | Composite Planetary Friction Drive | |
| US10228045B2 (en) | Gear device | |
| CN101932853A (en) | Differential cage made of half shells and method for producing a differential cage | |
| CN105980725A (en) | Edge load-reducing clutch | |
| CN108473052B (en) | Hub unit | |
| US10865852B2 (en) | Powertrain with cycloidal mechanism having reinforced contact surfaces |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| ASS | Succession or assignment of patent right |
Owner name: SCHAEFFLER FIFTH INVESTMENT MANAGEMENT GMBH + CO., Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG Effective date: 20150730 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| C53 | Correction of patent of invention or patent application | ||
| CB02 | Change of applicant information |
Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES AG & CO. KG Address before: German Herzogenaurach Applicant before: SCHAEFFLER TECHNOLOGIES GmbH & Co.KG Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES GmbH & Co.KG Address before: German Herzogenaurach Applicant before: Fifth Schaeffler investment management GmbH & Co.KG |
|
| COR | Change of bibliographic data |
Free format text: CORRECT: APPLICANT; FROM: SCHAEFFLER FIFTH INVESTMENT MANAGEMENT GMBH + CO., KG TO: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG Free format text: CORRECT: ADDRESS; FROM: Free format text: CORRECT: APPLICANT; FROM: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG TO: SCHAEFFLER TECHNOLOGY GMBH + CO. KG |
|
| TA01 | Transfer of patent application right |
Effective date of registration: 20150730 Address after: German Herzogenaurach Applicant after: Fifth Schaeffler investment management GmbH & Co.KG Address before: German Herzogenaurach Applicant before: SCHAEFFLER TECHNOLOGIES AG & CO. KG |
|
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20130605 |