Force transmission device of hydraulic machine

Abstract

The invention relates to a hydromechanical power transmission device (1), comprising an input shaft for at least indirectly connecting to a drive unit, in particular a drive machine (2) having a constant rotational speed, and at least one output shaft for connecting to a variable-speed working machine (3); the invention relates to a transmission basic structure, comprising a hydraulic torque converter (4) and a superimposed transmission (5) designed as a planetary transmission (7), an input shaft (E) being connected to a pump wheel (P) of the hydraulic torque converter (4) and to a first element of the superimposed transmission (5), and a turbine wheel (T) of the hydraulic torque converter (4) being connected to a second element of the superimposed transmission (5), the output shaft (A) is at least indirectly connected to a third element of the superimposed transmission (5). The invention is characterized in that a first element of the superimposed transmission (5) consists of a ring gear (8), a second element of the superimposed transmission (5) consists of a sun gear (9), and a third element of the superimposed transmission (5) consists of a planet carrier (11), and in that an additional transmission stage (6) is arranged between the superimposed transmission (5) and the output shaft (A) in the power transmission direction, the transmission stage (6) comprises an input (14) and an output (15), the input (14) of the transmission stage (6) being connected to a planet carrier (11) of the superimposed transmission (5) and the output (15) of the transmission stage (6) being connected to or forming an output shaft (A) of the power transmission device (1).

Description

[0001] The invention relates to a hydraulic mechanical power transmission device, in particular to the features of the preamble of claim 1. In particular, the invention relates to a hydraulic mechanical power transmission device for driving a variable-speed working machine.

[0002] There are many different embodiments of hydraulic mechanical power transmission devices for driving variable-speed working machines in the prior art.

[0003] The power transmission device of the type according to the invention comprises an input end for at least indirectly connecting to a drive device with a constant speed, and at least one output end for connecting to a working machine with a variable speed. In addition, a hydraulic torque converter and at least one superposition transmission designed as a planetary gear transmission are provided, which superposition transmission comprises a ring gear, a sun gear and a planet carrier with a plurality of planetary gears. The power is transmitted via a mechanical power branch and a fluid power branch. The input end is connected to the pump wheel of the hydraulic torque converter and the first element of the superposition transmission. The turbine wheel of the hydraulic torque converter is connected to the second element of the superposition transmission, and the output end is at least indirectly connected to the third element of the superposition transmission.

[0004] In the embodiment described in document DE 34 41 877 A1, the hydraulic power branch is operated via a hydraulic torque converter in the form of a synchronous torque converter and can be adjusted in terms of speed by adjusting the blade set of the torque converter guide wheel. The torque converter is combined with the mechanically driven power branch in a superposition transmission, so that the working machine is driven at a desired speed, although the drive unit of the power transmission unit on the drive input shaft is operated at a constant speed. Based on this structure, document DE 10 2008 034 607 describes a similar structure, but in this structure, the hollow shaft used here is replaced by a coupling shaft extending parallel to the central axis of the power transmission unit.

[0005] In such power transmission devices, the hydraulic torque converter has to meet different requirements between the driving machine and the machine to be driven, in particular the working machine. The main criteria are the achievable efficiency, the power consumption characteristics and the torque and speed change at the output, i.e. the turbine wheel. In the known power transmission devices, the operating state is influenced by adjusting the guide wheel and / or the working medium filling degree of the hydraulic torque converter.

[0006] A power transmission device is known from document WO 2012143123 A1, which has a hydraulic reverse torque converter instead of a hydraulic synchronous torque converter. Although the reverse torque converter has a low efficiency, it allows the structure of the entire power transmission device to be very simple and compact. The first element of the planetary gear transmission of the superposition transmission is formed by the planet carrier, the second element is formed by the sun gear of the planetary gear transmission, and the third element is formed by the ring gear of the planetary gear transmission. In this structure, the ring gear is connected to the output shaft directly or through another transmission, preferably a spur gear transmission, and the fluid power branch is input through the sun gear. This structure has a significant advantage, namely that the planetary gear transmission can be designed to be very compact due to the favorable rotational speed.

[0007] In order to transmit higher powers, the known embodiments need to be very large or require additional speed / torque transmission devices.

[0008] The technical problem to be solved by the invention is to develop a force transmission device which can transmit very high powers and which has a very simple and compact structure. In addition, the entire system should be designed so that various requirements in terms of transmission ratios and arrangements between input and output can be easily implemented.

[0009] This object is achieved according to the invention by the embodiments described in the independent claim. Further advantageous embodiments of the invention are described in the dependent claims.

[0010] A hydraulic mechanical force transmission device, comprising:

[0011] an input shaft for at least indirectly connecting to a drive unit, in particular a drive machine with a constant speed, and at least one output shaft for connecting to a working machine with a variable speed;

[0012] A transmission basic structure, comprising a hydraulic torque converter and a superposition transmission designed as a planetary gear transmission, the superposition transmission comprising a ring gear, a sun gear and a planet carrier with a plurality of planetary gears as elements of the planetary gear transmission, wherein the input shaft is connected to the pump wheel of the hydraulic torque converter and the first element of the superposition transmission, the turbine wheel of the hydraulic torque converter is connected to the second element of the superposition transmission, and the output shaft is at least indirectly connected to the third element of the superposition transmission;

[0013] It is characterized in that the first element of the superposition transmission is formed by the ring gear, the second element of the superposition transmission is formed by the sun gear, and the third element of the superposition transmission is formed by the planetary carrier, and an additional speed stage is arranged between the superposition transmission and the output shaft in the power transmission direction, and the speed stage includes an input end and an output end, wherein the input end of the speed stage is connected to the planetary carrier of the superposition transmission, and the output end of the speed stage is connected to the output shaft of the power transmission device or forms the output shaft.

[0014] A hydraulic torque converter is understood here to be a speed / torque conversion device. It comprises at least three blade wheels forming a working chamber that can be filled with a working medium and which serve to deflect the flow of the working medium.

[0015] The term "shaft" is to be understood functionally and comprises any component which is designed to rotate about an axis of rotation and which is rotatable and suitable for transmitting torque.

[0016] The basic transmission structure in the present invention refers in particular to the basic structure of a superposition transmission in the form of a torque converter and a planetary gear transmission. It can be provided prefabricated as a modular unit consisting of two structural units, or assembled from single modules of a superposition transmission in the form of a torque converter and a planetary gear transmission.

[0017] The solution according to the invention offers the advantages of a basic transmission structure consisting of a hydraulic torque converter and a planetary gear transmission, which, by means of the described connection, allows a power transmission in two power branches, which enables an output via the planetary carrier and is designed for the high power range, wherein an adaptation to the specific application requirements in terms of the transmission ratio and the orientation of the output is achieved by means of an additional downstream transmission stage. The basic transmission structure can be provided as a prefabricated modular unit, which can be completed in a simple manner to meet various requirements by supplementing it with further transmission stages, which are preferably also designed as modular units.

[0018] The combination of a torque converter and a superposition transmission also makes it possible to omit an additional hydraulic clutch for starting, since the function of starting without load can be realized solely based on the filling state of the torque converter.

[0019] In a particularly advantageous embodiment, the turbine wheel of the torque converter is connected to the sun gear of the superposition transmission on the side of the superposition transmission facing the torque converter, wherein the maximum radial dimension of the component connecting the turbine wheel to the sun gear in the radial direction is smaller than the diameter of the superposition transmission. In other words, the connection between the turbine wheel and the sun gear is directly effected, i.e. without bypassing the superposition transmission, and thus takes place on the shortest path between the input and the output of the power transmission device as viewed in the axial direction. The high-speed rotating component is characterized by a diameter that is significantly smaller than the outer diameter of the superposition transmission itself, which makes the basic transmission structure composed of the torque converter and the superposition transmission very compact as a whole and can save complex packaging of the planetary gear housing by bypassing the connecting shaft between the turbine wheel and the sun gear. The connection between the turbine wheel and the sun gear has advantages in terms of power density as a small-diameter high-speed rotating component, and the single shaft of the planetary gear transmission is simpler to support.

[0020] There are various possibilities for realizing the connection between turbine wheel and sun wheel itself, but these possibilities include, in particular, components that are designed to be rotationally symmetrical, in particular in the form of hollow shafts.

[0021] In an advantageous development, in order to reduce wear, the rolling bearings which are usually used in planetary transmissions for mounting the planetary gears are replaced in this embodiment by sliding bearings.

[0022] According to a first embodiment, the planet carrier of the superposition transmission is designed with a fixed planetary gear shaft, wherein the planetary gears are slidably supported on the planetary gear shaft. In a second alternative embodiment, the planetary gears are constructed integrally with the planetary gear shaft or the planetary gears are connected to the planetary gear shaft in a rotationally fixed manner and the planetary gear shaft is slidably supported in the planet carrier.

[0023] Depending on the requirements of the application, the input and output of the hydraulic mechanical power transmission device can be arranged coaxially with respect to one another according to a first embodiment, and can be arranged eccentrically with respect to one another according to a second embodiment. This is achieved in particular by the design of an additional gear stage.

[0024] The additional transmission stage can be implemented in various forms here, depending on the required transmission ratio. However, it is preferred to select a design which, in addition to being compact and possibly having few components, also has a small structural size.

[0025] According to a first advantageous embodiment, the input and output are coaxially implemented, or the drive and output are coaxially implemented, the gear stage is designed as a planetary gear, the planetary gear comprises at least one planet carrier that can be fixed or fixed to the housing, a plurality of planetary gears and gears meshing with the planetary gears, and a sun gear meshing with the planetary gears of the gear stage, the gears being coupled at least indirectly, preferably directly, to the planet carrier of the superposition transmission, and the sun gear being coupled to the output of the power transmission device or being integrally constructed therewith. This embodiment is characterized by a small space requirement in the axial and radial directions.

[0026] In a first variant of the first design, the planetary gear of the transmission stage is designed as a simple planetary gear stage, wherein the gear meshing with the planetary gears of the transmission stage is formed by the ring gear of the planetary gear stage. This allows a sufficiently high transmission speed between the superposition transmission and the output, thereby providing a low torque at the output, while maintaining a compact design in the radial and axial directions. The use of a simple planetary gear set in the downstream transmission stage also allows the use of standardized prefabricated planetary gear sets. In addition to saving space, this solution also has significant cost advantages.

[0027] In a second variant, the hydromechanical power transmission device is characterized in that the planetary gear device of the speed stage is designed as a multi-stage planetary gear set. The multi-stage planetary gear set includes first-stage and second-stage planetary gears with different tooth diameters and designed as multi-stage planetary gears, wherein the gear of the planetary gear device of the speed stage connected to the output end of the superposition transmission meshes with the first-stage planetary gear, and the sun gear of the planetary gear device of the speed stage meshes with the second-stage planetary gear.

[0028] Depending on the case where the gear of the planetary gear device connected to the output of the superposition transmission is designed as a ring gear or a sun gear, and depending on the case where the gear connected to the output part or forming the output part is designed as a sun gear, low speed and high torque can be achieved while still maintaining a relatively compact structure by means of a stepped design and introducing the torque into the transmission stage via the ring gear on the output side of the transmission stage. In a first sub-design mode, the gear of the planetary gear device of the transmission stage connected to the output of the superposition transmission and meshing with the first-stage planetary gear is formed by a ring gear, thereby allowing a larger transmission ratio than the embodiment according to the second sub-variant, in which the gear of the planetary gear device of the transmission stage connected to the output of the superposition transmission and meshing with the first-stage planetary gear is formed by a sun gear.

[0029] If the design of the transmission stage as a planetary gear arrangement allows a very compact structural unit in the radial and axial directions and enables large transmission ratios, then in the second variant, the additional transmission stage comprises at least one spur gear stage when an eccentric arrangement is desired between the input and the output of the power transmission device. Very large transmission ratios can be achieved if the spur gear stage is designed as a single-stage spur gear stage, the input of which is connected to the superposition transmission and the output of which is connected to the output of the power transmission device or forms the output shaft. In the case of limited radial space, the spur gear stage can be designed as a multi-stage spur gear stage, the input of which is connected to the superposition transmission and the output of which is coupled to the output of the power transmission device or forms the output shaft.

[0030] As already mentioned, the individual components can be provided as modules and assembled in a modular manner. This applies in particular to the torque converter and the superposition transmission of the basic transmission structure, as well as to the additional gear stages. In this case, the basic transmission structure can be assembled from modular units of the torque converter and the superposition transmission, or the entire basic configuration can be provided as a preassembled unit. The advantage of forming and assembling from prefabricated and possibly standardized modular units is that the variety of parts is reduced in the case of a large number of variants of the power transmission device.

[0031] The hydraulic torque converter can be designed in various forms, but is preferably designed as a regulating torque converter, comprising at least one pump wheel, a turbine wheel and at least one guide wheel, wherein preferably at least one of these wheels has adjustable blades or blade sections. According to a particularly advantageous design, the guide wheel is provided with regulating blades, thereby achieving higher efficiency and a wider characteristic curve range. The solution of the present invention has the advantages of adjusting the power consumption and expanding the possible operating range of the torque converter in the power transmission device by adjusting at least a single regulating blade and / or an adjustable blade section.

[0032] The torque converter of the power transmission device according to the present invention is designed as a synchronous torque converter. In this case, the pump wheel and the turbine wheel rotate in the same direction and allow the superposition transmission to be simply connected in the described manner.

[0033] The present invention is described below in conjunction with the accompanying drawings. In the accompanying drawings:

[0034] Figure 1 A simplified schematic diagram showing the basic structure of a force transmission device;

[0035] Figure 2 Show according to Figure 1 An embodiment of the power transmission device having a downstream transmission stage in the form of a simple planetary gear set;

[0036] Figure 3 Show according to Figure 1 Embodiment of the power transmission device having a downstream transmission stage with a single-stage planetary gear;

[0037] Figure 4 Show according to Figure 3 Embodiment of a power transmission device having a downstream alternative embodiment of a transmission stage with a single-stage planetary gear;

[0038] Figure 5 Show according to Figure 1 Embodiment of a power transmission device having a downstream transmission stage with a simple spur gear stage;

[0039] Figure 6 Show according to Figure 1 An embodiment of a power transmission device having a downstream transmission stage with a multi-stage spur gear stage.

[0040] Figure 1 A power transmission device 1 of a hydraulic machine according to the present invention is shown in a simplified schematic diagram, hereinafter referred to as the basic structure of the power transmission device, which is used to transmit power from a drive machine 2 to a machine to be driven, in particular a working machine 3. The power transmission device 1 includes at least one input end for introducing torque and at least one output end. The power transmission device 1 is particularly designed to be suitable for transmitting power from a drive machine 2 with a constant speed to a working machine 3 with a variable speed. The input end is designed as an input shaft E for at least indirectly connecting the drive machine 2. The output end is formed by an output shaft A for at least indirectly connecting the working machine 3. At least indirect connection here includes both direct connection and connection through other components arranged in the middle, which also includes a speed / torque converter.

[0041] The power transmission device 1 includes a hydraulic transmission / torque converter, hereinafter referred to as a hydraulic torque converter 4 and a superposition transmission 5 and a gear stage 6 arranged between the superposition transmission 5 and the output end A, for adapting to different required transmission ratios and / or installation conditions. The hydraulic torque converter 4, the superposition transmission 5 and the gear stage 6 are arranged in sequence between the input shaft E and the output shaft A in the axial direction.

[0042] For this purpose, the superposition transmission 5 has an input 12 and an output 13. The input 12 of the superposition transmission 5 is coupled to the torque converter 4 and the input E of the power transmission device 1. The output 13 of the superposition transmission 5 is connected to the input 14 of the transmission stage 6. The output 15 of the transmission stage 6 is connected to the output or output shaft A of the power transmission device or forms the output.

[0043] The input shaft E and the output shaft A of the power transmission device 1 can be configured as follows: Figure 1 The first embodiment shown is a coaxial arrangement, or an eccentric arrangement.

[0044] The superposition transmission 5 is designed as a planetary gear transmission 7, comprising at least one ring gear 8, a sun gear 9 and a planet carrier or support 11 carrying planetary gears 10. The planetary gears 10 are rotatably supported on the support 11. The support can be carried out in such a way that the support 12 has fixed planetary gear shafts 22 and the planetary gears 10 are rotatably supported on these shafts. An alternative design is that the planetary gear shafts 22 that support the planetary gears 10 in a rotationally fixed manner are rotatably supported.

[0045] The hydraulic torque converter 4 includes at least a pump wheel P, a turbine wheel T and a guide wheel L.

[0046] The torque converter 4 is designed as a single-phase hydraulic torque converter or a synchronous torque converter, that is, the pump wheel P and the turbine impeller T rotate in the same direction.

[0047] Other embodiments are also conceivable, for example a multi-stage torque converter.

[0048] The torque converter 4 is designed as a regulating torque converter for additionally changing the circulation flow and thus the characteristic curve. For this purpose, the blade set of at least one element, namely the pump wheel P, the turbine wheel T or the guide wheel L, comprises one or more regulating blades or adjustable blade sections. In the case shown, the guide wheel L is particularly advantageously equipped with an adjusting device 28 for blade adjustment.

[0049] The torque converter 4 and the superposition transmission 5 are arranged in sequence axially between the input end E and the output end A. The additional transmission stage 6 is arranged functionally and structurally downstream of the superposition transmission 5 when viewed axially. The torque converter 4, the superposition transmission 5 and the transmission stage 6 can be provided as prefabricated and preconfigured modules and combined with each other according to the requirements of use. The advantage of the modular design is that it can be quickly and easily adapted to different use conditions using as few basic components or structural units as possible.

[0050] According to the present invention, the pump wheel P of the torque converter 4 is coupled to the input E and is at least indirectly connected to the ring gear 8 of the planetary gear transmission 7 in a rotationally fixed manner, while the turbine wheel T is connected to the sun gear 9. The planet carrier or support 11 forms the output 13 of the superposition transmission 5. The hydraulic torque converter 4 and the planetary gear transmission 7 are arranged coaxially. The coupling structure implemented in this way and connected to the torque converter 4 allows a large power to be transmitted at the output of the superposition transmission. In order to adjust the speed or achieve the required overall transmission ratio when coupling the power transmission device 1 to the working machine 3, a gear stage 6 is arranged downstream of the superposition transmission 5. The gear stage 6 includes an input 14 connected to the output 13 of the superposition transmission 5, and an output 15 forming the output A of the power transmission device 1 or connected thereto.

[0051] The input end E and the output end A of the power transmission device 1 are as follows: Figure 1As shown, it can be arranged coaxially or eccentrically. The specific implementation depends on the specific use case.

[0052] There are various possibilities for designing the transmission stage 6. If a coaxial arrangement of the input E and the output A is desired, a transmission stage 6 in the form of a planetary gear arrangement is preferably used, which can be designed as a simple planetary gear set or planetary gear stage arrangement. Possible embodiments are as follows: Figures 2 to 4 , an embodiment of a power transmission device 1 is shown. The common feature of the transmission stages 6 shown in these figures is that they comprise a planetary gear 16 having at least one fixed, in particular housing-fixed carrier or planet carrier 17 and a sun gear 18, which forms the output 15 of the transmission stage 6 or is connected to it. For this purpose, the planet carrier 17 is either fixed in position, in particular housing-fixed, or alternatively actively held by a braking device (not shown). The input 14 of the transmission stage 6 is formed by another element of the planetary gear 16.

[0053] Figure 2 The downstream transmission stage 6 is shown as a simple planetary gear set 19, whose input 14 is formed by a ring gear 20. The connection between the ring gear 20 of the transmission stage 6 and the planet carrier 11 of the superposition transmission 5 is guided outside the outer diameter of the superposition transmission 5. The sun gear 18 is arranged coaxially with the input E of the power transmission device 1 and forms the output A of the power transmission device 1 or is connected to it in a rotationally fixed manner. The planetary gears 21 of the planetary transmission 19 mesh with the ring gear 20 and the sun gear 18. The sun gear 18 and the ring gear 20 are arranged in the same axial plane.

[0054] Figure 3 and Figure 4 An embodiment of a planetary gear arrangement 16 is shown, which has multi-stage planetary gears, in particular multi-stage planetary gears with steps, by using so-called multi-stage planetary gears 21.1 and 21.2. The multi-stage planetary gears 21.1, 21.2 are preferably mounted coaxially on the planet carrier 17 and can be present on integrally formed components with different tooth diameters or as individual independent multi-stage planetary gears 21.1, 21.2 connected to each other. In this case, they are preferably rotatably mounted on a planetary gear shaft 22, which is fixedly connected to the planet carrier 17 or is integrally formed on the planet carrier 17. It is also conceivable to design the multi-stage planetary gears 21.1, 21.2 as individual or interconnected gears, which are mounted on the rotatably mounted planetary gear shaft 22.

[0055] The hydraulic torque converter 4 and the superposition transmission 5 are Figure 2 The embodiments shown are identical.

[0056] exist Figure 3In the embodiment, the planetary gear device 16 of the transmission stage 6 is designed with a single-stage planetary gear. The input end 14 of the transmission stage 6 is formed by a ring gear 20, which meshes with the first-stage planetary gear 21.1. The first-stage planetary gear 21.1 is coupled to the second-stage planetary gear 21.2, in particular through a common planet carrier 17 fixed to the housing. The output end 15 is formed by a sun gear 18, which meshes with the second-stage planetary gear 21.2. The tooth diameter of the first-stage planetary gear 21.1 is smaller than the tooth diameter of the second-stage planetary gear 21.2. A reduction transmission is thus achieved. By selecting the tooth diameter of the multi-stage planetary gears 21.1 and 21.2, the required transmission ratio can be adjusted.

[0057] Figure 4 Shown with Figure 2 and Figure 3 Compared to the embodiment shown, an alternative embodiment of the gear stage 6 is provided. Here, the planetary gear arrangement 16 also comprises a multi-stage planetary gear with first-stage and second-stage planetary gears 21.1, 21.2, which have a common bearing shaft. Figure 3 Compared to the embodiment of the present invention, the input end 14 of the gear stage 16 is formed by the sun gear 23, and the output end is formed by the sun gear 18 meshing with the second-stage planetary gear 21.2. By fixing the planet carrier, a larger transmission ratio can be achieved.

[0058] on the contrary, Figure 5 and Figure 6 Exemplary embodiments of a power transmission device 1 having a transmission stage 6 in the form of a spur gear stage are shown, wherein these exemplary embodiments are primarily used for applications with a required offset between input E and output A.

[0059] Figure 5 A simple spur gear stage 25 is shown, comprising an even number, in particular two, of spur gears 26 and 27 meshing with one another. Here, the spur gear 26 forms the input 14 of the gear stage 6 or is connected thereto, and the spur gear 27 forms the output 15 of the gear stage 6 or is connected thereto. Such a gear stage 6 is very compact in the axial direction. However, in order to achieve large transmission ratios with this embodiment, the spur gear 26 must be designed with a correspondingly large diameter.

[0060] In order to keep the construction space as compact as possible in the radial direction, Figure 6The transmission stage 6 is designed as a spur gear transmission 29 with two spur gear stages 30 and 31 connected in series, wherein the output 32 of the first spur gear stage 30 is connected to the input 33 of the second spur gear stage 31 and they are arranged coaxially. The first spur gear stage 30 comprises a spur gear 36, which forms the input 34 of the first spur gear stage and thus also the input 14 of the transmission stage 6. It meshes with a spur gear 37, which forms the output 32 of the first spur gear stage 30. The output 37 is coupled to the input 33 of the second spur gear stage 31, which is formed by a spur gear 38. The two spur gears 37 and 38 are supported on the same shaft. The output 15 of the transmission stage 6 is formed by a gear 39 of the second spur gear stage 31 and is supported on the output shaft A.

[0061] About the basis Figures 1 to 6 There are many possibilities for the embodiment of the adjustment device 28 for the blade group of the torque converter 4 shown. They can be implemented in very different ways and differ in the realization of multiple sub-functions, including the way of generating the adjustment force, the direction of introduction of the adjustment force, the way of adjustment of individual adjustment blades or adjustable blade segments, and the way of blade control. Here, with regard to the control method, a distinction can be made between central control, that is, the adjustment of all adjustment blades and / or adjustable blade segments, or individual control or group control of adjustment blades and / or adjustable blade segments. The specific selection depends on the requirements of the application.

[0062] Reference numerals list

[0063] 1. Power transmission equipment

[0064] 2 Driving machine

[0065] 3 Working machines

[0066] 4 Torque converter

[0067] 5 Superposition transmission

[0068] 6 speed levels

[0069] 7 Planetary gear transmission

[0070] 8 Ring gear

[0071] 9 Sun gear

[0072] 10 Planetary gear

[0073] 11 Bracket, planet carrier

[0074] 12 Input of superposition transmission

[0075] 13 Output of superposition transmission

[0076] 14 Speed ​​stage input

[0077] 15 Speed ​​stage output

[0078] 16 Planetary gear unit

[0079] 17 planet carrier; bracket

[0080] 18 Sun gear

[0081] 19 Planetary gear set

[0082] 20 Ring gear

[0083] 21 Planetary gear

[0084] 21.1, 21.2 Multi-stage planetary gear

[0085] 22 Planetary gear shaft

[0086] 23 Sun gear

[0087] 25 spur gear stages

[0088] 26 First spur gear

[0089] 27 Second spur gear

[0090] 28 Adjustment device

[0091] 29 Spur gear

[0092] 30 spur gear stages

[0093] 31 spur gear stages

[0094] 32 Output of the first spur gear stage

[0095] 33 Input of the second spur gear stage

[0096] 34 Input of the first spur gear stage

[0097] 35 Output of the second spur gear stage

[0098] 36 First spur gear

[0099] 37 Second spur gear

[0100] 38 First spur gear

[0101] 39 Second spur gear

[0102] E Input end; input shaft of power transmission equipment

[0103] A Output end; output shaft of power transmission equipment

[0104] P Pump Impeller

[0105] T turbine impeller

[0106] L Guide wheel

Claims

1. A hydraulic mechanical force transmission device (1), comprising: An input shaft and at least one output shaft, the input shaft being used to be connected at least indirectly to a drive unit, in particular a drive machine (2) with a constant speed, and the at least one output shaft being used to be connected to a working machine (3) with a variable speed; A transmission basic structure, comprising a hydraulic torque converter (4) and a superposition transmission (5) designed as a planetary gear transmission (7), the superposition transmission (5) comprising a ring gear (8) as an element of the planetary gear transmission (7), a sun gear (9) and a planet carrier (11) having a plurality of planetary gears (10), wherein: The input shaft (E) is connected to the pump wheel (P) of the hydraulic torque converter (4) and the first element of the superposition transmission (5), the turbine wheel (T) of the hydraulic torque converter (4) is connected to the second element of the superposition transmission (5), and the output shaft (A) is at least indirectly connected to the third element of the superposition transmission (5); It is characterized in that the first element of the superposition transmission (5) is formed by the ring gear (8), the second element of the superposition transmission (5) is formed by the sun gear (9), and the third element of the superposition transmission (5) is formed by the planetary carrier (11), and an additional gear stage (6) is arranged between the superposition transmission (5) and the output shaft (A) in the power transmission direction, and the gear stage (6) includes an input end (14) and an output end (15), wherein the input end (14) of the gear stage (6) is connected to the planetary carrier (11) of the superposition transmission (5), and the output end (15) of the gear stage (6) is connected to the output shaft (A) of the power transmission device (1) or forms the output shaft (A).

2. The hydraulic mechanical power transmission device (1) according to claim 1, characterized in that The turbine impeller (T) is connected to the sun gear (9) of the superposition transmission (5) on the side of the superposition transmission (5) facing the torque converter (4), wherein the maximum radial dimension of the component connecting the turbine impeller (T) to the sun gear (9) in the radial direction is smaller than the diameter of the superposition transmission (5).

3. The hydraulic mechanical power transmission device (1) according to claim 1 or 2, characterized in that: The planet carrier of the superposition transmission is designed with fixed planet shafts and the planet gears are slidingly mounted on the planet shafts, or the planet gears are designed integrally with the planet shafts or the planet gears are connected to the planet shafts in a rotationally fixed manner and the planet shafts are slidingly mounted in the planet carrier.

4. The hydraulic mechanical power transmission device (1) according to any one of claims 1 to 3, characterized in that An input shaft (E) and an output shaft (A) of a hydromechanical power transmission device (1) are arranged coaxially with respect to one another.

5. The hydraulic mechanical power transmission device (1) according to any one of claims 1 to 3, characterized in that The input shaft (E) and the output shaft (A) of a hydromechanical power transmission device (1) are arranged eccentrically with respect to one another.

6. The hydraulic mechanical power transmission device (1) according to any one of claims 1 to 5, characterized in that The transmission stage (6) is designed as a planetary gear device (16), which includes at least one planet carrier (17) that can be fixed or fixed to the housing, a plurality of planetary gears (21) and gears meshing with the planetary gears (21), and a sun gear (18) meshing with the planetary gears (21) of the transmission stage (6), the gears being at least indirectly, preferably directly, coupled to the output end (13) of the superposition transmission (5), in particular the planet carrier (17) of the superposition transmission (5), and the sun gear (18) being coupled to the output shaft (A) of the power transmission device (1) or being constructed integrally with the output shaft.

7. The hydraulic mechanical power transmission device (1) according to claim 6, characterized in that The planetary gear (16) is designed as a simple planetary gear stage, wherein the gear which meshes with the planetary gears (21) of the transmission stage (6) and is coupled to the superposition transmission (5) is formed by the ring gear (20) of the planetary gear stage.

8. The hydraulic mechanical power transmission device (1) according to claim 6, characterized in that The planetary gear device (16) of the speed stage (6) is designed as a multi-stage planetary gear set, which includes first-stage and second-stage planetary gears with different tooth diameters and designed as multi-stage planetary gears (21.1, 21.2), wherein the gear of the planetary gear device (16) of the speed stage (6) connected to the output end (13) of the superposition transmission (5) is meshed with the first-stage planetary gear (21.1), and the sun gear (18) of the planetary gear device (16) of the speed stage (6) is meshed with the second-stage planetary gear (21.2).

9. The hydraulic mechanical power transmission device (1) according to claim 8, characterized in that The gear of the planetary gear device (16) of the gear stage (6) connected to the output end (13) of the superposition transmission (5) and meshing with the first-stage planetary gear is composed of a ring gear (20).

10. The hydraulic mechanical power transmission device (1) according to claim 8, characterized in that The gear of the planetary gear device (16) of the gear stage (6) connected to the output end (13) of the superposition transmission (5) and meshing with the first-stage planetary gear is formed by a sun gear (23).

11. The hydraulic mechanical power transmission device (1) according to any one of claims 1 to 5, characterized in that The additional transmission stage (6) is designed as a single-stage spur gear stage (25), the input end (14) of which is connected to the superposition transmission (5), and the output end (15) of which is connected to the output shaft (A) of the power transmission device (1) or forms the output shaft.

12. The hydraulic mechanical power transmission device (1) according to any one of claims 1 to 5, characterized in that The additional transmission stage (6) is designed as a multi-stage spur gear stage, the input end (14) of which is connected to the superposition transmission (5), and the output end (15) of which is coupled to the output shaft (A) of the power transmission device (1) or forms the output shaft.

13. The hydromechanical power transmission device (1) according to any one of claims 1 to 12, characterized in that The additional transmission stage (6) and the basic transmission structure or its individual components, namely the torque converter (4) and the superposition transmission (5), are designed as a modular unit.

14. The hydromechanical power transmission device (1) according to any one of claims 1 to 13, characterized in that The hydraulic torque converter (4) is designed as a synchronous torque converter.

15. The hydromechanical power transmission device (1) according to any one of claims 1 to 14, characterized in that The hydraulic torque converter (4) is designed as an adjustable torque converter and comprises a pump wheel (P), a turbine wheel (T) and at least one guide wheel (L), wherein preferably at least one of these wheels has adjustable blades or blade sections.

Images