CN213685176U

CN213685176U - Double-turbine hydraulic torque converter confluence mechanism

Info

Publication number: CN213685176U
Application number: CN202022524185.XU
Authority: CN
Inventors: 王松林; 章勇华; 鄢万斌; 曾垂远
Original assignee: Liugong Liuzhou Driving Member Co ltd; Guangxi Liugong Machinery Co Ltd
Current assignee: Liugong Liuzhou Driving Member Co ltd; Guangxi Liugong Machinery Co Ltd
Priority date: 2020-11-05
Filing date: 2020-11-05
Publication date: 2021-07-13
Anticipated expiration: 2030-11-05

Abstract

The utility model relates to a double-turbine hydraulic torque converter converging mechanism, which aims to solve the problem that the stall torque ratio of the existing double-turbine hydraulic torque converter converging mechanism can not meet the requirements of the power performance of the whole machine, and the utility model constructs a double-turbine hydraulic torque converter converging mechanism which comprises a I-stage gear and a II-stage gear in a double-turbine hydraulic torque converter, an outer ring gear and a middle shaft gear in an overrunning clutch; the I-stage gear is meshed with the outer ring gear to form a gear pair I, II, and the intermediate shaft gear Z4 is meshed to form a gear pair II; the module m of each gear is 6 mm or more and m or more and 5mm or more, and the total number of teeth z of each gear pair is 94 mm or more and z or more and 78 or more. The utility model discloses a gear modulus and the number of teeth of adjustment gear pair promote gear pair I velocity ratio, reduce gear pair II's velocity ratio, promote gear pair I's positive output torque, reduce gear pair II's negative output torque under the stall operating mode, promote the mechanism output torque that converges. Under the working condition of high speed and light load, the working efficiency of the whole machine is improved.

Description

Double-turbine hydraulic torque converter confluence mechanism

Technical Field

The utility model relates to a twin turbine hydraulic torque converter, more specifically say, relate to a twin turbine hydraulic torque converter mechanism that converges.

Background

The double-turbine hydraulic torque converter is an important transmission component of the existing loader. In the double-turbine hydraulic torque converter, as shown in fig. 1 and fig. 2, an engine 3 transmits power to a pump impeller 12, a converter cavity is filled with liquid, the pump impeller 12 converts mechanical energy of the engine into kinetic energy of liquid flow, and a stage I turbine 13 and a stage II turbine 14 absorb the kinetic energy of the liquid flow and output the power through a stage I gear Z1 and a stage II gear Z2. To the outer ring gear Z3 and the countershaft gear Z4 on the overrunning clutch. Power is input to the gearbox through the confluence of an outer ring gear Z3 and a middle shaft gear Z4. The gear pair I is formed by meshing an I-stage gear Z1 and an outer ring gear Z3, and the transmission ratio I1 is Z3/Z1; the gear Z2 of stage II is meshed with the intermediate shaft gear Z4 to form a gear pair II, and the transmission ratio i2 is equal to Z4/Z2. The gear pair I and the gear pair II are called a confluence mechanism.

The integral capacity of the domestic loader industry is 8-10 thousands of machines per year, wherein the proportion of a 5-ton loader is more than 80%, and the transmission of the 5-ton loader mainly adopts a double-turbine torque converter and planetary gearbox structure, so that the transmission has large torque conversion capacity and wide high-efficiency area and is widely applied in China.

For the double-turbine hydraulic torque converter confluence mechanism in the existing 5-ton loader, the center distance of a gear pair is 234mm, the gear module is 6.5mm, and the total number of teeth of the gear pair is 72. According to the confluence mechanism with the parameter configuration, under the stalling working condition, the output torque of the confluence mechanism is small, and the requirement of the output torque cannot be met.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is that current twin turbine torque converter converges the problem that the stall torque ratio of mechanism can not satisfy complete machine power performance requirement, and provides a twin turbine torque converter mechanism that converges, under the stall operating mode, improves the mechanism output torque that converges, reaches the demand of output torque.

The utility model discloses a realize that the technical scheme of its purpose is like: a double-turbine hydraulic torque converter confluence mechanism is constructed, and comprises a stage I gear Z1 and a stage II gear Z2 in a double-turbine hydraulic torque converter, an outer ring gear Z3 in an overrunning clutch and an intermediate shaft gear Z4; the stage I gear Z1 is meshed with the outer ring gear Z3 to form a gear pair I, and the stage II gear Z2 is meshed with the middle shaft gear Z4 to form a gear pair II; the gear is characterized in that the modulus m of each gear is 6 mm or more and m is more than or equal to 5mm, and the total number z of teeth of each gear pair is 94 mm or more and z is more than or equal to 78.

In the above-described twin-turbine torque converter confluence mechanism, the modules of the gears are the same, and the total number of teeth of the gear pairs is the same.

In the above-mentioned twin-turbine torque converter confluence mechanism, the module m of each gear is 6 mm, and the total number of teeth z of each gear pair is 78; wherein the tooth number Z1 of the gear Z1 of the I stage is Z1 ═ 23 or Z1 ═ 24, and the tooth number Z2 of the gear Z2 of the II stage is Z2 ═ 43; or the tooth number Z1 of the gear Z1 in the stage I is 21 which is equal to Z1, and the tooth number Z2 of the gear Z2 in the stage II is 42 which is equal to Z2. Or the tooth number Z1 of the I-stage gear Z1 is 22, and the tooth number Z2 of the II-stage gear Z2 is Z2 is 43.

In the above-mentioned twin-turbine torque converter confluence mechanism, the module m of each gear is 5.5 mm, and the total number of teeth z of each gear pair is 85; wherein the tooth number Z1 of the gear Z1 of the I stage is Z1 ═ 25 or Z1 ═ 26, and the tooth number Z2 of the gear Z2 of the II stage is Z2 ═ 47; or the tooth number Z1 of the I-stage gear Z1 is Z1-23, and the tooth number Z2 of the II-stage gear Z2 is Z2-46; or the tooth number Z1 of the I-stage gear Z1 is 24, and the tooth number Z2 of the II-stage gear Z2 is Z2 is 47.

In the above-mentioned twin-turbine torque converter confluence mechanism, the module m of each gear is 5mm, and the total number of teeth z of each gear pair is 94; wherein the tooth number Z1 of the gear Z1 of the I stage is Z1 ═ 28 or Z1 ═ 29, and the tooth number Z2 of the gear Z2 of the II stage is Z2 ═ 52; or the tooth number Z1 of the I-stage gear Z1 is Z1, and the tooth number Z2 of the II-stage gear Z2 is Z2 which is 51; or the tooth number Z1 of the I-stage gear Z1 is 27, and the tooth number Z2 of the II-stage gear Z2 is Z2 is 51.

In the above-described twin-turbine torque converter confluence mechanism, the center-to-center distance of each gear pair is 234 mm.

Compared with the prior art, the utility model discloses a gear modulus and the number of teeth of adjustment gear pair promote gear pair I velocity ratio, reduce gear pair II's velocity ratio simultaneously, promote gear pair I's positive output torque, reduce gear pair II's negative output torque under the stall operating mode, promote the mechanism output torque that converges. Under the working condition of high speed and light load, the highest speed of the whole machine is improved due to the reduction of the speed ratio of the gear pair II, so that the aim of improving the working efficiency of the whole machine is fulfilled.

Drawings

FIG. 1 is a schematic diagram of a twin turbine torque converter and overrunning clutch configuration.

Fig. 2 is a schematic diagram of a double-turbine torque converter confluence mechanism.

Fig. 3 is a graph of the relationship between the torque ratio and the speed ratio of the torque converter of the present invention.

Fig. 4 is a graph of the relationship between the thousand-turn capacity and the speed ratio of the torque converter of the present invention.

Fig. 5 is a graph of efficiency versus speed ratio for a torque converter according to the present invention.

Part names and serial numbers in the figure:

the double-turbine hydraulic torque converter comprises a double-turbine hydraulic torque converter 1, a cover wheel 11, a pump wheel 12, a first-stage turbine 13, a second-stage turbine 14, an overrunning clutch 2 and an engine 3.

Detailed Description

The following description of the embodiments refers to the accompanying drawings.

The first embodiment.

As shown in fig. 1 and fig. 2, a hydraulic conventional mechanism of a loader comprises a double-turbine hydraulic torque converter 1 and an overrunning clutch 2, and a shell of the torque converter 1 is fixedly connected with a shell of a gearbox (not shown). In the double-turbine hydraulic torque converter, the engine 3 transmits power to the pump impeller 12 through the shroud wheel 11, a cavity formed by the shroud wheel 11 and the pump impeller 12 of the torque converter 1 is filled with liquid, the pump impeller 12 converts mechanical energy of the engine 3 into kinetic energy of liquid flow, and the stage I turbine 13 and the stage II turbine 14 absorb the kinetic energy of the liquid flow and output the power through the stage I gear Z1 and the stage II gear Z2. To the outer ring gear Z3 and the countershaft gear Z4 on the overrunning clutch 2. Power is input to the gearbox through the confluence of an outer ring gear Z3 and a middle shaft gear Z4. The gear pair I is formed by meshing an I-stage gear Z1 and an outer ring gear Z3, and the transmission ratio (speed ratio) of the gear pair I1 is Z3/Z1; the gear Z2 of stage II is meshed with the intermediate shaft gear Z4 to form a gear pair II, and the transmission ratio i2 is equal to Z4/Z2. The gear pair I and the gear pair II are called a confluence mechanism. The ratio of the intermediate shaft gear speed to the engine speed is the torque converter speed ratio i. The I-stage gear Z1 and the II-stage gear Z2 are supported on the torque converter shell, and the overrunning intermediate shaft gear and the overrunning outer ring gear are supported on the torque converter shell and the transmission shell, and the center distance of the overrunning intermediate shaft gear and the overrunning outer ring gear is a.

In the present embodiment, the center distance a of each gear pair is 234mm, the module m of each gear is 6 mm, the total number Z of teeth of the gear pair is 78, the maximum stall torque ratio K0 is 4.10, wherein the number Z1 of teeth of the I-stage gear is 22, the number Z3 of teeth of the outer ring gear Z3 is 56, and the speed ratio I1 of the gear pair I is 2.55; the number of teeth z2 of the stage II gear is 43, the number of teeth z4 of the intermediate shaft gear is 35, and the speed ratio i2 of the gear pair II is 0.81 at i 2.

Compared with the existing confluence mechanism, under the condition that other configurations are not changed, the confluence mechanism in the embodiment can obviously improve the maximum stall and torque ratio of the torque converter, improves the power performance of the whole machine without influencing the maximum speed, and has higher operation efficiency. As shown in fig. 3, in the range where the rotation speed ratio i of the torque converter is less than 0.4, the maximum torque ratio of the torque converter using the confluence mechanism in the present embodiment is significantly larger than that of the torque converter using the conventional confluence mechanism. As shown in fig. 4, in the range where the rotation speed ratio i of the torque converter is less than 0.7, the thousand-revolution capacity of the torque converter using the confluence mechanism in the present embodiment is significantly larger than that of the torque converter using the conventional confluence mechanism. As shown in fig. 5, the efficiency of the whole machine is also improved. In fig. 3 to 5, the broken line corresponds to a characteristic curve of a torque converter using the conventional bus mechanism, and the solid line corresponds to a characteristic curve of a torque converter using the bus mechanism configured as described above in the present embodiment.

The parameters of the existing confluence mechanism are configured as follows: the center distance a of the gear pair is 234 millimeters, the modulus m of each gear is 6.5 millimeters, the total number Z of teeth of the gear pair is 72, the stall torque ratio K0 is 3.95, the number Z1 of teeth of the I-stage gear is 21, the number Z3 of teeth of the outer ring gear Z3 is 51, and the speed ratio I1 of the gear pair I is 2.43; the number of teeth z2 of the stage II gear is 39, the number of teeth z4 of the intermediate shaft gear is 33, and the speed ratio i2 of the gear pair II is 0.85.

According to the working principle of the twin-turbine hydraulic torque converter, the stage I turbine provides positive torque and the stage II turbine provides negative torque under the stall condition, and the stage II turbine begins to provide positive torque when the speed ratio I is larger than 0.12 along with the increase of the speed ratio I of the torque converter. According to the working principle of the overrunning clutch, under the working condition of low speed and heavy load, the power is output to the gearbox by the confluence of the gear pair I and the gear pair II, and under the working condition of high speed and light load, the gear pair I is disengaged and only the gear pair II outputs the power to the gearbox.

In this embodiment, compared with the existing confluence mechanism, through adjusting the gear module and the number of teeth of the gear pair, the speed ratio I1 of the gear pair I is improved, the speed ratio I2 of the gear pair II is reduced, the positive output torque of the gear pair I is improved under the stall working condition, the negative output torque of the gear pair II is reduced, the output torque of the confluence mechanism is improved (namely, the stall torque ratio is improved), under the high-speed light load working condition, because the speed ratio of the gear pair 2 is reduced, the maximum speed of the whole machine is improved, and therefore the purpose of improving the working efficiency of the whole machine is achieved.

In this embodiment, under the condition that the center distance a of the gear pair is 234mm, the module m of each gear is 6 mm, and the total number of teeth Z of the gear pair is 78, the number of teeth of the first-stage gear and the number of teeth of the second-stage gear are adjusted, so as to realize other configurations, for example, the number of teeth Z1 of the first-stage gear Z1 may be 23 or 24, and the number of teeth Z2 of the second-stage gear Z2 is 43; or the tooth number Z1 of the I-stage gear Z1 is 21, and the tooth number Z2 of the II-stage gear Z2 is 42. Specific configuration parameters are shown in table 1.

Example two.

In the embodiment, under the condition that the center distance a of the gear pair is kept to be 234mm, the module m of the gear may also be 5.5 mm, or 5 mm.

When the modulus m of the gear is 5.5 mm, the total number of teeth z of the gear pair is 85; wherein the tooth number Z1 of the I-stage gear Z1 can be an integer value between 24 and 26, and the tooth number Z2 of the II-stage gear Z2 is 47; or the tooth number Z1 of the I-stage gear Z1 is 23, and the tooth number Z2 of the II-stage gear Z2 is 46.

When the module m of the gear takes 5mm, the total number of teeth z of each gear pair is 94; wherein the tooth number Z1 of the I-stage gear Z1 is 29 or 28, and the corresponding tooth number Z2 of the II-stage gear Z2 is 52; or the tooth number Z1 of the I-stage gear Z1 is 27 or 26, and the corresponding tooth number Z2 of the II-stage gear Z2 is 51.

Table 1 shows the gear pair configuration parameters of the first and second embodiments of the converging mechanism.

Table 1. summary table of gear pair configuration parameters of the confluence mechanism.

Claims

1. A twin-turbine torque converter confluence mechanism comprises a stage I gear Z1 and a stage II gear Z2 in a twin-turbine torque converter, an outer ring gear Z3 in an overrunning clutch and an intermediate shaft gear Z4; the stage I gear Z1 is meshed with the outer ring gear Z3 to form a gear pair I, and the stage II gear Z2 is meshed with the middle shaft gear Z4 to form a gear pair II;

the gear is characterized in that the modulus m of each gear is 6 mm or more and m is more than or equal to 5mm, and the total number z of teeth of each gear pair is 94 mm or more and z is more than or equal to 78.

2. The twin-turbine torque converter manifold mechanism of claim 1, wherein the gears have the same module and the gear pairs have the same total number of teeth.

3. The twin-turbine torque converter manifold mechanism of claim 1, wherein the module m of each gear is 6 mm, and the total number of teeth z of each gear pair is 78 z;

wherein the tooth number Z1 of the I-stage gear Z1 is Z1 ═ 23 or Z1 ═ 24, and the tooth number Z2 of the II-stage gear Z2 is Z2 ═ 43;

or the tooth number Z1 of the I-stage gear Z1 is Z1-21, and the tooth number Z2 of the II-stage gear Z2 is Z2-42.

4. The twin-turbine torque converter manifold mechanism of claim 1, wherein the module m of each gear is 6 mm, and the total number of teeth z of each gear pair is 78 z; the tooth number Z1 of the stage I gear Z1 is 22, and the tooth number Z2 of the stage II gear Z2 is Z2 is 43.

5. The twin-turbine torque converter confluence mechanism according to claim 1 wherein each gear has a module m of 5.5 mm, and each gear pair has a total number of teeth z of 85;

wherein the tooth number Z1 of the I-stage gear Z1 is Z1 ═ 25 or Z1 ═ 26, and the tooth number Z2 of the II-stage gear Z2 is Z2 ═ 47;

or the tooth number Z1 of the I-stage gear Z1 is Z1-23, and the tooth number Z2 of the II-stage gear Z2 is Z2-46.

6. The twin-turbine torque converter confluence mechanism according to claim 1 wherein each gear has a module m of 5.5 mm, and each gear pair has a total number of teeth z of 85; the tooth number Z1 of the stage I gear Z1 is 24, and the tooth number Z2 of the stage II gear Z2 is Z2 is 47.

7. The twin-turbine torque converter manifold mechanism of claim 1, wherein the module m of each gear is 5mm, and the total number of teeth z of each gear pair is 94;

wherein the tooth number Z1 of the I-stage gear Z1 is Z1 ═ 28 or Z1 ═ 29, and the tooth number Z2 of the II-stage gear Z2 is Z2 ═ 52;

or the tooth number Z1 of the I-stage gear Z1 is Z1-26, and the tooth number Z2 of the II-stage gear Z2 is Z2-51.

8. The twin-turbine torque converter manifold mechanism of claim 1, wherein the module m of each gear is 5mm, and the total number of teeth z of each gear pair is 94; the tooth number Z1 of the stage I gear Z1 is 27, and the tooth number Z2 of the stage II gear Z2 is 51, Z2.

9. The twin-turbine torque converter confluence mechanism according to any one of claims 1 to 8, wherein the gear pairs have a center-to-center distance of 234 mm.