DE19737038A1 - Continuously adjustable gear with coupling elements - Google Patents

Abstract

The coupling elements (15) are radially and tangentially movable and transmit force radially and tangentially. The plastics coupling bars of one drive disc are injection molded in one piece in the shape of a star. The belt side of the coupling bars possess a high friction value and a high resistance to wear from the belt. The preferably plastics arms joining the coupling elements are in the form of restoring springs.

Description

This additional patent refers to German patent application 196 09 750.9-12, the here is taken over in full, and affects further refinements and improvements with new applications of the invention. All of these developments are based on the Main invention underlying novel dome principle, in which on the drive pulleys seated radially and tangentially movable coupling elements act laterally on the drive medium flanks, which the radial and tangential belt forces by means of lever and roller, or convert wedge mechanisms into a lateral, load-proportional coupling force. They have The coupling agent on the driving agent side has a material quality with a high coefficient of friction compared to the driving agent surface, on the drive pulley side, however, one with a low coefficient of friction to the drive pulley. This Difference in the coefficients of friction enables the transmission of high propellant forces simultaneous minimization of friction losses and wear. The radial and tangential The mobility of the coupling means enables a low-loss coupling process completely without Slip between the driving means and the coupling means, as these run along the belt along the inlet and Can follow the exit path until the coupling or uncoupling process is complete. Because of this In principle, the use of drive belts becomes possible for the first time, which, in contrast to Steel link chains a much higher transverse compressibility - this is synonymous with have relatively large engagement and disengagement paths.

With regard to the prior art, the content of the main patent application and the References from the inspection body and the comments on these references are referenced.

The object of the present additional invention is to further improve the invention of the main patent application, in particular

• - With regard to ease of manufacture and assembly (claim 1),
• - Reduction of friction losses (claim 2)
• - higher switching precision and insensitivity to interference (claims 3-10),
• - on the application of the new dome principle of the laterally acting on the propellant, radial and tangentially movable, self-supporting coupling means also on V-belt transmission (Claims 11-18).
• - As well as a reduction in the overall width (claim 19).

1. Easy to manufacture 1.1 Dome molding star

According to the invention, it is proposed to manufacture the coupling strips ( 15 ) from plastic, the side facing the belt ( 1 ), for. B. by embedded fibers and / or a rough structure of the surface or by a coating or planking with appropriate ceramic or metallic materials, eg. B. a wear-resistant, possibly corrugated sheet metal plate ( 35 ), has a high wet friction value on the belt material, while the inclined surfaces facing the drive pulley ( 6 , 6 ') are smooth and the lowest possible coefficient of friction compared to the material of the inclined surfaces located on the drive pulley ( 6 ) - preferably polished stainless steel drive pulley. If necessary, this can be achieved by a suitable coating with sliding plastics (coefficient of friction well below 0.2). These should also be able to incorporate smaller dirt particles without significantly affecting the coefficient of friction. Good friction values towards the belt are e.g. B. possible with fiber-reinforced polyamide or polyurethane. It is particularly advantageous in terms of manufacturing and assembly technology to combine the individual coupling strips ( 15 ) of a drive pulley in a single, star-shaped, permanently elastic plastic injection-molded part, the coupling strip star ( 30 ), by molding plastic webs ( 31 ) onto the individual coupling strips ( FIG. 18). . These plastic webs are preferably designed as return and retaining springs, for. B. by multiple curvature. They also carry snap pins ( 32 ) with which they snap into recesses in the drive pulley ( 5 ). The effect of these return springs made of plastic can, if necessary, be supported by metallic return springs.

The advantage of this additional invention is that it is greatly simplified and can be automated Gear assembly due to fewer components.

1.2 Positioner elements

A variant of the invention provides that the feeler roller ( 10 ) be dispensed with entirely and positioning elements (37, 38, 39; Figs. 19-24, Fig. 28) located between or on the coupling strips ( 15 ) for controlling the belt running circuit on the driven side -30) to be used, which automatically guide the belt to the maximum possible circle radius specified by the running circle on the drive side. These positioning elements consist of resilient or elastic sliding surfaces, which each want to keep the incoming belt at the greatest possible radius with a small force, since they come along from the inside along the belt flank. Only when the empty strand 28 of the belt tightens is it pulled into position and held there. On the output side, the switching point S is located at or shortly after the synchronization point G for the smallest running circle diameter and always remains in this position. The positioning elements can be designed as steel spring clips ( 39 ) or spring strips ( 37 ) made of plastic, or as brushes ( 38 ), or resilient sheet metal plates ( 35 ), each in the most wear-resistant quality. The same function can also be performed on the outer edge of the drive pulleys on both sides attached dirt deflectors ( 41 ), which always want to guide the belt to the maximum radius. It is important here that a flexible belt is used in order to make the holding forces of the positioning elements and thus the resulting friction losses as low as possible.

Four phases can be distinguished on the driven pulley during the rotation ( Fig. 25): In the positioning phase I, the belt slides onto the positioning elements coming from below until the empty strand 28 has been slightly tensioned. At the end of this first phase, he is in the maximum radial position specified by the running circle on the drive pulley. At the beginning of coupling phase II, the coupling strips couple the belt after passing coupling point E, which is located near synchronization point G for the smallest running circle diameter or even further in the running direction. In the disengaging phase III, the dome bars release the belt automatically. In the lifting phase IV, the coupling strips ( 15 ) are raised radially by the cam disc ( 8 ) and guided into the axially lowest position in order to be able to accommodate the belt in the subsequent phase I between them.

The advantage of this additional invention is a smaller number of moving components and a more compact design.

2. Reduction of friction losses

In order to minimize the frictional losses and wear when inserting the belt, the invention provides for the belt to be provided with spring strips ( 37 ), brushes ( 38 ), steel spring clips ( 39 ) on the coupling means or with a wear-resistant and wear-resistant spring band on the coupling strip over a narrow gap fastened sheet metal plate ( 35 ) with limited force and flex in bending zones ( 33 ) before the full coupling force begins ( Fig. 19-24). This avoids a loss of friction that would result from the belt flexing on the surfaces of the coupling strips at high lateral coupling forces. This resilient sheet metal plate can also be used as a positioning element that replaces the feeler roller ( 10 ) (see above).

The advantage of this additional invention is the lower friction and less wear on the Belt flex process.  

3. Insensitivity to interference and higher switching precision 3.1 Dirt deflector and clearing lips

In order to protect the sliding surfaces from small foreign bodies, it is advantageous to provide the edges of the sliding surfaces with clearing lips ( 36 ) and to provide hollow dirt deposits or through holes ( 44 ) in the corners ( FIG. 31) that receive the removed dirt particles or to the outside conduct.

For difficult operating conditions, it is proposed according to the invention that resilient or elastic, annular Schinutzabweiser ( 41 ) are attached to the outer edge of each drive pulley, which stand somewhat in the idle position in the pulley groove and whose mutual distance is less than the belt width, so that its flanks at the on - and run out into or out of the disc groove, slide past the dirt deflectors and remove any adhering dirt ( Fig. 28).

The advantage of this additional invention is that the transmission is less susceptible to dirt, which also enables use in the field.

3.2 Suspension compensation

For sprung vehicles in which changes in length in the empty run and thus influences the unevenness of the road on the translation result in the invention proposing to mount the bearing journal ( 21 ) of the control arm ( 19 ) on a displaceable adjusting ring ( 40 ) ( Fig. 26 ). A pushrod attached to the vehicle frame at a suitable point pivots this journal when it is deflected so that the change in the running circle thus caused largely compensates for the gear adjustment caused by the change in length of the empty run.

For unsprung vehicles, this addition mechanism can be used to achieve high quick-shift capability. For this purpose, the shift cable ( 18 ), which also causes the transmission to be adjusted on the drive side, is also used to turn the adjusting ring ( 40 ).

The particular advantage of this additional invention is that the transmission can also be used with Suspended drive wheels, where the chassis geometry changes when changing Empty strand length leads.  

3.3 Dome slats arranged at an angle to the radius

With a finite number of coupling bars ( 15 ) per drive pulley ( 5 ), the condition for running on a constant radius is: The coupling point of the straight incoming coupling bar ( 15 ) must be at the same distance from the center of rotation (M) of the driving pulley as the coupling point (K ) of the leading coupling bar, ie the coupling must take place at the synchronous point (G) and the triangle KMG must be an isosceles triangle.

Vibrations of the belt ( 1 ) can cause irregularities in the running radius when the tension strand is only slightly loaded, if the coupling strips ( 15 ) are aligned in their longitudinal axis in the direction of the radius beam of the drive pulley. Such a radial alignment inevitably results in a narrow switching angle, that is to say a relatively small area in which the cam disc ( 8 ) switches between the minimum diameter and the maximum diameter. The larger the center distance and the smaller the change in belt inclination, the more sensitive the circuit is to faults, dirt and tolerance errors. A guide roller ( 20 ) is essential for larger center distances and radial alignment of the coupling strips.

The object of the present invention is to develop the main invention in such a way that

• - That a higher switching precision, d. H. a larger switching angle (ε) is reached,
• - That the sensitivity to belt vibrations and component tolerances is lower and
• - That a guide roller ( 20 ) can be dispensed with even with large center distances.

This is achieved according to the invention in that the longitudinal axes of the coupling strips ( 15 ) are not arranged in the direction of the radius beam (r), but rather at a clear angle - referred to below as the advance angle (δ) -, preferably with an angle value of more than 180 ° divided by the number of coupling strips ( Fig. 33).

This has the effect that a belt running outwards due to a malfunction, related to the direction of rotation, is later coupled and quickly stirred inwards again without having to adjust the switching time by rotating the cam disc ( 8 ). Conversely, a belt running inwards is quickly stirred outwards again. The switching angle (ε) defined by the distance between the drive pulleys and the adjustment range for radially arranged coupling strips ( 15 ) increases by a dimension determined by the lead angle (δ) and the switching ratio for coupling strips arranged at an angle to the radius beam (r) ( Fig. 33). With the choice of the lead angle (δ), the size of the switching angle and thus the switching sensitivity can be determined. A large switching angle means that malfunctions due to belt vibrations, dirt or component tolerances have a much lower impact on a change in the running circuit.

In order to achieve a uniform running circuit stabilization over the entire switching range, it is proposed to curve the longitudinal axis of the coupling strips according to the rules of a real spiral, so that this longitudinal axis always has the same angle to the radius beam (r) at every point. A good approximation can be achieved by circular segment-shaped dome strips ( 15 ), which are easier to manufacture.

In the case of such curved coupling strips, the individual partial surfaces of the stepped inclined surfaces ( 6 ) must be arranged parallel to one another in order to guarantee that the coupling strips ( 15 ) lie on the counter surfaces of the traction sheaves over a large area.

It should be noted that reverse operation of such a transmission becomes unstable after a short time, which is irrelevant for the bicycle drive.

The advantage of this additional invention is a higher switching precision, ie more sensitive switching, and a lower sensitivity to interference such as vibrations and component tolerances. In addition, a guide roller ( 20 ) can be dispensed with.

3.4 Overload bolt with disc springs

To limit the loads on the drive parts, it is often advisable to provide an overload protection. According to the invention, it is proposed that the individual drive pulleys be axially displaceable relative to one another by 1-2 mm but non-rotatably on the connecting bolts ( 43 ) and that their tensioning force be applied to the drive pulley body via disc springs ( 42 ) or elastic rings or the like ( FIG. 28). By appropriately limiting the travel of the coupling means ( 4 ) by means of stops, it is possible to regulate the maximum coupling force by prestressing the disc springs ( 42 ). The maximum axial stroke of the coupling means over the drive pulley level must be less than the difference between the drive medium width and the maximum drive pulley distance. This is determined by the suspension travel available. It is sufficient to carry out this overload protection on only one side, preferably on the drive double disk.

The particular advantage of this additional invention is that the transmission does not reach the maximum expected force of a user must be designed, but according to precisely definable Maximum forces can be calculated, which can save a lot of weight.  

4. Application in V-belt transmissions 4.1 Variable wide V-belt transmission

According to the invention, it is proposed to attach the coupling means, preferably in a larger number and regularly distributed, on the conical surfaces of the drive pulleys ( 49 ) of V-belt transmissions. The coupling means are so far above the conical surface that the belt comes to rest on it. Because of the cone shape, the running circle diameter is determined by the cone pulley distance ( Fig. 14-17).

The inclined surface plane intersects the conical surface at an angle of preferably 10-30 °. The resulting cutting line is preferably parallel to the cone axis or the radius beam. So the tangential, but also the radial belt tension becomes a production due to the cone pitch the contact pressure. The coupling is done by just putting on a coupling agent Wide V-belts placed on the coupling means a little bit due to the effect of the belt tension takes along and this slides on generating a load-dependent contact pressure.

The travel of the coupling means is only approx. 1 mm in the case of conventional belt dimensions, since the belt comes to rest on the coupling means anyway due to the wedge shape, so that only a certain belt compression has to be achieved and the delivery path is eliminated. Possible coupling elements on inclined surfaces ( 6 , 6 ') and displaceable coupling strips ( 15 ) or coupling rods ( 52 ) which roll or tilt in the circumferential direction with a round, oval or polygonal cross section are possible. The latter can, due to the shape of the radial groove in which they roll, as well as their inherent shape with their belt-facing surface when rolling or tilting, raise them further from the surface of the cone and couple the overlying belt on its side flanks depending on the load. In the radial direction, the coupling rods ( 52 ) can slide a little on the drive pulleys and follow the belt.

Return springs return the coupling means to theirs after the belt has been lifted off Starting position, that is the position with the least protrusion over the conical surface. This always ensures the same travel path and good concentricity.

In the case of plastic coupling strips, cast-on plastic webs ( 31 ) or resilient holding elements ( 50 ) can take over this function. These plastic webs can connect the individual coupling strips to a single part, the coupling strip star ( 30 ), which brings advantages in terms of assembly technology. The coupling surfaces of the coupling means do not have to be rectangular, but can e.g. B. also be designed trapezoidal.

The coupling means can also by an oppositely directed sliding or rolling or Aufkippbahn act in the other direction of force, so that an operation in every force and in every Direction of rotation is possible.  

To securely hold the coupling means in their position even at higher speeds and To secure centrifugal forces, the coupling means are in the rear grip with the drive pulley. At correspondingly strong return springs are sufficient for medium centrifugal forces.

The use of such side-engaging, self-supporting and low-friction coupling means in V-belt drives has the following advantages:

• 1. The load-dependent coupling force ensures good efficiency, especially Partial load efficiency and high torque output achieved. Belt tension is too tight not necessary for this purpose.
• 2. The friction losses are greatly reduced by several effects:
• - due to the higher effective torque output (no significant preload) can same transmission power, the speed can be greatly reduced, resulting in less Power loss stirs,
• - Due to the low coefficient of friction of the coupling means on the conical washers Sliding friction losses of the belt are greatly reduced, which is particularly the case with V-belt variators flat conical washers is a huge advantage
• - Due to the minimal preload, the bearings are relieved, there are significantly less Stock losses
• 3. The thermal load caused by friction is often the limiting factor in Power throughput of belt drives, so that with the present invention through the very much lower friction losses better exploited the mechanical performance of the belt can be.
• 4. Because of the high coupling force of the coupling means, it can have smaller wrap angles driven, which enables larger translations in one step.

Overall, this results in significant improvements in the area of V-belt transmissions, especially when used in motor vehicles.

4.2 Variable narrow V-belt transmission

According to the invention, the drive pulleys are divided into individual drive pulley segments ( 54 ) which are known from other, but form-fitting gearboxes (e.g. CH 680 941 A5) and which are radially displaceable in guide grooves ( 60 ). Each of these drive pulley segments ( 54 ) carries one or more coupling elements, preferably arranged in pairs, which are mounted so as to be movable radially and tangentially and use the belt forces which occur to generate the coupling force by means of a corresponding force and displacement converting wedge, rolling element or lever mechanism ( Fig. 34 ). The coupling elements are advantageously designed as large-area coupling plates ( 64 ) and are mounted on radially and tangentially inclined sliding surfaces ( Fig. 35-38).

The special coupling principle of the invention allows the belt to be gripped at any position with a load-proportional coupling force. In contrast to known similar transmissions, it is thus possible to move the drive pulley segments ( 54 ) to any radial position, to fix them and to switch every gear shift. There is no need to pay attention to the toothing of the propellant. According to the invention, the holding mechanism of the drive pulley segments ( 54 ) is designed to be self-locking under belt load. To sit the driving wheel segments (54) in cantilever fashion in addition to the carrier disc (55) and tense up schraubzwingenartig by attacking belt forces against the carrier disc (55). A retaining spring ( 58 ), which tries to tilt the drive pulley segment ( 54 ) in the clamping direction, ensures that the drive pulley segment ( 54 ) remains in the respective position in the sector without a belt, provided the gear ratio is not changed ( Fig. 35, 36 ).

The shift ratio is changed by radially displacing the drive pulley segments ( 54 ) by means of adjusting rollers ( 57 ) which are attached to the drive pulley segments and which run against an inner ( 59 ) and an outer guide rail ( 59 '). These guide rails are fastened to the gear frame in the belt-free sector of the drive pulley and have the maximum radial distance from one another on the side of the outgoing belt, which tapers like a funnel in the running direction towards the incoming belt to the diameter of an adjusting roller ( 33 ). The tapered end is radially displaceable or pivotable by the shift cable ( 18 ). The guide rails ( 59 , 59 ') catch the adjusting rollers ( 57 ) in any radial positions and stir them to the desired new radial positions. The guide rails ( 59 , 59 ') are preferably stiff in the direction transverse to the carrier disk ( 55 ) and flexible in the radial direction. In the switching position for minimum running circle, they are more curved than in the switching position for maximum running circle. One of its ends is preferably rotatably mounted in bolts ( 62 ). The switching piece ( 65 ), which can be pivoted about the pivot point P, engages around the outer guide rail from the outside and the inner guide rail by means of a holding pin ( 66 ) from the inside and moves the movable ends of the guide rails to the desired position. The outer guardrail is preformed to the largest track radius, the inner guard rail, however, to the smallest track radius.

The adjustment rollers ( 57 ) run on the outer guide rails ( 59 ') not only on the end face but also on the flank side, by an obliquely inward to the force of the retaining spring ( 58 ) and onto the carrier disk ( 55 ), but still radially outside of the belt side To initiate the clamping nose ( 63 ) directed force to override the self-locking.

The controls of the input and output side are coupled in opposite directions via a tension spring ( 61 ), which clamps the two contact pieces ( 65 ) against each other in such a way that the guide rails on the output side are always pushed to the outermost possible radial position, which automatically leads to an automatic readjustment of the Barrel diameter on the driven pulley stirs when the barrel diameter on the drive pulley changes. The force of the tension spring ( 61 ) also determines the amount of belt pretension in the empty run. A parallel, but also radially flexible section is attached to the funnel-like section of the guide rails, which section has approximately the length of the distance between the adjusting rollers ( 57 ) of two adjacent drive pulley segments ( 54 ) in the outermost radial position. This prevents the guide rails from jumping back and forth during the transition from one adjustment roller ( 57 ) to the next. The shift cable ( 18 ) actuates the switching piece ( 65 ) on the drive side.

The particular advantage of this variant of the transmission is the possibility of using a conventional V-belt. Further advantages are that the overall width is small, that it is insensitive to belt vibrations and that the coupling forces within the drive pulley segments ( 30 ) are supported against one another in a short way, which leads to weight advantages.

5. Reduction of the overall width

According to the invention, a reduction in the overall width of the transmission is proposed by a step-like gradation of the inclined surfaces ( 6 , 6 '). The inclined surfaces of a coupling strip ( 15 ) and the corresponding inclined surfaces on the drive pulley are divided into several partial surfaces, preferably 3-5. It is important to arrange the individual partial surfaces in parallel so that large-area contact between the inclined surfaces is ensured when moving the coupling strips ( Fig. 27, 31, 32)
The advantage of this partial invention is the significant reduction in the overall width.

In the following, the invention is based on several implementation methods and functional principles illustrative drawings explained in more detail. Here go from the drawings and their Description further features and advantages of the invention essential to the invention. Show it:

Fig. 14 View of a conical drive double disc in the radial direction

Fig. 15 View of a conical drive pulley in the axial direction

Fig. 16 partial cross section of a drive pulley with coupling strips

Fig. 17 partial cross section of a drive pulley with coupling rods

Fig. 18 partial view of a dome star

Fig. 19 cross-sectional view of a dome strip with a resilient sheet metal plate and a slightly lying belt

Fig. 20 transverse view of a dome strip with resilient sheet metal plate and fully coupled belt

Fig. 21 transverse view of a dome bar with female connectors and slightly lying belt

Fig. 22 Transverse view of a dome bar with female connectors and fully coupled belt

Fig. 23 Transverse view of a dome bar with steel spring clips and a belt resting on it

Fig. 24 Transverse view of a dome strip with brush spring strips and a belt lying lightly

Fig. 25 showing the four operating phases of an output disc having positioning elements

Fig. 26 Representation of the interaction of the feeler roller and the adjusting ring

Fig. 27 partial cross section through a drive pulley made of pressed sheet metal with stepped inclined surfaces

Fig. 28 partial cross section through a drive double disc with overload protection and dirt deflector

Fig. 29 partial cross section through a drive pulley with brushes as a positioning element

Fig. 30 partial cross section through a drive pulley with steel spring clips as a positioning element

Fig. 31 partial cross section through a drive double disc with step-like inclined sliding surfaces

Fig. 32 top and side view of a dome bar with step-shaped oblique sliding surfaces

Fig. 33 shows the relationship between the flow angle to which the synchronism determining equilateral triangle CMM, the position of the switch point S and the size of the switching angle exemplarily with a drive pulley

Fig. 34 shows a Ausrührungsbeispiel a scheibengekuppelten Schmalkeilriemen- variable transmission in side view (Getrieberahnien not shown)
Fig. 35 shows the mechanism of self-locking positioning of the drive pulley segments in the coupled position

Fig. 36 shows the mechanism of self-locking Positionlerung the drive disc segments in the uncoupled position

Fig. 37 shows a drive pulley segment in side view

Fig. 38 shows a drive pulley segment in plan view.

In Figs. 14 to 17 the Ausrührungsbeispiel is illustrated a V-belt scheibengekuppelten Vario transmission. Eight radially arranged coupling strips 15 are arranged on the conical drive pulleys 5 . They sit in flat V-shaped grooves, which have the function of the inclined surfaces. The distance between the drive pulleys is variable to control the barrel diameter according to known systems. The dome strips 15 are made of plastic and have a surface with a high coefficient of friction to the rubber belt. On the drive pulley side, they have a very low coefficient of friction with the inclined surfaces 6 . A commercially available toothed wide V-belt 48 is used. Due to its relative movement to the drive pulley, it takes the coupling bars somewhat in the tangential and radial direction, which forces them to slide onto the inclined surfaces and thus to couple the belt laterally. The dome strips are held by cast-on resilient holding elements 50 which snap into fastening openings and are always pulled back into their rest position ( FIG. 16). The V-shaped arrangement of the inclined surfaces enables operation in any load and direction of rotation. Instead of coupling strips 15 , rolling elements, such as. B. coupling rods 52 are used, which sit in radial grooves 53 ( Fig. 17). The bottom of the groove is also V-shaped, so that the coupling rods increasingly come out of the drive pulley surface when they are offset and couple the belt. They are pulled into their rest position by return springs - not shown. The coupling rods 52 can slide a short distance radially in the grooves in order to also be able to implement the radial belt tension.

Fig. 18 shows a star coupling strips 30 a resilient engineered plastic such. B. polyamide or polyurethane. The plastic webs 31 connecting the individual coupling strips 15 act as return and retaining springs due to their shape. They carry snap pins 32 , which snap into holes in the drive pulley.

FIGS. 19-24 show the principle of early Riemenflexung. A curved, resilient sheet metal plate 35 , spring strips 37 attached to the side of or next to the coupling strips, or brushes 38 or steel spring clips 39 grasp and flex the belt 1 before the maximum lateral coupling force is applied. The flex zones of the belt are shown hatched. All of these resilient elements can also be used as positioning elements for automatic adjustment of the running circuit on the output side. In Figs. 19 and 20, the Räumlippen 36 are shown, which clean the slide surfaces of dirt and carrying in the through-holes 44.

Fig. 25 shows the four different phases in an automatic running circuit adjusting the output side by positioning elements. The process is described above.

Fig. 26 shows the principle of suspension compensation. The bearing pin 21 of the support arm 19 of the feeler roller 10 is mounted on an adjusting ring 40 which is actuated by a shift cable 18 . This is attached to a suitable location on the vehicle frame so that it can compensate for the fluctuations in the empty run caused by the compression. The geometry is to be chosen so that the position of the switching point S does not change during the compression.

Fig. 27 shows a deformed steel sheet metal or CFK panels drive disc with staircase-like arranged inclined surfaces. The starting form is a cone that is folded into the drive pulley and deep-drawn.

Fig. 28, 29, and 30 show the arrangement of dirt deflector 41 and positioning elements. They each protrude slightly into the pulley groove and slide on the belt flank with little holding force.

Fig. 31 and 32 show the space-saving principle of the stair-like arranged inclined surfaces. The dashed arrows indicate the fall line of the inclined surfaces. Five steps are shown in the example.

In Fig. 33 the relationship between the leading angle, the isosceles triangle KMG which determines the synchronism, the position of the switching point S and the size of the switching angle is explained by way of example on a drive pulley. The position of the coupling points Ki, Ka of the leading coupling bar and the position of the synchronizing points Gi, Ga for the straight incoming coupling bar for two different running radii (inside, outside), as well as the position of the associated switching point Si, Sa are shown. The situation is shown with a very large center distance between the input and output shafts, i.e. the case that would cause instability with radially arranged coupling strips. The lead angle of the coupling strips results in a clear switching angle. The extent of this switching angle increase is proportional to the lead angle and the size of the switching range. FIG. 33 shows the quasi-spiral arrangement of the domed strips 15 curved in the manner of an arc. They are slidably mounted and controlled on mutually parallel, step-like inclined surfaces radially and tangentially according to the principle of the main application.

Fig. 34-38 show a continuously variable transmission with a narrow V-belt. Laterally next to the carrier disk 55 on the drive side and the driven side, drive disk segments 54 are seated in a cantilever-like manner in radial, hardened guide grooves 60 and can be moved therein from the smallest to the largest running circle diameter. According to the principle of the adjustable screw clamp, two clamping lugs 63 (arrows), which are offset radially relative to one another, attach themselves to the carrier disk 54 under belt load and hold the drive pulley segment in position ( FIG. 35). In the sector without belt load, the retaining spring 58 , which is fastened to the drive pulley segment and is supported against the carrier pulley, tries to tilt the drive pulley segment and thereby fix it. In the keyway of the drive pulley segment 54 , four coupling plates 64 sit opposite one another in pairs, which are mounted on radially and tangentially inclined sliding surfaces. They are connected to each other by resilient plastic webs 31 and snapped into the outer collar of the keyway by means of a grip. The belt-side surface of the coupling plates 64 is rough, the surface of the drive pulley segment is smooth and slide-coated. The two funnel-like guide rails 59 , 59 'consist of flat or angled spring steel and are each mounted on two rotatable bolts 62 on the gear frame. At the other end, the guide rails in the switching piece 65 are slidably mounted in the longitudinal direction. The contact piece engages directly around the outer guide rail and the inner guide rail by means of a retaining pin 66 ( FIG. 34, section AB). The switching piece 65 is pivoted radially by the shift cable 18 . On the output side, this pivoting does not take place directly through the shifting cable 18 , but rather through a tension spring 61 which is coupled to the switching piece on the drive side and which presses the guide rails 59 , 59 'to the maximum radial position which is possible in each case. The guide rails 59 are extended beyond the funnel-like tapering point and are also flexible in this area and, to a certain extent, allow the running circle diameter to be changed despite the V-belt 56 lying thereon. This enables automatic readjustment of the output side.

Adjustment rollers 57 run on these guide rails, which are fastened to the drive pulley segments 54 and each guide them to the desired new radial position. The adjusting rollers 57 run on the end and flank sides on the outer guide rail 59 '. The resulting pressure (arrow) on the roller flank in the direction of the carrier disc counteracts the retaining spring 58 and rotates the drive pulley segment 54 from the clamping position into a slightly displaceable position ( FIG. 36).

For the rest, reference is made to the description of the main patent.  

Reference list

A outlet point
E engagement point
G synchronization point
S switching point
M center
K coupling point of the current Element
α clearance angle
β entry angle
γ outlet angle

1

belt

2nd

Double drive disc

3rd

Output double disc

4th

Coupling agent

5

Pulley

6

,

6

'' Sloping surfaces

7

Spacer ring

8th

Cam

9

Control pins

10th

Belt key roller

11

Spreader

12th

Belt cord

13

,

13

'' Tax roles

14

Lever arm

15

Dome strips

16

Carrier plate

17th

Return spring

18th

Shift cable

19th

Control arm

20th

Auxiliary role

21

Bearing journal

22

Driving pin

23

Dome strap

24th

Steel band

25th

corrugated steel band

26

Straps in straps

27

Belt flank

28

Empty strand

29

Reinforcement rib

30th

Dome molding star

31

Plastic webs

32

Snap pins

33

Bending zone

34

Spring gap

35

Sheet metal plate

36

Clearing lips

37

Female connectors

38

to brush

39

Steel spring clip

40

Collar

41

Dirt deflector

42

Belleville washers

43

Connecting bolt

44

Through holes

45

Fall lines of the inclined surfaces

46

Axle tube

47

Drive pulley made of sheet metal

48

Wide V-belts

49

Conical surface of the drive pulley

50

resilient holding element

51

Mounting hole

52

Dome rod

53

Radial groove
I positioning phase
II coupling phase III coupling phase
IV excavation phase

54

Drive pulley segment

55

Carrier disc

56

V-belts

57

Adjustment roller

58

Retaining spring

59

,

59

'Guardrails

60

Guide groove

61

Tension spring

62

bolt

63

Clamping lugs

64

Dome plate

65

Contact piece

66

Retaining pin
δ lead angle
ε switching angle

15

a Dome bar in switching position for outer running circuit

15

i Dome bar in switching position for inner running circuit
Sa switching point for outer running circuit
Si switching point for inner running circuit
Ga synchronization point for outer running circuit
Gi synchronization point for inner running circle coupling point of the preceding one
Ka coupling strip for outer running circle coupling point of the preceding one
Ki dome strip for inner running circle

Claims (19)

1. Infinitely switchable variable transmission according to the preamble and the claims of the main application with radially and tangentially movable and radially and tangentially force-transmitting coupling elements ( 4 , 15 ) that grasp the drive means laterally and according to one or more of claims 8 to 24 of the main application, characterized in that that the coupling strips ( 15 ) of a drive pulley consist of plastic and are injection molded in one piece as coupling strip star ( 30 ) and that the coupling strips on the belt side have a high coefficient of friction and wear resistance to the belt due to their material properties or surface structure, their sliding surfaces on the drive pulley side However, the coefficient of friction with the inclined surfaces is as low as possible, the plastic webs ( 31 ) connecting the individual coupling elements preferably being designed as return springs and preferably also as retaining elements ( 50 ) snapping into the drive disks, w o compensate both radial, tangential and axial displacement of the coupling elements with these return springs. 2. Transmission according to one of claims 8 to 24 of the main application, characterized in that female connectors ( 37 ), brushes ( 38 ) or steel spring clip ( 39 ) on or next to the coupling strips ( 15 ) or a slightly curved, over a spring gap ( 34 ) resilient, wear-resistant sheet metal plate ( 35 ) on the coupling strip grasp the belt in a narrow area and flex before the coupling force is fully applied. 3. Transmission according to one of claims 17 to 24 of the main application, characterized in that the bearing pin ( 21 ) of the control arm ( 19 ) is mounted on an adjusting ring ( 40 ) which by the shift cable ( 18 ) or - in the case of sprung vehicles - one the push rod attached to the vehicle frame at a suitable point is turned. 4. Transmission according to one of claims 1 to 17 of the main application, characterized in that for controlling the radius of the output double plate ( 3 ) resilient or elastic positioning elements, such as. B. female connectors ( 37 ), brushes ( 38 ) or steel spring clip ( 39 ) can be used to hold the incoming belt with a relatively low holding force to the maximum running radius given by the respective running radius on the drive double pulley ( 2 ), with these positioner elements extend the part of the drive pulley defined by the smallest and largest possible running circle and the belt on these positioning elements can move radially inward under the influence of the belt tension of the empty strand on the geometrically maximum possible running circle and the switching point (S) of the coupling means approximately at the synchronous point (G) for the smallest running circle diameter or is shifted further in the running direction and fixed. 5. Transmission according to one of claims 1 to 17 of the main application, characterized in that on the outer edge of the drive pulleys, left and right of the pulley groove, towards the belt, ring-shaped, elastic or resilient dirt deflectors ( 41 ) are attached, which are in the rest position protrude far into the pulley groove that the remaining distance from each other is slightly less than the belt width and the incoming and outgoing belt has to push the dirt deflector aside, the flank of the belt sliding past the cleaning edge of the dirt deflector during the inlet and outlet, and preferably the elastic or resilient dirt deflector ( 41 ) of the driven double pulley take over the function of the positioning elements and always move the belt to the maximum possible barrel diameter by running onto the belt flank from below. 6. Transmission according to one of claims 8 to 24 of the main application, characterized in that the coupling strips have clearing lips ( 36 ) on the edges of the sliding surfaces, which keep the sliding surfaces free of contaminants and that hollow dirt deposits or through holes ( 44 ) can be provided. 7. Transmission according to one of claims 8 to 24 of the main application, characterized in that the longitudinal axis of the coupling strips ( 15 ) seen outside - in the direction of rotation of the drive pulleys ( 2 , 3 , 5 ) - is further forward than the inside and that the longitudinal axis Radius beam (r) intersects with a lead angle (δ) greater than zero. 8. Transmission according to one of claims 8 to 24 of the main application, characterized shows that the leading angle (δ) of the coupling strips measured at the smallest running radius is larger is as: 180 ° / number of coupling strips per drive pulley. 9. Transmission according to claim 8 or 24, characterized in that the coupling strips ( 15 ) are curved in their longitudinal axis in a spiral or arc-like manner and this longitudinal axis preferably has the same or approximately the same lead angle (δ) to the radius beam (r) at each point. 10. Transmission according to one of claims 1 to 24 of the main application, characterized in that the heads of the connecting bolts ( 43 ), which connect the drive pulleys to one another, are preloaded with spring springs - preferably disc springs ( 42 ) or elastic elements, and that the drive pulleys diverge when a certain load is exceeded and that a stop is provided for the coupling means which limits their path of movement, the free space between the coupling means in the stop position being greater than the sum of the belt width and the spring travel available for locking. 11. Transmission according to one of claims 1 to 7 of the main application, characterized in that a commercially available V-belt ( 56 ) or wide V-belt ( 48 ) is used and the coupling elements ( 4 , 15 , 52 , 64 ) sit on the conical pulleys of V-belt drives or V-belt variable speed drives and that they are aligned with the side flanks of the V-belt and that they preferably extend parallel to the conical surface ( 49 ) over the entire possible radius range of the drive pulleys. 12. Transmission according to one of claims 1 to 7 of the main application, characterized in that the coupling elements are designed as coupling strips ( 15 ) which protrude somewhat above the surface of the conical disc, and that the coupling strips ( 15 ) on the conical surface ( 49 ) of the drive pulley obliquely Arranged sliding surfaces are mounted and are radially and tangentially displaceable over this in a certain way and that the coupling strips ( 15 ) increasingly come out of the conical surface during the displacement by the incoming belt and couple the overlying belt, the slope of the inclined surfaces relative to an imaginary one , plane perpendicular to the axis of rotation is preferably 1: 2 to 1: 6. 13. Transmission according to claim 11, characterized in that the coupling elements ( 4 ) from coupling rods ( 52 ) are round, oval or polygonal cross-section and are preferably arranged radially, these rods in radial grooves ( 53 ) in the conical surface ( 49 ) of the drive pulley are stored and in their rest position they protrude somewhat over the conical surface and roll or tilt under belt load over a certain distance in the circumferential direction and can slide in the radial direction and thus increase their projection over the conical surface and press onto the belt flank depending on the load. 14. Transmission according to one of claims 12 and 13, characterized in that the coupling means ( 4 ) by return springs or resilient holding elements ( 50 ) in their rest position, that is the position with the least protrusion on the surface of the conical disk, are withdrawn. 15. Infinitely variable vario transmission according to claim 11, characterized in that the drive double disks are divided into several drive disk segments ( 54 ), on each of which one or more radially and tangentially movable coupling elements ( 4 ) are attached in pairs, and that the drive disk segments ( 54 ) each are arranged radially displaceably on a carrier disk ( 55 ) and can be self-locking in any radial position under belt load and that a conventional V-belt ( 56 ) is used as the driving means, on the sides of which the coupling elements designed as coupling plates ( 64 ) are aligned and act. 16. A transmission according to claim 15, characterized in that the drive pulley segments ( 54 ) are radially adjusted by an adjusting mechanism which cancels the effect of the self-locking mechanism in the sector without an overlying V-belt ( 56 ) by initiating the adjusting forces with a force vector which obliquely directed at the carrier disc (55) inwardly towards and radially outwardly and which always applies radially outside the belt side clamping nose (63) on the carrier disc (55). 17. A transmission according to claim 16, characterized in that the adjusting mechanism is formed by two flexible and displaceable or pivotable guide rails ( 59 , 59 '), the spacing of which tapers in the direction of the funnel and on which adjusting rollers ( 57 ) start, which on each drive pulley segment ( 54 ) are attached, the adjusting rollers ( 57 ) being stirred by the outer guide rail ( 59 ') on the face and flank sides and thereby prevented from self-locking tilting and that the guide rails are fastened to the gear frame and do not rotate and that the position of the funnel-like tapered section can be adjusted radially by pivoting the switching element ( 65 ) via the shifting cable ( 18 ). 18. Gearbox according to claim 17, characterized in that the flexible guide rails ( 59 , 59 ') of the driven side on the funnel-like taper a piece approximately parallel to each other at a distance from the diameter of an adjusting roller ( 57 ) are stirred and by a tension spring ( 61 ) Press outwards until the incoming empty run of the V-belt ( 56 ) lies, whereby the control rollers in this parallel section no longer roll on the flank side but only on the end face on the guide rails ( 59 ') and allow the drive pulley segments to tilt independently. 19. Transmission according to claims 8-24 of the main application, characterized in that the Sloping surfaces of a dome bar and the sloping surfaces assigned to them on the drive pulley in several mutually parallel and stair-like sub-areas are divided.