CN114877046A - A multi-mode hydraulic transmission device - Google Patents

Abstract

The invention discloses a multi-mode machine-hydraulic transmission device, which comprises an input shaft, a hydraulic transmission assembly, an input end of the hydraulic transmission assembly is connected with the input shaft; a front planetary wheel assembly, the input end of the front planetary wheel is connected with the input shaft; The planetary wheel assembly, the rear planetary wheel assembly, the front planetary wheel assembly, the middle planetary wheel assembly and the rear planetary wheel assembly are connected in series through the intermediate shaft, and the output end of the rear planetary wheel assembly is connected with an output shaft; the hydraulic transmission assembly, the output of the hydraulic transmission assembly The end energy is connected with the input end of the middle planetary gear assembly; the double annular transmission assembly, the input end of the double annular transmission assembly is connected with the input shaft, and the double annular transmission assembly, the front planetary gear assembly and the hydraulic transmission assembly are connected in parallel with each other; The working state of the transmission assembly and the double-ring transmission assembly realizes power transmission of various working modes and has a wider application range.

Description

A multi-mode hydraulic transmission device

technical field

The invention relates to the technical field of power transmission, in particular to a multi-mode hydraulic transmission device.

Background technique

There are many ways to realize power transmission, such as hydraulic transmission, ring transmission and gear transmission, etc. A single hydraulic transmission, although the transmission power is large, but the efficiency is low; although the ring transmission can achieve stepless transmission, the transmission ratio range Limited; although gear transmission is more efficient, it is difficult to achieve infinitely variable speed. In the prior art, the power transmission is realized by means of a single power transmission, which cannot adapt to various complex working conditions and has a narrow scope of application.

SUMMARY OF THE INVENTION

The purpose of this section is to outline some aspects of embodiments of the invention and to briefly introduce some preferred embodiments. Some simplifications or omissions may be made in this section and the abstract and title of the application to avoid obscuring the purpose of this section, abstract and title, and such simplifications or omissions may not be used to limit the scope of the invention.

The present invention has been made in view of the above-mentioned and/or existing problems in power transmission.

Therefore, the purpose of the present invention is to provide a multi-mode machine-hydraulic transmission device, which realizes power transmission in multiple working modes by selecting the working states of the hydraulic transmission assembly and the double-ring transmission assembly, and has a wider application range.

In order to solve the above-mentioned technical problems, the present invention provides the following technical solutions: a multi-mode machine-hydraulic transmission device, which includes,

Input shaft,

a hydraulic transmission assembly, the input end of the hydraulic transmission assembly is connected with the input shaft;

a front planetary gear assembly, the input end of the front planetary gear is connected with the input shaft;

middle planetary gear assembly,

a rear planetary wheel assembly, the front planetary wheel assembly, the middle planetary wheel assembly and the rear planetary wheel assembly are connected in series through an intermediate shaft, and the output end of the rear planetary wheel assembly is connected with an output shaft;

a hydraulic transmission assembly, the output end of the hydraulic transmission assembly can be connected with the input end of the middle planetary gear assembly;

The double annular transmission assembly, the input end of the double annular transmission assembly is connected with the input shaft, the double annular transmission assembly, the front planetary wheel assembly and the hydraulic transmission assembly are connected in parallel with each other.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the front planetary gear assembly includes a front planet carrier, a front sun gear and a front ring gear connected to the input shaft, and the middle planetary gear assembly includes A middle sun gear, a middle ring gear connected with the front sun gear, and a middle planet carrier connected with the front planet carrier, the rear planetary gear assembly includes a rear ring gear that can be connected with the middle sun gear, and a middle sun gear. The rear planet carrier and the rear sun gear connected to the intermediate shaft, the front planet carrier and the middle planet carrier are both connected with the intermediate shaft.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the front planetary gear assembly further includes a front brake, and the front brake is used to selectively fix the front sun gear.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the middle planetary gear assembly further includes a middle brake, and the middle brake is used to selectively fix the middle sun gear.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the hydraulic transmission assembly includes a hydraulic transmission input shaft, the hydraulic transmission input shaft is connected with a hydraulic transmission input gear pair, and the hydraulic transmission input The output end of the gear pair is controllably connected with a variable pump, the variable pump is used to drive a quantitative motor, the output end of the quantitative motor is connected with a hydraulic transmission output shaft, and the hydraulic transmission output shaft is connected with a hydraulic transmission first output gear The first output gear pair of the hydraulic transmission can be connected with the front planet carrier.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the output end of the fixed motor is also connected with a second output gear pair of hydraulic transmission, and the second output gear pair of hydraulic transmission can be connected to the front sun. wheel connection.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the double annular transmission assembly includes a double annular transmission input shaft, and the double annular transmission input shaft is connected with a front annular transmission mechanism and energy and hydraulic pressure. The double annular transmission input gear pair is connected with the transmission gear pair, the output end of the front annular transmission mechanism is connected with the rear annular transmission mechanism, the output end of the rear annular transmission mechanism is connected with the double annular transmission output shaft, and the double annular transmission mechanism is connected with the output end of the double annular transmission mechanism. The output shaft is connected with a double annular transmission output gear pair, and the double annular transmission output gear pair can be connected with the middle sun gear.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the hydraulic transmission assembly further includes a first clutch, a second clutch and a third clutch, and the first clutch is used to selectively connect the input the shaft is connected for common rotation to the hydrotransmission input shaft, the second clutch is used to selectively connect the hydrotransmission output shaft to the front planet carrier for common rotation, the third clutch is used to selectively connect the hydrotransmission output shaft Connected to the front sun gear for common rotation.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the double annular transmission assembly further includes a fourth clutch and a fifth clutch, and the fourth clutch is used to selectively input the dual annular transmission The shaft is connected for common rotation with the input shaft, and the fifth clutch is used to selectively connect the dual annular output shaft to the middle sun gear for common rotation.

As a preferred solution of the multi-mode hydraulic transmission device of the present invention, wherein: the middle planetary gear assembly further includes a sixth clutch, and the sixth clutch is used for selectively connecting the middle ring gear to the middle sun gear For common rotation, the rear planetary gear assembly further includes a seventh clutch, an eighth clutch, a ninth clutch and a tenth clutch for selectively connecting the middle sun gear to the rear ring gear for common rotation , the eighth clutch is used to selectively connect the middle sun gear to the rear planet carrier for common rotation, the ninth clutch is used to selectively connect the rear ring gear to the output shaft for common rotation, and the tenth clutch is used to selectively connect the rear ring gear to the output shaft for common rotation. A clutch is used to selectively connect the rear carrier to the output shaft for common rotation.

The beneficial effects of the present invention: the present invention adopts four hydraulic transmission modes, which can meet the requirements of forward and reverse speed regulation; the double ring transmission mode expands the speed regulation range and can provide stepless speed regulation in the forward direction of the output end; the gear mode can meet the requirements of forward speed regulation and reverse gear; multi-gear not only expands the degree of freedom of speed regulation, but also has a strong fault-tolerant function; it has 4 gear hydraulic transmission modes to meet the requirements of high-power, high-efficiency stepless speed regulation of various speed regulation ranges and precisions ;Have 2 double-ring hydraulic transmission modes to meet the high-precision stepless speed regulation requirements of various speed regulation ranges and powers.

Description of drawings

In order to illustrate the technical solutions of the embodiments of the present invention more clearly, the following briefly introduces the accompanying drawings used in the description of the embodiments. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can also be obtained based on these drawings without any creative effort. in:

FIG. 1 is a schematic structural diagram of the present invention.

FIG. 2 is a schematic diagram of the power flow of the F(H1) gear of the present invention.

FIG. 3 is a schematic diagram of the power flow of the F(H2) gear according to the present invention.

FIG. 4 is a schematic diagram of the power flow of the F(H3) gear according to the present invention.

FIG. 5 is a schematic diagram of the power flow of the F(H4) gear of the present invention.

FIG. 6 is a schematic diagram of the power flow of the F(C) gear according to the present invention.

FIG. 7 is a schematic diagram of the power flow of the F(M1) gear according to the present invention.

FIG. 8 is a schematic diagram of the power flow of the F(M2) gear according to the present invention.

FIG. 9 is a schematic diagram of the power flow of the F(HM1) gear according to the present invention.

FIG. 10 is a schematic diagram of the power flow of the F(HM2) gear of the present invention.

FIG. 11 is a schematic diagram of the power flow of the F(HM3) gear of the present invention.

FIG. 12 is a schematic diagram of the power flow of the F(HM4) gear according to the present invention.

FIG. 13 is a schematic diagram of the power flow of the F(CH1) gear according to the present invention.

FIG. 14 is a schematic diagram of the power flow of the F(CH2) gear according to the present invention.

Among them, 100 input shaft, 200 front planetary gear assembly, 201 front sun gear, 202 front planet carrier, 203 front ring gear, 204 front brake, 300 hydraulic transmission assembly, 301 hydraulic transmission input gear pair, 302 hydraulic transmission input shaft, 303 The first clutch, 304 variable pump, 305 fixed motor, 306 first hydraulic transmission output gear pair, 307 second clutch, 308 third clutch, 309 hydraulic transmission output shaft, 310 second hydraulic transmission output gear pair, 400 medium planetary gear Assembly, 401 middle ring gear, 402 middle planet carrier, 403 middle sun gear, 404 middle brake, 405 sixth clutch, 500 rear planetary gear assembly, 501 rear ring gear, 502 seventh clutch, 503 ninth clutch, 504 eighth Clutch, 505 tenth clutch, 506 rear planet carrier, 507 rear sun gear, 600 intermediate shaft, 700 output shaft, 800 double annular transmission assembly, 801 fourth clutch, 802 double annular transmission input shaft, 803 front annular transmission mechanism, 804 Rear ring transmission mechanism, 805 dual ring transmission output shaft, 806 fifth clutch, 807 dual ring transmission output gear pair, 808 dual ring transmission input gear pair.

Detailed ways

In order to make the above objects, features and advantages of the present invention more clearly understood, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

Many specific details are set forth in the following description to facilitate a full understanding of the present invention, but the present invention can also be implemented in other ways different from those described herein, and those skilled in the art can do so without departing from the connotation of the present invention. Similar promotion, therefore, the present invention is not limited by the specific embodiments disclosed below.

Second, reference herein to "one embodiment" or "an embodiment" refers to a particular feature, structure, or characteristic that may be included in at least one implementation of the present invention. The appearances of "in one embodiment" in various places in this specification are not all referring to the same embodiment, nor are they separate or selectively mutually exclusive from other embodiments.

Example 1

Referring to FIGS. 1 to 14 , this embodiment provides a multi-mode machine-hydraulic transmission device, which realizes power in multiple working modes by selecting the working states of the hydraulic transmission assembly 300 , the planetary gear assembly 500 and the double annular transmission assembly 800 . Transmission, the scope of application is wider.

A multi-mode hydraulic transmission device includes an input shaft 100, a middle planetary gear assembly 400, a rear planetary gear assembly 500, a hydraulic transmission assembly 300 and a double annular transmission assembly 800. The input shaft 100 is connected to the input end of the hydraulic transmission assembly 300, the front The input end of the planetary gear assembly 200 and the input end of the double annular transmission assembly 800, the front planetary gear assembly 200, the middle planetary gear assembly 400 and the rear planetary gear assembly 500 are connected in series through the intermediate shaft 600, and the output end of the rear planetary gear assembly 500 is connected There is an output shaft 700; the output end of the hydraulic transmission assembly 300 can be connected with the input end of the middle planetary gear assembly 400; the input end of the double annular transmission assembly 800 is connected with the input shaft 100, the double annular transmission assembly 800, the front planetary gear assembly 200 and The hydraulic transmission assemblies 300 are connected in parallel with each other.

Further, the front planetary gear assembly 200 includes a front brake 204, a front planet carrier 202, a front sun gear 201, and a front ring gear 203 connected to the input shaft 100. The front brake 204 is used to selectively fix the front sun gear 201, and the middle The planetary gear assembly 400 includes a middle brake 404, a middle sun gear 403, a middle ring gear 401 connected to the front sun gear 201, and a middle planet carrier 402 that can be connected to the front planet carrier 202. The middle brake 404 is used for selectively driving the middle sun gear. The wheel 403 is fixed, and the rear planetary gear assembly 500 includes a rear ring gear 501 that can be connected to the middle sun gear 403, a rear planet carrier 506 that can be connected to the middle sun gear 403, and a rear sun gear 507 that is connected to the intermediate shaft 600. Both the carrier 202 and the middle planet carrier 402 are connected to the intermediate shaft 600 .

Further, the hydraulic transmission assembly 300 includes a hydraulic transmission input shaft 302, a first clutch 303, a second clutch 307 and a third clutch 308. The hydraulic transmission input shaft 302 is connected with a hydraulic transmission input gear pair 301, and the hydraulic transmission input gear pair 301 The output end of the variable pump 304 is controllably connected to the variable pump 304, and the displacement ratio of the hydraulic transmission mechanism assembly is adjusted by adjusting the displacement of the variable pump 304. The variable pump 304 is used to drive the quantitative motor 305, and the output end of the quantitative motor 305 is connected with a hydraulic transmission. The output shaft 309, the hydraulic transmission output shaft 309 is connected with a first output gear pair of hydraulic transmission and a second output gear pair of hydraulic transmission, the first output gear pair of hydraulic transmission can be connected with the front planet carrier 202, and the second output gear pair of hydraulic transmission is connected Can be connected to the front sun gear 201, the first clutch 303 is used to selectively connect the input shaft 100 to the hydraulic transmission input shaft 302 for common rotation, and the second clutch 307 is used to selectively connect the hydraulic transmission output shaft 309 to the front The planet carrier 202 is for common rotation, and a third clutch 308 is used to selectively connect the hydrotransmission output shaft 309 to the front sun gear 201 for common rotation.

Further, the double annular transmission assembly 800 includes a double annular transmission input shaft 802, a fourth clutch 801 and a fifth clutch 806. The double annular transmission input shaft 802 is connected with a front annular transmission mechanism 803 and a double annular transmission gear pair that can be connected to the hydraulic transmission gear pair. The output end of the front annular transmission mechanism 803 is connected with a rear annular transmission mechanism 804, the output end of the rear annular transmission mechanism 804 is connected with a double annular transmission output shaft 805, and the double annular transmission output shaft 805 is connected with a double annular transmission mechanism. The double annular transmission output gear pair 807 can be connected with the middle sun gear 403, the fourth clutch 801 is used to selectively connect the double annular transmission input shaft 802 to the input shaft 100 for common rotation, and the fifth clutch 806 is used to selectively connect the dual annular output shaft 700 to the middle sun gear 403 for common rotation.

Further, the middle planetary gear assembly 400 further includes a sixth clutch 405 for selectively connecting the middle ring gear 401 to the middle sun gear 403 for common rotation, and the rear planetary gear assembly 500 further includes a seventh clutch 502 , an eighth clutch 504, a ninth clutch 503 and a tenth clutch 505, the seventh clutch 502 is used to selectively connect the middle sun gear 403 to the rear ring gear 501 for common rotation, and the eighth clutch 504 is used to selectively connect The middle sun gear 403 is connected to the rear carrier 506 for common rotation, the ninth clutch 503 is used to selectively connect the rear ring gear 501 to the output shaft 700 for common rotation, and the tenth clutch 505 is used to selectively connect the rear carrier 506 is connected to output shaft 700 for common rotation.

Engage the first clutch 303, the second clutch 307, the seventh clutch 502, the tenth clutch 505 and the middle brake 404 to realize the first hydraulic transmission between the input shaft 100 and the output shaft 700; engage the first clutch 303, the second The clutch 307, the eighth clutch 504, the ninth clutch 503 and the middle brake 404 realize the second hydraulic transmission between the input shaft 100 and the output shaft 700; engage the first clutch 303, the second clutch 307, the seventh clutch 502, The eighth clutch 504, the ninth clutch 503 and the tenth clutch 505 realize the third hydraulic transmission between the input shaft 100 and the output shaft 700; engage the first clutch 303, the third clutch 308, the sixth clutch 405, and the seventh clutch 502 and the ninth clutch 503 realize the fourth type of hydraulic transmission between the input shaft 100 and the output shaft 700 .

The fourth clutch 801 , the fifth clutch 806 , the seventh clutch 502 , the eighth clutch 504 , the ninth clutch 503 and the tenth clutch 505 are engaged to realize the double annular transmission between the input shaft 100 and the output shaft 700 .

Engage the seventh clutch 502, the tenth clutch 505, the front brake 204 and the middle brake 404 to realize the first gear transmission between the input shaft 100 and the output shaft 700; engage the eighth clutch 504, the ninth clutch 503, the front brake 204 and The middle brake 404 realizes the second gear transmission between the input shaft 100 and the output shaft 700 .

The first clutch 303, the second clutch 307, the sixth clutch 405, the seventh clutch 502 and the ninth clutch 503 are engaged to realize the first gear hydraulic transmission between the input shaft 100 and the output shaft 700; The three clutches 308, the seventh clutch 502 and the ninth clutch 503 realize the second gear hydraulic transmission between the input shaft 100 and the output shaft 700; engage the first clutch 303, the third clutch 308, the seventh clutch 502 and the tenth clutch 505, realize the third gear hydraulic transmission between the input shaft 100 and the output shaft 700; engage the first clutch 303, the third clutch 308, the eighth clutch 504 and the ninth clutch 503, realize the transmission between the input shaft 100 and the output shaft 700; The fourth gear hydraulic transmission.

The fourth clutch 801, the fifth clutch 806, the seventh clutch 502, the tenth clutch 505 and the front brake 204 are engaged to realize the first double annular hydraulic transmission between the input shaft 100 and the output shaft 700; The nine clutches 503 and the front brake 204 realize the second double annular hydraulic transmission between the input shaft 100 and the output shaft 700 .

The present invention realizes various working modes, including 4 hydraulic transmission modes, 1 double annular transmission mode, 2 gear transmission modes, 4 gear hydraulic transmission modes and 2 double annular hydraulic transmission modes. Meet the forward and reverse speed regulation requirements; the double ring transmission mode expands the speed regulation range and can provide stepless speed regulation in the forward direction of the output end; the gear transmission mode can meet the requirements of forward and reverse gears; multi-speed not only expands the freedom of speed regulation It also has a strong fault-tolerant function; 4 gear hydraulic transmission modes meet the requirements of high-power, high-efficiency stepless speed regulation of various speed regulation ranges and precisions; 2 double-ring hydraulic transmission modes meet various speed regulation ranges and High-precision stepless speed regulation requirements for power.

Example 2

2 to 14 , this embodiment provides a multi-mode machine-hydraulic transmission device. The difference between this embodiment and Embodiment 1 is that it can calculate the rotational speed of the output shaft 700 in each transmission mode.

A multi-mode machine-hydraulic transmission device, which has a hydraulic transmission mode, a double annular transmission mode, a gear transmission mode, a gear hydraulic transmission mode and a dual annular hydraulic transmission mode. Show.

Table 1. Expression of switching element states and speed regulation of each mode of transmission

i1 is the transmission ratio _of the hydraulic transmission input gear pair 301, _i2 is the transmission ratio of the first hydraulic transmission output gear pair 306, _i3 is the transmission ratio of the second hydraulic transmission output gear pair 310, _i4 is the double ring transmission input _The transmission ratio of the gear pair 808, i5 is the transmission ratio of the _double ring transmission output gear pair 807, _k1 is the characteristic parameter of the front planetary gear, k2 is the characteristic parameter of the middle planetary gear, _k3 is the characteristic parameter of the rear planetary gear, and e is The displacement ratio of the hydraulic transmission assembly 300, ne is the input speed of the engine, _{n o is} the output speed of the output shaft 700, i _T = i _T1 i _T2 is the front ring transmission mechanism 803 and the rear ring transmission mechanism 804 connected in series The transmission ratio at the time, i _T1 is the transmission ratio of the front annular transmission mechanism 803, i _T2 is the transmission ratio of the rear annular transmission mechanism 804, "▲" indicates that the shifting element is engaged, "△" indicates that the shifting element is disengaged, C ₁ ~ C ₁₀ represents the first clutch to the tenth clutch, B ₁ represents the middle brake, and B ₂ represents the front brake.

details as follows:

1 Hydraulic transmission mode includes F(H1) file, F(H2) file, F(H3) file and F(H4) file,

F (H1) gear: As shown in FIG. 2, when the first clutch 303, the second clutch 307, the seventh clutch 502, the tenth clutch 505 and the middle brake 404 are engaged, the other clutches and brakes are disengaged, and the hydraulic transmission assembly 300 is in In the working state, the engine power is sequentially transmitted to the hydraulic transmission output shaft 309 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable pump 304, and the quantitative motor 305, and then through the first hydraulic transmission output gear pair 306, the front planet carrier 202, The intermediate shaft 600, the rear sun gear 507 and the rear planet carrier 506 are output from the output shaft 700. At this time, the relationship between the output speed and the input speed is:

F (H2) gear: As shown in FIG. 3, when the first clutch 303, the second clutch 307, the eighth clutch 504, the ninth clutch 503 and the middle brake 404 are engaged, other clutches and brakes are disengaged, and the hydraulic transmission assembly 300 is in operation state, the engine power is sequentially transmitted to the hydraulic transmission output shaft 309 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable pump 304, and the quantitative motor 305, and then sequentially through the first hydraulic transmission output gear pair 306, the front planet carrier 202, the middle The shaft 600, the rear sun gear 507 and the rear ring gear 501 are output from the output shaft 700. At this time, the relationship between the output speed and the input speed is:

F (H3) gear: As shown in FIG. 4, when the first clutch 303, the second clutch 307, the seventh clutch 502, the eighth clutch 504, the ninth clutch 503 and the tenth clutch 505 are engaged, the other clutches and brakes are disengaged, The hydraulic transmission assembly 300 is in the working state, and the engine power is sequentially transmitted to the first hydraulic transmission output gear pair 306 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable pump 304, the quantitative motor 305 and the hydraulic transmission output shaft 309, and then through the hydraulic transmission output gear pair 306 in turn. The front planet carrier 202 , the intermediate shaft 600 and the fixed rear planetary gear assembly 500 are output from the output shaft 700 . At this time, the relationship between the output speed and the input speed is:

F (H4) gear: As shown in FIG. 5, when the first clutch 303, the third clutch 308, the sixth clutch 405, the seventh clutch 502 and the ninth clutch 503 are engaged, other clutches and brakes are disengaged, and the hydraulic transmission assembly 300 is in In the working state, the engine power is sequentially transmitted to the second hydraulic transmission output gear pair 310 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable pump 304, the quantitative motor 305 and the hydraulic transmission output shaft 309, and then through the middle gear ring 401, The middle sun gear 403 and the rear ring gear 501 are output from the output shaft 700. At this time, the relationship between the output speed and the input speed is:

2 Double ring transmission mode, which has F(C) gear, as shown in FIG. 6, when the fourth clutch 801, the fifth clutch 806, the seventh clutch 502, the eighth clutch 504, the ninth clutch 503 and the tenth clutch are engaged 505, other clutches and brakes are disengaged, the engine power is transmitted to the double ring transmission assembly 800 through the input shaft 100, and then output from the output shaft 700 through the rear ring gear 501. At this time, the relationship between the output speed and the input speed is,

3 gear transmission modes, including F (M1) gear and F (M2) gear;

F (M1) gear: As shown in FIG. 7 , the seventh clutch 502 , the tenth clutch 505 , the front brake 204 and the middle brake 404 are engaged, the other clutches and brakes are disengaged, and the engine power is sequentially transmitted to the front ring gear 203 through the input shaft 100 and the front planet carrier 202, and then output from the output shaft 700 through the intermediate shaft 600, the rear sun gear 507 and the rear planet carrier 506 in turn. At this time, the relationship between the output speed and the input speed is:

F (M2) gear: As shown in FIG. 8, the eighth clutch 504, ninth clutch 503, front brake 204 and middle brake 404 are engaged, other clutches and brakes are disengaged, and the engine power is transmitted to the front ring gear 203 and the front gear through the input shaft 100. The front planet carrier 202 is then output from the output shaft 700 through the intermediate shaft 600, the rear sun gear 507 and the rear ring gear 501 in sequence. At this time, the relationship between the output speed and the input speed is:

4-gear hydraulic transmission mode, including F(HM1), F(HM2), F(HM3) and F(HM4);

F (HM1) gear: As shown in FIG. 9 , the first clutch 303 , the second clutch 307 , the sixth clutch 405 , the seventh clutch 502 and the ninth clutch 503 are engaged, the other clutches and brakes are disengaged, and the engine power passes through the input shaft 100 Divided, one way is transmitted to the front planet carrier 202 through the hydraulic transmission assembly 300, and the other way is directly transmitted to the front gear ring 203. The power after the confluence is output from the output shaft 700 through the front sun gear 201, the middle ring gear 401 and the rear gear 501. , at this time, the relationship between the output speed and the input speed is,

F (HM2) gear: As shown in FIG. 10, the first clutch 303, the third clutch 308, the seventh clutch 502 and the ninth clutch 503 are engaged, the other clutches and brakes are disengaged, the engine power is split through the input shaft 100, and all the way is directly transmitted To the front ring gear 203 , one branch is again divided at the output end of the hydraulic transmission assembly 300 , and the other branch is transmitted to the front sun gear 201 and the power transmitted to the front ring gear 203 after confluence, and then transmitted to the middle planet carrier through the front planet carrier 202 402, the other branch is directly transmitted to the middle ring gear 401, and is confluent with the power transmitted to the middle planet carrier 402, and then passes through the middle sun gear 403 and the rear gear 501 in turn, and is output from the output shaft 700. At this time, the output speed and The relationship between the input speeds is,

F (HM3) gear: As shown in FIG. 11, the first clutch 303, the third clutch 308, the seventh clutch 502 and the tenth clutch 505 are engaged, the other clutches and brakes are disengaged, the hydraulic transmission assembly 300 is in a working state, and the engine power is The input shaft 100 is divided, one way is directly transmitted to the front gear ring 203, the other way is divided again at the output end of the hydraulic transmission assembly 300, and the other way is transmitted to the front sun gear 201 and the power transmitted to the front gear ring 203. The planet carrier 202 is transmitted to the middle planet carrier 402 and the rear sun gear 507, and a branch is directly transmitted to the middle ring gear 401, and is confluent with the power transmitted to the middle planet carrier 402, and then transmitted to the rear ring gear 501 through the middle sun gear 403, With the aforementioned power transmitted to the rear sun gear 507, after the rear planet carrier 506 converges, it is output from the output shaft 700. At this time, the relationship between the output rotational speed and the input rotational speed is:

F (HM4) gear: As shown in FIG. 12, the first clutch 303, the third clutch 308, the eighth clutch 504 and the ninth clutch 503 are engaged, the other clutches and brakes are disengaged, the hydraulic transmission assembly 300 is in a working state, and the engine power is The input shaft 100 is divided, one way is directly transmitted to the front gear ring 203, the other way is divided again at the output end of the hydraulic transmission mechanism, and the other way is transmitted to the front sun gear 201 and the power transmitted to the front gear ring 203. 202 is transmitted to the middle planet carrier 402 and the rear sun gear 507, and a branch is directly transmitted to the middle ring gear 401, where it merges with the power transmitted to the middle planet carrier 402 and is then transmitted to the rear planet carrier 506 through the middle sun gear 403. The power transmitted to the rear sun gear 507 is output from the output shaft 700 after the rear ring gear 501 converges. At this time, the relationship between the output speed and the input speed is:

4 gear hydraulic transmission mode, including F (CH1) gear and F (CH2) gear;

F (CH1) gear: as shown in FIG. 13 , engage the fourth clutch 801 , the fifth clutch 806 , the seventh clutch 502 , the tenth clutch 505 and the front brake 204 , the other clutches and brakes are disengaged, and the double ring transmission assembly 800 is in operation state, the engine power is split through the input shaft 100, one way is transmitted to the rear sun gear 507 through the front ring gear 203, the front planet carrier 202 and the intermediate shaft 600, and the other way is transmitted to the rear ring gear 501 through the double annular transmission mechanism. The output is output from the output shaft 700 through the rear planet carrier 506. At this time, the relationship between the output rotational speed and the input rotational speed is:

F (CH2) gear: As shown in Figure 14, the eighth clutch 504, the ninth clutch 503 and the front brake 204 are engaged, the other clutches and brakes are disengaged, the double annular transmission assembly 800 is in the working state, and the engine power is split through the input shaft 100, One way is transmitted to the rear sun gear 507 through the front ring gear 203, the front planet carrier 202 and the intermediate shaft 600, and the other way is transmitted to the rear planet carrier 506 through the double annular transmission mechanism. output, at this time, the relationship between the output speed and the input speed is,

It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be Modifications or equivalent substitutions without departing from the spirit and scope of the technical solutions of the present invention should be included in the scope of the claims of the present invention.

Claims (10)

1. A multi-mode machine-hydraulic transmission device, characterized in that: it comprises, input_shaft(100); a hydraulic transmission assembly (300), the input end of the hydraulic transmission assembly (300) is connected with the input shaft (100); a front planetary gear assembly (200), the input end of the front planetary gear is connected to the input shaft (100); Middle planetary gear assembly (400); A rear planetary gear assembly (500), the front planetary gear assembly (200), the middle planetary gear assembly (400) and the rear planetary gear assembly (500) are connected in series via an intermediate shaft (600), the rear planetary gear assembly (500) ) is connected with the output shaft (700); a hydraulic transmission assembly (300), the output end of the hydraulic transmission assembly (300) can be connected with the input end of the middle planetary gear assembly (400); A double annular transmission assembly (800), the input end of the double annular transmission assembly (800) is connected with the input shaft (100), the double annular transmission assembly (800), the front planetary gear assembly (200) and the hydraulic transmission assembly (300) parallel to each other. 2. The multi-mode hydraulic transmission device according to claim 1, wherein the front planetary gear assembly (200) comprises a front planetary carrier (202), a front sun gear (201) and an input shaft (100) A connected front ring gear (203), the middle planetary gear assembly (400) includes a middle sun gear (403), a middle ring gear (401) connected with the front sun gear (201), and a front planet carrier (202) A connected middle planet carrier (402), the rear planetary gear assembly (500) includes a rear ring gear (501) that can be connected to the middle sun gear (403), and a rear planet carrier (501) that can be connected to the middle sun gear (403). 506) and the rear sun gear (507) connected to the intermediate shaft (600), the front planet carrier (202) and the middle planet carrier (402) are both connected to the intermediate shaft (600). 3. The multi-mode hydraulic transmission device according to claim 2, wherein the front planetary gear assembly (200) further comprises a front brake (204), and the front brake (204) is used to selectively The front sun gear (201) is fixed. 4. The multi-mode hydraulic transmission device according to claim 2, characterized in that: the middle planetary gear assembly (400) further comprises a middle brake (404), and the middle brake (404) is used to selectively The middle sun gear (403) is fixed. 5. The multi-mode machine-hydraulic transmission device according to any one of claims 2 to 4, wherein the hydraulic transmission assembly (300) comprises a hydraulic transmission input shaft (302), and the hydraulic transmission input shaft (302) ) is connected with a hydraulic transmission input gear pair (301), the output end of the hydraulic transmission input gear pair (301) is controllably connected with a variable displacement pump (304), and the variable displacement pump (304) is used to drive a fixed motor ( 305), the output end of the quantitative motor (305) is connected with a hydraulic transmission output shaft (309), and the hydraulic transmission output shaft (309) is connected with a hydraulic transmission first output gear pair, the hydraulic transmission first output gear pair Can be connected to the front planet carrier (202). 6. The multi-mode hydraulic transmission device according to claim 5, characterized in that: the hydraulic transmission output shaft (309) is further connected with a hydraulic transmission second output gear pair, and the hydraulic transmission second output gear pair can Connect with the front sun gear (201). 7. The multi-mode hydraulic transmission device according to claim 6, characterized in that: the double annular transmission assembly (800) comprises a double annular transmission input shaft (802), and the double annular transmission input shaft (802) is mounted on the double annular transmission input shaft (802). A front annular transmission mechanism (803) and a double annular transmission input gear pair (808) that can be connected with a hydraulic transmission gear pair are connected, and the output end of the front annular transmission mechanism (803) is connected with a rear annular transmission mechanism (804), The output end of the rear annular transmission mechanism (804) is connected with a double annular transmission output shaft (805), and the double annular transmission output shaft (805) is connected with a double annular transmission output gear pair (807). The transmission output gear pair (807) can be connected with the middle sun gear (403). 8. The multi-mode hydraulic transmission device according to claim 5, wherein the hydraulic transmission assembly (300) further comprises a first clutch (303), a second clutch (307) and a third clutch (308) , the first clutch (303) is used to selectively connect the input shaft (100) to the hydraulic transmission input shaft (302) for common rotation, and the second clutch (307) is used to selectively output the hydraulic transmission A shaft (309) is connected for common rotation to the front planet carrier (202) and the third clutch (308) is used to selectively connect the hydrotransmission output shaft (309) to the front sun gear (201) for common rotation. 9. The multi-mode hydraulic transmission device according to claim 8, wherein the double annular transmission assembly (800) further comprises a fourth clutch (801) and a fifth clutch (806), the fourth clutch (801) for selectively connecting the dual toroidal drive input shaft (802) to the input shaft (100) for common rotation, the fifth clutch (806) for selectively connecting the dual toroidal output shaft (700) to the middle sun gear (403) to rotate together. 10. The multi-mode hydraulic transmission device according to any one of claims 2 to 4, characterized in that: the middle planetary gear assembly (400) further comprises a sixth clutch (405), the sixth clutch (405) ) for selectively connecting the middle ring gear (401) to the middle sun gear (403) for common rotation, the rear planetary gear assembly (500) further includes a seventh clutch (502), an eighth clutch (504), The ninth clutch ( 503 ) and the tenth clutch ( 505 ), the seventh clutch ( 502 ) for selectively connecting the middle sun gear ( 403 ) to the rear ring gear ( 501 ) for common rotation, the eighth clutch ( 502 ) A clutch (504) is used to selectively connect the middle sun gear (403) to the rear planet carrier (506) for common rotation, and the ninth clutch (503) is used to selectively connect the rear ring gear (501) to The output shaft (700) is for common rotation and the tenth clutch (505) is used to selectively connect the rear planet carrier (506) to the output shaft (700) for common rotation.

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