DE212018000129U1 - Transmission and device for torque and output speed change depending on driving resistance - Google Patents

Abstract

Transmission (1000) having an input member, an output member and two disposed between input member and output member planetary gear stages (100, 200) each having four Getriebestufenorganen, the (gear) a first central gear (104, 209), a planet carrier (101, 210) with at least a planetary gear (102, 208) and a second central gear (105, 206), wherein a gear stage member of the first planetary gear stage (100) cooperates with the input member and a gear stage member of the second planetary gear stage (200) with the output member, characterized by three, with exclusion a direct connection of the gear stage members cooperating with the input member and the output member respectively a gear stage member of a planetary gear stage (100) with a Getriebestufenorgan the other planetary gear stage (200) connecting the transmission connections (400, 500, 600), of which at least one as and / or on the frame is fixed.

Description

The invention relates to a transmission according to the preamble of claim 1 and a device according to the preamble of claim 7.

The invention relates to a transmission with a dependent on the output side load continuous torque and output speed change according to the preamble of claim 1 and to a device for torque and output speed change for mechanical engineering according to the preamble of claim. 7

From the prior art ( US 4932928 ) is a non-switchable continuous differential gear with a hydrodynamic converter in combination with a planetary gear known. This transmission is in the form of a hydrodynamic converter and a double planetary gear. The transmission includes a two-degree-of-freedom input power feeding device consisting of two input members (a sun gear and a first row planet carrier). The input members are connected to each other by means of the hydrodynamic converter. The transmission further includes an output side kinematic chain having a degree of freedom equal to zero in the form of a planetary gear (satellites) and a ring-shaped first-row gear, second-row gears and a driven-side planet gear carrier.

This transmission has the following shortcomings: The implementation of two degrees of freedom of the input power feeding device gives different speeds of rotation of the sun gear and the planet carrier (i.e., a differential coupling therebetween). It is generated by the hydrodynamic converter and requires a certain amount of power to achieve the hydrodynamic effect. The hydrodynamic converter with the hydrodynamic effect has a very low efficiency (about 0.5), a narrow speed change range and a low starting safety. For this reason, additional freewheels and overrunning clutches must be used. They complicate the design and worsen the quality of the transmission function (smoothness). In the end, the gearbox with hydrodynamic converter has too complicated a structure, a low efficiency, an inferior quality of operation and is not reliable at startup.

From the prior art (RU 2234626), a device is known to perform the method for automatic and continuous torque and output speed change depending on the driving resistance.

This device is designed in the form of a hydrodynamic converter and a triple planetary gear. The device includes an input power feed device with two degrees of freedom. It consists of two input members (two sun gears of the first and second series), which are movably coupled together by means of a hydrodynamic transducer, a planet gear and a planet carrier. The device further includes a kinematic chain having a degree of freedom equal to zero in the form of gears of the third row.

This device has the following shortcomings: The implementation of the two degrees of freedom of the input power feeding device ensures different speeds of the two sun gears. It is achieved by the hydrodynamic converter, which has a low efficiency, a narrow speed change range and a low tarnish. Consequently, additional devices must be used. These complicate the design and affect the smoothness. In the end, the transmission with the hydrodynamic converter proves to be complicated on-site and unreliable during startup. It has a low efficiency and low quality of operation.

From the prior art (KZ 14477) is also an adaptive gear train (embodiments) with automatically adjustable speed in the form of a dual planetary gear known. The gear transmission includes a two-degree-of-freedom input power feeding device and a zero-degree degree-of-freedom gear output-side kinematic chain of second-row gears. The power feeding device consists of two members (a central gear and a planetary gear or a planet carrier and a planetary gear of the first row). In this transmission, the drive torque is transmitted from an input shaft to the power feed device, and the output side kinematic chain transmits drag forces from an output shaft to the power feed device. In the existing two degrees of freedom of the power feed device, the input torque and the drag forces on the planet gear are independent and freely adjustable.

The deficiencies of this device are that there is no structural constraint that ensures kinematic definability, and that this device has low functionality. As an additional connection (stiffening) a differential connection is used. It ensures a closed circuit consisting of toothed gears. However, the closed loop structure does not diminish the degree of freedom of the kinematic chain. Therefore, the transmission can only be functional if there is friction. Such a stiffening has a low functionality and a low efficiency (efficiency).

From the prior art ( GB 2238090 Further, there is known a power transmission system including a two-degree of freedom power feeding device and a zero-degree-of-freedom output-side kinematic chain. The power feeding device consists of two links (a planet carrier and a planetary gear). In this system, the input shaft transmits the input drive torque to the power feed device, and the output side kinematic chain transmits drag forces from the output shaft to the power feed device. When the power feeding device has two degrees of freedom, the input torque and drag forces on the planetary gear are independent and freely adjustable. Such a connection allows the relationship between the kinematic and the force characteristics and represents a differential connection.

The shortcomings of this device are its low functionality and the lack of a structural connection, which ensures the kinematic definability. The gearbox can only be functional if there is friction. Such a transmission has a low functionality and a low efficiency.

The closest prior art ( DE 20 2012 101 273 ) compared to the present invention in its technical nature is a device for carrying out the method for automatic and continuous torque and output speed change depending on driving resistance.

This device is designed in the form of a revolving kinematic chain with a superimposed connection. It includes a drive-side planetary gear carrier (input planet carrier), an input planetary gear, a set of sun gears, a set of central gears, an output planetary gear, an output side carrier (output planet carrier) and has a gear ratio μ _1-7 from the input Planet wheel carrier to the output planetary gear.

The shortcomings of this device are its low functionality and the lack of a structural connection intended to ensure kinematic definability. As a stiffener a differential connection is used, which is ensured by a closed circuit. The closed circle consists of toothed gears. However, the closed loop structure does not diminish the degree of freedom of the kinematic chain. For this reason, the transmission can only be able to work if there is friction. Such a transmission has a low functionality and a low efficiency (efficiency).

By year A.: "There is no form-fitting continuously variable transmission possible", Antriebstechnik, United specialized publishers, Mainz, DE, Bd. 28, 1 January 1989, pp. 45/46, XP001160727, ISSN: 0722-8546 is known as the state of a discussion to date on the possibility or impossibility of positive, continuously variable transmission that the transmission ratio of such transmission is always a rational number and thus there is no continuously variable transmission.

By US 2011/0245015 A1 is a transmission with a dependent of the output side load continuous torque and output speed change known. The transmission comprises at least two planetary gear stages and kinematic chains with at least three degrees of freedom. The power transmission takes place via two power transmission cycles. The transmission has means for at least approximately fixing at least one transmission element at the beginning of an operation, with remaining transmission elements remaining movable over the entire service life.

By WO2016 / 105243 a transmission is known comprising a drive shaft and three planetary gear sets. The planetary gear sets are a driven set, an interim set and a subset. Each of the three planetary gear sets comprises three elements each: a drive element, a driven element and an auxiliary element. All elements of all planetary gear sets rotate at the same time. The torque is increased from the auxiliary member to the driven member of one planetary gear set and from one planetary gear set to another planetary gear set.

Based on the above prior art, the invention is based on the object to improve the generic transmission without undue constructive effort so that its functionality and its efficiency will increase.

The object is achieved in each case by the features of the independent claims.

Advantageous embodiments of the invention are set forth in the dependent claims, the drawings and the following description, including those associated with the drawings.

• - ein um eine Zentralachse drehbar angeordnetes Sonnenrad,
• - einen um die Zentralachse drehbar angeordneten Planetenradträger,
• - mindestens ein um eine eigene mit dem Planetenradträger um die Zentralachse umlaufende, parallel zur Zentralachse verlaufend und versetzt zu dieser angeordnete Planetenachse drehbar angeordnetes Planetenrad und
• - ein ebenfalls um die Zentralachse drehbar angeordnetes, beispielsweise durch ein Hohlrad mit Innenverzahnung gebildetes, auch als Gegenrad bezeichnetes sogenanntes zweites Zentralrad.

A first subject of the invention accordingly relates to a transmission having an input member and an output member and two planetary gear stages arranged between the input member and the output member. Each of the planetary gear stages is equipped with four gear stage organs each. The four gear stage members of each planetary gear stage are:

• a sun gear rotatably arranged about a central axis,
• a planet carrier rotatably mounted about the central axis,
• - At least one about its own with the planet carrier to the central axis rotating, parallel to the central axis extending and offset to this arranged planetary axis rotatably arranged planetary gear and
• - A likewise about the central axis rotatably arranged, for example, formed by a ring gear with internal teeth, also referred to as mating so-called second central wheel.

The term "second central wheel" is intended to express that the sun gear of a planetary gear stage is also referred to as "first central wheel". This designation emphasizes the difference between the sun gear and the counter wheel.

The input member cooperates with a gear stage member of a planetary gear stage.

The output member cooperates with a gear stage member of the other remaining planetary gear stage.

The transmission is characterized by three each one gear stage member of a planetary gear stage with a gear stage member of the other planetary gear stage connecting, advantageous power transmitting transmission connections between pairs of Getriebestufenorganen different planetary gear stages.

The term power transmitting serves to clarify the transmission of torque and speed across the transmission connections and thus takes into account the fact that all three transmission connections can be rotationally movable, but at least one, advantageously two transmission connections are formed rotatably movable.

Particularly preferably, two of the gearbox connections with the gear stage members of the planetary gear stages form a closed, circumferential kinematic chain when the output member is stationary. In this case, the third gear connection between the two gear stage members of their associated pair on a similar or the same gear ratio, as that prevailing within the kinematic chain between the cooperating with the input member Getriebestufenorgan the first planetary gear stage and the Getriebestufenorgan the second planetary gear stage of the third gear connection associated gear stage member ratio ,

In other words, while the gearbox on the third gear connection away between the two gear stage members of the third gearbox associated pair Getriebestufenorgane a similar or the same ratio, as that within the kinematic chain between the cooperating with the input member gear stage member of the first planetary gear stage and the via the third gear connection connected pair gear stage members belonging gear stage member of the second planetary gear stage prevailing gear ratio.

At least one of the transmission connections is expediently designed as a torque support.

For this purpose, at least one of the transmission connections can be defined as a frame of the transmission and / or fixed to a frame of the transmission.

The restriction also includes the fact that two of the gearbox connections form a superimposed connection via the gear members connected to them and interacting with one another, a circumferential kinematic chain and the remaining gearbox connection and the transmission members connected to it. The revolving kinematic chain, together with the superimposed connection, can produce a movable support which forms a torque support.

In other words, the constraint also includes the fact that the three gearboxes can together produce a movable support that forms a torque support.

Preferably, the input member cooperates with the planet carrier of a planetary gear stage. In this case, the input member with the planet carrier of a planetary gear stage is directly connected, includes this or is covered by this.

Preferably, the output member also cooperates with the planet carrier of the other remaining planetary gear stage. Preferably, the output member is directly connected to the planetary gear carrier of the other remaining planetary gear stage, comprises this or is covered by this.

A correspondingly formed transmission is characterized by three, each one gear stage member of a planetary gear stage with a gear stage member of the other planetary gear stage connecting transmission connections between pairs of Getriebestufenorganen different planetary gear stages.

A first gear connection preferably provides a direct non-rotatable shaft connection between the two sun gears of the two planetary gear stages which mesh with the planet gears of the two planetary gear stages and form primary gears. In this case, the two primary gears forming sun gears of the two planetary gear stages are non-rotatably connected by a primary shaft.

Preferably, a second transmission connection provides a direct non-rotatable shaft connection between the second central gears of the two planetary gear stages, which mesh with the planetary gears of the two planetary gear stages and form secondary gears. The two secondary gears forming second central gears of the two planetary gear stages are non-rotatably connected to each other by a secondary shaft.

One of the two non-rotatably interconnected by the second gear transmission secondary gears forming second central gears meshes with a toothing of the at least one planetary gear of a planetary gear and the other with a toothing of the at least one planetary gear of the other planetary gear.

The toothing of the at least one planetary gear or the teeth of the planetary gears of at least one of the two planetary gears, with which the secondary gears non-rotatably connected by the secondary gear meshing of the second transmission connection, preferably differ from that of teeth or those teeth, with or with those by the Combining primary shaft connected sun gears of the two planetary gear stages.

The two non-rotatably connected via the secondary shaft secondary gears of the second transmission connection can both be designed as spur gears with external teeth as teeth or both as ring gears with internal teeth as teeth or one as a spur gear with external teeth as its teeth and a ring gear with internal teeth as its teeth.

A third transmission connection preferably provides a stiffening between two Getriebestufenorganen the two planetary gear stages.

• - den Planetenradträger der ersten Planetengetriebestufe,
• - das mindestens eine Planetenrad der ersten Planetengetriebestufe,
• - die zweite Getriebeverbindung mit den durch die Sekundärwelle unverdrehbar verbundenen, jeweils mit einer Verzahnung des mindestens einen Planetenrads der ersten Planetengetriebestufe und mit einer Verzahnung des mindestens einen Planetenrads der zweiten Planetengetriebestufe kämmenden Sekundärzahnrädern,
• - das mindestens eine Planetenrad der zweiten Planetengetriebestufe, die erste Getriebeverbindung mit den durch die Primärwelle unverdrehbar verbundenen, jeweils mit einer Verzahnung des mindestens einen Planetenrads der ersten Planetengetriebestufe und mit einer Verzahnung des mindestens einen Planetenrads der zweiten Planetengetriebestufe kämmenden Primärzahnrädern beziehungsweise Sonnenrädern der beiden Planetengetriebestufen

This stiffening formed by the third gear connection in this case has a transmission ratio which is at least similar to that transmission ratio, which in an unmoved planet carrier of the second planetary gear stage by

• - the planet carrier of the first planetary gear stage,
• the at least one planet gear of the first planetary gear stage,
• the second gear connection with the secondary gears non-rotatably connected, each with a toothing of the at least one planetary gear of the first planetary gear stage and with a toothing of the at least one planetary gear of the second planetary gear stage meshing secondary gears,
• - The at least one planetary gear of the second planetary gear stage, the first transmission connection with the non-rotatably connected by the primary shaft, each with a toothing of the at least one planetary gear of the first planetary gear stage and with a toothing of the at least one planetary gear of the second planetary gear meshing primary gears or sun gears of the two planetary gear stages

Such a transmission can be realized by a device for torque and output speed change depending on the driving resistance, which is designed in the form of a rotating kinematic chain with a superimposed connection.

The device comprises an input planetary member operatively connected to and / or encompassed by the input member and / or the input member, an input planetary gear, a set of sun gears, a set of central gears, an output planetary gear and one operatively connected to the output member standing and / or encompassed by the output member and / or the output member comprehensive output planet carrier.

The device has a gear ratio
u _1-7
from the input planet carrier to the output planetary gear.

In this case, at least one member of the revolving kinematic chain and / or the stiffening of a torque support can serve.

For example, for this purpose, at least one member of the revolving kinematic chain or the stiffening can be defined as a frame of the transmission and / or fixed to a frame of the transmission.

Alternatively or additionally, the revolving kinematic chain together with the superimposed connection can produce a movable support which forms a torque support.

• die Versteifung in Form einer kinematischen Kette mit einem zusätzlichen Zahnradgetriebe ausgebildet ist und
• das zusätzliche Zahnradgetriebe ein ähnliches Übersetzungsverhältnis $$u_{}$$$${}_{1-7ad}={\mathrm{<figure-callout\; id="1"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{1-7}$$
  
  sicherstellt, wobei $$u_{1-7}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]},u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4},u_{96}^{\left(10\right)}=-\frac{z_6{z}_8}{z_7{z}_9},u_{76}^{\left(10\right)}=\frac{z6}{z7},$$
  
  $${\mathrm{<figure-callout\; id="1"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{1-7ad}=\frac{{\mathrm{<figure-callout\; id="11"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-{\mathrm{<figure-callout\; id="11"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{11-5}^{\left(1\right)}\right]},u_{12-6}^{\left(10\right)}=-\frac{z_6}{{\mathrm{<figure-callout\; id="12"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_{12}}$$
  

ist.The device is characterized in that:

• the stiffening in the form of a kinematic chain is formed with an additional gear transmission and
• the additional gear transmission a similar gear ratio $$u_{1-7ad}=u_{1-7}$$
  
  making sure $$u_{1-7}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]}.u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4}.u_{96}^{\left(10\right)}=-\frac{z_6{z}_{\mathrm{8th}}}{z_7{z}_9}.u_{76}^{\left(10\right)}=\frac{z6}{z7}.$$
  
  $$u_{1-7ad}=\frac{u_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{11-5}^{\left(1\right)}\right]}.u_{12-6}^{\left(10\right)}=-\frac{z_6}{z_{12}}$$
  

is.

For example, the third gear connection may provide a connection between the at least one, also referred to as input planetary gear of a planetary gear and the at least one, also referred to as output planetary gear of the other planetary gear by means of two additional, non-rotatably connected to each other via a shaft sun gears. This stiffening has two interconnected by a tertiary shaft, designed as additional sun gears tertiary gears, one of which meshes with a toothing of at least one planetary gear of a planetary gear and the other with a toothing of the at least one planetary gear of the other planetary gear stage.

The toothing of the at least one planetary gear or the teeth of the planetary gears of at least one of the two planetary gear sets, with which the tertiary gears meshed non-rotatably connected by the tertiary gear of the third gear connection, differ from those teeth or those teeth, with or with which respectively at least one of by the primary shaft non-rotatably interconnected primary gears forming sun gears or at least one of the non-rotatably connected by the secondary shaft non-rotatably connected secondary gears.

Such a transmission can be realized by a device for torque and output speed change depending on the driving resistance, which is designed in the form of a rotating kinematic chain with a superimposed connection.

The device comprises an input planetary member operatively connected to and / or encompassed by the input member and / or the input member, an input planetary gear, a set of sun gears, a set of central gears, an output planetary gear and one operatively connected to the output member standing and / or encompassed by the output member and / or the output member comprehensive output planet carrier.

vom Eingangs-Planetenradträger bis zum Ausgangs-Umlaufrad auf.The device has a gear ratio $$u_{1-7}$$

from the input planet carrier to the output planetary gear.

In this case, at least one member of the revolving kinematic chain and / or the stiffening of a torque support can serve.

For example, for this purpose, at least one member of the revolving kinematic chain or the stiffening can be defined as a frame of the transmission and / or fixed to a frame of the transmission.

Alternatively or additionally, the revolving kinematic chain together with the superimposed connection can produce a movable support which forms a torque support.

• die Versteifung in Form einer kinematischen Kette mit einem zusätzlichen Zahnradgetriebe ausgebildet ist,
• das zusätzliche Zahnradgetriebe in Form eines Satzes Sonnenräder ausgebildet ist,
• der Satz Sonnenräder ein mit dem Eingangs-Umlaufrad gekoppeltes Rad und ein mit dem Ausgangs-Umlaufrad gekoppeltes Rad enthält und das zusätzliche Zahnradgetriebe ein ähnliches Übersetzungsverhältnis $$u_{}$$$${}_{1-7ad}={\mathrm{<figure-callout\; id="1"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{1-7}$$
  
  sicherstellt, wobei $$u_{1-7}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]},u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4},u_{96}^{\left(10\right)}=-\frac{z_6{z}_8}{z_7{z}_9},u_{76}^{\left(10\right)}=\frac{z6}{z7},$$
  
  $${\mathrm{<figure-callout\; id="1"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{1-7ad}=\frac{{\mathrm{<figure-callout\; id="11"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-{\mathrm{<figure-callout\; id="11"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{11-5}^{\left(1\right)}\right]},u_{12-6}^{\left(10\right)}=-\frac{z_6}{{\mathrm{<figure-callout\; id="12"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_{12}}$$
  

ist.The device is characterized in that:

• the stiffening is designed in the form of a kinematic chain with an additional gear transmission,
• the additional gear transmission is designed in the form of a set of sun gears,
• the sun gear set includes a wheel coupled to the input epicyclic gear and a wheel coupled to the output epicyclic gear, and the additional gear drive includes a similar gear ratio $$u_{1-7ad}=u_{1-7}$$
  
  making sure $$u_{1-7}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]}.u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4}.u_{96}^{\left(10\right)}=-\frac{z_6{z}_{\mathrm{8th}}}{z_7{z}_9}.u_{76}^{\left(10\right)}=\frac{z6}{z7}.$$
  
  $$u_{1-7ad}=\frac{u_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{11-5}^{\left(1\right)}\right]}.u_{12-6}^{\left(10\right)}=-\frac{z_6}{z_{12}}$$
  

is.

Alternatively, the third transmission connection another connection between the at least one, also referred to as input planet gear of the planetary gear stage and the at least one, also referred to as output planet gear of the other planetary gear stage by means of two additional non-rotatably connected via a tertiary shaft second central gears provide. This stiffening has two interconnected by a tertiary shaft formed as additional second central gears tertiary gears, one of which meshes with a toothing of the at least one planetary gear of a planetary gear and the other with a toothing of the at least one planetary gear of the other planetary gear stage.

The toothing of the at least one planetary gear or the teeth of the planetary gears of at least one of the two planetary gear sets, with which the tertiary gears meshed non-rotatably connected by the tertiary gear of the third gear connection, differ from those teeth or those teeth, with or with which respectively at least one of by the primary shaft non-rotatably interconnected primary gears forming sun gears or at least one of the non-rotatably connected by the secondary shaft non-rotatably connected secondary gears.

Such a transmission can be realized by a device for torque and output speed change depending on the driving resistance, which is designed in the form of a rotating kinematic chain with a superimposed connection.

In this case, at least one member of the revolving kinematic chain and / or the stiffening of a torque support can serve.

For example, for this purpose, at least one member of the revolving kinematic chain or the stiffening can be defined as a frame of the transmission and / or fixed to a frame of the transmission.

Alternatively or additionally, the circumferential kinematic chain together with the stiffener can produce a movable support which forms a torque support.

The stiffening is designed in the form of a kinematic chain with an additional gear transmission, which is designed in the form of a set of central wheels.

The set of central gears includes a wheel coupled to the input epicyclic gear and a wheel coupled to the output epicyclic gear.

sicher, wobei $$u_{1-8ad}=\frac{u_{4-11}^{\left(1\right)}-u_{9-12}^{\left(10\right)}}{u_{8-12}^{\left(10\right)}\left[1-u_{4-11}^{\left(1\right)}\right]},u_{4-11}^{\left(1\right)}=-\frac{z_{11}}{z_4},u_{9-12}^{\left(10\right)}=-\frac{z_{12}}{z_9},u_{8-12}^{\left(10\right)}=\frac{z12}{z8}$$

ist.The additional gear transmission provides a similar gear ratio $$u_{1-\mathrm{8th}ad}=u_{1-7}$$

sure, being $$u_{1-\mathrm{8th}ad}=\frac{u_{4-11}^{\left(1\right)}-u_{9-12}^{\left(10\right)}}{u_{\mathrm{8th}-12}^{\left(10\right)}\left[1-u_{4-11}^{\left(1\right)}\right]}.u_{4-11}^{\left(1\right)}=-\frac{z_{11}}{{\mathrm{<figure-callout\; id="4"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_4}.u_{9-12}^{\left(10\right)}=-\frac{z_{12}}{{\mathrm{<figure-callout\; id="9"\; label="z"\; filenames="DE212018000129U1\_0059.png,DE212018000129U1\_0060.png"\; state="\{\{state\}\}">z</figure-callout>}}_9}.u_{\mathrm{8th}-12}^{\left(10\right)}=\frac{z12}{z\mathrm{8th}}$$

is.

Alternatively, the third transmission connection can be a connection between the planetary gear carrier, which is also referred to as an input planet carrier, of the one planetary gear stage and the at least one planetary gear Also provide as output planet gear designated planetary gear of the other planetary gear stage. In this case, the planet carrier of a planetary gear stage via a tertiary shaft is non-rotatably connected to a designed as an additional sun gear tertiary gear. The tertiary gear meshes with the at least one also referred to as the output planet gear planetary gear of the other planetary gear.

Such a transmission can be realized by a device for torque and output speed change depending on the driving resistance, which is designed in the form of a rotating kinematic chain with a stiffener.

In this case, at least one member of the revolving kinematic chain and / or the stiffening of a torque support can serve.

For example, for this purpose, at least one member of the revolving kinematic chain or the stiffening can be defined as a frame of the transmission and / or fixed to a frame of the transmission.

Alternatively or additionally, the revolving kinematic chain together with the superimposed connection can produce a movable support which forms a torque support.

The stiffener is in the form of a kinematic chain with an additional gear transmission, which is in the form of a rigidly connected to the input planet carrier, the tertiary gear forming wheel is formed.

The Tertiärzahnrad forming wheel meshes with a toothing of the output planetary gear. This may be formed on a non-rotatably coupled to the output planetary wheel. In other words, the gear transmission may be in the form of a rigidly connected to the input-Planetenradträger connected to a wheel which is rigidly connected to the output planetary gear.

sicher, wobei $$u_{1-7ad}=\frac{z_{12}}{z_{11}}$$

ist.The additional gear transmission provides a similar gear ratio $$u_{1-7ad}=u_{1-7}$$

sure, being $$u_{1-7ad}=\frac{z_{12}}{{\mathrm{<figure-callout\; id="11"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_{11}}$$

is.

A definition of the meanings of the symbols and indices used above and below in connection with the device can be found in the following description of the exemplary embodiments illustrated in the individual figures of the drawings.

It can be seen that the first object of the invention can be realized by a transmission with an input member, an output member and two disposed between input member and output member planetary gear stages. Each of the planetary gear stages is equipped with four gear stage organs each. The gear stage members of each planetary gear stage is a sun gear rotatably disposed about a central axis, a so-called second central gear also rotatably disposed about the central axis, for example, a counter gear known as a counter gear, a planet carrier rotatably disposed about the center axis at least one about its own, parallel to the central axis and offset from this arranged, with the planet carrier about the central axis rotating planetary axis rotatably arranged planet gear.

The transmission has three, each a gear stage member of a planetary gear stage with a gear stage member of the other planetary gear stage connecting transmission connections between pairs of two gear stage organs of the various planetary gear stages.

Here, omitting an immediate pairing of cooperating with the input member and the output member gear stage organs of the two planetary gear stages, in particular a pairing of the planet carrier of the two planetary gear stages, each one gear stage connection between each one briefly referred to as a pair gear stage organ pair, consisting of a gear stage member of a planetary gear stage and a gear stage member of the remaining other planetary gear stage provided. Each of the gear connections connects a gear stage member of a planetary gear stage with a gear stage member of the other planetary gear stage.

At least one of the transmission connections is advantageously used for a torque support.

For this purpose, at least one of the transmission connections is preferably defined as a frame of the transmission and / or fixed to a frame of the transmission.

The restriction also includes the fact that two of the gearbox connections form a circumferential kinematic chain and the remaining gearbox connection and the transmission members connected to it via the gear members connected to them and interacting with one another. The revolving kinematic chain, together with the superimposed connection, can produce a movable support which forms a torque support.

In other words, the constraint also includes the fact that the three gearboxes can together produce a movable support that forms a torque support.

A second object of the invention relates to a device described above realizing device for torque and output speed change depending on the driving resistance.

The device is designed in the form of a circumferential kinematic chain with a stiffener. The device comprises an input planetary member operatively connected to and / or encompassed by the input member and / or the input member, an input planetary gear, a set of sun gears, a set of central gears, an output planetary gear and one operatively connected to the output member standing and / or encompassed by the output member and / or the output member comprehensive output planet carrier.

The device has within the circulating kinematic chain at stationary output planet carrier a gear ratio
μ1-7
from the input planet carrier to the output planetary gear.

• - die Versteifung in Form einer kinematischen Kette mit einem zusätzlichen Zahnradgetriebe ausgebildet ist und
• - das zusätzliche Zahnradgetriebe ein ähnliches Übersetzungsverhältnis wie dasjenige innerhalb der umlaufenden kinematischen Kette bei unbewegtem Ausgangs-Planetenradträger sicherstellt.

The device is characterized in that:

• - The stiffening is designed in the form of a kinematic chain with an additional gear transmission and
• - The additional gear transmission ensures a similar ratio as that within the revolving kinematic chain at stationary output planet carrier.

In this case, at least one member of the revolving kinematic chain and / or the stiffening of a torque support can serve.

For example, for this purpose, at least one member of the revolving kinematic chain or the stiffening can be defined as a frame of the transmission and / or fixed to a frame of the transmission.

Alternatively or additionally, the circumferential kinematic chain together with the stiffener can produce a movable support which forms a torque support.

The device may comprise individual or a combination of the features described above and / or subsequently in connection with the transmission, just as the transmission may comprise and / or implement individual or a combination of a plurality of features previously and / or subsequently described in connection with the device can

The device and / or the transmission may alternatively or additionally be single or a combination of several in the context of the prior art and / or in one or more of the prior art documents and / or in the following description to those in the drawings having illustrated embodiments described features.

Advantages over the prior art result from a complete solution of the problem.

The invention will be explained in more detail with reference to embodiments shown in the drawings.

The proportions of the individual elements to one another in the figures do not necessarily correspond to the actual size ratios, since some shapes may be simplified and other shapes may be enlarged in relation to other elements for better illustration. For identical or equivalent elements of the invention, identical reference numerals are used. Furthermore, for the sake of clarity, only reference symbols are shown in the individual figures, which are required for the description of the respective figure. The illustrated embodiments are merely examples of how the invention may be configured and are not an exhaustive limitation.

• 1 ein erstes Ausführungsbeispiel einer Einrichtung zur Drehmoment- und Abtriebsdrehzahländerung je nach Fahrwiderstand,
• 2 ein zweites Ausführungsbeispiel einer Einrichtung zur Drehmoment- und Abtriebsdrehzahländerung je nach Fahrwiderstand mit einem zusätzlichen Satz von Zentralrädern,
• 3 ein drittes Ausführungsbeispiel einer Einrichtung zur Drehmoment- und Abtriebsdrehzahländerung je nach Fahrwiderstand mit einem zusätzlichen Zahnradgetriebe vom Eingangs-Planetenradträger zum Ausgangs-Umlaufrad,
• 4 ein Ausführungsbeispiel eines durch eine vereinfachte in 3 dargestellte Einrichtung verwirklichbaren Getriebes in einem entlang dessen mit der Zentralachse fluchtenden Eingangswelle und Ausgangswelle verlaufenden Längsschnitt,
• 5 das Getriebe aus 4 in einer perspektivischen Explosionsdarstellung und
• 6 eine schematische Darstellung einer ein in 4 und 5 dargestelltes Getriebe verwirklichenden Einrichtung zur Drehmoment- und Abtriebsdrehzahländerung je nach Fahrwiderstand mit einem zusätzlichen Zahnradgetriebe vom Eingangs-Planetenradträger zum Ausgangs-Umlaufrad.

In a schematic representation:

• 1 a first embodiment of a device for torque and output speed change depending on driving resistance,
• 2 A second embodiment of a device for torque and output speed change depending on the driving resistance with an additional set of central wheels,
• 3 A third embodiment of a device for torque and output speed change depending on driving resistance with an additional gear transmission from the input planet carrier to the output planetary gear,
• 4 an embodiment of a simplified by in 3 illustrated device realizable transmission in a along its aligned with the central axis of the input shaft and output shaft longitudinal section,
• 5 the gearbox out 4 in a perspective exploded view and
• 6 a schematic representation of a in 4 and 5 illustrated gear realizing means for torque and output speed change depending on driving resistance with an additional gear transmission from the input planet carrier to the output planetary gear.

• - einen um eine Zentralachse 300 drehbar angeordneten, auch als Eingangs-Planetenradträger 1 bezeichneten Planetenradträger 101 einer ersten Planetengetriebestufe 100,
• - mindestens ein um eine parallel zur Zentralachse 300 versetzt zu dieser angeordnete und mit dem Planetenradträger 101 um die Zentralachse 300 umlaufende erste Planetenachse 301 drehbar angeordnetes, auch als Eingangs-Umlaufrad 2 bezeichnetes Planetenrad 102 der ersten Planetengetriebestufe 100,
• - ein um die Zentralachse 300 drehbar angeordnetes, auch als Sonnenrad 4 bezeichnetes erstes Zentralrad 104 der ersten Planetengetriebestufe 100,
• - ein um die Zentralachse 300 drehbar angeordnetes, auch als Zentralrad 5 bezeichnetes zweites Zentralrad 105 der ersten Planetengetriebestufe 100,
• - einen um die Zentralachse 300 drehbar angeordneten abtriebsseitigen, auch als Ausgangs-Planetenradträger 10 bezeichneten Planetenradträger 210 einer zweiten Planetengetriebestufe 200,
• - mindestens ein um eine parallel zur Zentralachse 300 versetzt zu dieser angeordnete und mit dem Planetenradträger 210 um die Zentralachse 300 umlaufende zweite Planetenachse 302 drehbar angeordnetes, auch als Ausgangs-Umlaufrad 7 bezeichnetes Planetenrad 208 der zweiten Planetengetriebestufe 200,
• - ein um die Zentralachse 300 drehbar angeordnetes, auch als Sonnenrad 9 bezeichnetes erstes Zentralrad 209 der zweiten Planetengetriebestufe 200, und
• - ein um die Zentralachse 300 drehbar angeordnetes, auch als Zentralrad 6 bezeichnetes zweites Zentralrad 206 der zweiten Planetengetriebestufe 200.

An in 1 . 2 . 3 and 6 in various schematic embodiments and in 4 and 5 in a specific embodiment illustrated inventive transmission 1000 includes:

• - one around a central axis 300 rotatably arranged, as an input planet carrier 1 designated planet carrier 101 a first planetary gear stage 100 .
• - at least one around a parallel to the central axis 300 offset to this arranged and with the planet carrier 101 around the central axis 300 circumferential first planetary axis 301 rotatably arranged, also as an input pulley 2 designated planetary gear 102 the first planetary gear stage 100 .
• - one around the central axis 300 rotatably arranged, as a sun gear 4 designated first central wheel 104 the first planetary gear stage 100 .
• - one around the central axis 300 rotatably arranged, as a central wheel 5 designated second central wheel 105 the first planetary gear stage 100 .
• - one around the central axis 300 rotatably arranged output side, as output planet carrier 10 designated planet carrier 210 a second planetary gear stage 200 .
• - at least one around a parallel to the central axis 300 offset to this arranged and with the planet carrier 210 around the central axis 300 circumferential second planetary axis 302 rotatably arranged, also as an output planetary gear 7 designated planetary gear 208 the second planetary gear stage 200 .
• - one around the central axis 300 rotatably arranged, as a sun gear 9 designated first central wheel 209 the second planetary gear stage 200 , and
• - one around the central axis 300 rotatably arranged, as a central wheel 6 designated second central wheel 206 the second planetary gear stage 200 ,

The planet carrier 101 the first planetary gear stage 100 that has at least one planetary gear 102 the first planetary gear stage 100 , the first central wheel 104 the first planetary gear stage 100 and the second central wheel 105 the first planetary gear stage 100 form the gear stage members of the first planetary gear stage 100 ,

The planet carrier 210 the second planetary gear stage 200 that has at least one planetary gear 208 the second planetary gear stage 200 , the first central wheel 209 the second planetary gear stage 200 and the second central wheel 206 the second planetary gear stage 200 form the Getriebestufenorgane the second planetary gear stage 200 ,

A gear stage member of the first planetary gear stage 100 acts with an input member, such as an input shaft, together, for example, by being connected to, encompassing or being encompassed by the input member.

A gear stage member of the second planetary gear stage 200 acts with an output member, such as an output shaft, together, for example, by being connected to, comprising or being encompassed by the output member.

Between the remaining three each gear stage organs of the first planetary gear stage 100 and the second planetary gear stage 200 are three gear connections 400 . 500 . 600 educated.

The gear 1000 Thus, with omission of cooperating with the input member and the output member gear stage organs three transmission connections 400 . 500 . 600 on. In each case, there is a transmission connection 400 . 500 . 600 formed between two gear stage members associated with each other by a pair, one gear stage member each of a first planetary gear stage 100 and one of the remaining other second planetary gear stages 200 , The Getriebestufenorgane of a pair so formed are the respective transmission connection 400 . 500 . 600 assigned.

Advantageously, at least one of the transmission connections is used 400 . 500 . 600 a rotary om entabstützung.

Preferred for this purpose is one of the transmission connections 400 . 500 . 600 set as a frame of the transmission and / or fixed to a frame of the transmission.

The transmission connection is preferred 500 between the second central wheel 105 the first planetary gear stage 100 and the second central wheel 206 the second planetary gear stage 200 set as a frame of the transmission and / or fixed to a frame of the transmission. This allows an execution of the second central wheel 105 the first planetary gear stage 100 and the second central wheel 206 the second planetary gear stage 200 each as a ring gear with internal teeth. In this case, the two ring gears together at least a portion of an example, stationary housing of the transmission 1000 form.

It is important to emphasize that at least one of the gear connections serves for a torque support, in that two of the gearbox connections form a circumferential kinematic chain and the remaining gearbox connection and the transmission elements connected to them via the gear elements which interact with them. The revolving kinematic chain, together with the superimposed connection, can produce a movable support which forms a torque support.

In other words, the constraint also includes the fact that the three gearboxes can together produce a movable support that forms a torque support.

Two of the transmission connections 400 . 500 , hereinafter referred to as a first transmission connection 400 and as a second transmission connection 500 referred form with the gear stage members of the planetary gear stages 100 . 200 at unmoved output member a closed circumferential kinematic chain.

Each of the transmission connections 400 . 500 forms hereinafter each one member of the closed circumferential kinematic chain.

One of the three transmission connections 400 . 500 . 600 , hereinafter referred to as third transmission connection 600 refers to working with at least one of the remaining two transmission connections 400 . 500 together.

Through the third transmission connection 600 It is achieved that a comparable transmission ratio between the Getriebestufenorganen prevails as a result of this in unmoved output member, as is the case within the kinematic chain.

In this regard, the advantageous as the frame of the transmission fixed transmission connection 500 at least in thought not set for torque support.

Preferably, the input member acts with the planet carrier 101 the first planetary gear stage 100 together. Preferably, the input member with the planet carrier 101 the first planetary gear stage 100 directly connected, includes or is covered by this.

Preferably, the output member acts with the planet carrier 210 the second planetary gear stage 200 together. Preferably, the output member is connected to the planet carrier 210 the second planetary gear stage 200 directly connected, includes or is covered by this.

In a suitably trained transmission 1000 act the input member and the output member with the Planetenradträgern 101 . 210 the two planetary gear stages 100 . 200 together. It is characterized by three, excluding an immediate direct connection between the planet carrier 101 . 210 the two planetary gear stages 100 . 200 , In each case a Getriebestufenorgan the first planetary gear stage 100 with a gear stage member of the second planetary gear stage 200 connecting transmission connections 400 . 500 . 600 between each of a gear stage member of the first planetary gear stage 100 and a gear stage member of the second planetary gear stage 200 formed pairs of Getriebestufenorganen the two planetary gear stages 100 . 200 ,

Preferably, a first transmission connection 400 a direct non-rotatable shaft connection between the two with the planetary gears 102 . 208 the two planetary gear stages 100 . 200 meshing, primary gears forming first central wheels 104 . 209 the two planetary gear stages 100 . 200 in front. Here are the two primary gears forming the first central wheels 104 . 209 the two planetary gear stages 100 . 200 through a primary wave 401 non-rotatably connected.

Preferably, a second transmission connection 500 a direct non-rotatable shaft connection between those with the planetary gears 102 . 208 the two planetary gear stages 100 . 200 meshing, secondary gears forming second central wheels 105 . 206 the two planetary gear stages 100 . 200 in front. The two are each a secondary gear forming second central wheels 105 . 206 the two planetary gear stages 100 . 200 through a secondary shaft 501 non-rotatably connected.

A second central wheel 105 the two by means of the second transmission connection 500 non-rotatably connected to each other secondary gears forming second central wheels 105 . 206 meshes with a toothing of the at least one planetary gear 102 the first planetary gear stage 100 , The remaining second central wheel 206 the two by means of the second transmission connection 500 non-rotatably connected to each other secondary gears forming second central wheels 105 . 206 meshes with a toothing of the at least one planetary gear 208 the second planetary gear stage 200 ,

Preferably prevails along the second transmission connection 500 another gear ratio between the two planetary gear stages 100 . 200 as along the first transmission connection 400 ,

In this consideration, at least theoretically neither the advantageous as the frame of the transmission fixed transmission connection 500 still the transmission connection 400 set for torque support.

The toothing of the one planetary gear 102 . 208 one of the two planetary gear stages 100 . 200 , with which the secondary gears of the second transmission connection 500 Comb, differ from that gearing, with the central wheels 104 . 209 the two planetary gear stages 100 . 200 comb.

• - ein unverdrehbar mit dem Eingangs-Umlaufrad 2 verbundenes Rad 3 mit einem vom Außendurchmesser des Eingangs-Umlaufrads 2 unterschiedlichen Außendurchmesser für das Planetenrad 102 der ersten Planetengetriebestufe 100 und
• - durch ein unverdrehbar mit dem Ausgangs-Umlaufrad 7 verbundenes Rad 8 mit einem vom Außendurchmesser des Ausgangs-Umlaufrads 7 unterschiedlichen Außendurchmesser für das Planetenrad 208 der zweiten Planetengetriebestufe 200 Rechnung getragen.

This circumstance is in 1 . 2 . 3 by

• - a non-rotatable with the input pulley 2 connected bike 3 with one of the outer diameter of the input Umlaufrads 2 different outer diameter for the planetary gear 102 the first planetary gear stage 100 and
• - By a non-rotatable with the output planetary gear 7 connected bike 8th with one of the outer diameter of the output Umlaufrads 7 different outer diameter for the planetary gear 208 the second planetary gear stage 200 Taken into account.

• - beide als Stirnräder mit Außenverzahnungen als Verzahnungen oder
• - beide als Hohlräder mit Innenverzahnungen als Verzahnungen oder
• - eines als Stirnrad mit Außenverzahnung als dessen Verzahnung und
• - eines als Hohlrad mit Innenverzahnung als dessen Verzahnung ausgeführt sein.

The two are non-rotatable with each other via the secondary shaft 501 connected, secondary gears forming second central wheels 105 . 206 the second transmission connection 500 can

• - Both as spur gears with external teeth as gears or
• - Both as ring gears with internal gears as gears or
• - One as a spur gear with external teeth as its teeth and
• - Be executed as a ring gear with internal teeth as the toothing.

A third transmission connection 600 preferably sees one of the first gear connection 400 and / or the second transmission connection 500 Stiffening between two Getriebestufenorganen the two planetary gear stages 100 . 200 in front.

• - den Planetenradträger 101 der ersten Planetengetriebestufe 100,
• - das mindestens eine Planetenrad 102 der ersten Planetengetriebestufe 100,
• - die zweite Getriebeverbindung 500 mit den durch die Sekundärwelle 501 unverdrehbar verbundenen, jeweils mit einer Verzahnung des mindestens einen Planetenrads 102 der ersten Planetengetriebestufe 100 und mit einer Verzahnung des mindestens einen Planetenrads 208 der zweiten Planetengetriebestufe 200 kämmenden zweiten Zentralrädern 105, 206,
• - das mindestens eine Planetenrad 208 der zweiten Planetengetriebestufe 200,
• - die erste Getriebeverbindung 400 mit den durch die Primärwelle 401 unverdrehbar verbundenen, jeweils mit einer Verzahnung des mindestens einen Planetenrads 102 der ersten Planetengetriebestufe 100 und mit einer Verzahnung des mindestens einen Planetenrads 208 der zweiten Planetengetriebestufe 200 kämmenden ersten Zentralrädern 104, 209 der beiden Planetengetriebestufen 100, 200,
• - und wieder das mindestens eine Planetenrad 102 der ersten Planetengetriebestufe 100 gebildeten umlaufenden kinematischen Kette zwischen dem Planetenradträger 101 der ersten Planetengetriebestufe 100 und dem mindestens einen Planetenrad 208 der zweiten Planetengetriebestufe 200.

This through the third transmission connection 600 formed stiffener has a gear ratio, which is comparable to the gear ratio, in an unmoved planet carrier 210 the second planetary gear stage 200 prevails and is achieved by:

• - the planet carrier 101 the first planetary gear stage 100 .
• - The at least one planetary gear 102 the first planetary gear stage 100 .
• - The second transmission connection 500 with the through the secondary shaft 501 non-rotatably connected, each with a toothing of the at least one planetary gear 102 the first planetary gear stage 100 and with a toothing of the at least one planetary gear 208 the second planetary gear stage 200 meshing second central wheels 105 . 206 .
• - The at least one planetary gear 208 the second planetary gear stage 200 .
• - the first transmission connection 400 with those through the primary wave 401 non-rotatably connected, each with a toothing of the at least one planetary gear 102 the first planetary gear stage 100 and with a toothing of the at least one planetary gear 208 the second planetary gear stage 200 meshing first central wheels 104 . 209 the two planetary gear stages 100 . 200 .
• - and again the at least one planetary gear 102 the first planetary gear stage 100 formed circulating kinematic chain between the planet carrier 101 the first planetary gear stage 100 and the at least one planetary gear 208 the second planetary gear stage 200 ,

Such a transmission 1000 can by a in 1 . 2 . 3 and 6 shown device for torque and output speed change be realized depending on the driving resistance, which is designed in the form of a rotating kinematic chain with a stiffener.

• - einen mit dem Eingangsorgan in Wirkverbindung stehenden und/oder vom Eingangsorgan umfassten und/oder das Eingangsorgan umfassenden Eingangs-Planetenradträger 1,
• - ein Eingangs-Umlaufrad 2 mit einem unverdrehbar mit diesem verbundenen Rad 3 anderen Durchmessers, nachfolgend vereinfacht durch den Ausdruck Eingangs-Umlaufrad 2-3 beschrieben,
• - einen Satz Sonnenräder 4, 9,
• - einen Satz Zentralräder 5, 6,
• - ein Ausgangs-Umlaufrad 7 mit einem unverdrehbar mit diesem verbundenen Rad 8 anderen Durchmessers, nachfolgend vereinfacht durch den Ausdruck Ausgangs-Umlaufrad 7-8 beschrieben, und
• - einen mit dem Ausgangsorgan in Wirkverbindung stehenden und/oder vom Ausgangsorgan umfassten und/oder das Ausgangsorgan umfassenden Ausgangs-Planetenradträger 10.

The facility includes:

• a input planetary gear carrier 1, which is in operative connection with the input member and / or encompassed by the input member and / or which comprises the input member,
• - an input pulley 2 with a non-rotatable wheel connected to it 3 other diameter, hereafter simplified by the term input orbital gear 2-3 described,
• - a set of sun gears 4 . 9 .
• - a set of central wheels 5 . 6 .
• an output planetary gear 7 with a non-rotatable wheel connected to it 8th other diameter, hereinafter simplified by the term output orbital 7-8 described, and
• - One with the output member operatively connected and / or encompassed by the output member and / or the output member comprehensive output planet carrier 10 ,

The device has a gear ratio
u _1-7
from the input planet carrier 1 to the output planetary gear 7 on.

In this case, at least one member of the revolving kinematic chain and / or the stiffening of a torque support can serve.

For example, this may be a member of the rotating kinematic chain or the stiffening defined as a frame of the transmission and / or fixed to a frame of the transmission.

Alternatively or additionally, the revolving kinematic chain together with the superimposed connection can produce a movable support which forms a torque support.

• die Versteifung in Form einer kinematischen Kette mit einem zusätzlichen Zahnradgetriebe ausgebildet ist und
• das zusätzliche Zahnradgetriebe ein ähnliches Übersetzungsverhältnis $$u_{}$$$${}_{1-7ad}={\mathrm{<figure-callout\; id="1"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{1-7}$$
  
  sicherstellt, wobei $$u_{1-7}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]},u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4},u_{96}^{\left(10\right)}=-\frac{z_6{z}_8}{z_7{z}_9},u_{76}^{\left(10\right)}=\frac{z6}{z7},$$
  
  $${\mathrm{<figure-callout\; id="1"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{1-7ad}=\frac{{\mathrm{<figure-callout\; id="11"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-{\mathrm{<figure-callout\; id="11"\; label="u"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">u</figure-callout>}}_{11-5}^{\left(1\right)}\right]},u_{12-6}^{\left(10\right)}=-\frac{z_6}{{\mathrm{<figure-callout\; id="12"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_{12}}$$
  

ist.The device is also advantageous in that:

• the stiffening in the form of a kinematic chain is formed with an additional gear transmission and
• the additional gear transmission a similar gear ratio $$u_{1-7ad}=u_{1-7}$$
  
  making sure $$u_{1-7}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]}.u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4}.u_{96}^{\left(10\right)}=-\frac{z_6{z}_{\mathrm{8th}}}{z_7{z}_9}.u_{76}^{\left(10\right)}=\frac{z6}{z7}.$$
  
  $$u_{1-7ad}=\frac{u_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{11-5}^{\left(1\right)}\right]}.u_{12-6}^{\left(10\right)}=-\frac{z_6}{z_{12}}$$
  

is.

• - eine Verbindung zwischen als Eingangs-Umlaufrad 2 bezeichneten Planetenrad 102 der ersten Planetengetriebestufe 100 und dem als Ausgangs-Umlaufrad 7 bezeichneten Planetenrad 208 der zweiten Planetengetriebestufe 200 mittels zweier zusätzlicher erster Zentralräder vor,
• - die über eine Welle unverdrehbar miteinander verbunden sind.

Preferably, the third gear connection 600 in a transmission described above, which can be realized by means of a previously mentioned device 1000 :

• - A connection between as an input pulley 2 designated planetary gear 102 the first planetary gear stage 100 and as the output planetary gear 7 designated planetary gear 208 the second planetary gear stage 200 by means of two additional first central wheels,
• - Which are non-rotatably connected to each other via a shaft.

This stiffening points two through a tertiary wave 601 interconnected, designed as additional first central wheels tertiary gears 111 . 212 on, one of which with a toothing of a planetary gear 102 the first planetary gear stage 100 and the other with a toothing of the one planetary gear 208 the second planetary gear stage 200 combs.

The toothing of the one planetary gear 102 . 208 one of the two planetary gear stages 100 . 200 , with which the non-rotatably connected tertiary gears 111 . 212 the third transmission connection 600 Comb, differ from the gearing, with the primary wave 401 non-rotatably interconnected primary gears forming first central wheels 104 . 209 or at least one of the through the secondary shaft 501 non-rotatably connected to each other secondary gears forming second central wheels 105 . 206 comb.

This circumstance is in 1 . 2 . 3 by a non-rotatable with the input-impeller 2 connected bike 3 with one of the outer diameter of the input Umlaufrads 2 different outer diameter for the planetary gear 102 the first planetary gear stage 100 and by a non-rotatable with the output planetary gear 7 connected bike 8th with an outside diameter of the original Umlaufrads 7 different outer diameter for the planetary gear 208 the second planetary gear stage 200 Taken into account. The first transmission connection acts 400 with those through the sun gears 4 . 9 formed first central wheels 104 . 209 with the wheels 2 and 8th the planet wheels 102 and 208 together. On the other hand, the wheels designed as additional sun gears act 11 . 12 and about the tertiary wave 601 connected as additional first central wheels running tertiary gears 111 . 212 with the wheels 3 and 7 the planet wheels 102 and 208 together. As a result, different transmission ratios along the first transmission connection 400 and along the third transmission link 600 ensured. The over the secondary shaft 501 non-rotatable second central wheels 105 . 206 Although also work with the wheels 3 and 7 the planet wheels 102 and 208 together, however, this pairing of the second gear connection 500 due to the larger diameter of the second central wheels 105 . 206 towards the means of the third transmission connection 600 interconnected, as additional first central wheels running tertiary gears 111 . 212 another gear ratio.

A transmission described above 1000 realizing device for torque and output speed change depending on driving resistance is in 1 shown in whole or in part.

The device is designed in the form of a revolving kinematic chain with a superimposed connection. The device includes an input planet carrier 1 , an input pulley 2 with a non-rotatable wheel connected to it 3 , a set of sun gears 4 . 9 , a set of central wheels 5 . 6 , an output planetary gear 7 with a non-rotatable wheel connected to it 8th , a driven-side planet carrier 10 and has a gear ratio μ1-7 from the input planet carrier 1 to the output planetary gear 7 , The stiffening is designed in the form of a kinematic chain with an additional gear transmission. The gear transmission is in the form of a set of sun gears 11 . 12 educated. The set of sun gears contains a wheel 11 that with the non-rotatable with the input-impeller 2 connected wheel 3 coupled, and a wheel 12 that with the output planetary gear 7 is coupled. This gear mechanism ensures a similar gear ratio μ1-7ad = μ1-7.

Advantageously, the stiffening in conjunction with the revolving kinematic chain generates a movable support, which forms a torque support.

Alternatively or additionally, at least one member of the revolving kinematic chain or the stiffening advantageously serves as a torque support.

In the event that at least one member of the revolving kinematic chain or the stiffening of an alternative torque support is used, for example, at least one member of the revolving kinematic chain or the stiffener can be set as a frame of the transmission and / or fixed to a frame of the transmission.

• zi wobei i = 1, 2, 3, 4, 5, 6, 7, 8, 9, 11, 12 (Zahnzahlen bei Zahnrädern) ist,
• µ Übersetzungsverhältnis,
• r Radius,
• ω Drehgeschwindigkeit.

In describing the function of the device according to the invention, the following terms are used:

• zi where i = 1, 2, 3, 4, 5, 6, 7, 8, 9, 11, 12 (numbers of teeth in gears),
• μ gear ratio,
• radius,
• ω rotational speed.

How the device works:

The input shaft 0 transmits the movement from the input planet carrier 1 on the input planetary gear 2 and the non-rotatable with this connected wheel 3 , The input pulley 2 and the non-rotatable with this connected wheel 3 transfer the movement to the gears 4 and 5 , The over the primary wave 401 wheels non-rotatably connected to a wheel set 4 . 9 and the over the secondary shaft 501 wheels non-rotatably connected to a wheel set 5 . 6 transfer the movement to the output planetary gear 7 , on that with this non-rotatably connected wheel 8th as well as on the output planet carrier 10 , At the same time transmits the kinematic chain with the through the wheels 3 . 11 . 12 . 7 formed additional gear transmission, the movement of the input planet carrier 1 and the input planetary gear 2 and the non-rotatably connected to this wheel 3 on the output planetary gear 7 as well as the non-rotatably connected to this wheel 8th , The wheels 11 . 12 are about the tertiary wave 601 non-rotatable to a third transmission connection 600 forming wheelset interconnected.

The gear ratio of the kinematic chain with that through the wheels 3 . 11 . 12 . 7 formed additional gear transmission (from the input planet carrier 1 to the output planetary gear 7 and the non-rotatably connected to this wheel 8th ) and the gear ratio of the kinematic chain without by the wheels 3 . 11 . 12 . 7 formed additional gear transmission (from the input planet carrier 1 to the output planetary gear 7 and the non-rotatably connected to this wheel 8th ) are identical.

The same gear ratios of the planetary gear and the kinematic chain with the additional gear transmission are defined below.

The relationship between the rotational speeds of the wheels 4 and 5 of a gearbox 1000 the first planetary gear stage 100 forming first planetary gear set at immovable planet carrier 1 is described as follows $$\frac{{\omega }_4-{\mathrm{<figure-callout\; id="1"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_1}{{\omega }_5-{\mathrm{<figure-callout\; id="1"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_1}=u_{45}^{\left(1\right)}$$

das Übersetzungsverhältnis der Räder 4 und 5 beim unbeweglichen $$u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4}.u_{11-5}^{\left(1\right)}=-\frac{z_5}{z_4}$$

Planetenradträger 1.It is $u_{45}^{\left(1\right)}$

the gear ratio of the wheels 4 and 5 at immovable $$u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{\mathrm{<figure-callout\; id="4"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_4},u_{11-5}^{\left(1\right)}=-\frac{z_5}{{\mathrm{<figure-callout\; id="4"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_4}$$

planet 1 ,

The relationship between the rotational speeds of the wheels 9 and 6 at the stationary planet carrier 10 is described as follows: $$\frac{{\omega }_9-{\mathrm{<figure-callout\; id="10"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_{10}}{{\omega }_6-{\mathrm{<figure-callout\; id="10"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_{10}}=u_{96}^{\left(10\right)}$$

das Übersetzungsverhältnis der Räder 9 und 6 beim unbeweglichen Planetenradträger 10. $$u_{96}^{\left(10\right)}=-\frac{z_6{z}_8}{z_7{z}_9}.u_{12-6}^{\left(10\right)}=-\frac{z_6}{z_{12}}$$

Man schaffe die Zwischen-Drehgeschwindigkeit ω₉ = ω₄ aus den Gleichungen (1) und (2) fort. Unter Berücksichtigung von ω₅ = ω₆ ergibt dies beim unbeweglichen Planetenradträger 10 (ω₁₀ = 0) $${\omega }_6=-{\omega }_1\frac{1-u_{45}^{\left(1\right)}}{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}$$

It is $u_{96}^{\left(10\right)}$

the gear ratio of the wheels 9 and 6 at the stationary planet carrier 10 , $$u_{96}^{\left(10\right)}=-\frac{z_6{z}_{\mathrm{8th}}}{z_7{\mathrm{<figure-callout\; id="9"\; label="z"\; filenames="DE212018000129U1\_0059.png,DE212018000129U1\_0060.png"\; state="\{\{state\}\}">z</figure-callout>}}_9},u_{12-6}^{\left(10\right)}=-\frac{z_6}{{\mathrm{<figure-callout\; id="12"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_{12}}$$

Make the intermediate rotational speed ω ₉ = ω ₄ from equations (1) and (2). Taking into account ω ₅ = ω ₆ , this results in the immovable planet carrier 10 (ω ₁₀ = 0) $${\mathrm{<figure-callout\; id="6"\; label="\omega "\; filenames="DE212018000129U1\_0057.png,DE212018000129U1\_0058.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_6=-{\mathrm{<figure-callout\; id="1"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_1\frac{1-u_{45}^{\left(1\right)}}{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}$$

The relationship between the rotational speeds of the wheels 7 and 6 of a gearbox 1000 the second planetary gear stage 200 forming second planetary gear set at immovable planet carrier 10 looks like this: $$\frac{{\omega }_7-{\mathrm{<figure-callout\; id="10"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_{10}}{{\omega }_6-{\mathrm{<figure-callout\; id="10"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_{10}}=u_{76}^{\left(10\right)}$$

das Übersetzungsverhältnis der Räder 7 und 6 beim unbeweglichen Planetenradträger 10. $$u_{76}^{\left(10\right)}=\frac{z_6}{z_7}.$$

Bei ω₁₀ = 0 aus der Gleichung (4) beträgt $${\omega }_6=\frac{{\omega }_7}{u_{76}^{\left(10\right)}}.$$

It is $u_{76}^{\left(10\right)}$

the gear ratio of the wheels 7 and 6 at the stationary planet carrier 10 , $$u_{76}^{\left(10\right)}=\frac{z_6}{z_7},$$

At ω ₁₀ = 0 from equation (4) $${\omega }_6=\frac{{\omega }_7}{u_{76}^{\left(10\right)}},$$

der Glieder 1 und 7 der Umlaufkette 1-2-3-5-6-7-8-9-4-2 $$u_{17}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]}$$

Substituting this value into the equation (3) gives an equation for the relationship of the rotational speeds of the links 1 and 7 , From this equation, the gear ratio results $u_{17}=\frac{{\mathrm{<figure-callout\; id="1"\; label="\omega "\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_1}{{\omega }_7}$

the limbs 1 and 7 the circulation chain 1 - 2 - 3 - 5 - 6 - 7 - 8th - 9 - 4 - 2 $${\mathrm{<figure-callout\; id="17"\; label="u"\; filenames="DE212018000129U1\_0056.png"\; state="\{\{state\}\}">u</figure-callout>}}_{17}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]}$$

durch $u_{11-5}^{\left(1\right)}=-\frac{z_5}{z_4}$

und Substitution $u_{96}^{\left(10\right)}$

durch $u_{12-6}^{\left(10\right)}=-\frac{z_6}{z_{12}}.$

$$u_{1-7ad}=-\frac{u_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{11-5}^{\left(1\right)}\right]}$$

The kinematic chain with the through the wheels 3 . 11 . 12 . 7 formed additional gear transmission copies the translation of the gears of the circulation chain 1 - 2 - 3 - 5 - 6 - 7 -8-9-4-2 in the form of a wheelset 11 - 12 that the gear 11 coupled with the wheel 3 of the input planetary gear 2 and the gear 12 coupled with the wheel 7 of the output planetary gear 7 contains, and has a similar gear ratio. The gear ratio u _{1-7ad of} the kinematic chain, which by the wheels 3 . 11 . 12 . 7 formed additional gear results from the equation (5) by means of substitution $u_{45}^{\left(1\right)}$

by $u_{11-5}^{\left(1\right)}=-\frac{z_5}{{\mathrm{<figure-callout\; id="4"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_4}$

and substitution $u_{96}^{\left(10\right)}$

by $u_{12-6}^{\left(10\right)}=-\frac{z_6}{z_{12}},$

$$u_{1-7ad}=-\frac{u_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{11-5}^{\left(1\right)}\right]}$$

The kinematic chain with the additional gear transmission has the same gear ratio as the revolving kinematic chain $$u_{1-7ad}=u_{1-7}$$

The condition of equality of gear ratios ( 7 ) makes it possible to select or adjust the numbers of teeth in gears of the additional transmission based on the given gear numbers of the rotating kinematic chain.

The additional connection reduces the number of degrees of freedom of the chain by one unit. This leads to the fact that the movement becomes definable and the functionality and the efficiency increase. The additional connection also acts as a copy (alternative) connection. This ensures that the adaptability of the kinematic chain with two degrees of freedom is maintained depending on the variable force load.

Alternatively, the third transmission connection 600 another connection between the at least one, as an input-impeller 2 designated planetary gear 102 the first planetary gear stage 100 and the at least one, also as an output planetary gear 7 designated planetary gear 208 the second planetary gear stage 200 by means of two additional, over a tertiary wave 601 non-rotatably interconnected second central wheels as Tertiärzahnräder 111 . 212 provide. This stiffener has two by one, for example as in 2 shown, formed as a hollow shaft tertiary wave 601 interconnected, designed as additional second central gears tertiary gears 111 . 212 on, one of which with a toothing of the at least one planetary gear 102 the first planetary gear stage 100 and the other with a toothing of the at least one planetary gear 208 the second planetary gear stage 200 combs.

The gears of the planet gears 102 . 208 one of the two planetary gear stages 100 . 200 with which the tertiary gears 111 . 212 the third transmission connection 600 Comb, differ from those gears, with second central wheels 105 . 206 comb. As a result, different transmission ratios of the transmission connections 400 . 500 . 600 ensured.

A device with a gearbox 1000 for torque and output speed change depending on driving resistance is in 2 shown in whole or in part.

The device is designed in the form of a revolving kinematic chain (kinematic circulation chain) with a superimposed connection (stiffening). The device includes an input planet carrier 1 , an input pulley 2 with a non-rotatable wheel connected to it 3 , a set of sun gears 4 . 9 , a set of central wheels 5 . 6 , an output planetary gear 7 with a non-rotatable wheel connected to it 8th , a driven-side planet carrier 10 and has a gear ratio μ1-7 from the input planet carrier 1 to the output planetary gear 7 , The stiffening is designed in the form of a kinematic chain with an additional gear transmission.

The additional gear, which is the translation of the gears through the input planet carrier 1 and the wheels 2 . 3 . 5 . 6 . 7 . 8th . 9 . 4 formed circulatory chain 1 - 2 - 3 - 5 - 6 - 7 - 8th - 9 - 4 copied, may be formed in the form of a set of central wheels. The set of central wheels contains a gear wheel 11 that with the wheel 2 of the input planetary gear 2 coupled, and a gear 12 that with the wheel 8th of the output planetary gear 7 is coupled. This transmission, accordingly 2 , ensures a similar transmission ratio.

The device is in the form of a through the input planet carrier 1 and the wheels 2 . 3 . 5 . 6 . 7 . 8th . 9 . 4 formed circumferential kinematic chain 1 - 2 - 3 - 5 - 6 - 7 -8-9-4 with a superimposed connection with a gear ratio u _{1-7 of} the input planet gear carrier 1 up to the two non-rotatably connected wheels 7 . 8th of the output planetary gear 7 educated.

The stiffening is in the form of a kinematic chain with an additional gear transmission, with a similar transmission ratio u _{1-8ad is} ensured.

durch $u_{4-11}^{\left(1\right)}=\frac{z_{11}}{z_4},$

Substitution $u_{96}^{\left(10\right)}$

durch $u_{9-12}^{\left(10\right)}=-\frac{z_{12}}{z_9}$

undThe gear ratio u _1-8ad by the input planet _carrier 1 and the wheels 2 . 11 . 12 . 8th formed kinematic chain 1 - 2 - 11 - 12 - 8th containing the additional gear is obtained from Equation (5) by substitution $u_{45}^{\left(1\right)}$

by $u_{4-11}^{\left(1\right)}=\frac{z_{11}}{{\mathrm{<figure-callout\; id="4"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_4}.$

substitution $u_{96}^{\left(10\right)}$

by $u_{9-12}^{\left(10\right)}=-\frac{z_{12}}{{\mathrm{<figure-callout\; id="9"\; label="z"\; filenames="DE212018000129U1\_0059.png,DE212018000129U1\_0060.png"\; state="\{\{state\}\}">z</figure-callout>}}_9}$

and

durch $u_{8-12}^{\left(10\right)}=-\frac{z_{12}}{z_8}.$

$$u_{1-8ad}=-\frac{u_{4-11}^{\left(1\right)}-u_{9-12}^{\left(10\right)}}{u_{8-12}^{\left(10\right)}\left[1-u_{4-11}^{\left(1\right)}\right]}$$

substitution $u_{76}^{\left(10\right)}$

by $u_{\mathrm{8th}-12}^{\left(10\right)}=-\frac{z_{12}}{z_{\mathrm{8th}}},$

$$u_{1-\mathrm{8th}ad}=-\frac{u_{4-11}^{\left(1\right)}-u_{9-12}^{\left(10\right)}}{u_{\mathrm{8th}-12}^{\left(10\right)}\left[1-u_{4-11}^{\left(1\right)}\right]}$$

The kinematic chain 1 - 2 - 11 - 12 - 8th with the additional gear transmission has the same gear ratio ( 5 ) like that of the circulating kinematic chain 1 -2-3-5-6-7-8-9-4, corresponding to: $$u_{1-\mathrm{8th}ad}=u_{1-7}$$

The condition of equality of gear ratios ( 7 ) makes it possible to select / adjust the numbers of teeth in gears of the additional transmission based on the given gear numbers of the rotating kinematic chain.

Alternatively, the third transmission connection 600 a connection between that as an input planet carrier 1 designated planet carrier 101 the first planetary gear stage 100 and the at least one, also as an output planetary gear 7 designated planetary gear 208 the second planetary gear stage 200 , provide. Here is the planet carrier 101 the first planetary gear stage 100 over a tertiary wave 601 non-rotatable with a designed as an additional sun gear or an additional first central Tertiary gear 111 connected. This one tertiary gear 111 meshes with one with the at least one also as the output planetary gear 7 designated planetary gear 208 the second planetary gear stage 200 non-rotatably connected other tertiary gear 212 ,

A device with a gearbox 1000 for torque and output speed change depending on driving resistance is in 3 shown in whole or in part.

The device is designed in the form of a revolving kinematic chain (kinematic circulation chain) with a superimposed connection (stiffening). The device includes an input planet carrier 1 , an input pulley 2 with a non-rotatable wheel connected to it 3 , a set of sun gears 4 . 9 , a set of central wheels 5 . 6 , an output planetary gear 7 with a non-rotatable wheel connected to it 8th , a driven-side planet carrier 10 and has a gear ratio μ1-7 from the input planet carrier 1 to the output planetary gear 7 , The stiffening is designed in the form of a kinematic chain with an additional gear.

The additional gear can, as in 3 represented in the form of a transmission from the input planet carrier 1 to the output planetary gear 7 be educated. The gearbox contains a wheel 11 that is non-rotatable with the input planet carrier 1 connected, and a wheel 12 that is non-rotatable with the output planetary gear 7 and with the non-rotatable wheel connected to it 8th connected is. This the input planet carrier 1 and the wheels 11 . 12 . 7 comprehensive gearbox copies the rotating kinematic chain 1 - 2 - 3 - 5 - 6 - 7 - 8th - 9 - 4 from the input planet carrier 1 to the output planetary gear 7 and has a similar gear ratio u _1-7ad .

The gear ratio u _1-7ad by the input planet _carrier 1 and the wheels 11 . 12 . 7 comprehensive gear formed kinematic chain 1 - 11 -12-7 looks like this: $$u_{1-7ad}=-\frac{z_{12}}{{\mathrm{<figure-callout\; id="11"\; label="z"\; filenames="DE212018000129U1\_0056.png,DE212018000129U1\_0057.png"\; state="\{\{state\}\}">z</figure-callout>}}_{11}}$$

The kinematic chain 1 - 11 - 12 - 7 with the additional gear transmission has the same gear ratio ( 5 ) like that of the circulating kinematic chain 1 -2-3-5-6-7-8-9-4, corresponding to: $$u_{1-7ad}=u_{1-7}$$

The condition of equality of gear ratios ( 11 ) makes it possible to select / adjust the numbers of teeth in gears of the additional gear on the basis of the predetermined numbers of teeth of the rotating kinematic chain.

A simplified embodiment of one in its function of previously in connection with 3 described device corresponding transmission 1000 is in 4 . 5 and 6 shown.

The design is opposite 3 simplified to the effect that neither the input pulley 2 as the planetary gear 102 the first planetary gear stage 100 two non-rotatably connected wheels 2 . 3 different outer diameter for cooperation with the first gear connection 400 and with the second transmission connection 500 includes, nor the output planetary gear 7 as the planetary gear 208 the second planetary gear stage 200 two non-rotatably connected wheels 7 . 8th different outer diameter for cooperation with the first gear connection 400 and with the second transmission connection 500 includes.

Instead, in the simplified embodiment according to 4 . 5 and 6 one by a single wheel 2 - 3 formed common input-impeller 2 and one by a wheel 7 - 8th and a non-rotatably connected to this wheel 12 formed common output planetary gear 7 intended. Different transmission ratios are here by different radii and thus numbers of teeth of the input planetary gear 2 or of the planetary gear 102 the first planetary gear stage 100 and the output planetary gear 7 or of the planetary gear 208 the second planetary gear stage 200 and by different radii or numbers of teeth as ring gears with internal teeth trained central wheels 5 . 6 or second central wheels 105 . 206 the two planetary gear stages 100 . 200 and by different radii or numbers of teeth designed as spur gears with external gears sun gears 2 . 9 or first central wheels 102 . 209 the two planetary gear stages 100 . 200 ensured.

• Die Räder 2 und 3 sind als ein Rad 2-3 mit z₂ = z₃ ausgebildet.
• Die Räder 7 und 8 sind als ein Rad 7-8 mit z₈ = z₇ ausgebildet.

Opposite the in 3 The device shown is the in 6 shown, one in 4 . 5 and 6 illustrated transmission 1000 , Implementing device also shown somewhat simplified. The following simplifications apply:

• The wheels 2 and 3 are as a wheel 2 - 3 formed with z ₂ = z. ₃
• The wheels 7 and 8th are as a wheel 7 - 8th formed with z ₈ = z ₇ .

• einen mit einem Eingangsorgan zusammenwirkenden Planetenradträger 101 der ersten Planetengetriebestufe 100 (Getriebe 1000) beziehungsweise einen mit einer Eingangswelle 0 verbundenen Eingangs-Planetenradträger 1 (Einrichtung),
• als Teil der dritten Getriebeverbindung 600 eine unverdrehbar mit dem Planetenradträger 101 der ersten Planetengetriebestufe 100 verbundene Tertiärwelle 601 und ein unverdrehbar mit dieser verbundenes Tertiärzahnrad 111 (Getriebe 1000) beziehungsweise ein unverdrehbar mit dem Eingangs-Planetenradträger 1 verbundenes Rad 11 (Einrichtung),
• ein Planetenrad 102 der ersten Planetengetriebestufe 100 (Getriebe 1000) beziehungsweise ein durch ein Rad 2-3 gebildetes Eingangs-Umlaufrad 2 (Einrichtung),
• als erste Getriebeverbindung 400 zwei über eine Primärwelle 401 unverdrehbar miteinander verbundene erste Zentralräder 104, 109 der beiden Planetengetriebestufen 100, 200 (Getriebe 1000) beziehungsweise einen Satz unverdrehbar miteinander verbundener Sonnenräder 4, 9 (Einrichtung),
• als zweite Getriebeverbindung 500 zwei über eine Sekundärwelle 501 unverdrehbar miteinander verbundene zweite Zentralräder 105, 206 der beiden Planetengetriebestufen 100, 200 (Getriebe 1000) beziehungsweise einen Satz unverdrehbar miteinander verbundener Zentralräder 5, 6 (Einrichtung),
• ein Planetenrad 208 der zweiten Planetengetriebestufe 100 sowie ein unverdrehbar mit diesem verbundenes Tertiärzahnrad 212 als verbleibender Teil der dritten Getriebeverbindung 600 (Getriebe 1000) beziehungsweise ein durch ein Rad 7-8 und ein unverdrehbar mit diesem verbundenes Rad 12 gebildetes Ausgangs-Umlaufrad 7 (Einrichtung) und
• einen mit einem Ausgangsorgan zusammenwirkenden Planetenradträger 210 der zweiten Planetengetriebestufe 200 (Getriebe 1000) beziehungsweise einen mit einer Ausgangswelle verbundenen Ausgangs-Planetenradträger 10 (Einrichtung).

This in 4 . 5 and 6 shown gear or the in 6 The device for torque and output speed change shown includes the following components:

• a cooperating with an input member planet carrier 101 the first planetary gear stage 100 (Transmission 1000 ) or one with an input shaft 0 connected input planet carrier 1 (Facility),
• as part of the third transmission connection 600 a non-rotatable with the planet carrier 101 the first planetary gear stage 100 connected tertiary wave 601 and a non-rotatably connected with this tertiary gear 111 (Transmission 1000 ) or a non-rotatable with the input planet carrier 1 connected bike 11 (Facility),
• a planetary gear 102 the first planetary gear stage 100 (Transmission 1000 ) or one by a wheel 2 - 3 formed entrance pulley 2 (Facility),
• as the first transmission connection 400 two over a primary wave 401 non-rotatably interconnected first central wheels 104 . 109 the two planetary gear stages 100 . 200 (Transmission 1000 ) or a set of non-rotatably interconnected sun gears 4 . 9 (Facility),
• as second transmission connection 500 two over a secondary shaft 501 non-rotatably interconnected second central wheels 105 . 206 the two planetary gear stages 100 . 200 (Transmission 1000 ) or a set of non-rotatably interconnected central wheels 5 . 6 (Facility),
• a planetary gear 208 the second planetary gear stage 100 and a non-rotatably connected to this tertiary gear 212 as a remaining part of the third transmission connection 600 (Transmission 1000 ) or one by a wheel 7 - 8th and a non-rotatably connected to this wheel 12 formed output planetary gear 7 (Institution) and
• a cooperating with an output member planet carrier 210 the second planetary gear stage 200 (Transmission 1000 ) or one connected to an output shaft output planet carrier 10 (Facility).

The third transmission connection 600 is in the form of an additional gear transmission or gear train from the input planet carrier 1 to the output planetary gear 7 educated. The gear train contains a gear 11 and a bike 12 , The gear 11 is non-rotatable with the input planet carrier 1 connected via a wave. The wheel 12 is with the by the wheel 7 - 8th formed output planetary gear 7 non-rotatably connected. The additional gear train copies the rotating kinematic chain 1 - 2 - 3 - 5 - 6 - 7 - 8th - 9 - 4 from the input planet carrier 1 to the output planetary gear 7 and has a similar gear ratio u _1-7ad ,

5 shows an exploded view with the Getriebestufenorganen the two planetary gear stages 100 . 200 of the transmission according to the invention 1000 and the components of such a transmission 1000 realizing device according to the invention.

This in 4 and 5 illustrated gear 1000 has a first planetary gear stage 100 and a second planetary gear stage 200 on.

• - der dem Eingangs-Planetenradträger 1 der Einrichtung entsprechende Planetenradträger 101 der ersten Planetengetriebestufe 100,
• - das auf der parallel zur Zentralachse 300 mit dem Planetenradträger 101 um diese umlaufenden Planetenachse 301 drehbar angeordnete, dem durch das Rad 2-3 gebildeten Eingangs-Umlaufrad 2 der Einrichtung entsprechende Planetenrad 102 der ersten Planetengetriebestufe 100,
• - das dem Sonnenrad 4 der Einrichtung entsprechende erste Zentralrad 104 der ersten Planetengetriebestufe 100 und
• - das dem Zentralrad 5 der Einrichtung entsprechende zweite Zentralrad 105 der ersten Planetengetriebestufe 100.

The gear stage members of the first planetary gear stage 100 are:

• - the input planet carrier 1 the device corresponding planet carrier 101 the first planetary gear stage 100 .
• - that on the parallel to the central axis 300 with the planet carrier 101 around this orbiting planetary axis 301 rotatably arranged by the wheel 2 - 3 formed input-impeller 2 the device corresponding planetary gear 102 the first planetary gear stage 100 .
• - the sun wheel 4 the device corresponding first central wheel 104 the first planetary gear stage 100 and
• - the central wheel 5 the device corresponding second central wheel 105 the first planetary gear stage 100 ,

• - der dem Ausgangs-Planetenradträger 10 der Einrichtung entsprechende Planetenradträger 210 der zweiten Planetengetriebestufe 200,
• - das auf der parallel zur Zentralachse 300 mit dem Planetenradträger 210 um diese umlaufenden Planetenachse 302 drehbar angeordnete, dem durch das Rad 7-8 gebildeten Ausgangs-Umlaufrad 7 der Einrichtung entsprechende Planetenrad 208 der zweiten Planetengetriebestufe 200,
• - das dem Sonnenrad 9 der Einrichtung entsprechende erste Zentralrad 209 der zweiten Planetengetriebestufe 200 und
• - das dem Zentralrad 6 der Einrichtung entsprechende zweite Zentralrad 206 der zweiten Planetengetriebestufe 200.

The gear stage members of the second planetary gear stage 200 are:

• - the output planet carrier 10 the device corresponding planet carrier 210 the second planetary gear stage 200 .
• - that on the parallel to the central axis 300 with the planet carrier 210 around this orbiting planetary axis 302 rotatably arranged by the wheel 7 - 8th formed output planetary gear 7 the device corresponding planetary gear 208 the second planetary gear stage 200 .
• - the sun wheel 9 the device corresponding first central wheel 209 the second planetary gear stage 200 and
• - the central wheel 6 the device corresponding second central wheel 206 the second planetary gear stage 200 ,

The first transmission connection 400 sees a non-rotatable connection between the sun gears 4 . 9 the device corresponding first central wheels 104 . 209 the two planetary gear stages 100 . 200 in front. The first transmission connection 400 this includes one of the first central wheels 104 . 209 the two planetary gear stages 100 . 200 non-rotatably interconnecting primary shaft 401 ,

The second transmission connection 500 sees a non-rotatable connection between the central wheels 5 . 6 the device corresponding second central wheels 105 . 206 the two planetary gear stages 100 . 200 in front. The second transmission connection 500 For this purpose, one comprises the second central wheels 105 . 206 the two planetary gear stages 100 . 200 non-rotatably interconnecting secondary shaft 501 ,

The third transmission connection 600 is between the input planet carrier 1 the device corresponding planet carrier 101 the first planetary gear stage 100 and the output planetary gear 7 corresponding planetary gear 208 the second planetary gear stage 200 educated. For this purpose, the third transmission connection comprises a via a tertiary shaft 601 non-rotatable with the planet carrier 101 the first planetary gear stage 100 connected first tertiary gear 111 , which with a non-rotatable with the planetary gear 208 the second planetary gear stage 200 connected second tertiary gear 212 combs.

Accordingly, the device is a wheel 11 non-rotatable with the input planet carrier 1 and one with this bike 11 combing wheel 12 unrotatable with the by the wheel 7 - 8th formed output planetary gear 7 connected.

The operation of the transmission 1000 is analogous to the operation of the device described below.

The input shaft 0 transmits the movement from the input planet carrier 1 on that the input planetary gear 2 forming wheel 2 - 3 , This is the input planetary gear 2 forming wheel 2 - 3 transfers the movement to the sun gear 4 and the central wheel 5 , The one by the first central wheel 104 formed wheelset and the wheelset 5 - 6 transfer the movement to the output planetary gear 7 and the output planet carrier 10 , At the same time transmits the kinematic chain 1 - 11 - 12 - 7 with the third transmission connection 600 corresponding, the gear 11 and the wheel 12 comprehensive additional gear transmission the movement of the input planet carrier 1 and by the wheel 2 - 3 formed input-impeller 2 to that by the wheel 2 - 3 formed output planetary gear 7 ,

The gear ratio u _{1-7ad of} the kinematic chain 1 - 11 - 12 - 7 looks like this: $$u_{1-7ad}=-\frac{z_{12}}{z_{11}},$$

The kinematic chain with an additional gear has a gear ratio that corresponds to the gear ratio ( 5 ) of the circulating kinematic chain 1 - 2 - 3 - 5 - 6 - 7 - 8th - 9 - 4 is identical. $$u_{1-7ad}=u_{1-7},$$

The transmission ratio of the kinematic chain 1 - 11 - 12 - 7 with the wheels 11 . 12 comprehensive additional transmission from the input planet carrier 1 to the wheel 7 - 8th comprehensive output planetary gear 7 falls with the gear ratio ( 5 ) of the circulating kinematic chain 1 - 2 - 3 - 5 - 6 - 7 - 8th - 9 - 4 from the input planet carrier 1 to the output planetary gear 7 together.

The equality of gear ratios u _1-7 and u _1-7ad must be strictly adhered to, otherwise the mismatch of the movements of the rotating kinematic chain and the alternative (copying) chain will increase. The result is that one degree of freedom is actually lost and that the entire kinematic chain gets stuck. Therefore, the numbers of teeth of the teeth must be the gear ratio u _1-7 the rotating kinematic chain from the input planet carrier 1 to the output planetary gear 7 and the gear ratio u _1-7ad of the alternative (copying) transmission, by the equation u _1-7 / u _1-7ad = 1 or u _1-7 / u _1-8ad = 1 be connected to each other.

In many cases (eg in the gearbox of a truck) it is necessary that the overcoming of the increased resistance force during startup must be increased. To achieve this goal, the input planet carrier must 1 and the output planet carrier 10 be formed with the same radii r ₁ = r10.

Here, the term used to refer to equal radii of the input planet carrier 1 and the output planet carrier 10 the same offset or distances of each of the planetary axes 301 at the input planet carrier 1 from one to the central axis 300 aligned input shaft 0 like each of the planet axles 302 the planet gears on the output planet carrier 10 from one also with the central axis 300 aligned, the output of the device and a device implementing a corresponding gear 1000 forming output shaft.

The formation of the planetary carrier with the same radii causes the starting resistance force increases significantly. Missing the additional connection 11 - 12 Thus, the starting resistance force is endless because the device will clamp at a dead center (the lines of action of the input force and the output force coincide). At dead center, there is no point in time that brings the closed circuit out of the dead state and causes the formation of the second degree of freedom, because the force arm (distance between the lines of action of the input and output forces) is equal to zero. At dead center, the output drag force and the input drive force are the same. The magnitude of the output resistance depends only on the engine power during startup. Only the additional connection can bring the closed circuit out of the dead state, where the resistance reaches its maximum value, and make the change to the motion mode.

In many cases (for example, in emergency situations that cause the drive to lock up), it is necessary to overcome the increased resistance without increasing the input power. To achieve this goal, the output planetary gear must be formed with an imbalance mass.

The mass inequality of the output planetary wheel results in an unbalanced mass force being transmitted as a vibration action to an immovable (clamped) output planet carrier. This vibration action significantly increases the ability to overcome the initial load during startup and eventual emergency situations that cause the operation to change with a stop of the output planet carrier.

During the operation of the device can be a certain mismatch (deviation) of the movement of the wheels 7 and 8th arise, which lead to an air in the toothing. The airing can lead to the transmission of power by means of the wheels 11 - 12 the additional gear is disturbed and that the entire device is unstable. In order to increase the reliability of the device, the connection between the gear of the additional gear and the rotating kinematic chain must be elastic (for example in the form of a spring which eliminates the air in the toothing), the relative displacement of the wheel to the chain must be possible. This ensures a reliable power contact of the gears of the additional transmission. This increases the functionality of the device in the motion mode and when changing the states of motion.

In some cases, for example, when it is not possible to describe the gear ratio of the additional gear as tooth number ratio that is identical to the gear ratio of the planetary gear, the mismatch (deviation) of the movement of the wheels of the additional gear must be compensated. To accomplish this, the connection between the gear of the additional gear and the input planet carrier must be formed as a frictional connection with relative slip possibility. This solution ensures that the error in the relative position between the wheel and the planet carrier (mismatching their movement) due to the imprecise transmission ratio of the wheels of the additional transmission is eliminated.

The device and / or the transmission 1000 may alternatively or additionally comprise single or a combination of several in the context of the prior art and / or in one or more of the documents mentioned in the prior art and / or features mentioned in the preceding description. Likewise, the transmission can 1000 single or a combination of several features mentioned to the device and vice versa.

The invention is not limited by the description with reference to the embodiments. Rather, the invention includes every new feature as well as any combination of features. This includes in particular any combination of features in the claims, even if this feature or combination itself is not explicitly stated in the claims or exemplary embodiments.

The invention is particularly applicable in the field of production of transmissions, such as drive gears for vehicles, especially motor vehicles, industrially applicable.

The invention has been described with reference to preferred embodiments. However, it will be apparent to those skilled in the art that modifications or changes may be made to the invention without departing from the scope of the following claims.

It will be appreciated that the invention is in any case realized when it comes to a transmission ( 1000 ) with an input member (eg input shaft 0 ), an output member (eg output shaft) and two planetary gear stages arranged between input member and output member ( 100 . 200 ).

Each planetary gear stage ( 100 . 200 ) has four gear stage organs. For the gear stage members per planetary gear stage ( 100 . 200 ) is a first central wheel ( 104 . 209 ; sun 4 . 9 ), a planet carrier ( 101 . 210 ; Input planet 1 , Output planet carrier 10 ), at least one planetary gear ( 102 . 208 ; Input planet gear 2 , Output planetary gear 7 ) and a second central wheel ( 105 . 206 ; central wheel 5 . 6 ).

A gear stage member of the first planetary gear stage ( 100 ) interacts with the input member. A gear stage member of the second planetary gear stage ( 200 ) interacts with the source organ. The transmission has three transmission connections ( 400 . 500 . 600 ) on. The gearbox connections can be all or part of a power transmission (torque and speed). Each transmission connection ( 400 . 500 . 600 ) connects a gear stage member of a planetary gear stage ( 100 ) with a gear stage member of the other planetary gear stage ( 200 ). None of the transmission connections ( 400 . 500 . 600 ) connects the gear stage member cooperating with the input member directly (directly) with the gear stage member cooperating with the output member.

The invention also includes a transmission which, when the output member is stationary (stationary, held stationary, does not rotate), two of the transmission links ( 400 . 500 ), namely a first transmission connection ( 400 ) and a second transmission connection ( 500 ), with the gear stage members of the planetary gear stages ( 100 . 200 ) a closed circumferential kinematic chain ( 1 - 2 - 5 - 6 - 7 - 9 - 4 ). The third transmission connection ( 600 ) has a transmission ratio between the two gear stage members ( u _1-7ad ), which is similar or the same as that within the closed revolving kinematic chain ( 1 - 2 - 5 - 6 - 7 - 9 - 4 ) prevailing ratio ( u _1-7 ) between the cooperating with the input member gear stage member of the first planetary gear stage ( 100 ) and that gear stage member of the second planetary gear stage ( 200 ), which via the third transmission connection ( 600 ) with a gear stage member of the first planetary gear stage ( 100 ) connected is.

The invention also includes a transmission in which a first transmission connection ( 400 ) a primary wave ( 401 ), the primary wave ( 401 ) the two first central wheels ( 104 . 209 ; sun gears 4 . 9 ) of the two planetary gear stages ( 100 . 200 ) non-rotatably connects, the two first central wheels ( 104 . 209 ; sun gears 4 . 9 ) with the planetary gears ( 102 . 208 ) of the two planetary gear stages ( 100 . 200 ), a second transmission connection ( 500 ) a secondary wave ( 501 ), the secondary wave ( 501 ) the two second central wheels ( 105 . 206 ; Central wheels 5 . 6 ) of the two planetary gear stages ( 100 . 200 ) non-rotatably connects to each other and the two second central wheels ( 105 . 206 ; Central wheels 5 . 6 ) with the planetary gears ( 102 . 208 ; Input planet gear 2 , Output planetary gear 7 ) of the two planetary gear stages ( 100 . 200 ) comb.

The invention also includes a transmission, wherein the third transmission connection ( 600 ) a tertiary wave ( 601 ), the tertiary wave ( 601 ) two tertiary gears ( 111 . 212 ) non-rotatably interconnecting a tertiary gear ( 111 ; wheel 11 ) with the planetary gear ( 102 ; Input planet gear 2 ) of the first planetary gear stage ( 100 ) meshes and the other tertiary gear ( 212 ; wheel 12 ) with the planetary gear ( 208 ; Output planet gear 7 ) of the second planetary gear stage ( 200 ) combs.

The invention also includes a transmission, wherein the third transmission connection ( 600 ) a tertiary wave ( 601 ), the tertiary wave ( 601 ) a first tertiary gear ( 111 ) non-rotatable with the planet carrier ( 101 ) of the first planetary gear stage ( 100 ), the third transmission connection ( 600 ) also a non-rotatable with the planetary gear ( 208 ; Output planet gear 7 ) of the second planetary gear stage ( 200 ) connected second tertiary gear ( 212 ) and the first tertiary gear ( 111 ) with the second tertiary gear ( 212 ) combs (engages).

The means for torque and output speed change depending on driving resistance in the form of a rotating kinematic chain with a superposed connection includes an input planet carrier, an input planetary gear, a set of sun gears, a set of central gears, an output planetary gear and an output planet carrier and has a gear ratio
u _1-7
from the input planet carrier to the output planetary gear, with the stiffener ensuring a similar gear ratio.

It is important to emphasize that the additional gear transmission and / or the superimposed connection formed, for example, by a kinematic chain with an additional gear transmission fulfills and / or produces the function of a so-called torque support or torque support, on which external forces are compensated.

For example, two of the transmission connections via the associated with them and cooperating transmission members a rotating kinematic chain and the remaining gear connection and the associated gear members form a superimposed connection, which rotating kinematic chain together with the superimposed connection can produce a movable support, which Torque support forms.

The function of the torque arm or torque support can be performed by the example executed as an output orbital wheel 7 - 8th be fulfilled. The additional gear transmission transmits the driving input force to the planet gear at a contact point of the one part of the kinematic chain 1 - 11 -12-7 forming transmission 12 - 7 , The output resistance force is applied to the wheel designed as a planet wheel 7 - 8th transmitted in a contact point, which is the central wheel formed for example by a planetary gear 5 connects to the output planet carrier. The immovable point of the wheel designed as a planet wheel 7 - 8th is its instantaneous speed pole P7 which is generated by the rotating kinematic chain. The equation of the additional connection of external forces corresponding to the law of conservation of energy is the attack moment equation with respect to the instantaneous velocity pole P7 similar.

LIST OF REFERENCE NUMBERS

0

input shaft

1

Input planet

2

Input planet gear

3

wheel

4

sun

5

central wheel

6

central wheel

7

Output planet gear

8th

wheel

9

sun

10

Output planet

11

wheel

12

wheel

2-3

wheel

5-6

wheelset

7-8

wheel

100

first planetary gear stage

101

Planetary gear carrier of the first planetary gear stage 100

102

Planetary gear of the first planetary gear stage 100

104

first central gear of the first planetary gear stage 100

105

second central gear of the first planetary gear stage 100

111

Tertiary gear of the third gear connection

200

second planetary gear stage

206

second central gear of the second planetary gear stage 200

208

Planetary gear of the second planetary gear stage 200

209

first central gear of the second planetary gear stage 200

210

Planetary gear carrier of the second planetary gear stage 200

212

Tertiary gear of the third gear connection

300

central axis

301

Planetary axis of the first planetary gear stage 100

302

Planetary axis of the second planetary gear stage 200

400

first transmission connection

401

primary shaft

500

second transmission connection

501

secondary shaft

600

third transmission connection

601

tertiary wave

1000

transmission

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 4932928 [0003]
• GB 2238090 [0010]
• DE 202012101273 [0012]
• US 2011/0245015 A1 [0016]
• WO 2016/105243 [0017]

Claims (15)

Transmission (1000) having an input member, an output member and two disposed between input member and output member planetary gear stages (100, 200) each having four Getriebestufenorganen, the (gear) a first central gear (104, 209), a planet carrier (101, 210) with at least a planet gear (102, 208) and a second central gear (105, 206), wherein a gear stage member of the first planetary gear stage (100) cooperates with the input member and a gear stage member of the second planetary gear stage (200) with the output member, characterized by three, with exclusion a direct connection of the gear stage members cooperating with the input member and the output member respectively a gear stage member of a planetary gear stage (100) with a Getriebestufenorgan the other planetary gear stage (200) connecting the transmission connections (400, 500, 600), of which at least one as and / or on the frame is fixed. Gearbox after Claim 1 , characterized in that the transmission connection (500) between the second central gear (105) of the first planetary gear stage (100) and the second central gear (206) of the second planetary gear stage (200) is fixed as and / or on the frame. Gearbox after Claim 1 or 2 , characterized in that two of the transmission connections (400, 500) with the gear stage members of the planetary gear stages (100, 200) form a closed circumferential kinematic chain with the output member stationary and the third gear connection (600) between the two gear stage members connected by them a similar or the same Gear ratio (u1-7ad), as that within the kinematic chain between the cooperating with the input member gear stage member of the first planetary gear stage (100) and the means of the third gear connection (600) with a Getriebestufenorgan the first planetary gear stage (100) connected Getriebestufenorgan the second planetary gear stage (200) prevailing ratio (u1-7). Transmission to one of the Claims 1 to 3 , characterized in that a first transmission connection (400) one the two with the planetary gears (102, 208) of the two planetary gear stages (100, 200) meshing first central gears (104, 209) of the two planetary gear stages (100, 200) non-rotatably interconnecting primary shaft (401) and a second transmission connection (500) one the two with the planetary gears (102, 208) of the two planetary gear stages (100, 200) meshing second central wheels (105, 206) of the two planetary gear stages (100, 200) non-rotatably interconnecting secondary shaft ( 501). Gearbox after Claim 4 characterized in that said third transmission linkage (600) comprises two tertiary gears (111, 212) non-rotatably interconnected by a tertiary shaft (601), one of which meshing with said planetary gear (102) of said first planetary gear set (100) and the other Planetary gear (208) of the second planetary gear stage (200) meshes. Gearbox after Claim 4 , characterized in that the third gear connection (600) a non-rotatably connected via a tertiary shaft with the planet carrier (101) of the first planetary gear stage (100) first tertiary gear (111) and a meshing with this non-rotatably with the planetary gear (208) of the second planetary gear stage ( 200) connected second tertiary gear (212). Means for torque and output speed change depending on the driving resistance in the form of a rotating kinematic chain with a stiffener, said means an input planet carrier, an input planetary gear, a set of sun gears, a set of central gears, an output planetary gear and an output planet carrier contains and a gear ratio U _1-7 from the input planet gear carrier to the output planetary gear, wherein at least one member of the rotating kinematic chain and / or the stiffening of a torque support are used and the stiffening ensures a defined gear ratio. Setup after Claim 7 , characterized in that the stiffening in the form of a kinematic chain is formed with an additional gear transmission, that the additional gear transmission is designed in the form of a set of sun gears, that the set of sun gears coupled to the input planet wheel and one with the output planet gear coupled wheel contains and that the additional gear transmission a similar gear ratio $$u_{1-7ad}=u_{1-7}$$

making sure $$u_{1-7}=\frac{u_{45}^{\left(1\right)}-u_{96}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{45}^{\left(1\right)}\right]}.u_{45}^{\left(1\right)}=-\frac{z_5{z}_2}{z_3{z}_4}.u_{96}^{\left(10\right)}=-\frac{z_6{z}_{\mathrm{8th}}}{z_7{z}_9}.u_{76}^{\left(10\right)}=\frac{z6}{z7}.$$

$$u_{1-7ad}=-\frac{u_{11-5}^{\left(1\right)}-u_{12-6}^{\left(10\right)}}{u_{76}^{\left(10\right)}\left[1-u_{11-5}^{\left(1\right)}\right]}.u_{12-6}^{\left(10\right)}=-\frac{z_6}{z_{12}}$$

is. Setup after Claim 7 , characterized in that the stiffening in the form of a kinematic chain is formed with an additional gear transmission formed in the form of a set of central gears, the set of central gears including a wheel coupled to the input epicyclic gear and a wheel coupled to the output epicyclic gear and wherein the additional gear transmission a similar gear ratio $$u_{1-\mathrm{8th}ad}=u_{1-7}$$

making sure $$u_{1-\mathrm{8th}ad}=-\frac{u_{4-11}^{\left(1\right)}-u_{9-12}^{\left(10\right)}}{u_{\mathrm{8th}-12}^{\left(10\right)}\left[1-u_{4-11}^{\left(1\right)}\right]}.u_{4-11}^{\left(1\right)}=-\frac{z_{11}}{z_4}.u_{9-12}^{\left(10\right)}=-\frac{z_{12}}{z_9}.u_{\mathrm{8th}-12}^{\left(10\right)}=\frac{z_{12}}{z_{\mathrm{8th}}}$$

is. Setup after Claim 7 , characterized in that the stiffening is in the form of a kinematic chain with an additional gear transmission formed in the form of a rigidly connected to the input Planetenradträger associated with a wheel which is rigidly connected to the output planetary gear wherein the additional gear transmission has a similar gear ratio $$u_{1-7ad}=u_{1-7}$$

making sure $$u_{1-7ad}=-\frac{z_{12}}{z_{11}}$$

is. Furnishing according to one of the Claims 7 to 10 , characterized in that the transmission ratios $$u_{1-7ad}$$

the kinematic chain with the additional gear transmission and $$u_{1-7}$$

the circumferential kinematic chain from the input planet carrier to the output planetary gear through the equation $$u_{1-7ad}\text{/}{u}_{1-7}=1$$

are defined. Furnishing according to one of the Claims 7 to 11 , characterized in that the input-Planetenradträger and the output planet carrier with the same radii r ₁ = r _{10 are} formed. Furnishing according to one of the Claims 7 to 12 , characterized in that the output planetary wheel has an imbalance mass. Furnishing according to one of the Claims 7 to 13 , characterized in that a connection between the gear of the additional gear and the rotating kinematic chain elastic, z. B. in the form of a spring which eliminates the air in the toothing is formed. Furnishing according to one of the Claims 7 to 14 , characterized in that a connection between the gear of the additional transmission and the input planet carrier is designed as a frictional connection with relative slip possibility.

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