CN2035414U - Combined planetary speed reducer - Google Patents

Abstract

The utility model belongs to a speed reducing mechanism. The utility model is additionally provided with two sets of fixed shaft transmission mechanisms which are composed of any two of three wheels fixedly connected with an input shaft and two of three wheels fixedly connected with a sun wheel, a revolving arm and an internal gear respectively, wherein, the two of the three wheels fixedly connected with the input shaft are correspondingly engaged with the two of three wheels fixedly connected with the sun wheel, the revolving arm and the internal gear respectively, on the basis of a differential planetary mechanism. The utility model has a wide speed-change range, and the transmission ratio can be realized through the adjustment of the fixed shaft wheel train and is not relevant to the planetary mechanism. The number of planetary wheels in the planetary mechanism can be from 3 to 10. The utility model has the advantages of high carrying capacity, stable transmission, high reliability, small size and simple structure, compared with other speed reducers of the same standard. The utility model is suitable for mass production.

Description

Combined planetary speed reducer

This is a kind of device that is used for the mechanical speed change process.

Traditional epicyclic transmission mechanism principle as shown in Figure 1.It is by sun gear (2), planet wheel (4), planetary carrier (pivoted arm) (5), internal gear formations such as (3), when fixed annulus (3), and make sun gear (2) when rotation, planet wheel (4) is rotation just, and drive pivoted arm (5) rotation, the rotating speed of output pivoted arm (5) has so constituted the deceleration relation between sun gear (2) and the pivoted arm (5).The shortcoming of this mechanism is that reduction speed ratio can not be too big, generally be no more than 10, and reduction speed ratio only with sun gear (2), planet wheel (4), the number of teeth of internal gear (3) is relevant, different reduction speed ratio must be used sun gear, internal gear, planet wheel and the pivoted arm thereof of different size instead, and obviously this is disadvantageous for batch process.Other is as cycloid pinwheel planetary gear transmission system, planetary drive with small teeth difference, Harmonic Gears or the like, because its velocity ratio is only closely related with the number of teeth of meshing wheel, the conversion velocity ratio just must change the number of teeth of two or more meshing wheels, and the processing of this meshing wheel with relatively difficulty often is installed, so also be very disadvantageous for the production in enormous quantities of many specifications, many kinds.

The purpose of this utility model is to provide a kind of slewing range wide, and the velocity ratio adjustment is easy, and bearing capacity is big, and is simple in structure, the speed reducer of being convenient to produce in enormous quantities.

The utility model is on the basis of differential planetary mechanism, other has established two cover ordinary transmission mechanisms, they are by any two that are fixed in wheel (8) on the input shaft (I), wheel (9), the wheel (10), be fixed in sun gear (2) on wheel (7), be fixed in wheel (6) on the planetary carrier (5), be fixed in two corresponding engagements formations in the wheel (1) on the internal gear (3).

When the internal gear in the planetary mechanism of Fig. 1 (3) can rotate around central shaft, then this mechanism promptly became differential planetary mechanism.Installed wheel (1) on the internal gear (3) of the utility model in differential planetary mechanism, on planetary carrier (5), installed wheel (6), they can be gone up at axle (II) and rotate, corresponding therewith, on another root axle ［ being input shaft (I) ］, installed wheel (10), wheel (9), when utilizing certain type of belt drive (Figure 2 shows that the standard roller chain drives) to make wheel (10) on the input shaft (I), the wheel (9) respectively with differential attachment on wheel (1), the corresponding engagement of wheel (6), and when the I axle rotates as input shaft, then take turns (6), wheel (1) drives planetary carrier (5) respectively, internal gear (3) rotation, this moment is because both rotations of planet wheel (4), also revolution, its difference just makes and sun gear (2) rotation has so promptly constituted the speed change drive connection between input shaft (I) and the sun gear (2).In like manner, when on input shaft (I), installing wheel (8), on sun gear (2), install wheel (7) (or by axle II), make wheel (8) and wheel (7) simultaneously, wheel (9) and wheel (6) corresponding engagement, and the rotating speed of output inner gear (3); Perhaps make wheel (8) and wheel (7), wheel (10) and wheel (1) corresponding engagement and the rotating speed of output planetary wheel support (5), then promptly constituted the utility model mechanism other two kinds make up and the way of output.The combination of these three kinds of ordinary transmission and output relation, be referred to as respectively mode A the wheel (7) with the wheel (8) remove need not, mode B the wheel (10) with the wheel (1) remove need not, mode C the wheel (6) with the wheel (9) remove need not.If the number of teeth of sun gear (2), internal gear (3) is respectively Z ₂, Z ₃, the number of teeth of wheel (1), (6), (7), (8), (9), (10) is respectively Z ₁, Z ₆, Z ₇, Z ₈, Z ₉, Z ₁₀, then the velocity ratio of three kinds of modes relation is as follows:

${\mathrm{A：i}}_{\mathrm{2I}}=\frac{{\mathrm{<figure-callout\; id="2"\; label="\omega "\; filenames="882132407\_DRIMG1.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_2}{{\omega }_I}\mathrm{=(1+}\frac{Z_3}{Z_2})\frac{Z_9}{Z_6}-\frac{{\mathrm{K\; ·\; Z}}_3}{Z_2}\frac{Z_{\mathrm{10}}}{Z_1}\mathrm{(ⅰ)}$

${\mathrm{B：i}}_{\mathrm{3I}}=\frac{{\mathrm{<figure-callout\; id="3"\; label="\omega "\; filenames="882132407\_DRIMG1.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_3}{{\omega }_I}\mathrm{=(1+}\frac{Z_2}{Z_3})\frac{Z_9}{Z_6}-\frac{{\mathrm{K\; ·\; Z}}_2}{Z_3}\frac{Z_6}{Z_7}\mathrm{(ⅱ)}$

${\mathrm{C：i}}_{\mathrm{5I}}=\frac{{\mathrm{<figure-callout\; id="5"\; label="\omega "\; filenames="882132407\_DRIMG1.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_5}{{\omega }_I}\mathrm{=(}\frac{Z_6}{{\mathrm{<figure-callout\; id="7"\; label="Z"\; filenames="882132407\_DRIMG1.png"\; state="\{\{state\}\}">Z</figure-callout>}}_7}+\frac{{\mathrm{K\; ·\; Z}}_3}{Z_2}·\frac{Z_{\mathrm{10}}}{Z_1}\mathrm{)/(1+}\frac{Z_3}{Z_2}\mathrm{)\; (ⅲ)}$

At formula (i), (ii), (iii) in, when wheel (7), wheel (6), two wheels of wheel in (1) turn to when identical K=1; During switched in opposite, K=-1.

Therefore mechanism of the present utility model is made up of two-part mechanism, and a part is a differential planetary mechanism, promptly by sun gear (2), and the planetary mechanism that internal gear (3), planet wheel (4), planetary carrier (5) constitute; Another part is allotment mechanism, and promptly two overlap the ordinary transmission mechanism of engagement simultaneously.Owing to be that a back part provides the different rotating speeds of two members in the preceding part, and realized the variable motion of the 3rd member by the speed discrepancy of these two members, allocating mechanism thus is to constitute key of the present utility model.This also is the major character that is different from other driving mechanism.

Two cover ordinary transmission mechanisms in the allotment mechanism can adopt chain transmission, belt transmission, gear transmission or their mixed drive mode.When producing by batch, the most suitable in the chain-driven mode, this is because the length of chain can suitably be adjusted, when using different teeth number of sprocket instead when the different velocity ratio of needs, as long as change the length of chain, can solve and need not to change centre distance, this is favourable for batch process.

The utility model can adopt the number of teeth ratio of bigger sun gear (2) and internal gear (3), the number that so then can hold more planet wheel, the gear ratio that is desirable sun gear (2) and internal gear (3) is 1/2～2/3, the number of getting planet wheel (4) is 3～10, this compares with common planetary mechanism, the overlapping number of teeth that is equivalent to increase engagement has also just increased bearing capacity and transmission stability more than one times, has improved reliability and operating life.Because utilizing speed discrepancy realizes slowing down, so reduction speed ratio only with planetary mechanism in the relative rotation speed difference of any two members relevant with relative size poor (or the number of teeth is poor), and it is irrelevant with their absolute rotating speed and absolute dimension (number of teeth), be that velocity ratio can be only decided by the gear ratio of two pairs of wheels in the ordinary transmission mechanism, and it is irrelevant with differential planetary mechanism, this just makes and is difficult to sun gear (2), internal gear (3), planet wheel (4) and the planetary carrier easy uniform specification of member such as (5) of processing and installing, and suitablely carries out mass production.Slewing range of the present utility model is extremely broad, suppose that each wheel can be selected 20 kinds of numbers of teeth in the ordinary transmission mechanism, then reduction speed ratio can reach 160,000 kinds of variations, as long as so obtain the number of teeth of corresponding wheel, the utility model almost can satisfy any velocity ratio requirement that the user arbitrarily proposes, and cost almost do not have increase yet, and this is very significant to enlarging product marketing.The utility model is compared with other speed reducer of equal specification, and volume is little, and is simple in structure.

The utility model has the advantages that:

1. velocity ratio can be only by the gear ratio decision of two pairs of wheels in the ordinary transmission mechanism, and it is standardized to make the sun gear (2), internal gear (3), planet wheel (4) and the planetary carrier members such as (5) that are difficult to process and install be easy to specification, is convenient to mass production.

2. slewing range is very broad, and it is easy to change velocity ratio, and the number of teeth that only needs to change one or several wheel in the ordinary transmission mechanism can realize, and manufacture cost is almost without any increase.

3. can increase the number of planet wheel (4) and velocity ratio is unaffected, so that the overlapping number of teeth of the comparable common planetary mechanism engagement of its overlapping number of teeth doubles is above, bearing capacity, transmission stability, reliability and operating life all are improved.

Embodiment:

An embodiment of the present utility model as shown in Figure 3, this embodiment's the combination and the way of output meet aforesaid mode A, promptly go up affixed sprocket wheel (9), sprocket wheel (10) at input shaft (I), on the II axle, sun gear (2) with splined, planetary carrier (5) uses junction of the edges of two sheets of paper screw (11), (14) to carry out affixed with sprocket wheel (6), internal gear (3) respectively with sprocket wheel (1), they can rotate on the II axle by rolling bearing, between wheel (9) and the wheel (6), wheel (10) and taking turns between (1) with the standard roller chain as the engagement driving part.Consider the number of teeth ratio that strengthens sun gear and internal gear,, connect in the sliding bearing mode between the back shaft (12) of planet wheel (4) and planetary carrier (5) that part (13) is wear-resisting the body of sliding bearing with the number of increase planet wheel.The tooth number Z of sun gear (2) ₂, internal gear (3) tooth number Z ₃, planet wheel (4) tooth number Z ₄Be chosen as 40,74,17 respectively, the number of teeth of other sprocket wheel (1), (6), (9), (10) is respectively 45,45,20,31, and then reduction speed ratio is 128, and the planet wheel number is 6.

Description of drawings:

Fig. 1 is the planetary mechanism schematic representation

The 2-sun gear; The 3-internal gear; The 4-planet wheel; 5-planetary carrier (pivoted arm).

Fig. 2 is the principle schematic of combined type planetary reduction gear.

The wheel that 1-and internal gear are affixed; The 2-sun gear; The 3-internal gear; The 4-planet wheel; 5-planetary carrier (pivoted arm); The wheel that 6-and planetary carrier are affixed; The wheel (realizing by the axle II among the figure) that 7-and sun gear are affixed; The wheel of 8-and the corresponding engagement of wheel (7); The wheel of 9-and the corresponding engagement of wheel (6); (10)-with the wheel (1) corresponding engagement wheel; I-input shaft; The axle (among the figure as output shaft) of II-connect firmly with sun gear.

Fig. 3 is the erection drawing of combined type planetary reduction gear

11,14-junction of the edges of two sheets of paper screw; 12-planet wheel supporting axle; 13-the body of sliding bearing; The 15-roller chain.

Claims (4)

1, a kind of planetary reduction gear of forming by sun gear (2), internal gear (3), planet wheel (4) and planetary carrier (5), it is characterized in that being fixed in any two in wheel (8) on the input shaft (I), wheel (9), the wheel (10), with the wheel (7) that is fixed on the sun gear (2), be fixed in the wheel (6) on the planetary carrier (5), be fixed in two corresponding engagements in the wheel (1) on the internal gear (3).

2, by the described planetary reduction gear of claim 1, it is characterized in that having three kinds of compound modes, mode A: for be fixed in wheel (10) on the input shaft (I), wheel (9) respectively be fixed in internal gear (3) on wheel (1) and be fixed in the corresponding engagement of wheel (6) on the pivoted arm (5), export sun gear (2) rotating speed; Mode B: for be fixed in wheel (9) on the input shaft (I), wheel (8) respectively be fixed in pivoted arm (5) on wheel (6), be fixed in the corresponding engagement of wheel (7) on the sun gear (2), the rotating speed of output inner gear (3); Mode C: for be fixed in wheel (8) on the input shaft (I), wheel (10) respectively be fixed in sun gear (2) on wheel (7), be fixed in the corresponding engagement of wheel (1) on the internal gear (3), output planetary is taken turns the rotating speed of pivoted arm (5).

3,, it is characterized in that described three kinds of its velocity ratios of compound mode are definite by following formula respectively by the described planetary reduction gear of claim 2:

${\mathrm{A：i}}_{\mathrm{2I}}=\frac{{\omega }_2}{{\omega }_I}\mathrm{=(1+}\frac{Z_3}{Z_2})\frac{Z_9}{Z_6}-\frac{{\mathrm{K\; ·\; Z}}_3}{Z_2}\frac{Z_{\mathrm{10}}}{Z_1}$

${\mathrm{B：i}}_{\mathrm{3I}}=\frac{{\omega }_3}{{\omega }_I}\mathrm{=(1+}\frac{Z_2}{Z_3})\frac{Z_9}{Z_6}-\frac{{\mathrm{K\; ·\; Z}}_2}{Z_3}\frac{Z_6}{Z_7}$

${\mathrm{C：i}}_{\mathrm{5I}}=\frac{{\omega }_5}{{\omega }_I}\mathrm{=(}\frac{Z_6}{Z_7}+\frac{{\mathrm{K\; ·\; Z}}_3}{Z_2}·\frac{Z_{\mathrm{10}}}{Z_1}\mathrm{)/(1+}\frac{Z_3}{Z_2})$

4, by the described planetary reduction gear of claim 1, it is characterized in that ordinary transmission can adopt chain-driven, belt transmission, gear transmission or their mixed drive.

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