WO2011140821A1 - 一种无级变速器 - Google Patents

一种无级变速器 Download PDF

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Publication number
WO2011140821A1
WO2011140821A1 PCT/CN2011/000664 CN2011000664W WO2011140821A1 WO 2011140821 A1 WO2011140821 A1 WO 2011140821A1 CN 2011000664 W CN2011000664 W CN 2011000664W WO 2011140821 A1 WO2011140821 A1 WO 2011140821A1
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WO
WIPO (PCT)
Prior art keywords
flat
active
flat plate
plate
shaft
Prior art date
Application number
PCT/CN2011/000664
Other languages
English (en)
French (fr)
Inventor
谭波
Original Assignee
Tan Bo
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tan Bo filed Critical Tan Bo
Publication of WO2011140821A1 publication Critical patent/WO2011140821A1/zh

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Classifications

    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members

Definitions

  • the invention belongs to the field of continuously variable transmissions.
  • the CVT Since the most successful CVT has been the CVT continuously variable transmission, the CVT is powered by a cone and a steel belt. The limitations of this CVT limit the widespread use of this CVT.
  • the inventive continuously variable transmission is powered by an active flat plate, a passive flat plate and an intermediate flat plate.
  • the object of the present invention is to solve the problem that the conventional continuously variable transmission needs to be additionally equipped with a forward reverse gear mechanism, which causes an increase in cost and loss of power.
  • the intermediate flat disk is respectively The upper half of the active flat plate cooperates with the lower half to realize the conversion of the passive flat disk forward and reverse.
  • the structure of the continuously variable transmission includes: a casing, an active flat plate frame, a movable flat plate, a fixed passive flat plate, a middle flat plate shaft, a middle flat plate adjusting nut, a middle flat plate adjusting screw, a sliding passive flat plate, and a power input.
  • the active flat frame and the housing are fixedly connected or integrated, and the active flat disk and the active flat disk gear are fixedly connected or integrated, and the fixed passive flat plate and the power output shaft are fixedly connected or integrated, and the sliding passive flat is acted by the guiding key.
  • the disc can slide axially on the power output shaft and cannot rotate relative to the power output shaft.
  • the hydraulic cylinder fixed disc is fixed on the power output shaft.
  • the middle flat plate adjusting nut is matched with the middle flat plate adjusting screw
  • the middle flat plate adjusting gear is meshed with the adjusting ring gear
  • the adjusting gear on the adjusting shaft is meshed with the adjusting ring gear
  • the outer circular surface of the intermediate movable frame is The inner circular surface of the casing cooperates, and the intermediate flat disk movable frame slides in the inner circular surface of the casing along the inner circular axis direction of the casing, but the intermediate flat disk movable frame is in the inner circle of the casing under the action of the guiding key The surface cannot be rotated.
  • the power output shaft passes through the hole in the middle flat shaft base.
  • the middle flat plate and the middle flat plate positioning plate are fixedly connected by the intermediate flat plate fixing bolts, and the nut of the middle flat plate fixing bolt is flat in the middle.
  • the middle flat disc adjusting nut angle is in the annular groove formed by the middle flat and middle flat disc positioning disc, and can be freely rotated relative to the middle flat disc, and the middle cross-over gear sleeve is fixed on the active flat disc frame, and the middle cross Rotationally engaged gear is formed.
  • the ends of the active flat shaft and the active flat core have arcs, and the diameter of the arc is slightly larger than the diameter of the intermediate flat plate, which ensures that the displacement of the intermediate flat disc is minimized when it protrudes across the axial end of the active flat disc.
  • the active flat core is inserted in the hole of the active flat shaft.
  • the active flat shaft is in the center hole of the active flat gear, and is rotated with the active flat gear. It can also be rotated by the bearing, and the active flat gear is
  • the active flat plate is fixedly connected or integrated.
  • the sliding passive flat plate, the hydraulic cylinder fixed plate and the oil seal ring form a hydraulic cylinder.
  • the active flat frame special case 1 the outer circular surface of the active flat frame cooperates with the inner circular surface of the casing, and the active flat disk frame slides in the inner circular surface of the casing along the inner circular axis of the casing, but is guided Under the action of the key, the active flat frame cannot rotate in the inner circular surface of the housing.
  • Active flat frame special case 2 The active flat frame is divided into two parts, namely the upper plate of the active flat frame special case and the lower plate of the active flat plate special case 2.
  • the outer circular surface of the active flat frame is also divided into Two parts, the active flat panel special case 2 and the active flat tray special case 2
  • the flat frame fixing bolt is fixedly connected, and the outer circular surface of the active flat plate frame cooperates with the inner circular surface of the casing, and the active flat disk frame slides in the inner circular surface of the casing along the inner circular axis direction of the casing, but The active flat tray cannot be rotated in the inner circular surface of the housing by the guide keys.
  • Active flat frame special case 3 The active flat frame is divided into two parts, namely the upper plate of the active flat frame and the lower plate of the special flat plate special case three, the upper plate and the active flat of the active flat frame special case three
  • the lower plate of the special case 3 is fixedly connected by the active flat frame fixing bolt, and the outer circular surface of the active flat frame cooperates with the inner circular surface of the casing, and the active flat plate frame is located along the inner circular surface of the casing.
  • the inner circular surface slides in the axial direction, but the active flat tray cannot rotate in the inner circular surface of the housing under the action of the guide key.
  • Intermediate flat plate special case 1 The nut of the middle servo plate fixing bolt for fixing the intermediate flat plate and the intermediate flat plate positioning plate is on the intermediate flat plate positioning plate.
  • Intermediate flat plate special case 2 The snap ring on the middle flat plate limits the blocking piece so that it cannot be separated from the intermediate flat plate.
  • the middle flat plate adjusting nut angle can be relatively flat in the middle groove formed by the intermediate flat plate and the blocking piece.
  • the disc rotates freely.
  • Sliding passive flat plate special case 1 There is a pressing block between the sliding passive flat plate and the hydraulic cylinder fixed plate, the hydraulic cylinder movable plate and the stopper.
  • the stopper is fixed on the power output shaft by the fixing pin, and the pressing block is active in the hydraulic cylinder.
  • the disc guide groove and the stopper guide groove are slid with respect to the hydraulic cylinder movable disc guide groove and the stopper guide groove.
  • Active flat shaft special case 1 A long active shaft shaft and an active flat shaft bracket at only one end, with active flat shaft end projections.
  • Active flat shaft special case 2 The outer end of the active flat spindle and the outer end of the active flat shaft are flat with the disk surface of the active flat disc, and there is no active flat shaft end projection. There is no active flat shaft end projection by Ding.
  • Intermediate flat plate adjustment nut angle special case 1 The middle flat plate adjustment nut has only one intermediate flat plate adjustment nut angle, and the middle flat plate adjustment nut angular end has an annular or semi-circular structure around the middle flat plate shaft.
  • the working principle of the continuously variable transmission 1. Power transmission path: The power enters the continuously variable transmission from the power input shaft, drives the power input gear to rotate, and the power is then input from the power input gear to the active flat gear, and then the power is divided into two paths. All the way from the active flat gear to the active flat, the other from the active flat gear through the intermediate bridge gear to the other active flat gear, the power from the active flat gear to the active flat, then the power from the active flat The disk is transferred to the middle flat plate, and the power is divided into two channels from the middle flat plate. One way from the middle flat plate passes the fixed passive flat plate to the power output shaft, and the other from the middle flat plate through the sliding passive flat plate to the power output shaft, and the power passes through.
  • the PTO shaft is transmitted from the power output gear.
  • Principle of transmission power One end of the intermediate flat plate is in contact with the fixed passive flat plate or the sliding passive flat plate, and the other end is in contact with the active flat plate.
  • the hydraulic oil in the hydraulic cylinder has pressure, acting on the sliding passive flat plate, and The sliding passive flat plate is pressed tightly with the intermediate flat plate, and the hydraulic pressure is transmitted through the intermediate flat plate, so that the intermediate flat plate is pressed against the active flat plate, and the intermediate flat plate is pressed against the fixed passive flat plate, and the pressing force is generated. Friction force, the power input shaft drives the power input gear to rotate, and the power input gear drives the active flat disk to rotate.
  • the friction force drives the intermediate flat disk to rotate
  • the middle flat disk drives the fixed passive flat plate and the sliding passive flat.
  • the disk rotates, and the fixed passive plate and the sliding passive plate drive the power output shaft to rotate and output power.
  • 3. Speed ratio adjustment The adjustment shaft drives the adjustment gear to rotate, the adjustment gear drives the adjustment of the ring gear rotation, the adjustment ring gear drives the middle flat plate to adjust the gear rotation, the middle flat plate adjustment gear drives the middle flat plate to adjust the screw rotation, and the middle flat plate adjustment
  • the screw rod drives the middle flat plate adjusting nut up or down, and the middle flat plate adjusting nut drives the middle flat plate to move up and down through the middle flat plate adjusting nut angle, because the speed ratio is contacted by the fixed passive flat plate or the sliding passive flat plate and the intermediate flat plate.
  • the ratio of the diameter of the circle to the diameter of the contact circle between the intermediate plate and the active plate is determined. Therefore, the up and down movement of the intermediate plate realizes the change of the diameter of the contact circle, thereby realizing the change of the speed ratio and achieving the purpose of adjusting the speed ratio.
  • positive and negative adjustment The active flat plate is bounded by the active flat disk axis, divided into the upper half of the active flat plate and the lower half of the active flat plate.
  • the middle flat In the case where the active flat disk rotates in the same direction, the middle flat The power output shaft rotation direction when the disk is in contact with the upper half of the active plate and the power output shaft is rotated when the intermediate plate is in contact with the lower half of the active plate In the opposite direction, the up-and-down movement of the intermediate plate across the axial end of the active flat shaft achieves positive power output shaft Reverse conversion. 5.
  • the middle flat plate straddles the active flat shaft end. When the middle flat plate reaches the active flat shaft end, the hydraulic cylinder is released, and the continuously variable transmission is in an idling state.
  • the active flat shaft end projection continues to travel, and the active flat shaft end extrusion squeezes the intermediate flat plate together with the intermediate flat disk movable frame to move outward, which also increases the distance between the fixed passive flat plate and the sliding passive flat plate, and the sliding passive The distance between the flat plate and the hydraulic cylinder fixed plate is reduced. 6.
  • sliding passive flat plate when the middle flat plate is raised over the axial end of the active flat plate, the hydraulic cylinder is released, and the axial end of the active flat plate is pressed to push the intermediate flat plate to move outward, and the pressing block is pressed.
  • the CVT has the following beneficial effects:
  • Figure 1 is a cross-sectional view showing the structure of the continuously variable transmission in which the intermediate flat plate is in the forward rotation position of the power output shaft;
  • Figure 2 is a cross-sectional view showing the structure of the continuously variable transmission in which the intermediate flat disk is in an idle position of the power output shaft;
  • Figure 3 is a cross-sectional view showing the structure of the continuously variable transmission in which the intermediate flat plate is reversed in the power output shaft;
  • Figure 4 is a cross-sectional view showing the structure of the first embodiment of the active flat tray
  • Figure 5 is a cross-sectional view taken along line A - A of Figure 4.
  • Figure 6 is a structural diagram of a special case of a sliding passive flat plate, in which the sliding passive flat plate is at the innermost position;
  • Figure 7 is a structural view of the sliding passive flat special case 1, the sliding passive flat plate is at the outermost position;
  • Figure 8 is a cross-sectional view of the active flat shelf
  • Figure 9 is a structural diagram of a special case of the active flat frame
  • Figure 10 is a cross-sectional view taken along line A - A of Figure 9;
  • Figure 11 is a structural view of the upper plate of the special flat plate of the active flat frame of the third embodiment of the active flat frame;
  • Figure 12 is a cross-sectional view taken along line A - A of Figure 11;
  • Figure 13 is a structural view of the lower plate of the special flat plate of the active flat frame of the third embodiment of the active flat frame;
  • Figure 14 is a cross-sectional view taken along line A - A of Figure 13;
  • Figure 15 is a structural diagram of a special case 2 of the active flat frame
  • Figure 16 is a cross-sectional view taken along line A - A of Figure 15;
  • Figure 17 is a structural view of the upper plate of the special flat tray special case 2;
  • Figure 18 is a structural view of the lower tray of the special flat tray special case 2;
  • Figure 19 is a structural view of a special case 1 of the active flat frame
  • Figure 20 is a cross-sectional view taken along line A - A of Figure 19;
  • Figure 21 is a structural view of the intermediate flat shaft base
  • Figure 22 is a structural view of the adjustment ring gear
  • Figure 23 is a partial cross-sectional view of the continuously variable transmission in which the intermediate flat disk is in a position where the power output shaft is reversed;
  • Figure 24 is a partial cross-sectional view of the continuously variable transmission, the intermediate flat disk is in a forward rotation position of the power output shaft;
  • Figure 25 is a cross-sectional view taken along line A - A of Figure 2;
  • Figure 26 is a structural view of a special example of the active flat shaft
  • Figure 27 is a structural view of the second embodiment of the active flat shaft
  • Figure 28 is a right side view of Figure 21; ' Figure 29 is a cross-sectional view taken along line B---B of Figure 2;
  • Figure 30 is a cross-sectional view taken along line A - A of Figure 3;
  • Figure 31 is a structural view of the intermediate flat plate adjusting nut
  • Figure 32 is a right side view of Figure 31;
  • Figure 33 is a structural view of the intermediate flat disc and the intermediate flat disc positioning disc assembly in the middle flat special case 1;
  • Figure 34 is a structural view of the intermediate flat disk and the middle servo flat disk positioning disk assembly
  • Figure 35 is a structural view of a special example of the intermediate flat disc adjusting nut angle
  • Figure 36 is a cross-sectional view taken along line A - A of Figure 35;
  • Figure 37 is a positional distribution diagram of three pressurizing blocks during operation
  • Figure 38 is a cross-sectional view taken along line A - A of Figure 7;
  • Figure 39 is a structural diagram of a special case of the intermediate flat disk
  • Figure 40 is a cross-sectional view taken along line CTM of Figure 2;
  • the active flat tray 2 and the housing 1 are fixedly connected or integrated, and the active flat disc 3 and the active flat disc gear 26 are fixedly connected or integrated, and the fixed flat disc 4 and the power output shaft 7 are fixedly connected.
  • the sliding passive flat plate 9 can slide axially on the power output shaft 17, and cannot rotate relative to the power output shaft 17, and the hydraulic cylinder fixed disk 20 is fixed to the power output shaft 17.
  • a set of intermediate flat discs 13 are sandwiched between the active flat disc 3 and the fixed passive flat disc 4 by frictional force transfer, and the other set of intermediate flat discs 13 are sandwiched between the active flat disc 3 and the sliding passive flat disc 9
  • the power is transferred between the frictional forces, and the intermediate flat plate adjusting nut 6 is matched with the intermediate flat plate adjusting screw 8, and the intermediate flat plate adjusting gear 12 is engaged with the adjusting ring gear 33, the adjusting gear 32 on the adjusting shaft 31 is engaged with the adjusting ring gear 33, and the outer circular surface of the intermediate flat movable frame 25 is engaged with the inner circular surface of the casing 1, and the intermediate flat movable frame 25 is
  • the inner circular surface of the casing 1 slides in the axial direction of the inner circular surface of the casing 1, but the intermediate flat movable frame 25 cannot be rotated in the inner circular surface of the casing 1 by the guide key 21, and the power output shaft 17 Passing through the hole of the intermediate flat shaft base 15, the intermediate flat plate 13 and the intermediate flat plate
  • the intermediate flat plate adjusting nut angle 34 is freely rotatable relative to the intermediate flat plate 13 in the annular groove formed by the intermediate flat plate 13 and the intermediate flat disk positioning plate 14, and the intermediate bridge gear sleeve 24 is fixed on the active flat plate frame 2. And forming a rotational fit with the intermediate bridge gear 29, the sliding passive flat plate 9, the hydraulic cylinder fixed disk 20 and the oil seal ring 23 constitute a hydraulic cylinder 36.
  • the intermediate flat plate 13 is at the lowermost end, and the rotational speed of the power input shaft 11 is constant. In this case, the power output shaft 17 is the fastest forward rotation.
  • the intermediate flat plate 13 is on the active flat shaft end projection 49, at which point the hydraulic cylinder 36 has been relieved.
  • the intermediate flat plate 13 is at the uppermost end.
  • the dynamic output shaft 17 is the fastest reverse when the rotational speed of the power input shaft 11 is constant.
  • the outer circular surface of the active flat frame 2 cooperates with the inner circular surface of the casing 1, and the active flat plate 2 is in the inner circular surface of the casing 1.
  • the inner circular surface of the casing 1 slides in the axial direction, but the active flat tray 2 cannot be rotated in the inner circular surface of the casing 1 by the guide key 21.
  • the distribution relationship of the three intermediate flat disc shafts 5 and the three intermediate flat discs 13 may also be two or more intermediate flat disc shafts 5 and two or more intermediate flat discs. 13.
  • the structural drawing of the special case 1 of the sliding passive flat plate 9 is shown, and the sliding passive flat plate 9 is in the most inner position.
  • the structural drawing of the special case 1 of the sliding passive flat plate 9 is shown, and the sliding passive flat plate 9 is at the outermost position.
  • the active flat shelf 2 is integral with the housing 1.
  • the active flat tray 2 is a special case three, and the active flat tray 2 is divided into two parts, namely, the upper tray 44 of the active flat tray special case 3 and the active flat disk.
  • the lower plate 45 of the special case three, the upper plate 44 of the special flat frame special case and the lower plate 45 of the active flat frame special case three are fixedly connected by the active flat frame fixing bolt 46, and the outer circular surface of the active flat frame 2 is
  • the inner circular surface of the housing 1 is fitted, and the active flat tray 2 slides in the inner circular surface of the housing 1 along the inner circular axis of the housing 1, but the active flat tray 2 is in the shell under the action of the guide key 21.
  • the inner circular surface of the body 1 cannot be rotated.
  • the active flat tray 2 is divided into two parts, namely, the upper tray 47 of the active flat tray special case 2 and the active flat tray special case 2
  • the lower disc 43, the outer circular surface of the active flat tray 2 is also divided into two active flat trays.
  • the upper tray 47 of the special case 2 and the lower tray 43 of the active flat tray special case 2 are fixedly connected by the active flat frame fixing bolts 46.
  • the outer circular surface of the active flat tray 2 cooperates with the inner circular surface of the housing 1, and the active flat tray 2 slides in the inner circular surface of the housing 1 along the inner circular axis of the housing 1, but at the guide key Under the action of 21, the active flat tray 2 cannot rotate in the inner circular surface of the housing 1.
  • the first embodiment of the active flat tray 2 the outer circular surface of the active flat tray 2 cooperates with the inner circular surface of the housing 1, and the active flat tray 2 is in the inner circular surface of the housing 1.
  • the inner circular surface of the casing 1 slides in the axial direction, but the active flat tray 2 cannot be rotated in the inner circular surface of the casing 1 by the guide key 21.
  • the intermediate flat shaft 5 has an intermediate flat shaft guide groove 7, the intermediate portion has an intermediate flat shaft base 15, and the plurality of intermediate flat shafts 5 are joined together by the intermediate flat shaft base 15. .
  • the ends of the active flat shaft 27 and the active flat spindle 28 have arcs which are slightly larger in diameter than the intermediate flats 13, ensuring that the intermediate flat 13 is over the active flat When the shaft end is raised 49, the displacement is minimal.
  • the active flat spindle 28 is inserted into the hole of the active flat shaft 27, and the active flat shaft 27 is in the center hole of the active flat gear 26, and is rotated and cooperated with the active flat gear 26, or is rotated by the bearing to actively
  • the flat disc gear 26 is fixedly coupled or integral with the active flat disc 13.
  • the active flat shaft 27 special case one, a long active main flat spindle 28 and an active flat shaft bracket 50 at only one end, has an active flat shaft end projection 49.
  • the active flat shaft 27 special case 2 the outer end of the active flat core shaft 28 and the outer end of the active flat shaft 27 are flat with the disk surface of the active flat disc 3, and there is no active flat shaft end projection 49, since there is no The active flat shaft end projection 49, when the intermediate flat plate 13 crosses the axial end of the active flat shaft 27, the intermediate flat movable frame 25 does not move, and the sliding passive flat plate 9 does not move.
  • both the intermediate flat disc adjusting nut 6 and the intermediate flat disc adjusting screw 8 are in the bore of the intermediate flat shaft 5, and the intermediate flat disc adjusting nut angle 34 extends from the intermediate flat shaft guiding groove 7 Flat plate shaft 5.
  • the intermediate flat plate adjusting nut 6 and the intermediate flat plate adjusting nut angle 34 are integral.
  • the intermediate flat plate 13 is a special case in which the nuts of the intermediate flat plate fixing bolts 18 for fixing the intermediate flat plate 13 and the intermediate flat plate positioning plate 14 are on the intermediate flat plate positioning plate 14.
  • the intermediate flat plate 13 and the intermediate flat disk positioning plate 14 are fixedly connected by the intermediate flat plate fixing bolts 18, and the nuts of the intermediate flat plate fixing bolts 18 are on the intermediate flat plate 13, and the intermediate flat plate 13 has edges. Chamfering.
  • the intermediate flat plate adjusts the nut angle 34 in the first example
  • the intermediate flat plate adjusting nut 6 has only one intermediate flat plate adjusting nut angle 34
  • the intermediate flat plate adjusting nut angle 34 has an end around the intermediate flat plate shaft. 5 annular or semi-circular structure.
  • the intermediate plate 13 is in the second embodiment.
  • the snap ring 40 on the intermediate plate 13 limits the flap 48 from the intermediate plate 13, and the intermediate plate adjusts the nut angle 34 in the intermediate plate 13
  • the annular groove formed by the spacer 48 can be freely rotated relative to the intermediate flat plate B.
  • the meshing relationship of the power input gear 10, the active sheave gear 26 and the intermediate bridge gear 29 can be seen in FIG.
  • the working principle of the continuously variable transmission 1.
  • Power transmission path The power enters the continuously variable transmission from the power input shaft 11 to drive the power input gear 10 to rotate, and the power is further input from the power input gear 10 to the active level.
  • the output shaft 17 and the other path pass from the intermediate flat disk 13 to the power output shaft 17 by sliding the passive flat disk 9, and the power is transmitted from the power output gear 16 through the power output shaft 17.
  • One end of the intermediate flat plate 13 is in contact with the fixed passive flat plate 4 or the sliding passive flat plate 9, and the other end is in contact with the active flat plate 3, and the liquid in the hydraulic cylinder 36
  • the pressure oil has a pressure acting on the sliding passive flat plate 9, and the sliding passive flat plate 9 is pressed against the intermediate flat plate 13, while the hydraulic pressure is transmitted through the intermediate flat plate 13, so that the intermediate flat plate 13 and the active flat plate 3 are pressed. Tightly, the intermediate flat plate 13 is pressed against the fixed passive flat plate 4, the pressing force generates frictional force, the power input shaft 11 drives the power input gear 10 to rotate, and the power input gear 10 drives the active flat disk 3 to rotate.
  • the friction force drives the intermediate flat disc 13 to rotate, and the intermediate flat disc 13 drives the fixed passive flat disc 4 and the sliding passive flat disc 9 to rotate, and the passive flat disc 4 and the sliding passive flat disc 9 are fixed to drive the power output.
  • the shaft 16 rotates to output power.
  • the adjustment shaft 31 drives the adjustment gear 32 to rotate, the adjustment gear 32 drives the adjustment ring gear 33 to rotate, the adjustment ring gear 33 drives the intermediate plate adjustment gear 12 to rotate, and the intermediate plate adjustment gear 12 drives the intermediate plate adjustment wire
  • the bar 8 rotates, the middle flat plate adjusts the screw rod 8 to drive the middle flat plate adjusting nut 6 up or down, and the middle flat plate adjusting nut 6 drives the intermediate flat plate 13 to move up and down through the intermediate flat plate adjusting nut angle 34, since the speed ratio is fixed
  • the ratio of the contact circle diameter of the passive flat plate 4 or the sliding passive plate 9 and the intermediate flat plate 13 to the diameter of the contact circle of the intermediate plate 13 and the active plate 3 is determined, so that the up and down movement of the intermediate plate 13 achieves the above contact circle diameter.
  • the change of the speed ratio is achieved, and the purpose of adjusting the speed ratio is achieved. 4.
  • the adjustment of the positive and negative rotation The active flat disk 3 is divided into the upper half of the active flat disk 3 by the active flat disk axis 27. And the lower half of the active flat plate 3, in the case where the rotational direction of the active flat disk 3 is uniform, the rotational direction of the power output shaft 17 and the intermediate flat disk 13 when the intermediate flat disk 13 is in contact with the upper half of the active flat disk 3 Active flat 3 17 opposite to the rotational direction of the output shaft when in contact with the lower half, so the intermediate flat disc shaft 13 moves up and down across the flat disk of the active shaft 27 to achieve the reversible conversion of the output shaft 17. 5.
  • the process of the intermediate flat plate 13 spanning the active flat shaft end projection 49 When the intermediate flat plate 13 reaches the active flat shaft end projection 49, the hydraulic cylinder 36 is released from pressure, and the continuously variable transmission is idling.
  • the intermediate flat disk 13 begins to travel along the active flat shaft end projection 49, while the active flat shaft end projection 49 presses the intermediate flat disk 13 together with the intermediate flat movable frame 25 to move outward, thereby also fixing the passive flat disk 4
  • the distance from the sliding passive flat plate 9 is increased, and the distance between the sliding passive flat plate 9 and the hydraulic cylinder fixed plate 20 is reduced. 6.
  • the active flat shaft end projection 49 presses the intermediate flat plate 13 to move, and also presses the active flat tray 2 to move. 8.
  • the active flat shaft special case two since the active flat shaft end projection 49 is absent, when the middle flat 13 is crossed the axial end of the active flat shaft 27, the intermediate flat movable frame 25 does not move.
  • the sliding passive flat plate 9 also does not move.

Description

—种无级变速器
技术领域
本发明属于无级变速器领域。
背景技术
由于以前最成功的无级变速器是 CVT无级变速器，这种无级变速器是靠锥盘与钢带传动 动力， 这种无级变速器的局限性限制了这种无级变速器的广泛使用， 而本发明的无级变速器 是靠主动平盘、 被动平盘和中间平盘来传动动力的。
发明内容
本发明的目的是为了解决以前的无级变速器需要另外加装前进倒退档机构， 造成成本的 升高和动力的损耗的问题， 在主动平盘转动方向一致的情况下， 通过中间平盘分别与主动平 盘的上半部与和下半部的配合来实现被动平盘正反转的转换。
该无级变速器的结构包括： 壳体、主动平盘架、 主动平盘、 固定被动平盘、 中间平盘轴、 中间平盘调节螺母、 中间平盘调节丝杠、 滑动被动平盘、动力输入齿轮、 动力输入轴、 中间 平盘调节齿轮、 中间平盘、动力输出齿轮、 动力输出轴、 液压缸周定盘、 液压油路、 中间平 盘活动架、 主动平盘齿轮、 主动平盘轴、 主动平盘芯轴、 中间过桥齿轮、 调节轴、 调节齿轮、 调节齿圈、 液压缸等。 主动平盘架和壳体固定连接或是一体， 主动平盘和主动平盘齿轮固定 连接或是一体， 固定被动平盘和动力输出轴固定连接或是一体， 由于导向键的作用， 滑动被 动平盘可以在动力输出轴上轴向滑动， 不能相对动力输出轴转动， 液压缸固定盘固定在动力 输出轴上。 工作时， 一组中间平盘夹在主动平盘与固定被动平盘之间靠摩擦力转递动力， 另 一组中间平盘夹在主动平盘与滑动被动平盘之间靠摩擦力转递动力， 中间平盘调节螺母与中 间平盘调节丝杠配合， 中间平盘调节齿轮与调节齿圈啮合， 调节轴上的调节齿轮与调节齿圈 啮合， 中间^ ^盘活动架的外圆面与壳体的内圆面配合， 中间平盘活动架在壳体的内圆面中沿 壳体的内圆面轴线方向滑动， 但在导向键的作用下中间平盘活动架在壳体的内圆面中不能转 动， 动力输出轴从中间平盘轴底座的孔中穿过， 中间平盘和中间平盘定位盘由中间平盘固定 螺栓固定连接， 而且中间平盘固定螺栓的螺帽在中间平盘上， 中间平盘调节螺母角在中间平 和中间平盘定位盘所形成的环形槽中， 可以相对中间平盘自由转动， 中间过桥齿轮轴套固 定在主动平盘架上， 并与中间过桥齿轮形成转动配合。 主动平盘轴和主动平盘芯轴的端头都 有圆弧， 圆弧直径比中间平盘直径略大， 保证了中间平盘在跨过主动平盘轴端凸起时， 位移 最小。 主动平盘芯轴插在主动平盘轴的孔中， 主动平盘轴在主动平盘齿轮中心孔中， 与主动 平盘齿轮做转动配合， 也可以通过轴承做转动配合， 主动平盘齿轮与主动平盘固定连接， 也 可以是一体。 滑动被动平盘、 液压缸固定盘和油封环组成了液压缸。 主动平盘架特例一： 主 动平盘架的外圆面与壳体的内圆面配合， 主动平盘架在壳体的内圆面中沿壳体的内圆面轴线 方向滑动，但在导向键的作用下主动平盘架在壳体的内圆面中不能转动。主动平盘架特例二: 主动平盘架被分为两部分， 即主动平盘架特例二的上盘和主动平盘架特例二的下盘， 主动平 盘架的外圆面也被分为两部分， 主动平盘架特例二的上盘和主动平盘架特例二的下盘由主动 平盘架固定螺栓固定连接， 主动平盘架的外圆面与壳体的内圆面配合， 主动平盘架在壳体的 内圆面中沿壳体的内圆面轴线方向滑动， 但在导向键的作用下主动平盘架在壳体的内圆面中 不能转动。 主动平盘架特例三： 主动平盘架被分为两部分， 即主动平盘架特例三的上盘和主 动平盘架特例三的下盘， 主动平盘架特例三的上盘和主动平盘架特例三的下盘由主动平盘架 固定螺栓固定连接， 主动平盘架的外圆面与壳体的内圆面配合， 主动平盘架在壳体的内圆面 中沿壳体的内圆面轴线方向滑动， 但在导向键的作用下主动平盘架在壳体的内圆面中不能转 动。 中间平盘特例一： 固定中间平盘和中间平盘定位盘的中伺平盘固定螺栓的螺帽在中间平 盘定位盘上。 中间平盘特例二： 在中间平盘上的卡环限制了挡片， 使之不能脱离中间平盘， 中间平盘调节螺母角在中间平盘和挡片所形成的环形槽中可以相对中间平盘自由转动。 滑动 被动平盘特例一： 滑动被动平盘和液压缸固定盘之间有加压块、 液压缸活动盘和挡块， 挡块 由固定销固定在动力输出轴上， 加压块在液压缸活动盘导向槽和挡块导向槽中， 并相对液压 缸活动盘导向槽和挡块导向槽滑动。 主动平盘轴特例一： 一根通长的主动平盘轴和只在一端 的主动平盘轴托架， 具有主动平盘轴端凸起。 主动平盘轴特例二： 主动平盘芯轴外端和主动 平盘轴外端与主动平盘的盘面平， 没有主动平盘轴端凸起。 由丁没有了主动平盘轴端凸起， 当中间平盘跨过主动平盘轴的轴端时， 中间平盘活动架并不移动，滑动被动平盘也并不移动。 中间平盘调节螺母角特例一： 中间平盘调节螺母上只有一个中间平盘调节螺母角， 中间平盘 调节螺母角端部有围绕中间平盘轴的环形或半圆形结构。
该无级变速器的工作原理： 1.动力传递路径： 动力从动力输入轴进入该种无级变速器， 带动动力输入齿轮转动， 动力再由动力输入齿轮到主动平盘齿轮， 然后动力分两路， 一路从 主动平盘齿轮直接到主动平盘， 另一路从主动平盘齿轮通过中间过桥齿轮再到另外的主动平 盘齿轮， 动力再从主动平盘齿轮到主动平盘， 然后动力从主动平盘到中间平盘， 动力从中间 平盘再分两路， 一路从中间平盘通过固定被动平盘到动力输出轴， 另一路从中间平盘通过滑 动被动平盘到动力输出轴， 动力再通过动力输出轴从动力输出齿轮传出。 2.传动动力的原理: 中间平盘一端与固定被动平盘或滑动被动平盘接触， 另一端与主动平盘接触， 液压缸中的液 压油具有压力， 作用在滑动被动平盘上， 并使滑动被动平盘与中间平盘压紧， 同时通过中间 平盘传递液压力， 使中间平盘与主动平盘压紧， 还使中间平盘与固定被动平盘压紧， 上述压 紧力产生了摩擦力， 动力输入轴带动动力输入齿轮转动， 动力输入齿轮带动主动平盘转动， 在主动平盘转动时， 该摩擦力带动中间平盘转动， 中间平盘再带动固定被动平盘和滑动被动 平盘转动， 固定被动平盘和滑动被动平盘再带动动力输出轴转动， 输出动力。 3.速比调节- 调节轴带动调节齿轮转动， 调节齿轮带动调节齿圈转动， 调节齿圈带动中间平盘调节齿轮转 动， 中间平盘调节齿轮带动中间平盘调节丝杠转动， 中间平盘调节丝杠带动中间平盘调节螺 母上行或下行， 中间平盘调节螺母通过中间平盘调节螺母角带动中间平盘上下移动， 由于速 比是由固定被动平盘或滑动被动平盘和中间平盘接触圆直径与中间平盘和主动平盘接触圆直 径的比值决定的， 因此中间平盘的上下移动实现了上述接触圆直径的变化， 也就实现了速比 的变化， 达到了调节速比的目的， 4正反转的调节： 主动平盘以主动平盘轴为界， 分为主动 平盘的上半部和主动平盘的下半部， 在主动平盘转动方向一致的情况下， 中间平盘与主动平 盘的上半部接触时的动力输出轴转动方向和中间平盘与主动平盘的下半部接触时的动力输出 轴转动方向相反， 因此中间平盘跨过主动平盘轴的轴端的上下移动就实现了动力输出轴的正 反转的转换。 5.中间平盘跨过主动平盘轴端凸起过程： 当中间平盘上行到达主动平盘轴端凸 起时， 液压缸泄压， 该种无级变速器处于空转状态， 中间平盘开始沿着主动平盘轴端凸起继 续行进， 同时主动平盘轴端凸起挤压中间平盘连同中间平盘活动架外移， 也使固定被动平盘 和滑动被动平盘距离增大， 滑动被动平盘和液压缸固定盘距离缩小。 6.滑动被动平盘特例一 中， 当中间平盘跨过主动平盘轴端凸起时， 液压缸泄压， 主动平盘轴端凸起挤压中间平盘外 移， 挤压加压块推动液压缸活动盘外移； 当中间平盘跨过主动平盘轴端凸起后， 液压推动液 压缸活动盘、 加压块和滑动被动平盘向里移动。 7.在主动平盘架 例一、主动平盘架特例二 和主动平盘架特例三中， 当中间平盘跨过主动平盘轴端凸起时， 液压缸泄压， 主动平盘轴端 凸起挤压中间平盘移动， 也挤压主动平盘架移动。 8.在主动平盘轴特例二中， 由于没有了主 动平盘轴端凸起， 当中间平盘跨过主动平盘轴的轴端时， 中间平盘活动架并不移动， 滑动被 动平盘也并不移动。
由于采用了本发明结构， 使该种无级变速器具有以下有益效果是：
1. 动力传输的功率和扭矩大。
2. 功率损耗小。
3. 具有正反转的功能。
附图说明
下面对附图进行说明：
图 1是该种无级变速器结构的剖视图， 中间平盘在动力输出轴正转位置；
图 2是该种无级变速器结构的剖视图， 中间平盘在动力输出轴空转位置；
图 3是该种无级变速器结构的剖视图， 中间平盘在动力输出轴反转位置；
图 4是主动平盘架特例一的结构的剖视图；
图 5是图 4的 A— A剖视图；
图 6是滑动被动平盘特例一的结构图， 滑动被动平盘在最靠里的位置；
图 7是滑动被动平盘特例一的结构图， 滑动被动平盘在最靠外的位置；
图 8是主动平盘架的剖视图；
图 9是主动平盘架特例三的结构图；
图 10是图 9的 A— A剖视图；
图 11是主动平盘架特例三的主动平盘架特例三的上盘的结构图；
图 12是图 11的 A— A剖视图；
图 13是主动平盘架特例三的主动平盘架特例三的下盘的结构图；
图 14是图 13的 A— A剖视图；
图 15是主动平盘架特例二的结构图；
图 16是图 15的 A— A剖视图；
图 17是主动平盘架特例二的上盘的结构图；
图 18是主动平盘架特例二的下盘的结构图；
图 19是主动平盘架特例一的结构图；
图 20是图 19的 A— A剖视图；
图 21是中间平盘轴底座的结构图； 图 22是调节齿圈的结构图;
图 23是该种无级变速器的局部剖视图， 中间平盘在动力输出轴反转的位置上； 图 24是该种无级变速器的局部剖视图， 中间平盘在动力输出轴正转的位置上； 图 25是图 2的 A— A剖视图；
图 26是主动平盘轴特例一的结构图；
图 27是主动平盘轴特例二的结构图；
图 28是图 21的右视图； ' 图 29是图 2的 B---B剖视图；
图 30是图 3的 A— A剖视图；
图 31是中间平盘调节螺母的结构图；
图 32是图 31的右视图；
图 33是中间平盘特例一中， 中间平盘和中间平盘定位盘组件的结构图；
图 34是中间平盘和中伺平盘定位盘组件的结构图；
图 35是中间平盘调节螺母角特例一的结构图；
图 36是图 35的 A— A剖视图；
图 37是三个加压块在工作时的位置分布图；
图 38是图 7的 A— A剖视图；
图 39是中间平盘特例二的结构图；
图 40是图 2的 C™ 剖视图；
在各图中： 1—壳体； 2—主动平盘架； 3—主动平盘； 4一固定被动平盘； 5—中间平盘轴； 6—中间平盘调节螺母； 7—中间平盘轴导向槽； 8—中间平盘调节丝杠； ^一滑动被动平盘； 10~动力输入齿轮； 11一动力输入轴； 12—中间平盘调节齿轮； 13—中间平盘； 14一中间平 盘定位盘； 15—中间平盘轴底座； 16—动力输出齿轮； 17—动力输出轴； 18—中间平盘固定 螺栓； 1 -轴承； 20" -液压缸固定盘； 21—导向键； 22—液压油路； 23—油封环； 24—中间 过桥齿轮轴套； 25—中间平盘活动架； 26—主动平盘齿轮； 27—主动平盘轴； 28—主动平盘 芯轴； 29 "—中间过桥齿轮； 30~主动平盘轴固定螺栓， 31—调节轴； 32—调节齿轮； 33—调 节齿圈； 34—中间平盘调节螺母角； 35—固定销； 36~液压缸; 37—加压块； 38—液压缸活 动盘； 39" -挡块； 40~卡环； 41一液压缸活动盘导向槽； 42—挡块导向槽； 43—主动平盘架 特例二的下盘； 44一主动平盘架特例三的上盘； 45—主动平盘架特例三的下盘； 46—主动平 盘架固定螺栓； 47—主动平盘架特例二的上盘； 48—挡片； 49~主动平盘轴端凸起； 50~—主 动平盘轴托架。
具体实施方式
在图 1中可见， 主动平盘架 2和壳体 1固定连接或是一体， 主动平盘 3和主动平盘齿轮 26固定连接或是一体， 固定被动平盘 4和动力输出轴】7同定连接或是一体， 由于导向键 21 的作用， 滑动被动平盘 9可以在动力输出轴 17上轴向滑动， 不能相对动力输出轴 17转动， 液压缸固定盘 20固定在动力输出轴 17上。工作时，一组中间平盘 13夹在主动平盘 3与固定 被动平盘 4之间靠摩擦力转递动力，另一组中伺平盘 13夹在主动平盘 3与滑动被动平盘 9之 间靠摩擦力转递动力， 中间平盘调节螺母 6与中间平盘调节丝杠 8配合， 中间平盘调节齿轮 12与调节齿圈 33啮合，调节轴 31上的调节齿轮 32与调节齿圈 33啮合， 中间平盘活动架 25 的外圆面与壳体 1的内圆面配合，中间平盘活动架 25在壳体 1的内圆面中沿壳体 1的内圆面 轴线方向滑动， 但在导向键 21的作用下中间平盘活动架 25在壳体 1的内圆面中不能转动， 动力输出轴 17从中间平盘轴底座 15的孔中穿过， 中间平盘 13和中间平盘定位盘 14由中间 平盘固定螺栓 18固定连接， 而且中间平盘固定螺栓 18的螺帽在中间平盘上， 中间平盘调节 螺母角 34在中间平盘 13和中间平盘定位盘 14所形成的环形槽中， 可以相对中间平盘 13自 由转动， 中间过桥齿轮轴套 24固定在主动平盘架 2上，并与中间过桥齿轮 29形成转动配合， 滑动被动平盘 9、液压缸固定盘 20和油封环 23组成了液压缸 36ο此时中间平盘 13在最下端， 在动力输入轴 11转速一定的情况下， 动力输出轴 17是正转最快。
在图 2中可见， 中间平盘 13在主动平盘轴端凸起 49上， 此时液压缸 36已泄压。
在图 3中可见， 中间平盘 13在最上端， 此时， 在动力输入轴 11转速一定的情况下， 动 力输出轴 17是反转最快。
在图 4中可见， 主动平盘架 2特例一中， 主动平盘架 2的外圆面与壳体 1的内圆面配合, 主动平 ¾：架 2在壳体 1的内圆面中沿壳体 1的内圆面轴线方向滑动，但在导向键 21的作用下 主动平盘架 2在壳体 1的内圆面中不能转动。
在图 5中可见，三个中间平盘轴 5和三个中间平盘 13的分布关系， 也可以是两个或三个 以上的中间平盘轴 5和两个或三个以上的中间平盘 13。
在图 6中可见， 滑动被动平盘 9特例一的结构图， 滑动被动平盘 9在最靠里的位置。 在图 7中可见， 滑动被动平盘 9特例一的结构图， 滑动被动平盘 9在最靠外的位置。 在图 8中可见， 主动平盘架 2与壳体 1是一体的。
在图 9、 10、 11、 12、 13、 14中可见， 主动平盘架 2特例三， 主动平盘架 2被分为两部 分， 即主动平盘架特例三的上盘 44和主动平盘架特例三的下盘 45， 主动平盘架特例三的上 盘 44和主动平盘架特例三的下盘 45由主动平盘架固定螺栓 46固定连接，主动平盘架 2的外 圆面与壳体 1的内圆面配合， 主动平盘架 2在壳体 1的内圆面中沿壳体 1的内圆面轴线方向 滑动， 但在导向键 21的作用下主动平盘架 2在壳体 1的内圆面中不能转动。
在图 15、 16、 17、 18中可见， 主动平盘架 2特例二， 主动平盘架 2被分为两部分， 即主 动平盘架特例二的上盘 47和主动平盘架特例二的下盘 43， 主动平盘架 2的外圆面也被分为 两部 主动平盘架特例二的上盘 47和主动平盘架特例二的下盘 43由主动平盘架固定螺栓 46固定连接， 主动平盘架 2的外圆面与壳体 1的内圆面配合， 主动平盘架 2在壳体 1的内圆 面中沿壳体 1的内圆面轴线方向滑动，但在导向键 21的作用下主动平盘架 2在壳体 1的内圆 面中不能转动。
在图 19、 20中可见， 主动平盘架 2特例一， 主动平盘架 2的外圆面与壳体 1的内圆面配 合，主动平盘架 2在壳体 1的内圆面中沿壳体 1的内圆面轴线方向滑动，但在导向键 21的作 用下主动平盘架 2在壳体 1的内圆面中不能转动。
在图 21、 28中可见， 中间平盘轴 5上有中间平盘轴导向槽 7， 中间部位有中间平盘轴底 座 15, 多个中间平盘轴 5靠中间平盘轴底座 15结合在一起。
在图 22中可见， 调节齿圈 33的结构。
在图 23中可见， 动力输出轴 17反转时的中间平盘 13的状态。 在图 24中可见， 动力输出轴 17正转时的中间平盘 13的状态。
在图 25中可见，主动平盘轴 27和主动平盘芯轴 28的端头都有圆弧， 圆弧直径比中间平 盘 13直径略大，保证了中间平盘 13在跨过主动平盘轴端凸起 49时，位移最小。主动平盘芯 轴 28插在主动平盘轴 27的孔中， 主动平盘轴 27在主动平盘齿轮 26中心孔中， 与主动平盘 齿轮 26做转动配合，或通过轴承做转动配合，主动平盘齿轮 26与主动平盘 13固定连接或是 一体。
在图 26中可见， 主动平盘轴 27特例一，一根通长的主动平盘芯轴 28和只在一端的主动 平盘轴托架 50, 具有主动平盘轴端凸起 49。
在图 27中可见， 主动平盘轴 27特例二， 主动平 芯轴 28外端和主动平盘轴 27外端与 主动平盘 3的盘面平， 没有主动平盘轴端凸起 49， 由于没有了主动平盘轴端凸起 49， 当中间 平盘 13跨过主动平盘轴 27的轴端时， 中间平盘活动架 25并不移动，滑动被动平盘 9也并不 移动。
在图 29中可见， 动力输出轴 17、 动力输入轴 11和调节轴 31的位置关系。
在图 30中可见， 中间平盘调节螺母 6和中间平盘调节丝杠 8都在中间平盘轴 5的孔中， 中间平盘调节螺母角 34从中间平盘轴导向槽 7里伸出中间平盘轴 5。
在图 31、 32中可见， 中间平盘调节螺母 6和中间平盘调节螺母角 34是一体的。
在图 33中可见， 中间平盘 13特例一， 固定中间平盘 13和中间平盘定位盘 14的中间平 盘固定螺栓 18的螺帽在中间平盘定位盘 14上。
. 在图 34中可见， 中间平盘 13和中间平盘定位盘 14用中间平盘固定螺栓 18固定连接， 中间平盘固定螺栓 18的螺帽在中间平盘 13上， 中间平盘 13边缘有倒角。
在图 35、 36中可见， 中间平盘调节螺母角 34特例一， 中间平盘调节螺母 6上只有一个 中间平盘调节螺母角 34， 中间平盘调节螺母角 34端部有围绕中间平盘轴 5的环形或半圆形 结构。
在图 37中可见， 在滑动被动平盘 9特例一中， 三块加压块 37在工作时的位置关系。 在图 38中可见， 在滑动被动平盘 9特例一中， 液压缸活动盘导向槽 41和挡块导向槽 42 的位置关系。
在图 39中可见， 中间平盘 13特例二， 在中间平盘 13上的卡环 40限制了挡片 48, 使之 不能脱离中间平盘 13, 中间平盘调节螺母角 34在中间平盘 13和挡片 48所形成的环形槽中 可以相对中间平盘 B自由转动。
在图 40中可见， 动力输入齿轮 10、 主动平盘齿轮 26和中间过桥齿轮 29的啮合关系。 在各图中可见， 该无级变速器的工作原理： 1.动力传递路径： 动力从动力输入轴 11进入 该种无级变速器，带动动力输入齿轮 10转动，动力再由动力输入齿轮 10到主动平盘齿轮 26, 然后动力分两路， 一路从主动平盘齿轮 26直接到主动平盘 3， 另一路从主动平盘齿轮 26通 过中间过桥齿轮 29再到另外的主动平盘齿轮 26, 动力再从主动平盘齿轮 26到主动平盘 3, 然后动力从主动平盘 3到中间平盘 13， 动力从中间平盘 13再分两路，一路从中间平盘 13通 过固定被动平盘 4到动力输出轴 17， 另一路从中间平盘 13通过滑动被动平盘 9到动力输出 轴 17, 动力再通过动力输出轴 17从动力输出齿轮 16传出。 2.传动动力的原理： 中间平盘 13 一端与固定被动平盘 4或滑动被动平盘 9接触，另一端与主动平盘 3接触，液压缸 36中的液 压油具有压力，作用在滑动被动平盘 9上， 并使滑动被动平盘 9与中间平盘 13压紧， 同时通 过中间平盘 13传递液压力，使中间平盘 13与主动平盘 3压紧，还使中间平盘 13与固定被动 平盘 4压紧， 上述压紧力产生了摩擦力， 动力输入轴 11带动动力输入齿轮 10转动， 动力输 入齿轮 10带动主动平盘 3转动， 在主动平盘 3转动时， 该摩擦力带动中间平盘 13转动， 中 间平盘 13再带动固定被动平盘 4和滑动被动平盘 9转动， 固定被动平盘 4和滑动被动平盘 9 再带动动力输出轴 16转动， 输出动力。 3.速比调节： 调节轴 31带动调节齿轮 32转动， 调节 齿轮 32带动调节齿圈 33转动， 调节齿圈 33带动中间平盘调节齿轮 12转动， 中间平盘调节 齿轮 12带动中间平盘调节丝杠 8转动，中间平盘调节丝杠 8带动中间平盘调节螺母 6上行或 下行， 中间平盘调节螺母 6通过中间平盘调节螺母角 34带动中间平盘 13上下移动， 由于速 比是由固定被动平盘 4或滑动被动平盘 9和中间平盘 13接触圆直径与中间平盘 13和主动平 盘 3接触圆直径的比值决定的， 因此中间平盘 13的上下移动实现了上述接触圆直径的变化， 也就实现了速比的变化， 达到了调节速比的目的， 4.正反转的调节： 主动平盘 3 以主动平盘 轴 27为界，分为主动平盘 3的上半部和主动平盘 3的下半部，在主动平盘 3转动方向一致的 情况下， 中间平盘 13与主动平盘 3的上半部接触时的动力输出轴 17转动方向和中间平盘 13 与主动平盘 3的下半部接触时的动力输出轴 17转动方向相反， 因此中间平盘 13跨过主动平 盘轴 27的轴端的上下移动就实现了动力输出轴 17的正反转的转换。 5. 中间平盘 13跨过主 动平盘轴端凸起 49的过程： 当中间平盘 13上行到达主动平盘轴端凸起 49时， 液压缸 36泄 压， 该种无级变速器处于空转状态， 中间平盘 13开始沿着主动平盘轴端凸起 49继续行进， 同时主动平盘轴端凸起 49挤压中间平盘 13连同中间平盘活动架 25外移，也使固定被动平盘 4和滑动被动平盘 9距离增大，滑动被动平盘 9和液压缸固定盘 20距离缩小。 6.滑动被动平 盘 9特例一中， 当中间平盘 13跨过主动平盘轴端凸起 49时， 液压缸 36泄压，主动平盘轴端 凸起 49挤压中间平盘 13外移，挤压加压块 37推动液压缸活动盘 38外移； 当中间平盘】 3跨 过主动平盘轴端凸起 49后， 液压推动液压缸活动盘 38、 加压块 37和滑动被动平盘 9向里移 动。 7.在主动平盘架 2特例一、 主动平盘架 2特例二和主动平盘架 2特例三中， 当中间平盘 13跨过主动平盘轴端凸起 49时， 液压缸 36泄压， 主动平盘轴端凸起 49挤压中间平盘 13移 动， 也挤压主动平盘架 2移动。 8.在主动平盘轴特例二中， 由于没有了主动平盘轴端凸起 49， 当中间平 13盘跨过主动平盘轴 27的轴端时， 中间平盘活动架 25并不移动， 滑动被动平盘 9 也并不移动。

Claims

1.本发明提供了一种无级变速器， 它包括： 壳体、 主动平盘架、 动力输入齿轮、 动力输 入轴、 动力输出齿轮、 动力输出轴、 液压缸固定盘、 液压油路、 中间平盘活动架、 主动平盘 齿轮、 主动平盘芯轴、 中间过桥齿轮、 调节轴、调节齿轮、调节齿圈、 液压缸， 其特征在于： 它具有主动平盘、 固定被动平盘、 滑动被动平盘、 中间平盘、 主动平盘轴， 主动平盘轴在主 动平盘齿轮中心孔中， 与主动平盘齿轮做转动配合， 也可以通过轴承做转动配合， 主动平盘 齿轮与主动平盘固定连接， 也可以是一体， 主动平盘以主动平盘轴为界， 分为主动平盘的上 半部和主动平盘的下半部， 在主动平盘转动方向一致的情况下， 中间平盘与主动平盘的上半 部接触时的动力输出轴转动方向和中间平盘与主动平盘的下半部接触时的动力输出轴转动方 向相反， 因此中间平盘跨过主动平盘轴的轴端的上下移动就实现了动力输出轴的正反转的转 换。
2. 根据权利要求 1所述的无级变速器， 其特征在于： 它具有中间平盘轴、 中间平盘调节 螺母、 中间平盘调节丝杠、 中间平盘调节齿轮。
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