WO2007028318A1

WO2007028318A1 - Pulsating stepless gear box

Info

Publication number: WO2007028318A1
Application number: PCT/CN2006/002176
Authority: WO
Inventors: Huafeng Wu
Original assignee: Huafeng Wu
Priority date: 2005-09-06
Filing date: 2006-08-25
Publication date: 2007-03-15
Also published as: CN1800674A; CN100434755C

Abstract

Pulsating stepless gear box comprises a transmission mechanism for transferring a uniform rotating motion to variable-speed rotating motion, an output mechanism for outputting the power and a speed control mechanism for varying position relation between the parts of the speed control mechanism. The output mechanism employs 2Z-X typed differential wheel set in the same direction as an output means, and two center wheels of the differential wheel set are respectively connected to an input end and an output end of the transmission mechanism. A rotary arm is used to output the power. The pulsating stepless gear box outputs the power step by step by means of a combination of two or more transmission mechanisms and differential wheel sets between which there are a phase difference.

Description

Pulsating continuously variable transmission

Technical field

The present invention relates to a mechanical continuously variable transmission, and more particularly to a pulsating continuously variable transmission. Background technique

As is known, a conventional pulsating continuously variable transmission uses a transmission mechanism to convert a uniform rotational motion of a transmission main shaft into a variable-speed rotational motion applied to a one-way overrunning clutch, and then converts into a one-way pulsating rotational motion of the output shaft through a one-way overrunning clutch; The output shaft obtains a one-way rotational motion with a small pulsation amplitude through a plurality of combined mechanisms having a certain phase difference. The speed governing mechanism is used to change the length of a component in the transmission mechanism or change the eccentricity of a component to form a new dimensional proportional relationship between the components, thereby changing the angular velocity change rate of the shifting rotational motion, and the rotational speed of the output shaft is generated by the overrunning clutch. Change, so as to achieve the purpose of infinitely variable speed. It is described in detail in the specification of the "Design and Guide of Mechanical Continuously Variable Transmission" edited by Zhai Zhongtang, Chinese Patent Publication No. CN2128983Y and CN2078823Y.

The disadvantage of the conventional pulsating continuously variable transmission is that it is limited by the bearing capacity and the impact resistance of the one-way overrunning clutch. The output mechanism becomes a fatal defect of the conventional pulsating continuously variable transmission, and therefore can only be applied to low speed medium and small power. Moreover, the one-way overrunning clutch can only increase the power output of the transmission mechanism with the maximum instantaneous angular velocity, and the pulsation is large. The method of increasing the phase number of the combined mechanism is used to reduce the pulsation, and the pulsating continuously variable transmission structure tends to be complicated. .

Summary of the invention

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems in the prior art, and provides a pulsating continuously variable transmission which solves the technical problem of changing a method of transmitting power by an overrunning clutch as a main component of an output mechanism in a conventional pulsating continuously variable transmission. The other component is used to replace the overrunning clutch to output the power, so that the whole mechanism power chain has no weak link, and the power can be combined with the transmission mechanism to convert the transmission mechanism into the variable speed rotational motion. , reduce the pulsation of the output power.

The technical solution of the present invention is realized as follows: A pulsating continuously variable transmission, capable of being uniform The rotary motion is converted into a transmission mechanism of the variable speed rotational motion, the output mechanism of the output power and the speed governing mechanism for changing the dimensional relationship between the components of the transmission mechanism are characterized in that: the 2Z-X type positive mechanism differential gear train is used as the output mechanism. The two center wheels of the 2Z-X type positive mechanism differential gear train are respectively closed by the input and output ends of the transmission mechanism, and the power is output by the rotating arm; two or more transmission mechanisms with a certain phase difference and the difference are used. The combination of the moving trains outputs power phase by phase.

In the technical solution of the present invention: the 2Z-X type positive mechanism differential gear train is a 2Z-X type positive mechanism bevel gear differential gear train with a transmission ratio of 1:1, and the swing arm adopts a single-row double-cone gear form.

In the technical solution of the present invention, the transmission mechanism includes a concentric cylinder coupled to the center wheel of the differential gear train and an eccentric cylinder sleeved outside the concentric cylinder. Under the action of the adjustment mechanism, the eccentric cylinder can be changed. The eccentricity of the concentric cylinder; the inner wall of the eccentric cylinder and the outer wall of the concentric cylinder each have a helical tooth of the same direction of rotation.

In the technical solution of the present invention, the tooth surface of the same radius of the helical tooth on the concentric cylinder corresponds to a fixed helix angle, and the center radius of the helical tooth surface and the concentric cylinder The larger the distance, the smaller the helix angle of the corresponding tooth surface on the helical tooth.

The pulsating continuously variable transmission according to the present invention has the following advantages compared with the conventional pulsating continuously variable transmission: Since the transmission mechanism is used to close the center wheel of the differential gear train to output power, the overrunning clutch is no longer used, so that the entire pulsating continuously variable transmission power chain No weak links can maximize the potential of each link, improve the reliability, load carrying capacity and impact resistance of the pulsating continuously variable transmission, so that the pulsating continuously variable transmission can be applied to high speed and high power. At the same time, the combination mechanism converts the part of the power output with a small change in the angular speed of the variable speed rotation after the transmission mechanism, so that the output of the pulsating continuously variable transmission is stable and the performance is stable.

DRAWINGS

1 is a schematic diagram showing the structure of an embodiment of the present invention;

Figure 2 is a cross-sectional view taken along line A-A of Figure 1;

Figure 3 is a cross-sectional view taken along line B-B of Figure 1.

In the figure: 1, input shaft, 2, input shaft cylinder, 3, output shaft, 4, bearing, 5, bearing, 6, bearing, 7, bearing, 8, housing, 9, the center wheel, 10, the arm, 11, the center wheel, 12, the arm, 13, the center wheel, 〗 4, the front concentric cylinder, 15, after the concentric Cylinder, 16, eccentric cylinder, 17, coupling, 18, eccentric cylinder bracket, 19, eccentric cylinder bracket shaft, 20, output gear, 21, eccentric cylinder adjustment mechanism, 22, semicircular gear, 23, Helical, 24, helical, 25, spring, 26, straight, 27, straight, 28, straight, 29, straight.

Specific implementation method

The drawings disclose, without limitation, the specific structure of an embodiment of the present invention, and the present invention will be further described in detail below with reference to the accompanying drawings:

As can be seen from Fig. 1, the input shaft 1 of the present invention and the input shaft cylinder 2 and the output shaft 3, which are integrally integrated with the input shaft 1, are kept concentric, and they are supported on the casing 8 via bearings 6, 7 and input shaft 1 and output. The shafts 3 are supported by the bearings 4; the center wheel 9, the rotating arm 10, the center wheel 11 and the center wheel 11, the rotating arm 12, and the center wheel 13 constitute two sets of 2Z-X type positive mechanism bevel gear differential gear trains (two The bevel gear differential wheel train shares a center wheel 11), and each group of 2Z-X type positive mechanism bevel gear differential gear train has a gear ratio of 1:1, and the center wheel 11 is integrated with the input shaft cylinder 2, The center wheel 11 is fitted over the output shaft 3 via a bearing 5. The front concentric circle 14 and the rear concentric cylinder 15 concentric with the input shaft 1 output shaft 3 are integrated with the center wheel 9 and the center wheel 13, respectively, and they are all fitted to the output shaft 3 through bearings. The arm 10 and the arm 12 are also fitted on the output shaft 3 by bearings; the eccentric cylinder 16 is coupled to the input shaft cylinder 2 by a coupling 17 capable of maintaining an angular velocity with the input shaft 1, and is placed around the input shaft. Outside of the barrel 2. The eccentric cylinder 16 is fixed on the eccentric cylinder bracket 18 by bearings, and the eccentric cylinder bracket 18 is fixed on the eccentric cylinder bracket shaft 19 by bearings, and the eccentric cylinder bracket shaft 19 is integrated with the housing 8 to adjust the eccentric cylinder. The mechanism 21 is fixed on the casing 8, and the output gear 20 of the eccentric cylinder adjusting mechanism 21 and the semicircular gear 22 on the eccentric cylinder bracket 18 are engaged with each other, and the eccentric cylinder adjusting mechanism 21 can drive the semicircular gear 22 to rotate through the output gear 20. Thereby, the eccentric cylinder bracket 18 and the eccentric cylinder 16 thereon are rotated around the eccentric cylinder bracket shaft 19 within a certain range, so that the eccentric cylinder 16 and the input shaft cylinder 2 and the front concentric cylinder 14, the rear concentric cylinder 15 forms different eccentricities.

As shown in FIG. 2, the eccentric cylinder 16 is provided with a helical tooth 23 having a certain helix angle on the inner circumference thereof. A slot having a certain width is opened on the shaft 2 corresponding to the helical tooth 23, and the helical tooth 23 can be inserted, and the input shaft cylinder 2 is also provided on the outer circumference of the front concentric cylinder 14. a helical tooth 24 having the same direction as the helical tooth 23, and the tooth surface of the helical tooth 24 having the same radius from the center of the concentric cylinder corresponds to a fixed helix angle, and the distance from the center radius of the helical tooth surface to the concentric cylinder Large, the helix angle of the corresponding tooth surface on the helical tooth is uniformly reduced. When the concentric cylinder 14 and the eccentric cylinder 16 are concentric, the helical teeth 24 and the helical teeth 23 can closely fit from the tooth end to the tooth tail. At this time, the helical angle of the tooth surface of the helical tooth 24 is equal to the helix angle of the helical tooth 23, At this time, the helical teeth 23 and the helical teeth 24 have the same tooth length; the actual tooth root thickness of the helical teeth 24 and the helical teeth 24 have the same helical angle as the helical teeth 23, and the difference between the tooth root thickness of the helical tails is smaller than the helical teeth 24 The radius of the tooth surface on the tooth surface having the same helix angle as the helical tooth 23 to the center of the front concentric cylinder 14 and the radius of the helical tooth 24 to the center radius of the front concentric cylinder (14) are π times. A spring 25 is disposed between the input shaft cylinder 2 and the front concentric cylinder 14. The elastic force of the spring 25 can support the force distance much less than the input shaft input force distance, and the spring 25 can make the helical teeth 23 and the helical teeth 24 as much as possible fit. Similarly, the interconnection relationship between the rear concentric cylinder 15 and the adjacent members is the same as that of the front concentric cylinder 14: there are corresponding helical teeth on the rear concentric cylinder 15 and the eccentric cylinder 16, and the input shaft cylinder 2 and the rear concentric circle Springs are also provided between the barrels 15. The two helical teeth on the eccentric cylinder 16 are 180° out of phase.

As shown in Fig. 3, the arm 10 is provided with two symmetrical straight teeth 28 and 29, and the output shaft 3 is also provided with two symmetrical straight teeth 26 and 27. In normal operation, the arm 10 can push the straight teeth 27 on the output shaft 3 through the straight teeth 28, and the straight teeth 29 push the straight teeth 26 to drive the output shaft 3 to rotate the output power. At the same time, the rotating arm 12 and the output shaft 3 corresponding thereto are also provided with straight teeth acting thereon; the output shaft 3 and the rotating arm 10 and the output shaft 3 and the rotating arm 12 can be relatively rotated within a certain range. The angle of rotation is generally 90. about.

The working principle of the invention is based on: According to the characteristics of the differential gear train of the 2Ζ-Χ-type bevel gear positive mechanism with a transmission ratio of 1:1, when the steering speeds of the two center wheels are not equal, the steering arm will be in steering with the center wheel. The opposite state of rotational motion. In the present invention, the input shaft cylinder 2 is coupled to the center wheel 11 such that the center wheel 11 is always equal to the input speed, and the front and rear concentric cylinders 14 and 15 are coupled to the other center wheel 9 and 3, front and rear concentric Cylinders 14 and 15 are controlled by eccentric cylinder 16 (see Figure 1), only When the front and rear concentric cylinders 14 and 15 are pushed by the eccentric cylinder 16 and the rotational speed does not coincide with the rotational speed of the input shaft cylinder 2, the arms 10 and 12 are reversely outputted with power. Since the two center wheels of the differential gear train are closed by the transmission mechanism, the force distance applied to the two center wheels when the arm outputs power is in a bootstrap state, as long as the rotational speeds of the two center wheels are inconsistent, added to two The force distance on the center wheel is reduced as the absolute value of the rotational speed difference between the two central wheels becomes larger, that is, the force distance of the output power of the rotating arm becomes smaller as the speed of the rotating arm becomes larger.

In an embodiment of the invention:

When the eccentric cylinder 16 is concentric with the input shaft cylinder 2 under the adjustment of the eccentric cylinder adjusting mechanism 21, the power is input from the input shaft 1, and the input shaft cylinder 2 drives the eccentric cylinder 16 through the coupling 17 to Rotate in a fixed direction of rotation. The eccentric cylinder 16 in turn drives the front concentric cylinder 14 and the rear concentric cylinder 15 to rotate in the same direction by the helical teeth thereon, since the front concentric cylinder 14 and the rear concentric cylinder 15 are concentric with the input shaft cylinder 2, At this time, the rotational speeds of the front concentric cylinder 14 and the rear concentric cylinder 15 are equal to the rotational speeds of the eccentric cylinder 16 and the input shaft cylinder 2, the rotating arm 10 and the rotating arm 12 are in a stationary state, the output shaft 3 has no power output, and the pulsation is stepless. The transmission is in zero output.

When the eccentric cylinder 16 is adjusted by the eccentric cylinder adjusting mechanism 21, the eccentric cylinder 16 and the input shaft cylinder 2, the front concentric cylinder 14, and the rear concentric cylinder 15 have a certain degree of eccentricity, by the eccentric cylinder 16 and the concentric The geometrical position of the cylinder 14 shows that the action point (face) of the helical teeth 23 and the helical teeth 24 are changed. The actual tooth root thickness of the helical teeth 24 and the helical teeth 24 have the same helical angle as the helical teeth 23 The difference in the root thickness of the tail should be smaller than the radius of the tooth surface of the helical tooth 24 having the same helix angle as the helical tooth 23 to the center of the front concentric cylinder 14 and the toothed root of the helical tooth 24 to the front concentric cylinder ( 14) π times the difference in center radius. Therefore, the pushing point (face) of the tooth end of the helical tooth 23 and the tooth end of the helical tooth 24 is at a position after the tooth tip of the helical tooth 23 in the direction of rotation of the input shaft cylinder 2 is closest to the center of the front concentric cylinder 14, the helical tooth 23 and the oblique The tooth 24 is turned in the same direction at the line speed such as the line speed at the pushing point (face), and the pushing point (face) when the helical tooth 23 and the helical tooth 24 push each other from the tooth end at the time of the contact until the tooth end constantly changes, pushing the point ( Face) is always in a similar geometric position. When the helical teeth 23 and the helical teeth 24 push and push each other, the concentric cylinder 14 maintains a certain uniform motion that is greater than the rotational speed of the input shaft cylinder 2, and the rotating arm 16 rotates in a reverse direction. Dynamic output power. As the helical teeth 23 and the helical teeth 24 are constantly turned over, the tooth end distances of the helical teeth 23 and the helical teeth 24 are continuously increased, and the tooth tails are constantly approaching. When the pushing point (face) changes to the tooth tail, the helical teeth 23 and The pushing point (face) of the helical tooth 24 will no longer be maintained at a similar geometric position, and the front concentric cylinder 14 will no longer maintain a uniform motion. According to the geometric positional relationship between the eccentric cylinder 16 and the front concentric cylinder 14, the front The concentric cylinder 14 will be in a rapidly decelerating state. When the current rotation speed of the concentric cylinder 14 is lower than the rotation speed of the eccentric cylinder 16, the elastic force of the spring 25 can support the force distance much less than the input shaft torque, and the converted power cannot make the rotation arm 10 push the output shaft 3 to rotate, so only the normal operation is only When the rotational speed of the front concentric cylinder 14 is greater than the rotational speed of the eccentric cylinder 16, the arm 10 can push the output shaft 3 to rotate. Since the eccentric cylinder 16 rotates 360° to push the concentric cylinder 14 to also rotate 360°, when the rotational speed of the front concentric cylinder 14 is greater than the rotational speed of the eccentric cylinder 16, the front concentric cylinder 14 and the input shaft cylinder 2 have a difference in angle of rotation and a front concentric circle. When the rotation speed of the cylinder 14 is smaller than the rotation speed of the eccentric cylinder 16, the rotation angle difference between the input shaft cylinder 2 and the front concentric cylinder 14 is equal. Once the rotational speed of the front concentric cylinder 14 is just smaller than the rotational speed of the eccentric cylinder 16, it is 180° out of phase with the combination mechanism of the input shaft cylinder 2, the front concentric cylinder 14, the center wheels 9 and 11, and the rotating arm 10. The combination mechanism consisting of the input shaft cylinder 2, the rear concentric cylinder 15 and the center wheels 11 and 13, and the rotating arm 12 is driven by the eccentric cylinder 16 to output power phase by phase through the output shaft 3. The output shaft 3 will remain at a constant speed for most of the time.

The specific operating state is as follows: When the front concentric cylinder 14 is in the hook speed state in the combination mechanism of the input shaft cylinder 2, the front concentric cylinder 14 and the center wheels 9 and 11 and the rotating arm 10, the boom 10 pushes the output at a hook speed When the shaft 3 is swiftly rotated, when the current concentric cylinder 14 is rapidly decelerated from the constant speed state, the boom 10 is slowly decelerated by the inertia, and the distance between the straight teeth 28 on the swing arm 10 and the straight teeth 27 on the output shaft 3 gradually becomes gradually. Increase. When the rotational speed of the current concentric cylinder 14 is just less than the rotational speed of the input shaft cylinder 2, the combination mechanism of the input shaft cylinder 2, the rear concentric cylinder 15 and the center wheels 11 and 13 and the rotating arm 12 continues to push the output shaft 3 to maintain a constant speed state. . Since the rotation speed of the front concentric cylinder 14 is just smaller than the rotation speed of the input shaft cylinder 2, the speed of the rotation speed is particularly large, so that the distance between the straight teeth 28 on the rotating arm 10 and the straight teeth 27 on the output shaft 3 is continuously reduced until the Hehe. After the straight teeth 28 and the straight teeth 27 are attached, the tooth ends of the helical teeth 23 and the helical teeth 24 start to separate and are no longer fitted. With the rotation of the eccentric cylinder 16 and the front concentric cylinder 14, the helical teeth 23 and the oblique The tooth tails of the teeth 24 are kept in a separated state, and the tooth ends of the helical teeth 23 and the helical teeth 24 are continuously approached until they are fitted together, pushing each other instead of the input shaft cylinder 2, the rear concentric cylinder 15 and the center wheels 11 and 13, The combination mechanism composed of the arm 10 outputs power. This reciprocating cycle allows the pulsating continuously variable transmission to continue to operate.

As the eccentric cylinder 16 is adjusted by the eccentric cylinder adjusting mechanism 21, the eccentricity of the eccentric cylinder 16 and the input shaft cylinder 2 is increased, the helical teeth on the eccentric cylinder 16 and the helical teeth on the concentric cylinder The pushing point (face) continuously changes to the root of the helical tooth on the concentric cylinder. Since the helical tooth surface on the concentric cylinder is larger toward the root helix angle, the rotation speed of the concentric cylinder is higher at a constant speed, and the rotating arm is uniform. The rotational speed during the rotation also increases continuously, and the rotational speed of the output shaft 3 is also continuously increased after the phase-by-phase output, realizing the continuously variable transmission.

In actual design, the eccentric cylinder 16, the helical teeth on the front and rear concentric cylinders 14, 15 can be designed with adult teeth or other shapes to reduce the axial direction of the front and rear concentric cylinders 14, 15 and the eccentric cylinder 16. The stress is such that the shorter front and rear concentric cylinders 14 and 15, the eccentric cylinder 16, and the input shaft cylinder 2 are used to reduce the volume of the pulsating continuously variable transmission.

The preferred embodiment of the present invention is more practical for use in a vehicle gearbox.

Claims

Rights request

1. A pulsating continuously variable transmission, which is composed of a transmission mechanism capable of converting a uniform rotational motion into a variable speed rotational motion, an output mechanism for outputting power, and a speed governing mechanism for changing the size proportional relationship between components of the transmission mechanism, wherein: 2Z is adopted. -X type positive mechanism differential gear train as the output mechanism, the two input and output ends of the transmission mechanism respectively close the two center wheels of the 2Z-X type positive mechanism differential gear train, and the power is output by the rotary arm; Or a combination of two or more transmission mechanisms and differential gear trains having a certain phase difference output power phase by phase.

2. The pulsating continuously variable transmission according to claim 1, wherein: the 2Z-X type positive mechanism differential gear train is a 2Z-X type positive mechanism bevel gear differential gear train having a transmission ratio of 1:1. The arms are in the form of single row double bevel gears.

A pulsating continuously variable transmission according to claim 1, wherein: the transmission mechanism includes a concentric cylinder coupled to the center wheel of the differential gear train and an eccentric cylinder sleeved outside the concentric cylinder, Under the action of the mechanism, the eccentric cylinder can change the eccentricity of the concentric cylinder; the inner wall of the eccentric cylinder and the outer wall of the concentric cylinder each have a helical tooth of the same direction.

4. The pulsating continuously variable transmission according to claim 3, wherein: the flank of the same radius of the helical teeth on the concentric cylinders corresponds to a fixed helix angle, The larger the distance between the tooth surface and the center radius of the concentric cylinder, the smaller the helix angle of the corresponding tooth surface on the helical tooth.