Stacked transmission
阅读说明:本技术 叠加式变速器 (Stacked transmission ) 是由 M.佩希 于 2020-02-25 设计创作,主要内容包括:本发明涉及一种用于特别是移动的破碎装置的叠加式变速器,带有:机械的功率分支,所述机械的功率分支带有能与驱动机联接的变速器输入端、能与破碎装置联接的变速器输出端和第一行星齿轮传动级,变速器输入端通过所述第一行星齿轮传动级与变速器输出端处于传动的转动连接或至少能带到这种传动的转动连接;和静液压的功率分支,带有至少一个第一液压机,所述第一液压机的第一驱动轴与第一行星齿轮传动级的第一空心轮处于间接或直接的嵌接。(The invention relates to a superimposed gearbox for a, in particular, mobile, crushing plant, having: a mechanical power branch having a transmission input which can be coupled to the drive machine, a transmission output which can be coupled to the breaking device, and a first planetary gear stage, via which the transmission input is in driving rotational connection with the transmission output or at least can be brought into such driving rotational connection; and a hydrostatic power branch having at least one first hydraulic machine, the first drive shaft of which is in indirect or direct engagement with the first ring gear of the first planetary gear train stage.)
1. A superimposed gearbox for a, in particular, mobile crushing plant (1), with: a mechanical power branch having a transmission input (8) which can be coupled to the drive machine (19), a transmission output (10) which can be coupled to the breaking device, and a first planetary gear stage (20) by means of which the transmission input (8) is in driving rotational connection or at least can be brought into driving rotational connection with the transmission output (10); and a hydrostatic power branch (2) having at least one first hydraulic machine (14, 16), the first drive shaft (42) of which is in indirect or direct engagement with the first ring gear (26) of the first planetary gear train stage (20), characterized in that the rotational axis (41) of the first drive shaft (42) is arranged within the diameter (D) of the first ring gear (26).
2. The superposition transmission according to claim 1, comprising a plurality of, in particular two, such first hydraulic machines (14, 16), the first drive shaft (42) of which is in indirect or direct engagement with the first ring gear (26).
3. The superposition transmission according to claim 2, wherein the rotational axes (41) and/or the engagement means are arranged uniformly distributed along the circumference of the first ring gear (26).
4. The superposition transmission according to one of the preceding claims, wherein the at least one first drive shaft (42) is in indirect or direct engagement with the first ring gear (26) on the inner circumference thereof.
5. The superimposed transmission according to any one of the preceding claims, wherein the engagement means are formed by external toothing on the drive shaft side and internal toothing of the first ring gear (26).
6. The superposition transmission according to any of the preceding claims, with a second hydraulic machine (18, 18') that can be fluidically connected in a hydraulic circuit with or to said at least one first hydraulic machine (14, 16).
7. The superposition transmission according to claim 6, wherein a second drive shaft (46) of the second hydraulic machine (18) is in rotational connection or at least can be brought into rotational connection with the transmission input (8), wherein a rotational axis (45) of the second drive shaft (46) is spaced apart from the rotational axis (3) of the transmission input (8) and is arranged within the diameter (D) of the first ring gear (26).
8. The superposition transmission according to claim 7, wherein the second drive shaft (46) is in indirect or direct engagement with the transmission input (8).
9. The superposition transmission according to any of the preceding claims, wherein at least one of said hydraulic machines (16, 18') has an adjustable displacement volume.
10. A superposition transmission according to any of the preceding claims, wherein at least one of said hydraulic machines (18) has a reversible displacement volume and/or wherein a 2-way valve (21) is provided for reversing the flow direction.
Technical Field
The invention relates to a superposition transmission according to the preamble of
Background
In particular mobile crushers, a large amount of recyclate or a large amount of compost to be crushed is continuously fed to the machine space and "crushed" by the crushing rollers. The rollers are driven, for example, by a diesel motor via a multi-stage planetary gear train. The latter reduces the rotational speed of the diesel motor and amplifies the torque. The planetary gear set has a constant transmission ratio. Thus in a constantly rotating firewood motor, the shredder rollers move at the same speed and direction of rotation.
The disadvantage here is that, for example, when the article is jammed, an overload of the diesel motor occurs or mechanically expensive clutches and transmission stages are provided for the change in direction of rotation required to eliminate the jam.
In order to be able to flexibly adapt the rotational speed to the requirements of the material to be comminuted, document DE 202011103675U 1 proposes the use of a planetary gear, which has the possibility of a continuously variable transmission. The stepless transmission is realized by an additional hydrostatic power branch. The ring gear of the first planetary gear train stage is driven via an external toothing by a hydrostatic power-branched hydraulic motor. The hydraulic motor is supplied with pressure medium by a hydraulic pump, which is driven by a diesel motor.
Although the disadvantages can be countered by a continuously variable transmission, the entire transmission is of radially large design. The installation space required for the gear mechanism is thus large in the radial direction.
A specific technical practice of this solution is indicated by the mobile crusher INVENTHOR TYPE 9 of doprostat (Doppstadt). In this case, it is also disadvantageous that, in order to drive the hydraulic pump by the diesel motor, an additional distributor gear is provided in the axial direction, which requires additional installation space and maintenance expenditure.
Disclosure of Invention
In contrast, the object of the present invention is to create a superposition transmission, in particular for a crushing plant, which requires a smaller overall installation space while flexibility and durability remain unchanged.
This object is achieved by a superposition transmission having the features of
A superposition transmission for a, in particular, mobile crushing plant, has a mechanical power branch with a transmission input, in particular a transmission input shaft, which can be coupled to a drive machine. The superposition transmission also has a transmission output, in particular a transmission output shaft, which can be coupled to the breaking device. Both, i.e. the input and the output, are in driving rotational connection or can be brought into rotational connection at least via the first planetary gear stage. The additional planetary gear stage can intensify the transmission, in particular the reduction. The superposition transmission also has a hydrostatic power branch with at least one first hydraulic machine, which is designed in particular as a hydraulic motor, the first drive shaft of which is in indirect or direct engagement with the first ring gear of the first planetary gear train stage. According to the invention, the axis of rotation of the first drive shaft is arranged within the diameter of the first ring gear. This is achieved in particular by the arrangement of the first hydraulic machine radially opposite the first ring gear.
The installation space requirement according to the invention in this direction is reduced compared to the solutions according to the prior art (in which the external toothing of the ring gear engages or meshes with the external toothing of the pinion of the first drive shaft of the first hydraulic machine via a further externally toothed intermediate wheel and thus leads to a large installation space requirement in the radial direction).
In a further embodiment, the housing of the first hydraulic machine is arranged at least partially within the diameter of the first ring gear. The gain in structural space in the radial direction is thus still greater compared to conventional solutions in which the first hydraulic machine is laterally extended radially outwards.
In a preferred embodiment, a plurality of, in particular two or three, such first hydraulic machines are provided, the first drive shaft of which is indirectly or directly engaged with the first ring gear of the first planetary gear train stage. In this way, the first ring gear can be loaded symmetrically with respect to the transverse forces caused by the engagement, which results in a simplified, less expensive and more cost-effective mounting of the first ring gear.
All the rotational axes of the first drive shaft of the first hydraulic machine are preferably arranged within the diameter of the first ring gear, whereby the already mentioned advantage of reduced radial installation space is achieved overall.
In a preferred embodiment, the rotational axis or the engagement structure is arranged uniformly distributed along the circumference of the first ring gear. In particular, in the two first hydraulic machines, they are arranged opposite one another and in the three first hydraulic machines, they are arranged at a circumferential angle of, in particular, 120 °. This results in a particularly uniform and, if appropriate, symmetrical transverse force loading of the first ring gear, with the already mentioned advantages of simplified support.
In a preferred embodiment, at least one first drive shaft or a plurality of first drive shafts are in indirect or direct engagement with the first ring gear on the inner circumference of the first ring gear.
In a preferred embodiment, at least one or more engagement means are formed by a drive-shaft-side external toothing of a pinion, which is connected in each case in a rotationally fixed manner to the drive shaft, and an internal toothing of the first ring gear.
In a preferred embodiment, the second hydraulic machine, in particular the hydraulic pump, can be fluidically connected to or with at least one first hydraulic machine, in particular with all first hydraulic machines, in a, in particular closed, hydraulic circuit of the superimposed transmission.
In a further embodiment, a third hydraulic machine, preferably a hydraulic pump, is provided, in particular in the open hydraulic circuit, for supplying pressure medium to the other hydraulic devices.
The third drive shaft of the third hydraulic machine is in particular connected coaxially with the second drive shaft of the second hydraulic machine, provided that the third hydraulic machine has a through drive (durchrieb). As an alternative to the through drive, the third hydraulic machine is coupled/fixed to the superposition drive as described for the second hydraulic machine and also described below.
The second and third drive shafts are preferably arranged offset by 180 °, in particular opposite, with respect to the longitudinal axis of the superposition transmission. They are each connected to a pinion with straight toothing, wherein the pinion engages in the same spur gear of the transmission input shaft.
In a preferred embodiment, the second drive shaft of the second hydraulic machine is in a rotary connection or at least can be brought into a rotary connection with the transmission input. In this way, the second hydraulic machine and the mechanical power branch, in particular the first planetary gear stage, can be driven by the same drive machine.
In one variant, the second drive shaft engages indirectly with the transmission input. A technically simple solution to this is to provide the second drive shaft and the transmission input shaft with pinions, in particular with straight toothing, which engage in one another. In a technically expensive solution, the second drive shaft engages with the transmission input shaft via the pump distributor gear.
In a preferred embodiment, the axis of rotation of the second hydrostatic machine is spaced apart from, in particular parallel to, the axis of rotation of the transmission input and is arranged within the diameter of the first ring gear.
In a preferred embodiment, the second hydraulic press is designed with an adjustable displacement volume. The design of a swash plate axial piston machine with a pivotable swash plate is particularly suitable. Other configurations than this may be selected.
In a preferred embodiment, at least one of the hydraulic machines has an adjustable displacement volume. In this way, the rotational speed and/or the torque transmitted by the one or more first hydraulic machines to the first hollow wheel can be flexibly changed.
In a preferred embodiment, at least one of the hydraulic machines, in particular the second hydraulic machine, is adjustable and reversible with respect to its displacement volume, so that by adjusting the associated displacement volume beyond a zero value, while the direction of rotation of the transmission input and thus in particular of the drive machine remains unchanged, a reversal of the flow in the hydraulic circuit and thus of the direction of rotation of the first drive shaft or of the first drive shafts can be brought about. In this way, the rollers of the crushing device can be rotated in opposite directions and released from jamming or entanglement without complex switching and clutching devices. For this purpose, a second hydraulic press which is designed reversibly, in particular when a plurality of first hydraulic presses engage on the first ring gear, is particularly suitable.
Alternatively or in addition to this, the flow reversal can be achieved in that a switching valve, in particular an 4/2 switching valve, is provided to control the closed hydraulic circuit. The hydraulic machine, in particular the second hydraulic machine, can then even be designed with a constant displacement volume and a constant direction of rotation, and the reversal of the flow of the wiring by switching of the pressure connections can be effected via the reversing valve while the direction of rotation of the second hydraulic machine remains unchanged.
In a further embodiment with a plurality of first hydraulic machines, the displacement volume of the first hydraulic machine is constant. The constant machine advantageously has a high efficiency.
This embodiment is simple and efficient in terms of installation technology, but is also less flexible in terms of rotational speed and torque, given that the rotational speed of the drive machine and thus also of the second hydraulic machine remains constant.
Thus, alternatively or additionally, at least one of the first hydraulic machines or the at least one first hydraulic machine may thus have an adjustable displacement volume, for example.
In a preferred embodiment, the first hydraulic machine has at least one similar maximum displacement volume, in particular the same maximum displacement volume, regardless of whether it is adjustable or constant.
Instead of having only one large hydraulic machine with a plurality of small first hydraulic machines, this results in a higher efficiency and can continue to ensure operation in the event of a failure of one of the first hydraulic machines on the basis of redundancy.
In a preferred embodiment, the superposition transmission has a housing in which at least one mechanical power branch is arranged.
The superposition transmission preferably has a housing with a housing section at the end, to which at least one of the hydraulic machines is connected or fastened at an end flange. This fastening provides a simple possibility for reducing the installation space required in the radial direction.
If a rotary connection of the transmission input shaft to the second drive shaft and/or of the first drive shaft to the first ring gear and/or a pump distributor gear is also arranged in the housing section, this results in a lower maintenance effort due to the common oil budget with the mechanical power branch of the superposition transmission.
In a further embodiment, a transmission for the drive-fit rotational connection of the at least one first drive shaft or the first drive shaft to the first ring gear is provided, in particular, in the housing section.
In one embodiment, the at least one first drive shaft is arranged radially inwardly by the transmission so far that the housing of the at least one hydraulic machine is also arranged radially or at least largely radially within the diameter.
The drawing shows an embodiment of a superimposed transmission according to the invention for a crusher or a crushing plant. The invention will now be explained in detail with the aid of drawings.
Drawings
In the figure:
fig. 1 shows a perspective view of a superposition transmission according to the invention with a planetary gear, a hydraulic pump and a hydraulic motor according to a first exemplary embodiment;
fig. 2 shows the superimposed transmission according to fig. 1 in a longitudinal section through section plane a according to fig. 1;
fig. 3 shows the superimposed transmission according to fig. 1 and 2 in a longitudinal section through section plane B according to fig. 1;
FIG. 4 is a schematic transmission diagram of the stacked transmission according to the previous figures;
FIG. 5 is a hydraulic circuit diagram of a hydraulic power branch of the superposition transmission according to the previous figures;
FIG. 6 is a power flow of the stacked transmission according to the previous figures in fast operation;
FIG. 7 is a power flow of the stacked transmission according to the previous figures in direct operation;
FIG. 8 is a power flow of the stacked transmission according to the previous figures in slow operation;
FIG. 9 is a power flow of the stacked transmission according to the previous figures in free rotation;
FIG. 10 is a power flow of the stacked transmission according to the previous figures in reverse operation;
FIG. 11 is a speed-ratio chart of the stacked transmission according to the previous figures.
Detailed Description
Fig. 1 shows a perspective view of an exemplary embodiment of a
The
The likewise
The two first
Fig. 4 shows a schematic structure of the superimposed
Fig. 4 furthermore shows a first
Fig. 5 shows the hydraulic pressure medium supply of the first
An alternative second hydraulic machine 18' with a constant direction of rotation and an irreversible displacement volume is shown in addition. In order to reverse the pressure medium volume flow and thus the direction of rotation of the first
Fig. 2 shows a section a-a of the superimposed
The second hydraulic machine provides the required pressure medium volume flow for the two first
The gears of the transmission input shaft and of the second drive shaft can alternatively be designed as separate components. Instead of edge keys, other forms of shaft key connections, such as gear shaft connections, are also possible. The pinion and the first drive can alternatively be designed integrally as a pinion shaft.
Instead of the flange connection described by means of cylindrical screws, other types of shaft connections, for example a geared shaft connection, may alternatively be provided in order to transmit torque from the first ring gear to the ring gear flange. The first ring gear and the ring gear flange can alternatively be of one-piece design or be formed from one part. Instead of the tapered roller bearing of the X-shaped arrangement, an O-shaped arrangement may be provided. Furthermore, the angular ball bearing can replace a tapered roller bearing in an X-arrangement or an O-arrangement. Instead of a plurality of radial thrust ball bearings, at least one large radial thrust ball bearing can be provided, which is arranged between the first ring gear and the housing section. In this case, in particular, the ring gear flange and the cylindrical screws can be dispensed with. In principle, all rolling bearings in the superimposed transmission can be replaced by other rolling bearing types. Ideally, all of the first hydraulic machines should have the same or at least similar displacement or displacement volume.
In the following, different operating states of the
In the rapid mode according to fig. 6, as in the exemplary embodiment and in all other operating modes, the speed n of the drive engine or diesel motor is also the same8= constant. In rapid operation, a steplessly adjustable transmission ratio i = n is achieved depending on the rotational speed of the first
Fig. 7 shows a direct drive, in which the volume flow of the
In the slow mode according to fig. 8, the reactive power flow from the
In the free-wheeling special operating mode according to fig. 9, the displacement volume is adjusted in slow operation in such a way that the first
The reverse operation according to fig. 10 is used as a special operating mode in slow operation at very high rotational speeds n of the first
FIG. 11 is a graph based on the rotational speed n of the
A superposition transmission, in particular for a crusher, with a mechanical power branch and a hydraulic power branch is disclosed. In this case, the drive shaft of the hydraulic power branch, which can be operated as a hydraulic motor, with external toothing, or a pinion connected to this drive shaft, engages with the internal toothing of the ring gear of the planetary gear stage of the mechanical power branch.
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