WO2005001312A1 - Transmission mecanique de vitesse variable a l'infini - Google Patents

Transmission mecanique de vitesse variable a l'infini Download PDF

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Publication number
WO2005001312A1
WO2005001312A1 PCT/CN2004/000576 CN2004000576W WO2005001312A1 WO 2005001312 A1 WO2005001312 A1 WO 2005001312A1 CN 2004000576 W CN2004000576 W CN 2004000576W WO 2005001312 A1 WO2005001312 A1 WO 2005001312A1
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Prior art keywords
transmission
speed
input
traction
output
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PCT/CN2004/000576
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English (en)
Chinese (zh)
Inventor
Guobin Wang
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Guobin Wang
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Publication of WO2005001312A1 publication Critical patent/WO2005001312A1/fr

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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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action

Definitions

  • the invention belongs to the field of mechanical design and manufacturing, and particularly relates to the design and manufacturing of a mechanical continuously variable transmission. Background of the invention
  • Continuously variable transmission is a transmission that can continuously and continuously change the transmission ratio. It has a wide range of applications and is especially suitable for: (1) machines with variable process parameters; (2) machines that require continuous changes in speed; (3) Equipment that seeks the optimal working speed; (4) Coordinate the operating speed between several operating units in the drive system of one or more equipment; (5) Slow start: For machines with large inertia or starting with load, use After the continuously variable transmission, it can start with high torque at nearly zero speed, and continuously change speed to the rated speed under load to avoid excessive inertial load, so a prime mover with less power can be used.
  • the mechanical continuously variable transmission can achieve continuously variable transmission, it has the following defects: 1. It is difficult to obtain ultra-low speed output, and the transmission range is relatively narrow; 2 , There are defects such as small transmission torque, low transmission power, etc. 3. Low load-carrying capacity, poor resistance to overload and impact resistance; 4. High processing and lubrication requirements for parts, short life, complex structure and technology, and manufacturing costs High; 5. Large sliding rate and low mechanical efficiency; In addition, some mechanical continuously variable transmissions also have shortcomings such as pulsating output and discontinuous power flow.
  • the transmission power of all friction type continuously variable transmissions depends on a large normal pressing force, which results in an increase in the load on each bearing, and the phenomena of elastic sliding and geometric sliding between transmission bodies are obvious; friction type
  • the effective contact surface of the continuously variable transmission for transmitting power is small. In theory, it is line or point contact, which results in large local stress and even serious work surfaces. Scratches or glues, resulting in low transmission efficiency, limited transmission power, and short transmission life.
  • a continuously variable transmission of a sliding vane chain This transmission is currently the only chain continuously variable transmission that uses a slotted sprocket (toothed sprocket) and a sliding chain to transfer power in a quasi-meshing manner.
  • the reciprocating body components in the pulsating transmission restrict its progress towards the high-speed field.
  • the vibration caused by its unbalanced inertial force and moment of inertia will be significantly intensified at high speeds, and the dynamic load generated by it will cause low mechanical efficiency.
  • the overrunning clutch is the only friction transmission component in the entire body. It also has a series of corresponding shortcomings in friction transmission. It is a weak link in the power chain of the entire mechanism. Its bearing capacity and impact resistance are relatively Low, restricts the pulsation type continuously variable transmission to high power, high efficiency and high speed 4.
  • the multi-phase structure set to reduce the pulsation will cause too many repeated constraints in the system, resulting in the machine's sensitivity to errors and the working environment, reduced efficiency, and increased dynamic load. It complicates the amount of mechanism and the debugging and installation process, so that the failure rate increases and the cost increases.
  • the main object of the present invention is to provide a mechanical continuously variable transmission, which can overcome the shortcomings of the mechanical continuously variable transmission in the prior art above, so as to meet and adapt to the needs of the modern chemical industry, especially the needs of the automotive industry.
  • This mechanical continuously variable transmission combines and expands most of the current continuously variable transmission function points, and realizes a unique non-friction low pairless non-pulsation uniform speed zero-crossing ultra-wide range continuously variable transmission. , It is a new concept of high power and efficient mechanical continuously variable transmission.
  • the equivalent coplanarity is a concept for different rotating rods, that is, a plane having an equal or complementary angle to the rotation plane of the respective rotating rod.
  • the concept of equivalent coplanarity can also be applied to the following analysis of the principle of equiangular velocity co-turning inversion.
  • Point or plane motion in any direction such as: plane pendulum motion, conical pendulum motion; when the rotation axis is perpendicular to the linear rod, it is a plane pendulum motion; when the rotation axis is not perpendicular to the linear rod, it is conical pendulum motion.
  • the conical pendulum motion can be regarded as a collection of microelement plane pendulum motions with common rotation points, that is, the space conical pendulum motion can be decomposed into infinite microelement plane pendulum motions, and the instantaneous motion of any point on the space conical pendulum is a plane motion . Therefore, the above-mentioned equiangular velocity isomorphic motion principle can be applied not only to plane motion but also to space. Exercise.
  • Constant angular velocity The instantaneous rotational angular rate (absolute angular velocity) of the rotating rod is equal;
  • Isomorphic position For the motion in the plane of rotation of the rotating rod, isomorphic position refers to a motion that is equal to or complementary to the angle of the rod itself
  • the directional feature is a directional feature for two or more movements. For example: Two movements have the same shape characteristic, which means that the direction of movement of the two movements in the plane of rotation of the respective rotation lever and the rotation lever. The angles are equal.
  • This concept can also be used to describe the positional relationship between entities, such as: The positional feature expression between the transmission arm and the motion transmission part mentioned below also uses this concept.
  • Iso-regular motion (hereinafter referred to as iso-characteristic motion)
  • iso-characteristic motion One-to-one motion with the same change law, in general terms, that is: if the speed is uniform, all speeds are uniform; if the speed is changed, all speeds are changed; the following refers to:
  • the instantaneous rate ratio of the mass point in the isomorphic direction is equal to the movement characteristic of the distance direction of each point from the center of rotation.
  • the input and output instantaneous rate ratio is always equal to the current nominal transmission ratio at any time during operation.
  • a kind of speed-change characteristic relationship that is, the original motion property before the speed change is not changed after the speed change, and if this relationship is satisfied, it indicates that the speed change mechanism has the speed change characteristics with regularity.
  • the speed and acceleration in this concept are measured by scalars, and do not involve the direction of vector motion.
  • the expressions of speed and velocity have the same meaning.
  • Variable speed power arm and historical speed resistance arm consistent with the concept of lever power arm and resistance arm
  • the shifting power arm refers to: the distance between the center of rotation of the shift lever M and the straight line where the motion axis of the linear motion input member a is located;
  • the shifting resistance arm refers to: the shift center of the shift lever M to the linear motion output member b The distance of the line on which the axis of motion is located.
  • an integral but folding line rotating lever is called a shifting arm; That is to say, the rotating lever in the reciprocating speed changing mode is called a shifting lever, and the rotating lever in continuous rotating speed changing mode is called a shifting arm.
  • shifting arm There is no essential difference between the shifting lever and the shifting arm. It is just a concise and intuitive customary title, only There is a physical distinction between the variable speed power arm and the variable speed resistance arm.
  • the variable speed power arm and the variable speed resistance arm are collectively referred to as an effective variable speed arm.
  • the input shift arm and the output shift arm refer to the driving end and the driven end of the shifting arm, respectively.
  • Speed regulation The process of changing the transmission gear ratio. Speed regulation and speed change are two different concepts. Speed change refers to the process of speed change.
  • m and n are any linear rods with an instantaneous equal angular velocity that rotate around any point on the line where they are located in space.
  • the included angles are complementary.
  • the speeds of points a, b, and c in the direction of the arrow have regular characteristics.
  • the position on the rotating rod can be changed steplessly, and the linear characteristic speed of stepless changes can be obtained.
  • M, M ,, N, N ', and V rotating rods are connected by a constant angular velocity device, with equal instantaneous angular velocity, a, b, cd, e, f, g, h
  • the arrow direction of a point has the same shape feature, so we get:
  • the characteristic linear velocity of movement, and the ratio of the magnitude of the velocity is equal to the distance from the direction of the arrow to the rotation center of each point.
  • steplessly changing the position of each point on the rod can change the linear velocity of the point steplessly.
  • a is a linear motion input part
  • b and c are linear motion output parts, where the motion trajectories of a and b are parallel to each other, and at the moment of motion shown in the figure, the motions of a, b, and c are three.
  • the angle between the trajectory and the shift lever M is exactly equal, and it can be clearly seen that the instantaneous linear rates of b and c are equal, and the linear rates of the three a, b, and c have regular characteristics.
  • the shift lever M When rotation occurs, it will be found that: the motion relationship of a and b can maintain the isomorphic relationship at all times, so that the linear rate maintains regular characteristics, while c can no longer maintain the isomorphic relationship, and the linear velocity with &, b no longer has the same regularity. Characteristics, if you want to guarantee the regular characteristics of c and a, you must change the motion output direction of c at all times. This is obviously not very realistic in practical continuously variable transmission applications. Therefore, c has a difficult implementation. Therefore, b should be adopted as a motion output in practical applications.
  • connection methods of the shift lever are connected by a mobile pair and a rotary pair, as shown in the figure.
  • stepless change of the rotation center position of the shift lever M can achieve stepless speed change.
  • b, c and the moving pair of the shifting pestle overlap at the current position but are independent of each other and do not interfere with each other.
  • the principle of constant angular velocity isomorphic motion is a transient process. Based on the principle of implementability, it can realize continuous and stable continuously variable output.
  • the constant angular velocity isomorphic characteristic motion rule should be constructed to last. Existence, that is, it has the characteristics of isochronous isochronous position in real time during the dynamic process of effective speed change.
  • the specific conditions for achieving this design are: (1) Always ensure that the instantaneous angular rates of the input and output sections of the shift lever are equal;
  • any transmission arm m and its corresponding linear motion transmission piece a are equivalently transformed into the rotation plane of any other transmission arm n and the rotation direction is the same, and the transmission arm m goes around the transmission.
  • the center of rotation is rotated until the position of the arbitrary shift arm n coincides with or is parallel to the shift arm n, and the motion trajectories of the two linear motion transmission members a and b corresponding to the two shift arms ⁇ and n will be parallel or coincide (see the illustration drawing) 4).
  • the instant geometric relationship between the motion trajectory of the transmission arm and the linear motion transmission member in any transmission unit can be passed by the instant geometric relationship between the transmission trajectory and the linear motion transmission member at any other position. Obtained by flipping the space in the same direction.
  • the homomorphic bit relationship can be transformed into a bit-likelihood relationship by the same-space flipping transformation. When this condition is satisfied, it has the characteristics of dynamic real-time constant angular velocity isomorphic motion.
  • This theorem is a design basis criterion for judging whether or not continuous characteristic of continuously variable transmission with equal characteristics can be achieved.
  • Transmission unit Refers to a one-to-one combination of a transmission arm or lever and an associated corresponding motion transmission member.
  • a transmission arm corresponds to multiple motion transmission parts, it is counted as multiple transmission units; the transmission unit may be a motion input part, or a motion output part; as shown in FIG. 3 Three transmission units.
  • Co-directional space flip transformation The transformation process that enables several motion or speed change units to change to the same plane and co-rotation without changing their motion conditions.
  • Effective motion trajectory The motion trajectory of the motion transmission part participating in the variable speed work process.
  • Motion transmission mechanism (a single component is called a motion transmission member):
  • the input and output connection mechanism of the power flow on the shift lever, such as the motion input member & motion output members b and c in FIG. 3 are collectively referred to as a motion transmission member (or a motion transmission mechanism) )
  • Fig. 6 shows the case where the input and output shift arms are not collinear.
  • this figure is a schematic diagram of the theoretical modeling structure, which is only a representation of the path setting relationship of the moving parts and the transformation of the movement state.
  • Figure 6.1 represents the input-output transmission arm fixed-connection type
  • Figure 6.2 represents the input-output transmission arm connected by constant angular gear transmission.
  • Figure 6 ⁇ 1 and Figure 6.2.1 represent the shift arm n and its corresponding motion transmission parts b and c in the two connected situations, respectively.
  • Figure 7 shows a space motion type.
  • the shift arms m and n are connected by a constant angular space bevel gear.
  • the rotation planes of m and n are not in the same plane. That is, at any time, in the effective transmission space, the transmission arm m and its corresponding linear motion transmission member a are equivalently transformed into the rotation plane where the transmission arm n is located, and the rotation direction is ensured to be the same, and then rotate around the transmission rotation center to When the position of the shift arm n coincides with or is placed in parallel at this moment, the movement trajectories of the linear motion transmission members a and b corresponding to the two shift arms 111 and n will be parallel or coincide. Therefore, the space mechanism also satisfies the conditions of stepless speed change of equal characteristics. See Figure 48 for more space mechanisms.
  • the input-output speed change unit can be arranged in different planes.
  • the input-output speed change unit can be designed in any orientation. It has great flexibility in the structural design of the body, which can further optimize the space of the mechanism. Utilization. This initiative is generally designed to address the needs of a particular space layout.
  • the power-to-weight ratio and power-to-volume ratio can be increased through any constant angular velocity transmission mechanism, variation mechanism and related plane, space motion conversion, and transmission mechanism (such as: plane gear, space gear, plane gear train) , Space gear train, shaft, belt, connecting rod mechanism, flexible steel wire shaft transmission, worm gear transmission, constant angular velocity coupling, etc.) to perform constant angular velocity transmission.
  • constant angular velocity transmission mechanism variation mechanism and related plane, space motion conversion, and transmission mechanism
  • plane gear, space gear, plane gear train space gear train
  • Space gear train shaft, belt, connecting rod mechanism, flexible steel wire shaft transmission, worm gear transmission, constant angular velocity coupling, etc.
  • the guiding principle of the principle of equiangular velocity co-rotating position similarity shifting principle is to design a free and flexible space arrangement.
  • the principle of isokinetic isomorphic motion is also applicable to curved motion.
  • the transient process of the microelements of curved motion is straight-line motion.
  • the real-time motion direction of any point of curved motion is in the tangent direction of the point, so the curve motion model can also be based on, etc.
  • Angular speed co-rotation, similarity, shifting principle, guiding principle, design, and other characteristics of the continuously variable transmission can also be based on, etc.
  • Figure 8, Figure 9, and Figure 10 show several types of space and other characteristics.
  • a schematic diagram of the principle of shifting For the motion input and output guide mechanism, refer to the following embodiments.
  • the position of the rotation point k of the shift lever can be adjusted steplessly to change the transmission ratio steplessly.
  • FIG. 10 represents a separate type of input-output transmission unit.
  • the input-output transmission unit is driven by a constant angular space gear.
  • the speed change process of such a device is performed by changing the included angle of the conical pendulum.
  • the scheme of arranging input and output moving parts in a parallel and straight manner has the best overall performance, that is, the power flow is introduced into the shift unit in a linear motion mode, and the three-point and one-line lever of the shift lever is used to shift the speed.
  • the principle changes the rate ratio, and the corresponding linear motion output power can be further converted into rotary motion output as required.
  • This shifting mode is a parallel three-point, one-line shifting mode. The specific conditions are:
  • the input and output parts are located on both sides of the rotation fulcrum, and the input and output movement directions are opposite; the right picture shows the same side transmission, and the input and output parts are on the same side of the rotation point, and the input and output movement directions are the same.
  • Changing any of the three positions can achieve the purpose of shifting speed.
  • the output and input terminals can be determined on the same side or different sides of the fulcrum according to specific needs.
  • the shifting process is generally accomplished by shifting the rotation fulcrum.
  • a parallel (1) to ensure that the motion is transmitted in the same direction, that is: to meet the isomorphic position Characteristics, (2) ensuring that the ratio of the variable speed power arm and the variable resistance arm is constant;
  • the basic framework of the parallel three-point, one-line speed change mode is: The two input and output parts that move in parallel with each other are organically connected by a middle element of a speed change lever to form an integrated set of speed change mechanisms.
  • the gear shifting device can be divided into: to complex type, continuous operation type;
  • the reciprocating transmission mechanism moves through regular characteristics such as the reciprocating swing output of the shift lever.
  • a multi-phase or two-phase device can be used with a certain phase difference to eliminate the interruption of the power flow in the reciprocating commutation zone.
  • the design principles are:
  • Rotary motion is converted to reciprocating linear motion I.
  • the comparison of the part numbers in the drawings is as follows:
  • the input shaft (4) transmits power to the slide bar through the timing belt wheel (1) and timing belt (2).
  • each motion transmission mechanism is connected to the shift lever through a mobile pair and a rotary pair, and the position of the connection point between the rotary pair and the shift lever is fixed.
  • the rotation center shaft 9 is connected to the shift lever using a rotating pair with adjustable turning point position. It is obvious that the trajectories of the linear motion input and output parts are parallel to each other.
  • the speed completely satisfies the conditions of constant angular velocity and isomorphism, so it can output stable and regular motions.
  • the speed can be adjusted by changing the positions of the rotating center shaft 9 and the rotating pair of the shift lever.
  • the rotating pair and the shift lever where the rotating center axis 9 is located are connected by a controllable moving pair M.
  • This controllable moving pair is usually locked and connected to the gearshift lever in a fixed relationship, and unlocked during speed adjustment.
  • you can change the speed by changing the position of the input and output force points on the gearshift lever. .
  • Characteristic movements such as alternate output through unidirectional rotation of multiple shift levers.
  • the design principle is to convert rotary motion to one-way linear motion, one-to-one, parallel three-point, one-line variable-speed mode conversion output, and other characteristics. See the description of the part number for comparison:
  • This mechanism uses continuous unidirectional running linear motion input and output traction timing belts (16, 17) to realize rotation / unidirectional linear motion conversion, and sets multiple shift levers to be evenly distributed at a certain included angle. Alternate rotation combined with the traction timing belt in the same running direction to complete the power transmission work. When the shift lever enters the effective area, it engages with the traction timing belt.
  • the corresponding mutation pattern is shown in Figure 15. Its working principle is similar to the reciprocating type. The key technology is to ensure that each shift lever must guarantee the same shape characteristics when it is combined with the traction timing belt. For speed adjustment, you can take I / O shift arm separate setting type. Summary: The universal type has a moving pair on the shift lever to ensure that the ratio of the power shifting arm and the resistance arm is constant during the non-speed-adjusting operation; the variant has a rotating pair on the shift lever to ensure the input and output of the shift arm. The position of the force point is constant, and the ratio of the variable speed power arm and the resistance arm is constant. Both of them are based on the principle of constant angular velocity and same direction reversal, and have the same angular velocity and homomorphic position conditions in the effective working process, so they can achieve stepless transmission with constant characteristics.
  • the conversion process between uniform rotating motion and hook speed linear motion can be transformed with the help of many current mechanisms.
  • the key of this patent is the constant angular velocity isomorph
  • the motion trajectory of the input-output coupling mechanism is a linear motion, which avoids the design steps of the stepless variable wheel and stepless variable curve body that are currently difficult to solve.
  • Special variable speed motion output can be obtained by changing the arrangement angle of the motion transmission parts, or designing the motion transmission mechanism with curves, arcs, and multi-point polylines, and changing the angle of the shift arm.
  • FIG. 16 where this diagram is a schematic diagram of a theoretical modeling structure, and is only a schematic representation of a path setting relationship and a movement state of a moving part.
  • a solid line represents a shift arm
  • a dotted line represents a trajectory of a moving transmission part.
  • A is a motion input part
  • b, c, and d are motion output parts.
  • Figure 16.1 shows a linear arrangement of the shift arm, a is input at a constant speed, and at the output end, b outputs at an accelerated speed, c outputs at a deceleration, and d decelerates first and then accelerates;
  • Figure 16.2 shows a linear arrangement of the shift arm, a For uniform motion input, at the output end, b and c are used to accelerate the motion output, and d is decelerated first and then accelerated.
  • variable transmission ratio data can be designed according to the requirements of output motion characteristics to allow uniform rotation
  • the movement is output according to the required variable speed form, and a special movement curve is obtained to meet the requirements of special working conditions.
  • Special shift output can also be obtained in ways other than the straight line of the lever itself.
  • This type of transmission is a low-pair transmission, which can be used to replace the cam mechanism in specific occasions, to achieve the effect of low-pair replacing high-pair transmission, improve load capacity, transmission efficiency, compete for low cost, and extend life.
  • Such mechanisms can also be applied in reverse, filtering and shaping specific complex motions and pulsating motions as needed, and outputting them in uniform, near uniform, or other special regular motion forms.
  • This patent adopts a completely different transmission idea from the traditional transmission, and achieves a unique transmission effect. It can easily and quickly realize the easy modulation of any transmission ratio. When the gear position is at zero, it will smoothly cut off the power flow and can be replaced safely. Disengage clutch and set neutral. The speed regulation process does not interrupt the power flow, so that the rate change tends to transition extremely smoothly. The speed regulation process in the running state cleverly and naturally uses the periodic power-assisting effect of the lateral flow of the power flow to achieve a power-assisted speed change.
  • the transmittable torque range has almost no restrictive factors. As long as the space range is suitable, it can transmit arbitrarily large torque, so that the transmission of the present invention is widely applicable to various heavy, light, mini vehicles and other transmission occasions.
  • the whole working process has no large mechanical impact and collision, and has overload protection function.
  • the device's sensitive, free, precise and stable maneuverability makes it extremely easy to achieve automatic control.
  • After adopting the automatic control mode it has an excellent automatic fast wide-range stepless speed change function.
  • the main transmission system of the transmission is a low-pair transmission, with high bearing capacity, reliable operation, stable performance, and extremely wide speed range. It can increase, reduce, zero-cross, and reverse (the transmission characteristics of forward and reverse are exactly the same. Input steering is unconditional) and ultra-near zero and ultra-low speed precision and stable output torque, strong adaptability, long life, easy and simple adjustment.
  • Figure 1 Schematic diagram of isokinetic isomorphic motion
  • FIG. 4 Schematic diagram of the principle of similar angular velocity inversion in the same direction (Part I);
  • Figure 5 Schematic diagram of the principle of similar angular shift in the same direction and in the same direction (two);
  • Figure 6 Schematic illustration of the principle of similar angular shifting in the same direction and in the same direction (three);
  • Figure 7 Schematic illustration of the principle of similar angular velocity in the same direction and reversed position (IV)
  • FIG 8 Schematic of the principle of continuously variable transmission such as space (I)
  • Figure 9 Schematic diagram of the principle of continuously variable transmission such as space (2);
  • Figure 10 Schematic diagram of the principle of continuously variable transmission such as space (3);
  • Figure 11 Geometric model of parallel three-point one-line speed change principle
  • Figure 12 Schematic diagram of parallel three-point one-line speed change mode (a)
  • Figure 13 Principle of parallel three-point one-line speed change (1) Variation mode diagram
  • Figure 14 Principle of parallel three-point one-line speed change (2) schematic diagram
  • Figure 15 Principle of parallel three-point one-line speed change mode (two) Variation mode diagram
  • Figure 16 Diagram of theoretical model of non-equivalence transmission
  • Figure 17 Schematic diagram of constant angular velocity reciprocating continuously variable transmission mechanism
  • Figure 19 Vertical arrangement scheme of the motion conversion mechanism
  • Figure 20 A schematic diagram of a vertical arrangement mechanism of a motion conversion mechanism
  • Figure 21 Assembly diagram of constant angular velocity reciprocating continuously variable transmission
  • Figure 22 Several connection methods of the gearshift lever, linear motion input and output parts, and speed control block;
  • Figure 23 Transmission power flow distribution structure layout scheme of the transmission (2);
  • Figure 24 Arrangement diagram of a spur gear distributor disc type selective clutch mechanism
  • Fig. 25 Schematic diagram of constant angular velocity reciprocating continuously variable transmission mechanism (2)
  • Fig. 26 Rolling contact type mobile pair scheme capable of transmitting torque
  • Figure 31 Structure diagram of electromagnetic selective clutch
  • Figure 33 Cam contour curve unfolded image and analysis of motion pattern image
  • Figure 34 Expansion view of the contour curve of the double-cycle cam
  • Figure 35 Double-roller type linear follower cylindrical cam mechanism
  • Fig. 36 Layout drawing of a disc cam change-over transmission with a linear follower
  • Figure 37 Contour diagram of disc cam and image analysis of motion pattern
  • Figure 38 Double-roller-type linear follower disc cam mechanism
  • Figure 39 Assembly diagram of constant angular constant-speed continuous rotation type continuously variable transmission
  • Figure 40 Structure of speed lock block (1)
  • Figure 41 Structure diagram of speed lock block (2)
  • Figure 42 Structural diagram of internal and external dual-track restraint and pressurization device
  • Figure 43 Assembly drawing and parts drawing of the shift arm assembly
  • Figure 44 Assembly example of practical application of continuously rotating continuously variable transmission
  • Figure 45 Assembly drawing of an electromagnetic traction type transmission
  • Figure 47 Transverse wafer traction type transmission mechanism diagram
  • Fig. 48 A schematic diagram of a space structure type embodiment model of a constant-angle isomorphous continuously variable transmission
  • Fig. 49 A general component symbol table of a mechanism barrel diagram
  • Figure 50 Space transmission mechanism barrel diagram.
  • Timing belt wheel 2. Timing belt 3. Slider 4. Input shaft 5. Moving pair
  • control cam 36 control power transmission shaft 37, feather key 38, flow selection wobble plate
  • Static carrier 72 on both sides, Pressure roller 73, Piston rod 74, Pressure roller, Pulley 76, Brush 77, Electric ring 78, Spring pad 79, Electromagnetic chuck, Movable armature selective friction disc 81, Reset Spring 82, deflector 83, prime mover, cylindrical cam 85, synchronous speed control mechanism 86, inner wall contour cylindrical cam, disc cam 88, cam rotating shaft 89, cam bracket 90, traction timing belt pulley, ring track 92 , Speed lock block 93, Track support 94, Gearshift arm
  • Offside traction spring 96 Offside traction spring 96, traction belt tensioner 97, friction traction surface 98, guide roller, circulation fairway 100, mobile auxiliary sleeve 101, lock block traction lug 102, pressure body 3, pressure roller 104, plus Pressure chain plate 105, flat metal traction belt
  • Figure 17 shows a cylinder diagram of a zero-speed continuously variable transmission of the same angular reciprocating reciprocating type.
  • this diagram is a simplified diagram of the mechanism, which is only a brief description of the principle structure arrangement relationship.
  • Each component is not strictly drawn in the same view direction.
  • Figure 21 please refer to Figure 21; and the direction of the arrow in the figure only represents the type of movement (curve The arrow represents rotation; the straight arrow represents translational movement), and does not represent the specific direction of work movement.
  • This type of transmission includes: input shaft, output shaft, input and output rotary / reciprocating linear motion conversion mechanism, input and output speed locks, input and output speed lock tracks, shift lever, speed control block, speed control track, screw nut Main parts such as speed governing device, current selective clutch and roller, cam control device.
  • Main parts such as speed governing device, current selective clutch and roller, cam control device.
  • the connection and transmission process of the power flow is completed by a series of motion transmission parts.
  • the auxiliary parts used in this embodiment include: a guide rail, a slider, a moving pair, a rotating pair, a gear transmission group, a transmission pin, a speed regulating handle, and a bevel gear transmission group. , Speed transmission chain, etc.
  • the input rotation / linear motion conversion mechanism of the transmission includes timing belt wheels, timing belts, and corresponding auxiliary components such as moving pairs and rotating pairs.
  • the analysis of the motion conversion process is shown in Figure 18:
  • the moving pair is connected, and the timing belt 2 and the slide are connected.
  • the block 20 is connected by a pin 19 and a rotating pair 7.
  • the speed lock pillow 22 obtains a reciprocating linear motion at a uniform speed.
  • the hinge point a enters the arc area of the pulley
  • the speed lock pillow reverses the direction of movement, and the commutation process is simple and harmonic. Movement, smooth reversing, low impact, and the linear running interval of this type of conversion mechanism can be Much larger than the arc transition area, it is very suitable for this type of transmission.
  • the input speed lock 22 transmits power to the shift lever 8 through the transmission pin 19 and the rotation pair 7, and the shift lever rotates around the rotation center axis 9 under the action of the power and passes the power through the slider 20 and the rotation pair 7
  • the pin 19 is transmitted to the movement output piece output lock pillow 26, and the output lock pillow runs along its track under the constraint of the output lock track 25.
  • the input and output lock tracks 23 and 25 are arranged in parallel, the input and output The speed locks 22, 26, the operating point of the shift lever 8, and the 9-axis center of the rotation center axis have a "three-point, one-line” relationship, that is, this transmission mechanism meets the "parallel three-point, one-line” transmission mode; "Three points and one line” is a theoretical model of plane motion.
  • plane motion refers to: the movement of the motion trajectory in the same plane, not all the moving parts in the same plane; the research principles for specific mechanisms are: For plane moving parts that are not in the same plane, they can be transformed into the same plane for analysis, and for space moving parts, the real-time motion rule is analyzed by the micro-element method.
  • the output shaft centerline of the rotation pair 7 (or here the pin rotation axis center line) at the joint of the output lock pillow 26 and the shift lever 8, during the shifting process
  • the "equal-characteristic speed change" can be satisfied. Therefore, if the input speed lock is moving at a constant speed at this time, the output speed lock will also output a linear motion of hook speed with regular characteristics, and the speed ratio is equal to the length ratio of the variable speed power arm and the variable resistance arm at this time, that is: input ⁇ Output the distance ratio between the two action points of the speed lock pillow and the gear shift lever to the center of the rotation center.
  • the speed control block 15 is connected to the nut of the movable member of the screw nut speed control device 24. Rotating the speed control handle 28 can continuously adjust the position of the speed control block to achieve stepless speed change.
  • the transmission's output rotation / linear motion conversion mechanism consists of a timing belt, a timing belt wheel, etc.
  • control type clutch which can be controlled by external signals to selectively transmit torque and filter out motions that do not meet output requirements.
  • This device adopts the input terminal control principle, and only outputs the articulation point a (see Figure 18) at a uniform speed in the linear running area of the synchronous belt (the specific control scheme is shown in Figure 29: Image Analysis below).
  • the power flow path is as follows: the linear motion of the output lock speed pillow is converted into a rotary motion via a transmission pin, a timing belt, and a timing belt pulley, and then the selection clutch main shaft 30 is input, and a slip key is used between the selection clutch main shaft and the selection wobble plate 38 ( Guide key) 37 coupling (in order to reduce friction, ball spline coupling can be adopted, that is, a ball is placed in the spline groove to change the sliding friction into rolling friction, and its specific implementation is shown in Figure 26). At the same time, it can move in the axial direction. The axial movement of the deflection wobble plate 38 is controlled by the motion of the input end of the transmission.
  • the power flow at the input end is introduced by the control power transmission shaft 36, and is transmitted to the control cam 35 via a speed transmission chain composed of a timing pulley and a timing belt (wherein the function of the speed transmission chain is to transfer the torque output by the transmission shaft 36 to a specific
  • the gear ratio drives the control cam to coordinate the pace between the control cam and the shift phase. Therefore, a variety of other transmission methods can be used to build a speed transmission chain, such as the method shown in Figure 25.
  • the cam profile curve is designed according to a certain rule (see Figure 29, ( Figures 30.1 and 30.2). The displacement of the roller 34 is controlled in a timely manner.
  • the displacement of the roller 34 is passed through the selection drive frame 33 (Note: In the illustration, the boundary between the transmission frame and the bevel gear distribution plate is drawn with a dashed line to indicate the space position between the two. There is no mutual interference.
  • the slewing support 43 is transmitted to the flow selection plate 38, and the clutch timing with the bevel gear flow plate 32 on the left and right sides is controlled to achieve the timing of the clutch.
  • the rotational movements of the friction wobble plate in different directions are respectively transmitted to the bevel gear flow plates on the left and right sides, or in other words: let the left and right flow plates only accept A unidirectional torque driving rotation direction, to achieve the purpose of the optional traffic shaping, complete rectification process reciprocating torque power flow, and finally by the bevel gear
  • the group outputs the power flow of the left and right bevel gear distribution plates in parallel.
  • the working steps of the left and right two-phase transmission units differ by 1/4 or 3/4 cycles, that is, when the working step of the left camera group is in the reciprocating commutation interruption interval, the right camera group is just in the best stable and uniform speed working area, and vice versa
  • the alternating operation is smoothly connected to the output shaft, and the parallel current output is continuous and stable power flow.
  • the direction of the output shaft movement can be changed by changing the clutch steps of the current selection pendulum and the left and right flow distribution plates. For example: If the original clockwise torque was transmitted to the left valve plate and the counterclockwise torque was transmitted to the right valve plate, the clockwise torque is now transmitted to the right valve plate and the counterclockwise torque is transmitted to the left valve plate. , Then the purpose of commutation is achieved.
  • This process can be realized by changing the transmission coordination phase of the control cam 35 and the roller 34, wherein: the left and right units should be switched at the same time.
  • the advantage of this type of mechanism is that it can further reduce the reciprocating frequency of the reciprocating motion system, reduce the reciprocating inertia impact, and improve the transmission efficiency.
  • the gear transmission group 18 and the input timing belt drive motion conversion system (its linear running range can be much larger than the arc transition area, which has a frequency reduction effect) have a frequency reduction effect; at the output end, it can be driven by a bevel gear transmission group 31 Speed increase compensation and restoration are performed with the output synchronous belt drive motion conversion system.
  • control cams 35 of the left and right camera groups can be combined to use a single cam for unified control, as long as the rollers 34 of the two stream-selective transmission frames are placed at different positions on the same cam profile, so that the cam control system is the left and right camera groups Shared (can be placed in the middle of the transmission), which reduces control aids by half and simplifies design.
  • Figures 19 and 20 show: The vertical arrangement scheme of the transmission movement conversion mechanism and the corresponding mechanism diagram.
  • the structure, function, and working principle of its components are the same as those shown in Figure 17, the only difference is that:
  • the timing belt and timing belt wheels of the conversion mechanism are arranged vertically in the rotating shaft, which is more suitable for use in some occasions.
  • Figure 21 Assembly diagram of constant angular velocity reciprocating zero-cross continuously variable transmission.
  • the drawings in this patent specification have not been drawn strictly according to engineering drawing standards. Some parts of the figure It is expressed in detail and in a condensed manner.
  • the nut screw speed regulation mechanism in the figure is expressed in a clearer way.
  • the working principle of FIG. 21 is the same as that shown in FIG. 17, but in this figure, a slewing support is formed between the current selective transmission frame 33 and the current selective wobble plate 38 through a current selective pressure plate 39, a thrust bearing 40, and a radial bearing 41. The mechanism is connected to transmit the selective compression force.
  • this method can further reduce the rotational inertia of the slewing system and increase the bearing capacity.
  • the existing slewing support standard parts can be used instead, as shown in the mechanism barrel diagram.
  • Figure 22 shows several ways of connecting the shift lever with the linear motion input and output parts and the speed control block, a represents the linear motion input part, b represents the linear motion output part, and k represents the speed control block and the rotation center axis; where: A, B The type is the same as the corresponding connection relationship in the embodiment of FIG. 21, and the difference between B and A is only in the interchange position of the connection relationship between the shift lever and the linear motion input and output parts.
  • the connection relationship in C is the same as that in FIG. 12, hereinafter
  • the continuous rotation type also adopts this similar structure.
  • the input and output parts of the shift lever in Figure D are relatively separated and connected with each other in a moving pair relationship, while they are connected with the linear motion input and output parts by a rotating pair to achieve the speed change process.
  • the limit position of the trajectory of the shift lever end does not exceed the range of the two parallel lines where the trajectory of the linear motion input and output parts is located. This structure is helpful to reduce the space layout of the transmission, and the separate transmission arm with the telescopic movable auxiliary sleeve 120 mentioned below. The purpose is roughly the same (see Figure 44.3).
  • Figure 23 shows another configuration of the transmission input power flow.
  • This solution uses a pair of transmission gears to input power flow, and splits the power through the shaft ends on the two sides of the same gear, which are respectively transmitted to the synchronous pulleys of the two-phase transmission unit.
  • the mechanism is further simplified, but its disadvantages are: the distance between the shift levers of the left and right camera groups is increased, which is not conducive to the uniform and precise control of the speed control block.
  • the structure shown on the right is better, and the distance between the two shift levers is closer than on the left.
  • Figure 24 Arrangement diagram of a spur gear flow-disc type selective clutch mechanism.
  • the flow-selective clutch uses a flat cylindrical gear flow plate instead of a space bevel gear flow plate, which is beneficial to reducing costs and eliminating or reducing axial loads.
  • the disadvantages are: a transitional reversing gear 47 is added.
  • the axial force of the bevel gear distribution disc type selective clutch can be balanced internally and belongs to the system internal force, which is not reflected externally, and the axial component force on the output shaft is obtained by the bevel gear design of the left and right camera groups. balance. Therefore, the entire system still has good stability in work.
  • Figure 25 Tube diagram (2) of the constant-angle homomorphic reciprocating zero-cross continuously variable transmission mechanism.
  • This solution differs from the mechanism shown in Figure 17 in that: the setting of the current-selection clutch at the power flow output end and the matching speed transmission chain are different.
  • the current selection clutch adopts: the reciprocating torque output by the synchronous belt pulley at the output end is directly transmitted to the bevel gear distribution disk, and the current selection reshaping and the rotation of the left and right rotation rotation distribution disks are periodically performed to complete the current selection shaping and selection. Take one-way rotating power, and output the rectified one-way torque through the main shaft of the selective clutch coupled with the sliding key.
  • the part that reciprocates inside the selective clutch is the flow plate, and the selective swing plate rotates in one direction; the opposite is the case.
  • the design principle here is generally: Take the one with the smaller moment of inertia as the reciprocating rotating part.
  • the speed transmission chain in this figure is: Controlling the power transmission shaft-one space bevel gear-transmission rod-one flat gear-control cam. In specific applications, it can be designed in a flexible and diverse manner according to the actual situation.
  • Figure 26 shows: A series of rolling contact type moving pairs capable of transmitting torque. Since the main shaft of the selective clutch and the selective wobble plate carry the main power flow torque during work, and the number of axial movements is frequent, it is appropriate to adopt rolling pairs. The specific method of connection is shown in Figure 26. This structural part can be produced as a standard part. It is used in various occasions that require torque transmission but axial movement.
  • a rolling type mobile pair with a steel ball circulation track can be adopted, as shown in Figure 26.4
  • its rolling cross-section can be circular, and the existing rolling-type mobile substandard parts can be used.
  • non-circular cross-section rolling type moving standard parts can be adopted; or two or more cylindrical cross-section or non-cylindrical cross-section rolling contact type shifting can be adopted.
  • the standard parts of the moving pair are arranged in parallel and non-coaxial, and used as a shaft, so as to achieve torque transmission while being able to move axially.
  • 4 parallel moving pairs ie: rolling
  • the guide rail is combined into a torque-transmitting mobile pair.
  • the guide rail is connected to the main shaft of the selective clutch, and the slider is connected to the selective wobble plate (where the name of the guide rail and the slider here refers to the existing rolling type mobile pair.
  • the names of the parts in the standard parts do not refer to the part numbers in the drawings of this patent).
  • Figure 27 Series of self-locking control modes of the current-selective wobble plate, as shown in Figure 27.1, a link mechanism 61 with a self-locking function is used to control the current-selective wobble plate 38, so that the control cam is required to control the current-selective wobble only at the time of commutation
  • the effect of the pressure of the disc, once the linkage mechanism is self-locking, the force between the cam and the selective swing plate can be eliminated, so the cam profile curve can be taken as shown in Figure 30.4 ( Figure 30.4 is an expanded view of the cam contour curve)
  • Method The corresponding link mechanism of roller 34 is in the self-locking compression state when in zone a, so the cam contour groove is wide here, and it is in a loose fit state with roller 34.
  • crank link mechanism 64 and the link booster lock mechanism 65 are used for traction control of the selective wobble plate, which has a double locking effect.
  • the link booster lock mechanism 65 is locked in a linear state
  • the crank link mechanism 64 is also in the dead point locked position, which has a more reliable effect.
  • the clamping force application scheme of the clamp type clamping force applying device 66 is similar to the manual forceps, as shown in Figure 28.1.
  • the left tong-type clamping force applying mechanism applies pressure to the flow plate 32 and the selective wobble plate 38 to tightly clamp the two to transmit friction torque, while the right tong-type clamping force applying mechanism is at In the open state, conversely, when the piston rod 73 moves to the left, the right side is clamped and the left side is opened.
  • FIG. 28.1 The clamping power of the clamp type clamping force application device comes from the oil cylinder (or cylinder, traction electromagnet);
  • Figure 28.2 The pressure of the clamp type clamping force application device is mechanically pressurized, and the legend represents eccentricity
  • the cam pressure device can adopt a variety of mechanical pressure methods in practice;
  • Figure 28.3 shows:
  • the power source Such as: oil cylinder, gas rainbow, traction electromagnet, electric motor, mechanical force applying device, etc. It is located far away from the current-selecting wobble plate and distribution plate system, which is conducive to optimizing the space layout setting.
  • a pressure roller 74 can be installed at the clamping force applying end to form rolling contact (see a partially enlarged view in FIG. 28.3).
  • Figures 28.4, 28.5, and 28.6 The closed movable middle pressure member and the static bearing members on both sides are used to pressurize the pressure, and in which:
  • Figure 28.4 is a self-closed pressurized force cam device. Relying on the cooperation between the middle contour groove of the cam and the contour grooves on both sides (see Figure 30.3 for the cam profile curve development view), the effect of closed pressure on the pressure is achieved.
  • FIG 28.5 The stationary bearing member 71 is connected to the fixed frame of the eccentric cam pressure mechanism 67, and the middle movable pressure member 70 is connected to the movable frame portion of the movable member of the eccentric cam mechanism 67 to form a closed pressure system.
  • Figure 28.6 is the same as the pressure principle in Figure 28.5, except that the eccentric cam pressure mechanism is replaced by an oil cylinder (or cylinder or traction electromagnet).
  • the middle movable pressure member 70 is connected to the cylinder piston rod 73, and the stationary bearing members 71 on both sides Connected to the cylinder.
  • the pressure transmission of the pressure-selecting plate to the selective swing plate and the distribution plate can be performed by the slewing support, the thrust bearing, and the pressure roller 72 (see FIG. 28.1).
  • the pressure roller 72, the pressure plate 72, and the force receiving surface portion of the selective flow pendulum that are in contact with it are all carried out by means of a tapered surface with a certain taper to transmit the pressing force) and the like to reduce wear.
  • a strong steel spring with a large elastic coefficient can be added in series between the cam, the selective transmission frame, and the selective swing plate to indirectly press the selective swing plate, as shown in Figure 27.2.
  • the elastic cushioning device 62 in the example such as: relying on a damping spring or the contact of the roller 34 and the cam groove with an elastic material (such as a rubber wheel) instead of pure rigid contact, to convert rigid pressure into elastic pressure, Change line contact to surface contact to reduce vibration shock.
  • the use of spring indirect pressure method can achieve automatic compensation effect.
  • P bar has low manufacturing and installation accuracy requirements, and realizes automatic wear compensation function.
  • the following related cam mechanisms can also adopt this connection method.
  • the contact between the roller and the cam groove can be in the form of rolling contact or fluid lubricated sliding contact.
  • Figure 29 Image analysis of the movement laws of the input speed pillow and the selective wobble plate (displacement-time curve diagram, ie: s-t diagram);
  • a curve represents: st diagram of the movement of the speed lock of the left camera group
  • b curve (dashed line) represents: st diagram of the movement of the speed lock of the right camera group
  • the c curve represents: st diagram of the movement pattern of the left camera group selection plate
  • d curve (dotted line) represents: the st diagram of the movement pattern of the right camera group selection plate
  • (D) below the abscissa indicates: synchronization
  • the trajectory development view of the hinge point a (the driving pin 19) of the belt and the slider 20 is compared with each other at a glance.
  • e curve represents the corresponding situation of the left camera group
  • f curve represents the corresponding situation of the right camera group.
  • the part (B) in the figure indicates: The contour curve of the control cam 35 and the movement pace configuration diagram of the input-side speed lock. Under the control of the cam profile, the current-selection wobble plate is operated at this pace. When the speed-lock pillow is operated in the linear section of the corresponding st diagram, the current-selection wobble plate contacts the flow plate to transmit power; the input speed-lock pillow is in the corresponding st diagram. When the arc section completes the reciprocating reversing operation, the separation of the current-selecting wobble plate and the distribution plate is in an idling transition state.
  • the two camera groups are arranged and matched according to a certain working phase difference to obtain continuous power flow output.
  • the working phase difference is 1/4 or 3/4 cycle (as shown in the figure), but when the linear constant speed running area of the input speed lock is much larger than the commutation area, the phase difference is not strictly taken 1/4 or 3 / 4 cycles, as long as the left and right Han units work in an alternating relay mode to obtain continuous output power flow (the reflection on the image is that the a and b graph lines do not appear at the same time axis on the same time axis);
  • (C) part of the figure shows the running state of the selective swing plate when the transition area of the contour curve of the cam 35 is at the maximum.
  • the current selection plate has a long transition interval. Among them: To ensure the continuous power flow, there must be a certain amount of power transfer between the two phases. Area, so the transition interval should be less than this value.
  • the general principles are: On the premise of ensuring that the smooth and free commutation and the left-right alternative flow plate and the distribution plate can achieve the full synchronous clutch on the premise of increasing the overlap of the two units as much as possible.
  • the situation described in this image is consistent with the state shown in Figure 21 and can be referred to each other.
  • the working speed of the input speed lock and shift lever of the left camera group is in the reciprocating reversing area, and it is impossible to output uniform speed movement.
  • the corresponding flow selection plate is now in the middle position and does not contact the left and right flow distribution plates.
  • the group is in a state of cutoff at the moment; however, the right camera group is now in the best working area.
  • the input and output speed locks make a linear motion at a constant speed, and the current-selection wobble plate makes a constant-speed rotational movement.
  • the current position is in contact with the right-hand distribution disk.
  • the torque is transmitted to the right side of the disk output. If it is in contact with the left side of the disk at this time, the output shaft will output torque in the opposite direction.
  • the connection of the contour curve transition reversing area of the control cam 35 with the work area should be smooth and soft (as shown in the figure "Enlarged View of Reversing Transition Curvature"), so that the swinging pace of the flow selection wobble is in a harmonic state as much as possible. Speed up the pulsation of motion by softening the wobble plate.
  • Fig. 30 Expansion diagrams of several design schemes of the cam profile.
  • the cam profile shown in Fig. 30.1 corresponds to the image (B) in Fig. 29.
  • the cam wheel shown in Fig. 30.2 is designed to make the cam be symmetrically stressed in both directions.
  • the double-cycle periodic contour that is, contains two cyclic periods in the same closed contour curve, so that two rollers can be symmetrically arranged at an angle of 180 degrees to each other to optimize the force effect.
  • the electromagnetic reversing torque is used to select and reshape the output reciprocating torque.
  • the difference lies in that the mechanical attraction force is replaced by the electromagnetic attractive force, which is convenient and accurate. , Fewer peripheral accessories, simple structure and other advantages.
  • the working current of the electromagnetic chuck 79 is introduced by the electric ring 77 and the brush 76 through an external control circuit. With the help of electromagnetic traction technology, its control scheme will become flexible and flexible. Control system to obtain more flexible, precise and diverse control schemes.
  • the electromagnetic chucks are arranged in the two side flow plates.
  • the working pace is the same as that of the mechanical type selective clutch.
  • the electromagnetic attraction force is generated.
  • the movable armature selective friction disc 80 is tightly closed together to complete the torque.
  • the transmission between the movable selective disc 80 and the deflector 82 through the convex-concave gap is coupled with a short-stroke mobile pair, which can transmit torque while being relatively axially moved.
  • the two are implicated by a return spring 81, which is electromagnetic. After the sucker is de-energized, the selector disc 80 is separated from the distribution disc by the reset spring 81.
  • the spring pad 78 on the flow distribution plate also plays a role of assisting resetting.
  • the deflector 82 in this mechanism only reciprocates, does not make axial movement, and is fixedly connected to the main shaft of the selective clutch to transmit torque. Among them: The situation of the legend indicates that the current state is that the right-hand electromagnetic chuck is energized, and the current-selection disc on the right of the deflector and the distribution disc are attracted to transmit torque.
  • the current-selective wobble plate 38 in the mechanical type current-selective clutch can also be directly used for current-selective shaping by the electromagnetic suction cup in the current-distribution disk, but its mass is large and the response is slightly poor.
  • An electromagnetic chuck may also be provided in the deflector disc 82, and the movable armature selective friction disc 80 is connected to the side flow discs through a moving pair.
  • the deflector rotates back and forth, and the effect is not good.
  • the deflector is rotated in one direction, and the two sides of the deflectors are reciprocated. Therefore, in such a mechanism mode, an electromagnetic chuck should be set in the deflector.
  • Fig. 32 Cylindrical cam-shift gearbox series of direct-acting followers:
  • the input rotation / linear motion conversion mechanism in this solution is circled by a linear follower. It is composed of a cylindrical cam mechanism, a cylindrical cam 84 is a rotary motion active part, and the input lock 22 and the roller 34 are fixedly connected to form a roller direct follower.
  • the movement rule is controlled by the cam profile.
  • the rational design of the contour curve can achieve the schedule. Movement pacing, due to the design flexibility of the cam contour curve, the movement trajectory of the straight-moving follower can also achieve the movement conversion effect in the mechanism of FIG.
  • the left and right two-phase transmission units are identical in structure, but the operating phase difference is 1/4 or 3 / 4 cycles, on a single-cycle working contour cam, the roller direct-moving follower composed of the two sets of input locks 22 and rollers 34 are fixedly arranged at a phase difference of 90 degrees (as shown);
  • cam contour It can also be designed as a multi-period type as required.
  • the contour curve is a dual-period type.
  • the input speed lock of each camera group is pulled by two rollers that are symmetrically arranged at 180 degrees to each other. Optimize the force effect.
  • the output rotation / linear motion conversion mechanism of this transmission is composed of a gear and a rack mechanism.
  • the rack 11 is fixedly connected to the output lock pillow 26, and the linear lock of the lock pillow 26 is converted into a rotary motion by meshing with the gear 12. It meshes with another same gear, and the two gears are respectively connected to an overrunning clutch, and the clutch rotation directions of the two overrunning clutches are the same. Because the rotation directions of the two meshing gears are opposite, the two clutches work in complementary states, and the two overrunning clutches pass through the other end shaft respectively.
  • the upper gear meshes with a common gear to output one-way torque.
  • Figures 32.4 and 32.5 The schematic diagrams of the two-way continuous working overrunning clutch mechanism are shown in Figures 32.4 and 32.5, where: Figure 32.4 consists of 5 spur gears and 2 overrunning clutches.
  • the two overrunning clutches work alternately in turns to achieve continuous output torque in the Chinese direction.
  • the dynamic process is as follows: When the gear meshing with the rack rotates clockwise, the upper overrunning clutch works, and the lower clutch is in an overrunning idle state. Conversely, when it rotates counterclockwise, the lower overrunning clutch works and the upper overrunning idler.
  • Figure 32.5 there are 1 spur gear, 3 bevel gears, and 2 super gears.
  • the overrunning clutch is composed of an overrunning clutch on each side of the gear meshing with the rack, and the two overrunning clutches respectively output a one-way torque through meshing with a bevel gear and a common bevel gear.
  • the rotary motion output by the rack-and-pinion rotary / linear motion conversion mechanism can also be directly input to the selective clutch disclosed above for current selective shaping to complete the one-way rotary motion output.
  • This rack-and-pinion conversion mechanism and double overrunning clutch mode can also be used in other transmission-type mechanisms, such as in the mechanism of Figure 21.
  • Figure 32 lists several typical layout structures.
  • Figure 32.1 structure is conducive to reducing the longitudinal size of the body;
  • Figure 32.2 structure is conducive to reducing the horizontal size of the body;
  • the layout of Figure 32.3 is more compact, but the two-phase transmission unit is far away, which is not conducive to unified speed regulation.
  • the synchronous speed control transmission mechanism 85 is needed to connect the two-phase speed regulation system to achieve integrated control.
  • Figure 32.6 is a diagram of a cylindrical cam movement conversion mechanism with a working wheel on the inner wall. This solution uses the inside of the cam as a working space. It can design a larger cam working wheel without increasing the outer size of the body, which is beneficial to Without reducing the linear velocity, the linear motion with lower reciprocating frequency is output, and the body layout is further compacted.
  • Figure 35 In order to improve the transmission accuracy of the cam mechanism of the linear follower, the cam and follower can be closed as shown in Figure 35, where: Figure 35.1 is a double-roller concave contour grooved cylindrical cam mechanism; Figure 35.2 is a double-roller Convex-shaped grooved cylindrical cam mechanism. These two closed forms are tightly contacted with the groove wall surfaces of the cam wheel gallery groove on both sides through the double rollers that can freely rotate with each other. They are pure rolling contacts with high transmission accuracy and low wear. , Low noise and other advantages.
  • Figure 36 Layout diagram of a straight-acting follower disc cam conversion type transmission.
  • This solution uses a straight-acting follower disc cam mechanism as the input rotation / linear motion conversion mechanism of the transmission. It is obvious:
  • the disc cam structure is more conducive to compact design.
  • Two-phase variable speed units can be set on both sides of the same disc cam to optimize the space layout. In order to make the two-phase speed-changing unit's speed-locking tracks parallel to each other so as to uniformly adjust the speed with a relatively simple synchronous speed-adjusting transmission mechanism 85, and ensure the two-phase
  • the unit works alternately to output continuous power flow, and the phase of the wheel gallery layout on both sides of the disc cam should be arranged 1/4 or 3/4 cycles apart as shown in the diagram. See the front view, top view, and left view.
  • the lines and dashed lines represent the curve of the front and back of the cam, respectively. To simplify and improve the speed regulation accuracy, it can also be arranged as shown in Figure 36.1. In this case, the disc cams of the two-phase transmission unit need to be set separately.
  • Figure 37 Contour curve of the disc cam and analysis of the image of the movement pattern.
  • the contour curve design of the disc cam is similar to that of the cylindrical cam.
  • the purpose is also to make the motion trajectory of the linear follower achieve the motion conversion effect in the mechanism of Figure 21.
  • the input speed lock achieves the motion regular effect as shown in part A of the image in FIG. 29:
  • the linear region moves at a constant speed, and the transitional reciprocating commutation region shows a simple harmonic motion.
  • (I) the graph represents a single-cycle type
  • (II) the graph represents a double-period type
  • (III) the graph represents a 4-period type.
  • the disc cam rotates once, and the corresponding follower completes 1, 2, and 4 reciprocating working cycles respectively.
  • the respective dynamic motion images are obtained.
  • the abscissa can be replaced by the time axis, see the corresponding figure on the right. Among them: the abscissa represents the rotation period of the disc cam;
  • Figure 38 Double-roller type straight-moving follower disc cam mechanism, similar to the scheme in Figure 35, the disc cam and follower are closed in the form of a double-roller and cam profile groove that can rotate freely between each other The walls are in tight contact.
  • Figure 38.1 is a double-roller concave contour grooved disc cam mechanism
  • Figure 38.2 is a double-roller convex contour grooved disc cam mechanism.
  • the solid line section represents the profile profile of the disc cam AA
  • the two-dot chain line profile represents the profile of the disc cam BB to the rim.
  • the contour curves on both sides are so arranged for the two-phase transmission unit.
  • the speed-locked tracks are parallel to each other to ensure that the two camera units work alternately to lose Out continuous power flow.
  • Figure 39 Assembly diagram of constant angular constant-speed continuous rotation type continuously variable transmission
  • Figure 39.1 is a barrel diagram of this type of transmission mechanism
  • This type of transmission generally includes: input shaft, output shaft, input and output traction timing belt pulleys, tensioning wheels, input and output traction timing belts, pressurization devices, variable speed rotation assemblies, ring guides, speed governing devices and other components.
  • variable-speed rotation assembly is composed of a certain number of variable-speed arms with a common rotation center and a speed-locking block that cooperates with the moving pair.
  • the variable-speed arms on the same line are in a fixed state, and the variable-speed arms on different lines are within a certain range. It has independent degrees of freedom of rotation, see FIG. 43 for details.
  • the shift arms are connected by an offside traction spring 95, which can compensate for the "angular speed difference between the shift arms in different working areas "Vibration" effect (refers to: in the working area combined with the traction belt, due to the uniform speed movement of the traction belt and the radial movement of the lock block on the gear shift arm, the gear shift arm presents a certain regular speed pulsation phenomenon. The fluctuation rates on the shift arms of different working phases are different, which results in the instantaneous angular velocity differential phenomenon between different shift arms).
  • the offside traction springs connected to each other can be used to complete the transition.
  • the two-way balanced elastic action of the offside traction spring can also automatically and instantly eliminate the angular displacement offset phenomenon formed by the shifting arm in the working area, and restore the state of the angle between the shifting arms.
  • the alternate operation of multiple shift arms is equivalent to the alternate operation of multiple units, so the shift arms at different phases can have different angular velocities.
  • (1) Flat type traction belt a: metal type—a hole-shaped metal sheet laminated timing belt formed by stacking multiple layers of perforated thin metal belts (perforated annular metal sheets on top), each layer of metal The hole layers on the belt correspond to the meshing holes, which mesh with the meshing teeth on the special traction timing pulley, as shown in Figure 39.3; b: non-metallic type-one-by-one non-metallic flat belts. Its working structure principle is similar to that of the metal type.
  • the only difference is that: due to the flexibility of the non-metals, it is not necessary to adopt a multi-layer thin belt superposition, and it can be set by a thicker single-layer integrated method; of which: special organic materials
  • the strength is no less than that of metal, so a traction belt made of a suitable non-metallic material can also transmit a large amount of power.
  • the advantages of using a flat traction belt are: the pressurized chain plate attached to it is in flat contact, and the pressure area is large; the driven tensioning pulley does not need to be toothed, it can be a smooth wheel, thereby reducing costs and reducing The meshing holes of the belt are worn and noisy.
  • the timing belt in the aforementioned reciprocating transmission type can also use a metal belt to increase strength and reduce volume, and has the advantages of high efficiency, large carrying capacity, compact size, and long life.
  • Combined traction belt, a a parallel combination of a flat belt and a toothed belt; as shown in the traction belt used in FIG. 42, it can be seen from the enlarged sectional view of the left view: the middle compression area of the traction belt is a flat belt, The synchronous traction areas on both sides are toothed belts.
  • the pressure device is separately shown from the pressure chain plate device, that is, only the pressure body 102 and the pressure roller 103 are drawn on the left. Device, only the pressurizing chain plate 104 and the chain plate tensioning wheel 106 are shown on the right side. In practice, both sides are the same, as shown in the top view.
  • the layered combination of flat metal belt and non-metal toothed belt is mainly used for electromagnetic traction; as shown in the composite electromagnetic traction belt used in Figure 45, the inner layer is a non-metal toothed meshing layer. The pulley meshes to achieve synchronous traction.
  • the outer layer is an electromagnetic traction traction layer made of a ferromagnetic metal sheet material. It is used to achieve magnetic traction and pressure traction with the electromagnetic chuck.
  • the electromagnetic traction belt can also use the flat type shown in Figure 39.3. Metal traction belt.
  • the input power of the input shaft 4 flows through the traction synchronous belt pulley 90 and is introduced into the flat metal traction belt 105.
  • the input and output traction belt groups are respectively two parallel side by side.
  • the traction belt is composed of two parts, as shown in the figure A and B.
  • the working sides of the two opposite traction belts run in the same direction and the speed is synchronized.
  • the working surfaces of each traction belt are pressed by a pressure device. , Pressurizing roller 103, pressurizing chain plate 104, etc.
  • the speed-locking block is tightly clamped to transmit power by friction traction transmission.
  • the speed lock block and the shift lever are connected in a moving pair relationship, and can move freely along the shift lever.
  • the slide arm of the speed change arm and the moving sub sleeve on the speed block constitute a mobile pair link, which can be directly formed by the cooperation between the two.
  • the mobile pair can be lined with a low friction material sliding sleeve and lubricating oil), can also use a variety of existing rolling type mobile pair, as shown in Figure 39.2, while the speed lock block itself can freely rotate around the speed rotation axis 112, about
  • the details of the speed-lock block are shown in the relevant parts of Figures 40, 41, and 42 to achieve free movement and rotation while transmitting power.
  • the circular guide 91 is the running track of the speed lock block.
  • the effective motion trajectory after being combined with the traction belt is determined by the effective working surface of the traction belt and the effective working area of the circular guide.
  • the circular guide is composed of the linear area (working area) and the arc of the track.
  • Area (transition zone) consists of trajectory constrained positioning and guidance for the speed lock block, and its input and output working area guide rails are parallel to each other to ensure that the speed lock block can achieve real-time and other characteristics of speed change when it is effectively working, that is:
  • the design principle is: The range of the linear area of the ring guide should be longer than the length of the effective working area of the traction belt, that is, the effective working area of the traction synchronous belt can only be entered when the speed lock block is fully linear.
  • the main advantage of this solution is that it converts the reciprocating operation of the shift lever into continuous unidirectional rotation, eliminating a series of reciprocating linear motion conversion links and running smoothly. And high efficiency.
  • the mechanism uses continuous unidirectional input and output traction timing belts to operate a series of continuously circulating shift arms that have a common rotation center in the variable speed rotation assembly and are distributed at a certain angle.
  • Corresponding lock blocks are alternately combined to realize power transmission. Continuously adjusting the position of the central axis of the variable-speed rotation by the speed-adjusting handle can achieve stepless speed change.
  • the input and output sections are basically the same in structure; for example: the input / output traction belt and the input / output traction pulley mechanism are basically the same, which is beneficial to simplicity Design, reduce production costs.
  • Figure 40 Structure of speed lock block (1)
  • Figure 41 Structure of speed lock block (2)
  • Figure 42 Structure of internal and external dual-track restraint type and pressure device
  • the speed lock block includes: a speed lock positioning base 111, a radial bearing 41, a speed lock rotation shaft 112, a moving auxiliary sleeve 100, a speed lock traction lug 101, a speed lock pressure bearing connection body 110, and friction Traction surface 97, guide roller 98.
  • the speed-locking rotating shaft 112 is fixedly connected to the moving auxiliary sleeve 100, and forms a rotating pair connection with the speed-locking positioning base 111 through the radial bearing 41.
  • the speed-locking positioning base 111 is pressure-connected to the speed-locking lug 101 and the speed-locking block.
  • the body 110 and the friction traction surface 97 are fixedly connected to form the main body frame of the speed lock.
  • the friction traction surface 97 is actually the outside of the traction lug 101 of the speed lock.
  • the material is selected from the material with a large surface friction coefficient combined with the work of the traction belt.
  • the block pressure connecting body 110 connects the two symmetrical halves, and mainly bears the pressing force of the speed lock block from the traction belt.
  • the pressure connecting body 110 is designed as As shown in the figure, for the same reason, in order to avoid the movement interference in the arc area of the track, the speed-lock positioning base 111 is designed as shown in the figure (the preferred embodiment), and it is aligned with the guide roller 98 and the ring guide 91.
  • the middle wheel and the speed positioning base cooperate to lock the main body of the speed lock block.
  • the guide rollers on both sides constrain the degree of freedom of the lock block to a specific range to ensure that the lock block stays upright when entering the linear area of the ring guide. In the case of lower accuracy, the middle can also be removed.
  • Roller which uses two guide rollers and speed-locking positioning seat installed symmetrically to limit the running trajectory.
  • the locking block traction ear plate 101 can be designed as a sector or an offset offset type to obtain a more concentrated and effective space utilization rate, thereby improving the space layout on the basis of the total area of the ear plate and obtaining a larger Gear ratio range.
  • the speed lock block can be designed as a two-half mating type, and the two halves are connected into one by bolt 114. As shown in Figure 41, the speed lock block works under pressure, so the strength of the bolt Not too demanding.
  • a guide opposite roller 113 can be added to the speed-locking positioning base 111, which is reflected in the front view, that is, a directly below the middle guide roller, as shown in FIG. 40. , 40.1.
  • the solution in FIG. 41 can also be adopted, and the speed-locking positioning base 111 is designed to be circular, and a large radial rolling bearing is equipped on the outer surface to implement rolling guidance.
  • the dual-track constrained-guided speed lock block in Fig. 42 can also adopt full rolling contact guidance.
  • a guide roller can be set to convert the sliding guidance into rolling guidance.
  • the inner and outer dual-track constraints run in the middle of the dual-track and have a symmetrical structure.
  • the dual-track paired-clip-locking speed positioning seat is a constraint-guided type
  • the same large rolling bearing cannot be used to achieve the effect of rolling guidance.
  • large rolling bearings do not contact the inner and outer tracks at the same time.
  • this guide rail only serves as an auxiliary guide, while the track arc transition area has no precision requirements for the guidance, and only requires high accuracy within the short range of the track entering the work area.
  • each speed-locking block can be cross-combined.
  • the thrust bearing type in FIG. 42 can also adopt FIG. 40.
  • the speed lock block should minimize the mass and size of the traction lug on the cornerstones that meet the strength and traction ability, in order to reduce the rotational inertia of the rotating system and the working space, and obtain more Wide range of gear ratios.
  • FIGs 4, 42.1, 42.2, and 42.3 are related diagrams of the pressure device of the patent.
  • the pressure device includes a pressure body 102, a pressure roller 103, a pressure chain plate 104, a chain plate tensioning wheel 106, and the pressure of the pressure body. It is transferred to the pressure chain plate by the pressure roller.
  • the pressure chain plate is composed of a single row of convex and concave mating and overlapping chain plates hinged by the chain plate pins 116. As shown in Figure 42.2, the two rows of chain plates can be overlapped and overlapped with each other.
  • the combination is shown in Figure 42.3, so as to achieve uninterrupted contact pressure with the pressure roller 103 and achieve a stable and continuous pressure effect.
  • the other side of the pressure chain plate is in contact with the inner side of the traction belt, and evenly transmits the pressure to the traction belt.
  • the pressurizing power of the pressurizing body 102 may be a pre-compressed spring force, a mechanical rigid force, an electromagnetic force, a hydro-pneumatic force, and the like.
  • the traction belt and the lock block of this type of transmission are fully synchronous tangential clutches, there is no geometric sliding, and it is easy to achieve precise pressure. Therefore, it can also be adopted. Compact in a rigid manner.
  • the shift arm assembly is composed of a certain number of shift arms with a common rotation center. Due to the "angular velocity differential vibration" effect between different shift arms when entering the work area, the shift arms on different straight lines cannot be fixedly connected. Connection as shown: Transmission arm on the same straight line It is fixedly connected through the same coupling ring that cooperates with the radial bearing. The transmission arms on different straight lines are connected through different coupling rings that have a common rotation axis. They have independent degrees of freedom for rotation within a certain range. With transitional offside and centering issues when entering the arc area of the ring guide rail, the shifting arms are connected to each other by an offside traction spring 95.
  • Figure 43.1 shows the axial arrangement schemes of different coupling rings, which have smaller radial dimensions, and are used in the field of speed regulation with large gear ratios.
  • Figures 43.2 and 43.3 show the radial arrangement schemes of different coupling rings, which have superimposed radial dimensions and have relatively large The large radial size is used in the area where the speed adjustment range is small.
  • a symmetrical connection can be adopted as shown in Figure 43.3.
  • the situation shown in the figure is not removable. The removable type is bolted at the corresponding welding place in the figure.
  • the axial arrangement of different coupling rings can also increase the balance reinforcement rib 119 for symmetrical connection; as shown in Figure 43.4, this illustration is detachable, and the reinforcement rib 119 and the transmission arm are adopted.
  • Bolted connection When the speed adjustment range is small, the shifting range of the shifting arm is small, which can reduce the number of shifting arms to simplify the structure. As shown in Figure 43.5, the three pairs of shifting arms have a compact and symmetrical structure.
  • the effective working area of the traction belt is short and the speed adjustment range is small, there will be no situation where three adjacent transmission arms are combined with the traction belt at the same time, that is, three adjacent transmission arms will not participate in the work at the same time.
  • Fig. 44 Assembly drawing of continuous rotation type continuously variable transmission.
  • the parallel and vertical assembly process of input and output traction belts is generally adopted.
  • the advantages of this are: (1) the translation direction of the variable speed rotation assembly is horizontal in speed adjustment, which facilitates easy speed adjustment; (2) traction The belt runs vertically, and will not cause slight deflection due to the influence of gravity. Good transmission ratio stability and strong anti-interference performance; (3) It is convenient to retain the traction oil film on the traction belt, and it is automatically and uniformly distributed under the combined effect of gravity and traction motion; (4) It is beneficial to the shifter arm to better transition to offside and The angle return is sufficient to fully recover the pulsation deviation phenomenon of the rotational angular displacement.
  • the gear shifter adopts a retractable design.
  • the gear shifter is divided into two, and the two parts are connected in a movable pair relationship through a telescopic movable auxiliary sleeve 120.
  • the inner part is connected to the gear arm coupling ring, and the outer part is connected to the speed lock.
  • the blocks are connected in a rotating pair relationship, and the mobile pair is cancelled, so that during the shifting process, the limit position of the trajectory end of the shifting arm does not exceed the space surrounded by the outer ring guide rail.
  • the other structure of the lock block is roughly the same as the previous one. Details can be Refer to the related drawings of Figs. 40, 41, and 42.
  • the peripheral ring guide can also be combined into an integrated type by the bilateral setting structure described above. If the return spring 81 is installed in the moving auxiliary sleeve 120, the inner rail can also be removed, as shown in the figure. This structure can greatly reduce the transmission space size.
  • Fig. 45 Assembly drawing of electromagnetic traction transmission
  • the combination process of the traction timing belt and the speed lock block adopts electromagnetic suction traction.
  • the speed lock block includes an electromagnetic chuck 123, a speed lock positioning base 111, a radial bearing 41, a speed lock rotation shaft 112, and a moving auxiliary sleeve.
  • the corresponding electromagnetic traction belt is a composite electromagnetic traction belt, as shown in the figure:
  • the inner layer is a non-metal toothed meshing layer that meshes with the timing belt wheel to achieve synchronous traction, and the outer layer is an electromagnetic made of ferromagnetic metal sheet material
  • the suction traction layer is used to realize magnetic suction and pressure traction with the electromagnetic chuck;
  • the variable speed rotation assembly includes a speed variator 121, a radial track 122, and an electromagnetic lock block.
  • the interlocking working pace of the lock blocks on different straight lines is achieved through electromagnetic control, thereby eliminating the "angular speed differential vibration" effect between different shift arms when entering the work area, so each shift arm can adopt an integrated approach
  • the arrangement as shown in the figure, adopts an integrated disc-type shifting structure.
  • the mobile sub-sets 100 of all the speed-locking blocks cooperate with the radial track 122 on the shifting plate 121 and are guided by the ring guide 91 at the same time.
  • the working current of the electromagnetic chuck is introduced by the external control circuit through the brush, electric ring, sliding static contact piece, and moving contact piece.
  • the control follows the "interlock priority" control principle: the speed of the electromagnetic chucks of the lock blocks on the same line is the same.
  • the speed-locking block is electrified, that is, only one pair of collinear electromagnetic chucks can work at any time, and it is controlled according to the principle of priority, which always makes the speed-locking block in the best force state work preferentially. .
  • the electromagnetic attraction force is the internal force of the system, and the system balances itself locally without the need for a pressure device.
  • the control method is flexible, convenient and easy to adjust. Because it can ensure interlocking traction, it can get more
  • the large boost interval achieves the same quick and easy speed adjustment effect as the wide boost interval with the reciprocating effect.
  • the electromagnetic shifting disk belongs to the solid shaft type. All the speed-locking blocks are set on the same rotating body.
  • the integrated disc shifting system has a reasonable structure, simple and reliable, stable operation and smooth offside.
  • the single-track restraint type of Figure 39 can also be adopted.
  • the electromagnetic chuck can be designed as a square, sector or offset type to obtain more concentrated and effective space utilization. On the basis of the total area of the suction cup being improved, the space layout is improved to obtain a wider range of speed ratios.
  • the electromagnetic traction belt can also be a flat metal traction belt as shown in Figure 39.3.
  • the speed-locking positioning seat can also add radial rolling bearings as shown in Figure 42.4 to reduce wear.
  • this electromagnetic interlocking control method can not have overlapping working areas at the time of alternate working of different speed-locking blocks, so there is a power flow micro-gap interruption interval.
  • double The unit works in a staggered cross-relay mode, eliminating this transient power flow interruption zone (as shown in Figure 45.1) and obtaining a stable continuous power flow output.
  • the traction belt works on both sides.
  • the traction belt wheel can be designed as a two-wheel drive, that is, both the driving wheel and the driven tensioner are set as the driving wheel, and the traction timing belt is worked together.
  • Fig. 46 Derivative series of electromagnetic traction transmission
  • the solution shown in Figure 46.1 is an enhanced design for the unilateral stress conditions of the speed lock block in Figure 45.
  • electromagnetic chucks are symmetrically arranged on both sides of the speed lock block, and double sets of traction belts are used to transmit power to increase the load. Capacity, suitable for high power occasions.
  • a two-phase or multi-phase parallel transmission unit can be set up to divide the original number of speed lock blocks into two or more component phase settings to reduce the number of speed lock blocks in each camera group.
  • the electromagnetic control pace is still equivalent to the single-phase type, that is, it is controlled according to the principle of "interlock priority" in the range of multiple camera groups.
  • the effects of interrupting the micro-gap power flow and expanding the gear ratio can be achieved at the same time.
  • a set of speed-locking blocks are evenly distributed in each phase transmission disc, and the phases and phases are connected by elastic couplings; as shown in Figure 46.2, the radial track distribution on the left and right transmission discs is shown in the right figure.
  • This elastic coupling 127 is equivalent to the action of an offside traction spring 95. It makes the two phases not only implicate each other, but also maintains a certain degree of freedom of rotation. On the basis of smooth traction, the "angular velocity differential vibration" effect is eliminated, so that there is no need for interlock control between the two phases.
  • the speed lock blocks between different phases allow the existence of electrified crossover and overlapping work areas, eliminating the phenomenon of micro-gap power flow interruption. Continuous power flow output is obtained through complementary work of the speed lock blocks between the two phases.
  • the left and right transmission discs in the 46.2 illustration transmit power through the two sides of the same traction belt, and the transmission discs rotate in opposite directions. This coupling is a reverse elastic coupling;
  • the mechanical traction type transmission shown in FIG. 39 can also adopt the split-phase setting method as shown in FIG. 46.2, so that the number of speed-locking blocks in the variable-speed rotation assembly of each phase is reduced, and the included angle of the transmission arm is increased.
  • the phase-to-phase elastic connection is used to eliminate the "angular velocity differential vibration" effect, thereby obtaining a wider range of speed changes.
  • the design principle is: The phases of the traction belt are connected, and the phases of the variable-speed rotating assembly are connected in an elastic coupling manner.
  • the transmission structure can be arranged as shown in Figure 46.3.
  • the electromagnetic traction belt and the electromagnetic lock block are radially arranged, and the shifting arm is designed for scalability.
  • the detailed structure is shown in Figure 44.3. .
  • Figure 47.1 is a simplified diagram of this type of transmission mechanism. This solution is roughly the same as the overall mechanism of the type in FIG. 39, with the following differences:
  • the combination of the traction belt and the speed lock block is different, and the transverse clip is used for traction.
  • the The side-mounted speed lock block 128 has a simple structure, the speed lock positioning base 111, the speed lock rotation shaft 112, the radial bearing 41, and the mobile auxiliary sleeve 100 are all located on the outer side of the pressure traction body 129 of the speed lock block, and cooperate with the shift arm.
  • the swing space of the moving pair is not limited by the interference of the lock block, and there are no components inside the pressure-bearing traction body 129, which is conducive to reducing the size of the lock block and optimizing the force design.
  • the details are shown in Figure 47.2.
  • This figure is a unilateral pressure-bearing traction body. Although there is a biased component, the structure is simple. In the case of high power, pressure-bearing traction can be set symmetrically on both sides of the shift arm moving sub-set 100. And add a set of traction systems, as shown in Figure 47.1.
  • Figure 47.3 is a simplified mechanism for the solution shown in Figure 39 above. It adopts a unilateral traction belt to press and lock the speed lock block. The other side balances the pressure by a balance pressure bearing device. As shown in the figure, it depends on the balance bearing on the transmission arm. The contact between the pressure roller 130 and the balance pressure plate 131 balances the pressing force of the pressure device on the speed lock block. At this time, the speed lock block also becomes half, as shown in Figure 47.3.1, thereby simplifying the structure, Reduced moment of inertia. In addition, in order to further simplify the mechanism, the roller balancing device can also be removed, but in this way, the variable speed rotation assembly will be subject to a large axial force, which can be solved by adding thrust bearings in the axial direction.
  • the balance plate In order to improve the force contact surface, a cone wheel surface contact can be adopted, but the balance plate needs to move synchronously with the speed control block, so that the central axis of the balance pressure plate 131 is always coaxial with the variable-speed rotation central axis 9.
  • the balance plate In general, the balance plate can be fixed and stationary.
  • Fig. 48 Model tube diagram of the embodiment of the space structure type of the constant angular isomorphous continuously variable transmission
  • Fig. 48 Model tube diagram of the embodiment of the space structure type of the constant angular isomorphous continuously variable transmission
  • the speed lock track is arranged in a direction perpendicular to the drawing.
  • the section in the figure is the vertical section of the speed lock track, as shown in Figure 21.
  • the speed lock pillow is along the speed lock track in the direction perpendicular to the drawing as shown in the figure.
  • the moving pair marked with k in the figure acts as a speed control block. It only moves in the direction of the arrow during the speed adjustment process and is usually in a static state. This is the difference from other moving pairs: it is allowed to lock in the direction perpendicular to the drawing.
  • the speed pillows move along the parallel direction of the speed lock track, as shown in Figures 48.2 and 48.4.
  • the m rod fixed to the speed lock is the equivalent speed track of the speed control block k, so as long as it is not relative to the direction of the speed track Movement does not change the transmission ratio.
  • Any speed change unit (lock speed pillow, speed lock track and corresponding speed change arm combination) shown in the picture can be designed as the transmission input or output speed change unit, that is: if one speed change unit is used as the input speed change unit, the other The transmission unit is an output transmission unit, and vice versa, both can be used interchangeably.
  • the input and output shift units (speed lock pillows, speed lock rails, and shift arms) in Figure 48.1 are located on the same level and are symmetrically arranged.
  • the input and output shift arms are separated from each other and can be flexibly extended through a set of head ends at both ends.
  • the variable constant angular double universal joint 132 connects the two shift arms, that is, the torque of the shift arm around the rotation center axis can be transmitted to the other variable shift arm through the constant angular double universal joint 132, Make the two transmission arms have the characteristics of constant angular velocity motion, and the relationship between the input and output transmission units meets the "equal angular velocity reversal position similarity shift principle", and the position of the speed control block k can be changed steplessly by stepless movement.
  • the structure has “equilibrium continuously variable transmission characteristics".
  • the input-output transmission unit can be rotated at any angle about the rotation center axis 9 to constitute a space transmission type.
  • the "space shift type” here refers to the movement relationship between the input and output motion transmission members is a space motion type, which is different from the "special space shift structure type”.
  • the two shift arms are fixedly connected.
  • Each lock and the speed control block k are in a mobile pair relationship when the speed is adjusted, and they are fixedly connected when the speed is not adjusted. They are connected to the corresponding shift arm through the corresponding rotary pair and mobile pair.
  • the speed-changing device steplessly adjusts the position of the speed control block k in the direction of the arrow, and changes its distance from the rotation center axis 9, which can equivalently change the distance between the rotation center axis 9 and the speed-locking track, that is, changes the effective transmission arm The length of the transmission ratio changes.
  • This solution can evolve into a space-shifting type by changing the fixed azimuth of the two shift arms, and changing the azimuth of the shift unit simultaneously; for example:
  • the parallel fixed structure of the two shift arms in the illustration is rotated 90 degrees along the rotation center axis 9 Even if the transmission unit changes in the same step, it will be transformed into a space transmission type.
  • Figure 48.3 In this solution, the two shifting units share a shifting arm, but the distances from the center axis of rotation are different, that is: the effective shifting arm length varies, and the k position of the governing block is adjusted steplessly in the direction of the arrow, and the ratio of the two effective shifting arm lengths will occur. Change, so the transmission ratio changes.
  • the characteristics of this speed regulation scheme are: The farther the speed regulation block k is from the locked track area, the closer the two speeds are, and the accuracy of the speed regulation transmission ratio is gradually refined, and the rate of change of the transmission ratio shows a deceleration trend, which belongs to the speed regulation accuracy.
  • Variable types, but be clear its transmission ratio is still infinitely variable. This type of mode is suitable for the occasions that require different adjustment accuracy for different transmission ratios in different areas, such as the occasions that require higher speed accuracy for low speed areas.
  • Figures 48.4, 48.5, 48.6, and 48.7 are special space transmission structure types.
  • the input and output transmission units are connected by a space isoangular speed transmission mechanism (the space bevel gear transmission is shown).
  • the input and output units can be set in any space orientation. It is shown that the illustrated mechanism is still drawn in the same plane.
  • Speed control block, lock block, transmission arm connection method, speed control method is similar to Figure 48.2, except that the two transmission arms pass through the space of constant angular velocity Gear connection, can change two
  • the speed change unit relatively moves with the plane to form a space speed change mechanism.
  • the transmission ratio can be changed by steplessly adjusting the position of the speed control block k in the direction of the arrow.
  • Figures 48.5 and 48.6 are similar in structure, and the speed control block, speed lock block, transmission arm connection method and speed control method are similar to Figure 48.1, the difference is that the equal angular velocity connection mechanism of the two transmission arms is different, and the moving elements are different during the speed adjustment process.
  • the position of the speed control block k is adjusted steplessly in the direction of the arrow, and the elements in the dotted frame move in synchronization with it.
  • the center axis 9 of the shift arm changes the plane of motion through the bevel gear transmission group 31, and meshes with a common ultra-long spur gear 133 through the plane gear 12 to achieve the motion connection between the two shift units.
  • the plane gear 12 moves axially relative to the ultra-long spur gear 133, the transmission angular velocity does not change, ensuring constant angular speed transmission, and the distance between the rotation center axis 9 and the speed-locking track is changed, that is, the effective transmission arm is changed Length, thus changing the transmission ratio.
  • the gear 12 and the ultra-long cylindrical gear 133 can also adopt a helical gear transmission structure, but when the speed is adjusted, the two transmission units need to coordinate with each other; the scheme of FIG.
  • the auxiliary pair 134 is connected, and can move axially at the same time while transmitting torque, so that the elements in the dotted frame ensure constant angular speed transmission when the speed is adjusted.
  • the two meshing gears 12 in FIG. 48.6 can be space gears, which can make the overall layout of the transmission mechanism more flexible and diversified.
  • the scheme of Figure 48.7 obtains the change of the effective transmission arm by moving the space bevel gear train to adjust the speed.
  • the space bevel gear is fixedly connected to the rotation center axis 9 of the transmission arm, and between the transmission arm and the respective rotation center axis 9 It is connected by the sliding key pair 134, which can move axially while transmitting torque.
  • the rotatable movable pair speed control block 135 is connected in a rotational pair relation with the rotation center axis 9 and only the radial translation of the rotation center axis 9 The amount of displacement is restricted, and both can rotate freely and move axially.
  • the types of mechanisms disclosed in this illustration are applicable to both reciprocating and continuous rotating types.
  • the illustrated embodiment is a reciprocating variable speed type.
  • the speed lock pillow and the speed lock track need to be replaced by a traction belt and a speed lock block.
  • the single shift lever is replaced by multiple shift arms (see the relevant mechanism above).
  • Its disadvantages are: For the input and output transmission units that are not in the same plane of movement, most of the related components such as the speed lock block, the guide rail, and the shift arm cannot be cyclically used at the input and output ends, and the input and output component separation methods need to be set separately. This increases the number of parts and complicates the mechanism.
  • variable angular speed transmission mechanism In order to meet the needs of more occasions, to increase the power-to-weight ratio and power-to-volume ratio, it is possible to use any constant angular speed transmission mechanism, variable mechanism and related plane, space motion conversion, transmission mechanism (such as: flat gear, Space gears, plane gear trains, space gear trains, shafts, belts, connecting rod mechanisms, flexible steel wire shaft drives, worm gear drives, constant angular velocity couplings, etc.) are used for constant angular velocity transmission.
  • constant angular velocity transmission conditions can be met .
  • variable angular speed transmission can be adopted to obtain special speed and specific regular speed output.
  • Figure 49 A schematic diagram of a common component symbol of a mechanism, where the component symbol table is a general symbol for the patent;
  • the shifting mechanism of FIG. 48 is still a flat shifting type, and only the spatial layout structure between different shifting units is provided, and the movement inside the same shifting unit is still It is a plane motion, that is, the movement of the shift arm is still a plane motion.
  • the speed change mechanism is a type of space speed change, and the movement of the speed change arm is space movement. As shown: Power flow from input shaft
  • timing belt 2 directly drives the shift lever 8 for a space pendulum movement equivalent to the cyclic trajectory of the timing belt.
  • This illustration is a reciprocating type.
  • a rack and pinion mechanism passes the overrunning clutch.
  • Output one-way torque (other methods can also be adopted, see above).
  • the stepless adjustment of the position of the rotation center shaft 9 of the shift lever can steplessly change the transmission ratio. Since the variable speed pestle is a space motion, its corresponding motion pair is a space motion pair.
  • the illustration shows a combined pendulum ring mechanism. Among them, the trajectory of the timing belt is constrained by a special limit guide track limit, which has extremely high motion accuracy.
  • the space type is similar to the plane type continuously variable transmission mechanism, except that the plane swing or rotation of the shift lever is changed to a space swing (also can be viewed as a space combination of a multi-phase plane swing transmission mechanism for analysis).
  • the main difference lies in the motion output link after the gear lever is shifted.
  • the motion input link generally adopts the timing belt wheel to transmit power to the timing belt.
  • the timing belt is hinged with the shift lever. Therefore, the synchronization
  • the running trajectory of the belt will determine the spatial trajectory of the shift lever; its motion output mode can adopt reciprocating or continuous rotation type.
  • the output mode of the reciprocating type is shown in Figure 50 (refer to the related structure of the plane reciprocating variable speed type).
  • the output structure of the continuous rotation type is also similar to that of the flat-speed transmission type, and can be output by the wafer traction belt or electromagnetic suction traction belt.
  • the one-way continuous traction is output by the one-way suction traction of the electromagnetic chuck and the traction belt.
  • a multi-unit out-of-phase arrangement scheme can be adopted.
  • a track guide area is provided in order to smoothly engage the lock block with the traction belt.
  • This figure is a diagram of the mechanism.
  • the input and output motion coupling mechanisms of the space type and the plane type are basically the same.
  • sliding pairs can be replaced by rolling pairs;
  • rolling pairs include: sliding moving pairs, sliding rotating pairs; rolling pairs include: rolling moving pairs, Scroll and rotate the pair).

Abstract

La présente invention concerne une transmission mécanique de vitesse variable à l'infini possédant une vitesse angulaire égale, une orientation identique, une paire inférieure d'éléments et un rapport de vitesse variable élevé. Ladite transmission fait partie du domaine de la technologie de fabrication et de conception d'une transmission mécanique de vitesse variable à l'infini. Cette transmission est conçue en fonction du principe de vitesse variable de vitesse angulaire égale, de transformation de la direction identique et d'orientation similaire. Des modules de vitesse variable d'entrée et de sortie de la transmission sont placés par rapport à une vitesse angulaire égale et à une orientation identique. Le mode de réalisation préféré de la transmission est spécifié par le mode de vitesse variable de parallèle et de trois points alignés. Les éléments de vitesse de verrouillage d'entrée et de sortie présentent une trace parallèle dans la zone du mouvement efficace. Les modules de vitesse variable à phase identique satisfont la relation des trois points alignés. Ladite transmission constitue une transmission mécanique de vitesse variable à l'infini de grande puissance et très efficace, exempte d'impulsions, de vitesse uniforme, spécialement non frictionnelle, ladite transmission possédant une paire inférieure d'éléments. Le module de transmission principal de la transmission permet d'effectuer une transmission avec la paire inférieure d'éléments, de telle manière qu'il possède des charges importantes et une plage importante de vitesses variables. La transmission peut produire avec précision et en douceur un couple de sortie lors d'une accélération, d'un ralentissement, d'un passage par zéro, d'une marche arrière, d'une proximité de zéro et d'une vitesse ultra lente. Elle peut être commandée de manière adéquate et simple. Selon ladite invention, cette transmission peut être utilisée dans les domaines de l'éclairage, du transport maritime et terrestre lourd, du textile, de la métallurgie, de l'industrie chimique, du forage, de l'agriculture, de l'industrie de la défense nationale, et similaire, où des exigences en matière de vitesse variable sont ressenties.
PCT/CN2004/000576 2003-05-30 2004-05-31 Transmission mecanique de vitesse variable a l'infini WO2005001312A1 (fr)

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CNB03140569XA CN100371628C (zh) 2003-05-30 2003-05-30 等角速同形位低副高变速比机械无级变速器
CN03140569.X 2003-05-30

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CN106838030A (zh) * 2017-04-13 2017-06-13 青岛科技大学 一种轴向位移补偿的等角速万向联轴器
CN107939933A (zh) * 2017-11-17 2018-04-20 中国人民解放军陆军装甲兵学院 一种齿轮连杆脉动式无级变速器
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CN104533983A (zh) * 2014-12-20 2015-04-22 重庆钰康机械有限公司 摩擦式凸轮单向转动机构
CN106838030A (zh) * 2017-04-13 2017-06-13 青岛科技大学 一种轴向位移补偿的等角速万向联轴器
CN106838030B (zh) * 2017-04-13 2023-09-05 青岛科技大学 一种轴向位移补偿的等角速万向联轴器
CN107939933A (zh) * 2017-11-17 2018-04-20 中国人民解放军陆军装甲兵学院 一种齿轮连杆脉动式无级变速器
CN110084955A (zh) * 2019-06-05 2019-08-02 聚龙股份有限公司 制动装置及货币处理机

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