EP3728900A1

EP3728900A1 - Toothing arrangement

Info

Publication number: EP3728900A1
Application number: EP18808253.1A
Authority: EP
Inventors: Matthias Reisch; Christoph Erkens; Eckhardt LÜBKE; Martin Rattay; Marc Seeberger
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2017-12-18
Filing date: 2018-11-16
Publication date: 2020-10-28
Also published as: US20210088119A1; CN111480022B; DE102017223019A1; US11215271B2; CN111480022A; WO2019120799A1

Abstract

A toothing arrangement (1) is proposed, comprising at least one first helically toothed spur gear (3) and one second helically toothed spur gear (4) which form a common running toothing, and at least one thrust collar (7) with two raceways (8, 9) for axial force compensation on both sides in the region of the running toothing, wherein the ring-shaped thrust collar (7) is designed with an internal toothing (10) which, in the assembled state, is supported in an encircling groove (11) which interrupts the toothing (5) of the first spur gear (3), wherein the thrust collar (7) is assigned at least one rotation prevention means, wherein the rotation prevention means is designed such that the rotation prevention means is movable from a radially inner region to a radially outer region of the first spur gear (3) into the blocking position. A transmission having the toothing arrangement is also proposed.

Description

Verzahnungsanordnunq

The present invention relates to a tooth arrangement according to the genus defined in more detail in the preamble of claim 1. Furthermore, the invention relates to a transmission with the toothing arrangement.

In today's gear transmissions, for example. In the drive train for a motor vehicle, mainly helical gears are used for acoustic reasons. Compared to a straight toothing caused by a helical toothing between the gears additional axial forces, which must be supported. Most of these forces are introduced via the respective shaft bearings in the housing. By the mechanical

Additional effort for this cause disadvantages in size and cost. Furthermore, additional storage losses occur which worsen the efficiency. To reduce this problem, there are solutions in which the axial forces are compensated directly in the area of the gears by corresponding contact surfaces on so-called pressure combs.

For example, from the document DE 30 22 020 C2 is an axial

Power transmission device for a spur gear known. The spur gear comprises two meshing spur gears, the helical teeth as

have common running teeth. In one of the spur gears a toothing interrupting circumferential groove is provided, in which a pressure ring or an annular pressure comb with two raceways is arranged for bilateral Axialkraftaufnahme. For assembly, the pressure comb on an internal toothing, which corresponds to the toothing of the spur gear, so that the pressure comb with the internal teeth on the teeth of the spur gear is axially pushed to be brought into the central groove of the spur gear. For axial locking of the pressure comb is half a

Tooth pitch twisted against the spur gear. In order to prevent undesired rotation of the pressure comb, it is provided in the known spur gear that a bolt is guided from the outside radially through the pressure comb, which protrudes into a tooth gap of the toothing of the spur gear.

It has been shown that in such a rotation of the pressure comb is disadvantageously mechanically weakened. In addition, the bolt must be dimensioned accordingly to ensure the absorption of the torsional forces occurring. The present invention has for its object to provide a gearing arrangement and a transmission with the gearing arrangement of the type described above, which ensure in a structurally simple and safe way anti-rotation of a pressure comb.

This object is achieved by the features of claim 1 or 1 1. Advantageous and claimed developments emerge from the

Subclaims and the description and the drawing.

Accordingly, a toothed arrangement is proposed, comprising at least a first at least partially helical gear, in particular a spur gear and a second at least partially helical spur gear, which form a common running toothing. Furthermore, the toothing arrangement comprises at least one pressure comb with two raceways for bilateral Axialkraftausgleich in the field of running teeth of the gears, wherein the annular pressure comb with a

Internal toothing or the like is executed, which is received or supported in the mounted state in a toothing of the first spur gear breaking circumferential groove, and wherein the pressure comb is associated with at least one rotation. To perform a particularly cost-effective and secure rotation, it is provided that the rotation is movable from a radially inner region to a radially outer region of the first spur gear in the blocking position or blocking acts.

In this way, a gearing arrangement is proposed with a pressure comb, which can be particularly easily pushed axially with its preferably also helical internal teeth on the gear or spur gear and can absorb axial forces in both directions of the running gear in the assembled state using its axially provided trajectories. This results, if any, only a small axial play. By the inventively provided anti-rotation, which is quasi at least from the radially inner region to the radially outer region in the

assigned gear is brought into the locked position or operative position, a particularly cost-effective and compact gear arrangement is realized. In particular, only a few components are needed and saved radial space.

Regardless of the specific structural design of the rotation is provided that the rotation in the locked position from the groove bottom of the groove of the first spur gear radially outward into the internal teeth of the pressure comb

interlocking or blocking engages. As a result, the pressure comb in an advantageous manner not mechanically weakened. The rotation thus acts by a movement from a radially inner region to a radially outer region in the locking position in the associated spur gear. The provided on the spur circumferential groove thus serves not only for receiving and centering of the pressure comb, but also for

Realization of the anti-twist device. The groove base of the associated gear thus forms the centering diameter for the tip circle diameter of the pressure comb. Here, the groove base diameter of the associated gear or spur gear is greater than the Fußkreisdurchmesser to achieve the desired centering. The

Nutgrunddurchmesser is thus a broken diameter by the diameter.

A particularly simple solution of the idea according to the invention is achieved in that the anti-rotation device comprises at least one blocking element and at least one detent for holding the blocking element in the blocking position. For example, it is also possible that the blocking element and the locking quasi one piece as a screw, for example, a grub screw or the like are executed. The possible constructive

Versions of the locking element and the lock are thus varied. Particularly expedient seems a pen-shaped, sleeve-shaped or the like executed

Locking element, wherein the lock can be realized for example via a spring, a snap ring or other the gear, for example, from the radially inward associated component. The blocking element and the lock can be provided in an arbitrarily designed radial bore or through hole in the associated gear. The at least one radial bore or at least one

Through hole for receiving the rotation can z. B. perpendicular with respect to the longitudinal axis of the first spur gear from the radially inner region to the radially outer region may be arranged in the first spur gear. It is also quite possible that the radial bore or through-bore runs obliquely from the radially inner region to the radially outer region in or through the gearwheel at a predetermined angle. In contrast to the vertical orientation of the radial bore or through hole of the predetermined angle is greater or less than 90 degrees, so that an oblique course of the radial bore or through hole is realized in or through the gear.

In the context of an advantageous development of the invention it is provided that in the blocking position of the locking element, a predetermined radial distance between the pressure comb-facing end of the locking element and the root circle of the internal toothing of the pressure comb is provided. As a result, for a possible disassembly, the blocking element or the anti-rotation device can be grasped particularly simply in order to move the blocking element radially inward. Regardless of the specific embodiments, it is provided that the proposed toothing arrangement is associated with a plurality of anti-rotation devices distributed over the circumference of the pressure comb.

Furthermore, the present invention also claims any transmission of a vehicle with at least one toothing arrangement according to the invention.

Hereinafter, the present invention will be further explained with reference to the drawings. Show it:

Figure 1 is a three-dimensional view of an inventive

Gear arrangement with a pressure comb based on gears designed as spur gears;

Figure 2 is a three-dimensional view of one of the spur gears of

Gear arrangement with the pressure comb before assembly;

Figure 2A is a purely schematic view of a transmission with the

Tooth arrangement;

Figure 3 is a sectional view of the gear arrangement;

Figure 4 is a cross-sectional view of a first embodiment of a

Anti-rotation of the pressure comb of the gear arrangement;

Figure 5 is a longitudinal sectional view of the gear arrangement with an alternative embodiment of the pressure comb;

Figure 6 is a cross-sectional view of a second embodiment of

Anti-rotation of the pressure comb of the gear arrangement;

Figure 7 is a cross-sectional view of a third embodiment of the rotation of the pressure comb of the toothing arrangement;

Figure 8 is a longitudinal sectional view of the third embodiment of the rotation of the pressure comb of the toothing arrangement; Figure 9 is a cross-sectional view of a fourth embodiment of the rotation of the pressure comb of the toothing arrangement;

Figure 10 is a longitudinal sectional view of the fourth embodiment of the rotation of the pressure comb of the toothing arrangement;

Figure 1 1 is a longitudinal sectional view of a fifth embodiment of

Anti-rotation of the pressure comb of the gear arrangement; and

Figure 12 is a longitudinal sectional view of a sixth embodiment of

Anti-rotation of the pressure comb of the toothing arrangement.

FIGS. 1 to 12 show various views of a device according to the invention

Gear arrangement 1 exemplified for use in any gear 2 exemplified.

In the embodiments shown by way of example, the toothing arrangement 2 according to the invention comprises a first helical gear 3 and a second helical gear 4 which, with their toothings 5, 6, form a common circumferential one

Forming running toothing. Further, at least one pressure comb 7 is provided with two axial side raceways 8, 9 for bilateral Axialkraftausgleich in the field of running gear. The closed annular pressure comb 7 has an internal toothing 10 on the inner diameter. In the mounted state, the pressure comb 7 is received with its internal toothing 10 in a toothing 5 of the first spur gear 3 interrupting circumferential groove 1 1, as can be seen in particular from Figure 1 and 2.

The pressure comb 7 comprises at least one rotation, the concrete

Embodiments subject of Figures 3 to 12 is. The anti-rotation holds the

Pressure comb 7 in its desired position. According to the invention it is provided that the

Anti-rotation is carried out such that the rotation in the first spur gear 3 is substantially movable from radially inward to radially outward into the active or locking position.

FIG. 1 shows a perspective view of the gear arrangement in which the

Pressure comb 7 is rotated relative to the first spur gear 3 in the groove 1 1 by half a tooth and thereby can transmit axial force in both directions. The raceways 8, 9 of the pressure comb 7 transmit the axial forces to the corresponding contact surfaces 14 in a toothing 6 of the second spur gear 4 interrupting recess 15. The contact surfaces 14 of the second spur gear 4 are located radially below the Fußkreisdurchmessers. On both sides of the pressure comb 7 is the running teeth of the two spur gears 3, 4. The profile displacement of the running gear is selected so that the contact radius is close to the rolling radius. As a result, the losses at the contact point or at the contact surface of the pressure comb 7 are minimized. The geometry of the raceways 8, 9 of the pressure comb 7 and the corresponding contact surfaces 14 of the second spur gear 4 at least approximately correspond to the lateral surface of a

Truncated cone. The cone geometry is superimposed on a crown. The first spur gear 3 and the second spur gear 4 may be designed, for example, in one piece or also in several parts with a shaft. Depending on the embodiments, it is possible that one of the two spur gears 3, 4 is designed as a switchable idler gear, which does not have its own axial bearing. The intended pressure comb 7 can also be used in a wheel chain of one or more gears. Thus, the pressure comb 7 and the groove 1 1 is used multiple times. It can also be several same axis rotating gears with pressure comb 7 and / or groove 1 1 are arranged side by side.

In Figure 2, the first spur gear 3 and the pressure comb 7 is shown prior to assembly. From this representation, the centering diameter 12 of the first spur gear 3 can be seen, on which the head diameter 13 of the internal toothing 10 of the pressure comb 7 is centered. To assemble the pressure comb 7, the pressure comb with its internal toothing 10 is pushed onto the toothing 5 of the first spur gear 3 until the pressure comb is centered in the groove 11 between the toothing 5 interrupted by the groove 11. Subsequently, the pressure comb 7 is rotated about half a pitch to the first spur gear 3.

Finally, the rotation is activated and the pressure comb 7 is fully assembled.

FIG. 2A diagrammatically shows a transmission 2 of any type, for example for vehicles, which comprises the toothing arrangement 1 according to the invention, and thus shows a possible use.

FIG. 3 shows a sectional view of the toothing arrangement according to the invention, in which the pressure comb 7 is shown in installation positions. In order to mount this, the tooth gaps of the internal teeth 10 of the pressure comb 7 are brought into coincidence with the teeth of the toothing 5 of the first spur gear 3, so that an axial movement is possible. In order to clarify the functioning, at this point a

Straight toothing shown. In a helical gearing, the assembly of the Pressure comb 7 accordingly by an axial and rotational movement, ie by a screwing movement. The pressure comb 7 has on both sides of running surfaces or raceways 8, 9 to the spur gears 3, 4. Thus, the rotation remains effective even with Axialkraftrichtungsumkehr.

FIG. 4 shows a first embodiment of an anti-twist device on the basis of FIG

Gear arrangement shown as an example. As a blocking element of the rotation of a arranged in a radial bore 16 of the first spur gear 3 sleeve 17 is provided, which is movable via a spring element 18 as a lock radially outward into the locking position of the pressure comb 7. In the blocking position remains a predetermined radial distance 19 between the pressure comb 7 facing the end of the locking element and the sleeve 17 and the root circle of the internal teeth 10 of the pressure comb 7. In this embodiment, the sleeve 17 for mounting the pressure comb 7 as a locking element against the spring element 18 pressed as a lock radially inward. When rotating the pressure comb 7 in the direction of installation position, the spring element 18 relaxes and brings the sleeve 17 radially outward into its blocking operative position. The radial bore 16 for receiving the anti-rotation is designed as a blind bore and extends from a radially inner region to a radially outer region of the first spur gear 3 perpendicular to a rotational or longitudinal axis of the first spur gear 3. For disassembly of the pressure comb 7, it is necessary to press the sleeve 17 against the spring force radially inward. This is favored by the radial distance 19, since here with a

Auxiliary tool can be attacked.

In contrast to FIG. 3, FIG. 5 shows a further embodiment of the pressure comb 7 by means of laterally provided shoulders on the top circle of the associated first

Spur wheel 3 centered. This feature reduces the load on the pressure comb 7 and allows higher axial forces, but requires more axial space. It is possible to make the centering on one side. This solution may be in the presence of a

Preferred torque direction allow a cheaper size.

FIG. 6 shows a second embodiment of the anti-twist device. At this

The first spur gear 3 has a radial through hole 20 for receiving a pin 21 as a blocking element whose length is dimensioned such that the pin 21 after mounting the spur gear 3 on a shaft is provided as a lock in the locked position. For this purpose, the pin 21 is moved by the shaft from a radially inner region to a radially outer region of the first spur gear 3 in the blocking position. At the second Embodiment, the pin 21 is inserted from radially inward into the first spur gear 3. After the first spur gear 3 is mounted on the shaft, the pin 21 is positively secured by the shaft against falling inwards. The pin 21 can also be secured otherwise force, form or cohesive. The through-bore 20 for receiving the anti-rotation device extends perpendicularly from a radially inner region to a radially outer region through the first spur gear 3 relative to a rotational or longitudinal axis of the first spur gear 3

In Figures 7 and 8, a third embodiment of the rotation is shown, in which again a through hole 20 is provided for receiving a pin 21 as a blocking element. However, the positive locking takes place radially inward in contrast to the second embodiment by a bearing 22. The pin 21 is moved from radially inward to radially outward into its locking position after the pressure comb 7 has reached its final angular position. After mounting the bearing 22 of the pin 21 A is secured or locked. The locking takes place via the bearing 22nd

FIGS. 9 and 10 show a fourth embodiment of the anti-rotation device, in which, as a blocking element, a radial bore 16 or through-bore 20 is again shown

provided pin 21 is used, which has, for example, a snap ring 23 as a detent. This embodiment is particularly useful if a fuse according to Figures 6 or 7 and 8 is not possible because a rotating shaft or other component runs inside and the wall thickness of the first spur gear 3 is not sufficient to realize a spring solution. The radial bore 16 and the radial through hole 20 has radially outside a larger diameter than radially inward, for example by a groove or step.

As a result, the snap ring 23 can secure the pin 21 against falling out radially inwards with its expanding action.

In Figure 1 1, a fifth embodiment of the rotation is shown in the as

Blocking a provided in a through hole 20 A pin 21 A is provided, wherein the through hole 20 A is associated with an opposite recess 24 for receiving a spring element 18 A as a detent, which biases the pin 21 A in the locked position. This embodiment is particularly suitable when a toothing sits directly on a shaft with a relatively small diameter and in the interior of the shaft is a bore, for example for guiding oil. The basic idea corresponds to the first version. The difference is that the

Spring element 18A on the opposite side directly or as shown in a recess 24 is supported. FIG. 12 shows, by way of example, a sixth embodiment of the anti-rotation device, in which the radial bore 16 or through-bore 20, 20 A is arranged at a predetermined angle at an angle from a radially inner region to a radially outer region in the first spur gear 3. This embodiment is particularly useful when a spring solution, for example, due to insufficient radial space excretes and a

Snap ring solution is not permitted, as there must be no through hole 20, 20 A inside. This is the case, for example, if an oil pressure is present in the interior or, as shown, a rolling bearing raceway is provided. Notwithstanding the previous solutions, the rotation is mounted from obliquely inward to radially outward. Regardless, in this embodiment, the rotation is carried out as a grub screw 25. Also another of the versions shown so far can be used here. Likewise, designed as a screw rotation can be used even with pure radial mounting.

Bezuaszeichen gearing arrangement

transmission

first spur gear or gear

second spur gear or gear

Gearing of the first spur gear

Toothing of the second spur gear

thrust collar

career

internal gearing

Groove of the first spur gear

centering

Tip diameter of the internal teeth Contact surfaces of the second spur gear

Recess of the second spur gear

radial bore

shell

, 18AFederelement

radial distance

, 20A radial through hole

, 21 AStift

warehouse

snap ring

deepening

grub screw

Claims

claims

1. gearing arrangement (1) comprising at least a first helical gear

Spur gear (3), a second helical gear (4), which a common

Forming running toothing, and at least one pressure comb (7) with two raceways (8, 9) for bilateral Axialkraftausgleich in the region of the running toothing, wherein the annular pressure comb (7) with an internal toothing (10) is executed in the assembled state in one of the teeth (5) of the first spur gear (3) interrupting circumferential groove (11) is supported, and wherein the pressure comb (7) is associated with at least one rotation, characterized in that the rotation is carried out such that the rotation of a radially inner region a radially outer portion of the first spur gear (3) is movable in a locking position.

2. gearing arrangement (1) according to claim 1, characterized in that the

Anti-rotation in the locked position of the groove bottom of the groove (1 1) of the first

Spur gear (3) radially outwardly into the internal toothing (10) of the pressure comb (7) engages locking.

3. gearing arrangement (1) according to claim 1 or 2, characterized in that the anti-rotation comprises at least one locking element and at least one detent for holding the locking element in the locking position.

4. gearing arrangement (1) according to one of the preceding claims, characterized in that for receiving the rotation at least one

Radial bore (16) or at least one through hole (20, 20A) relative to the longitudinal axis of the first spur gear (3) is arranged perpendicular or at a predetermined angle obliquely from the radially inner region to the radially outer region in the first spur gear (3).

5. gearing arrangement (1) according to claim 4, characterized in that as

Blocking element in the radial bore (16) of the first spur gear (3) arranged sleeve (17) or in the radial bore (16) of the first spur gear (3) arranged pin (21) is provided, which or via a spring element (18) can be moved as a lock radially outward in the locked position.

6. tooth arrangement (1) according to claim 4 or 5, characterized in that the first spur gear (3) has a shaft or bearing receptacle, wherein the first spur gear (3) the radial through hole (20) for receiving a pin (21) as a blocking element whose length is dimensioned such that the pin (21) after the assembly of the first spur gear (3) on a shaft or on a bearing (22) by positive locking is provided with the shaft or the bearing as a lock in the locked position.

7. tooth arrangement (1) according to one of claims 4 to 6, characterized in that as a blocking element in the radial bore (16) or the through hole (20 A) provided pin (21 A) is provided which has a snap ring (23) as a locking ,

8. gear arrangement (1) according to one of claims 4 to 7, characterized in that as a blocking element in the through hole (20 A) provided pin (21 A) is provided, wherein the through hole (20 A) an opposite recess (24) for receiving a spring element (18A) is associated as a detent, which biases the pin (21A) in the locking position.

9. gearing arrangement (1) according to one of claims 3 to 8, characterized in that in the blocking position of the locking element, a predetermined radial distance (19) between the pressure comb (7) facing the end of the locking element and the root circle of the internal toothing (10) Pressure comb (7) is provided.

10. gearing arrangement (1) according to one of the preceding claims, characterized in that a plurality of distributed over the circumference of the pressure comb (7) arranged anti-rotation devices are provided.

11. Transmission (2) of a vehicle with at least one toothing arrangement (1) according to one of the preceding claims.