WO2006122507A1

WO2006122507A1 - Variable-dimeter transmission wheel, speed-varied device and automatic stepless transmission

Info

Publication number: WO2006122507A1
Application number: PCT/CN2006/001043
Authority: WO
Inventors: Huidong Zhang
Original assignee: Huidong Zhang
Priority date: 2005-05-20
Filing date: 2006-05-19
Publication date: 2006-11-23
Also published as: CN1865733A

Abstract

A variable-diameter transmission wheel, a variable-diameter device and an automatic stepless transmission are disclosed. The transmission device is composed of variable-diameter transmission wheels, a medial transmission belt and a corresponding speed-adjusting device. A traction belt winds to form the work surface of said wheel, and the idle portion of the belt is wound at the center of the wheel. The traction belt and the transmission belt form a meshed transmission set. The transmission wheel transmits moment through a traction shank that can slide in radial slots of the taper transmission plates. The pitch circle radius of the wheel is determined by the position of the shank. Due to the cooperation of the wheel-enlarged device and the wheel-shrinked device, the variable-diameter wheel can change its diameter. The transmission device realizes a speed-varied transmission through the variability of the radius of the transmission wheel. The device can be applied on the machine that needs vary frequently transmission ratio.

Description

Reducer drive wheel, shifting gear and automatic micro transmission

Technical field

The present invention relates to a mechanical transmission mechanism capable of continuously changing gears, and more particularly to a transmission device and an automatic micro-speed transmission that can smoothly change the radius of the transmission wheel.

Background technique

The transmission plays an important role in the mechanical system, and its advantages and disadvantages directly affect the overall performance of the system. When the speed adjustment with the prime mover is uneconomical or impossible, the transmission needs to be used to meet the needs of the frequent shifting of the working machine. In the textile, food, paper and other industries, in order to adapt to the continuous changes of process parameters or rapid changes, the mechanical continuously variable transmission is generally used for speed adjustment.

At present, the machine type continuously variable transmission has almost the same structure, but it is almost driven by friction (traction) force. Even if it is a toothed chain type continuously variable transmission that assists part of the meshing force transmission, there is slippage in the transmission process, and it cannot be transmitted. Big power.

According to the different modes of operation, the transmission is divided into two types: manual shifting and power shifting. The human shifting structure is simple, reliable, easy to manufacture, light in weight and high in efficiency. However, the labor intensity is large; the power cut-off time is longer when shifting, which affects the work efficiency. Application to the car will reduce the passage on the bad road. The power shifting transmission uses a shifting clutch to fix the gears of different gears, respectively, to change the gear. The shifting clutch is operated by a hydraulic device. The pressure oil is supplied by the prime mover to drive the oil pump. Its structure is complex, manufacturing is difficult, and precision is required. Heavy weight and volume; the shifting clutch has friction loss and the transmission efficiency is low.

Continuously variable transmission for automotive applications CVT transmission has high efficiency and good transmission quality. However, the problems are the strength of the belt, the limitation of the life, and the slip between the belt and the pulley. These defects affect the promotion and application of CVT.

Summary of the invention

It is an object of the present invention to overcome the deficiencies of the prior art. The utility model provides a mechanical automatic micro-gear transmission with high transmission efficiency, which is reliable in operation, stable in operation, capable of transmitting high power, simple in structure, light in weight and low in cost.

The variable transmission wheel of the present invention comprises a transmission shaft and two cones mounted thereon and movable relative to each other, and a wheel traction belt is disposed between the two cones, the wheel One end of the traction belt is connected to the traction frame, and the other end is connected to the pull wire; the other end of the pull wire is connected with a reel or a pull coil mounted on the drive shaft, and the traction frame is slidably mounted on the two cones In the radial sliding groove, both sides of the wheel surface traction belt and the tapered surface of the cone disk cooperate to form a motion pair.

The variable-distance transmission wheel of the present invention is characterized in that: the center of the cone surface of the cone disk is provided with a tape groove, and the main cone surface of the cone disk is provided with a concave auxiliary cone surface in the radial direction, and the auxiliary cone surface a sliding groove is arranged on one side; a transitional inclined surface is arranged between the sliding groove and the main cone surface; the wheel surface traction belt is a chain formed by a round chain plate and a chain link, which is composed of a wide section, an excessive section and a narrow section. Sections are connected in series; the wide section The tapered surface of the tapered pin on both sides cooperates with the secondary tapered surface, and the tapered surface of the tapered pin on both sides of the narrow joint cooperates with the main tapered surface. In the variable transmission wheel of the present invention, a side of the radial sliding groove of the cone has a transition slope; a center of the cone of the cone is provided with a groove; the radial groove is located at the cone a cone surface is in communication with the tape groove; the wheel surface traction belt is a double row roller chain, and a tapered surface of the tapered roller on both sides is in rolling engagement with a tapered surface of the cone disk, and the wire is drawn For two.

In the variable-diameter transmission wheel of the present invention, the cone disk is composed of a bottom cone face plate and a crescent top cone face plate and a weight plate respectively mounted on the inner and outer sides thereof; the transitional inclined surface is arranged on the crescent cone face plate The sliding groove is located on the bottom cone surface plate; the wheel surface traction belt is a double row roller chain, which is formed by a wide chain link, a wide chain transition joint, a narrow chain transition joint, and a narrow chain link; The tapered roller on both sides of the wide link is in rolling engagement with the tapered surface of the bottom cone, and the tapered roller on both sides of the narrow link is in rolling engagement with the tapered surface of the crescent cone; The pull wire is an elastic cable; the two sides and the front end surface of the traction frame are both provided with rolling elements; the traction frame is provided with a chain channel, and the narrow chain link is thereby accessed.

Another variable transmission wheel of the present invention includes a transmission shaft and a flat plate fixed thereto, and a bracket is mounted on the transmission shaft, and the bracket includes two symmetrically mounted on the transmission shaft and a winch that is movable relative to the axial direction and a plurality of struts arranged in a circumferential direction; both sides of the gusset are spliced to each side winch by a spoke; each gusset is mounted on the flat plate and corresponds thereto In the radial chute, the traction frame is mounted in a radial open slot of the flat plate, and the two sides are respectively hinged on the winch by the spokes; the wheel table is installed in the wheel groove of the flat plate a traction belt; one end of the wheel traction belt is connected to the traction frame, and the other end is bypassed by the struts of the bracket and passes through slots in the transmission shaft to be connected with the cable spring in the transmission shaft.

The shifting device of the variable-diameter transmission wheel according to the present invention has two variable-transmission transmission wheels, one of which is a driving wheel and the other is a driven wheel, and the winding directions of the two driving wheel-wheel traction belts are opposite, one A drive belt that meshes with the two-wheel gauge belt connects the two variable diameter wheels together.

The automatic low-speed transmission of the present invention comprises a transmission housing, an input shaft and an output shaft: the variable-transmission transmission wheel is further mounted in the transmission housing; the transmission shaft of the variable-transmission transmission wheel serves as an output shaft, from the housing The opposite side of the input shaft extends; the tapered drive wheel fixed to the power output end of the output shaft is a fixed cone, and the other cone is a moving cone; the input shaft is provided with a sizing The wheel, the sizing wheel and the wheel table traction belt are connected together by a transmission belt engaged therewith; a tensioning pulley of the transmission belt is arranged between the sizing wheel and the variable diameter transmission wheel, and the tensioning wheel passes through the turret The housing is fixed to the housing, and a control device for controlling the axial movement of the moving disc is further disposed in the housing.

In the automatic micro-speed transmission of the present invention, the sizing wheel and the tensioning wheel are composed of a wheel disc and a driving pin shaft; the driving pin shaft is evenly arranged in the hole in the wheel disc, and the axial spacing of the adjacent pin shafts is The pitches of the belt links are equal.

According to the automatic differential transmission of the present invention, the control device includes a shifter mounted on the housing, a propulsion device, a shifting device, and a roller disc, a serrated tooth tube, and a distance measuring cylinder on one side of the moving disc; a pair of roller discs on one side of the moving disc a radially symmetrically arranged roller carriage; the serrated toothed tube is mounted on an outer side of the roller disc; the serrated toothed tube and the movable disc are fixed together; the shifter includes a shifting bracket and is movable therein a shifting sprocket; the shifting bracket cooperates with two threaded rods mounted in the housing; the shifting frame is displaced by a stepping motor by a sub-synchronous belt, a twisting belt, a threaded rod, and a secondary threaded rod; a roller on the roller frame is mounted on an end face side of the shift frame; the distance measuring cylinder is fixed on the other end of the output shaft, and the teeth of the sawtooth tooth block and the tooth phase of the sawtooth tooth tube Engaging; the propulsion device includes a pair of synchronously acting shoe blocks mounted on the shoe box on both sides of the shift frame, which are arranged radially on both sides of the gear tooth plate to control the feed disk The shifting device includes a three-position electromagnet, a control pull rod, a transfer pull wire and a main pull wire; a control rod mounted on the housing and a disc cam or a jack push rod on the distance cylinder Cooperate with, control the action of pushing the shoe block or topping the sawtooth block, adjusting the shift Moving the disk forward and backward,

In the automatic micro-speed transmission of the present invention, the fixed length cylinder has four sliding slots at one end, and four sawtooth shaped blocks are arranged in the square through holes formed by the sliding slot and the annular end cover; On the outer groove of each serrated tooth block; the outer wall of the fixed distance cylinder has four ejector pins for pushing the serrated tooth block, the head of the ejector pin acts on the groove of the serrated tooth block; and the other end of the fixed distance cylinder has a cam The shaft end of the cam is threaded, and the push rod of the jack is screwed onto the thread through the screw hole of the middle portion; a torsion spring is arranged between the cam and the push rod of the jack, and the two ends are hooked on the sleeve body respectively And the ejector push plate; the ejector push plate is equipped with a baffle and a retaining ring.

In the automatic micro-speed transmission of the present invention, the surface of the serrated toothed tube has a plurality of mutually parallel rotating tooth-shaped teeth, and the cross-section is serrated.

The variable-speed transmission wheel of the present invention is characterized in that: the feed tooth plate has two symmetrically distributed spiral teeth, and two pairs of spiral teeth are two planes.

The automatic transmission provided by the present invention has the following features and advantages:

Compared with the existing automatic transmission, the automatic transmission provided by the present invention has a multi-stage close-range gear. It belongs to the category of stepped transmissions. It has a large number of gears and a dense and uniform distribution of gear ratios, so it can also be called a micro transmission or a close transmission.

The transmission mode of the automatic transmission belongs to the meshing transmission, and there is no problem that the belt is slipping, and a large power can be transmitted. The automatic transmission ratio depends on the radial position of the traction frame on the variable diameter wheel. During the shifting of the gear position, the traction frame moves smoothly in the direction of the diameter of the variable wheel body. Therefore, it has the characteristics of stepless speed change when changing gears.

The automatic transmission is a power shift, and the shifting power is directly obtained from the output shaft by the mechanical device, and no external input force is required. The power supply device such as the oil pump and the power source used in the conventional automatic transmission is omitted, and the corresponding power loss is reduced.

Therefore, the present invention belongs to a power shift type automatic mechanical transmission capable of continuously changing gears having a plurality of stable close-range gears. The invention is characterized in that the length of the portion of the reduction drive wheel that participates in the formation of the wheel chain chain can be varied. The part that does not participate in the transmission for the time being is wound around the wheel center. Located on the side of the traction frame, the place where the wheel traction belt enters and exits is called the variable diameter opening. As long as the diameter is open The wheel diameter can be adjusted by turning the mouth to the non-wrapped area of the belt. Therefore, there is a chance to change gears every time the variable wheel rotates. The automatic transmission provided by the present invention automatically changes the gear ratio in accordance with a given shift schedule. The shift program is provided by a microcomputer. For different working machines, the reference signals to be analyzed and processed by the computer are not the same. For example, for a car transmission, the most important reference signal for shifting is a combination of engine load and vehicle speed signal. For a continuously variable transmission used in chemical production, the reference signal for shifting may be the production process. A combination of other signals such as temperature, humidity, etc.

DRAWINGS

Figure ί (a) ― ( c ) is the basic structure diagram of the variable diameter transmission wheel;

Figure 2 (a) - (c) is a top view and a sectional view of the variable transmission wheel;

Figure 3 (a) - (c) is a schematic diagram of the variable diameter transmission wheel changing the wheel diameter;

Figure 4 (a) - (e) is a double-head chain type meshing pair and a double-head chain link structure diagram;

Figure 5 is a shifting transmission mechanism composed of two variable diameter wheels;

Figure 6 (a) - (f) is a schematic view of the structure of the spoke type variable diameter wheel;

Figure 7 (a) is a perspective view of the assembly of the gearbox, and (b) is a full view of the transmission;

Figure 8 (a) is a view of the part 37 of Figure 7 (a), (b) is a reduction wheel split diagram, (c) is a cross-sectional view of the shaft end 32-1; Figure 9 (a) is the structure of the drive belt 33 And the split map, (b) is a split view of the wheeled traction belt;

Figure 10 (a) is an exploded view of the transmission, and (b) is another diagram of a fixed diameter transmission wheel;

• Figure 11 (a) ― (c) is a view of the driven shaft component and the control lever;

Figure 12 (a) a (d) is a sectional view of the spacer and moving cone components

Figure 13 (a), (b) is a positional relationship diagram of the transmission components.

Figure 14 is a plan view showing the diameter of the reducer wheel shown in Figure 13 in two extreme states;

Figure 15 (a) is the gear selection device mounted on the transmission case, (b) is the split view of the shift frame 35 and its accessories; Figure 16 (a) - (d) is the automatic transmission using the spindle power automatically Schematic diagram of shifting;

Figure 17 (a) ― (e) Working principle diagram of the feed sprocket 36;

Figure 18 (a), (b) is the shifting principle diagram; (c) Figure is a half section of the feed sprocket;

Figure 19 (a) - (c) shows a plan view and a split view of a composite tapered disk reducer drive wheel and components; Figure 20 (a) - (c) Figure is a composite cone face reducer drive The structure of the wheel.

detailed description

The features of the variable transmission wheel, the variable diameter transmission, and the fully automatic micro gear transmission will be described in detail below with reference to the accompanying drawings. Figure 1 (a) - (c) is the basic structural diagram of the variable-diameter transmission wheel; (a) Figure is the case when the diameter of the reducer wheel is expanded to the maximum, The traction frame 1 is mounted on a pair of cones 5, and the double-headed chain wheel traction belt 3 forms a wheel surface chain loop around the wheel core, one end of which is connected to the traction frame 1 and the other end of which is connected to the wire 2 . The drive shaft 7 is provided with a reel 4, and the tapered pin 6 is evenly arranged on both sides of the wheel reel 3, and the tapered surface of the pin cooperates with the tapered surface of the pair of cones 5 to form a sliding pair, and the tapered surface of the cone The central portion of the side has an annular concave shaped groove 5-1. (b) The figure shows the case where the diameter of the variable-diameter wheel is minimized, the traction frame 1 slides down to the lowest point along the radial chute 10, and a part of the wheel-type traction belt is wound on the reel 4. In the figure, 8 is a cone-shaped tapered surface, 9 is a main tapered surface, and 11 is a transitional inclined surface. The cone on the left side of the figure is cut away. (c) The figure is a structural view of the development of the traction belt of the wheel table. The part is a chain connected by a double-head chain plate and a chain link, and one end is connected to the traction frame 1 having a V-shaped frame structure, and One end is attached to the reel 4 by a pull wire 2, and the reel 4 is internally provided with a torsion spring, the torsion of which causes the reel 4 to rotate relative to the drive shaft 7.

Figure 2 (a) - (c) is a top view and a sectional view of the variable transmission wheel; (a) is a top view of a pair of cones, from which you can see the secondary cone 8, the main cone 9, slippery Slot 10 and transition bevel 11. The tapered surface of the tapered pin 6 forms a sliding pair with the main tapered surface 9. The secondary cone 8 and the main cone 9 have the same cone angle. (b) The figure shows the case where the traction frame 1, the drive shaft 7 and the wheel table traction belt are mounted on the cone. The wheel gauge belt has a wide chain 12 and a narrow chain 13. The two parts are connected by the overrun 12-1; (c) The cone is cut away, showing the relative position of the wheel traction belt 3, the drum 4, the drive shaft 7, and the cone pin 6 mating with the cone surface of the cone situation.

Figure 3 (a) - (c) is a schematic diagram of the variable diameter transmission wheel changing the wheel diameter. In the figure, the cone pins on the wheel table are numbered, where 0 is the pin on the traction frame. (a) The figure shows the case where the wheel diameter is the largest, and the full length of the wheel table is pulled out. (c) The figure is the case where the wheel diameter is the smallest: the wheel table traction belt does not participate in the partial winding of the wheel surface chain to be stored in the wheel center. (b) The figure shows the movement trajectory of each cone pin during the change of the wheel diameter. In the figure, 0-0 is the trajectory of the pin on the traction frame and is a straight line. The curves 1 - 1 , 2-2 ... in the figure are the trajectories of the cone pins 1, 2, ... when the wheel diameter changes.

Figure 4 (a) - (e) is a double-head chain type meshing pair and double-head chain link structure diagram; (a), (b) Figure is the case where the transmission wheel diameter is minimum and infinity, in the figure The pitch of all the chain plates is L. During the transmission process, the chain head round head R01 of the wheel table traction belt 3 is engaged in the central concave arc R2 of the belt 14 of the transmission belt, and the chain head round head R02 of the transmission belt is inserted into the wheel table. In the central concave arc R1 of the traction belt 3 chain plate, the meshing pair transmits power by the squeeze between the round heads of the chain plates. Figures (c) and (d) are the split and assembled views of the basic links, (e) are cross-sectional views of the links, links and taper pins, and a is the taper angle of the taper pins.

Figure 5 is a shifting transmission consisting of two variable diameter wheels; this mechanism transmits only one-way torque. The left is the driving wheel and the right is the driven wheel. The arrows in the figure indicate the direction of movement of the reducer and the speed of the belt. The left and right of the left-hand variable-wheel traction frame 1-1 and the inlet and outlet of the wheel-type traction belt are called variable-diameter openings. The variable diameter opening of the right variable diameter wheel is on the right side of the traction frame 1-2. The reducer wheel must be turned to the non-enveloped area of the drive belt 14 to adjust the wheel diameter. In the figure, the variable diameter opening of the left variable diameter wheel is about to enter the wrap angle area, and the variable diameter operation cannot be performed; the variable diameter opening of the right variable diameter wheel just turns away from the wrap angle area, and the variable diameter operation can be performed. 4-1 and 4-2 are reels and 2 are pull wires. The two-wheeled table traction belt is wound in the opposite direction. The load is completely absorbed by the tractor frames 1-1 and 1-2. Figure 6 (a) - (f) is a schematic view of the structure of the spoke type variable diameter wheel; as shown in (d): The wheel table traction belt 3 - 3 is propped up by a plurality of brackets 30, one end of which is attached to the traction frame 1-3; the two ends of the strut 26 are respectively hinged with the spoke winch 27 and the bracket 30, and a pair of spoke winches 27 are symmetrically mounted on the hollow shaft 28. When the two discs move toward each other, the bracket 30 rises and the wheel table The wheel chain chain formed by the traction belts 3 - 3 is enlarged. (a) Yes (d) The case where the flat plate 25 is added. (b) The figure shows the case where the wheel diameter is the smallest. The flat plate 25 is provided with the strut guiding groove 30-1 and the traction frame guiding groove 29, and the traction frame 1 - 3 slides to the lowest point in the groove 29; the winch 27 is moved to The end of the hollow shaft 28; (e) is the case where the flat disc 25 is removed in (b). (c) is a sectional view of the flat plate 25, and the traction frame 1-3 can be seen; the chain that does not participate in the formation of the wheel chain chain enters the shaft from the hole 28-1 of the hollow shaft 28. (f) is a sectional view in which the wheel-type traction belt 3-3 does not participate in the transmission and is wound into the hollow shaft. The end of the chain is connected to the cable spring 2 - 1

Figure 7 (a) is an assembled perspective view of the automatic transmission. The output shaft 32 is mounted on the lower casing 42; the fixed cone 31 is mounted on the end of the output shaft 32, and the spacer 37 is mounted on the other end of the output shaft 32 to fix the axial position of the moving cone 34. A threaded hole is formed in the support rods on both sides of the shifting frame 35, and the threaded rod 38 is screwed therein; when the stepping motor 40 drives the pair of threaded rods 38 to rotate by the timing belt 39, the shifting bracket 35 and the forward mounted thereon can be driven. The crankset 36 translates. The power transmitted by the transmission is input from the input shaft 41, and is output from the output shaft 32 to one end of the fixed cone 31 via the transmission belt 33. (b) is a full view of the transmission, and the upper casing 43, the lower casing 42 and the casing front cover 44 constitute a transmission casing, and the input shaft 41 and the output shaft 32 project from the casing.

Figure 8 (a) is the spacer 37 of Figure 7 (a) with a ram pusher 45 with a notch 45-1 at the rear end. The front end is provided with four serrated blocks 47 which are pressed against the fixed length cylinder by elastic steel strips 48. The ram 46 is mounted on the surface of the barrel. (b) is a splitter split diagram on the output shaft: The roller chain 52 is wound to form a wheeled traction belt; one end is attached to the traction frame 51 and the other end is connected to the spool 59 by two pull wires 50. When the axial distance between the two cones 31 and 34 is increased, the chain 52 is guided to the wheel core by the winding of the spool 59, and is wound in the tape loop groove 58. When the axial spacing of the discs 31 and 34 is reduced, a plurality of tapered rollers 49 on either side of the chain act under the action of the tapered faces of the cones 31 and 34. Driving the wheel surface traction belt 52 to expand outward in the radial direction of the disk, which achieves the purpose of increasing the wheel circumference and expanding the wheel diameter. A traction frame chute 51-1 for mounting the traction frame 51 is mounted on the cone disk along the tapered busbar. The other function of the groove is to form a passage for the wheel surface traction belt 52 to enter and exit the wheel center; the tapered roller 49 on both sides of the chain It is accessed by the slope 31-1. The shaft 34-1 at the end of the cone 34 is interference-fitted with the hole 54-1 in the serrated tube 54 to sandwich the roller disc 57 between the moving cone 34 and the serrated tube 54. The roller tray 57 is provided with two roller holders 56 on which the rollers 55 are mounted. The shaft 32 is machined with a spline 32-3, a rear end is provided with a retaining ring 32-2 and a baffle 53 , and a portion of the end 32-1 is partially varnished. (c) The figure is (b) a section view at Figure 32-1, and the thick black line indicates a portion of the arc of the brush varnish.

The arcuate teeth of the belt 33 and the roller chain roller 52 or the wheel 60 in Fig. 9 (a) may constitute an engaging pair. The drive belt 33 is assembled by a link plate 62 through a needle bearing 63 and a pin 63-1. The drive belt is composed of two rows of parallel chains, and the guide rods 61 also function as a joint, and the shafts 61-1 at both ends thereof are interference-fitted with the holes 62-1 on the chain plates. (b) The figure is a split view of the wheeled belt, the wheel The lead belt is modified by a common roller sleeve chain, one end is connected to the traction frame 51, and the other end is connected to the reel 59 through the cable connector 50-1 and the cable 50. The reel spring 64 is mounted in the reel 59. The roller chain roller 52, the sleeve 65 and the tapered roller 49 are separated.

Figure 10 (a) is an exploded view of the transmission, which is the case where the lower casing is disassembled: The fixed cone 31 is mounted on the casing front cover 44 with bearings 32-4. The wheel diameter of the variable wheel has been adjusted to a minimum, and a part of the wheel of the wheel is wound around the wheel center. The tractor frame 51 is moved to the position closest to the center of the wheel. The shaft end of the guide rod 61 is in contact with the tapered surface of the cone 34. The driving wheel 60 drives the variable diameter wheel through the belt 33. The shaft 66-1 of the tension pulley 66 is mounted on a pair of turrets 67 which are rotatable about the turret shaft 67-1. The turret shaft 67-1 can be mounted in the hole 44-1. (b) The figure is another fixed diameter drive wheel that replaces the drive wheel 60 and the tensioner 66 in (a). A pin hole 68-2 is evenly arranged on the wheel 68 of the wheel, and the drive pin 68-3 mounted in the hole is equivalent to the scallop of the driving wheel 60 and the tensioning wheel 66.

Figure 11 (a) is the output shaft split view, which is the case when the reducer wheel diameter is the smallest. The roller disc 57 and the serrated tooth tube 54 move to the end of the output shaft 32 with the moving cone 34, and the moving cone 34 is The spacing of the fixed cones 31 at the collar 32-4 is maximized. The traction frame 51 also descends to the lowest point of the traction frame chute 51-1, and the inclined faces 51-2 and the grooves 51-1 on both sides form a sliding pair. The parts that are not cut away in the figure are an elastic steel strip 48 and a torsion spring 69. (b) The figure is a view of the output shaft and the attachment mounted on the lower casing 42. This is the case where the reducer wheel diameter is maximized, and the roller disc 57 and the serrated tooth tube 54 move axially with the moving cone 34 to the position closest to the cone 31. It can be seen that the spacer 37 is provided with a jack pusher with a notch 45-1.

45. Disc cam 37-1. A control lever 71 is mounted on the housing, which is fixed by a positioning plate 72, and the control lever 71 is connected to the three-position electromagnet 70 through the connecting rod 70-1. The output shaft 32 is provided with a brush 73 at its end, which is the two contacts of the switch. When it comes into contact with the insulating arc of the end of the shaft, the circuit of the three-position electromagnet 70 is cut off. (c) The figure is an enlarged view of the control lever 71 in the figure (b), the wire puller of 74 soft pull wires, and 74-1 is the pull sleeve. The push rod 75 can pull the wire puller 74 through the connecting rod 75-1. 76 is a retaining lug that prevents the disc 45 from rotating with the spacer 37 when acting against the notch 45-1 on the jack pusher 45 of Fig. (b).

Figure 12 (a) is a sectional view of the spacer, the front end of the cylinder is provided with four sliding grooves 37-2, and the annular end cover 37-3 can form four square through holes, in which the sawtooth blocks 47 are mounted. . The four blocks are held by the elastic steel band 48. One pedestal for each tooth block

46. 47-0 is a half-cut tooth block. A disc cam 37-1 is machined on the spacer. The jack pusher 45 is mounted on the thread at the end of the barrel with a torsion spring 69 in the middle. (b) The figure is a pattern of the opposite direction of the spacer shown in (a). The end thread 37-4 can be seen. The ejector pusher 45 has a notch 45-1, a threaded hole 45-2, and a torsion spring. The head is hooked on the jack pusher 45, and the other head is hooked on the cylinder. When the pusher 45 overcomes the torsion of the spring 69 and rotates on the thread 37-4, the jack head 46-1 can be pushed.

(c) The tapered disk 34, the roller disk 57 and the roller frame 56, which are divided, are attached to the roller disk 57 by bolts 56-1. 54 is a serrated toothed tube, and 58 is a tape loop groove on the cone 34. (d) is an enlarged cross-sectional view of the serrated block 47 in Fig. (a), the groove 47-1 interacting with the ejector head; the groove 47-3 is for embedding the elastic steel strip. 47-2 is a circular saw tooth.

Figure 13 (a), (b) is a diagram of the positional relationship of the transmission components. (a) is the case where the diameter of the variable diameter wheel is the smallest. Input shaft 41, The turret shaft 67-1 is mounted on the housing front cover 44, and the driving wheel 60 and the tensioning pulley 66 act on the belt 33. The tensioning axle 66-1 is mounted on the turret 67. (b) is the case where the diameter of the reducer wheel is the largest, and the tension pulley 66 rotates with the turret 67 and approaches the drive wheel 60.

Fig. 14 (a) and (b) are plan views showing the diameter of the reducer wheel shown in Fig. 13 in two limit states, showing the positional relationship of the traction frame 51, the drive wheel 60 and the tension pulley 66. The arrow indicates the characteristics of this variable speed transmission in one direction.

Figure 15 (a) is a control device mounted on the lower housing 42 of the transmission. The struts on both sides of the shifting frame 35 have threaded holes; they cooperate with the threaded rod 38 and the secondary threaded rod 38-2, and the threaded rod 38 is mounted on the casing 42 by the thrust bearing 38-1, and the shifting frame 35 is large The feed sprocket 36 mounted in the hole is translatable within the large hole by a pair of pusher blocks 78. The housing is provided with a stepping motor 40 which drives the two levers 38 and 38-2 to rotate synchronously by means of the short timing belt 39-1 and the timing belt 39, thereby driving the shifting frame 35 and the engaging disk 36 to move horizontally. The control lever 71 is driven by a three-position electromagnet, and a soft pull tube 77 is connected to the shift frame 35. (b) The figure is a split view of the shifting frame 35 and its attachments, and 36 is a feed sprocket with two spiral teeth symmetrically distributed at its front end, 36-1, 36-2 being the return spring and the spring-supporting screw. The shift bracket 35 has threaded holes at the ends of the rods on both sides. The two shoe block box 35-1 is bolted to the two poles of the shift frame 35. The cable holder 35-2 and the shoe block 78 are mounted in the shoe box 35-1. The shoes on both sides are connected by the transfer cable 77-1 and can be synchronized. The shoe block 78 is rotatable about its axis of rotation 78-1.

Figure 16 is a schematic diagram of the automatic transmission using the spindle power automatic shifting. Roller disc 57 represents a moving cone. Here, the rollers 55 on the roller disc 57 are separately separated to illustrate the force. The spacer 37 and the roller disc 57 have the same angular velocity. (a) The figure is the initial state in which the shift is prepared. At this time, the large circle of the shifting frame 35 is close to the roller 55, but the intake disk 36 is also retracted in the ring. The roller 55 does not come into contact with any of the crests 36-e of the advancer disk 36 during the revolution of the disk 57. At this time, the control rod 71 drives the push rod 75 thereon to move to the disc cam 37-1, and the cam 37-1 will push the push rod 75. After the push rod 75 is actuated, the shoe 78 will be turned over by the transmission cable. The insertion sprocket 36 is pushed out. (b) When the figure is in the state shown in (a), when viewed from the back of the shift frame 35, the feed sprocket 36 is retracted into the loop of the shift frame 35. The shoe block 78 has not yet been turned over. (c) The figure shows the case where the feed sprocket is pushed by the shoe 78 and fully extended to the outside of the gear frame 35; the push rod 75, the pull wires 74, 74-2 and the undrawn main cable are the hoof Block 78 flipped transmission. During this process, the roller 55 just turns to the root of the next spiral. That is, the roller tray 57 rolls on the spiral teeth and drives the roller disc 57 to move in the d direction. (d) The figure is in the state shown in (c), when viewed from the back of the shifting frame 35, the engaging sprocket is pushed out by the pushing block 78, and the screw crest 36-e is extended to the shifting frame 35. Outside the circle. During this process, the swivel shoe 78 is turned 90 degrees around the shoe shaft 78-1.

Figure 17 (a) - (c) is a process diagram of the axial movement of the feed disk 36. The cam 37-1 and the roller 55 have the same angular velocity, and the arrows indicate the direction of rotation. The feed sprocket 36 has two symmetrical spiral teeth, f and F represent the roots, and e and E represent the crests. The force in which the feed disk 36 moves axially is provided by the cam 37-1 through the jacking pusher 75. (a) In the figure, the jack 75 is also placed on the base circle of the cam 37-1, and the feed jaw 36 is not pushed. (b) The figure shows that the roller has been turned over the top of the screw c, at this time The cam begins to jack up the push rod 75. (c) The figure shows that the cam has pushed the push rod 75 to the far stop point, and the roller has not yet been turned to the root F of the next spiral tooth. After the process (c), the roller will roll on the spiral tooth FE to achieve axial movement. It can be understood from the above process diagram that the process of the insertion sprocket 36 extending out of the 35-piece fixed frame is just the process of the roller moving from the crest e of one spiral tooth to the root of the next spiral tooth, therefore, the insertion tooth The extension of the disc does not interfere with the roller. (d) The figure is a cross-sectional view of the disc cam. (e) is the case where the feed sprocket wheel is placed in the section diagram of the transmission wheel. The angle range included in the obtuse angle AoB is the non-enveloped area when the diameter of the variable diameter wheel is the smallest. The acute angle CoD includes the non-enveloped area where the diameter of the variable diameter wheel is the largest. The acute angle EoF is marked by the angle range of a spiral tooth on the tooth plate, which is smaller than the non-wrap angle range of any wheel diameter.

Figure 18 is a schematic diagram of the shifting. (a) is the forward principle, at which time the control lever 71 is moved to the rightmost end, the push rod 75 is lifted up by the disk cam 37-1, and the shoe 78 is rotated by the transmission member 78 around the rotating shaft 78-1 by 90 degrees, and The insertion sprocket 36 is pushed out to the left, and the spiral teeth project out of the circle of the shifting frame 35. The roller 55 is about to roll on the helical teeth of the advancement disk 36 and achieve movement in the d direction. (b) The figure is a retraction schematic diagram in which the feed sprocket 36 is retracted into the loop of the shift frame 35. The control lever 71 is moved to the leftmost end, and the stop pawl 76 thereon is embedded in the notch of the jack pusher 45 and forces the jack pusher 45 to stop, but the jack pusher 45 is opposite to the rotating thread 37-4. The helical motion is performed and the ejector 46 is pushed to the left against the torsion of the torsion spring 69. The ram 46 urges the serration block 47 out of engagement with the serrations on the serrated tube 54. The moving cone 34 and the roller 55 are automatically moved to the right at this time until the roller 55 is blocked by the outer ring of the shifting frame 35. After the retracting operation is completed, the control rod 72 returns to the intermediate position, and under the action of the torsion spring, the ejector push plate 45 will be rotated back to the original position, and the serrated tooth block 47 is also reset under the action of the elastic steel strip, and is pressed against the serrated shape. The serrated teeth of the tube 54. The ds in the figure is the axial spacing of the two swivel serrated teeth on the serrated toothed tube 54, and d _X is the distance from the cylindrical surface of the pair of rollers 55 to the front end face of the shifting frame 35. The roller 55 can be divided into two sections bl and b2 according to the working characteristics, the bl section and the spiral tooth of the insertion sprocket 36, and the b2 section and the front end surface of the shifting frame 35. (c) is the cut-in sprocket wheel. A complete spiral tooth can be seen from the figure, and the value of the axial tooth distance is d0.

During the shifting operation of the transmission, the gear can be continuously advanced. The maximum number of consecutive forward gears depends on the value of d0, and d0 is an integral multiple of ds. The number of consecutive forwards (reverses) during a shifting operation depends on the value of dx. If the forward gear is selected, the value of the number of advance steps is (d0-dx) /ds, and the value is negative or 0 means If the gear is selected, the value of the reverse gear is dx/ds.

Figure 19 (a) - (c) is a plan view and a split view of a composite tapered disk variable diameter transmission wheel and components; (a5 is a plan view; the composite cone disk in the figure is a bottom cone disk 80 And a crescent top cone plate 81 mounted thereon. The wheel surface traction belt is a roller chain: a portion from the first section of the chain 82-0 to the wide chain transition section 82-1 is a wide chain section, which is The bottom cone 80 is supported; the portion from the narrow chain transition 82-2 to the elastic cable 83 is a narrow section chain, and the portion of the narrow chain participating in forming the wheel bracelet is supported by the crescent cone 81 and does not participate in the formation of the wheel chain The portion is coiled around the inner layer of the wide chain loop and is supported by the bottom cone 80. When the wheel diameter becomes large, the coiled portion of the narrow chain is pulled from the bottom cone disk 80 to the crescent cone face 81 via the transition slope 81-1. The crescent curve 81-2 is the locus of motion of the wide chain transition section 82-1. (b) The figure shows the splitting diagram of the variable-speed transmission wheel. The tapered disk on each side is assembled by the weight plate 79, the bottom cone disk 80 and the crescent-face cone disk 81. There is a traction frame chute 80-1 on the 80, a weight rib 80-3 on the back, and a spline hole 80-2 on the shaft end. The wide band portion of the wheel traction band 82 from the first section 82-0 to the wide chain transition section 82-1 is supported by the bottom cone disk 80. During the change of the wheel diameter, the shaft end of the wide chain transition section 82-1 always rolls on the curve 81-2. (c) The figure is a plan view of the part of the wheel traction belt, the 82-d section chain is the narrow section chain of the wheel table traction belt, the inner chain plate width is b; the 82-c section is the wide section chain area, the outer chain plate The width is B. 82-1 is a wide chain transition joint, 82-2 is a narrow chain transition joint; 82-3 is a tapered roller on the side of the chain; 82-4 is a drive roller.

Figure 20 (a) is a schematic view of the wheel surface of the wheel on the cone disk, in the figure 84 - 0 is a half-section of the traction frame, a flat hole in the middle, for the wheel table traction belt narrow section chain area 82- d is in and out; bounded by the flat hole of the traction frame 84-0, the narrow chain section 82-d does not participate in the part forming the wheel chain chain, and one end is connected to the elastic cable 83, supported by the bottom cone 80, and participates in forming the wheel bracelet The portion of the loop is supported by a narrow chain transition section 82-2 supported on the crescent cone faceplate 81. The narrow chain chain is guided by the inclined face 81-1 when transitioning between the tapered faces of the two plates 80 and 81. The wide chain section 82-c of the wheel traction belt, one end is a wide chain transition section 82-1, and the other end is attached to the traction frame 84. When adjusting the wheel diameter, the shaft end of the transition section 82-1 rolls along the curve 81-2. The wide chain 82-c is rolled up and supported by the bottom cone 80. The bottom cone 80, the crescent cone 81 and the counterweight 79 are integrally joined by bolts 85. (b) The figure shows the case where the reduction wheel diameter is minimized. In the figure, the axial end of the narrow chain transition section 82-2 slides on the top cone disk 81 above the crescent curve 81-2. When the narrow chain supported on the bottom cone 80 enters and exits the crescent top cone disk 81, the tapered rollers 82-3 on both sides are guided by the inclined surface 81-1. The narrow chain is threaded through the flat hole at the back 84-4 of the tractor. There is no rolling element at the back of the traction frame 84-4, and the slot for mounting the pin at 84-5. (c) The figure is a view of the traction frame, and the flat hole 84-2 of the front end face of the traction frame is a passage of the chain; the front end face and the side surface are provided with a rolling body fitting groove 84-1, and the rolling body 84-3 is mounted. In this way, the contact surface of the traction frame and the chute is formed into a rolling pair, which is beneficial to changing the working condition of the traction frame.

Structural features of the control mechanism:

The shifting program of the control computer is implemented by the shifting bracket 35 mounted on the lower casing 42 of the transmission, and the stepping motor 40 for driving the shifting bracket 35 only needs to move the shifting bracket 35 to the correct position, which is not a power unit. , Micro motor can be used.

The control lever 37 mounted on the lower casing 42 is pulled by the three-position electromagnet 70 and is the implementer of the shifting command, but is not the provider of the shifting power. Only the corresponding mechanism is guided to obtain the shifting power on the rotating driven shaft, and a miniature electromagnet can be selected.

Industrial applicability

The reduction transmission wheel, the shifting device and the automatic micro-gear transmission of the present invention are mainly used for the transmission devices of automobiles, textiles and chemical machinery.

Claims

A reducer transmission wheel comprising a drive shaft (7, 32) and two oppositely movable cones (5, 31, 34, 80) mounted thereon, wherein: A wheel traction belt (3, 52, 82) is disposed between the two cones, and one end of the wheel traction belt (3, 52, 82) is connected to the traction frame (1, 51, 84), and One end is connected to the pull wire (2, 50, 83); the other end of the pull wire (2, 50, 83) and the reel (4, 59) mounted on the drive shaft (7, 32) with a torsion spring (64) or Pulling coils (83-1) are connected; the traction frames (1, 51, 84) are slidably mounted in radial chutes (10, 51, 80-1) of the two cones, the wheel table The two sides of the traction belt (3, 52, 82) cooperate with the tapered surfaces of the cones (5, 31, 34, 80) to form a motion pair. -

The variable-distance transmission wheel according to claim 1, characterized in that: the center of the taper surface of the cone (5) is provided with a tape groove (5-1), and the main body of the cone disk (5) A concave sub-cone surface (8) is disposed on the tapered surface (9) in a radial direction, and one side of the auxiliary conical surface is provided with a sliding groove (10); between the sliding groove (10) and the main tapered surface (9) a transitional inclined surface (11) is provided; the wheeled traction belt (3) is a chain of double-headed chain plates and links, which are composed of a wide section (12), an excessive section (12-1) and a narrow section. Section (13) is formed in series; the tapered surface of the tapered pin (6) on both sides of the wide section (12) is engaged with the secondary tapered surface (8), and the tapered pin on both sides of the narrow section (13) The tapered surface of (6) is matched with the main cone surface (9). '

The variable transmission wheel according to claim 1, characterized in that: the tapered disc (31, 34) has a transition slope (31-1) on one side of the radial chute (51 - 1); The center of the cone of the disc (31, 34) is provided with a tape groove (58); the radial groove (51-1) is located on the tapered surface of the cone (31, 34) and the tape The groove (58) is in communication; the wheel surface traction belt (52) is a double row roller chain, and the tapered surface of the tapered roller (49) on both sides and the tapered surface of the cone disk (31, 34) are rolled In cooperation, the cable is two.

4. The variable transmission wheel according to claim 1, wherein: the cone (80) is composed of a bottom cone (80) and a crescent cone (81) mounted on the inner and outer sides thereof, respectively. And a weight plate (79); the crescent cone (81) has a transition slope (81-1); the chute (80-1) is located on the bottom cone (80); The wheel surface traction belt (82) is a double row roller chain, which is formed by a wide chain link, a wide chain transition joint (82-1), a narrow chain transition joint (82-2), and a narrow chain link; The tapered roller (82-3) on both sides of the wide link is in rolling engagement with the tapered surface of the bottom cone (80), and the tapered roller (82-3) on both sides of the narrow link a tapered rolling fit of the crescent cone (81); the pull wire (83) is an elastic pull wire;

] 1 The two sides and the front end surface of the traction frame (84) are respectively provided with rolling elements (84-3); the pulling frame (84) has a chain passage (84-2), and the narrow links are connected thereto. .

5. A variable diameter transmission wheel comprising a transmission shaft (28) and a flat plate (25) fixed thereto, characterized in that: a bracket is mounted on the transmission shaft (28), the bracket comprises two a winch (27) symmetrically mounted on the drive shaft (28) and movable relative to the axial direction and a plurality of circumferentially arranged struts (30); both sides of the struts (30) are passed through the spokes (26) spliced on each side winch (27); each gusset (30) is mounted in a corresponding radial runway (30-1) on the flat plate (25), the traction frame (1-3) mounted in a radial opening groove (29) of the flat plate (25), the two sides being hinged to the winch (27) by the spokes (26), respectively; a wheeled traction belt (3-3) is mounted in the wheel groove; the wheel surface traction belt (3-3) is connected to the traction frame (1-3), and the other end is bypassed by the support The plate (30) passes through a slot (28-1) in the drive shaft (28) and is connected to a cable spring (2-1) in the drive shaft (28).

6. A shifting device for a variable transmission wheel according to any one of claims 1 to 5, characterized in that: said variable reduction transmission wheels are two, one of which is a driving wheel and the other is a driven wheel, and two transmission wheels The winding of the wheeled traction belt is reversed, and a belt that meshes with the two-wheeled traction belt connects the two variable diameter wheels together.

An automatic low-speed transmission using the variable transmission wheel according to any one of claims 1 to 4, comprising a transmission housing (42, 43, 44), an input shaft (41), and an output shaft (32), characterized in that The transmission housing (42, 43, 44) is further provided with the variable transmission wheel; the transmission shaft (32) of the reduction transmission wheel serves as an output shaft, and the input shaft is input from the housing (44) (41) the opposite side protrudes; the tapered drive wheel (5, 31, 80) fixed to the power output end of the output shaft (32) is a fixed cone disk, and the other cone disk (5, 34, 80) is a moving cone; the input shaft (41) is provided with a sizing wheel (60, 68), the sizing wheel (60, 68) and the wheel surface traction belt (3, 52, 82) are passed The meshed drive belts (33) are coupled together; a tensioning pulley (66) of the drive belt (33) is provided between the sizing wheel (66, 68) and the variable diameter drive wheel, the tensioning wheel (66) ) fixed to the housing (41, 44) by a turret (67), and a control file for controlling the axial movement of the moving disc (5, 34, 80) is also mounted in the housing (42, 44) Device.

The automatic differential transmission according to claim 7, wherein: said sizing wheel (60) and or tensioning wheel (66) are composed of a wheel (68) and a drive pin (68-3). ; the drive pin (68-3) is evenly arranged in the hole (68-2) on the wheel (68), the axial spacing of the adjacent pin (68-3) and the belt (33) link The pitch is equal.

The automatic differential transmission according to claim 7 or 8, wherein: said shifting means comprises a shifter mounted on the casing (42), a propulsion device, a shifting device, and a moving plate (5) , 34, 80) a roller disc (57) on one side, a serrated tube (54), a spacer cylinder (37); a roller disc (57) on one side of the moving disc (5, 34, 80) is provided with a a roller frame (56) arranged symmetrically in a radial direction; the sawtooth tube (54) is mounted on the outside of the roller disc (57); the serrated teeth a tube (54) and a moving disc (5, 34, 80) are fixed together; the shifter includes a shifting bracket (35) and a shifting sprocket (36) mounted therein; the shifting The frame (35) cooperates with two threaded rods (38, 38-2) mounted in the housing (42, 43, 44); the shifting frame (35) is passed by the stepping motor (40) through the secondary timing belt (39-1), the timing belt (39), the threaded rod (38), the secondary threaded rod (38-2) are driven to be displaced; the roller (55) on the roller frame (56) is mounted on the shift frame The end face side of (35); the distance measuring cylinder (37) is fixed to the other end of the output shaft (32), the teeth of the serrated tooth block (47) and the teeth of the serrated tooth tube (54) The propulsion device includes a pair of synchronously acting shoe blocks (35-1) mounted in the shoe box (35-1) on both sides of the shift frame (35), which are arranged radially in the The two sides of the feed sprocket wheel (36) control the expansion and contraction of the feed sprocket wheel (36); the shifting device comprises a three-position electromagnet (70), a control pull rod (71), and a transfer pull wire (77- 1) and main pull wire (77); mounted in the housing (42 43-44) The control lever (71) cooperates with the disc cam (37-1) or the jack pusher (45) on the spacer (37) to control the push shoe (78) or Open the action of the sawtooth block (47), adjust the moving plate (5, 34, 80) to move back and forth.

The automatic differential transmission using a variable diameter wheel according to claim 7, wherein: the fixed length cylinder (37) has four sliding grooves (37-2) at one end of the cylinder, and four sawtooth shapes. The block (47) is mounted in a square through hole formed by the chute (37-2) and the annular end cap (37-3); the elastic steel strip (48) acts on the groove of each serrated tooth block (47) (47) -3) upper; the outer wall of the fixed cylinder has four ejector pins (46) for pushing the serrated tooth block (47), and the head (46-1) of the ejector pin (46) acts on the serrated tooth block

(47) on the groove (47-1); the other end of the fixed cylinder has a cam (37-1), the shaft (37-4) on the side of the cam (37-1) is threaded (37-4), the push rod pusher (45) is screwed onto the thread (37-4) through the screw hole (45-2) of the middle portion; a torsion spring (69) is mounted between the cam (37-1) and the pusher plate (45), which The two ends are respectively hooked on the sleeve (37) cylinder and the jack pusher (45); the top pusher (45) is provided with a flap (53) and a retaining ring (32-2).

11. The automatic differential transmission according to claim 9, wherein: the serrated toothed tube (54) has a plurality of mutually parallel revolving tooth surfaces on its surface, the cross section of which is serrated.

12. The automatic low-speed transmission according to claim 9, wherein: the feed sprocket (36) has two symmetrically distributed helical teeth (36-e), and two pairs of helical teeth are between two Segment plane.