CN2244116Y - Planet gear series high transmission ratio speed reducer - Google Patents

Abstract

The utility model relates to a speed reducer with high transmission ratio of a planetary gear train. The utility model is composed of a drive shaft (1), gears (2) (3) (7), a planetary gear (6), a planetary wheel carrier (3), internal gears (4) (5), an output shaft (10) and a housing (9). The utility model has the connection method that a gear (2) and a gear (7) are arranged on the drive shaft (1), wherein, the gear drives an internal gear (4) via an intermediate gear (3); the gear (7) is engaged with the planetary gear (6) which is engaged with an internal gear (5) which is fixed with the internal gear (4) into a whole; a planetary gear carrier (8) is connected with the output shaft (10). The utility model has the advantages of large transmission ratio, equalizing mechanical stress, high transmission efficiency, simple and compact structure, and especially small axial dimension.

Description

The high transmission ratio retarder of planetary gear train

The utility model relates to a kind of retarder, especially a kind of planetary gear train be the high transmission ratio retarder.

Retarder is used very extensive in mechanical transmission, and most widely used in mechanical transmission is NGW type (as shown in Figure 1).Its structural feature is: the axis of gear (11) and internal gear (12) and planet carrier (14) overlaps with fixed axis, so gear (11) and internal gear (12) are called central gear again, planetary pinion (13) is contained on the planet carrier (14) by bearing, planetary pinion (13) is in the time of self rotational, himself axis rotates with the rotation of planet carrier (14), and promptly gear (13) is the rotation axis motion; Planetary pinion (13) meshes with gear (11) and internal gear (12) simultaneously.The advantage of this type of belt drive is: the efficient height, in light weight, simple in structure, easily manufactured, the transmission power scope is big, axial dimension is little, but its gear range generally has only about 1.13～13.7.For solving this defective, often several basic NGW type driver one-level levels need be contacted, both made like this, its velocity ratio is also big inadequately, for the transmission more than three grades and three grades, parts is increased, mechanism's complexity, volume (particularly axial dimension) increases, and cost obviously improves.

Volume (second edition in October nineteen eighty-two) also provides several type of belt drive in " mechanical design handbook " that Chemical Industry Press publishes, as: NW type gear range is than NGW type big (1～50), but the manufacturing installation is all very complicated; N type gear range is big (7～100), but efficient is lower than NGW type, and radial force is bigger after the interior engagement displacement; NGWN type gear range is big (being not more than 500), but efficient is lower than NGW type, and manufacturability is poor, uses when only being applicable to middle low power or short-term job; WW type gear range big (1.2～several thousand), but external dimension and weight are big, efficient is low, manufacturing is difficult.

The purpose of this utility model is: at the problem that exists in the above-mentioned retarder, create a kind of advantage that can keep common NGW type speed reducer, can increase the new type speed reducer of its velocity ratio again greatly.

The purpose of this utility model is achieved in that a kind of high transmission ratio retarder of planetary gear train, is made up of driving shaft (1), gear (2) (3) (7), planetary pinion (6), planetary wheel carrier (8), internal gear (4) (5), output shaft (10), housing (9).It is characterized in that: driving shaft (1) is provided with gear (2) and gear (7).Wherein, gear (2) drives internal gear (4) by intermediate gear (3), gear (7) and planetary pinion (6) engagement, planetary pinion (6) and internal gear (5) engagement, internal gear (4) is solidified as a whole with internal gear (5), and planetary carrier (8) links to each other with output shaft (10).

Advantage of the present utility model is: gear range is not only wide but also big, is easy to realize velocity ratios thousands of, ten thousand; Mechanically stressed equilibrium, the transmission efficiency height, the transmitted power scope is big; Simple in structure, compact, particularly axial dimension is little.

Fig. 1 is basic NGW type planetary pinion transmission schematic representation;

Fig. 2 is a twin-stage NGW type planetary pinion transmission schematic representation;

Fig. 3 is the utility model structural representation;

Fig. 4 is the utility model working principle schematic representation;

Fig. 5 is the utility model middle gear (7), planetary pinion (6) and internal gear (5) kinematic relation figure.

Below in conjunction with accompanying drawing enforcement of the present utility model is further described.

As seen from Figure 3, gear (2) and gear (7) are housed on the driving shaft (1), gear (2) drives internal gear (4) by intermediate gear (3), gear (7) and planetary pinion (6) engagement, internal gear (4) is solidified as a whole with internal gear (5), planetary carrier (8) links to each other with output shaft (10), and the central shaft of intermediate gear (3) is installed on the casing (9).

Fig. 4 is a fundamental diagram of the present utility model, as seen from the figure, driving shaft (1) rotates, driven gear (2) is rotated synchronously, under the effect of intermediate gear (3), internal gear (4) is solidified as a whole with internal gear (5), then internal gear (5) will be synchronized with the movement with internal gear (4), at this moment, planetary pinion (6) will be subjected to the effect of two power, is fixed on that driving shaft (1) is gone up and with the active force of the internal gear (5) of the active force of its gear (7) that rotates synchronously and contrary driving shaft (1) moving direction motion that is:.Under two point of force application normal velocity differential actions, planet wheel (6) will have following three kinds of forms of motion: as seen from Figure 5, establishing gear (7) point of action normal velocity is V ₁, internal gear (5) point of action normal velocity is V ₂, the revolution speed of planetary pinion (6) is V, works as V ₁Equal V ₂The time, planetary pinion (6) will equal zero around its axle center rotation and V, and planetary wheel carrier (8) is motionless; Work as V ₁Greater than V ₂The time, planetary pinion (6) is not equal to zero around its axle center rotation and V, and its axle center will drive planetary carrier (8) and rotate synchronously along the revolution of driving shaft moving direction; Work as V ₁Less than V ₂The time, planetary pinion (6) is not equal to zero around its axle center rotation and V, and will revolve round the sun against driving shaft moving direction in its axle center, and drive planetary carrier (8) rotation synchronously.The motion state of planetary carrier (8) will be exported by output shaft (10), thereby realize speed change.

Velocity ratio formula of the present utility model is: $I=\frac{(Z_7+Z_5)*Z_4}{{\mathrm{<figure-callout\; id="4"\; label="Z"\; filenames="Y9524045000081.png"\; state="\{\{state\}\}">Z</figure-callout>}}_4*Z_7-{\mathrm{<figure-callout\; id="2"\; label="Z"\; filenames="Y9524045000081.png"\; state="\{\{state\}\}">Z</figure-callout>}}_2*Z_5}$

Wherein: I is the speed ratio of driving shaft (1) and output shaft (10);

Z ₂The number of teeth for gear (2);

Z ₄The number of teeth for internal gear (4);

Z ₅The number of teeth for internal gear (5);

Z ₇The number of teeth for gear (7).Work as Z ₄/ Z ₂=Z ₅/ Z ₇The time I=0 output shaft motionless; Work as Z ₄/ Z ₂＞Z ₅/ Z ₇The time I＞0 output shaft and driving shaft rotate in the same way;

Work as Z ₄/ Z ₂＜Z ₅/ Z ₇The time I＜0 output shaft and driving shaft reverse rotation.

It is as follows now to lift a specific embodiment:

If Z ₂=146 Z ₃=59 Z ₄=264

Z ₅＝85 Z ₆＝19 Z ₇＝47

(notes: Z is expressed as gear. the number of teeth, and it is designated as the label of respective gears down, and its label is consistent with accompanying drawing.)

Z ₄/Z ₂＝264/146＝1.808?Z ₅/Z ₇＝85/47＝1.809

1.808＜1.809 output shafts and driving shaft reverse rotation. $I=\frac{({\mathrm{<figure-callout\; id="7"\; label="Z"\; filenames="Y9524045000081.png"\; state="\{\{state\}\}">Z</figure-callout>}}_7+Z_5)*Z_4}{{\mathrm{<figure-callout\; id="4"\; label="Z"\; filenames="Y9524045000081.png"\; state="\{\{state\}\}">Z</figure-callout>}}_4*Z_7-{\mathrm{<figure-callout\; id="2"\; label="Z"\; filenames="Y9524045000081.png"\; state="\{\{state\}\}">Z</figure-callout>}}_2*Z_5}=\frac{(47+85)*264}{264*47-146*85}=-17424$

As seen, its velocity ratio can reach 17424, improves thousands of times to nearly ten thousand times than NGW type driver gear ratio.

In the present embodiment, mechanically stressed more reasonable in order to make, need (3) five of adapted intermediate gears, (6) three of adapted planetary pinions.

Claims (1)

1. the high transmission ratio retarder of a planetary gear train is made up of driving shaft (1), gear (2) (3) (7), planetary pinion (6), planetary wheel carrier (8), internal gear (4) (5), output shaft (10), housing (9), it is characterized in that:

A) driving shaft is provided with gear (2) and gear (7);

B) gear (2) and gear (3) engagement, gear (3) and internal gear (4) engagement;

C) gear (7) and planetary pinion (6) engagement, planetary pinion (6) and internal gear (5) engagement;

D) planetary carrier (8) is connected with output shaft (10);

E) internal gear (4) is solidified as a whole with internal gear (5).

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