CN101858404B - Switchable high-load transmission - Google Patents
Switchable high-load transmission Download PDFInfo
- Publication number
- CN101858404B CN101858404B CN2010101054532A CN201010105453A CN101858404B CN 101858404 B CN101858404 B CN 101858404B CN 2010101054532 A CN2010101054532 A CN 2010101054532A CN 201010105453 A CN201010105453 A CN 201010105453A CN 101858404 B CN101858404 B CN 101858404B
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- input shaft
- gear
- countershaft
- heavy
- axially
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- Expired - Fee Related
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- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
- F16H3/22—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially
- F16H3/24—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts coaxial
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The present invention relates to a switchable high-load transmission, and particularly to an industrial transmission. The switchable high-load transmission comprises the following components: an input shaft (1); a secondary shaft arrangement of secondary shafts (2A,2B) which is provided with at least driven gears (2A.1,2A.2,2B.1,2B.2) and is connected with the input shaft through the driven gearsthrough an antitorque mode; an output shaft (3) which is connected with the secondary shafts through an antitorque mode; and at least two driving pinions (1.1,1.2) which are used for the secondary shaft arrangement and are connected with the input shaft through an antitorque mode; wherein the input shaft can axially move between a first gear and a second gear (picture 1,picture 2); the driving pinions are axially fixed and are connected with the input shaft through an antitorque mode and can axially move along with the input shaft; wherein in the first gear (picture 1), the first driving pinion (1.1) is engaged with first driven pinions (2A.1,2B.1) provided on at least one secondary shaft; and furthermore in the second gear (picture 2), the second driving pinion (1.2) is engaged with second driven gears (2A.2,2B.2) provided on at least one secondary shaft.
Description
Technical field
The present invention relates to a kind of heavy-duty transmission of shifting gears, especially an industrial speed changer has an input shaft, and a countershaft that can connect on different gears arranges and an output shaft that this output shaft can be arranged antitorquely with countershaft in its side and be connected antitorquely.
Background technique
Heavy-duty transmission, especially transmit a 10kNm at least who interrelates with the axle of low cruise, the speed changer of 50kNm moment of torsion is used in different occasions especially at least, for example be used for the equipment of STEELMAKING PRODUCTION and steel-making processing, in rubber and plastics industry, be used for transportation and conveying equipment and as the special-purpose speed changer of the single piece production of surface mining industry or production of energy equipment.
Here for the output speed speed change of a motor being arrived the different input shaft rotating speed of working machine, speedup not only here wherein, be that gear ratio is less than 1, and slow down, be so-calledly to have gear ratio and under meaning of the present invention, be called as speed change greater than 1 deceleration, be well-known by the speed changer that especially has a small gear on input shaft and output shaft or countershaft in the practice, wherein all small gears are meshing with each other all the time, and have only a driver pinion to be connected with input shaft respectively in the mode of selecting or a driven gear can be connected with output shaft by the gearshift sleeve, therefore the definite interchangeable retaining of the small gear rotation by different-diameter arrives different gear ratio antitorquely.
Shortcoming is that the small gear of not shifting gears here also is in engagement all the time, and especially this may cause vibration, namely has the motion of corresponding wearing and tearing and unwelcome vibrational excitation within backlash.In addition disadvantageously, the small gear of gearshift is supported on the bearing, and this bearing bears dead load, therefore may cause the deflection of small gear and the damage of bearing.
Summary of the invention
Task of the present invention provides a kind of improved heavy-duty transmission of shifting gears.
This task achieves a solution by the following heavy-duty transmission of shifting gears.Described heavy-duty transmission of shifting gears has an input shaft; One countershaft that has at least one countershaft arranges that this countershaft has at least two driven gears, and wherein countershaft is arranged and can be connected with input shaft by driven gear antitorquely; One output shaft, this output shaft can be arranged antitorquely with countershaft and be connected; And at least two are used for countershaft and arrange and the antitorque driver pinion that is connected of input shaft; Wherein input shaft can be axially mobile between first and second gears; Driver pinion axially is connected with input shaft regularly and antitorquely, and can axially move with input shaft; Wherein one first driver pinion is meshed with at least one first driven gear that countershaft is arranged in first gear; And one second driver pinion is meshed with at least one second driven gear that countershaft is arranged in second gear.
Heavy-duty transmission of shifting gears according to the present invention especially is designed for industrial speed changer.According to a first aspect of the invention it have one can be with a motor, for example the input shaft that is connected of a gas turbine or steam turbine, an internal-combustion engine or motor, can be with working machine, for example the output shaft and that is connected of a generator, a haulage device or the conveying equipment countershaft that has one or more countershaft is arranged, the antitorque ground of two or more driven gears and preferably being arranged on the described countershaft same axial restraint.Driven gear for example can constitute integrated with countershaft, especially with this countershaft cast molding, perhaps constitute dismountable, for example by fine grade press fit or a gear and an axial retention element, perhaps constitute non-removable, for example be fixed on the countershaft by hot pressing.
Countershaft arranges preferably all the time with the antitorque ground of output shaft, especially by a gear, for example a single-stage or multistage cylindrical gears speed changer or planetary transmission are connected, this speed changer can have one greater than, be equal to or less than 1 gear ratio.Same output shaft also can directly constitute the countershaft that countershaft is arranged, namely constitutes in the same manner with this countershaft and for example constitutes integrally for this reason.
Countershaft is arranged and can be connected with input shaft at two or more gears by driven gear antitorquely.Input shaft can be axially mobile between gear according to the present invention for this reason, and have two or more driver pinions, and this driver pinion axially is connected with input shaft regularly and antitorquely, and can axially move with input shaft.Driver pinion for example can constitute integrally with input shaft, especially with this input shaft moulding, perhaps constitute dismountable, for example by a fine grade press fit or a gear and an axial retention element, perhaps constitute non-removable, for example be fixed on the input shaft by hot pressing.
First driver pinion of an input shaft is with one or more, preferably first driven gear of all countershafts is meshed in first gear, and the driven gear that second driver pinion and countershaft are arranged is thrown off engagement.In contrast, second driver pinion is with one or more, preferably second driven gear of all countershafts is meshed in second gear, and at this moment the driven gear arranged of first driver pinion and countershaft is thrown off engagement.Wherein, on the one hand first driver pinion and first driven gear, and second driver pinion is realized different gear ratio with second driven gear on the other hand.In a particularly preferred structure, in first and/or second gear, realize slowing down.
Can realize other the gear ratio of shifting gears under same mode, for example the 3rd driver pinion by having only an input shaft in another gear is with one or more, preferably the 3rd driven gear of all countershafts is meshed.Equally preferably implement all the time here to slow down.
In a preferred construction, countershaft arrange have that two or more can connect with output shaft antitorquely, advantageously basically structure identical, preferably respectively have a countershaft of two or more driven gears, wherein at least one preferably gear at all transmitted powers the driver pinion of an input shaft with at least two, preferably the driven gear of all countershafts is meshed.In gear, be assigned on the countershaft in this mode by the input torque that input shaft imports into, the driver pinion of input shaft is meshed with the driven small gear of a plurality of countershafts in this gear, advantageously this has reduced the load of single gear and countershaft, and therefore especially can use littler gear and countershaft, and therefore can make heavy-duty transmission compacter.
Preferably be provided with a neutral at least, in this neutral, do not transmit moment of torsion.Input shaft is axially movable to the 3rd gear for this reason, and the driven gear that does not have driver pinion and countershaft to arrange in this gear is meshed.
For this reason between first and second driver pinions axially in spacing in case of necessity only than the axial width of driven gear big a little.Can be arranged between first and second driver pinions with this mode this driven gear in neutral, another driven gear can be disposed axially in before first or second driver pinion or afterwards.
Same between first and second driver pinions axially in spacing in case of necessity only than the axial olo of two driven gears of countershaft big a little.So just guaranteed that two driven gears can be arranged between first and second driver pinions in neutral.
Driven gear also can mutual like this maintenance one determining deviation under corresponding mode, so that one or more driver pinion can be arranged between them in neutral.
Do not have neutral in a selectable structure, namely a driver pinion is meshed with the driven gear that countershaft is arranged respectively all the time.Therefore advantageously transmission shaft is shorter to what can do.Especially preferred is that such speed changer for example can have an electronic position detecting device, in order to show and/or the control gear, can shift gears between first and second gears in this gear.
For axially movable property, preferably input shaft is supported in one or more thrust-bearing in the housing of heavy-duty transmission.At least one of this bearing can have an outer collar bearing, and this bearer ring axially is connected with housing securely, and has an inner bearing collar, and this bearer ring axially is connected with input shaft securely, and can axially move with respect to outer collar bearing.Input shaft axially can move with respect to the movement of outer collar bearing by inner bearing collar in a preferred construction so.Wherein inner bearing collar or input shaft itself for example can hydraulically and/or pneumatically move by corresponding annular piston or plunger, especially mechanically mobile by the element of a shifting fork, screw threaded arrangement or this class, perhaps also can be electrically or electromagnetic ground move, wherein heavy-duty transmission can comprise the device of corresponding circuit, driving mechanism and this class.
In a preferred construction, input shaft axially can move by a shifting fork, preferably input shaft axially freely is supported in the housing for this reason, and its axial position can move axially in housing by one or adjustable shifting fork is determined, this shifting fork and input shaft for example by a circular groove axial restraint ground and preferably there is not layout with reversing.
In a preferred construction, input shaft and output shaft are axially arranged in a line mutually, and this makes heavy-duty transmission constitute a long and narrow structural type.Compacter for the axial formation that makes heavy-duty transmission, input shaft are in one or more gear, for example can partly insert the output shaft that for this reason constitutes hollow shaft in a neutral and second gear.Also can in one or more gear, insert input shaft according to the specific output axle between input torque and output torque and corresponding shaft diameter equally conversely.
In a selectable structure, input shaft and output shaft on the circumference of countershaft each other, 180 ° of layouts of dislocation especially approximately basically, yet this makes it can constitute a wideer advantageously axial shorter structural type.
In a preferred construction, between input shaft and motor, be provided with a compensation clutch, this compensation clutch compensation between two axial gears of input shaft at least with respect to the axial dislocation of motor.This compensation clutch for example can have one and have the hollow shaft of internal gear and have external gear, and this external gear axially movably is supported in the hollow shaft, and is meshing with each other constantly or can be meshing with each other with its internal gear.Especially it can comprise a tooth sector clutch.
Same compensation clutch also can have two can antitorque ground flange connecting, selectively can arrange one or more spacer element between described flange.Though gearshift requires packing into of spacer element or dismantles in this structure, yet this does not usually play decision in the duration of work of the heavy-duty transmission that belongs to this class.
First aspect of the present invention has been described above, has been connected with a motor according to this aspect input shaft that output shaft is connected with a working machine, be about to power and be delivered to output shaft from input shaft.Input shaft also can be with a working machine according to a second aspect of the invention, for example a generator, a haulage device or conveying equipment are connected, and output shaft also can be with a motor, for example a gas turbine or steam turbine, an internal-combustion engine or a motor are connected, and wherein structure is identical.The axially movable axle of the representation of concept one of " input shaft " in this point just, can the shift gears driver pinion of engagement of the driven gear that is used for arranging with countershaft is arranged in this axle, and can import or output power by this axle, namely needn't be a driving shaft and also can be a driven shaft in case of necessity.
Correspondingly top according to a third aspect of the invention we first and second aspects of mentioning also can make up therewith, namely the driven shaft of the driving shaft that not only can be connected with motor but also the heavy-duty transmission that can be connected with working machine can constitute axially movable input shaft, and the different driven gear that its driver pinion can be arranged with the countershaft that is arranged between driving shaft and the driven shaft in different gears be meshed.
As beginning time explanation, output shaft also can directly constitute the countershaft arranged of unique countershaft preferably.Therefore if abandon an independent countershaft, for example respectively power is delivered on the driven gear of gearshift of countershaft the so same direct representation output shaft of this countershaft according to the first aspect input shaft.
Description of drawings
Other feature and advantage are obtained by following embodiment.For this reason wherein partly schematically:
Fig. 1 has represented that one has the heavy-duty transmission of shifting gears according to structure of the present invention in first gear of one first gear ratio;
Fig. 2 represented to have one second gear ratio in second gear according to heavy-duty transmission shown in Figure 1; And
Fig. 3 represented in the neutral position according to heavy-duty transmission illustrated in figures 1 and 2, in this neutral, do not transmit moment of torsion.
Embodiment
Fig. 1 represented one according to the heavy-duty transmission of shifting gears of structure of the present invention in first gear.It comprises an input shaft 1, and this input shaft is connected with the driven shaft 100 of motor or the driving shaft of working machine (not shown) by a compensation clutch 10 of describing below.
Input shaft 1 supports the diameter of one first driver pinion 1.1 and one second driver pinion, 1.2, the second driver pinions greater than the diameter of first driver pinion 1.1 on a side that is in compensation clutch 10 opposites.The antitorque ground of two driver pinions and axial restraint ground are connected with input shaft.
Heavy-duty transmission comprises that a countershaft that has two countershaft 2A, 2B arranges in addition, described countershaft structure identical and on the circumference of input shaft 1 180 ° of layouts of dislocation, therefore the first countershaft 2A only is described below.This countershaft supports one first driven gear 2A.1 and one second driven gear 2A.2, and the diameter of second driven gear is less than the diameter of first driven gear.The antitorque ground of two driven gears and axial restraint ground are connected with countershaft.
Countershaft 2A supports the combination small gear 2A.3 of a countershaft side on a side that is in driven gear 2A.1 and 2A.2 opposite, and this combination small gear is meshed with the built-up gear 3.1 of the output shaft side of an output shaft 3 of arranging in a line with input shaft 1.The driving shaft of this output shaft and a working machine or the driven shaft of the motor (not shown) that is connected.Built-up gear 3.1 antitorque ground and axial restraint ground are connected with output shaft 3.
Input shaft 1 is by axially movable bearings (not shown) in housing.This thrust-bearing has an outer collar bearing 4.1, and this bearer ring is connected with housing securely, and has an inner bearing collar 4.2, and this bearer ring axially is connected with input shaft securely, and axially can move with respect to outer collar bearing.Its annular piston (not shown) by both sides of this inner bearing collar 4.2 and input shaft 1 usefulness hydraulically axially can move between three gears of representing in Fig. 1 to Fig. 3 that describe below.
In first gear shown in Fig. 1, heavy-duty transmission has one first gear ratio between input shaft and output shaft 1,3, this gear ratio is obtained by the ratio of the diameter between the first driven gear 2A.1, the 2B.1 of first driver pinion 1.1 and countershaft 2A, 2B.Input shaft 1 is axially arranged so for this reason, so that have only its first driver pinion 1.1 to be meshed with the first driven gear 2A.1, the 2B.1 of two countershaft 2A, 2B, and its second driver pinion 1.2 and driven gear 2A.2, the 2B.2 of countershaft 2A, 2B throw off engagement.Be assigned to equably on two countershaft 2A, the 2B at the moment of torsion that transmits between input shaft and the output shaft 1,3 in this mode, so its moment load is lowered, and axle and gear correspondingly can constitute compacter.
In second gear shown in Fig. 2, heavy-duty transmission has second gear ratio between input shaft and output shaft 1,3, this gear ratio is obtained by the ratio of the diameter between the second driven gear 2A.2, the 2B.2 of second driver pinion 1.2 and countershaft 2A, 2B, and less than first gear ratio.Input shaft 1 is axially arranged so for this reason, so that have only its second driver pinion 1.2 to be meshed with the second driven gear 2A.2, the 2B.2 of two countershaft 2A, 2B, and its first driver pinion 1.1 and driven gear 2A.1, the 2B.1 of countershaft 2A, 2B throw off engagement now.Therefore, in second gear, be assigned to equably on two countershaft 2A, the 2B at the moment of torsion that transmits between input shaft and the output shaft 1,3 equally.
In second gear, input shaft 1 partly inserts in the output shaft 3 that for this reason constitutes hollow shaft.Can dwindle the axial length of heavy-duty transmission in this mode.
In order to compensate the axial dislocation on the other end of input shaft, compensation clutch 10 comprises that one has the hollow shaft of internal gear 10.1, the external gear 10.2 of input shaft 1 axially movably is supported in this internal gear, and input shaft 1 in first and second gears (shown in Fig. 1,2) is connected with driven shaft 100 with hollow shaft and by this hollow shaft antitorquely, and this driven shaft has an external gear that is meshed with the internal gear of hollow shaft in its side for this reason.
In the 3rd shown in Fig. 3 or neutral position, input shaft 1 is axially arranged like this, so that not only the first driven gear 2A.1, the 2B.1 of its driver pinion 1.1 and two countershaft 2A, 2B but also its second driver pinion 1.2 and driven gear 2A.2, the 2B.2 of countershaft 2A, 2B throw off engagement, therefore between input shaft and output shaft 1,3, do not transmit moment of torsion.In order to occupy this gear, driven gear 2A.1 to 2B.2 is disposed axially between the driving wheel 1.1,1.2 in this gear, between first and second driver pinions 1.1,1.2 axially in spacing greater than the axial olo of driven gear 2A.1,2A.2 or 2B.1, the 2B.2 of two countershaft 2A, 2B.
In the neutral position, input shaft 1 partly inserts in the output shaft 3 that constitutes hollow shaft equally.When not transmitting moment of torsion, the external gear 10.2 of input shaft 1 is thrown off engagement with the internal gear of the hollow shaft of clutch 10 10.1.This makes the conversion between first and second gears become easier.
Be equipped with two countershafts for the moment branch in an embodiment.In a variation scheme of not representing, can cancel a countershaft.Especially so can cancel the independent structure that countershaft and output shaft and it are connected with built-up gear by the combination small gear, and unique countershaft direct formation output shaft simultaneously then.
The reference character table
1 input shaft
1.1 first driver pinion
1.2 second driver pinion
2A first countershaft
2A.1 first driven gear
2A.2 second driven gear
2A.3 the combination small gear of countershaft side
2B second countershaft
2B.1 first driven gear
2B.2 second driven gear
2B.3 the combination small gear of countershaft side
3 output shafts
3.1 the combination small gear of output shaft side
4.1 outer collar bearing
4.2 inner bearing collar
10 compensation clutches
10.1 internal gear
10.2 external gear
The driven shaft of 100 motors
Claims (16)
1. the heavy-duty transmission that can shift gears has an input shaft (1);
One have at least one countershaft (2A, 2B) countershaft arrange, this countershaft have at least two driven gears (2A.1,2A.2,2B.1,2B.2), wherein countershaft is arranged and can be connected with input shaft by driven gear antitorquely;
One output shaft (3), this output shaft can be arranged antitorquely with countershaft and be connected; And
At least two are used for countershaft and arrange and the antitorque driver pinion that is connected of input shaft (1.1,1.2);
Wherein input shaft can be axially mobile between first and second gears;
Driver pinion axially is connected with input shaft regularly and antitorquely, and can axially move with input shaft; Wherein
(2A.1's at least one first driven gear that one first driver pinion (1.1) and countershaft are arranged in first gear 2B.1) is meshed; And
(2A.2's at least one second driven gear that one second driver pinion (1.2) and countershaft are arranged in second gear 2B.2) is meshed.
2. heavy-duty transmission according to claim 1, it is characterized in that, countershaft arranges that having two at least can have a driven gear (2A.1 with output shaft is connected antitorquely, 2A.2,2B.1,2B.2) countershaft (2A, 2B), first driven gear (the 2A.1 of first driver pinion (1.1) and at least two countershafts in first gear wherein, 2B.1) be meshed and/or in second gear second driven gear of second driver pinion (1.2) and at least two countershafts (2A.2 2B.2) is meshed.
3. heavy-duty transmission according to claim 1 and 2 is characterized in that, input shaft is axially movable in one the 3rd gear, and the driven gear that does not wherein have driver pinion and countershaft to arrange in the 3rd gear is meshed.
4. heavy-duty transmission according to claim 3, it is characterized in that, at first and second driver pinions (1.1,1.2) between axially in spacing greater than the axial width of driven gear, greater than two driven gear (2A.1,2A.2) axial olo and/or between first and second driven gears of countershaft axially in spacing greater than the axial width of driver pinion, greater than the axial olo of second driver pinion.
5. heavy-duty transmission according to claim 1 and 2 is characterized in that a housing, and a thrust-bearing that supports input shaft is arranged in this housing.
6. heavy-duty transmission according to claim 5, it is characterized in that, thrust-bearing has an outer collar bearing (4.1), this outer collar bearing axially is connected with housing securely, and has an inner bearing collar (4.2), this inner bearing collar axially is connected with input shaft securely, and can axially move with respect to outer collar bearing.
7. heavy-duty transmission according to claim 1 and 2 is characterized in that, input shaft can hydraulically and/or pneumatically move.
8. heavy-duty transmission according to claim 1 and 2 is characterized in that, input shaft mechanically moves by a shifting fork.
9. heavy-duty transmission according to claim 1 and 2 is characterized in that, input shaft can move electrically.
10. heavy-duty transmission according to claim 1 and 2, it is characterized in that, input shaft and output shaft are axially arranged in a line mutually, and input shaft (1) and output shaft one inserts at least one gear in another of input shaft and output shaft (3) at least in part.
11. heavy-duty transmission according to claim 1 and 2 is characterized in that, input shaft and output shaft 180 ° of layouts of dislocation each other on the circumference of countershaft.
12. heavy-duty transmission according to claim 1 and 2 is characterized in that, arranges a gear (2A.3,2B.3,3.1) between output shaft and countershaft layout.
13. heavy-duty transmission according to claim 1 and 2 is characterized in that, output shaft constitutes unique countershaft that countershaft is arranged.
14. heavy-duty transmission according to claim 1 and 2 is characterized in that, input shaft has a compensation clutch (10), the axial dislocation of this compensation clutch compensation between two axial gears of input shaft at least.
15. heavy-duty transmission according to claim 14, it is characterized in that, the compensation clutch has one and has the hollow shaft of internal gear and have an external gear (10.2), this external gear axially movably is supported in the hollow shaft, and can be meshing with each other or be meshed with its internal gear (10.1), the compensation clutch has a tooth sector clutch.
16. heavy-duty transmission according to claim 14 is characterized in that, the compensation clutch has two selectively can antitorque ground flange connecting under connecting in the middle of at least one spacer element.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009006118.5 | 2009-01-26 | ||
| DE102009006118.5A DE102009006118B4 (en) | 2009-01-26 | 2009-01-26 | Switchable heavy duty gearbox |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101858404A CN101858404A (en) | 2010-10-13 |
| CN101858404B true CN101858404B (en) | 2013-09-11 |
Family
ID=42308797
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010101054532A Expired - Fee Related CN101858404B (en) | 2009-01-26 | 2010-01-26 | Switchable high-load transmission |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5319563B2 (en) |
| CN (1) | CN101858404B (en) |
| DE (1) | DE102009006118B4 (en) |
| FR (1) | FR2941509B1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012014273A1 (en) * | 2012-07-19 | 2014-05-15 | Renk Aktiengesellschaft | Gearbox with power split |
| JP6750197B2 (en) * | 2015-07-13 | 2020-09-02 | デクセリアルズ株式会社 | Anisotropic conductive film and connection structure |
| CN105156606B (en) * | 2015-07-22 | 2024-01-16 | 梅州五指石科技有限公司 | Shifting piece rotation-stopping type sliding gearbox |
| CN107489742B (en) * | 2017-08-14 | 2019-07-19 | 永祺（中国）车业股份有限公司 | Transmission shaft and gearbox integrated driving structure |
| DE102018132351A1 (en) | 2018-12-14 | 2020-06-18 | Renk Aktiengesellschaft | Switchable load gear |
| DE102020000462A1 (en) | 2020-01-24 | 2021-07-29 | Man Truck & Bus Se | Modular transmission kit for a motor vehicle |
| CN113339466B (en) * | 2021-05-25 | 2024-04-23 | 武汉市精华减速机制造有限公司 | Tower multistage gear shifting decelerator of reconfiguration |
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| CN1143022A (en) * | 1995-04-12 | 1997-02-19 | 易通公司 | Automobile speed variator |
| CN1806135A (en) * | 2003-06-13 | 2006-07-19 | Zf腓德烈斯哈芬股份公司 | Planetary transmission |
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| DE591298C (en) | 1934-01-18 | J M Voith Maschinenfabrik | Gear change transmission | |
| DE2033865C2 (en) * | 1970-07-01 | 1974-07-25 | Mannesmann-Meer Ag, 4050 Moenchengladbach | Angularly movable tooth coupling that can be engaged and disengaged with crowned teeth |
| AT382121B (en) * | 1979-05-09 | 1987-01-12 | Evg Entwicklung Verwert Ges | POWERTRAIN TRANSMISSION |
| US4388838A (en) * | 1980-07-03 | 1983-06-21 | Eaton Corporation | Multiple countershaft simple transmission |
| DE3416232A1 (en) * | 1984-05-02 | 1985-11-07 | Weiler-Werkzeugmaschinen, 8522 Herzogenaurach | MULTI-STAGE MANUAL GEARBOX, ESPECIALLY SELECTING GEARBOX FOR MACHINE TOOLS |
| JPH059564Y2 (en) * | 1986-04-07 | 1993-03-09 | ||
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| JPH0628395U (en) * | 1992-09-16 | 1994-04-15 | 三田工業株式会社 | clutch |
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| JP3697622B2 (en) * | 1996-08-08 | 2005-09-21 | 株式会社マシンエンジニアリング | Backlashless transmission |
| DE19938934A1 (en) * | 1999-08-17 | 2001-04-12 | Inst Maschinenelemente Uni Stu | transmission |
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2009
- 2009-01-26 DE DE102009006118.5A patent/DE102009006118B4/en not_active Expired - Fee Related
-
2010
- 2010-01-14 JP JP2010005909A patent/JP5319563B2/en not_active Expired - Fee Related
- 2010-01-25 FR FR1050451A patent/FR2941509B1/en not_active Expired - Fee Related
- 2010-01-26 CN CN2010101054532A patent/CN101858404B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1143022A (en) * | 1995-04-12 | 1997-02-19 | 易通公司 | Automobile speed variator |
| CN1806135A (en) * | 2003-06-13 | 2006-07-19 | Zf腓德烈斯哈芬股份公司 | Planetary transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2010169263A (en) | 2010-08-05 |
| CN101858404A (en) | 2010-10-13 |
| DE102009006118B4 (en) | 2019-09-12 |
| DE102009006118A1 (en) | 2010-08-05 |
| JP5319563B2 (en) | 2013-10-16 |
| FR2941509A1 (en) | 2010-07-30 |
| FR2941509B1 (en) | 2015-12-18 |
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