CN113983138A - Mechanical-hydraulic compound transmission device comprising single-pump-control double-acting motor system - Google Patents

Mechanical-hydraulic compound transmission device comprising single-pump-control double-acting motor system Download PDF

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CN113983138A
CN113983138A CN202111255412.6A CN202111255412A CN113983138A CN 113983138 A CN113983138 A CN 113983138A CN 202111255412 A CN202111255412 A CN 202111255412A CN 113983138 A CN113983138 A CN 113983138A
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electrified
hydraulic
clutch
reversing valve
motor
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CN113983138B (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)
  • Structure Of Transmissions (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

The invention provides a mechanical-hydraulic compound transmission device comprising a single-pump-control double-acting motor system, which comprises an input member, a front planet row mechanism, a rear planet row 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 an input of a front planetary gearset and an input of a hydraulic transmission, respectively, the clutch assembly connects an output of the hydraulic transmission to a front planetary gearset and a rear planetary gearset, respectively, the clutch assembly connects the front planetary gearset to the rear planetary gearset, the clutch assembly connects the rear planetary gearset to an output member, the clutch assembly, the brake assembly and the control valve assembly providing a continuous gear ratio between the input member and the output member. The invention is beneficial to improving the dynamic property and the fuel economy of the vehicle and prolonging the service life.

Description

Mechanical-hydraulic 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 engineering machinery walking system is complex in operation condition and severe in environment, and relates to starting, operation and transition working conditions, wherein the transmission device is required to provide a transmission ratio with low rotating speed and high torque during starting, and the transmission device is required to provide a transmission ratio with high rotating speed and low torque during operation. Therefore, the complexity of the working conditions of the engineering machinery walking system determines that the transmission device has higher requirements and more complex structure than the transmission device of a common vehicle.
The mechanical-hydraulic compound transmission has the characteristics of hydraulic transmission stepless speed regulation and mechanical transmission efficient speed change, and the performance of the transmission device is improved. The mechanical-hydraulic compound 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, and the mechanical-hydraulic compound transmission device which integrates multiple transmission modes and has multiple modes is a feasible scheme for improving the performance of the transmission device.
The hydrostatic transmission technology is usually applied to a traveling system of engineering machinery, 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 carried out under the condition of low-speed operation, and the stable operation of a vehicle is kept; the device can be adjusted in a wide range under the condition of transition so as to meet 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 in the prior art, the invention provides a mechanical-hydraulic compound transmission device comprising a single-pump-control double-acting motor system, which 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 property, the fuel economy and the service life of a vehicle.
The present invention achieves the above-described object by the following technical means.
A mechanical-hydraulic compound transmission device containing a single-pump-control double-acting motor system comprises an input member, a front planet row mechanism, a rear planet row 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 one output shaft; the output shaft is the output end of the hydraulic transmission mechanism; controlling the outer motor or/and the inner motor to be communicated with the hydraulic pump through a 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 an input of a front planetary gearset and an input of a hydraulic transmission, respectively, the clutch assembly connects an output of the hydraulic transmission to a front planetary gearset and a rear planetary gearset, respectively, the clutch assembly connects the front planetary gearset to the rear planetary gearset, the clutch assembly connects the rear planetary gearset to an output member, the clutch assembly, the brake assembly and the control valve assembly providing a continuous gear ratio between the input member and the output member.
Further, the front planet row mechanism comprises a front planet row sun gear, a front planet row planet carrier and a front planet row 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 row planet carrier is connected with the output component;
the brake assembly comprises a first brake B1A second brake B2And a third brake B3(ii) a The first brake B1For selectively connecting the rear planet carrier ring gear to the stationary member; the second brake B2For selectively connecting the front planet row sun gear to the mount; the third brake B3For selectively connecting the rear planet row sun gear to the stationary member;
the clutch assembly comprises a first clutch C1A second clutch C2A third clutch C3And a fourth clutch C4Fifth clutch C5Sixth clutch C6And a seventh clutch C7(ii) a The first clutch C1For selectively connecting the input member for common rotation with the forward planet carrier; the second clutch C2For selectively connecting the front carrier to the rear ring gear for common rotation; the third clutch C3For selectively connecting the forward planet carrier to the forward planet carrier for common rotation; the fourth clutch C4For selectively connecting the front planet carrier to the rear planet carrier for common rotation; the fifth clutch C5For selectively connecting the input member to the hydraulic transmission input for common rotation; the sixth clutch C6For selectively connecting the hydraulic drive mechanism output to the rear planet row sun gear for common rotation; the seventh clutch C7For selectively connecting the hydrostatic transmission output to the front planet row sun gear for common rotation;
two independent first outer motor flow passages and two independent second outer motor flow passages are respectively arranged in the outer motor, 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 two independent second inner motor flow passages are respectively arranged in the inner motor, 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 includes a first reversing valve S1A second reversing valve S2And a third reversing valve S3And a fourth direction-changing valve S4A second reversing valve S is arranged between the first outer motor flow passage and the hydraulic pump2A first reversing valve S is arranged between the second outer motor flow passage and the hydraulic pump1A fourth reversing valve S is arranged between the first inner motor flow passage and the hydraulic pump4A third reversing valve S is arranged between the second inner motor flow passage and the hydraulic pump3。
Furthermore, the hydraulic transmission mechanism is a single-pump-control double-acting motor system, the discharge capacity of one flow passage in the inner motor is set to be V, and when two flow passages of the inner motor work simultaneously, the discharge capacity of the inner motor is 2V; the outer motor displacement is CV, when two runners of the outer motor work simultaneously, the inner motor displacement is 2CV, wherein C is a displacement coefficient, C>1; the total discharge volume V of the hydraulic motor of the hydraulic transmission mechanismm＝2V+2CV；VpmaxIndicating hydraulic pump displacement VpMaximum value of (d); the displacement ratio of the hydraulic pump is:
Figure BDA0003323689210000021
when the first direction valve S1The second reversing valve S is electrified for the right position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the middle position4When the middle position is electrified, the hydraulic pump is respectively communicated with the first outer motor flow passage and the second outer motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the middle position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the middle position4When the middle position is electrified, the hydraulic pump is communicated with the first outer motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the middle position2The third reversing valve S is electrified for the middle position3The fourth reversing valve S is electrified for the right position4When the right position is electrified, the hydraulic pump is respectively communicated with the first inner motor flow passage and the second inner motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the middle position2The third reversing valve S is electrified for the middle position3The fourth reversing valve S is electrified for the right position4When the middle position is electrified, the hydraulic pump is communicated with a second inner motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the right position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the right position4When the right position is electrified, the hydraulic pump is respectively communicated with the first outer motor flow passage, the second outer motor flow passage, the first inner motor flow passage and the second inner motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the right position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the right position4When the middle position is electrified, the hydraulic pump is respectively communicated with the first outer motor flow passage, the second outer motor flow passage and the second inner motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the middle position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the right position4When the right position is electrified, the hydraulic pump is respectively communicated with the first outer motor flow passage, the first inner motor flow passage and the second inner motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the middle position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the right position4When the middle position is electrified, the hydraulic pump is respectively communicated with the first outer motor flow passage and the second inner motor flow passage;
when the first direction valve S1The second reversing valve S is electrified for the right position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the left position4When the middle position is electrified, the outlet of the hydraulic pump is respectively connected with the inlet of the first outer motor flow passage, the inlet of the second outer motor flow passage and the outlet of the second inner motor flow passageThe outlet of the first outer motor flow passage, the outlet of the second outer motor flow passage and the inlet of the second inner motor flow passage are respectively communicated with the inlet of the hydraulic pump;
when the first direction valve S1The second reversing valve S is electrified for the right position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the left position4When 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 direction valve S1The second reversing valve S is electrified for the middle position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the left position4When 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 direction valve S1The second reversing valve S is electrified for the middle position2The third reversing valve S is electrified for the right position3The fourth reversing valve S is electrified for the left position4When the left position is electrified, 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 direction changing valve S1A second reversing valve S2And a third reversing valve S3And a fourth direction-changing valve S4The state of (1) causing the hydraulic transmission mechanism to output the following rotational speed ranges:
and (3) a medium speed regulation mode:
Figure BDA0003323689210000041
low speed regulation mode:
Figure BDA0003323689210000042
high speed regulation mode:
Figure BDA0003323689210000043
in the formula: n ispFor input of the rotational speed of the hydraulic pump, nmThe rotating speed output by the hydraulic motor.
Further, providing a transmission between the input member and the output member by adjusting a displacement ratio of the hydraulic transmission mechanism and selectively controlling engagement of the brake assembly, clutch assembly, and control valve assembly includes: hydraulic, mechanical hydraulic, and mechanical transmissions.
Further, the fifth clutch C is selectively controlled by adjusting the displacement ratio of the hydraulic transmission mechanism, selectively controlling the control valve assembly and selectively controlling the hydraulic transmission mechanism5And a first brake B1Engaged by selectively controlling the sixth clutch C6Engaging or second clutch C2And a fourth clutch C4And a seventh clutch C7And engagement, hydraulic drive means providing a plurality of drive means between the input member and the output member.
Further, the fifth clutch C is selectively controlled by adjusting the displacement ratio of the hydraulic transmission mechanism, selectively controlling the control valve assembly and selectively controlling the hydraulic transmission mechanism5And a first clutch C1Engaged by selectively controlling the fourth clutch C4And a seventh clutch C7Engaging or second clutch C2And a sixth clutch C6And engagement, a hydro-mechanical drive means providing a plurality of drive means between the input member and the output member.
Further, selectively controlling theFirst clutch C1Engaged by selectively controlling the second clutch C2And a third brake B3Engaging or third clutch C3And a fourth clutch C4Engaging or fourth clutch C4And a second brake B2And a mechanical drive means providing multiple drive means between the input member and the output member.
Furthermore, the control valve component is selectively controlled by adjusting the displacement ratio of the hydraulic transmission mechanism, so that the forward stepless speed regulation in a low speed regulation mode, a medium speed regulation mode and a high speed regulation mode is realized, and the operation requirement of low speed and large torque is met; the hydraulic transmission mode is switched to the mechanical-hydraulic transmission mode without power interruption by adjusting the displacement ratio of the hydraulic transmission mechanism.
The invention has the beneficial effects that:
1. the invention relates to a mechanical-hydraulic compound transmission device comprising a single-pump-control double-acting motor system, wherein the single-pump-control double-acting motor system is a novel single-pump-control double-acting motor system formed by a plurality of double-acting motors on the basis of a variable pump-fixed displacement motor hydraulic system, the freedom degree of adjustment of the hydraulic system can be obviously improved, and the performance of the mechanical-hydraulic compound transmission device is improved.
2. The mechanical-hydraulic compound transmission device comprising the single-pump-control double-acting motor system can be switched among three modes of hydraulic transmission, mechanical-hydraulic transmission and mechanical transmission, each transmission mode has a plurality of gears and different speed regulation modes to be selected, when the medium speed regulation mode is adopted, only one motor is needed to work, the service life of a hydraulic component is prolonged, the low speed regulation mode and the high speed regulation mode can provide a plurality of operation modes according to complex operation working conditions by utilizing the plurality of motors, and the improvement of the dynamic property and the fuel economy of a vehicle is facilitated.
3. In each mode of the mechanical-hydraulic compound transmission device comprising the single-pump-control double-acting motor system, hydraulic transmission is quick in starting, stable in working and easy to realize quick speed change and reversing, the mechanical-hydraulic transmission effectively widens the speed regulation range, improves the transmission efficiency of the system, can meet the requirement of high-efficiency stepless speed regulation in a region, and is wide in speed regulation range and good in controllability.
Drawings
FIG. 1 is a schematic diagram of a mechanical-hydraulic compound transmission device including a single-pump-control double-acting motor system according to the present invention;
FIG. 2 is a schematic power flow diagram of a speed regulation mode 1 in the hydraulic mechanism according to the present invention;
FIG. 3 is a schematic power flow diagram of the speed regulation mode 2 in the hydraulic mechanism according to the present invention;
FIG. 4 is a schematic power flow diagram of the speed regulation mode 3 of the hydraulic mechanism according to the present invention;
FIG. 5 is a schematic diagram of the power flow direction of the governor mode 4 in the hydraulic mechanism according to the present invention;
FIG. 6 is a schematic power flow diagram of the hydraulic mechanism in the low speed regulation mode 1 according to the present invention;
FIG. 7 is a schematic power flow diagram of the low speed regulation mode 2 of the hydraulic mechanism according to the present invention;
FIG. 8 is a schematic power flow diagram of the low speed regulation mode 3 of the hydraulic mechanism according to the present invention;
FIG. 9 is a schematic power flow diagram of the low speed regulation mode 4 of the hydraulic mechanism according to the present invention;
FIG. 10 is a schematic power flow diagram of the hydraulic mechanism in the high speed regulation mode 1 according to the present invention;
FIG. 11 is a schematic power flow diagram of the hydraulic mechanism in the high speed regulation mode 2 according to the present invention;
FIG. 12 is a schematic power flow diagram of the hydraulic mechanism in the high speed regulation mode 3 according to the present invention;
FIG. 13 is a schematic power flow diagram of the hydraulic mechanism in the high speed regulation mode 4 according to the present invention;
FIG. 14 is a schematic flow chart of the first power stage of the hydrostatic transmission mode of the present invention;
FIG. 15 is a schematic representation of the hydraulic drive mode second gear power flow according to the present invention;
FIG. 16 is a schematic illustration of the power flow in the first gear of the mechanical-hydraulic transmission mode of the present invention;
FIG. 17 is a schematic illustration of the power flow in the second gear of the mechanical-hydraulic transmission mode of the present invention;
FIG. 18 is a schematic power flow diagram of the mechanical transmission M1 gear of the present invention;
FIG. 19 is a schematic power flow diagram of the mechanical transmission M2 according to the present invention;
FIG. 20 is a schematic power flow diagram of the mechanical transmission M3 according to the present invention;
FIG. 21 is a graph showing a speed-adjusting characteristic of the speed-adjusting gear according to the present invention;
FIG. 22 is a graph showing a low gear speed control characteristic of the present invention;
fig. 23 is a graph of the speed control characteristic of the high-speed gear of the present invention.
In the figure:
1-an input shaft; 2-front planet row mechanism; 21 first Clutch C1(ii) a 22-second Clutch C2(ii) a 23-third Clutch C3(ii) a 24-front planet row sun gear; 25-front planet carrier; 26-front planet row gear ring; 27-first brake B1(ii) a 28-second brake B2(ii) a 3-rear planet row mechanism; 31-fourth clutch C4(ii) a 32-rear planet row planet carrier; 33-rear planet row ring gear; 34-rear planet row sun gear; 35-third brake B3(ii) a 4-a hydraulic transmission mechanism; 41-fifth Clutch C5(ii) a 42-hydraulic transmission input gear pair; 43-a hydraulic pump; 44-a safety valve; 45-first direction valve S1(ii) a 46-an external motor; 46-1-an outer motor first inlet; 46-2-outer motor second inlet; 46-3-an outer motor first outlet; 46-4-an outer motor second outlet; 47-second reversing valve S2(ii) a 48-third direction valve S3(ii) a 49-internal motor; 49-1-inner motor first inlet; 49-2-inner motor first outlet; 49-3-inner motor second outlet; 49-4-inner motor second inlet; 410-fourth reversing valve S4(ii) a 411-hydraulic transmission first output gear pair; 412-sixth clutch C6(ii) a 413 seventh Clutch C7(ii) a 414-hydraulic drive second output gear pair; 5-an output member; 51-output gear set; 52-output shaft.
Detailed Description
The invention will be further described with reference to the following figures and specific examples, but the scope of the invention is not limited thereto.
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "axial," "radial," "vertical," "horizontal," "inner," "outer," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present invention and for simplicity in description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting. Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
In the present invention, unless otherwise expressly specified or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
As shown in fig. 1, the mechanical-hydraulic compound transmission device including a single-pump-control double-acting motor system according to the present invention includes an input shaft 1, a front planetary gear train 2, a rear planetary gear train 3, a hydraulic transmission mechanism 4, an output member 5, a brake assembly, and a clutch assembly.
The front planetary gear mechanism 2 comprises a first clutch C 121. Second clutch C 222. Third clutch C 323. A front planet row sun gear 24, a front planet row planet carrier 25, a front planet row gear ring 26 and a first brake B 127 and a second brake B 228; 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 121 for selectively connecting the input shaft 1 to the front planetary carrier 25 for common rotation; the second clutch C 222 for selectively connecting the front planet carrier 25 to the rear planet carrier 33 for common rotation; the third clutch C 323 for selectively connecting the front planet carrier 25 to the front planet ring gear 26 for common rotation; the first brake B 127 for selectively connecting the rear ring gear 33 to the stationary member; the second brake B 228 are used to selectively connect the front planet sun gear 24 to the mount.
The rear planetary gear mechanism 3 comprises a fourth clutch C 431. A rear carrier 32, a rear ring gear 33, a rear sun gear 34 and a third brake B 335; the rear planet row planet carrier 32, the rear planet row gear ring 33 and the rear planet row sun gear 34 form a planetary gear train; the fourth clutch C 431 for selectively connecting the front planet row ring gear 26 to the rear planet row carrier 32 for common rotation; the third brake B 335 are provided for selectively connecting the rear planet row sun gear 34 to the stationary member.
The hydraulic transmission mechanism 4 includes a fifth clutch C 541. A hydraulic transmission input gear pair 42, a hydraulic pump 43, a safety valve 44, and a first direction changing valve S 145. An external motor 46, a second direction changing valve S 247. Third change valve S 348. Inner motor 49, fourth direction changing valve S 4410. Hydraulically driven first output gear pair 411 and sixth clutch C 6412. Seventh clutch C 7413 and a hydraulically driven second output gear pair 414; the fifth clutch C 541 for selectively connecting the input shaft 1 for common rotation to the input shaft of a hydraulic pump 43 through a hydraulically driven input gear pair 42; the sixth clutch C 6412 for selectively connecting the output of the hydrostatic transmission 4 to the rear planet row sun gear 34 for common rotation; the seventh clutch C 7413 for selectively connecting the output of the hydrostatic transmission 4 to the front planet row sun gear 24 for common rotation; the outer motor 46 is connected in parallel with the 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 145. Second direction changing valve S 247. Third change valve S 348 and a fourth direction changing valve S 4410 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 relief valve 44 in parallel.
Two independent first outer motor flow passages and two independent second outer motor flow passages are respectively arranged in the outer motor 46, and the displacement volumes of the first outer motor flow passages and the second outer motor flow passages are the same; the inlet and outlet of the first outer motor flow passage 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 flow passage are respectively an outer motor second inlet 46-2 and an outer motor second outlet 46-4, two independent first inner motor flow passages and two independent second inner motor flow passages are respectively arranged in the inner motor 49, and the displacement of the first inner motor flow passage and the displacement of the second inner motor flow passage are the same; the inlet and outlet of the first inner motor flow passage 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 flow passage 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 flow passage and the hydraulic pump 43247, a first reversing valve S is arranged between the second external motor flow passage and the hydraulic pump 43145, a fourth reversing valve S is arranged between the first inner motor flow passage and the hydraulic pump 434410, a third reversing valve S is arranged between the second inner motor flow passage and the hydraulic pump 433 48。
The hydraulic transmission mechanism 4 is a single-pump-control double-acting motor systemWhen two flow passages of the inner motor 49 work simultaneously, the displacement of the inner motor 49 is 2V; the displacement of the outer motor 46 is CV, and when 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 is a displacement coefficient>1; the total discharge volume V of the hydraulic motor of the hydraulic transmission mechanism 4m＝2V+2CV；VpmaxIndicating the displacement V of the hydraulic pump 43pMaximum value of (d); displacement ratio of the hydraulic pump 43:
Figure BDA0003323689210000081
when the first direction valve S is as shown in FIG. 2145 is electrified at the right position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified in a middle position, and the fourth reversing valve S4When 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 and the second inlet 46-2 of the outer motor, and the first outlet 46-3 of the outer motor and the second outlet 46-4 of the outer motor are respectively communicated with the inlet of the hydraulic pump 43; the inner motor first inlet 49-1 is communicated with the inner motor first outlet 49-2, and the inner motor second inlet 49-4 is communicated with the inner motor second outlet 49-3; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 145 and a second direction-changing valve S 247 to an external motor 46 for driving the shaft to rotate at an output speed.
When the first direction valve S is as shown in FIG. 3145 is electrified in a middle position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified in a middle position, and the fourth reversing valve S 4410 when the middle position is electrified, 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 inner motor first inlet 49-1 is communicated with the inner motor first outlet 49-2, and the inner motor second inlet 49-4 is communicated with the inner motor second 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 247 to an external motor 46 for driving the shaft to rotate at an output speed.
When the first direction valve S is as shown in FIG. 4145 is electrified in a middle position, and the second reversing valve S 247 is electrified at the middle position, and the third reversing valve S 348 is electrified at the right position, and the fourth reversing valve S4When the right position is electrified 410, 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 is in communication with the outer motor first outlet 46-3 and the outer motor second inlet 46-2 is in communication with the outer motor second outlet 46-4; the oil pumped by the hydraulic pump 43 passes through a third reversing valve S 348 and a fourth direction changing valve S 4410 to the inner motor 49, which drives the rotating shaft to rotate and output the rotating speed.
When the first direction valve S is as shown in FIG. 5145 is electrified in a middle position, and the second reversing valve S 247 is electrified at the middle position, and the third reversing valve S 348 is electrified at the right position, and the fourth reversing valve S 4410 when the middle position is electrified, 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 is in communication with the outer motor first outlet 46-3, the outer motor second inlet 46-2 is in communication with the outer motor second outlet 46-4, and the inner motor first inlet 49-1 is in communication with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through a third reversing valve S 348 to an internal motor 49 for driving the shaft to rotate at an output speed.
When the first direction valve S is as shown in FIG. 6145 is electrified at the right position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified at the right position, and the fourth reversing valve S4When the position 410 is right, 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 throughFirst reversing valve S 145 and a second direction-changing valve S 247 to the external motor 46, via a third reversing valve S 348 and a fourth direction changing valve S 4410 to the inner motor 49, which together drive the rotating shaft to rotate and output the rotating speed.
When the first direction valve S is as shown in FIG. 7145 is electrified at the right position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified at the right position, and the fourth reversing valve S4When 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 is in communication with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 145 and a second direction-changing valve S 247 to the external motor 46, via a third reversing valve S 348 to an internal motor 49 which together drive the shaft to rotate at an output speed.
When the first direction valve S is as shown in FIG. 8145 is electrified in a middle position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified at the right position, and the fourth reversing valve S4When the position 410 is right-hand position, 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 247 to the external motor 46, via a third reversing valve S 348 and a fourth direction changing valve S 4410 to the inner motor 49, which together drive the rotating shaft to rotate and output the rotating speed.
When the first direction valve S is as shown in FIG. 9145 is electrified in a middle position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is right position electrified, and the fourth reversing valveS4When 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 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 is in communication with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 247 to the external motor 46, via a third reversing valve S 348 to an internal motor 49 which together drive the shaft to rotate at an output speed
As shown in fig. 10, when the first direction valve S 145 is electrified at the right position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified at the left position, and the fourth reversing valve S4When 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 outlet 49-3 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 inlet 49-4 of the inner motor are respectively communicated with the inlet of the hydraulic pump 43; the inner motor first inlet 49-1 is in communication with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the first reversing valve S 145 and a second direction-changing valve S 247 to the external motor 46, via a third reversing valve S 348 to an internal motor 49 which together drive the shaft to rotate at an output speed.
When the first direction valve S is used as shown in FIG. 11145 is electrified at the right position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified at the left position, and the fourth reversing valve S4When the power is switched on at the left position 410, 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 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 second outlet 46-4 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 oil pumped by the hydraulic pump 43 passes through the first reversing valve S 145 and a second direction-changing valve S 247 to the external motor 46, via a third reversing valve S 348 and a fourth direction changing valve S 4410 to the inner motor 49, which together drive the rotating shaft to rotate and output the rotating speed.
When the first direction valve S is as shown in FIG. 12145 is electrified in a middle position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified at the left position, and the fourth reversing valve S4When 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 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 is in communication with the inner motor first outlet 49-2; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 247 to the external motor 46, via a third reversing valve S 348 to an internal motor 49 which together drive the shaft to rotate at an output speed.
When the first direction valve S is used, as shown in FIG. 13145 is electrified in a middle position, and the second reversing valve S 247 is right position electrified and the third reversing valve S 348 is electrified at the left position, and the fourth reversing valve S4When the power is switched on at the left position 410, 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 is in communication with the outer motor second outlet 46-4; the oil pumped by the hydraulic pump 43 passes through the second reversing valve S 247 to the external motor 46, via a third reversing valve S 348 and a fourth direction changing valve S 4410 to the inner motor 49, which together drive the rotating shaft to rotate and output the rotating speed.
By controlling the first reversing valve S 145. Second direction changing valve S 247. Third change valve S 348 and a fourth direction changing valve S 4410, the hydraulic transmission mechanism 4 is caused to output the following rotational speed ranges:
and (3) a medium speed regulation mode:
Figure BDA0003323689210000111
low speed regulation mode:
Figure BDA0003323689210000112
high speed regulation mode:
Figure BDA0003323689210000121
in the formula: n ispFor input of the rotational speed of the hydraulic pump, nmThe rotating speed output by the hydraulic motor.
The single pump control double acting motor system has an inner and an outer motor and shares a common shaft, the outer motor 46 has a larger 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 at the same time, the total displacement of the hydraulic motors is the sum of the displacements of the outer motor 46 and the inner motor 49, the output rotating speed is low, and the low-speed work of the hydraulic motors 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, the total displacement of the hydraulic motor is the difference between the displacements of the outer motor 46 and the inner motor 49 because the displacement of the outer motor 46 is greater than the displacement of the inner motor 49, the output rotating speed is greater, and the high-speed work of the hydraulic motor is realized. When oil enters from two inlets of the double-acting motor at the same time, the discharge capacity is twice of that of a single inlet, and the output rotating speed is half of that of the original one.
The control valve assembly is controlled to have a low speed regulating mode, a medium speed regulating mode and a high speed regulating mode. Based on these 3 modes, and as shown in table 1, the following transmission modes between the input member and the output member can be provided by adjusting the displacement ratio of the hydraulic transmission mechanism 4 and selectively controlling the brake assembly and the clutch assembly, including: hydraulic drive and mechanical-hydraulic drive. Selective control of only the brake and clutch assemblies alone provides mechanical transmission between the input member and the output member.
Table 1 shows the relationship between the shift positions and the shift elements of the shift pattern
Figure BDA0003323689210000122
Figure BDA0003323689210000131
Figure BDA0003323689210000141
TABLE 2 Low Shift mode Transmission gears vs. Shift elements Table
Figure BDA0003323689210000142
Figure BDA0003323689210000151
TABLE 3 high shift mode transmission gear and shift element relationship table
Figure BDA0003323689210000152
Figure BDA0003323689210000161
Figure BDA0003323689210000171
Note: "a" represents the components being engaged, "left" indicates the reversing valve is left position energized, "center" indicates the reversing valve is center position, "right" indicates the reversing valve is right position energized. B is1Is a first brake, B2Is a second brake, B3Is a third brake, C1Is a first clutch C2Is a second clutch, C3Is a third clutch C4Is a fourth clutch C5Is a fifth clutch C6Is a sixth clutch C7Is a seventh clutch, S1Is a first change valve, S2Is a second change valve, S3Is a third change valve, S4Is a fourth reversing valve.
The main parameters are as follows: n isIFor input of a rotational speed, noFor output speed, e is the displacement ratio of the hydraulic transmission mechanism, C is the displacement coefficient, VpmaxIs the maximum value of the displacement of the variable displacement pump, V is the internal motor displacement of the hydraulic motor, CV is the external motor displacement of the hydraulic motor, k1Characteristic parameter, k, of the planet gear of the front planetary gear train2Characteristic parameters of the planet gear of the rear planet row mechanism are obtained; i.e. i1For hydraulic transmission input gear pair transmission ratio, i2For hydraulically driving the first output gear pair transmission ratio, i3For the second output gear pair transmission ratio of hydraulic transmission, C is 2.5, i1＝0.6，i2＝0.4，i3＝0.6，i4i5＝1，Vpmax＝196ml/r，V＝56ml/r，k1＝2，k2＝1.5。
As shown in fig. 14, the first hydraulic transmission mode: fifth clutch C 541. Sixth clutch C 6412 and brake B 127 are engaged, the change-over between the gears with different transmission ratios in the first mode of the hydraulic transmission mode is realized through the change-over of the reversing valve, the rear planet gear ring gear 33 is braked, and the power is transmitted through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 541 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 6412 and the first output gear pair 411 are transmitted to the rear planetary row sun gear 34, and then output from the output shaft 52 via the rear planetary row carrier 32.
As shown in fig. 15, the second hydraulic transmission mode: second clutch C 222. Fourth clutch C 431. Fifth clutch C 541. Seventh clutch C 7413 andbrake B 127 are engaged, the gears with different transmission ratios in the hydraulic transmission mode two are switched by switching of the reversing valve, the front planet carrier 25 and the rear planet gear ring 33 are braked, and power is transmitted through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 541 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 7413 and a second hydraulically driven output gear pair 414 to the front planet row sun gear 34 and then through the front planet row ring gear 26 and the rear planet row carrier 32, from the output shaft 52.
As shown in fig. 16, the first mechanical-hydraulic transmission mode: first clutch C 121. Fourth clutch C 431. Fifth clutch C 541 and a seventh clutch C 7413 is engaged, the gear with different transmission ratios in the first mechanical-hydraulic transmission mode is switched by switching of the reversing valve, the power is divided by the input shaft 1, and the power of a hydraulic path is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 7413 and a hydraulic transmission second output gear pair 414 to the front planet row sun gear 24, and the mechanical power is transmitted to the front planet row planet carrier 25 through the input shaft 1, finally is converged to the front planet row gear ring 26 and the rear planet row planet carrier 32, and is output from the output shaft 52.
As shown in fig. 17, the second mechatronic transmission mode: first clutch C 121. Second clutch C 222. Fifth clutch C 541 and a sixth clutch C 6412 is engaged, the gears with different transmission ratios in the mechanical-hydraulic transmission mode II are switched by switching of the reversing valve, the power is divided by the input shaft 1, and the power of a hydraulic path is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 6412 and a hydraulic transmission first output gear pair 411 are transmitted to a rear planet row sun gear 34, mechanical path power is transmitted to a rear planet row gear ring 33 through an input shaft 1, and finally the mechanical path power is converged to a rear planet rowThe carrier 32 is output from the output shaft 52.
As shown in fig. 18, the mechanical transmission M1 gear: first clutch C 121. Second clutch C 222 and brake B 335 is engaged, the rear planet carrier 34 brakes, and power is transmitted through the input shaft 1 to the rear ring gear 33 via the front planet carrier 25, then through the planet carrier 32, and out the output shaft 52.
As shown in fig. 19, the mechanical transmission M2 gear: first clutch C 121. Third clutch C 323 and a fourth clutch C 431, the front planet row carrier 25 and the front planet row gear ring 26 are fixedly connected into a whole, and power is transmitted to the front planet row carrier 25 through the input shaft 1 and then is output from the output shaft 52 through the front planet row gear ring 26 and the rear planet row carrier 32.
As shown in fig. 20, the mechanical transmission M3 gear: first clutch C 121. Fourth clutch C 431 and brake B 228 are engaged, the front planetary sun gear 24 is braked, and power is transmitted to the front planetary carrier 25 via the input shaft 1, and then is 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, the power flow of the hydraulic mechanism is shown in the figures 2, 3, 4 and 5, and the specific implementation method is as follows:
hydraulic transmission H1 gear: fifth clutch C 541. Sixth clutch C 6412 and brake B 127 engaged, first direction valve S 145 is energized at the right position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S 4410 is electrified at the middle position, the rear planet row gear ring 33 is braked, and power is transmitted to the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 541 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 6412 and the hydraulically driven first output gear pair 411 are transmitted to the rear planet row sun gear 34, through the rear planet row carrier 32,is output from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝1.17enI
in the formula, noFor input of a rotational speed, nITo output the rotational speed, e is the displacement ratio of the hydraulic transmission mechanism 5.
Hydraulic transmission H2 gear: fifth clutch C 541. Sixth clutch C 6412 and brake B 127 engaged, first direction valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S 4410 is electrified at the middle position, the rear planet row gear ring 33 is braked, and power is transmitted to the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 541 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 6412 and the first output gear pair 411 are transmitted to the rear planetary row sun gear 34, and then output from the output shaft 52 via the rear planetary row carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝2.33enI
hydraulic transmission H3 gear: fifth clutch C 541. Sixth clutch C 6412 and brake B 127 engaged, first direction valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S 4410 is electrified at the right position, the rear planet row gear ring 33 is braked, and power is transmitted through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 541 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 6412 and the first output gear pair 411 are transmitted to the rear planetary row sun gear 34, and then output from the output shaft 52 via the rear planetary row carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝2.92enI
hydraulic transmission H4 gear: first, theFive clutches C 541. Sixth clutch C 6412 and brake B 127 engaged, first direction valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S 4410 is electrified at the right position, the rear planet row gear ring 33 is braked, and power is transmitted through the input shaft 1, the hydraulic transmission input gear pair 42 and the fifth clutch C 541 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 6412 and the first output gear pair 411 are transmitted to the rear planetary row sun gear 34, and then output from the output shaft 52 via the rear planetary row carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝5.83enI
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, the power flow of the hydraulic mechanism is shown in the figures 2, 3, 4 and 5, and the specific implementation method is as follows:
hydraulic transmission R1 gear: second clutch C 222. Fourth clutch C 431. Fifth clutch C 541. Seventh clutch C 7413 and brake B 127 engaged, first direction valve S 145 is energized at the right position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S4The middle position is electrified, the front planet carrier 25 and the rear planet gear ring gear 33 are braked, and the power is transmitted to the input gear pair 42 and the fifth clutch C through the input shaft 1 and the hydraulic transmission 541 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 7413 and a second hydraulically driven output gear pair 414 to the front planet row sun gear 34 and then through the front planet row ring gear 26 and the rear planet row carrier 32, from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝-0.97enI
hydraulic transmissionMoving R2 gear: second clutch C 222. Fourth clutch C 431. Fifth clutch C 541. Seventh clutch C 7413 and brake B 127 engaged, first direction valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S4The middle position is electrified, the front planet carrier 25 and the rear planet gear ring gear 33 are braked, and the power is transmitted to the input gear pair 42 and the fifth clutch C through the input shaft 1 and the hydraulic transmission 541 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 7413 and a second hydraulically driven output gear pair 414 to the front planet row sun gear 34 and then through the front planet row ring gear 26 and the rear planet row carrier 32, from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝-1.94enI
hydraulic transmission R3 gear: second clutch C 222. Fourth clutch C 431. Fifth clutch C 541. Seventh clutch C 7413 and brake B 127 engaged, first direction valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S4The right position 410 is electrified, the front planet carrier 25 and the rear planet gear ring gear 33 are braked, and power is transmitted to the input gear pair 42 and the fifth clutch C through the input shaft 1 and the hydraulic transmission 541 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 7413 and a second hydraulically driven output gear pair 414 to the front planet row sun gear 34 and then through the front planet row ring gear 26 and the rear planet row carrier 32, from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝-2.43enI
hydraulic transmission R4 gear: second clutch C 222. Fourth clutch C 431. Fifth clutch C 541. Seventh clutch C 7413 and brake B 127 engaged, first direction valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S4The right position 410 is electrified, the front planet carrier 25 and the rear planet gear ring gear 33 are braked, and power is transmitted to the input gear pair 42 and the fifth clutch C through the input shaft 1 and the hydraulic transmission 541 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 7413 and a second hydraulically driven output gear pair 414 to the front planet row sun gear 34 and then through the front planet row ring gear 26 and the rear planet row carrier 32, from the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝-4.86enI
the first mechanical-hydraulic transmission mode of the medium speed regulation mode comprises a mechanical-hydraulic transmission HM1 gear, a mechanical-hydraulic transmission HM2 gear, a mechanical-hydraulic transmission HM3 gear and a mechanical-hydraulic transmission HM4 gear, 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 HM1 gear: first clutch C 121. Fourth clutch C 431. Fifth clutch C 541 and a seventh clutch C 7413 engaged, first direction changing valve S 145 is energized at the right position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S 4410 is electrified in the middle position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 7413 and a hydraulic transmission second output gear pair 414 to the front planet row sun gear 24, and the mechanical power is transmitted to the front planet row planet carrier 25 through the input shaft 1, finally is converged to the front planet row gear ring 26 and the rear planet row planet 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 as follows:
no＝(1.5-0.97e)nI
mechanical-hydraulic transmission HM2 gear: first clutch C 121. Fourth clutch C 431. Fifth clutch C 541 and a seventh clutch C 7413 engaged, first direction changing valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S 4410 is electrified in the middle position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 7413 and a hydraulic transmission second output gear pair 414 to the front planet row sun gear 24, and the mechanical power is transmitted to the front planet row planet carrier 25 through the input shaft 1, finally is converged to the front planet row gear ring 26 and the rear planet row planet 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 as follows:
no＝(1.5-1.94e)nI
mechanical-hydraulic transmission HM3 gear: first clutch C 121. Fourth clutch C 431. Fifth clutch C 541 and a seventh clutch C 7413 engaged, first direction changing valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S 4410 is electrified at the right position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 7413 and a hydraulic transmission second output gear pair 414 to the front planet row sun gear 24, and the mechanical power is transmitted to the front planet row planet carrier 25 through the input shaft 1, finally is converged to the front planet row gear ring 26 and the rear planet row planet 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 as follows:
no＝(1.5-2.43e)nI
mechanical-hydraulic transmission HM4 gear: first separationCombiner C 121. Fourth clutch C 431. Fifth clutch C 541 and a seventh clutch C 7413 engaged, first direction changing valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S 4410 is electrified at the right position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 7413 and a hydraulic transmission second output gear pair 414 to the front planet row sun gear 24, and the mechanical power is transmitted to the front planet row planet carrier 25 through the input shaft 1, finally is converged to the front planet row gear ring 26 and the rear planet row planet 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 as follows:
no＝(1.5-4.86e)nI
the second mechanical-hydraulic transmission mode of the medium speed regulation mode comprises a mechanical-hydraulic transmission HMs1 gear, a mechanical-hydraulic transmission HMs2 gear, a mechanical-hydraulic transmission HMs3 gear and a mechanical-hydraulic transmission HMs4 gear, 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 HMs1 gear: first clutch C 121. Second clutch C 222. Fifth clutch C 541 and a sixth clutch C 6412 engaged, first reversing valve S 145 is energized at the right position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S 4410 is electrified in the middle position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 6412 and the hydraulic transmission first output gear pair 411 are transmitted to the rear planet row sun gear 34, and the mechanical path power is transmitted to the rear planet row ring gear 33 through the input shaft 1, finally is merged to the rear planet row carrier 32, and is output from the output shaft 52. At this time, the output rotation speed is related to the input rotation speedThe method comprises the following steps:
no＝(0.6+1.17e)nI
mechanical-hydraulic transmission HMs2 gear: first clutch C 121. Second clutch C 222. Fifth clutch C 541 and a sixth clutch C 6412 engaged, first reversing valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized at right position, and the third change valve S 348 is energized in the neutral position, and the fourth direction changing valve S 4410 is electrified in the middle position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 6412 and the hydraulic transmission first output gear pair 411 are transmitted to the rear planet row sun gear 34, and the mechanical path power is transmitted to the rear planet row ring gear 33 through the input shaft 1, finally is merged to the rear planet row 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 as follows:
no＝(0.6+2.33e)nI
mechanical-hydraulic transmission HMs3 gear: first clutch C 121. Second clutch C 222. Fifth clutch C 541 and a sixth clutch C 6412 engaged, first reversing valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S 4410 is electrified at the right position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 6412 and the hydraulic transmission first output gear pair 411 are transmitted to the rear planet row sun gear 34, and the mechanical path power is transmitted to the rear planet row ring gear 33 through the input shaft 1, finally is merged to the rear planet row 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 as follows:
no＝(0.6+2.92e)nI
mechanical-hydraulic transmission HMs4 gear: first clutch C 121. Second clutch C 222. Fifth clutch C 541 and a sixth clutch C 6412 engaged, first reversing valve S 145 is electrified in a middle position, and the second reversing valve S 247 is energized in the neutral position, and the third change valve S 348 is energized to the right, and the fourth direction changing valve S 4410 is electrified at the right position, the power is divided by the input shaft 1, the power of a hydraulic circuit is input into the gear pair 42 and the fifth clutch C through hydraulic transmission 541 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 6412 and the hydraulic transmission first output gear pair 411 are transmitted to the rear planet row sun gear 34, and the mechanical path power is transmitted to the rear planet row ring gear 33 through the input shaft 1, finally is merged to the rear planet row 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 as follows:
no＝(0.6+5.83e)nI
the mechanical transmission modes comprise a mechanical transmission M1 gear and a mechanical transmission M2 gear, and the specific implementation method comprises the following steps:
mechanical transmission M1 gear: first clutch C 121. Second clutch C 222 and brake B 335 are engaged, the rear planet row sun gear 34 brakes, and power is transmitted through the input shaft 1 to the rear planet row ring gear 33, then through the planet row carrier 32, and out the output shaft 52. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝0.6nI
mechanical transmission M2 gear: first clutch C 121. Third clutch C 323 and a fourth clutch C 431, the front planet row carrier 25 and the front planet row gear ring 26 are fixedly connected into a whole, and power is transmitted to the front planet row carrier 25 through the input shaft 1 and then is output from the output shaft 52 through the front planet row gear ring 26 and the rear planet row carrier 32. At this time, the relationship between the output rotation speed and the input rotation speed is as follows:
no＝nI
mechanical transmission M3 gear: first clutch C 121. Fourth stepCombiner C 431 and brake B 228 are engaged, the front planetary sun gear 24 is braked, and power is transmitted to the front planetary carrier 25 via the input shaft 1, and then is 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 as follows:
no＝1.5nI
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 shown in figures 6, 7, 8 and 9, and the specific implementation method is the same as that of each gear of the first hydraulic transmission mode of the medium speed regulation mode.
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H1 gear is as follows: n iso＝0.83enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H2 gear is as follows: n iso＝0.97enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H3 gear is as follows: n iso＝1.30enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H4 gear is as follows: n iso＝1.67enI；
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 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 the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R1 gear is as follows: n iso＝-0.69enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R2 gear is as follows: n iso＝-0.81enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R3 gear is as follows: n iso＝-1.08enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R4 gear is as follows: n iso＝-1.39enI；
The first mechanical-hydraulic transmission mode of the low speed regulation mode comprises a first mechanical-hydraulic transmission mode HM1 gear, a first mechanical-hydraulic transmission mode HM2 gear, a first mechanical-hydraulic transmission mode HM3 gear and a first mechanical-hydraulic transmission mode HM4 gear, the power flow of the hydraulic mechanism is shown in FIGS. 6, 7, 8 and 9, and the specific implementation method is the same as that of each gear of the first mechanical-hydraulic transmission mode of the medium speed regulation mode.
At this time, the relationship between the output rotating speed and the input rotating speed of the hydraulic transmission HM1 gear is as follows: n iso＝(1.5-0.69e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the hydraulic transmission HM2 gear is as follows: n iso＝(1.5-0.81e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the hydraulic transmission HM3 gear is as follows: n iso＝(1.5-1.08e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the hydraulic transmission HM4 gear is as follows: n iso＝(1.5-1.39e)nI；
The second mechanical-hydraulic transmission mode of the low speed regulation mode comprises HMs1 gear mechanical-hydraulic transmission, HMs2 gear mechanical-hydraulic transmission, HMs3 gear mechanical-hydraulic transmission and HMs4 gear mechanical-hydraulic transmission, the power flow of the hydraulic mechanism is shown in fig. 6, 7, 8 and 9, and the specific implementation method is the same as that of each gear of the second mechanical-hydraulic transmission mode of the medium speed regulation mode.
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs1 gear is as follows: n iso＝(0.6+0.83e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs2 gear is as follows: n iso＝(0.6+0.97e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs3 gear is as follows: n iso＝(0.6+1.30e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs4 gear is as follows: n iso＝(0.6+1.67e)nI；
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 shown in figures 10, 11, 12 and 13, and the specific implementation method is the same as that of each gear of the first hydraulic transmission mode of the medium speed regulation mode.
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H1 gear is as follows: n iso＝1.46enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H2 gear is as follows: n iso＝1.94enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H3 gear is as follows: n iso＝3.89enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission H4 gear is as follows: n iso＝11.67enI；
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 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 the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R1 gear is as follows: n iso＝-1.22enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R2 gear is as follows: n iso＝-1.62enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R3 gear is as follows: n iso＝-3.24enI；
At the moment, the relation between the output rotating speed and the input rotating speed of the hydraulic transmission R4 gear is as follows: n iso＝-9.72enI；
The first mechanical-hydraulic transmission mode of the high speed regulation mode comprises a first mechanical-hydraulic transmission mode HM1 gear, a first mechanical-hydraulic transmission mode HM2 gear, a first mechanical-hydraulic transmission mode HM3 gear and a first mechanical-hydraulic transmission mode HM4 gear, the power flow of the hydraulic mechanism is shown in fig. 10, 11, 12 and 13, and the specific implementation method is the same as that of each gear of the first mechanical-hydraulic transmission mode of the medium speed regulation mode.
At this time, the relationship between the output rotating speed and the input rotating speed of the hydraulic transmission HM1 gear is as follows: n iso＝(1.5-1.22e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the hydraulic transmission HM2 gear is as follows: n iso＝(1.5-1.62e)nI；
At this timeThe relation between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HM3 gear is as follows: n iso＝(1.5-3.24e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the hydraulic transmission HM4 gear is as follows: n iso＝(1.5-9.72e)nI；
The second mechanical-hydraulic transmission mode of the high speed regulation mode comprises HMs1 gear mechanical-hydraulic transmission, HMs2 gear mechanical-hydraulic transmission, HMs3 gear mechanical-hydraulic transmission and HMs4 gear mechanical-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 each gear of the second mechanical-hydraulic transmission mode of the medium speed regulation mode.
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs1 gear is as follows: n iso＝(0.6+1.46e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs2 gear is as follows: n iso＝(0.6+1.94e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs3 gear is as follows: n iso＝(0.6+3.89e)nI；
At this time, the relationship between the output rotating speed and the input rotating speed of the mechanical-hydraulic transmission HMs4 gear is as follows: n iso＝(0.6+11.67e)nI；
The speed control characteristic curve of the intermediate speed gear is shown in fig. 20. When e is equal to [0, 1.00 ]]In the range, starting is carried out by utilizing four gears of a first hydraulic transmission mode, linear speed regulation is carried out at the moment, then the four gears can be switched to four gears corresponding to a first mechanical-hydraulic transmission mode without power interruption, and the four gears of the first mechanical-hydraulic transmission mode can reach a maximum speed regulation point; the four gears of the first mechanical-hydraulic transmission mode can be switched to the four gears of the second mechanical-hydraulic transmission mode without power interruption, the mechanical-hydraulic transmission mode mainly adopts low-speed high torque to meet the working condition with higher power requirement, and the linear speed regulation is carried out at the moment; the speed regulation range of the hydraulic transmission H1 gear is no∈[0，0.82]nIWhen e is 0.70, the hydraulic transmission H1 gear can be switched to the mechanical hydraulic transmission HM1 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.50]nIWhen e is 0.42, the mechanical-hydraulic transmission HM1 gear can be switched to the mechanical-hydraulic transmission HMs1 gear without power interruption, and at the moment, the linear speed regulation is carried out, wherein the speed regulation range is no∈[0.60，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H2 gear is no∈[0，0.82]nIWhen e is 0.35, the hydraulic transmission H2 gear can be switched to the mechanical hydraulic transmission HM2 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.21, the mechanical-hydraulic transmission HM2 gear can be switched to the mechanical-hydraulic transmission HMs2 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H3 gear is no∈[0，0.82]nIWhen e is 0.28, the hydraulic transmission H3 gear can be switched to the mechanical hydraulic transmission HM3 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.17, the mechanical-hydraulic transmission HM3 gear can be switched to the mechanical-hydraulic transmission HMs3 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H4 gear is no∈[0，0.82]nIWhen e is 0.14, the hydraulic transmission H4 gear can be switched to the mechanical hydraulic transmission HM4 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.08, the mechanical-hydraulic transmission HM4 gear can be switched to the mechanical-hydraulic transmission HMs4 gear without power interruption, and at the moment, the linear speed regulation is carried out, wherein the speed regulation range is no∈[0.82，1.09]nI(ii) a Compared with the hydraulic transmission mode, the switched mechanical-hydraulic transmission mode has higher rotation speed under the condition of the same displacement ratio, and realizes stepless speed regulation. And when the speed is regulated in the negative direction, the four gears in the second hydraulic transmission mode are utilized, the displacement ratio of the hydraulic transmission mechanism is regulated, the speed is regulated linearly in the variation range of the displacement ratio, the operation requirement of low speed and high torque is met, and the stepless speed regulation is realized.
Fig. 21 shows a low shift speed control characteristic curve of the present invention. When e is equal to [0, 1.00 ]]In the range, starting is carried out by utilizing four gears of a first hydraulic transmission mode, linear speed regulation is carried out at the moment, then the four gears can be switched to four gears corresponding to a first mechanical-hydraulic transmission mode without power interruption, and the four gears of the first mechanical-hydraulic transmission mode can reach a maximum speed regulation point; four gears of the first mechanical-hydraulic transmission mode can be switched to four gears of the corresponding second mechanical-hydraulic transmission mode without power interruptionThe mechanical-hydraulic transmission mode mainly adopts a low-speed large torque to meet the working condition with higher power requirement, and at the moment, the linear speed regulation is carried out; the speed regulation range of the hydraulic transmission H1 gear is no∈[0，0.82]nIWhen e is 0.99, the hydraulic transmission H1 gear can be switched to the mechanical hydraulic transmission HM1 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.50]nIWhen e is 0.59, the mechanical-hydraulic transmission HM1 gear can be switched to the mechanical-hydraulic transmission HMs1 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.60，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H2 gear is no∈[0，0.82]nIWhen e is 0.84, the hydraulic transmission H2 gear can be switched to the mechanical hydraulic transmission HM2 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.51, the mechanical-hydraulic transmission HM2 gear can be switched to the mechanical-hydraulic transmission HMs2 gear without power interruption, and the linear speed regulation is carried out in the speed regulation range no∈[0.82，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H3 gear is no∈[0，0.82]nIWhen e is 0.63, the hydraulic transmission H3 gear can be switched to the mechanical hydraulic transmission HM3 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.50]nIWhen e is 0.38, the mechanical-hydraulic transmission HM3 gear can be switched to the mechanical-hydraulic transmission HMs3 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H4 gear is no∈[0，0.82]nIWhen e is 0.49, the hydraulic transmission H4 gear can be switched to the mechanical hydraulic transmission HM4 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.29, the mechanical-hydraulic transmission HM4 gear can be switched to the mechanical-hydraulic transmission HMs4 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.09]nI(ii) a Compared with the hydraulic transmission mode, the switched mechanical-hydraulic transmission mode has higher rotation speed under the condition of the same displacement ratio, and realizes stepless speed regulation. In the negative speed regulation, four gears of the hydraulic transmission mode two are utilized, the displacement ratio of the hydraulic transmission mechanism is regulated, the linear speed regulation is carried out in the displacement ratio variation range, and the low-speed and high-torque operation requirement is metAnd realizing stepless speed regulation.
Fig. 22 shows a high-shift speed control characteristic curve of the present invention. When e is equal to [0, 1.00 ]]In the range, starting is carried out by utilizing four gears of a first hydraulic transmission mode, linear speed regulation is carried out at the moment, then the four gears can be switched to four gears corresponding to a first mechanical-hydraulic transmission mode without power interruption, and the four gears of the first mechanical-hydraulic transmission mode can reach a maximum speed regulation point; the four gears of the first mechanical-hydraulic transmission mode can be switched to the four gears of the second mechanical-hydraulic transmission mode without power interruption, the mechanical-hydraulic transmission mode mainly adopts low-speed high torque to meet the working condition with higher power requirement, and the linear speed regulation is carried out at the moment; the speed regulation range of the hydraulic transmission H1 gear is no∈[0，0.82]nIWhen e is 0.56, the hydraulic transmission H1 gear can be switched to the mechanical hydraulic transmission HM1 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.33, the mechanical-hydraulic transmission HM1 gear can be switched to the mechanical-hydraulic transmission HMs1 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.60，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H2 gear is no∈[0，0.82]nIWhen e is 0.42, the hydraulic transmission H2 gear can be switched to the mechanical hydraulic transmission HM2 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.25, the mechanical-hydraulic transmission HM2 gear can be switched to the mechanical-hydraulic transmission HMs2 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H3 gear is no∈[0，0.82]nIWhen e is 0.21, the hydraulic transmission H3 gear can be switched to the mechanical hydraulic transmission HM3 gear without power interruption, and the speed is regulated linearly in the speed regulation range no∈[0.82，1.50]nIWhen e is 0.13, the mechanical-hydraulic transmission HM3 gear can be switched to the mechanical-hydraulic transmission HMs3 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.09]nI(ii) a The speed regulation range of the hydraulic transmission H4 gear is no∈[0，0.82]nIWhen e is 0.07, the hydraulic transmission H4 gear can be switched to the mechanical hydraulic transmission HM4 gear without power interruption, and at the moment, the linear speed regulation is carried out, and the speed regulation range is no∈[0.82，1.50]nIWhen e is 0.04,the mechanical-hydraulic transmission HM4 gear can be switched to the mechanical-hydraulic transmission HMs4 gear without power interruption, and at the moment, the linear speed regulation is carried out, wherein the speed regulation range is no∈[0.82，1.09]nI(ii) a Compared with the hydraulic transmission mode, the switched mechanical-hydraulic transmission mode has higher rotation speed under the condition of the same displacement ratio, and realizes stepless speed regulation. And when the speed is regulated in the negative direction, the four gears in the second hydraulic transmission mode are utilized, the displacement ratio of the hydraulic transmission mechanism is regulated, the speed is regulated linearly in the variation range of the displacement ratio, the operation requirement of low speed and high torque is met, and the stepless speed regulation is realized.
It should be understood that although the present description has been described in terms of various embodiments, not every embodiment includes only a single embodiment, and such description is for clarity purposes only, and those skilled in the art will recognize that the embodiments described herein may be combined as suitable to form other embodiments, as will be appreciated by those skilled in the art.
The above-listed detailed description is only a specific description of a possible embodiment of the present invention, and they are not intended to limit the scope of the present invention, and equivalent embodiments or modifications made without departing from the technical spirit of the present invention should be included in the scope of the present invention.

Claims (9)

1. The mechanical-hydraulic compound transmission device containing a single-pump-control double-acting motor system 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 component and a clutch component, wherein the hydraulic transmission mechanism (4) comprises a hydraulic pump (43), an outer motor (46), an inner motor (49) and a control valve component; the outer motor (46) and the inner motor (49) share an output shaft; the output shaft is the output end of the hydraulic transmission mechanism (4); controlling the outer motor (46) or/and the inner motor (49) to communicate with the hydraulic pump (43) by means of 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 a front planetary gear train (2) and the input of a hydraulic transmission mechanism (4), respectively, the clutch assembly connects the output of the hydraulic transmission mechanism (4) to the front planetary gear train (2) and a rear planetary gear train (3), respectively, the clutch assembly connects the front planetary gear train (2) to the rear planetary gear train (3), the clutch assembly connects the rear planetary gear train (3) to an output member (5), the clutch assembly, brake assembly and control valve assembly providing a continuous gear ratio between the input member and the output member (5).
2. The mechanical-hydraulic compound transmission device comprising a single-pump-control double-acting motor system according to claim 1, wherein the front planetary row mechanism (2) comprises a front planetary row sun gear (24), a front planetary row planet carrier (25) and a front planetary row ring gear (26); the rear planet row mechanism (3) comprises a rear planet row planet carrier (32), a rear planet row gear ring (33) and a rear planet row sun gear (34); the rear planet row planet carrier (32) is connected with the output component (5);
the brake assembly comprises a first brake B1(27) A second brake B2(28) And a third brake B3(35) (ii) a The first brake B1(27) For selectively connecting the rear planet row ring gear (33) to the stationary member; the second brake B2(28) For selectively connecting the front planet sun gear (24) to the mount; the third brake B3(35) For selectively connecting the rear planet row sun gear (34) to the stationary member;
the clutch assembly comprises a first clutch C1(21) A second clutch C2(22) A third clutch C3(23) And a fourth clutch C4(31) Fifth clutch C5(41) Sixth clutch C6(412) And a seventh clutch C7(413) (ii) a The first clutch C1(21) For selectively connecting the input member for common rotation with a forward planet carrier (25); the second clutch C2(22) For selectively connecting the front planet carrier (25) to the rear planet carrier (33) for common rotation; the third clutch C3(23) For selectively connecting a front planet carrier (25) to a front planet ring gear (26) to shareRotating simultaneously; the fourth clutch C4(31) For selectively connecting the front planet row ring gear (26) to the rear planet row carrier (32) for common rotation; the fifth clutch C5(41) For selectively connecting the input member to the input of the hydraulic transmission (4) for common rotation; the sixth clutch C6(412) For selectively connecting the hydraulic transmission (4) output to the rear planet row sun gear (34) for common rotation; the seventh clutch C7(413) For selectively connecting the hydraulic transmission (4) output to the front planet row sun gear (24) for common rotation;
two independent first outer motor flow passages and two independent 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 two independent 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 includes a first reversing valve S1(45) A second reversing valve S2(47) And a third reversing valve S3(48) And a fourth direction-changing valve S4(410) A second reversing valve S is arranged between the first outer motor flow passage 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 arranged between the first inner motor flow passage and the hydraulic pump (43)4(410) A third reversing valve S is arranged between the second inner motor flow passage and the hydraulic pump (43)3(48)。
3. The mechanical-hydraulic compound transmission device comprising a single-pump-control double-action motor system according to claim 2, wherein the hydraulic transmission mechanism (4) is the single-pump-control double-action motor system, the displacement of one flow passage in the inner motor (49) is set to be V, and when 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, when two flow channels of the outer motor (46) work simultaneously, the displacement of the inner motor (49) is 2CV, wherein C is a displacement coefficient, and C is>1; the total displacement of the hydraulic motor of the hydraulic transmission mechanism (4)Vm＝2V+2CV；VpmaxIndicating the displacement V of the hydraulic pump (43)pMaximum value of (d); a displacement ratio of the hydraulic pump (43):
Figure FDA0003323689200000021
when the first direction valve S1(45) The second reversing valve S is electrified for the right position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the middle position4(410) When the middle position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor flow passage and the second outer motor flow passage;
when the first direction valve S1(45) The second reversing valve S is electrified for the middle position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the middle position4(410) When the middle position is electrified, the hydraulic pump (43) is communicated with the first outer motor flow passage;
when the first direction valve S1(45) The second reversing valve S is electrified for the middle position2(47) The third reversing valve S is electrified for the middle position3(48) The fourth reversing valve S is electrified for the right position4(410) When the right position is electrified, the hydraulic pump (43) is respectively communicated with the first inner motor flow passage and the second inner motor flow passage;
when the first direction valve S1(45) The second reversing valve S is electrified for the middle position2(47) The third reversing valve S is electrified for the middle position3(48) The fourth reversing valve S is electrified for the right position4(410) When the middle position is electrified, the hydraulic pump (43) is communicated with a second inner motor flow passage;
when the first direction valve S1(45) The second reversing valve S is electrified for the right position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the right position4(410) When the right position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor flow passage, the second outer motor flow passage, the first inner motor flow passage and the second inner motor flow passage;
when the first change is madeTo the valve S1(45) The second reversing valve S is electrified for the right position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the right position4(410) When the middle position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor flow passage, the second outer motor flow passage and the second inner motor flow passage;
when the first direction valve S1(45) The second reversing valve S is electrified for the middle position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the right position4(410) When the right position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor flow passage, the first inner motor flow passage and the second inner motor flow passage;
when the first direction valve S1(45) The second reversing valve S is electrified for the middle position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the right position4(410) When the middle position is electrified, the hydraulic pump (43) is respectively communicated with the first outer motor flow passage and the second inner motor flow passage;
when the first direction valve S1(45) The second reversing valve S is electrified for the right position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the left position4(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 direction valve S1(45) The second reversing valve S is electrified for the right position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the left position4(410) When the left position is electrified, the outlet of the hydraulic pump (43) is respectively communicated with the inlet of the first outer motor flow passage, the inlet of the second outer motor flow passage, the outlet of the first inner motor flow passage and the outlet of the second inner motor flow passage, and the outlet of the first outer motor flow passageThe port, the outlet of the second outer motor flow passage, the inlet of the first inner motor flow passage and the inlet of the second inner motor flow passage are respectively communicated with the inlet of a hydraulic pump (43);
when the first direction valve S1(45) The second reversing valve S is electrified for the middle position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the left position4(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 flow passage and the outlet of the second inner motor flow passage, and the outlet of the first outer motor flow passage and the inlet of the second inner motor flow passage are respectively communicated with the inlet of the hydraulic pump (43);
when the first direction valve S1(45) The second reversing valve S is electrified for the middle position2(47) The third reversing valve S is electrified for the right position3(48) The fourth reversing valve S is electrified for the left position4(410) When the left position is electrified, 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).
4. The transmission of claim 3, wherein the first reversing valve S is controlled1(45) A second reversing valve S2(47) And a third reversing valve S3(48) And a fourth direction-changing valve S4(410) The hydraulic transmission mechanism (4) is caused to output the following rotation speed ranges:
and (3) a medium speed regulation mode:
Figure FDA0003323689200000041
low speed regulation mode:
Figure FDA0003323689200000042
high speed regulation mode:
Figure FDA0003323689200000043
in the formula: n ispFor input of the rotational speed of the hydraulic pump, nmThe rotating speed output by the hydraulic motor.
5. The mechatronic transmission of claim 3 including a single pump controlled double acting motor system wherein providing a drive pattern between the input member and the output member by adjusting the displacement ratio of the hydraulic drive mechanism (4) and selectively controlling the engagement of the brake assembly, clutch assembly and control valve assembly comprises: hydraulic, mechanical hydraulic, and mechanical transmissions.
6. The mechatronic transmission comprising a single-pump-controlled double-acting motor system according to claim 5, characterized in that the control valve assembly is selectively controlled and the fifth clutch C is selectively controlled by adjusting the displacement ratio of the hydraulic transmission mechanism (4)5(41) And a first brake B1(27) Engaged by selectively controlling the sixth clutch C6(412) Engaging or second clutch C2(22) And a fourth clutch C4(31) And a seventh clutch C7(413) And engagement, hydraulic drive means providing a plurality of drive means between the input member and the output member.
7. The mechatronic transmission comprising a single-pump-controlled double-acting motor system according to claim 5, characterized in that the control valve assembly is selectively controlled and the fifth clutch C is selectively controlled by adjusting the displacement ratio of the hydraulic transmission mechanism (4)5(41) And a first clutch C1(21) Engaged by selectively controlling the fourth clutch C4(31) And a seventh clutch C7(413) Engaging or second clutch C2(22) And a firstSix clutches C6(412) And engagement, a hydro-mechanical drive means providing a plurality of drive means between the input member and the output member.
8. The transmission of claim 5, wherein the first clutch C is selectively controlled1(21) Engaged by selectively controlling the second clutch C2(22) And a third brake B3(35) Engaging or third clutch C3(23) And a fourth clutch C4(31) Engaging or fourth clutch C4(31) And a second brake B2(28) And a mechanical drive means providing multiple drive means between the input member and the output member.
9. The mechanical-hydraulic compound transmission device comprising a single-pump-control double-acting motor system according to claim 5,
the control valve component is selectively controlled by adjusting the displacement ratio of the hydraulic transmission mechanism (4), so that the forward stepless speed regulation in a low speed regulation mode, a medium speed regulation mode and a high speed regulation mode is realized, and the operation requirement of low speed and large torque is met;
the hydraulic transmission mode is switched to the mechanical-hydraulic transmission mode without power interruption by adjusting the displacement ratio of the hydraulic transmission mechanism (4).
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CN112128338A (en) * 2020-08-03 2020-12-25 江苏大学 Mechanical-hydraulic composite transmission device with participation of double hydraulic transmission mechanisms
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US20090105028A1 (en) * 2005-05-24 2009-04-23 Hikosaburo Hiraki Transmission system
WO2014095317A1 (en) * 2012-12-17 2014-06-26 Linde Hydraulics Gmbh & Co. Kg Power-split gearbox with different operating states
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