CN101131200B - Contact device for cone ring transmission - Google Patents
Contact device for cone ring transmission Download PDFInfo
- Publication number
- CN101131200B CN101131200B CN2007101464465A CN200710146446A CN101131200B CN 101131200 B CN101131200 B CN 101131200B CN 2007101464465 A CN2007101464465 A CN 2007101464465A CN 200710146446 A CN200710146446 A CN 200710146446A CN 101131200 B CN101131200 B CN 101131200B
- Authority
- CN
- China
- Prior art keywords
- hold down
- hydraulic piston
- down gag
- cone
- hydraulic
- 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.)
- Expired - Fee Related
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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
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned members
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
- F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The present invention relates to a pressing device (14) used for the conical ring speed changer (1), the speed changer includes two cone friction wheels (2, 3) and a friction ring (8) arranged between the two cone friction wheels (2, 3), the pressing device is provided with a mechanical pressing unit (15) and a hydraulic pressing unit (16), wherein the mechanical pressing unit (15) exerts one pressing force to at least one cone friction wheel (3) in order to cause the cone friction wheels (2, 3) impacting with each other at the condition that the friction ring (8) is used, the device is characterized in that the mechanical pressing unit (15) does not exert pressing force or obvious-diminished pressing force when the hydraulic pressing unit (16) is in the non-pressure position.
Description
Technical field
The present invention relates to a kind of hold down gag that is used for cone ring transmission, this cone ring transmission comprises that two cone friction wheels and one are arranged on two friction rings between the cone friction wheel.
Background technique
Disclose the hold down gag that a kind of cone ring transmission is used among DE 103 48 718 A1, this hold down gag has mechanical compaction unit and hydraulic pressure compressing unit.The mechanical compaction unit that also has a spring part is applied to impacting force in these cone friction wheels one, thereby under the situation of using friction ring, these cone friction wheels can compress mutually.Compress by this, torque can be delivered on another cone friction wheel through friction ring from a cone friction wheel.
The mechanical compaction unit is supported on the bearing that bears axial force on the one hand, is supported on one of cone friction wheel on the other hand.In this case, exert pressure in the mechanical compaction unit, by this pressure, the cone friction wheel with the effect of mechanical compaction unit matching is pressed onto on another cone friction wheel by friction ring.Hydraulic pressure can be applied on the ring surface of mechanical compaction unit by the hydraulic pressure compressing unit,, the power of mechanical compaction unit extruding cone friction wheel be reduced by this hydraulic pressure.Therefore, the hydraulic pressure compressing unit is used for the impacting force that (partly) compensation mechanical compaction unit is applied.If the hydraulic pressure compressing unit is adjusted to no pressure,, do not compensate so, thereby the mechanical compaction unit makes two cone friction wheels clamp mutually constantly if the pressure promptly on the ring surface of mechanical compaction unit is changed to zero.
For security reasons can in case of emergency the torque flow in the cone ring transmission be disconnected.If for example cone ring transmission is installed in the Motor Vehicle, can in case of emergency disconnect the connection between motor and the power train so thus.In the hold down gag of DE 103 48 718 A1, come the impacting force of full remuneration mechanical driving unit can realize this torque flow interruption basically by the equilibrant force that is applied with the hydraulic pressure compressing unit.Therefore can interrupt torque flow by the hydraulic pressure compressing unit, and needn't exert one's influence the mechanical compaction unit.But the hold down gag of DE 103 48 718 A1 has such shortcoming, but promptly in case of emergency must have enough big pressure feed flow to press compressing unit to use.If but the system that in case of emergency is used to provide this pressure equally also suffers damage, then the torque flow in the cone ring transmission is no longer interrupted as requested like that.
Summary of the invention
Therefore, the objective of the invention is to, a kind of hold down gag is provided, it guarantees in case of emergency will interrupt reliably by the torque flow of cone ring transmission.
The object of the invention is achieved by following measure.Preferred embodiment can be by obtaining in the improved technological scheme.
According to the present invention, a kind of hold down gag that is used for cone ring transmission is proposed, this speed changer comprises that two cone friction wheels and one are arranged in two friction rings between the cone friction wheel, this hold down gag has a mechanical compaction unit and a hydraulic pressure compressing unit, wherein said mechanical compaction unit is applied to an impacting force at least one cone friction wheel, so that make under the situation of described friction ring that described cone friction wheel compresses mutually utilizing, it is characterized in that, when described hydraulic pressure compressing unit was in no pressure position, described mechanical compaction unit did not apply impacting force or applies the impacting force that obviously reduces.
The characteristics of described hold down gag are that when the hydraulic pressure compressing unit was in no pressure position, the mechanical compaction unit did not apply impacting force or applies the impacting force that obviously reduces.By the mechanical compaction unit be changed to zero impacting force or the impacting force that obviously reduces, two cone friction wheels compress no longer mutually, can not transmitting torque or can transmit the torque that obviously reduces thereby be arranged on two friction rings between the cone friction wheel.Therefore, in case of emergency, no longer need the hydraulic pressure compressing unit is loaded with corresponding high pressure.Therefore, even when being used for providing the system of pressure to break down, also can interrupt by the torque flow of cone ring transmission for the hydraulic pressure compressing unit.
The possibility of no pressure position " shutoff " the mechanical compaction unit by the hydraulic pressure compressing unit has attendant advantages, promptly in existing Motor Vehicle, friction ring can axial adjustment, so that adjust another velocity ratio, because friction ring is not clamped between the cone friction wheel.And when Motor Vehicle started, friction ring also can rotate at first zero loadly, so that make ring obtain good fuel feeding.And the cone ring transmission in the Motor Vehicle also can be coupled with clutch, and (normal engagement clutch) is provided under normal state under the situation that pressure that will provide or the power that will provide are not provided this clutch.
In a preferred embodiment, the hydraulic pressure compressing unit has first hydraulic piston, and the mechanical compaction unit supports is on this piston.If hydraulic piston is adjusted to no pressure, it can not strength so, and promptly the mechanical compaction unit can not be applied to impacting force on described at least one cone friction wheel owing to support.
The oil pressure that affacts on first hydraulic piston can change (schaltbar).Therefore, can load with maximum oil pressure hydraulic piston on the one hand, hydraulic piston can be adjusted into no pressure on the other hand.Under the situation of considering the hydraulic piston useful area, maximum oil pressure meets the destination greater than the maximum impacting force that is produced by the mechanical compaction unit.If this is the case, hydraulic piston has constituted fixed support to the mechanical compaction unit so.
When on-load pressure, first hydraulic piston can abut on the backstop.By this backstop, limit the exact position of hydraulic piston, the oil pressure that wherein affacts on the hydraulic piston makes hydraulic piston press to backstop.Accurately be identified for the Support Position of mechanical compaction unit thus.
In a preferred embodiment, the mechanical compaction unit has torque-force regulator, and this regulator causes axial adjustment or produces axial force according to torque.If for example torque-force regulator obtains big torque, this causes axial adjustment or axial force so, axially adjusts or axial force by this, has improved the impacting force of mechanical compaction unit, consequently, can become big by the cone ring transmission torque transmitted.
For the realization response time short especially, torque-force regulator can be designed to pure machinery.Wherein, torque-force regulator can comprise one first slope shell, the second slope shell and at least one rolling element, and this rolling element is arranged between these two slope shells and transmitting torque between the shell of slope.Two slope shells can reverse in certain rotation angle range at least relatively, wherein change the position of rolling element in these slope shells by changing two torques between the shell of slope, and wherein this change in location causes moving to axial of slope shell.
The mechanical compaction unit can have at least one spring part, and this at least one spring part helps the impacting force of mechanical compaction unit.This spring part can be in parallel with torque-force regulator or be connected in series.Also can be provided with a plurality of spring parts, these spring parts can differently be arranged.Can draw out the characteristic curve of mechanical compaction unit according to the size of connection type and spring part, because torque-force regulator, this characteristic curve depends on the torque of cone ring transmission.The spring part by being connected in parallel for example, the characteristic curve of torque-force regulator can move a definite amount with the form of initial straight from zero point.Therefore, when not having torque, the mechanical compaction unit also can produce impacting force.
In a preferred embodiment, hydraulic compressing device has one second hydraulic piston, and this second hydraulic piston is applied to additional impacting force or the equilibrant force opposite with the impacting force of mechanical compaction unit on described at least one cone friction wheel.Wherein preferably, the oil pressure that affacts on second hydraulic piston can be regulated.Because the controllability of oil pressure can be regulated synthetic impacting force by second hydraulic piston, that is be regulated impacting force and the impacting force of hydraulic drive unit or the summation of equilibrant force of mechanical driving unit by second hydraulic piston.Therefore, can in the limit of broadness, influence the composite characteristic of describing synthetic impacting force according to torque.The hydraulic compressing device that wherein has second hydraulic piston can so form, so that when the hydraulic pressure compressing unit is in no pressure position, no longer impacting force is applied on described at least one cone friction wheel by second hydraulic piston.
First hydraulic piston and/or second hydraulic piston can be configured to annular piston.Can be arranged to mutually with one heart at this first hydraulic piston and second hydraulic piston.
Between first hydraulic piston and described at least one cone friction wheel, can be provided with one first rolling bearing.By this first rolling bearing, first hydraulic piston can be applied to a pressure on the mechanical compaction unit, and needn't rotate around a spin axis in the mechanical compaction unit in a preferred embodiment.This makes the sealing of first hydraulic piston in corresponding oil hydraulic cylinder obtain simplifying.Also can make second hydraulic piston and described at least one cone friction wheel on sense of rotation, take off coupling by one second rolling body bearing in a similar fashion.
Description of drawings
Describe the present invention in detail according to an embodiment illustrated in the accompanying drawings.Shown in the figure:
Fig. 1 has the schematic representation of the cone ring transmission of hold down gag; And
Fig. 2 is with the hold down gag of the Fig. 1 shown in the ratio of amplifying.
Embodiment
Fig. 1 shows cone ring transmission, and this cone ring transmission is totally used 1 mark.Cone ring transmission 1 has first cone friction wheel 2 and second cone friction wheel 3. Cone friction wheel 2,3 layouts opposite each other, wherein their spin axis extends abreast and leaves distance mutually.The running shaft of cone friction wheel 2,34,5 is represented by a dotted line.Each cone friction wheel 2,3 has a subtended angle α.
Except cone ring transmission 1, Fig. 1 also shows the clutch 6 of the Motor Vehicle that does not further illustrate here.Between first cone friction wheel 2 and clutch 6, connect a preposition transmission device 7.This preposition transmission device 7 by the epicyclic train form can the interpreter motor-car two direction of travel (forward, backward).Under jointing state, clutch 6 by preposition transmission device 7 the transmission of torque of drive unit or motor (not shown) to first cone friction wheel 2.For this torque is delivered on second cone friction wheel 3 from first cone friction wheel 2, be provided with a friction ring 8, this friction ring 8 matches with two cone friction wheels 2,3, and surrounds first cone friction wheel 2.Friction ring 8 can move axially by the spin axis 4,5 that a regulating mechanism that does not here illustrate is parallel to cone friction wheel 2,3.By moving axially of friction ring 8, can adjust the velocity ratio of cone ring transmission 1.Because the axial position of friction ring 8 can infinitely be adjusted, so this cone ring transmission 1 has the velocity ratio that can infinitely change.
The torque that is delivered on second cone friction wheel 3 is delivered to driver element 11 by gear mesh, and this gear mesh is made up of a gear 9 and a ring gear 10 that is meshed with gear 9.This driver element 11 is made up of a differential mechanism 12 and two axle 13a, 13b.
Second cone friction wheel 3 in the axial direction, promptly on the direction of its spin axis 5 movably the supporting.The hold down gag of representing by overall usefulness 14, second cone friction wheel 3 can be depressed on first cone friction wheel 2 in the situation of utilizing friction ring 8, friction ring 8 is clamped between cone friction wheel 2,3 thus, and correspondingly be loaded with pressure, can realize from the transmission of torque of first cone friction wheel, 2 to second cone friction wheels 3 by this pressure.
Further describe hold down gag 14 with reference to Fig. 2.
Fig. 2 shows hold down gag 14 together with second cone friction wheel 3 with the ratio of amplifying.Hold down gag 14 comprises mechanical compaction unit 15 and hydraulic pressure compressing unit 16.Mechanical compaction unit 15 is made of torque-force regulator 17 substantially, and this torque-force regulator 17 is arranged in the columniform cavity 18 of second cone friction wheel 3.Cavity 18 is substantially by end face 19 and bus surface 20 limited boundaries.
Torque-force regulator 17 comprises a columniform fastening body 21, and this fastening body 21 is not connected with gear 9 with not relatively rotating.On the end 22 of second cone friction wheel 3, fastening body 21 constitutes a plurality of guide rails 23, is used to be distributed in rolling elements on the circumference of fastening body 21, ball 24 forms.In addition, these balls 24 are maintained by other guide rail 25, and these guide rails 25 roughly constitute to the transition part of end face 19 on bus surface 20 on second cone friction wheel 3.
Carry out transmission of torque by ball 24 from second cone friction wheel 3 to fastening body 21.In this case, the fastening body 21 and second cone friction wheel 3 can rotate relative to one another in certain rotation angle range.Guide rail 23,25 and by the rolling element 24 that their the keep effect that cooperatively interacts in this wise, promptly basis is delivered to torque on the fastening body 21 from ball 24, and fastening body 21 and cone friction wheel 3 are squeezed in the axial direction and are separated from each other.Torque transmitted is big more, and fastening body 21 and cone friction wheel 3 are squeezed and separate far more.
At 26 places, end that deviate from cone friction wheel 3, fastening body 21 is supported on first hydraulic piston 27.First hydraulic piston 27 is configured to annular piston and can be in the inside of oil hydraulic cylinder 28 moves along axially the direction of spin axis 5 (promptly along).Between first hydraulic piston 27 and fastening body 21, be provided with one first rolling bearing 29, this rolling bearing is delivered to the axial pressure of the first cylinder piston on the fastening body 21, but makes that fastening body 21 can be around spin axis 5 with respect to hydraulic piston 27 rotations fixing, that promptly do not rotate around spin axis 5.
Can be loaded by hydraulic pipe line 30, the first hydraulic pistons 27 with pressure.Wherein hydraulic pipe line 30 makes pressure chamber 31 be connected with valve cell 32, and this valve cell 32 will be described in the back in further detail by hydraulic piston 27 and oil hydraulic cylinder 28 gauges by pressure chamber 31.
Second hydraulic piston 33 is arranged to first hydraulic piston 27 coaxial.Second hydraulic piston 33 of annular surrounds first hydraulic piston 27 diametrically.Second hydraulic piston 33 is supported in the oil hydraulic cylinder 34 of annular movably.Opposite with first oil hydraulic cylinder 27, second hydraulic piston 33 is not to be pressed on the fastening body 21, but is pressed on the taper basal plane 36 of second cone friction wheel 3 by middle second rolling bearing 35 that connects.Wherein second hydraulic piston 33 depends on the pressure that exists in the pressure chamber 37 in order to the power on the taper basal plane 36 that is pressed in second cone friction wheel 3, and this pressure chamber 37 is by second hydraulic piston 33 and second oil hydraulic cylinder, 34 gauges.Pressure chamber 37 links to each other with valve cell 32 by hydraulic pipe line 38.
Valve cell 32 comprises selector valve 39 and modulating valve 40.On the position of rest that is spring loaded of selector valve 39, by hydraulic pipe line 30,38, pressure chamber 31,37 is adjusted to no pressure.On the contrary, on by the position of current excitation, by hydraulic pipe line 30, pressure chamber 31 is loaded with system pressure 41, and this system pressure is in the front of selector valve 39.By this system pressure 41, first hydraulic piston 27 is towards backstop 42 motions, wherein effective piston area of first hydraulic piston 27 is so determined size, so that first hydraulic piston 27 abuts on the backstop 42, even also be like this at fastening body 21 during with maximum, force extrusion piston 27.In other words, first hydraulic piston 27 forms the fixedly rigid support to fastening body 21 when loading with system pressure 41.
Second hydraulic piston 33 can be regulated by modulating valve 40 in order to the power of the basal plane 36 of pressing to second cone friction wheel 3.Therefore, on the one hand, use on the cone friction wheel 3 by the masterpiece that second hydraulic piston 33 is produced, on the other hand, the power that is produced by torque-force regulator 17 also acts on this friction wheel 3.When needed or in case of emergency, the power that affacts on the cone friction wheel 3 can be by being reduced to zero with selector valve 39 from switched to position of rest by the position of current excitation.Thus pressure chamber 31,37 is adjusted to no pressure, thereby the power that second hydraulic piston 33 affacts on second cone friction wheel 3 is changed to zero.And torque-force regulator 17 can no longer support on the fastening body 21, thereby impacting force also is changed to zero by mechanical compaction unit 15.Be provided with a plurality of springs 43, when the hydraulic pressure compressing unit is in no pressure position, make fastening body 21 turn back to definite initial position.But power 17 that produced with torque-force regulator, that be used for clamping cone friction wheel 2,3 is compared, and the active force of spring 43 is obviously less.
Therefore, can realize by hold down gag of the present invention, by hydraulic pressure compressing unit 16, under the situation of utilizing friction ring 8, by a commutation process with cone friction wheel 2,3 compress releasing mutually, thereby interrupt torque flow thus by cone ring transmission 1.Because the interruption of this torque flow can not control preposition selector valve 39 again the time, also can take place in fault.
Hold down gag 14 of the present invention also can be used for other transmission device, wherein the transmission element of transmitting torque must be clamped, so that by the incompatible transmitting torque of friction lock.
Reference character
1 cone ring transmission, 2 first cone friction wheels
3 second cone friction wheels, 4 running shafts
5 spin axiss, 6 clutches
7 preposition transmission device 8 friction rings
9 gears, 10 ring gears
11 driver elements, 12 differential mechanisms
13 (13a, 13b) 14 hold down gags
15 mechanical compaction unit, 16 hydraulic pressure compressing units
17 torques-force regulator 18 cavitys
19 end faces, 20 bus surfaces
21 fastening bodies, 22 ends
23 guide rails, 24 rolling elements/ball
25 guide rails, 26 ends
27 first hydraulic pistons, 28 first oil hydraulic cylinders
29 first rolling bearings, 30 hydraulic pipe lines
31 pressure chambers, 32 valve cells
33 second hydraulic pistons, 34 second oil hydraulic cylinders
35 second rolling bearings, 36 taper basal planes
37 pressure chambers, 38 hydraulic pipe lines
39 selector valves, 40 modulating valve
41 system pressures, 42 backstops
43 springs
Claims (12)
1. hold down gag (14) that is used for cone ring transmission (1), this speed changer comprises two cone friction wheels (2,3) and one be arranged in two cone friction wheels (2,3) friction ring between (8), this hold down gag has a mechanical compaction unit (15) and a hydraulic pressure compressing unit (16), wherein said mechanical compaction unit (15) is applied to an impacting force at least one cone friction wheel (3), so that under the situation of utilizing described friction ring (8), make described cone friction wheel (2,3) compress mutually, it is characterized in that, when being in no pressure position, described mechanical compaction unit (15) does not apply impacting force or applies the impacting force that obviously reduces at described hydraulic pressure compressing unit (16).
2. hold down gag according to claim 1 (14) is characterized in that, described hydraulic pressure compressing unit (16) has first hydraulic piston (27), and described mechanical compaction unit (15) is supported on this piston.
3. hold down gag according to claim 2 (14) is characterized in that, the oil pressure that affacts on described first hydraulic piston (27) is changeable.
4. according to claim 2 or 3 described hold down gags (14), it is characterized in that when on-load pressure, described first hydraulic piston (27) abuts against on the backstop (42).
5. according to the described hold down gag of one of claim 1-3 (14), it is characterized in that described mechanical compaction unit (15) has one torque-force regulator (17), this torque-force regulator produces according to torque and axially adjusts or produce impacting force.
6. according to the described hold down gag of one of claim 1-3 (14), it is characterized in that described mechanical compaction unit (15) has at least one spring part.
7. hold down gag according to claim 2 (14), it is characterized in that, described hydraulic pressure compressing unit (16) has one second hydraulic piston (33), and this second hydraulic piston is applied to an impacting force of adding or the equilibrant force opposite with the impacting force of described mechanical compaction unit (15) on described at least one cone friction wheel (3).
8. hold down gag according to claim 7 (14) is characterized in that, the oil pressure that affacts on described second hydraulic piston (33) can be regulated.
9. hold down gag according to claim 7 (14) is characterized in that, described first hydraulic piston (27) and/or described second hydraulic piston (33) are configured to annular piston.
10. according to the described hold down gag of one of claim 7-9 (14), it is characterized in that described first hydraulic piston (27) and described second hydraulic piston (33) are arranged to mutually with one heart.
11. hold down gag according to claim 3 (14) is characterized in that, is provided with one first rolling bearing (29) between described first hydraulic piston (27) and described at least one cone friction wheel (3).
12. according to the described hold down gag of one of claim 7-9 (14), it is characterized in that, between described second hydraulic piston (33) and described at least one cone friction wheel (3), be provided with one second rolling bearing (35).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006023648.3 | 2006-05-18 | ||
| DE200610023648 DE102006023648B4 (en) | 2006-05-18 | 2006-05-18 | Pressing device for a cone ring gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101131200A CN101131200A (en) | 2008-02-27 |
| CN101131200B true CN101131200B (en) | 2011-11-09 |
Family
ID=38622055
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007101464465A Expired - Fee Related CN101131200B (en) | 2006-05-18 | 2007-05-18 | Contact device for cone ring transmission |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5392996B2 (en) |
| CN (1) | CN101131200B (en) |
| DE (1) | DE102006023648B4 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4924511B2 (en) * | 2008-03-31 | 2012-04-25 | アイシン・エィ・ダブリュ株式会社 | Power transmission device |
| JP5012621B2 (en) * | 2008-03-31 | 2012-08-29 | アイシン・エィ・ダブリュ株式会社 | Power transmission device |
| DE112009003633T5 (en) * | 2008-12-26 | 2012-08-16 | Aisin Aw Co., Ltd. | Continuously variable friction gear |
| JP2011085255A (en) * | 2009-09-18 | 2011-04-28 | Aisin Aw Co Ltd | Drive device |
| CN102959278B (en) * | 2010-06-24 | 2015-11-25 | 乌尔里克·罗斯 | Bevel friction ring gearing |
| DE102011013070A1 (en) * | 2011-03-04 | 2012-09-06 | Ulrich Rohs | Conical friction ring gearbox has friction ring with circular friction ring outer edge between friction ring outer surface and outer friction surface, where radius of friction ring outer edge is preset times of friction ring width |
| US9212743B2 (en) * | 2012-05-29 | 2015-12-15 | Gm Global Technology Operations, Llc | Containment control for a continuously variable transmission |
| CN102817984B (en) * | 2012-08-27 | 2015-05-06 | 北京理工大学 | Axial-loading biconical traction drive device |
| CN104006127B (en) * | 2014-06-06 | 2016-08-24 | 张阳松 | Buncher and be provided with the motor vehicles of this buncher |
| CN108591381B (en) * | 2018-04-12 | 2021-11-16 | 江苏理工学院 | Novel cone pulley transmission stepless speed change system |
| CN114100742A (en) * | 2021-11-19 | 2022-03-01 | 哈尔滨职业技术学院 | Crushing device of biological pharmaceutical equipment and operation method |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1724972A1 (en) * | 1990-01-03 | 1992-04-07 | Камский политехнический институт | Variable speed drive |
| US5924953A (en) * | 1997-05-21 | 1999-07-20 | Rohs; Ulrich | Friction cone gearing |
| US6277048B1 (en) * | 1998-08-18 | 2001-08-21 | Ulrich Rohs | Conical friction ring gear and process for regulating the transmission ratio in a conical gear |
| DE10361546A1 (en) * | 2003-01-06 | 2004-07-15 | Ulrich Dr.-Ing. Rohs | Friction gears operating method, involves compressing input portion and output portion, one against another, by compression device where compression device functions with characteristic state of compressed operating force |
| CN1623053A (en) * | 2002-10-07 | 2005-06-01 | 乌尔里克·罗斯 | Transmission |
| DE10348718A1 (en) * | 2003-06-17 | 2005-06-30 | Ulrich Dr.-Ing. Rohs | Compression device for tensioning intermeshing gearing elements of friction gearing in automobile operated in dependence on detected parameter for preventing slip |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02168055A (en) * | 1988-12-22 | 1990-06-28 | Kubota Ltd | Friction type continuously variable speed change gear |
| WO2004031617A2 (en) * | 2002-09-30 | 2004-04-15 | Ulrich Rohs | Gearbox consisting of infinitely variable adjustable partial gear mechanisms |
| DE112004001100D2 (en) * | 2003-06-17 | 2006-02-23 | Ulrich Rohs | Friction gear and method for operating such a friction gear |
-
2006
- 2006-05-18 DE DE200610023648 patent/DE102006023648B4/en not_active Expired - Fee Related
-
2007
- 2007-05-18 JP JP2007133330A patent/JP5392996B2/en not_active Expired - Fee Related
- 2007-05-18 CN CN2007101464465A patent/CN101131200B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1724972A1 (en) * | 1990-01-03 | 1992-04-07 | Камский политехнический институт | Variable speed drive |
| US5924953A (en) * | 1997-05-21 | 1999-07-20 | Rohs; Ulrich | Friction cone gearing |
| US6277048B1 (en) * | 1998-08-18 | 2001-08-21 | Ulrich Rohs | Conical friction ring gear and process for regulating the transmission ratio in a conical gear |
| CN1623053A (en) * | 2002-10-07 | 2005-06-01 | 乌尔里克·罗斯 | Transmission |
| DE10361546A1 (en) * | 2003-01-06 | 2004-07-15 | Ulrich Dr.-Ing. Rohs | Friction gears operating method, involves compressing input portion and output portion, one against another, by compression device where compression device functions with characteristic state of compressed operating force |
| DE10348718A1 (en) * | 2003-06-17 | 2005-06-30 | Ulrich Dr.-Ing. Rohs | Compression device for tensioning intermeshing gearing elements of friction gearing in automobile operated in dependence on detected parameter for preventing slip |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102006023648B4 (en) | 2009-08-13 |
| DE102006023648A1 (en) | 2007-11-29 |
| JP2007309522A (en) | 2007-11-29 |
| CN101131200A (en) | 2008-02-27 |
| JP5392996B2 (en) | 2014-01-22 |
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