WO2005001312A1

WO2005001312A1 - A mechanical infinitely variable speed transmission

Info

Publication number: WO2005001312A1
Application number: PCT/CN2004/000576
Authority: WO
Inventors: Guobin Wang
Original assignee: Guobin Wang
Priority date: 2003-05-30
Filing date: 2004-05-31
Publication date: 2005-01-06
Also published as: CN100371628C; CN1553064A

Abstract

A mechanical infinitely variable speed transmission with equal angular speed, identical orientation, low pair of elements and high variable speed ratio is disclosed, which belongs in mechanical infinitely variable speed transmission design and manufacture technology field. The transmission is designed in terms of “the variable speed principle of equal angular speed, identical direction transformation and similar orientation”. The input and output variable speed units of the transmission are arranged with equal angular speed and identical orientation. The preferred embodiment of the transmission is embodied by the variable speed mode of “parallel and three points in one line”. The input and output lock speed elements have parallel track in the area of the effective movement. The variable speed units with identical phase meet the relationship of “three points in one line”. The transmission is a special non-frictional, uniform speed, non-pulsed, high effective and large powered mechanical infinitely variable speed transmission with low pair of elements. The main transmission unit of the transmission transmits with low pair of elements such that it has large loads and large variable speed range. The transmission can precisely and smoothly output torque in speed-up, speed-down, zero crossing, reverse moving, zero ultra-proximity and ultra-low speed, and conveniently and simply be controlled. The transmission according to the invention can be used in the light and heavy vehicle, ship, textile, light industry, experiment and the like where there are requirements for variable speed.

Description

Mechanical continuously variable transmission

Technical field

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.

In the prior art, friction-driven mechanical continuously variable transmissions are widely used. Although 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.

In addition, at present, 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. In the prior art, there is also 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. It is different from meshing transmission and friction transmission. It is a quasi-meshing transmission mode between the two. It has the advantages of low sliding rate, precise transmission, high wear resistance and high impact capacity. The manufacturing cost of the chain is relatively high, and the quality of the chain is large, which restricts the further increase of the running speed. In addition, the polygon effect of the chain transmission will cause a certain pulsation of the output speed.

In the prior art, there is also a pulsation type continuously variable transmission, which adopts a geometrically closed low pair mechanism, which has the advantages of reliable operation, high bearing capacity and stable transmission performance. However: The current pulsating continuously variable transmission has several fatal weaknesses, which restrict its development to a wider field: 1. The pulsation of the output makes it impossible to use in places with high requirements on the uniformity of the output; The auxiliary cooperation of the overrunning clutch and the optional flow filter can reduce the pulsation, but the actual power flow transmission is still output in the form of pulse intervals according to the theoretical value. This discontinuity of the power flow is a major factor that causes the low efficiency of the pulsation continuously variable transmission. Second, 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. Important reasons; Third, as an output mechanism, 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. Summary of the invention

In view of this, 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.

In the following, the basic working principle and guiding design ideas of the present invention are introduced: The principle of constant angular velocity, isomorphic motion—any one or more linear rods make a rotational movement, and the rotation center of the rotational motion is on the line where the respective linear rods are located, but Except when the linear rod rotates along its own axis, when the instantaneous rotation angular rate (absolute value) of the linear rod is equal (or proportional), any point on the linear rod other than the center of rotation is at an angle with the linear rod itself Movements with equal regularity in the directions that are equal or complementary and coplanar or equivalent coplanar (except for directions with an included angle equal to 0 degrees or 180 degrees).

Among them: 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. Since the angle between the rotation axis and the linear rod is equal to 0 degrees or 180 degrees, it is meaningless for the study of the transmission of the present invention, so it is excluded. In fact: 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.

The following focuses on the movement in the plane of rotation of the rotating rod:

Before introducing, first explain each term:

Constant angular velocity isomorphism:

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.

Real-time constant angular speed rotation-rotation with equal instantaneous rotation angular rate (absolute value). Iso-regular motion (hereinafter referred to as 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. For a transmission, it means that 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.

Among them, the speed and acceleration in this concept are measured by scalars, and do not involve the direction of vector motion. For example, 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,

3 as an example, 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. Among them, for the sake of brevity, Make the following provisions: The linearly arranged and integrated rotating rods can be collectively referred to as shifting levers, and the other types of rotating rods are referred to as shifting arms. For example, 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. 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.

In accordance with the principle of practical value, the following description focuses on the case where the angular velocities are equal.

As shown in Figure 1: 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. At this time, the speeds of points a, b, and c in the direction of the arrow have regular characteristics.

Based on the above principles, a theoretical model of continuously variable transmission with equal characteristics can be constructed:

a: According to the principle of lever amplification of the rotating lever, when the angular velocity is constant, changing the length of the lever can change the point and line speed;

b: According to the principle of constant angular velocity and isomorphic motion, for a rotating rod that moves at the same angular velocity in real time, as long as the isomorphic characteristics are satisfied, isomorphic motion can be obtained.

Therefore, on one or several real-time constant angular velocity rotating rods, on the premise that the isomorphic position characteristics are satisfied, the position on the rotating rod can be changed steplessly, and the linear characteristic speed of stepless changes can be obtained.

As shown in Figure 2: 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. Obviously, steplessly changing the position of each point on the rod can change the linear velocity of the point steplessly.

The following is a model of the continuously variable transmission with the same characteristics: Take any point a in Figure 2 and use it as the input point of a uniform linear motion along the direction of the arrow, then the arrows at points b, c, d, e, f, g, and h The pointed direction will have a uniform speed linear motion output. Steplessly changing the position of the rod on each point can obtain a uniform speed linear motion output with a stepless change in the transmission ratio. This mode can be used in applications with multiple gear ratios, multiple output shafts, and power parallel and shunt applications.

As shown in FIG. 3: 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. However, with the movement of the input a, 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. In order to ensure that b can move stably with a specific transmission ratio, it must be ensured that the arm ratio of a and b transmitting power remains constant. To this end, the connection methods of the shift lever are connected by a mobile pair and a rotary pair, as shown in the figure. As shown in 3, stepless change of the rotation center position of the shift lever M can achieve stepless speed change. Among them, in Fig. 3, 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. When designing the transmission mechanism, 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;

In order to further clarify and refine the reference general principles in the specific design, the second determination theorem of constant angular velocity, isomorphic stepless speed change is introduced below:

Principle of equiangular velocity inversion in the same direction:

At any time, in the effective transmission space, 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). That is, at any moment, within the effective transmission space, 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. In other words: 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.

Among them, the general research and analysis methods of motion are: (1) Space motion is researched into a plane motion in accordance with the "instant space motion as a plane element method"; (2) Plane motion that is not in the same plane is transformed into the same plane Internal research, such as: The conversion research is carried out according to the principle of isotropic angular rotation in the same direction.

In order to make the description clearer, the following is a glossary of some terms:

Transmission unit: Refers to a one-to-one combination of a transmission arm or lever and an associated corresponding motion transmission member. When 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) )

Explanation and analysis of FIG. 4: The combination of the transmission arm m and the corresponding transmission units a, c of the transmission unit a, is equivalent to the same-direction space flipping to the position of the transmission arm n, and after the conversion, the transmission arm m and its The position of the transmission unit combination corresponding to the motion transmission members a and c is shown in Figure 4.1. It is obvious that the motion trajectory of the motion transmission member a in the equivalent flip transformation diagram is parallel to the motion trajectory of the motion transmission member b corresponding to the transmission arm n, and is parallel to c. It is not parallel. Therefore, the arrangement of the motion transmission member c in the original drawing does not meet the characteristics of stepless speed change conditions such as characteristics, and the method of a is adopted in the actual design.

In FIG. 5, the shift arms m and n are connected by constant angular gear transmission, the rotation directions are opposite, and the equivalent shifting transformation diagram of the shift arm m and its corresponding transmission unit a, c of the transmission unit is converted to the position of the shift arm n. As shown in Figure 5.1, it is obvious: In this case, the motion trajectory of c is parallel to b and not parallel to a. Therefore, the arrangement of the motion transmission part a in the original drawing does not meet the characteristics of stepless speed change conditions such as characteristics. c way.

Fig. 6 shows the case where the input and output shift arms are not collinear. Among them, 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. In the figure: Represents the shift arm, and the dotted line represents the motion trajectory of the motion transmission member. Among them: 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 丄 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. The equivalent flip transformation diagram of the figure is obvious: in Figure 6.1.1, the motion trajectory of b is parallel to a, but not parallel to c, the b method is adopted in the actual design; in Figure 6.2.1, the motion trajectory of c is parallel to a, It is not parallel to b, and the c method is adopted in the actual design.

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.

According to the above-mentioned guiding ideology, the input-output speed change unit can be arranged in different planes. Through the constant angular speed transmission mechanism, 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. In order to meet the needs of more occasions, 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. In short, as long as the conditions of constant angular velocity transmission can be satisfied, the above 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. 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. The cross-section of the cone-shaped or pyramid-shaped pendulum and space pendulum running track of the space shift lever can be: polygons such as circle, ellipse, triangle, rectangle, hexagon, or deformation curve and combination curve. Among them, FIG. 10 represents a separate type of input-output transmission unit. The input-output transmission unit is driven by a constant angular space gear. Generally, the speed change process of such a device is performed by changing the included angle of the conical pendulum.

Based on the above types of shifting modes, it is not difficult to find that: 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:

(1) the movement trajectories of the linear motion input and output pieces are parallel;

(2) Three points of the motion input, output point, shift rotation center fulcrum on the shift lever are in line. Mathematical analysis of the principle of parallel three-point, one-line speed change: The introduction of geometric theory, which can be proved by the proportionality theorem of parallel line segments, as shown in Figure 11, its geometric model is: two parallel lines and an intersection line are mutually The cross-combination geometric relationship model; it can be proved that: when the rotation axis k of the intersecting oblique line is constant, the length ratio of the line segment intercepted on the upper and lower parallel lines during the rotation of the intersecting oblique line is always equal to the distance ratio between the rotating axis and the upper and lower parallel lines. On the other side, 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. In practical applications, 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.

Analysis of kinematic mechanism:

The purpose of 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;

B. The purpose of three points and one line: It is caused by the principle of constant angular rotation in the same direction, and the parallel direction of input and output linear movement. If the input and output linear movement directions are not parallel, the angle between the input and output shifting arms is determined according to the principle of the principle of equiangular speed in the same direction and reversing position.

The design principles are:

The general working conditions are

Among them: stepless speed change with constant characteristics

Stepless reversal speed.

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.

According to the input-output motion conversion method and the type of gear lever rotation, the gear shifting device can be divided into: to complex type, continuous operation type;

Parallel three-point one-line speed change principle mode (one) one by one Reciprocating type:

The reciprocating transmission mechanism moves through regular characteristics such as the reciprocating swing output of the shift lever. In order to ensure the continuous output power flow, 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. One-by-parallel three-point one-line variable-speed mode conversion output and other characteristics. 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).

(3) The slider is connected to the linear motion input member (6) through the moving pair, and the power is transmitted to the shift lever (8) by the rotating pair and the moving pair. The shift lever transmits the power to the shift pair and the rotating pair at a specific transmission ratio. Linear motion output (10) is output in linear motion and passed through a rack and pinion machine The structure (11, 12) and the overrunning clutch (14) are converted into a one-way continuous rotary motion, and the motion is output through an output shaft (13). Continuously moving the position of the speed control block (15) up and down can achieve stepless speed change. For details, refer to the embodiments shown in FIG. 21 and the like below.

The variation mode is shown in Figure 13: In this mode, 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. Through the connection of the moving pair and the rotating pair, the fixed position points on the shift lever can be transmitted in the same direction. 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. Among them, the rotating pair and the shift lever where the rotating center axis 9 is located They 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. In addition, you can change the speed by changing the position of the input and output force points on the gearshift lever. .

Parallel three-point one-line speed change principle mode (two) one-to-one continuous operation

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. When the shift lever turns away from the effective area, it separates from the traction timing belt to achieve the effect of one-way continuous operation and continuously adjust the transmission. Stepless speed change can be achieved by rotating the central axis position. For details, refer to the embodiments shown in FIG. 39 and the like below.

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.

According to the above-mentioned guiding ideology: under the condition of meeting the similarity of constant angular velocity isomorphic position and constant angular velocity codirectional reversal position, more variant mechanisms can be designed to meet the needs of different occasions.

The conversion process between uniform rotating motion and hook speed linear motion can be transformed with the help of many current mechanisms. Refer to the "input / output rotation / linear motion conversion mechanism" listed in the examples below. The key of this patent is the constant angular velocity isomorph The construction of the principle of positional movement, the principle of constant angular velocity reversal, the construction of the similarity shifting principle, that is, the construction of a continuously variable transmission model with isochronous characteristics, and specifically constructs a transmission mode that can be easily connected by a linear motion mechanism in current technology. No matter how the transmission ratio changes, 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.

Extending and expanding the application of the principle of shifting-non-equivalence shifting:

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. As shown in 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. In the figure, a solid line represents a shift arm, and 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. In specific applications, 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.

Features and advantages of the invention:

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. At the same time, 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.

This type of transmission has the advantages of reasonable structure, simple operation, accurate and stable, convenient implementation, cost-effective and so on. 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. Adopt the design of "equal angular velocity isomorphic motion principle" and "equal angular velocity co-rotating position similarity shift principle" to overcome the problem The fatal flaws related to the pulsating continuously variable transmission, the entire mechanism's power chain has no weak links, has an equivalent load capacity, can maximize the potential of each link, and has strong load capacity and shock resistance. Its space structure series mechanism design is flexible and changeable, and the drive shaft can be designed in any orientation. It is a unique non-friction type constant speed non-pulsation low-pair high-efficiency high-power mechanical continuously variable transmission. Brief description of the drawings

Figure 1: Schematic diagram of isokinetic isomorphic motion;

Figure 2: The theoretical model of isochronous continuously variable transmission;

Figure 3: Theoretical analysis chart of CVT;

Figure 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)

Figure 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 18: Analysis of the transformation process of motion input;

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 27: Self-locking control series of current-selective wobble plate;

Figure 28: Self-closing internal force pressure control method series

Figure 29: Image analysis of motion laws of input lock and pillow

Figure 30: Several design options for cam profile;

Figure 31: Structure diagram of electromagnetic selective clutch;

Figure 32: Cylindrical Cam Convertible Transmission Arrangement Series

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 46: Derived series of electromagnetic traction 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.

among them:

1. Timing belt wheel 2. Timing belt 3. Slider 4. Input shaft 5. Moving pair

6.Linear motion input 7.Rotary pair 8.Shift lever 9.Rotary central axis

10, linear motion output parts 11, rack 12, gear 13, output shaft

14, overrunning clutch 15, speed control block 16, input traction timing belt

17, output traction timing belt 18, gear transmission 19, transmission pin 20, slider

21, Reversing guide rail 22, Speed lock input 23, Speed lock input

24. Screw nut speed regulating device 25. Output lock track 26. Output lock pillow

27, Speed regulating track 28, Speed regulating handle 29, Transmission pin 30, Selective clutch main shaft

31.Bevel gear transmission group 32, Bevel gear distribution plate 33, Selective transmission frame 34, Roller wheel

35, control cam 36, control power transmission shaft 37, feather key 38, flow selection wobble plate

39, Selective pressure plate 40, Thrust bearing 41, Radial bearing 42, Friction disk surface

43, slewing support 44, speed transmission chain 45, left cylindrical gear distribution plate

46, right cylindrical gear distribution plate 47, transitional reversing gear 48, right output gear

49 、 Left output gear 50 、 Rolling mobile auxiliary outer ring 51 、 Rolling mobile auxiliary inner ring

52, ball (roller, needle) 53, cage 54, key

55.Circular recirculation ball 56.Working area ball

57. Split combined outer ring with circulating ball path 58, ball circulation tunnel tube

59. Integrated outer ring with circulation channel 60. Rolling type mobile pair (rolling guide) , Link mechanism 62 with self-locking function, elastic buffering device

, Oil cylinder (air rainbow, traction electromagnet) 64, Crank connecting rod mechanism

、 Linkage force locking mechanism 66 、 Clamp type clamping force applying device

、 Mechanical traction mechanism 68 、 Remote control traction line

、 Self-closing pressure-applying force cam device 70 、 Movable pressure applying part in the middle

, 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, 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

6. Chain plate tensioning wheel 107, traction pulley meshing teeth 108, traction belt meshing holes 9, annular metal sheet 110, speed lock block pressure connection body 111, speed lock positioning seat, speed lock rotation shaft 113, guide opposite Roller 114, bolt

5.Composite synchronous traction belt 116, chain plate pin 117, toothed pressure chain plate

8. Shift arm coupling ring 119, balance reinforcement rib 120, telescopic movable auxiliary sleeve 1, shift disc 122, radial track of shift disc 123, electromagnetic chuck

4.Combined electromagnetic traction belt 125, toothed meshing layer 126, electromagnetic traction layer 7, elastic coupling 128, side-mounted speed lock block 129, pressure traction body

0, Balanced pressure bearing roller 131, Balanced pressure bearing plate 132, Double angular universal joint with constant angular velocity 3, Ultra-long straight toothed spur gear 134, Sliding key moving pair

5. Rotary movable auxiliary speed control block 136, combined swing ring mechanism Mode of Carrying Out the Invention

The present invention is described in detail below with reference to the drawings.

Figure 17 shows a cylinder diagram of a zero-speed continuously variable transmission of the same angular reciprocating reciprocating type. Among them, 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. For details, 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. 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.

Working principle: The input power flow of the input shaft 4 is distributed among the two symmetrically arranged transmission units via the left and right gear transmission groups 18, and the left and right two-phase transmission units are identical in structure, but in the operating step, the working phase difference is 1/4 or 3/4 cycle (see Figure 29: image analysis below), work in an alternating relay mode to compensate each other. The input of each phase lock lock 22 is reversed when the drive pin 19 enters the arc area of the pulley. The phenomenon of "interruption of current" caused by the process results in continuous power flow output. In order to facilitate the expression, the figure is still drawn in full symmetry.

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. When the input shaft drives the synchronous belt wheel to rotate at a uniform speed, the speed lock pillow 22 obtains a reciprocating linear motion at a uniform speed. When 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.

Referring again to FIG. 17, 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. Since 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. In practical applications, the so-called 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. So in this specific mechanism, as long as: The projection of three points in the same reference plane (parallel to the plane where the trajectory is located) satisfies the "three points and one line" relationship. In addition, as in this type of mechanism, it can also be summarized as the "three-line coplanar" principle. Three-line: Refers to the centerline of the rotation axis of the rotating pair 7 at the joint of the speed lock 22 and the shift lever 8 (or the pin rotation axis here). Center line), 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 In China, as long as the three wires are guaranteed to be in the same plane at all times, 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.

•] ÷ h -h-^. ^ ΙΞΙ (山 ^ ίί ϋ ^ fe j ^ 山 151 ^ ΓίΙ ^ Translational relationship, so there is no need for a rotating pair at its joint, and it can be fixed by a transmission pin). Then, it is converted into a rotary motion at the timing belt pulley 1. Because the # Γ out-lock speed pillow is a reciprocating linear motion, the synchronous belt pulley is also a reciprocating rotary motion. It is necessary to perform flow selective shaping by the current selective clutch in this device. The current selective clutch disclosed in this patent is different from the traditional overrunning clutch. Differently, it belongs to a 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. For a specific connection relationship, refer to a partially enlarged view of A in FIG. 21 :), 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.

Because 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 However, 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. At the input end, 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.

In addition: the 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. For the sake of simplicity and clarity, 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. In practical applications, this method can further reduce the rotational inertia of the slewing system and increase the bearing capacity. In the non-dedicated design, in order to achieve the purpose of transmitting compression force and isolating torque, 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. However, the disadvantages are: a transitional reversing gear 47 is added. Among them: 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. Obviously: In this solution, 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. In addition: 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. When the relative displacement stroke is long (such as: speed lock and speed lock) Between the track, between the slider and the shift lever, the reversing guide rail, and between the speed lock block and the shift arm in the continuous operation type transmission below), a rolling type mobile pair with a steel ball circulation track can be adopted, as shown in Figure 26.4 As shown in Figure 26.5, of course, when the torque is not required to be transmitted, its rolling cross-section can be circular, and the existing rolling-type mobile substandard parts can be used. In addition: For the occasions where torque transmission is required, 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. As shown in Figure 26.6, 4 parallel moving pairs (ie: rolling The guide rail is combined into a torque-transmitting mobile pair. Generally, 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. When the roller is in zone b, the corresponding link mechanism is in The work area, so the cam contour groove is narrower here, and fully cooperate with the roller to transmit pressure. There are many ways to affect the selection of the wobble plate. Such as: electromagnetic, hydraulic, pneumatic, mechanical and other methods (as shown in Figures 27.2, 27.3); except for mechanical traction, which requires direct control power flow from the input terminal, the rest can use sensors to collect control signals from the input terminal to complete the corresponding actuators. control.

As shown in Figure 27.4, the 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. When 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.

Figure 28: Self-closing internal force pressure control method series

In this solution: The process of pressurizing the flow plate by the flow selection plate is either clamped or attracted (see Figure 31, an electromagnetic flow selection clutch), so as to form a local pressure system between the flow selection plate and the flow plate. Converting the frictional preload pressure into the system's internal force The disk and the distribution plate are self-balanced and closed, which is not reflected to the outside and is conducive to eliminating axial loads.

28.1, 28.2, and 28.3 are shown as follows: 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. When moving to the right, 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. Among them: Figure 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 clamp type clamp force application device adopts a remote traction control scheme. With the remote control of the traction line 68 for power transmission, 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. In addition, in order to eliminate a small amount of slippage during the tightening process of the clamp-type clamping force applying mechanism, 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). In 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. In Figure 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.

Among them, 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). In order to increase the contact force surface, 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.

It can be seen that after the pressure-selection process of the flow-selective wobble plate adopts the self-closed internal force pressure control method, if the transmission process between the flow plate and the output shaft adopts the mechanism shown in FIG. Thrust bearings outside the distributor can be eliminated.

In order to improve the rigid impact phenomenon and reduce the accuracy requirements of the control system, 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. In order to reduce energy loss, improve efficiency, reduce noise, vibration, and extend life, attention should be paid to minimizing the total mass of the reciprocating system and optimizing the system's moment of inertia. It can be made by reducing mass, using high-strength low-density materials and optimizing the structure Designed to reduce the moment of inertia and pay attention to optimize the dynamic balance of the entire system.

Among them: The contact between the roller and the cam groove can be in the form of rolling contact or fluid lubricated sliding contact.

In order to further eliminate the pulsation and improve the force effect, all mechanisms should be arranged and designed in accordance with the principle of symmetry to optimize unbalance vibration and reduce invalid energy consumption, and achieve static and dynamic balance of the entire system.

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);

Among them: a curve (solid line) 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 (solid line) 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. Among them: 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. Generally, 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. In this state, "the time period during which the selective swing plate and the distribution plate contact and transfer power" and "The time period between the current selection plate and the distribution plate in the idling transition zone is equal." 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. As far as the ideal state is concerned: as long as the two sets of working rotations can be ensured and there is no power flow interruption zone, this will help reduce the reciprocating swing acceleration of the selective swing plate, reduce the impact, and optimize the design of the swing plate working conditions. However, in this way: the total effective working time of the two units will be reduced, and the load of each camera unit will be increased, that is, the common working time of the two units will be reduced (at this time, each single unit will only carry half the total transmission power). Therefore, in practical applications, it should be within the two limit ranges shown in (B) and (C). Selection, 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. Among them: The situation described in this image is consistent with the state shown in Figure 21 and can be referred to each other. In the picture, 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. In addition: 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.

Since the current selection pendulum plate and the distribution plate have a short power stroke from contact to compression force, the theoretically close to zero, so the power consumption of this current selection shaping process is very small.

Figure 31: Structure of electromagnetic selective clutch

The electromagnetic reversing torque is used to select and reshape the output reciprocating torque. Compared with the mechanical type selective clutch disclosed above, 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.

As shown in the figure: 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. When working, 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. In addition, the spring pad 78 on the flow distribution plate also plays a role of assisting resetting. It and the return spring together play a resetting and damping role. It can quickly separate the flow selection disk from the flow distribution plate at the moment of power failure, which is beneficial to reduce Wear and power consumption, and at the same time play a role in reducing vibration and noise. 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.

It should be noted that: In this mechanism, 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. However: In the mechanism mode of Fig. 21, the deflector rotates back and forth, and the effect is not good. For the structure shown in FIG. 25, 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.

In addition: You can also use a traction electromagnet / electromagnetic chuck to pull the selection pendulum plate 38 to complete the selection movement shaping work, which also achieves the effect of the electromagnetic selection clutch. This can achieve a cylindrical design based on the advantages of electromagnetic control. Keep the relevant electromagnetic components from participating in mechanical movement (see Figure 28).

Fig. 32: Cylindrical cam-shift gearbox series of direct-acting followers:

As shown in the figure: 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. 21, that is, let the input speed lock achieve the movement rule shown in part A of the image 29 As a result, the linear area moves at a constant speed, and the transitional reciprocating commutation area exhibits a cylinder harmonic motion. The cam profile curve unfolded image and the analysis of the motion pattern image are shown in Figure 33. In order to obtain continuous power flow output, two symmetrical transmission units can be set at different positions on the same cam. 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); In addition: cam contour It can also be designed as a multi-period type as required. As shown in Figure 34, 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. 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. In 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.

In addition: 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. The same reason: 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.

In order to adapt to a variety of workplaces, this type of mechanism can adopt a variety of spatial layout settings. 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; and 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.

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.

Among them: In order to simplify the picture, the mechanism after the output of the speed lock 26 components is not shown in this figure, please refer to the related illustrations above;

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. : When the disc cam of the driver rotates at a hook speed, 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. Among them: (I) the graph represents a single-cycle type; (II) the graph represents a double-period type; (III) the graph represents a 4-period type. That is, the disc cam rotates once, and the corresponding follower completes 1, 2, and 4 reciprocating working cycles respectively. Taking the rotational angle displacement of the disc cam of the master as the abscissa and the linear displacement of the follower as the ordinate, the respective dynamic motion images are obtained. In order to facilitate the unification with the image in the previous figure 29, when the disc cam is rotated at a uniform speed 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. Among them: 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. In the left view of Figure 38.2: The solid line section represents the profile profile of the disc cam AA, and 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;

Aiming at the principle mode of parallel three-point, one-line speed change disclosed in the previous theoretical part (2)-continuous operation, see Figures 14 and 15, the detailed implementation structure is explained below:

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.

Among them: The 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. In order to solve the problem of the transitional offside of each shift arm when it is separated from the traction belt and enters the arc area of the circular guide rail, 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). When entering the arc track area, 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. Among them, 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.

Classification of continuous rotation type transmission traction timing belt:

(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. Among them: 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.

(2) 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. In order to clearly indicate and distinguish the details of the pressure device, 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. b: The layered combination of flat metal belt and non-metal toothed belt. This type of traction 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. In addition: The electromagnetic traction belt can also use the flat type shown in Figure 39.3. Metal traction belt.

(3) Traditional synchronous toothed belts and ordinary flat belts. Traditional synchronous toothed belts can also be selected for the traction synchronous belts in this transmission, but the side of the pressurized chain plate needs to have a tooth shape that matches it, as shown in Figure 42.1. It can also be replaced by ordinary flat belt in the occasions with lower power and lower precision requirements.

Working principle: As shown in FIG. 39, 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. For details, see Fig. 42. 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. Compared with the previous "parallel three-point, one-line" shifting principle mode (1), 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. In conjunction with the schematic diagram 14 above, 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.

In the continuous rotation speed change mode, 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.

Among them, the restatement of the concept of "input and output traction timing belts" mentioned in Figures 14 and 15 above: In the continuous rotation type, the input and output parts are structurally non-essentially different, "input and output traction timing belts" It is only a functional distinction, there is no essential difference in actual function and structure, and it can even be used interchangeably; just as a car tire can be used interchangeably after a period of time to extend its life. In order to further expand the transmission range, a "phase-separated" setting scheme can be adopted to reduce the number of speed-locking blocks in the variable-speed rotation assembly of each phase, increase the included angle of the transmission arm, and adopt an elastic connection between phases to eliminate the "angular speed difference" Vibration "effect. The design principle is: The phases of the traction belt are connected, and the phases of the variable speed rotation assembly are connected in the form of elastic couplings, as shown in Figure 46.2.

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

As shown in the figure, 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. In order to avoid interference with the movement of the ring guide 91 and the moving auxiliary sleeve 100, 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. Cooperate to restrict and guide the movement track of the speed lock block. There are 3 guide rollers in the picture. 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. In addition, 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.

In consideration of assembly and processing issues, 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.

In addition, in order to convert the sliding guide to the rolling guide to reduce wear, 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 same reason: The dual-track constrained-guided speed lock block in Fig. 42 can also adopt full rolling contact guidance. As shown in b in the figure, 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. As for the type shown in Figure 42.4, although the dual-track paired-clip-locking speed positioning seat is a constraint-guided type, theoretically, the same large rolling bearing cannot be used to achieve the effect of rolling guidance. However, in practice, large rolling bearings do not contact the inner and outer tracks at the same time. Moreover, after the combination of entering the work area and the traction belt, 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. There can be a large gap between the ring guide and the speed lock block, so it still makes sense to adopt this structure and achieve the effect of rolling guidance.

For the traction lugs on both sides of the lock block, they are connected by a pressure-bearing connection body, as shown in Figures 40 and 41. Because the two sides are fixedly connected, the degree of freedom of movement is exactly the same. Therefore, a ring can be provided on only one side. Type guide rails, but for the left and right halves of the speed lock block connected by the thrust bearing 40, as shown in the corresponding lock block type in Figure 42, the left and right halves of this type of speed lock block are designed separately, and the thrust bearing bears the traction belt to the speed lock block. The compression force of the lock block 110 is eliminated, and the speed-locking traction lugs on both sides have relatively free rotational freedom, and ring guide rails must be separately established.

Among them: The various types of speed-locking blocks disclosed in this patent are only preferred embodiments of the implementation mechanism, and do not indicate specific types of restrictions. The characteristics of each speed-locking block can be cross-combined. For example: The thrust bearing type in FIG. 42 can also adopt FIG. 40. In addition, the monorail constrained guidance method in Figures 41 and 41; In addition, 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.

Figures 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. During the operation, the pressure chain plate and the pressure roller only generate a vertical positive pressing force on the traction belt. There is no power in the belt running direction, and it follows the traction belt in a driven form. 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. For general occasions, it is advisable to adopt the elastic floating compression method. In special occasions, since 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.

Figure 43: Assembly drawing and parts drawing of gear shifter assembly

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. In order to improve the force, 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. In the same way, in order to improve the force, 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. In addition, in the case where 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. Reflected in Figure 43.6 is that ml and ml will not participate in the combination of the traction belt at the same time, or that the gear arm with an angle of 90 degrees or more will not participate in the work at the same time, so in order to simplify the structure and improve the force, the clip The shifting arm with an angle equal to 90 degrees is fixed to the same coupling ring, as shown in Figure 43.6. Moreover, this method can also optimize the shifting condition of the shifting arm in the arc track area, and greatly reduce the elasticity of the shifting arm by traction offspring. , Transition offside area.

Among them: In order to reduce the size of the map and enlarge the connection details, the length of each shift arm is greatly shortened from the actual situation. For specific proportions, please refer to the assembly drawing;

Fig. 44: Assembly drawing of continuous rotation type continuously variable transmission. In practical applications, 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.

In Figures 44.2 and 44.3, 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. Therefore, 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

As shown in the figure: 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. 100; 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. After adopting the electromagnetic traction scheme, 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. On different lines 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. .

Advantages of electromagnetic shifting disk: 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.

In addition: Because the rotation speed of the transmission disc is pulsating due to the uniform speed operation of the speed lock block in the linear area of the track, the moment of inertia of the variable speed rotation assembly should be reduced as much as possible. Therefore, the structure shown in Figure 43.7 can be adopted to change all the speed changes. The arms are fixedly connected to the same coupling ring to replace the integral transmission disc with radial tracks.

This figure represents the type of double-track clip-constrained track. The single-track restraint type of Figure 39 can also be adopted. After the guide and positioning rollers are added, 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. In addition, 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.

In principle, 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. In order to fully ensure the continuity of power flow and stable load carrying capacity, 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. At this time, the traction belt works on both sides. In order to reduce the load of the traction belt, 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. It is driven to realize power flow offload in different areas of the traction belt and eliminate the phenomenon of power flow cross-loading. Actually, when The control precision is high, it can achieve the alternate clutch when the two adjacent speed-locking blocks are in the same symmetrical phase, and they can work overlapped (because the radial size of the two speed-locking blocks are equal at the moment, they have the same linear speed), Even if there is a cutoff, the cutoff interval is very small, so in general, a single unit is still used.

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. In this solution, 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.

Figure 46.2: In order to further expand the shifting range, 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. However, 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. In fact, after the number of speed-locking blocks is set in phases, as long as the phases and phases are elastically connected, the effects of interrupting the micro-gap power flow and expanding the gear ratio can be achieved at the same time. That is, 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. In order to reduce the size of the drawing, a reduced scale drawing is adopted. 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. Among them, 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;

Similarly: 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. In special occasions, in order to reduce the thickness of the transmission as much as possible, 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: Transverse Wafer Traction Transmission Mechanism

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. Compared with the former, 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. 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. 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 Here are some descriptions of the figure:

1: The various transmission types shown in the figure follow the "equal angular velocity homomorphic motion principle" and "equal angular velocity co-rotational similarity shift principle".

2: 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 same applies: the speed lock pillow is along the speed lock track in the direction perpendicular to the drawing as shown in the figure. On exercise.

3: 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. At this time: 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.

4: The components in the dashed box shown in the figure move with the speed block during the speed adjustment process.

5: 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.

6: The common components in this figure are not marked with part numbers, see the general component symbol table of the schematic diagram in Figure 49;

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. Gear arm length, so this gearbox The structure has "equilibrium continuously variable transmission characteristics". In addition, according to the needs of the occasion, the input-output transmission unit can be rotated at any angle about the rotation center axis 9 to constitute a space transmission type. Among them, 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".

In Figure 48.2, 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. It is obvious that 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. In Figure 48.4: 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. Similarly, 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. During the speed adjustment, 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. In Figure 48.5: 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. Among them, 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. 49.6 adopts a sliding key movement between the bevel gear transmission group 31 and the gear 12 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. In addition, 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. As shown in the figure, 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. When the bevel gear train is translated in the horizontal direction, (B) the effective transmission arm length of the transmission unit changes; when the bevel gear train is vertically translated, (A) the effective transmission arm length of the transmission unit changes. In actual operation, the horizontal, The vertical displacement can be adjusted at the same time, so as to realize more flexible transmission ratio changes. Except for Figure 48.3, the two The effective transmission arms of the end-speed transmission unit can be adjusted simultaneously or separately, without affecting each other. This technical feature supports the authority in the independent right book. This feature is conducive to quick and easy speed regulation, and makes the regulation of the transmission ratio variable and controllable. .

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. When used in a continuous rotating 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. For the transmission gears and bevel gears in Figures 48.4, 48.5, 48.6, and 48.7, if they are used in reciprocating transmissions, the gears only reciprocate and do not perform continuous rotation on a large circumference. Therefore, in order to reduce the weight of the body at low speeds, Sector gears can be used.

To sum up: 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. In short, as long as the constant angular velocity transmission conditions can be met , According to the guiding principle of "equal angular velocity co-rotating position similarity shifting principle", a free and flexible space layout design can be performed. In special occasions, 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;

Figure 50: Simplified space transmission mechanism

According to the comparative analysis of the shifting mechanism in FIG. 48, 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. In the figure, 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

4 inputs, through the timing belt wheel 1, 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. At the output end of the shift lever, 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. It is obvious that 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). For different types of space transmissions, 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. For example, the one-way continuous traction is output by the one-way suction traction of the electromagnetic chuck and the traction belt. In order to eliminate the interruption of power flow, a multi-unit out-of-phase arrangement scheme can be adopted. In order to smoothly engage the lock block with the traction belt, a track guide area is provided. 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. For details about the relevant components and other mechanisms, please refer to the corresponding detailed diagrams of the above-mentioned flat-speed transmission types.

Summary: 1: In order to obtain continuous power flow output, a multi-phase mechanism can be set to work alternately. 2: The "travel cone-like or pyramidal pendulum, space pendulum" type running track cross-section of its spatial shifting lever can be circular, oval, triangular, rectangular, hexagonal, etc. So: deformation curves and combined curves, as shown in Figures 8, 9, and 10. 3: For this type of space transmission, the center of rotation of the space motion gearshift lever needs to be restricted by a space motion pair. Existing general space ball bearings can be used, such as: joint ball bearings, three-dimensional degrees of freedom combined ring and other mechanisms.

Notes:

Note 1: On the basis of this transmission, the derivative series transmission formed by combining other stepped transmissions can obtain a wider transmission range and greater load capacity.

Note 2: In order to reduce friction, all sliding pairs can be replaced by rolling pairs; In order to simplify the structure, all rolling pairs can be replaced by sliding pairs (sliding pairs include: sliding moving pairs, sliding rotating pairs; rolling pairs include: rolling moving pairs, Scroll and rotate the pair).

Note 3: The shifting theory given in this article focuses on the "principle of isokinetic isomorphic motion" and "equal angular velocity reversal position similarity shifting principle", which can be used to guide the design of shifting, its theoretical model, embodiment model , Schematic tube diagrams, mechanism diagrams, specific embodiments, etc.

The technical category of any model, mechanism, and component disclosed herein is cross-recombined and combined with each other, and the combined mechanism scheme and examples of various application fields in this technical category are all within the protection scope of the present invention. Any unauthorized use of this shifting principle for the design and application of shifting is an infringement.

Note 4: The purpose of the drawings in this patent is only to briefly explain the facility concept and principle structure of the patent. The purpose is to clearly express the patent disclosure with the minimum number of drawings and clearly express the key structure. Therefore, the expression of "detailed details" is adopted. In other words, in order to reduce the size of the drawing, the drawings of similar structures will not be drawn in other directions, cross-sections, or enlarged details; and the standard parts and general Parts, and parts without special meaning or special functions, have adopted a uniform name and part number in different drawings, so as to be more clear and clear, such as: Input shaft, output shaft, etc.

Claims

Claim

1. A mechanical continuously variable transmission comprising at least: an input shaft, an output shaft, a transmission mechanism, and a frame, characterized in that:

The transmission mechanism includes a one-phase or at least two-phase input and output motion conversion mechanism, and a one-phase or at least two-phase input and output speed conversion unit; the input and output motion conversion mechanism is a rotary / reciprocating linear motion conversion mechanism, or a rotary / unidirectional Linear motion conversion mechanism, each transmission unit includes at least one group of transmission arm and motion transmission mechanism; at least one corresponding input and output transmission unit in the same phase, at least one of the effective length of the transmission arm or lever in the transmission unit Stepless adjustable

The shift arm or shift lever between any corresponding set of corresponding input and output shift units in the same phase is connected in a fixed manner with a common rotating shaft. The angle between the input and output shift arm or shift lever is 180 degrees or any other angle Each motion transmission mechanism is connected to a shift arm or a shift lever through a rotating pair, or a rotating pair and a moving pair. The effective motion trajectory of each motion transmission mechanism and the instant geometric relationship of the corresponding shift arm or shift lever satisfy the same angular velocity in the same direction. Relativistic variable speed characteristic relationship;

Or: Any group of corresponding input and output transmission units in the same phase, correspondingly, the transmission arm or the transmission lever are formed by a constant angular velocity transmission mechanism, or a combination of a constant angular velocity transmission mechanism and a plane or space motion conversion transmission mechanism, etc. The angular speed transmission combination mechanism is used for constant angular speed transmission connection. Each motion transmission mechanism is connected to a shift arm or a shift lever through a rotating pair, or a rotating pair and a moving pair. The effective motion trajectory of each motion transmission mechanism is corresponding to the corresponding shift arm or shift. The real-time geometric relationship of the rods satisfies the relationship of the similar shifting characteristics of constant angular velocity and the same direction flipping position;

Or: The shift arm or shift lever between any of the corresponding input and output shift units in the same phase is connected in a fixed manner with a three-dimensional rotating shaft in a common space. The angle between the input and output shift arms or the shift lever can be 180 Degrees or any other angle, each motion transmission mechanism communicates The space rotation pair, or the space rotation pair and the movement pair, are connected to a shift arm or a shift lever, and the effective motion trajectory of each motion transmission mechanism and the instantaneous geometric relationship of the corresponding shift arm or shift lever satisfy each other in the same angular velocity and the same direction. Similarity shift characteristic relationship;

Or: The shift arm or shift lever between any corresponding input and output shift units in the same phase is formed by a space iso angular speed transmission mechanism, or a space iso angular speed transmission mechanism and a plane and space motion conversion transmission mechanism. The space constant angular speed transmission combination mechanism is used for constant angular speed transmission connection. Each motion transmission mechanism is connected to the shift arm or the shift lever through the space rotation pair, or the space rotation pair and the movement pair. The effective motion trajectory of each motion transmission mechanism is The real-time geometric relationship of the corresponding shift arm or lever meets the relationship of the similar shifting characteristics of constant angular velocity in the same direction;

Among them, the relationship between the isochronous velocity and the same-direction reversing positional similarity transmission characteristics refers to: the real-time geometry of the motion trajectory of the transmission arm or lever and the corresponding motion transmission member in any transmission unit in the same transmission space in the same phase The relationship can be obtained from the real-time geometric relationship between the shift arm or the shift lever in another shift unit in the effective shift space and the motion trajectory of its corresponding motion transmission member through the same-direction space transformation.

2. A mechanical continuously variable transmission comprising at least: an input shaft, an output shaft, a transmission mechanism, and a frame, which are characterized by:

The effective motion trajectory of each motion transmission mechanism and the instantaneous geometrical relationship of the corresponding shift arm or lever satisfy the non-equal angular velocity co-rotating positional similarity shift characteristic relationship;

Or, the rotational angular velocity of the shift arm or the shift lever in each shift unit is different, or the rotational angular velocity of the shift arm or the shift lever in each shift unit is a ratio other than 1: 1;

Alternatively, the center of rotation of the shift arm or the shift lever is outside the line where the shift arm or the shift lever is located.

The continuously variable transmission according to claim 1, characterized in that:

The input rotary / reciprocating linear motion conversion mechanism includes at least:

Input shaft (4), timing belt wheel (1), timing belt (2), rotating pair (7), slider (3), The moving pair and the motion input member (6), the input shaft (4) is fixedly connected to the timing belt pulley (1), and the timing belt (2) is connected to the sliding rod (3) through the rotating pair (7), and the sliding rod passes through The mobile pair is connected with the motion input (6);

Alternatively, the input rotary / reciprocating linear motion conversion mechanism includes at least: an input shaft, a timing belt wheel, a timing belt, and a corresponding moving pair and a rotating pair, and the input speed lock (22) as a motion input piece is respectively connected to the input speed lock track ( 23). The slider (20) constitutes the joint of the moving pair, and the timing belt (2) and the slider (20) are coupled through the pin (19) and the rotary pair (7);

Alternatively, the input rotary / reciprocating linear motion conversion mechanism includes at least: a linear cam follower cylindrical cam mechanism, the cylindrical cam (84) is a rotary motion active part, and the input speed lock (22) and the roller (34) are fixedly connected to form a roller straight The cam follower curve of the moving follower is such that the timing of the movement of the linear follower can reach the timing belt and timing belt wheel described in the first and second types of input rotary / reciprocating linear motion conversion mechanism The input lock speed bolster (22) in the type motion conversion mechanism has an equivalent contour curve; the cylindrical cam mechanism is a cylindrical cam motion conversion mechanism with a working contour on the inner wall, or a double roller concave contour groove cylindrical cam mechanism or Double-roller convex contour grooved cylindrical cam mechanism; cam contour curve is double-cycle or multi-cycle

Alternatively, the input rotation / reciprocating linear motion conversion mechanism includes at least: a linear cam follower disc cam conversion mechanism, the cam profile curve of which enables the motion regularity of the linear follower to reach the first and second types in the claim. The contour curve equivalent to the motion regularity of the input speed lock (22) in the timing belt and timing belt wheel type motion conversion mechanism described in the input rotary / reciprocating linear motion conversion mechanism; its disc cam mechanism is: a double roller concave contour Groove disc cam mechanism or double-roller convex contour groove disc cam mechanism; cam contour curve is double-cycle or multi-cycle; output rotation / reciprocating linear motion conversion mechanism includes at least:

The motion output (10), the rack and pinion mechanism, the overrunning clutch (14), the output shaft (13), the motion output (10) is connected to the rack, and the gear is connected to one end of the overrunning clutch (14). The other end of the clutch is connected to the output shaft (13);

Alternatively, the output rotation / reciprocating linear motion conversion mechanism includes at least:

The output lock speed pillow (26), the gear (11), the gear (12), and the overrunning clutch; the output lock speed pillow (26) is fixedly connected to the rack (11), and the rack (11) passes through the gear (12) ) Meshing, the gear meshes with another identical gear, and the two gears are connected to an overrunning clutch, respectively, and the two overrunning clutches respectively output a one-way torque through meshing with a gear on the other end shaft; or the output conversion mechanism is: An overrunning clutch is installed on each side of the gear that is engaged with the rack, and the two overrunning clutches respectively output a one-way torque through a bevel gear and a common bevel gear;

Alternatively, the output rotation / reciprocating linear motion conversion mechanism is: the output speed lock (26) converts the power transmission and the timing belt (2) and the timing belt wheel (1) via the transmission pin (29) into a rotation motion and inputs the current selection The clutch main shaft (30), the selective clutch main shaft and the selective wobble plate (38) are connected through a sliding key (37), the control power transmission shaft (36) is connected to the input end power shaft, and the control power is introduced to flow through the speed The transmission chain is transmitted to the control cam (35), and the contour curve of the control cam is a specific curve that can control the current-selective wobble plate for current-selective shaping. The displacement of the roller (34) is controlled in a timely manner. The displacement of the roller is passed through the current-selective transmission frame (33). The slewing support (43) is transmitted to the current-selective wobble plate (38), and controls the clutch timing step with the bevel gear distribution plate (32) on the left and right sides to complete the rectification of the reciprocating torque power flow, and finally passes the bevel gear The transmission group (31) outputs the power flow of the left and right bevel gear distribution plates in parallel, and then outputs them through the output shaft; or: The flow selection pressure plate (39) can be passed between the flow selection drive frame (33) and the flow selection wobble plate (39). ), Thrust bearing (40), radial bearing (41) The slewing support mechanism transmits the selective pressure; or: The selective clutch can use a flat cylindrical gear distribution plate instead of the space bevel gear distribution plate; or: The connection between the selective clutch and the output timing pulley can be picked up: Synchronous pulley The output reciprocating torque is directly transmitted to the bevel gear flow plate, and the flow selection plate is periodically coupled with the left and right reciprocating rotation flow plates to complete the flow selection and shaping, and the unidirectional rotating power is selected and slipped with it. The coupling-selective clutch main shaft outputs a rectified one-way torque; Adopt rolling contact type mobile pair that can transmit torque. For long stroke, you can adopt rolling type mobile pair with steel ball circulation track, or adopt two or more cylindrical or non-cylindrical section rolling contact type mobile pair. The pieces are arranged in parallel and non-coaxially and used as one shaft; or: The traction control of the current-selective wobble plate can be performed by a link mechanism (61) with a self-locking function, or a crank link mechanism with a double locking effect (64) The connecting rod force-increasing locking mechanism (65) can be completed; or a self-closing internal force pressurizing device can be adopted: a clamp-type clamping force applying pressure device, and a pressure roller (74) can be installed at the clamping force applying end Rolling contact, or: Adopt a self-closing pressure-applying force cam device, the middle movable pressure member and the static bearing members on both sides form a closed pressure-applying force device, or take a static bearing member (71) and an eccentric cam pressure mechanism The fixed frame of (67) is connected, and the middle movable pressure member (70) is connected with the movable frame of the eccentric cam mechanism (67) to form a closed pressure applying device, or the middle movable pressure member 70) It is connected with the piston rod (73) of the oil cylinder, and the static bearing parts (71) on both sides are connected with the cylinder body to form a hydraulic pressurizing device; slewing support and thrust can be installed between the pressure member and the selective swing plate and the distribution plate Bearings, pressurizing rollers (72); the traction pressurizing power can come directly from at least one of the power sources of electromagnetic, hydraulic, pneumatic, mechanical, eccentric cam pressure devices, or take remote traction control; An elastic cushioning device (62) may be added in series between the frame and the selective swing plate, or the contact between the roller (34) and the cam groove is covered with elastic material. The contact between the roller and the cam groove may be rolling contact or fluid lubrication Sliding contact; or the clutch that realizes current shaping can be an electromagnetic current selective clutch that replaces mechanical pressing force by electromagnetic attraction, and its electromagnetic chuck

(79) The working current is introduced by the electric ring (77) and the brush (76) through an external control circuit. An electromagnetic chuck is arranged in the two side distribution plates. The movable selection plate (80) and the deflector plate (82) A short-stroke mobile pair is fitted through a convex-concave gap between the two, and the two are implicated by a return spring (81). A spring pad (78) is arranged on the flow plate, and the guide plate (82) is fixedly connected with the main shaft of the selective clutch; Or the element that is selected by the electromagnetic chuck in the flow plate for flow shaping can be a flow selection plate

(38); Or the electromagnetic chuck can be set in the deflector (82), and the movable armature can be selected The wiper disc (80) is connected to the two side distribution discs through a moving pair.

4. The continuously variable transmission according to claim 1, wherein the input / output rotation / unidirectional linear motion conversion mechanism is:

Vertical clip traction type: At least input shaft and output shaft, input and output traction timing belts facing each other in parallel, input and output traction timing belt wheels, tensioning wheels, pressure devices, input shaft (4) input power Flow through the traction timing belt wheel (90) into the flat metal traction belt (105). The input and output traction belt groups are respectively composed of two parallel side-by-side opposite traction belts. The working surface of each traction belt is pressed by a pressure device. The pressure device includes a pressure body (102), a pressure roller (103), and a pressure chain plate (104). The power is transmitted by the friction traction transmission mode; the pressure traction mode or the unilateral traction belt is used to perform unilateral pressure traction on the lock block, and the other side is provided with a balance pressure device; wherein the pressure device includes pressure Body (102), pressure roller (103), pressure chain plate (104), chain plate tensioning wheel (106), the pressure of the pressure body is transmitted to the pressure chain plate through the pressure roller, and the pressure chain plate Single row hinged for chain plate pin (116) It is composed of chain plates connected by concave inserts or overlaps, or two rows of chain plates are overlapped and overlapped with each other. The other side of the pressure chain plate is in contact with the inner side of the traction belt. The pressure force of the pressure body (102) is Pre-compressed spring force, mechanical rigid force, electromagnetic force, or hydraulic pneumatic power; the compression method adopts the elastic floating method or the rigid method; or, the input / output rotation / unidirectional linear motion conversion mechanism is a lateral wafer traction Type: At least input shaft, output shaft, input and output traction timing belts facing each other in parallel, input and output traction timing belt wheels, tensioning wheels, pressure devices; the combination of the traction belt and the lock block adopts a horizontal alignment Clip traction, speed-locking positioning base (111), speed-locking rotating shaft (112), radial bearing (41), mobile auxiliary sleeve (100) of side-mounted speed-locking block (128) are all under pressure-locking traction of the speed-locking block The outer part of the body (129); the speed-locking block is a one-sided pressure-bearing traction body, or the pressure-bearing traction body is symmetrically arranged on both sides of the mobile auxiliary sleeve (100);

Or the input / output rotation / unidirectional linear motion conversion mechanism is an electromagnetic traction type: At least the input shaft and the output shaft, the input and output traction timing belts facing each other in parallel, the input and output traction timing belt wheels, the tensioning wheels, and the pressure device; the combination process of the traction timing belt and the speed lock block captures electromagnetic attraction According to the traction method, the speed lock block includes at least an electromagnetic chuck (123), a speed lock positioning base (111), a radial bearing (41), a speed lock rotation shaft (112), and a mobile auxiliary sleeve (100). The corresponding electromagnetic traction belt is Compound electromagnetic traction belt; 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 lock blocks on the same straight line have the same situation as the electromagnetic chucks, and the locks on different straight lines The speed of the speed block is interlocked, and priority is given to the speed lock block in the best force state; or: The traction belt wheel is driven by dual driving wheels; or: The two sides of the speed lock block are provided with electromagnetic suction cups. Double sets of traction belts transmit power; or: The electromagnetic traction belt and the electromagnetic lock block are arranged in a radial manner; or: Flat metal traction belts for electromagnetic traction belts;

The input and output motion conversion mechanisms have the same structure and are interchangeable, and may be collectively referred to as: a rotary / unidirectional linear motion conversion mechanism;

The continuously variable transmission according to claim 1, wherein the effective transmission arm has a continuously adjustable transmission arm or a transmission lever:

In the same transmission unit, the relationship between the motion transmission member and the transmission arm or the transmission lever is: the rotation axis of the transmission arm is fixed, the movement transmission member and the transmission arm are connected by a moving pair and a rotation pair, or: The rotating pair is connected, and the moving arm and the rotating pair are connected between the transmission arm and the rotating shaft, and the position of the rotating shaft is adjustable;

Or: For the collinear structure mode of the input and output shift arms, the relationship between the shift lever and the motion input, output, and variable speed rotation central axis is: The three include a rotation joint connection, and any two of the three Including mobile secondary connection;

Or: The shift lever (8) is connected with a slider (20) with a rotation central axis (9) connected by a rotating pair (Ί) in a moving pair relationship, and this slider is connected with a regulating device having a fixed speed regulating track (27). The speed block (15) is connected with a rotating pair, and the speed control block (15) and the screw nut speed regulating device (24) The moving parts are connected with nuts, one end of the shift lever is connected with the speed lock of the lock pair, and the other end is connected with the slider.

(20) it is connected as a moving pair, and the slider (20) is connected with the speed lock as a rotating pair;

Alternatively, the continuously variable transmission arm or the transmission lever of the effective transmission arm length is a continuously rotating type:

The variable-speed rotation assembly includes at least two speed-changing arms having a common rotation center and a lock block that cooperates with the moving pair. The speed-shift arms on the same line are fixedly connected through the same coupling ring that cooperates with the radial bearing. The shifting arms are connected through different coupling rings with a common rotating shaft, and have independent degrees of freedom of rotation within a certain range. The shifting arms are connected by an offside traction spring (95). The variable-speed rotation assembly is connected with the rotation center shaft in a rotating pair. The rotating central shaft is connected to a speed regulating block with a fixed speed regulating track; the shift arm assembly adopts different axial arrangements of the coupling rings, or the radial arrangement of different coupling rings is adopted; the shift arm assembly is not an integral or Detachable type adopting bolt connection; Or, the axial arrangement scheme of different coupling rings further includes balanced reinforcing ribs (119) for symmetrical connection; or, the transmission arm with an angle equal to 90 degrees is fixed on the same coupling ring; or The shifting arm adopts a retractable structure, which divides the shifting arm into two, and the two parts move the auxiliary sleeve through telescoping (120) The moving pair is connected, the inner part is connected with the transmission arm coupling ring, the outer part is connected with the speed-locking block in a rotating pair relationship, and the telescoping mobile auxiliary sleeve (120) is equipped with a return spring (81) of the internal device; or, the speed-locking block is connected with the transmission arm. The speed-locking block itself can rotate freely about the speed-locking rotating shaft (112). The speed-locking block at least includes: a speed-locking positioning base (111), a radial bearing (41), Speed-locking rotating shaft (112), mobile auxiliary sleeve (100), speed-locking block traction lug (101), speed-locking block pressure connection body (110), friction traction surface (97), guide roller (98); lock The high-speed rotating shaft (II ² ) is fixedly connected with the moving auxiliary sleeve (100), and forms a rotating pair connection with the speed-locking positioning base (111) through a radial bearing (41), and the speed-locking positioning base (111) is traction with the speed-locking block. The ear plate (101), the lock block pressure-connecting body (110), and the friction traction surface (97) are fixedly connected to form the lock block main frame, the speed lock positioning seat (111) and the guide roller (98) together with the ring guide ( 91) Cooperate with the operation of the lock block The moving trajectory is used for constraint guidance; the speed-locking block traction lug (101) is fan-shaped or shifted offset type; the speed-locking block is a two-half mating type, and the two halves are connected by a bolt (114); the speed-locking positioning seat (111) further includes a guide opposite roller (113), or the speed-locking positioning base (111) is circular, and the outer surface is equipped with large radial rolling bearings; or, the speed-locking block is a left and right half separated type, and The thrust bearing (40) carries the pressing force of the traction belt on the speed lock block; the ring guide (91) is composed of a track straight area (working area) and an arc area (transition area); the ring track is a single-track type or an internal and external double-track type;

Alternatively, the continuously variable adjustable transmission arm or transmission lever of the effective transmission arm length is an electromagnetic type: the variable speed rotation assembly includes at least a transmission disc (121), a radial track (122), an electromagnetic lock block, and all the lock blocks The moving auxiliary sleeve (100) is matched with the radial track (122) on the speed change plate (121), and is guided by the ring guide (91) at the same time; the input and output lock blocks and the speed change plate are sucked by the electromagnetic traction suction cup and the traction belt. Combined with the transmission power, all the lock blocks are evenly distributed on the side of the speed-variable disc body that can be moved steplessly at the center of rotation. The speed-lock blocks are connected to the radial track of the shift body, and can be rotated along its own rotation axis. The rotating central shaft is connected with a rotating pair, and the rotating central shaft is connected with a speed regulating block having a fixed speed regulating track; or, the variable-speed rotation assembly includes at least all the fixed-speed transmission arm assemblies fixedly connected to the same coupling ring; electromagnetic The suction cup is square, or fan-shaped, or offset, or the speed-locking positioning base further includes a radial rolling bearing; or, the shifting arm is retractable The structure divides the shift arm into two, and the two parts are connected in a movable pair relationship through a telescopic movable auxiliary sleeve (120), and the inner part is connected with the shift arm coupling ring, and the outer part is connected in a rotational pair relationship with the lock block, and is telescopic. The moving auxiliary sleeve (120) further includes a return spring (81) inside;

Alternatively, the continuously variable adjustable transmission arm or transmission lever of the effective transmission arm length is a variant: each motion transmission mechanism is connected to the transmission lever through a moving pair, a rotating pair, and the connection point of the rotating pair and the transmission lever is fixed; a rotation center The shaft is connected with a rotating pair whose shift point position is adjustable.

6. The continuously variable transmission according to claim 1, wherein the input and output transmission units are:

The input and output transmission units are located at the same horizontal position, and are symmetrically arranged. The input and output transmission arms are separated. The two angular transmissions (132) are connected by a set of constant-speed dual universal joints (132) that are freely variable in telescopic distance. The arms are connected, and the relationship between the input and output transmission units satisfies the similar angular velocity co-rotating positional similarity transmission relationship, and the position of the speed control block k can be steplessly changed to change the effective transmission arm length steplessly; or: It can be arranged at any angle around the rotation center axis to form a space-variable type;

Or: The two shifting arms are fixedly connected, and each of the speed lock pillows and the speed control block k has a moving pair relationship when the speed is adjusted, and is fixedly connected when the speed is not adjusted, and the corresponding rotating pair and the mobile pair are connected to the corresponding shifting arm to form a speed change Device, the k position of the speed control block can be moved steplessly so as to change its distance from the rotation center axis (9) to change the transmission ratio; or: adopt a space shift type, the fixed position of the two shift arms and the position of the shift unit are changed accordingly To form a space transmission type; or: the two transmission arms are connected by a constant angular space gear, and a space transmission mechanism is formed by changing the relative movement plane of the two transmission units;

Or: The two transmission units share a transmission arm, but the distance from the central axis of rotation is different, and the k position of the speed control block is infinitely movable;

Or: The input / output transmission arm is connected through a space-equivalent angular speed transmission mechanism, and the input / output transmission unit can be set in any spatial orientation, which specifically includes: (a), the rotation central axis of the input / output transmission arm is transmitted through a bevel gear transmission group (31) Change the plane of movement and mesh the two gear units with a common super long spur gear (133) by engaging the plane gear (12) with the common super long spur gear (133). When adjusting the speed, the flat gear (12) is relatively super long spur gear (133) ) Axial movement occurs; or: a sliding key pair (134) is connected between the bevel gear transmission group (31) and the gear (12), which can move axially at the same time when transmitting torque; or the two meshing gears (12) are Space gear; (b), the space bevel gear is fixedly connected to the rotation center axis of the speed change arm (9), and the speed change arm It is connected to the respective rotating central axis (9) by a sliding key moving pair (134), and can move axially at the same time when transmitting torque. The rotatable moving auxiliary speed regulating block (135) and the rotating center axis (9) show The rotating and moving pairs are connected in a relationship, and only the radial translational displacement of the rotation central axis (9) is restricted. The two can be freely rotated and moved axially. The position of the space bevel gear train can be moved to obtain an effective transmission arm. Stepless change.

7. The continuously variable transmission according to claim 6, wherein the space layout type input and output speed change units are: all mechanism types adopt a reciprocating speed change structure or a continuous rotation type speed change structure; In the speed-changing structure, a gear used for constant angular speed transmission, a bevel gear is a complete gear, or a sector gear.

8. The continuously variable transmission according to claim 1, 2, 3, 4, 5, 6, 7, and 7, characterized in that the transmission system is: the input power flow of the input shaft (4) through the left and right gear transmission groups (18) The two left-phase and two-phase speed-changing units are identical in structure, but in the operation step, the working phase difference is 1/4 or 3/4 cycle; the control cams of the left-right camera group (35 ) Use each independently, or use a cam unified control, in this case, the rollers (34) on the two flow selection frames are arranged at different positions on the same cam wheel gallery;

Or: Use a pair of transmission gears to input the power flow, and connect the left and right two-phase transmission units of the synchronous belt pulley through the shaft ends on both sides of the same gear;

Or, a cylindrical cam conversion type of direct-acting follower: two symmetrical transmission units can be set at different positions of the same cam, the working phase difference is 1/4 or 3/4 cycle, the cam profile is single cycle, or Multi-cycle

Or, a linear cam follower with a cam follower: The two-phase speed change unit is set on each side of the same disc cam, and the outline layout phases of the two sides of the disc cam are arranged in a 1/4 or 3/4 period difference; The disc cams of the two-phase transmission unit are connected as a whole, or they are provided separately.

Or, continuous rotation type: Set up two-phase or multi-phase side-by-side variable speed units, divide the total number of speed lock blocks evenly into two or more component phases, and set the phases to adopt an elastic connection between phases. Pick up.

9. The continuously variable transmission according to claim 1, wherein the transmission system is: a motion transmission member of a motion transmission member and a transmission arm or a shift lever rotation plane are not in the same plane, but are motion transmission members of different transmission units in the same phase. The layout relationship between the motion trajectory and the respective shift arm or shift lever still follows the similar shifting relationship of the same angular velocity in the same direction.

The continuously variable transmission according to claim 3, 4, and 5, characterized in that the timing belt is:

The flat type traction belt specifically includes: a. Metal type—a hole-shaped metal sheet laminated synchronous belt formed by stacking multiple layers of perforated thin metal belts, and the hole layers on each metal belt form corresponding meshing holes; , Meshing with the meshing teeth on the special traction synchronous pulley; b. Non-metallic type one-by-one punching or pitting non-metallic flat belt;

Or, the combined traction belt specifically includes: a. A parallel combination of a flat belt and a toothed belt, the middle pressure zone of the traction belt is a flat belt, and the synchronous traction areas on both sides are toothed belts; b, flat metal The layered combination of the belt and the non-metal toothed belt, the inner layer is a non-metal toothed meshing layer, and the outer layer is an electromagnetic attracting traction layer made of a ferromagnetic metal sheet material; or, the electromagnetic traction belt is a flat metal traction belt.