A mechanical-double-ring-hydraulic composite transmission mechanism

Abstract

The present invention provides a mechanical - double - ring - hydraulic compound transmission mechanism, which includes an input member, a current - collecting mechanism, a hydraulic transmission mechanism, a double - ring mechanism, an output member, a clutch assembly and a brake assembly; the clutch assembly connects the left planetary gear train and the right planetary gear train, the clutch assembly connects the input member to the hydraulic transmission mechanism, the double - ring mechanism, the left planetary gear train and the right planetary gear train respectively, the clutch assembly connects the hydraulic transmission mechanism to the right planetary gear train, the clutch assembly connects the double - ring mechanism to the left planetary gear train, and the clutch assembly connects the left planetary gear train and the right planetary gear train to the output member respectively; by adjusting the displacement ratio of the hydraulic transmission mechanism, adjusting the transmission ratio of the double - ring transmission mechanism and selectively controlling the engagement of the clutch assembly and the brake assembly, a continuous transmission ratio between the input member and the output member is provided. The present invention can realize the free switching of various transmission modes.

Description

Technical Field

[0001] The present invention relates to the field of variable speed transmission devices, and particularly to a mechanical-double-ring-hydraulic composite transmission device. Background Art

[0002] Mechanical transmission has high efficiency, but it is difficult to meet the requirements of stepless speed regulation; hydraulic transmission can meet the requirements of stepless speed regulation, but its efficiency and accuracy are relatively low; ring transmission has high efficiency and accuracy, but the range of transmission ratio adjustment is limited. Based on this, a variable speed transmission device that integrates multiple transmission methods and can adapt to different working conditions has good development prospects.

[0003] Compound transmission can carry forward the advantages of transmission and discard its disadvantages, becoming the development trend of variable speed transmission devices. Integrating multiple transmission methods into one and being able to freely combine into a compound transmission device will be the new trend in the design of variable speed transmission devices. Summary of the Invention

[0004] In view of the deficiencies in the prior art, the present invention provides a mechanical-double-ring-hydraulic composite transmission device, which integrates mechanical transmission, double-ring transmission, hydraulic transmission, mechanical-double-ring composite transmission, and mechanical-hydraulic composite transmission.

[0005] The present invention achieves the above technical objectives through the following technical means.

[0006] A mechanical-double-ring-hydraulic composite transmission mechanism includes an input member, a confluence mechanism, a hydraulic transmission mechanism, a double-ring mechanism, an output member, a clutch assembly, and a brake assembly; the confluence mechanism includes a left planetary gear train and a right planetary gear train, the clutch assembly connects the left planetary gear train and the right planetary gear train, the clutch assembly connects the input member to the hydraulic transmission mechanism, the double-ring mechanism, the left planetary gear train, and the right planetary gear train respectively, the clutch assembly connects the hydraulic transmission mechanism to the right planetary gear train, the clutch assembly connects the double-ring mechanism to the left planetary gear train, and the clutch assembly connects the left planetary gear train and the right planetary gear train to the output member respectively; by adjusting the displacement ratio of the hydraulic transmission mechanism, adjusting the transmission ratio of the double-ring transmission mechanism, and selectively controlling the engagement of the clutch assembly and the brake assembly, a continuous transmission ratio between the input member and the output member is provided.

[0007] Furthermore, by adjusting the displacement ratio of the hydraulic transmission mechanism, adjusting the transmission ratio of the double-ring transmission mechanism, and selectively controlling the engagement of the clutch assembly and the brake assembly, the transmission methods between the input member and the output member include: mechanical transmission, double-ring transmission, hydraulic transmission, mechanical-double-ring composite transmission, and mechanical-hydraulic composite transmission.

[0008] Further, the left planetary gear train includes a left ring gear, a left planet carrier, and a left sun gear; the right planetary gear train includes a right ring gear, a right planet carrier, and a right sun gear; the right ring gear is connected to the left planet carrier; the left sun gear is connected to the right sun gear;

[0009] The clutch assembly includes a fifth clutch C5, a sixth clutch C6, a seventh clutch C7, an eighth clutch C8, a ninth clutch C9, a tenth clutch C 10 and an eleventh clutch C 11 , the fifth clutch C5 is used to selectively connect the input member to the left planet carrier; the sixth clutch C6 is used to selectively connect the input member to the right sun gear; the seventh clutch C7 and the eighth clutch C8 are used to selectively connect the left ring gear to the output member with different speed ratios; the ninth clutch C9 and the tenth clutch C 10 are used to selectively connect the right planet carrier to the output member with different speed ratios; the eleventh clutch C 11 is used to selectively connect the left planet carrier to the left sun gear;

[0010] The brake assembly includes a first brake B1, a second brake B2, and a third brake B3; the first brake B1 is used to selectively connect the left ring gear to a fixed member; the second brake B2 is used to selectively connect the right ring gear to a fixed member; the third brake B3 is used to selectively connect the left planet carrier to a fixed member;

[0011] By engaging the fifth clutch C5, the seventh clutch C7, and the eleventh clutch C 11 , a mechanical transmission M1 in the forward direction between the input member and the output member is provided, and in the mechanical transmission M1, the rotational speeds of the input member and the output member satisfy the following relationship:

[0012]

[0013] wherein, n o is the rotational speed of the output member, n I is the rotational speed of the input member; i5 is the transmission ratio between the input member and the left planet carrier, and i7 is the transmission ratio between the left ring gear and the output member;

[0014] By engaging the fifth clutch C5, the eighth clutch C8, and the eleventh clutch C 11 , a mechanical transmission M2 in the reverse direction between the input member and the output member is provided, and in the mechanical transmission M2, the rotational speeds of the input member and the output member satisfy the following relationship:

[0015]

[0016] Wherein, i8i9 is the transmission ratio between the left gear ring and the output member.

[0017] Furthermore, the clutch assembly further includes a first clutch C1 and a second clutch C2; the first clutch C1 is used to selectively connect the input member to the input end of the double-ring mechanism; the second clutch C2 is used to selectively connect the output end of the double-ring mechanism to the left planet carrier;

[0018] By adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the ninth clutch C9 and the first brake B1, a reverse-direction double-ring transmission T1 between the input member and the output member is provided, and in the double-ring transmission T1, the rotational speeds of the input member and the output member satisfy the following relationship:

[0019]

[0020] Wherein: k1 is the planetary gear characteristic parameter of the left planetary gear train, k2 is the planetary gear characteristic parameter of the right planetary gear train, i1 is the transmission ratio between the input member and the input end of the double-ring mechanism, i2 is the transmission ratio between the output end of the double-ring mechanism and the left planet carrier, i 10 is the transmission ratio between the right planet carrier and the output member, i T1 i T2 is the transmission ratio of the double-ring mechanism;

[0021] By adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the eleventh clutch C 11 and the ninth clutch C9, a reverse-direction double-ring transmission T3 between the input member and the output member is provided, and in the double-ring transmission T3, the rotational speeds of the input member and the output member satisfy the following relationship:

[0022]

[0023] By adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the first brake B1 and the tenth clutch C 10 , a forward-direction double-ring transmission T2 between the input member and the output member is provided, and in the double-ring transmission T2, the rotational speeds of the input member and the output member satisfy the following relationship:

[0024]

[0025] Wherein, i 11 i 12 is the transmission ratio between the right planet carrier and the output member;

[0026] By adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the tenth clutch C 10 and the eleventh clutch C 11 , a double-ring transmission T4 in the forward direction between the input member and the output member is provided. In the double-ring transmission T4, the rotational speeds of the input member and the output member satisfy the following relationship:

[0027]

[0028] Furthermore, the clutch assembly further includes a third clutch C3 and a fourth clutch C4. The third clutch C3 connects the input member to the input end of the hydraulic transmission mechanism; the fourth clutch C4 connects the output end of the hydraulic transmission mechanism to the right sun gear;

[0029] By adjusting the displacement ratio of the hydraulic transmission mechanism, by engaging the third clutch C3, the fourth clutch C4, the ninth clutch C9, the second brake B2 and the third brake B3, a hydraulic transmission H1 in the reverse direction between the input member and the output member is provided. In the hydraulic transmission H1, the rotational speeds of the input member and the output member satisfy the following relationship:

[0030]

[0031] In the formula: e is the displacement ratio of the hydraulic transmission mechanism, i3 is the transmission ratio between the input member and the input end of the hydraulic transmission mechanism, and i4 is the transmission ratio between the output end of the hydraulic transmission mechanism and the right sun gear;

[0032] By adjusting the displacement ratio of the hydraulic transmission mechanism, by engaging the third clutch C3, the fourth clutch C4, the ninth clutch C9 and the eleventh clutch C 11 , a hydraulic transmission H3 in the reverse direction between the input member and the output member is provided. In the hydraulic transmission H3, the rotational speeds of the input member and the output member satisfy the following relationship:

[0033]

[0034] By adjusting the displacement ratio of the hydraulic transmission mechanism, by engaging the third clutch C3, the fourth clutch C4, the tenth clutch C 10 , the second brake B2 and the third brake B3, a hydraulic transmission H2 in the forward direction between the input member and the output member is provided. In the hydraulic transmission H2, the rotational speeds of the input member and the output member satisfy the following relationship:

[0035]

[0036] By adjusting the displacement ratio of the hydraulic transmission mechanism, by engaging the third clutch C3, the fourth clutch C4, the tenth clutch C10 and the eleventh clutch C 11 , a hydraulic drive H4 in the forward direction between the input member and the output member is provided, and in the hydraulic drive H4, the rotational speeds of the input member and the output member satisfy the following relationship:

[0037]

[0038] Furthermore, by adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the sixth clutch C6 and the seventh clutch C7, a mechanical-double-ring compound drive MT1 in the reverse direction between the input member and the output member is provided, and in the mechanical-double-ring compound drive MT1, the rotational speeds of the input member and the output member satisfy the following relationship:

[0039]

[0040] By adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the sixth clutch C6 and the ninth clutch C9, a mechanical-double-ring compound drive MT3 in the reverse direction between the input member and the output member is provided, and in the mechanical-double-ring compound drive MT3, the rotational speeds of the input member and the output member satisfy the following relationship:

[0041]

[0042] By adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the sixth clutch C6 and the eighth clutch C8, a mechanical-double-ring compound drive MT2 in the forward direction between the input member and the output member is provided, and in the mechanical-double-ring compound drive MT2, the rotational speeds of the input member and the output member satisfy the following relationship:

[0043]

[0044] By adjusting the transmission ratio of the double-ring mechanism, by engaging the first clutch C1, the second clutch C2, the sixth clutch C6 and the tenth clutch C 10 , a mechanical-double-ring compound drive MT4 in the forward direction between the input member and the output member is provided, and in the mechanical-double-ring compound drive MT4, the rotational speeds of the input member and the output member satisfy the following relationship:

[0045]

[0046] Further, by adjusting the displacement ratio of the hydraulic transmission mechanism and engaging the third clutch C3, fourth clutch C4, fifth clutch C5, and seventh clutch C7, a mechanical-hydraulic compound drive MH1 in the forward direction between the input member and the output member is provided, and in the mechanical-hydraulic compound drive MH1, the rotational speeds of the input member and the output member satisfy the following relationship:

[0047]

[0048] By adjusting the displacement ratio of the hydraulic transmission mechanism and engaging the third clutch C3, fourth clutch C4, fifth clutch C5, and ninth clutch C9, a mechanical-hydraulic compound drive MH3 in the forward direction between the input member and the output member is provided, and in the mechanical-hydraulic compound drive MH3, the rotational speeds of the input member and the output member satisfy the following relationship:

[0049]

[0050] By adjusting the displacement ratio of the hydraulic transmission mechanism and engaging the third clutch C3, fourth clutch C4, fifth clutch C5, and eighth clutch C8, a mechanical-hydraulic compound drive MH2 in the reverse direction between the input member and the output member is provided, and in the mechanical-hydraulic compound drive MH2, the rotational speeds of the input member and the output member satisfy the following relationship:

[0051]

[0052] By adjusting the displacement ratio of the hydraulic transmission mechanism and engaging the third clutch C3, fourth clutch C4, fifth clutch C5, and tenth clutch C 10 , a mechanical-hydraulic compound drive MH4 in the reverse direction between the input member and the output member is provided, and in the mechanical-hydraulic compound drive MH4, the rotational speeds of the input member and the output member satisfy the following relationship:

[0053]

[0054] Further, by adjusting the displacement ratio of the hydraulic transmission mechanism, adjusting the transmission ratio of the double-ring transmission mechanism, and selectively controlling the engagement of the clutch assembly and the brake assembly, a hydraulic start-up H4 is adopted, and the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the hydraulic transmission H4 reaches the positive maximum value;

[0055] When satisfying e·i T ∈[n o (H4) = n o (T4)], and e ∈ [0, 1], and When within the determined transmission ratio range, the hydraulic transmission H4 can be synchronously switched to the double-ring transmission T4. When the transmission ratio of the double-ring speed change mechanism changes from the maximum value to the minimum value, n o (T4) increases non-linearly; when e·i T ∈[n o (T4) = n o (T2)], and when within the determined transmission ratio range, the double-ring transmission T2 can be synchronously switched to the double-ring transmission T4. When the transmission ratio i of the double-ring speed change mechanism T changes from the maximum value to the minimum value, n o (T4) increases non-linearly;

[0056] Start and reverse using the hydraulic transmission H3. The output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = -1, the hydraulic transmission H3 reaches the negative maximum value; when e·i T ∈[n o (H3) = n o (T3)], and e ∈ [0, 1], and when within the determined transmission ratio range, the hydraulic transmission H3 can be synchronously switched to the double-ring transmission T3. When the transmission ratio of the double-ring speed change mechanism changes from the maximum value to the minimum value, n o (T3) increases non-linearly;

[0057] Use the double-ring transmission T1 to reverse. The output speed increases linearly with the increase of the transmission ratio i of the double-ring speed change mechanism T . When , the double-ring transmission T1 reaches the negative maximum value; when e·i T ∈[n o (T3) = n o (T1)], and when within the determined transmission ratio range, the double-ring transmission T1 can be synchronously switched to the double-ring transmission T3. When the transmission ratio of the double-ring speed change mechanism changes from the maximum value to the minimum value, n o (T4) increases non-linearly.

[0058] Furthermore, by adjusting the displacement ratio of the hydraulic transmission mechanism, adjusting the transmission ratio of the double-ring transmission mechanism, and selectively controlling the engagement of the clutch assembly and the brake assembly,

[0059] Advance using the mechanical - hydraulic compound drive MH1, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the mechanical - hydraulic compound drive MH1 reaches the positive maximum value; Advance using the mechanical - double - ring compound drive MT2, the output speed increases non - linearly with the increase of i T ; When e·i T ∈[n o (MT2) = n o (MH3)], and e ∈ [0, 1], and within the determined transmission ratio range, the mechanical - double - ring compound drive MT2 can be synchronously switched to the mechanical - hydraulic compound drive MH3. When the displacement ratio e of the hydraulic drive mechanism changes from the maximum value to the minimum value, n o (MH3) increases linearly;

[0060] When e·i T ∈[n o (MT4) = n o (MH3)], and e ∈ [0, 1], within the determined transmission ratio range, the mechanical - hydraulic compound drive MH3 can be synchronously switched to the mechanical - double - ring compound drive MT4, and the output speed decreases non - linearly with the increase of the transmission ratio i of the double - ring speed - changing mechanism T ;

[0061] Retreat using the mechanical - hydraulic compound drive MH2, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the mechanical - hydraulic compound drive MH2 reaches the negative maximum value; Retreat using the mechanical - double - ring compound drive MT1, the output speed increases non - linearly with the increase of ; When e·i T ∈[n o (MT1) = n o (MH4)], and e ∈ [0, 1], and within the determined transmission ratio range, the mechanical - double - ring compound drive MT1 can be synchronously switched to the mechanical - hydraulic compound drive MH4; When the displacement ratio e of the hydraulic drive mechanism changes from the maximum value to the minimum value, n o (MH4) increases linearly; When e·i T ∈[n o (MT3) = n o (MH4)], and e ∈ [0, 1], and within the determined transmission ratio range, the mechanical - hydraulic compound drive MH4 can be synchronously switched to the mechanical - double - ring compound drive MT3, and the output speed decreases non - linearly with the increase of the transmission ratio of the double - ring speed - changing mechanism.

[0062] The beneficial effects of the present invention are as follows:

[0063] 1. For the mechanical - double - ring - hydraulic compound transmission device of the present invention, the double - ring transmission is formed by connecting the front - ring transmission mechanism and the rear - ring transmission mechanism in series, which increases the adjustment range of the transmission ratio and improves the adjustment accuracy and freedom degree.

[0064] 2. The mechanical - double - ring - hydraulic compound transmission device of the present invention is a device integrating mechanical transmission, double - ring transmission, hydraulic transmission, mechanical - double - ring compound transmission, and mechanical - hydraulic compound transmission.

[0065] 3. The mechanical - double - ring - hydraulic compound transmission device of the present invention can realize the free switching of various transmission modes. BRIEF DESCRIPTION OF THE DRAWINGS

[0066] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or in the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0067] Figure 1 It is the structural schematic diagram of the mechanical - double - ring - hydraulic compound transmission device of the present invention.

[0068] Figure 2 It is the schematic diagram of the power flow of the mechanical transmission M1 of the present invention.

[0069] Figure 3 It is the schematic diagram of the power flow of the mechanical transmission M2 of the present invention.

[0070] Figure 4 It is the schematic diagram of the power flow of the double - ring transmission T1 of the present invention.

[0071] Figure 5 It is the schematic diagram of the power flow of the double - ring transmission T2 of the present invention.

[0072] Figure 6 It is the schematic diagram of the power flow of the double - ring transmission T3 of the present invention.

[0073] Figure 7 It is the schematic diagram of the power flow of the double - ring transmission T4 of the present invention.

[0074] Figure 8 It is the schematic diagram of the power flow of the hydraulic transmission H1 of the present invention.

[0075] Figure 9 It is the schematic diagram of the power flow of the hydraulic transmission H2 of the present invention.

[0076] Figure 10 Schematic diagram of the H3 power flow of the hydraulic transmission according to the present invention.

[0077] Figure 11 Schematic diagram of the H4 power flow of the hydraulic transmission according to the present invention.

[0078] Figure 12 Schematic diagram of the MT1 power flow of the mechanical - double - ring transmission according to the present invention.

[0079] Figure 13 Schematic diagram of the MT2 power flow of the mechanical - double - ring transmission according to the present invention.

[0080] Figure 14 Schematic diagram of the MT3 power flow of the mechanical - double - ring transmission according to the present invention.

[0081] Figure 15 Schematic diagram of the MT4 power flow of the mechanical - double - ring transmission according to the present invention.

[0082] Figure 16 Schematic diagram of the MH1 power flow of the mechanical - hydraulic transmission according to the present invention.

[0083] Figure 17 Schematic diagram of the MH2 power flow of the mechanical - hydraulic transmission according to the present invention.

[0084] Figure 18 Schematic diagram of the MH3 power flow of the mechanical - hydraulic transmission according to the present invention.

[0085] Figure 19 Schematic diagram of the MH4 power flow of the mechanical - hydraulic transmission according to the present invention.

[0086] Figure 20 Diagram showing the relationship between the output speed and the input speed of the transmission according to the present invention.

[0087] Figure 21 Diagram showing the relationship between the output speed and the input speed of the compound transmission according to the present invention.

[0088] In the figure:

[0089] 1 - Input shaft; 2 - Mechanical transmission mechanism; 3 - Confluence mechanism; 4 - Hydraulic transmission mechanism; 5 - Double-ring mechanism; 6 - Output shaft; 201 - Left gear pair of mechanical transmission; 202 - Fifth clutch C5; 203 - Right gear pair of mechanical transmission; 204 - Sixth clutch C6; 301 - Left planet carrier shaft; 302 - Left ring gear; 303 - First brake B1; 304 - Left planet carrier; 305 - Left sun gear; 306 - Second brake B2; 307 - Right ring gear; 308 - Right sun gear; 309 - Right planet carrier; 310 - Right sun gear shaft; 311 - Seventh clutch C7; 312 - First confluence output gear pair; 313 - Eighth clutch C8; 314 - Second confluence output gear pair; 315 - Eleventh clutch C 11 ; 316 - Third confluence output gear pair; 317 - Ninth clutch C9; 318 - Fourth confluence output gear pair; 319 - Tenth clutch C 10 ; 401 - Hydraulic transmission input gear pair; 402 - Third clutch C3; 403 - Hydraulic pump input shaft; 404 - Pump control motor mechanism; 405 - Hydraulic transmission output gear pair; 406 - Fourth clutch C4; 407 - Hydraulic motor output shaft; 501 - Double-ring output gear pair; 502 - Second clutch C2; 503 - Double-ring output shaft; 504 - Ring mechanism; 505 - Third brake B3; 506 - Double-ring input shaft; 507 - First clutch C1; 508 - Double-ring input gear pair. Detailed implementation manners

[0090] 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.

[0091] The embodiments of the present invention will be described in detail below. The examples of the embodiments are shown in the accompanying drawings, in which the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions from beginning to end. 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.

[0092] In the description of the present invention, it should be understood that the orientation or positional relationships indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "axial", "radial", "vertical", "horizontal", "inner", "outer", etc. are based on the orientation or positional relationships shown in the 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 thus 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, "a plurality" means two or more unless otherwise specifically defined.

[0093] 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.

[0094] As Figure 1 shown, the mechanical - double - ring - hydraulic compound transmission device of the present invention includes an input shaft 1, a mechanical transmission mechanism 2, a confluence mechanism 3, a hydraulic transmission mechanism 4, a double - ring mechanism 5, an output shaft 6, a clutch assembly, and a brake assembly.

[0095] The mechanical transmission mechanism 2 includes a mechanical transmission left gear pair 201, a fifth clutch C5 202, a mechanical transmission right gear pair 203, and a sixth clutch C6 204; the confluence mechanism 3 includes a left planet carrier shaft 301, a left ring gear 302, a first brake B1 303, a left planet carrier 304, a left sun gear 305, a second brake B2 306, a third brake B3 505, a right ring gear 307, a right sun gear 308, a right planet carrier 309, a right sun gear shaft 310, a seventh clutch C7 311, a first confluence output gear pair 312, an eighth clutch C8 313, a second confluence output gear pair 314, an eleventh clutch C 11 315, a third confluence output gear pair 316, a ninth clutch C9 317, a fourth confluence output gear pair 318, a tenth clutch C 10 319; the right ring gear 307 is connected to the left planet carrier 304; the left sun gear 305 is connected to the right sun gear 308;

[0096] The fifth clutch C5202 is used to selectively connect the input shaft 1 to the left planet carrier shaft 301 of the left planet carrier 304 through the mechanical transmission left gear pair 201; the sixth clutch C6204 is used to selectively connect the input shaft 1 to the right sun gear shaft 310 of the right sun gear 308 through the mechanical transmission right gear pair 203; the seventh clutch C7311 is used to selectively connect the left ring gear 302 to the output shaft 6 through the first confluence output gear pair 312; the eighth clutch C8313 is used to selectively connect the left ring gear 302 to the output shaft 6 through the second confluence output gear pair 314; the ninth clutch C9317 is used to selectively connect the right planet carrier 309 to the output shaft 6 through the third confluence output gear pair 316; the tenth clutch C 10 319 is used to selectively connect the right planet carrier 309 to the output shaft 6 through the fourth confluence output gear pair 318; the eleventh clutch C 11 315 is used to selectively connect the left planet carrier 304 to the left sun gear 305. The first brake B1303 is used to selectively connect the left ring gear 302 to the fixing member; the second brake B2307 is used to selectively connect the right ring gear 307 to the fixing member; the third brake B3505 is used to selectively connect the left planet carrier 304 to the fixing member.

[0097] The hydraulic transmission mechanism 4 includes a hydraulic transmission input gear pair 401, a third clutch C3402, a hydraulic pump input shaft 403, a hydraulic transmission output gear pair 405, a fourth clutch C4406, and a hydraulic motor output shaft 407;

[0098] The third clutch C3402 connects the input shaft 1 to the hydraulic pump input shaft 403 through the hydraulic transmission input gear pair 401; the fourth clutch C4406 connects the hydraulic motor output shaft 407 to the right sun gear 308 through the hydraulic transmission output gear pair 405.

[0099] The double-ring transmission mechanism 5 includes a double-ring output gear pair 501, a second clutch C2502, a double-ring output shaft 503, a ring mechanism 504, a double-ring input shaft 506, a first clutch C1507, and a double-ring input gear pair 508; the first clutch C1507 is used to connect the double-ring input shaft 506 and the input shaft 1, and the second clutch C2502 is used to connect the double-ring output gear pair 501 and the double-ring output shaft 503.

[0100] By adjusting the transmission ratio of the double-ring mechanism 5, the displacement ratio of the hydraulic transmission mechanism 4, and selectively controlling the engagement of the clutch assembly and the brake assembly, the transmission modes between the input shaft 1 and the output shaft 6 include: mechanical transmission, double-ring transmission, hydraulic transmission, mechanical-double-ring compound transmission, and mechanical-hydraulic compound transmission. The engaging elements of each transmission mode are shown in Table 1. Specifically as follows:

[0101] Table 1 Engagement status of mode switching elements

[0102]

[0103]

[0104] Among them: ▲ represents that the actuator is in the engaged state, and △ represents that the actuator is in the disengaged state; n0(M1) is the output speed of the mechanical transmission M1, n0(M2) is the output speed of the mechanical transmission M2, n0(T1) is the output speed of the double-ring transmission T1, n0(T2) is the output speed of the double-ring transmission T2, n0(T3) is the output speed of the double-ring transmission T3, n0(T4) is the output speed of the double-ring transmission T4, n0(H1) is the output speed of the hydraulic transmission H1, n0(H2) is the output speed of the hydraulic transmission H2, n0(H3) is the output speed of the hydraulic transmission H3, n0(H4) is the output speed of the hydraulic transmission H4, n0(MT1) is the output speed of the mechanical-double-ring transmission MT1, n0(MT2) is the output speed of the mechanical-double-ring transmission MT2, n0(MT3) is the output speed of the mechanical-double-ring transmission MT3, n0(MT4) is the output speed of the mechanical-double-ring transmission MT4, n0(MH1) is the output speed of the mechanical-hydraulic transmission MH1, n0(MH2) is the output speed of the mechanical-hydraulic transmission MH2, n0(MH3) is the output speed of the mechanical-hydraulic transmission MH3, n0(MH4) is the output speed of the mechanical-hydraulic transmission MH4, n I is the engine speed, k1 is the planetary gear characteristic parameter of the left planetary gear mechanism of the confluence mechanism, k2 is the planetary gear characteristic parameter of the right planetary gear mechanism of the confluence mechanism, i1 is the transmission ratio of the double-ring input gear pair 508, i2 is the transmission ratio of the double-ring output gear pair 501, i3 is the transmission ratio of the hydraulic transmission input gear pair 401, i4 is the transmission ratio of the hydraulic transmission output gear pair 404, i5 is the transmission ratio of the left gear pair 201 of the mechanical transmission, i6 is the transmission ratio of the right gear pair 203 of the mechanical transmission, i7 is the transmission ratio of the first confluence output gear pair 312, i8i9 is the transmission ratio of the second confluence output gear pair 314, i 10 is the transmission ratio of the third confluence output gear pair 316, i 11 i 12 is the transmission ratio of the fourth confluence output gear pair 318, i T1 iT2 is the transmission ratio of the ring mechanism 504, and e is the displacement ratio of the hydraulic transmission mechanism.

[0105] The mechanical transmission M1 is transmitted as Figure 2 shown, only the fifth clutch C5202, the seventh clutch C7311 and the eleventh clutch C 11 315 are engaged. At this time, the engine power transmitted by the input shaft 1 drives the left planet carrier 304 through the mechanical transmission left gear pair 201 and the fifth clutch C5202. At this time, the left and right planetary gears of the confluence mechanism 3 are fixedly connected as a whole, and the power is transmitted to the first confluence output gear pair 312 and then transmitted to the output shaft 6 through the seventh clutch C7311, and the power is output from the output shaft 6.

[0106] The mechanical transmission M2 is transmitted as Figure 3 shown, only the fifth clutch C5202, the eighth clutch C8313 and the eleventh clutch C 11 315 are engaged. At this time, the engine power transmitted by the input shaft 1 drives the left planet carrier 304 through the mechanical transmission left gear pair 201 and the fifth clutch C5202. At this time, the left and right planetary gears of the confluence mechanism 3 are fixedly connected as a whole, and the power is transmitted to the second confluence output gear pair 314 and then transmitted to the output shaft 6 through the eighth clutch C8313, and the power is output from the output shaft 6.

[0107] The double-ring transmission T1 is transmitted as Figure 4 shown, only the first clutch C1507, the second clutch C2502, the ninth clutch C9317 and the first brake B1303 are engaged. At this time, the engine power transmitted by the input shaft 1 drives the left planet carrier 304 of the confluence mechanism 3 through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501 and the second clutch C2502, and then through the right ring gear 307, the right planet carrier 309 and the third confluence output gear pair 316 and is transmitted to the output shaft 6 through the ninth clutch C9317, and the power is output from the output shaft 6.

[0108] The double-ring transmission T2 is transmitted as Figure 5 shown, only the first clutch C1507, the second clutch C2502, the tenth clutch C 10 319 and the first brake B1303 are engaged. At this time, the engine power transmitted by the input shaft 1 drives the left planet carrier 304 of the confluence mechanism 3 through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501 and the second clutch C2502, and then through the right ring gear 307, the right planet carrier 309 and the fourth confluence output gear pair 318 and is transmitted to the output shaft 6 through the tenth clutch C 10 319, and the power is output from the output shaft 6.

[0109] The double-ring drive T3 transmission is as follows Figure 6 shown. Only the first clutch C1507, the second clutch C2502, the ninth clutch C9317, and the eleventh clutch C 11 315 are engaged. At this time, the engine power transmitted by the input shaft 1 passes through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501, and the second clutch C2502 to drive the left planet carrier 304 of the confluence mechanism 3. At this time, the left and right planetary gears of the confluence mechanism 3 are fixedly connected as a whole, and the power is transmitted through the confluence mechanism 3 to the third confluence output gear pair 316 and then through the ninth clutch C9317 to the output shaft 6, and the power is output from the output shaft 6.

[0110] The double-ring drive T4 transmission is as follows Figure 7 shown. Only the first clutch C1507, the second clutch C2502, the tenth clutch C 10 319, and the eleventh clutch C 11 315 are engaged. At this time, the engine power transmitted by the input shaft 1 passes through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501, and the second clutch C2502 to drive the left planet carrier 304 of the confluence mechanism 3. At this time, the left and right planetary gears of the confluence mechanism 3 are fixedly connected as a whole, and the power is transmitted through the confluence mechanism 3 to the fourth confluence output gear pair 318 and then through the tenth clutch C 10 319 to the output shaft 6, and the power is output from the output shaft 6.

[0111] The hydraulic drive H1 transmission is as follows Figure 8 shown. Only the third clutch C3402, the fourth clutch C4405, the ninth clutch C9317, the second brake B2306, and the third brake B3505 are engaged. At this time, the engine power transmitted by the input shaft 1 passes through the hydraulic drive input gear pair 401, the third clutch C3402, the hydraulic drive input shaft 403, the pump-controlled motor mechanism 404, the hydraulic drive output shaft 407, the fourth clutch C4406, and the hydraulic drive output gear pair 405 to drive the right sun gear shaft 310, and then through the right sun gear 308, the right planet carrier 309 of the confluence mechanism 3, and the third confluence output gear pair 316 and through the ninth clutch C9317 to the output shaft 6, and the power is output from the output shaft 6.

[0112] The hydraulic drive H2 transmission is as follows Figure 9 shown. Only the third clutch C3402, the fourth clutch C4405, the tenth clutch C 10319, the second brake B2306 and the third brake B3505. At this time, the engine power transmitted by the input shaft 1 passes through the hydraulic transmission input gear pair 401, the third clutch C3402, the hydraulic transmission input shaft 403, the pump-controlled motor mechanism 404, the hydraulic transmission output shaft 407, the fourth clutch C4406, and the hydraulic transmission output gear pair 405 to drive the right sun gear shaft 310. Then, through the right sun gear 308, the right planet carrier 309 of the confluence mechanism 3 and the fourth confluence output gear pair 318, it is transmitted to the output shaft 6 through the tenth clutch C 10 319, and the power is output from the output shaft 6.

[0113] The hydraulic transmission H3 is as follows Figure 10 shown. Only the third clutch C3402, the fourth clutch C4405, the ninth clutch C9317, and the eleventh clutch C 11 315 are engaged. At this time, the engine power transmitted by the input shaft 1 passes through the hydraulic transmission input gear pair 401, the third clutch C3402, the hydraulic transmission input shaft 403, the pump-controlled motor mechanism 404, the hydraulic transmission output shaft 407, the fourth clutch C4406, and the hydraulic transmission output gear pair 405 to drive the right sun gear shaft 310. At this time, the left and right planetary gears of the confluence mechanism 3 are fixedly connected as a whole, and the power is transmitted to the third confluence output gear pair 316 through the confluence mechanism 3 and then transmitted to the output shaft 6 through the ninth clutch C9317, and the power is output from the output shaft 6.

[0114] The hydraulic transmission H4 is as follows Figure 11 shown. Only the third clutch C3402, the fourth clutch C4405, the tenth clutch C 10 319, and the eleventh clutch C 11 315 are engaged. At this time, the engine power transmitted by the input shaft 1 passes through the hydraulic transmission input gear pair 401, the third clutch C3402, the hydraulic transmission input shaft 403, the pump-controlled motor mechanism 404, the hydraulic transmission output shaft 407, the fourth clutch C4406, and the hydraulic transmission output gear pair 405 to drive the right sun gear shaft 310. At this time, the left and right planetary gears of the confluence mechanism 3 are fixedly connected as a whole, and the power is transmitted to the fourth confluence output gear pair 318 through the confluence mechanism 3 and then transmitted to the output shaft 6 through the tenth clutch C 10 319, and the power is output from the output shaft 6.

[0115] The mechanical-double-ring MT1 compound transmission is as follows Figure 12As shown, only the first clutch C1507, the second clutch C2502, the sixth clutch C6204, and the seventh clutch C7311 are engaged. At this time, the power transmitted by the engine through the input shaft 1 is transmitted in two paths: one path drives the left planet carrier 304 of the confluence mechanism 3 through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501, and the second clutch C2502; the other path drives the left sun gear 305 through the mechanical transmission right gear pair 203 and the sixth clutch C6204. After the two paths of power converge at the left ring gear 302, they are transmitted to the output shaft 6 through the first confluence output gear pair 312 and the seventh clutch C7311, and the power is output from the output shaft 6.

[0116] The mechanical-double-ring MT2 compound transmission is as Figure 13 As shown, only the first clutch C1507, the second clutch C2502, the sixth clutch C6204, and the eighth clutch C8313 are engaged. At this time, the power transmitted by the engine through the input shaft 1 is transmitted in two paths: one path drives the left planet carrier 304 of the confluence mechanism 3 through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501, and the second clutch C2502; the other path drives the left sun gear 305 through the mechanical transmission right gear pair 203 and the sixth clutch C6204. After the two paths of power converge at the left ring gear 302, they are transmitted to the output shaft 6 through the second confluence output gear pair 314 and the eighth clutch C8313, and the power is output from the output shaft 6.

[0117] The mechanical-double-ring MT3 compound transmission is as Figure 14 As shown, only the first clutch C1507, the second clutch C2502, the sixth clutch C6204, and the ninth clutch C9317 are engaged. At this time, the power transmitted by the engine through the input shaft 1 is transmitted in two paths: one path drives the left planet carrier 304 of the confluence mechanism 3 through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501, and the second clutch C2502; the other path drives the right sun gear 308 through the mechanical transmission right gear pair 203 and the sixth clutch C6204. After the two paths of power converge at the right planet carrier 309, they are transmitted to the output shaft 6 through the third confluence output gear pair 316 and the ninth clutch C9317, and the power is output from the output shaft 6.

[0118] The mechanical-double-ring MT4 compound transmission is as Figure 15 As shown, only the first clutch C1507, the second clutch C2502, the sixth clutch C6204, and the tenth clutch C 10319. At this time, the power transmitted by the engine through the input shaft 1 is divided into two paths: one path drives the left planet carrier 304 of the confluence mechanism 3 through the double-ring input gear pair 508, the double-ring input shaft 506, the first clutch C1507, the double-ring mechanism 504, the double-ring output gear pair 501 and the second clutch C2502; the other path drives the right sun gear 308 through the mechanical transmission right gear pair 203 and the sixth clutch C6204. After the two paths of power converge at the right planet carrier 309, they are transmitted to the output shaft 6 through the fourth confluence output gear pair 318 and the tenth clutch C 10 319 and then output from the output shaft 6.

[0119] The mechanical-hydraulic MH1 compound transmission is as Figure 16 shown. Only the third clutch C3402, the fourth clutch C4405, the fifth clutch C5202 and the seventh clutch C7311 are engaged. At this time, the power transmitted by the engine through the input shaft 1 is divided into two paths: one path drives the left sun gear 305 through the hydraulic transmission input gear pair 401, the third clutch C3402, the hydraulic transmission input shaft 403, the pump-controlled motor mechanism 404, the hydraulic transmission output shaft 407, the fourth clutch C4406, the hydraulic transmission output gear pair 405, the right sun gear shaft 310 and the right sun gear 308; the other path drives the left planet carrier 304 through the mechanical transmission left gear pair 203 and the fifth clutch C5202. After the two paths of power converge at the left ring gear 302, they are transmitted to the output shaft 6 through the first confluence output gear pair 312 and the seventh clutch C7311, and the power is output from the output shaft 6.

[0120] The mechanical-hydraulic MH2 compound transmission is as Figure 17 shown. Only the third clutch C3402, the fourth clutch C4405, the fifth clutch C5202 and the eighth clutch C8313 are engaged. At this time, the power transmitted by the engine through the input shaft 1 is divided into two paths: one path drives the left sun gear 305 through the hydraulic transmission input gear pair 401, the third clutch C3402, the hydraulic transmission input shaft 403, the pump-controlled motor mechanism 404, the hydraulic transmission output shaft 407, the fourth clutch C4406, the hydraulic transmission output gear pair 405, the right sun gear shaft 310 and the right sun gear 308; the other path drives the left planet carrier 304 through the mechanical transmission left gear pair 203 and the fifth clutch C5202. After the two paths of power converge at the left ring gear 302, they are transmitted to the output shaft 6 through the second confluence output gear pair 314 and the eighth clutch C8313, and the power is output from the output shaft 6.

[0121] The mechanical-hydraulic MH3 compound transmission is as Figure 18As shown, only the third clutch C3402, the fourth clutch C4405, the fifth clutch C5202, and the ninth clutch C9317 are engaged. At this time, the power transmitted by the engine through the input shaft 1 is transmitted in two paths: one path passes through the hydraulic transmission input gear pair 401, the third clutch C3402, the hydraulic transmission input shaft 403, the pump-controlled motor mechanism 404, the hydraulic transmission output shaft 407, the fourth clutch C4406, the hydraulic transmission output gear pair 405, and the right sun gear shaft 310 to drive the right sun gear 308, and the other path passes through the mechanical transmission left gear pair 203, the fifth clutch C5202, and the left planet carrier 304 to drive the right ring gear 307. The two paths of power converge at the right planet carrier 309 and are then transmitted to the output shaft 6 through the third confluence output gear pair 316 and the ninth clutch C9317, and the power is output from the output shaft 6.

[0122] The mechanical-hydraulic MH4 compound transmission is as Figure 19 shown, only the third clutch C3402, the fourth clutch C4405, the fifth clutch C5202, and the tenth clutch C 10 319 are engaged. At this time, the power transmitted by the engine through the input shaft 1 is transmitted in two paths: one path passes through the hydraulic transmission input gear pair 401, the third clutch C3402, the hydraulic transmission input shaft 403, the pump-controlled motor mechanism 404, the hydraulic transmission output shaft 407, the fourth clutch C4406, the hydraulic transmission output gear pair 405, and the right sun gear shaft 310 to drive the right sun gear 308, and the other path passes through the mechanical transmission left gear pair 203, the fifth clutch C5202, and the left planet carrier 304 to drive the right ring gear 307. The two paths of power converge at the right planet carrier 309 and are then transmitted to the output shaft 6 through the fourth confluence output gear pair 318 and the tenth clutch C 10 319, and the power is output from the output shaft 6.

[0123] As Figure 20 shown, by adjusting the transmission ratio of the double-ring mechanism 5, adjusting the displacement ratio of the hydraulic transmission mechanism 4, and selectively controlling the engagement of the clutch assembly, starting and moving forward with H4, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the hydraulic transmission H4 reaches the positive maximum value; when e·i T ∈[n o (H4) = n o (T4)], and e ∈ [0, 1], i T within the determined transmission ratio range, the hydraulic transmission H4 can be synchronously switched to the double-ring transmission T4. When the transmission ratio i of the double-ring speed change mechanism T changes from the maximum value to the minimum value, n o (T4) increases non-linearly; moving forward with the double-ring transmission T2, the output speed increases linearly with the increase of the transmission ratio i of the double-ring speed change mechanism T of, when iT When it is 4, the double-ring drive T2 reaches the positive maximum value; when e·i simultaneously satisfies T ∈[n o (T4) = n o (T2)], i T Within the determined transmission ratio range, the double-ring drive T2 can be synchronously switched to the double-ring drive T4. When the transmission ratio i of the double-ring speed change mechanism T changes from the maximum value to the minimum value, n o (T4) increases non-linearly; starting and reversing with H3, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the hydraulic drive H4 reaches the negative maximum value; when e·i simultaneously satisfies T ∈[n o (H3) = n o (T3)], and e ∈ [0, 1], i T Within the determined transmission ratio range, the hydraulic drive H3 can be synchronously switched to the double-ring drive T3. When the transmission ratio i of the double-ring speed change mechanism T changes from the maximum value to the minimum value, n o (T3) increases non-linearly; reversing with the double-ring drive T1, the output speed increases linearly with the increase of the transmission ratio i of the double-ring speed change mechanism T When i T = 4, the double-ring drive T1 reaches the negative maximum value; when e·i simultaneously satisfies T ∈[n o (T3) = n o (T1)], i T Within the determined transmission ratio range, the double-ring drive T1 can be synchronously switched to the double-ring drive T3. When the transmission ratio i of the double-ring speed change mechanism T changes from the maximum value to the minimum value, n o (T4) increases non-linearly.

[0124] As Figure 21 shown, by adjusting the transmission ratio of the double-ring mechanism 5, adjusting the displacement ratio of the hydraulic drive mechanism 4 and selectively controlling the engagement of the clutch assembly, moving forward with the mechanical-hydraulic compound drive MH1, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the mechanical-hydraulic compound drive MH1 reaches the positive maximum value; moving forward with the mechanical-double-ring compound drive MT2, the output speed increases non-linearly with the increase of i T When e·i simultaneously satisfies T ∈[n o (MT2) = n o (MH3)], and e ∈ [0, 1], i TWhen within the determined transmission ratio range, the mechanical-double-ring compound transmission MT2 can be synchronously switched to the mechanical-hydraulic compound transmission MH3. When the displacement ratio e of the hydraulic transmission mechanism changes from the maximum value to the minimum value, n o (MH3) increases linearly; when e·i T ∈[n o (MT4) = n o (MH3)], and e ∈ [0, 1], i T When within the determined transmission ratio range, the mechanical-hydraulic compound transmission MH3 can be synchronously switched to the mechanical-double-ring compound transmission MT4, and the output speed decreases non-linearly as the transmission ratio i of the double-ring speed-changing mechanism T increases; when using the mechanical-hydraulic compound transmission MH2 to reverse, the output speed increases linearly as the displacement ratio e of the hydraulic transmission mechanism increases. When e = 1, the mechanical-hydraulic compound transmission MH2 reaches the negative maximum value; when using the mechanical-double-ring compound transmission MT1 to reverse, the output speed increases non-linearly as i T increases; when e·i T ∈[n o (MT1) = n o (MH4)], and e ∈ [0, 1], i T When within the determined transmission ratio range, the mechanical-double-ring compound transmission MT1 can be synchronously switched to the mechanical-hydraulic compound transmission MH4. When the displacement ratio e of the hydraulic transmission mechanism changes from the maximum value to the minimum value, n o (MH4) increases linearly; when e·i T ∈[n o (MT3) = n o (MH4)], and e ∈ [0, 1], i T When within the determined transmission ratio range, the mechanical-hydraulic compound transmission MH4 can be synchronously switched to the mechanical-double-ring compound transmission MT3, and the output speed decreases non-linearly as the transmission ratio i of the double-ring speed-changing mechanism T increases.

[0125] Example of an embodiment:

[0126] The main parameters are: i1i2 = 0.5, i3i4 = 0.5, i5 = 2.5, i6 = 0.5, i7 = 1, i8i9 = 1, i 10 = 1, i 11 i 12 = 1, k1 = 1.6, k2 = 4, i T1 ∈[0.5, 2], i T2 ∈[0.5, 2], i T = i T1 i T2 ∈[0.25, 4].

[0127] The output-input speed relationship of the mechanical transmission M1 is as follows:

[0128] The output-input speed relationship of the mechanical transmission M2 is as follows:

[0129] The output-input speed relationship of the double-ring transmission T1 is as follows:

[0130]

[0131] The output-input speed relationship of the double-ring transmission T2 is as follows:

[0132]

[0133] The output-input speed relationship of the double-ring transmission T3 is as follows:

[0134] The output-input speed relationship of the double-ring transmission T4 is as follows:

[0135] The output-input speed relationship of the hydraulic transmission H1 is as follows:

[0136] The output-input speed relationship of the hydraulic transmission H2 is as follows:

[0137] The output-input speed relationship of the hydraulic transmission H3 is as follows:

[0138] The output-input speed relationship of the hydraulic transmission H4 is as follows:

[0139] As Figure 20 shown, by adjusting the transmission ratio of the double-ring mechanism 5, adjusting the displacement ratio of the hydraulic transmission mechanism 4, and selectively controlling the engagement of the clutch assembly, starting and moving forward with H4, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the hydraulic transmission H4 reaches the positive maximum value of 2n I ; when e·i T ∈[n o (H4) = n o (T4) = 2n I , and when e = 1 and i T = 1, the hydraulic transmission H4 can be synchronously switched to the double-ring transmission T4. When the transmission ratio i T of the double-ring speed-changing mechanism changes from the maximum value to the minimum value, n o (T4) increases non-linearly; moving forward with the double-ring transmission T2, the output speed follows the transmission ratio i of the double-ring speed-changing mechanismT increases linearly with the increase of i T = 4, the double-ring drive T2 reaches the positive maximum value of 2.64n I ; when e·i T ∈[n o (T4) = n o (T2) = 1.156n I , i T = 1.75, the double-ring drive T2 can be synchronously switched to the double-ring drive T4. When the transmission ratio i of the double-ring variable-speed mechanism T changes from the maximum value to the minimum value, n o (T4) increases non-linearly; starting and reversing with H3, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the hydraulic transmission H4 reaches the negative maximum value of -2n I ; when e·i T ∈[n o (H3) = n o (T3) = 2n I , and e = 1, i T = 1, the hydraulic transmission H3 can be synchronously switched to the double-ring drive T3. When the transmission ratio i of the double-ring variable-speed mechanism T changes from the maximum value to the minimum value, n o (T3) increases non-linearly; reversing with the double-ring drive T1, the output speed increases linearly with the increase of the transmission ratio i of the double-ring variable-speed mechanism T When i T = 4, the double-ring drive T1 reaches the negative maximum value of -2.64n I ; when e·i T ∈[n o (T3) = n o (T1) = -1.156n I , i T = 1.75, the double-ring drive T1 can be synchronously switched to the double-ring drive T3. When the transmission ratio i of the double-ring variable-speed mechanism T changes from the maximum value to the minimum value, n o (T4) increases non-linearly.

[0140] The output-input speed relationship of the mechanical-double-ring compound drive MT1 is as follows:

[0141]

[0142] The output-input speed relationship of the mechanical-double-ring compound drive MT2 is as follows:

[0143]

[0144] The output-input speed relationship of the mechanical-double-ring compound drive MT3 is as follows:

[0145]

[0146] The output-input speed relationship of the mechanical-double-ring compound drive MT4 is as follows:

[0147]

[0148] The output-input speed relationship of the mechanical-hydraulic compound drive MH1 is as follows:

[0149]

[0150] The output-input speed relationship of the mechanical-hydraulic compound drive MH2 is as follows:

[0151]

[0152] The output-input speed relationship of the mechanical-hydraulic compound drive MH3 is as follows:

[0153]

[0154] The output-input speed relationship of the mechanical-hydraulic compound drive MH4 is as follows:

[0155]

[0156] As Figure 21 shown, by adjusting the transmission ratio of the double-ring mechanism 5, adjusting the displacement ratio of the hydraulic transmission mechanism 4, and selectively controlling the engagement of the clutch assembly, when using the mechanical-hydraulic compound drive MH1 to move forward, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the mechanical-hydraulic compound drive MH1 reaches the positive maximum value of 1.9n I ; when using the mechanical-double-ring compound drive MT2 to move forward, the output speed increases non-linearly with the increase of i T ; when simultaneously satisfying e·i T ∈[n o (MT2) = n o (MH3) = 0.14n I , and e = 0.575, i T = 0.575, the mechanical-double-ring compound drive MT2 can be synchronously switched to the mechanical-hydraulic compound drive MH3. When the displacement ratio e of the hydraulic transmission mechanism changes from the maximum value to the minimum value, n o (MH3) increases linearly; when simultaneously satisfying e·i T ∈[n o (MT4) = n o (MH3) = 0.0625n I, and e = 0.7, i T When = 0.7, the mechanical - hydraulic compound transmission MH3 can be synchronously switched to the mechanical - double - ring compound transmission MT4, and the output speed decreases non - linearly with the increase of the transmission ratio i of the double - ring speed - changing mechanism T For the mechanical - hydraulic compound transmission MH2 in reverse, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism. When e = 1, the mechanical - hydraulic compound transmission MH2 reaches the negative maximum value of - 1.9n I For the mechanical - double - ring compound transmission MT1 in reverse, the output speed increases non - linearly with the increase of i T When simultaneously satisfying e·i T ∈[n o (MT1)=n o (MH4)= - 0.14n I , and e = 0.575, i T When = 0.575, the mechanical - double - ring compound transmission MT1 can be synchronously switched to the mechanical - hydraulic compound transmission MH4. When the displacement ratio e of the hydraulic transmission mechanism changes from the maximum value to the minimum value, n o (MH4) increases linearly. When simultaneously satisfying e·i T ∈[n o (MT3)=n o (MH4)= - 0.0625n I , and e = 0.7, i T When = 0.7, the mechanical - hydraulic compound transmission MH4 can be synchronously switched to the mechanical - double - ring compound transmission MT3, and the output speed decreases non - linearly with the increase of the transmission ratio i of the double - ring speed - changing mechanism T decreases non - linearly.

[0157] It should be understood that although this specification is described according to each embodiment, 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.

[0158] The series of detailed descriptions listed above are only specific descriptions of the feasible embodiments of the present invention, and they are not used to limit the protection scope of the present invention. Any equivalent embodiments or changes 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 mechanical - double - ring - hydraulic compound transmission mechanism, characterized in that, It includes an input member, a confluence mechanism (3), a hydraulic transmission mechanism (4), a double-ring mechanism (5), an output member, a clutch assembly and a brake assembly; the confluence mechanism (3) includes a left planetary gear train and a right planetary gear train, the clutch assembly connects the left planetary gear train and the right planetary gear train, the clutch assembly connects the input member to the hydraulic transmission mechanism (4), the double-ring mechanism (5), the left planetary gear train and the right planetary gear train respectively, the clutch assembly connects the hydraulic transmission mechanism (4) to the right planetary gear train, the clutch assembly connects the double-ring mechanism (5) to the left planetary gear train, and the clutch assembly connects the left planetary gear train and the right planetary gear train to the output member respectively; by adjusting the displacement ratio of the hydraulic transmission mechanism (4), adjusting the transmission ratio of the double-ring mechanism (5) and selectively controlling the engagement of the clutch assembly and the brake assembly, a continuous transmission ratio between the input member and the output member is provided; By adjusting the displacement ratio of the hydraulic transmission mechanism (4), adjusting the transmission ratio of the double-ring mechanism (5) and selectively controlling the engagement of the clutch assembly and the brake assembly, the transmission modes between the input member and the output member include: mechanical transmission, double-ring transmission, hydraulic transmission, mechanical-double-ring compound transmission and mechanical-hydraulic compound transmission; The left planetary gear train includes a left ring gear (302), a left planet carrier (304) and a left sun gear (305); the right planetary gear train includes a right ring gear (307), a right planet carrier (309) and a right sun gear (308); the right ring gear (307) is connected to the left planet carrier (304); the left sun gear (305) is connected to the right sun gear (308); The clutch assembly includes a fifth clutch C5 (202), a sixth clutch C6 (204), a seventh clutch C7 (311), an eighth clutch C8 (313), a ninth clutch C9 (317), a tenth clutch C 10 (319), and an eleventh clutch C 11 (315). The fifth clutch C5 (202) is used to selectively connect the input member to the left planet carrier (304); the sixth clutch C6 (204) is used to selectively connect the input member to the right sun gear (308); the seventh clutch C7 (311) and the eighth clutch C8 (313) are used to selectively connect the left ring gear (302) to the output member with different speed ratios; the ninth clutch C9 (317) and the tenth clutch C 10 (319) are used to selectively connect the right planet carrier (309) to the output member with different speed ratios; the eleventh clutch C 11 (315) is used to selectively connect the left planet carrier (304) to the left sun gear (305); The brake assembly includes a first brake B1 (303), a second brake B2 (306) and a third brake B3 (505); the first brake B1 (303) is used to selectively connect the left ring gear (302) to a fixed member; the second brake B2 (306) is used to selectively connect the right ring gear (307) to a fixed member; the third brake B3 (505) is used to selectively connect the left planet carrier (304) to a fixed member; By engaging the fifth clutch C5 (202), the seventh clutch C7 (311), and the eleventh clutch C 11 (315), a mechanical transmission M1 in the forward direction between the input member and the output member is provided, and in the mechanical transmission M1, the rotational speeds of the input member and the output member satisfy the following relationship: In the formula, n o is the rotational speed of the output member, and n I is the rotational speed of the input member; i5 is the transmission ratio between the input member and the left planet carrier (304), and i7 is the transmission ratio between the left gear ring (302) and the output member; By engaging the fifth clutch C5 (202), the eighth clutch C8 (313), and the eleventh clutch C 11 (315), a reverse-direction mechanical transmission M2 is provided between the input member and the output member, and in the mechanical transmission M2, the rotational speeds of the input member and the output member satisfy the following relationship: Wherein, i8i9 is the transmission ratio between the left ring gear (302) and the output member.

2. The mechanical - double - annular - hydraulic compound transmission mechanism according to claim 1, wherein, The clutch assembly further includes a first clutch C1 (507) and a second clutch C2 (502); the first clutch C1 (507) is used to selectively connect the input member to the input end of the double-ring mechanism (5); the second clutch C2 (502) is used to selectively connect the output end of the double-ring mechanism (5) to the left planet carrier (304); By adjusting the transmission ratio of the double-ring mechanism (5), by engaging the first clutch C1 (507), the second clutch C2 (502), the ninth clutch C9 (317) and the first brake B1 (303), a double-ring transmission T1 in the reverse direction between the input member and the output member is provided, and in the double-ring transmission T1, the rotational speeds of the input member and the output member satisfy the following relationship: Where: k1 is the planetary gear characteristic parameter of the left planetary gear train, k2 is the planetary gear characteristic parameter of the right planetary gear train, i1 is the transmission ratio between the input member and the input end of the double-ring mechanism (5), i2 is the transmission ratio between the output end of the double-ring mechanism (5) and the left planet carrier (304), i 10 is the transmission ratio between the right planet carrier (309) and the output member, i T1 i T2 is the transmission ratio of the double-ring mechanism (5); By adjusting the transmission ratio of the double-ring mechanism (5), by engaging the first clutch C1 (507), the second clutch C2 (502), the eleventh clutch C 11 (315) and the ninth clutch C9 (317), a double-ring transmission T3 in the reverse direction between the input member and the output member is provided, and the rotational speeds of the input member and the output member in the double-ring transmission T3 satisfy the following relationship: By adjusting the transmission ratio of the double-annular mechanism (5), by engaging the first clutch C1 (507), the second clutch C2 (502), the first brake B1 (303) and the tenth clutch C 10 (319), a double-annular drive T2 in the forward direction between the input member and the output member is provided, and in the double-annular drive T2, the rotational speeds of the input member and the output member satisfy the following relationship: where i 11 i 12 is the transmission ratio between the right planet carrier (309) and the output member; By adjusting the transmission ratio of the double-ring mechanism (5), by engaging the first clutch C1 (507), the second clutch C2 (502), the tenth clutch C 10 (319) and the eleventh clutch C 11 (315), a double-ring drive T4 in the forward direction between the input member and the output member is provided, and in the double-ring drive T4, the rotational speeds of the input member and the output member satisfy the following relationship:

3. The mechanical-double-ring-hydraulic composite transmission mechanism according to claim 2, characterized in that, The clutch assembly further includes a third clutch C3 (402) and a fourth clutch C4 (406). The third clutch C3 (402) connects the input member to the input end of the hydraulic transmission mechanism (4); the fourth clutch C4 (406) connects the output end of the hydraulic transmission mechanism (4) to the right sun gear (308); By adjusting the displacement ratio of the hydraulic transmission mechanism (4), and by engaging the third clutch C3 (402), the fourth clutch C4 (406), the ninth clutch C9 (317), the second brake B2 (306) and the third brake B3 (505), a reverse-direction hydraulic transmission H1 between the input member and the output member is provided. In the hydraulic transmission H1, the rotational speeds of the input member and the output member satisfy the following relationship: where: e is the displacement ratio of the hydraulic transmission mechanism (4), i3 is the transmission ratio between the input member and the input end of the hydraulic transmission mechanism (4), and i4 is the transmission ratio between the output end of the hydraulic transmission mechanism (4) and the right sun gear (308); By adjusting the displacement ratio of the hydraulic transmission mechanism (4), by engaging the third clutch C3 (402), the fourth clutch C4 (406), the ninth clutch C9 (317) and the eleventh clutch C 11 (315), a reverse hydraulic transmission H3 between the input member and the output member is provided, and in the hydraulic transmission H3, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (4), by engaging the third clutch C3 (402), the fourth clutch C4 (406), the tenth clutch C 10 (319), the second brake B2 (306) and the third brake B3 (505), a forward hydraulic transmission H2 between the input member and the output member is provided, and in the hydraulic transmission H2, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (4), by engaging the third clutch C3 (402), the fourth clutch C4 (406), the tenth clutch C 10 (319) and the eleventh clutch C 11 (315), a hydraulic transmission H4 in the forward direction between the input member and the output member is provided, and in the hydraulic transmission H4, the rotational speeds of the input member and the output member satisfy the following relationship:

4. The mechanical - double - ring - hydraulic compound transmission mechanism according to claim 3, wherein By adjusting the transmission ratio of the double-ring mechanism (5), and by engaging the first clutch C1 (507), the second clutch C2 (502), the sixth clutch C6 (204) and the seventh clutch C7 (311), a mechanical-double-ring compound transmission MT1 in the reverse direction between the input member and the output member is provided. In the mechanical-double-ring compound transmission MT1, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the transmission ratio of the double-ring mechanism (5), and by engaging the first clutch C1 (507), the second clutch C2 (502), the sixth clutch C6 (204) and the ninth clutch C9 (317), a mechanical-double-ring compound transmission MT3 in the reverse direction between the input member and the output member is provided. In the mechanical-double-ring compound transmission MT3, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the transmission ratio of the double-ring mechanism (5), and by engaging the first clutch C1 (507), the second clutch C2 (502), the sixth clutch C6 (204) and the eighth clutch C8 (313), a mechanical-double-ring compound transmission MT2 in the forward direction between the input member and the output member is provided. In the mechanical-double-ring compound transmission MT2, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the transmission ratio of the double-ring mechanism (5), by engaging the first clutch C1 (507), the second clutch C2 (502), the sixth clutch C6 (204) and the tenth clutch C 10 (319), a mechanical-double-ring compound transmission MT4 in the forward direction between the input member and the output member is provided. In the mechanical-double-ring compound transmission MT4, the rotational speeds of the input member and the output member satisfy the following relationship:

5. The mechanical - double - annular - hydraulic composite transmission mechanism according to claim 3, characterized in that, By adjusting the displacement ratio of the hydraulic transmission mechanism (4), and by engaging the third clutch C3 (402), the fourth clutch C4 (406), the fifth clutch C5 (202) and the seventh clutch C7 (311), a mechanical-hydraulic compound transmission MH1 in the forward direction between the input member and the output member is provided. In the mechanical-hydraulic compound transmission MH1, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (4), and by engaging the third clutch C3 (402), the fourth clutch C4 (406), the fifth clutch C5 (202) and the ninth clutch C9 (317), a mechanical-hydraulic compound drive MH3 in the forward direction between the input member and the output member is provided, and in the mechanical-hydraulic compound drive MH3, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (4), and by engaging the third clutch C3 (402), the fourth clutch C4 (406), the fifth clutch C5 (202) and the eighth clutch C8 (313), a mechanical-hydraulic compound drive MH2 in the reverse direction between the input member and the output member is provided, and in the mechanical-hydraulic compound drive MH2, the rotational speeds of the input member and the output member satisfy the following relationship: By adjusting the displacement ratio of the hydraulic transmission mechanism (4), by engaging the third clutch C3 (402), the fourth clutch C4 (406), the fifth clutch C5 (202) and the tenth clutch C 10 (319), a mechanical - hydraulic compound drive MH4 in the reverse direction between the input member and the output member is provided, and in the mechanical - hydraulic compound drive MH4, the rotational speeds of the input member and the output member satisfy the following relationship:

6. The mechanical-double-ring-hydraulic compound transmission mechanism according to claim 3, characterized in that, By adjusting the displacement ratio of the hydraulic transmission mechanism (4), adjusting the transmission ratio of the double-ring mechanism (5) and selectively controlling the engagement of the clutch assembly and the brake assembly, a hydraulic drive H4 is used for starting, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic transmission mechanism, and when e = 1, the hydraulic drive H4 reaches the positive maximum value; When e·i is satisfied T ∈[n o (H4) = n o (T4)], and e ∈ [0, 1], and within the determined transmission ratio range, the hydraulic transmission H4 can be synchronously switched to the double-ring transmission T4. When the transmission ratio of the double-ring speed-changing mechanism changes from the maximum value to the minimum value, n o (T4) increases non-linearly; When e·i is simultaneously satisfied T ∈[n o (T4) = n o (T2)], and within the determined transmission ratio range, the double-ring transmission T2 can be synchronously switched to the double-ring transmission T4. When the transmission ratio i of the double-ring speed-changing mechanism T changes from the maximum value to the minimum value, n o (T4) increases non-linearly; The hydraulic drive H3 starts to move backward, and the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the hydraulic drive H3 reaches the negative maximum value; when e·i T ∈[n o (H3) = n o (T3)], and e ∈ [0, 1], and within the determined transmission ratio range, the hydraulic drive H3 can be synchronously switched to the double-ring drive T3. When the transmission ratio of the double-ring speed change mechanism changes from the maximum value to the minimum value, n o (T3) increases non-linearly; The double-ring drive T1 retreats, and the output speed increases linearly with the increase of the transmission ratio i of the double-ring speed-changing mechanism T When = max, the double-ring drive T1 reaches the negative maximum value; when e·i T ∈[n o (T3) = n o (T1)], and within the determined transmission ratio range, the double-ring drive T1 can be synchronously switched to the double-ring drive T3. When the transmission ratio of the double-ring speed-changing mechanism changes from the maximum value to the minimum value, n o (T4) increases non-linearly.

7. The mechanical-double-ring-hydraulic composite transmission mechanism according to claim 5, wherein By adjusting the displacement ratio of the hydraulic transmission mechanism (4), adjusting the transmission ratio of the double-ring mechanism (5) and selectively controlling the engagement of the clutch assembly and the brake assembly, Advance using the mechanical - hydraulic compound drive MH1. The output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the mechanical - hydraulic compound drive MH1 reaches the positive maximum value. Advance using the mechanical - double - ring compound drive MT2. The output speed increases non - linearly with the increase of i T ; When e·i T ∈[n o (MT2)=n o (MH3)], and e ∈ [0, 1], and within the determined transmission ratio range, the mechanical - double - ring compound drive MT2 can be synchronously switched to the mechanical - hydraulic compound drive MH3. When the displacement ratio e of the hydraulic drive mechanism changes from the maximum value to the minimum value, n o (MH3) increases linearly; When both e·i T ∈[n o (MT4) = n o (MH3)], and e ∈ [0, 1], When within the determined transmission ratio range, the mechanical - hydraulic composite drive MH3 can be synchronously switched to the mechanical - double - ring composite drive MT4, and the output speed decreases non - linearly with the increase of the transmission ratio i of the double - ring speed - changing mechanism T in a non - linear manner; Adopt mechanical - hydraulic compound drive MH2 to reverse, the output speed increases linearly with the increase of the displacement ratio e of the hydraulic drive mechanism. When e = 1, the mechanical - hydraulic compound drive MH2 reaches the negative maximum value; adopt mechanical - double - ring compound drive MT1 to reverse, the output speed increases non - linearly with the increase of ; when e·i T ∈[n o (MT1) = n o (MH4)], and e ∈ [0, 1], and within the determined transmission ratio range, the mechanical - double - ring compound drive MT1 can be synchronously switched to the mechanical - hydraulic compound drive MH4; when the displacement ratio e of the hydraulic drive mechanism changes from the maximum value to the minimum value, n o (MH4) increases linearly; when e·i T ∈[n o (MT3) = n o (MH4)], and e ∈ [0, 1], and within the determined transmission ratio range, the mechanical - hydraulic compound drive MH4 can be synchronously switched to the mechanical - double - ring compound drive MT3, and the output speed decreases non - linearly with the increase of the transmission ratio of the double - ring speed - changing mechanism .

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