CN113983138B - Machine-liquid compound transmission device comprising single-pump control double-acting motor system - Google Patents

Machine-liquid compound transmission device comprising single-pump control double-acting motor system Download PDF

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Publication number
CN113983138B
CN113983138B CN202111255412.6A CN202111255412A CN113983138B CN 113983138 B CN113983138 B CN 113983138B CN 202111255412 A CN202111255412 A CN 202111255412A CN 113983138 B CN113983138 B CN 113983138B
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China
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reversing valve
clutch
hydraulic
motor
energizing
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CN113983138A (en
Inventor
朱镇
邓雨林
蔡英凤
陈龙
曾令新
田翔
孙晓东
曾发林
夏长高
徐兴
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Jiangsu University
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Jiangsu University
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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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements
    • 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
    • F16H61/04—Smoothing ratio shift
    • 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
    • F16H2047/045—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 the fluid gearing comprising a plurality of pumps or motors

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Fluid Gearings (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention provides a machine-liquid compound transmission device comprising a single-pump control double-acting motor system, which comprises an input member, a front planetary gear mechanism, a rear planetary gear mechanism, a hydraulic transmission mechanism, an output member, a brake assembly and a clutch assembly, wherein the hydraulic transmission mechanism comprises a hydraulic pump, an outer motor, an inner motor and a control valve assembly; the clutch assembly connects the input member to the input of the front planetary gear set and the input of the hydraulic transmission mechanism, respectively, the clutch assembly connects the output of the hydraulic transmission mechanism to the front planetary gear set and the rear planetary gear set, respectively, the clutch assembly connects the front planetary gear set to the rear planetary gear set, the clutch assembly connects the rear planetary gear set to the output member, and the clutch assembly, brake assembly and control valve assembly provide a continuous transmission ratio between the input member and the output member. The invention is beneficial to improving the dynamic property, the fuel economy and the service life of the vehicle.

Description

Machine-liquid compound transmission device comprising single-pump control double-acting motor system
Technical Field
The invention relates to the field of variable speed transmission devices, in particular to a mechanical-hydraulic compound transmission device comprising a single-pump control double-acting motor system.
Background
The running system of engineering machinery has complex operation condition and severe environment, and relates to starting, operation and transition working conditions, wherein the transmission device is required to provide a transmission ratio with low rotation speed and high torque during starting, and the transmission device is required to provide a transmission ratio with high rotation speed and low torque during operation. Therefore, the complexity of the working condition of the engineering machinery running system determines that the transmission device has higher requirements and more complex structure than the transmission device of a common vehicle.
The mechanical-hydraulic composite transmission has the characteristics of stepless speed regulation of hydraulic transmission and efficient speed change of mechanical transmission, and improves the performance of the transmission device. The mechanical-hydraulic composite transmission device can realize high-efficiency stepless speed change by improving the design scheme and design parameters of a mechanical transmission mechanism and a hydraulic transmission mechanism, integrates multiple transmission modes into a whole and has multiple modes, and is a feasible scheme for improving the performance of the transmission device.
The hydrostatic transmission technology is commonly applied to the engineering machinery traveling system, but is greatly influenced by the action environment, the degree of freedom of adjustment of a hydraulic system can be greatly improved by adopting a single-pump control double-acting motor system, high-precision adjustment can be performed under the condition of low-speed operation, and the stable running of a vehicle is kept; the wide-range adjustment can be performed under the transition condition so as to adapt to the requirement of high-speed running of the vehicle and further improve the performance of the mechanical-hydraulic compound transmission device.
Disclosure of Invention
Aiming at the defects existing in the prior art, the invention provides a mechanical-hydraulic compound transmission device comprising a single-pump control double-acting motor system, provides a plurality of operation modes and speed regulation modes according to complex operation working conditions, can fully utilize the high-efficiency speed change performance of mechanical transmission and the stepless speed regulation performance of hydraulic transmission by switching a clutch and a brake and adjusting the displacement ratio of a hydraulic transmission mechanism, and is beneficial to improving the dynamic performance, the fuel economy and the service life of a vehicle.
The present invention achieves the above technical object by the following means.
A hydraulic compound transmission device comprising a single-pump control double-acting motor system, which comprises an input member, a front planetary gear mechanism, a rear planetary gear mechanism, a hydraulic transmission mechanism, an output member, a brake assembly and a clutch assembly, wherein the hydraulic transmission mechanism comprises a hydraulic pump, an outer motor, an inner motor and a control valve assembly; the outer motor and the inner motor share an output shaft; the output shaft is an output end of the hydraulic transmission mechanism; the outer motor or/and the inner motor is/are controlled to be communicated with the hydraulic pump through the control valve assembly; the displacement of the outer motor is larger than that of the inner motor;
the clutch assembly connects the input member to the input of the front planetary gear set and the input of the hydraulic transmission mechanism, respectively, the clutch assembly connects the output of the hydraulic transmission mechanism to the front planetary gear set and the rear planetary gear set, respectively, the clutch assembly connects the front planetary gear set to the rear planetary gear set, the clutch assembly connects the rear planetary gear set to the output member, and the clutch assembly, brake assembly and control valve assembly provide a continuous transmission ratio between the input member and the output member.
Further, the front planetary gear mechanism comprises a front planetary gear sun gear, a front planetary gear carrier and a front planetary gear ring; the rear planet row mechanism comprises a rear planet row planet carrier, a rear planet row gear ring and a rear planet row sun gear; the rear planet carrier is connected with an output member;
the brake assembly comprises a first brake B 1 Second brake B 2 And a third brake B 3 The method comprises the steps of carrying out a first treatment on the surface of the The first brake B 1 For selectively connecting the rear planet row ring gear to the stationary member; the second brake B 2 For selectively connecting the front planet row sun gear to the mount; the third brake B 3 For selectively connecting the rear planet row sun gear to the mount;
the clutch assembly includes a first clutch C 1 Second clutch C 2 Third clutch C 3 Fourth clutch C 4 Fifth clutch C 5 Sixth clutch C 6 And a seventh clutch C 7 The method comprises the steps of carrying out a first treatment on the surface of the The first clutch C 1 For selectively connecting the input member to the front planet carrier for common rotation; the second partClutch C 2 For selectively connecting the front planet carrier to the rear planet ring gear for common rotation; the third clutch C 3 For selectively connecting the front planet carrier to the front planet ring gear for common rotation; the fourth clutch C 4 For selectively connecting the front planet ring gear to the rear planet carrier for common rotation; the fifth clutch C 5 For selectively connecting the input member to the hydraulic transmission input for common rotation; the sixth clutch C 6 For selectively connecting the output of the hydraulic drive to the rear planet row sun gear for common rotation; the seventh clutch C 7 For selectively connecting the hydraulic drive mechanism output to the front planetary row sun gear for common rotation;
the inside of the outer motor is respectively provided with two independent first outer motor flow passages and second outer motor flow passages, and the displacement of the first outer motor flow passages is the same as that of the second outer motor flow passages; the inner motor is internally provided with two independent first inner motor flow passages and second inner motor flow passages respectively, and the displacement of the first inner motor flow passages is the same as that of the second inner motor flow passages; the control valve assembly comprises a first reversing valve S 1 Second reversing valve S 2 Third reversing valve S 3 And a fourth reversing valve S 4 A second reversing valve S is arranged between the first outer motor runner and the hydraulic pump 2 A first reversing valve S is arranged between the second outer motor runner and the hydraulic pump 1 A fourth reversing valve S is arranged between the first inner motor runner and the hydraulic pump 4 A third reversing valve S is arranged between the second inner motor runner and the hydraulic pump 3 。
Further, the hydraulic transmission mechanism is a single-pump control double-acting motor system, the displacement of one flow passage in the inner motor is set to be V, and when the two flow passages of the inner motor work simultaneously, the displacement of the inner motor is set to be 2V; the displacement of the outer motor is CV, and when the two flow passages of the outer motor work simultaneously, the displacement of the inner motor is 2CV, wherein C is a displacement coefficient, C>1, a step of; total displacement V of hydraulic motor of hydraulic transmission mechanism m ＝2V+2CV；V pmax Representing hydraulic pump displacement V p Is the maximum value of (2); the displacement ratio of the hydraulic pump:
when the first reversing valve S 1 Energizing the right position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the middle position, the fourth reversing valve S 4 When the middle position is electrified, the hydraulic pump is respectively communicated with the first outer motor runner and the second outer motor runner;
when the first reversing valve S 1 Energizing the middle position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the middle position, the fourth reversing valve S 4 When the middle position is electrified, the hydraulic pump is communicated with the first outer motor runner;
when the first reversing valve S 1 Energizing the middle position, the second reversing valve S 2 Energizing the middle position, the third reversing valve S 3 Energizing the right position, the fourth reversing valve S 4 When the right position is electrified, the hydraulic pump is respectively communicated with the first inner motor runner and the second inner motor runner;
when the first reversing valve S 1 Energizing the middle position, the second reversing valve S 2 Energizing the middle position, the third reversing valve S 3 Energizing the right position, the fourth reversing valve S 4 When the middle position is electrified, the hydraulic pump is communicated with the second inner motor runner;
when the first reversing valve S 1 Energizing the right position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the right position, the fourth reversing valve S 4 When the right position is electrified, the hydraulic pump is respectively communicated with the first outer motor runner, the second outer motor runner, the first inner motor runner and the second inner motor runner;
when the first reversing valve S 1 Energizing the right position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the right position, the fourth reversing valve S 4 When the middle position is electrified, the hydraulic pump is respectively communicated with the first outer motor runner, the second outer motor runner and the second inner motor runner;
when the first reversing valve S 1 Energizing the middle position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the right position, the fourth reversing valve S 4 When the right position is electrified, the hydraulic pump is respectively communicated with the first outer motor runner, the first inner motor runner and the second inner motor runner;
when the first reversing valve S 1 Energizing the middle position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the right position, the fourth reversing valve S 4 When the middle position is electrified, the hydraulic pump is respectively communicated with the first outer motor runner and the second inner motor runner;
when the first reversing valve S 1 Energizing the right position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the left position, the fourth reversing valve S 4 When the middle position is electrified, the outlet of the hydraulic pump is respectively communicated with the inlet of the first outer motor runner, the inlet of the second outer motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner, the outlet of the second outer motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump;
when the first reversing valve S 1 Energizing the right position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the left position, the fourth reversing valve S 4 When the left position is electrified, the outlet of the hydraulic pump is respectively communicated with the inlet of the first outer motor runner, the inlet of the second outer motor runner, the outlet of the first inner motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner, the outlet of the second outer motor runner, the inlet of the first inner motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump;
when the first reversing valve S 1 Energizing the middle position, the second reversing valve S 2 Electrifying the right position,The third reversing valve S 3 Energizing the left position, the fourth reversing valve S 4 When the middle position is electrified, the outlet of the hydraulic pump is respectively communicated with the inlet of the first outer motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump;
when the first reversing valve S 1 Energizing the middle position, the second reversing valve S 2 Energizing the right position, the third reversing valve S 3 Energizing the left position, the fourth reversing valve S 4 When the power is on in the left position, the outlet of the hydraulic pump is respectively communicated with the inlet of the first outer motor runner, the outlet of the first inner motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner, the inlet of the first inner motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump.
Further, by controlling the first reversing valve S 1 Second reversing valve S 2 Third reversing valve S 3 And a fourth reversing valve S 4 To cause the hydraulic transmission mechanism to output the following rotational speed ranges:
medium speed regulation mode:
low speed mode:
high speed regulation mode:
wherein: n is n p To input the rotation speed of the hydraulic pump, n m Is the rotational speed of the hydraulic motor output.
Further, providing a transmission between the input member and the output member by adjusting a displacement ratio of the hydraulic transmission and selectively controlling engagement of the brake assembly, the clutch assembly, and the control valve assembly includes: hydraulic transmission, mechanical-hydraulic transmission and mechanical transmission.
Further, selectively controlling the control valve assembly and selectively controlling the fifth clutch C by adjusting a displacement ratio of the hydraulic transmission 5 And a first brake B 1 Engagement by selectively controlling the sixth clutch C 6 Engaging or second clutch C 2 Fourth clutch C 4 And a seventh clutch C 7 Engagement provides a hydraulic transmission of multiple transmission between the input member and the output member.
Further, selectively controlling the control valve assembly and selectively controlling the fifth clutch C by adjusting a displacement ratio of the hydraulic transmission 5 And a first clutch C 1 Engagement by selective control of fourth clutch C 4 And a seventh clutch C 7 Engaging or second clutch C 2 And a sixth clutch C 6 Engagement provides a plurality of transmission modes between the input member and the output member.
Further, the first clutch C is selectively controlled 1 Engagement by selectively controlling the second clutch C 2 And a third brake B 3 Engaging or third clutch C 3 And a fourth clutch C 4 Engaging or fourth clutch C 4 And a second brake B 2 Engagement provides a mechanical transmission of multiple transmission between the input member and the output member.
Further, the displacement ratio of the hydraulic transmission mechanism is regulated, and the control valve assembly is selectively controlled, so that the low speed regulation mode, the medium speed regulation mode and the high speed regulation mode are forward stepless speed regulation, and the low speed and high torque operation requirements are met; the hydraulic transmission mode is switched to the machine liquid transmission mode without power interruption by adjusting the displacement ratio of the hydraulic transmission mechanism.
The invention has the beneficial effects that:
1. the single-pump control double-acting motor system is a novel single-pump control double-acting motor system formed by utilizing a plurality of double-acting motors on the basis of a variable pump-quantitative motor hydraulic system, the degree of freedom of adjustment of the hydraulic system can be remarkably improved, and meanwhile, the performance of the single-pump control double-acting motor system is improved.
2. The hydraulic compound transmission device comprising the single-pump control double-acting motor system can be switched among three modes of hydraulic transmission, hydraulic transmission and mechanical transmission, each transmission mode has a plurality of gears and different speed regulation modes for selection, when the medium speed regulation mode is adopted, only one motor is required to work, the service life of a hydraulic assembly is prolonged, and a plurality of motors can be used for providing a plurality of operation modes according to complex operation conditions in the low speed regulation mode and the high speed regulation mode, so that the dynamic property and the fuel economy of a vehicle are improved.
3. In each mode of the mechanical-hydraulic compound transmission device comprising the single-pump control double-acting motor system, the hydraulic transmission starts quickly, works stably, is easy to realize quick speed change and reversing, effectively widens the speed regulation range of the mechanical-hydraulic transmission, improves the transmission efficiency of the system, can meet the requirement of efficient stepless speed regulation in a region, and has wider speed regulation range and better controllability.
Drawings
FIG. 1 is a schematic diagram of a mechanical-hydraulic compound transmission incorporating a single pump controlled double acting motor system in accordance with the present invention;
FIG. 2 is a schematic diagram of the power flow of the speed regulation mode 1 in the hydraulic mechanism according to the present invention;
FIG. 3 is a schematic diagram of the power flow of the speed regulation mode 2 in the hydraulic mechanism according to the present invention;
FIG. 4 is a schematic diagram of the power flow of the speed regulation mode 3 in the hydraulic mechanism according to the present invention;
FIG. 5 is a schematic diagram of the power flow direction of the speed regulation mode 4 in the hydraulic mechanism according to the present invention;
FIG. 6 is a schematic diagram of the power flow of the hydraulic mechanism in the low speed regulation mode 1 according to the present invention;
FIG. 7 is a schematic diagram of the power flow of the hydraulic mechanism in the low speed regulation mode 2 according to the present invention;
FIG. 8 is a schematic diagram of the power flow of the hydraulic mechanism in the low speed regulation mode 3 according to the present invention;
FIG. 9 is a schematic diagram of the power flow of the hydraulic mechanism in the low speed regulation mode 4 according to the present invention;
FIG. 10 is a schematic diagram of the power flow of the hydraulic mechanism in the high speed regulation mode 1 according to the present invention;
FIG. 11 is a schematic diagram of the power flow of the hydraulic mechanism in the high speed regulation mode 2 according to the present invention;
FIG. 12 is a schematic diagram of the power flow of the hydraulic mechanism in the high speed mode 3 according to the present invention;
FIG. 13 is a schematic diagram of the power flow of the hydraulic mechanism in the high speed mode 4 according to the present invention;
FIG. 14 is a schematic diagram of hydraulic drive mode first gear power flow according to the present invention;
FIG. 15 is a schematic diagram of a hydraulic drive mode second gear power flow according to the present invention;
FIG. 16 is a schematic diagram illustrating a first gear power flow in a hydraulic transmission mode according to the present invention;
FIG. 17 is a schematic diagram illustrating a second power flow in the hydraulic transmission mode according to the present invention;
FIG. 18 is a schematic diagram illustrating the power flow of the mechanical drive M1 gear according to the present invention;
FIG. 19 is a schematic diagram illustrating the power flow of the mechanical transmission M2 gear according to the present invention;
FIG. 20 is a schematic diagram of the power flow in M3 gear of the mechanical transmission according to the present invention;
FIG. 21 is a chart of the speed ratio characteristics of the speed ratio gear of the present invention;
FIG. 22 is a chart of the low speed ratio steps of the present invention;
fig. 23 is a graph of the speed regulation characteristics of the high speed gear of the present invention.
In the figure:
1-an input shaft; 2-front planetary gear set; 21-first clutch C 1 The method comprises the steps of carrying out a first treatment on the surface of the 22-second clutch C 2 The method comprises the steps of carrying out a first treatment on the surface of the 23-third Clutch C 3 The method comprises the steps of carrying out a first treatment on the surface of the 24-front planet row sun gear; 25-front planet carrier; 26-front planet row ring gear; 27-first brake B 1 The method comprises the steps of carrying out a first treatment on the surface of the 28-second brakeB 2 The method comprises the steps of carrying out a first treatment on the surface of the 3-rear planetary gear set; 31-fourth clutch C 4 The method comprises the steps of carrying out a first treatment on the surface of the 32-rear planet carrier; 33-rear planet row gear ring; 34-rear planet row sun gear; 35-third brake B 3 The method comprises the steps of carrying out a first treatment on the surface of the 4-a hydraulic transmission mechanism; 41-fifth Clutch C 5 The method comprises the steps of carrying out a first treatment on the surface of the 42-a hydraulic transmission input gear pair; 43-hydraulic pump; 44-a safety valve; 45-first reversing valve S 1 The method comprises the steps of carrying out a first treatment on the surface of the 46-an outer motor; 46-1-an outer motor first inlet; 46-2-an outer motor second inlet; 46-3-outer motor first outlet; 46-4-an outer motor second outlet; 47-second reversing valve S 2 The method comprises the steps of carrying out a first treatment on the surface of the 48-third reversing valve S 3 The method comprises the steps of carrying out a first treatment on the surface of the 49-an inner motor; 49-1-an inner motor first inlet; 49-2-inner motor first outlet; 49-3-inner motor second outlet; 49-4-an inner motor second inlet; 410-fourth reversing valve S 4 The method comprises the steps of carrying out a first treatment on the surface of the 411-hydraulically driven first output gear pair; 412-sixth clutch C 6 The method comprises the steps of carrying out a first treatment on the surface of the 413-seventh clutch C 7 The method comprises the steps of carrying out a first treatment on the surface of the 414-hydraulically transmitting a second output gear pair; 5-an output member; 51-an output gear pair set; 52-output shaft.
Detailed Description
The invention will be further described with reference to the drawings and the specific embodiments, but the scope of the invention is not limited thereto.
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present invention and should not be construed as limiting the invention.
In the description of the present invention, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "axial," "radial," "vertical," "horizontal," "inner," "outer," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate describing the present invention and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
As shown in fig. 1, the hydraulic compound transmission device comprising a single-pump control double-acting motor system according to the present invention comprises an input shaft 1, a front planetary gear set 2, a rear planetary gear set 3, a hydraulic transmission mechanism 4, an output member 5, a brake assembly and a clutch assembly.
The front planetary gear mechanism 2 includes a first clutch C 1 21. Second clutch C 2 22. Third clutch C 3 23. Front planet sun gear 24, front planet carrier 25, front planet ring gear 26, first brake B 1 27 and a second brake B 2 28; the front planet row sun gear 24, the front planet row planet carrier 25 and the front planet row gear ring 26 form a planetary gear train; the first clutch C 1 21 for selectively connecting the input shaft 1 to the front planet carrier 25 for common rotation; the second clutch C 2 22 for selectively connecting the front planetary carrier 25 to the rear planetary ring gear 33 for common rotation; the third clutch C 3 23 for selectively connecting the front planet carrier 25 to the front planet ring gear 26 for common rotation; the first brake B 1 27For selectively connecting the rear planetary gear set 33 to the stationary member; the second brake B 2 28 are used to selectively connect the front planetary row sun gear 24 to the stationary member.
The rear planetary gear mechanism 3 includes a fourth clutch C 4 31. Rear planet carrier 32, rear planet ring gear 33, rear planet sun gear 34 and third brake B 3 35; the rear planet carrier 32, the rear planet ring gear 33 and the rear planet sun gear 34 form a planetary gear train; the fourth clutch C 4 31 for selectively connecting the front planet carrier ring gear 26 to the rear planet carrier 32 for common rotation; the third brake B 3 35 are used to selectively connect the rear planet row sun gear 34 to the mount.
The hydraulic transmission mechanism 4 comprises a fifth clutch C 5 41. A hydraulic transmission input gear pair 42, a hydraulic pump 43, a relief valve 44, a first reversing valve S 1 45. Outer motor 46, second reversing valve S 2 47. Third reversing valve S 3 48. Inner motor 49, fourth reversing valve S 4 410. Hydraulic transmission first output gear pair 411, sixth clutch C 6 412. Seventh clutch C 7 413 and a hydraulically driven second output gear pair 414; the fifth clutch C 5 41 for selectively connecting the input shaft 1 for common rotation with an input shaft of a hydraulic pump 43 through a hydraulic transmission input gear pair 42; the sixth clutch C 6 412 for selectively connecting the output of the hydraulic drive mechanism 4 to the rear planet row sun gear 34 for common rotation; the seventh clutch C 7 413 for selectively connecting the output of the hydraulic drive mechanism 4 to the front planetary row sun gear 24 for common rotation; the outer motor 46 is connected in parallel with an inner motor 49; the outer motor 46 and the inner motor 49 share an output shaft; the shared output shaft is the output end of the hydraulic transmission mechanism 4; through a first reversing valve S 1 45. Second reversing valve S 2 47. Third reversing valve S 3 48 and fourth reversing valve S 4 410 controls the outer motor 46 or/and the inner motor 49 to communicate with the hydraulic pump 43; the inlet and outlet of the hydraulic pump 43 are connected with a safety valve 44 in parallel.
The outer horseTwo independent first outer motor flow passages and second outer motor flow passages are respectively arranged in the motor frame 46, and the displacement of the first outer motor flow passages is the same as that of the second outer motor flow passages; the inlet and outlet of the first outer motor runner are respectively an outer motor first inlet 46-1 and an outer motor first outlet 46-3, the inlet and outlet of the second outer motor runner are respectively an outer motor second inlet 46-2 and an outer motor second outlet 46-4, two independent first inner motor runners and second inner motor runners are respectively arranged in the inner motor 49, and the displacement of the first inner motor runner and the second inner motor runner is the same; the inlet and outlet of the first inner motor runner are respectively an inner motor first inlet 49-1 and an inner motor first outlet 49-2, and the inlet and outlet of the second inner motor runner are respectively an inner motor second inlet 49-4 and an inner motor second outlet 49-3; a second reversing valve S is arranged between the first outer motor runner and the hydraulic pump 43 2 47, a first reversing valve S is arranged between the second outer motor flow passage and the hydraulic pump 43 1 45, a fourth reversing valve S is provided between the first inner motor flow passage and the hydraulic pump 43 4 410, a third reversing valve S is provided between the second inner motor flow passage and the hydraulic pump 43 3 48。
The hydraulic transmission mechanism 4 is a single-pump control double-acting motor system, the displacement of one flow passage in the inner motor 49 is set to be V, and when the two flow passages of the inner motor 49 work simultaneously, the displacement of the inner motor 49 is set to be 2V; the displacement of the outer motor 46 is CV, and the displacement of the inner motor 49 is 2CV when the two flow passages of the outer motor 46 are simultaneously operated, wherein C is a displacement coefficient, C>1, a step of; the total displacement V of the hydraulic motor of the hydraulic transmission mechanism 4 m ＝2V+2CV；V pmax Representing the displacement V of the hydraulic pump 43 p Is the maximum value of (2); the displacement ratio of the hydraulic pump 43:
as shown in fig. 2, when the first reversing valve S 1 45 is right-position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is neutral position energized, the fourth reversing valve S 4 410 is neutral position, the hydraulic pumpThe outlet 43 is respectively communicated with an outer motor first inlet 46-1 and an outer motor second inlet 46-2, and the outer motor first outlet 46-3 and the outer motor second outlet 46-4 are respectively communicated with the inlet of the hydraulic pump 43; the first inner motor inlet 49-1 is communicated with the first inner motor outlet 49-2, and the second inner motor inlet 49-4 is communicated with the second inner motor outlet 49-3; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 1 45 and a second reversing valve S 2 47 to the outer motor 46, which drives the spindle to rotate at an output rotational speed.
As shown in fig. 3, when the first reversing valve S 1 45 is neutral position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is neutral position energized, the fourth reversing valve S 4 410 is neutral power, the outlet of the hydraulic pump 43 is communicated with the first inlet 46-1 of the outer motor, and the first outlet 46-3 of the outer motor is communicated with the inlet of the hydraulic pump 43; the first inner motor inlet 49-1 is communicated with the first inner motor outlet 49-2, and the second inner motor inlet 49-4 is communicated with the second inner motor outlet 49-3; the outer motor second inlet 46-2 and the outer motor second outlet 46-4 are in communication; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 2 47 to the outer motor 46, which drives the spindle to rotate at an output rotational speed.
As shown in fig. 4, when the first reversing valve S 1 45 is neutral position power-on, the second reversing valve S 2 47 is neutral position energizing, the third reversing valve S 3 48 is electrified at the right position, and the fourth reversing valve S 4 410 is to be right-hand, the outlet of the hydraulic pump 43 is respectively communicated with the first inlet 49-1 of the inner motor and the second inlet 49-4 of the inner motor, and the first outlet 49-2 of the inner motor and the second outlet 49-3 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the outer motor first inlet 46-1 communicates with the outer motor first outlet 46-3, and the outer motor second inlet 46-2 communicates with the outer motor second outlet 46-4; the oil pumped by the hydraulic pump 43 passes through the third reversing valve S 3 48 and fourth reversing valve S 4 410 to the inner motor 49, and drives the rotation shaft to rotate at an output rotation speed.
As shown in fig. 5, when the first reversing valve S 1 45 is neutral position power-on, the second reversing valve S 2 47 is neutral position energizing, the third reversing valve S 3 48 is electrified at the right position, and the fourth reversing valve S 4 410 is neutral power, the outlet of the hydraulic pump 43 is communicated with the second inlet 49-4 of the inner motor, and the second outlet 49-3 of the inner motor is communicated with the inlet of the hydraulic pump 43; the outer motor first inlet 46-1 communicates with the outer motor first outlet 46-3, the outer motor second inlet 46-2 communicates with the outer motor second outlet 46-4, and the inner motor first inlet 49-1 communicates with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the third reversing valve S 3 48 to an inner motor 49, and drives the rotating shaft to rotate at an output rotation speed.
As shown in fig. 6, when the first reversing valve S 1 45 is right-position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is electrified at the right position, and the fourth reversing valve S 4 410 is to be right-hand, the outlet of the hydraulic pump 43 is respectively communicated with the first inlet 46-1 of the outer motor, the second inlet 46-2 of the outer motor, the first inlet 49-1 of the inner motor and the second inlet 49-4 of the inner motor, and the first outlet 46-3 of the outer motor, the second outlet 46-4 of the outer motor, the first outlet 49-2 of the inner motor and the second outlet 49-3 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 1 45 and a second reversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 and fourth reversing valve S 4 410 to the inner motor 49, together drive the shaft to rotate at an output rotational speed.
As shown in fig. 7, when the first reversing valve S 1 45 is right-position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is electrified at the right position, and the fourth reversing valve S 4 410 is that when the middle position is electrified, the outlet of the hydraulic pump 43 is respectively communicated with the first inlet 46-1 of the outer motor, the second inlet 46-2 of the outer motor and the second inlet 49-4 of the inner motor, and the first outlet 46-3 of the outer motor, the second outlet 46-4 of the outer motor and the second outlet 49-3 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the inner motor first inlet 49-1 communicates with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 1 45 and secondReversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 to an inner motor 49, which jointly drives the rotary shafts to rotate at output rotational speeds.
As shown in fig. 8, when the first reversing valve S 1 45 is neutral position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is electrified at the right position, and the fourth reversing valve S 4 When the right position is electrified, the outlet of the hydraulic pump 43 is respectively communicated with the first inlet 46-1 of the outer motor, the first inlet 49-1 of the inner motor and the second inlet 49-4 of the inner motor, and the first outlet 46-3 of the outer motor, the first outlet 49-2 of the inner motor and the second outlet 49-3 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the outer motor second inlet 46-2 and the outer motor second outlet 46-4 are in communication; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 and fourth reversing valve S 4 410 to the inner motor 49, together drive the shaft to rotate at an output rotational speed.
As shown in fig. 9, when the first reversing valve S 1 45 is neutral position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is electrified at the right position, and the fourth reversing valve S 4 410 is neutral position, the outlet of the hydraulic pump 43 is respectively communicated with the first inlet 46-1 of the outer motor and the second inlet 49-4 of the inner motor, and the first outlet 46-3 of the outer motor and the second outlet 49-3 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the outer motor second inlet 46-2 and the outer motor second outlet 46-4 are in communication; the inner motor first inlet 49-1 communicates with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 to an inner motor 49, which jointly drives the rotary shafts to rotate and output the rotation speed
As shown in fig. 10, when the first reversing valve S 1 45 is right-position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is left-position power-on, the fourth reversing valve S 4 410 is neutral position, the outlet of the hydraulic pump 43 is respectively connected with the first inlet 46-1 and the outside of the outside motor The motor second inlet 46-2 and the inner motor second outlet 49-3 are communicated, and the outer motor first outlet 46-3, the outer motor second outlet 46-4 and the inner motor second inlet 49-4 are respectively communicated with the inlet of the hydraulic pump 43; the inner motor first inlet 49-1 communicates with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 1 45 and a second reversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 to an inner motor 49, which jointly drives the rotary shafts to rotate at output rotational speeds.
As shown in fig. 11, when the first reversing valve S 1 45 is right-position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is left-position power-on, the fourth reversing valve S 4 410 is left position when power is supplied, the outlet of the hydraulic pump 43 is respectively communicated with an outer motor first inlet 46-1, an outer motor second inlet 46-2, an inner motor first outlet 49-2 and an inner motor second outlet 49-3, and the outer motor first outlet 46-3, the outer motor second outlet 46-4, the inner motor first inlet 49-1 and the inner motor second inlet 49-4 are respectively communicated with the inlet of the hydraulic pump 43; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 1 45 and a second reversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 and fourth reversing valve S 4 410 to the inner motor 49, together drive the shaft to rotate at an output rotational speed.
As shown in fig. 12, when the first reversing valve S 1 45 is neutral position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is left-position power-on, the fourth reversing valve S 4 410 is neutral position, the outlet of the hydraulic pump 43 is respectively communicated with the first inlet 46-1 of the outer motor and the second outlet 49-3 of the inner motor, and the first outlet 46-3 of the outer motor and the second inlet 49-4 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the outer motor second inlet 46-2 and the outer motor second outlet 46-4 are in communication; the inner motor first inlet 49-1 communicates with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 to an inner motor 49, which jointly drives the rotary shafts to rotate and output rotary shaftsAnd (5) speed.
As shown in fig. 13, when the first reversing valve S 1 45 is neutral position power-on, the second reversing valve S 2 47 is right-position power-on, the third reversing valve S 3 48 is left-position power-on, the fourth reversing valve S 4 When 410 is electrified in the left position, the outlet of the hydraulic pump 43 is respectively communicated with the first inlet 46-1 of the outer motor, the first outlet 49-2 of the inner motor and the second outlet 49-3 of the inner motor, and the first outlet 46-3 of the outer motor, the first inlet 49-1 of the inner motor and the second inlet 49-4 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the outer motor second inlet 46-2 communicates with the outer motor second outlet 46-4; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 2 47 to the outer motor 46 via a third reversing valve S 3 48 and fourth reversing valve S 4 410 to the inner motor 49, together drive the shaft to rotate at an output rotational speed.
By controlling the first reversing valve S 1 45. Second reversing valve S 2 47. Third reversing valve S 3 48 and fourth reversing valve S 4 410, causing the hydraulic transmission mechanism 4 to output the following rotational speed ranges:
medium speed regulation mode:
low speed mode:
high speed regulation mode:
wherein: n is n p To input the rotation speed of the hydraulic pump, n m Is the rotational speed of the hydraulic motor output.
The single pump controlled double acting motor system has an inner motor and an outer motor and shares a common shaft, the outer motor 46 being larger in displacement than the inner motor 49. When the hydraulic pump 43 supplies oil to the oil inlet of the outer motor 46 and the oil inlet of the inner motor 49 simultaneously, the total displacement of the hydraulic motor is the sum of the displacements of the outer motor 46 and the inner motor 49, the output rotating speed is small, and the low-speed work of the hydraulic motor is realized. When the hydraulic pump 43 supplies oil to the oil inlet of the outer motor 46 and the oil outlet of the inner motor 49 at the same time, since the displacement of the outer motor 46 is larger than the displacement of the inner motor 49, the total displacement of the hydraulic motor is the difference between the displacements of the outer motor 46 and the inner motor 49, the output rotation speed is larger, and the high-speed operation of the hydraulic motor is realized. When oil enters from two inlets of the double-acting motor at the same time, the displacement is twice that of a single inlet, and the output rotating speed is half of that of the original motor.
The control valve assembly is controlled to have a low speed mode, a medium speed mode and a high speed mode. As shown in table 1 below on the basis of these 3 modes, by adjusting the displacement ratio of the hydraulic transmission 4 and selectively controlling the brake assembly and clutch assembly, a transmission between the input member and the output member may be provided comprising: hydraulic transmission and mechanical-hydraulic transmission. Further comprising solely selectively controlling only the brake assembly and clutch assembly to provide mechanical transmission between the input member and the output member.
Table 1 illustrates a speed-adjusting mode gear and shift element relationship table
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Table 2 low speed mode transmission gear and shift element relationship table
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Table 3 high speed mode transmission gear and shift element relationship table
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Note that: "in" means that the elements are in an engaged state, "left" means that the reversing valve is energized in the left position, "middle" means that the reversing valve is in the neutral position, and "right" means that the reversing valve is energized in the right position. B (B) 1 Is a first brake, B 2 Is a second brake, B 3 Is a third brake, C 1 Is a first clutch, C 2 Is a second clutch, C 3 Is a third clutch, C 4 Is a fourth clutch, C 5 Is a fifth clutch C 6 Is a sixth clutch, C 7 Is a seventh clutch S 1 Is a first reversing valve S 2 Is a second reversing valve S 3 Is a third reversing valve S 4 Is a fourth reversing valve.
The main parameters are as follows: n is n I To input rotation speed n o For output rotation speed, e is the displacement ratio of the hydraulic transmission mechanism, C is the displacement coefficient, V pmax For maximum variable pump displacement, V is the internal motor displacement of the hydraulic motor, CV is the external motor displacement of the hydraulic motor, k 1 Is the characteristic parameter k of the planet gear of the front planetary gear mechanism 2 The characteristic parameters of the planetary gears of the rear planetary gear mechanism are obtained; i.e 1 Input gear pair transmission ratio, i for hydraulic transmission 2 A first output gear pair transmission ratio, i is hydraulically driven 3 For hydraulically driving the second output gear pair transmission ratio, c=2.5, i 1 ＝0.6，i 2 ＝0.4，i 3 ＝0.6，i 4 i 5 ＝1，V pmax ＝196ml/r，V＝56ml/r，k 1 ＝2，k 2 ＝1.5。
As shown in fig. 14, the first hydraulic transmission mode: fifth clutch C 5 41. Sixth clutch C 6 412 and brake B 1 27 are engaged, the shift between gears of different gear ratios in the first mode of the hydraulic transmission mode is realized by the shift of the reversing valve, the rear planetary gear set 33 is braked, and the power passes through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 are transmitted to the rear planetary carrier 34 and then output from the output shaft 52 via the rear planetary carrier 32.
As shown in fig. 15, the hydraulic transmission mode two: second clutch C 2 22. Fourth clutch C 4 31. Fifth clutch C 5 41. Seventh clutch C 7 413 and brake B 1 27 are engaged, the switching between the gears of different transmission ratios in the second hydraulic transmission mode is realized by the switching of the reversing valve, the front planet carrier 25 and the rear planet ring 33 are braked, and the power is braked by the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the hydraulically driven second output gear pair 414 are transferred to the front planetary gear set sun gear 34 and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32.
As shown in fig. 16, the first hydraulic transmission mode: first clutch C 1 21. Fourth clutch C 4 31. Fifth clutch C 5 41 and seventh Clutch C 7 413, switching between gears with different transmission ratios in the first machine-liquid transmission mode is realized through switching of the reversing valveThe power is split through the input shaft 1, and the hydraulic path power is input through the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the second hydraulic transmission output gear pair 414 are transmitted to the front planetary sun gear 24, mechanical power is transmitted to the front planetary carrier 25 via the input shaft 1, and finally, is merged to the front planetary ring gear 26 and the rear planetary carrier 32, and is output from the output shaft 52.
As shown in fig. 17, the machine-liquid transmission mode two: first clutch C 1 21. Second clutch C 2 22. Fifth clutch C 5 41 and a sixth clutch C 6 412, switching between gears with different transmission ratios in the mechanical-hydraulic transmission mode II is realized through switching of the reversing valve, power is split through the input shaft 1, and hydraulic path power is transmitted through the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 of the hydraulic transmission are transmitted to the rear planetary gear set sun gear 34, mechanical power is transmitted to the rear planetary gear set ring gear 33 via the input shaft 1, and finally, is merged to the rear planetary carrier 32, and is output from the output shaft 52.
As shown in fig. 18, the mechanical transmission M1 gear: first clutch C 1 21. Second clutch C 2 22 and brake B 3 35 are engaged, the rear planetary sun gear 34 is braked, power is transmitted to the rear planetary ring gear 33 via the front planetary carrier 25 via the input shaft 1, and then output from the output shaft 52 via the planetary carrier 32.
As shown in fig. 19, the mechanical transmission M2 gear: first clutch C 1 21. Third clutch C 3 23 and fourth clutch C 4 31 are engaged, the front planetary carrier 25 and the front planetary ring gear 26 are fixedly connected as a unit, and power is transmitted to the front planetary carrier 25 via the input shaft 1, and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32.
As shown in fig. 20, the mechanical transmission M3: first clutch C 1 21. First, theFour clutches C 4 31 and brake B 2 28 are engaged, the front planetary sun gear 24 is braked, power is transmitted to the front planetary carrier 25 via the input shaft 1, and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32.
The first hydraulic transmission mode of the medium speed regulation mode comprises a hydraulic transmission H1 gear, a hydraulic transmission H2 gear, a hydraulic transmission H3 gear and a hydraulic transmission H4 gear, and the power flow of the hydraulic mechanism is as shown in figures 2, 3, 4 and 5, and the specific implementation method is as follows:
hydraulic transmission H1 gear: fifth clutch C 5 41. Sixth clutch C 6 412 and brake B 1 27 joint, first reversing valve S 1 45 is electrified at the right position, and a second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral position energized, the rear planet gear ring 33 brakes, and power passes through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 are transmitted to the rear planetary carrier 34 and then output from the output shaft 52 via the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝1.17en I
wherein n is o To input rotation speed n I For output rotational speed, e is the displacement ratio of the hydraulic transmission 5.
Hydraulic transmission H2 gear: fifth clutch C 5 41. Sixth clutch C 6 412 and brake B 1 27 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral position energized, the rear planet gear ring 33 brakes, and power passes through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixthClutch C 6 412 and the first output gear pair 411 are transmitted to the rear planetary carrier 34 and then output from the output shaft 52 via the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝2.33en I
Hydraulic transmission H3 gear: fifth clutch C 5 41. Sixth clutch C 6 412 and brake B 1 27 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is electrified in the right position, the rear planet gear 33 is braked, and power passes through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 are transmitted to the rear planetary carrier 34 and then output from the output shaft 52 via the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝2.92en I
hydraulic transmission H4 gear: fifth clutch C 5 41. Sixth clutch C 6 412 and brake B 1 27 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is electrified in the right position, the rear planet gear 33 is braked, and power passes through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 are transmitted to the rear planetary carrier 34 and then output from the output shaft 52 via the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝5.83en I
the second hydraulic transmission mode of the medium speed regulation mode comprises a hydraulic transmission R1 gear, a hydraulic transmission R2 gear, a hydraulic transmission R3 gear and a hydraulic transmission R4 gear, and the power flow of the hydraulic mechanism is as shown in figures 2, 3, 4 and 5, and the specific implementation method is as follows:
hydraulic transmission R1 gear: second clutch C 2 22. Fourth clutch C 4 31. Fifth clutch C 5 41. Seventh clutch C 7 413 and brake B 1 27 joint, first reversing valve S 1 45 is electrified at the right position, and a second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral powered, front planet carrier 25 and rear planet ring 33 brake, power is transmitted through input shaft 1, hydraulic drive input gear pair 42 and fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the hydraulically driven second output gear pair 414 are transferred to the front planetary gear set sun gear 34 and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝-0.97en I
Hydraulic drive R2 gear: second clutch C 2 22. Fourth clutch C 4 31. Fifth clutch C 5 41. Seventh clutch C 7 413 and brake B 1 27 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral powered, front planet carrier 25 and rear planet ring 33 brake, power is transmitted through input shaft 1, hydraulic drive input gear pair 42 and fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the hydraulically driven second output gear pair 414 are transferred to the front planetary gear set sun gear 34 and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝-1.94en I
hydraulic transmission R3 gear: second clutch C 2 22. Fourth clutch C 4 31. Fifth clutch C 5 41. Seventh clutch C 7 413 and brake B 1 27 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is energized to the right, the front planet carrier 25 and the rear planet ring 33 brake, power is transmitted through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the hydraulically driven second output gear pair 414 are transferred to the front planetary gear set sun gear 34 and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝-2.43en I
hydraulic drive R4 gear: second clutch C 2 22. Fourth clutch C 4 31. Fifth clutch C 5 41. Seventh clutch C 7 413 and brake B 1 27 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is energized to the right, the front planet carrier 25 and the rear planet ring 33 brake, power is transmitted through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the hydraulically driven second output gear pair 414 are transferred to the front planetary gear set sun gear 34 and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝-4.86en I
The first hydraulic transmission mode of the medium speed regulation mode comprises a hydraulic transmission HM1 gear, a hydraulic transmission HM2 gear, a hydraulic transmission HM3 gear and a hydraulic transmission HM4 gear, and the power flow of the hydraulic mechanism is as shown in figures 2, 3, 4 and 5, and the specific implementation method is as follows:
mechanical-hydraulic transmission HM1 gear: first clutch C 1 21. Fourth clutch C 4 31. Fifth clutch C 5 41 and seventh Clutch C 7 413 joint, first reversing valve S 1 45 is electrified at the right position, and a second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral position energized, power is split through input shaft 1, hydraulic path power is input through hydraulic transmission input gear pair 42 and fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the second hydraulic transmission output gear pair 414 are transmitted to the front planetary sun gear 24, mechanical power is transmitted to the front planetary carrier 25 via the input shaft 1, and finally, is merged to the front planetary ring gear 26 and the rear planetary carrier 32, and is output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(1.5-0.97e)n I
mechanical-hydraulic transmission HM2 gear: first clutch C 1 21. Fourth clutch C 4 31. Fifth clutch C 5 41 and seventh Clutch C 7 413 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral position energized, power is split through input shaft 1, hydraulic path power is input through hydraulic transmission input gear pair 42 and fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the second hydraulic transmission output gear pair 414 are transmitted to the front planetary sun gear 24, mechanical power is transmitted to the front planetary carrier 25 via the input shaft 1, and finally, is merged to the front planetary ring gear 26 and the rear planetary carrier 32, and is output from the output shaft 52.At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(1.5-1.94e)n I
mechanical-hydraulic transmission HM3 gear: first clutch C 1 21. Fourth clutch C 4 31. Fifth clutch C 5 41 and seventh Clutch C 7 413 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is powered on in the right position, power is split through the input shaft 1, and hydraulic path power is input through the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the second hydraulic transmission output gear pair 414 are transmitted to the front planetary sun gear 24, mechanical power is transmitted to the front planetary carrier 25 via the input shaft 1, and finally, is merged to the front planetary ring gear 26 and the rear planetary carrier 32, and is output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(1.5-2.43e)n I
mechanical-hydraulic transmission HM4 gear: first clutch C 1 21. Fourth clutch C 4 31. Fifth clutch C 5 41 and seventh Clutch C 7 413 joint, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is powered on in the right position, power is split through the input shaft 1, and hydraulic path power is input through the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a seventh clutch C 7 413 and the second hydraulic transmission output gear pair 414 are transmitted to the front planetary sun gear 24, mechanical power is transmitted to the front planetary carrier 25 via the input shaft 1, and finally, is merged to the front planetary ring gear 26 and the rear planetary carrier 32, and is output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(1.5-4.86e)n I
The second hydraulic transmission mode of the medium speed regulation mode comprises a HMs gear, HMs gear, HMs gear and HMs gear, and the power flow of the hydraulic mechanism is as shown in fig. 2, 3, 4 and 5, and the specific implementation method is as follows:
mechanical-hydraulic transmission HMs gear: first clutch C 1 21. Second clutch C 2 22. Fifth clutch C 5 41 and a sixth clutch C 6 412, first reversing valve S 1 45 is electrified at the right position, and a second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral position energized, power is split through input shaft 1, hydraulic path power is input through hydraulic transmission input gear pair 42 and fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 of the hydraulic transmission are transmitted to the rear planetary gear set sun gear 34, mechanical power is transmitted to the rear planetary gear set ring gear 33 via the input shaft 1, and finally, is merged to the rear planetary carrier 32, and is output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(0.6+1.17e)n I
mechanical-hydraulic transmission HMs gear: first clutch C 1 21. Second clutch C 2 22. Fifth clutch C 5 41 and a sixth clutch C 6 412, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is electrified at the right position, and a third reversing valve S 3 48 is neutral position energized, and a fourth reversing valve S 4 410 is neutral position energized, power is split through input shaft 1, hydraulic path power is input through hydraulic transmission input gear pair 42 and fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 of the hydraulic transmission are transmitted to the rear planet gear row sun gear 34, mechanical path power is transmitted to the rear planet gear row ring gear 33 through the input shaft 1, and finallyTo the rear planet carrier 32 and output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(0.6+2.33e)n I
mechanical-hydraulic transmission HMs gear: first clutch C 1 21. Second clutch C 2 22. Fifth clutch C 5 41 and a sixth clutch C 6 412, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is powered on in the right position, power is split through the input shaft 1, and hydraulic path power is input through the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 of the hydraulic transmission are transmitted to the rear planetary gear set sun gear 34, mechanical power is transmitted to the rear planetary gear set ring gear 33 via the input shaft 1, and finally, is merged to the rear planetary carrier 32, and is output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(0.6+2.92e)n I
mechanical-hydraulic transmission HMs gear: first clutch C 1 21. Second clutch C 2 22. Fifth clutch C 5 41 and a sixth clutch C 6 412, first reversing valve S 1 45 is neutral position energized, the second reversing valve S 2 47 is neutral position energized, the third reversing valve S 3 48 is electrified at the right position, and a fourth reversing valve S 4 410 is powered on in the right position, power is split through the input shaft 1, and hydraulic path power is input through the hydraulic transmission input gear pair 42 and the fifth clutch C 5 41 drives a hydraulic pump 43 to work, the hydraulic pump 43 drives a hydraulic motor to work, and the power output by the hydraulic motor passes through a sixth clutch C 6 412 and the first output gear pair 411 of the hydraulic transmission are transmitted to the rear planetary gear set sun gear 34, mechanical power is transmitted to the rear planetary gear set ring gear 33 via the input shaft 1, and finally, is merged to the rear planetary carrier 32, and is output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝(0.6+5.83e)n I
the mechanical transmission mode comprises a mechanical transmission M1 gear and a mechanical transmission M2 gear, and the specific implementation method is as follows:
Mechanical transmission M1 keeps off: first clutch C 1 21. Second clutch C 2 22 and brake B 3 35 are engaged, the rear planetary sun gear 34 is braked, power is transmitted to the rear planetary ring gear 33 via the input shaft 1, and then output from the output shaft 52 via the planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝0.6n I
mechanical transmission M2 keeps off: first clutch C 1 21. Third clutch C 3 23 and fourth clutch C 4 31 are engaged, the front planetary carrier 25 and the front planetary ring gear 26 are fixedly connected as a unit, and power is transmitted to the front planetary carrier 25 via the input shaft 1, and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝n I
mechanical transmission M3 keeps off: first clutch C 1 21. Fourth clutch C 4 31 and brake B 2 28 are engaged, the front planetary sun gear 24 is braked, power is transmitted to the front planetary carrier 25 via the input shaft 1, and then output from the output shaft 52 via the front planetary ring gear 26 and the rear planetary carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is:
n o ＝1.5n I
the first hydraulic transmission mode of the low speed regulation mode comprises a hydraulic transmission H1 gear, a hydraulic transmission H2 gear, a hydraulic transmission H3 gear and a hydraulic transmission H4 gear, the power flow of the hydraulic mechanism is as shown in figures 6, 7, 8 and 9, and the specific implementation method is the same as each gear of the first hydraulic transmission mode of the medium speed regulation mode.
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission H1 gear is as follows: n is n o ＝0.83en I ；
At the moment, the output rotating speed and the input rotating speed of the H2 gear of the hydraulic transmission are relatedThe method comprises the following steps: n is n o ＝0.97en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission H3 gear is as follows: n is n o ＝1.30en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission H4 gear is as follows: n is n o ＝1.67en I ；
The second hydraulic transmission mode of the low speed regulation mode comprises a hydraulic transmission R1 gear, a hydraulic transmission R2 gear, a hydraulic transmission R3 gear and a hydraulic transmission R4 gear, the power flow of the hydraulic mechanism is as shown in figures 6, 7, 8 and 9, and the specific implementation method is the same as that of each gear of the second hydraulic transmission mode of the medium speed regulation mode.
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R1 gear is as follows: n is n o ＝-0.69en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R2 gear is as follows: n is n o ＝-0.81en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R3 gear is as follows: n is n o ＝-1.08en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R4 gear is as follows: n is n o ＝-1.39en I ；
The first hydraulic transmission mode of the low speed regulation mode comprises a first hydraulic transmission HM1 gear, a first hydraulic transmission HM2 gear, a second hydraulic transmission HM3 gear and a first hydraulic transmission HM4 gear, the power flows of the hydraulic mechanisms are shown in figures 6, 7, 8 and 9, and the specific implementation method is the same as each gear of the first hydraulic transmission mode of the medium speed regulation mode.
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM1 gear at the moment is as follows: n is n o ＝(1.5-0.69e)n I ；
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM2 gear at the moment is as follows: n is n o ＝(1.5-0.81e)n I ；
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM3 gear at the moment is as follows: n is n o ＝(1.5-1.08e)n I ；
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM4 gear at the moment is as follows: n is n o ＝(1.5-1.39e)n I ；
The second hydraulic transmission mode of the low speed regulation mode comprises a HMs gear, HMs gear, HMs gear and HMs gear, the power flow of the hydraulic mechanism is as shown in fig. 6, 7, 8 and 9, and the specific implementation method is the same as that of the second hydraulic transmission mode of the medium speed regulation mode.
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+0.83e)n I ；
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+0.97e)n I ；
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+1.30e)n I ；
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+1.67e)n I ；
The first hydraulic transmission mode of the high speed regulation mode comprises a hydraulic transmission H1 gear, a hydraulic transmission H2 gear, a hydraulic transmission H3 gear and a hydraulic transmission H4 gear, the power flow of the hydraulic mechanism is as shown in figures 10, 11, 12 and 13, and the specific implementation method is the same as each gear of the first hydraulic transmission mode of the medium speed regulation mode.
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission H1 gear is as follows: n is n o ＝1.46en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission H2 gear is as follows: n is n o ＝1.94en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission H3 gear is as follows: n is n o ＝3.89en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission H4 gear is as follows: n is n o ＝11.67en I ；
The second hydraulic transmission mode of the high speed regulation mode comprises a hydraulic transmission R1 gear, a hydraulic transmission R2 gear, a hydraulic transmission R3 gear and a hydraulic transmission R4 gear, the power flow of the hydraulic mechanism is as shown in figures 10, 11, 12 and 13, and the specific implementation method is the same as that of each gear of the second hydraulic transmission mode of the medium speed regulation mode.
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R1 gear is as follows: n is n o ＝-1.22en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R2 gear is as follows: n is n o ＝-1.62en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R3 gear is as follows: n is n o ＝-3.24en I ；
At this time, the relation between the output rotation speed and the input rotation speed of the hydraulic transmission R4 gear is as follows: n is n o ＝-9.72en I ；
The first hydraulic transmission mode of the high speed regulation mode comprises a first hydraulic transmission HM1 gear, a first hydraulic transmission HM2 gear, a first hydraulic transmission HM3 gear and a second hydraulic transmission HM4 gear, the power flows of the hydraulic mechanisms are as shown in figures 10, 11, 12 and 13, and the specific implementation method is the same as each gear of the first hydraulic transmission mode of the medium speed regulation mode.
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM1 gear at the moment is as follows: n is n o ＝(1.5-1.22e)n I ；
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM2 gear at the moment is as follows: n is n o ＝(1.5-1.62e)n I ；
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM3 gear at the moment is as follows: n is n o ＝(1.5-3.24e)n I ；
The relation between the output rotating speed and the input rotating speed of the liquid transmission HM4 gear at the moment is as follows: n is n o ＝(1.5-9.72e)n I ；
The second hydraulic transmission mode of the high speed regulation mode comprises a HMs gear, HMs gear, HMs gear and HMs gear of hydraulic transmission, the power flow of the hydraulic mechanism is as shown in fig. 10, 11, 12 and 13, and the specific implementation method is the same as that of the second hydraulic transmission mode of the medium speed regulation mode.
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+1.46e)n I ；
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+1.94e)n I ；
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+3.89e)n I ；
The relation between the output rotating speed and the input rotating speed of the hydraulic transmission HMs gear at the moment is as follows: n is n o ＝(0.6+11.67e)n I ；
The mid-range gear speed regulation characteristic curve of the present invention is shown in fig. 20. When e is E [0,1.00 ]]In the range, the four gears of the first hydraulic transmission mode are utilized for starting, at the moment, the speed is regulated linearly, then the power interruption can be switched to the four gears corresponding to the first hydraulic transmission mode, and the four gears of the first hydraulic transmission mode can reach the maximum speed regulation point; the four gears of the first hydraulic transmission mode can be switched to the four gears of the second hydraulic transmission mode without power interruption, and the hydraulic transmission mode mainly adopts low-speed large torque to meet the working condition with higher power requirement, and at the moment, the speed is regulated linearly; the speed regulation range of the hydraulic transmission H1 gear is n o ∈[0，0.82]n I When e=0.70, the hydraulic transmission H1 gear can be switched to the hydraulic transmission HM1 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.42, the machine liquid transmission HM1 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.60，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H2 gear is n o ∈[0，0.82]n I When e=0.35, the hydraulic transmission H2 gear can be switched to the hydraulic transmission HM2 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.21, the machine liquid transmission HM2 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H3 gear is n o ∈[0，0.82]n I When e=0.28, the hydraulic transmission H3 gear can be switched to the hydraulic transmission HM3 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.17, the machine liquid transmission HM3 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the Hydraulic transmissionThe speed regulation range of the H4 gear is n o ∈[0，0.82]n I When e=0.14, the hydraulic transmission H4 gear can be switched to the hydraulic transmission HM4 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.08, the machine liquid transmission HM4 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the Compared with the hydraulic transmission mode, the switched hydraulic transmission mode has higher rotating speed under the condition of the same displacement ratio, and realizes stepless speed regulation. When the speed is regulated in the negative direction, four gears of the second hydraulic transmission mode are utilized, the displacement ratio of the hydraulic transmission mechanism is regulated, the linear speed regulation is realized in the displacement ratio variation range, and the operation requirement of low speed and large torque is met, so that the stepless speed regulation is realized.
The low speed gear of the present invention has a speed regulation characteristic curve as shown in fig. 21. When e is E [0,1.00 ]]In the range, the four gears of the first hydraulic transmission mode are utilized for starting, at the moment, the speed is regulated linearly, then the power interruption can be switched to the four gears corresponding to the first hydraulic transmission mode, and the four gears of the first hydraulic transmission mode can reach the maximum speed regulation point; the four gears of the first hydraulic transmission mode can be switched to the four gears of the second hydraulic transmission mode without power interruption, and the hydraulic transmission mode mainly adopts low-speed large torque to meet the working condition with higher power requirement, and at the moment, the speed is regulated linearly; the speed regulation range of the hydraulic transmission H1 gear is n o ∈[0，0.82]n I When e=0.99, the hydraulic transmission H1 gear can be switched to the hydraulic transmission HM1 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.59, the machine liquid transmission HM1 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.60，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H2 gear is n o ∈[0，0.82]n I When e=0.84, the hydraulic transmission H2 gear can be switched to the hydraulic transmission HM2 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.51, the machine liquid transmission HM2 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the speed is linearly regulated at the moment, and the speed regulation range is changedEnclose n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H3 gear is n o ∈[0，0.82]n I When e=0.63, the hydraulic transmission H3 gear can be switched to the hydraulic transmission HM3 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.38, the machine liquid transmission HM3 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H4 gear is n o ∈[0，0.82]n I When e=0.49, the hydraulic transmission H4 gear can be switched to the hydraulic transmission HM4 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.29, the machine liquid transmission HM4 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the Compared with the hydraulic transmission mode, the switched hydraulic transmission mode has higher rotating speed under the condition of the same displacement ratio, and realizes stepless speed regulation. When the speed is regulated in the negative direction, four gears of the second hydraulic transmission mode are utilized, the displacement ratio of the hydraulic transmission mechanism is regulated, the linear speed regulation is realized in the displacement ratio variation range, and the operation requirement of low speed and large torque is met, so that the stepless speed regulation is realized.
The high speed gear of the present invention has a speed regulating characteristic curve as shown in fig. 22. When e is E [0,1.00 ]]In the range, the four gears of the first hydraulic transmission mode are utilized for starting, at the moment, the speed is regulated linearly, then the power interruption can be switched to the four gears corresponding to the first hydraulic transmission mode, and the four gears of the first hydraulic transmission mode can reach the maximum speed regulation point; the four gears of the first hydraulic transmission mode can be switched to the four gears of the second hydraulic transmission mode without power interruption, and the hydraulic transmission mode mainly adopts low-speed large torque to meet the working condition with higher power requirement, and at the moment, the speed is regulated linearly; the speed regulation range of the hydraulic transmission H1 gear is n o ∈[0，0.82]n I When e=0.56, the hydraulic transmission H1 gear can be switched to the hydraulic transmission HM1 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.33, the engine-hydraulic transmission HM1 gear can be unpoweredThe gear is switched to the gear HMs of the hydraulic transmission, at the moment, the linear speed is regulated, and the speed regulating range is n o ∈[0.60，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H2 gear is n o ∈[0，0.82]n I When e=0.42, the hydraulic transmission H2 gear can be switched to the hydraulic transmission HM2 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.25, the machine liquid transmission HM2 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H3 gear is n o ∈[0，0.82]n I When e=0.21, the hydraulic transmission H3 gear can be switched to the hydraulic transmission HM3 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.13, the machine liquid transmission HM3 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the The speed regulation range of the hydraulic transmission H4 gear is n o ∈[0，0.82]n I When e=0.07, the hydraulic transmission H4 gear can be switched to the hydraulic transmission HM4 gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.50]n I When e=0.04, the machine liquid transmission HM4 gear can be switched to the machine liquid transmission HMs gear without power interruption, and the linear speed regulation is carried out at the moment, and the speed regulation range is n o ∈[0.82，1.09]n I The method comprises the steps of carrying out a first treatment on the surface of the Compared with the hydraulic transmission mode, the switched hydraulic transmission mode has higher rotating speed under the condition of the same displacement ratio, and realizes stepless speed regulation. When the speed is regulated in the negative direction, four gears of the second hydraulic transmission mode are utilized, the displacement ratio of the hydraulic transmission mechanism is regulated, the linear speed regulation is realized in the displacement ratio variation range, and the operation requirement of low speed and large torque is met, so that the stepless speed regulation is realized.
It should be understood that although the present disclosure has been described in terms of various embodiments, not every embodiment is provided with a separate technical solution, and this description is for clarity only, and those skilled in the art should consider the disclosure as a whole, and the technical solutions in the various embodiments may be combined appropriately to form other embodiments that will be understood by those skilled in the art.
The above list of detailed descriptions is only specific to practical embodiments of the present invention, and they are not intended to limit the scope of the present invention, and all equivalent embodiments or modifications that do not depart from the spirit of the present invention should be included in the scope of the present invention.

Claims (7)

1. A hydraulic compound transmission device comprising a single-pump control double-acting motor system, which is characterized by comprising an input component, a front planetary gear mechanism (2), a rear planetary gear mechanism (3), a hydraulic transmission mechanism (4), an output component (5), a brake assembly and a clutch assembly, wherein the hydraulic transmission mechanism (4) comprises a hydraulic pump (43), an outer motor (46), an inner motor (49) and a control valve assembly; the outer motor (46) and the inner motor (49) share an output shaft; the output shaft is an output end of the hydraulic transmission mechanism (4); controlling the outer motor (46) or/and the inner motor (49) to be communicated with the hydraulic pump (43) through a control valve assembly; the displacement of the outer motor (46) is larger than that of the inner motor (49);
the clutch assembly connects the input member to the input of the front planetary gear set (2) and the input of the hydraulic transmission mechanism (4), respectively, the clutch assembly connects the output of the hydraulic transmission mechanism (4) to the front planetary gear set (2) and the rear planetary gear set (3), respectively, the clutch assembly connects the front planetary gear set (2) to the rear planetary gear set (3), the clutch assembly connects the rear planetary gear set (3) to the output member (5), the clutch assembly, the brake assembly and the control valve assembly provide a continuous transmission ratio between the input member and the output member (5);
The front planetary gear mechanism (2) comprises a front planetary sun gear (24), a front planetary planet carrier (25) and a front planetary gear ring (26); the rear planetary gear mechanism (3) comprises a rear planetary carrier (32), a rear planetary gear ring (33) and a rear planetary sun gear (34); the rear planet carrier (32) is connected with the output member (5);
the brake assembly comprises a first brake B 1 (27) Second brake B 2 (28) And a third brake B 3 (35) The method comprises the steps of carrying out a first treatment on the surface of the The first brake B 1 (27) For selectively connecting the rear planet row ring gear (33) to the stationary member; the second brake B 2 (28) For selectively connecting the front planet row sun gear (24) to the mount; the third brake B 3 (35) For selectively connecting the rear planet row sun gear (34) to the mount;
the clutch assembly includes a first clutch C 1 (21) Second clutch C 2 (22) Third clutch C 3 (23) Fourth clutch C 4 (31) Fifth clutch C 5 (41) Sixth clutch C 6 (412) And a seventh clutch C 7 (413) The method comprises the steps of carrying out a first treatment on the surface of the The first clutch C 1 (21) For selectively connecting the input member to a front planet carrier (25) for common rotation; the second clutch C 2 (22) For selectively connecting the front planet carrier (25) to the rear planet ring (33) for common rotation; the third clutch C 3 (23) For selectively connecting the front planet carrier (25) to the front planet ring (26) for common rotation; the fourth clutch C 4 (31) For selectively connecting the front planet ring gear (26) to the rear planet carrier (32) for common rotation; the fifth clutch C 5 (41) For selectively connecting an input member to an input of a hydraulic transmission (4) for common rotation; the sixth clutch C 6 (412) For selectively connecting the output of the hydraulic transmission (4) to the rear planet row sun gear (34) for common rotation; the seventh clutch C 7 (413) For selectively connecting the output of the hydraulic transmission (4) to the front planetary row sun gear (24) for common rotation;
two independent first outer motor flow passages and second outer motor flow passages are respectively arranged in the outer motor (46), and the displacement of the first outer motor flow passages is the same as that of the second outer motor flow passages; two independent first inner motor flow passages and second inner motor flow passages are respectively arranged in the inner motor (49), and the displacement of the first inner motor flow passages is the same as that of the second inner motor flow passages; the control valve assembly comprises a first reversing valve S 1 (45) Second reversing valve S 2 (47) Third direction changeValve S 3 (48) And a fourth reversing valve S 4 (410) A second reversing valve S is arranged between the first outer motor runner and the hydraulic pump (43) 2 (47) A first reversing valve S is arranged between the second outer motor runner and the hydraulic pump (43) 1 (45) A fourth reversing valve S is arranged between the first inner motor runner and the hydraulic pump (43) 4 (410) A third reversing valve S is arranged between the second inner motor runner and the hydraulic pump (43) 3 (48)；
The hydraulic transmission mechanism (4) is a single-pump control double-acting motor system, the displacement of one flow passage in the inner motor (49) is set to be V, and when the two flow passages of the inner motor (49) work simultaneously, the displacement of the inner motor (49) is set to be 2V; the displacement of the outer motor (46) is CV, and when the two flow passages of the outer motor (46) work simultaneously, the displacement of the inner motor (49) is 2CV, wherein C is a displacement coefficient, C>1, a step of; the total displacement V of the hydraulic motor of the hydraulic transmission mechanism (4) m ＝2V+2CV；V pmax Representing the displacement V of the hydraulic pump (43) p Is the maximum value of (2); -displacement ratio of the hydraulic pump (43):
when the first reversing valve S 1 (45) Energizing the right position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the middle position, the fourth reversing valve S 4 (410) When the neutral position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor runner and the second outer motor runner;
When the first reversing valve S 1 (45) Energizing the middle position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the middle position, the fourth reversing valve S 4 (410) When the middle position is electrified, the hydraulic pump (43) is communicated with the first outer motor runner;
when the first reversing valve S 1 (45) Energizing the middle position, the second reversing valve S 2 (47) Energizing the middle position, the third reversing valve S 3 (48) Energizing the right position, the fourth reversing valve S 4 (410) When the right bit is electrifiedThe hydraulic pump (43) is respectively communicated with the first inner motor runner and the second inner motor runner;
when the first reversing valve S 1 (45) Energizing the middle position, the second reversing valve S 2 (47) Energizing the middle position, the third reversing valve S 3 (48) Energizing the right position, the fourth reversing valve S 4 (410) When the middle position is electrified, the hydraulic pump (43) is communicated with a second inner motor runner;
when the first reversing valve S 1 (45) Energizing the right position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the right position, the fourth reversing valve S 4 (410) When the right position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor runner, the second outer motor runner, the first inner motor runner and the second inner motor runner;
When the first reversing valve S 1 (45) Energizing the right position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the right position, the fourth reversing valve S 4 (410) When the middle position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor runner, the second outer motor runner and the second inner motor runner;
when the first reversing valve S 1 (45) Energizing the middle position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the right position, the fourth reversing valve S 4 (410) When the right position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor runner, the first inner motor runner and the second inner motor runner;
when the first reversing valve S 1 (45) Energizing the middle position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the right position, the fourth reversing valve S 4 (410) When the neutral position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor runner and the second inner motor runner;
when the first reversing valve S 1 (45) Energizing the right position, the second reversing valve S 2 (47) Energizing right bit, the third switchDirection valve S 3 (48) Energizing the left position, the fourth reversing valve S 4 (410) When the middle position is electrified, the outlet of the hydraulic pump (43) is respectively communicated with the inlet of the first outer motor runner, the inlet of the second outer motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner, the outlet of the second outer motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump (43);
When the first reversing valve S 1 (45) Energizing the right position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the left position, the fourth reversing valve S 4 (410) When the power is applied to the left position, the outlet of the hydraulic pump (43) is respectively communicated with the inlet of the first outer motor runner, the inlet of the second outer motor runner, the outlet of the first inner motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner, the outlet of the second outer motor runner, the inlet of the first inner motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump (43);
when the first reversing valve S 1 (45) Energizing the middle position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the left position, the fourth reversing valve S 4 (410) When the middle position is electrified, the outlet of the hydraulic pump (43) is respectively communicated with the inlet of the first outer motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump (43);
when the first reversing valve S 1 (45) Energizing the middle position, the second reversing valve S 2 (47) Energizing the right position, the third reversing valve S 3 (48) Energizing the left position, the fourth reversing valve S 4 (410) When the power is on for the left position, the outlet of the hydraulic pump (43) is respectively communicated with the inlet of the first outer motor runner, the outlet of the first inner motor runner and the outlet of the second inner motor runner, and the outlet of the first outer motor runner, the inlet of the first inner motor runner and the inlet of the second inner motor runner are respectively communicated with the inlet of the hydraulic pump (43).
2. A machine-fluid compound transmission incorporating a single pump controlled double acting motor system as claimed in claim 1 wherein by controlling the first reversing valve S 1 (45) Second reversing valve S 2 (47) Third reversing valve S 3 (48) And a fourth reversing valve S 4 (410) The hydraulic transmission mechanism (4) is caused to output the following rotation speed ranges:
medium speed regulation mode:
low speed mode:
high speed regulation mode:
wherein: n is n p To input the rotation speed of the hydraulic pump, n m Is the rotational speed of the hydraulic motor output.
3. A compound transmission incorporating a single pump, double acting motor system as claimed in claim 1 wherein providing a gearing between the input and output members by adjusting the displacement ratio of the hydraulic transmission (4) and selectively controlling the engagement of the brake, clutch and control valve assemblies comprises: hydraulic transmission, mechanical-hydraulic transmission and mechanical transmission.
4. A compound transmission incorporating a single pump controlled double acting motor system as claimed in claim 3 wherein the control valve assembly is selectively controlled and the fifth release is selectively controlled by adjusting the displacement ratio of the hydraulic transmission (4)Combiner C 5 (41) And a first brake B 1 (27) Engagement by selectively controlling the sixth clutch C 6 (412) Engaging or second clutch C 2 (22) Fourth clutch C 4 (31) And a seventh clutch C 7 (413) Engagement provides a hydraulic transmission of multiple transmission between the input member and the output member.
5. A compound transmission incorporating a single pump double acting motor system as claimed in claim 3 wherein the control valve assembly is selectively controlled and the fifth clutch C is selectively controlled by adjusting the displacement ratio of the hydraulic transmission (4) 5 (41) And a first clutch C 1 (21) Engagement by selective control of fourth clutch C 4 (31) And a seventh clutch C 7 (413) Engaging or second clutch C 2 (22) And a sixth clutch C 6 (412) Engagement provides a plurality of transmission modes between the input member and the output member.
6. A compound transmission incorporating a single pump, double acting motor system as claimed in claim 3 wherein the first clutch C is selectively controlled 1 (21) Engagement by selectively controlling the second clutch C 2 (22) And a third brake B 3 (35) Engaging or third clutch C 3 (23) And a fourth clutch C 4 (31) Engaging or fourth clutch C 4 (31) And a second brake B 2 (28) Engagement provides a mechanical transmission of multiple transmission between the input member and the output member.
7. A machine-fluid compound transmission incorporating a single pump controlled double acting motor system as defined in claim 3, wherein,
the control valve assembly is controlled by adjusting the displacement ratio and the selectivity of the hydraulic transmission mechanism (4), so that the low speed regulation mode, the medium speed regulation mode and the high speed regulation mode are used for forward stepless speed regulation and meet the operation requirement of low speed and large torque;
the hydraulic transmission mode is switched to the hydraulic transmission mode without power interruption by adjusting the displacement ratio of the hydraulic transmission mechanism (4).
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