WO2021164048A1 - Single-pump-controlled dual-motor mechanical and hydraulic composite transmission device - Google Patents

Abstract

A single-pump-controlled dual-motor mechanical and hydraulic composite transmission device, comprising an input member, a planetary gear assembly, an output member, a hydraulic transmission mechanism (6), a power output mechanism (7), a clutch assembly, and a brake assembly. The hydraulic transmission mechanism (6) comprises two constant displacement motors (6-4, 6-7), and the two constant displacement motors (6-4, 6-7) are controlled by a control valve assembly to be connected in series or in parallel. By means of the clutch assembly, the input member is separately connected to the hydraulic transmission mechanism (6) and the planetary gear assembly, the output of one constant displacement motor (6-4, 6-7) is connected to the planetary gear assembly, the output of the other constant displacement motor (6-4, 6-7) is connected to the power output mechanism, and the output member is connected to the planetary gear assembly. The clutch assembly and the brake assembly provide a continuous transmission ratio of the input member to the output member and/or the power output mechanism. This device not only ensures power output, but also has the multi-mode efficient stepless speed change function of a conventional mechanical and hydraulic continuously variable transmission.

Description

A single-pump-controlled dual-motor mechanical-hydraulic composite transmission device Technical field

The present invention relates to the field of automatic transmission devices, in particular to a device with a multifunctional stepless speed change and a power output function.

Background technique

The operating conditions of construction vehicles are complex and the environment is harsh, which not only involves starting, operating and transition conditions, but also requires the operating vehicle to have both continuously variable transmission and power output functions, and the two can achieve reasonable power matching. At present, it is difficult for working vehicles with mechanical hydraulic stepless speed change function and power output function to achieve the desired effect under the above-mentioned three occasions.

The different modes of the speed change device are suitable for different working conditions. The single pump controlled double motor stepless speed change device adopted in the present invention has designed two transmission modes for different working conditions. For the working conditions, a large torque transmission mode is adopted. Satisfy the power required during operation and improve operation efficiency; adopt high-speed transmission mode for transition conditions to meet the required speed during transition and shorten the transition time.

The traditional mechanical hydraulic continuously variable transmission hydraulic system has a limited working range and a single adjustment accuracy. For low-speed operations, the vehicle needs to be kept running smoothly, so high-precision adjustment is required; and in the case of a transition, a wide range is required. The adjustment range of the hydraulic system is adapted to the needs of high-speed operation of the vehicle.

Summary of the invention

In view of the shortcomings in the prior art, the present invention provides a single-pump-controlled dual-motor mechanical-hydraulic composite transmission device. On the basis of ensuring power output, it combines the traditional mechanical-hydraulic continuously variable transmission with multi-mode high-efficiency continuously variable transmission. Function.

The present invention achieves the above-mentioned technical objects through the following technical means.

A single-pump-controlled dual-motor mechanical-hydraulic composite transmission device includes an input member, a planetary gear assembly, an output member, a hydraulic transmission mechanism, a power output mechanism, a clutch assembly, and a brake assembly. The hydraulic transmission mechanism includes two quantitative motors, The two quantitative motors are controlled in series or in parallel through the control valve assembly; the clutch assembly connects the input member to the hydraulic transmission mechanism and the planetary gear assembly, connects the output of a quantitative motor to the planetary gear assembly, and connects The output of the other quantitative motor is connected with the power output mechanism, connecting the output member with the planetary gear assembly, and the clutch assembly and the brake assembly provide a continuous transmission ratio between the input member and the output member and/or the power output mechanism.

Further, the planetary gear assembly includes a second planetary gear mechanism, a third planetary gear mechanism, a fourth planetary gear mechanism, and a first planetary gear mechanism; an output of the quantitative motor is connected to the ring gear of the first planetary gear mechanism , The planet carrier of the first planetary gear mechanism is connected with the ring gear of the second planetary gear mechanism, the sun gear of the first planetary gear mechanism is connected with the sun gear of the second planetary gear mechanism, and the sun gear of the second planetary gear mechanism is connected with the third The sun gear of the planetary gear mechanism is connected, the ring gear of the third planetary gear mechanism is connected with the sun gear of the fourth planetary gear mechanism, and the output of the other quantitative motor is connected with the ring gear of the fourth planetary gear mechanism; the clutch assembly At least one of the planet carrier of the first planetary gear mechanism, the planet carrier of the third planetary gear mechanism, and the planet carrier of the fourth planetary gear mechanism is connected to the output member; the clutch assembly connects the planet carrier of the second planetary gear mechanism or The sun gear of the third planetary gear mechanism is connected with the input member.

Further, by adjusting the displacement ratio of the hydraulic transmission mechanism and selectively controlling the engagement of the clutch assembly, the control valve assembly and the brake assembly, the transmission modes between the input member and the output member include: hydraulic transmission, mechanical transmission and mechanical hydraulic pressure transmission.

Further, the clutch assembly includes a third clutch C ₃ , a fourth clutch C ₄ , a sixth clutch C ₆ and a seventh clutch C ₇ ; the third clutch C _{3 is} used to selectively connect the first planetary gear mechanism The planet carrier is connected to the output member for common rotation; the fourth clutch C _{4 is} used to selectively connect the planet carrier of the third planetary gear mechanism to the output member for common rotation; the sixth clutch C _{6 is} used to selectively Connect the ring gear of the first planetary gear mechanism to one of the fixed-rate motors for common rotation; the seventh clutch C _{7 is} used to selectively connect the ring gear of the fourth planetary gear mechanism to the other fixed-rate motor To rotate together

The brake assembly includes a first brake B ₁ , a second brake B ₂ , a third brake B ₃ and a fourth brake B ₄ , and the first brake B _{1 is} used to selectively turn the ring gear of the first planetary gear mechanism Is connected to the fixed part; the second brake B _{2 is} used to selectively connect the planet carrier of the third planetary gear mechanism to the fixed part; the third brake B _{3 is} used to selectively connect the fourth planetary gear mechanism The planet carrier is connected to the fixed part; the fourth brake B _{4 is} used to selectively connect the ring gear of the fourth planetary gear mechanism to the fixed part;

The control valve assembly includes a first reversing valve and a second reversing valve. The first reversing valve is used to control the forward and reverse rotation of a quantitative motor, and the second reversing valve is used to control two of the quantitative motors. Motors in series or parallel;

By adjusting the displacement ratio of the hydraulic transmission mechanism, the third clutch C ₃ , the fourth clutch C ₄ , the sixth clutch C ₆ , the seventh clutch C ₇ , the first brake B ₁ , and the second brake B _{2 are selectively controlled.} the third brake B ₃ and the fourth brake B is engaged, and ₄ selectively controlling the first valve and the second valve, there is provided a hydraulic transmission between the input member and the output member.

Further, the third clutch C ₃ , the fourth clutch C ₄ , the sixth clutch C ₆ , the third brake B ₃ and the fourth brake B _{4 are} engaged, and the third clutch C ₃ , the seventh clutch C ₇ , The first brake B ₁ , the second brake B ₂ and the third brake B ₃ respectively provide hydraulic transmission modes with different forward or reverse directions between the input member and the output member.

Further, the clutch assembly further includes a first clutch C ₁ , a second clutch C ₂ and a fifth clutch C ₅ ; the first clutch C _{1 is} used to selectively connect the input member to the planets of the second planetary gear mechanism The second clutch C _{2 is} used to selectively connect the input member to the sun gear of the third planetary gear mechanism for common rotation; the fifth clutch C _{5 is} used to selectively connect the fourth planet The planet carrier of the gear mechanism is connected to the output member for common rotation;

By selectively controlling the first clutch C ₁ , the second clutch C ₂ , the third clutch C ₃ , the fourth clutch C ₄ , the fifth clutch C ₅ , the first brake B ₁ , the second brake B ₂ , and the third The engagement of the brake B ₃ and the fourth brake B ₄ provides a mechanical transmission mode for forward or backward movement between the input member and the output member.

Further, engaging the second clutch C ₂ , the fourth clutch C ₄ , the third brake B _3, and the fourth brake B ₄ provides a mechanical transmission mode for retreating between the input member and the output member;

Engage the second clutch C ₂ , the fifth clutch C ₅ , the second brake B ₂ and the fourth brake B ₄ , engage the first clutch C ₁ , the third clutch C ₃ and the first brake B ₁ , engage the The first clutch C ₁ , the third clutch C ₃ , the fourth clutch C ₄ , the third brake B ₃ and the fourth brake B ₄ , the second clutch C ₂ , the fourth clutch C ₄ , the fifth clutch C ₅ and The fourth brake B ₄ respectively provides different mechanical transmission modes for forward movement between the input member and the output member.

Further, the second clutch C ₂ , the third clutch C ₃ and the sixth clutch C _{6 are} engaged, the first clutch C ₁ , the third clutch C ₃ and the sixth clutch C _{6 are} engaged, and the first clutch C ₁ and the third clutch are engaged C ₃ , the fourth clutch C ₄ , the seventh clutch C ₇ and the third brake B ₃ , the second clutch C ₂ , the fifth clutch C ₅ , the seventh clutch C ₇ and the second brake B ₂ are engaged, respectively providing input members A mechanical hydraulic transmission method that is different from the forward or reverse of the output member.

Further, by controlling the linear change of the displacement ratio of the hydraulic transmission mechanism and selectively controlling the combination of the clutch and the brake, the hydraulic transmission is converted into a hydromechanical transmission.

Further, the clutch assembly includes an eighth clutch C ₈ and a ninth clutch C ₄ , the eighth clutch C _{8 is} used to selectively connect the output of a fixed amount motor to the power output mechanism for common rotation; the ninth clutch C 8 Clutch C _{4 is} used to selectively connect the output of another quantitative motor to the power output mechanism for common rotation; selectively control the coupling of the eighth clutch C ₈ or the ninth clutch C ₄ , and selectively control the coupling of the valve assembly, providing The continuous transmission ratio between the input member and the power take-off mechanism.

The beneficial effects of the present invention are:

The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device of the present invention has three transmission modes: hydraulic, mechanical hydraulic and mechanical. Multiple gears are available for selection. The clutch, brake and hydraulic valve can be switched to meet various working conditions. Simple and reliable; adopts a single pump control double motor structure, which can not only choose different input modes in the mechanical-hydraulic transmission, but also solve the power matching problem between the output shaft and the power output shaft, and improve the work efficiency; this structure can change the two motors When the two are connected in parallel, the output torque is large, and the displacement ratio of the pump and the motor is adjusted with high accuracy, which is suitable for low-speed working conditions; when the two are connected in series, the output speed is high. The displacement ratio is larger than the adjustment range, which is suitable for high-speed transition conditions.

Description of the drawings

Figure 1 is a diagram of the single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to the present invention.

Figure 2 is a schematic diagram of the power flow of the low-speed forward hydraulic transmission of the present invention;

Figure 3 is a schematic diagram of the power flow of the low-speed reverse hydraulic transmission of the present invention;

Figure 4 is a schematic diagram of the power flow of the high-speed forward hydraulic transmission of the present invention;

Figure 5 is a schematic diagram of the power flow of the high-speed reverse hydraulic transmission of the present invention;

Fig. 6 is a schematic diagram of the power flow of the mechanical reverse gear of the present invention;

Figure 7 is a schematic diagram of the power flow of the first gear of the machine of the present invention;

Figure 8 is a schematic diagram of the power flow of the second gear of the machine of the present invention;

Figure 9 is a schematic diagram of the power flow of the third gear of the machine of the present invention;

Fig. 10 is a schematic diagram of the power flow of the 4th gear of the machine of the present invention;

Figure 11 is a schematic diagram of the power flow of the low-speed reverse mechanical-hydraulic composite transmission of the present invention;

Figure 12 is a schematic diagram of the power flow of the low-speed forward mechanical-hydraulic composite transmission of the present invention;

Fig. 13 is a schematic diagram of the power flow in the first gear of the high-speed forward mechanical-hydraulic compound transmission of the present invention;

Fig. 14 is a schematic diagram of the power flow of the high-speed forward mechanical-hydraulic compound transmission of the present invention with 2 gears;

15 is a schematic diagram of the power flow of the power output (mode 1) of the present invention;

Figure 16 is a schematic diagram of the power flow of the power output (mode 2) of the present invention;

Figure 17 is a low-speed transmission diagram of the present invention;

Figure 18 is a high-speed transmission diagram of the present invention;

In the picture:

1- Input shaft; 2- Splitter mechanism; 2- 1- Splitter gear pair; 3- Second planetary gear mechanism; 3- 1- Second planetary gear sun gear; 3-2 Second planetary gear ring gear; 3- 3-second planetary gear carrier; 3-4-second planetary carrier gear pair; 3-5-first clutch C ₁ ; 4-third planetary gear mechanism; 4-1-2 second clutch C ₂ ; 4-2-Third planetary gear sun gear pair; 4-3-Second brake B ₂ ; 4-4-Third planetary gear sun gear; 4-5-Third planetary gear carrier; 4-6-No. Three planetary gear ring gear; 4-7-fourth clutch C ₄ ; 5-fourth planetary gear mechanism; 5-1-5 third brake B ₃ ; 5-2-fourth brake B ₄ ; 5-3-fourth Planetary gear ring gear; 5-4-fourth planetary gear sun gear; 5-5-fourth planetary gear carrier; 5-6-fifth clutch C ₅ ; 5-7-fourth planetary gear ring gear input gear pair ; 5-8-seventh clutch C ₇ ; 6-hydraulic transmission mechanism; 6-1-one-way pump P; 6-2-overflow valve V ₁ ; 6-3-one-way valve V ₂ ; 6-4- quantitative motor M _1; 6-5- three-way solenoid valve V _3; 6-6- two-way solenoid valve V _4; 6-7- quantitative motor M _2; 7- power output mechanism; 7-1- Front PTO gear pair; 7-2-Eighth clutch C ₈ ; 7-3-Rear PTO gear pair; 7-4-Ninth clutch C ₉ ; 7-5-PTO shaft; 8-First planetary gear Mechanism; 8-1-sixth clutch C ₆ ; 8-2-first planetary gear ring gear input gear pair; 8-3-first planetary gear ring gear; 8-4-first brake B ₁ ; 8-5 -The third clutch C ₃ ; 8-6-the first planetary gear carrier; 8-7-the first planetary gear sun gear; 9-the output shaft.

Detailed ways

The present invention will be further described below with reference to the drawings and specific embodiments, but the protection scope of the present invention is not limited to this.

As shown in Figure 1, the single-pump-controlled dual-motor mechanical-hydraulic composite transmission device of the present invention includes an input shaft 1, a splitter mechanism 2, a second planetary gear mechanism 3, a third planetary gear mechanism 4, and a fourth planetary gear mechanism 5. Hydraulic transmission mechanism 6, power output mechanism 7, first planetary gear mechanism 8, output shaft 9, clutch assembly and brake assembly;

The hydraulic transmission mechanism 6 includes a one-way pump P 6-1, an overflow valve V ₁ 6-2, a one-way valve V ₂ 6-3, a quantitative motor M ₁ 6-4, and a three-position four-way solenoid valve V ₃ 6 -5. Two-position four-way solenoid valve V ₄ 6-6 and quantitative motor M ₂ 6-7; the input end of the one-way pump P 6-1 and the input shaft 1 pass through the shunt mechanism gear pair 2-1 of the shunt mechanism 2 The output end of the quantitative motor M ₁ 6-4 is connected with the first planetary gear ring gear 8-3 through the first planetary gear ring gear input gear pair 8-2, and the output end of _{the quantitative motor M 2 6-7 passes through} The fourth planetary gear ring gear input gear pair 5-7 is connected to the fourth planetary gear ring gear 5-3. The outlet of the one-way pump P 6-1 is connected to the overflow valve V ₁ 6-2, the one-way valve V ₂ 6-3 and the three-position four-way solenoid valve V ₃ 6-5 in turn; the three-position four-way solenoid valve V ₃ 6- the outlet 5 is connected to the fixed displacement motor and the fixed displacement motor M ₁ 6-4 M ₂ 6-7, connected by two-way solenoid valve V ₄ 6-6 quantitative control of the motor M ₁ 6-4 and quantification of the motor M ₂ 6-7 relationship, when the two-way solenoid valve V ₄ 6-6 remains normal, the motor M ₁ 6-4 quantitative and quantitative motor M ₂ 6-7 are connected in parallel, when the two-way solenoid valve V ₄ 6-6 energized , The fixed motor M ₁ 6-4 and the fixed motor M ₂ 6-7 are connected in series. The three-position four-way solenoid valve V ₃ 6-5 is used to control the direction of rotation of the _{quantitative motor M 1} 6-4 and the quantitative motor M _{2 6-7.}

The first planetary gear mechanism 8 comprises a sixth clutch C ₆ 8-1, a first planetary gear sub-gear input gear 8-2, 8-3 ring gear of the first planetary gear, the first brake B ₁ 8-4, The third clutch C ₃ 8-5, the first planetary gear carrier 8-6, and the first planetary gear sun gear 8-7. The first planetary gear ring gear 8-3, the first planetary gear carrier 8-6, and the first planetary gear sun gear 8-7 constitute a planetary gear structure; the first planetary gear ring gear 8-3 passes through the first planetary gear The planetary gear ring gear input gear pair 8-2 is connected to the output end of the _{fixed amount motor M 1 6-4, and the sixth clutch C 6} 8-1 is used to selectively connect the first planetary gear ring gear 8-3 to the fixed amount motor. The motor M ₁ 6-4 rotates together; the first planetary gear carrier 8-6 is connected to the second planetary gear ring gear 3-2, the first planetary gear sun gear 8-7, the second planetary gear sun The wheel 3-1 and the third planetary gear sun gear 4-4 are connected as one body. The third clutch C ₃ 8-5 is used to selectively connect the first planetary gear carrier 8-6 to the output shaft 9 for common rotation; the first brake B ₁ 8-4 is used to selectively connect The first planetary gear ring gear 8-3 is connected to the fixed member.

The second planetary gear mechanism 3 includes a second planetary gear sun gear 3-1, a second planetary gear ring gear 3-2, a second planetary gear carrier 3-3, and a second planetary gear carrier gear pair 3-4 And the first clutch C ₁ 3-5. The second planetary gear sun gear 3-1, the second planetary gear ring gear 3-2, and the second planetary gear carrier 3-3 constitute a planetary gear structure; the input shaft 1 passes through the second planetary gear carrier gear pair 3-4 is connected with the second planetary gear carrier 3-3. The first clutch C ₁ 3-5 is used to selectively connect the input shaft 1 to the second planetary gear carrier 3-3 for common rotation.

The third planetary gear mechanism 4 includes a second clutch C ₂ 4-1, a third planetary gear sun gear pair 4-2, a second brake B ₂ 4-3, a third planetary gear sun gear 4-4, and a third planetary gear sun gear 4-4. The three planetary gear carrier 4-5, the third planetary gear ring gear 4-6 and the fourth clutch C ₄ 4-7, the third planetary gear sun gear 4-4, the third planetary gear carrier 4-5, The third planetary gear ring gear 4-6 constitutes a planetary gear structure; the input shaft 1 is connected to the third planetary gear sun gear 4-4 through the third planetary gear sun gear pair 4-2; the second clutch C ₂ 4-1 is used to selectively connect the input shaft 1 to the third planetary gear sun gear 4-4 for common rotation; the second brake B ₂ 4-3 is used to selectively connect the third planetary gear carrier 4 -5 is connected to the fixed part; the fourth clutch C ₄ 4-7 is used to selectively connect the third planetary gear carrier 4-5 to the output shaft 9 for common rotation; the third planetary gear ring 4 -6 is fixedly connected with the fourth planetary gear sun gear 5-4.

The fourth planetary gear mechanism 5 includes a third brake B ₃ 5-1, a fourth brake B ₄ 5-2, a fourth planetary gear ring gear 5-3, a fourth planetary gear sun gear 5-4, and a fourth planetary gear. The planetary gear carrier 5-5, the fifth clutch C ₅ 5-6, the fourth planetary gear ring gear input gear pair 5-7, and the seventh clutch C ₇ 5-8, the fourth planetary gear ring gear 5-3, The fourth planetary gear sun gear 5-4 and the fourth planetary gear carrier 5-5 constitute a planetary gear structure, and the third brake B ₃ 5-1 is used to selectively connect the fourth planetary gear carrier 5-5 To the fixed part; the fourth brake B ₄ 5-2 is used to selectively connect the fourth planetary gear ring gear 5-3 to the fixed part; the fourth planetary gear ring gear 5-3 passes through the fourth planetary gear The ring gear input gear pair 5-7 is connected with the output end of the _{fixed motor M 2 6-7.} The fifth clutch C ₅ 5-6 is used to selectively connect the fourth planetary gear carrier 5-5 to the output shaft 9 for common rotation; the seventh clutch C ₇ 5-8 is used to selectively connect The fourth planetary gear ring gear 5-3 is connected to the fixed amount motor M ₂ 6-7 for common rotation.

The power output mechanism 7 includes a front power output gear pair 7-1, an eighth clutch C ₈ 7-2, a rear power output gear pair 7-3, a ninth clutch C ₉ 7-4, and a power output shaft 7-5; The output end of the fixed motor M ₁ 6-4 is connected to the power output shaft 7-5 through the front power output gear pair 7-1, and the _{output end of the fixed motor M 2} 6-7 is connected to the power output shaft 7-5 through the rear power output gear pair 7-3. The power output shaft 7-5 is connected; the eighth clutch C ₈ 7-2 is used to selectively _{connect the output of the quantitative motor M 1} 6-4 to the power output shaft 7-5 for common rotation; the ninth clutch The C ₄ 7-4 is used to selectively _{connect the output of the fixed motor M 2} 6-7 to the power output shaft 7-5 for common rotation.

By adjusting the displacement ratio of the hydraulic transmission mechanism 6 and selectively controlling the engagement of the clutch assembly, the control valve assembly and the brake assembly, the transmission modes between the input member and the output member include: hydraulic transmission, mechanical transmission and mechanical hydraulic transmission . Specific examples are given below in conjunction with Table 1:

Hydraulic transmission includes forward low-speed hydraulic transmission, reverse low-speed hydraulic transmission, forward high-speed hydraulic transmission and reverse high-speed hydraulic transmission.

As shown in Figures 2 and 17, the forward low-speed hydraulic transmission: only engages the third clutch C ₃ 8-5, the fourth clutch C ₄ 4-7, the sixth clutch C ₆ 8-1, and the third brake B ₃ 5- 1. The fourth brake B ₄ 5-2, the three-position four-way solenoid valve V ₃ 6-5 is energized at the right position, and the two-position four-way solenoid valve V ₄ 6-6 is in the normal position; the power of the input shaft 1 passes through the shunt mechanism gear vice 2-2, unidirectional pump P 6-1, fixed displacement motors M ₁ 6-4, and the sixth clutch C ₆ 8-1 ring gear of the first planetary gear is transmitted to the input gear pair 8-2 ring gear of the first planetary gear 8-3, part of the power is transmitted to the output shaft 9 through the first planetary gear carrier 8-6 and the third clutch C ₃ 8-5; the other part of the power is transmitted through the first planetary gear sun gear 8-7 and the third planetary gear sun The wheel 4-4, the third planetary gear carrier 4-5 and the fourth clutch C ₄ 4-7 are transmitted to the output shaft 9, and the steering of the input shaft 1 and the output shaft 9 are the same within the set displacement ratio range, At this time, the working condition is the CD section in Fig. 17.

As shown in Figures 3 and 17, in the same way, when the three-position four-way solenoid valve V ₃ 6-5 is energized in the left position, the positions of other devices remain unchanged, and the quantitative motor M ₁ 6-4 reverses, and the input shaft 1 and output The rotation of the shaft 9 is opposite within the range of the set displacement ratio, and the reverse low-speed hydraulic transmission is realized. At this time, the working condition is working in the BC section.

As shown in Figures 4 and 17, forward high-speed hydraulic transmission: engage the third clutch C ₃ 8-5, the seventh clutch C ₇ 5-8, the first brake B ₁ 8-4, and the second brake B ₂ 4-3 And the third brake B ₃ 5-1; the three-position four-way solenoid valve V ₃ 6-5 is energized at the right position, and the two-position four-way solenoid valve V ₄ 6-6 is energized, and the power of the input shaft 1 is transmitted to the hydraulic drive through the shunt mechanism 2. The input end of mechanism 6, via fixed motor M ₂ 6-7, seventh clutch C ₇ 5-8, fourth planetary gear ring gear input gear pair 5-7, fourth planetary gear ring gear 5-2, fourth planetary gear Sun gear 5-4, third planetary gear ring gear 4-6, third planetary gear sun gear 4-4, first planetary gear sun gear 8-7, first planetary gear carrier 8-6, and third clutch C ₃ 8-5 is transmitted to the output shaft 9, and the steering of the input shaft 1 and the output shaft 9 are the same within the set displacement ratio range. At this time, the working condition is the GH section in Fig. 17.

As shown in Figures 5 and 17, in the same way, when the three-position four-way solenoid valve V ₃ 6-5 is energized in the left position, the positions of other devices remain unchanged, and the quantitative motor M ₂ 6-7 reverses, and the input shaft 1 and the output The rotation of the shaft 9 is opposite within the range of the set displacement ratio, and the reverse high-speed hydraulic transmission is realized. At this time, the FG section in the working condition in Fig. 17 is realized.

Mechanical transmission includes reverse gear, mechanical 1 gear, mechanical 2 gear, mechanical 3 gear, and mechanical 4 gear.

As shown in Figures 6 and 17, mechanical reverse gear: engage the second clutch C ₂ 4-1, the fourth clutch C ₄ 4-7, the third brake B ₃ 5-1 and the fourth brake B ₄ 5-2, because The third brake B ₃ 5-1 and the fourth brake B ₄ 5-2 are engaged, the fourth planetary gear mechanism 5 is locked as a whole, and the third planetary gear ring gear 4-6 is also locked. Power goes through the input shaft 1, the second clutch C ₂ 4-1, the third planetary gear sun gear pair 4-2, the third planetary gear sun gear 4-4, the third planetary gear carrier 4-5 and the fourth clutch C ₄ 4-7 is transmitted to the output shaft 9, and the input shaft 1 and the output shaft 9 rotate in opposite directions. At this time, point B in the working condition in FIG. 17.

As shown in Figures 7 and 18, mechanical first gear: engage the second clutch C ₂ 4-1, the fifth clutch C ₅ 5-6, the second brake B ₂ 4-3 and the fourth brake B ₄ 5-2, power Via the input shaft 1, the second clutch C ₂ 4-1, the third planetary gear sun gear pair 4-2, the third planetary gear sun gear 4-4, the third planetary gear ring gear 4-6, and the fourth planetary gear The sun gear 5-4, the fourth planetary gear carrier 5-5, and the fifth clutch C ₅ 5-6 are transmitted to the output shaft 9, and the input shaft 1 and the output shaft 9 rotate in the same direction. I point.

As shown in Figures 8 and 18, mechanical second gear: engage the first clutch C ₁ 3-5, the third clutch C ₃ 8-5 and the first brake B ₁ 8-4, the power passes through the input shaft 1, the second planetary gear The planet carrier gear pair 3-5 is transmitted to the second planetary gear carrier 3-3, and part of the power is transmitted to the first planetary gear carrier 8 through the second planetary gear sun gear 3-1 and the first planetary gear sun gear 8-7 -6, the other part of the power is transmitted to the first planetary gear carrier 8-6 through the second planetary gear ring 3-2, and the power converged to the first planetary gear carrier 8-6 is through the third clutch C ₃ 8-5 It is transmitted to the output shaft 9, and the rotation of the input shaft 1 and the output shaft 9 are the same. At this time, the operation in Fig. 18 is at point J.

As shown in Figures 9, 17 and 18, the mechanical third gear: engage the first clutch C ₁ 3-5, the third clutch C ₃ 8-5, the fourth clutch C ₄ 4-7, and the third brake B ₃ 5-1 And the fourth brake B ₄ 5-2, because the fourth planetary mechanism 5 is locked, the third planetary gear ring gear 4-6 is also locked, and the power is transmitted to the _{first clutch C 1 3-5 through the input shaft 1, the first clutch C 1 3-5} Two planetary gear carrier gear pair 3-4, part of the power is transmitted to the third planetary gear carrier 4-5 via the second planetary gear sun gear 3-1 and the third planetary gear sun gear 4-4, and the other part of the power is transmitted via the second planetary gear sun gear 3-1 and the third planetary gear sun gear 4-4. The second planetary gear ring 3-2, the first planetary gear carrier 8-6 and the third clutch C ₃ 8-5 are transmitted to the first planetary gear carrier 8-6, because the third clutch C ₃ 8-5 and the third clutch C 3 8-5 The four clutches C ₄ 4-7 are connected to the output shaft 9 and are in the engaged state at the same time. The power is output through the output shaft 9. The input shaft 1 and the output shaft 9 rotate in the same direction. point.

As shown in Figures 10 and 18, mechanical fourth gear: engage the second clutch C ₂ 4-1, the fourth clutch C ₄ 4-7, the fifth clutch C ₅ 5-6 and the fourth brake B ₄ 5-2, power It is transmitted to the third planetary gear sun gear 4-4 through the input shaft 1 and the second clutch C ₂ 4-1, and part of the power is transmitted through the third planetary gear ring gear 4-6, the fourth planetary gear sun gear 5-4 and the fourth planetary gear ring gear 4-6. The planetary gear carrier 5-5 is transmitted to the fifth clutch C ₅ 5-6, and the other part of the power is transmitted to the fourth clutch C ₄ 4-7 via the third planetary gear carrier 4-5. The fourth clutch C ₄ 4- 7 and the fifth clutch C ₅ 5-6 are connected with the output shaft 9 and are in the engaged state at the same time. The power is output through the output shaft 9. The input shaft 1 and the output shaft 9 rotate in the same direction. point.

Mechanical hydraulic transmission includes low-speed forward mechanical-hydraulic compound transmission, low-speed reverse mechanical-hydraulic compound transmission, high-speed mechanical-hydraulic compound transmission 1st gear and high-speed mechanical-hydraulic compound transmission 2nd gear.

As shown in Figures 11 and 17, the low-speed reverse mechanical-hydraulic compound transmission: engage the second clutch C ₂ 4-1, the third clutch C ₃ 8-5 and the sixth clutch C ₆ 8-1, three-position four-way solenoid valve The right position is energized V ₃ 6-5, the two-position four-way solenoid valve V ₄ 6-6 is in the normal position, and a part of the power transmitted to the input shaft 1 passes through the shunt mechanism 2, the hydraulic transmission mechanism 6, and the sixth clutch C ₆ 8-1 And the first planetary gear ring gear input gear pair 8-2, which is transmitted to the first planetary gear ring gear 8-3, and the other part of the power is passed through the second clutch C ₂ 4-1 and the third planetary gear sun gear pair 4-2 , The hydraulic power transmitted to the first planetary gear sun gear 8-7, the hydraulic power transmitted to the first planetary gear ring gear 8-3 and the mechanical power transmitted to the first planetary gear sun gear 8-7 in the first planetary gear carrier 8- 6 merges and is transmitted to the output shaft 9 through the third clutch C ₃ 8-5. At this time, it works in section AB in Fig. 17 under this working condition.

As shown in Figures 12 and 17, the low-speed forward mechanical-hydraulic compound transmission: engage the first clutch C ₁ 3-5, the third clutch C ₃ 8-5, the sixth clutch C ₆ 8-1, three-position four-way solenoid valve The right position is energized V ₃ 6-5, the two-position four-way solenoid valve V ₄ 6-6 is in the normal position, and a part of the power transmitted to the input shaft 1 passes through the shunt mechanism 2, the hydraulic transmission mechanism 6, and the sixth clutch C ₆ 8-1 And the first planetary gear ring gear input gear pair 8-2, which is transmitted to the first planet gear ring gear 8-3, and the other part of the power is transmitted through the first clutch C ₁ 3-5 and the second planetary gear carrier gear pair 3-4 , Is transmitted to the second planetary gear carrier 3-3, at this time the power is divided again, all the way through the second planetary gear sun gear 3-1 to the first planetary gear sun gear 8-7, all the way through the second planetary gear ring gear 3-2 The hydraulic power transmitted to the first planetary gear carrier 8-6, the hydraulic power transmitted to the first planetary gear ring gear 8-3, and the first planetary gear sun gear 8-7 and the first planetary gear carrier 8 The mechanical power of -6 is _{transmitted to the output shaft 9 through the third clutch C 3} 8-5. At this time, it works in the DE section in Fig. 17 under this working condition.

As shown in Figures 13 and 18, the high-speed forward mechanical-hydraulic compound transmission 1st gear: engage the first clutch C ₁ 3-5, the third clutch C ₃ 8-5, the fourth clutch C ₄ 4-7, and the seventh clutch C ₇ 5-8. The third brake B ₃ 5-1, the three-position four-way solenoid valve V ₃ 6-5 is energized in the right position, the two-position four-way solenoid valve V ₄ 6-6 is energized, and a part of the power transmitted by the input shaft 1 is energized. The shunt mechanism 2 is transmitted to the hydraulic transmission mechanism 6, through the seventh clutch C ₇ 5-8, the fourth planetary gear ring gear input gear pair 5-7, the fourth planetary gear ring gear 5-3, and the fourth planetary gear sun gear 5 -4, transmitted to the third planetary gear ring gear 4-6, the other part of the power transmitted by the input shaft 1 is through the first clutch C ₁ 3-6, the second planetary gear carrier gear pair 3-4 and the second planetary gear planet The carrier 3-3 is divided into two parts, one part is connected to the output shaft 9 through the second planetary gear ring 3-2, the first planetary gear carrier 8-6 and the third clutch C ₃ 8-5, and the other part is connected to the output shaft 9 through the second planetary gear ring 3-2. The planetary gear sun gear 3-1, the third planetary gear sun gear 4-4 and the hydraulic power from the third planetary gear ring gear 4-6 converge to the third planetary gear carrier 4-5, due to the third clutch C ₃ 8 -5 and the fourth clutch C ₄ 4-7 are connected to the output shaft 9 and are in the engaged state at the same time, and the power is output through the output shaft 9. At this time, it works in the HK section in FIG. 18 under this working condition.

As shown in Figures 14 and 18, the high-speed forward mechanical-hydraulic compound transmission 2nd gear: engage the second clutch C ₂ 4-1, the fifth clutch C ₅ 5-6, the seventh clutch C ₇ 5-8, and the second brake B ₂ 4-3, the right position of the _three -position four-way solenoid valve is energized V 3 6-5, the two-position four-way solenoid valve is energized V ₄ 6-6, part of the power transmitted by the input shaft 1 is transmitted to the hydraulic transmission mechanism 6 through the shunt mechanism 2 , Through the seventh clutch C ₇ 5-8 and the fourth planetary gear ring gear input gear pair 5-7, transmitted to the fourth planetary gear ring gear 5-3; the other part of the power transmitted by the input shaft 1 through the second clutch C ₂ 4-1. The third planetary gear sun gear pair 4-2, the third planetary gear sun gear 4-4, and the third planetary gear ring gear 4-6 are transmitted to the fourth planetary gear sun gear 5-4. The hydraulic power transmitted by the four planetary gear ring gear 5-3 and the mechanical power transmitted by the fourth planetary gear sun gear 5-4 converge at the fourth planetary gear carrier 5-5 and pass through the fifth clutch C ₅ 5-6. The output shaft 9 outputs. At this time, it works in the KN section in Fig. 18 under this working condition.

Table 1 Joining table of each component

In the table: 1. "B" stands for brake, "C" stands for clutch, and "V" stands for hydraulic valve;

2. "▲" represents the shifting element is engaged, and "△" represents the shifting element is separated.

15, a power output: motor M ₁ 6-4 quantitative and quantitative motor M ₂ 6-7 in a parallel state, when the motor M ₁ 6-4 quantitative and quantitative large torque motor M ₂ 6-7 , The specific implementation is as follows: the three-position four-way solenoid valve V ₃ 6-5 is energized in the right position, the two-position four-way solenoid valve V ₄ 6-6 is in the normal position, the ninth clutch C ₉ 7-4 is engaged, and the power is passed through the fixed motor M ₂ 6-7. The rear power output gear pair 7-3 is transmitted to the power output shaft 7-5. This working condition is suitable for working scenarios with high torque requirements.

16, two power output: motor M ₁ 6-4 quantitative and quantitative motor M ₂ 6-7 in the series state, when the motor M ₁ 6-4 quantitative and quantitative high speed motor M ₂ 6-7, The specific implementation is as follows: the three-position four-way solenoid valve V ₃ 6-5 is energized at the right position, the two-position four-way solenoid valve V ₄ 6-6 is energized, the eighth clutch C ₈ 7-2 is engaged, and the power is _{passed through the fixed motor M 1} 6- 4. The front power output gear pair 7-1 is transmitted to the power output shaft 7-5.

The following describes the transmission relationship:

Low-speed hydraulic pressure: The relationship between the rotational speed of the input shaft 1 and the output shaft 9 is:

High-speed hydraulic pressure: The relationship between the speed of input shaft 1 and output shaft 9 is:

Low-speed reverse mechanical-hydraulic compound transmission: The rotational speed relationship between input shaft 1 and output shaft 9 is:

Low-speed forward mechanical-hydraulic compound transmission: The relationship between the rotational speeds of the input shaft 1 and the output shaft 9 is:

High-speed forward mechanical-hydraulic compound transmission 1st gear: The relationship between the speed of input shaft 1 and output shaft 9 is:

High-speed forward mechanical-hydraulic compound transmission 2nd gear: The relationship between the speed of input shaft 1 and output shaft 9 is:

In the above formulas: n _o is the rotation speed of the output shaft 9, n _e is the rotation speed of the input shaft 1, and e ₁ is the one-way pump 6-1 displacement and fixed displacement motor M ₁ 6-4 and fixed displacement motor M ₂ 6-7 row The ratio of the sum of the quantities, e ₂ is the ratio of the displacement of the one-way pump 6-1 to the displacement of the fixed motor M ₂ 6-7, k ₁ , k ₂ , k ₃ , and k ₄ are the first planetary gear characteristic parameters, The characteristic parameters of the second planetary gear, the characteristic parameters of the third planetary gear, and the characteristic parameters of the fourth planetary gear, i ₁ is the gear ratio of the split mechanism gear pair 2-1, i ₂ is the second planetary gear carrier gear pair 3 -4 gear ratio, i ₃ is the gear ratio of the third planetary gear sun gear pair 4-2, i ₄ is the gear ratio, i ₅ is the first planetary gear ring gear input gear ratio, i ₆ is the transmission ratio of the fourth planetary gear ring gear input gear pair,

Let i ₁ =0.62, i ₂ =0.8, i ₃ =0.3, i ₄ =0.7, i ₅ =1, i ₆ =0.9

k ₁ =3.3, k ₂ =3.8, k ₃ =1.6, k ₄ =1.5

The hydraulic transmission relationship is as follows:

As shown in Figure 17, the low-speed hydraulic pressure: ① is substituted into the parameter, when e ₁ ∈[-1,1], the corresponding range is n ₀ ∈[-3.13, 3.13]n _e

Combining type ① and type ③ can get intersection B; combining type ① and ④ can get intersection D.

According to the intersection point, the corresponding graphic range of the positive low-speed hydraulic pressure is obtained:

e ₁ ∈[0,0.428], n ₀ ∈[0,1.339]n _e

Graphical range corresponding to reverse low-speed hydraulic pressure:

e ₁ ∈[-0.410,0], n ₀ ∈[-1.282,0]n _e

As shown in Figure 18, the high-speed hydraulic pressure: ② is substituted into the parameters, when e ₂ ∈[-2,2], the corresponding range is n ₀ ∈[-2,2]n _e

The intersection point H can be obtained by combining formula ② and formula ⑤.

According to the intersection point, the corresponding graphic range of the positive high-speed hydraulic pressure is obtained:

e ₂ ∈[0,0.800], n ₀ ∈[0,0.800]n _e

Graphical range corresponding to reverse high-speed hydraulic pressure:

e ₂ ∈[-1,0], n ₀ ∈[-1, 0]n _e

The machine-hydraulic transmission relationship is as follows:

As shown in Figure 17, the low-speed reverse mechanical-hydraulic compound transmission:

③ Substituting the parameters into the formula: n _o =1.238e ₁ -0.775

When e ₁ ∈[-1,0], the corresponding range n ₀ ∈[-2.013, -0.775]n _e

The intersection point B is obtained by the above calculation, and the illustrated range is obtained according to the intersection point:

e ₁ ∈[-1,-0.410], n ₀ ∈[-2.013,-1.282]n _e

As shown in Figure 17, the low-speed forward mechanical-hydraulic compound transmission:

④ Substituting the parameters into the formula: n _o =0.657e ₁ +1.058

When e ₁ ∈[0,1], n ₀ ∈[1.058,1.715]n _e

The intersection point D is obtained by the above calculation, and the range of the figure is obtained according to the intersection point:

e ₁ ∈[0.428,1], n ₀ ∈[1.339,1.715]n _e

As shown in Figure 18, the high-speed forward mechanical-hydraulic compound transmission is in the first gear:

⑤ Substituting the parameters into the formula: n _o =-0.672e ₂ +1.339

When e ₂ ∈[0,2], n ₀ ∈[-0.005,1.339]n _e

Combine ⑤ and ⑥ to get the intersection point K, the above calculations get the intersection point H

According to the intersection point, the range of the figure is obtained:

e ₂ ∈[0.290,0.800], n ₀ ∈[0.800,1.144]n _e

As shown in Figure 18, the high-speed forward mechanical-hydraulic compound transmission is in 2 gears:

⑥ Substituting the parameters into the formula: n _o =1.075e ₂ +0.833

When e ₂ ∈[0,2], n ₀ ∈[0.833, 2.984]n _e

The intersection point K is obtained by the above calculation, and the range of the figure is obtained according to the intersection point:

e ₂ ∈[0.290,2], n ₀ ∈[1.144, 2.984]n _e

The mechanical transmission relationship is as follows:

Mechanical reverse gear: The relationship between the speed of input shaft 1 and output shaft 9 is:

Substituting in the parameters is: n _o =-1.282n _e

Mechanical 1st gear: The relationship between the speed of input shaft 1 and output shaft 9 is:

Substituting the parameters into: n _o =0.833n _e

Mechanical 2nd gear: The relationship between the speed of input shaft 1 and output shaft 9 is:

Substituting the parameters into: n _o =1.058n _e

Mechanical 3rd gear: The relationship between the speed of input shaft 1 and output shaft 9 is:

Substituting the parameters into: n _o =1.339n _e

Mechanical 4th gear: The relationship between the speed of input shaft 1 and output shaft 9 is:

Substituting the obtained parameters: n _o = 2.381n _e.

According to the above transmission relationship, the switching of different transmission modes is realized by selectively controlling the combination of the clutch and the brake, and the displacement ratio of the hydraulic transmission mechanism 6 is controlled to convert the hydraulic transmission to the hydromechanical transmission. details as follows:

It can realize the switching mode of hydraulic transmission→mechanical-hydraulic compound transmission. In this mode, the fixed motor M ₁ 6-4 and the fixed motor M ₂ 6-7 are connected in parallel, and the output torque of the fixed motor is large, which can meet the requirements of the operation. .

Hydraulic transmission: engage the third clutch C ₃ 8-5, the fourth clutch C ₄ 4-7, the sixth clutch C ₆ 8-1, the third brake B ₃ 5-1, the fourth brake B ₄ 5-2, three position four-way solenoid valve V ₃ 6-5 energized right position, two-way solenoid valve V ₄ 6-6 is in the normal position, the motor M powered _16-4 quantitative forward to the output shaft 9, the start of hydraulic, At this time, the displacement ratio changes in the range of (0, 0.428); when the three-position four-way solenoid valve V ₃ 6-5 is energized in the left position and the working conditions of other devices remain unchanged, the _{power of the fixed motor M 1} 6-4 is reversed. It is transmitted to the output shaft 9 to realize hydraulic reversing. At this time, the displacement ratio changes in the range of (-0.410,0).

Positive mechanical hydraulic compound transmission: engage the first clutch C ₁ 3-6, the third clutch C ₃ 8-5, and the sixth clutch C ₆ 8-1. The three-position four-way solenoid valve is energized on the right position V ₃ 6-5, two-way solenoid valve V ₄ 6-6 is in the normal position, when the motor M ₁ 6-4 quantitative and complex mechanical drive power through the third clutch C ₃ 8-5 forward transmitted to the output shaft 9, to achieve mechanical hydraulic Compound forward driving, the range of displacement ratio at this time is (0.428,1).

Reverse mechanical hydraulic compound transmission: engage the second clutch C ₂ 4-1, the third clutch C ₃ 8-5, and the sixth clutch C ₆ 8-1. The three-position four-way solenoid valve is energized on the right position V ₃ 6-5, two-way solenoid valve V ₄ 6-6 is in the normal position, when the motor M ₁ 6-4 quantitative and complex mechanical drive power through the third clutch C ₃ 8-5 reverse to the output shaft 9, to achieve mechanical hydraulic Compound reverse driving, the range of displacement ratio at this time is (-1, -0.410).

It can realize the switching mode two of hydraulic transmission→mechanical-hydraulic compound transmission: in this mode, the motor M ₁ and the motor M ₂ are in series relationship, and the motor speed is high, which can meet the transition requirements.

Hydraulic transmission: engaging the third clutch C ₃ 8-5, seventh clutch C ₇ 5-8, the first brake B ₁ 8-4, the second brake B ₂ 4-3, the third brake B ₃ 5-1, three The right position of the four-way solenoid valve is energized by V ₃ 6-5, and the two-position four-way solenoid valve is energized by V ₄ 6-6. The power of the fixed motor M ₂ 6-7 is forwardly transmitted to the output shaft 9 to realize the hydraulic start. The range of displacement ratio is (0,0.800).

Forward mechanical hydraulic transmission 1st gear: engage the first clutch C ₁ 3-5, the third clutch C ₃ 8-5, the fourth clutch C ₄ 4-7, the seventh clutch C ₇ 5-8, and the third brake B ₃ 5-1, the right position of the _three -position four-way solenoid valve is energized by V 3 6-5, and the two-position four-way solenoid valve is energized by V ₄ 6-6. At this time, the _{combined power of the fixed motor M 2} 6-7 and the mechanical transmission passes through the third position. The clutch C ₃ 8-5 and the fourth clutch C ₄ 4-7 are forwarded to the output shaft 9 to realize the mechanical and hydraulic compound forward driving. At this time, the displacement ratio changes in the range of (0.290, 0.800).

Forward mechanical hydraulic transmission 2nd gear: engage the second clutch C ₂ 4-1, the fifth clutch C ₅ 5-6, the seventh clutch C ₇ 5-8, the second brake B ₂ 4-3, three-position four-way electromagnetic The right position of the valve is energized V ₃ 6-5, and the two-position four-way solenoid valve is energized V ₄ 6-6. At this time, the _{combined power of the fixed motor M 2} 6-7 and the mechanical transmission is forwarded _{through the fifth clutch C 5 5-6} For the output shaft 9, a higher-speed mechanical-hydraulic compound forward driving is realized, and the displacement ratio changes in the range of (0.290, 2) at this time.

The embodiments are the preferred embodiments of the present invention, but the present invention is not limited to the above-mentioned embodiments. Without departing from the essence of the present invention, any obvious improvements, substitutions or substitutions can be made by those skilled in the art. The variants all belong to the protection scope of the present invention.

Claims (10)

1. A single-pump-controlled dual-motor mechanical-hydraulic composite transmission device, which is characterized by comprising an input member, a planetary gear assembly, an output member, a hydraulic transmission mechanism (6), a power output mechanism (7), a clutch assembly and a brake assembly. The hydraulic transmission mechanism (6) includes two quantitative motors (6-4, 6-7), and the two quantitative motors (6-4, 6-7) are controlled in series or parallel through a control valve assembly; the clutch assembly Connect the input member to the hydraulic transmission mechanism (6) and the planetary gear assembly respectively, connect the output of one fixed motor (6-4, 6-7) to the planetary gear assembly, and connect the other fixed motor (6- 4. The output of 6-7) is connected with the power output mechanism (7), the output member is connected with the planetary gear assembly, the clutch assembly and the brake assembly provide the input member and the output member and/or the power output mechanism (7) ) Continuous transmission ratio.
2. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 1, wherein the planetary gear assembly includes a second planetary gear mechanism (3), a third planetary gear mechanism (4), and a fourth planetary gear mechanism (3). The gear mechanism (5) and the first planetary gear mechanism (8); the output of one of the quantitative motors (6-4, 6-7) is connected with the ring gear of the first planetary gear mechanism (8), and the first planetary gear mechanism The planet carrier of (8) is connected to the ring gear of the second planetary gear mechanism (3), the sun gear of the first planetary gear mechanism (8) is connected to the sun gear of the second planetary gear mechanism (3), and the second planetary gear mechanism The sun gear of (3) is connected to the sun gear of the third planetary gear mechanism (4), the ring gear of the third planetary gear mechanism (4) is connected to the sun gear of the fourth planetary gear mechanism (5), and the other said quantitative The output of the motors (6-4, 6-7) is connected with the ring gear of the fourth planetary gear mechanism (5); the clutch assembly connects at least the planet carrier of the first planetary gear mechanism (8) and the third planetary gear mechanism ( 4) One of the planet carrier of the fourth planetary gear mechanism (5) and the planet carrier is connected to the output member; the clutch assembly connects the planet carrier of the second planetary gear mechanism (3) or the third planetary gear mechanism (4) The sun gear is connected to the input member.
3. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 2, characterized in that by adjusting the displacement ratio of the hydraulic transmission mechanism (6) and selectively controlling the clutch assembly, control valve assembly and brake assembly Engagement provides transmission modes between the input member and the output member including: hydraulic transmission, mechanical transmission and mechanical hydraulic transmission.
4. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 3, wherein the clutch assembly includes a third clutch C ₃ (8-5), a fourth clutch C ₄ (4-7), and a third clutch C 4 (4-7). Six clutches C ₆ (8-1) and seventh clutch C ₇ (5-8); the third clutch C ₃ (8-5) is used to selectively connect the planet carrier of the first planetary gear mechanism (8) Is connected to the output member for common rotation; the fourth clutch C ₄ (4-7) is used to selectively connect the planet carrier of the third planetary gear mechanism (4) to the output member for common rotation; the sixth clutch C ₆ (8-1) is used to selectively connect the ring gear of the first planetary gear mechanism (8) to one of the fixed motors (6-4, 6-7) for common rotation; the seventh clutch C ₇ (5-8) is used to selectively connect the ring gear of the fourth planetary gear mechanism (5) to another fixed motor (6-4, 6-7) for common rotation;

   The brake assembly includes a first brake B ₁ (8-4), a second brake B ₂ (4-3), a third brake B ₃ (5-1), and a fourth brake B ₄ (5-2), so The first brake B ₁ (8-4) is used to selectively connect the ring gear of the first planetary gear mechanism (8) to the fixed part; the second brake B ₂ (4-3) is used to selectively connect Connect the planet carrier of the third planetary gear mechanism (4) to the fixed part; the third brake B ₃ (5-1) is used to selectively connect the planet carrier of the fourth planetary gear mechanism (5) to the fixed part The fourth brake B ₄ (5-2) is used to selectively connect the ring gear of the fourth planetary gear mechanism (5) to the fixed part;

   The control valve assembly includes a first reversing valve and a second reversing valve. The first reversing valve is used to control the forward and reverse rotation of the quantitative motor (6-4, 6-7), and the second reversing valve The valve is used to control the two quantitative motors (6-4, 6-7) in series or in parallel;

   By adjusting the displacement ratio of the hydraulic transmission mechanism (6), the third clutch C ₃ (8-5), the fourth clutch C ₄ (4-7), and the sixth clutch C ₆ (8-1) are selectively controlled , The seventh clutch C ₇ (5-8), the first brake B ₁ (8-4), the second brake B ₂ (4-3), the third brake B ₃ (5-1) and the fourth brake B ₄ (5-2) The engagement and selective control of the first reversing valve and the second reversing valve provide a hydraulic transmission mode between the input member and the output member.
5. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 4, wherein the third clutch C ₃ (8-5), the fourth clutch C ₄ (4-7), and the sixth clutch are engaged C ₆ (8-1), the third brake B ₃ (5-1) and the fourth brake B ₄ (5-2), engage the third clutch C ₃ (8-5), the seventh clutch C ₇ ( 5-8), the first brake B ₁ (8-4), the second brake B ₂ (4-3), and the third brake B ₃ (5-1), which respectively provide a positive or Different hydraulic transmission modes in the opposite direction.
6. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 4, wherein the clutch assembly further comprises a first clutch C ₁ (3-5), a second clutch C ₂ (4-1) and The fifth clutch C ₅ (5-6); the first clutch C ₁ (3-5) is used to selectively connect the input member to the planet carrier of the second planetary gear mechanism (3) for common rotation; The second clutch C ₂ (4-1) is used to selectively connect the input member to the sun gear of the third planetary gear mechanism (4) for common rotation; the fifth clutch C ₅ (5-6) is used to select Sexually connect the planet carrier of the fourth planetary gear mechanism (5) to the output member for common rotation;

   By selectively controlling the first clutch C ₁ (3-5), the second clutch C ₂ (4-1), the third clutch C ₃ (8-5), the fourth clutch C ₄ (4-7), The fifth clutch C ₅ (5-6), the first brake B ₁ (8-4), the second brake B ₂ (4-3), the third brake B ₃ (5-1), and the fourth brake B ₄ ( The engagement of 5-2) provides a mechanical transmission mode for forward or backward movement between the input member and the output member.
7. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 6, wherein the second clutch C ₂ (4-1), the fourth clutch C ₄ (4-7), and the third brake are engaged B ₃ (5-1) and the fourth brake B ₄ (5-2) provide a mechanical transmission method for retreating between the input member and the output member;

   Engage the second clutch C ₂ (4-1), the fifth clutch C ₅ (5-6), the second brake B ₂ (4-3) and the fourth brake B ₄ (5-2), engage the The first clutch C ₁ (3-5), the third clutch C ₃ (8-5) and the first brake B ₁ (8-4), the first clutch C ₁ (3-5), the third clutch are engaged C ₃ (8-5), fourth clutch C ₄ (4-7), third brake B ₃ (5-1) and fourth brake B ₄ (5-2), engage second clutch C ₂ (4- 1) The fourth clutch C ₄ (4-7), the fifth clutch C ₅ (5-6), and the fourth brake B ₄ (5-2) provide different forward paths between the input member and the output member. Mechanical transmission mode.
8. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 6, wherein the second clutch C ₂ (4-1), the third clutch C ₃ (8-5), and the sixth clutch C _{6 are engaged} (8-1), engage the first clutch C ₁ (3-5), the third clutch C ₃ (8-5) and the sixth clutch C ₆ (8-1), engage the first clutch C ₁ (3-5) ), third clutch C ₃ (8-5), fourth clutch C ₄ (4-7), seventh clutch C ₇ (5-8) and third brake B ₃ (5-1), engage the second clutch C ₂ (4-1), the fifth clutch C ₅ (5-6), the seventh clutch C ₇ (5-8), and the second brake B ₂ (4-3) are provided between the input member and the output member. Different mechanical hydraulic transmission modes in forward and reverse directions.
9. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 3, characterized in that by controlling the displacement ratio of the hydraulic transmission mechanism (6) to change linearly and selectively controlling the combination of the clutch and the brake, Convert hydraulic transmission to hydraulic mechanical transmission.
10. The single-pump-controlled dual-motor mechanical-hydraulic composite transmission device according to claim 1, wherein the clutch assembly includes an eighth clutch C ₈ (7-2) and a ninth clutch C ₄ (7-4), so The eighth clutch C ₈ (7-2) is used to selectively connect the output of a fixed amount motor (6-4, 6-7) to the power output mechanism (7) for common rotation; the ninth clutch C ₄ (7-4) Used to selectively connect the output of another fixed motor (6-4, 6-7) to the power output mechanism (7) for common rotation; selectively control the eighth clutch C ₈ (7-2 ) Or the combination of the ninth clutch C ₄ (7-4) and the selective control valve assembly to provide a continuous transmission ratio between the input member and the power output mechanism (7).

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