CN116324217A

CN116324217A - Flat ring chain and conical disc belt transmission device

Info

Publication number: CN116324217A
Application number: CN202180068516.8A
Authority: CN
Inventors: C·特劳特曼
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2020-11-12
Filing date: 2021-09-24
Publication date: 2023-06-23
Also published as: DE102020129931B4; DE102020129931A1; WO2022100777A1

Abstract

The invention relates to a flat endless chain (1) for a conical belt drive with steplessly adjustable transmission ratio. According to the invention, each link set (30) of the flat ring chain has a width (B) of exactly thirty-three link plates (2) of a predetermined link plate width (B1), wherein the intermediate link (3-2) is placed on the link plate positions one (KLP 1), five (KLP 5), eight (KLP 8), eleven (KLP 11), fourteen (KLP 14), seventeen (KLP 17), twenty (KLP 20), twenty-three (KLP 23), twenty-six (KLP 26), twenty-nine (KLP 29) and thirty-three (KLP 33), wherein the first link (3-1) adjacent to the intermediate link (3-2) is placed on the link plate positions three (KLP 3), four (KLP 4), nine (KLP 9), twelve (KLP 12), fifteen (KLP 15), eighteen (KLP 18), twenty-one (KLP 21), twenty-four (KLP 24), twenty-seven (KLP 27), twenty-eight (KLP 28) and thirty-two (KLP 32), and wherein the first link (3-1) adjacent to the intermediate link (3-2) is placed on the link plate positions three (KLP 4), nine (KLP 9), twelve (KLP 12), fifteen (KLP 15), eighteen (KLP 18), twenty-eight (KLP 18) and twenty-seven (KLP 32) adjacent to the intermediate link links (3-2) are placed on the link plate positions twenty-six (3-six (8), twenty-seven (KLP) and twenty-six) and twenty-eight (9) link plates (9) and six (25) to be placed on the link chain Thirty (KLP 30) and thirty-one (KLP 31) are used for placing the chain plate (2).

Description

Flat ring chain and conical disc belt transmission device

Technical Field

The invention relates to a flat link chain for a conical pulley belt drive with a continuously variable transmission ratio, wherein the rocking joints of the flat link chain, which are connected to individual links formed by a pallet group having a plurality of pallet plates, are formed as rocking pressure elements which are pushed into recesses of the pallet plates in pairs and which have rolling surfaces which bear against one another. Here, three links arranged adjacent to each other in the circumferential direction of the flat ring chain form a link set. The flat ring chain is formed by a plurality of link sets placed directly next to one another in the circumferential direction, wherein the link plates are arranged symmetrically in the link sets with respect to the center point of the link sets, as seen over the entire width of the flat ring chain. The invention also relates to a conical belt drive for a motor vehicle, the drive ratio of which can be adjusted steplessly.

Background

Flat ring chains are used as belt mechanisms in mechanically adjustable continuously variable transmissions for motor vehicles. A mechanically adjustable continuously variable transmission (in english Continuously Variable Transmission, CVT for short) enables stepless adaptation of the transmission ratio without interruption of the traction force. The flat link chain has link plates arranged side by side with each other connected via a pressure member. In the chains currently existing on the market, the axial locking of the pressure element is achieved via a locking element, for example a short wire element.

The following characteristics characterize a flat ring chain (or CVT flat ring chain or CVT chain):

with the CVT chain, low consumption and excellent running dynamics are achieved. This is possible by means of a wobble hinge structure of the CVT chain, with which a small swivel circle on the conical disc is achieved, thus achieving a high transmission shift range.

A CVT chain can be utilized to transmit high torque. Thicker straps that may optionally be used provide for even load distribution in the outer regions of the line.

The element is characterized by low internal friction losses caused by the rolling of the rocking pressure, ensuring good transmission efficiency.

The CVT chain is insensitive to track deflection by the optionally earth-like implemented end faces of the rocking pressure member. In combination with the optionally arched implementation of the conical disk, the additional component of the track offset which must occur in the adjustment is reduced. Furthermore, CVT chains are insensitive to disc pack deformation under load, angular errors, and relative torsion between the fixed and movable conical discs. Thus, no ball guide for an axially movable conical disc is required.

When using CVT chains, low axial forces are obtained at the main disc set. This makes it possible to work with low hydraulic pressure on a given cylinder surface, which is a further advantage in terms of transmission efficiency.

The line can be implemented as a three-strap assembly, enabling a short basic division. In short links, only the bows of the access plates are between adjacent hinges.

The second strap length enables advantageous acoustic performance to be achieved by computationally optimizing the division sequence of the long and short straps.

A flat ring chain for a continuously variable transmission of a motor vehicle is known from EP 2 587 091 B1, wherein the element groups of the flat ring chain are formed by three chain elements following one another, wherein the arrangement patterns in the respective element groups are identical, and wherein the number of links in the three link units contained in each element group is 9, 8 or 8, respectively.

Disclosure of Invention

The present invention is based on the object of providing a flat ring chain or a continuously variable transmission having a flat ring chain, wherein the flat ring chain or the continuously variable transmission is further optimized with respect to wear characteristics. Advantageously, a reduced loading of the link plate and of the rocking pressure element is to be achieved by the invention.

The object is achieved by a flat endless chain for a conical pulley transmission with the features of claim 1 for steplessly adjustable transmission ratios and a conical pulley transmission with the features of claim 4. In the flat ring chain constructed according to the invention, the rocking joint elements connected by the individual links formed by the pallet string having a plurality of pallet blocks are constructed as rocking pressure elements which are pushed into the recesses of the pallet blocks in pairs, the rocking pressure elements having rolling surfaces which bear against one another, wherein three links arranged adjacent to one another in the circumferential direction of the flat ring chain form a link string. The flat ring chain is formed by a plurality of link groups which are placed directly next to one another in the circumferential direction, wherein the link plates are arranged symmetrically in the link groups relative to the center point of the link groups, as seen over the entire width of the flat ring chain. According to the invention, each link set of the flat ring chain has a width of exactly thirty-three link plates, which have a predetermined link plate width. The intermediate link occupies a first link plate position, a fifth link plate position, an eighth link plate position, an eleventh link plate position, a fourteenth link plate position, a seventeenth link plate position, a twentieth link plate position, a twenty third link plate position, a twenty sixth link plate position, a twenty ninth link plate position, and a thirty third link plate position with the link plates. In addition, a first link disposed immediately adjacent to the intermediate link occupies a third link position, a fourth link position, a ninth link position, a twelfth link position, a fifteenth link position, an eighteenth link position, a twenty-first link position, a twenty-fourth link position, a twenty-seventh link position, a twenty-eighth link position, and a thirty-second link position of the link with the link. Finally, a second link disposed immediately adjacent (in the other direction) to the intermediate link occupies a second link position, a sixth link position, a seventh link position, a tenth link position, a thirteenth link position, a sixteenth link position, a nineteenth link position, a twenty-second link position, a twenty-fifth link position, a thirty-first link position, and a link position of the thirty-first link position with the link. The following advantages are achieved in this way: individual link plates of flat-ring chains of different widths and rocking pressure members are subjected to significantly reduced loads. The strap force can be distributed very uniformly by the structure described above and the load on the individual elements can thereby be reduced, whereby an extended service life of the flat link chain is achieved with the same load (torque transmission). Alternatively, a flat ring chain of such a modified design can also transmit higher torques with a constant service life.

First of all, the individual elements of the claimed subject matter are set forth in the order they are presented in the claims or their meanings, and particularly preferred embodiments of the subject matter are described below.

The link plates are an essential component of a flat link chain. The link plate is an elongate plate having one or more through-openings extending transversely to the longitudinal direction of the plate and for receiving so-called rocking pressure elements (also referred to as pressure elements or rocking elements).

The rocking pressure member is also an essential component of the flat ring chain other than the link plates. The rocking pressure element forms a so-called rocking hinge together with the through opening through which the rocking pressure element of the link plate is guided. By means of the rocking hinge structure of the flat link chain, it is possible to achieve a small swivel circle on the conical disk, so that a high transmission gear range can be achieved.

The component or the structural design for the link plate that cannot be laterally and axially displaced from the pressure element is called a locking element. In the simplest case, the pressure element is locked at least at its axial ends by means of welded wire elements or the like.

Further advantageous embodiments of the invention are given in the dependent claims. The features listed individually in the dependent claims can be combined with one another in a technically meaningful way and further embodiments of the invention can be defined. Furthermore, the features specified in the claims are explained and illustrated in detail in the description, wherein further preferred embodiments of the invention are shown.

According to an advantageous embodiment of the invention, it can be provided that, in at least a plurality of directly adjacent link positions, which are directly transverse to the longitudinal extension direction of the chain, in one link of the flat link chain, the link plates for one link of the plurality of link positions are formed by a single link plate, so that within the link group, there is a link plate having a first link plate width and a link plate having a second link plate width which is different from the first link plate width. The advantage of this embodiment is that the load on the components of the flat link chain, in particular the total frictional losses between the link plates of the flat link chain, are further reduced.

According to a further preferred development of the invention, it can also be provided that each link set is formed by eighteen link plates each having a minimum link plate width, as a result of which the assembly and storage effort of the components can be further optimized.

The object on which the invention is based is furthermore achieved by a conical pulley belt drive with steplessly adjustable transmission ratio, comprising a first conical pulley pair arranged on a first shaft and a second conical pulley pair arranged on a second shaft, and a flat ring chain arranged for transmitting torque between the first conical pulley pair and the second conical pulley pair, wherein the flat ring chain is constructed according to the invention as described hereinabove.

Advantageously, the conical discs of the first conical disc pair and the conical discs of the second conical disc pair have the following conical disc angles, respectively: the cone disc angle is greater than seven degrees and less than thirteen degrees, especially between nine degrees and eleven five degrees. This allows an optimized interaction with the flat link chain constructed according to the invention.

Furthermore, the conical pulley transmission can also be modified as follows: the conical discs of the first conical disc pair and the conical discs of the second conical disc pair are formed of carburized steel, named CrMo or named CoNiMo, which is also beneficial for the low wear co-action of the flat ring chain constructed according to the invention with the conical discs of the transmission.

According to a further preferred embodiment of the conical pulley transmission, it can be provided that the conical pulley transmission, together with its conical pulley pair, is configured to be driven on the drive side at a rotational speed of approximately 4000 rpm to 6500 rpm and on the output side at a rotational speed of approximately 12000 rpm, in such a way that the following operation is ensured: within this operation, a wear-reducing operation of the flat link chain can be achieved.

Finally, the invention can also be advantageously implemented as follows: the driven pair of conical discs is configured to transmit at least 150Nm of torque. The conical disk pair is advantageously optimized for a torque range up to a maximum of 460 Nm.

Drawings

The invention and the technical field are described in detail below with reference to the accompanying drawings. It should be noted that the invention should not be limited by the illustrated embodiments. In particular, if not explicitly stated otherwise, it is also possible to extract sub-aspects of the facts set forth in the figures and to combine them with other components and knowledge in the present description and/or in the figures. It should be noted in particular that the figures and the size relationships particularly shown are only schematic. Like reference numerals designate like objects so that the description from other figures may be used in addition as necessary.

The drawings show:

figure 1 shows in a perspective view a part of a flat loop chain according to the prior art,

fig. 2 shows a conventional flat ring chain partially in a top view in an upper view, and a sectional view of a rocking pressure member along the flat ring chain in a lower view, wherein the construction and the designation of the individual elements of the flat ring chain are probed according to the schematic drawing,

fig. 3 shows the basic construction of a link set in a schematic view in a top view, wherein three individual links are shown in the upper view, and the connection of the three links is shown in the form of a link set of the three links in the lower view,

FIG. 4 partially shows a flat endless chain constructed in accordance with the present invention in a top view, and

fig. 5 shows in schematic diagram a CVT transmission unit with a conical pulley gear connected into the powertrain of a hybrid vehicle.

Detailed Description

Fig. 1 shows a flat ring chain 1 for a mechanically adjustable continuously variable transmission of a motor vehicle according to the prior art. The flat link chain 1 comprises a plurality of link plates 2, a plurality of oscillating pressure members 5 and a plurality of locking elements 50, wherein the oscillating pressure members 5 for the articulated connection of the link plates 2 transversely to the longitudinal direction of the flat link chain 1 are arranged in recesses 20 of the link plates 2 for forming the oscillating hinges 4, and wherein the link plates 2 are arranged in such a way that they remain locked against axial displacement relative to the oscillating pressure members 5 via the locking elements 50.

Fig. 2 shows a conventional flat ring chain 1 partially in a top view in an upper view and a section view of a rocking pressure element 5 along a rocking hinge 4 of the flat ring chain 1 in a lower view, wherein the construction and the designation of the individual elements of the flat ring chain 1 are to be elucidated from the schematic. In the upper illustration, it can be clearly seen here that: each link 3;3-1,3-2,3-3 how the individual link sets 30 are formed in a orderly fashion within the endless flat chain 1, and how the link sets 30 of the same construction are formed in an orderly fashion within the endless flat chain 1.

In the lower illustration, the arrangement of the individual link plates 2 at the respective link plate positions KLP following one another from the first link plate position KLP1 to the last link plate position KLPn over the width B of the link plate group can be clearly seen. The width B of the link plate assembly corresponds approximately to the inner distance between the two locking elements 50 at the shown rocking pressure element 5. The outer chain width b, which is also shown, corresponds approximately to the axial length of the rocking pressure element 5, measured in its central axis.

Fig. 3 shows a schematic representation of the basic structure of a link set 30 in a top view. In the upper illustration, three individual chain links 3 are shown; 3-1,3-2,3-3, and the connection of the three links 3-1,3-2,3-3 is shown in the lower illustration in the form of a link set 30 made up of the three links 3-1,3-2,3-3 as part of the flat ring chain 1. The individual links 3 are coupled or connected to one another via a rocking hinge 4, which is formed by two pressure elements 5 of adjacent links 3, which pass through openings 20 in the link plates 2 of the links 3. The flat ring chain 1 is composed of a plurality of link groups 30 of the same construction, which are disposed one after another and connected to each other. In the lower illustration, the flat link chain 1 has a plurality of link plates 2 over its width (strap group width) B extending transversely to the longitudinal direction of the flat link chain 1. Each link plate 2 is here associated with a link plate position KLP, seen in the width B of the flat link chain 1, which is shown here by link plate positions from a first link plate position "one" KLP1 (lower edge) to a last link plate position "n" KLPn (upper edge).

In the region of the axial ends of the oscillating pressure members 5, they each have a locking element 50 via which the link plate 2 is prevented from being lost laterally.

Fig. 4 shows a part of a flat link chain 1 constructed according to the invention in a top view. The flat chain 1 shown constitutes a conical pulley belt drive 100 for a motor vehicle, the drive ratio of which can be adjusted steplessly (see fig. 5). The rocking joints 4 connected by the individual links 3 formed by the pallet group with a plurality of pallet plates 2 are formed here as rocking pressure elements 5 which are pushed into recesses 20 of the pallet plates 2 in pairs and have rolling surfaces W (fig. 1) which bear against one another. The three links 3 arranged next to one another in the circumferential direction of the endless flat chain 1 each form a link set 30, wherein the endless flat chain 1 is formed by a plurality of link sets 30 lying directly next to one another in the circumferential direction, and wherein the link plates 2 are arranged in the link sets 30 point-symmetrically with respect to the center point P of the link sets 30, as seen over the entire width of the endless flat chain 1 or over the width B of the link sets. Each link set 3;3-1,3-2,3-3 have a predetermined width B of exactly thirty-three link plates 2 of link assembly 30, wherein intermediate link 3-2 of link assembly 30 rests on link plates 2 of predetermined link plate width B1 at link plate positions one KLP1, five KLP5, eight KLP8, eleven KLP11, fourteen KLP14, seventeen KLP17, twenty-three KLP20, twenty-three KLP23, twenty-six KLP26, twenty-nine KLP29 and thirty-three KLP 33. The first link 3-1 disposed immediately adjacent to the intermediate link 3-2 has a link plate 2 at the link plate positions three-KLP 3, four-KLP 4, nine-KLP 9, twelve-KLP 12, fifteen-KLP 15, eighteen-KLP 18, twenty-one-KLP 21, twenty-four-KLP 24, twenty-seven-KLP 27, twenty-eight-KLP 28, and thirty-two-KLP 32, and the second link 3-3 disposed immediately adjacent to the intermediate link 3-2 (in the other direction) places the link plate 2 at the link plate positions two-KLP 2, six-KLP 6, seven-KLP 7, ten-KLP 10, thirteenth-KLP 13, sixteen-KLP 16, nineteen-KLP 19, twenty-two-KLP 22, twenty-five-KLP 25, thirty-KLP 30, and thirty-one-KLP 31. Each link set 3 is formed here by thirty-three link plates 2 of the same link plate width b 1.

Fig. 5 shows in schematic diagram a CVT transmission unit with a conical pulley drive 100 connected into the powertrain of a hybrid vehicle. The conical pulley drive 100 (also referred to as a gearbox) comprises: a first conical disk pair 300 having a first conical disk 301 configured as a fixed disk and a second conical disk 302 configured as a displacement disk, which is arranged so as to be axially movable; and a second conical disk group 500 having a first conical disk 501 configured as a fixed disk and a second conical disk 502 configured as a displacement disk, which is axially movably provided; connecting two cone disc sets 300;500 are configured as belt mechanisms of the endless flat chain 1. The CVT transmission unit further includes an actuator unit AE by means of which the first and second cone disc sets 300;500, a displacement plate 302;502 may be axially adjusted so that a desired gear ratio between the first cone disc set 300 and the second cone disc set 500 may be set. The first cone disc set 300 may be driven via an electric motor EM and/or an internal combustion engine BKM. Here, between the internal combustion engine BKM and the driven transmission, the electric machine EM is connected into the powertrain via a disconnect clutch provided on the internal combustion engine side and a disconnect clutch provided on the transmission side. The second conical disc set 500 is connected to a drive shaft of the motor vehicle via a transmission unit. The actuator unit AE is actuated via a control unit, not shown.

Fig. 5 furthermore shows that the

conical discs

301, 302 of the first conical disc pair 300 and the

conical discs

501, 502 of the second conical disc pair 500 have conical disc angles θ1, θ2, respectively. The cone disc angle is advantageously greater than seven degrees and less than thirteen degrees, and particularly preferably between nine degrees and eleven five degrees.

The invention is not limited to the embodiments shown in the figures. Accordingly, the foregoing description is not to be considered as limiting, but rather as explanatory. The following claims should be studied to determine the existence of such features in at least one embodiment of the invention. This does not preclude the presence of other features. If the claims and the above description define "first" and "second" features, the names are used to distinguish two features of the same type, without specifying a priority.

List of reference numerals

1. Flat loop chain

2. Chain plate

20. Blank part

3. Chain link

3-1 first chain link

3-2 second chain link

3-3 third chain link

30. Chain link set

4. Swing hinge

5. Swinging pressure piece

W rolling surface

50. Locking element

100. Conical disk belt transmission device

200. First shaft (taper disk belt driving device)

300. First conical disk pair

301. First conical disk of first conical disk pair

302. Second conical disk of first conical disk pair

400. Second shaft (taper disk belt driving device)

500. Second conical disk pair

501. First conical disk of second conical disk pair

502. Second conical disk of second conical disk pair

KLP chain plate position

Width of chain plate group B

b (average) width of pressure member

Angle of theta 1, theta 2 conical disk

BKM internal combustion engine

EM motor

AE actuator unit

P midpoint or symmetry point (Point symmetry for a set of links)

Claims

1. A flat endless chain (1) for a conical pulley belt drive with steplessly adjustable transmission ratio,

the rocking joint (4) of the flat link chain, which is to be connected by individual links (3) of a pallet group having a plurality of pallet plates (2), is designed as a rocking pressure element (5) which is pushed into recesses (20) of the pallet plates (2) in pairs and has rolling surfaces (W) which bear against one another,

wherein three links (3; 3-1,3-2, 3-3) arranged adjacently in the circumferential direction of the Ping Huanlian (1) form a link set (30),

wherein the Ping Huanlian (1) is formed by a plurality of link sets (30) placed directly next to each other in the circumferential direction,

and wherein the link plate (2) is arranged point-symmetrically in the link set (30) with respect to the center point (P) of the link set (30) as seen over the entire width of the Ping Huanlian (1),

it is characterized in that the method comprises the steps of,

each link set (30) has a width (B) of exactly thirty-three link plates (2) having a predetermined link plate width (B1),

wherein the intermediate link (3-2) places the link plate (2) at link plate positions (KLP) one (KLP 1), five (KLP 5), eight (KLP 8), eleven (KLP 11), fourteen (KLP 14), seventeen (KLP 17), twenty (KLP 20), twenty-three (KLP 23), twenty-six (KLP 26), twenty-nine (KLP 29) and thirty-three (KLP 33),

-wherein a first link (3-1) adjacent to the intermediate link (3-2) places a link plate (2) on link plate positions (KLP) three (KLP 3), four (KLP 4), nine (KLP 9), twelve (KLP 12), fifteen (KLP 15), eighteen (KLP 18), twenty-one (KLP 21), twenty-four (KLP 24), twenty-seven (KLP 27), twenty-eight (KLP 28) and thirty-two (KLP 32), and

-wherein a second link (3-3) adjacent to the intermediate link (3-2) places the link plate (2) on link plate positions (KLP) two (KLP 2), six (KLP 6), seven (KLP 7), ten (KLP 10), thirteen (KLP 13), sixteen (KLP 16), nineteen (KLP 19), twenty-two (KLP 22), twenty-five (KLP 25), thirty (KLP 30) and thirty-one (KLP 31).

2. The flat loop chain (1) according to claim 1,

it is characterized in that the method comprises the steps of,

in at least a plurality of directly adjacent link plate positions (KLP), in one link (3, 3-1,3-2, 3-3) of the Ping Huanlian (1), the link plate (2) is formed by a single link plate (2) having an increased link plate width (b 2), in particular having twice the link plate width (b 2).

3. The flat loop chain (1) according to claim 1,

it is characterized in that the method comprises the steps of,

each link set (30) is formed by eighteen link plates (2) each having a minimum link plate width (b 1).

4. A continuously variable transmission ratio conical pulley belt drive (100) comprising a first conical pulley pair (300) arranged on a first shaft (200) and a second conical pulley pair (500) arranged on a second shaft (400), and a flat endless chain (1) arranged for transmitting torque between the first conical pulley pair (300) and the second conical pulley pair (500),

it is characterized in that the method comprises the steps of,

the Ping Huanlian (1) is constructed according to any one of the preceding claims.

5. The conical pulley drive (100) according to claim 4,

it is characterized in that the method comprises the steps of,

the conical discs (301, 302) of the first conical disc pair (300) and the conical discs (501, 502) of the second conical disc pair (500) have the following conical disc angles (θ1, θ2), respectively: the cone disc angle is greater than seven degrees and less than thirteen degrees, especially between nine degrees and eleven five degrees.

6. The conical pulley belt drive (100) according to claim 4 or 5,

it is characterized in that the method comprises the steps of,

the conical discs (301, 302) of the first conical disc pair (300) and the conical discs (501, 502) of the second conical disc pair (500) are formed of carburized steel named 15CrMo5 or named 17CoNiMo 6.

7. The conical pulley transmission (100) according to any of the preceding claims 4 to 6,

it is characterized in that the method comprises the steps of,

the drive cone disk pair (300) is designed to be driven at a rotational speed of up to a maximum of 12000 revolutions per minute, in particular up to a maximum of 6500 revolutions per minute.

8. The conical pulley transmission (100) according to any of the preceding claims 4 to 7,

it is characterized in that the method comprises the steps of,

the drive cone pair (300) is configured to transmit at least 150Nm of torque.