A transmission device with hydraulic machinery in series and parallel coexistence and a control method thereof

Abstract

The present invention discloses a transmission device in which hydraulic machinery coexists in series and parallel and a control method thereof, comprising an input shaft assembly, a hydraulic transmission assembly, a planetary gear transmission assembly, an intermediate gear transmission assembly, and an output shaft assembly; the switching of the hydraulic transmission mode, the mechanical transmission mode, and the hydraulic-mechanical composite transmission mode is realized by the combined switching between the clutch and the brake. Beneficial effects: The present invention expands the speed regulation range of the hydraulic transmission through the hydraulic-mechanical series transmission, and at the same time meets the requirements of accuracy and speed regulation range in combination with the hydraulic transmission; meets the requirements of low-power and high-power working conditions respectively through the combination of hydraulic-mechanical series and parallel transmission; forms a variety of transmission modes suitable for starting, working and transitioning conditions.

Description

Technical Field

[0001] The present invention relates to a transmission device and a control method thereof, and in particular to a transmission device and a control method thereof in which hydraulic machinery coexists in series and parallel, belonging to the technical field of variable speed transmission devices. Background Art

[0002] Hydraulic transmission has the characteristics of low speed and high torque, but the transmission efficiency is not high; mechanical transmission has high transmission efficiency, but it is difficult to achieve stepless speed change. Combining hydraulic transmission with mechanical transmission can give full play to the advantages of both and abandon their disadvantages. The technology of hydraulic transmission mechanism and mechanical transmission mechanism in series is relatively mature, which can expand the speed regulation range of the same type of hydraulic transmission mechanism, but the overall efficiency is not high; the technology of hydraulic transmission mechanism and mechanical transmission mechanism in parallel is difficult to control, but it has the characteristics of efficient stepless speed regulation. In some low-power operation requirements, the hydraulic-mechanical series mode can be better matched to avoid the situation of "big horse pulling small cart"; in some high-power operation requirements, the hydraulic-mechanical parallel mode can achieve stepless speed change under the premise of meeting the power. Designing a variable speed transmission device including hydraulic transmission, mechanical transmission and hydraulic-hydraulic transmission to meet various working conditions, and the hydraulic-hydraulic transmission includes two types of hydraulic-mechanical series transmission and hydraulic-mechanical parallel transmission to meet different power requirements, and ensure the power and fuel economy of the system, has practical significance. Summary of the invention

[0003] Purpose of the invention: In view of the deficiencies in the prior art, the present invention provides a transmission device in which hydraulic and mechanical series and parallel coexist and a control method thereof. The present invention includes variable speed transmission modes of hydraulic transmission, mechanical transmission and mechanical-hydraulic compound transmission, which can meet various working conditions, and the mechanical-hydraulic compound transmission includes two types, hydraulic-mechanical series transmission and hydraulic-mechanical parallel transmission, to meet different power requirements and ensure the power and fuel economy of the system.

[0004] Technical solution: A hydraulic mechanical series-parallel transmission device includes an input shaft assembly, the input shaft assembly includes an input shaft, a first clutch C 1 , linked intermediate gear set and fifth clutch C 5 ;

[0005] The hydraulic transmission assembly includes a variable displacement pump, a quantitative motor and a second clutch C 2 The variable pump passes through the second clutch C 2 Connected with the input shaft;

[0006] The planetary gear transmission assembly includes an outer ring gear, a planet carrier, a sun gear and a sixth clutch C 6 , the sixth clutch C 6 Connected to the sun gear, the fifth clutch C5 Connected with the outer gear ring;

[0007] The intermediate gear transmission assembly includes a first transmission gear, a second transmission gear, a third transmission gear, a fourth transmission gear, a third clutch C 3 , Fourth clutch C 4 and brake B 1 The first transmission gear is fixedly connected to the output shaft of the quantitative motor, the first transmission gear is meshed with the second transmission gear, and the second transmission gear is connected to the output shaft of the quantitative motor through the fourth clutch C 4 The third transmission gear is connected to the fourth transmission gear, and the fourth transmission gear is respectively connected to the sun gear and the brake B 1 The output shaft of the quantitative motor is connected through the third clutch C 3 and the fifth clutch C 5 The output shaft of the quantitative motor is connected to the linkage intermediate gear set through the third clutch C 3 and the sixth clutch C 6 Connected with the sun gear;

[0008] An output shaft assembly comprises an output shaft and an intermediate gear, and the output shaft is connected to the planet carrier through the intermediate gear.

[0009] A control method for a transmission device in which hydraulic and mechanical series and parallel coexist, realizing switching among a hydraulic transmission mode, a mechanical transmission mode and a hydraulic and mechanical compound transmission mode through combined switching between a clutch and a brake.

[0010] Preferably, the hydraulic-mechanical compound transmission mode includes a hydraulic-mechanical series transmission mode and a hydraulic-mechanical parallel transmission mode.

[0011] Preferably, the control method of the hydraulic transmission mode is as follows:

[0012] Second clutch C 2 、Third clutch C 3 and the sixth clutch C 6 Engage, while the first clutch C 1 , Fourth clutch C 4 、Fifth clutch C 5 and brake B 1 Separation; power from the input shaft through the second clutch C 2 The variable displacement pump is driven to work. The variable displacement pump outputs high-pressure oil to drive the quantitative motor to rotate. The power output by the output shaft of the quantitative motor passes through the third clutch C 3 、Sixth clutch C 6 , sun gear, planet carrier and intermediate gear to the output shaft.

[0013] The output shaft speed n of the hydraulic transmission mode o The calculation method is as follows:

[0014]

[0015] Where n o is the output shaft speed, n I is the input shaft speed, i 5 is the transmission ratio between the outer ring gear and the intermediate gear, i 6 is the transmission ratio between the intermediate gear and the output shaft, and e is the displacement ratio of the hydraulic transmission component.

[0016] Preferably, the mechanical transmission mode includes mechanical transmission 1st gear, mechanical transmission 2nd gear and mechanical transmission 3rd gear, and the specific control method is as follows:

[0017] Mechanical transmission 1st gear: First clutch C 1 、Fifth clutch C 5 and brake B 1 Engage, while the second clutch C 2 、Third clutch C 3 , Fourth clutch C 4 and the sixth clutch C 6 Separation; the power is transmitted from the input shaft through the first clutch C 1 , linkage intermediate gear set, fifth clutch C 5 , outer ring gear, planet carrier and intermediate gear to output shaft;

[0018] Mechanical transmission 2nd gear: 1st clutch C 1 、Fifth clutch C 5 and the sixth clutch C 6 Engage, while the second clutch C 2 、Third clutch C 3 , Fourth clutch C 4 and brake B 1 Separation; the power is transmitted from the input shaft through the first clutch C 1 , linkage intermediate gear set, fifth clutch C 5 、Sixth clutch C 6 , sun gear, planet carrier and intermediate gear to output shaft;

[0019] Mechanical transmission 3rd gear: First clutch C 1 、Third clutch C 3 , Fourth clutch C 4 and the fifth clutch C 5 Engage, while the second clutch C 2 、Sixth clutch C 6 and brake B 1Separation; the power is transmitted from the input shaft through the first clutch C 1 , linking the intermediate gear set to the fifth clutch C 5 After the split, all the way through the third clutch C 3 , first transmission gear, second transmission gear, fourth clutch C 4 , the third transmission gear, the fourth transmission gear, the sun gear to the planetary carrier, and the other power through the outer ring gear and the intermediate gear transmission assembly converges at the planetary carrier. The merged power is output from the planetary carrier and the intermediate gear to the output shaft.

[0020] The output shaft speed n of the mechanical transmission 1st gear, mechanical transmission 2nd gear and mechanical transmission 3rd gear o The calculation method is as follows:

[0021] Mechanical transmission 1st gear:

[0022]

[0023] Where n o is the output shaft speed, n I is the input shaft speed, i 1 The first clutch C 1 The transmission ratio with the linked intermediate gear set, i 2 To link the intermediate gear set and the fifth clutch C 5 The transmission ratio, i 5 is the transmission ratio between the outer ring gear and the intermediate gear, i 6 is the transmission ratio between the intermediate gear and the output shaft, k is the characteristic parameter of the gear set in the planetary gear transmission assembly;

[0024] Mechanical transmission 2 gears:

[0025]

[0026] Where n o is the output shaft speed, n I is the input shaft speed, i 1 The first clutch C 1 The transmission ratio with the linked intermediate gear set, i 2 To link the intermediate gear set and the fifth clutch C 5 The transmission ratio, i 5 is the transmission ratio between the outer ring gear and the intermediate gear, i 6 is the transmission ratio between the intermediate gear and the output shaft;

[0027] Mechanical transmission 3 gears:

[0028]

[0029] Where n o is the output shaft speed, nI is the input shaft speed, i 1 The first clutch C 1 The transmission ratio with the linked intermediate gear set, i 2 To link the intermediate gear set and the fifth clutch C 5 The transmission ratio, i 3 is the transmission ratio between the first transmission gear and the second transmission gear, i 4 is the transmission ratio between the third transmission gear and the fourth transmission gear, i 5 is the transmission ratio between the outer ring gear and the intermediate gear, i 6 is the transmission ratio between the intermediate gear and the output shaft, and k is the characteristic parameter of the gear set in the planetary gear transmission assembly.

[0030] Preferably, the control method of the hydraulic mechanical series transmission mode and the hydraulic mechanical parallel transmission mode is as follows:

[0031] Hydraulic mechanical series transmission mode: Second clutch C 2 , Fourth clutch C 4 and the sixth clutch C 6 Engage, while the first clutch C 1 、Third clutch C 3 、Fifth clutch C 5 and brake B 1 Separation; power from the input shaft through the second clutch C 2 The variable displacement pump is driven to work. The variable displacement pump outputs high-pressure oil to drive the quantitative motor to rotate. The power output by the output shaft of the quantitative motor passes through the first transmission gear, the second transmission gear, the fourth clutch C in sequence. 4 , the third transmission gear, the fourth transmission gear, the sun gear, the planet carrier and the intermediate gear to the output shaft for output;

[0032] Hydraulic mechanical parallel transmission mode: first clutch C 1 , Second clutch C 2 , Fourth clutch C 4 and the fifth clutch C 5 Engage, while the third clutch C 3 、Sixth clutch C 6 and brake B 1 Separation; the power is diverted from the input shaft assembly, and the power flows from the input shaft through the second clutch C 2 The variable displacement pump is driven to work. The variable displacement pump outputs high-pressure oil to drive the quantitative motor to rotate. The power output by the output shaft of the quantitative motor passes through the first transmission gear, the second transmission gear, the fourth clutch C in sequence. 4 , the third transmission gear, the fourth transmission gear, the sun gear to the planet carrier,

[0033] The other power passes through the first clutch C1 , linkage intermediate gear set, fifth clutch C 5 The outer gear ring and the power passing through the hydraulic transmission component and the intermediate gear transmission component are combined at the planetary carrier, and the combined power is output from the planetary carrier and the intermediate gear to the output shaft.

[0034] The output shaft speed n of the hydraulic mechanical series transmission mode and the hydraulic mechanical parallel transmission mode o The calculation method is as follows:

[0035] Hydraulic mechanical series transmission mode:

[0036]

[0037] Where n o is the output shaft speed, n I is the input shaft speed, i 3 is the transmission ratio between the first transmission gear and the second transmission gear, i 4 is the transmission ratio between the third transmission gear and the fourth transmission gear, i 5 is the transmission ratio between the outer ring gear and the intermediate gear, i 6 is the transmission ratio between the intermediate gear and the output shaft;

[0038] Hydraulic mechanical parallel transmission mode:

[0039]

[0040] Where n o is the output shaft speed, n I is the input shaft speed, i 1 The first clutch C 1 The transmission ratio with the linked intermediate gear set, i 2 To link the intermediate gear set and the fifth clutch C 5 The transmission ratio, i 3 is the transmission ratio between the first transmission gear and the second transmission gear, i 4 is the transmission ratio between the third transmission gear and the fourth transmission gear, i 5 is the transmission ratio between the outer ring gear and the intermediate gear, i 6 is the transmission ratio of the intermediate gear to the output shaft, k is the characteristic parameter of the gear set in the planetary gear transmission assembly, and e is the displacement ratio of the hydraulic transmission assembly.

[0041] Beneficial effects: The present invention expands the speed regulation range of hydraulic transmission through hydraulic mechanical series transmission, and at the same time meets the requirements of accuracy and speed regulation range when combined with hydraulic transmission; meets the requirements of low-power and high-power operating conditions respectively through the combination of hydraulic mechanical series and parallel transmission; forms a variety of transmission modes suitable for starting, operation and transfer conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art are briefly introduced below. Obviously, the drawings in the following description are only embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on the provided drawings without creative work.

[0043] Figure 1 It is a structural principle diagram of the present invention;

[0044] Figure 2 It is a schematic diagram of power flow in the hydraulic transmission mode of the present invention;

[0045] Figure 3 It is a schematic diagram of power flow of the first gear of the mechanical transmission of the present invention;

[0046] Figure 4 It is a schematic diagram of the power flow of the second gear of the mechanical transmission of the present invention;

[0047] Figure 5 It is a schematic diagram of power flow of the third gear of the mechanical transmission of the present invention;

[0048] Figure 6 It is a schematic diagram of power flow in the hydraulic mechanical series transmission mode of the present invention;

[0049] Figure 7 It is a schematic diagram of power flow in the hydraulic mechanical parallel transmission mode of the present invention;

[0050] Figure 8 It is the speed regulation characteristic curve diagram of the present invention. DETAILED DESCRIPTION

[0051] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0052] In the description of the present invention, it is necessary to understand that the terms "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship are based on the orientation or position relationship 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 therefore cannot be understood as a limitation on the present invention.

[0053] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0054] like Figure 1 As shown, a hydraulic mechanical series-parallel transmission device comprises an input shaft assembly 1, wherein the input shaft assembly 1 comprises an input shaft 11, a first clutch C 1 12. Linking the intermediate gear set 13 and the fifth clutch C 5 14;

[0055] The hydraulic transmission assembly 2 includes a variable displacement pump 21, a fixed displacement motor 22 and a second clutch C 2 23, the variable displacement pump 21 passes through the second clutch C 2 23 is connected to the input shaft 11;

[0056] The planetary gear transmission assembly 3 includes an outer ring gear 31, a planet carrier 32, a sun gear 33 and a sixth clutch C 6 34, the sixth clutch C 6 34 is connected to the sun gear 33, the fifth clutch C 5 14 is connected to the outer gear ring 31;

[0057] The intermediate gear transmission assembly 4 includes a first transmission gear 41, a second transmission gear 42, a third transmission gear 43, a fourth transmission gear 44, a third clutch C 3 45. Fourth clutch C 4 46 and brake B 1 47, the first transmission gear 41 is fixedly connected to the output shaft of the quantitative motor 22, the first transmission gear 41 is meshed with the second transmission gear 42, and the second transmission gear 42 is connected to the output shaft of the quantitative motor 22 through the fourth clutch C 4 46 is connected to the third transmission gear 43, the third transmission gear 43 is meshed with the fourth transmission gear 44, the fourth transmission gear 44 is respectively connected to the sun gear 33 and the brake B 1 47, the output shaft of the quantitative motor 22 is respectively connected through the third clutch C 3 45 and fifth clutch C 514 is connected to the linkage intermediate gear set 13, and the output shaft of the quantitative motor 22 is respectively connected to the third clutch C 3 45 and sixth clutch C 6 34 is connected with the sun gear 33;

[0058] The output shaft assembly 5 includes an output shaft 51 and an intermediate gear 52 . The output shaft 51 is connected to the planet carrier 32 via the intermediate gear 52 .

[0059] As shown in Table 1, a control method for a transmission device in which hydraulic and mechanical series and parallel coexist is characterized in that the switching of the hydraulic transmission mode, the mechanical transmission mode and the hydraulic and mechanical compound transmission mode is achieved by combined switching between the clutch and the brake.

[0060] The hydraulic-mechanical compound transmission mode includes a hydraulic-mechanical series transmission mode and a hydraulic-mechanical parallel transmission mode.

[0061] Table 1 Mode switching element engagement status

[0062]

[0063] Note: “B” stands for brake, “C” stands for clutch; “▲” stands for the actuator in the engaged state, and “△” stands for the actuator in the disengaged state.

[0064] like Figure 2 As shown, the control method of the hydraulic transmission mode is as follows:

[0065] Second clutch C 2 23. Third clutch C 3 45 and sixth clutch C 6 34 is engaged, while the first clutch C 1 12. Fourth clutch C 4 46. ​​Fifth clutch C 5 14 and brake B 1 47 is separated; the power is transmitted from the input shaft 11 through the second clutch C 2 23 drives the variable displacement pump 21 to work, and the variable displacement pump 21 outputs high-pressure oil to drive the quantitative motor 22 to rotate. The power output by the output shaft of the quantitative motor 22 passes through the third clutch C 3 45. Sixth clutch C 6 34, sun gear 33, planet carrier 32 and intermediate gear 52 are output to output shaft 51.

[0066] The output shaft 51 speed n of the hydraulic transmission mode o The calculation method is as follows:

[0067]

[0068] Where n o is the output shaft 51 speed, n I is the speed of input shaft 11, i 5 is the transmission ratio between the outer gear ring 31 and the intermediate gear 52, i 6 is the transmission ratio between the intermediate gear 52 and the output shaft 51 , and e is the displacement ratio of the hydraulic transmission assembly 2 .

[0069] like Figure 3 , 4 As shown in FIG. 5 , the mechanical transmission mode includes mechanical transmission 1st gear, mechanical transmission 2nd gear and mechanical transmission 3rd gear. The specific control method and the output shaft 51 speed n of each mode are o The calculation method is as follows:

[0070] like Figure 3 As shown, mechanical transmission 1st gear: first clutch C 1 12. Fifth clutch C 5 14 and brake B 1 47 is engaged, while the second clutch C 2 23. Third clutch C 3 45. Fourth clutch C 4 46 and sixth clutch C 6 34 separation; the power is sequentially passed through the first clutch C by the input shaft 11 1 12. Intermediate gear set 13. Fifth clutch C 5 14. The outer ring gear 31, the planet carrier 32 and the intermediate gear 52 are output to the output shaft 51;

[0071]

[0072] Where n o is the output shaft 51 speed, n I is the speed of input shaft 11, i 1 The first clutch C 1 The transmission ratio of 12 and the linkage intermediate gear set 13 is i 2 To link the intermediate gear set 13 and the fifth clutch C 5 14 gear ratio, i 5 is the transmission ratio between the outer gear ring 31 and the intermediate gear 52, i 6 is the transmission ratio between the intermediate gear 52 and the output shaft 51, and k is the characteristic parameter of the gear set in the planetary gear transmission assembly 3;

[0073] like Figure 4 As shown, mechanical transmission 2nd gear: first clutch C 1 12. Fifth clutch C 5 14 and sixth clutch C 6 34 is engaged, while the second clutch C2 23. Third clutch C 3 45. Fourth clutch C 4 46 and brake B 1 47 is separated; the power is transmitted from the input shaft 11 through the first clutch C 1 12. Intermediate gear set 13. Fifth clutch C 5 14. Sixth clutch C 6 34, sun gear 33, planet carrier 32 and intermediate gear 52 to output shaft 51;

[0074]

[0075] Where n o is the output shaft 51 speed, n I is the speed of input shaft 11, i 1 The first clutch C 1 The transmission ratio of 12 and the linkage intermediate gear set 13 is i 2 To link the intermediate gear set 13 and the fifth clutch C 5 14 gear ratio, i 5 is the transmission ratio between the outer gear ring 31 and the intermediate gear 52, i 6 is the transmission ratio between the intermediate gear 52 and the output shaft 51;

[0076] like Figure 5 As shown, mechanical transmission 3rd gear: first clutch C 1 12. Third clutch C 3 45. Fourth clutch C 4 46 and fifth clutch C 5 14 Engagement, while the second clutch C 2 23. Sixth clutch C 6 34 and brake B 1 47 is separated; the power is transmitted from the input shaft 11 through the first clutch C 1 12. Link the intermediate gear set 13 to the fifth clutch C 5 14 after the split, all the way through the third clutch C 3 45, first transmission gear 41, second transmission gear 42, fourth clutch C 4 46, the third transmission gear 43, the fourth transmission gear 44, the sun gear 33 to the planetary carrier 32, and the other power through the outer ring gear 31 and the intermediate gear transmission assembly 4 is merged into the planetary carrier 32, and the merged power is output from the planetary carrier 32 and the intermediate gear 52 to the output shaft 51.

[0077]

[0078] Where n o is the output shaft 51 speed, nI is the speed of input shaft 11, i 1 The first clutch C 1 The transmission ratio of 12 and the linkage intermediate gear set 13 is i 2 To link the intermediate gear set 13 and the fifth clutch C 5 14 gear ratio, i 3 is the transmission ratio of the first transmission gear 41 to the second transmission gear 42, i 4 is the transmission ratio of the third transmission gear 43 to the fourth transmission gear 44, i 5 is the transmission ratio between the outer gear ring 31 and the intermediate gear 52, i 6 is the transmission ratio between the intermediate gear 52 and the output shaft 51 , and k is the characteristic parameter of the gear set in the planetary gear transmission assembly 3 .

[0079] like Figure 6 and 7 As shown, the control method of the hydraulic mechanical series transmission mode and the hydraulic mechanical parallel transmission mode and the output shaft 51 speed n o The calculation method is as follows:

[0080] like Figure 6 As shown, hydraulic mechanical series transmission mode: the second clutch C 2 23. Fourth clutch C 4 46 and sixth clutch C 6 34 is engaged, while the first clutch C 1 12. Third clutch C 3 45. Fifth clutch C 5 14 and brake B 1 47 is separated; the power is transmitted from the input shaft 11 through the second clutch C 2 23 drives the variable displacement pump 21 to work, and the variable displacement pump 21 outputs high-pressure oil to drive the quantitative motor 22 to rotate. The power output by the output shaft of the quantitative motor 22 passes through the first transmission gear 41, the second transmission gear 42, the fourth clutch C 4 46, the third transmission gear 43, the fourth transmission gear 44, the sun gear 33, the planet carrier 32 and the intermediate gear 52 to the output shaft 51 for output;

[0081] Hydraulic mechanical series transmission mode:

[0082]

[0083] Where n o is the output shaft 51 speed, n I is the speed of input shaft 11, i 3 is the transmission ratio of the first transmission gear 41 to the second transmission gear 42, i 4is the transmission ratio of the third transmission gear 43 to the fourth transmission gear 44, i 5 is the transmission ratio between the outer gear ring 31 and the intermediate gear 52, i 6 is the transmission ratio between the intermediate gear 52 and the output shaft 51;

[0084] like Figure 7 As shown, hydraulic mechanical parallel transmission mode: the first clutch C 1 12. Second clutch C 2 23. Fourth clutch C 4 46 and fifth clutch C 5 14 Engagement, while the third clutch C 3 45. Sixth clutch C 6 34 and brake B 1 47 is separated; the power is diverted from the input shaft assembly 1, and the power flows from the input shaft 11 through the second clutch C 2 23 drives the variable displacement pump 21 to work, and the variable displacement pump 21 outputs high-pressure oil to drive the quantitative motor 22 to rotate. The power output by the output shaft of the quantitative motor 22 passes through the first transmission gear 41, the second transmission gear 42, the fourth clutch C 4 46, the third transmission gear 43, the fourth transmission gear 44, the sun gear 33 to the planet carrier 32,

[0085] The other power passes through the first clutch C 1 12. Intermediate gear set 13. Fifth clutch C 5 14. The outer gear ring 31 and the power passing through the hydraulic transmission assembly 2 and the intermediate gear transmission assembly 4 are combined at the planet carrier 32. The combined power is output from the planet carrier 32 and the intermediate gear 52 to the output shaft 51.

[0086] Hydraulic mechanical parallel transmission mode:

[0087]

[0088] Where n o is the output shaft 51 speed, n I is the speed of input shaft 11, i 1 The first clutch C 1 The transmission ratio of 12 and the linkage intermediate gear set 13 is i 2 To link the intermediate gear set 13 and the fifth clutch C 5 14 gear ratio, i 3 is the transmission ratio of the first transmission gear 41 to the second transmission gear 42, i 4 is the transmission ratio of the third transmission gear 43 to the fourth transmission gear 44, i 5 is the transmission ratio between the outer gear ring 31 and the intermediate gear 52, i 6is the transmission ratio between the intermediate gear 52 and the output shaft 51 , k is the characteristic parameter of the gear set in the planetary gear transmission assembly 3 , and e is the displacement ratio of the hydraulic transmission assembly 2 .

[0089] like Figure 8 As shown, the characteristic parameters of each gear pair and planetary gear transmission assembly are set to obtain the speed regulation characteristic curve. Let: i i i 2 =1.0,i 3 i 4 =0.25, i 5 i 6 =1.0, k=3, then

[0090] Hydraulic transmission mode: n o =en I

[0091] Hydraulic mechanical series transmission mode: n o =4en I

[0092] Hydraulic mechanical parallel transmission mode:

[0093] Mechanical transmission 1st gear:

[0094] Mechanical transmission 2nd gear: n o =n I

[0095] Mechanical transmission 3 gears:

[0096] In this specification, each embodiment is described in a progressive manner, and each embodiment focuses on the differences from other embodiments. The same or similar parts between the embodiments can be referred to each other. For the device disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant parts can be referred to the method part.

[0097] The above description of the disclosed embodiments enables one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention will not be limited to the embodiments shown herein, but rather to the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A control method for a transmission device in which hydraulic machinery coexists in series and parallel, characterized in that: The transmission device comprises an input shaft assembly (1), wherein the input shaft assembly (1) comprises an input shaft (11), a first clutch C1 (12), a linkage intermediate gear set (13) and a fifth clutch C5 (14); A hydraulic transmission assembly (2), the hydraulic transmission assembly (2) comprising a variable displacement pump (21), a fixed displacement motor (22) and a second clutch C2 (23), the variable displacement pump (21) being connected to the input shaft (11) via the second clutch C2 (23); A planetary gear transmission assembly (3), the planetary gear transmission assembly (3) comprising an outer ring gear (31), a planet carrier (32), a sun gear (33) and a sixth clutch C6 (34), the sixth clutch C6 (34) being connected to the sun gear (33), and the fifth clutch C5 (14) being connected to the outer ring gear (31); An intermediate gear transmission assembly (4), the intermediate gear transmission assembly (4) comprising a first transmission gear (41), a second transmission gear (42), a third transmission gear (43), a fourth transmission gear (44), a third clutch C3 (45), a fourth clutch C4 (46) and a brake B1 (47), the first transmission gear (41) being fixedly connected to an output shaft of a quantitative motor (22), the first transmission gear (41) being meshed with the second transmission gear (42), the second transmission gear (42) being engaged through the fourth clutch C4 (46) and the brake B1 (47). 6) is connected to the third transmission gear (43), the third transmission gear (43) is meshed with the fourth transmission gear (44), the fourth transmission gear (44) is respectively connected to the sun gear (33) and the brake B1 (47), the output shaft of the quantitative motor (22) is respectively connected to the linkage intermediate gear set (13) through the third clutch C3 (45) and the fifth clutch C5 (14), and the output shaft of the quantitative motor (22) is respectively connected to the sun gear (33) through the third clutch C3 (45) and the sixth clutch C6 (34); An output shaft assembly (5), the output shaft assembly (5) comprising an output shaft (51) and an intermediate gear (52), the output shaft (51) being connected to the planet carrier (32) via the intermediate gear (52); Control method: Switching between hydraulic transmission mode, mechanical transmission mode and hydraulic-mechanical compound transmission mode is achieved through combined switching between clutch and brake; The control method of the hydraulic transmission mode is as follows: The second clutch C2 (23), the third clutch C3 (45) and the sixth clutch C6 (34) are engaged, while the first clutch C1 (12), the fourth clutch C4 (46), the fifth clutch C5 (14) and the brake B1 (47) are disengaged; power is transmitted from the input shaft (11) through the second clutch C2 (23) to drive the variable displacement pump (21) to work, the variable displacement pump (21) outputs high-pressure oil to drive the fixed displacement motor (22) to rotate, and the power output by the output shaft of the fixed displacement motor (22) is sequentially transmitted through the third clutch C3 (45), the sixth clutch C6 (34), the sun gear (33), the planetary carrier (32) and the intermediate gear (52) to the output shaft (51) for output; the mechanical transmission mode includes mechanical transmission 1st gear, mechanical transmission 2nd gear and mechanical transmission 3rd gear, and the specific control method is as follows: Mechanical transmission 1st gear: the first clutch C1 (12), the fifth clutch C5 (14) and the brake B1 (47) are engaged, while the second clutch C2 (23), the third clutch C3 (45), the fourth clutch C4 (46) and the sixth clutch C6 (34) are disengaged; the power is transmitted from the input shaft (11) in sequence through the first clutch C1 (12), the linkage intermediate gear set (13), the fifth clutch C5 (14), the outer ring gear (31), the planetary carrier (32) and the intermediate gear (52) to the output shaft (51); Mechanical transmission 2nd gear: the first clutch C1 (12), the fifth clutch C5 (14) and the sixth clutch C6 (34) are engaged, while the second clutch C2 (23), the third clutch C3 (45), the fourth clutch C4 (46) and the brake B1 (47) are disengaged; the power is transmitted from the input shaft (11) in sequence through the first clutch C1 (12), the linkage intermediate gear set (13), the fifth clutch C5 (14), the sixth clutch C6 (34), the sun gear (33), the planetary carrier (32) and the intermediate gear (52) to the output shaft (51); Mechanical transmission 3rd gear: the first clutch C1 (12), the third clutch C3 (45), the fourth clutch C4 (46) and the fifth clutch C5 (14) are engaged, while the second clutch C2 (23), the sixth clutch C6 (34) and the brake B1 (47) are disengaged; the power is transmitted from the input shaft (11) through the first clutch C1 (12), the linkage intermediate gear set (13) to the fifth clutch C5 (14) in sequence, and then divided into two paths, one path passes through the third clutch C3 (45), the first transmission gear (41), the second transmission gear (42), the fourth clutch C4 (46), the third transmission gear (43), the fourth transmission gear (44), the sun gear (33) to the planetary carrier (32), and the other path passes through the outer ring gear (31) and the power of the intermediate gear transmission assembly (4) and merges with the planetary carrier (32). The merged power is output from the planetary carrier (32) and the intermediate gear (52) to the output shaft (51).

2. The control method of a hydraulic mechanical transmission device in series and parallel coexistence according to claim 1, characterized in that: The hydraulic-mechanical compound transmission mode includes a hydraulic-mechanical series transmission mode and a hydraulic-mechanical parallel transmission mode.

3. The control method of the transmission device in which hydraulic machinery coexists in series and parallel according to claim 2 is characterized in that: The control method of the hydraulic mechanical series transmission mode and the hydraulic mechanical parallel transmission mode is as follows: Hydraulic mechanical series transmission mode: the second clutch C2 (23), the fourth clutch C4 (46) and the sixth clutch C6 (34) are engaged, while the first clutch C1 (12), the third clutch C3 (45), the fifth clutch C5 (14) and the brake B1 (47) are disengaged; power is transmitted from the input shaft (11) through the second clutch C2 (23) to drive the variable displacement pump (21) to work, the variable displacement pump (21) outputs high-pressure oil to drive the quantitative motor (22) to rotate, and the power output by the output shaft of the quantitative motor (22) is sequentially transmitted through the first transmission gear (41), the second transmission gear (42), the fourth clutch C4 (46), the third transmission gear (43), the fourth transmission gear (44), the sun gear (33), the planetary carrier (32) and the intermediate gear (52) to the output shaft (51) for output; Hydraulic mechanical parallel transmission mode: the first clutch C1 (12), the second clutch C2 (23), the fourth clutch C4 (46) and the fifth clutch C5 (14) are engaged, while the third clutch C3 (45), the sixth clutch C6 (34) and the brake B1 (47) are disengaged; power is split from the input shaft assembly (1), one path of power is from the input shaft (11) through the second clutch C2 (23) to drive the variable pump (21) to work, the variable pump (21) outputs high-pressure oil to drive the fixed motor (22) to rotate, and the power output from the output shaft of the fixed motor (22) passes through the first transmission gear (41), the second transmission gear (42), the fourth clutch C4 (46), the third transmission gear (43), the fourth transmission gear (44), the sun gear (33) to the planetary carrier (32), The other power sequentially passes through the first clutch C1 (12), the linkage intermediate gear set (13), the fifth clutch C5 (14), the outer ring gear (31), and the power passing through the hydraulic transmission assembly (2) and the intermediate gear transmission assembly (4) to merge with the planetary carrier (32). The merged power is output from the planetary carrier (32) and the intermediate gear (52) to the output shaft (51).

4. The control method of a hydraulic mechanical transmission device in series and parallel coexistence according to claim 1, characterized in that: The output shaft (51) speed n of the hydraulic transmission mode o The calculation method is as follows: Where n o is the output shaft (51) speed, n I is the rotation speed of the input shaft (11), i5 is the transmission ratio between the outer gear ring (31) and the intermediate gear (52), i6 is the transmission ratio between the intermediate gear (52) and the output shaft (51), and e is the displacement ratio of the hydraulic transmission assembly (2).

5. The control method of a hydraulic mechanical transmission device in series and parallel coexistence according to claim 1, characterized in that: The output shaft (51) of the mechanical transmission 1st gear, the mechanical transmission 2nd gear and the mechanical transmission 3rd gear has a rotation speed n o The calculation method is as follows: Mechanical transmission 1st gear: Where n o is the output shaft (51) speed, n I is the speed of the input shaft (11), i1 is the transmission ratio of the first clutch C1 (12) and the linked intermediate gear set (13), i2 is the transmission ratio of the linked intermediate gear set (13) and the fifth clutch C5 (14), i5 is the transmission ratio of the outer ring gear (31) and the intermediate gear (52), i6 is the transmission ratio of the intermediate gear (52) and the output shaft (51), and k is the characteristic parameter of the gear set in the planetary gear transmission assembly (3); Mechanical transmission 2 gears: Where n o is the output shaft (51) speed, n I is the speed of the input shaft (11), i1 is the transmission ratio between the first clutch C1 (12) and the linked intermediate gear set (13), i2 is the transmission ratio between the linked intermediate gear set (13) and the fifth clutch C5 (14), i5 is the transmission ratio between the outer ring gear (31) and the intermediate gear (52), and i6 is the transmission ratio between the intermediate gear (52) and the output shaft (51); Mechanical transmission 3 gears: Where n o is the output shaft (51) speed, n I is the speed of the input shaft (11), i1 is the transmission ratio of the first clutch C1 (12) and the linked intermediate gear set (13), i2 is the transmission ratio of the linked intermediate gear set (13) and the fifth clutch C5 (14), i3 is the transmission ratio of the first transmission gear (41) and the second transmission gear (42), i4 is the transmission ratio of the third transmission gear (43) and the fourth transmission gear (44), i5 is the transmission ratio of the outer ring gear (31) and the intermediate gear (52), i6 is the transmission ratio of the intermediate gear (52) and the output shaft (51), and k is the characteristic parameter of the gear set in the planetary gear transmission assembly (3).

6. The control method of a hydraulic mechanical transmission device in series and parallel coexistence according to claim 3, characterized in that: The output shaft (51) speed n of the hydraulic mechanical series transmission mode and the hydraulic mechanical parallel transmission mode o The calculation method is as follows: Hydraulic mechanical series transmission mode: Where n o is the output shaft (51) speed, n I is the speed of the input shaft (11), i3 is the transmission ratio of the first transmission gear (41) to the second transmission gear (42), i4 is the transmission ratio of the third transmission gear (43) to the fourth transmission gear (44), i5 is the transmission ratio of the outer ring gear (31) to the intermediate gear (52), and i6 is the transmission ratio of the intermediate gear (52) to the output shaft (51); Hydraulic mechanical parallel transmission mode: Where n o is the output shaft (51) speed, n I is the speed of the input shaft (11), i1 is the transmission ratio of the first clutch C1 (12) and the linked intermediate gear set (13), i2 is the transmission ratio of the linked intermediate gear set (13) and the fifth clutch C5 (14), i3 is the transmission ratio of the first transmission gear (41) and the second transmission gear (42), i4 is the transmission ratio of the third transmission gear (43) and the fourth transmission gear (44), i5 is the transmission ratio of the outer ring gear (31) and the intermediate gear (52), i6 is the transmission ratio of the intermediate gear (52) and the output shaft (51), k is the characteristic parameter of the gear set in the planetary gear transmission assembly (3), and e is the displacement ratio of the hydraulic transmission assembly (2).

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