CN203488646U - Speed changer with parallelly-connected planetary gear train - Google Patents

Abstract

The utility model relates to a transmission with a parallel planetary gear train. Including input shaft, first output shaft, second output shaft, reverse gear shaft, first planetary gear train, second planetary gear train, first clutch, second clutch, first coupling, second coupling and Differential driven gear; the utility model adopts common tooth transmission, the first forward gear which is empty on the input shaft is simultaneously connected with the I-III gear driven gear which is empty on the first output shaft and the idler which is on the second output shaft The driven gears of Ⅱ-Ⅳ gears are in constant mesh, and the second forward gears fixed on the input shaft simultaneously follow the driven gears of Ⅴ-Ⅶ gears on the first output shaft and the Ⅵ-Ⅷ gears on the second output shaft. The moving gears are constantly meshed, which can effectively reduce the number of shifting gear pairs and simplify the structure of the transmission system; two different transmission ratios of planetary differential transmission and direct transmission can be formed by using an adapter or coupling in the same planetary gear train , making the overall structure of the transmission more concise and compact.

Description

Transmission with parallel planetary gear train

technical field

The utility model belongs to a transmission for vehicles, in particular to a parallel planetary gear train transmission using the two-speed transmission characteristic of a planetary mechanism.

Background technique

At present, vehicle transmissions are divided into manual transmission (MT), automatic mechanical transmission (AMT), electrohydraulic automatic transmission (AT), dual clutch transmission (DSG) and continuously variable transmission (CVT). The manual transmission is manually shifted through a clutch and multiple pairs of gear pairs installed on a fixed shaft system, and cannot realize the automatic transmission function; the mechanical automatic transmission is based on the manual transmission, and an automatic control device is added to control the clutch and select The gear pair on the fixed shaft system performs automatic shifting, and there is power interruption during the shifting process, and the shifting smoothness is not good; the electro-hydraulic control automatic transmission has a set of planetary gear trains in series and multiple clutches and adapters, which can Automatic shifting is carried out through electronically controlled hydraulic drive, but the structure and control system are complex, the transmission efficiency is low, the processing of parts is difficult, and the manufacturing and maintenance costs are high; the dual-clutch transmission is based on the mechanical automatic transmission. The original parallel clutch and the output shaft connected to it can allow two gear pairs with different gears to mesh at the same time to realize the gear preset. The transmission route of the transmission is determined by selecting the working status of different clutches, and the automatic shift control is installed. The device can realize automatic shifting, but the clutch must be combined and separated under the overall rotation state, the oil circuit is complicated, the failure rate is high, and the maintenance is difficult; the continuously variable transmission changes the V-shaped transmission belt between the driving conical disc and the driven conical disc. The transmission radius on the disc realizes continuous stepless speed regulation, but the transmission torque is small, the parts are difficult to process and manufacture, the parts wear during use, and the service life is short.

Utility model content

In order to increase the number of transmission gears, improve transmission efficiency, effectively control the structural size of the transmission, and reduce the difficulty of processing parts and manufacturing costs, the utility model provides a vehicle transmission with a new structure.

Concrete structural design scheme of the present utility model is as follows:

A transmission with a parallel planetary gear train includes an input shaft ZR1, a first output shaft Z1, a second output shaft Z2, a reverse gear shaft ZD1, a first planetary gear train X1, a second planetary gear train X2, a first clutch J1, a second planetary gear train Second coupling J2, first coupling L1 and second coupling L2, differential driven gear CZ;

The end of one side of the first output shaft Z1 is fixed with the I-III gear driven gear C1, and the other side is fixed with the first planetary gear system sun gear XT1; the end of the second output shaft Z2 is fixed The driven gear C2 for Ⅱ-Ⅳ gears is fixed, the sun gear XT2 of the second planetary gear system is fixed on the other side, the first reverse shaft gear CD2 and the second reverse shaft gear are fixed on the reverse shaft ZD1 CD3;

The input shaft ZR1 is provided with a first forward gear CR1 and a reverse gear CD1 at the same time, and the input shaft ZR1 between the first forward gear CR1 and the reverse gear CD1 is provided with an input shaft synchronizer T1 ; The first forward gear CR1 is in constant mesh with the I-III gear driven gear C1 and the II-IV gear driven gear C2 at the same time, the reverse gear CD1 and the first reverse shaft gear CD2 is in constant mesh, and the second reverse shaft gear CD3 is in constant mesh with the II-IV gear driven gear C2;

The first planetary gear system X1 includes the first planetary gear system ring gear XQ1, the first planetary gear system carrier XJ1 and the first planetary gear system sun gear XT1; the first planetary gear system carrier XJ1 is empty on the first output shaft Z1, and is fixedly connected to the first output shaft output gear CC1, which is in constant mesh with the differential driven gear CZ; the first planetary gear ring gear XQ1 is fixedly connected to the first engaging One end of the first adapter J1, the other end of the first adapter J1 is fixedly connected to the transmission housing, the first planetary gear ring gear XQ1 is also fixedly connected to one end of the first coupler L1, and the other end of the first coupler L1 is fixedly connected to The first output shaft Z1; the planetary carrier XJ1 of the first planetary gear system is provided with more than two planetary gears of the first planetary gear system, the sun gear XT1 of the first planetary gear system, and more than two first planetary gears The planetary gear, the first planetary gear carrier XJ1 and the first planetary gear ring gear XQ1 constitute the transmission mechanism of the first planetary gear X1;

The second planetary gear system X2 includes the second planetary gear ring gear XQ2, the second planetary gear carrier XJ2 and the second planetary gear sun gear XT2; the second planetary gear carrier XJ2 is empty in the second output shaft Z2, and is fixedly connected to the second output shaft output gear CC2, which is constantly meshed with the differential driven gear CZ; the second planetary gear ring gear XQ2 is fixedly connected to the second engaging One end of the second coupling J2, the other end of the second coupling J2 is fixedly connected to the transmission housing; the second planetary gear ring gear XQ2 is also fixedly connected to one end of the second coupling L2, and the other end of the second coupling L2 is fixedly connected to The second output shaft Z2; the planet carrier XJ2 of the second planetary gear system is provided with more than two planetary gears of the second planetary gear system, the sun gear XT2 of the planetary gear system, and more than two planets of the second planetary gear system wheel, the second planetary gear carrier XJ2 and the second planetary gear ring gear XQ2 constitute the transmission mechanism of the second planetary gear X2;

The input end of the input shaft ZR1, the output end of the first output shaft Z1 and the output end of the second output shaft Z2 are all located on the same side;

The first planetary gear set X1 is located on the output side of the first output shaft Z1, and the second planetary gear set X2 is located on the output side of the second output shaft Z2;

The above-mentioned speed changer realizes four-speed and reverse gear shifting.

A transmission with a parallel planetary gear train includes an input shaft ZR1, a first output shaft Z1, a second output shaft Z2, a reverse gear shaft ZD1, a first planetary gear train X1, a second planetary gear train X2, a first clutch J1, a second planetary gear train Second coupling J2, first coupling L1 and second coupling L2, differential driven gear CZ;

One side of the first output shaft Z1 is provided with I-III gear driven gear C1 and V-VII gear driven gear C3, and I-III gear driven gear C1 and V-VII gear driven gear C3 A first output shaft synchronizer T2 is provided on the first output shaft Z1 between them, and a first planetary gear system sun gear XT1 is fixed on the other side of the first output shaft Z1;

One side of the second output shaft Z2 is provided with II-IV gear driven gear C2 and VI-VIII gear driven gear C4, and II-IV gear driven gear C2 and VI-VIII gear driven gear C4 A second output shaft synchronizer T3 is provided on the second output shaft Z2 between them, and a second planetary gear system sun gear XT2 is fixed on the other side of the second output shaft Z2;

The first reverse gear CD2 and the second reverse gear CD3 are fixed on the reverse gear ZD1;

The input shaft ZR1 is fixed with the second forward gear CR2, and the first forward gear CR1 and the reverse gear CD1 are set in the empty sleeve. The input between the first forward gear CR1 and the reverse gear CD1 An input shaft synchronizer T1 is provided on the shaft ZR1; the first forward gear CR1 is in constant mesh with the I-III gear driven gear C1 and the II-IV gear driven gear C2; the second forward gear The gear CR2 is in constant mesh with the V-VII gear driven gear C3 and the VI-VIII gear driven gear C4 at the same time, the reverse gear CD1 is in constant mesh with the first reverse shaft gear CD2, the The second reverse shaft gear CD3 is in constant mesh with the II-IV gear driven gear C2;

The first planetary gear system X1 includes the first planetary gear system ring gear XQ1, the first planetary gear system carrier XJ1 and the first planetary gear system sun gear XT1; the first planetary gear system carrier XJ1 is empty on the first output shaft Z1, and is fixedly connected to the first output shaft output gear CC1, which is in constant mesh with the differential driven gear CZ; the first planetary gear ring gear XQ1 is fixedly connected to the first engaging One end of the first adapter J1, the other end of the first adapter J1 is fixedly connected to the transmission housing, the first planetary gear ring gear XQ1 is also fixedly connected to one end of the first coupler L1, and the other end of the first coupler L1 is fixedly connected to The first output shaft Z1; the planetary carrier XJ1 of the first planetary gear system is provided with more than two planetary gears of the first planetary gear system, the sun gear XT1 of the first planetary gear system, and more than two first planetary gears The planetary gear, the first planetary gear carrier XJ1 and the first planetary gear ring gear XQ1 constitute the transmission mechanism of the first planetary gear X1;

The second planetary gear system X2 includes the second planetary gear ring gear XQ2, the second planetary gear carrier XJ2 and the second planetary gear sun gear XT2; the second planetary gear carrier XJ2 is empty in the second output shaft Z2, and is fixedly connected to the second output shaft output gear CC2, which is constantly meshed with the differential driven gear CZ; the second planetary gear ring gear XQ2 is fixedly connected to the second engaging One end of the second coupling J2, the other end of the second coupling J2 is fixedly connected to the transmission housing; the second planetary gear ring gear XQ2 is also fixedly connected to one end of the second coupling L2, and the other end of the second coupling L2 is fixedly connected to The second output shaft Z2; the planet carrier XJ2 of the second planetary gear system is provided with more than two planetary gears of the second planetary gear system, the sun gear XT2 of the second planetary gear system, and more than two second planetary gears The planetary gear, the second planetary gear carrier XJ2 and the second planetary gear ring gear XQ2 constitute the transmission mechanism of the second planetary gear X2;

The input end of the input shaft ZR1, the output end of the first output shaft Z1 and the output end of the second output shaft Z2 are all located on the same side;

The first planetary gear set X1 is located on the output side of the first output shaft Z1, and the second planetary gear set X2 is located on the output side of the second output shaft Z2;

The above-mentioned speed changer realizes eight-speed and reverse gear speed change.

The beneficial technical effects of the utility model are embodied in the following aspects:

1. The transmission involved in this utility model adopts common gear transmission (see Figure 1 and Figure 7), and the first forward gear CR1, which is empty on the input shaft ZR1, is at the same time driven by the I-III gears on the first output shaft Z1. The driven gear C1 is in constant mesh with the idling II-IV gear driven gear C2 on the second output shaft Z2, and the second forward gear CR2 fixed on the input shaft ZR1 simultaneously engages with the Ⅴ-VII gear idler on the first output shaft Z1. The driven gear C3 is constantly meshed with the Ⅵ-Ⅷ gear driven gear C4 which is empty on the second output shaft Z2, which can effectively reduce the number of shift gear pairs and simplify the structure of the transmission system; The gear or coupling can form two different transmission ratios of planetary differential transmission and direct transmission, and the realized two-speed transmission has great practical engineering application value, making the overall structure of the transmission more concise and compact;

2. The utility model uses an adapter or coupling to interrupt or combine power transmission. Through the combination of the adapter, coupling, synchronizer and two planetary gear systems X1, X2, the first output shaft Z1 and the second output shaft Z2 can Select the transmission route of the output power; according to the driver's operation intention, the shift-in gear can be preset (pre-engaged) by controlling the position of each synchronizer, and the transmission route can be realized by controlling the state of each adapter and coupling The conversion can effectively avoid power interruption during the shifting process and achieve smooth shifting;

3. The utility model adopts the combined structure of the ordinary NGW three-element planetary gear train and the fixed-shaft variable-speed transmission gear train. The working state is stable and reliable, the manufacturability is good, and the manufacturing cost is low;

4. For the transmission involved in this utility model, on the basis of Figure 1, each additional row of gears (three gears) can increase the speed of 4 gears. For transmissions with a large number of gears, the advantages in structural size control are more significant ;

5. On the basis of the utility model, an automatic shift control device can be installed to realize automatic shifting.

Description of drawings

Fig. 1 is a schematic diagram of the four-speed transmission structure of the utility model.

Fig. 2 is a diagram of the operation state of gear I of the four-speed transmission structure of the present invention.

Fig. 3 is the running state diagram of the second gear of the four-speed transmission structure of the utility model.

Fig. 4 is the operating state diagram of the third gear of the four-speed transmission structure of the utility model.

Fig. 5 is the operating state diagram of the fourth gear of the four-speed transmission structure of the utility model.

Fig. 6 is a reverse gear state diagram of the four-speed transmission structure of the utility model.

Fig. 7 is a schematic diagram of the structure of the eight-speed transmission according to Embodiment 2 of the present utility model.

Fig. 8 is a diagram of the operation state of gear I of the eight-speed transmission structure of Embodiment 2 of the present utility model.

Fig. 9 is a diagram of the operating state of gear II of the eight-speed transmission structure in Embodiment 2 of the present utility model.

Fig. 10 is a diagram of the operating state of gear III of the eight-speed transmission structure in Embodiment 2 of the present utility model.

Fig. 11 is a diagram of the operation state of gear IV of the eight-speed transmission structure in Embodiment 2 of the utility model.

Fig. 12 is a running state diagram of V gear of the eight-speed transmission structure of Embodiment 2 of the utility model.

Fig. 13 is a diagram of the operation state of gear VI of the eight-speed transmission structure of Embodiment 2 of the utility model.

Fig. 14 is a diagram of the operating state of gear VII of the eight-speed transmission structure of Embodiment 2 of the present utility model.

Fig. 15 is a running state diagram of eight-speed transmission structure VIII of Embodiment 2 of the utility model.

Fig. 16 is a reverse gear state diagram of the eight-speed transmission structure of Embodiment 2 of the present utility model.

Code in the picture above: input shaft ZR1, first output shaft Z1, second output shaft Z2, reverse shaft ZD1, first planetary gear system X1, first planetary gear system ring gear XQ1, first planetary gear system carrier XJ1 , The first planetary gear sun gear XT1, the second planetary gear X2, the second planetary gear ring gear XQ2, the second planetary gear carrier XJ2, the second planetary gear sun gear XT2, the first forward gear CR1 , Second forward gear CR2, Ⅰ-Ⅲ driven gear C1, Ⅱ-Ⅳ driven gear C2, Ⅴ-Ⅶ driven gear C3, Ⅵ-Ⅷ driven gear C4, reverse gear CD1, 1st reverse shaft gear CD2, 2nd reverse shaft gear CD3, 1st output shaft output gear CC1, 2nd output shaft output gear CC2, differential driven gear CZ, input shaft synchronizer T1, 1st output shaft synchronous T2, second output shaft synchronizer T3, first joint J1, second joint J2, first joint L1, second joint L2.

Detailed ways

Below in conjunction with accompanying drawing, the utility model is described further through embodiment.

Example 1

Referring to Figure 1, a transmission with a parallel planetary gear train includes an input shaft ZR1, a first output shaft Z1, a second output shaft Z2, a reverse gear shaft ZD1, a first planetary gear train X1, a second planetary gear train X2, a first coupling J1, the second coupling J2, the first coupling L1 and the second coupling L2, the differential driven gear CZ;

The end of one side of the first output shaft Z1 is fixed with the I-III gear driven gear C1, and the other side is fixed with the first planetary gear system sun gear XT1; the end of the second output shaft Z2 is fixed The driven gear C2 for Ⅱ-Ⅳ gears is fixed, the sun gear XT2 of the second planetary gear system is fixed on the other side, the first reverse shaft gear CD2 and the second reverse shaft gear are fixed on the reverse shaft ZD1 CD3;

The input shaft ZR1 is provided with a first forward gear CR1 and a reverse gear CD1 at the same time, and the input shaft ZR1 between the first forward gear CR1 and the reverse gear CD1 is provided with an input shaft synchronizer T1 ; The first forward gear CR1 is in constant mesh with the I-III gear driven gear C1 and the II-IV gear driven gear C2 at the same time, the reverse gear CD1 and the first reverse shaft gear CD2 is in constant mesh, and the second reverse shaft gear CD3 is in constant mesh with the II-IV gear driven gear C2;

The first planetary gear system X1 includes the first planetary gear system ring gear XQ1, the first planetary gear system carrier XJ1 and the first planetary gear system sun gear XT1; the first planetary gear system carrier XJ1 is empty on the first output shaft Z1, and is fixedly connected to the first output shaft output gear CC1, which is in constant mesh with the differential driven gear CZ; the first planetary gear ring gear XQ1 is fixedly connected to the first engaging One end of the first adapter J1, the other end of the first adapter J1 is fixedly connected to the transmission housing, the first planetary gear ring gear XQ1 is also fixedly connected to one end of the first coupler L1, and the other end of the first coupler L1 is fixedly connected to The first output shaft Z1; the planetary carrier XJ1 of the first planetary gear system is provided with more than two planetary gears of the first planetary gear system, the sun gear XT1 of the first planetary gear system, and more than two first planetary gears The planetary gear, the first planetary gear carrier XJ1 and the first planetary gear ring gear XQ1 constitute the transmission mechanism of the first planetary gear X1;

The second planetary gear system X2 includes the second planetary gear ring gear XQ2, the second planetary gear carrier XJ2 and the second planetary gear sun gear XT2; the second planetary gear carrier XJ2 is empty in the second output shaft Z2, and is fixedly connected to the second output shaft output gear CC2, which is constantly meshed with the differential driven gear CZ; the second planetary gear ring gear XQ2 is fixedly connected to the second engaging One end of the second coupling J2, the other end of the second coupling J2 is fixedly connected to the transmission housing; the second planetary gear ring gear XQ2 is also fixedly connected to one end of the second coupling L2, and the other end of the second coupling L2 is fixedly connected to The second output shaft Z2; the planet carrier XJ2 of the second planetary gear system is provided with more than two planetary gears of the second planetary gear system, the sun gear XT2 of the second planetary gear system, and more than two second planetary gears The planetary gear, the second planetary gear carrier XJ2 and the second planetary gear ring gear XQ2 constitute the transmission mechanism of the second planetary gear X2;

The input end of the input shaft ZR1, the output end of the first output shaft Z1 and the output end of the second output shaft Z2 are all located on the same side;

The first planetary gear set X1 is located on the output side of the first output shaft Z1, and the second planetary gear set X2 is located on the output side of the second output shaft Z2.

The above-mentioned transmission realizes four-speed and reverse gear shifting, and the specific shifting states of each gear are described as follows:

Referring to Figure 1, the figure shows that the transmission is in the neutral state; the input shaft synchronizer T1 is in the middle position, and the first joint J1, the second joint J2, the first joint L1, and the second joint L2 are all in the disengaged state .

See Figure 2, the figure shows that the transmission is in gear I; when the neutral gear is switched to gear I to start, the input shaft synchronizer T1 moves to the left position, and the first adapter J1 is engaged to form gear I to complete the vehicle start; the second The adapter J2, the first coupler L1, and the second coupler L2 are in a disengaged state;

When the first gear is running, the input shaft ZR1 inputs the engine power, and the input shaft synchronizer T1 is in the left position so that the input shaft ZR1 is connected to the first forward gear CR1, because the first forward gear CR1 is connected to the I-III gear driven gear C1 In the state of constant meshing, the power is transmitted from the input shaft ZR1 to the first output shaft Z1, and the first output shaft Z1 drives the sun gear XT1 of the first planetary gear system to rotate, and the first adapter J1 is in the engaged state to make the ring gear of the first planetary gear system XQ1 forms a fixed connection with the transmission housing, so the sun gear XT1 of the first planetary gear system and the carrier XJ1 of the first planetary gear system form a reduction transmission and transmit the power to the output gear CC1 of the first output shaft, and the first output shaft outputs The gear CC1 is constantly meshed with the differential driven gear CZ, which drives the differential to rotate and drives the vehicle to drive in gear I; when the first output shaft Z1 transmits power in gear I, the second joint J2, the first coupling L1, Both the second couplers L2 are in the disengaged state, and the second planetary gear ring gear XQ2 is not constrained, so the second output shaft Z2 does not transmit power at this time.

See Figure 3, the figure shows that the transmission is in gear II; after the car starts running in gear I, as the vehicle speed increases, when it is necessary to shift from gear I to gear II, the input shaft synchronizer T1 is in the left position. At the moment of shifting, the first adapter J1 is disengaged, and the second adapter J2 is engaged, so that the transmission completes the shift and enters the working state of the second gear;

When the second gear is running, the input shaft ZR1 inputs the engine power, and the input shaft synchronizer T1 is in the left position so that the input shaft ZR1 is connected to the first forward gear CR1, because the first forward gear CR1 is connected to the driven gear C2 of II-IV gears. In the state of constant meshing, the power is transmitted from the input shaft ZR1 to the second output shaft Z2, the second output shaft Z2 drives the sun gear XT2 of the second planetary gear system to rotate, the second adapter J2 is in the engaged state, and the ring gear of the second planetary gear system XQ2 forms a fixed connection with the transmission housing, so the sun gear XT2 of the second planetary gear system and the carrier XJ2 of the second planetary gear system form a reduction transmission and transmit the power to the output gear CC2 of the second output shaft, and the second output shaft outputs The gear CC2 is in constant mesh with the differential driven gear CZ, which drives the differential to rotate and drives the vehicle to drive in the second gear; when the second output shaft Z2 transmits the power in the second gear, the first joint J1, the first coupling L1 and Both the second couplers L2 are in the disengaged state, and the first planetary gear ring gear XQ1 is not constrained, so the first output shaft Z1 does not transmit power at this time.

See Figure 4, the figure shows that the transmission is in gear III; when gear II is switched to gear III, the input shaft synchronizer T1 is in the left position, and at the moment of gear shifting, the second joint J2 is separated, and the first joint L1 Combined, the transmission completes the shift and enters the working state of the third gear;

When the third gear is running, the input shaft ZR1 inputs the engine power, and the input shaft synchronizer T1 is in the left position so that the input shaft ZR1 is connected to the first forward gear CR1, because the first forward gear CR1 is connected to the I-III gear driven gear C1 In the state of constant meshing, the power is transmitted from the input shaft ZR1 to the first output shaft Z1, the first output shaft Z1 drives the first planetary gear system sun gear XT1 to rotate, the first coupling L1 is in a combined state, the first planetary gear system sun gear XT1 and the planet carrier XJ1 of the first planetary gear train form a fixed connection to realize direct transmission and transmit the power to the output gear CC1 of the first output shaft. The output gear CC1 of the first output shaft is constantly meshed with the driven gear CZ of the differential to drive the differential The transmission rotates and drives the vehicle to drive at the third gear; when the first output shaft Z1 transmits the power of the third gear, the first joint J1, the second joint J2 and the second joint L2 are in a disengaged state, and the second planetary gear train gears Circle XQ2 is not constrained, so the second output shaft Z2 does not transmit power.

Refer to Figure 5, the figure shows that the transmission is in gear IV; when gear III is switched to gear IV, the input shaft synchronizer T1 is in the left position, and at the moment of shifting, the first coupling L1 is separated, and the second coupling L2 Combined, the transmission completes the shift and enters the working state of the fourth gear;

When the fourth gear is running, the input shaft ZR1 inputs the engine power, and the input shaft synchronizer T1 is in the left position so that the input shaft ZR1 is connected with the first forward gear CR1, because the first forward gear CR1 is connected with the driven gear C2 of the II-IV gear. In the state of constant meshing, the power is transmitted from the input shaft ZR1 to the second output shaft Z2, the second output shaft Z2 drives the sun gear XT2 of the second planetary gear system to rotate, the second coupling L2 is in a combined state, and the sun gear of the second planetary gear system XT2 and the planet carrier XJ2 of the second planetary gear train form a fixed connection to realize direct transmission and transmit the power to the output gear CC2 of the first output shaft, and the output gear CC2 of the second output shaft is constantly meshed with the driven gear CZ of the differential to drive the differential The transmission rotates and drives the vehicle to drive at the fourth gear; when the second output shaft Z2 transmits the power of the fourth gear, the first joint J1, the second joint J2 and the first joint L1 are in a disengaged state, and the gears of the first planetary gear train The circle XQ1 is not constrained, so the first output shaft Z1 does not transmit power.

Referring to Figure 6, the figure shows that the transmission is in reverse gear; when in reverse gear, the input shaft synchronizer T1 moves to the right position, and the second adapter J2 engages to form reverse gear transmission;

When the reverse gear is running, the input shaft ZR1 inputs the engine power, and the input shaft synchronizer T1 is in the right position to connect the reverse gear CD1 with the input shaft ZR1, because the reverse gear CD1 and the first reverse gear CD2 on the reverse shaft ZD1 In the state of constant meshing, the power is transmitted from the input shaft ZR1 to the reverse gear shaft ZD1, and the second reverse gear CD3 on the reverse gear ZD1 is in a constant meshing state with the II-IV gear driven gear C2 on the second output shaft Z2. Therefore, the second output shaft Z2 is driven to rotate, and the second joint J2 is in the engaged state, so a reduction transmission is formed between the sun gear XT2 of the second planetary gear system and the carrier XJ2 of the second planetary gear system and the power is transmitted to the second output shaft Output gear CC2, the second output shaft The output gear CC2 is constantly meshed with the differential driven gear CZ, thereby driving the differential to rotate and driving the vehicle in reverse; when the second output shaft Z2 transmits reverse gear power, the first engagement J1, the first coupling L1 and the second coupling L2 are in a disengaged state, and the first planetary gear ring gear XQ1 is not constrained, so the first output shaft Z1 does not transmit power.

Example 2

Referring to Fig. 7, a transmission with a parallel planetary gear train includes an input shaft ZR1, a first output shaft Z1, a second output shaft Z2, a reverse gear shaft ZD1, a first planetary gear train X1, a second planetary gear train X2, a first coupling J1, the second coupling J2, the first coupling L1 and the second coupling L2, the differential driven gear CZ;

One side of the first output shaft Z1 is provided with I-III gear driven gear C1 and V-VII gear driven gear C3, and I-III gear driven gear C1 and V-VII gear driven gear C3 A first output shaft synchronizer T2 is provided on the first output shaft Z1 between them, and a first planetary gear system sun gear XT1 is fixed on the other side of the first output shaft Z1;

One side of the second output shaft Z2 is provided with II-IV gear driven gear C2 and VI-VIII gear driven gear C4, and II-IV gear driven gear C2 and VI-VIII gear driven gear C4 A second output shaft synchronizer T3 is provided on the second output shaft Z2 between them, and a second planetary gear system sun gear XT2 is fixed on the other side of the second output shaft Z2;

The first reverse gear CD2 and the second reverse gear CD3 are fixed on the reverse gear ZD1;

The input shaft ZR1 is fixed with the second forward gear CR2, and the first forward gear CR1 and the reverse gear CD1 are set in the empty sleeve. The input between the first forward gear CR1 and the reverse gear CD1 An input shaft synchronizer T1 is provided on the shaft ZR1; the first forward gear CR1 is in constant mesh with the I-III gear driven gear C1 and the II-IV gear driven gear C2; the second forward gear The gear CR2 is in constant mesh with the V-VII gear driven gear C3 and the VI-VIII gear driven gear C4 at the same time, the reverse gear CD1 is in constant mesh with the first reverse shaft gear CD2, the The second reverse shaft gear CD3 is in constant mesh with the II-IV gear driven gear C2;

The first planetary gear system X1 includes the first planetary gear system ring gear XQ1, the first planetary gear system carrier XJ1 and the first planetary gear system sun gear XT1; the first planetary gear system carrier XJ1 is empty on the first output shaft Z1, and is fixedly connected to the first output shaft output gear CC1, which is in constant mesh with the differential driven gear CZ; the first planetary gear ring gear XQ1 is fixedly connected to the first engaging One end of the first adapter J1, the other end of the first adapter J1 is fixedly connected to the transmission housing, the first planetary gear ring gear XQ1 is also fixedly connected to one end of the first coupler L1, and the other end of the first coupler L1 is fixedly connected to The first output shaft Z1; the planetary carrier XJ1 of the first planetary gear system is provided with more than two planetary gears of the first planetary gear system, the sun gear XT1 of the first planetary gear system, and more than two first planetary gears The planetary gear, the first planetary gear carrier XJ1 and the first planetary gear ring gear XQ1 constitute the transmission mechanism of the first planetary gear X1;

The second planetary gear system X2 includes the second planetary gear ring gear XQ2, the second planetary gear carrier XJ2 and the second planetary gear sun gear XT2; the second planetary gear carrier XJ2 is empty in the second output shaft Z2, and is fixedly connected to the second output shaft output gear CC2, which is constantly meshed with the differential driven gear CZ; the second planetary gear ring gear XQ2 is fixedly connected to the second engaging One end of the second coupling J2, the other end of the second coupling J2 is fixedly connected to the transmission housing; the second planetary gear ring gear XQ2 is also fixedly connected to one end of the second coupling L2, and the other end of the second coupling L2 is fixedly connected to The second output shaft Z2; the planet carrier XJ2 of the second planetary gear system is provided with more than two planetary gears of the second planetary gear system, the sun gear XT2 of the second planetary gear system, and more than two second planetary gears The planetary gear, the second planetary gear carrier XJ2 and the second planetary gear ring gear XQ2 constitute the transmission mechanism of the second planetary gear X2;

The input end of the input shaft ZR1, the output end of the first output shaft Z1 and the output end of the second output shaft Z2 are all located on the same side;

The first planetary gear set X1 is located on the output side of the first output shaft Z1, and the second planetary gear set X2 is located on the output side of the second output shaft Z2.

The above-mentioned transmission realizes eight-speed and reverse gear shifting, and the specific shifting states of each gear are described as follows:

Referring to Fig. 7, the figure shows that the transmission is in a neutral state; when in neutral, the input shaft synchronizer T1, the first output shaft synchronizer T2, and the second output shaft synchronizer T3 are all in the middle position, the first joint J1, the second joint The two joints J2, the first coupling L1, and the second coupling L2 are all in a disengaged state.

See Figure 8, the figure shows that the transmission is in gear I; when the neutral gear is switched to gear I to start, the input shaft synchronizer T1 moves to the left position, the first output shaft synchronizer T2 moves to the right position, and the first engagement The device J1 is engaged to form the first gear transmission to complete the vehicle start;

When the I gear is running, the input shaft ZR1 inputs the engine power, the input shaft synchronizer T1 is on the left side to connect the first forward gear CR1 to the input shaft ZR1, and the first output shaft synchronizer T2 is on the right side to make I-III gears The driven gear C1 is connected with the first output shaft Z1, because the first forward gear CR1 is in constant mesh with the I-III gear driven gear C1, the power is transmitted from the input shaft ZR1 to the first output shaft Z1, and the first output shaft Z1 drives the sun gear XT1 of the first planetary gear system to rotate, and the first adapter J1 is in the engaged state to form a fixed connection between the ring gear XQ1 of the first planetary gear system and the transmission housing, so the sun gear XT1 of the first planetary gear system and the first planetary gear system The planetary carrier XJ1 of the wheel system forms a reduction transmission and transmits the power to the output gear CC1 of the first output shaft. The output gear CC1 of the first output shaft is constantly meshed with the driven gear CZ of the differential to drive the differential to rotate and drive the vehicle to Driving in gear I; when the first output shaft Z1 transmits the power of gear I, the second output shaft synchronizer T3 is in the middle position, the second joint J2, the first coupling L1, and the second coupling L2 are in a disengaged state, and the second The planetary gear ring gear XQ2 is not constrained, so the second output shaft Z2 does not transmit power at this time.

Refer to Figure 9, the figure shows that the transmission is in the state of gear II; after the car starts running in gear I, as the vehicle speed increases, when it is necessary to switch from gear I to gear II, the input shaft synchronizer T1 is in the left position, and the second The output shaft synchronizer T3 moves to the right position. At the moment of shifting, the first joint J1 is separated, and the second joint J2 is engaged to form the second gear transmission to complete the shift; after that, the first output shaft synchronizer T2 moves to the middle Location;

When the second gear is running, the input shaft ZR1 inputs the engine power, the input shaft synchronizer T1 is in the left position, so that the first forward gear CR1 is connected with the input shaft ZR1, and the second output shaft synchronizer T3 is in the right position so that II-IV The gear driven gear C2 is connected to the second output shaft Z2, because the first forward gear CR1 and the II-IV gear driven gear C2 are in a constant mesh state, the power is transmitted from the input shaft ZR1 to the second output shaft Z2, and the second output shaft Z2 drives the sun gear XT2 of the second planetary gear system to rotate, the second adapter J2 is in the engaged state, and the ring gear XQ2 of the second planetary gear system forms a fixed connection with the transmission housing, so the sun gear XT2 of the second planetary gear set The reduction transmission is formed between the planetary carriers XJ2 of the wheel train and the power is transmitted to the output gear CC2 of the second output shaft. The output gear CC2 of the second output shaft is in constant mesh with the driven gear CZ of the differential to drive the differential to rotate and drive the vehicle to Driving in the second gear; when the second output shaft Z2 transmits power in the second gear, the first coupling J1, the first coupling L1 and the second coupling L2 are all in a disengaged state, and the first planetary gear ring gear XQ1 is not constrained, Therefore, the first output shaft Z1 does not transmit power at this time.

See Figure 10, the figure shows that the transmission is in gear III; when gear II is switched to gear III, the input shaft synchronizer T1 is at the left position, and the first output shaft synchronizer T2 is moved to the right position, at the moment of shifting , the second coupling J2 is separated, the first coupling L1 is combined, and the planetary carrier XJ1 of the first planetary gear system forms a fixed connection with the sun gear XT1 of the first planetary gear system, so that the first planetary gear system X1 forms the third gear transmission to complete the shifting gear process; after that, the second output shaft synchronizer T3 moves to the middle position;

When the third gear is running, the input shaft ZR1 inputs the engine power, the input shaft synchronizer T1 is in the left position, so that the first forward gear CR1 is connected with the input shaft ZR1, and the first output shaft synchronizer T2 is in the right position so that I-III The gear driven gear C1 is connected to the first output shaft Z1, because the first forward gear CR1 is in constant mesh with the I-III gear driven gear C1, the power is transmitted from the input shaft ZR1 to the first output shaft Z1, and the first output shaft Z1 drives the first planetary gear system sun gear XT1 to rotate, the first coupling L1 is in a combined state, the first planetary gear system sun gear XT1 forms a fixed connection with the first planetary gear system planet carrier XJ1 to realize direct transmission and transmit power to The first output shaft output gear CC1, the first output shaft output gear CC1 is in constant mesh with the differential driven gear CZ, drives the differential to rotate and drives the vehicle to drive in III gear; when the first output shaft Z1 transmits power in III gear , the first joint J1, the second joint J2 and the second coupling L2 are in a disengaged state, and the second planetary gear ring gear XQ2 is not constrained, so the second output shaft Z2 does not transmit power.

See Figure 11, the figure shows that the transmission is in the IV gear state; when the III gear is switched to the IV gear, the input shaft synchronizer T1 is in the left position, and the second output shaft synchronizer T3 moves to the right position, at the moment of shifting , the first coupling L1 is separated, the second coupling L2 is combined, and the planetary carrier XJ2 of the second planetary gear system forms a fixed connection with the sun gear XT2 of the second planetary gear system, so that the second planetary gear system X2 forms a fourth-speed transmission to complete the shift. gear process; after that, the first output shaft synchronizer T2 moves to the middle position;

When the fourth gear is running, the input shaft ZR1 inputs the engine power, the input shaft synchronizer T1 is in the left position, so that the first forward gear CR1 is connected with the input shaft ZR1, and the second output shaft synchronizer T3 is in the right position so that II-IV The gear driven gear C2 is connected with the second output shaft Z2, because the first forward gear CR1 is in constant mesh with the II-IV gear driven gear C2, the power is transmitted from the input shaft ZR1 to the second output shaft Z2, and the second output The shaft Z2 drives the sun gear XT2 of the second planetary gear system to rotate, and the second coupling L2 is in a combined state. The sun gear XT2 of the second planetary gear system and the carrier XJ2 of the second planetary gear system form a fixed connection to realize direct transmission and power transmission To the second output shaft output gear CC2, the second output shaft output gear CC2 is in constant mesh with the differential driven gear CZ, drives the differential to rotate and drives the vehicle to drive in IV gear; the second output shaft Z2 transmits the power of IV gear , the first coupling J1, the second coupling J2 and the first coupling L1 are in a disengaged state, and the first planetary gear ring gear XQ1 is not constrained, so the first output shaft Z1 does not transmit power.

Referring to Fig. 12, the figure shows that the transmission is in the V gear state; when the IV gear is switched to the V gear, the first output shaft synchronizer T2 moves to the left position, and at the moment of shifting, the second coupling L2 is separated, and the first The adapter J1 is combined, and the first planetary gear ring gear XQ1 forms a fixed connection with the transmission housing to form the fourth gear transmission to complete the shift; after that, the input shaft synchronizer T1 moves to the middle position, and the second output shaft synchronizer T3 moves to centre position;

When the V gear is running, the input shaft ZR1 inputs the engine power, the second forward gear CR2 fixed on the input shaft ZR1 rotates along with it, and the first output shaft synchronizer T2 is in the left position so that the V-VII gear driven gear C3 and The first output shaft Z1 is connected, because the second forward gear CR2 is in constant mesh with the V-VII gear driven gear C3, the power is transmitted from the input shaft ZR1 to the first output shaft Z1, and the first output shaft Z1 drives the first planet The sun gear XT1 of the gear system rotates, and the first adapter J1 is in a combined state, so that the ring gear XQ1 of the first planetary gear system forms a fixed connection with the transmission housing, so the sun gear XT1 of the first planetary gear system and the planet carrier of the first planetary gear system A reduction transmission is formed between XJ1 and the power is transmitted to the output gear CC1 of the first output shaft. The output gear CC1 of the first output shaft is in constant mesh with the driven gear CZ of the differential to drive the differential to rotate and drive the vehicle to travel in V gear; When the first output shaft Z1 transmits the power of gear V, the first coupling L1, the second coupling J2 and the second coupling L2 are in a disengaged state, and the second planetary gear ring gear XQ2 is not constrained, so the second output shaft The Z2 doesn't deliver power.

Refer to Fig. 13, the figure shows that the transmission is in the sixth gear state; when the V gear is switched to the VI gear, the input shaft synchronizer T1 is in the middle position, and the second output shaft synchronizer T3 moves to the left position. At the moment of shifting, The first clutch J1 is separated, the second clutch J2 is combined, and the second planetary gear ring gear XQ2 forms a fixed connection with the transmission case to form VI gear transmission to complete the shift; after that, the first output shaft synchronizer T2 moves to the middle Location;

When the Ⅵ gear is running, the input shaft ZR1 inputs the engine power, the second forward gear CR2 fixed on the input shaft ZR1 rotates with it, and the second output shaft synchronizer T3 is in the left position so that the Ⅵ-Ⅷ gear driven gear C4 and The second output shaft Z2 is connected, because the second forward gear CR2 is in constant mesh with the VI-VIII gear driven gear C4, the power is transmitted from the input shaft ZR1 to the second output shaft Z2, and the second output shaft Z2 drives the second planet The sun gear XT2 of the gear train rotates, and the second adapter J2 is in a combined state, so that the ring gear XQ2 of the second planetary gear train and the transmission case form a fixed connection, so the sun gear XT2 of the second planetary gear train and the planet carrier of the second planetary gear train A reduction transmission is formed between XJ2 and the power is transmitted to the second output shaft output gear CC2, the second output shaft output gear CC2 is constantly meshed with the differential driven gear CZ, driving the differential to rotate and driving the vehicle to drive in VI gear; When the second output shaft Z2 transmits the power of gear VI, the first joint J1, the first joint L1 and the second joint L2 are in a disengaged state, and the first planetary gear ring gear XQ1 is not constrained, so the first output shaft The Z1 doesn't deliver power.

See Fig. 14, the figure shows that the transmission is in gear VII; when gear VII is switched to gear VII, the input shaft synchronizer T1 is in the middle position, and the first output shaft synchronizer T2 moves to the left position. At the moment of shifting, The second coupling J2 is separated, the first coupling L1 is combined, and the first planetary gear ring gear XQ1 and the first planetary gear carrier XJ1 form a fixed connection to form VII gear transmission to complete the gear shift; after that, the second output shaft is synchronized The device T3 moves to the middle position;

When the VII gear is running, the input shaft ZR1 inputs the engine power, and the second forward gear CR2 fixed on the input shaft ZR1 rotates with it, and the first output shaft synchronizer T2 is in the left position so that the V-VII gear driven gear C3 and The first output shaft Z1 is connected, because the second forward gear CR2 is in constant mesh with the V-VII gear driven gear C3, the power is transmitted from the input shaft ZR1 to the first output shaft Z1, and the first coupling L1 is combined to make the second The sun gear XT1 of a planetary gear system forms a fixed connection with the planetary carrier XJ1 of the first planetary gear system so as to realize direct transmission and transmit power to the output gear CC1 of the first output shaft, and the output gear CC1 of the first output shaft and the driven gear of the differential CZ is constantly meshed, drives the differential to rotate and drives the vehicle to travel in VII gear; when the first output shaft Z1 transmits the power of VII gear, the first coupling L1, the second coupling J2 and the second coupling L2 are in a disengaged state, The second planetary gear ring gear XQ2 is not constrained, so the second output shaft Z2 does not transmit power.

See Figure 15, the figure shows that the transmission is in the VIII gear state; when the VII gear is switched to the VIII gear, the input shaft synchronizer T1 is in the middle position, and the second output shaft synchronizer T3 moves to the left position. At the moment of shifting, The first coupling L1 is separated, the second coupling L2 is combined, and the second planetary gear ring gear XQ2 is fixedly connected with the second planetary gear carrier XJ2 to form VIII gear transmission to complete the gear shift; after that, the first output shaft is synchronized The device T2 moves to the middle position;

When the Ⅷ gear is running, the input shaft ZR1 inputs the engine power, the second forward gear CR2 fixed on the input shaft ZR1 rotates with it, and the second output shaft synchronizer T3 is in the left position so that the Ⅵ-Ⅷ gear driven gear C4 and The second output shaft Z2 is connected, because the second forward gear CR2 and the VI-VIII gear driven gear C4 are in a constant mesh state, the power is transmitted from the input shaft ZR1 to the second output shaft Z2, and the second coupling L2 is combined to make the second The sun gear XT2 of the second planetary gear system forms a fixed connection with the planetary carrier XJ2 of the second planetary gear system to realize direct transmission and transmit power to the second output shaft output gear CC2, and the second output shaft output gear CC2 is connected to the differential driven gear CZ is constantly meshed, drives the differential to rotate and drives the vehicle to travel in VII gear; when the second output shaft Z2 transmits the power of VIII gear, the first joint J1, the first joint L1 and the second joint J2 are in a disengaged state, The second planetary gear ring gear XQ1 is not constrained, so the first output shaft Z1 does not transmit power.

Referring to Figure 16, the figure shows that the transmission is in reverse gear; when in reverse gear, the input shaft synchronizer T1 moves to the right position, the second output shaft synchronizer T3 moves to the right position, and the second clutch J2 engages to form reverse transmission;

When the reverse gear is running, the input shaft ZR1 inputs the engine power, and the reverse gear CD1 is connected to the input shaft ZR1 through the input shaft synchronizer T1, because the reverse gear CD1 and the first reverse gear CD2 on the reverse shaft ZD1 are in a constant mesh state , the power is transmitted from the input shaft ZR1 to the reverse gear shaft ZD1, the second reverse gear CD3 on the reverse gear ZD1 is in constant mesh with the II-IV gear driven gear C2 on the second output shaft Z2, and the II-IV gear The driven gear C2 is connected to the second output shaft Z2 through the second output shaft synchronizer T3, thereby driving the second output shaft Z2 to rotate, and the second joint J2 is in the engaged state, so the sun gear XT2 of the second planetary gear system and the second The reduction transmission is formed between the planetary gears XJ2 of the planetary gear system and the power is transmitted to the second output shaft output gear CC2. The second output shaft output gear CC2 is constantly meshed with the differential driven gear CZ, thereby driving the differential to rotate and drive The vehicle runs in the reverse direction; when the second output shaft Z2 transmits reverse power, the first joint J1, the first joint L1 and the second joint L2 are in a disengaged state, and the first planetary gear ring gear XQ1 is not constrained, Therefore, the first output shaft Z1 does not transmit power.

Claims (2)

1. the speed changer with parallel planet wheel system, is characterized in that: comprise input shaft (ZR1), the first output shaft (Z1), the second output shaft (Z2), reverse gear shaft (ZD1), the first row star wheel series (X1), the second planetary gear train (X2), the first coupling (J1), the second coupling (J2), the first joiner (L1) and the second joiner (L2), differential mechanism driven gear (CZ);

The end of described the first output shaft (Z1) side is fixed with I-III gear driven gear (C1), is fixed with the first row star wheel series sun gear (XT1) on opposite side; The end of the second output shaft (Z2) side is fixed with II-IV gear driven gear (C2), on opposite side, be fixed with the second planetary gear train sun gear (XT2), on reverse gear shaft (ZD1), be fixed with the first reverse gear shaft gear (CD2) and the second reverse gear shaft gear (CD3);

The upper empty set simultaneously of described input shaft (ZR1) is provided with the first forward gear gear (CR1) and reverse gear (CD1), and the input shaft (ZR1) between described the first forward gear gear (CR1) and reverse gear (CD1) is provided with input shaft synchronizer (T1); Described the first forward gear gear (CR1) often meshes with described I-III gear driven gear (C1) and described II-IV gear driven gear (C2) simultaneously, described reverse gear (CD1) and described the first reverse gear shaft gear (CD2) often mesh, and described the second reverse gear shaft gear (CD3) and described II-IV gear driven gear (C2) often meshes;

Described the first row star wheel series (X1) comprises the first row star wheel series gear ring (XQ1), the first row star wheel series planet carrier (XJ1) and the first row star wheel series sun gear (XT1); The first row star wheel series planet carrier (XJ1) empty set is upper at the first output shaft (Z1), and the first output shaft output gear (CC1) that is being fixedly connected, and described the first output shaft output gear (CC1) often meshes with differential mechanism driven gear (CZ); Be fixedly connected one end of the first coupling (J1) of the first row star wheel series gear ring (XQ1), the other end of the first coupling (J1) case of transmission that is fixedly connected, also be fixedly connected one end of the first joiner (L1) of the first row star wheel series gear ring (XQ1), the other end of the first joiner (L1) the first output shaft (Z1) that is being fixedly connected; Described the first row star wheel series planet carrier (XJ1) is provided with plural the first row star wheel series planet wheel, and described the first row star wheel series sun gear (XT1), plural the first row star wheel series planet wheel, the first row star wheel series planet carrier (XJ1) and the first row star wheel series gear ring (XQ1) form the driving mechanism of the first row star wheel series (X1);

Described the second planetary gear train (X2) comprises the second planetary gear train gear ring (XQ2), the second planetary gear train planet carrier (XJ2) and the second planetary gear train sun gear (XT2); The second planetary gear train planet carrier (XJ2) empty set is upper at the second output shaft (Z2), and the second output shaft output gear (CC2) that is being fixedly connected, and described the second output shaft output gear (CC2) often meshes with differential mechanism driven gear (CZ); Be fixedly connected one end of the second coupling (J2) of the second planetary gear train gear ring (XQ2), the other end of the second coupling (J2) case of transmission that is fixedly connected; Also be fixedly connected one end of the second joiner (L2) of the second planetary gear train gear ring (XQ2), the other end of the second joiner (L2) the second output shaft (Z2) that is being fixedly connected; Described the second planetary gear train planet carrier (XJ2) is provided with plural the second planetary gear train planet wheel, and described the second planetary gear train sun gear (XT2), plural the second planetary gear train planet wheel, the second planetary gear train planet carrier (XJ2) and the second planetary gear train gear ring (XQ2) form the driving mechanism of the second planetary gear train (X2);

The output terminal of the output terminal of the input end of described input shaft (ZR1), the first output shaft (Z1) and the second output shaft (Z2) is all positioned at the same side;

Described the first row star wheel series (X1) is positioned at the outlet side of the first output shaft (Z1), and described the second planetary gear train (X2) is positioned at the outlet side of the second output shaft (Z2);

Above-mentioned speed changer is realized four-speed and the speed change of reversing gear.

2. the speed changer with parallel planet wheel system, is characterized in that: comprise input shaft (ZR1), the first output shaft (Z1), the second output shaft (Z2), reverse gear shaft (ZD1), the first row star wheel series (X1), the second planetary gear train (X2), the first coupling (J1), the second coupling (J2), the first joiner (L1) and the second joiner (L2), differential mechanism driven gear (CZ);

One side empty set of described the first output shaft (Z1) is provided with I-III gear driven gear (C1) and V-VII gear driven gear (C3), and the first output shaft (Z1) between I-III gear driven gear (C1) and V-VII gear driven gear (C3) is provided with the first output shaft synchronous device (T2), is fixed with the first row star wheel series sun gear (XT1) on the opposite side of the first output shaft (Z1);

One side empty set of described the second output shaft (Z2) is provided with II-IV gear driven gear (C2) and VI-VIII gear driven gear (C4), and the second output shaft (Z2) between II-IV gear driven gear (C2) and VI-VIII gear driven gear (C4) is provided with the second output shaft synchronous device (T3), is fixed with the second planetary gear train sun gear (XT2) on the opposite side of the second output shaft (Z2);

On described reverse gear shaft (ZD1), be fixed with the first reverse gear shaft gear (CD2) and the second reverse gear shaft gear (CD3);

On described input shaft (ZR1), be fixed with the second forward gear gear (CR2) simultaneously, empty set is provided with the first forward gear gear (CR1) and reverse gear (CD1), the input shaft (ZR1) between described the first forward gear gear (CR1) and reverse gear (CD1) is provided with input shaft synchronizer (T1); Described the first forward gear gear (CR1) often meshes with described I-III gear driven gear (C1), described II-IV gear driven gear (C2) simultaneously; Described the second forward gear gear (CR2) often meshes with described V-VII gear driven gear (C3), described VI-VIII gear driven gear (C4) simultaneously, described reverse gear CD1 and described the first reverse gear shaft gear (CD2) often mesh, and described the second reverse gear shaft gear (CD3) often meshes with described II-IV gear driven gear (C2);

Described the first row star wheel series (X1) comprises the first row star wheel series gear ring (XQ1), the first row star wheel series planet carrier (XJ1) and the first row star wheel series sun gear (XT1); The first row star wheel series planet carrier (XJ1) empty set is upper at the first output shaft (Z1), and the first output shaft output gear (CC1) that is being fixedly connected, and described the first output shaft output gear (CC1) often meshes with differential mechanism driven gear (CZ); Be fixedly connected one end of the first coupling (J1) of the first row star wheel series gear ring (XQ1), the other end of the first coupling (J1) case of transmission that is fixedly connected, also be fixedly connected one end of the first joiner (L1) of the first row star wheel series gear ring (XQ1), the other end of the first joiner (L1) the first output shaft (Z1) that is being fixedly connected; Described the first row star wheel series planet carrier (XJ1) is provided with plural the first row star wheel series planet wheel, and described the first row star wheel series sun gear (XT1), plural the first row star wheel series planet wheel, the first row star wheel series planet carrier (XJ1) and the first row star wheel series gear ring (XQ1) form the driving mechanism of the first row star wheel series (X1);

Described the second planetary gear train (X2) comprises the second planetary gear train gear ring (XQ2), the second planetary gear train planet carrier (XJ2) and the second planetary gear train sun gear (XT2); The second planetary gear train planet carrier (XJ2) empty set is upper at the second output shaft (Z2), and the second output shaft output gear (CC2) that is being fixedly connected, and described the second output shaft output gear (CC2) often meshes with differential mechanism driven gear (CZ); Be fixedly connected one end of the second coupling (J2) of the second planetary gear train gear ring (XQ2), the other end of the second coupling (J2) case of transmission that is fixedly connected; Also be fixedly connected one end of the second joiner (L2) of the second planetary gear train gear ring (XQ2), the other end of the second joiner (L2) the second output shaft (Z2) that is being fixedly connected; Described the second planetary gear train planet carrier (XJ2) is provided with plural the second planetary gear train planet wheel, and described the second planetary gear train sun gear (XT2), plural the second planetary gear train planet wheel, the second planetary gear train planet carrier (XJ2) and the second planetary gear train gear ring (XQ2) form the driving mechanism of the second planetary gear train (X2);

The output terminal of the output terminal of the input end of described input shaft (ZR1), the first output shaft (Z1) and the second output shaft (Z2) is all positioned at the same side;

Described the first row star wheel series (X1) is positioned at the outlet side of the first output shaft (Z1), and described the second planetary gear train (X2) is positioned at the outlet side of the second output shaft (Z2);

Above-mentioned speed changer is realized eight speed and the speed changes of reversing gear.

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