Power split continuously variable transmission

Abstract

The present invention relates to a power split type continuously variable transmission device (100; 200; 300; 400; 500; 600; 700; 800; 900; 1000), which has a variator (16). A first planetary gear set has a first sun gear (30), a first planetary carrier (32), respective first planetary gears (36) and a first ring gear (34). A second planetary gear set has a second sun gear (40), a second planetary carrier (42), second and third planetary gears (46, 48) and a second ring gear (44). The first and second planetary carriers (32, 42) are connected to each other in a manner that prevents relative rotation. The second planetary gear (46) meshes with the second sun gear (40) and the second ring gear (44). The second and third planetary gears (46, 48) mesh with each other in pairs. The first and third planetary gears (36, 48) are connected to each other in a manner that prevents relative rotation. The variator (16) is mechanically connected to a drive end (12) and the first sun gear (30). The driving end (12) can be mechanically connected to the first gear ring (34).

Description

Technical Field

[0001] The present invention relates to a power split type continuously variable transmission device. In addition, the present invention also relates to a drive unit having such a power split type continuously variable transmission device. Background Art

[0002] Power-split continuously variable transmissions, such as hydrostatic power-split transmissions, are often used in the field of powered machines. An example of a powered machine is a tractor. Such hydrostatic transmissions allow a continuously variable adjustment of the transmission ratio with relatively high efficiency, but with a relatively low transmission ratio value. The transmission ratio value of a transmission is understood to be the ratio between a maximum and a minimum transmission ratio. In order to increase the transmission ratio value, it is known to provide a plurality of travel ranges in the continuously variable transmission, which have different transmission ratio ranges. Such a transmission is known, for example, from DE 197 41 510 A1. Summary of the invention

[0003] The first aspect of the present invention relates to a power-split continuously variable transmission. The transmission can be configured to be used in a working machine. The transmission ratio can be adjusted steplessly in the continuously variable transmission. The power split can be, for example, a hydrostatic mechanical power split. Alternatively or additionally, for example, an electromechanical power split can also be used. The transmission can achieve a higher transmission ratio ratio under high efficiency. The transmission includes a drive end, at which a variable to be transmitted is fed into the transmission. The transmission can have a drive shaft, which can form the drive end at one end. The drive shaft can extend through the transmission and can extract power output power at the end away from the drive end, for example, for driving a working device of a working machine. The transmission also includes a driven end, at which a variable transmitted by the transmission is output. At the driven end, for example, a torque for driving a driving force can be provided, in particular for rotating the wheels of the working machine. The drive end and the driven end can be arranged parallel to each other. However, other designs are also conceivable, such as a coaxial arrangement.

[0004] The transmission has a variator. The variator can be set up to, for example, continuously change the transmission ratio of the transmission within a driving range. The driving range of the transmission can be understood as a state in which a fixed mechanical transmission ratio exists between the drive end and the driven end of the transmission, wherein the transmission ratio of the transmission can be continuously changed by the variator within the driving range. The variator can have two energy converters, which are, for example, constructed as hydraulic regulators. However, the energy converter of the variator can also be constructed as an electric motor. The energy converter can be coaxial with the drive end of the transmission. It is also conceivable that they are constructed parallel to the drive end axis. The first energy converter can, for example, be a hydraulic machine with a fixed amount of fluid per revolution, and the second energy converter is a hydraulic machine with an adjustable amount of fluid per revolution.

[0005] The transmission device has a planetary assembly. The planetary assembly has a first and a second planetary gear set, which respectively have a sun gear, a planet carrier and a ring gear with planetary gears rotatably supported thereon. The first and second planetary gear sets are configured as negative planetary gear sets, for example. The negative planetary gear set has a negative fixed-axis transmission ratio.

[0006] If two elements are mechanically connected, they are directly or indirectly connected to each other in such a way that the movement of one element causes the other element to react. The mechanical connection can be provided, for example, by a form-locked or friction-locked connection. The mechanical connection can be equivalent to the meshing of corresponding toothings of two elements, for example. In two elements meshing with each other, their toothings are, for example, in engagement. The two elements can roll against each other. Here, other elements, such as one or more spur gear stages, can be arranged between these elements. In contrast, the permanent rotationally fixed connection of two elements is understood to be one in which the two elements are rigidly coupled to each other in all normal states of the transmission. Here, these elements can exist as single parts that are rotationally fixed to each other or can also exist in one piece.

[0007] If a clutch is provided between two elements of the transmission, these rotating elements are not permanently connected to each other in a rotationally-resistant manner, but can be connected to each other in a rotationally-resistant manner via the clutch. The clutch can be a switching element. The rotationally-resistant connection is only caused by operating the clutch located in the middle. Here, operating the clutch means that the clutch is transferred to a closed state, so that the structural elements directly coupled to the clutch are balanced with each other in terms of their rotational movement. The respective switching elements can, for example, be switched at least between the disconnected and closed states. If the relevant switching element is constructed as a form-locking switching element, the structural elements directly connected to each other in a rotationally-resistant manner via it run at the same speed. In the case of a friction-locking switching element, there may be a speed difference between the structural elements even after operating it. Nevertheless, this desired or undesirable state is still referred to as the rotationally-resistant connection of the respective structural elements within the scope of the present invention. In a friction-locking connection, for example, there may be a certain speed difference between two elements connected to each other based on slip. Here, despite the slip, the speeds of the two components are usually roughly the same. Accordingly, despite the slip, this connection is still considered to be rotationally-resistant here.

[0008] The respective planetary gear sets described here may not have other elements other than the elements described here, such as other ring gears, planet carriers, planetary parts and sun gears. The planetary structural assembly and the transmission device, for example, do not have other planetary gear sets of the planetary gear sets described here. The respective ring gears can be constructed as housing elements of the transmission device or the planetary structural assembly. It can be provided in the transmission device that its planetary structural assembly or all planetary gear sets are constructed as planetary rollers together. The planetary rollers can be compact and sturdy. Being constructed as planetary rollers can mean that the planetary structural assembly has only coaxial elements. In addition, being constructed as planetary rollers can mean that the planetary structural assembly has no cylindrical gears. The planetary structural assembly can be arranged coaxially with the driven end, for example.

[0009] The first planetary gear set is composed of a first sun gear, a first planet carrier and a first ring gear that rotatably supports a group of first planetary gears. The second planetary gear set is composed of a second sun gear, a second planet carrier and a second ring gear that rotatably supports a group of second planetary gears and a group of third planetary gears. The second planetary gear (which meshes with the second sun gear, the second ring gear and the third planetary gear) has a larger pitch circle diameter and a shorter axial length than the third planetary gear. The pitch circle diameter of the gear is the tooth diameter defined in the literature. This diameter describes the average diameter of the tooth. The planetary gears in a group of planetary gears can, for example, have respective axes of rotation arranged on the same circumference, alternatively or additionally have respective functional connections of the same type, alternatively or additionally be constructed as universal parts. The respective grouped planetary gears are, for example, arranged evenly spaced from each other on the circumference of the transmission.

[0010] The first and second planet carriers are permanently connected to each other in a rotationally fixed manner. The two planet carriers can be formed in one piece or constructed as a common component, for example. The first planet gear meshes with the first sun gear and the first ring gear. The second planet gear meshes with the second sun gear and the second ring gear. The second planet gear and the third planet gear mesh with each other in pairs. The first planet gear and the third planet gear are permanently connected to each other in a rotationally fixed manner in pairs. If the respective third planet gear rolls on the respective second planet gear, a corresponding rotation of the first planet gear can be achieved.

[0011] The variator is mechanically connected to the drive end and the first sun gear. The drive end can be mechanically connected to the first ring gear. These connections of the planetary components result in a particularly high transmission ratio. The transmission ratio is, for example, greater than in the following structural form, in which the drive end can be mechanically connected to an element of a second planetary gear set having two sets of planetary gears. The transmission is configured to transmit torque from the second planetary gear set to the driven end. The transmission can be performed mechanically, for example, via respective hollow shafts, spur gear stages, switching elements and other planetary gear sets.

[0012] All clutches of the transmission according to the invention can be designed as friction clutches, for example as diaphragm clutches. Likewise, some or all clutches can also be designed as form-locking clutches, for example dog clutches or synchronizers. A synchronizer is understood to be a form-locking clutch between two shafts, wherein the shafts are brought into simultaneous operation, i.e. synchronized, before the form-locking connection is established.

[0013] The power split transmission allows to provide multiple driving ranges with fewer switching elements and thus has a larger transmission ratio ratio. Here, the transition between the driving ranges can be carried out synchronously. This can mean that when the lower or upper limit of the speed of the respective driving range is reached, the next driving range can be engaged without having to perform adjustments on the variator. The variator does not have to change its speed or position, for example, in order to implement the driving range change. In addition, the variator can also be in the respective maximum position at one or both limits of the respective driving range. In the respective driving range, a small number of clutches can be in their respective disconnected positions, thereby reducing drag losses and thus improving transmission efficiency.

[0014] In one embodiment of the transmission, it can be provided that the respective first planetary gears and the respective third planetary gears are respectively configured as long planetary gears in pairs. The long planetary gears can, for example, have mechanical engagement with two elements spaced apart from each other in the axial direction. The long planetary gears can, for example, have elements for the action connection with other elements in two axial regions on the outer circumference. For example, the long planetary gears can have teeth for mechanical engagement at two opposite ends. However, the long planetary gears can also have continuous teeth, which are in mechanical engagement with the first and second other elements in different axial regions. The long planetary gears can, for example, be manufactured in one piece at low cost. In order to reduce weight, the middle part can be milled down to form a shaft connection frame. The long planetary gears can, for example, also be composed of two gears, which are connected to the hollow shaft of the long planetary gears in a rotationally fixed manner. With the help of the hollow shaft, the two gears can be rotatably supported on the assigned planetary carrier. The long planetary gears can, for example, have the same effective diameter or even the same teeth in two regions for mechanical action connection. The long planetary gears can be provided with a large degree of nesting, thereby making the transmission device particularly compact. In addition, the long planetary gears can be manufactured at low cost. Alternatively, the respective first planet gear and the respective third planet gear can each be designed in pairs as stepped planets.

[0015] In one embodiment of the transmission, it can be provided that the transmission has only two first planetary gears. Alternatively or additionally, the transmission can have only two second planetary gears. Alternatively or additionally, the transmission can have only two third planetary gears. By providing only two planetary gears, the transmission can be more compact. The second set of planetary gears and the third set of planetary gears can therefore be simply arranged in the radial direction between the second sun gear and the second ring gear. The second planetary gears and the third planetary gears can therefore be arranged radially in a good overlapping manner, i.e., for example, at least partially on the same circumference. The transmission can, for example, have only two long planetary gears, which form the two first planetary gears and the two third planetary gears.

[0016] In one embodiment of the transmission, it can be provided that the second ring gear can be mechanically connected to the output end by means of the first clutch. Thus, the second ring gear can form the output shaft of the planetary assembly, which can be used to provide the variable to be transmitted on the output end in a switchable manner. The first clutch can be arranged coaxially with the drive end or the output end, for example. The first clutch can be arranged axially on the output side relative to the planetary assembly, for example. The first clutch can be mechanically connected to the second ring gear by means of the first spur gear stage, for example. The first spur gear stage can be designed in a single stage, for example. The first clutch can be mechanically connected to the output end by means of the third spur gear stage only or alternatively by means of the third or fourth spur gear stage, for example via an intermediate shaft. The selection of the active connection can be achieved by means of another clutch. The third spur gear stage can be designed in a single stage or in a two-stage manner, for example. The fourth spur gear stage can be designed in a single stage or in a two-stage manner, for example. The mechanical active connection via the third spur gear stage can cause the output end to rotate in the opposite direction compared to the active connection via the fourth spur gear stage.

[0017] In one embodiment of the transmission, it can be provided that the second sun gear can be mechanically connected to the driven end by means of a second clutch. Thus, the second sun gear can form the output shaft of the planetary assembly, which can be used to provide the variable to be transmitted on the driven end in a switchable manner. The second clutch can be arranged coaxially with the drive end or the driven end, for example. The second clutch can be arranged axially on the driven side relative to the planetary assembly and alternatively or additionally relative to the first clutch, for example. The first clutch can be mechanically connected to the second sun gear by means of a second spur gear stage, for example. The second spur gear stage can be constructed in a single stage, for example. The second clutch can be mechanically connected to the driven end by means of, for example, only the third spur gear stage or alternatively, the third or fourth spur gear stage, for example, via an intermediate shaft. Here, it can be the third and fourth spur gear stages and the intermediate shaft that also mechanically connect the third clutch to the driven end. However, it can also be an additional spur gear stage and an additional intermediate shaft. The selection of the active connection can be achieved by means of another clutch. The third spur gear stage can be constructed in a single stage or in a two-stage manner, for example. The fourth spur gear stage can be constructed in a single stage or in a two-stage manner, for example. The mechanical active connection via the third spur gear stage can cause the output to rotate in the opposite direction compared to the active connection via the fourth spur gear stage. The first and second spur gear stages can have the same transmission ratio. The second spur gear stage can be arranged axially on the output side relative to the first spur gear stage and the second clutch. The third spur gear stage can be arranged axially on the output side relative to the second spur gear stage. The fourth spur gear stage can be arranged axially on the output side relative to the third spur gear stage.

[0018] The first clutch and the second clutch can be constructed as a common double switching element. The double switching element can be compact and simple in structure. The double switching element can be simply operated, for example, by means of a common single actuator. The double switching element can, for example, provide as a switching state alternatively an operative connection of the switching element formed according to one of the two double switching elements, i.e., for example, an operative connection according to the closed first or second clutch. In one embodiment, the double switching element can have a neutral position. The neutral position can correspond, for example, to the disconnected first and second clutches. The first clutch and the second clutch can be nested axially or radially. The first and second clutches can be mechanically connected to the driven end together via one or alternatively via an optionally selected spur gear stage and an alternative or additional intermediate shaft.

[0019] In one embodiment of the transmission device, it can be provided that the second planet carrier can be mechanically connected to the driven end by means of a third clutch. The second planet carrier can thus form the output shaft of the planetary structure assembly, which can be used to provide the variable to be transmitted on the driven end in a switchable manner. The third clutch can, for example, be arranged coaxially with the drive end or the driven end. The third clutch can, for example, be arranged axially on the driven side relative to the planetary structure assembly and perhaps relative to the first and second clutches. The third clutch can be connected to the second planet carrier, for example, in a manner that prevents relative rotation. The third clutch can be connected to the driven end, for example, in a manner that prevents relative rotation. Accordingly, the second planet carrier can be connected to the driven end in a manner that prevents relative rotation by means of the third clutch.

[0020] In one embodiment of the transmission, it can be provided that the second sun gear can be mechanically connected to the driven end by means of a fourth clutch. Thus, the second sun gear can form the output shaft of the planetary structure assembly, and the output shaft can be used to provide the variable to be transmitted on the driven end in a switchable manner. For example, the mechanical connection of the second sun gear can be provided alternatively by means of the second and fourth clutches. The mechanical connection via the second and fourth clutches can, for example, have different transmission ratios so that an additional driving range can be provided. In the action connection by means of the second clutch, one or more spur gear stages can be provided, for example. The action connection by means of the fourth clutch can, for example, connect the second sun gear to the driven end in a rotationally fixed manner. The fourth clutch can, for example, be arranged coaxially with the drive end or the driven end. The fourth clutch can, for example, be arranged axially on the driven side relative to the planetary structure assembly and perhaps relative to the first and second and third clutches. The fourth clutch can be connected to the second planet carrier, for example, in a rotationally fixed manner. The fourth clutch can be connected to the driven end, for example, in a rotationally fixed manner.

[0021] The third clutch and the fourth clutch can be constructed as a common double shift element. The third clutch and the fourth clutch can be nested axially or radially. The third and fourth clutches can be mechanically connected to the driven end via one or alternatively via an optionally selected spur gear stage and an alternative or additional intermediate shaft.

[0022] In one embodiment of the transmission, it can be provided that the transmission has a driving direction change component, which is configured to change the rotation direction of the driven end relative to the rotation direction of the driving end in at least one driving range of the transmission. In this way, for example, the driving direction can be adjusted. For this purpose, the driving direction change component can, for example, have at least one switching element and a spur gear stage or a planetary gear set. The driving direction change component can be arranged on the drive side, for example. In the case of the drive side arrangement, the drive end can be mechanically connected to the first ring gear by means of the driving direction change component, for example. In the case of the drive side arrangement, the torque acting on the driving direction change component and in particular its switching element is small. In the case of the driven end side arrangement, the planetary component can be mechanically connected to the driven end by means of the driving direction change component, for example. In the case of the driven end side arrangement, the driving direction change component can be more easily integrated into the transmission if necessary. In the case where the driving direction change component is arranged on the driven end side or the driving side, the driving direction change component can be configured to provide all forward driving ranges as reverse driving ranges. In the case of an arrangement on the output side, the first, second, third and fourth clutches can be mechanically connected to the output via the driving direction change component. In contrast, in the case of a nested arrangement, the load advantage of the driving direction change component can be achieved, but the full forward and reverse driving ranges may not be available.

[0023] In one embodiment of the transmission, it can be provided that the driving direction change assembly has a single-stage first spur gear stage, a double-stage second spur gear stage, a first clutch and a second clutch. The drive end can be mechanically connected to the output end in at least one driving range by means of the first clutch of the driving direction change assembly via the single-stage first spur gear stage and in at least another driving range by means of the second clutch of the driving direction change assembly via the double-stage second spur gear stage. The respective clutches and spur gear stages of the driving direction change assembly can be clutches different from the first to fourth clutches and spur gear stages described above, which are used to connect the respective output shafts of the planetary assembly to the output end.

[0024] For example, an operative connection can be established by means of the first clutch of the driving direction change assembly via the first spur gear stage to provide the respective forward driving range. For example, an operative connection can be established by means of the second clutch of the driving direction change assembly via the second spur gear stage to provide the respective reverse driving range. The respective clutch of the driving direction change assembly can be arranged coaxially with the drive end or the driven end. In the case of a coaxial arrangement with the drive end, the pressure oil supply can be simpler. For example, the pressure oil supply from the housing via the first sun gear to the hollow shaft of the first ring gear, which may be necessary in the case of a coaxial arrangement with the planetary assembly, can be omitted.

[0025] The first and second clutches of the driving direction change assembly can be designed as a common double shift element. The first and second clutches of the driving direction change assembly can be nested axially or radially. The first and second clutches of the driving direction change assembly can be mechanically connected to the output end jointly via one or alternatively via an optionally selected spur gear stage and an alternative or additional intermediate shaft.

[0026] The respective clutch of the driving direction change assembly can be arranged coaxially with the planetary assembly. Thus, for example, a common part of the first and second clutches connecting the output shaft of the planetary assembly to the output end can be used in the clutch. The first and second clutches can be designed as common parts, for example, with the first and second clutches of the driving direction change assembly.

[0027] The first and second clutches of the driving direction change assembly can be arranged axially between the respective assigned spur gear stages. The first clutch of the driving direction change assembly can be arranged axially on the drive side or the driven side relative to the second clutch of the driving direction change assembly, for example. When the clutches assigned to the same are arranged, the respective assigned spur gear stages of the two clutches of the driving direction change assembly can be arranged axially opposite to the other clutch of the driving direction change assembly. The first spur gear stage of the driving direction change assembly can be arranged axially on the drive side relative to the first clutch of the driving direction change assembly, the first clutch of the driving direction change assembly can be arranged axially on the drive side relative to the second clutch of the driving direction change assembly, and the second spur gear stage of the driving direction change assembly can be arranged axially on the driven side relative to the second clutch of the driving direction change assembly. This axial arrangement scheme can also be reversed, for example.

[0028] In one embodiment of the transmission device, it can be provided that the second ring gear can be mechanically connected to the driven end via the first clutch by means of a driving direction change component. The second sun gear can be mechanically connected to the driven end via the second clutch by means of a driving direction change component. The second planet carrier can be connected to the driven end with the help of a third clutch to prevent relative rotation. The second sun gear can be connected to the driven end with the help of a fourth clutch to prevent relative rotation. In this nested arrangement, for example, the driving range that can only be provided by the closed first and second clutches can be provided not only as a reverse driving range but also as a forward driving range. For example, only two reverse driving ranges can therefore be adjusted. The driving direction change component can therefore be arranged axially on the driven side, but despite this, it is only loaded with a smaller torque than, for example, an arrangement on the other driven end side.

[0029] In one embodiment of the transmission device, it can be provided that the second ring gear can be connected to the intermediate shaft in a rotationally fixed manner by means of the first clutch. The second sun gear can be connected to the intermediate shaft in a rotationally fixed manner by means of the second clutch. The intermediate shaft can be mechanically connected to the driven end by means of the fourth clutch. This design allows the first to fourth clutches to be arranged coaxially with the planetary structure assembly. The first to fourth clutches can be formed together with the planetary structure assembly as planetary rollers.

[0030] In one embodiment of the transmission, it can be provided that the transmission has a third sun gear, a third planetary carrier and a third ring gear, which form a third planetary gear set. The respective planetary gears can be rotatably supported on the third planetary carrier. The transmission can have a brake. The intermediate shaft can be connected to the third planetary carrier by means of a fourth clutch in a manner that prevents relative rotation. The second planetary carrier can be connected to the third planetary carrier by means of a third clutch in a manner that prevents relative rotation. The intermediate shaft can be connected to the third sun gear permanently in a manner that prevents relative rotation. The third ring gear can be fixed to a stationary component by means of a brake. The third planetary carrier can be connected to the driven end permanently in a manner that prevents relative rotation. Therefore, the third planetary gear set and the brake can provide another driving range. In addition, the third planetary gear set can also be constructed as part of a planetary roller. The third planetary gear set can be constructed as a negative planetary gear set. The brake can be constructed as a switching element of a form lock or a friction lock. The component can be fixed by means of a brake so that it can no longer rotate. The stationary component can be, for example, a component that does not move relative to the rotating element of the respective planetary gear set. The stationary component can be constructed as a housing, for example.

[0031] In addition, a synergistic effect is achieved when the electric motor is used as part of a variator, which is mechanically connected to the drive end. The electric motor can, for example, replace a hydraulic machine with a variable fluid intake per revolution. The driven end can be driven purely electrically. For this purpose, for example, in the case where the driving direction change structural component is arranged on the drive side, the first and second clutches of the driving direction change structural component are closed. They thus lock the first ring gear, thereby making the first sun gear form the input shaft of the planetary structural component. In addition, the driving range can be provided by closing at least one other switching element, such as the first or second clutch and an additional brake, so that the torque can be transmitted to the driven end. In addition, the electric motor may require an external energy supply, such as a battery. In order to ensure the supply of lubricating and cooling oil, an electrically driven pump can be provided. It can take over the supply of lubricating and cooling oil when the motor connected to the drive end is stopped.

[0032] In one embodiment of the transmission, it can be provided that the planetary assembly has a central shaft for the lubricating oil supply. The central shaft can be designed, for example, as a solid shaft, which has respective lubricating oil channels. The central shaft can be connected to the first sun gear, for example, in a permanently rotationally fixed manner, or can be formed by the first sun gear. Such a central shaft can be supported in a particularly simple manner. The central shaft can be connected to the second planet carrier, for example, in a permanently rotationally fixed manner, or can be formed by the second planet carrier. The second planet carrier can always rotate in all driving ranges when the motor is running, thereby facilitating the lubricating oil supply.

[0033] In one embodiment of the transmission, it can be provided that the fixed-shaft transmission ratio of the first planetary gear set is -2.7 to -3. In addition, the fixed-shaft transmission ratio of the second planetary gear set can be -3.5 to -3.8. The layout of the planetary structure assembly with the first and second planetary gear sets requires complex coordination. The fixed-shaft transmission ratio can achieve excellent transmission ratio ratio values ​​of the transmission device under high efficiency. The fixed-shaft transmission ratio of the first planetary gear set -2.83 and the fixed-shaft transmission ratio of the second planetary gear set -3.6 are very suitable. It is precisely in the design of the planetary structure assembly with only two first planetary gears, two second planetary gears and three third planetary gears that favorable coordination is obtained. The appropriate number of teeth, alternative or additional modules of the respective gears of the planetary structure assembly are disclosed in the front cross-sectional view of the first planetary gear set and the second planetary gear set.

[0034] In order to engage the driving range and control the various clutches and brakes, the transmission can have a control device designed for this purpose. The control device can be designed and set up to control the respective states of the clutches and brakes. The control device can have respective actuators for this purpose and alternatively or additionally have a position sensor and alternatively or additionally have a rotational speed sensor.

[0035] A second aspect relates to a drive unit having a power split continuously variable transmission according to the first aspect. The drive unit has a motor, which is mechanically connected to a drive end for driving the drive end. The motor can be, for example, an internal combustion engine. The drive unit can be used to drive the motor at a substantially constant speed. The respective driving speed and the optional driving direction can be controlled, for example, by means of a selected driving range and a variator. Another aspect relates to a working machine having a power split continuously variable transmission according to the first aspect and a drive unit according to the second aspect. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 A schematic view showing a transmission according to a first embodiment;

[0037] Figure 2 Show according to Figure 1 The switching matrix of the transmission device;

[0038] Figure 3 A schematic perspective view showing a long planet gear;

[0039] Figure 4 A front section view through the second planetary gear set of the transmission is shown;

[0040] Figure 5 A front section view through a first planetary gear set of the transmission is shown;

[0041] Figure 6 A schematic view showing a transmission according to a second embodiment;

[0042] Figure 7 A schematic view showing a transmission according to a third embodiment;

[0043] Figure 8 A schematic view showing a transmission according to a fourth embodiment;

[0044] Fig. 9 A schematic view showing a transmission according to a fifth embodiment;

[0045] Fig.10 A schematic view showing a transmission according to a sixth embodiment;

[0046] Fig.11 A schematic view showing a transmission according to a seventh embodiment;

[0047] Fig.12 A schematic view showing a transmission according to an eighth embodiment;

[0048] Fig.13 Show according to Figure 2 The switching matrix of the transmission device;

[0049] Fig.14 A schematic view showing a transmission according to a ninth embodiment;

[0050] Fig.15 A schematic view showing a transmission according to a tenth embodiment;

[0051] Fig.16 A schematic view showing a transmission according to an eleventh embodiment;

[0052] Fig.17 A schematic view showing a transmission according to a twelfth embodiment;

[0053] Fig.18 A schematic diagram of a transmission according to a thirteenth embodiment is shown. DETAILED DESCRIPTION

[0054] Figure 1 A first embodiment of a power split continuously variable transmission 100 is shown in a schematic view, which has a drive end 12, a driven end 14, a variator 16 and a planetary assembly 18. The planetary assembly 18 has two planetary gear sets and is used to provide different driving ranges. The drive end 12 is operatively connected to the motor. The transmission 100 has a drive shaft, which extends through the transmission 100. At the driven end side end, the drive shaft forms a power output shaft 20. The driven shaft 14 is arranged parallel to the drive shaft 12 axis and can be operatively connected to a differential, for example.

[0055] In the present case, the planetary assembly 18 is designed as a planetary roller.

[0056] The first planetary gear set is formed by the first sun gear 30, the first planet carrier 32 and the first ring gear 34. A set of first planetary gears 36 are rotatably supported on the first planet carrier 32. The second planetary gear set of the planetary assembly 18 is formed by the second sun gear 40, the second planet carrier 42 and the second ring gear 44. A set of second planetary gears 46 and a set of third planetary gears 48 are rotatably supported on the second planet carrier 42. The second planetary gears 46 (which mesh with the second sun gear 40, the second ring gear 44 and the third planetary gears 48) have a larger pitch circle diameter and a shorter axial length than the third planetary gears 48. The pitch circle diameter of a gear is the tooth diameter defined in the literature. This diameter describes the average diameter of the tooth.

[0057] The first planet carrier 32 and the second planet carrier 42 are permanently connected to each other in a rotationally fixed manner. The first planet gear 36 meshes with the first sun gear 30 and the first ring gear 34. Figure 5 The first planetary gear set is shown in a front cross-sectional view. Figure 5It is also shown that the set of first planet gears 36 has only two first planet gears 36 .

[0058] The second planetary gear 46 meshes with the second sun gear 40 and the second ring gear 44. The second planetary gear 46 and the third planetary gear 48 mesh with each other in pairs. Figure 4 4. The second planetary gear set of FIG. 4 is shown in a front cross-sectional view of FIG. It can be seen here that the second planetary gear 46 in a group and the third planetary gear 48 in a group each have only two gears. The second planetary gear 46 has a larger effective diameter than the third planetary gear 48. The first planetary gear 36 and the third planetary gear 48 have the same effective diameter. The second and third planetary gears 46, 48 are arranged side by side in the circumferential direction. The axis of rotation of the second planetary gear 46 and the axis of rotation of the third planetary gear 48 are arranged on the same circumference. However, they can also be arranged on different circumferences and therefore arranged radially spaced from the middle axis.

[0059] The first planetary gear 36 and the third planetary gear 48 are respectively connected to each other in pairs in a permanent rotationally fixed manner. In the transmission 100, for this purpose, the first and third planetary gears 48 are respectively configured as common long planetary gears in pairs, such as Figure 3 As shown. In the illustrated embodiment, the long planet gear is integrally formed, wherein the respective toothings at its two end regions are constructed identically. These toothings at the respective end regions can be manufactured together on a clamp, for example. The toothless middle region can be manufactured before the toothings are manufactured. The toothing of the long planet gear at one end region meshes with the first sun gear 30 and the first ring gear 34. The toothing of the long planet gear at the opposite end region meshes with one of the second planet gears 46. Based on the long planet gear, the transmission has a total of only four planetary gear components, namely two long planet gears and two second planet gears 46. As Figure 3 As shown, the long planet gears can be designed as spur-tooth planet gears, but there is also the possibility of designing the long planet gears as helical-tooth planet gears.

[0060] At least for the transmission device 100, according to Figure 4 and Figure 5 The front section of the toothing is at least proportional with respect to the respective tooth parameters. Figure 4 and Figure 5 In FIG. 1 , the modules and the numbers of teeth of the elements of the two planetary gear sets are to scale and are shown correctly with respect to their number.

[0061] The variator 16 has a first energy converter 80 and a second energy converter 82, which are coupled to each other. The two energy converters 80, 82 are configured as hydraulic machines, wherein the first energy converter 80 has a fixed fluid intake per revolution and the second energy converter 82 has a variable fluid intake per revolution. The first energy converter 80 is mechanically connected to the first sun gear 30 in order to transmit torque between the first sun gear 30 and the energy converter 80 and thus the variator 16. In the illustrated embodiment, the connection is indirect, i.e., by means of a single-stage spur gear stage 84. One of the spur gears is connected to the shaft of the first energy converter 80 in a rotationally fixed manner. The other spur gear is connected to the first sun gear 30 in a rotationally fixed manner. Here, the spur gear stage 84 is arranged axially on the drive side relative to the planetary assembly 18. The second energy converter 82 is mechanically connected to the drive end 12 in order to transmit torque between the drive end 12 and the second energy converter 82 and thus the variator 16. In the illustrated embodiment, the connection is indirect, i.e., by means of a single-stage spur gear stage 86. The spur gear stage 86 is arranged axially on the driven side, specifically at the level of the power output shaft 20 and thus on the driven side relative to the planetary assembly 18. The spur gear stage 86 is formed by two meshing spur gears, one of which is designed as a fixed gear and is connected to the shaft of the second energy converter 82 in a rotationally fixed manner. The other spur gear is designed as a counter gear and is permanently connected to the drive end 12 in a rotationally fixed manner.

[0062] The drive end 12 is mechanically connected to the first ring gear 34 via a driving direction change assembly 50. The driving direction change assembly 50 has a first clutch KV and a second clutch KR. The two clutches KV and KR are arranged coaxially with the drive end 12 and are directly connected to the drive end. The drive end 12 is mechanically connected to the first ring gear 34 via a single-stage spur gear stage 52 by means of the clutch KV. One gear of the spur gear stage 52 is permanently connected to the first ring gear 34 in a rotationally fixed manner, while another gear of the spur gear stage 52 can be connected to the drive end 12 in a rotationally fixed manner. The spur gear stage 50 is axially arranged between the spur gear stage 84 and the first planetary gear set. The drive end 12 is mechanically connected to the first ring gear 34 via a double-stage spur gear stage 54 by means of the clutch KR. The fixed gear of the spur gear stage 54 is permanently connected to the first ring gear 34 in a rotationally fixed manner, while another gear can be mechanically connected to the drive end 12 by means of the clutch KR. A further gear wheel of the spur gear stage 54 is arranged radially between the two gear wheels and meshes with the two gear wheels.

[0063] The spur gear stage 54 of the driving direction change assembly 50 is arranged axially on the driven side relative to the spur gear stage 84 that mechanically connects the variator 16 to the first sun gear. The clutch KR is arranged axially on the driven side relative to the spur gear stage 54. The clutch KV is arranged axially on the driven side relative to the clutch KR. The clutch KV and the clutch KR are nested axially and form a double shift element. The spur gear stage 52 is arranged axially on the driven side relative to the clutch KV, and the clutch KV is arranged axially on the drive side relative to the first planetary gear set.

[0064] The transmission 100 is configured to transmit torque from the second planetary gear set to the output 14. For this purpose, the second sun gear 40 forms the output shaft of the planetary assembly 18 and is connected to the friction-locked fourth clutch K4. With the help of the fourth clutch K4, the second sun gear 40 can be connected to the output 14 in a rotationally fixed manner. The second planet carrier 42 forms another output shaft of the planetary assembly 18 and is connected to the friction-locked third clutch K3. With the help of the third clutch K3, the second planet carrier 42 can be connected to the output 14 in a rotationally fixed manner. The third and fourth clutches K3, K4 are axially nested and arranged coaxially with the drive end 14. The third and fourth clutches K3, K4 form a double shift element. The third clutch K3 is axially arranged on the drive side relative to the spur gear stage 86 that connects the variator 16 to the drive end 12. The fourth clutch K4 is axially arranged on the driven side relative to the third clutch K3.

[0065] The second ring gear 44 forms a further output shaft of the planetary assembly 18. The second ring gear 44 is mechanically connected to the friction-locking first clutch K1 via a single-stage first spur gear stage 60. For this purpose, a gear of the first spur gear stage 60 is permanently connected in a rotationally fixed manner to the second ring gear 44 and another gear of the first spur gear stage 60 is permanently connected in a rotationally fixed manner to the first clutch K1. The first spur gear stage 60 is operatively connected to the intermediate shaft 70 by means of the first clutch K1. The intermediate shaft 70 is mechanically connected to the output 14 by means of the third spur gear stage 64. The intermediate shaft 70 is arranged coaxially with the drive 12. A gear of the third spur gear stage 64 is permanently connected in a rotationally fixed manner to the intermediate shaft 70 and another gear of the third spur gear stage 64 is permanently connected in a rotationally fixed manner to the output 14. Accordingly, the second ring gear 44 is mechanically connected to the output 14 by means of the first clutch K1 via the first spur gear stage 60 and the third spur gear stage 64.

[0066] The second sun gear 40 as the output shaft of the planetary assembly 18 can also be mechanically connected to the output 14 by means of the friction-locking second clutch K2. One gear of the single-stage second spur gear stage 62 is permanently connected to the second sun gear 40 in a rotationally fixed manner, while another gear of the second spur gear stage 62 is permanently connected to the second clutch K2 in a rotationally fixed manner. The second spur gear stage 62 can be connected to the intermediate shaft 70 by means of the second clutch K2. Accordingly, the second sun gear 40 can be operatively connected to the output 14 via the second spur gear stage 62, and the intermediate shaft 70 and the third spur gear stage 70 can be operatively connected by means of the second clutch K2.

[0067] The first spur gear stage 60 is arranged axially on the driven side relative to the second planetary gear set and axially on the drive side relative to the first clutch K1. The first clutch K1 is arranged axially on the drive side relative to the second clutch K2. The first and second clutches K1, K2 are arranged coaxially with the drive end 12 and are nested axially. The first and second clutches K1, K2 form a double shift element. The second spur gear stage 62 is arranged axially on the driven side relative to the second clutch K2 and axially on the drive side relative to the fourth clutch K4. The third spur gear stage 64 is arranged axially on the driven side relative to the third clutch K3 and axially on the drive side relative to the spur gear stage 86 that mechanically connects the variator 16 to the drive end 12.

[0068] The friction clutches K1, K2, K3, K4, KV and KR are designed as diaphragm clutches. The respective double shifting elements allow the provision of an active connection optionally by means of one of the two clutches forming them. In one embodiment of the double shifting element, it also allows the provision of a neutral position.

[0069] Figure 2 Show according to Figure 1The switching matrix of the transmission 100 of FIG. The corresponding columns show the switching states of the corresponding switchable elements. The transmission 100 has four forward driving ranges, which are represented by FB1, FB2, FB3 and FB4. The driving ranges are numbered in order of their maximum speeds. That is, the driving range FB2 can achieve a higher speed than the driving range FB1, and the driving range FB3 has a higher speed than FB1 and FB2. FB4 is the fastest forward driving range. The transmission 100 also has four reverse driving ranges FB1R, FB2R, FB3R and FB4R. The driving range FB4R is the fastest reverse driving range, and the order of speed is similar to the forward driving range. The speed range is shown next to the column indicating the driving range. The driving ranges FB1 and FB1R start at 0 km / h. At the limit speed A, it is possible to switch between the driving range FB1 and the driving range FB2. The same applies to the subsequent driving ranges and their maximum or minimum speeds. The driving speed in the reverse driving range is the same as the driving speed in the forward driving range, but the output 14 rotates in the opposite direction while the direction of rotation of the drive 12 remains unchanged.

[0070] The forward driving range is provided in principle by the closed clutch KV of the driving direction change component 50. The reverse driving range is provided in principle by the closed clutch KR of the driving direction change component 50. The driving range FB1 is provided by the additionally closed first clutch K1. The driving range FB2 is provided by the additionally closed second clutch K1. The driving range FB3 is provided by the additionally closed third clutch K3. The driving range FB4 is provided by the additionally closed fourth clutch K4. The reverse driving range is provided by the respective closed clutches identical to the forward driving ranges with the same number, wherein for this purpose, the clutch KR is closed instead of the clutch KV of the driving direction change component 50. The transmission 100 can provide four forward driving ranges and four reverse driving ranges with less mechanical effort. The subsequent driving ranges can be switched by connecting and disconnecting the clutches.

[0071] In the transmission device 100 , the fixed shaft transmission ratio of the first planetary gear set is −2.9, and the fixed shaft transmission ratio of the second planetary gear set is −3.7.

[0072] The further figures show further embodiments of the power split continuously variable transmission. Here, only the respectively relevant differences from the respective other embodiments are discussed. Therefore, components with the same function and also with the same design have the same reference numerals and are not further described. The switching matrix also applies to the further embodiments, unless otherwise stated. The respective differences can also be combined with one another in other embodiments. Fig.12 The additional planetary gear set and the additional brake of the transmission can also be combined with the additional planetary gear set according to Figure 6 and Figure 7 A system combination of driving direction changing components of a transmission.

[0073] Figure 6 A second embodiment of a transmission 200 is shown. This embodiment differs from the transmission 100 in that the axial positioning of the clutches KV and KR and the spur gear stages 52 and 54 of the driving direction change assembly 50 is interchanged. The clutch KV is now arranged axially on the drive side relative to the clutch KR. The two-stage spur gear stage 54 is now arranged axially on the output side relative to the clutch KR. The single-stage spur gear stage 52 is now arranged axially on the drive side relative to the clutch KV.

[0074] Figure 7 A third embodiment of a transmission 300 is shown. This embodiment differs from the transmission 100 primarily in the positioning of the clutches KV, KR of the driving direction change assembly 50. In the transmission 300, the two clutches KV, KR are arranged coaxially with the output 14 and thus with the planetary assembly 18. Accordingly, the clutch KR is connected to the drive end 12 by means of a two-stage spur gear stage 54. The fixed gear of the spur gear stage 54 is thus permanently connected to the drive end 12 in a rotationally fixed manner. Accordingly, the clutch KV is connected to the drive end 12 by means of a single-stage spur gear stage 52. The fixed gear of the spur gear stage 52 is thus permanently connected to the drive end 12 in a rotationally fixed manner. The axial arrangement of the components of the driving direction change assembly 50 corresponds to the axial arrangement of the transmission 100.

[0075] Due to the arrangement of the driving direction change assembly 50 in the transmission 300, its respective clutches KV, KR have a plurality of common parts compared to the dual shift element (which is formed by the first and second clutches K1, K2). In addition, the respective clutches KV, KR of the driving direction change assembly 50 are subjected to a smaller torque and are smaller in design than the corresponding clutches KV, KR in the transmission 100. In the transmission 300, compared to the transmission 100, an additional pressure oil supply to the clutches KV, KR of the driving direction change assembly 50 is provided. In the transmission 300, the additional pressure oil supply extends through the housing, the central shaft of the first sun gear 30 and the hollow shaft of the first ring gear 34.

[0076] Figure 8 A fourth embodiment of a transmission 400 is shown. This embodiment differs from the transmission 300 in the positioning of the clutches KV, KR and the spur gear stages 52 and 54 of the direction-of-travel change assembly 50. These are positioned identically to those in the transmission 200, so that the descriptions there also apply to the transmission 400.

[0077] Fig. 9 A fifth embodiment of a transmission 500 is shown. This embodiment shows that the driving direction change assembly is connected on the output side instead of on the drive side.

[0078] In the transmission 500, the drive end 12 is mechanically connected to the first ring gear 34 by means of a spur gear stage 502. One gear of the spur gear stage 502 is permanently connected to the drive end 12 in a rotationally fixed manner, and another gear of the spur gear stage 502 is connected to the first ring gear 34. The spur gear stage 502 is axially arranged on the driven side relative to the spur gear stage 84 that mechanically connects the variator 16 to the first sun gear 30. The spur gear stage 502 is axially arranged on the drive side relative to the first planetary gear set.

[0079] The clutches KV and KR of the driving direction change assembly are arranged coaxially with the output 14 and the planetary assembly 18. The second planet carrier 42 can be connected to another intermediate shaft 504 in a rotationally fixed manner in the transmission 500 by means of the third clutch K3. The second sun gear 40 can be connected to another intermediate shaft 504 in a rotationally fixed manner in the transmission 500 by means of the fourth clutch K4. The intermediate shaft 504 can be connected to the output 14 in a rotationally fixed manner by means of the clutch KV of the driving direction change assembly. The second planet carrier 42 can therefore be connected to the output 14 in a rotationally fixed manner via the third clutch K3 and the clutch KV.

[0080] In the transmission 500, the single-stage spur gear stage 52 forms a mechanical operative connection between the countershaft 70 and the further countershaft 504. One gear of the single-stage spur gear stage 52 is permanently connected to the countershaft 70 in a rotationally fixed manner, and the other gear is connected to the further countershaft 504. Thus, the second ring gear 44 can be mechanically operatively connected to the output via the first spur gear stage 60, the first clutch K1, the countershaft 70, the single-stage spur gear stage 52, the further countershaft 504 and the clutch KV. Thus, the second sun gear 40 can be mechanically operatively connected to the output via the second spur gear stage 60, the second clutch K2, the countershaft 70, the spur gear stage 52, the further countershaft 504 and the clutch KV. One gear of the double-stage spur gear stage 54 is permanently connected to the countershaft 70 in a rotationally fixed manner. The other gear of the double-stage spur gear stage 54 is connected to the clutch K3 of the driving direction change assembly.

[0081] In the transmission 500, the single-stage spur gear stage 52 and the double-stage spur gear stage 54 replace the third spur gear stage 64, wherein the drive end 12 is additionally connected via the spur gear stage 502. Here, the operative connection can be selectively adjusted to provide a corresponding forward driving range and reverse driving range.

[0082] The single-stage spur gear stage 52 is arranged on the driven side relative to the third clutch K3. The clutch KV is arranged on the driven side relative to the single-stage spur gear stage 52. Between the single-stage spur gear stage 52 and the clutch KV, another intermediate shaft 504 is arranged coaxially with the driven end 14. The clutch KR is arranged on the driven side relative to the clutch KV. The double-stage spur gear stage 54 is arranged on the driven side relative to the clutch KR.

[0083] The so-called power reversal of the driven machine can be improved by the design of the transmission 500. The driven machine can travel forward and, when changing from forward travel to reverse travel, use the clutch KV or KR in order to reverse the drive power of the motor connected to the drive end 12. This can cause a rotation direction at the output end 14 that is opposite to the current driving direction. The clutches KV and KR of the driving direction change assembly 50 in the transmission 500 are subjected to higher torques than in the transmission 100 and are therefore larger.

[0084] Fig.10 A sixth embodiment of a transmission 600 is shown. In this embodiment, only two reverse driving ranges are provided. Here, the driving direction change assembly 500 is implemented according to an intermediate arrangement.

[0085] The clutch KV of the driving direction change assembly 50 is connected to the intermediate shaft 70. The clutch KV is connected to the output 14 via the associated single-stage spur gear stage 52. Accordingly, one gear of the single-stage spur gear stage 52 is permanently connected to the output 14 in a rotationally fixed manner, and the other gear of the single-stage spur gear stage 52 can be connected to the intermediate shaft 70 by means of the clutch KV.

[0086] The clutch KR of the driving direction change assembly 50 is connected to the intermediate shaft 70. The clutch KR is connected to the output 14 via the associated double-stage spur gear stage 54. Accordingly, one gear of the double-stage spur gear stage 54 is permanently connected to the output 14 in a rotationally fixed manner, and the other gear of the double-stage spur gear stage 54 can be connected to the intermediate shaft 70 by means of the clutch KR.

[0087] Therefore, the first and second clutches K1 and K2 can be mechanically connected to the output end 14 by means of the clutch KV of the driving direction change component 50, so as to provide the variable to be transmitted as the forward driving range. Therefore, the first and second clutches K1 and K2 can be mechanically connected to the output end 14 by means of the clutch KR of the driving direction change component 50, so as to provide the variable to be transmitted as the reverse driving range. Accordingly, the transmission device 600 can provide the reverse driving ranges FB1R and FB2R.

[0088] In contrast, the third and fourth clutches K3 and K4 are directly connected to the output 14. In addition, the drive end 12 is mechanically connected to the first ring gear 34 by means of the spur gear stage 602. The rotation direction of the driving ranges provided by the third and fourth clutches K3 and K4 respectively cannot be reversed at the output 14 in the transmission 600. Accordingly, although the forward driving ranges FB3 and FB4 are provided in the transmission 600, the corresponding reverse driving ranges FB3R and FB4R are not provided.

[0089] The driving direction change assembly 50 is located on the output side, but is only connected to the first and second clutches K1, K2. As a result, the driving direction change assembly 50 is subjected to a smaller torque than, for example, the transmission 500, so the clutches KV and KR are smaller. For this reason, however, there are only two reverse driving ranges.

[0090] The spur gear stage 602 is arranged axially between the spur gear stage 84 that mechanically connects the variator 16 to the first sun gear 30 and the first planetary gear set. One gear of the spur gear stage 602 is permanently connected to the first ring gear 34 in a rotationally fixed manner, and another gear of the spur gear stage 602 is permanently connected to the drive end 12 in a rotationally fixed manner. The clutches KV and KR of the driving direction change assembly 50 are arranged coaxially with the drive end 12. The single-stage spur gear stage 52 is arranged axially on the output side relative to the third clutch K3 and axially on the drive side relative to the clutch KV. The clutch KR is arranged axially on the output side relative to the clutch KV. The double-stage spur gear stage 54 is arranged axially on the output side relative to the clutch KR and axially on the drive side relative to the spur gear stage 86 that connects the variator 16 to the drive end 12. In the transmission 600 , the spur gear stages 52 , 54 of the driving direction change assembly 50 replace the transmission of action by means of the third spur gear stage 64 according to the transmission 100 .

[0091] Fig.11 A seventh embodiment of a transmission 700 is shown. This embodiment is based on the transmission 600, but the KV / KR spur gear train is replaced. The transmission 700 differs from the transmission 600 in the same way as the transmission 200 differs from the transmission 100, whereby the axial positioning of the clutches KV and KR and the spur gear stages 52, 54 of the direction change assembly 50 is reversed.

[0092] In the transmission 700, the double-stage spur gear stage 54 is axially arranged on the output side relative to the third clutch K3 of the driving direction change assembly 50 and axially arranged on the drive side relative to the clutch KR. The clutch KR is axially arranged on the drive side relative to the clutch KV of the driving direction change assembly 50. The single-stage spur gear stage 52 is axially arranged on the output side relative to the clutch KV and axially arranged on the drive side relative to the spur gear stage 86 that mechanically connects the variator 16 to the drive end 12.

[0093] Fig.12 The eighth embodiment of the transmission 800 is shown. This embodiment differs from the first embodiment in the structure and arrangement of the respective clutches K1, K2, K3, K4, so that these clutches are described in full despite their respective commonalities. In addition, the transmission 800 has an additional third planetary gear set and a brake B, and the third planetary gear set together with the planetary structural assembly 18 forms a planetary roller. The connection method of the changer 16 and the driving direction change structural assembly 50 is the same as the connection method in the transmission 100, and therefore no further description is given here. In the transmission 800, the fixed shaft transmission ratio of the first planetary gear set is -2.78, the fixed shaft transmission ratio of the second planetary gear set is -3.60, and the fixed shaft transmission ratio of the third planetary gear set is -3.60. The fixed shaft transmission ratios of the second and third planetary gear sets are the same

[0094] The second ring gear 44 can be connected to the intermediate shaft 70 in a rotationally fixed manner by means of the first clutch K1, wherein the intermediate shaft 70 is arranged coaxially with the output 14 in the transmission 800. The second sun gear 40 can be connected to the intermediate shaft 70 in a rotationally fixed manner by means of the second clutch K2. The first clutch K1 and the second clutch K2 are again configured as double shift elements, but are radially nested in the transmission 800 and are configured coaxially with the output 14 and the planetary assembly 18. The first clutch K1 is arranged radially outside the second clutch K2. The intermediate shaft 70 can be mechanically connected to the output 14 by means of the fourth clutch K4.

[0095] The fourth clutch K4 is axially arranged on the driven side relative to the first and second clutches K1, K2. The first and second clutches K1, K2 are axially arranged on the driven side relative to the planetary assembly 18. The intermediate shaft 70 extends axially from the first and second clutches K1, K2 to the fourth clutch K4.

[0096] The transmission device 800 has a central shaft for lubricating oil supply, which is formed by the first sun gear 30 in the transmission device 800. The other parts of the planetary rollers are supported on the central shaft. By using the first sun gear 30 as the central shaft, the central shaft is simply supported.

[0097] The transmission device 800 has a third sun gear 850, a third planet carrier 852 and a third ring gear 854, which form a third planetary gear set. The respective planet gears 856 are rotatably supported on the third planet carrier 852. The third ring gear 854 can be fixed to a stationary component by means of a brake B. The intermediate shaft 70 and the third planet carrier 852 can be connected to each other in a rotationally fixed manner by means of a fourth clutch K4. The second planet carrier 42 can be connected to the third planet carrier 852 in a rotationally fixed manner via a hollow shaft 858 by means of a third clutch K3. The hollow shaft 858 is arranged radially outside the intermediate shaft 70. The intermediate shaft 70 is permanently connected to the third sun gear 850 in a rotationally fixed manner. The third planet carrier 852 is permanently connected to the driven end in a rotationally fixed manner.

[0098] The third planetary gear set is configured as a negative planetary gear set. The respective planetary gears 856 of the third planetary gear set mesh with the third sun gear 850 and the third ring gear 854 .

[0099] The third and fourth clutches K3, K4 are again constructed as double shift elements, wherein they are radially nested in the transmission 800. The third and fourth clutches K3, K4 are arranged axially on the drive side relative to the third planetary gear set. The third clutch K3 is arranged radially on the outside relative to the fourth clutch K3. The brake B is arranged axially on the driven side relative to the third ring gear 854 and axially on the drive side relative to the spur gear stage 86 that mechanically connects the variator 16 to the drive end 12.

[0100] The transmission 800 is extended by the third planetary gear set and the brake B compared to the transmission 100. In the transmission 800, a higher final speed is achieved in the respective forward driving range. In the transmission 800, the respective reverse driving ranges are not completely mirrored with respect to their speeds. In the embodiment shown, the reverse driving ranges each have a lower final speed than the corresponding forward driving ranges. As a result, a higher torque can be provided in the reverse driving range.

[0101] In the transmission 800, the driving direction change assembly 50 is arranged on the drive side, as in the transmission 100. As a result, the clutches KV and KR are loaded with relatively small torques and can be very small. High torques only load the third planetary gear set, which is optimal for component optimization. Larger shafts and gears required for higher torques can be provided there.

[0102] Fig.13 Show according to Fig.12 The basic structure of the switching matrix is ​​similar to Figure 2The switching matrix and the classification and labeling of the various motion ranges are the same. The respective speeds marked with double lines are smaller than the corresponding speeds marked with single lines. The maximum speed A" of the reverse driving range FB1R of the transmission 800 is slower than the maximum speed A' of the forward driving range FB1. The speeds marked with single lines are smaller than the speeds marked with single lines. Figure 2 The speed of the double-line marking is higher than that of the non-line marking in the switching matrix. Figure 2 The speeds A of FB1 and FB1R in transmission 100 are slower than the speed A′ of FB1 of transmission 800 and faster than the speed A″ of FB1R of transmission 800 .

[0103] In the transmission 800, each driving range is provided by three closed shifting elements. Driving range FB1 is provided by a closed first clutch K1, a closed brake B and a closed clutch KV. Driving range FB2 is provided by a closed second clutch K2, a closed brake B and a closed clutch KV. Driving range FB3 is provided by a closed second clutch K2, a closed third clutch K3 and a closed clutch KV. Driving range FB4 is provided by a closed second clutch K2, a fourth clutch and a closed clutch KV. Reverse driving ranges FB1R to FB4R are provided by using a closed clutch KR instead of a closed clutch KV, and the others are provided by the same closed shifting elements. In the transmission 800, only one shifting element is connected and one shifting element is disconnected each time the continuous driving ranges are changed.

[0104] Fig.14 A ninth embodiment of the transmission device 900 is shown. Fig.12 The eighth implementation method is based on Fig.13 The switching matrix of applies to the transmission 900 in the same manner.

[0105] The transmission 900 differs from the transmission 800 in its central shaft for the lubricating oil supply. In the transmission 800, the central shaft is permanently connected to the second planet carrier 42 and thus also to the first planet carrier 32 in a rotationally fixed manner in that the central shaft is formed by the second planet carrier 42. The second planet carrier 42 always rotates, while the first sun gear 30 has a rotational speed of 0 in the middle of each driving range. For the lubricating oil supply, a rotating shaft is preferred over a stationary shaft.

[0106] Fig.15 The tenth embodiment of the transmission device 1000 is shown. Fig.12The transmission 1000 is different from the transmission 800 in that the energy converter of the variator 16 is used as the basis for the eighth embodiment. Fig.13 The switching matrix of applies to transmission 1000 in the same manner.

[0107] In the transmission 1000, the variator 16 has a first energy converter 1080, which replaces the energy converter 80. In addition, the variator 16 has a second energy converter 1082, which replaces the energy converter 82. The two energy converters 1080, 1082 are configured as motors in the transmission 1000. The transmission 1000 is an electric power split transmission instead of a hydraulic power split transmission. The efficiency of the transmission 1000 is better than that of the hydraulic power split transmission. In addition, the electric power of the intermediate circuit can be provided to additional consumers. For this reason, the cost and structural space requirements are more favorable in the hydraulic power split transmission.

[0108] In addition, the transmission 1000 also has the possibility of driving the driven machine purely electrically when the motor on the drive end 12 is stopped, because a driving direction change component 50 with clutches KV, KR is provided on the drive side. For this purpose, in one embodiment, the corresponding driving range is provided by the closed first clutch K1 and the brake B and another closed shift element. In another embodiment, as an alternative or in addition to this, the corresponding driving range is provided by the closed second clutch K2 and the brake B and another closed shift element.

[0109] Fig.16 An eleventh embodiment of a transmission 1100 is shown. In this case, the drive end 12 is connected to the power take-off shaft 20, wherein the power take-off shaft 20 is connected to the variator 16 via a spur gear stage 86, and the variator is in turn connected to the first sun gear 30 via a spur gear stage 84. The drive end 12 can be connected to the first ring gear 34 via the clutch KR and the spur gear stage 54 of the driving direction change assembly 50 or via the clutch KV and the spur gear stage 52 of the driving direction change assembly 50. In this case, the driving direction change assembly 50 is arranged on the power take-off shaft 20. The second ring gear 44 is connected to the first clutch K1 via a spur gear stage 60, wherein the spur gear stage 60 can be connected to the intermediate shaft 70 and / or the second clutch K2 via the first clutch K1. In this case, the second clutch K2 can be connected to the second sun gear 40 and the fourth clutch K4 via the spur gear stage 62. The fourth clutch K4 is connected to the third clutch K3, wherein the third and fourth clutches K3, K4 are in turn connected to the output end 14. The planet carrier of the second planetary gear 46 is connected to the third clutch K3 . The intermediate shaft 70 is connected to the third clutch K3 and the output 14 via the spur gear stage 64 .

[0110] Relative to Figure 1 The embodiment shown, by Fig.16 The embodiment of the transmission 1100 shown in the embodiment of the transmission 1100 achieves a high degree of use of common parts with respect to the first and second clutches K1, K2, or the clutches KV, KR of the driving direction change component 50, because now the same or very similar clutches can be used. In addition, the arrangement shown here makes it possible to implement the pressure oil conveying part for actuating the clutches K1, K2, KV, KR less complicated, thereby achieving a higher efficiency of the transmission at the same time. A smaller structural space requirement can also be achieved by the new arrangement, because the distance between the variator 16 and the drive end 12 can be reduced. The measures for adjusting the distance between the driven end 14 and the drive end 12 do not need to be too extensive, because fewer components need to be changed.

[0111] Fig.17 The twelfth embodiment of the transmission 1200 is shown. In this case, the drive end 12 is connected to the power output shaft 20, wherein the power output shaft 20 is connected to the variator 16 via a spur gear stage 86. The variator is in turn connected to the first sun gear 30 via a spur gear stage 84. The drive end 12 is connected to the first ring gear 34 via a spur gear stage 52. The first clutch K1, the second clutch K2, the third clutch K3 and the two clutches KV, KR of the driving direction change assembly 50 are arranged on the intermediate shaft 70. The intermediate shaft 70 can be connected to the planet carrier of the third planetary gear 46 via the third clutch K3 and the spur gear stage 64. In addition, the intermediate shaft 70 can be connected to the output end 14 and the fourth clutch K4 via the clutch KR and the spur gear stage 54 of the driving direction change assembly 50. The intermediate shaft 70 can be connected to the output end 14 and the fourth clutch K4 via the clutch KV and the spur gear stage 56 of the driving direction change assembly 50. The second ring gear 44 is connected to the first clutch K1 via a spur gear stage 60, wherein the second ring gear 44 can in turn be connected to the intermediate shaft 70 and / or the second clutch K2 via the first clutch K1. The second clutch K2 is connected to the second sun gear 40 via a spur gear stage 62, wherein the second clutch K2 can be connected to the fourth clutch K4 via a spur gear stage 58 and thus to the output 14. The reduced transmission length in the embodiment shown here has proven to be particularly advantageous, i.e. the installation space between the transmission input and the transmission output is reduced.

[0112] Fig.18The thirteenth embodiment of the transmission 1300 is shown. In this case, the drive end 12 is connected to the power output shaft 20, wherein the power output shaft 20 is connected to the variator 16 via the spur gear stage 86, and the variator is connected to the first sun gear 30 via the spur gear stage 84. The drive end 12 can be connected to the first ring gear 34 via the clutch KR and the spur gear stage 54 of the driving direction change assembly 50 or via the clutch KV and the spur gear stage 52 of the driving direction change assembly 50. In this case, the driving direction change assembly 50 is arranged on the power output shaft 20. The second sun gear 40 is connected to the second clutch K2 via the spur gear stage 62 and can be connected thereto to the first clutch K1 and / or the output 14. In this case, the second sun gear 40 can be connected to the fourth clutch K4 via the spur gear stage 64 and can be connected thereto to the output 14. The first, second, third and fourth clutches K1, K2, K3, K4 are arranged on the output 14. The intermediate shaft 70 connects the planet carrier of the third planetary gear 46 to the third clutch K3 via the spur gear stage 60, whereby the intermediate shaft 70 can be connected to the output 14. The second ring gear 44 is connected to the first clutch K1 via the spur gear stage 56, whereby the second ring gear 44 can be connected to the output 14.

[0113] The embodiment of the transmission 1300 shown here also achieves the advantageous effect, among other advantages, that if the transmission 1300 is used to achieve the highest speed, the output end 14 on which the first to fourth clutches K1, K2, K3, K4 are arranged can be connected to the output end 14 according to Fig.16 Compared with the embodiment of the present invention, the transmission can be operated at a lower speed. This increases the service life of the components used (such as bearings) and reduces the drag losses due to the differential speed that is additionally generated at the first and second clutches. In addition, the application of the transmission in the vehicle is made more flexible, because a high variety of variations is achieved through the spur gear stages, or a series of axial distances between the drive end 12 and the driven end 14 can be realized in a simple manner. In particular, a small distance between the drive end 12 and the driven end 14 can be realized. Through the embodiment shown here, the first to fourth clutches K1, K2, K3, K4 can also be advantageously equipped with a high degree of common parts, just like the clutches KR, KV of the range change assembly 50. Advantageously, the spur gear stages 56, 62 and the spur gear stages 60, 64 can be equipped with common parts in corresponding pairs.

[0114] according to Figures 16 to 18 The embodiment shown is based on Figure 2 The switching matrix operates according to Fig.17However, limitations of the embodiment of the transmission 1200 apply, namely, due to the arrangement of the fourth clutch with the gear set, the driving range FB4R cannot be realized, so that only four forward driving ranges FB1 to FB4 and three reverse driving ranges FB1R to FB3R can be shown.

[0115] Reference numerals list

[0116] 100; 200; 300; 400; 500; 600; 700; 800; 900; 1000 Transmission

[0117] 12 Drive end

[0118] 14 Driven end

[0119] 16 Transformer

[0120] 18 Planetary Structure Components

[0121] 20 Power output shaft

[0122] 30,40;850 Sun gear

[0123] 32, 42; 852 planet carrier

[0124] 34, 44; 854 Ring gear

[0125] 36, 46, 48; 856 planetary gear

[0126] 50 Driving direction change structural components

[0127] 70 Intermediate shaft

[0128] 504 Another intermediate shaft

[0129] 80, 82; 1080, 1082 Energy Converter

[0130] 52, 54, 56, 58, 60, 62, 64, 84, 86; 502; 602 cylindrical gear stage

[0131] 858 Hollow shaft

[0132] K1 First Clutch

[0133] K2 Second Clutch

[0134] K3 Third Clutch

[0135] K4 Fourth Clutch

[0136] KV Clutch

[0137] KR Clutch

[0138] B Brake

Claims

1. A power split type continuously variable transmission device (1100), comprising a driving end (12), a driven end (14), a variator (16) and a planetary structure assembly (18), wherein: The transmission (1100) is configured to provide different driving ranges, wherein the planetary assembly (18) comprises a first sun gear (30) constituting a first planetary gear set, a first planet carrier (32) rotatably supporting a group of first planetary gears (36), a first ring gear (34), and a second sun gear (40) constituting a second planetary gear set, a second planet carrier (42) rotatably supporting a group of second planetary gears and a group of third planetary gears (46, 48), and a second ring gear (44), wherein the first and second planet carriers (32, 42) are permanently connected to each other in a rotationally fixed manner, wherein the first planetary gear (36) meshes with the first sun gear (30) and the first ring gear (34), wherein the second planetary gear (46) meshes with the second sun gear (40) and the second ring gear (44), wherein the second planetary gear (46) and the third planetary gear (48) mesh with each other in pairs, wherein the first planetary gear (36) and the third planetary gear (48) are permanently connected to each other in pairs to prevent relative rotation, wherein the converter (16) is mechanically connected to the drive end (12) and the first sun gear (30), wherein the drive end (12) can be mechanically connected to the first ring gear (34), and wherein the transmission device (1100) is configured to transmit torque from the second planetary gear set to the driven end (14), characterized in that The drive end (12) is connected to a power output shaft (20), wherein the power output shaft (20) is connected to the variator (16) via a spur gear stage (86), and the variator is connected to the first sun gear (30) via a spur gear stage (84); - the drive end (12) can be connected to the first ring gear (34) via a clutch (KR) and a spur gear stage (54) of a driving direction change component (50) or via a clutch (KV) and a spur gear stage (52) of the driving direction change component (50), wherein the driving direction change component (50) is arranged on the power output shaft (20); - the second ring gear (44) is connected to the first clutch (K1) via a spur gear stage (60), wherein the spur gear stage (60) can be connected to the intermediate shaft (70) and / or the second clutch (K2) via the first clutch (K1), wherein the second clutch (K2) can be connected to the second sun gear (40) and the fourth clutch (K4) via a spur gear stage (62); - the fourth clutch (K4) is connected to the third clutch (K3), wherein the third and fourth clutches (K3, K4) are in turn connected to the driven end (14); - the planet carrier of the second planetary gear (46) is connected to the third clutch (K3); The intermediate shaft (70) is connected to the third clutch (K3) and the output (14) via a spur gear stage (64).

2. A drive unit comprising a power split continuously variable transmission (1100) according to claim 1 and a motor, wherein the motor is mechanically connected to a drive end (12) for driving the drive end (12).

3. A power split type continuously variable transmission device (1200), comprising a driving end (12), a driven end (14), a variator (16) and a planetary structure assembly (18), wherein: The transmission (1200) is configured to provide different driving ranges, wherein the planetary assembly (18) comprises a first sun gear (30) constituting a first planetary gear set, a first planet carrier (32) rotatably supporting a group of first planetary gears (36), a first ring gear (34), and a second sun gear (40) constituting a second planetary gear set, a second planet carrier (42) rotatably supporting a group of second planetary gears and a group of third planetary gears (46, 48), and a second ring gear (44), wherein the first and second planet carriers (32, 42) are permanently connected to each other in a rotationally fixed manner, wherein the first planetary gear (36) meshes with the first sun gear (30) and the first ring gear (34), wherein the second planetary gear (46) meshes with the second sun gear (40) and the second ring gear (44), wherein the second planetary gear (46) and the third planetary gear (48) mesh with each other in pairs, wherein the first planetary gear (36) and the third planetary gear (48) are permanently connected to each other in pairs to prevent relative rotation, wherein the converter (16) is mechanically connected to the drive end (12) and the first sun gear (30), wherein the drive end (12) can be mechanically connected to the first ring gear (34), and wherein the transmission device (1200) is configured to transmit torque from the second planetary gear set to the driven end (14), characterized in that The drive end (12) is connected to a power output shaft (20), wherein the power output shaft (20) is connected to the variator (16) via a spur gear stage (86), and the variator is connected to the first sun gear (30) via the spur gear stage (84); - the drive end (12) is connected to the first gear ring (34) via a cylindrical gear stage (52); - the first clutch (K1), the second clutch (K2), the third clutch (K3) and the two clutches (KV, KR) of the driving direction change assembly (50) are arranged on an intermediate shaft (70), wherein the intermediate shaft (70) can be connected to the planetary carrier of the third planetary gear (48) via the third clutch (K3) and the spur gear stage (64), and the intermediate shaft (70) can be connected to the output end (14) and the fourth clutch (K4) via the clutch (KR) and the spur gear stage (54) of the driving direction change assembly (50); - the intermediate shaft (70) can be connected to the output end (14) and the fourth clutch (K4) via the clutch (KV) and the spur gear stage (56) of the driving direction change assembly (50); The second ring gear (44) is connected to the first clutch (K1) via a spur gear stage (60), wherein the second ring gear (44) can in turn be connected to the intermediate shaft (70) and / or the second clutch (K2) via the first clutch (K1), wherein the second clutch (K2) is connected to the second sun gear (40) via a spur gear stage (62), wherein the second clutch (K2) can be connected to the fourth clutch (K4) via a spur gear stage (58) and thus to the output end (14).

4. A drive unit comprising a power split continuously variable transmission (1200) according to claim 3 and a motor, the motor being mechanically operatively connected to a drive end (12) for driving the drive end (12).

5. A power split type continuously variable transmission device (1300), comprising a driving end (12), a driven end (14), a variator (16) and a planetary structure assembly (18), wherein: The transmission (1300) is configured to provide different driving ranges, wherein the planetary assembly (18) comprises a first sun gear (30) constituting a first planetary gear set, a first planet carrier (32) rotatably supporting a group of first planetary gears (36), a first ring gear (34), and a second sun gear (40) constituting a second planetary gear set, a second planet carrier (42) rotatably supporting a group of second planetary gears and a group of third planetary gears (46, 48), and a second ring gear (44), wherein the first and second planet carriers (32, 42) are permanently connected to each other in a rotationally fixed manner, wherein the first planetary gear (36) meshes with the first sun gear (30) and the first ring gear (34), wherein the second planetary gear (46) meshes with the second sun gear (40) and the second ring gear (44), wherein the second planetary gear (46) and the third planetary gear (48) mesh with each other in pairs, wherein the first planetary gear (36) and the third planetary gear (48) are permanently connected to each other in pairs to prevent relative rotation, wherein the converter (16) is mechanically connected to the drive end (12) and the first sun gear (30), wherein the drive end (12) can be mechanically connected to the first ring gear (34), and wherein the transmission device (1300) is configured to transmit torque from the second planetary gear set to the driven end (14), characterized in that The drive end (12) is connected to a power output shaft (20), wherein the power output shaft (20) is connected to the variator (16) via a spur gear stage (86), and the variator is connected to the first sun gear (30) via a spur gear stage (84); - the drive end (12) can be connected to the first ring gear (34) via a clutch (KR) and a spur gear stage (54) of a driving direction change component (50) or via a clutch (KV) and a spur gear stage (52) of the driving direction change component (50), wherein the driving direction change component (50) is arranged on the power output shaft (20); the second sun gear (40) is connected to the second clutch (K2) via a spur gear stage (62) and can thereby be connected to the first clutch (K1) and / or the output (14), wherein the second sun gear (40) is connected to the fourth clutch (K4) via a spur gear stage (64) and can thereby be connected to the output (14); - the first, second, third and fourth clutches (K1, K2, K3, K4) are arranged on the driven end (14); an intermediate shaft (70) connecting the planet carrier of the third planetary gear (48) to the third clutch (K3) via a spur gear stage (60), wherein the intermediate shaft (70) can thereby be connected to the output (14); The second ring gear (44) is connected to the first clutch (K1) via a spur gear stage (56), whereby the second ring gear (44) can be connected to the output (14).

6. A drive unit comprising a power split continuously variable transmission (1300) according to claim 5 and a motor, the motor being mechanically operatively connected to a drive end (12) for driving the drive end (12).

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