A multi-mode mechanical-hydraulic compound transmission device

Abstract

The present invention provides a multi-mode mechanical-hydraulic compound transmission device, comprising an input member, a hydraulic transmission mechanism, a mechanical transmission mechanism, a confluence mechanism, an output member, a clutch assembly and a brake assembly; the clutch assembly connects the output end of the input mechanism to the input end of the hydraulic transmission mechanism, the mechanical transmission mechanism and the confluence mechanism respectively, the clutch assembly connects the output end of the hydraulic transmission mechanism to the confluence mechanism, and the clutch assembly connects the mechanical transmission mechanism to the confluence mechanism; the confluence mechanism is connected to the output member; by adjusting the displacement ratio of the hydraulic transmission mechanism and by selectively controlling the engagement of the clutch assembly and the brake assembly, a continuously changing transmission ratio between the input member and the output member is provided. The present invention can realize the switching of modes such as mechanical transmission, hydraulic transmission and mechanical-hydraulic compound transmission, improve the adjustment freedom and expand the speed regulation range in the forward and backward directions under the premise of increasing the fault tolerance performance of the system.

Description

Technical Field

[0001] The present invention relates to the field of gearboxes, and in particular to a multi-mode mechanical-hydraulic compound transmission device. Background Art

[0002] The multifunctional hydraulic transmission device generally adopts hydraulic transmission to achieve flexible high-torque starting, mechanical transmission to complete efficient transition, and hydraulic-hydraulic composite transmission to meet the requirements of efficient stepless speed regulation and adapt to various working conditions within the entire speed regulation range. It is relatively easy for the common hydraulic-hydraulic composite transmission to achieve stepless speed regulation in each gear in the forward direction, but it fails to fully consider the adaptability of each gear in the reverse direction. The hydraulic-hydraulic composite transmission has an efficient stepless speed change function within the forward and reverse speed regulation range. The use of multiple gears to reasonably connect to realize the hydraulic-mechanical transmission mode can better solve this problem. Summary of the invention

[0003] In view of the deficiencies in the prior art, the present invention provides a multi-mode electro-hydraulic compound transmission device, which can realize switching of mechanical transmission, hydraulic transmission and electro-hydraulic compound transmission modes through the combined switching of clutches and brakes. While increasing the fault tolerance of the system, the adjustment freedom is improved and the speed regulation range in the forward and reverse directions is expanded.

[0004] The present invention achieves the above technical objectives through the following technical means.

[0005] A multi-mode hydraulic compound transmission device comprises an input member, a hydraulic transmission mechanism, a mechanical transmission mechanism, a confluence mechanism, an output member, a clutch assembly and a brake assembly; the clutch assembly connects the output end of the input mechanism with the input end of the hydraulic transmission mechanism, the mechanical transmission mechanism and the confluence mechanism respectively, the clutch assembly connects the output end of the hydraulic transmission mechanism with the confluence mechanism, and the clutch assembly connects the mechanical transmission mechanism with the confluence mechanism; the confluence mechanism is connected to the output member; by adjusting the displacement ratio of the hydraulic transmission mechanism and by selectively controlling the engagement of the clutch assembly and the brake assembly, a continuously variable transmission ratio between the input member and the output member is provided.

[0006] Further, the mechanical transmission mechanism includes a mechanical transmission output shaft, a left planetary gear train and a right planetary gear train;

[0007] The left planetary gear train includes a left sun gear, a left planet carrier and a left ring gear, and the right planetary gear train includes a right planet carrier, a right sun gear and a right ring gear, wherein the left sun gear is connected to the right sun gear, and the right ring gear is connected to the left planet carrier;

[0008] The clutch assembly includes a fifth clutch C5 and a sixth clutch C6; the fifth clutch C5 is used to connect the right ring gear to the mechanical transmission output shaft, and the sixth clutch C6 is used to connect the right sun gear to the mechanical transmission output shaft; the brake assembly includes a second brake B2 and a third brake B3, the second brake B2 is used to connect the left ring gear to the fixed part, and the third brake B3 is used to connect the right ring gear to the fixed part.

[0009] Further, the merging mechanism includes a left planetary gear train of the merging mechanism and a right gear train of the merging mechanism; the left planetary gear train of the merging mechanism includes a left planetary carrier of the merging mechanism, a left sun gear of the merging mechanism and a left ring gear of the merging mechanism; the right gear train of the merging mechanism includes a right sun gear of the merging mechanism, a right planetary carrier of the merging mechanism and a right ring gear of the merging mechanism; the left sun gear of the merging mechanism is connected to the right sun gear of the merging mechanism, and the left sun gear of the merging mechanism is connected to the output end of the hydraulic transmission mechanism; the left ring gear of the merging mechanism is connected to the right planetary carrier of the merging mechanism; the input member is connected to the left planetary carrier of the merging mechanism through a left gear pair and a right gear pair respectively; the right ring gear of the merging mechanism is connected to the mechanical transmission output shaft through a mechanical transmission output gear pair, and the right planetary carrier of the merging mechanism is connected to the output member;

[0010] The clutch assembly also includes a third clutch C3, a fourth clutch C4 and a seventh clutch C7; the third clutch C3 is used to connect the input member to the input end of the merging mechanism through a left gear pair, and the fourth clutch C4 is used to connect the input member to the input end of the merging mechanism through a right gear pair; the seventh clutch C7 is used to connect the right sun gear of the merging mechanism to the right planetary carrier of the merging mechanism; the brake assembly also includes a first brake B1 and a fourth brake B4, the first brake B1 is used to connect the left sun gear of the merging mechanism to the fixed part, and the fourth brake B4 is used to connect the right ring gear of the merging mechanism to the fixed part.

[0011] Furthermore, by adjusting the displacement ratio of the hydraulic transmission assembly and by selectively controlling the engagement of the clutch assembly and the brake assembly, the forward or reverse transmission modes provided between the input member and the output member include: hydraulic transmission, mechanical transmission and mechanical-hydraulic compound transmission.

[0012] Further, the third clutch C3 , the fourth clutch C4 , the fifth clutch C5 , the sixth clutch C6 , the first brake B1 , the second brake B2 , and the third brake B3 are engaged to provide mechanical transmission of various gear ratios between the input member and the output member in forward or reverse direction.

[0013] Further, the fifth clutch C5, the sixth clutch C6 and the first brake B1 are engaged to provide a forward mechanical transmission F(M1) between the input member and the output member, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0014]

[0015] Where n o is the speed of the output component, n I is the rotation speed of the input member; k4 is the characteristic parameter of the right gear train of the confluence mechanism; i6i7 is the transmission ratio between the mechanical transmission output shaft and the right gear ring of the confluence mechanism;

[0016] The sixth clutch C6, the first brake B1 and the third brake B3 are engaged to provide a forward mechanical transmission F(M2) between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship:

[0017]

[0018] In the formula, k1 is the characteristic parameter of the left planetary gear train; k2 is the characteristic parameter of the right planetary gear train;

[0019] The third clutch C3 and the seventh clutch C7 are engaged to provide a forward mechanical transmission F(M3) between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship:

[0020]

[0021] In the formula, i3i4 is the transmission ratio of the left gear pair;

[0022] The sixth clutch C6, the first brake B1 and the second brake B2 are engaged to provide a forward mechanical transmission F(M4) between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship:

[0023]

[0024] In combination with the fifth clutch C5, the first brake B1 and the second brake B2, a reverse mechanical transmission R (M1) between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0025]

[0026] The fourth clutch C4 and the first brake B1 are engaged to provide a reverse mechanical transmission R (M2) between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship:

[0027]

[0028] Wherein, k3 is the characteristic parameter of the left gear train of the confluence mechanism; i5 is the transmission ratio of the right gear pair.

[0029] Furthermore, the clutch assembly also includes a first clutch C1 and a second clutch C2, the first clutch C1 is used to connect the input member with the input end of the hydraulic transmission mechanism, and the second clutch C2 is used to connect the output end of the hydraulic transmission mechanism with the left sun gear of the merging mechanism; by adjusting the displacement ratio of the hydraulic transmission assembly and by engaging the first clutch C1, the second clutch C2, the seventh clutch C7 and the fourth brake B4, a hydraulic transmission with multiple transmission ratios for forward or reverse movement between the input member and the output member is provided.

[0030] Further, by adjusting the displacement ratio of the hydraulic transmission assembly, by engaging the first clutch C1, the second clutch C2 and the fourth brake B4, a forward or reverse hydraulic transmission F(H1) / R(H1) between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0031]

[0032] Wherein, k4 is the characteristic parameter of the right gear train of the confluence mechanism; e is the displacement ratio of the hydraulic transmission mechanism; i1 is the transmission ratio between the input end of the hydraulic transmission mechanism and the input member, and i2 is the transmission ratio between the output end of the hydraulic transmission mechanism and the left sun gear of the confluence mechanism; when e>0, it is F (H1) gear, and when e<0, it is R (H1) gear;

[0033] The first clutch C1, the second clutch C2 and the seventh clutch C7 are engaged to provide a forward or reverse hydraulic transmission F(H2) / R(H2) between the input member and the output member, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0034]

[0035] In the formula, when e>0, it is F(H2) gear, and when e<0, it is R(H2) gear.

[0036] Furthermore, by adjusting the displacement ratio of the hydraulic transmission assembly and by engaging the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4, the fifth clutch C5, the sixth clutch C6, the second brake B2 and the third brake B3, a hydraulic compound transmission with multiple gear ratios for forward or reverse movement between the input member and the output member is provided.

[0037] Further, by adjusting the displacement ratio of the hydraulic transmission assembly and by engaging the first clutch C1, the second clutch C2, the fifth clutch C5 and the sixth clutch C6, a hydraulic compound transmission F (HM1) is provided for forward movement between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship:

[0038]

[0039] By adjusting the displacement ratio of the hydraulic transmission assembly and by engaging the first clutch C1, the second clutch C2 and the third clutch C3, a forward hydraulic compound transmission F (HM2) between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0040]

[0041] By adjusting the displacement ratio of the hydraulic transmission assembly, by engaging the first clutch C1, the second clutch C2, the sixth clutch C6 and the third brake B3, a forward hydraulic compound transmission F (HM3) between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0042]

[0043] By adjusting the displacement ratio of the hydraulic transmission assembly and by engaging the first clutch C1, the second clutch C2, the sixth clutch C6 and the second brake B2, a hydraulic compound transmission F (HM4) is provided for forward movement between the input member and the output member, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0044]

[0045] By adjusting the displacement ratio of the hydraulic transmission assembly, by engaging the first clutch C1, the second clutch C2, the fifth clutch C5, and the second brake B2, a reverse hydraulic compound transmission R (HM1) between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0046]

[0047] By adjusting the displacement ratio of the hydraulic transmission assembly and by engaging the first clutch C1, the second clutch C2 and the fourth clutch C4, a reverse hydraulic compound transmission R (HM2) between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship:

[0048]

[0049] The beneficial effects of the present invention are:

[0050] The multi-mode electro-hydraulic composite transmission device described in the present invention adopts three modes of hydraulic transmission, mechanical transmission and electro-hydraulic composite transmission with 14 gears to meet the requirements of complex operations; it can realize the power-free interruption shifting between the hydraulic transmission gears and the electro-hydraulic transmission gears, and can also realize the stepless speed regulation between the electro-hydraulic transmission gears; it expands the speed regulation range in the forward and reverse directions and expands the adjustment freedom. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0052] Figure 1 This is a structural principle diagram of the multi-mode mechanical-hydraulic compound transmission device of the present invention;

[0053] Figure 2 It is a schematic diagram of the power flow direction of the mechanical transmission F (M1) gear of the present invention;

[0054] Figure 3 It is a schematic diagram of the power flow direction of the mechanical transmission F (M2) gear of the present invention;

[0055] Figure 4 It is a schematic diagram of the power flow direction of the mechanical transmission F (M3) gear of the present invention;

[0056] Figure 5 It is a schematic diagram of the power flow direction of the mechanical transmission F (M4) gear of the present invention;

[0057] Figure 6 It is a schematic diagram of the power flow direction of the mechanical transmission R (M1) gear of the present invention;

[0058] Figure 7 It is a schematic diagram of the power flow direction of the mechanical transmission R (M2) gear of the present invention;

[0059] Figure 8 It is a schematic diagram of the power flow direction of the hydraulic transmission F (H1) / R (H1) gear position of the present invention;

[0060] Fig. 9 It is a schematic diagram of the power flow direction of the hydraulic transmission F (H2) / R (H2) gear position of the present invention;

[0061] Fig.10 It is a schematic diagram of power flow in gear F (HM1) of the hydraulic-mechanical compound transmission of the present invention;

[0062] Fig.11 This is a schematic diagram of power flow in gear F (HM2) of the hydraulic-mechanical compound transmission of the present invention;

[0063] Fig.12 This is a schematic diagram of the power flow direction of the hydraulic-mechanical compound transmission F (HM3) of the present invention;

[0064] Fig.13 This is a schematic diagram of the power flow direction of the hydraulic-mechanical compound transmission F (HM4) of the present invention;

[0065] Fig.14 This is a schematic diagram of the power flow of the R (HM1) gear of the hydraulic-mechanical compound transmission of the present invention;

[0066] Fig.15 This is a schematic diagram of the power flow of the R (HM2) gear of the hydraulic-mechanical compound transmission of the present invention;

[0067] Fig.16 The figure is a graph showing the switching of various gear modes and their speed regulation characteristics in the present invention.

[0068] In the figure:

[0069] 1-input shaft; 2-mechanical transmission mechanism; 2-1-left gear pair; 2-2-third clutch C3; 2-3-right gear pair; 2-4-fourth clutch C4; 2-5-left sun gear; 2-6-left planetary carrier; 2-7-second brake B2; 2-8-left ring gear; 2-9-right planetary carrier; 2-10-right sun gear; 2-11-third brake B3; 2-12-right ring gear; 2-13-fifth clutch C5; 2-14-sixth clutch C6; 2-15-mechanical transmission output shaft; 2-16-mechanical transmission output gear pair; 3-output shaft; 4-convergence mechanism; 4-1-convergence mechanism left planetary carrier; 4-2-left sun gear of the confluence mechanism; 4-3-left ring gear of the confluence mechanism; 4-4-right sun gear of the confluence mechanism; 4-5-right planetary carrier of the confluence mechanism; 4-6-fourth brake B4; 4-7-right ring gear of the confluence mechanism; 4-8-seventh clutch C7; 5-intermediate shaft; 6-hydraulic transmission mechanism; 6-1-hydraulic transmission input gear pair; 6-2-hydraulic transmission input shaft; 6-3-first clutch C1; 6-4-variable pump; 6-5-hydraulic pipeline; 6-6-second clutch C2; 6-7-hydraulic transmission output shaft; 6-8-quantitative motor; 6-9-hydraulic transmission output gear pair; 6-10-first brake B1. DETAILED DESCRIPTION

[0070] The present invention is further described below in conjunction with the accompanying drawings and specific embodiments, but the protection scope of the present invention is not limited thereto.

[0071] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and should not be construed as limiting the present invention.

[0072] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "axial", "radial", "vertical", "horizontal", "inner", "outer" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are 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, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "multiple" is two or more, unless otherwise clearly and specifically defined.

[0073] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0074] like Figure 1 As shown, the multi-mode mechanical-hydraulic compound transmission device of the present invention comprises an input shaft 1, a mechanical transmission mechanism 2, an output shaft 3, a confluence mechanism 4, an intermediate shaft 5, a hydraulic transmission mechanism 6, a clutch assembly and a brake assembly;

[0075] The hydraulic transmission mechanism 6 includes a hydraulic transmission input gear pair 6-1, a hydraulic transmission input shaft 6-2, a first clutch C16-3, a variable pump 6-4, a hydraulic pipeline 6-5, a second clutch C26-6, a hydraulic transmission output shaft 6-7, a quantitative motor 6-8, a hydraulic transmission output gear pair 6-9 and a first brake B16-10; the first clutch C16-3 is used to connect the input shaft 1 with the hydraulic transmission input shaft 6-2, the second clutch C26-6 is used to connect the hydraulic transmission output shaft 6-7 with the intermediate shaft 5, and the first brake B16-10 is used to brake the intermediate shaft 5.

[0076] The mechanical transmission mechanism 2 includes a left sun gear 2-5, a left planetary carrier 2-6, a second brake B22-7, a left ring gear 2-8, a right planetary carrier 2-9, a right sun gear 2-10, a third brake B32-11, a right ring gear 2-12, a fifth clutch C52-13, a sixth clutch C62-14, a mechanical transmission output shaft 2-15 and a mechanical transmission output gear pair 2-16; the left planetary gear train includes a left sun gear 2-5, a left planetary carrier 2-6 and a left ring gear 2-8, the right planetary gear train includes a right planetary carrier 2-9, a right sun gear 2-10 and a right ring gear 2-12, the left sun gear 2-5 is connected to the right planetary carrier 2-6, and the right sun gear 2-10 is connected to the right ring gear 2-12. The positive gear 2-10 is connected, the right ring gear 2-12 is connected to the left planetary carrier 2-6; the fifth clutch C52-13 is used to connect the right ring gear 2-12 with the mechanical transmission output shaft 2-15, and the sixth clutch C62-14 is used to connect the right sun gear 2-10 with the mechanical transmission output shaft 2-15. The fifth clutch C52-13 and the sixth clutch C62-14 are engaged at the same time to fix the mechanical transmission mechanism 2 as a whole; the second brake B22-7 is used to connect the left ring gear 2-8 with the fixed part, and the third brake B32-11 is used to connect the right ring gear 2-12 with the fixed part.

[0077] The confluence mechanism 4 includes a left planetary gear train of the confluence mechanism, a right gear train of the confluence mechanism, a first brake B16-10, a fourth brake B44-6, a third clutch C32-2, a fourth clutch C42-4 and a seventh clutch C74-8; the left planetary gear train of the confluence mechanism includes a left planetary carrier 4-1 of the confluence mechanism, a left sun gear 4-2 of the confluence mechanism and a left ring gear 4-3 of the confluence mechanism; the right gear train of the confluence mechanism includes a right sun gear 4-4 of the confluence mechanism, a right planetary carrier 4-5 of the confluence mechanism and a right ring gear 4-7 of the confluence mechanism; the left sun gear 4-2 of the confluence mechanism is connected to the right sun gear 4-4 of the confluence mechanism, the left sun gear 4-2 of the confluence mechanism is connected to the intermediate shaft 5, and the left sun gear 4-2 of the confluence mechanism is connected to the output end of the hydraulic transmission mechanism 6; the left ring gear 4-3 of the confluence mechanism is connected to the right planetary carrier 4-5 of the confluence mechanism; the input Shaft 1 is connected to the left planetary carrier 4-1 of the confluence mechanism through the left gear pair 2-1 and the right gear pair 2-3 respectively; the right ring gear 4-7 of the confluence mechanism is connected to the mechanical transmission output shaft 2-15 through the mechanical transmission output gear pair 2-16, and the right planetary carrier 4-5 of the confluence mechanism is connected to the output shaft 3; the third clutch C32-2 is used to connect the input shaft 1 to the input end of the confluence mechanism 4 through the left gear pair 2-1, and the fourth clutch C42-4 is used to connect the input shaft 1 to the input end of the confluence mechanism 4 through the right gear pair 2-3; the seventh clutch C74-8 is used to connect the right sun gear 4-4 of the confluence mechanism to the right planetary carrier 4-5 of the confluence mechanism; the first brake B16-10 is used to connect the left sun gear 4-2 of the confluence mechanism to the fixed part, and the fourth brake B44-6 is used to connect the right ring gear 4-7 of the confluence mechanism to the fixed part.

[0078] The combined switching between the clutch and the brake realizes the switching of 14 forward and reverse gears in three modes: mechanical transmission, hydraulic transmission and mechanical-hydraulic combined transmission. The engagement status of the switching elements of each gear mode is shown in Table 1.

[0079] Table 1 Gear shift element engagement status

[0080]

[0081] In the table: C represents clutch, B represents brake; F represents reverse gear, R represents negative gear; H represents hydraulic transmission, M represents mechanical transmission, HM represents mechanical-hydraulic transmission; ▲ represents that the element is in the engaged state.

[0082] Engaging the third clutch C32-2, the fourth clutch C42-4, the fifth clutch C52-13, the sixth clutch C62-14, the first brake B16-10, the second brake B22-7 and the third brake B32-11 provides mechanical transmission of various gear ratios between the input member and the output member in forward or reverse direction.

[0083] Mechanical transmission F (M1) power flow is as follows Figure 2 As shown, only the fifth clutch C52-13, the sixth clutch C62-14 and the first brake B16-10 are engaged. The power is transmitted to the mechanical transmission output shaft 2-15 through the input shaft 1 and the mechanical transmission mechanism 2 which are fixedly connected as one, and then transmitted to the right gear ring 4-7 of the merging mechanism through the mechanical transmission output gear pair 2-16. The power is output from the output shaft 3 through the right planetary carrier 4-5 of the merging mechanism. The relationship between the output speed and the input speed is:

[0084]

[0085] Where n o is the speed of the output component, n I is the rotation speed of the input member; k4 is the characteristic parameter of the right gear train of the converging mechanism; i6i7 is the transmission ratio between the mechanical transmission output shaft 2-15 and the right gear ring 4-7 of the converging mechanism;

[0086] Mechanical transmission F (M2) power flow is as follows Figure 3 As shown, only the sixth clutch C62-14, the first brake B16-10 and the third brake B32-11 are engaged. The power is divided to the right planetary carrier 2-9 and the right sun gear 2-10 through the input shaft 1 and the left planetary carrier 2-6, and then converged to the mechanical transmission output shaft 2-15 through the right sun gear 2-10, and then transmitted to the right ring gear 4-7 of the converging mechanism through the mechanical transmission output gear pair 2-16. The power is output from the output shaft 3 through the right planetary carrier 4-5 of the converging mechanism. The relationship between the output speed and the input speed is:

[0087]

[0088] Wherein, k1 is the characteristic parameter of the left planetary gear train; k2 is the characteristic parameter of the right planetary gear train.

[0089] Mechanical transmission F (M3) power flow is as follows Figure 4 As shown, only the third clutch C32-2 and the seventh clutch C74-8 are engaged. The power is transmitted to the left planetary carrier 4-1 of the merging mechanism through the input shaft 1 and the left gear pair 2-1, and is output from the output shaft 3 through the merging mechanism 4 that is fixedly connected as one. The relationship between the output speed and the input speed is:

[0090]

[0091] In the formula, i3i4 is the 2-1 transmission ratio of the left gear pair;

[0092] Mechanical transmission F (M4) power flow is as follows Figure 5As shown, only the sixth clutch C62-14, the first brake B16-10 and the second brake B22-7 are engaged. The power is transmitted to the mechanical transmission output shaft 2-15 through the input shaft 1, the left planetary carrier 2-6, the left sun gear 2-5 and the right sun gear 2-10, and is transmitted to the right ring gear 4-7 of the merging mechanism through the mechanical transmission output gear pair 2-16. The power is output from the output shaft 3 through the right planetary carrier 4-5 of the merging mechanism. The relationship between the output speed and the input speed is:

[0093]

[0094] Mechanical transmission R (M1) power flow is as follows Figure 6 As shown, only the fifth clutch C52-13, the first brake B16-10 and the second brake B22-7 are engaged. The power is transmitted to the mechanical transmission output shaft 2-15 through the input shaft 1, the left planetary carrier 2-6, the left sun gear 2-5, the right sun gear 2-10 and the right ring gear 2-12, and is transmitted to the right ring gear 4-7 of the merging mechanism through the mechanical transmission output gear pair 2-16. The power is output from the output shaft 3 through the right planetary carrier 4-5 of the merging mechanism. The relationship between the output speed and the input speed is:

[0095]

[0096] Mechanical transmission R (M2) power flow is as follows Figure 7 As shown, only the fourth clutch C42-4 and the first brake B16-10 are engaged. The power is transmitted to the left planetary carrier 4-1 of the merging mechanism through the input shaft 1 and the left and right gear pairs 2-3, and is output from the output shaft 3 through the left ring gear 4-3 of the merging mechanism and the right planetary carrier 4-5 of the mechanism. The relationship between the output speed and the input speed is:

[0097]

[0098] Wherein, k3 is the characteristic parameter of the left gear train of the converging mechanism; i5 is the transmission ratio of the right gear pair 2-3.

[0099] By adjusting the displacement ratio of the hydraulic transmission assembly 6 and by engaging the first clutch C16-3, the second clutch C26-6, the seventh clutch C74-8 and the fourth brake B44-6, a hydraulic transmission with various gear ratios for forward or reverse movement between the input member and the output member is provided.

[0100] Hydraulic transmission F(H1) / R(H1) power flow as follows Figure 8As shown, only the first clutch C16-3, the second clutch C26-6 and the fourth brake B44-6 are engaged. The power is transmitted to the hydraulic transmission input shaft 6-2 through the input shaft 1 and the hydraulic transmission input gear pair 6-1 to drive the variable pump 6-4. The oil drives the quantitative motor 6-8 through the hydraulic pipeline 6-5, driving the hydraulic transmission output shaft 6-7. The power is output from the output shaft 3 through the hydraulic transmission output gear pair 6-9, the right sun gear 4-4 of the converging mechanism and the right planetary carrier 4-5 of the converging mechanism. The relationship between the output speed and the input speed is:

[0101]

[0102] Wherein, k4 is the characteristic parameter of the right gear train of the confluence mechanism; e is the displacement ratio of the hydraulic transmission mechanism 6; i1 is the transmission ratio between the input end of the hydraulic transmission mechanism 6 and the input member, and i2 is the transmission ratio between the output end of the hydraulic transmission mechanism 6 and the left sun gear 4-2 of the confluence mechanism; when e>0, it is F (H1) gear, and when e<0, it is R (H1) gear;

[0103] Hydraulic transmission F(H2) / R(H2) power flow as follows Fig. 9 As shown, only the first clutch C16-3, the second clutch C26-6 and the seventh clutch C74-8 are engaged. The power is transmitted to the hydraulic transmission input shaft 6-2 through the input shaft 1 and the hydraulic transmission input gear pair 6-1 to drive the variable pump 6-4. The oil drives the quantitative motor 6-8 through the hydraulic pipeline 6-5, driving the hydraulic transmission output shaft 6-7. The power is output from the output shaft 3 through the hydraulic transmission output gear pair 6-9 and the integrated confluence mechanism 4. The relationship between the output speed and the input speed is:

[0104]

[0105] In the formula, when e>0, it is F(H2), and when e<0, it is R(H2).

[0106] By adjusting the displacement ratio of the hydraulic transmission assembly 6 and by engaging the first clutch C16-3, the second clutch C26-6, the third clutch C32-2, the fourth clutch C42-4, the fifth clutch C52-13, the sixth clutch C62-14, the second brake B22-7 and the third brake B32-11, a hydraulic compound transmission with multiple gear ratios for forward or reverse movement between the input member and the output member is provided.

[0107] The power flow of the hydraulic transmission F (HM1) is as follows Fig.10As shown, only the first clutch C16-3, the second clutch C26-6, the fifth clutch C52-13 and the sixth clutch C62-14 are engaged. The power is split through the input shaft 1. One path is transmitted to the mechanical transmission output shaft 2-15 through the mechanical transmission mechanism 2 that is fixed as one, and then transmitted to the right ring gear 4-7 of the converging mechanism through the mechanical transmission output gear pair 2-16; the other path is transmitted to the right sun gear 4-4 of the converging mechanism through the hydraulic transmission mechanism 6. The mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after being merged by the right planetary carrier 4-5 of the converging mechanism. The relationship between the output speed and the input speed is:

[0108]

[0109] The power flow of the hydraulic transmission F (HM2) is as follows Fig.11 As shown, only the first clutch C16-3, the second clutch C26-6 and the third clutch C32-2 are engaged. The power is split through the input shaft 1, one way is transmitted to the left planetary carrier 4-1 of the merging mechanism through the left gear pair 2-1; the other way is transmitted to the left sun gear 4-2 of the merging mechanism through the hydraulic transmission mechanism 6. The mechanical power transmitted to the planetary carrier 4-1 and the hydraulic power transmitted to the left sun gear 4-2 are output from the output shaft 3 through the right planetary carrier 4-5 of the merging mechanism after merging at the left ring gear 4-3 of the merging mechanism. The relationship between the output speed and the input speed is:

[0110]

[0111] The power flow of the hydraulic transmission F (HM3) is as follows Fig.12 As shown, only the first clutch C16-3, the second clutch C26-6, the sixth clutch C62-14 and the third brake B32-11 are engaged. The power is split through the input shaft 1, one way is split through the left planetary carrier 2-6 to the right planetary carrier 2-9 and the right sun gear 2-10, and then converged to the mechanical transmission output shaft 2-15 through the right sun gear 2-10, and transmitted to the right ring gear 4-7 of the converging mechanism through the mechanical transmission output gear pair 2-16; the other way is transmitted to the right sun gear 4-4 of the converging mechanism through the hydraulic transmission mechanism 6. The mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after being converged by the right planetary carrier 4-5 of the converging mechanism. The relationship between the output speed and the input speed is:

[0112]

[0113] The power flow of the hydraulic transmission F (HM4) is as follows Fig.13As shown, only the first clutch C16-3, the second clutch C26-6, the sixth clutch C62-14 and the second brake B22-7 are engaged, and the power is split through the input shaft 1. One way is transmitted to the mechanical transmission output shaft 2-15 through the left planetary carrier 2-6, the left sun gear 2-5 and the right sun gear 2-10, and then transmitted to the right ring gear 4-7 of the converging mechanism through the mechanical transmission output gear pair 2-16; the other way is transmitted to the right sun gear 4-4 of the converging mechanism through the hydraulic transmission mechanism 6. The mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after being merged by the right planetary carrier 4-5 of the converging mechanism. The relationship between the output speed and the input speed is:

[0114]

[0115] The power flow of the hydraulic transmission R (HM1) is as follows Fig.14 As shown, only the first clutch C16-3, the second clutch C26-6, the fifth clutch C52-13, and the second brake B22-7 are engaged. The power is split through the input shaft 1, one way is transmitted to the mechanical transmission output shaft 2-15 through the left planetary carrier 2-6, the left sun gear 2-5, the right sun gear 2-10 and the right ring gear 2-12, and then transmitted to the right ring gear 4-7 of the converging mechanism through the mechanical transmission output gear pair 2-16; the other way is transmitted to the right sun gear 4-4 of the converging mechanism through the hydraulic transmission mechanism 6. The mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after being merged by the right planetary carrier 4-5 of the converging mechanism. The relationship between the output speed and the input speed is:

[0116]

[0117] The power flow of the hydraulic transmission RHM2 is as follows Fig.15 As shown, only the first clutch C16-3, the second clutch C26-6 and the fourth clutch C42-4 are engaged. The power is split through the input shaft 1, one way is transmitted to the left planetary carrier 4-1 of the merging mechanism through the right gear pair 2-3; the other way is transmitted to the left sun gear 4-2 of the merging mechanism through the hydraulic transmission mechanism 6. The mechanical power transmitted to the planetary carrier 4-1 and the hydraulic power transmitted to the left sun gear 4-2 are output from the output shaft 3 through the right planetary carrier 4-5 of the merging mechanism after merging at the left ring gear 4-3 of the merging mechanism. The relationship between the output speed and the input speed is:

[0118]

[0119] Example

[0120] The main parameters are set as follows: i1i2=1.00, i3i4=i5=i6i7=1.00, k1=k2=k4=2, k3=3.

[0121] Fig.16 The relationship between the ratio of the output speed to the input speed of the transmission and the displacement ratio is given, and the output shaft can be connected to the reduction device to drive the vehicle.

[0122] O is the origin;

[0123] (0, 0.67) is the characteristic point of the mechanical transmission F (M1) gear position, that is, n o =0.67n I ;

[0124] (0, 1.20) is the characteristic point of the mechanical transmission F (M2) gear position, that is, n o =1.20n I ;

[0125] (0, 1.33) is the characteristic point of the mechanical transmission F (M3) gear position, that is, n o =n I ;

[0126] (0, 2.00) is the characteristic point of the mechanical transmission F (M4) gear position, that is, n o =2.00n I ;

[0127] (0, -0.33) is the characteristic point of the mechanical transmission R (M1) gear position, that is, n o =-0.5n I ;

[0128] (0, -1.00) is the characteristic point of the mechanical transmission R (M2) gear position, that is, n o =-1.33n I ;

[0129] For H1 gear, When e∈[-1.00, 1.00], n o / n e ∈[-0.33, 0.33];

[0130] For H2 gear, n o =en I , when e∈[-1.00, 1.00], n o / n e ∈[-1.00, 1.00];

[0131] For F(HM1) gear, When e∈[-1.00, 1.00], n o / n e∈[0.33, 1.00];

[0132] For F(HM2) gear, When e∈[-1.00, 1.00], n o / n e ∈[1.00, 1.67];

[0133] For F(HM3) gear, When e∈[-1.00, 1.00], n o / n e ∈[0.87, 1.54];

[0134] For F(HM4) gear, When e∈[-1.00, 1.00], n o / n e ∈[1.67, 2.33];

[0135] For R (HM1) gear, When e∈[-1.00, 1.00], n o / n e ∈[-1.33,-0.67];

[0136] For R (HM2) gear, When e∈[-1.00, 1.00], n o / n e ∈[-1.67,-1.00];

[0137] When e=1.00, the F(H2) gear and the F(HM1) gear are switched without power interruption, and the characteristic point is (1.00, 1.00);

[0138] When e=1.00, the F(HM1) gear and the F(HM2) gear are switched without power interruption, and the characteristic point is (1.00, 1.00);

[0139] When e=0.20, the F(HM2) gear and the F(HM3) gear are switched without power interruption, and the characteristic point is (0.20, 1.27);

[0140] When e=-1.00, the F(HM2) gear and the F(HM4) gear are switched without power interruption, and the characteristic point is (-1.00, 1.67);

[0141] When e=-1.00, the F (H2) gear and the R (HM2) gear are switched without power interruption, (-1.00, -1.00).

[0142] When e=-0.50, the R(HM1) gear and the R(HM2) gear are switched without power interruption, and the characteristic point is (-0.50, -1.17);

[0143] When higher precision is required for hydraulic transmission, H1 gear is used to replace H2 gear, but H2 gear cannot switch to the hydraulic-hydraulic compound transmission gear without power interruption.

[0144] It should be understood that although this specification is described according to various embodiments, not every embodiment contains only one independent technical solution. This narrative method of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment may also be appropriately combined to form other implementation methods that can be understood by those skilled in the art.

[0145] The series of detailed descriptions listed above are only specific descriptions of feasible embodiments of the present invention. They are not intended to limit the scope of protection of the present invention. All equivalent embodiments or changes that do not deviate from the technical spirit of the present invention should be included in the scope of protection of the present invention.

Claims

1. A multi-mode hydraulic compound transmission device, characterized in that: The invention comprises an input member, a hydraulic transmission mechanism, a mechanical transmission mechanism, a confluence mechanism, an output member, a clutch assembly and a brake assembly; the clutch assembly connects the output end of the input mechanism with the input end of the hydraulic transmission mechanism, the mechanical transmission mechanism and the confluence mechanism respectively, the clutch assembly connects the output end of the hydraulic transmission mechanism with the confluence mechanism, and the clutch assembly connects the mechanical transmission mechanism with the confluence mechanism; the confluence mechanism is connected to the output member; a continuously variable transmission ratio between the input member and the output member is provided by adjusting the displacement ratio of the hydraulic transmission mechanism and by selectively controlling the engagement of the clutch assembly and the brake assembly; The mechanical transmission mechanism includes a mechanical transmission output shaft, a left planetary gear train and a right planetary gear train; the left planetary gear train includes a left sun gear, a left planetary carrier and a left ring gear, and the right planetary gear train includes a right planetary carrier, a right sun gear and a right ring gear. The left sun gear is connected to the right sun gear, and the right ring gear is connected to the left planetary carrier; the clutch assembly includes a fifth clutch C5, which is used to connect the right ring gear to the mechanical transmission output shaft. The sixth clutch C6 is used to connect the right sun gear to the mechanical transmission output shaft; The brake assembly includes a second brake B2, which is used to connect the left ring gear to the fixed member. The third brake B3 is used to connect the right ring gear to the fixed part; The confluence mechanism includes a left planetary gear train of the confluence mechanism and a right gear train of the confluence mechanism; the left planetary gear train of the confluence mechanism includes a left planet carrier of the confluence mechanism, a left sun gear of the confluence mechanism and a left ring gear of the confluence mechanism; the right gear train of the confluence mechanism includes a right sun gear of the confluence mechanism, a right planet carrier of the confluence mechanism and a right ring gear of the confluence mechanism; the left sun gear of the confluence mechanism is connected to the right sun gear of the confluence mechanism, and the left sun gear of the confluence mechanism is connected to the output end of the hydraulic transmission mechanism; the left ring gear of the confluence mechanism is connected to the right planet carrier of the confluence mechanism; the input member is connected to the left planet carrier of the confluence mechanism through a left gear pair and a right gear pair respectively; the right ring gear of the confluence mechanism is connected to the mechanical transmission output shaft through a mechanical transmission output gear pair, and the right planet carrier of the confluence mechanism is connected to the output member; The clutch assembly also includes a third clutch C3, which is used to connect the input member to the input end of the merging mechanism through the left gear pair. The fourth clutch C4 is used to connect the input member to the input end of the confluence mechanism through the right gear pair. The seventh clutch C7 is used to connect the right sun gear of the merging mechanism with the right planetary carrier of the merging mechanism; The brake assembly also includes a first brake B1, which is used to connect the left sun gear of the merging mechanism to the fixing member. The fourth brake B4 is used to connect the right ring gear of the merging mechanism with the fixing member.

2. The multi-mode hydraulic compound transmission device according to claim 1, characterized in that: The clutch assembly also includes a first clutch C1 (6-3) and a second clutch C2 (6-6), wherein the first clutch C1 (6-3) is used to connect the input member with the input end of the hydraulic transmission mechanism (6), and the second clutch C2 (6-6) is used to connect the output end of the hydraulic transmission mechanism (6) with the left sun gear (4-2) of the merging mechanism; by adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6), the seventh clutch C7 (4-8) and the fourth brake B4 (4-6), a hydraulic transmission with multiple transmission ratios for forward or reverse movement between the input member and the output member is provided.

3. The multi-mode hydraulic compound transmission device according to claim 2, characterized in that: By adjusting the displacement ratio of the hydraulic transmission mechanism (6) and selectively controlling the engagement of the clutch assembly and the brake assembly, the forward or backward transmission modes between the input member and the output member include: hydraulic transmission, mechanical transmission and mechanical-hydraulic compound transmission.

4. The multi-mode hydraulic compound transmission device according to claim 3, characterized in that: Engaging the third clutch C3 (2-2), the fourth clutch C4 (2-4), the fifth clutch C5 (2-13), the sixth clutch C6 (2-14), the first brake B1 (6-10), the second brake B2 (2-7) and the third brake B3 (2-11) provides a mechanical transmission with various gear ratios for forward or reverse movement between the input member and the output member.

5. The multi-mode hydraulic compound transmission device according to claim 4, characterized in that: The fifth clutch C5 (2-13), the sixth clutch C6 (2-14) and the first brake B1 (6-10) are engaged to provide a forward mechanical transmission F-M1 between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship: Where n o is the speed of the output component, n I is the rotation speed of the input member; k4 is the characteristic parameter of the right gear train of the converging mechanism; i6i7 is the transmission ratio between the mechanical transmission output shaft (2-15) and the right gear ring (4-7) of the converging mechanism; The sixth clutch C6 (2-14), the first brake B1 (6-10) and the third brake B3 (2-11) are engaged to provide a forward mechanical transmission F-M2 between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship: In the formula, k1 is the characteristic parameter of the left planetary gear train; k2 is the characteristic parameter of the right planetary gear train; The third clutch C3 (2-2) and the seventh clutch C7 (4-8) are engaged to provide a forward mechanical transmission F-M3 between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship: In the formula, i3i4 is the transmission ratio of the left gear pair (2-1); The sixth clutch C6 (2-14), the first brake B1 (6-10) and the second brake B2 (2-7) are engaged to provide a forward mechanical transmission F-M4 between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship: In combination with the fifth clutch C5 (2-13), the first brake B1 (6-10) and the second brake B2 (2-7), a reverse mechanical transmission R-M1 between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship: The fourth clutch C4 (2-4) and the first brake B1 (6-10) are engaged to provide a reverse mechanical transmission R-M2 between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship: Wherein, k3 is the characteristic parameter of the left gear train of the converging mechanism; i5 is the transmission ratio of the right gear pair (2-3).

6. The multi-mode hydraulic compound transmission device according to claim 5, characterized in that: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6) and the fourth brake B4 (4-6), a forward or reverse hydraulic transmission F-H1 / R-H1 between the input member and the output member is provided, and the rotation speeds of the input member and the output member in the hydraulic transmission F-H1 / R-H1 satisfy the following relationship: Wherein, k4 is the characteristic parameter of the right gear train of the converging mechanism; e is the displacement ratio of the hydraulic transmission mechanism (6); i1 is the transmission ratio between the input end of the hydraulic transmission mechanism (6) and the input member, and i2 is the transmission ratio between the output end of the hydraulic transmission mechanism (6) and the left sun gear (4-2) of the converging mechanism; when e>0, it is F-H1, and when e<0, it is R-H1; The first clutch C1 (6-3), the second clutch C2 (6-6) and the seventh clutch C7 (4-8) are engaged to provide a forward or reverse hydraulic transmission F-H2 / R-H2 between the input member and the output member, in which the rotation speeds of the input member and the output member satisfy the following relationship: In the formula, when e>0, it is F-H2, and when e<0, it is R-H2.

7. The multi-mode hydraulic compound transmission device according to claim 6, characterized in that: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6), the third clutch C3 (2-2), the fourth clutch C4 (2-4), the fifth clutch C5 (2-13), the sixth clutch C6 (2-14), the second brake B2 (2-7) and the third brake B3 (2-11), a hydraulic compound transmission with various forward or reverse gear ratios between the input member and the output member is provided.

8. The multi-mode hydraulic compound transmission device according to claim 7, characterized in that: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6), the fifth clutch C5 (2-13) and the sixth clutch C6 (2-14), a forward hydraulic compound transmission F-HM1 between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6) and the third clutch C3 (2-2), a forward hydraulic compound transmission F-HM2 between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6), the sixth clutch C6 (2-14) and the third brake B3 (2-11), a forward hydraulic compound transmission F-HM3 between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6), the sixth clutch C6 (2-14) and the second brake B2 (2-7), a forward hydraulic compound transmission F-HM4 between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6), the fifth clutch C5 (2-13), and the second brake B2 (2-7), a hydraulic compound transmission R-HM1 for reverse movement between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (6), by engaging the first clutch C1 (6-3), the second clutch C2 (6-6) and the fourth clutch C4 (2-4), a hydraulic compound transmission R-HM2 for reverse movement between the input member and the output member is provided, in which the rotation speeds of the input member and the output member satisfy the following relationship:

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