阅读说明：本技术 轧机技术中的切换变速器 (Shifting transmission in rolling mill technology ) 是由 M·克鲁格 F·莫勒林格 N·卡蒂克 于 2018-06-13 设计创作，主要内容包括：一种具有至少两个切换级的切换变速器(1)、优选使用在轧机技术中的切换变速器(1),其具有：可旋转地支承的驱动轴(20),输入扭矩可施加到该驱动轴上；可旋转地支承的第一从动轴(30)和可旋转地支承的第二从动轴(40),两个从动轴并行地布置并且通过从动变速器级彼此连接,从而这两个从动轴在切换变速器(1)的每个切换级中在施加到驱动轴(20)上的输入扭矩作用下反向地、优选以相同的转速旋转；第一联轴器(50),设置第一联轴器以便使驱动轴(20)和第一从动轴(30)以可切换的方式彼此连接和分离,其中,在第一联轴器(50)的接合状态中实现切换变速器(1)的第一切换级,在第一切换级中,驱动轴(20)和第一从动轴(30)彼此连接,从而使得驱动轴(20)的输入扭矩在没有增速比或降速比的情况下、优选在没有偏转以及未设置圆柱齿轮级的情况下传递到第一从动轴(30)上。(A change-over gearbox (1) having at least two switching steps, preferably a change-over gearbox (1) used in rolling mill technology, having a rotatably mounted drive shaft (20) to which an input torque can be applied, a rotatably mounted th driven shaft (30) and a rotatably mounted second driven shaft (40), which are arranged in parallel and are connected to one another by means of the driven gearbox steps, so that the two driven shafts rotate in opposite directions, preferably at the same rotational speed, under the action of the input torque applied to the drive shaft (20) in each switching step of the change-over gearbox (1), a th coupling (50) is provided, which is a th coupling, in order to connect and disconnect the drive shaft (20) and the th driven shaft (30) to one another in a switchable manner, wherein in the engaged state of the th coupling (50) a th switching step of the change-over gearbox (1) is effected, and in the th switching step the drive shaft (20) and the ) are connected to one another, so that the input torque of the drive shaft (20) is transmitted without a step increase or decrease in the gear ratio, preferably without a gear ratio, and without a cylindrical step being provided.)

A shift transmission (1) having at least two shift steps, preferably for use in rolling mill technology, of the kind , having:

a rotatably mounted drive shaft (20) to which an input torque can be applied;

a rotatably mounted th output shaft (30) and a rotatably mounted second output shaft (40), which are arranged in parallel and are connected to one another by means of a driven transmission stage, so that they rotate in each shift stage of the shift transmission (1) in opposite directions, preferably at the same rotational speed, under the effect of an input torque applied to the drive shaft (20);

a shaft coupling (50) arranged to connect and disconnect the drive shaft (20) and the driven shaft (30) to and from each other in a switchable manner, wherein,

in the engaged state of the -th coupling (50), a shift stage of the manual transmission (1) is realized, in which shift stage the drive shaft (20) and the output shaft (30) are connected to one another, so that the input torque of the drive shaft (20) is transmitted to the output shaft (30) without a step-up or step-down ratio, preferably without a step-up and without a spur gear stage.

2. The switching transmission (1) according to claim 1, wherein said drive shaft (20) and said th driven shaft (30) are axially supported in sequence along the same axis of rotation.

3. The switching transmission (1) according to claim 1 or 2, characterized in that the driven transmission stage has a comb roller (31) fixedly connected to the th driven shaft (30) and a second comb roller (41) fixedly connected to the second driven shaft (40) and in toothed engagement with the th comb roller (31), wherein the comb roller (31) and the second comb roller (41) preferably have the same diameter.

4. The switching transmission (1) according to any of the preceding claims, wherein the coupling (50) is a form-fitting coupling, the coupling preferably having a th switching sleeve (51) arranged concentrically with respect to the th driven shaft (30), the th switching sleeve being axially movable for switching the coupling (50).

5. The switching transmission (1) according to any of the preceding claims, characterized in that it has a driving transmission stage which in a second switching stage achieves a step-up or step-down ratio between the drive shaft (20) and the second output shaft (40).

6. Switching transmission (1) according to claim 5, characterized in that the drive transmission stage has -th spur gear (21) fixedly connected to the drive shaft (20) and a second spur gear (42) which is in toothed engagement with the -th spur gear (21) and can thus be connected to the second output shaft (40), so that in the second switching stage an input torque is converted by the drive shaft (20) via the two spur gears (21, 42) and is transmitted to the second output shaft (40), wherein the -th spur gear (21) preferably has a smaller diameter than the second spur gear (42).

7. The switching transmission (1) according to claim 5 or 6, characterised in that the drive transmission stage has a second coupling (60) which is provided in order to switchably connect and disconnect the drive shaft (20) and the second output shaft (40), preferably the second spur gear (42) and the second output shaft (40), to one another, wherein a second switching stage of the switching transmission (1) is realized in the engaged state of the second coupling (60).

8. Switching transmission (1) according to claim 7, characterized in that the second coupling (60) is a form-fitting coupling, preferably having a second switching sleeve (61) arranged concentrically with the second driven shaft (40), which is axially movable to switch the second coupling (60).

9. Switching transmission (1) according to claim 7 or 8, characterized in that the th coupling (50) and the second coupling (60) are coupled to each other so that they are always switched jointly and oppositely, preferably the th coupling (50) and the second coupling (60) are mechanically coupled to each other.

Rolling mill for rolling metal strips with a switching gearbox (1) according to any of the previous claims, wherein the driven shaft (30) and the second driven shaft (40) are connected with work rolls, intermediate rolls or back-up rolls, respectively.

Technical Field

The invention relates to an shift transmission, in particular a spur-gear comb-roller shift transmission, having at least two shift stages, with a rotatably mounted drive shaft and a rotatably mounted th driven shaft and a rotatably mounted second driven shaft, which are arranged in parallel and are connected to one another by means of a driven transmission stage, such that the driven shafts rotate in opposite directions in each shift stage of the shift transmission under the effect of an input torque applied to the drive shaft.

Background

In the rolling mill art, transmissions with spur gear shift stages and combing roller stages are used in the machine frame main drive. The spur gear switching stage serves to vary the output rotational speed (or output torque) relative to the drive rotational speed (or drive torque). The upper and lower rolls connected to the combing roller stage are driven in opposite directions by the combing roller stage, for example, at the same rotational speed.

Document DE 4219399 a1 describes, for example, roll drives for mechanical rolls, which have a shift transmission between a drive shaft and a pressure roll to be driven.

In particular in fast-running rolling plants, such an excitation from the drive train can excite the natural vibration forms of the rolling stands or roll stacks (for example, vibrations according to the so-called "fifth-order frequency"), which can significantly impair the product quality, in order to avoid critical vibration excitations, it is often necessary to limit the production speed, in particular the teeth of the step-up or step-down gear step participate in such an excitation proportional to the rotational speed, because they have a higher torque load than the comb roller step.

Disclosure of Invention

The object of the present invention is to provide shifting gears, in particular for use in rolling mill technology, which have improved vibration behavior and thus preferably enable a reduction in productivity losses and mass losses.

This object is achieved by a shift transmission having the features of claim 1. Advantageous developments emerge from the dependent claims of the invention, the following figures and the description of preferred embodiments.

A shift transmission having at least two shift stages is particularly suitable for use in rolling mill technology, preferably as part of a main drive for rolling rolls, for example drive rolls, intermediate rolls and/or support rolls, which are used in cold rolling of strip-shaped products, for example cold rolling of metal strips made of steel or nonferrous metals, so-called NE metals.

The change-over gearbox has a rotatably mounted drive shaft to which an input torque can be applied, which can be driven, i.e. rotated, for example by an electric motor, and a rotatably mounted second driven shaft, which are arranged in parallel in the axial direction thereof and are connected to one another via a driven gearbox stage, so that they rotate in each of the shift stages of the change-over gearbox in the opposite direction, preferably at the same rotational speed, with the input torque applied to the drive shaft, the change-over gearbox furthermore has a -th coupling, the -th coupling being set such that the drive shaft and the -th driven shaft are connected or disconnected from one another in a switchable manner, wherein in the engaged state of the coupling the -th shift stage of the change-over gearbox is realized, in the -th shift stage the drive shaft and the -th driven shaft are connected to one another, so that the input torque is transmitted to the -th driven shaft without a step-up or step-down ratio, in other words, in the engaged state of the , the input torque is transmitted directly from the drive shaft -up shaft to the second driven shaft -th coupling for the purpose of the drive shaft and is preferably connected to the drive shaft in a non-driven shaft -driven shaft for the purpose.

Before setting forth the technical effects of shifting the transmission, it should be noted that the terms "" and "second" are used merely for language differentiation of the relevant components, and thus are to be understood as part of the term , but not referring to order, dependency, or the like.

By implementing the shift stage of the shift transmission in the engaged state of the th coupling, the vibrational excitation of the shift transmission by possible transmission gearing is eliminated, since the driveshaft and the th driven shaft are connected to one another without gearing by the th coupling, whereby in the th shift stage of the shift transmission, the speed ratio stage with gearing is omitted, whereby a more favorable dynamic behavior of the drive train in the th shift stage is obtained, since inertial masses, such as spur gears like conventional shift stages, are omitted.

In this case, the drive shaft and the th driven shaft are separate components, which are however technically connected, so that the drive shaft and the driven shaft act as a single shaft.

Preferably, the driven transmission stage has a th comb roller which is fixedly connected to the th driven shaft and a second comb roller which is fixedly connected to the second driven shaft and meshes with the th comb roller teeth, wherein the th comb roller and the second comb roller have the same diameter.

Preferably, the th coupling is a form-fitting coupling, according to special embodiments, the coupling has a th shift sleeve arranged concentrically with respect to the driven shaft, the th shift sleeve being axially displaceable for shifting the th coupling, in this way the engagement and disengagement of the drive shaft and the driven shaft is achieved in a technically simple and reliable manner by axially displacing, that is to say pressing in or pressing out, the th shift sleeve for actuating the th coupling.

Preferably, the th switching stage, which has a gear ratio of approximately or equal to , is used for high rolling speeds, where the problem of vibration excitation is particularly important.

Preferably, the drive transmission stage has a spur gear fixedly connected to the drive shaft and a second spur gear which meshes with a spur gear tooth and can thus be connected to a second output shaft, so that in a second shift stage the input torque is transferred from the drive shaft via the two spur gears and to the second output shaft, wherein, for the reasons mentioned above, the diameter of the spur gear is preferably smaller than the diameter of the second spur gear.

The second spur gear pair is omitted by the rigid coupling between the drive input shaft and the output shaft in the -th shift stage, as a result of which a particularly suitable dynamic behavior of the drive train is achieved due to the reduced moment of inertia.

In this way, the engagement and disengagement of the drive shaft, specifically of the second spur gear, with the second output shaft is achieved in a technically simple and reliable manner by axially displacing, that is to say pressing in or pressing out, the second shift sleeve for actuating the second coupling.

According to particularly preferred embodiments, the and second couplings are mechanically coupled to each other, for example by a lever mechanism.

The described shift transmission is primarily designed for use in rolling mill technology, in particular for cold rolling of metal strips, wherein vibrations caused by the drive of the rolls can significantly impair the product quality. Of course, the shift transmission can be applied in other fields as well.

Drawings

The features described herein can be implemented individually or in combinations of or more of the above features, provided that the features are not mutually inconsistent.

FIG. 1 schematically illustrates the spur gear comb transmission in the shift stage state;

fig. 2 schematically shows the spur gear comb transmission in the state of the second shift stage.

Preferred embodiments are described below with reference to the accompanying drawings. Here, the same, similar or functionally same elements are provided with the same reference numerals, and overlapping description of these elements is partially omitted to avoid redundancy.

Detailed Description

Fig. 1 and 2 show a shift transmission 1, which is designed as a spur gear comb transmission, for example, in two different shift states.

The shift transmission 1 has a housing 10 in which a drive shaft 20, an th output shaft 30 and a second output shaft 40 are rotatably mounted, in fig. 1 and 2, a rotary bearing is shown, but no reference numerals are provided for the sake of clarity, in this embodiment, the drive shaft 20, the th output shaft 30 and the second output shaft 40 are arranged in parallel, wherein the drive shaft 20 and the th output shaft 30 are arranged axially one behind the other and can be rigidly connected to and disconnected from one another by a coupling 50, the drive shaft 20 can be rotated, for example, by an electric motor, which is not shown, in the shift transmission 1, the torque of the drive shaft 20 is converted (as described in detail below) if necessary and transmitted to the two output shafts 30 and 40.

In the engaged state of the coupling 50, the drive shaft 20 and the driven shaft 30 are rigidly connected to one another without toothing, preferably the th coupling 50 achieves a positive-locking connection of the two shafts, in the present exemplary embodiment, a cylindrical th shifting sleeve 51 is provided for this purpose, which is arranged concentrically with respect to the drive shaft 20 and the th driven shaft 30 and is movable in the axial direction, in the engaged state, the th shifting sleeve 51 is simultaneously engaged with the drive shaft 20 and the 4 driven shaft 30, whereby the two shafts 20 and 30 are positively connected, this engagement can be carried out directly, or, as in the illustrated exemplary embodiment, by an axial movement of the coupling partners 52 and 53, which are fixedly connected to the drive shaft 20 and the th driven shaft 30, respectively, the th shifting sleeve 51 is pushed, by an axial movement of the shifting sleeve 51, at least 84 of the two shafts 20 and 30 are engaged with the shifting sleeve, whereby the th coupling 50 is disengaged and the two shafts 20 and 30 are separated from one another, whereby the shafts 20 and the 854 th shifting sleeve 30 are connected to one another pneumatically, which can be rotationally connected to the other ways of the pneumatic coupling sleeve 8925, which can be carried out.

Fig. 1 shows a state in which the th coupling 50 is actuated, so that the drive shaft 20 and the th driven shaft 30 are rigidly connected to each other, whereby the input torque of the drive shaft 20 is transmitted to the th driven shaft 30 in a ratio .

The th comb roller 31 is fixedly connected to the th driven shaft 30, for example, configured as with the driven shaft, the th comb roller 31 is in toothed engagement with the second comb roller 41, which in turn is fixedly connected to the second driven shaft 40, for example, configured as with the second driven shaft, the two comb rollers 31 and 41 preferably have the same diameter, so that the two driven shafts 30 and 40 are driven in opposite directions at the same rotational speed when an input torque is applied, in the present embodiment, the two comb rollers 31 and 41 form the driven transmission stage described above.

In the engaged state ( th switching step) shown in fig. 1, a torque transmission takes place as indicated by the arrows in the drawing, i.e. the input torque is transmitted directly and without rotation by the rigid connection of the drive shaft 20 and the th output shaft 30 to the th comb roller 31, which in turn drives the second comb roller 41 and thus the second output shaft 40 in the opposite direction.

In the state shown in fig. 2, the drive shaft 20 and the -th output shaft 30 are disengaged, i.e. the -th coupling 50 is pressed open, the -th spur gear 21, which is fixedly connected to the drive shaft 20 and is embodied, for example, as , is in toothed engagement with the second spur gear 42, the second spur gear 42 can be connected to the second output shaft 40, so that the second output shaft 40 can be driven by the rotation of the second spur gear 42, a bearing 43 is provided between the second spur gear 42 and the second output shaft 40, which bearing is designed such that, in the -th switching stage of fig. 1, i.e. during the force transmission from the -th comb roller 31 to the second comb roller 41, the second spur gear 42 rotates torque-free.

The second coupling 60 acts between the second spur gear 42 and the second output shaft 40, which is likewise switchable in the second coupling 50 by means of an axially movable, cylindrical second switching sleeve 61, in the engaged state of the second coupling 60 the second output shaft 40 and the second spur gear 42 are rigidly connected to one another, preferably the second coupling 60 also achieves a form-fitting connection, in the present embodiment a cylindrical second switching sleeve 61 is furthermore provided, which is arranged concentrically and movable in the axial direction relative to the second output shaft 40, in the engaged state the second switching sleeve 61 simultaneously engages with the second output shaft 40 and the second spur gear 42, whereby the two elements are form-fittingly connected, can be directly engaged, or, as in the illustrated embodiment, can be pushed by a second coupling fitting 62 and 63 fixedly connected with the second spur gear 42 and the second output shaft 40, respectively, pushing out the switching sleeve 61, thereby disengaging the second coupling 60 and the second output shaft 40, in other, pneumatically switchable coupling technologies, such as the second coupling 3560, the second coupling 60, is also rotationally switchable, as indicated, by axial pressing out of the switching sleeve 61, thereby enabling the second coupling 60 to be rotationally switchable, in other, electrically operated, and/or rotationally switchable, as in other ways.

In the engaged state (second switching stage) shown in fig. 2, a torque transmission takes place, as indicated by the arrow in the figure, i.e. the input torque of the drive shaft 20 is transmitted from the -th spur gear 21 to the second spur gear 42, the -th spur gear 21 is preferably smaller than the second spur gear 42, in order to achieve a reduction ratio in this second switching stage, at the same time the second coupling 60 is actuated, so that torque is transmitted from the second spur gear 42 to the second output shaft 40, which in turn transmits torque to the -th output shaft 30 via the two comb rollers 41 and 31, said -th output shaft being mechanically decoupled from the drive shaft 20 by the non-switched -th coupling 50.

According to the above-described configuration, the th shift stage shown in fig. 1 achieves a fixed transmission ratio (no step-up or step-down ratio) of between the transmission drive and the transmission driven devices, a tooth is omitted in the th shift stage, and a technical contribution can be achieved by the th coupling 50, in the th shift stage, the switchable coupling 50 connects the drive shaft 20 and the driven shaft 30 in a rigid manner without a tooth, if the second shift stage shown in fig. 2 is switched with a step-up or step-down ratio of not , the drive shaft 20 and the th shaft 30 are disconnected, so that the step-up ratio then passes through the spur gears 21 and 42 and the teethThe portions are engaged. For this purpose, the two couplings 50 and 60 are synchronously switched in opposite directions

Preferably, the two couplings 50 and 60 are mechanically coupled.

The shift transmission 1 is preferably designed for so-called main frame drives, therefore, the th shift stage with a transmission ratio of about or equal to is used for high rolling speeds, where the problem of vibration excitation is particularly important, conversely, it is preferred to implement low rolling speeds in the second shift stage at a speed reduction ratio, for which the plant as a whole is less sensitive to vibrations.

The proposed shift transmission 1, which is preferably designed as a spur-gear-comb transmission, achieves a significant reduction in the excitation of vibrations of the rolling stand in the drive train by eliminating the spur gear stage in the -shift stage, thereby, in addition, a more favorable dynamic behavior of the drive train in the -shift stage is achieved, since inertial masses, such as the spur gears of the entire shift stage, are eliminated, the mechanical coupling of the two coupling members 50 and 60, which are operated synchronously during the shift, serves for the safety of the system of the shift transmission itself, and, furthermore, by eliminating the spur gear stage, the spur gear stage of the shift transmission 1 is inexpensive, compact and low in maintenance.

List of reference numerals:

1-shift transmission

10 casing

20 drive shaft

21 st cylindrical gear

30 th th driven shaft

31 st comb roller

40 second driven shaft

41 second comb roller

42 second cylindrical gear

43 support part

50 th shaft coupling

51 st th switching sleeve

52. 53 st coupling fitting

60 second coupling

61 second switching sleeve

62. 63 second coupling fitting