CN1043678C - Differential type internally meshing planetary gear structure - Google Patents
Differential type internally meshing planetary gear structure Download PDFInfo
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- CN1043678C CN1043678C CN94115796A CN94115796A CN1043678C CN 1043678 C CN1043678 C CN 1043678C CN 94115796 A CN94115796 A CN 94115796A CN 94115796 A CN94115796 A CN 94115796A CN 1043678 C CN1043678 C CN 1043678C
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
Abstract
The planetary gear train structure with internal meshing and of the differential type comprises a casing, an input shaft and an output shaft which are mounted so that they can rotate in a casing. It includes first and second eccentric bodies (106, 108) fixed to the said input shaft (102), first and second external gear wheels (110, 112) mounted around the said eccentric bodies and which have a plurality of first and second internal spindle holes (111, 113); first and second internal gear wheels (114, 116) mounted in the casing (118, 120) and a plurality of first internal spindles (122) which prevent the rotation of the first external gear wheel (110) and allow it to pivot, this pivoting being brought about by the rotation of the first eccentric body (106). Application to extremely compact planetary gear train-type reducers exhibiting very high reduction ratios.
Description
The present invention relates to a kind of internal-meshing planetary gear construction, more particularly, relate to a kind of (comprising an additional motion) internal-meshing planetary gear construction that uses differential motion.
A kind of gear reducer that uses internal-gearing planet gear shown in Figure 7 has for example been proposed in unexamined Japan Patent publication No.HEI3-27348.In this gear reducer, all elements all are made of plastics.The rotating speed of input shaft 1 is lowered, and the rotating speed that is lowered is by output shaft 8 (small gear 9) output.Eccentric body 2 is integrally formed on the input shaft 1, and external gear 3 is supported by eccentric body 2 rotationally.
External tooth 3a with cycloid tooth portion integrally forms around the periphery of external gear 3.The sold inside the country 3b of a plurality of cylindricalitys integrally stretches out from external gear 3 along the circumference with input shaft 1 coaxial line.
Plate-like flange 8d is integrally formed in the end of output shaft 8.Form a plurality of inner pinhole 8a on flange 8d, sold inside the country 3b freely cooperates with inner pinhole 8a.
Output shaft 8 is covered 7 support 7a supporting by supporting.Input shaft 1 by a bearing hole 8c who forms in the end of output shaft 8 by rotatably mounted.Small gear 9 is installed around the other end of output shaft 8 in the unlikely mode of rotating and skidding off relative to output shaft 8.
Below with the function of schematic illustration gear reducer.A rotation of input shaft 1 causes a rotation of eccentric body 2.A rotation of eccentric body 2 forces gear 3 to be forced to swingingly rotate around input shaft 1.But the rotation of external gear 3 is restricted by internal gear 4, therefore, in fact external gear 3 only when with internal gear 4 in when engagement swing.
The number of teeth of supposing external gear 3 is N, and the number of teeth of internal gear 4 is (N+1), and number of teeth difference between the two is 1.Like this, transfer, move a tooth with respect to fixing internal tooth 4 around the external gear 3 of its rotation for each of input shaft 1.In other words, the rotation of input shaft 1 is reduced to the rotation of external gear 3-1/N (negative sign refers to reverse rotation).
About the swing and the rotative component of external gear 3, wobble component is absorbed by the space between sold inside the country 3b and inner pinhole 8a, has only rotative component to be sent on the output shaft 8 by sold inside the country 3a, thereby obtains the deceleration that reduction speed ratio is 1/N.
The rotation of output shaft 8 is passed on the hard-wired small gear 9 in the end of output shaft 8.The gear W of associated devices and small gear 9 engagements are delivered to output on the associated devices.
In internal-meshing planetary gear construction shown in Figure 7, under the condition of input shaft 1 and output shaft 8 coaxial lines, can obtain big relatively reduction speed ratio.But in this gear structure, the eccentric rotary of external gear can cause rotation imbalance, will produce vibration at run duration like this.
In order to address the above problem, a kind of gear structure of type shown in Figure 8 has been proposed, the eccentric phase place between this structure comprises mutually is an external gear wheel 3 and 3 of 180 °.Be mutually 180 ° by the eccentric phase place that makes eccentricity gear 3 and 3 with respect to input shaft 1, just can guarantee the balance that whole parts rotate, thereby the vibration of run duration is suppressed to a certain extent.
Because the actual size (modulus) of gear, Fig. 7 or gear reducer shown in Figure 8 are difficult to unlimited raising reduction speed ratio, but have a upper limit, and for the gear reducer with 60 mm outer diameter, this upper limit is about 80.
On the other hand,, a kind of gear reducer that comprises superimposed mutually two above-mentioned inside engaged gear structure A and B shown in Figure 9 has been proposed in order to obtain higher reduction speed ratio (for example hundreds of or higher), or a kind of differential type gear structure.
Figure 10 illustrates a kind of differential type planetary gear construction of being announced in unexamined Japanese Utility Model No.HEI4-111947.In this structure, the eccentric phase place (phase difference of crank section 14) with respect to input shaft 13 between the external gear 11 and 12 is set to 180 °.Internal gear 9 engagements that external gear 11 and internal gear 16 engagements that are installed on the shell 15, external gear 12 and peripheral part round the dish 18 that becomes one with output shaft 17 form.Then, external gear 11 and 12 is connected to each other by crank-like sold inside the country 20.
This structure can obtain hundreds of or more reduction speed ratio by the differential motion between external gear 11,12 and internal gear 16,19.
But the internal-meshing planetary gear construction of this prior art still has following shortcoming:
1) crank-like sold inside the country 20 needs as annex (requiring in above-mentioned file has three), thereby, increased number of spare parts.
2) unless the error that is produced in the practical set of each crank-like by pin 20 in a restricted portion, otherwise can not obtain level and smooth differential motion, thereby efficient reduces, and noise increases.For this reason, each crank-like sold inside the country 20 need so just increase manufacture cost with high dimensional accuracy manufacturing under the quality control condition of height.
3) at run duration, each crank-like sold inside the country 20 is born the load of double power from external gear 11 and 12, and with the rotational synchronization ground of the crank section 14 of input shaft around it self rotational.Thereby, pressing down damping force simultaneously in order to obtain level and smooth differential rotation, bearing parts 21 and 22 needs suitable dimensions precision and suitable intensity, and then needs a suitable measure of cover so that initial assembly performance is kept for a long time.In this respect, cost can increase or weight can improve.
Therefore, the differential type internally meshing planetary gear structure that the purpose of this invention is to provide a kind of high reduction speed ratio.It can realize miniaturization, light, cost is low, noise prevention and vibrationproof.
To achieve these goals, first embodiment according to the invention provides a kind of differential type internally meshing planetary gear structure, and it comprises: a shell; An input shaft and an output shaft by described shell rotatably support; First and second eccentric bodies are fixed on the described input shaft, and this axially is provided with, and become 180 ° of phase differences mutually; First and second external gears rotatably center on the periphery setting of described first and second eccentric bodies respectively, and have a plurality of difference to pass through first and second inner pinholes of described first and second external gears vertically; First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually; A plurality of first is sold inside the country, outstanding from described shell, and freely cooperate with first inner pinhole of described first external gear, is used to limit the rotation of described first external gear, and allow because the swing of described first external gear that rotation produced of described first eccentric body; And a plurality of second is sold inside the country, outstanding from described output shaft, and freely cooperate with described second inner pinhole of described second external gear, is used for only transmitting the rotative component of described second external gear, and absorbs the wobble component of described second external gear.
In order to achieve the above object, according to a second embodiment of the present invention, provide a kind of differential type internally meshing planetary gear structure, it comprises:
A shell; An input shaft and an output shaft by described shell rotatably support; First and second eccentric bodies are fixed on the described input shaft, are provided with vertically, become 180 ° of phase differences mutually; First and second external gears respectively rotatably around the periphery setting of described first and second eccentric bodies, and have outstanding vertically first and second sold inside the country of a plurality of difference; First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually; A plurality of first inner pinholes, be arranged on the described shell, sold inside the country freely cooperates with described first of described first external gear, be used to limit the rotation of described first external gear, and permission is owing to the swing of described first external gear that rotation produced of described first eccentric body; And a plurality of second inner pinholes, be formed on the described output shaft, sold inside the country freely cooperate with described second of described second external gear, be used for only transmitting the rotative component of described second external gear, and absorb described second gear and wobble component.
In order to achieve the above object, a third embodiment in accordance with the invention provides a kind of differential type internally meshing planetary gear structure, and it comprises:
A shell; An input shaft and an output shaft by described shell rotatably support; First and second eccentric bodies are fixed on the described input shaft, and this axially is provided with, and become 180 ° of phase differences mutually; First external gear, rotatably around described first and the periphery of eccentric body put, and have a plurality of first inner pinholes by described first external gear vertically; Second external gear rotatably around the periphery setting of described second eccentric body, and has a plurality of outstanding vertically second sold inside the country; First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually; A plurality of first is sold inside the country, outstanding from described shell, and freely cooperate with first inner pinhole of described first external gear, is used to limit the rotation of described first external gear, and allow because the swing of described first external gear that rotation produced of described first eccentric body; And a plurality of second inner pinholes, on described output shaft, form, be sold inside the country with described second of described second external gear and freely mesh, be used for the rotative component of described second external gear is delivered to described output shaft, and absorb the wobble component of described second external gear.
In order to achieve the above object, a fourth embodiment in accordance with the invention provides a kind of differential type internally meshing planetary gear structure, and it comprises:
A shell; An input shaft and an output shaft by described shell rotatably support; First and second eccentric bodies are fixed on the described input shaft, establish axial setting, become 180 ° of phase differences mutually; First external gear rotatably around the periphery setting of described first eccentric body, and has a plurality of outstanding vertically first sold inside the country; Second external gear rotatably centers on the periphery setting of described second eccentric body, and has a plurality of second inner pinholes that pass through described second external gear vertically; First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually; A plurality of first inner pinholes, be formed on the described shell, sold inside the country freely cooperates with described first of described first external gear, be used to limit the rotation of described first external gear, and permission is owing to the swing of described first external gear that rotation produced of described first eccentric body; And
A plurality of second is sold inside the country, outstanding from described output shaft, and freely cooperate with described second inner pinhole of described second external gear, only is used for the rotative component of described second external gear is passed to output shaft, and absorbs the wobble component of described second external gear.
According to first embodiment, about one in two external gears (first external gear), its rotation is restricted, and only by a plurality of first sold inside the country its swings of permission of giving prominence to from shell.About another external gear (second external gear), its vibration is absorbed, and only by a plurality of second sold inside the country its rotative components that transmit of giving prominence to from output terminal.
Two external gears all mesh respectively with in two internal gears of mutual formation one, and these internal gears by the shell rotatably support.As a result, output shaft can obtain scope from negative tens to infinity with respect to the input shaft forward rotation, or from positive tens to infinitely-great reduction speed ratio, wherein, negative sign is meant backward rotation, and positive sign is meant forward rotation.In addition, when reduction speed ratio infinitely increased, the rotating speed vanishing of output shaft was no matter and how many input shaft rotational speed is.
In second to the 4th embodiment, first and second sold inside the country change mutually with first and second inner pinholes, to obtain the effect identical with first embodiment.
According to the present invention, when the phase difference of two external gears was 180 °, two external gears swingingly rotated, thereby might keep transient equiliblium at run duration, and suppressed the generation of vibration.
Do not need crank-like sold inside the country, thereby may reduce cost at an easy rate, reduce physical dimension and reduce noise.
Because that has cancelled prior art is sold inside the country the structure of bearing double power in the run duration crank-like, might keep the rigidity of height at an easy rate.
Like this, the present invention just can obtain big reduction speed ratio reducing number of spare parts under the situation of designs simplification, and can obtain various reduction speed ratio by the combination that changes the gear number of teeth under the situation of same outer diameter as.
Since two external gears on eccentric direction each other phase displacement be 180 °, this just may keep internal balance at run duration, and the generation of inhibition noise.
In addition, need to make accurately and the accurate crank-like pin of assembling owing to cancelled, thereby may reduce cost, eliminate the damage and the noise that on the crank-like pin, produce, and reduce owing to apply the load of the crankshaft bearing that double power caused.
Above-mentioned purpose, characteristic and advantage with other of the present invention will become clearer from following description taken in conjunction with the accompanying drawings of the present invention, indicate same or analogous part with identical Part No. in explanation.
The front view that Fig. 1 is to use an embodiment's the partial vertical of the gear reducer of differential type internally meshing planetary gear structure of the present invention to analyse and observe;
Fig. 2 is the sectional view of being done along cutting line II-II of Fig. 1;
Fig. 3 represents the sketch of a power transmission system of present embodiment;
Fig. 4 is a table, and the example of a reduction speed ratio that obtains by the number of teeth that changes each gear in the present embodiment is shown;
Fig. 5 is an embodiment's a broken section front view, and differential type internally meshing planetary gear structure wherein of the present invention is used on the output of a small size direct current motor.
Fig. 6 (a) and Fig. 6 (b) are partial enlarged drawings, and every figure illustrates the pin and the first interior pin hole in first, the state that pin hole is changed mutually respectively in the second interior pin and second;
Fig. 7 is the front view of a broken section, and the example of the gear reducer of the internal-meshing planetary gear construction that uses prior art is shown;
Fig. 8 is a sketch, and an example is shown, and wherein uses two external gears in gear structure shown in Figure 7;
Fig. 9 is a sketch, and a structure is shown, and gear structure wherein shown in Figure 8 is superimposed mutually, to obtain big reduction speed ratio; And
Figure 10 is a sketch, and an example in order to the differential type internally meshing planetary gear structure that obtains big reduction speed ratio is shown.
Embodiments of the invention are described hereinafter with reference to the accompanying drawings.
Fig. 1 and Fig. 2 illustrate a plastics reduction gear of using differential type internally meshing planetary gear structure of the present invention.Fig. 3 is a sketch that the power transmission system of reduction gear illustrated in figures 1 and 2 is shown.Fig. 4 is the chart that the reduction speed ratio that is obtained is shown.
In the present embodiment, the rotation of input shaft 102 is decelerated, and the rotation that has been decelerated is from output shaft 104 outputs.
First and second external gears 110 and 112 also are made of plastics, and they rotatably are provided with around the periphery of first and second eccentric bodies 106 and 108 respectively.Around the periphery of first and second external gears 110 and 112, they have external tooth 110a and 112a respectively, and each external tooth all has a cycloidal profile.A plurality of first and second inner pinholes 111 and 113 are separately positioned on first and second external gears 110 and 112, axially penetrate them.
First and second external gears 110 and 112 the first and second external tooth 110a and 112a respectively with first and second internal tooths (circular arc profile) 114a of first and second internal gears 114 that are made of plastics and 116 and 116a in engagement.First and second internal gears 114 and 116 form mutually one when whole (Unitarily molded in advance in the example shown in the figure), and they are rotatably supported by the guide portion 118b that the inside at first shell 118 forms.
Be used for the hole 118a of rotatably mounted input shaft 102 and be used for the interior all side formation of the above-mentioned guide portion 118b of rotatably mounted first and second internal gears 114 and 116 at first shell 118.Be suitable on first shell 118, integrally and saliently forming through a plurality of first sold inside the country 122 of first inner pinhole 111 of first external gear 110.
The hole 120a that is used for rotatably mounted output shaft 104 forms on second shell 120.Work in coordination first and second shells 118 and 120 coaxial lines and become integral body.
Hereinafter, will be in conjunction with the function of sketch explanation present embodiment shown in Figure 3.
In Fig. 3, first external gear 110 and second external gear 112 along the mutual opposite direction at the relative center of input shaft 102 swingingly (prejudicially) rotate, so just offset the dynamic unbalance that is caused owing to the single pendulum rotation.
In the present embodiment without any need for the interior pin of crank shape, thereby reduced number of spare parts, and eliminated the caused inconvenience of interior pin of crank shape.
The rotational velocity of supposing input shaft 102 is N1, and the rotational velocity of output shaft 104 is N2, can get following relationship:
N2={1-(S2P1)/(S1P2) } wherein P1 and P2 are the numbers of teeth of first and second external gears 110 and 112 to N1; S1 and S2 are the numbers of teeth of first and second internal gears 114 and 116.When N2 be on the occasion of the time, the output sense of rotation is with to import sense of rotation identical; And when N2 is negative value, output sense of rotation and input direction of rotation.
From top formula as can be seen, when making first system and second system engages, so that the number of teeth is when consistent with each other, and reduction speed ratio increases without limitation, the output speed vanishing.Here, will specify input and rotate and how to slow down, and subtract fast rotation and how to export.Speed-down action produces simultaneously by the total movement of part, yet for convenience's sake, here with these speed-down action described separately.
Now, the number of teeth of getting gear is P1=29, P2=30, S1=30 and S2=31.When input shaft 102 rotates once, first external gear 110 swingingly rotates once, and wherein first external gear 110 first is sold inside the country 122 restrictions around the rotation of its axis by what form on first shell 118.As a result, with first internal gear 114 of first external gear 110 engagement around its axis along rotating (S1-P1)/S1, i.e. 1/30 rotation with input shaft 102 identical sense of rotation.
On the other hand, suppose that secondary annulus 116 is not around its rotational, when input shaft 102 rotates one time, with the same second external gear 112 of first system around its axis along the sense of rotation opposite with input shaft 102 rotate-(S2-P2)/P2, promptly-1/30 rotation.But because in fact secondary annulus 116 forms an integral body with first internal gear 114, secondary annulus 116 rotates 1/30 rotation around its axis along the sense of rotation identical with input shaft 102.Like this, be used to make effective rotation of input shaft 102 of each gear engagement of second system to become (1-1/30) individual rotation, thereby second external gear 112 in fact around oneself axle around along sense of rotation rotation-(1/30) * (1-1/30) individual rotation opposite, promptly-1/31.03448277 with input shaft 102 ... individual rotation.
As a result, because the terminal output revolutions becomes the poor of first internal gear 114 and second external gear 112, so 1/30-1/30.03448277 ...=1/900 rotation becomes the revolution corresponding to the output shaft of a rotation of input shaft 102.So just can obtain reduction speed ratio up to 900.
By the number of teeth difference between first external gear 110 and second external gear 112 is diminished, can obtain bigger reduction speed ratio (in the example of aforementioned calculation, when the number of teeth difference of external gear and internal gear equals 1, can obtain maximum reduction speed ratio).
Fig. 4 is at P+1=S, and promptly the difference of the number of teeth between external gear and the internal gear is under 1 the situation, and (P1, combination P2) illustrate the example that calculates reduction speed ratio by changing the number of teeth.Drawing the oblique line part, reduction speed ratio infinitely increases, and the output revolutions vanishing is irrelevant with the input revolution.See too clearly from table, by changing the number of teeth of each gear a little, same external diameter can obtain various reduction speed ratio, and this is one of main feature of such gear reducer.
Below, will directly link to each other with direct current motor in conjunction with Fig. 5 explanation, have an embodiment of the gear reducer of differential or internal-meshing planetary gear construction.
The rotation of the motor reel identical with input shaft 202 is slowed down, and the rotation through slowing down is from output shaft 204 outputs.Small-sized DC motor by motor attachment screw 232 coaxial lines be installed on first shell 218.First eccentric body 206 and second eccentric body 208 that are made of plastics fuse by press fit and motor reel 202.
First and second eccentric bodies 206 and 208 each other phase displacement on eccentric direction is 180 ° (in the opposite direction).In this example, first and second eccentric bodies 206 and 208 are made of one in advance, and still, they also can separately be manufactured, mutual then integrator.First and second shells 218 are made with small-sized with 220 outside dimension has the external diameter of stream motor 200 identical substantially.As a result, this gear reducer can be given the user with the form pin the same with free-standing Ultra-Low Speed small-sized DC motor.Other structure the same with among first embodiment, therefore, below in two accompanying drawings, with same figure denote same or similar part, so can omit explanation.
In the present embodiment, each element of gear reducer is all made of plastic, and still, in the present invention, the material of each element is not limited to plastics.
In first and second embodiments, first inner pinhole 111 and 211 is separately positioned on the side of first external gear 110 and 210, first sold inside the country 122 and 222 is separately positioned on first shell 118 and 218, but, shown in Fig. 6 (a), even when first sold inside the country 122 and 222 and inner pinhole 111 and 211 forming with the reverse side of present embodiment, also can obtain same effect.
Equally, shown in Fig. 6 (b), even second sold inside the country 124 and 224 and second inner pinhole 113 and 213 also can obtain identical effect in the side formation reverse with present embodiment.
Claims (4)
1. differential type internally meshing planetary gear structure, it comprises:
A shell;
An input shaft and an output shaft by described shell rotatably support;
First and second eccentric bodies are fixed on the described input shaft, are provided with vertically, become 180 ° of phase differences mutually;
It is characterized in that described planetary gear construction also comprises:
First and second external gears rotatably center on the periphery setting of described first and second eccentric bodies respectively, and have a plurality of difference to pass through first and second inner pinholes of described first and second external gears vertically;
First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually;
A plurality of first is sold inside the country, outstanding from described shell, and freely cooperate with first inner pinhole of described first external gear, is used to limit the rotation of described first external gear, and allow because the swing of described first external gear that rotation produced of described first eccentric body; And
A plurality of second is sold inside the country, outstanding from described output shaft, and freely cooperate with described second inner pinhole of described second external gear, is used for only transmitting the rotative component of described second external gear, and absorbs the wobble component of described second external gear.
2. differential type internally meshing planetary gear structure, it comprises:
A shell;
An input shaft and an output shaft by described shell rotatably support;
First and second eccentric bodies are fixed on the described input shaft, are provided with vertically, become 180 ° of phase differences mutually;
It is characterized in that described planetary gear construction also comprises:
First and second external gears respectively rotatably around the periphery setting of described first and second eccentric bodies, and have outstanding vertically first and second sold inside the country of a plurality of difference;
First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually;
A plurality of first inner pinholes, be arranged on the described shell, sold inside the country freely mesh with described first of described first external gear, be used to limit the rotation of described first external gear, and permission is owing to the swing of described first external gear that rotation produced of described first eccentric body; And
A plurality of second inner pinholes are formed on the described output shaft, are sold inside the country with described second of described second external gear freely to cooperate, and are used for only transmitting the rotative component of described second external gear, and absorb described second gear and wobble component.
3. differential type internally meshing planetary gear structure, it comprises:
A shell;
An input shaft and an output shaft by described shell rotatably support;
First and second eccentric bodies are fixed on the described input shaft, are provided with vertically, become 180 ° of phase differences mutually;
It is characterized in that described planetary gear construction also comprises:
First external gear is rotatably put around the periphery of described first eccentric body, and has a plurality of first inner pinholes that pass through described first external gear vertically;
Second external gear rotatably around the periphery setting of described second eccentric body, and has a plurality of outstanding vertically second sold inside the country;
First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually;
A plurality of first is sold inside the country, outstanding from described shell, and freely cooperate with first inner pinhole of described first external gear, is used to limit the rotation of described first external gear, and allow because the swing of described first external gear that rotation produced of described first eccentric body; And
A plurality of second inner pinholes form on described output shaft, are sold inside the country with described second of described second external gear and freely mesh, and are used for the rotative component of described second external gear is delivered to described output shaft, and absorb the wobble component of described second external gear.
4. differential type internally meshing planetary gear structure, it comprises:
A shell;
An input shaft and an output shaft by described shell rotatably support;
First and second eccentric bodies are fixed on the described input shaft, are provided with vertically, become 180 ° of phase differences mutually;
It is characterized in that described planetary gear construction also comprises:
First external gear rotatably around the periphery setting of described first eccentric body, and has a plurality of outstanding vertically first sold inside the country;
Second external gear rotatably centers on the periphery setting of described second eccentric body, and has a plurality of second inner pinholes that pass through described second external gear vertically;
First and second internal gears rotatably by described outer casing supporting, mesh respectively with in described first and second external gears, and two internal gears form one mutually;
A plurality of first inner pinholes, be formed on the described shell, sold inside the country freely cooperates with described first of described first external gear, be used to limit the rotation of described first external gear, and permission is owing to the swing of described first external gear that rotation produced of described first eccentric body; And
A plurality of second is sold inside the country, outstanding from described output shaft, and freely cooperate with described second inner pinhole of described second external gear, only is used for the rotative component of described second external gear is passed to output shaft, and absorbs the wobble component of described second external gear.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP212424/93 | 1993-08-27 | ||
| JP21242493A JPH0763243A (en) | 1993-08-27 | 1993-08-27 | Diffrential type internal meshing planetary gear structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1104306A CN1104306A (en) | 1995-06-28 |
| CN1043678C true CN1043678C (en) | 1999-06-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN94115796A Expired - Fee Related CN1043678C (en) | 1993-08-27 | 1994-08-25 | Differential type internally meshing planetary gear structure |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH0763243A (en) |
| CN (1) | CN1043678C (en) |
| FR (1) | FR2709339B1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100443417B1 (en) * | 2001-11-07 | 2004-08-09 | 주식회사 슈버 | Speed change system using planetary gear assembly |
| CN100410562C (en) * | 2005-06-02 | 2008-08-13 | 商春荣 | Stepless automatic gear shifting in gear drive |
| JP2007285354A (en) * | 2006-04-13 | 2007-11-01 | Sumitomo Heavy Ind Ltd | Rocking internally meshing type speed reducer |
| JP5388971B2 (en) * | 2010-08-24 | 2014-01-15 | 住友重機械工業株式会社 | Reduction gear |
| DE102016118427A1 (en) | 2016-09-29 | 2018-03-29 | Schunk Gmbh & Co. Kg Spann- Und Greiftechnik | cycloidal drive |
| JP6953321B2 (en) * | 2018-02-01 | 2021-10-27 | 住友重機械工業株式会社 | Manufacturing method of eccentric swing type speed reducer and internal gear |
| JP6898876B2 (en) * | 2018-02-28 | 2021-07-07 | 住友重機械工業株式会社 | Eccentric swing type speed reducer |
| KR102118473B1 (en) * | 2019-11-13 | 2020-06-03 | 장재혁 | Differential reducer with high ratio |
| JP7273782B2 (en) * | 2020-08-31 | 2023-05-15 | 美的集団股▲フン▼有限公司 | Internal meshing planetary gear system, wheel system and vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN2034218U (en) * | 1988-10-12 | 1989-03-15 | 河南省浚县科学技术开发中心 | Floating type differential-gear speed reducer |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3160032A (en) * | 1961-05-25 | 1964-12-08 | Black Tool Inc | Epicyclic speed changing device and gear form therefor |
| EP0101349A1 (en) * | 1982-08-02 | 1984-02-22 | François Durand | Planetory gear box with eccentrics |
| US4640154A (en) * | 1983-09-09 | 1987-02-03 | Osborn Merritt A | Epicyclic power transmission |
-
1993
- 1993-08-27 JP JP21242493A patent/JPH0763243A/en active Pending
-
1994
- 1994-08-25 CN CN94115796A patent/CN1043678C/en not_active Expired - Fee Related
- 1994-08-26 FR FR9410322A patent/FR2709339B1/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2034218U (en) * | 1988-10-12 | 1989-03-15 | 河南省浚县科学技术开发中心 | Floating type differential-gear speed reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2709339A1 (en) | 1995-03-03 |
| JPH0763243A (en) | 1995-03-07 |
| FR2709339B1 (en) | 1996-07-26 |
| CN1104306A (en) | 1995-06-28 |
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