WO2022016606A1 - 一种带有能量管理机构的机液复合传动装置 - Google Patents

一种带有能量管理机构的机液复合传动装置 Download PDF

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Publication number
WO2022016606A1
WO2022016606A1 PCT/CN2020/106674 CN2020106674W WO2022016606A1 WO 2022016606 A1 WO2022016606 A1 WO 2022016606A1 CN 2020106674 W CN2020106674 W CN 2020106674W WO 2022016606 A1 WO2022016606 A1 WO 2022016606A1
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WO
WIPO (PCT)
Prior art keywords
clutch
planetary gear
transmission
energy management
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2020/106674
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English (en)
French (fr)
Inventor
蔡英凤
朱镇
陈龙
夏长高
王骏骋
田翔
韩江义
朱建国
赖龙辉
徐兴
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jiangsu University
Original Assignee
Jiangsu University
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Filing date
Publication date
Application filed by Jiangsu University filed Critical Jiangsu University
Priority to DE112020000586.0T priority Critical patent/DE112020000586T5/de
Priority to US17/296,558 priority patent/US11499616B2/en
Priority to CH70235/21A priority patent/CH717777B1/de
Priority to GB2107444.8A priority patent/GB2593629B/en
Publication of WO2022016606A1 publication Critical patent/WO2022016606A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
    • F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefor
    • F16H2061/0034—Accumulators for fluid pressure supply; Control thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight engaging means

Definitions

  • the invention relates to the field of automatic speed change devices, in particular to a machine-hydraulic composite transmission device with an energy management mechanism.
  • the machine-hydraulic composite transmission consisting of hydraulic transmission and mechanical transmission is suitable for high-power agricultural or engineering vehicles.
  • the low-speed and high-torque characteristics of hydraulic transmission are suitable for starting conditions, the high-efficiency stepless speed regulation characteristics of mechanical-hydraulic transmission are suitable for working conditions, and the high-efficiency variable-speed characteristics of mechanical transmission are suitable for driving conditions.
  • the mechanical-hydraulic composite transmission device integrating mechanical transmission has high engineering application value.
  • the present invention provides a mechanical-hydraulic composite transmission device with an energy management mechanism.
  • the invention integrates hydraulic transmission, machine-hydraulic transmission and mechanical transmission, and can realize the energy recovery and reuse function of the transmission mechanism and the power output mechanism.
  • the present invention achieves the above technical purpose through the following technical means.
  • a mechanical-hydraulic composite transmission device with an energy management mechanism comprising an input member, a mechanical transmission mechanism, an energy management mechanism, a power output mechanism, an output member, a confluence mechanism, a starting mechanism, a hydraulic transmission mechanism, a clutch assembly and a brake assembly;
  • the clutch assembly connects the input member to the mechanical transmission mechanism, the power output mechanism and the hydraulic transmission mechanism respectively, connects the output of the hydraulic transmission mechanism to the mechanical transmission mechanism and the output member respectively, and connects the output of the mechanical transmission mechanism to the confluence mechanism,
  • the output member is connected with the merging mechanism, and the energy management mechanism is connected to the mechanical transmission mechanism and the power output mechanism respectively;
  • the clutch assembly and the brake assembly provide between the input member and the output member and/or the power output mechanism, providing energy management Between the mechanism and the output member and/or the power take-off, there is provided a continuous transmission ratio between the energy management mechanism and the input member together and the output member and/or the power take-off.
  • the transmission modes provided between the input member and the output member include hydraulic transmission, hydraulic transmission and mechanical transmission.
  • the mechanical transmission mechanism includes a front planetary gear mechanism and a middle planetary gear mechanism, the planet carrier of the front planetary gear mechanism is connected with the input member, and the planet carrier of the front planetary gear mechanism is connected with the ring gear of the middle planetary gear mechanism , the sun gear of the front planetary gear mechanism is connected with the sun gear of the middle planetary gear mechanism, and the sun gear of the middle planetary gear mechanism is connected with the output end of the hydraulic transmission mechanism;
  • the confluence mechanism includes a rear planetary gear mechanism, the rear planetary gear The ring gear of the mechanism is connected with the output member, and the clutch assembly connects the ring gear of the front planetary gear mechanism or the planet carrier of the middle planetary gear mechanism with the sun gear of the rear planetary gear mechanism;
  • the clutch assembly includes a clutch C 2 and a clutch C 3 ; the clutch C 2 is used for selectively connecting the input end of the hydraulic transmission mechanism with the input member for common rotation; the clutch C 3 is used for selectively connecting the hydraulic output terminal and the output member of the transmission mechanism connected for common rotation; engaged ratio by adjusting the displacement of the hydraulic actuators and selectively controlling the clutch C 2 and the clutch C 3 is provided between the continuous forward input member and the output member or Reverse hydraulic transmission.
  • the clutch assembly further includes a clutch C 1 , a clutch C 4 , a clutch C 5 and a clutch C 6 ;
  • the clutch C 1 is used for selectively connecting the input member with the planet carrier of the front planetary gear mechanism for common rotation;
  • the clutch C 4 in the planetary gear mechanism for selectively planet carrier and the sun gear of the planetary gear mechanism is connected for common rotation;
  • C 6 after the clutch gear with the sun gear of the planetary gear mechanism of the planetary gear mechanism for selectively connecting to common rotation;
  • said brake assembly comprises a brake B 2, the rear brake B 2 is connected to the planet gear carrier for selectively fixing member; a ratio by adjusting the displacement of the hydraulic actuators and controlling the selective clutch C 1, C 2 clutch, the clutch C 4, clutch C 5, C 6 engaging the clutch and the brake B 2, there is provided a continuous forward or reverse machine Transmissions between the input member and the output member.
  • engaging the clutch C 1 , clutch C 2 , clutch C 4 and clutch C 6 engaging the clutch C 1 , clutch C 2 , clutch C 5 and clutch C 6 , engaging the clutch C 1 , clutch C 2 , clutch C 4 and brake B 2 , engage the clutch C 1 , clutch C 2 , clutch C 5 and brake B 2 , respectively, to provide different hydraulic transmissions between the input member and the output member for forward or backward.
  • the brake assembly further includes a brake B 1 ; the brake B 1 is used for selectively connecting the output end of the hydraulic transmission mechanism to the fixed part; engaging the clutch C 1 , the clutch C 4 , the clutch C 6 and the brake B 1 , engaging the clutch C 1 , clutch C 5 , clutch C 6 and brake B 1 , engaging the clutch C 1 , clutch C 4 , brake B 1 and brake B 2 , engaging the clutch C 1 , clutch C 5.
  • the brake B 1 and the brake B 2 respectively provide different mechanical transmissions for advancing or retreating between the input member and the output member.
  • the energy management mechanism includes a pump/motor mechanism, an electromagnetic reversing valve V 1 , a pilot proportional relief valve V 2 , an accumulator A 1 , an electromagnetic reversing valve V 3 , a pilot proportional relief valve V 4 and an accumulator transducer A 2;
  • the pump / motor means are connected to the accumulator and the accumulator A 1 A 2;
  • the pump A pilot proportional relief valve V 2 is installed between the motor mechanism and the accumulator A 1
  • the electromagnetic reversing valve V 3 is used to control the connection between the pump/motor mechanism and the accumulator A 2
  • the pump/motor mechanism and the accumulator A 2 a 2 is the ratio between the pilot relief valve V 4;
  • said clutch assembly further includes a clutch C 7, C 8 clutch and the clutch C 9, the clutch C 7 pump / motor and the mechanism for selective front planetary gear
  • the planet carrier of the mechanism is connected for common
  • the output member when braking the output member, engaging the clutch C 7, clutches and brakes B 1 C 4, or engaging the clutch C 7, clutches and brakes B 1 C 5, the output member are provided with the pump / motor
  • the continuous transmission ratio between the mechanisms by selectively controlling the electromagnetic reversing valve V 1 and the electromagnetic reversing valve V 3 , the energy generated when the output member is braked is input into the accumulator A 1 or/and the accumulator energy device A 2 ;
  • the engagement of the clutch C 9 provides a continuous transmission ratio between the power output mechanism and the pump / motor mechanism; by selectively controlling the solenoid valve V 1 and the solenoid valve V 3 , which is used to input the energy generated when the power output mechanism brakes into the accumulator A 1 or/and the accumulator A 2 .
  • Engaging clutch C 9 provides a continuous gear ratio between the energy management mechanism and the power take-off mechanism
  • engaging the clutch C 8 and clutch C 9 , engaging the clutch C 1 and clutch C 7 respectively providing a continuous transmission ratio between the input member and the pump/motor mechanism; by selectively controlling the electromagnetic reversing valve V 1 and the electromagnetic reversing valve V 3 , for inputting the energy of the input member into the accumulator A 1 or/and the accumulator A 2 .
  • the machine-hydraulic composite transmission device with an energy management mechanism is a multi-mode machine-hydraulic composite transmission device integrating hydraulic transmission, machine-hydraulic transmission and mechanical transmission, and is suitable for the requirements of different working conditions. .
  • the machine-hydraulic composite transmission device with the energy management mechanism of the present invention adopts different energy storage systems to increase the freedom of the energy management mechanism.
  • the energy management mechanism can be used alone or together with the engine to drive the transmission mechanism or the power output mechanism. .
  • the engine first stores energy for the energy management mechanism, and then the energy management mechanism releases the energy to meet the dynamic requirements of extreme working conditions together with the engine;
  • Machine liquid compound transmission having an energy management mechanism of the present invention according to 4., the bus control mechanism by engaging clutch or brake B 2 C 6 or hydraulic actuators to change the ratio of positive and negative displacement, energy management control The direction of rotation of the pump/motor mechanism in the mechanism.
  • Fig. 1 is the structural principle diagram of the present invention
  • FIG. 2 is a schematic diagram of the power flow of the F(H) gear of the present invention.
  • Fig. 3 is the schematic diagram of F 1 (HM) gear power flow of the present invention.
  • FIG. 6 is a schematic diagram of the power flow of the R 1 (HM) gear of the present invention.
  • Fig. 8 is the output-input rotational speed ratio and the displacement ratio relation diagram of the present invention.
  • FIG. 9 is a schematic diagram of the energy recovery power flow of the transmission mechanism of the present invention.
  • FIG. 10 is a schematic diagram of the energy recovery power flow of the power take-off mechanism of the present invention.
  • FIG. 11 is a schematic diagram of the power flow of the energy management mechanism of the present invention alone driving the transmission mechanism;
  • FIG. 12 is a schematic diagram of the power flow of the energy management mechanism and the engine jointly driving the transmission mechanism of the present invention
  • FIG. 13 is a schematic diagram of the power flow of the power output mechanism independently driven by the energy management mechanism of the present invention.
  • FIG. 14 is a schematic diagram of the power flow of the power output mechanism jointly driven by the energy management mechanism and the engine of the present invention.
  • FIG. 15 is a schematic diagram of the flow of stored power from the engine to the energy management mechanism according to the present invention.
  • the mechanical-hydraulic composite transmission device with an energy management mechanism includes an input shaft 1 , a mechanical transmission mechanism 2 , an energy management mechanism 3 , a power output mechanism 4 , an output shaft 5 , and a confluence mechanism 6 , starting mechanism 7, hydraulic transmission mechanism 8, clutch assembly and brake assembly.
  • the hydraulic transmission mechanism 8 includes a clutch C 2 81 , a hydraulic transmission input gear pair 82 , a pump input shaft 83 , a variable displacement pump 84 , a constant displacement motor 85 , a motor output shaft 86 , a hydraulic transmission output gear pair 87 and a brake B 1 88 .
  • the pump input shaft 83 is connected with the input shaft 1 through a hydraulic transmission input gear pair 82
  • the motor output shaft 86 of the quantitative motor 85 is connected with the middle planetary gear sun gear 24 through a hydraulic transmission output gear pair 87
  • the motor output shaft 86 is also connected to the output shaft 5 through the starting mechanism gear pair 71 of the starting mechanism 7
  • the variable displacement pump 84 is used to provide the hydraulic energy of the constant-volume motor 85 .
  • the brake B 1 88 is used to selectively connect the motor output shaft 86 to the fixed member; the clutch C 2 81 is used to selectively connect the pump input shaft 83 of the hydraulic transmission mechanism 8 to the input gear pair 82 through the hydraulic transmission.
  • the input shaft 1 is connected for common rotation.
  • the starting mechanism 7 includes a starting mechanism gear pair 71 and a clutch C 3 72 ; the clutch C 3 72 is used to selectively connect the motor output shaft 86 with the output shaft 5 through the starting mechanism gear pair 71 for common rotation.
  • the pump input shaft 83 drives the variable pump 84 , and the variable pump 84 drives the quantitative motor 85 by changing the inclination of the swash plate, and then the motor output shaft 86 outputs power to the mechanical transmission mechanism 2 or the starting mechanism 7 .
  • the mechanical transmission mechanism 2 includes a clutch C 1 21 , a front planetary gear carrier 22 , a front planetary gear sun gear 23 , a middle planetary gear sun gear 24 , a middle planetary gear ring gear 25 , a middle planetary gear carrier 26 , and a front planetary gear Ring gear 27 , clutch C 4 28 and clutch C 5 29 .
  • the front planetary gear carrier 22 , the front planetary gear sun gear 23 and the front planetary gear ring gear 27 constitute a front planetary gear mechanism;
  • the middle planetary gear sun gear 24 , the middle planetary gear ring gear 25 and the middle planetary gear carrier 26 a planetary gear mechanism configuration;
  • mechanical transmission mechanism 22 as a second input to the front end of the planet gear carrier, an input shaft 21 and the connector 1 via the clutch C, the front planetary gear carrier of the planetary gear 22 is connected to the ring gear 25,
  • the front planetary gear sun gear 23 is connected with the middle planetary gear sun gear 24 and is connected with the motor output shaft 86 through the hydraulic transmission output gear pair 87 .
  • Front planetary gear 27 and the ring gear carrier 26 of the planetary gear 428 may be respectively connected to the input bus 6 via the clutch mechanism and the clutch C 5 29 C.
  • the bus planetary gear mechanism 6 comprises a sun gear 61, the planet gear carrier 62, the ring gear of the planetary gear 63, the clutch C 6 64, the brake B 2 65 and the mechanical transmission gear pair 66 and the bus means; said rear
  • the planetary gear sun gear 61 , the rear planetary gear carrier 62 and the rear planetary gear ring gear 63 constitute a rear planetary gear mechanism; the rear planetary gear ring gear 63 is connected with the output shaft 5 .
  • the clutch C 1 21 is used to selectively connect the input shaft 1 and the front planetary gear carrier 22; the clutch C 4 28 is used to selectively connect the middle planetary gear carrier 26 with the confluence gear pair 66 through the mechanical transmission mechanism connected to the rear sun gear 61 of the planetary gear for co-rotation; C 5 29 of the clutch for the selective front planetary ring gear 2766 connected to the rear sun gear 61 of the planetary gear mechanism by a mechanical transmission gear mechanism to a common sub-bus Rotation; the clutch C 6 64 is used to selectively connect the rear planetary gear sun gear 61 and the rear planetary gear ring gear 63 ; the brake B 2 65 is used to selectively fix the rear planetary gear carrier 62 .
  • the energy management mechanism 3 includes a transmission mechanism and an energy management mechanism gear pair 31, a clutch C 7 32, a pump/motor mechanism 33, an electromagnetic reversing valve V 1 34, a pilot proportional relief valve V 2 35, an accumulator A 1 36, Electromagnetic reversing valve V 3 37, pilot proportional relief valve V 4 38, accumulator A 2 39, power take-off mechanism and energy management mechanism gear pair 310 and clutch C 9 311;
  • the pump/motor mechanism 33 can be A device for switching functions between a pump and a hydraulic motor, that is, when the pump/motor mechanism 33 inputs mechanical energy, the pump/motor mechanism 33 outputs hydraulic energy, and when the pump/motor mechanism 33 inputs hydraulic energy, the pump/motor mechanism 33 output mechanical energy.
  • the pump/motor mechanism 33 is connected to the front planetary gear carrier 22 through a transmission mechanism and an energy management mechanism gear pair 31 .
  • the pump/motor mechanism 33 is connected with the power output mechanism 4 through the power output mechanism and the energy management mechanism gear pair 310; the electromagnetic reversing valve V 1 34 , the pilot proportional relief valve V 2 35 and the accumulator A 1 36 connected to form a first energy storage system, the electromagnetic reversing valve V 3 37, pilot proportional relief valve V 4 38 and accumulator A 2 39 are connected to form a second energy storage system, the first energy storage system In parallel with the second energy storage system, and connected to the pump/motor mechanism 33 .
  • the power output mechanism 4 includes a power output gear pair 41 , a clutch C 8 42 and a power output shaft 43 ; the power output shaft 43 is connected to the input shaft 1 through the power output gear pair 41 .
  • the clutch C 7 32 is used to selectively connect the pump/motor mechanism 33 with the front planetary gear carrier 22 for common rotation through the transmission mechanism and the energy management mechanism gear pair 31; the clutch C 9 311 is used for selective The pump/motor mechanism 33 is connected to the power take-off shaft 43 for common rotation through the power take-off mechanism and the energy management mechanism gear pair 310; the clutch C 8 42 is used to selectively connect the input shaft 1 with the power take-off gear pair 41
  • the output shaft 43 is connected for common rotation.
  • the transmission modes provided between the input member and the output member include hydraulic transmission, hydraulic transmission and mechanical transmission.
  • Table 1 The following is a specific example in conjunction with Table 1:
  • the hydraulic transmission includes a forward hydraulic transmission F(H) and a backward hydraulic transmission R(H).
  • the power flow direction of the F(H) gear of the present invention is shown in FIG. 2 .
  • the clutch C 2 81 and the clutch C 3 72 are engaged, the power provided by the engine is output from the output shaft 5 through the input shaft 1, the hydraulic transmission mechanism 8 and the starting mechanism 7.
  • the displacement ratio of the hydraulic transmission mechanism 8 is positive, For the F (H) gear.
  • the relationship between the output shaft speed and the engine speed is:
  • n o is the rotational speed of the output shaft
  • n I is the rotational speed of the input shaft
  • e is the displacement ratio of the hydraulic transmission mechanism
  • i 1 is the transmission ratio of the input gear pair 82 of the hydraulic transmission
  • i 3 is the gear ratio of the starting mechanism of the sub-gear 71.
  • the power flow of the R(H) gear of the present invention is shown in FIG. 5 .
  • the clutch C 2 81 and the clutch C 3 72 are engaged, the power provided by the engine is output from the output shaft 5 through the input shaft 1, the hydraulic transmission mechanism 8 and the starting mechanism 7.
  • the displacement ratio of the hydraulic transmission mechanism 8 is negative, For R (H) gear.
  • the relationship between the output shaft speed and the engine speed is:
  • the hydraulic transmission includes forward hydraulic transmission F 1 (HM), forward hydraulic transmission F 2 (HM), reverse hydraulic transmission R 1 (HM), Hydraulic transmission R 2 (HM).
  • the power flow direction of the F 1 (HM) gear of the present invention is shown in FIG. 3 .
  • the clutch C 1 21, the clutch C 2 81, the clutch C 4 28 and the clutch C 6 64 are engaged, the power provided by the engine is split at the input shaft 1 and transmitted all the way through the front planetary gear carrier 22 to the middle planetary gear ring gear 25 , all the way through the hydraulic transmission mechanism 8 to the middle planetary gear sun gear 24, the mechanical power reaching the middle planetary gear ring gear 25 and the hydraulic power reaching the middle planetary gear sun gear 24 converge at the middle planetary gear carrier 26.
  • the transmission mechanism and the gear pair 66 of the confluence mechanism are transmitted to the confluence mechanism 6 .
  • the confluence mechanism 6 is connected as a whole, and the power is output from the output shaft 5 .
  • the relationship between the output shaft speed and the engine speed is:
  • i 2 is the transmission ratio of the hydraulic transmission output gear pair
  • k 2 is the characteristic parameter of the middle planetary gear mechanism.
  • the power flow of the F 2 (HM) gear of the present invention is shown in FIG. 4 .
  • the clutch C 1 21, the clutch C 2 81, the clutch C 5 29 and the clutch C 6 64 are engaged, the power provided by the engine is split at the input shaft 1, all the way is directly transmitted to the front planetary gear carrier 22, all the way through the hydraulic transmission mechanism 8 is transmitted to the front planetary gear sun gear 23, the mechanical power reaching the front planetary gear carrier 22 and the hydraulic power reaching the front planetary gear sun gear 23 converge at the front planetary gear ring gear 27, and then pass through the mechanical transmission mechanism and the confluence mechanism gear.
  • the pair 66 is transmitted to the confluence mechanism 6 .
  • the confluence mechanism 6 is connected as a whole, and the power is output from the output shaft 5 .
  • the relationship between the output shaft speed and the engine speed is:
  • k 1 is the characteristic parameter of the front planetary gear mechanism.
  • the power flow of the R 1 (HM) gear of the present invention is shown in FIG. 6 .
  • the clutch C 1 21 , the clutch C 2 81 , the clutch C 4 28 and the brake B 2 65 are engaged, the power provided by the engine is split at the input shaft 1 and transmitted all the way through the front planetary gear carrier 22 to the middle planetary gear ring gear 25 , all the way through the hydraulic transmission mechanism 8 to the middle planetary gear sun gear 24, the mechanical power reaching the middle planetary gear ring gear 25 and the hydraulic power reaching the middle planetary gear sun gear 24 converge at the middle planetary gear carrier 26.
  • the transmission mechanism and the confluence mechanism gear pair 66 are transmitted to the rear planetary gear sun gear 61 , and output from the output shaft 5 via the rear planetary gear ring gear 63 .
  • the relationship between the output shaft speed and the engine speed is:
  • k 3 is the characteristic parameter of the rear planetary gear mechanism.
  • the power flow of the R 2 (HM) gear of the present invention is shown in FIG. 7 .
  • the clutch C 1 21, the clutch C 2 81, the clutch C 5 29 and the brake B 2 65 are engaged, the power provided by the engine is split at the input shaft 1, all the way directly to the front planetary gear carrier 22, all the way through the hydraulic transmission mechanism 8 is transmitted to the front planetary gear sun gear 23, the mechanical power reaching the front planetary gear carrier 22 and the hydraulic power reaching the front planetary gear sun gear 23 converge at the front planetary gear ring gear 27, and then pass through the mechanical transmission mechanism and the confluence mechanism gear.
  • the pair 66 is transmitted to the rear planetary gear sun gear 61 , and then passes through the rear planetary gear ring gear 63 , and is output from the output shaft 5 .
  • the relationship between the output shaft speed and the engine speed is:
  • the mechanical transmission includes a forward mechanical transmission F 1 (M), a forward mechanical transmission F 2 (M), a backward mechanical transmission R 1 (M), and a backward mechanical transmission R 2 (M).
  • the power flow of the F 1 (M) gear of the present invention is shown in FIG. 3 for reference, and the hydraulic circuit does not transmit power at this time.
  • the clutch C 1 21, clutch C 4 28, clutch C 6 64 and brake B 1 88 are engaged, the power provided by the engine passes through the input shaft 1, the front planetary gear carrier 22, the middle planetary gear ring gear 25, the middle planetary gear planet The frame 26 , the mechanical transmission mechanism and the confluence mechanism The gear pair 66 and the confluence mechanism 6 are output from the output shaft 5 .
  • the relationship between the output shaft speed and the engine speed is:
  • the power flow of the F 2 (M) gear of the present invention is shown in Figure 4 for reference, and the hydraulic circuit does not transmit power at this time.
  • the clutch C 1 21, the clutch C 5 29, the clutch C 6 64 and the brake B 1 88 are engaged, the power provided by the engine passes through the input shaft 1, the front planetary gear carrier 22, the front planetary gear ring gear 27, the mechanical transmission mechanism and the The manifold gear pair 66 and the manifold 6 are output from the output shaft 5 .
  • the relationship between the output shaft speed and the engine speed is:
  • the power flow of the R 1 (M) gear of the present invention is shown in FIG. 6 for reference, and the hydraulic circuit does not transmit power at this time.
  • the clutch C 1 21, the clutch C 4 28, the brake B 1 88 and the brake B 2 65 are engaged, the power provided by the engine passes through the input shaft 1, the front planetary gear carrier 22, the middle planetary gear ring gear 25, the middle planetary gear planet
  • the frame 26 , the mechanical transmission mechanism and the confluence mechanism gear pair 66 , the rear planetary gear sun gear 61 and the rear planetary gear ring gear 63 are output from the output shaft 5 .
  • the relationship between the output shaft speed and the engine speed is:
  • the power flow of the R 2 (M) gear of the present invention is shown in Figure 7 for reference, and the hydraulic circuit does not transmit power at this time.
  • the clutch C 1 21 , the clutch C 5 29 , the brake B 1 88 and the brake B 2 65 are engaged, the power provided by the engine passes through the input shaft 1 , the front planetary gear carrier 22 , the front planetary gear ring gear 27 , the mechanical transmission mechanism and the
  • the combination gear pair 66 , the rear planetary gear sun gear 61 and the rear planetary gear ring gear 63 are output from the output shaft 5 .
  • the relationship between the output shaft speed and the engine speed is:
  • FIG. 8 The relationship between the output-input speed ratio and the displacement ratio of the present invention is shown in FIG. 8 .
  • F (H ) of the gear speed range [0,1.00] n I When the range e ⁇ [-1.00,1.00], F 1 ( HM) stall speed The range is [0.44, 1.00]n I ; when e ⁇ [-1.00, 1.00], the F 2 (HM) gear speed regulation range is [1.00, 2.28]n I ; when e ⁇ [-1.00, 0] Within the range, the speed regulation range of R(H) gear is [-1.00, 0]n I ; when e ⁇ [-1.00, 1.00], the speed regulation range of R 1 (HM) gear is [-0.39,- 0.17]n I ; R 2 (HM) gear speed regulation range is [-0.89, -0.39]n I .
  • the speeds of F 1 (M) gear and F 2 (M) gear are 0.72n I and 1.64n I respectively ; the speeds of R 1 (M) gear and R 2 (M) gear are -0.28n I respectively and -0.64n I.
  • the electromagnetic reversing valve V 1 34 , the pilot proportional relief valve V 2 35 and the accumulator A 1 36 are connected to form a first energy storage system.
  • the electromagnetic reversing valve V 1 34 controls the hydraulic oil on-off
  • the pilot proportional relief valve V 2 35 controls the system pressure
  • the small energy storage system is used alone for low braking energy conditions.
  • the electromagnetic reversing valve V 3 37 , the pilot proportional relief valve V 4 38 and the accumulator A 2 39 are connected to form a second energy storage system.
  • the electromagnetic reversing valve V 3 37 controls the on-off of hydraulic oil
  • the pilot proportional relief valve V 4 38 controls the system pressure
  • the second energy storage system is used alone for medium braking energy conditions.
  • the common use of the first energy storage system and the second energy storage system is suitable for large braking energy conditions.
  • the electromagnetic reversing valve V 1 34 and the electromagnetic reversing valve V 3 37 control the hydraulic oil on and off of the first energy storage system and the second energy storage system respectively.
  • the pilot proportional relief valve V 2 35 and the pilot proportional The set pressure of the relief valve V 4 38 is the same.
  • the braking energy recovery power flow of the transmission mechanism is shown in Figure 9.
  • the rotation direction of the pump/motor mechanism 33 is determined by the confluence mechanism 6, and the clutch C 7 32 and the brake B 1 88 are engaged. and clutch C 4 28, engaging said clutch C 7 32, brake B 1 88 and clutch C 5 29, respectively providing a continuous transmission ratio between the output member and the pump/motor mechanism 33; the braking energy generated by the transmission mechanism is merged Mechanism 6 , mechanical transmission mechanism 2 , transmission mechanism and energy management mechanism gear pair 31 and clutch C 7 32 , transmitted to pump/motor mechanism 33 .
  • the electromagnetic reversing valve V 1 34 or the electromagnetic reversing valve V 3 37 By selectively and individually controlling the electromagnetic reversing valve V 1 34 or the electromagnetic reversing valve V 3 37 , the energy generated when the output member is braked is input into the accumulator A 1 36 or the accumulator A 2 39 .
  • the size of the stored energy is controlled by the pilot proportional relief valve V 2 35 or the pilot proportional relief valve V 4 38 respectively; the electromagnetic reversing valve V is jointly controlled by the selective control.
  • the energy generated when the power output mechanism 4 is braked is input into the accumulator A 1 36 or the accumulator A 2 39 by selectively and individually controlling the electromagnetic reversing valve V 1 34 or the electromagnetic reversing valve V 3 37 , at this time the accumulator A 1 36 or the accumulator A 2 39 is controlled by the pilot proportional relief valve V 2 35 or the pilot proportional relief valve V 4 38 respectively; the electromagnetic commutation is jointly controlled by selective valve V 1 34 and the solenoid valve V 3 37, the braking energy generated when the power take-off means 4 is input to the accumulator and the accumulator a 1 36 a 2 39, this time the ratio of the pilot relief valve V 2 35 and pilot proportional relief valve V 4 38 have the same settings and determine the amount of energy stored in accumulator A 1 36 and accumulator A 2 39 .
  • the power flow of the energy management mechanism alone drives the transmission mechanism as shown in Figure 11. At this time, only the clutch C 1 21, the clutch C 2 81, the clutch C 3 72 and the clutch C 7 32 only need to be engaged, and the power output by the energy management mechanism 3 passes through the transmission mechanism.
  • the gear pair 31 of the energy management mechanism, the input shaft 1 , the hydraulic transmission mechanism 8 and the starting mechanism 7 are output from the output shaft 5 .
  • the energy stored in the accumulator A 1 36 or the accumulator A 2 39 is released separately by selectively controlling the electromagnetic reversing valve V 1 34 or the electromagnetic reversing valve V 3 37, respectively, at this time the pump/motor mechanism
  • the input oil pressure of 33 is controlled separately by the pilot proportional relief valve V 2 35 or the pilot proportional relief valve V 4 38; by selectively controlling the electromagnetic reversing valve V 1 34 and the electromagnetic reversing valve V 3 37, the storage to
  • the energy in the accumulator A 1 36 and the accumulator A 2 39 is released at the same time, at this time the pilot proportional relief valve V 2 35 and the pilot proportional relief valve V 4 38 have the same oil pressure settings, which together determine the pump /The input hydraulic pressure of the motor mechanism 33.
  • the clutch C 8 42 and the clutch C 9 311 are engaged, the first way is, the engine power passes through the power output gear pair 41, the clutch C 8 42, The clutch C 9 311 and the power take-off mechanism and the energy management mechanism gear pair 310 are transmitted to the energy management mechanism 3.
  • the pump/motor mechanism 33 rotates in the same direction as the engine rotation; when the clutch C 1 21 and the clutch C 7 32 are engaged for the second approach, the engine via a power transmission mechanism and the gear mechanism 31 and the energy management sub-clutch C 7 32, is transmitted to the energy management means 3, the opposite case the pump / motor 33 rotation direction means the rotational direction of the engine.
  • the energy transmitted by the engine is input into the accumulator A 1 36 or the accumulator A 2 39.
  • the reversing valve V 3 37 inputs the energy generated when the input shaft 1 is braked into the accumulator A 1 36 and the accumulator A 2 39, at this time the pilot proportional relief valve V 2 35 and the pilot proportional overflow valve Flow valve V 4 38 is set to the same value and determines the amount of energy stored in accumulator A 1 36 and accumulator A 2 39 .

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Abstract

本发明提供了一种带有能量管理机构的机液复合传动装置，包括输入构件、机械传动机构、能量管理机构、动力输出机构、输出构件、汇流机构、起步机构、液压传动机构、离合器组件和制动器组件；所述离合器组件将所述输入构件分别连接到机械传动机构、动力输出机构和液压传动机构，将能量管理机构分别连接到机械传动机构和动力输出机构；所述离合器组件和制动器组件提供输入构件与输出构件和/或动力输出机构之间，提供能量管理机构与输出构件和/或动力输出机构之间，提供能量管理机构和输入构件共同与输出构件和/或动力输出机构之间连续的传动比。本发明集液压传动、机液传动和机械传动为一体，实现传动机构和动力输出机构能量的回收再利用功能。

Description

一种带有能量管理机构的机液复合传动装置 技术领域
本发明涉及自动变速装置领域，特别涉及一种带有能量管理机构的机液复合传动装置。
背景技术
由液压传动和机械传动构成的机液复合传动装置适用于大功率农用或工程车辆。液压传动的低速大转矩特性适用于起步工况，机液传动的高效无级调速特性适用于作业工况，机械传动的高效变速特性适用于行驶工况，集液压传动、机液传动和机械传动为一体的机液复合传动装置具有较高的工程应用价值。
大功率车辆之所以功率较大，主要是动力源除提供传动系统外，还要提供给动力输出系统驱动其它装置对外做功。因此，合理分配传动系统和动力输出系统的能量，并对多余能量进行回收再利用，是提高此类车辆牵引功率和传动效率的重要环节。
发明内容
针对现有技术中存在的不足，本发明提供了一种带有能量管理机构的机液复合传动装置。本发明集液压传动、机液传动和机械传动为一体，并能够实现传动机构和动力输出机构能量的回收再利用功能。
本发明是通过以下技术手段实现上述技术目的的。
一种带有能量管理机构的机液复合传动装置，包括输入构件、机械传动机构、能量管理机构、动力输出机构、输出构件、汇流机构、起步机构、液压传动机构、离合器组件和制动器组件；所述离合器组件将所述输入构件分别连接到机械传动机构、动力输出机构和液压传动机构，将液压传动机构的输出分别连接到机械传动机构和输出构件，将机械传动机构的输出与汇流机构连接，将所述输出构件与汇流机构连接，将能量管理机构分别连接到机械传动机构和动力输出机构；所述离合器组件和制动器组件提供输入构件与输出构件和/或动力输出机构之间，提供能量管理机构与输出构件和/或动力输出机构之间，提供能量管理机构和输入构件共同与输出构件和/或动力输出机构之间连续的传动比。
进一步，通过调节液压传动机构的排量比和选择性控制所述离合器组件和制动器组件的接合，提供输入构件与输出构件之间的传动方式包括：液压传动、机液传动和机械传动。
进一步，所述机械传动机构包括前行星齿轮机构和中行星齿轮机构，所述前行星齿轮机构的行星架与输入构件连接，所述前行星齿轮机构的行星架与中行星齿轮机构的齿圈连接，所述前行星齿轮机构的太阳轮与中行星齿轮机构的太阳轮连接，中行星齿轮机构的太阳轮与 液压传动机构输出端连接；所述汇流机构包括后行星齿轮机构，所述后行星齿轮机构的齿圈与输出构件连接，所述离合器组件将前行星齿轮机构的齿圈或中行星齿轮机构的行星架与后行星齿轮机构的太阳轮连接；
所述离合器组件包括离合器C 2和离合器C 3；所述离合器C 2用于选择性的将液压传动机构的输入端与输入构件连接以共同旋转；所述离合器C 3用于选择性的将液压传动机构的输出端与输出构件连接以共同旋转；通过调节液压传动机构的排量比和选择性控制所述离合器C 2和离合器C 3的接合，提供输入构件与输出构件之间的连续前进或后退液压传动。
进一步，所述离合器组件还包括离合器C 1、离合器C 4、离合器C 5和离合器C 6；所述离合器C 1用于选择性的将输入构件与前行星齿轮机构的行星架连接以共同旋转；所述离合器C 4用于选择性的将中行星齿轮机构的行星架与后行星齿轮机构的太阳轮连接以共同旋转；所述离合器C 5用于选择性的将前行星齿轮机构的齿圈与后行星齿轮机构的太阳轮连接以共同旋转；所述离合器C 6用于选择性的将后行星齿轮机构的齿圈与后行星齿轮机构的太阳轮连接以共同旋转；所述制动器组件包括制动器B 2，所述制动器B 2用于选择性的将后行星齿轮行星架连接到固定件；通过调节液压传动机构的排量比和选择性控制所述离合器C 1、离合器C 2、离合器C 4、离合器C 5、离合器C 6和制动器B 2的接合，提供输入构件与输出构件之间的连续前进或后退的机液传动。
进一步，接合所述离合器C 1、离合器C 2、离合器C 4和离合器C 6，接合所述离合器C 1、离合器C 2、离合器C 5和离合器C 6，接合所述离合器C 1、离合器C 2、离合器C 4和制动器B 2，接合所述离合器C 1、离合器C 2、离合器C 5和制动器B 2，分别提供输入构件与输出构件之间前进或后退各自相异的机液传动。
进一步，所述制动器组件还包括制动器B 1；所述制动器B 1用于选择性的将液压传动机构的输出端连接到固定件；接合所述离合器C 1、离合器C 4、离合器C 6和制动器B 1，接合所述离合器C 1、离合器C 5、离合器C 6和制动器B 1，接合所述离合器C 1、离合器C 4、制动器B 1和制动器B 2，接合所述离合器C 1、离合器C 5、制动器B 1和制动器B 2，分别提供输入构件与输出构件之间前进或后退各自相异的机械传动。
进一步，所述能量管理机构包括泵/马达机构、电磁换向阀V 1、先导比例溢流阀V 2、蓄能器A 1、电磁换向阀V 3、先导比例溢流阀V 4和蓄能器A 2；所述泵/马达机构分别与蓄能器A 1和蓄能器A 2连接；所述电磁换向阀V 1用于控制泵/马达机构与蓄能器A 1连接，泵/马达机构与蓄能器A 1之间安装先导比例溢流阀V 2，所述电磁换向阀V 3用于控制泵/马达机构与蓄能器A 2连接，泵/马达机构与蓄能器A 2之间先导比例溢流阀V 4；所述离合器组件还包括离合器C 7、离合器C 8和离合器C 9，所述离合器C 7用于选择性的将泵/马达机构与前行星齿轮机构的 行星架连接以共同旋转；所述离合器C 9用于选择性的将泵/马达机构与动力输出机构连接以共同旋转；所述离合器C 8用于选择性的将输入构件与动力输出机构连接以共同旋转。
进一步，当所述输出构件制动时，接合所述离合器C 7、制动器B 1和离合器C 4，或接合所述离合器C 7、制动器B 1和离合器C 5，分别提供输出构件与泵/马达机构之间连续的传动比；通过选择性的控制电磁换向阀V 1和电磁换向阀V 3，用于将所述输出构件制动时产生的能量输入蓄能器A 1或/和蓄能器A 2；
当所述动力输出机构制动时，接合所述离合器C 9提供动力输出机构与泵/马达机构之间连续的传动比；通过选择性的控制电磁换向阀V 1和电磁换向阀V 3，用于将所述动力输出机构制动时产生的能量输入蓄能器A 1或/和蓄能器A 2。
进一步，通过选择性控制电磁换向阀V 1和/或电磁换向阀V 3使蓄能器A 1或/和蓄能器A 2作为能量管理机构的输出；
接合离合器C 1、离合器C 2、离合器C 3和离合器C 7，提供能量管理机构与输出构件之间，能量管理机构和输入构件与输出构件之间连续的传动比；
接合离合器C 9提供能量管理机构与动力输出机构之间连续的传动比；
接合离合器C 8和离合器C 9，提供输入构件和能量管理机构与动力输出机构之间连续的传动比。
进一步，接合所述离合器C 8和离合器C 9，接合所述离合器C 1和离合器C 7、分别提供输入构件与泵/马达机构之间连续的传动比；通过选择性的控制电磁换向阀V 1和电磁换向阀V 3，用于将所述输入构件的能量输入蓄能器A 1或/和蓄能器A 2。
本发明的有益效果在于：
1.本发明所述的带有能量管理机构的机液复合传动装置，为一款集液压传动、机液传动和机械传动为一体的多模式机液复合传动装置，适用于不同工况的要求。
2.本发明所述的带有能量管理机构的机液复合传动装置，采用不同的蓄能系统增加能量管理机构的自由度，能量管理机构可单独，或与发动机一道驱动传动机构或动力输出机构。
3.本发明所述的带有能量管理机构的机液复合传动装置，发动机先给能量管理机构存储能量，然后能量管理机构释放能量，与发动机一起满足极端工况的动力性要求；
4.本发明所述的带有能量管理机构的机液复合传动装置，通过控制汇流机构中离合器C 6或制动器B 2的接合，或改变液压传动机构的排量比的正负，控制能量管理机构中泵/马达机构的旋转方向。
附图说明
图1为本发明的结构原理图；
图2为本发明的F(H)档位功率流向示意图；
图3为本发明的F 1(HM)档位功率流向示意图；
图4为本发明的F 2(HM)档位功率流向示意图；
图5为本发明的R(H)档位功率流向示意图；
图6为本发明的R 1(HM)档位功率流向示意图；
图7为本发明的R 2(HM)档位功率流向示意图；
图8为本发明的输出-输入转速比与排量比关系图；
图9为本发明的传动机构能量回收功率流向示意图；
图10为本发明的动力输出机构能量回收功率流向示意图；
图11为本发明的能量管理机构单独驱动传动机构功率流向示意图；
图12为本发明的能量管理机构和发动机共同驱动传动机构功率流向示意图；
图13为本发明的能量管理机构单独驱动动力输出机构功率流向示意图；
图14为本发明的能量管理机构和发动机共同驱动动力输出机构功率流向示意图。
图15本发明的发动机向能量管理机构储能功率流向示意图。
图中：
1-输入轴；2-机械传动机构；21-离合器C 1；22-前行星齿轮行星架；23-前行星齿轮太阳轮；24-中行星齿轮太阳轮；25-中行星齿轮齿圈；26-中行星齿轮行星架；27-前行星齿轮齿圈；28-离合器C 4；29-离合器C 5；3-能量管理机构；31-传动机构与能量管理机构齿轮副；32-离合器C 7；33-泵/马达机构；34-电磁换向阀V 1；35-先导比例溢流阀V 2；36-蓄能器A 1；37-电磁换向阀V 3；38-先导比例溢流阀V 4；39-蓄能器A 2；310-动力输出机构与能量管理机构齿轮副；311-离合器C 9；4-动力输出机构；41-动力输出齿轮副；42-离合器C 8；43-动力输出轴；5-输出轴；6-汇流机构；61-后行星齿轮太阳轮；62-后行星齿轮行星架；63-后行星齿轮齿圈；64-离合器C 6；65-制动器B 2；66-机械传动机构与汇流机构齿轮副；7-起步机构；71-起步机构齿轮副；72-离合器C 3；8-液压传动机构；81-离合器C 2；82-液压传动输入齿轮副；83-泵输入轴；84-变量泵；85-定量马达；86-马达输出轴；87-液压传动输出齿轮副；88-制动器B 1。
具体实施方式
下面结合附图以及具体实施例对本发明作进一步的说明，但本发明的保护范围并不限于此。
如图1所示，本发明所述的带有能量管理机构的机液复合传动装置，包括输入轴1、机械传动机构2、能量管理机构3、动力输出机构4、输出轴5、汇流机构6、起步机构7、液压传动机构8、离合器组件和制动器组件。
所述液压传动机构8包括离合器C 281、液压传动输入齿轮副82、泵输入轴83、变量泵84、定量马达85、马达输出轴86、液压传动输出齿轮副87和制动器B 188。所述泵输入轴83与输入轴1通过液压传动输入齿轮副82连接，所述定量马达85的马达输出轴86通过液压传动输出齿轮副87与中行星齿轮太阳轮24，所述定量马达85的马达输出轴86还通过起步机构7的起步机构齿轮副71与输出轴5连接，所述变量泵84用于提供定量马达85的液压能。所述制动器B 188用于选择性的将马达输出轴86连接到固定件；所述离合器C 281用于选择性的将液压传动机构8的泵输入轴83通过液压传动输入齿轮副82与输入轴1连接以共同旋转。所述起步机构7包括起步机构齿轮副71和离合器C 372；所述离合器C 372用于选择性的将马达输出轴86通过起步机构齿轮副71与输出轴5连接以共同旋转。泵输入轴83带动变量泵84，变量泵84通过改变斜盘倾角驱动定量马达85，继而马达输出轴86输出动力给机械传动机构2或起步机构7。
所述机械传动机构2包括离合器C 121、前行星齿轮行星架22、前行星齿轮太阳轮23、中行星齿轮太阳轮24、中行星齿轮齿圈25、中行星齿轮行星架26、前行星齿轮齿圈27、离合器C 428和离合器C 529。所述前行星齿轮行星架22、前行星齿轮太阳轮23和前行星齿轮齿圈27构成前行星齿轮机构；所述中行星齿轮太阳轮24、中行星齿轮齿圈25和中行星齿轮行星架26构成中行星齿轮机构；所述前行星齿轮行星架22作为机械传动机构2输入端，通过离合器C 121与输入轴1连接，所述前行星齿轮行星架22与中行星齿轮齿圈25连接，所述前行星齿轮太阳轮23与中行星齿轮太阳轮24连接，并通过液压传动输出齿轮副87与马达输出轴86连接。前行星齿轮齿圈27和中行星齿轮行星架26可分别通过离合器C 529和离合器C 428与汇流机构6输入端连接。所述汇流机构6包括后行星齿轮太阳轮61、后行星齿轮行星架62、后行星齿轮齿圈63、离合器C 664、制动器B 265和机械传动机构与汇流机构齿轮副66；所述后行星齿轮太阳轮61、后行星齿轮行星架62和后行星齿轮齿圈63构成后行星齿轮机构；后行星齿轮齿圈63与输出轴5连接。所述离合器C 121用于选择性连接输入轴1和前行星齿轮行星架22；所述离合器C 428用于选择性的将中行星齿轮行星架26通过机械传动机构与汇流机构齿轮副66与后行星齿轮太阳轮61连接以共同旋转；所述离合器C 529用于选择性的将前行星齿轮齿圈27通过机械传动机构与汇流机构齿轮副66与后行星齿轮太阳轮61连接以共同旋转；所述离合器C 664用于选择性的将后行星齿轮太阳轮61和后行星齿轮齿圈63连接；所述制动器B 265用于选择性的将后行星齿轮行星架62固定。
能量管理机构3包括传动机构与能量管理机构齿轮副31、离合器C 732、泵/马达机构33、电磁换向阀V 134、先导比例溢流阀V 235、蓄能器A 136、电磁换向阀V 337、先导比例溢流阀V 438、蓄能器A 239，动力输出机构与能量管理机构齿轮副310和离合器C 9311；所述泵/ 马达机构33为可以在泵和液压马达之间进行功能切换的装置，即当泵/马达机构33输入机械能，所述泵/马达机构33输出液压能，当泵/马达机构33输入液压能，所述泵/马达机构33输出机械能。所述泵/马达机构33通过传动机构与能量管理机构齿轮副31与前行星齿轮行星架22连接。所述泵/马达机构33通过动力输出机构与能量管理机构齿轮副310与动力输出机构4连接；所述电磁换向阀V 134、先导比例溢流阀V 235和蓄能器A 136连接，构成第一蓄能系统，所述电磁换向阀V 337、先导比例溢流阀V 438和蓄能器A 239连接，构成第二蓄能系统，所述第一蓄能系统和第二蓄能系统并联，并与泵/马达机构33连接。所述动力输出机构4包括动力输出齿轮副41、离合器C 842和动力输出轴43；动力输出轴43通过动力输出齿轮副41与输入轴1连接。所述离合器C 732用于选择性的将泵/马达机构33通过传动机构与能量管理机构齿轮副31与前行星齿轮行星架22连接以共同旋转；所述离合器C 9311用于选择性的将泵/马达机构33通过动力输出机构与能量管理机构齿轮副310与动力输出轴43连接以共同旋转；所述离合器C 842用于选择性的将输入轴1通过动力输出齿轮副41与动力输出轴43连接以共同旋转。
通过调节液压传动机构8的排量比和选择性控制所述离合器组件和制动器组件的接合，提供输入构件与输出构件之间的传动方式包括：液压传动、机液传动和机械传动。下面结合表1具体举例说明：
如图2和图5所示，液压传动包括前进液压传动F(H)和后退液压传动R(H)。
本发明的F(H)档位功率流向如图2所示。当接合离合器C 281和离合器C 372时，发动机提供的动力经输入轴1、液压传动机构8和起步机构7，从输出轴5输出，当液压传动机构8的排量比为正时，为F(H)档位。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000001
式中，n o为输出轴转速，n I为输入轴转速，e为液压传动机构的排量比，i 1为液压传动输入齿轮副82的传动比。i 3为起步机构齿轮副71的传动比。
本发明的R(H)档位功率流向如图5所示。当接合离合器C 281和离合器C 372时，发动机提供的动力经输入轴1、液压传动机构8和起步机构7，从输出轴5输出，当液压传动机构8的排量比为负时，为R(H)档位。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000002
如图3、图4、图6和图7所示，机液传动包括前进机液传动F 1(HM)、前进机液传动F 2(HM)、后退机液传动R 1(HM)、后退机液传动R 2(HM)。
本发明的F 1(HM)档位功率流向如图3所示。当接合离合器C 121、离合器C 281、离合器C 428和离合器C 664时，发动机提供的动力在输入轴1处分流，一路经前行星齿轮行星架22传递到中行星齿轮齿圈25，一路经液压传动机构8传递到中行星齿轮太阳轮24，到达中行星齿轮齿圈25的机械动力和到达中行星齿轮太阳轮24的液压动力在中行星齿轮行星架26处汇流后，经机械传动机构与汇流机构齿轮副66传递到汇流机构6，此时汇流机构6连为一体，动力从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000003
式中，i 2为液压传动输出齿轮副的传动比，k 2为中行星齿轮机构特性参数。
本发明的F 2(HM)档位功率流向如图4所示。当接合离合器C 121、离合器C 281、离合器C 529和离合器C 664时，发动机提供的动力在输入轴1处分流，一路直接传递到前行星齿轮行星架22，一路经液压传动机构8传递到前行星齿轮太阳轮23，到达前行星齿轮行星架22的机械动力和到达前行星齿轮太阳轮23的液压动力在前行星齿轮齿圈27处汇流后，经机械传动机构与汇流机构齿轮副66传递到汇流机构6，此时汇流机构6连为一体，动力从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000004
式中，k 1为前行星齿轮机构特性参数。
本发明的R 1(HM)档位功率流向如图6所示。当接合离合器C 121、离合器C 281、离合器C 428和制动器B 265时，发动机提供的动力在输入轴1处分流，一路经前行星齿轮行星架22传递到中行星齿轮齿圈25，一路经液压传动机构8传递到中行星齿轮太阳轮24，到达中行星齿轮齿圈25的机械动力和到达中行星齿轮太阳轮24的液压动力在中行星齿轮行星架26处汇流后，经机械传动机构与汇流机构齿轮副66传递到后行星齿轮太阳轮61，经后行星齿轮齿圈63，从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000005
式中，k 3为后行星齿轮机构特性参数。
本发明的R 2(HM)档位功率流向如图7所示。当接合离合器C 121、离合器C 281、离合器C 529和制动器B 265时，发动机提供的动力在输入轴1处分流，一路直接传递到前行星 齿轮行星架22，一路经液压传动机构8传递到前行星齿轮太阳轮23，到达前行星齿轮行星架22的机械动力和到达前行星齿轮太阳轮23的液压动力在前行星齿轮齿圈27处汇流后，经机械传动机构与汇流机构齿轮副66传递到后行星齿轮太阳轮61，再经后行星齿轮齿圈63，从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000006
机械传动包括前进机械传动F 1(M)、前进机械传动F 2(M)、后退机械传动R 1(M)、后退机械传动R 2(M)。
本发明的F 1(M)档位功率流向借鉴图3所示，此时液压路不传递动力。当接合离合器C 121、离合器C 428、离合器C 664和制动器B 188时，发动机提供的动力经输入轴1、前行星齿轮行星架22、中行星齿轮齿圈25、中行星齿轮行星架26、机械传动机构与汇流机构齿轮副66和汇流机构6，从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000007
本发明的F 2(M)档位功率流向借鉴图4所示，此时液压路不传递动力。当接合离合器C 121、离合器C 529、离合器C 664和制动器B 188时，发动机提供的动力经输入轴1、前行星齿轮行星架22、前行星齿轮齿圈27、机械传动机构与汇流机构齿轮副66和汇流机构6，从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000008
本发明的R 1(M)档位功率流向借鉴图6所示，此时液压路不传递动力。当接合离合器C 121、离合器C 428、制动器B 188和制动器B 265时，发动机提供的动力经输入轴1、前行星齿轮行星架22、中行星齿轮齿圈25、中行星齿轮行星架26、机械传动机构与汇流机构齿轮副66、后行星齿轮太阳轮61和后行星齿轮齿圈63，从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000009
本发明的R 2(M)档位功率流向借鉴图7所示，此时液压路不传递动力。当接合离合器C 121、离合器C 529、制动器B 188和制动器B 265时，发动机提供的动力经输入轴1、前行星齿轮行星架22、前行星齿轮齿圈27、机械传动机构与汇流机构齿轮副66、后行星齿轮太 阳轮61和后行星齿轮齿圈63，从输出轴5输出。此时，输出轴转速与发动机转速关系为：
Figure PCTCN2020106674-appb-000010
表1各元件接合表
Figure PCTCN2020106674-appb-000011
表中：1.“B”代表制动器，“C”代表离合器，“F”代表前进挡，“R”代表后退档，“H”代表液压传动，“M”代表机械传动，“HM”代表机液复合传动。
2.“▲”代表换挡元件接合，“△”代表换挡元件分离。
实施例，选取参数如下：i 1i 2＝1.00，i 1i 3＝1.00，k 1＝1.56，k 2＝k 3＝2.56。
本发明的输出-输入转速比与排量比关系如图8所示。当e∈[0，1.00]范围内，F(H)档位调速范围为[0，1.00]n I；当e∈[-1.00，1.00]范围内，F 1(HM)档位调速范围为[0.44，1.00]n I；当e∈[-1.00，1.00]范围内，F 2(HM)档位调速范围为[1.00，2.28]n I；当e∈[-1.00，0]范围内，R(H)档位调速范围为[-1.00，0]n I；当e∈[-1.00，1.00]范围内，R 1(HM)档位调速范围为[-0.39，-0.17]n I；R 2(HM)档位调速范围为[-0.89，-0.39]n I。F 1(M)档位和F 2(M)档位的速度分别为0.72n I和1.64n I；R 1(M)档位和R 2(M)档位的速度分别为-0.28n I和-0.64n I。当e＝1.00时，F(H)档位切换到F 1(HM)档位可实现无动力中断调速，此时n o＝n I；当e＝1.00时，F(H)档位切换到F 2(HM)档位可实现无动力中断调速，此时n o＝n I；当e＝1.00时，F 1(HM)档位切换到F 2(HM)档位可实现无动力中断调速，此时n o＝n I。当e＝-0.25时，R(H)档位切换到R 1(HM)档位可实现无动力中断调速，此时n o＝-0.25n I；当e＝-0.85时， R(H)档位切换到R 2(HM)档位可实现无动力中断调速，此时n o＝-0.85n I；当e＝1.00时，R 1(HM)档位切换到R 2(HM)档位可实现无动力中断调速，此时n o＝-0.39n I。
电磁换向阀V 134、先导比例溢流阀V 235和蓄能器A 136连接，构成第一蓄能系统。通电磁换向阀V 134控制液压油通断，先导比例溢流阀V 235控制系统压力，小蓄能系统单独使用适用于低制动能量工况。
电磁换向阀V 337、先导比例溢流阀V 438和蓄能器A 239连接，构成第二蓄能系统。电磁换向阀V 337控制液压油通断，先导比例溢流阀V 438控制系统压力，第二蓄能系统单独使用适用于中制动能量工况。
第一蓄能系统和第二蓄能系统共同使用适用于大制动能量工况。此时电磁换向阀V 134和电磁换向阀V 337分别控制第一蓄能系统和第二蓄能系统的液压油通断，此刻所述先导比例溢流阀V 235和先导比例溢流阀V 438的设定压力相同。
传动机构制动能量回收功率流向如图9所示，当所述输出轴5制动时，泵/马达机构33的旋转方向由汇流机构6决定，接合所述离合器C 732、制动器B 188和离合器C 428，接合所述离合器C 732、制动器B 188和离合器C 529，分别提供输出构件与泵/马达机构33之间连续的传动比；传动机构产生的制动能量经汇流机构6、机械传动机构2、传动机构与能量管理机构齿轮副31和离合器C 732，传递到泵/马达机构33。通过选择性单独控制电磁换向阀V 134或电磁换向阀V 337，将所述输出构件制动时产生的能量输入到蓄能器A 136或蓄能器A 239里，此时蓄能器A 136或蓄能器A 239内的蓄能大小由先导比例溢流阀V 235或先导比例溢流阀V 438分别控制；通过选择性共同控制电磁换向阀V 134和电磁换向阀V 337，将所述输出构件制动时产生的能量输入到蓄能器A 136和蓄能器A 239里，此时先导比例溢流阀V 235和先导比例溢流阀V 438的设定值相同，且决定蓄能器A 136和蓄能器A 239内的蓄能大小。
动力输出机构制动能量回收功率流向如图10所示，当所述动力输出机构4制动时，接合所述离合器C 9311，动力输出机构产生的制动能量经离合器C 9311和动力输出机构与能量管理机构齿轮副310，传递到泵/马达机构33。通过选择性单独控制电磁换向阀V 134或电磁换向阀V 337，将所述动力输出机构4制动时产生的能量输入到蓄能器A 136或蓄能器A 239里，此时蓄能器A 136或蓄能器A 239内的蓄能大小由先导比例溢流阀V 235或先导比例溢流阀V 438分别控制；通过选择性共同控制电磁换向阀V 134和电磁换向阀V 337，将所述动力输出机构4制动时产生的能量输入到蓄能器A 136和蓄能器A 239里，此时先导比例溢流阀V 235和先导比例溢流阀V 438的设定值相同，且决定蓄能器A 136和蓄能器A 239内的蓄能大小。
能量管理机构单独驱动传动机构功率流向如图11所示，此时只需接合离合器C 121、离 合器C 281、离合器C 372和离合器C 732，能量管理机构3输出的动力经传动机构与能量管理机构齿轮副31、输入轴1、液压传动机构8和起步机构7，从输出轴5输出。
能量管理机构和发动机共同驱动传动机构功率流向如图12所示，此时只需接合离合器C 121、离合器C 281、离合器C 372和离合器C 732，能量管理机构3输出的动力经传动机构与能量管理机构齿轮副31，与传递到输入轴1的发动机动力混合，混合动力经液压传动机构8和起步机构7，从输出轴5输出。
能量管理机构单独驱动动力输出机构功率流向如图13所示，此时只需接合离合器C 9311，能量管理机构3输出的动力经动力输出机构与能量管理机构齿轮副310和离合器C 9311，从动力输出轴43输出。
能量管理机构和发动机共同驱动动力输出机构功率流向如图14所示，此时只需接合离合器C 842和离合器C 9311，能量管理机构3输出的动力经传动机构与能量管理机构齿轮副31和C 9311，与经动力输出齿轮副41和离合器C 842传递到动力输出轴43的发动机动力汇合，从动力输出轴43输出。
通过选择性单独控制电磁换向阀V 134或电磁换向阀V 337，将存储到蓄能器A 136或蓄能器A 239里的能量分别释放出来，此时泵/马达机构33的输入油压由先导比例溢流阀V 235或先导比例溢流阀V 438分别控制；通过选择性共同控制电磁换向阀V 134和电磁换向阀V 337，将存储到蓄能器A 136和蓄能器A 239里的能量同时释放出来，此时先导比例溢流阀V 235和先导比例溢流阀V 438油压的设定值相同，共同决定泵/马达机构33的输入油压。
发动机向能量管理机构储能功率流向如图15所示，有两种方式；当离合器C 842和离合器C 9311接合时为方式一，发动机动力经动力输出齿轮副41、离合器C 842、离合器C 9311和动力输出机构与能量管理机构齿轮副310，传递到能量管理机构3，此时泵/马达机构33旋转方向与发动机旋转方向相同；当离合器C 121和离合器C 732接合时为方式二，发动机动力经传动机构与能量管理机构齿轮副31和离合器C 732，传递到能量管理机构3，此时泵/马达机构33旋转方向与发动机旋转方向相反。通过选择性单独控制电磁换向阀V 134或电磁换向阀V 337，将所述发动机传递的能量输入到蓄能器A 136或蓄能器A 239里，此时蓄能器A 136或蓄能器A 239内的蓄能大小由先导比例溢流阀V 235或先导比例溢流阀V 438分别控制；通过选择性共同控制电磁换向阀V 134和电磁换向阀V 337，将所述输入轴1制动时产生的能量输入到蓄能器A 136和蓄能器A 239里，此时先导比例溢流阀V 235和先导比例溢流阀V 438的设定值相同，且决定蓄能器A 136和蓄能器A 239内的蓄能大小。
所述实施例为本发明的优选的实施方式，但本发明并不限于上述实施方式，在不背离本发明的实质内容的情况下，本领域技术人员能够做出的任何显而易见的改进、替换或变型均 属于本发明的保护范围。

Claims (10)

  1. 一种带有能量管理机构的机液复合传动装置，其特征在于，包括输入构件、机械传动机构(2)、能量管理机构(3)、动力输出机构(4)、输出构件、汇流机构(6)、起步机构(7)、液压传动机构(8)、离合器组件和制动器组件；所述离合器组件将所述输入构件分别连接到机械传动机构(2)、动力输出机构(4)和液压传动机构(8)，将液压传动机构(8)的输出分别连接到机械传动机构(2)和输出构件，将机械传动机构(2)的输出与汇流机构(6)连接，将所述输出构件与汇流机构(6)连接，将能量管理机构(3)分别连接到机械传动机构(2)和动力输出机构(4)；所述离合器组件和制动器组件提供输入构件与输出构件和/或动力输出机构(7)之间，提供能量管理机构(3)与输出构件和/或动力输出机构(7)之间，提供能量管理机构(3)和输入构件共同与输出构件和/或动力输出机构(7)之间连续的传动比。
  2. 根据权利要求1所述的带有能量管理机构的机液复合传动装置，其特征在于，通过调节液压传动机构(8)的排量比和选择性控制所述离合器组件和制动器组件的接合，提供输入构件与输出构件之间的传动方式包括：液压传动、机液传动和机械传动。
  3. 根据权利要求2所述的带有能量管理机构的机液复合传动装置，其特征在于，所述机械传动机构(2)包括前行星齿轮机构和中行星齿轮机构，所述前行星齿轮机构的行星架与输入构件连接，所述前行星齿轮机构的行星架与中行星齿轮机构的齿圈连接，所述前行星齿轮机构的太阳轮与中行星齿轮机构的太阳轮连接，中行星齿轮机构的太阳轮与液压传动机构(8)输出端连接；所述汇流机构(6)包括后行星齿轮机构，所述后行星齿轮机构的齿圈与输出构件连接，所述离合器组件将前行星齿轮机构的齿圈或中行星齿轮机构的行星架与后行星齿轮机构的太阳轮连接；
    所述离合器组件包括离合器C 2(81)和离合器C 3(72)；所述离合器C 2(81)用于选择性的将液压传动机构(8)的输入端与输入构件连接以共同旋转；所述离合器C 3(72)用于选择性的将液压传动机构(8)的输出端与输出构件连接以共同旋转；通过调节液压传动机构(8)的排量比和选择性控制所述离合器C 2(81)和离合器C 3(72)的接合，提供输入构件与输出构件之间的连续前进或后退液压传动。
  4. 根据权利要求3所述的带有能量管理机构的机液复合传动装置，其特征在于，所述离合器组件还包括离合器C 1(21)、离合器C 4(28)、离合器C 5(29)和离合器C 6(64)；所述离合器C 1(21)用于选择性的将输入构件与前行星齿轮机构的行星架连接以共同旋转；所述离合器C 4(28)用于选择性的将中行星齿轮机构的行星架与后行星齿轮机构的太阳轮连接以共同旋转；所述离合器C 5(29)用于选择性的将前行星齿轮机构的齿圈与后行星齿轮机构的太阳轮连接以共同旋转；所述离合器C 6(64)用于选择性的将后行星齿轮机构的齿圈与后行 星齿轮机构的太阳轮连接以共同旋转；所述制动器组件包括制动器B 2(65)，所述制动器B 2(65)用于选择性的将后行星齿轮机构的行星架连接到固定件；通过调节液压传动机构(8)的排量比和选择性控制所述离合器C 1(21)、离合器C 2(81)、离合器C 4(28)、离合器C 5(29)、离合器C 6(64)和制动器B 2(65)的接合，提供输入构件与输出构件之间的连续前进或后退的机液传动。
  5. 根据权利要求4所述的带有能量管理机构的机液复合传动装置，其特征在于，接合所述离合器C 1(21)、离合器C 2(81)、离合器C 4(28)和离合器C 6(64)，接合所述离合器C 1(21)、离合器C 2(81)、离合器C 5(29)和离合器C 6(64)，接合所述离合器C 1(21)、离合器C 2(81)、离合器C 4(28)和制动器B 2(65)，接合所述离合器C 1(21)、离合器C 2(81)、离合器C 5(29)和制动器B 2(65)，分别提供输入构件与输出构件之间前进或后退各自相异的机液传动。
  6. 根据权利要求4所述的带有能量管理机构的机液复合传动装置，其特征在于，所述制动器组件还包括制动器B 1(88)；所述制动器B 1(88)用于选择性的将液压传动机构(8)的输出端连接到固定件；接合所述离合器C 1(21)、离合器C 4(28)、离合器C 6(64)和制动器B 1(88)，接合所述离合器C 1(21)、离合器C 5(29)、离合器C 6(64)和制动器B 1(88)，接合所述离合器C 1(21)、离合器C 4(28)、制动器B 1(88)和制动器B 2(65)，接合所述离合器C 1(21)、离合器C 5(29)、制动器B 1(88)和制动器B 2(65)，分别提供输入构件与输出构件之间前进或后退各自相异的机械传动。
  7. 根据权利要求6所述的带有能量管理机构的机液复合传动装置，其特征在于，所述能量管理机构(3)包括泵/马达机构(33)、电磁换向阀V 1(34)、先导比例溢流阀V 2(35)、蓄能器A 1(36)、电磁换向阀V 3(37)、先导比例溢流阀V 4(38)和蓄能器A 2(39)；所述泵/马达机构(33)分别与蓄能器A 1(36)和蓄能器A 2(39)连接；所述电磁换向阀V 1(34)用于控制泵/马达机构(33)与蓄能器A 1(36)连接，泵/马达机构(33)与蓄能器A 1(36)之间安装先导比例溢流阀V 2(35)，所述电磁换向阀V 3(37)用于控制泵/马达机构(33)与蓄能器A 2(39)连接，泵/马达机构(33)与蓄能器A 2(39)之间安装先导比例溢流阀V 4(38)；所述离合器组件还包括离合器C 7(32)、离合器C 8(42)和离合器C 9(311)，所述离合器C 7(32)用于选择性的将泵/马达机构(33)与前行星齿轮机构的行星架连接以共同旋转；所述离合器C 9(311)用于选择性的将泵/马达机构(33)与动力输出机构(4)连接以共同旋转；所述离合器C 8(42)用于选择性的将输入构件与动力输出机构(4)连接以共同旋转。
  8. 根据权利要求7所述的带有能量管理机构的机液复合传动装置，其特征在于，当所述输出构件制动时，接合所述离合器C 7(32)、制动器B 1(88)和离合器C 4(28)，或接合所 述离合器C 7(32)、制动器B 1(88)和离合器C 5(29)，分别提供输出构件与泵/马达机构(33)之间连续的传动比；通过选择性的控制电磁换向阀V 1(34)和电磁换向阀V 3(37)，用于将所述输出构件制动时产生的能量输入蓄能器A 1(36)或/和蓄能器A 2(39)；
    当所述动力输出机构(4)制动时，接合所述离合器C 9(311)提供动力输出机构(4)与泵/马达机构(33)之间连续的传动比；通过选择性的控制电磁换向阀V 1(34)和电磁换向阀V 3(37)，用于将所述动力输出机构(4)制动时产生的能量输入蓄能器A 1(36)或/和蓄能器A 2(39)。
  9. 根据权利要求7所述的带有能量管理机构的机液复合传动装置，其特征在于，通过选择性控制电磁换向阀V 1(34)和/或电磁换向阀V 3(37)，使蓄能器A 1(36)或/和蓄能器A 2(39)作为能量管理机构(3)的输出；
    接合离合器C 1(21)、离合器C 2(81)、离合器C 3(72)和离合器C 7(32)，提供能量管理机构(3)与输出构件之间，能量管理机构(3)和输入构件与输出构件之间连续的传动比；
    接合离合器C 9(311)提供能量管理机构(3)与动力输出机构(4)之间连续的传动比；
    接合离合器C 8(42)和离合器C 9(311)，提供能量管理机构(3)和输入构件与动力输出机构(4)之间连续的传动比。
  10. 根据权利要求7所述的带有能量管理机构的机液复合传动装置，其特征在于，接合所述离合器C 8(42)和离合器C 9(311)，接合所述离合器C 1(21)和离合器C 7(32)，分别提供输入构件与泵/马达机构(33)之间连续的传动比；通过选择性的控制电磁换向阀V 1(34)和电磁换向阀V 3(37)，用于将所述输入构件的能量输入蓄能器A 1(36)或/和蓄能器A 2(39)。
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