DE102004031418A1 - Crankshaft torque converter, for torque control of torque absorption and torque transmission of crank mechanisms - Google Patents

Abstract

The invention relates to a crank drive torque converter, for torque control of torque absorption and torque transmission of crank gear, in particular of - hand, reciprocating, engine and pedal crank - which smoothes the torque fluctuations in crank mechanisms. The disadvantages of the rotational force transmission of the crank mechanism to the constant resistance force, caused by the different fall or lifting speeds on the different tangential leverage on the crank mechanism during a working stroke, cause too long a translation in the top and bottom dead center and a too short translation in the middle Rotary cutting of the crank mechanism during a working stroke, which leads to high torque fluctuations. For this purpose, an eccentric gear, which is arranged between the rotational force of the crank mechanism and the constant resistance force and translated with the rotating component of the eccentric function for crank operation with two to one and adjusted at the time of control to the crank position, causes the control of a lag of the crank mechanism, between two shared overruns to the constant resistance, during a crankshaft stroke. Thus, the Kurbeltriebmomentwandler the respective fall or lifting speed, the tangential leverage, closer to.

Description

The The invention relates to a crank drive torque converter for torque control the torque absorption and torque transmission of crank mechanisms, especially from - hand, Reciprocating, machine and pedal cranks - which reduces the torque fluctuations during crank mechanisms during smoothing a crank drive stroke or decimated.

It is known that in the torque transmission of crank mechanisms up to a resistance, translations in the form of gearbox or torque converter as power transmissions be used, whereby by the constant resistance force, if this big enough is, a steady speed in the specified ratio at the Crank drive pretends, whereupon the tangential force on the crank mechanism acts.

Of the Disadvantage of the torque transmission of the crank mechanism to the constant resistance, lies in the Rotational force fluctuations due to the irregular force on the rotary motion of the crank mechanism and cause that alternately too much and too little Force is present. The reasons for that were above all at the force effects in the areas of the upper and lower Dead center of a working stroke of the crank mechanism, wherein the vertical Force of the falling or lifting speed on the tangential leverage, as well as its lever travel is the lowest and thus too little of the power, for lack of proper translation implements. In contrast, the force impact is the focus a working stroke at 90 ° of Crank radius, where the vertical force of the fall speed up the tangential leverage, as well as its lever travel is highest, too short translated, what an optimal power transmission contrary, with which the whole Kraftdrehweg to a low efficiency the applied power leads.

Of the Invention is based on the object for each position of the crank radius a better translation between the vertical force of the falling or lifting speed on the tangential leverage and its respective lever travel to allow the crank mechanism. For this purpose, the fall or lifting speed in the areas of upper and lower dead center a much higher speed because of achieve the lowest tangential leverage on the crank mechanism, and in between at 90 ° crank radius a much lower speed because of the highest tangential Leverage, so the torque fluctuations on the crank mechanism to minimize.

The The object is achieved according to the invention, the a Kurbeltriebmomentwandler, for torque control of the torque absorption and torque transmission of crank mechanisms, by the conversion of uniform rotational speeds of the crank mechanism in periodic different rotational speeds while crankshaft rotation, in particular of - hand, reciprocating, Machine and pedal drives -, arranged and installs directly or indirectly between the torque of the Crankshaft and the resistance, equipped with at least an eccentric whose rotating component of the eccentric function, for Crankshaft with two to one translates and is adjusted to the crank position at the time of the control, and the control of a lag of the crank mechanism, between two shared leads to the constant resisting force during one Crankshaft stroke causes.

Based the following example, with a crank drive on a bicycle, its rear wheel during power transmission equipped with no freewheel, is the basic idea of the invention clarified. At full power from upper to lower Dead center on its pedal, without resistance on the rear wheel, would the Stroke speed on the pedal remain almost the same. It would become the rear wheel, as well as the crank drive axle at the pedal stroke first fast, then slower and faster again, due to the undisturbed force curve without the constant resistance. In order to maintain a constant resistance, the no changing rotational speeds within a working stroke the crank drive permits, a advantageous matched stroke speed in the crank mechanism too enable, is an eccentric invention as a power transmission, set between the crank mechanism and the constant resistance force, so that the crankshaft axis despite constant resistance, first fast, then slower and faster again. This causes the eccentric an eccentric orbital speed, of slow up to fast per revolution, passing through the connection at the constant Resistance, where the orbital velocity remains the same, and at the connection to the crank drive an eccentric rotational speed is given.

There the crank mechanism only makes half a turn during a working stroke, must the Leading and lag of the orbital speed, by a full Exzenterumdrehung done, including the eccentric to the crank mechanism, two according to the invention one translated becomes.

Because the crank mechanism during the working stroke, first fast, then slower and faster to run again, according to the invention, the timing of the eccentric to the crank position such that the lead of the crank mechanism is divided into the constant resistance force, preferably at the top and bottom dead center, with the lag being therebetween. Due to the double speed of the eccentric to the crank mechanism, the workflow is repeated from 180 ° to 360 ° of the crank position, whereby a second oppositely arranged crank could start the same stroke of action when the first crank has ended its action stroke. Due to the selected arrangement of the control time of the eccentric, to the position of the crank mechanism and the uniform rotation by the constant resistance force, the eccentric causes the crank mechanism to the constant resistance, preferably from the top dead center at 0 ° to 45 ° always slower leading from 45 ° to 90 ° to the constant resistance lags more and more, from 90 ° to 135 ° less and less lags, from 135 ° to 180 ° faster and faster, from 180 ° to 225 ° always slower, from 225 ° to 270 ° always lags more and leads faster and faster from 315 ° to 360 °. The lead causes a faster rotation of the crank mechanism and the lag causes a slower rotation of the crank mechanism to the constant rotation of the resistance force. At 0 ° and 180 ° in the lead, and at 90 ° and 270 ° in the lag, the crank drive and the constant resistance force overlap at each revolution. At the intersections, the force transmission point on the eccentric is in relation to the crank gear, even at an upper or lower dead center, and makes use of the inertia of the known crank drive system, since the transition takes place very slowly in the slowest and fastest areas. As a result, the ratio change runs from the crank mechanism to the constant resistance force, rising from 0 ° to 90 °, falling from 90 ° to 180 °, increasing from 180 ° to 270 ° and falling again from 270 ° to 360 °. Due to the smooth transitions of fore and aft, the torque fluctuations on the crank mechanism are greatly reduced and the efficiency against the constant resistance or load forces is increased.

Of the Advantage of advances and retardations in the working stroke of the crank mechanism You can see very clearly when approaching a very steep mountain with a usual Recognize bicycle, with the bike in the main power range of the force-carrying Pedal from about 45 ° to 135 °, especially at 90 ° of Crankshaft position very jerkily accelerated forward, and through the longer continuing phase of the subsequent 45 ° of Crank drive at bottom dead center, and the subsequent 45 ° in the upper Dead center, with its ever slowing stroke speed almost comes to a standstill, and thus loses all momentum and must rebuild.

At the Use of a crank drive torque converter, the unfavorable phase in the top and bottom dead center, of two times 45 ° of the crank mechanism, clearly faster and with noticeable Torque completed, and the main force range of 90 °, can thereby still take momentum from the otherwise powerless phase and implement which is also advantageous for use with pedal boats.

The the same advantage is achieved even with hand crank drives, such. in winches with a crank, whereby a predetermined forced position, tear through or press on the crank, which uses strength and the reversal points faster operated with more torque, but without crank drive torque converter at the reversal points with very strong resistance, mostly stand sideways and press would have to, where the exercise of power less becomes.

at Steam locomotives could be observed, when driving under heaviest load, the drive wheels which are driven as a crank mechanism, in the crank position began to spin on the rail, where the greatest force the irregular torque was free, with a Kurbeltriebmomentwandler, the torque would be transmitted smoothed because the greatest power is not delivered in a small rotating field cutout. As well an advantage is the use of a home exercise bike with pedal crank drive, where you go to the big one Inertia, for the Good concentricity, can do without and the devices significantly lighter become.

at Reciprocating engines also achieves the crank drive torque converter the advantage at 0 ° to 180 ° and at 180 ° to 360 ° in the Crankshaft, which is why he in the versions as a single cylinder, or Multi-cylinder offset by 180 ° Crank jaws used with equally distributed work strokes per periodic processes can be.

As well would be an advantage an insert for controlling the rotational force of a second crankshaft in a two-stroke engine, with twin pistons in a common cylinder. Where the second crankshaft, over the first drive crankshaft is arranged, and one between them Powering auxiliary piston with very eccentric lifting speeds, which runs in the working cylinder of the working piston and burned there Exhaust gases in the downward movement ejects and the Working cylinder with the upward movement with Fresh gas filled.

According to various preferred embodiments of eccentric types according to the invention, said objective is achieved by use of rotary ring eccentric, or gear eccentric, or chain or toothed belt eccentric, or chainring or sprocket eccentric, or toothed belt pulley or toothed belt wheel eccentric enough.

there can the eccentric optionally on the axes of the crank mechanism, or the power transmission, or the resistance force and their power transmission over the Type of gear, or gear, or chain, or toothed belt drive, or crank drive.

The power transmission between the crank mechanism and an eccentric is with the speed ratio from one to two or other translations in the manner of a transmission or by crank or chain or gear or belt drives performed and on axes of the crank mechanism or the power transmission or the resistance, rotatable or fixed.

In Another embodiment of the invention is the so-called lifting height of the eccentric adjustable in order to vary the amount of advance and retardation, by performing the adjustment in stages or stepless to the torque of the crank mechanism at variable speeds and load changes, to adapt the flywheel.

A further increase of the invention can be achieved by that the Control times of the eccentric to the crank drive position, also in Stages or Infinitely adjustable to better the flywheel To be able to handle or in order to enable an optimal body position with handwheel drives, or even when standing uphill on the bike the pitch angle To compensate, as with reciprocating engines to the timing with the ignition timing, optimally adapt.

Further Details, features and advantages of the invention will become apparent from the following eight embodiments, of preferred embodiments and applications. The invention includes design features, combinations of elements and arrangements of parts, in different applications, which are given only as examples below and thus interchangeable, and will become apparent from the attached drawings explained in more detail.

It shows:

1 Drawings page 1 with the reference list 1 on page 11 A crank drive torque converter with chain drive eccentric, on a hand crank drive, in 1a as an exploded view and in 1b as an isometric projection,

2 Drawings page 2 with the reference list 1 on page 11 Function sequence of 1 , as a schematic drawing,

3 Drawings page 3 with the reference list 1 on page 11 systematic operation of the complete drive system in the sequence, in ten view positions,

4 Drawings Page 4 with the list of reference numbers 1 on page 11 Component for eccentric stroke adjustment of 1 and 2 , in 4a as axial section and in 4b as a cross section along the line I-I of 4a in zero position of the eccentric stroke,

5 Drawings page 5 with the reference list 1 on page 11 Component for eccentric stroke adjustment of 1 and 2 , as a cross section along the line I-I of 4a , in minimum position of the eccentric stroke,

6 Drawings page 5 with the reference list 1 on page 11 Component for eccentric stroke adjustment of 1 and 2 , as a cross section along the line I-I of 4a , in maximum position of the eccentric stroke,

7 Drawings page 6 with the reference list 1 on page 11 a crank drive torque converter with gear drive eccentric, on a hand crank drive, in 7a as an exploded view and in 7b as an isometric projection,

8th Drawings page 7 with the reference list 2 on page 16 a crank drive torque converter with rotary ring eccentric, for mounting on the rear wheel axle of a bicycle, in 8a as an exploded view and in 8b as an isometric projection,

9 Drawings page 8 with the reference list 2 on page 16 Function sequence of 8th , as a schematic drawing,

10 Drawings page 9 with the reference list 2 on page 16 Adjustment functions of the eccentric stroke and the eccentric control times of 8th in six views,

11 Drawings page 10 with the reference list 3 on page 19 a crank drive torque converter with rotary ring eccentric, for mounting on the pedal crank axle of a bicycle, in 11a as an exploded view and in 11b as an isometric projection,

12 Drawings page 11 with the reference list 4 on page 23 a crank drive torque converter with rotary ring eccentric, for installation in a special bicycle frame, as an exploded view and in isometric projections,

13 Drawings page 12 with the reference list 5 on page 27 a crank drive torque converter with rotary ring eccentric, for mounting on reciprocating engines, axial section in simple representation,

14 Drawings page 13 with the reference list 5 on page 27 cross section according to the line II of the 13 .

15 Drawings page 13 with the reference list 5 on page 27 cross section along the line II-II of the 13 .

16 Drawings page 14 with the list of references 5 on page 27 cross section along the line III-III of the 13 .

17 Drawings Page 14 with the reference list 5 on page 27 Cross-section according to the IV-IV line of the 13 .

18 Drawings page 15 with the reference list 5 on page 27 Arrangement concept of 12 , as a conceptual drawing,

19 Drawings Page 16 with the reference list 5 on page 27 Arrangement concept of 12 , as a conceptual drawing,

20 Drawings page 17 with the reference list 5 on page 27 Arrangement concept of 12 , as a conceptual drawing,

21 Drawings page 18 with the reference list 6 on page 29 a crank drive torque converter with sprocket eccentric, for mounting on the rear wheel axle of a bicycle, in side view,

22 Drawings page 19 with the reference list 6 on page 29 systematic mode of action of the complete drive system, in the expiration of the sprocket eccentric, in ten view positions,

23 Drawings page 20 with the reference list 6 on page 29 and adjustment effects of the eccentric stroke on rotating field cutouts of 21 in four views.

A first preferred embodiment according to The invention shows at the beginning, after the reference character list 1, a Winch drive with crank drive torque converter in the manner of a chain drive cam, because thus the eccentric function to the crank mechanism, in the drain below The angular divisions on the basis of drawings, can best explain.

The in 1 illustrated hand crank drive with chain drive eccentric consists of a hollow shaft 1 passing through the support frame 2 leads and is arrested. The eccentric driven chainring 3 is with the Mitnehmerarm 4 firmly connected and runs with two thrust washers 5 , in front of and behind each, rotatable and slidably mounted on the hollow axle 1 , and is connected to the constant resistance force via a chain (not shown in the drawing). Next to it sits the timing chain 6 that with a splined connection 7 , on the hollow axle 1 arrested and with the hollow axle nut 8th is secured. The chain pinion holder 9 , is with an off-center eccentric seated eccentric pin 10 provided, the a rolling bearing eccentric race 11 receives, as well as with the concentric chain sprocket 12 firmly connected and concentric and sliding with the sprocket axle 13 at the Kurbeltriebarm 14 screwed. The crank handle bar 14 is with the crank drive axle 15 firmly connected, the sliding bearings in the hollow axle 1 with two thrust washers 16 runs and with two crankshaft nuts 17 is secured. The timing chain 6 is via the timing chain (not shown in the drawing) with the sprocket 12 , which is half the size of the timing chain, connected and the rolling bearing eccentric race 11 sits in the eccentric track 18 of the driving arm 4 ,

The functional sequence is in 2 shown. At the selected starting point, the timing of the crank mechanism is the top dead center with 0 ° degrees, the eccentric 11 also stands at 0 ° degrees to the chain sprocket axis 13 , this is the crank drive position and the position of the driver 4 from the constant resistance at the point of intersection,

When turning the turn handle 19 to the right in the clockwise direction from 0 ° to 45 °, the sprocket turns 12 90 ° to the left because it's over the timing chain 20 with the fixed timing chain 6 is connected and because the timing chain 6 has twice the effective diameter. This turns the eccentric 11 in the eccentric track 18 from the driving arm 4 also by 90 ° to the left, bringing the eccentric output link leaf 3 , firmly connected to the driving arm 4 , which rotates less than 45 ° to the right, causing the crank drive, to the constant speed running at a constant speed on the output sprocket 21 that go beyond the drive chain 22 with the eccentric drive chain blade 3 is connected, leads.

As in 2 , is represented in all further rotations of the crank mechanism by 45 ° in eight positions, it can be seen that the crank mechanism, from 0 ° to 45 °, from 135 ° to 180 °, from 180 ° to 225 ° and from 315 ° to 360 ° precedes the constant resisting force, and travels from 45 ° to 135 °, and from 225 ° to 315 °, and is located at 0 °, 90 °, 180 ° and 270 °, in the point of intersection with the resistance force. Since the area of action repeats every 180 °, occurs the advantageous torque increase from 180 ° to 360 °, the effect in the hand crank drive also in the upstroke engages, and at a second opposite crank, such as pedal cranksets, with each downward stroke of a crank, as in 3 is apparent.

In 3 the ratio change of the crank mechanism during a working stroke is shown as an example. While the constant drag on the output sprocket 21 turns evenly through 45 °, recognizable in the 3a to 3y at the turning mark 23 , the rotational path of the Kurbeltriebarm changes 14 , visible from the rotating field cutout 24 before. Thereby sets the Kurbeltriebarm 14 its rotary path, for each rotary field cutout 24 , in the same time back, where it turns the fastest in the largest spin range, and slowest in the smallest. As a result, the lifting speed is better aligned to the tangential leverage, resulting in an increase in torque.

The extent of the fore and aft is determined by the eccentric stroke, which is the distance from the sprocket axis 13 and the eccentric 11 , as well as the distance from the crankshaft axis 15 to the sprocket axle 13 ,

Another embodiment of the invention, the adjustment of the Exzenterhub in several stages, in 4 . 5 and 6 is pictured.

This will be done in 4 , on chain pinion holder 9 , a trunnion eccentric off the axis as the adjustment axis 25 attached, whereupon the adjusting disk 26 rotatably and eccentrically eccentrically mounted, which is also eccentric and off-center the eccentric end pin 10 receives, the rotatable and sliding eccentric race 11 leads. The adjustment axis 25 contains adjustment holes 27 , wherein the locking pin 28 by pressure from the compression spring 29 , clicks into place. The locking pin 28 is in the guide sleeve 30 guided, which vertically at the location of the adjusting disc 26 where it is a hole to the adjustment axis 25 having. The compression spring 29 is in the guide sleeve 30 from the safety screw 31 secured. About the at the adjusting disc 26 attached guide sleeve 30 becomes the adjusting lever tube 32 This is a transverse sapwood 33 having, by the Verstellhebelrohr 32 through a bayonet adjustment groove 34 in the guide sleeve 30 across the locking pin 28 leads, and so is secured.

As in 4b it can be seen, the distance from the axes of the eccentric end pin 10 and the adjustment axis 25 so chosen, that in the latching at 4b the eccentric function is out of service because of the eccentric 11 concentric with the chain sprocket axis 13 runs and the power flow in 2 from the swivel handle 19 over the sprocket axle 13 , directly over the driving arm 4 with the eccentric drive chain blade 3 would run without an eccentric function in the eccentric track 18 perform.

The adjustment of the Exzenterhub takes place by, when the crank mechanism, the Verstellhebelrohr 32 turns, so that the sapwood 33 in the bayonet guide groove 34 the guide sleeve 30 with the locking pin 28 turns and up against the pressure of the compression spring 29 pull, while the locking pin 28 from the adjustment hole 27 the adjustment axis 25 pushes and by a lateral turn on Verstellhebelrohr 32 , the adjusting disc 26 with the eccentric endpin 10 and eccentric race 11 on the adjustment axis 25 until the next adjustment hole 27 rotates 5 and 6 , and by the compression spring 29 the locking pin 28 engage again and by rotation in the bayonet guide groove 34 back up again. Thus, the rotational force of the crank mechanism, the respective requirements in terms of speeds, load change and inertia can be adapted meaningfully.

In a further designed embodiment, the control time of the eccentric can be adjusted to the crank mechanism in one or more stages with simple means by also the hollow axle 1 (please refer 1 ) in their attachment, rotatable and lockable outfit, and as in 2 explained, the effect can be used in any required angle, which allows an optimal body position, especially in hand crank drives.

A second preferred embodiment of the invention, according to the reference numeral list 1, a hand crank drive with crank drive torque converter in the manner of a Zahnradtriebexzenter in 7 ,

The Zahnradtriebexzenter consists of a driven gear 35 , on whose waistband the drive disc 36 with the driving screws 37 connected, and runs with two thrust washers 5 , in front of and behind each, rotatable and slidably mounted on the crank axle 38 , and is connected to another gear with the resistance force (not shown in the drawing). Behind it is rotatably and slidably mounted the eccentric receiving disc 39 , The planetary gears 40 are on the front side behind the bearing collar, with eccentrically eccentric arranged end pins 41 formed in the eccentric guides 42 the drive disc 36 lead, and are with the bearing collar in the eccentric receiving disc 39 , rotatable and sliding. Between the planetary gears 40 , the control gear engages 43 one, which is twice the number of teeth as the planetary gears 40 and with a splined connection 7 on the crank axle 38 arre is animal. The housing ring 44 comes with the housing screws 45 passing through the crank arm plate 46 lead, with these to the eccentric receiving disc 39 attached, being in the crank arm plate 46 , the journal of the planetary gears 40 are rotatably mounted slide. The crank arm plate 46 rotates sliding on the crank axle 38 , and is with a bearing bolt 47 secured.

The operation of the gear drive eccentric is the same as in the chain drive eccentric in the first preferred embodiment, except for the position of the eccentric at the timing of the crank mechanism. Because when turning on the crank handle 19 to the right in clockwise direction from 0 ° to 45 °, the planetary gears 40 with the eccentric seated endpin 41 , about that with double the number of teeth, fixed control gear 43 , turns 90 ° to the right and not to the left, as with the chain drive eccentric, the end pin must 41 to the basic setting as with the chain drive eccentric rotated by 180 °. So that the end pin 41 in the eccentric guide 42 , the driving disc 36 with the output gear 35 , does not drive in the wrong direction and makes outcallings, retards and vice versa.

As with the embodiment as a chain drive eccentric, there is also the possibility of attaching a second crank here, when using a hollow axle 1 (as in 1 shown), and a fixed connection from the crank drive axle 15 (as in 1 shown) to the crank arm plate 46 , and vice versa the chain drive eccentric, with a crank axle 38 and rotatable Kurbeltriebarm 14 (as in 1 shown) is provided.

Likewise, as with the chain drive eccentric, the timing can also be adjusted with the same means and the eccentric stroke adjustment (as in FIG 4 shown), preferably with a planetary gear.

01

hollow shaft

02

support frame

03

Exzenterabtriebskettenblatt

04

driver arm

05

thrust washer

06

Control chainring

07

Spline connection

08

Hohlachsmutter

09

Sprocket holder

10

Exzenterstirnzapfen

11

Exzenterlaufring

12

sprocket

13

Sprocket axis

14

Kurbeltriebarm

15

Crank axle

16

thrust washer

17

Kurbelachsmutter

18

Exzenterlaufschiene

19

Crank handle

20

timing chain

21

driven sprocket

22

drive chain

23

rotary labeling

24

Rotating field cut

25

adjustment axis

26

adjusting disk

27

adjustment holes

28

locking pin

29

compression spring

30

guide sleeve

31

locking screw

32

Verstellhebelrohr

33

cotter

34

Bajonettverstellungsnut

35

output gear

36

driver disc

37

Mitnehmerschrauben

38

crank axle

39

Exzenteraufnahmescheibe

40

Planet gear

41

trunnion

42

Exzenterführungen

43

timing gear

44

housing ring

45

housing screws

46

Kurbelarmplatte

47

Bearing collar screw

A third preferred embodiment according to the invention, according to the reference character list 2, in 8th as a crank drive torque converter a rotary ring eccentric, which is provided for installation in a bicycle with hub gear and shift guide by the rear wheel axle as an example, which is placed on the fixed rear axle, because of the favorable translation solution to the crank mechanism and the space advantage offered for the components.

It is a version that is equipped with a stepless Exzenterhubverstellung, as well as with a stepless timing adjustment, wherein in 8th , the eccentric stroke is set to zero, and the timing is exactly at TDC.

For this purpose, a commercial bicycle is used with hub gear, which is preferably already translated with one to two with a primary ratio of the chainring on the bottom bracket, chain sprocket on the rear hub. Instead of the output flange to the planetary gear with attached chain sprocket on the rear hub, a force distribution flange 1 used, which consists of a gearbox flange 2 with gearbox attached to it schmit participants 3 consists of what a rolling bearing 4 for rotatably receiving the chain pinion holder 5 , is mounted. The drive holder end pin 6 with safety collar, slidably takes the drag lever for the eccentric drive 7 on and is in the drive holder 8th bolted and will be with him along with the sprocket 9 , on the chain pinion holder 5 bolted, bringing the chain sprocket 9 on the power distribution flange 1 is rotatable. The output shaft end pin 10 with safety collar, slidably takes the drag lever for the eccentric drive 11 on and is in the output holder 12 bolted to the collar of the Getriebeflanschmitnehmer 3 is bolted, and thus translated directly to the hub gear. From the rotatable output holder 12 , the left side of the bicycle frame against rotation secured rear axle protrudes 13 , concentric.

The eccentric component 14 consists of a rotary ring holder 15 , with an internal rotating ring 16 is provided and the on the "Rolling in Exzenterbauteil 17 "is rotatably mounted.

The eccentric receiving pin 18 includes a safety collar and is rotatably mounted sliding, through the Exzenteraufnahmebohrung 19 of the eccentric receptacle holder 20 guided, and in the Exzenterbauteil 14 screwed. This is the eccentric component 14 with the eccentric receptacle holder 20 rotatably connected.

The "lock carriage for the stroke adjustment 21 ", is the" lock nut of the stroke adjustment 22 ", on the" spindle shaft for the stroke adjustment 23 ", between the receptacles 24 , guided. This is the spindle shaft 23 with the "locking ring of the stroke adjustment 25 "on the eccentric receptacle holder 20 secured.

The eccentric component 14 is through the receiving recess at the front of the "lock slide of the stroke adjustment 21 "is guided, and is with the" lock slide bolt lock 26 "with collar and thread, through the bolt receiving hole 27 and through the bolt securing hole 28 in the "lock slide of the stroke adjustment 21 "bolted, bringing the eccentric component 14 on the eccentric receptacle holder 20 locked against rotation.

The "retaining plate of the Stellscheibekappe of the stroke adjustment 29 ", is on the" spindle shaft of the stroke adjustment 23 "pushed and the eccentric receptacle holder 20 screwed, whereupon the "adjusting disk of the stroke adjustment 30 "with the square drive of the stroke adjustment 31 This is covered by the "adjusting cap of the stroke adjustment 32 ", the" adjusting disc of the stroke adjustment 30 "off, and is due to the edge fit of the retaining plate 29 guided and of the "clamp of the stroke adjustment 33 " held.

The eccentric receptacle holder 20 , is with the eccentric component 14 and the sled 21 with the components of the locking and adjustment, via the axle receiving bore 34 on the rear wheel axle 13 postponed. This is the eccentric drive spigot 35 with safety collar, rotatable and slidingly supported by the drive bearing bushing 36 at the rotary ring 16 guided, and in the "drag lever for the eccentric drive 7 Also screwed is the eccentric output pin 37 with safety collar, rotatable and slidingly supported by the output bearing bushing 38 at the rotary ring 16 guided, and in the "drag lever for the eccentric drive 11 "screwed.

The "lock slide for the timing adjustment 39 ", by the lock nut on the" spindle shaft for the timing adjustment 40 ", between the recording bars 41 of the frame hitch holder 42 , guided. This is the spindle shaft 40 with the "locking ring of the timing adjustment 43 "on the frame attachment holder 42 secured. The "retaining plate of the dial cap from the timing adjustment 44 "is on the" spindle shaft of the timing adjustment 40 "pushed and attached to the frame attachment holder 42 screwed, whereupon the "adjusting disk of the timing adjustment 45 "with the" square recording of the timing adjustment 46 On it covers the "Stellscheibekappe the Steuerzeitverstellung 47 ", the" adjusting disk of the timing adjustment 45 "off, and is due to the edge fit of the retaining plate 44 guided and of its clamp 48 held.

The frame attachment holder 42 , is with the sled of the timing adjustment 39 and with the components of the locking and adjustment, over the Radachsenaufnahmebohrung 49 against the eccentric holder 20 on the rear wheel axle 13 postponed. This is the Exzenteraufnahmehalter 20 over the drawbar 50 , with the "lock slide of the timing adjustment 39 "on the frame attachment holder 42 connected. The connection takes place on the one hand, via the Zugstangenstirnzapfen 51 with safety collar, which is the drawbar 50 rotatable in the receiving bore 52 leads and on the eccentric holder 20 is screwed. On the other hand, the drawbar 50 through the receiving recess at the front of the "lock slide of the timing adjustment 39 "is guided, and is with the" lock slide bolt of the timing adjustment 53 "with collar and thread, through the guide hole 54 over the bolt hole 55 screwed. Finally, the frame attachment holder 42 , on the rear axle 13 with an axle securing ring 56 secured axially, and with a screw through the frame bore 57 on the bicycle frame 58 , in the holder hole 59 secured against rotation, and provided with a bolted housing with gaskets (not shown in the drawing), to protect against dust and dirt.

For stroke adjustment are two cables 60 , which are actuated by a rotary handle on the bicycle handlebar, by the cable guide 61 in the wheel cap 32 , in the guide grooves of the adjusting disc 30 guided and in the nipple holder 62 hooked. Similarly, in the control timing adjustment two cables 63 , which are actuated by an adjusting lever on the handlebars, through the cable guides in the Stellscheibekappe 47 , guided in the guide grooves of the adjusting disc and in the nipple holder 64 hooked. Thus, the crank drive torque converter is in the nature of the rotary ring eccentric, on the rear wheel axle 13 next to the rear wheel 65 , between the rear hub 66 and the axle mount on the bicycle frame 58 and gets off the bottom bracket via the drive chainring 67 , which is twice the number of teeth as the sprocket 9 has, driven directly by a chain, and passes the torque directly to the rear hub, or via a hub gear on.

When removing the rear wheel 65 from the bicycle frame 58 , In addition, the screw on the frame bore 57 (or alternatively on a clamp on the frame) and the clamps 33 and 48 from the parking disc caps 32 and 47 be solved to the Stellscheibekappen with the adjusting discs 30 and 45 and the cables attached to it 60 and 63 (from the stroke and timing adjustment), from the holding plates 29 and 44 and the square shot 31 and 46 to separate.

In the functional sequence 9a and b, pull the sprocket 9 (powered by a chain from the drive chainring 67 ), above the drive holder 8th with the end pins 6 the rocker arm 7 , in turn, over the endpin 35 the rotary ring 16 pulling in a rotary motion. A second endpin 37 on the rotation ring 16 , pulls on the drag lever 11 who again over a trunnion 10 the drive holder 12 in a rotary motion, and thus in conjunction with the resistance. By the distance between the rear wheel axle 13 and the axis point 68 from the rotation ring 16 , an eccentric function occurs because the rocker arms 7 and 11 , on the circular path of the rotation ring 16 are arranged in its circle radius to a predetermined distance and the other end of the finger levers 7 and 44 , in each case on one of the independent drivers 8th and 12 are connected, and on its axis 13 , the two circular paths intersect twice, causing the drivers 8th and 12 in the radius at each half turn, once very close in the "position minimum 69 "and once quite far in the" position maximum 70 "and thus the speed of rotation within the power flow varies, thereby changing the arrangement of the bushings 36 and 38 for receiving the rocker arms 7 and 11 in the rotation ring 16 chosen so that both drag levers exert their power transmission as Zugbauteil, rather than as a pressure member to keep the dimensions of the components as small as necessary.

The eccentric position in 9a , corresponds by the selected basic adjustment of the chain to the crank mechanism, the pedal positions in 9b and 9c , also corresponds to the eccentric position in 9d , the pedal positions in 9e and 9f , In the movement sequence this corresponds to the order of 9b . 9e . 9c and then 9f because the eccentric rotates through 180 °, with a pedal travel of 90 °, as at the pedal positions 71 can be seen.

The effect of the constant resistance force, on the crank drive torque converter in the type of Rotationsringexzenter on the crank mechanism, that of the first embodiment and has been described there and in the 2 and 3 , explained in more detail.

The function of the infinitely variable eccentric stroke adjustment is in 8th and 10 apparent, wherein by rotation of the rotary ring holder 15 on the eccentric receiving pin 18 , the "axle point of the rotation ring 68 " in 9 , from the rear wheel axle 13 , from zero (see 10a ) to maximum (see 10b ) is infinitely adjustable by the eccentric receptacle 20 sliding lock carriage 21 , by its rotary connection to the rotary ring holder 15 through the lock carriage bolt 26 is connected, and by the rotatable spindle shaft 23 , is self-locking or movable. To adjust the spindle shaft 23 from the adjusting disc 30 turned over by two cables 60 (For each direction of rotation, a cable), on a handle on the bicycle handlebar, through the Stellscheibekappe 32 guided, which over the holding plate 29 on the eccentric receptacle holder 20 locked, is adjusted. Here is the adjustment radius of the lock slide 21 and the Verstellgeometrie designed such that a double joint to the rotary joint through the lock slide pin 26 on the rotary ring holder 20 is saved, since the bearing tolerances of the rotatable adjusting receive the Verstellradiusspiel and thereby has the lock much less game.

The function of the stepless eccentric timing adjustment is also in 8th and 10 can be seen, wherein by rotation of the Exzenteraufnahmehalter 20 , on the rear axle 13 , the complete crank drive torque converter with eccentric stroke adjustment, from top dead center 10b from, infinitely presented 10c or reset 10d can be. By the pull rod end pin 51 with safety collar, on the crank arm-like recording of Exzenteraufnahmehalter 20 is bolted, the drawbar 50 rotatably accommodates. The pull rod 50 on the other hand, with the, on the Rah menanbauhalter 42 sliding lock carriage 39 , through the lock carriage bolt 26 (with safety collar), is rotatably connected, and by the rotatable spindle shaft 40 , is self-locking or movable. To adjust the spindle shaft 40 from the adjusting disc 45 turned over by two cables 63 (For each direction of rotation, a cable), via an adjusting lever on the bicycle handlebar, through the adjusting cap 47 guided, which over the holding plate 44 on the frame attachment holder 42 locked, is adjusted. The arrangement of the crank arm-like recording of Exzenteraufnahmehalter 20 , for rotatably receiving the drawbar 50 chosen such that the power transmission as Zugbauteil, rather than as a pressure member is made to keep the dimensions of the components, as small as necessary. In the third preferred embodiment according to the invention, a simple embodiment without adjustable timing, based on a cultivation example, in zero position 10e , as well as at maximum position 10f the Exzenterhubverstellung shown.

01

Kraftverteilungsflansch

02

gearbox

03

Getriebeflanschmitnehmer

04

roller bearing for chain sprockets

05

Sprocket holder

06

Drive bracket trunnion

07

cam follower eccentric

08

drive holder

09

sprocket

10

Output support trunnion

11

cam follower eccentric

12

output support

13

rear axle

14

eccentric

15

Rotating ring holder

16

rotating ring

17

roller bearing eccentric

18

Exzenteraufnahmestirnzapfen

19

Exzenteraufnahmebohrung

20

Exzenteraufnahmehalter

21

cam carriages stroke

22

lock nut stroke

23

spindle shaft stroke

24

up cup

25

circlip stroke

26

Cam carriage bolts Hubverstell.

27

Pin receiving bore

28

Pin lock hole

29

Retaining plate stroke

30

adjusting disk stroke

31

Square drive

32

Adjusting disk cap stroke

33

Clamp strap stroke adjustment

34

Achsaufnahmebohrung

35

Exzenterantriebsstirnzapfen

36

Drive bushing

37

Exzenterabtriebsstirnzapfen

38

Output bushing

39

cam carriages Steuerzeitverstell.

40

spindle shaft Timing adjustment

41

runner connectors

42

Adaptation bracket

43

circlip Timing adjustment

44

Retaining plate Timing adjustment

45

adjusting disk Timing adjustment

46

Square drive Steuerzeitverst.

47

Adjusting disk cap Steuerzeitverst.

48

Clamping strap timing adjustment

49

Radachsenaufnahmebohrung

50

pull bar

51

Zugstangenstirnzapfen

52

location hole

53

Cam carriage bolts St.zeitverst.

54

guide bore

55

pin bore

56

Achssicherungsring

57

frame hole

58

bicycle frame

59

holder bore

60

cable stroke

61

cable guide

62

nipple holder

63

cable Timing adjustment

64

nipple holder

65

rear wheel

66

rear hub

67

Drive sprocket

68

axis point rotating ring

69

position minimal

70

position maximum

71

pedal position

72

bicycle chain

A fourth preferred embodiment according to the invention, according to the reference list 3, in 11 as Kurbeltriebmomentwandler a rotary ring eccentric, which is intended for attachment to a bicycle as an example, by subsequently in front of the bottom bracket receiving tube 1 is placed to allow further transmission of power to a derailleur.

This is a version that is equipped with a stepless Exzenterhubverstellung, where in 11 , the eccentric stroke is shown to zero. This is a standard bicycle with derailleur use, the usual bottom bracket, against a modified bottom bracket 2 is exchanged, for which their storage requires no change. On the left side of the bottom bracket receiving tube 1 , is the left holder flange 3 placed. Behind it is the left pedal arm 4 with the eccentric drive sprocket attached thereto 5 with a splined connection 6 on the bottom bracket axle 2 locked and with a screw 7 secured.

The finger follower pin 8th with bearing collar, rotatably and slidingly guided by the bearing bush of the drive rotor 9 , and is in the drive rocker arm 10 screwed. The spigot of the drive rotor 9 , leads with the thrust washer 11 and the rolling bearing 12 through the covenant hole 13 , at the end of a thrust washer 14 with the eccentric drive pinion 15 (with half the number of teeth as the eccentric drive sprocket 5 ), via a spline connection 16 arrested, and by a mother 17 is secured. The drive chain 18 , connects the eccentric drive sprocket 5 with the eccentric drive pinion 15 ,

The eccentric component 19 , consists of a rotary ring holder 20 , with an internal rotating ring 21 is provided and the over the rolling bearing 22 , is rotatably mounted. This is the Exzenterbauteil 19 through the receiving recess on the eccentric receptacle holder 23 guided, and with the bearing pin 24 threaded, through the bolt receiving bore 25 and through the bolt securing hole 26 in the eccentric receptacle holder 23 bolted, bringing the eccentric component 19 with the eccentric receptacle holder 23 is rotatably connected.

The castle sledge 27 for the stroke adjustment, is from the lock nut 28 , on the spindle shaft 29 , between the two spindle shaft holders 30 , guided. This is the spindle shaft 29 with the circlip 31 , on the eccentric receiving holder 23 secured.

The eccentric component 19 is through the receiving recess on the front of the lock slide 27 passed, and is with the lock sled bolt 32 with collar and thread, through the bolt receiving bore 33 and through the bolt securing hole 34 in the castle sledge 27 bolted, bringing the eccentric component 19 on the eccentric receptacle holder 23 locked against rotation.

The holding plate 35 the adjusting disc cap 36 from the stroke adjustment, is on the spindle shaft 29 pushed and on the eccentric receptacle holder 23 screwed. On it is the adjusting disc 37 the stroke adjustment with the square socket 38 connected, with the Stellscheibekappe 36 , to the retaining plate 35 is screwed and the adjusting disc 37 covers.

The eccentric receptacle holder 23 , is with the eccentric component 19 and the sled 27 and with the components of the locking and adjustment, on the left holder flange 3 with the screws 39 attached. The drive cam lever end pin is for this purpose 40 with safety collar, rotatable and slidingly supported by the drive bearing bushing 41 at the rotary ring 21 guided, and in the drive rocker arm 10 screwed. Also is the output cam follower pin 42 with safety collar, rotatable and slidingly supported by the output bearing bushing 43 at the rotary ring 21 guided, and in the output cam follower 44 screwed.

The finger follower pin 45 with bearing collar, rotatably and slidingly guided through the bearing bush of the output rotor 46 , and is in the output rocker arm 44 screwed. The spigot of the driven rotor 46 , guides with the spacer disc 47 and the rolling bearing 48 through the covenant hole 49 from the right holder flange 50 , at the end of a thrust washer 51 with the eccentric output pinion 52 (with half the number of teeth like the eccentric driven sprocket 53 ), via a spline connection 54 arrested, and by a mother 55 is secured.

The right holder flange 50 , is with the driven rotor 46 and the eccentric driven sprocket 52 , over the distance plate 56 , with the screws 57 , on the eccentric holder 23 connected, and on the right side of the bottom bracket receiving tube 1 placed and with the lag screws 58 , on the left holder flange 3 bolted and locked against rotation.

The chainring driver 59 , takes the eccentric driven sprocket 53 and the chainring 60 (or the Kettenblattpacket with several chainrings), as a firmly connected component and running roller bearings, with the rolling bearing 61 and the two thrust washers 62 , on the bottom bracket axle 2 ,

The drive chain 63 , connects the eccentric drive sprocket 53 with the eccentric output pinion 52 , and the right pedal arm 64 , is with a splined connection 65 on the bottom bracket axle 2 locked and with a screw 66 secured.

At the two holder flanges 3 and 50 , a housing is bolted, which is provided with gaskets (not shown in the drawing), to protect against dust and dirt.

The process in the function 11 begins by the rotational movement of the pedal arms 4 and 64 passing over the bottom bracket axle 2 are firmly connected and via the eccentric drive sprocket 5 , the drive via the drive chain 18 to the eccentric drive sprocket 15 forward with the double rotational speed as the crank mechanism the eccentric on the drive rocker arm 10 drives.

Subsequently, the rotational speed of the eccentric on the output rocker arm 44 to the eccentric output pinion 52 over the output chain 63 to the eccentric driven sprocket 53 and associated chainring 60 (or the Kettenblattpacket with several chainrings) transferred at half the rotational speed, after which the further Kraftü Transmission via a derailleur occurs.

Of the Functional sequence and the mode of action of the rotating ring eccentric as Crankshaft torque converters, and those of the stroke adjustment, are the same as in the third preferred embodiment of the invention, and are detailed there described and read.

01

Tretlageraufnahmerohr

02

Bottom Bracket

03

holder flange Left

04

pedal arm Left

05

Exzenterantriebskettenrad

06

Spline connection

07

screw

08

Cam follower pin

09

driving slide

10

Driving rocker arms

11

thrust washer

12

roller bearing driving slide

13

drilling drive

14

thrust washer

15

Exzenterantriebsritzel

16

Spline connection

17

mother

18

drive chain

19

eccentric

20

Rotating ring holder

21

rotating ring

22

roller bearing rotating ring

23

Exzenteraufnahmehalter

24

bearing bolt

25

Pin receiving bore

26

Pin lock hole

27

cam carriages

28

lock nut

29

spindle shaft

30

Spindle shaft holder

31

circlip

32

Cam carriage bolts

33

Pin receiving bore

34

Pin lock hole

35

Retaining plate

36

Adjusting disk cap

37

adjusting disk

38

Square drive

39

screw

40

Drive cam followers trunnion

41

Drive bushing

42

Output cam followers trunnion

43

Output bushing

44

Output cam followers

45

Cam follower pin

46

driven runners

47

Distance thrust washer

48

roller bearing driven runners

49

drilling output

50

holder flange right

51

thrust washer

52

Exzenterabtriebsritzel

53

Exzenterabtriebskettenrad

54

Spline connection

55

mother

56

spacer plate

57

screw

58

lag screws

59

Kettenblattmitnehmer

60

chainring

61

roller bearing Bottom Bracket

62

thrust washers

63

drive chain

64

Pedalram right

65

Spline connection

66

screw

A fifth preferred embodiment according to the invention, according to the reference character list 5, in 12 as a crank drive torque converter, a rotary ring eccentric suitable for installation in a special bicycle frame 12a as an example, by acting as a separate component in a separate housing 12b , with inclusion of the bottom bracket and the pedal crank, also acts as a co-bearing component 12c and by the arrangement on the crank axle, ideal for receiving an additional derailleur, for further power transmission. It is a version that is equipped with a stepless Exzenterhubverstellung, as well as with a stepless timing adjustment, wherein in 12d , the eccentric stroke is shown to zero.

This is to the bottom bracket 1 , on the left side an internal gear 2 attached to the drive of the eccentric, and is inside of the bell housing 3 guided and from the outside with the pedal ball bearing 4 , through the screwed bearing seat ring 5 with the bearing lock nut 6 , against the ball bearing seat on the bell housing 3 rotatably mounted, and with the left pedal arm 7 , via a splined connection 8th on the bottom bracket axle 1 locked and with the screw 9 secured.

On the drive rotor 10 with the sun wheel attached 11 , the planetary wheel holder is running 12 on the needle roller bearings 13 and 14 , which are on both sides of the Planet wheels 15 are in engagement with the sun gear 11 are. In the hollow axle of the drive rotor 10 , are the two needle bearings 16 and 17 taken against a covenant and with the thrust washer 18 on the bottom bracket axle 1 postponed.

The "lock slide for the timing adjustment 19 ", is from the lock nut 20 on the "spindle shaft for the timing adjustment 21 ", between the receiving bridge 22 and the pilot hole 23 the bell housing 3 , guided. Is to the spindle shaft 21 with the "locking ring of the timing adjustment 24 "to the bell housing 3 secured, whereupon the "adjusting disk of the timing adjustment 25 "with the" square recording of the timing adjustment 26 This is the planetary wheel holder 12 over the drawbar 27 , with the "lock slide of the timing adjustment 19 "over the spindle shaft 21 to the bell housing 3 connected. The connection takes place on the one hand, via the Planetradhalterstirnzapfen 28 with safety collar, which is the drawbar 27 rotatably in the receiving bore leads and on the Planetradhalter 12 is screwed. On the other hand, the drawbar 27 through the receiving recess at the front of the "lock slide of the timing adjustment 19 "is guided, and is with the" lock slide bolt of the timing adjustment 29 "with collar and thread, through the guide hole over the pin hole 30 screwed. The eccentric component 31 , consists of a rotary ring holder 32 , with an internal rotating ring 33 is provided and the over the rolling bearing 34 , is rotatably mounted. This is the Exzenterbauteil 31 at the base recess 35 in the bell housing 3 on, and is with the bearing pin 36 threaded, through the bolt receiving bore 37 , on the one hand on the base recess 35 bolted and on the other hand by the housing cover 38 , Guided by a receiving bore and a base, bringing the Exzenterbauteil 31 is rotatably guided in the housing. The "lock carriage for the stroke adjustment 39 ", is from the lock nut 40 on the "spindle shaft for the stroke adjustment 41 ", between the receiving bridge 42 and the pilot hole 43 the bell housing 3 , guided. This is the spindle shaft 41 with the "locking ring of the stroke adjustment 44 "to the bell housing 3 secured, whereupon the "adjusting disc of the stroke adjustment 45 "with the square drive of the stroke adjustment 46 " connected is.

The eccentric component 31 is through the receiving recess on the front of the lock slide 39 passed, and is with the lock sled bolt 47 with collar and thread, through the bolt receiving bore 48 and through the bolt securing hole 49 in the castle sledge 39 bolted, bringing the eccentric component 31 locked against rotation.

The drive cam follower pin 50 with bearing collar, rotatably and slidingly guided by the bearing bush of the drive rotor 10 , and is in the drive rocker arm 51 screwed.

For this purpose, the second Antriebsschlepphebelstirnzapfen with securing collar, rotatable and slidably supported by the drive bearing bushing 52 at the rotary ring 33 guided, and in the drive rocker arm 51 screwed. Also is the output cam follower pin 53 with safety collar, rotatable and slidingly supported by the output bearing bushing 54 at the rotary ring 33 guided, and in the output cam follower 55 screwed. The finger follower pin 56 with bearing collar, rotatably and slidingly guided through the bearing bush of the output rotor 57 , and is in the output rocker arm 55 screwed. Where the output rotor 57 with the sun wheel 61 , in its hollow axle, the two needle bearings 58 and 59 against a covenant, and with the spacer sleeve 60 , on the bottom bracket axle 1 is placed rotatably.

The internal gear 62 for the output is with its hollow axle, through the housing cover 38 guided and with the chainring holder 63 bolted, with the ball bearing 64 between the bearing seat 65 on the housing cover and the bearing seat 66 the chainring holder 63 making storage.

The Planetradhalterflansch 67 is provided with spigots, and with it rotatably and slidably mounted planet wheels 68 , on the housing cover 38 screwed, bringing the planetary wheels 68 with the external gear 62 and the sun wheel 61 engage. The ball bearing 69 takes the slewing connection between the bearing seat 70 in the hollow axle of the external gear 62 and on the bottom bracket axle 1 screwed bearing seat ring 71 on, and leads the storage of the chainring holder 63 against the housing cover 38 ,

The chainring 72 is on the sprocket holder 63 bolted, and the right pedal arm 73 is on the bottom bracket axle 1 , via a splined connection 74 locked and with the screw 75 secured.

For stroke adjustment are two cables 76 , which are actuated by a rotary handle on the bicycle handlebar, through the cable guide in the housing cap 77 , in the guide grooves of the adjusting disc 45 guided and in the nipple holder 78 hooked. Similarly, in the control timing adjustment two cables 79 , which are actuated by an adjusting lever on the handlebar, through the cable guides in the housing cap 77 , in the guide grooves of the adjusting disc 25 guided and in the nipple holder 80 hooked. The bell housing 3 is with the housing cover 38 , and the housing cap 77 screwed on both.

The mating surfaces of the bell housing 3 and the housing cover 38 , are provided with a seal, and the bell housing 3 is with an oil inlet screw 81 , as well as with an oil drain plug 82 Mistake.

The process in the function 12 begins by the rotational movement of the pedal arms 7 and 73 passing over the bottom bracket axle 1 are firmly connected and over the external gear 2 , the left-hand wheels 15 drives, with the sun gear 11 with the drive rotor 10 , via the drive rocker arm 51 , the eccentric with twice the rotation speed of the crank mechanism rotates. Subsequently, the rotational speed of the eccentric, via the output cam follower 55 to the driven rotor 57 with the sun wheel 61 , about the Planet wheels 68 to the external gear 62 that with the chainring 72 (or the Kettenblattpacket with several chainrings) is connected, forwarded at half the rotational speed, after which the further power transmission takes place via a derailleur. The doubling, or the halving of the speed in the power transmission of the crank drive torque converter, is done by twice the number of teeth in the outer gears 2 and 62 like the number of teeth on the sun gears 15 and 68 , You could do without the second planetary gear after the eccentric output, either by reducing the chainrings, or would increase the chain sprockets.

The stepless control time adjustment is done by the rotation of the Planetradhalters 12 from the eccentric drive.

Of the Further functional sequence and the mode of action of the rotating ring eccentric as a crank drive torque converter, and the stroke adjustment and the Timing adjustment, are the same as in the third preferred embodiment according to the invention, and are there described in detail, and read.

01

Bottom Bracket

02

internal gear drive

03

housing bell

04

Tretkurbelkugellager Left

05

Bearing seat ring Left

06

Bearing locknut

07

pedal arm Left

08

Spline connection Left

09

axle bolt Left

10

driving slide

11

sun drive

12

Planetradhalter drive

13

needle roller bearings

14

needle roller bearings

15

Planetary gears drive

16

needle roller bearings

17

needle roller bearings

18

thrust washer

19

cam carriages Steuerzeitverstell.

20

lock nut Timing adjustment

21

spindle shaft Timing adjustment

22

female web Timing adjustment

23

guide bore Steuerzeitverstell.

24

circlip Steuerzeitverstell.

25

adjusting disk Timing adjustment

26

Square drive St.zeitverstellung

27

pull bar

28

Planetradhalterstirnzapfen

29

Cam carriage bolts timing

30

pin bore Steuerzeitverstell.

31

eccentric

32

Rotating ring holder

33

Rotatinring

34

roller bearing rotating ring

35

socket recess

36

bearing bolt

37

Pin receiving bore eccentric

38

housing cover

39

cam carriages stroke

40

lock nut stroke

41

spindle shaft stroke

42

female web stroke

43

guide bore stroke

44

circlip stroke

45

adjusting disk stroke

46

Four known recording stroke

47

Cam carriage bolts Hubverstell.

48

Pin receiving bore Hubverst.

49

Pin lock hole Hubverst.

50

Drive cam followers trunnion

51

Driving rocker arms

52

Drive bushing

53

Output cam followers trunnion

54

Output bushing

55

Output cam followers

56

Cam follower pin

57

driving slide

58

needle roller bearings

59

needle roller bearings

60

Distanzbuchse

61

sun output

62

internal gear output

63

Chainring retainer

64

ball-bearing output

65

bearing seat casing

66

bearing seat Chainring retainer

67

Planetradhalterflansch output

68

Planetary wheels downforce

69

Tretkurbelkugellager right

70

bearing seat right bottom bracket

71

Bearing seat ring right

72

chainring

73

pedal arm right

74

Spline connection right

75

axle bolt right

76

Cables lifting adjustment

77

housing cap

78

nipple holder stroke

79

Cables timing adjustment

80

nipple holder Steuerzeitverstell.

81

Oil inlet screw

82

Oil drain plug

A sixth preferred embodiment according to the invention, according to the reference character list 5, in 13 to 18 as Kurbeltriebmomentwandler a rotary ring eccentric, which is used to control the rotational force of a reciprocating engine becomes.

It is a version that is equipped with a stepless Exzenterhubverstellung, as well as with a stepless timing adjustment, wherein in 13 to 16 , the eccentric stroke is shown to zero.

This is the force input gear 1 with neck pin, on the left side in the bell housing 2 sliding bearing and on the right side, slidingly supported by the drive housing cover 3 guided, with a splined connection 4 to the crankshaft. Likewise, the eccentric drive gear becomes 5 , with half the number of teeth as the power input gear 1 and engaged with it, on the eccentric drive shaft 6 , on the left side in the bell housing 2 and on the right side in the drive housing cover 3 , slidably guided, with the eccentric drive shaft 6 at the left end a drive crank arm 7 having the drive rocker arm 8th , forked via a slide bearing pin 9 receives.

The drive cam follower is on the rotation ring 10 , also by the forked Antriebsaufname 11 with a sliding bearing pin bolt 12 connected. For this purpose, the rotating ring 10 a second shot, as a forked output recording 13 with a sliding bearing pin bolt 14 , the output rocker arm 15 leads. The driven crank arm 16 the axially adjacent the drive crank arm 7 sits, forked with a slide-bearing rocker pin 17 the other end of the output rocker arm 15 on, and sits on the eccentric output shaft 18 in the housing flange 19 is slidably mounted and at the other end by the Exzenterabtriebszahnrad 20 leads and slides in the output housing cover 21 ends. The power output gear 22 , with twice the number of teeth as the Eccentric output gear 20 is engaged with it, and is with a neck pin, on the right side in the housing flange 19 Sliding and on the left side, slidingly supported by the output housing cover 21 guided, with a splined connection 23 to the clutch. The eccentric component 24 consists of a rotary ring holder 25 , with an internal rotating ring 10 is provided and the on the "Rolling in Exzenterbauteil 26 "is rotatably mounted.

The eccentric receptacle holder 27 consists of the receiving plate 28 , which slide on the receiving collar 29 the bell housing 2 resting, and out of the adjusting plate 30 the sliding bearing on the Verstellaufnahmebund 31 of the housing flange 19 sits, and through the cylinder segment 32 , as well as with the spindle shaft holder 33 and the Hubverstellungshalter 34 are bolted.

The eccentric component 24 is between the receiving plate 28 and the adjustment plate 30 of the eccentric holder 27 led and is with the eccentric mounting bolt 35 sliding bearing and rotatably connected.

In the forked nose 36 of the rotary ring holder 25 becomes the lock nut 37 for stroke adjustment, centered on two spigots 38 , slide-guided. The spindle shaft 39 leads through the lock nut 37 and is rotatable between the spindle shaft holder 33 and the Hubverstellungshalter 34 of the eccentric holder 27 locked, and with a servomotor 40 Standing on the Hubverstellungshalter 34 is mounted, connected to the adjusting drive, bringing the Exzenterbauteil 24 on the eccentric holder 27 is rotatably locked.

The adjusting plate 30 of the eccentric holder 27 , is provided with an offset, which with a worm wheel segment 41 is connected, wherein a wave 42 with snail reaching across the bell housing 2 runs and to these, rotatable and slidably mounted, axially locked.

Opposite the worm wheel segment 41 from the eccentric holder 27 , is a second worm wheel segment 43 engaged with the shaft 42 to the emerging forces on the shaft 42 to center. Where the worm wheel segment 43 for centering, to a disk segment 44 is attached, which is rotatably and slidably mounted on the trunnion 45 is guided for centering and on the housing flange 19 is attached. In addition, behind the worm wheel segment 43 at the disk segment 44 , another gear segment 46 attached to the second gear segment 47 engages behind the worm wheel segment 41 from the adjusting plate 30 of the eccentric holder 27 is attached, and so the outgoing forces on the adjustment bundles. In addition, the wave 42 with a servomotor 48 connected to the outside of the housing flange 19 and on the bell housing 2 is mounted, and provides for the adjustment, bringing the eccentric holder 27 to the bell housing 2 is rotatably locked.

The process in the function 18 starts by the torque of the crankshaft 49 in the reciprocating engine 50 , via the power input gear 1 , in the flanged crank drive torque converter 51 , to the eccentric drive gear 5 , via the eccentric drive shaft 6 , to the drive crank arm 7 that over the drive rocker arm 8th , with the drive input 11 connected and the rotation ring 10 drives at twice the speed. The rotation ring 10 whose axle point is from the eccentric drive shaft 6 and the eccentric output shaft 18 is offset, forms the core of the eccentric and rotates in the rotary ring holder 25 which is held by the eccentric receptacle in the housing. The output recording 13 on the rotation ring 10 , pulls over the output rocker arm 15 on the driven crank arm 16 that's about the eccentric output shaft 18 , the eccentric output gear 20 drives and thus the power output gear 22 rotates at half the speed and from there via the clutch 52 in the flanged clutch bell 53 , the further power transmission to the flanged gear 54 , with the average speed of the crankshaft 49 passes.

You could get the clutch 52 also directly with the eccentric output shaft 18 connect by changing the final gear ratio to the drive.

The Adjustment of the Exzenterhubes and the tax time on the Actuators are via sensors electronically controlled, and achieved in slow-runners, e.g. big ship engines, the greatest efficiency, because you use there the largest eccentric lift ratio can.

Of the Further functional sequence and the mode of action of the rotating ring eccentric as a crank drive torque converter, and the stroke adjustment and the Timing adjustment, are the same as in the third preferred embodiment according to the invention, and are there described in detail, and read.

A seventh preferred embodiment according to the invention, according to the reference character list 5, in 19 as a crank drive torque converter, a rotary ring eccentric which is used to control the rotational force of a second crankshaft in a two-stroke engine. Wherein the second crankshaft drives an auxiliary piston with very eccentric stroke speeds, which runs in the working cylinder of the working piston and there ejects the burned exhaust gases in the downward movement and filled the working cylinder in the upward movement with fresh gas.

This is a two-stroke dual-clutch engine 55 with common cylinder, formed on the engine front side with a gear cascade, the three gears 56 having, via the force input gear 1 from the crankshaft 49 , the crank drive torque converter via the control gear 57 drives, which has the same size as the force input gear 1 , The control gear 57 drives the eccentric drive shaft directly 6 , at the same speed as the crankshaft 49 at. The rotary ring holder 25 is with its axis, eccentric from the axis of the eccentric drive shaft 6 and the eccentric output shaft 18 , attached to the motor housing, thus giving an extremely large eccentric stroke. The eccentric output shaft 18 drives the control crankshaft 58 directly to. The remaining components of the rotary ring eccentric and its structure between the eccentric drive shaft 6 and the eccentric output shaft 18 , are reversed in the sixth preferred embodiment in FIG 13 to 18 described in detail.

The process in the function 19 begins by the rotation of the crankshaft 49 in two-stroke double piston engine 55 , whereby the force input gear 1 over the gears 56 the control gear 57 , drives at the same speed. The control gear 57 drives with the eccentric drive shaft 6 and the drive crank arm 7 , above the drive rocker arm 8th that with the drive input 11 connected, the rotation ring 10 at. The rotation ring 10 whose axle point is from the eccentric drive shaft 6 and the eccentric output shaft 18 is offset, forms the core of the eccentric and rotates in the rotary ring holder 25 which is fixed to the motor housing. The output recording 13 on the rotation ring 10 , pulls over the output rocker arm 15 on the driven crank arm 16 that's about the eccentric output shaft 18 , the control crankshaft 58 drives. Whereby by the timing timing of the rotary ring eccentric, the control crankshaft 58 the auxiliary piston 59 standing in front of the working piston 60 in the common cylinder 61 runs, very slowly in top dead center and drives very fast at bottom dead center to the burned exhaust gases through the outlet channels 62 eject.

Of the Further functional sequence and the mode of action of the rotating ring eccentric as crankshaft torque converters are the same as in the third preferred embodiment according to the invention, and are there described in detail, and read.

Another embodiment of the two-stroke double piston engine 55 , is found in the 20 , wherein additionally still a crank drive torque converter 51 for the torque control of the crankshaft 49 is attached, which corresponds to the same embodiment of the sixth preferred embodiment, and thus can be combined by the force input gear 1 in addition to the gears 56 and the control gear 57 , also the eccentric drive gear 5 from the crank drive torque converter 51 drives.

01

Force input gear

02

housing bell

03

Drive cover

04

Spline connection crankshaft

05

Exzenterantriebszahnrad

06

eccentric drive shaft

07

drive crank

08

Driving rocker arms

09

Rocker arm bolt

10

rotating ring

11

drive connector

12

Rocker arm bolt

13

driven recording

14

Rocker arm bolt

15

Abtriebsschlebhebel

16

Abtriebskurbelarm

17

Rocker arm bolt

18

Exzenterabtriebswelle

19

housing flange

20

Exzenterabtriebszahnrad

21

Output cover

22

Power output gear

23

Spline connection clutch

24

eccentric

25

Rotating ring holder

26

roller bearing eccentric

27

Exzenteraufnahmehalter

28

mounting plate

29

receiving collar

30

adjusting plate

31

Verstellaufnahmebund

32

cylinder segment

33

Spindle shaft holder

34

Hubverstellungshalter

35

Exzenteraufnahmebolzen

36

nose

37

lock nut

38

trunnion lock nut

39

spindle shaft

40

servomotor stroke

41

worm gear

42

wave slug

43

worm gear

44

disk segment

45

trunnion

46

gear segment

47

gear segment

48

servomotor Timing adjustment

49

crankshaft

50

reciprocating engine

51

Crankshaft torque converter

52

clutch

53

Kupplungsglocke

54

transmission

55

Two-stroke twin piston engine

56

gears

57

timing gear

58

control crankshaft

59

auxiliary piston

60

working piston

61

cylinder

62

outlet channels

An eighth preferred embodiment of the invention, according to the reference character list 6, in 21 as Kurbeltriebmomentwandler a Kettenradexzenter, which is provided for installation in a bicycle with hub gear and shift guide by the rear axle as an example, which is planed at the fixed rear axle, because of the favorable translation solution to the crank mechanism. It is a version that is equipped with a Exzenterhubverstellung in three stages.

For this purpose, a commercial bicycle is used with hub gear, preferably already with a primary ratio of the chainring 1 at the bottom bracket, to the sprocket 2 at the rear hub, with one to two being translated. Instead of a chain sprocket 2 as a driven pinion, a sprocket package is 3 of several chain sprockets 2 . 4 . 5 and 6 , which are connected together as a component, attached to the output flange to the planetary gear on the rear hub. This is the sprocket package 3 , from the chain sprocket 2 which is arranged concentrically on the rear wheel axle, and from the chain sprockets 4 . 5 , and 6 which have in order an increasingly eccentric arrangement to the rear wheel axle. This is a Kettenumwerfer 7 , with attached chain tensioner 8th , as attached to the derailleurs. Where the chain tensioner 7 modified is what the pivot bearing 9 and the voltage angle 10 concerns the chain guide, because the chain tensioner in contrast to the inserts in derailleurs, the eccentric is constantly in motion. The chain derailleur 7 is over a turning handle on the handlebars with the cable 11 connected, the cable pull 12 also via another rotary handle on the handlebar with the control box 13 the sub-circuit is connected.

The functional sequence is in 22a to 22j , shown during a working stroke as an example, where the changed radius of action on the chain sprocket 6 can be seen, by the uniformly varied transmission radius from minimum to maximum, caused by its eccentric arrangement to the rear wheel axle 14 , While the constant resistance on the rear wheel 15 turns evenly through 45 °, recognizable in the 22a to 22j at the turning mark 16 , the rotational path of the Kurbeltriebarm changes 17 , visible from the rotating field cutout 18 before. Thereby sets the Kurbeltriebarm 17 its rotary path, for each rotary field cutout 18 , in the same time back, where it turns the fastest in the largest spin range, and slowest in the smallest. The inevitable extension and shortening of the chain path 21 between the eccentric chain sprockets 4 . 5 and 6 , and the chainring 1 , gets through the chain tensioner 8th balanced. The effect of the constant resistance, on the crank drive torque converter in the manner of Kettenrradexzenter on the crank mechanism, that of the first embodiment and has been described there and in the 2 and 3 , explained in more detail.

The extent of the fore and aft is determined by the Exzenterhub, resulting from the Distance of the axes of the center and the pivot point of the eccentric chain pinion 4 . 5 and 6 results. In order to adjust the optimum torque of the crank mechanism, the respective requirements regarding the speeds, load changes and momentum, it became a normal chain sprocket 2 with several eccentric chain sprockets 4 . 5 and 6 with increased lift ratios as a sprocket pack 3 designed, wherein one on the turning handle on the handlebars over the cable 11 with the chain derailleur 7 (as in the derailleur), the respective sprocket for the desired operation in engagement with the chainring 1 brings.

This is in 23a to 23d the different efficiency of the individual chain sprockets from the sprocket package 3 , in the rotating field cutouts 18 recognizable. Whereby here also per rotary field cutout on the chainring 1 , the respective chain sprocket continues to turn 45 °. The 23a shows the crank turn of chain pinion 2 , the 23b the eccentric pinion 4 , the 23c the eccentric pinion 5 and 23d the eccentric pinion 6 ,

01

chainring

02

sprocket

03

pinion Packet

04

Exzenterkettenritzel Minimal

05

Exzenterkettenritzel medial

06

Exzenterkettenritzel Maximum

07

derailleur

08

chain tensioner

09

pivot bearing

10

voltage angle

11

cable stroke

12

cable circuit

13

switchbox

14

rear axle

15

rear wheel

16

rotary labeling

17

Kurbeltriebarm

18

Rotating field cut

Claims (12)

Translation converter for crank mechanisms, characterized in that a crank drive torque converter consists of an eccentric gear, with timing adjustment and torque connection to the crank mechanism, in particular of manual, reciprocating, machine and pedal drives. Crank drive torque converter according to claim 1, characterized characterized in that Crankshaft torque converter on axles, the crank mechanism, or the power transmission, or the resistance, is rotatable or fixed. Crankshaft torque converter according to one of the previous claims, characterized in that components for the power transmission with the speed ratio from one to two, or other translations between the crank mechanism and the rotating component of the eccentric function, in the manner of gears, as crank, or chain, or gear, or timing belt drives, integrated and on axles of the crank mechanism, or the power transmission, or the resistance, be rotatable or fixed. Crankshaft torque converter according to one of the previous claims, characterized in that components for lifting height adjustment, the lead and lag, in stages or Infinitely adjustable, arranged become. Crankshaft torque converter according to one of the previous claims, characterized in that components for timing adjustment, the pre- and lag, in stages or Infinitely adjustable, can be arranged. Crankshaft torque converter according to one of the previous claims, characterized in that a Rotating ring eccentric, consisting of an off-center and eccentric of the driver axis adjusted holder, with rotatable concentric arranged rotary ring, with at least one articulated connection for concentrically arranged on the driving axis Verbindungsmitnehmer the Cranking torque, and with at least one articulated connection for concentrically arranged on the driving axis Verbindungsmitnehmer the resistance, as a component for the crank drive torque converter acts. Crankshaft torque converter according to claim 1 to 5, characterized characterized in that a Gear drive eccentric consisting of a fixed gear arranged concentrically to the driving axis, as well as at least one revolving planetary gear, this one formed with an eccentric sitting entrainment pin, a planetary wheel concentric on the Driver axle placed with drive connection to the crank torque, and a concentric with the driving axis arranged Verbindungsmitnehmer the Resistance force with a drive input of the eccentric or the sitting driving pin of the planet or the Planet wheels, as a component for the Crankshaft torque converter acts. Crankshaft torque converter according to claim 1 to 5, characterized in that a Kettentriebexzenter, consisting of a festverankertes chainring with chain arranged concentrically to the driving axis, and a circulating therein sprocket, this formed with an eccentrically seated driving pin, a Kettenradhalter for the order running sprocket, concentrically placed on the driving axle with drive connection to the cranking torque, and a concentric with the driving axis arranged connecting driver of the resistance force with a drive receiving the eccentrically seated driving pin of the sprocket, acts as a component for the Kurbeltriebmomentwandler. Crankshaft torque converter according to claim 1 to 5, characterized characterized in that a Sprocket eccentric, consisting of an off-center and eccentric too attached or stored chainring or sprocket, with a drive connection to the crank mechanism, as well as with a connection for resistance, and with at least one chain tensioner, or at least one driven eccentric pinion as a chain tensioner, as Component for the Kurbeltriebmomentwandler acts. Crankshaft torque converter according to claim 1 to 5, characterized in that a Toothed belt eccentric, consisting of a fixed-toothed belt pulley with timing belt arranged concentrically to the driving axis, as well a circulating in it pulley, this formed with an off-center seated driving pin, a timing belt holder for the circulating Timing belt pulley, concentric with the driving axle, placed with Drive connection to the crank torque, and concentric with the Mitnehmerachse arranged Verbindungsmitnehmer the resistance with a drive receiving from the off-center seated driving pin the timing belt pulley, as a component for the crank drive torque converter acts. Crankshaft torque converter according to claim 1 to 5, characterized in that a Toothed belt wheel eccentric, consisting of one off-center and eccentric too its axle fixed or stored toothed belt, with a Drive connection to the crank mechanism, as well as with a connection to the Resistance, and with at least one toothed belt tensioner or at least one driven toothed belt wheel eccentric as toothed belt tensioner, as a component for the Kurbeltriebmomentwandler acts. Crankshaft torque converter according to one of the previous claims, characterized in that as a control and drive member, for a second crankshaft with auxiliary piston, in a two-stroke double piston engine acts.