CN206111961U - Poor planet gear of tridentate linkage double crank pinwheel few tooth of output cycloid - Google Patents

Abstract

A three-tooth linkage double crank pin wheel output cycloid planetary reducer with less tooth difference belongs to the technical field of mechanical transmission, which includes an output shaft, two output shaft support bearings, two No. 1 crankshaft support bearings, eight outer ring-free Cylindrical roller bearings, three spacer rings, pin pins, No. 1 involute planetary gear, No. 1 crankshaft, two input gear shaft support bearings, input gear shaft, No. 2 involute planetary gear, No. 2 crank Shaft, two No. Ⅱ crankshaft support bearings, four cycloidal wheels, equal load disc, equal load disc support bearing, bushing, upper case cover, connecting bolts and lower case. The planetary reducer of the utility model has the advantages of small size, light weight, large bearing capacity, stable transmission, high transmission efficiency and good rigidity.

Description

A three-tooth linkage double crank pin wheel output cycloid planetary reducer with less tooth difference

technical field

The utility model belongs to the technical field of mechanical transmission, and provides a three-tooth linkage double crank pin wheel output cycloid with few teeth which can be applied to the deceleration system actuator in the mechanical equipment of mining, metallurgy, chemical industry, lifting transportation, construction engineering and other industrial departments Poor planetary reducer.

Background technique

At present, the involute small tooth difference planetary reducer has the following main defects in the actual use process: first, the number of meshing teeth is small at the same time, and the bearing capacity is low; second, when the transmission load is large, the gear teeth will have a large Elastic deformation leads to unstable transmission of the whole machine and high noise; thirdly, the overall size and volume of the whole machine are large and difficult to reduce.

Utility model content

In order to solve the technical problems of the existing planetary reducer, such as large volume, low carrying capacity, unstable transmission, low transmission efficiency, and easy deformation, the utility model provides a three-tooth linkage double crank pin wheel output cycloid planet with less tooth difference reducer.

The technical scheme that the utility model solves the technical problem that takes is as follows:

A three-tooth linkage double crank pin wheel output cycloid planetary reducer with less tooth difference, which includes an output shaft, a first output shaft support bearing, a second output shaft support bearing, a first No. I crankshaft support bearing, a first no Cylindrical roller bearing with outer ring, first spacer ring, second cylindrical roller bearing without outer ring, second spacer ring, third cylindrical roller bearing without outer ring, third spacer ring, pin tooth pin, fourth without outer ring Ring cylindrical roller bearing, No. 2 crankshaft support bearing, No. 1 involute planetary gear, No. 1 crankshaft, first input gear shaft support bearing, second input gear shaft support bearing, input gear shaft, No. Ⅱ Involute planetary gear, #2 crankshaft, #2 #2 crankshaft support bearing, eighth cylindrical roller bearing without outer ring, first cycloid wheel, seventh cylindrical roller bearing without outer ring, second cycloid wheel, the sixth cylindrical roller bearing without outer ring, the third cycloidal wheel, the fourth cycloidal wheel, the fifth cylindrical roller bearing without outer ring, the equalizing disc, the first Ⅱ crankshaft support bearing, the equalizing disc Support bearing, shaft sleeve, upper case cover, connecting bolts and lower case; input gear shaft is supported by first input gear shaft support bearing and second input gear shaft support bearing, first input gear shaft support bearing and second input gear The outer ring of the shaft support bearing is installed on the bearing support of the upper box cover and the lower box body, and the gear pair of the input gear shaft meshes with the gear pairs of No. Ⅰ involute planetary gear and No. Ⅱ involute planetary gear respectively; Ⅰ The No. 1 involute planetary gear and the No. 1 crankshaft are connected by involute splines, and the No. 1 crankshaft is supported by the first No. 1 crankshaft support bearing and the second No. 1 crankshaft support bearing; the first No. 1 crankshaft support The outer ring of the bearing is installed in the bearing hole of the equalizing disc, and the outer ring of the second No. 1 crankshaft support bearing is installed on the upper case cover and the bearing support of the lower case; the No. 1 crankshaft has four eccentrics, eccentric Install the inner rings of the first cylindrical roller bearing without outer ring, the second cylindrical roller bearing without outer ring, the third cylindrical roller bearing without outer ring and the fourth cylindrical roller bearing without outer ring respectively; The linear planetary gear and the No. Ⅱ crankshaft are connected by involute splines; the No. 2 crankshaft is supported by the first No. 2 crankshaft supporting bearing and the second No. The ring is installed on the bearing support of the upper box cover and the lower box, and the outer ring of the second crankshaft support bearing is installed in the bearing hole; the second crankshaft has four eccentricities, and the eccentric positions are installed with the eighth no Cylindrical roller bearings with outer rings, the seventh cylindrical roller bearings without outer rings, the sixth cylindrical roller bearings without outer rings and the inner rings of the fifth cylindrical roller bearings without outer rings; The diameter of the center circle of the bearing hole is equal to the center distance between the No. Ⅰ involute planetary gear and the No. Ⅱ involute planetary gear. The inner walls of the two bearing holes are respectively used as the fourth cylindrical roller bearing without outer ring and the eighth The outer ring of the cylindrical roller bearing without an outer ring; two bearing holes are symmetrically arranged on the second cycloid wheel, and the diameter of the center circle of the bearing hole is equal to the center distance between the No. Ⅰ involute planetary gear and the No. Ⅱ involute planetary gear , the inner walls of the two bearing holes serve as the outer rings of the third cylindrical roller bearing without outer ring and the seventh cylindrical roller bearing without outer ring respectively; on the third cycloid wheel There are two bearing holes symmetrically. The diameter of the center circle of the bearing hole is equal to the center distance between the No. Ⅰ involute planetary gear and the No. Ⅱ involute planetary gear. The bearing and the outer ring of the sixth cylindrical roller bearing without outer ring; two bearing holes are symmetrically arranged on the fourth cycloidal wheel, and the diameter of the center circle of the bearing hole is equal to that of the No. I involute planetary gear and No. II involute planet The center distance of the gear, the inner walls of the two bearing holes are respectively used as the outer rings of the first cylindrical roller bearing without outer ring and the fifth cylindrical roller bearing without outer ring; the first cycloidal wheel and the second cycloidal wheel pass through the third The spacer ring is separated, the second cycloid wheel is separated from the third cycloid wheel by the second spacer ring, the fourth cycloid wheel is separated from the third cycloid wheel by the first spacer ring; the pin tooth pin is installed on the output shaft The equalizing disc is supported by the supporting bearing of the equalizing disc, and the supporting bearing of the equalizing disc is installed on the output shaft; the output shaft is supported by the supporting bearing of the first output shaft and the supporting bearing of the second output shaft, and the first output The outer rings of the shaft support bearing and the second output shaft support bearing are installed on the bearing supports of the upper case cover and the lower case body; the shaft sleeves for positioning the inner rings of the first output shaft support bearing and the second output shaft support bearing are installed On the input shaft, the upper case cover and the lower case body are connected by connecting bolts.

The beneficial effects of the utility model are as follows:

First, the transmission ratio of the planetary reducer of the utility model is large, and the whole machine adopts two-stage deceleration, the first stage adopts involute spur gear transmission, and the second stage adopts cycloid wheel and pin wheel meshing transmission, in which the cycloid The pin wheel transmission ratio can reach 9~87;

Second, the planetary reducer of the utility model has a strong load-bearing capacity. The cycloidal wheel and the pin wheel belong to the multi-teeth meshing of the hard tooth surface, and the number of meshing teeth is large at the same time, which can theoretically reach half of the total number of pin teeth;

Third, the structure of the planetary reducer of the utility model is simple and compact. On the one hand, the pin output mechanism of the traditional cycloid pin wheel meshing transmission is omitted; Reduced overall size and weight of the reducer;

Fourth, the first-stage deceleration system of the planetary reducer of the present invention adopts involute cylindrical gear meshing, which realizes power splitting, and at the same time effectively overcomes the dead point problem in the second-stage cycloid wheel meshing transmission;

Fifth, four cycloidal wheels are used in the second-stage cycloidal pin-wheel meshing transmission of the planetary reducer of the present utility model, and the phase difference between the two is 180°, which can effectively overcome the vibration and realize the static balance of the mechanism force at the same time and dynamic balance.

Description of drawings

Fig. 1 is a schematic diagram of the appearance, front view and structure of the utility model three-tooth linkage double crank pin wheel output cycloid planetary reducer with less tooth difference.

FIG. 2 is a schematic top view of the axial section of FIG. 1 .

detailed description

Below in conjunction with accompanying drawing, the utility model is described in further detail.

As shown in Figure 1 and Figure 2, the three-tooth linkage double crank pin wheel output cycloid planetary reducer with less tooth difference of the present invention includes an output shaft 1, a first output shaft support bearing 2, a second output shaft support bearing 3, The first No. I crankshaft support bearing 4, the first cylindrical roller bearing without an outer ring 5, the first spacer ring 6, the second cylindrical roller bearing without an outer ring 7, the second spacer ring 8, and the third cylinder without an outer ring Roller bearing 9, third spacer ring 10, pin tooth pin 11, fourth cylindrical roller bearing without outer ring 12, second No. 1 crankshaft support bearing 13, No. 1 involute planetary gear 14, No. 1 crankshaft 15. The first input gear shaft support bearing 16, the second input gear shaft support bearing 17, the input gear shaft 18, the No. Ⅱ involute planetary gear 19, the No. 2 crank shaft 20, the second No. 2 crank shaft support bearing 21, The eighth cylindrical roller bearing without outer ring 22, the first cycloidal roller bearing 23, the seventh cylindrical roller bearing without outer ring 24, the second cycloidal roller bearing 25, the sixth cylindrical roller bearing without outer ring 26, the third pendulum Wire pulley 27, fourth cycloid pulley 28, fifth cylindrical roller bearing without outer ring 29, equalizing disc 30, first Ⅱ crankshaft support bearing 31, equalizing disc supporting bearing 32, bushing 33, upper case Cover 34, connecting bolts 35 and lower case 36.

The input gear shaft 18 is supported by the first input gear shaft support bearing 16 and the second input gear shaft support bearing 17, and the outer rings of the first input gear shaft support bearing 16 and the second input gear shaft support bearing 17 are installed on the upper case cover 34 And on the bearing support of the lower case 36, the gear pair of the input gear shaft 18 meshes with the gear pair of No. I involute planetary gear 14 and No. II involute planetary gear 19 respectively.

The No. I involute planetary gear 14 and the No. I crankshaft 15 are connected by an involute spline, and the No. I crankshaft 15 is supported by the first No. I crankshaft support bearing 4 and the second No. I crankshaft support bearing 13; The outer ring of the No. 1 crankshaft support bearing 4 is installed in the bearing hole of the equal load plate 30, and the outer ring of the second No. 1 crankshaft support bearing 13 is installed on the bearing support of the upper case cover 34 and the lower case 36 .

No. Ⅰ crankshaft 15 has four eccentricities, and the eccentric positions are respectively installed with the first cylindrical roller bearing without outer ring 5, the second cylindrical roller bearing without outer ring 7, the third cylindrical roller bearing without outer ring 9 and the fourth cylindrical roller bearing without outer ring. The inner ring of the outer ring cylindrical roller bearing 12; the No. II involute planetary gear 19 and the No. II crankshaft 20 are connected by involute splines.

The No. Ⅱ crankshaft 20 is supported by the first No. Ⅱ crankshaft support bearing 31 and the second No. 2 crankshaft support bearing 21, and the outer ring of the first No. 2 crankshaft support bearing 21 is installed on the upper case cover 34 and the lower case body 36 On the bearing support, the outer ring of the second No. II crankshaft support bearing 31 is installed in the bearing hole of 30; the No. II crankshaft 20 has four eccentricities, and the eccentric positions are respectively installed with the eighth cylindrical roller bearing without outer ring 22 , the inner rings of the seventh cylindrical roller bearing without outer ring 24 , the sixth cylindrical roller bearing without outer ring 26 and the fifth cylindrical roller bearing without outer ring 29 .

The first cycloidal wheel 23 is symmetrically provided with two bearing holes. The diameter of the center circle of the bearing hole is equal to the center distance between the No. I involute planetary gear 14 and the No. II involute planetary gear 19. As the outer rings of the fourth cylindrical roller bearing without outer ring 12 and the eighth cylindrical roller bearing without outer ring 22 .

Two bearing holes are symmetrically arranged on the second cycloidal wheel 25. The diameter of the center circle of the bearing hole is equal to the center distance between the No. I involute planetary gear 14 and the No. II involute planetary gear 19. The inner walls of the two bearing holes are As the outer rings of the third cylindrical roller bearing without outer ring 9 and the seventh cylindrical roller bearing without outer ring 24 .

The third cycloid wheel 27 is symmetrically provided with two bearing holes. The diameter of the center circle of the bearing hole is equal to the center distance between the No. I involute planetary gear 14 and the No. II involute planetary gear 19. The inner walls of the two bearing holes are As the outer rings of the second cylindrical roller bearing without outer ring 7 and the sixth cylindrical roller bearing without outer ring 26 .

The fourth cycloid wheel 28 is symmetrically provided with two bearing holes. The diameter of the center circle of the bearing hole is equal to the center distance between the No. I involute planetary gear 14 and the No. II involute planetary gear 19. The inner walls of the two bearing holes are As the outer rings of the first outer-ring-less cylindrical roller bearing 5 and the fifth outer-ring-less cylindrical roller bearing 29 .

The first cycloidal wheel 22 and the second cycloidal wheel 25 are separated by the third spacer ring 10 to avoid collision; the second cycloidal wheel 25 and the third cycloidal wheel 27 are separated by the second spacer ring 8 to avoid collision; The fourth cycloidal wheel 28 and the third cycloidal wheel 27 are separated by the first spacer ring 6 to avoid collision; the pin tooth pin 11 is installed in the pin tooth pin hole of the output shaft 1 .

The load sharing disc 30 is supported by the load sharing disc support bearing 32, and the load sharing disc support bearing 32 is installed on the output shaft 1; the output shaft 1 is supported by the first output shaft support bearing 2 and the second output shaft support bearing 3, and the first output shaft The outer rings of the shaft support bearing 2 and the second output shaft support bearing 3 are installed on the bearing supports of the upper case cover 34 and the lower case body 36; for positioning the first output shaft support bearing 2 and the second output shaft support bearing 3 The shaft sleeve 33 of the inner ring is installed on the input shaft 1 , and the upper case cover 34 and the lower case body 36 are connected by connecting bolts 35 . The whole machine of the utility model adopts two-stage deceleration, the first stage is the involute cylindrical gear transmission, and the second stage is the cycloid pin-wheel meshing transmission.

The working principle of the three-tooth linkage double crank pinwheel output cycloid planetary reducer with less tooth difference of the utility model is: the input gear shaft 18 is a high-speed shaft, and the output shaft 1 is a low-speed shaft. The first-stage reduction mechanism is composed of an input gear shaft 18, a No. I involute planetary gear 14, and a No. II involute planetary gear 19. When the motor drives the input gear shaft 18 to rotate, the gear pair of the input gear shaft 18 meshes with the No. I involute planetary gear 14 and the No. II involute planetary gear 19 respectively. The No. I involute planetary gear 14 and the No. II involute planetary gear 19 rotate on a fixed axis in the same rotation direction and opposite to the rotation direction of the input gear shaft 18 to realize power splitting. The second stage reduction mechanism is made up of four cycloidal wheels (namely the first cycloidal wheel 23, the second cycloidal wheel 25, the third cycloidal wheel 27, the fourth cycloidal wheel 28) and the pin tooth pin 13. The magnitude and direction of the rotational speed of No. I crankshaft 15 are consistent with those of No. I involute planetary gear 14 , and the magnitude and direction of the rotational speed of No. II crankshaft 20 are consistent with those of No. II involute planetary gear 19 . The four cycloidal wheels pass through eight cylindrical roller bearings without outer rings (namely, the first cylindrical roller bearing without outer ring 5, the second cylindrical roller bearing without outer ring 7, the third cylindrical roller bearing without outer ring 9, The fourth cylindrical roller bearing without outer ring 12, the fifth cylindrical roller bearing without outer ring 29, the sixth cylindrical roller bearing without outer ring 26, the seventh cylindrical roller bearing without outer ring 24, the eighth cylindrical roller bearing without outer ring The roller bearing 22) is installed on the No. I crankshaft 15 and the No. II crankshaft 20. Driven by the rotation of the crankshaft 15 and the crankshaft 20 , the four cycloidal wheels move in a translational motion and mesh with the pin-toothed pins 11 respectively. The phase difference of the first cycloid wheel 23 and the second cycloid wheel 25 is 180 °, the phase difference of the fourth cycloid wheel 28 and the third cycloid wheel 27 is 180 °, the second cycloid wheel 25 and the third cycloid wheel The phases of the wire wheels 27 are the same. The pin tooth pin 11 is installed in the pin tooth pin hole of the output shaft 1, and the output shaft 1 rotates on a fixed axis to output motion and power.

Claims (1)

1. a kind of three teeth linkage double-crank pinwheel exports cycloid planetary speed reducer with small tooth number difference, it is characterised in that the planetary reduction gear Including output shaft（1）, the first output shaft spring bearing（2）, the second output shaft spring bearing（3）, the one No. I crank axle support shaft Hold（4）, first without outer ring cylinder roller bearing（5）, the first spacer ring（6）, second without outer ring cylinder roller bearing（7）, second Spacer ring（8）, the 3rd without outer ring cylinder roller bearing（9）, the 3rd spacer ring（10）, gear pin（11）, the 4th without outer ring cylinder Roller bearing（12）, the 2nd No. I crank axle spring bearing（13）, No. I involute planet gear（14）, No. I crank axle（15）, One input gear axle spring bearing（16）, the second input gear axle spring bearing（17）, input gear axle（18）, No. II involute Planetary gear（19）, No. II crank axle（20）, the 2nd No. II crank axle spring bearing（21）, the 8th without outer ring cylinder roller bearing （22）, the first Cycloidal Wheel（23）, the 7th without outer ring cylinder roller bearing（24）, the second Cycloidal Wheel（25）, the 6th without outer ring cylinder Roller bearing（26）, the 3rd Cycloidal Wheel（27）, the 4th Cycloidal Wheel（28）, the 5th without outer ring cylinder roller bearing（29）, equal load plate （30）, the one No. II crank axle spring bearing（31）, equal load plate spring bearing（32）, axle sleeve（33）, upper box lid（34）, connection spiral shell Bolt（35）And lower box（36）；

Input gear axle（18）By the first input gear axle spring bearing（16）With the second input gear axle spring bearing（17） Support, the first input gear axle spring bearing（16）With the second input gear axle spring bearing（17）Outer ring be arranged on upper box lid （34）And lower box（36）Bearing spider on, input gear axle（18）Gear pair respectively with No. I involute planet gear （14）, No. II involute planet gear（19）Gear pair engagement；

No. I involute planet gear（14）With No. I crank axle（15）Coupled using involute spline, No. I crank axle（15）Pass through One No. I crank axle spring bearing（4）With the 2nd No. I crank axle spring bearing（13）Support；One No. I crank axle spring bearing （4）Outer ring be arranged on equal load plate（30）Dead eye in, the 2nd No. I crank axle spring bearing（13）Outer ring be arranged on top box Lid（34）, lower box（36）Bearing spider on；

No. I crank axle（15）With four bias, eccentric position is respectively mounted first without outer ring cylinder roller bearing（5）, second Without outer ring cylinder roller bearing（7）, the 3rd without outer ring cylinder roller bearing（9）With the 4th without outer ring cylinder roller bearing（12）'s Inner ring；No. II involute planet gear（19）, No. II crank axle（20）Coupled using involute spline；

No. II crank axle（20）By the one No. II crank axle spring bearing（31）With the 2nd No. II crank axle spring bearing（21） Support, the one No. II crank axle spring bearing（21）Outer ring be arranged on upper box lid（34）, lower box（36）Bearing spider on, 2nd No. II crank axle spring bearing（31）Outer ring be arranged on（30）Dead eye in；No. II crank axle（20）With four partially The heart, eccentric position is respectively mounted the 8th without outer ring cylinder roller bearing（22）, the 7th without outer ring cylinder roller bearing（24）, the 6th Without outer ring cylinder roller bearing（26）With the 5th without outer ring cylinder roller bearing（29）Inner ring；

First Cycloidal Wheel（23）On be arranged with two dead eyes, dead eye center diameter of a circle is equal to No. I involute planetary tooth Wheel（14）With No. II involute planet gear（19）Centre-to-centre spacing, the inwall of two dead eyes is respectively as the 4th without outer ring cylinder Roller bearing（12）With the 8th without outer ring cylinder roller bearing（22）Outer ring；

Second Cycloidal Wheel（25）On be arranged with two dead eyes, dead eye center diameter of a circle is equal to No. I involute planetary tooth Wheel（14）With No. II involute planet gear（19）Centre-to-centre spacing, the inwall of two dead eyes is respectively as the 3rd without outer ring cylinder Roller bearing（9）With the 7th without outer ring cylinder roller bearing（24）Outer ring；

3rd Cycloidal Wheel（27）On be arranged with two dead eyes, dead eye center diameter of a circle is equal to No. I involute planetary tooth Wheel（14）With No. II involute planet gear（19）Centre-to-centre spacing, the inwall of two dead eyes is respectively as second without outer ring cylinder Roller bearing（7）With the 6th without outer ring cylinder roller bearing（26）Outer ring；

4th Cycloidal Wheel（28）On be arranged with two dead eyes, dead eye center diameter of a circle is equal to No. I involute planetary tooth Wheel（14）With No. II involute planet gear（19）Centre-to-centre spacing, the inwall of two dead eyes is respectively as first without outer ring cylinder Roller bearing（5）With the 5th without outer ring cylinder roller bearing（29）Outer ring；

First Cycloidal Wheel（22）With the second Cycloidal Wheel（25）By the 3rd spacer ring（10）Separate, the second Cycloidal Wheel（25）With the 3rd Cycloidal Wheel（27）By the second spacer ring（8）Separate, the 4th Cycloidal Wheel（28）With the 3rd Cycloidal Wheel（27）By the first spacer ring （6）Separate；Gear pin（11）Installed in output shaft（1）Gear pin hole in；

Equal load plate（30）By equal load plate spring bearing（32）Support, equal load plate spring bearing（32）Installed in output shaft（1）On； Output shaft（1）By the first output shaft spring bearing（2）With the second output shaft spring bearing（3）Support, the first output shaft is supported Bearing（2）With the second output shaft spring bearing（3）Outer ring be arranged on upper box lid（34）And lower box（36）Bearing spider on； For positioning the first output shaft spring bearing（2）With the second output shaft spring bearing（3）The axle sleeve of inner ring（33）Installed in input Axle（1）On, upper box lid（34）And lower box（36）By attachment bolt（35）Connection.