Large-capacity torque converter matched with low-rotating-speed engine

Abstract

The utility model relates to the technical field of torque converters, in particular to a large-capacity torque converter matched with a low-rotating-speed engine, which comprises a torque converter shell, a cover wheel is arranged in an inner cavity of the torque converter shell, a cover wheel shaft is integrally formed on the left side of the cover wheel, the left end of the cover wheel shaft extends to the left side of the torque converter shell, and a guide wheel seat is arranged on the right side of the cover wheel. The right end of the guide wheel base is fixedly connected to the torque converter shell, the circumferential outer wall of the middle section of the guide wheel base is movably sleeved with a pump wheel, the left end of the pump wheel is fixedly connected with the right end of the cover wheel, and the circumferential outer wall of the left end of the guide wheel base is fixedly sleeved with a guide wheel. The middle section of the double-turbine set penetrates through the middle space of the guide wheel base, and the right end of the double-turbine set is connected with an overrun clutch in a matched mode. The utility model has the following beneficial effects: the engine clutch can be matched with an engine with the speed of 1800rpm and can work together with the engine in a low-oil-consumption area, so that the loader has good working efficiency and fuel economy under the condition that the dynamic property requirement of the loader is met.

Description

Technical Field

[0001] The utility model relates to the technical field of torque converters, in particular to a large-capacity torque converter matched with a low-speed engine. Background Art

[0002] Wheel loaders are a type of construction machinery used for earthmoving operations. They still occupy an important share in the market because of their wide range of uses, high productivity, good mobility, and low cost of short-distance earthmoving operations. As the core component of the hydromechanical transmission system in wheel loaders, twin-turbine torque converters are still widely used as a preferred choice in wheel loader transmission systems because they have a large torque range and a wide high-efficiency range, which can effectively simplify the transmission system structure.

[0003] With the development of highway, port, construction, mining and other projects, wheel loaders have higher requirements for power performance and fuel economy. Therefore, improving fuel economy to save energy and reduce consumption has become one of the main tasks of each main engine manufacturer. The main measure to improve fuel economy is to reduce the rated speed of the engine so that it works in a low fuel consumption area. In order to ensure good working performance between the engine and the torque converter, it is necessary to develop a low-speed torque converter that matches it.

[0004] For example, in the patent document with patent publication number CN202091463U, a new type of hydraulic torque converter is disclosed, which includes a shaft head, an adjustment pad, a pressure plate, a turbine, an elastic plate, an elastic plate assembly, a cover wheel, a bearing seat, a guide wheel, a pump wheel, a retaining ring, a pin, a gear, a bearing, a thrust bearing, a spline sleeve, and a turbine hub. The hydraulic torque converter blades matching the low-speed and high-power engine are adopted, the guide wheel assembly adopts an alloy steel spline sleeve, a keyway is designed in the gear, and the gear pump is directly connected. The left end of the cover wheel is bolted Multiple elastic plates are connected, the cover wheel is separated from the shaft head, the shaft head is connected to the cover wheel by bolts, the pressure plate, the elastic plate, and the elastic plate assembly are connected to the cover wheel by bolts to form a power input component, the pump wheel and the cover wheel are rigidly connected together by bolts, the turbine is riveted together with the turbine hub by rivets, and is supported on the cover wheel by bearings. The guide wheel, spline sleeve and retaining ring constitute the guide wheel assembly, and the guide wheel assembly is supported between the pump wheel and the turbine by two bearing seats and two thrust bearings. Oil passages are cast on the two bearing seats, and the gear is connected to the pump wheel by bolts and pins.

[0005] According to the existing technical literature, it can be seen that the maximum efficiency and high-efficiency zone of the existing torque converter are relatively small. Therefore, when it is used in conjunction with an engine, the engine's utilization efficiency is low, and the engine cannot be effectively operated in a low fuel consumption area, resulting in poor fuel economy of the engine.

[0006] To this end, the utility model optimizes and improves the problem of low fuel economy in the prior art, and hereby proposes a new twin-turbo torque converter that can further improve the fuel economy of the loader by matching with a low-speed engine of 1800rpm, so as to better solve the problems in the prior art. Utility Model Content

[0007] The utility model is to solve one of the above technical problems, and the technical scheme adopted is: a large-capacity torque converter matching a low-speed engine, comprising a torque converter housing, a cover wheel is coaxially arranged in the inner cavity on the left side of the torque converter housing, a cover wheel axle is integrally formed on the left side of the cover wheel along its axial direction, the left end of the cover wheel axle extends to the left side of the torque converter housing, a guide wheel seat is coaxially arranged on the right side of the cover wheel, the guide wheel seat is hollowly arranged along its axial direction, the right end of the guide wheel seat is fixedly connected to the torque converter housing, a pump wheel is coaxially sleeved on the circumferential outer wall of the middle section of the guide wheel seat, the circumferential connection part of the left end of the pump wheel is fixedly connected to the circumferential connection part of the right end of the cover wheel, a guide wheel is coaxially sleeved on the circumferential outer wall of the left end of the guide wheel seat, and also comprises a twin turbine group, the left end of the twin turbine group is arranged in the space between the cover wheel and the guide wheel, the middle section of the twin turbine group passes through the middle space of the guide wheel seat and extends to the right side thereof, and one side of the right end of the twin turbine group is cooperatively connected with an overrunning clutch.

[0008] In any of the above schemes, preferably, the dual-turbine group includes a first turbine, a turbine cover and a first turbine output shaft, the turbine cover is coaxially arranged in the space between the cover wheel and the guide wheel, the circumferential connecting part of the right end of the turbine cover is coaxially fixedly connected to the circumferential connecting part of the left end of the first turbine, the left end of the turbine cover is coaxially fixedly sleeved on the circumferential outer wall of the left end of the first turbine output shaft, the middle section of the first turbine output shaft is axially movably inserted in the central space of the guide wheel seat, and a first output shaft gear is coaxially fixedly sleeved on the circumferential outer wall of the right end of the first turbine output shaft, and the first output shaft gear is meshingly connected with the first end gear at the corresponding position of the overrunning clutch.

[0009] In any of the above schemes, preferably, the dual-turbine group also includes a second turbine and a second turbine output shaft, the second turbine is coaxially arranged in the space surrounded by the first turbine, the turbine cover and the guide wheel, the second turbine output shaft is hollow along its axial direction, the middle section of the second turbine output shaft is movably inserted in the middle space of the guide wheel seat along the axial direction, the middle section of the first turbine output shaft is movably inserted in the middle space of the second turbine output shaft along the axial direction, the second turbine is coaxially fixedly sleeved on the circumferential outer wall of the left end of the second turbine output shaft, a second output shaft gear is coaxially provided on the left side of the first output shaft gear, the second output shaft gear is coaxially fixedly sleeved on the circumferential outer wall of the right end of the second turbine output shaft, and the second output shaft gear is meshed and connected with the second end gear at the corresponding position of the overrunning clutch.

[0010] In any of the above schemes, preferably, there is a gap between the circumferential inner wall of the guide wheel seat and the circumferential outer wall of the second turbine output shaft for the working fluid to flow.

[0011] In any of the above schemes, preferably, the circulation circle diameter of the torque converter is 347 mm, the zero-speed torque coefficient is 3.98, and the nominal torque is approximately 211 N·m.

[0012] In any of the above solutions, preferably, the transmission ratio between the first output shaft gear 11 and the first end gear 7.1 is 2.6:1.

[0013] In any of the above solutions, it is preferred that the transmission ratio between the second output shaft gear 14 and the second end gear 7.2 is 1:0.8.

[0014] In any of the above solutions, it is preferred that the number of teeth of the first output shaft gear 11 is 52, and the number of teeth of the first end gear 7.1 is 20.

[0015] In any of the above solutions, it is preferred that the number of teeth of the second output shaft gear 14 is 32, and the number of teeth of the second end gear 7.2 is 40.

[0016] Compared with the prior art, the beneficial effects of the utility model are as follows:

[0017] 1. The utility model optimizes the blades of each impeller and increases the diameter of the circulation circle, thereby increasing the nominal torque of the torque converter with the minimum manufacturing cost, ensuring the highest efficiency and high efficiency range of the torque converter, and effectively improving the efficiency of the engine.

[0018] 2. The circulation circle diameter of the twin-turbine torque converter of the utility model is increased to 347 mm, the torque ratio is 3.98, and the nominal torque is about 211 N m. The transmission ratio between the first output shaft gear and the first end gear is reasonably adjusted to 2.6, and the transmission ratio between the second output shaft gear and the second end gear is reasonably adjusted to 0.8, so that the torque converter can match the 1800 rpm (170 kW) low-speed engine of the 5-ton loader, and work together with the engine in the low fuel consumption area, so that the loader has good working efficiency and fuel economy while meeting the power requirements of the loader. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solution of the specific implementation of the utility model, the following will briefly introduce the drawings required for the specific implementation. In all the drawings, similar elements or components are generally identified by similar reference numerals. In the drawings, each element or component is not necessarily drawn according to the actual scale.

[0020] Figure 1 It is a schematic cross-sectional structure diagram of the torque converter of the utility model.

[0021] Figure 2 The utility model is a schematic diagram of the transmission principle of the torque converter.

[0022] In the figure, 1, torque converter housing; 2, cover wheel shaft; 3, cover wheel; 4, guide wheel seat; 5, pump wheel; 6, guide wheel; 7, overrunning clutch; 8, first turbine; 9, turbine cover; 10, first turbine output shaft; 11, first output shaft gear; 12, second turbine; 13, second turbine output shaft; 14, second output shaft gear; 7.1, first end gear; 7.2, second end gear. DETAILED DESCRIPTION

[0023] The following is a detailed description of the embodiments of the technical solution of the utility model in conjunction with the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the utility model, and are therefore only used as examples, and cannot be used to limit the scope of protection of the utility model. Figure 1-Figure 2 as shown in .

[0024] A large-capacity torque converter matching a low-speed engine comprises a torque converter housing 1, a cover wheel 3 is coaxially arranged in the inner cavity on the left side of the torque converter housing 1, a cover wheel shaft 2 is integrally formed on the left side of the cover wheel 3 along its axial direction, the left end of the cover wheel shaft 2 extends to the left side of the torque converter housing 1, a guide wheel seat 4 is coaxially arranged on the right side of the cover wheel 3, the guide wheel seat 4 is hollow along its axial direction, the right end of the guide wheel seat 4 is fixedly connected to the torque converter housing 1, and a guide wheel seat 4 is provided around the middle section of the guide wheel seat 4. A pump wheel 5 is coaxially mounted on the outer wall, and the circumferential connection portion at the left end of the pump wheel 5 is fixedly connected to the circumferential connection portion at the right end of the cover wheel 3. A guide wheel 6 is coaxially mounted on the circumferential outer wall at the left end of the guide wheel seat 4. The guide wheel 6 also includes a twin turbine group, and the left end of the twin turbine group is arranged in the space between the cover wheel 3 and the guide wheel 6. The middle section of the twin turbine group passes through the middle space of the guide wheel seat 4 and extends to the right side thereof. An overrunning clutch 7 is connected to one side of the right end of the twin turbine group.

[0025] An installation cavity is formed inside the torque converter housing 1. The left end of the cover wheel shaft 2 is transmission-connected to the output end of the power machine, and the right end is coaxially arranged with the cover wheel 3. The right end of the cover wheel 3 is coaxially fixedly connected to the left end of the pump wheel 5 by means of rivets. At the same time, the right end of the pump wheel 5 is fixedly mounted on the pump wheel hub by means of rivets. The pump wheel 5 and the pump wheel hub are assembled on the circumferential outer wall in the middle of the guide wheel seat 4 through bearings. At the same time, the guide wheel seat 4 is fixedly mounted on the torque converter housing 1 so that its position remains unchanged. In this way, when the power machine is working, the cover wheel 3 is driven to rotate by the cover wheel shaft 2, and then the pump wheel 5 is driven to rotate synchronously under the support of the guide wheel seat 4.

[0026] Through the fixed connection between the cover wheel 3 and the pump wheel 5, a cavity is formed between the two, and the guide wheel 6 is arranged in the cavity. The guide wheel 6 is fixedly connected to the left end of the guide wheel seat 4 by spline connection to achieve radial positioning of the guide wheel 6, and its right end is pressed against the inner ring of the bearing used to assemble the pump wheel 5, and a retaining ring is arranged on its left side to achieve axial positioning of the guide wheel 6.

[0027] The left end of the twin turbine group is arranged in the cavity between the cover wheel 3 and the pump wheel 5, and is also located in the space between the cover wheel 3 and the guide wheel 6. The middle section thereof is movably inserted in the middle of the guide wheel seat 4, and extends to the right side thereof to be transmission-connected with the overrunning clutch 7.

[0028] The pump wheel 5 rotates under the drive of the cover wheel 3. Under the action of the pump wheel blades, the working fluid flows to the left end of the twin turbine group and drives it to rotate, and then transmits the overrunning clutch 7 through its right end, so that the overrunning clutch 7 performs the corresponding action. Then the working fluid flows out from the blade flow channel at the left end of the twin turbine group and flows into the blade flow channel of the guide wheel 6, and then returns to the blade flow channel of the pump wheel 5 through the blade flow channel of the guide wheel 6, so as to carry out the next working cycle.

[0029] In any of the above schemes, it is preferred that the dual-turbine group includes a first turbine 8, a turbine cover 9 and a first turbine output shaft 10, the turbine cover 9 is coaxially arranged in the space between the cover wheel 3 and the guide wheel 6, the circumferential connection part at the right end of the turbine cover 9 is coaxially fixedly connected to the circumferential connection part at the left end of the first turbine 8, the left end of the turbine cover 9 is coaxially fixedly sleeved on the circumferential outer wall of the left end of the first turbine output shaft 10, the middle section of the first turbine output shaft 10 is axially movably inserted in the central space of the guide wheel seat 4, and a first output shaft gear 11 is coaxially fixedly sleeved on the circumferential outer wall at the right end of the first turbine output shaft 10, and the first output shaft gear 11 is meshingly connected with the first end gear 7.1 at the corresponding position of the overrunning clutch 7.

[0030] The turbine cover 9 is coaxially arranged between the cover wheel 3 and the guide wheel 6, and its left end is assembled on the left end of the first turbine output shaft 10 by means of spline connection, and its right end is coaxially fixedly connected with the left end of the first turbine 8 by means of rivet connection. After the working liquid delivered by the blades of the pump wheel 5 enters the blade channel of the first turbine 8, under the action of the centrifugal rotation of the liquid, the first turbine 8 is driven to perform corresponding rotational motion, and then the first turbine output shaft 10 is driven to rotate through the turbine cover 9, and further the first output shaft gear 11 is driven to rotate, and the transmission is transmitted to the first end gear 7.1 of the overrunning clutch 7.

[0031] In any of the above schemes, it is preferred that the dual-turbine group also includes a second turbine 12 and a second turbine output shaft 13, the second turbine 12 is coaxially arranged in the space surrounded by the first turbine 8, the turbine cover 9 and the guide wheel 6, the second turbine output shaft 13 is hollow along its axial direction, the middle section of the second turbine output shaft 13 is movably inserted in the middle space of the guide wheel seat 4 along the axial direction, the middle section of the first turbine output shaft 10 is movably inserted in the middle space of the second turbine output shaft 13 along the axial direction, the second turbine 12 is coaxially fixedly sleeved on the circumferential outer wall of the left end of the second turbine output shaft 13, a second output shaft gear 14 is coaxially provided on the left side of the first output shaft gear 11, the second output shaft gear 14 is coaxially fixedly sleeved on the circumferential outer wall of the right end of the second turbine output shaft 13, and the second output shaft gear 14 is meshed and connected with the second end gear 7.2 at the corresponding position of the overrunning clutch 7.

[0032] The second turbine output shaft 13 is a sleeve structure, and the circumferential side wall in the middle thereof is movably inserted into the annular gap between the first turbine output shaft 10 and the guide wheel seat 4, so that the second turbine output shaft 13 is movably inserted into the middle space of the guide wheel seat 4, and the second turbine output shaft 13 is movably sleeved on the periphery of the first turbine output shaft 10. Its left end extends to the space surrounded by the first turbine 8, the turbine cover 9 and the guide wheel 6, and the second turbine 12 is coaxially fixedly assembled at its left end by spline connection.

[0033] The working fluid flowing out through the blade channel of the first turbine 8 then enters the blade channel of the second turbine 12, thereby continuing to drive the second turbine 12 to rotate, further driving the second turbine output shaft 13 to rotate, and finally transmitted to the second end gear 7.2 of the overrunning clutch 7 through the second output shaft gear 14.

[0034] In any of the above schemes, it is preferred that there is a gap between the circumferential inner wall of the guide wheel seat 4 and the circumferential outer wall of the second turbine output shaft 13 for the working fluid to flow.

[0035] A portion of the working fluid flowing out through the blade channel of the second turbine 12 flows out of the guide wheel seat 4 through the gap between the inner wall of the guide wheel seat 4 and the outer wall of the second turbine output shaft 13, enters the cooling circulation system, and finally flows back into the working fluid pool.

[0036] In any of the above schemes, preferably, the circulation circle diameter of the torque converter is 347 mm, the zero-speed torque coefficient is 3.98, and the nominal torque is approximately 211 N·m.

[0037] In any of the above solutions, preferably, the transmission ratio between the first output shaft gear 11 and the first end gear 7.1 is 2.6:1.

[0038] In any of the above solutions, it is preferred that the transmission ratio between the second output shaft gear 14 and the second end gear 7.2 is 1:0.8.

[0039] In any of the above solutions, it is preferred that the number of teeth of the first output shaft gear 11 is 52, and the number of teeth of the first end gear 7.1 is 20.

[0040] In any of the above solutions, it is preferred that the number of teeth of the second output shaft gear 14 is 32, and the number of teeth of the second end gear 7.2 is 40.

[0041] The circulating circle diameter of the torque converter is 347mm, its zero-speed torque coefficient is 3.98, and the nominal torque is about 211N·m. The number of teeth of the first output shaft gear 11 is 52, the number of teeth of the first end gear 7.1 is 20, the number of teeth of the second output shaft gear 14 is 32, and the number of teeth of the second end gear 7.2 is 40. Through the above design parameters, the torque converter can be better adapted to the 5-ton loader, and after matching it with the 1800rpm (170KW) engine, it can not only meet the traction and power requirements of the loader, but also ensure that the loader has good fuel economy.

[0042] Specific working principle:

[0043] Under the action of the power machine, the cover wheel shaft 2 drives the cover wheel 3 to rotate in the torque converter housing 1, and then drives the pump wheel 5 to rotate under the support of the guide wheel seat 4. Through the rotation of the pump wheel 5 blades, the working fluid is thrown out from the blade channel of the pump wheel 5, and then flows into the blade channel of the first turbine 8. Driven by the impact of the rotating working fluid, the first turbine 8 drives the turbine cover 9 to rotate around its axial direction, and at the same time drives the first turbine output shaft 10 and the first output shaft gear 11 to rotate. After that, the working fluid flows out of the blade channel of the first turbine 8 and then enters the blade channel of the second turbine 12, and drives the second turbine 12 to rotate around its axial direction, and then drives the second turbine output shaft 13 and the second output shaft gear 14 to rotate. After that, the working fluid flows out of the blade channel of the second turbine 12 and then enters the blade channel of the guide wheel 6. Under the torque-increasing action of the guide wheel 6, it returns to the blade channel of the pump wheel 5 to carry out the next working cycle.

[0044] Under the meshing action of the first output shaft gear 11 and the first end gear 7.1, and the meshing action of the second output shaft gear 14 and the second end gear 7.2, the output shaft of the overrunning clutch 7 is driven to rotate accordingly, thereby driving the input end of the gearbox to perform a corresponding rotation action.

[0045] The above shows and describes the basic principle, main features and advantages of the utility model. Those skilled in the art should understand that the utility model is not limited by the above embodiments, and the above embodiments and descriptions are only for explaining the principle of the utility model. Without departing from the spirit and scope of the utility model, the utility model may have various changes and improvements, and these changes and improvements fall within the scope of the utility model to be protected.

[0046] The matters not described in detail in the present invention are all known technologies to those skilled in the art.

Claims

1. A large-capacity torque converter matching a low-speed engine, characterized by: The invention comprises a torque converter housing (1), a cover wheel (3) is coaxially arranged in an inner cavity on the left side of the torque converter housing (1), a cover wheel shaft (2) is integrally formed on the left side of the cover wheel (3) along its axial direction, the left end of the cover wheel shaft (2) extends to the left side of the torque converter housing (1), a guide wheel seat (4) is coaxially arranged on the right side of the cover wheel (3), the guide wheel seat (4) is hollow along its axial direction, the right end of the guide wheel seat (4) is fixedly connected to the torque converter housing (1), and a guide wheel seat (4) is coaxially arranged on the circumferential outer wall of the middle section of the guide wheel seat (4). The shaft movable sleeve is provided with a pump wheel (5), the circumferential connection part of the left end of the pump wheel (5) is fixedly connected to the circumferential connection part of the right end of the cover wheel (3), and a guide wheel (6) is coaxially fixedly sleeved on the circumferential outer wall of the left end of the guide wheel seat (4). It also includes a twin turbine group, the left end of the twin turbine group is arranged in the space between the cover wheel (3) and the guide wheel (6), the middle section of the twin turbine group passes through the middle space of the guide wheel seat (4) and extends to the right side thereof, and one side of the right end of the twin turbine group is cooperatively connected with an overrunning clutch (7).

2. A large-capacity torque converter matching a low-speed engine according to claim 1, characterized in that: The twin turbine group comprises a first turbine (8), a turbine cover (9) and a first turbine output shaft (10); the turbine cover (9) is coaxially arranged in the space between the cover wheel (3) and the guide wheel (6); the circumferential connection portion at the right end of the turbine cover (9) is coaxially fixedly connected to the circumferential connection portion at the left end of the first turbine (8); the left end of the turbine cover (9) is coaxially fixedly sleeved on the circumferential outer wall of the left end of the first turbine output shaft (10); the middle section of the first turbine output shaft (10) is movably inserted into the middle space of the guide wheel seat (4) along the axial direction; a first output shaft gear (11) is coaxially fixedly sleeved on the circumferential outer wall of the right end of the first turbine output shaft (10); the first output shaft gear (11) is meshingly connected with the first end gear (7.1) at the corresponding position of the overrunning clutch (7).

3. A large-capacity torque converter matching a low-speed engine according to claim 2, characterized in that: The twin turbine group further comprises a second turbine (12) and a second turbine output shaft (13); the second turbine (12) is coaxially arranged in a space surrounded by the first turbine (8), the turbine cover (9) and the guide wheel (6); the second turbine output shaft (13) is hollowly arranged along its axial direction; the middle section of the second turbine output shaft (13) is movably inserted into the middle space of the guide wheel seat (4) along the axial direction; the middle section of the first turbine output shaft (10) is movably inserted into the middle space of the second turbine output shaft (13) along the axial direction; the second turbine (12) is coaxially fixedly sleeved on the circumferential outer wall of the left end of the second turbine output shaft (13); a second output shaft gear (14) is coaxially arranged on the left side of the first output shaft gear (11); the second output shaft gear (14) is coaxially fixedly sleeved on the circumferential outer wall of the right end of the second turbine output shaft (13); the second output shaft gear (14) is meshingly connected with the second end gear (7.2) at the corresponding position of the overrunning clutch (7).

4. A large-capacity torque converter matching a low-speed engine according to claim 3, characterized in that: There is a gap between the circumferential inner wall of the guide wheel seat (4) and the circumferential outer wall of the second turbine output shaft (13) for the working fluid to flow.

5. The large-capacity torque converter matching a low-speed engine according to claim 4, characterized in that: The torque converter has a circulating circle diameter of 347 mm, a zero-speed torque coefficient of 3.98, and a nominal torque of approximately 211 N·m.

6. A large-capacity torque converter matching a low-speed engine according to claim 5, characterized in that: The transmission ratio between the first output shaft gear (11) and the first end gear (7.1) is 2.6:

1.

7. A large-capacity torque converter matching a low-speed engine according to claim 6, characterized in that: The transmission ratio between the second output shaft gear (14) and the second end gear (7.2) is 1:0.

8.

8. The large-capacity torque converter matching a low-speed engine according to claim 7, characterized in that: The number of teeth of the first output shaft gear (11) is 52, and the number of teeth of the first end gear (7.1) is 20.

9. The large-capacity torque converter matching a low-speed engine according to claim 8, characterized in that: The number of teeth of the second output shaft gear (14) is 32, and the number of teeth of the second end gear (7.2) is 40.

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