A multi-mode composite transmission device integrating gear - hydraulic - multi-disc

Abstract

The present invention provides a multi-mode composite transmission device integrating a gear-hydraulic-multi-disc, which includes an input component, a hydraulic transmission mechanism, a front planetary gear mechanism, a multi-disc continuously variable transmission mechanism, a rear planetary gear mechanism, an output component, a clutch component and a brake component; the clutch component connects the output end of the input component to the input end of the hydraulic transmission mechanism and the input end of the front planetary gear mechanism respectively; the clutch component connects the output end of the hydraulic transmission mechanism to the front planetary gear mechanism and the rear planetary gear mechanism respectively; the clutch component connects the front planetary gear mechanism, the multi-disc continuously variable transmission mechanism, the rear planetary gear mechanism and the output component in sequence; the clutch component and the brake component provide a continuous transmission ratio between the input component and the output component. The present invention can meet the requirements of multi-condition operations of construction machinery, improve the utilization rate of engine power and improve fuel economy.

Description

Technical Field

[0001] The present invention relates to the field of variable speed transmission devices, and particularly to a multi-mode composite transmission device integrating gears, hydraulics, and multi-discs. Background Art

[0002] During the operation of agricultural machinery, the operating conditions are harsher than those of road vehicles, and situations where the resistance surges frequently occur. Small-power agricultural machinery often has to sacrifice a certain amount of operation efficiency to overcome these extreme situations, along with increased fuel consumption; large-power agricultural machinery has problems such as high cost and large volume, and there is also a problem of power surplus under relatively good operating conditions.

[0003] Currently, the variable speed transmission methods applied to construction machinery generally include single-flow gear transmission, single-flow hydraulic transmission, and hydraulic-gear compound transmission; single-flow gear transmission has high efficiency, but the transmission ratio is fixed, and frequent gear shifting is required during operation; single-flow hydraulic transmission can conveniently achieve stepless speed regulation and has a large transmission torque, but its transmission efficiency is low; hydraulic-gear compound transmission is a transmission method in which a hydraulic power flow and a mechanical power flow are in parallel, combining the high efficiency of gear transmission and the large torque of hydraulic transmission, but it has high requirements for variable hydraulic pumps, fixed-displacement hydraulic motors, and hydraulic systems. Multi-disc stepless variable speed transmission has the characteristics of large transmission power, strong load-bearing capacity, high service life, and high transmission efficiency, and is also mostly used in construction machinery, but its transmission ratio change range is limited.

[0004] The prior art only involves the design of single-flow transmission devices and composite transmission devices in which two single-flows are in parallel, and fails to fully meet the design requirements of multi-mode, especially various composite modes, of transmission devices under different working conditions of construction machinery. Summary of the Invention

[0005] In view of the deficiencies in the prior art, the present invention provides a multi-mode composite transmission device integrating gears, hydraulics, and multi-discs. By switching the clutch assembly and the brake assembly, switching among multiple modes such as hydraulic transmission, gear transmission, multi-disc stepless variable speed transmission, gear-multi-disc composite transmission, hydraulic-gear series composite transmission, hydraulic-gear parallel composite transmission, hydraulic-multi-disc series composite transmission, hydraulic-multi-disc parallel composite transmission, hydraulic-gear-multi-disc series composite transmission, and hydraulic-gear-multi-disc parallel composite transmission is realized.

[0006] The present invention achieves the above technical objectives through the following technical means.

[0007] A multi-mode composite transmission device integrating gear - hydraulic - multi-disc, comprising an input component, a hydraulic transmission mechanism, a front planetary gear mechanism, a multi-disc continuously variable transmission mechanism, a rear planetary gear mechanism, an output component, a clutch component and a brake component; the clutch component connects the output end of the input component to the input ends of the hydraulic transmission mechanism, the front planetary gear mechanism and the multi-disc continuously variable transmission mechanism respectively; the clutch component connects the output end of the hydraulic transmission mechanism to the front planetary gear mechanism, the rear planetary gear mechanism and the multi-disc continuously variable transmission mechanism respectively; the clutch component connects the front planetary gear mechanism to the multi-disc continuously variable transmission mechanism, connects the front planetary gear transmission mechanism to the rear planetary gear mechanism, and connects the rear planetary gear mechanism to the output component; the clutch component and the brake component provide a continuous transmission ratio between the input component and the output component.

[0008] Furthermore, by adjusting the displacement ratio of the hydraulic transmission mechanism, adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism and selectively controlling the engagement of the clutch component and the brake component, a transmission mode of any one or any two combinations or three combinations of hydraulic transmission H, gear transmission G and multi-disc continuously variable transmission S between the input component and the output component is provided.

[0009] Further, the clutch assembly includes a first clutch C1, a second clutch C2, a third clutch C3, a fourth clutch C4, a fifth clutch C5, a sixth clutch C6, a seventh clutch C7, an eighth clutch C8, a ninth clutch C9, and a brake B; the first clutch C1 is used to selectively connect the input assembly to the front planetary gear mechanism and the input end of the multi-disc continuously variable transmission; the second clutch C2 is used to selectively connect the input assembly to the input end of the hydraulic transmission mechanism; the third clutch C3 is used to selectively connect the output end of the hydraulic transmission mechanism to the front planetary gear mechanism or the multi-disc continuously variable transmission mechanism in series or in parallel; the fourth clutch C4 is used to selectively connect the hydraulic transmission mechanism or the input assembly to the input end of the multi-disc continuously variable transmission, and the fifth clutch C5 is used to selectively connect the output end of the hydraulic transmission mechanism or the input assembly to the ring gear of the front planetary gear mechanism to rotate together; the sixth clutch C6 is used to selectively connect the output end of the multi-disc continuously variable transmission to the input end of the front gear mechanism; the seventh clutch C7 is used to selectively connect the sun gear of the front planetary gear mechanism to the planet carrier of the front planetary gear mechanism to rotate together;; the eighth clutch C8 is used to selectively connect the output end of the hydraulic transmission mechanism to the sun gear of the rear planetary gear mechanism to rotate together; the ninth clutch C9 selectively connects the planet carrier of the rear planetary gear mechanism to the ring gear of the rear planetary gear mechanism to rotate together; the brake B is used to selectively connect the sun gear of the front planetary gear mechanism to a fixed member; by adjusting the displacement ratio of the hydraulic transmission mechanism and selectively controlling the engagement of the second clutch C2, the eighth clutch C8, and the ninth clutch C9, a hydraulic transmission H between the input assembly and the output assembly is provided.

[0010] Further, by controlling the engagement of the first clutch C1, the fifth clutch C5, the ninth clutch C9, and the brake B, a gear transmission G between the input assembly and the output assembly is provided.

[0011] Further, by adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism and selectively controlling the engagement of the first clutch C1, the fourth clutch C4, the sixth clutch C6, the seventh clutch C7, and the ninth clutch C9, a multi-disc continuously variable transmission S between the input assembly and the output assembly is provided.

[0012] Further, by adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism and selectively controlling the engagement of the first clutch C1, the fourth clutch C4, the fifth clutch C5, the sixth clutch C6, and the ninth clutch C9, a gear-multi-disc compound transmission GS between the input assembly and the output assembly is provided.

[0013] A hydraulic-gear series compound transmission HG1 between an input component and an output component is provided by adjusting the displacement ratio of a hydraulic transmission mechanism and selectively controlling the engagement of a second clutch C2, a third clutch C3, a fifth clutch C5, a ninth clutch C9, and a brake B.

[0014] A hydraulic-multi-disc series compound transmission HS1 between an input component and an output component is provided by adjusting the displacement ratio of a hydraulic transmission mechanism and selectively controlling the engagement of a second clutch C2, a third clutch C3, a fourth clutch C4, a sixth clutch C6, a seventh clutch C7, and a ninth clutch C9.

[0015] Furthermore, by adjusting the displacement ratio of a hydraulic transmission mechanism, adjusting the transmission ratio of a multi-disc continuously variable transmission mechanism, and selectively controlling the second clutch C2, the third clutch C3, the fourth clutch C 4、 A hydraulic-gear-multi-disc series compound transmission HGS1 between an input component and an output component is provided by adjusting the displacement ratio of a hydraulic transmission mechanism, adjusting the transmission ratio of a multi-disc continuously variable transmission mechanism, and selectively controlling the engagement of a fifth clutch C5, a sixth clutch C6, and a ninth clutch C9.

[0016] Furthermore, a hydraulic-gear parallel compound transmission HG2 between an input component and an output component is provided by adjusting the displacement ratio of a hydraulic transmission mechanism and selectively controlling the engagement of a first clutch C1, a second clutch C2, a fifth clutch C5, an eighth clutch C8, and a brake B;

[0017] A hydraulic-multi-disc parallel compound transmission HS2 between an input component and an output component is provided by adjusting the displacement ratio of a hydraulic transmission mechanism, adjusting the transmission ratio of a multi-disc continuously variable transmission mechanism, and selectively controlling the engagement of a first clutch C1, a second clutch C2, a fourth clutch C4, a sixth clutch C6, a seventh clutch C7, and an eighth clutch C8;

[0018] Furthermore, a hydraulic-gear-multi-disc parallel compound transmission HGS2 between an input component and an output component is provided by adjusting the displacement ratio of a hydraulic transmission mechanism, adjusting the transmission ratio of a multi-disc continuously variable transmission mechanism, and selectively controlling the engagement of a first clutch C1, a second clutch C2, a fourth clutch C4, a fifth clutch C5, a sixth clutch C6, and an eighth clutch C8.

[0019] Furthermore, stepless speed regulation switching between "hydraulic transmission H → multi-disc continuously variable transmission S → hydraulic-multi-disc compound transmission HS" drive modes is provided by adjusting the displacement ratio of a hydraulic transmission mechanism, adjusting the transmission ratio of a multi-disc continuously variable transmission mechanism, and controlling the engagement of a clutch assembly.

[0020] Furthermore, by adjusting the displacement ratio of the hydraulic transmission mechanism, the transmission ratio of the multi-disc continuously variable transmission mechanism, and selectively controlling the engagement of the clutch and brake assembly, stepless speed regulation switching between the transmission modes of "hydraulic transmission H → gear transmission G → hydraulic-gear compound transmission HG → hydraulic-gear-multi-disc compound transmission HGS" is provided.

[0021] Furthermore, by adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism and selectively controlling the engagement of the clutch and brake assembly, stepless speed regulation switching between the transmission modes of "hydraulic transmission H → gear-multi-disc compound transmission GS → hydraulic-gear-multi-disc compound transmission HGS" is provided.

[0022] Furthermore, by adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism and selectively controlling the engagement of the clutch and brake assembly, stepless speed regulation switching between the transmission modes of "hydraulic-gear compound transmission HG → multi-disc continuously variable transmission S → hydraulic multi-disc compound transmission HS" is provided.

[0023] The beneficial effects of the present invention are as follows:

[0024] 1. The multi-mode compound transmission device integrating gear-hydraulic-multi-disc of the present invention realizes the switching of multiple modes such as gear transmission, hydraulic transmission, multi-disc continuously variable transmission, gear-multi-disc compound transmission, hydraulic-gear series compound transmission, hydraulic-gear parallel compound transmission, hydraulic-multi-disc series compound transmission, hydraulic-multi-disc parallel compound transmission, hydraulic-gear-multi-disc series compound transmission, and hydraulic-gear-multi-disc parallel compound transmission by switching the clutch assembly and the brake assembly, which can meet the operation requirements of construction machinery under multiple working conditions, improve the utilization rate of engine power, and improve fuel economy.

[0025] 2. The multi-mode compound transmission device integrating gear-hydraulic-multi-disc of the present invention effectively reduces the shift shock and increases the speed ratio adjustment range; the hydraulic transmission has a fast start, smooth operation, and is easy to realize fast and impact-free speed change and reverse. The transmission ratio change process of the multi-disc continuously variable transmission is continuous, and the impact on the mechanism during use is extremely small.

[0026] 3. The multi-mode compound transmission device integrating gear-hydraulic-multi-disc of the present invention is provided with two transmission modes each for hydraulic-multi-disc series, hydraulic-gear-multi-disc series, hydraulic-multi-disc parallel, and hydraulic-gear-multi-disc parallel. The hydraulic-multi-disc series and hydraulic-gear-multi-disc series transmission modes effectively broaden the speed regulation range and can meet the requirements of large-range non-linear stepless speed regulation. The hydraulic-multi-disc parallel and hydraulic-gear-multi-disc parallel transmission modes improve the system transmission efficiency and can meet the requirements of high-efficiency stepless speed regulation within a region. Description of the Drawings

[0027] Figure 1 This is the structural schematic diagram of the multi-mode composite transmission device integrating gear - hydraulic - multi-disc of the present invention.

[0028] Figure 2 This is the schematic diagram of the power flow of the hydraulic transmission H mode of the present invention.

[0029] Figure 3 This is the schematic diagram of the power flow of the gear transmission G mode of the present invention.

[0030] Figure 4 This is the schematic diagram of the power flow of the multi-disc continuously variable transmission S mode of the present invention.

[0031] Figure 5 This is the schematic diagram of the power flow of the gear - multi-disc composite transmission GS of the present invention.

[0032] Figure 6 This is the schematic diagram of the power flow of the hydraulic - gear series composite transmission HG1 of the present invention.

[0033] Figure 7 This is the schematic diagram of the power flow of the hydraulic - multi-disc series composite transmission HS1 of the present invention.

[0034] Figure 8 This is the schematic diagram of the power flow of the hydraulic - gear - multi-disc series composite transmission HGS1 of the present invention.

[0035] Figure 9 This is the schematic diagram of the power flow of the hydraulic - gear parallel composite transmission HG2 of the present invention.

[0036] Figure 10 This is the schematic diagram of the power flow of the hydraulic - multi-disc parallel composite transmission HS2 of the present invention.

[0037] Figure 11 This is the schematic diagram of the power flow of the hydraulic - gear - multi-disc parallel composite transmission HGS2 of the present invention.

[0038] Figure 12 This is the relationship diagram of the output speed and the input speed during the mode switching process (H1→S→HS) of the present invention.

[0039] Figure 13 This is the relationship diagram of the output speed and the input speed during the mode switching process (H→G→HG or H→HGS) of the present invention.

[0040] Figure 14 This is the relationship diagram of the output speed and the input speed during the mode switching process (H→GS→HGS1) of the present invention.

[0041] Figure 15Output speed vs. input speed relationship diagram for the mode switching process (HG→S→HS1) described in the present invention.

[0042] In the figure:

[0043] 1 - Input component; 1-1 - Engine; 1-2 - Second gear pair; 1-3 - Input shaft; 1-4 - First gear pair; 1-5 - First clutch C1; 1-6 - Engine output shaft; 2 - Hydraulic transmission mechanism; 2-1 - Hydraulic transmission input shaft; 2-2 - Second clutch C2; 2-3 - Variable hydraulic pump; 2-4 - Fixed-displacement hydraulic motor; 2-5 - Hydraulic transmission output shaft; 2-6 - Third clutch C3; 2-7 - Third gear pair; 2-8 - Eighth clutch C8; 3 - Multi-disc continuously variable transmission mechanism; 3-1 - Fourth gear pair; 3-2 - Fifth gear pair; 3-3 - Power input shaft of multi-disc continuously variable transmission mechanism; 3-4 - Fourth clutch C4; 3-5 - Multi-disc continuously variable transmission; 3-6 - Sixth gear pair; 3-7 - Sixth clutch C6; 3-8 - Power output shaft of multi-disc continuously variable transmission mechanism; 3-9 - Brake B; 4 - Front planetary gear mechanism; 4-1 - Seventh gear pair; 4-2 - Fifth clutch C5; 4-3 - Front planetary gear ring gear; 4-4 - Front planetary gear sun gear; 4-5 - Seventh clutch C7; 4-6 - Front planetary gear carrier; 4-7 - Power output shaft of front planetary gear mechanism; 5 - Rear planetary gear mechanism; 5-1 - Ninth clutch C9; 5-2 - Rear planetary gear carrier; 5-3 - Rear planetary gear ring gear; 5-4 - Rear planetary gear sun gear; 5-5 - Eighth gear pair; 6 - Output component. Detailed implementation manners

[0044] The present invention will be further described below in conjunction with the accompanying drawings and specific embodiments, but the protection scope of the present invention is not limited thereto.

[0045] Embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the accompanying drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the accompanying drawings are exemplary and are intended to explain the present invention and should not be construed as limiting the present invention.

[0046] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "axial", "radial", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, the meaning of "a plurality of" is two or more unless otherwise specifically defined.

[0047] In the present invention, unless otherwise clearly specified and defined, the terms "mounted", "connected", "coupled", "fixed", etc. shall be construed in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0048] As Figure 1 shown, the multi-mode composite transmission device integrating gear - hydraulic - multi-disc of the present invention includes an input assembly 1, a hydraulic transmission mechanism 2, a multi-disc continuously variable transmission mechanism 3, a front planetary gear mechanism 4, a rear planetary gear mechanism 5, an output assembly 6, a clutch assembly, and a brake assembly; the clutch assembly connects the output end of the input assembly 1 to the input ends of the hydraulic transmission mechanism 2 and the multi-disc continuously variable transmission mechanism 3 respectively; the clutch assembly connects the output end of the hydraulic transmission mechanism 2 to the multi-disc continuously variable transmission mechanism 3 and the rear planetary gear mechanism 5 respectively; the clutch assembly connects the multi-disc continuously variable transmission mechanism 3 to the front planetary gear mechanism 4, connects the front planetary gear mechanism 4 to the rear planetary gear mechanism 5, and connects the rear planetary gear mechanism 5 to the output assembly 6; the clutch assembly and the brake assembly provide a continuous transmission ratio between the input assembly 1 and the output assembly 6.

[0049] The input component 1 includes 1-1 - engine, 1-2 - second gear pair; 1-3 - engine input shaft, 1-4 - first gear pair, 1-5 - first clutch C1, 1-6 - engine output shaft; the input shaft 1-2 of the engine 1-1 is connected to the input end of the multi-disk continuously variable transmission mechanism 3 through the first gear pair 1-3. The first clutch C1 1-5 is used to selectively connect the input shaft 1-3 to the multi-disk continuously variable transmission mechanism 3. The input shaft 1-3 of the engine 1-1 is connected to the input end of the hydraulic transmission mechanism 2 through the second gear pair 1-2.

[0050] The hydraulic transmission mechanism 2 includes 2-1 - hydraulic transmission input shaft, 2-2 - second clutch C2, 2-3 - variable hydraulic pump, 2-4 - fixed-displacement hydraulic motor, 2-5 - hydraulic transmission output shaft, 2-6 - third clutch C3, 2-7 - third gear pair, 2-8 - eighth clutch C8; the hydraulic transmission input shaft 2-1 is connected to the variable hydraulic pump 2-3, the fixed-displacement hydraulic motor 2-4 is connected to the hydraulic transmission output shaft 2-5, the variable hydraulic pump 2-3 is used to drive the fixed-displacement hydraulic motor 2-4, and the second clutch C2 2-2 is used to selectively connect the input shaft 1-2 to the hydraulic transmission input shaft 2-1; the third clutch C3 2-6 is used to selectively connect the hydraulic transmission output shaft 2-5 to the multi-disk continuously variable transmission mechanism 3 through the third gear pair 2-7; the eighth clutch C8 2-8 is used to selectively connect the hydraulic transmission output shaft 2-5 to the rear planetary gear sun gear 5-4 through the eighth gear pair 5-5 to rotate together.

[0051] The multi-disk continuously variable transmission mechanism 3 includes 3-1 - fourth gear pair, 3-2 - fifth gear pair, 3-3 - multi-disk continuously variable transmission mechanism power input shaft, 3-4 - fourth clutch C4, 3-5 - multi-disk continuously variable transmission, 3-6 - sixth gear pair, 3-7 - sixth clutch C6, 3-8 - multi-disk continuously variable transmission mechanism power output shaft, 3-9 - brake B; the fourth clutch C4 3-4 is used to selectively connect the engine output shaft 1-6 or the hydraulic transmission output shaft 2-5 to the multi-disk continuously variable transmission mechanism power input shaft 3-3 to rotate together; the sixth clutch C6 is used to selectively connect the multi-disk continuously variable transmission mechanism power output shaft 3-8 to the front planetary gear sun gear 4-4 to rotate together; the brake B 3-9 is used to fix the front planetary gear mechanism sun gear.

[0052] The front planetary gear mechanism 4 includes 4-1 - the seventh gear pair; 4-2 - the fifth clutch C5; 4-3 - the front planetary gear ring; 4-4 - the front planetary gear sun gear; 4-5 - the seventh clutch C7; 4-6 - the front planetary gear carrier; 4-7 - the power output shaft of the front planetary gear mechanism;; The front planetary gear ring 4-3, the front planetary gear sun gear 4-4 and the front planetary gear carrier 4-6 form a planetary gear train; The brake B 3-5 is used to selectively fix the front planetary gear sun gear 4-4; The fifth clutch C5 4-5 is used to selectively connect the engine output shaft 1-6 to the front planetary gear ring 4-3 to rotate together; The seventh clutch C7 4-5 connects the front planetary gear sun gear 4-4 to the front planetary gear carrier 4-6 to rotate together, that is, the front planetary gear mechanism 4 is fixedly connected as a whole; The power output shaft 4-7 of the front planetary gear mechanism is connected to the front planetary gear carrier 4-6.

[0053] The rear planetary gear mechanism 5 includes 5-1 - the ninth clutch C9; 5-2 - the rear planetary gear carrier; 5-3 - the rear planetary gear ring; 5-4 - the rear planetary gear sun gear; 5-5 - the eighth gear pair; The 5-2 - rear planetary gear carrier, 5-3 - rear planetary gear ring, 5-4 - rear planetary gear sun gear form a planetary gear train; The ninth clutch C9 5-1 is used to selectively connect the 5-2 - rear planetary gear carrier to the 5-3 - rear planetary gear ring to rotate together, that is, the rear planetary gear mechanism is fixedly connected as a whole; The output assembly 6 is connected to the rear planetary gear carrier 5-2.

[0054] By adjusting the displacement ratio of the hydraulic transmission mechanism 2, adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism 3 and selectively controlling the engagement of the clutch assembly and the brake assembly, provide the switching of multiple modes including gear transmission, hydraulic transmission, multi-disc continuously variable transmission, gear-multi-disc compound transmission, hydraulic-gear series compound transmission, hydraulic-gear parallel compound transmission, hydraulic-multi-disc series compound transmission, hydraulic-multi-disc parallel compound transmission, hydraulic-gear-multi-disc series compound transmission, and hydraulic-gear-multi-disc parallel compound transmission between the input assembly 1 and the output assembly 6. The engaging elements of each transmission mode are shown in Table 1. Specifically as follows:

[0055] Table 1 Engagement status of mode switching elements

[0056]

[0057] Where: ▲ represents that the actuator is in the engaged state, and △ represents that the actuator is in the disengaged state; n o (H) is the output speed of the hydraulic transmission H mode, n o (G) is the output speed of the gear transmission G mode, n o(S) is the output speed of the multi-disc continuously variable transmission in S mode, n o (HG1) is the output speed of the hydraulic-gear series compound transmission in HG1 mode, n o (HS1) is the output speed of the hydraulic-multi-disc series compound transmission in HS1 mode, n o (HGS1) is the output speed of the hydraulic-gear-multi-disc series compound transmission in HGS1 mode, n o (GS) is the output speed of the gear-multi-disc compound transmission in GS mode, n o (HG2) is the output speed of the hydraulic-gear parallel compound transmission in HG2 mode, n o (HS2) is the output speed of the hydraulic-multi-disc parallel compound transmission in HS2 mode, n o (HGS2) is the output speed of the hydraulic-gear-multi-disc compound transmission in HGS2 mode, n I is the engine speed, k1 is the planetary gear characteristic parameter of the front planetary gear mechanism, k2 is the planetary gear characteristic parameter of the rear planetary gear mechanism, e is the displacement ratio of the hydraulic transmission mechanism, i S is the transmission ratio of the multi-disc continuously variable transmission mechanism, i1 is the transmission ratio of the first gear pair 1-4, i2 is the transmission ratio of the second gear pair 1-2, i3 is the transmission ratio of the third gear pair 2-7, i4 is the transmission ratio of the fourth gear pair 3-1, i5 is the transmission ratio of the fifth gear pair 3-2, i6 is the transmission ratio of the sixth gear pair 3-6, i7 is the transmission ratio of the seventh gear pair 4-1, i8 is the transmission ratio of the eighth gear pair 5-5.

[0058] The hydraulic transmission H transmission mode is as Figure 2 shown. Only the second clutch C22-2, the eighth clutch C82-8 and the ninth clutch C9 5-1 are engaged, and other clutches and brakes are disengaged. At this time, the engine power transmitted by the input shaft 1-2 drives the variable hydraulic pump 2-3 to work through the second gear pair 12, and then drives the fixed-displacement hydraulic motor 2-4 to rotate. The power output by the fixed-displacement hydraulic motor 2-4 is then transmitted to the multi-disc continuously variable transmission mechanism 3 through the third gear pair or transmitted to the rear planetary gear sun gear 5-4 through the eighth gear pair 5-5. At this time, the rear planetary gear mechanism 5 is connected as a whole, and the power is output from the output assembly 6.

[0059] The gear transmission G transmission mode is as Figure 3As shown, only the first clutch C11-5, the fifth clutch C5 4-2, the ninth clutch C9 5-1 and the brake B 3-9 are engaged, and other clutch components are disengaged. At this time, the engine power transmitted by the input shaft 1-2 drives the front planetary gear ring 4-3 through the first clutch C1 1-5 and the fifth clutch C5 4-2. Since the front planetary gear sun gear 4-4 is braked by the brake B 3-9, the power is output from the front planetary gear carrier 4-6 to the power output shaft 4-7 of the front planetary gear mechanism. Since the ninth clutch C9 5-1 is engaged, the rear planetary gear mechanism 5 is connected as a whole, and the power is output from the output assembly 6.

[0060] The multi-disc continuously variable transmission S mode is as Figure 4 shown. The first clutch C1 1-5, the fourth clutch C4 3-4, the sixth clutch C6 4-1, the seventh clutch C7 4-5 and the ninth clutch C9 5-1 are engaged, and other clutches and brakes are disengaged. The engine power is transmitted from the input shaft 1-2 to the sun gear 3-1 of the front planetary gear mechanism. At this time, the front planetary gear mechanism 3 is connected as a whole, and the engine power is transmitted to the power input shaft 3-3 of the multi-disc continuously variable transmission mechanism to drive the multi-disc continuously variable transmission 3-5. The multi-disc continuously variable transmission 3-5 changes the center distance a v between the conical disc and the T-shaped disc through the speed control mechanism to change the working radius of the conical disc, thereby realizing speed change. The power output by the multi-disc continuously variable transmission is transmitted from the power output shaft 3-8 of the multi-disc continuously variable transmission mechanism to the sun gear 4-4 of the front planetary gear mechanism. At this time, the front planetary gear mechanism 4 is fixed as a whole, and then transmitted to the rear planetary gear ring 5-3. At this time, the rear planetary gear mechanism 5 is connected as a whole, and the power is output from the output assembly 6.

[0061] The hydraulic-gear series compound transmission HG1 transmission mode is as Figure 5 shown. Only the second clutch C2 2-2, the third clutch C3 2-6, the fifth clutch C5 4-2, the ninth clutch C9 5-1 and the brake B 3-9 are engaged, and other clutches are disengaged. At this time, the engine power transmitted by the input shaft 1-2 is transmitted to the hydraulic transmission input shaft 2-1 through the second gear pair 1-2 to drive the variable hydraulic pump 2-3, and then drives the fixed-displacement hydraulic motor 2-4 to rotate. The power output by the fixed-displacement hydraulic motor 2-4 is transmitted through the hydraulic transmission output shaft 2-5, the third gear pair 2-7 and the fourth gear pair 3-1 to drive the front planetary gear ring 4-3. Since the front planetary gear sun gear 4-4 is braked by the brake B 3-9, the power is output from the front planetary gear carrier 4-6 to the power output shaft 4-7 of the front planetary gear mechanism. Since the ninth clutch C9 5-1 is engaged, the rear planetary gear mechanism 5 is connected as a whole, and the power is output from the output assembly 6.

[0062] The hydraulic-multi-disc series HS1 transmission mode is as Figure 6As shown, only the second clutch C2 2-2, the third clutch C3 3-6, the fourth clutch C4 3-4, the sixth clutch C6 3-7, the seventh clutch C7 4-5, and the ninth clutch C9 5-1 are engaged, and other clutches and brakes are disengaged. At this time, the engine power transmitted by the input shaft 1-2 is transmitted to the hydraulic transmission input shaft 2-1 through the first gear pair 1-4 to drive the variable hydraulic pump 2-3, and then drives the fixed-displacement hydraulic motor 2-4 to rotate. The power output by the fixed-displacement hydraulic motor 2-4 is transmitted to the power input shaft 3-3 of the multi-disc continuously variable transmission mechanism through the hydraulic transmission output shaft 2-5, the third gear pair 2-7, the fourth gear pair 3-1, and the fifth gear pair 3-2, driving the multi-disc continuously variable transmission 3-5. The power output by the multi-disc continuously variable transmission is transmitted to the sun gear 4-4 of the front planetary gear mechanism through the power output shaft 3-8 of the multi-disc continuously variable transmission mechanism. At this time, the front planetary gear mechanism 4 is integrated as a whole, and then transmitted to the ring gear 5-3 of the rear planetary gear mechanism. At this time, the rear planetary gear mechanism 5 is fixedly connected as a whole, and the power is output from the output assembly 6.

[0063] The hydraulic-gear-multi-disc compound transmission HGS1 mode is as Figure 7 As shown, only the second clutch C2 2-2, the third clutch C3 2-6, the fourth clutch C4 3-4, the sixth clutch C6 3-7, and the ninth clutch C9 5-1 are engaged, and other clutches and brakes are disengaged. At this time, the engine power transmitted by the input shaft 1-2 is transmitted to the hydraulic transmission input shaft 2-1 through the first gear pair 1-4 to drive the variable hydraulic pump 2-3, and then drives the fixed-displacement hydraulic motor 2-4 to rotate. The power output by the fixed-displacement hydraulic motor 2-4 is transmitted through the hydraulic transmission output shaft 2-5 and the third gear pair 2-7, the fourth gear pair 3-1. At this time, the power is transmitted in two paths: one path drives the front planetary gear ring gear 4-3 through the fifth clutch C5 4-2, and the other path drives the multi-disc continuously variable transmission through the fourth clutch C4 3-4. The power output by the multi-disc continuously variable transmission is transmitted to the sun gear 4-4 of the front planetary gear mechanism through the power output shaft 3-8 of the multi-disc continuously variable transmission mechanism. The two paths of power converge at the front planetary gear carrier 4-6, and the power is output from the front planetary gear carrier 4-6 to the power output shaft 4-7 of the front planetary gear mechanism. Since the ninth clutch C9 5-1 is engaged, the rear planetary gear mechanism 5 is fixedly connected as a whole, and the power is output from the output assembly 6.

[0064] The gear-multi-disc compound transmission GS transmission mode is as Figure 8As shown, only the first clutch C11-5, the fourth clutch C43-4, the fifth clutch C54-2, the sixth clutch C63-7, and the ninth clutch C95-1 are engaged, and the other clutches and brakes are disengaged. The engine power transmitted by the input shaft 1-2 is divided into two paths after passing through the first gear pair 1-4: one path is transmitted to the front planetary gear ring gear 4-3 through the fifth clutch C54-2; the other path is transmitted to the power input shaft 3-3 of the multi-disc continuously variable transmission mechanism through the fifth gear pair 3-2 and the fourth clutch C43-4 to drive the multi-disc continuously variable transmission 3-5. The power output by the multi-disc continuously variable transmission is transmitted to the front planetary gear mechanism sun gear 4-4 through the power output shaft 3-8 of the multi-disc continuously variable transmission mechanism; the two paths of power converge at the front planetary gear carrier 4-6 and are output to the power output shaft 4-7 of the front planetary gear mechanism. Since the ninth clutch C95-1 is engaged, the rear planetary gear mechanism 5 is connected as a whole, and the power is output from the output assembly 6.

[0065] The hydraulic-gear parallel compound transmission HG2 transmission mode is as Figure 9 As shown, only the first clutch C11-5, the second clutch C22-2, the fifth clutch C54-2, the eighth clutch C82-8, and the brake B3-9 are engaged, and the other clutches are disengaged. The engine power transmitted by the input shaft 1-2 is divided into two paths after passing through the first gear pair 1-4 and the second gear pair 1-2: one path is transmitted to the hydraulic transmission input shaft 2-1 through the first gear pair 1-4 to drive the variable hydraulic pump 2-3, which in turn drives the fixed-displacement hydraulic motor 2-4 to rotate. The power output by the fixed-displacement hydraulic motor 2-4 is transmitted to the rear planetary gear sun gear 5-4 through the hydraulic transmission output shaft 2-5 and the eighth clutch C82-8; the other path drives the front planetary gear ring gear 4-3 through the first clutch C11-5 and the fifth clutch C54-2. Since the front planetary gear sun gear 4-4 is braked by the brake B3-9, the power is output from the front planetary gear carrier 4-6 to the power output shaft 4-7 of the front planetary gear mechanism. The power output shaft 4-7 of the front planetary gear mechanism transmits the power to the rear planetary gear ring gear 5-3; the two paths of power converge at the rear planetary gear carrier 5-2, and the power is output from the output assembly 6.

[0066] The hydraulic-multi-disc parallel HS2 transmission mode is as Figure 10As shown in the figure, only the first clutch C11-5, the second clutch C22-2, the fourth clutch C4 3-4, the sixth clutch C6 3-7, the seventh clutch C7 4-5 and the eighth clutch C8 2-8 are engaged, and other clutches and brakes are disengaged. The engine power transmitted by the input shaft 1-2 is divided into two paths after passing through the first gear pair 1-4 and the second gear pair 1-2: one path is transmitted to the hydraulic transmission input shaft 2-1 through the first gear pair 1-4 to drive the variable hydraulic pump 2-3, which in turn drives the fixed-displacement hydraulic motor 2-4 to rotate. The power output by the fixed-displacement hydraulic motor 2-4 is transmitted to the sun gear 5-4 of the rear planetary gear through the hydraulic transmission output shaft 2-5 and the eighth clutch C8 2-8; the other path is transmitted to the power input shaft 3-3 of the multi-disc continuously variable transmission mechanism through the fifth gear pair 3-2 and the fourth clutch C4 3-4 to drive the multi-disc continuously variable transmission 3-5. The power output by the multi-disc continuously variable transmission is transmitted to the ring gear 5-3 of the rear planetary gear through the power output shaft 3-8 of the multi-disc continuously variable transmission mechanism. At this time, the seventh clutch C7 4-5 is engaged, and the front planetary gear mechanism is fixed as a whole; the two paths of power converge at the rear planetary gear carrier 5-2, and the power is output from the output assembly 6.

[0067] The hydraulic-gear-multi-disc parallel compound transmission HGS2 mode is as Figure 11 As shown in the figure, only the first clutch C11-5, the second clutch C2 2-2, the fourth clutch C4 3-4, the fifth clutch C5 4-2, the sixth clutch C6 3-7 and the eighth clutch C8 2-8 are engaged, and other clutches and brakes are disengaged. The engine power transmitted by the input shaft 1-2 is divided into two paths after passing through the first gear pair 1-4 and the second gear pair 1-2: one path is transmitted to the hydraulic transmission input shaft 2-1 through the first gear pair 1-4 to drive the variable hydraulic pump 2-3, which in turn drives the fixed-displacement hydraulic motor 2-4 to rotate. The power output by the fixed-displacement hydraulic motor 2-4 is transmitted to the sun gear 5-4 of the rear planetary gear through the hydraulic transmission output shaft 2-5 and the eighth clutch C8 2-8; the other path is divided into two paths after passing through the first clutch C11-5: one path is transmitted to the ring gear 4-3 of the front planetary gear through the fifth clutch C5 4-2; the other path is transmitted to the power input shaft 3-3 of the multi-disc continuously variable transmission mechanism through the fifth gear pair 3-2 and the fourth clutch C4 3-4 to drive the multi-disc continuously variable transmission 3-5. The power output by the multi-disc continuously variable transmission is transmitted to the sun gear 4-4 of the front planetary gear mechanism through the power output shaft 3-8 of the multi-disc continuously variable transmission mechanism; the two paths of power converge at the front planetary gear carrier 4-6, and the power is output to the power output shaft 4-7 of the front planetary gear mechanism. The power output shaft 4-7 of the front planetary gear mechanism transmits the power to the ring gear 5-3 of the rear planetary gear; the two paths of power converge at the rear planetary gear carrier 5-2, and the power is output from the output assembly 6.

[0068] As Figure 12As shown, by adjusting the displacement ratio of the hydraulic transmission mechanism 2, the transmission ratio of the multi-disc continuously variable transmission mechanism 3 is adjusted and the engagement of the clutch assembly is selectively controlled to provide stepless speed regulation switching between the "hydraulic transmission H → multi-disc continuously variable transmission S → hydraulic-multi-disc compound transmission HS" transmission modes. Starting with mode H, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the hydraulic transmission H mode reaches the positive maximum value; when e·i S ∈[n o (H) = n o (S)], and e ∈ [0, 1], i S within the determined transmission ratio range, the hydraulic transmission H mode can be synchronously switched to the multi-disc continuously variable transmission S mode. When the transmission ratio i of the multi-disc continuously variable transmission S changes from the maximum value to the minimum value, n o (S) decreases non-linearly; when e·i S ∈[n o (S) = n o (HS1)], and e ∈ [0, 1], i S within the determined transmission ratio range, the multi-disc continuously variable transmission S mode can be synchronously switched to the hydraulic-multi-disc compound transmission HS mode; when e·i S ∈[n o (S) = n o (HS2)], and e ∈ [0, 1], i S within the determined transmission ratio range, the multi-disc continuously variable transmission S mode can be synchronously switched to the hydraulic-multi-disc compound transmission HS2 mode. Different switching positions result in different output values of the hydraulic-multi-disc compound transmission HS1 mode, but the output speed decreases linearly with the decrease of the displacement ratio e of the hydraulic transmission mechanism.

[0069] Such as Figure 13As shown, by adjusting the displacement ratio of the hydraulic transmission mechanism 2, adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism 3, and selectively controlling the engagement of the clutch assembly and the brake assembly, stepless speed regulation switching between the transmission modes of "hydraulic transmission H → gear transmission G → hydraulic-gear compound transmission HG2 or hydraulic transmission H → hydraulic-gear-multi-disc HGS2" is provided. Starting with the hydraulic mode H, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = -1, the hydraulic transmission H mode reaches the negative maximum value, and when e = 1, the hydraulic transmission H mode reaches the positive maximum value; when e ∈ [n0(H) = n0(G)], the gear transmission G mode can be synchronously switched at this time, and the gear transmission G mode is a fixed transmission ratio transmission; when e ∈ [n0(G) = n0(HG2)], the hydraulic-gear compound transmission HG mode can be synchronously switched, and when e ∈ [n0(H) = n0(HGS2)] and e ∈ [0, 1], i S When within the determined transmission ratio range, it can be synchronously switched to the hydraulic-gear-multi-disc HGS2 mode.

[0070] As Figure 14 shown, by adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism 3 and selectively controlling the engagement of the clutch assembly and the brake assembly, stepless speed regulation switching between the transmission modes of "hydraulic transmission H → gear-multi-disc compound transmission GS → hydraulic-gear-multi-disc series compound transmission HGS1" is provided. Starting with the hydraulic mode H, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = -1, the hydraulic transmission H mode reaches the negative maximum value, and when e = 1, the hydraulic transmission H mode reaches the positive maximum value. When n o (H) = n o (GS) and i S When within the determined transmission ratio range, the hydraulic transmission H mode can be synchronously switched to the gear-multi-disc compound transmission GS mode; when the transmission ratio of the multi-disc continuously variable transmission satisfies i S ∈ [n o (GS) = n o (HGS1)] and e = 1, the gear-multi-disc compound transmission GS mode can be synchronously switched to the multi-disc continuously variable transmission HGS1 mode. When the transmission ratio i of the multi-disc continuously variable transmission S changes from the maximum value to the minimum value, n o (S) increases non-linearly; when the displacement ratio e of the hydraulic transmission mechanism is fixed at e = 1, the transmission device steplessly changes speed only by changing i S within the determined transmission ratio range.

[0071] As Figure 15As shown, by adjusting the displacement ratio of the hydraulic transmission mechanism 2, adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism 3 and selectively controlling the engagement of the clutch assembly, stepless speed regulation switching between the "hydraulic-gear series compound transmission HG1 → multi-disc continuously variable transmission S → hydraulic-multi-disc series compound transmission HS1" transmission modes is provided. Starting with the hydraulic-gear series compound transmission mode HG1, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the hydraulic transmission H mode reaches the positive maximum value; when the transmission ratio of the multi-disc continuously variable transmission satisfies n o (HG) = n o (S) and e = 1, the gear-multi-disc compound transmission GS mode can be synchronously switched to the multi-disc continuously variable transmission HGS1 mode. When the transmission ratio i of the multi-disc continuously variable transmission S changes from the maximum value to the minimum value, n o (S) increases non-linearly; when the displacement ratio e of the hydraulic transmission mechanism is fixed at e = 1, the transmission device steplessly varies the speed only by changing i S within the determined transmission ratio range. Example of an embodiment:

[0072] The main parameters are: i1i8 = 1, i2i7 = 1, i2i5i6 = 0.2, i1i3i4i7 = 1, i1i3i4i5i6 = 0.2, k1 = 1.5, k2 = 2.5, i S ∈[1.32, 13.2].

[0073] Mode switching process 1: Hydraulic transmission H → multi-disc continuously variable transmission S → hydraulic-multi-disc compound transmission HS

[0074] The output-input speed relationship of the hydraulic transmission H is:

[0075] The output-input speed relationship of the multi-disc continuously variable transmission S is:

[0076] The output-input speed relationship of the hydraulic-multi-disc series compound transmission HS1 is:

[0077] The output-input speed relationship of the hydraulic-multi-disc parallel compound transmission HS2 is:

[0078] As Figure 12 shown, starting with mode H1, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 0.397, the H mode reaches the positive 0.397n I ; when e·i S = 5.0 is satisfied simultaneously, and e ∈ [0, 1], and i SWhen the three conditions of ∈[1.32, 13.2] are met, the H mode can be synchronously switched to the S mode or the HS2 mode. When synchronously switched to the S mode, when i S changes from 13.2 to 1.32, n o (S) non-linearly increases from 0.379n I to 3.79n I ; when e = 1 is satisfied, the S mode can be synchronously switched to the HS1 mode. When e·i S = 5.0, and e ∈[0, 1], i S ∈[1.32, 13.2] are met, the S mode can be synchronously switched to the HS2 mode. Different switching positions result in different output values of the hydraulic-multi-disc series or parallel composite drive mode, but the output speed linearly decreases with the decrease of the displacement ratio e of the hydraulic drive mechanism.

[0079] Mode switching process 2: Hydraulic drive H → Gear drive G → Hydraulic-gear composite drive HG2 or Hydraulic drive H → Hydraulic-gear-multi-disc HGS2

[0080] The output-input speed relationship of the hydraulic drive H is:

[0081] The output-input speed relationship of the gear drive G is:

[0082] The output-input speed relationship of the hydraulic-gear parallel composite drive HG2 is:

[0083] The output-input speed relationship of the hydraulic-gear-multi-disc parallel composite drive HGS2 is:

[0084] As Figure 13 shown, starting with the hydraulic drive mode H, the output speed linearly increases with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the hydraulic drive H mode reaches the positive maximum value n I ; when e = 0.6, the hydraulic drive mode H can be synchronously switched to the gear drive G mode, and at this time the gear drive has a fixed transmission ratio; the gear drive G mode can also be synchronously switched to the hydraulic-gear parallel composite drive HG2 mode; when e = 0.8022, i S = 10, the hydraulic drive mode H reaches the positive 0.8022n I , and at this time the hydraulic drive H mode can be synchronously switched to the hydraulic-gear-multi-disc parallel HGS2 mode. When i S changes from 13.2 to 1.32, n o (HGS) non-linearly increases, and the transmission device changes e and iS Stepless speed change within the range of [0.82, 1.79]n I is carried out.

[0085] Mode switching process three: Hydraulic drive H → Gear-multi-disc compound drive GS → Hydraulic-gear-multi-disc series compound drive HGS1

[0086] The output-input speed relationship of the hydraulic drive H is as follows:

[0087] The output-input speed relationship of the gear-multi-disc stepless speed change drive GS is as follows:

[0088] The output-input speed relationship of the hydraulic-gear-multi-disc series compound drive HGS1 is as follows:

[0089] As Figure 14 shown, starting with the hydraulic mode H, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 0.8, the H mode reaches 0.8n I ; when both conditions of i S = 10 are satisfied, the H mode can be synchronously switched to the GS mode. When synchronously switched to the GS mode, when i S changes from 13.2 to 1.32, n o (GS) non-linearly increases from 0.75n I to 2.12n I ; when e = 1 is satisfied, the GS mode can be synchronously switched to the HGS1 mode. The GS mode and the HGS1 mode are in a positive correlation of e times. When switched to the HGS1 mode, n o (HGS1) non-linearly increases from 0 to 2.12n I ; different switching positions result in different output values of the gear-multi-disc compound drive or the hydraulic-gear-multi-disc series compound drive mode, but the output speed decreases linearly with the decrease of the displacement ratio e of the hydraulic drive mechanism.

[0090] Mode switching process four: Hydraulic-gear series compound drive HG1 → Multi-disc stepless speed change drive S → Hydraulic-multi-disc series compound drive HS1

[0091] The output-input speed relationship of the hydraulic-gear series drive HG1 is as follows:

[0092] The output-input speed relationship of the multi-disc stepless speed change drive S is as follows:

[0093] The output-input speed relationship of the hydraulic-multi-disc series compound drive HS1 is as follows:

[0094] As shown Figure 15 in the figure, starting with the hydraulic-gear series drive HG1, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the H mode reaches the positive maximum value of 0.6n I ; when the two conditions of i S = 8.3 are satisfied simultaneously, the HG1 mode can be synchronously switched to the S mode. When synchronously switched to the S mode, when i S changes from 13.2 to 1.32, n o (S) non-linearly increases from 0.379n I to 3.79n I ; when e = 1 is satisfied, the S mode can be synchronously switched to the HS1 mode. The GS mode and the HGS1 mode are positively correlated by e times. When switched to the HS1 mode, n o (HS1) non-linearly increases from 0 to 3.79n I ; different switching positions result in different output values of the hydraulic-gear series compound drive or the hydraulic-multi-disc series compound drive mode, but the output speed decreases linearly with the decrease of the displacement ratio e of the hydraulic drive mechanism.

[0095] The cone disks and T-shaped disks of the multi-disc continuously variable transmission have a large cone apex half-angle, so the equivalent curvature of the contact area is very small, the contact stress is low, and a tough traction oil film is formed on the contact surface to transmit power. Therefore, the load-bearing capacity and service life are high. It can be used continuously for many years under normal use conditions and can withstand a certain impact load; the speed stability is good, the transmission efficiency can be as high as 90%, the specific power of the hydraulic components is large, but the transmission efficiency is relatively low, usually between 80% - 90%. If the transmission efficiency of the multi-disc continuously variable transmission is taken as 90% and the total efficiency of the hydraulic components is 80%, when the multi-disc-hydraulic series HS1 mode is adopted, the system transmission efficiency = 90% × 80% = 72%. When the multi-disc-hydraulic parallel HS2 mode is adopted, assuming that the input powers of the two paths are the same, the system transmission efficiency = 0.5 × 90% + 0.5 × 80% = 85%. Compared with the hydraulic-multi-disc series drive HS1, its efficiency is increased by 13%. Assuming that 9 / 10 of the input power passes through the multi-disc path and 1 / 10 of the input power passes through the hydraulic path, the system transmission efficiency = 0.9 × 90% + 0.1 × 80% = 89%. Compared with the hydraulic-multi-disc series drive HS1, its efficiency is increased by 17%. Therefore, this mode can effectively improve the system transmission efficiency, but its speed regulation range is limited. The output speed no(HS2) changes within the positive speed regulation range [0, 2.98]n I and is suitable for high-efficiency stepless speed regulation within the region. Although the hydraulic-multi-disc series drive HS1 has a relatively low transmission efficiency, its speed regulation range is wide. The output speed no(HS1) is in [0, 3.9]n IIt varies within a range and is applicable to large-range non-linear stepless speed regulation.

[0096] It should be understood that although this specification is described according to various embodiments, not every embodiment only contains an independent technical solution. This narrative way of the specification is only for clarity. Those skilled in the art should regard the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0097] The series of detailed descriptions listed above are only specific descriptions of the feasible embodiments of the present invention, and they are not intended to limit the protection scope of the present invention. Any equivalent embodiments or modifications made without departing from the technical spirit of the present invention should be included in the protection scope of the present invention.

Claims

1. A multi-mode composite transmission device integrating gears, hydraulics, and multiple discs, characterized in that, It includes an input component (1), a hydraulic transmission mechanism (2), a multi-disc continuously variable transmission mechanism (3), a front planetary gear mechanism (4), a rear planetary gear mechanism (5), an output component (6), a clutch component and a brake component; the clutch component connects the output end of the input component (1) to the input end of the hydraulic transmission mechanism (2), the input end of the multi-disc continuously variable transmission mechanism (3) and the input end of the front planetary gear mechanism (4) respectively; the clutch component connects the output end of the hydraulic transmission mechanism (2) to the multi-disc continuously variable transmission mechanism (3), the front planetary gear mechanism (4) and the rear planetary gear mechanism (5) respectively; the clutch component connects the multi-disc continuously variable transmission mechanism (3) to the front planetary gear mechanism (4), connects the front planetary gear mechanism (4) to the rear planetary gear mechanism (5), and connects the rear planetary gear mechanism (5) to the output component (6); by adjusting the displacement ratio of the hydraulic transmission mechanism (2), adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism (3) and selectively controlling the engagement of the clutch component and the brake component, a continuous transmission ratio between the input component (1) and the output component (6) is provided; By adjusting the displacement ratio of the hydraulic transmission mechanism (2), adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism (3) and selectively controlling the engagement of the clutch component and the brake component, a transmission mode of any one or any two combinations or three combinations of hydraulic transmission H, gear transmission G and multi-disc continuously variable transmission S between the input component (1) and the output component (6) is provided; The clutch assembly includes a first clutch C1(1-5), a second clutch C2(2-2), a third clutch C3(2-6), a fourth clutch C4(3-4), a fifth clutch C5(4-2), a sixth clutch C6(3-7), a seventh clutch C7(4-5), an eighth clutch C8(2-8), a ninth clutch C9(5-1), and a brake B; the first clutch C1(1-5) is used to selectively connect the input shaft(1-3) to the multi-disc continuously variable transmission mechanism(3); the second clutch C2(2-2) is used to selectively connect the input assembly(1) to the input end of the hydraulic transmission mechanism(2); the third clutch C3(2-6) is used to selectively connect the hydraulic transmission output shaft(2-5) to the multi-disc continuously variable transmission mechanism(3) through the third gear pair(2-7); the fourth clutch C4(3-4) is used to selectively connect the engine output shaft(1-6) or the hydraulic transmission output shaft(2-5) to the power input shaft(3-3) of the multi-disc continuously variable transmission mechanism to rotate together; the fifth clutch C5(4-5) is used to selectively connect the engine output shaft(1-6) to the front planetary gear ring(4-3) to rotate together; the sixth clutch C6(3-7) is used to selectively connect the power output shaft(3-8) of the multi-disc continuously variable transmission mechanism to the front planetary gear sun gear(4-4) to rotate together; the seventh clutch C7(4-5) connects the front planetary gear sun gear(4-4) to the front planetary gear carrier(4-6) to rotate together; the eighth clutch C8(2-8) is used to selectively connect the hydraulic transmission output shaft(2-5) to the rear planetary gear sun gear(5-4) to rotate together through the eighth gear pair(5-5); the ninth clutch C9(5-1) is used to selectively connect the rear planetary gear carrier(5-2) to the rear planetary gear ring(5-3) to rotate together; the brake B(3-9) is used to fix the sun gear(4-4) of the front planetary gear mechanism.

2. The multi-mode composite transmission device integrating a gear, a hydraulic system, and multiple discs as claimed in claim 1, wherein By adjusting the displacement ratio of the hydraulic transmission mechanism(2) and selectively controlling the engagement of the second clutch C2(2-2), the eighth clutch C8(2-8), and the ninth clutch C9(5-1), a hydraulic transmission H between the input assembly(1) and the output assembly(6) is provided.

3. The multi-mode composite transmission device integrating gear, hydraulic and multi-disc as claimed in claim 2, characterized in that, By controlling the engagement of the first clutch C1(1-5), the fifth clutch C5(4-2), the ninth clutch C9(5-1), and the brake B(3-9), a gear transmission G between the input assembly(1) and the output assembly(6) is provided.

4. The multi-mode composite transmission device integrating a gear, a hydraulic system, and multiple discs according to claim 3, characterized in that, By adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism(4) and selectively controlling the engagement of the first clutch C1(1-5), the fourth clutch C4(3-4), the sixth clutch C6(4-1), the seventh clutch C7(4-5), and the ninth clutch C9(5-1), a multi-disc continuously variable transmission S between the input assembly(1) and the output assembly(6) is provided.

5. The multi-mode compound transmission device integrating a gear, a hydraulic system, and multiple discs as claimed in claim 4, wherein, By adjusting the displacement ratio of the hydraulic transmission mechanism (2) and selectively controlling the engagement of the second clutch C2 (2-2), the third clutch C3 (2-6), the fifth clutch C5 (4-2), the ninth clutch C9 (5-1), and the brake B (3-9), and by selectively controlling the engagement of the first clutch C1 (1-5), the second clutch C2 (2-2), the fifth clutch C5 (4-2), the eighth clutch C8 (2-8), and the brake B (3-9), respective different hydraulic-gear HGs between the input assembly (1) and the output assembly (6) are provided; By adjusting the transmission ratio of the multi-disk continuously variable transmission mechanism (4) and selectively controlling the engagement of the first clutch C1 (1-5), the fourth clutch C4 (3-4), the fifth clutch C5 (4-2), the sixth clutch C6 (3-7), and the ninth clutch C9 (5-1), a gear-multi-disk composite transmission GS between the input assembly (1) and the output assembly (6) is provided; By adjusting the displacement ratio of the hydraulic transmission mechanism (2), adjusting the transmission ratio of the multi-disk continuously variable transmission mechanism (3), and selectively controlling the engagement of the second clutch C2 (2-2), the third clutch C3 (3-6), the fourth clutch C4 (3-4), the sixth clutch C6 (3-7), the seventh clutch C7 (4-5), and the ninth clutch C9 (5-1), and by selectively controlling the engagement of the first clutch C1 (1-5), the second clutch C2 (2-2), the fourth clutch C4 (3-4), the sixth clutch C6 (3-7), the seventh clutch C7 (4-5), and the eighth clutch C8 (2-8), respective different hydraulic-multi-disk HSs between the input assembly (1) and the output assembly (6) are provided; 6. The multi-mode composite transmission device integrating a gear, a hydraulic system, and multiple discs as claimed in claim 5, wherein By adjusting the displacement ratio of the hydraulic transmission mechanism (2), adjusting the transmission ratio of the multi-disk continuously variable transmission mechanism (4), and selectively controlling the engagement of the second clutch C2 (2-2), the third clutch C3 (2-6), the fourth clutch C4 (3-4), the sixth clutch C6 (3-7), and the ninth clutch C9 (5-1), and by selectively controlling the engagement of the first clutch C1 (1-5), the second clutch C2 (2-2), the fourth clutch C4 (3-4), the fifth clutch C5 (4-2), the sixth clutch C6 (3-7), and the eighth clutch C8 (2-8), respective different hydraulic-gear-multi-disk composite transmissions HGSs between the input assembly (1) and the output assembly (6) are provided; 7. The multi-mode composite transmission device integrating gear - hydraulic - multi-disc as claimed in claim 5, characterized in that, By adjusting the displacement ratio of the hydraulic transmission mechanism (2), adjusting the transmission ratio of the multi-disk continuously variable transmission mechanism (3), and selectively controlling the engagement of the clutch and brake assembly, stepless speed regulation switching between the "hydraulic transmission H → multi-disk continuously variable transmission S → hydraulic-multi-disk composite transmission HS" transmission modes is provided.

8. The multi-mode composite transmission device integrating a gear, a hydraulic system, and multiple discs as claimed in claim 6, characterized in that, By adjusting the displacement ratio of the hydraulic transmission mechanism (2), the transmission ratio of the multi-disc continuously variable transmission mechanism (3), and selectively controlling the engagement of the clutch and brake components, stepless speed regulation switching between the "hydraulic transmission H → gear transmission G → hydraulic-gear compound transmission HG2 or hydraulic transmission H → hydraulic-gear-multi-disc HGS2" transmission modes is provided.

9. The multi-mode composite transmission device integrating gear, hydraulic and multi-disc as claimed in claim 6, wherein, By adjusting the displacement ratio of the hydraulic transmission mechanism (2), adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism (3), and controlling the engagement of the clutch components, stepless speed regulation switching between the "hydraulic transmission H → gear-multi-disc compound transmission GS → hydraulic-gear-multi-disc series compound transmission HGS1" transmission modes is provided.

10. The multi-mode composite transmission device integrating gear, hydraulic and multi-disc as claimed in claim 5, wherein, By adjusting the displacement ratio of the hydraulic transmission mechanism (2), adjusting the transmission ratio of the multi-disc continuously variable transmission mechanism (3), and controlling the engagement of the clutch components, stepless speed regulation switching between the "hydraulic-gear series compound transmission HG1 → multi-disc continuously variable transmission S → hydraulic-multi-disc series compound transmission HS1" transmission modes is provided.

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