CN204610711U - Speed change gear - Google Patents
Speed change gear Download PDFInfo
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- CN204610711U CN204610711U CN201390000767.3U CN201390000767U CN204610711U CN 204610711 U CN204610711 U CN 204610711U CN 201390000767 U CN201390000767 U CN 201390000767U CN 204610711 U CN204610711 U CN 204610711U
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- gear
- teeth
- tooth
- speed change
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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
- 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
- F16H2001/324—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 comprising two axially spaced, rigidly interconnected, orbital gears
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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
- F16H2001/325—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 comprising a carrier with pins guiding at least one orbital gear with circular holes
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
一种变速装置，其利用第1齿轮、第2齿轮以及第3齿轮。第1齿轮固定于壳体，并具有内齿。第3齿轮固定于输出轴，并可相对于壳体自转。在第3齿轮为外齿的情况下，在第2齿轮上形成有内齿，在第3齿轮为内齿的情况下，在第2齿轮上形成有外齿。第2齿轮与第1齿轮和第3齿轮这两者啮合。“第1齿轮和第2齿轮之间”与“第2齿轮和第3齿轮之间”中的一方或者双方设置有齿数差。当第2齿轮进行公转时，第3齿轮进行自转，并且输出轴旋转。
A transmission using a first gear, a second gear, and a third gear. The first gear is fixed to the housing and has internal teeth. The third gear is fixed to the output shaft and is rotatable relative to the housing. When the third gear has external teeth, internal teeth are formed on the second gear, and when the third gear has internal teeth, external teeth are formed on the second gear. The second gear meshes with both the first gear and the third gear. One or both of "between the first gear and the second gear" and "between the second gear and the third gear" are provided with a difference in the number of teeth. When the second gear revolves, the third gear rotates on its own, and the output shaft rotates.
Description
Technical field
The Japanese Patent that the utility model was filed an application based on September 21st, 2012 goes out hope 2012-207791 CLAIM OF PRIORITY.The full content of this application is cited in this manual as reference.In this manual, disclose a kind of device of speed change as follows: a part for internal tooth engages with a part for external tooth, between internal tooth and external tooth, be provided with number of teeth difference, utilize the revolution motion due to gear to cause the phenomenon of the spinning motion of gear to carry out speed change.
Background technique
Speed change gear shown in known a kind of Fig. 1.In FIG, reference character 107 represents housing, and reference character 105 represents internal tooth.Internal tooth 105 is fixed on housing 107, and housing 107 is also as internal gear.Reference character 103 represents external gear.External tooth 103f is formed in the periphery of external gear 103.A part of external tooth 103f engages with a part for internal tooth 105.The number of teeth of external tooth 103f is different from the number of teeth of internal tooth 105.Bent axle 101a runs through the center 103e of external gear 103.Bent axle 101a is connected with input shaft 101.Bent axle 101a is from input shaft 101 only offset distance D.Internal tooth 105 to be formed at centered by input shaft 101 circumferentially.External tooth 103f to be formed at centered by 103e circumferentially.In this manual, the center of the circumference residing for internal tooth or external tooth is called geometrical center.
External gear 103 is formed through hole 103c, 103d.Reference character 109 represents output shaft, its top bifurcated.The top 109c of bifurcated is inserted into through hole 103c, and the top 109d of bifurcated is inserted into through hole 103d.When input shaft 101 rotates around axis A, the geometrical center 103e of external gear 103 revolves round the sun around axis A.When external gear 103 revolves round the sun relative to internal tooth 105, external gear 103 also carries out rotation.External gear 103 carries out rotation while revolving round the sun.In this manual the motion carrying out rotation while revolution is called planetary motion.When external gear 103 carries out planetary motion, because top 109c, 109d of bifurcated run through external gear 103, so output shaft 109 carries out rotation.Top 109c, 109d of bifurcated and through hole 103c, 103d are the torque-transfer members for the rotation of the external gear 103 carrying out planetary motion being delivered to output shaft 109.Gear ratio can be adjusted by the difference of the number of teeth of adjustment external tooth 103f and the number of teeth of internal tooth 105.
Fig. 2 exemplifies the speed change gear utilizing two external gears 103,104.The bent axle 101a running through the external gear 103 and bent axle 101b running through external gear 104 offsets round about centered by input shaft 101.The top 109c of the bifurcated of output shaft 109 is inserted into the through hole 103c of the external gear 103 and through hole 104c of external gear 104, and the top 109d of bifurcated is inserted into the through hole 103d of the external gear 103 and through hole 104d of external gear 104.Reference character 106 represents the internal tooth being fixed on housing 107.The reference character identical with Fig. 1 represents the component identical with Fig. 1.
Although the speed change gear illustrated in Fig. 1, Fig. 2 is applicable to obtain larger gear ratio, however also there is boundary.Japanese Unexamined Patent Publication 7-63243 publication (hereinafter referred to as patent documentation 1) proposes a kind of speed change gear for realizing larger gear ratio.For the device of patent documentation 1, as illustrated in Fig. 3, two external gears 103,104 are utilized to revolve round the sun as the device of Fig. 2 to make this device.Pin 107c, 107d is extended from housing 107.Pin 107c is inserted into the through hole 103c of external gear 103.Pin 107d is inserted into the through hole 103d of external gear 103.External gear 103 can not rotation.When external gear 103 does not carry out from then revolves round the sun, internal tooth 105 carries out rotation.Internal tooth 105 is supported as can relative to housing 107 rotation by inner housing 116.When internal tooth 105 time rotational, internal tooth 106 also carries out rotation.Under the state that a part of external tooth 104f and a part for internal tooth 106 engage, when external gear 104 revolves round the sun, external gear 104 also carries out rotation.Namely, external gear 104 carries out planetary motion.External gear 104 and output shaft 109 from revolution and the revolution number of external gear 104 and the relevant from revolution of internal tooth 106.
Even if adopt any one structure in Fig. 1 to Fig. 3, all need to revolve round the sun while the rotation of external gear 103,104 of rotation (namely, carrying out planetary motion) is delivered to the component (in the illustrative situation of Fig. 1 to Fig. 3, being top 109c, the 109d of the bifurcated running through external gear 103,104) of output shaft 109.Namely, in the structure of Fig. 1 to Fig. 3, the component rotation of the gear carrying out planetary motion being delivered to output shaft is needed.In order to by speed change gear miniaturization, the component that the rotation of the gear carrying out planetary motion is delivered to output shaft is also needed miniaturization, cause the situation cannot guaranteeing desirable strength to occur.The existence of torque-transfer members self also becomes the obstacle of the miniaturization of speed change gear.Structure illustrated in Fig. 1 to Fig. 3 is unsuitable for miniaturization.
Japanese Patent Publication 4-111947 publication (hereinafter referred to as patent documentation 2) discloses the speed change gear of Fig. 4.This speed change gear also utilizes two external gears 103,104 and makes it revolve round the sun as Fig. 2, Fig. 3.A part of external tooth 103f engages with a part for internal tooth 105, and when external gear 103 revolves round the sun, external gear 103 also carries out rotation.Inserted by crank pin 114 between external gear 103 and external gear 104, when external gear 103 carries out time rotational, external gear 104 also carries out rotation.External gear 104 carries out rotation while revolving round the sun.Crank pin 114 is while the relative displacement allowing external gear 103 and external gear 104, the rotation of external gear 103 is delivered to the torque-transfer members of external gear 104.A part of external tooth 104f engages with a part for internal tooth 106.Internal tooth 106 is fixed on output shaft 109 by inner housing 110.When external gear 104 carries out planetary motion, internal tooth 106 carries out rotation, and output shaft 109 also carries out rotation.
The speed change gear of Fig. 4 utilizes the external gear 104 carrying out planetary motion make internal tooth 106 rotation and output shaft 109 is rotated.Carrying out between the external gear 104 of planetary motion and output shaft 109 without the need to torque-transfer members.But, between external gear 103 and external gear 104, need crank pin (torque-transfer members) 114.When miniaturized structure by Fig. 4, the diameter of crank pin 114 also diminishes, and causes the situation cannot guaranteeing desirable strength to occur.The existence of crank pin 114 self also becomes the obstacle of the miniaturization of speed change gear.Structure shown in Fig. 4 is also unsuitable for miniaturization.
Model utility content
As mentioned above, even if in any one structure in Fig. 1 ~ Fig. 4, all arrange through hole on the gear carrying out planetary motion, and torque-transfer members is inserted this through hole.When by when being provided with through hole and torque-transfer members being inserted the miniaturized structure of this through hole on gear, the diameter of torque-transfer members diminishes, and causes the situation cannot guaranteeing desirable strength to occur.When becoming large in order to avoid such situation by the diameter of torque-transfer members, the diameter of through hole also becomes large, causes the situation of the intensity cannot guaranteed needed for gear to occur.For structure in the past, need to arrange through hole on gear, and need torque-transfer members to insert this through hole, and these will become the obstacle of miniaturization.Therefore, a kind of structure of the torque-transfer members without the need to inserting in gear is needed.
Speed change gear disclosed in this specification at least has the 1st gear ~ the 3rd gear.Such as, as illustrated in Fig. 5, the 1st gear (can dual-purpose do housing) 107 is formed with internal tooth 105.2nd gear 103 is at least formed with external tooth 103f.A part for the internal tooth 105 of the 1st gear 107 engages with a part of the external tooth 103f of the 2nd gear 103.In the illustrative situation of Fig. 5, the 2nd gear 103 is formed with internal tooth 103g, the 3rd gear 118 is formed with external tooth 118f.A part of the internal tooth 103g of the 2nd gear 103 engages with a part of the external tooth 118f of the 3rd gear 118.Either party between the internal tooth 105 of the 1st gear 107 and the external tooth 103f of the 2nd gear 103 engaged with internal tooth 105 and between the internal tooth 103g of the 2nd gear 103 and the external tooth 118f of the 3rd gear 118 engaged with internal tooth 103g is provided with number of teeth difference.
When being set with number of teeth difference between internal tooth 105 and external tooth 103f, when the 2nd gear 103 revolves round the sun, the 2nd gear 103 also carries out rotation.Namely, the 2nd gear 103 carries out planetary motion.The 2nd gear 103 revolution number and between revolution, obtain speed change phenomenon.In addition, when being set with number of teeth difference between internal tooth 103g and external tooth 118f, when the 2nd gear 103 revolves round the sun, the 3rd gear 118 carries out rotation.Between revolution, speed change phenomenon is obtained at the revolution number of the 2nd gear 103 and the 3rd gear 118.
As mentioned above, when being set with number of teeth difference between internal tooth 105 and external tooth 103f or between internal tooth 103g and external tooth 118f, the 3rd gear 118 when the 2nd gear 103 revolves round the sun can being obtained and carry out the phenomenon of rotation.Poor by the adjustment number of teeth, the revolution number of the 2nd gear 103 and the relation from revolution (gear ratio) of the 3rd gear 118 can be adjusted.In addition, also can be provided with number of teeth difference between internal tooth 105 and external tooth 103f and between internal tooth 103g and external tooth 118f.
As the example shown in figure 6, the 2nd gear 103 is formed with external tooth 103h, the 3rd gear 120 is formed with internal tooth 120h, a part of external tooth 103h can be the relation engaged with a part of internal tooth 120h.Under these circumstances, number of teeth difference is set by least one party between internal tooth 105 and external tooth 103f and between external tooth 103h and internal tooth 120h, also can obtains the 3rd gear 120 when the 2nd gear 103 revolves round the sun and carry out the phenomenon of rotation.Poor by the adjustment number of teeth, the revolution number of the 2nd gear 103 and the relation from revolution (gear ratio) of the 3rd gear 120 can be adjusted.In addition, also number of teeth difference can be provided with between internal tooth 105 and external tooth 103f and between external tooth 103h and internal tooth 120h.
As described above, for speed change gear disclosed in this specification, internal tooth 103g can be formed with on the 2nd gear 103, on the 3rd gear 118, be formed with external tooth 118f, also can be formed with external tooth 103h on the 2nd gear 103, on the 3rd gear 120, be formed with internal tooth 120h.Namely, the gear of speed change gear disclosed in this specification in the 2nd gear and the 3rd gear is formed on external tooth, another gear in the 2nd gear and the 3rd gear and is formed with internal tooth.
For speed change gear disclosed in this specification, the 2nd gear carrying out revolution motion makes the 3rd gear carry out rotation.3rd gear does not revolve round the sun.Therefore, it is possible in advance the 3rd gear is fixed on output shaft.Speed change gear disclosed in this specification is not illustrated in Fig. 1 ~ Fig. 3, that the 2nd gear of planetary motion is carried out in utilization rotation directly makes output shaft rotation structure, therefore, without the need to arranging the torque-transfer members running through the 2nd gear.In addition, necessary crank pin (torque-transfer members) 114 in the structure of Fig. 4 is not needed yet.In speed change gear disclosed in this specification, the 3rd gear becomes the component making output shaft rotation.
As long as the 3rd gear utilizes the 2nd gear carrying out planetary motion to make the component of output shaft rotation.Therefore, the 3rd gear the number of teeth and be not particularly limited with the relation of the number of teeth of the 2nd gear of the 3rd gears meshing.Even if the 2nd gear is the same with the number of teeth of the 3rd gear, utilizes the 2nd gear carrying out planetary motion, also can make the 3rd gear and output shaft rotation.Even if the number of teeth of the 2nd gear is the same with the number of teeth of the 3rd gear, as long as set number of teeth difference between the 1st gear and the 2nd gear, just also speed change phenomenon can be obtained.
If the 3rd gear the number of teeth and and the 3rd gears meshing the 2nd gear the number of teeth between number of teeth difference is set, just utilizing the 2nd gear carrying out planetary motion to make the 3rd gear carry out also can obtaining speed change phenomenon in the process of rotation.Not only do not need the torque-transfer members running through the 2nd gear, the 2nd gear and the 3rd gear can also be utilized to adjust gear ratio.When there is number of teeth difference between the 2nd gear and the 3rd gear, the 1st gear also can be the same with the number of teeth of the 2nd gear.As long as between the 1st gear and the 2nd gear and between the 2nd gear and the 3rd gear at least there is number of teeth difference in either party, just can obtain speed change phenomenon, and the 3rd gear and output shaft rotation can be made.
Disclosed in this specification, speed change gear has: the 1st gear (internal tooth 105), and it is fixed on housing 107; 3rd gear 118,120, it is supported to can relative to housing 107 rotation; Output shaft 109, it is fixed on the 3rd gear 118,120; Input shaft 101, it is supported to can relative to housing 107 rotation; Eccentric swing body (bent axle 101a is the one of carrying out the eccentric swing body revolved round the sun around input shaft 101), it is fixed on input shaft 101, and when input shaft 101 carries out time rotational, eccentric swing body revolves round the sun; 2nd gear 103, it engages with a part for the 1st gear 107 and a part for the 3rd gear 118,120.
2nd gear 103 utilizes eccentric swing body 101a to locate.When eccentric swing body 101a revolves round the sun around input shaft 101, the 2nd gear 103 revolves round the sun around input shaft 101.At least one party between the 1st gear 107 and the 2nd gear 103 engaged with the 1st gear 107 and between the 2nd gear 103 and the 3rd gear 118,120 engaged with the 2nd gear 103 is provided with number of teeth difference.
As long as arrange number of teeth difference between the 1st gear 107 and the 2nd gear 103 engaged with the 1st gear 107, then can realize gear ratio at the revolution number of the 2nd gear 103 and the 2nd gear 103 between revolution, the 2nd gear 103 carrying out planetary motion can be utilized to make the 3rd gear 118,120 rotation.As long as arrange number of teeth difference between the 2nd gear 103 and the 3rd gear 118,120 engaged with the 2nd gear 103, then can realize gear ratio at the revolution number of the 2nd gear 103 and the 3rd gear 118,120 between revolution, the 2nd gear 103 (not limiting the rotation of the 2nd gear 103) at least carrying out revolving round the sun can be utilized to make the 3rd gear 118,120 rotation.3rd gear 118,120 does not revolve round the sun, therefore, it is possible to output shaft 109 is fixed on the 3rd gear 118,120 in advance.Speed change gear disclosed in this specification does not need the torque-transfer members running through the 2nd gear 103.
The technical solution of the utility model is speed change gear, it is characterized in that, it at least has the 1st gear, 2nd gear and the 3rd gear, 1st gear is formed with internal tooth, 2nd gear is at least formed with external tooth, a part for the internal tooth of the 1st gear engages with a part for the external tooth of the 2nd gear, one in the internal tooth of the 1st gear and the external tooth of the 2nd gear, it is the tooth being formed with pericycloid profile of tooth on side face, another one is for pin being inserted the groove and the tooth that formed that are formed at side face, one in the 2nd gear and the 3rd gear is formed with external tooth, another one in the 2nd gear and the 3rd gear is formed with internal tooth, a part for 2nd gear engages with a part for the 3rd gear, be formed at the external tooth in the one in the 2nd gear and the 3rd gear, be formed at the tooth of the side in the internal tooth in the another one in the 2nd gear and the 3rd gear, it is the tooth being formed with pericycloid profile of tooth on side face, the tooth of the opposing party is for pin being inserted the groove being formed at side face and the tooth formed, at least one party in " between the 1st gear and the 2nd gear " and " between the 2nd gear and the 3rd gear " is provided with number of teeth difference, when the 2nd gear revolves round the sun, 3rd gear carries out rotation.
Preferably, on the same axis, the geometrical center of the 2nd gear is from described journal offset in the axle center configuration of the geometrical center of the 1st gear, the geometrical center of the 3rd gear and output shaft.
Preferably, the 1st gear dual-purpose does housing, and the 3rd gear and output shaft are fixed together, and the 3rd gear and output shaft are supported to can relative to housing rotation.
Preferably, be attached with: the input shaft extended on the same axis with output shaft; And around the eccentric swing body revolved round the sun in the axle center of input shaft, when the axle center revolution of eccentric swing body around input shaft, the 2nd gear revolves round the sun.
Preferably, eccentric swing body has the periphery being centrally located at the position offset from the axle center of input shaft, between the periphery of eccentric swing body and the inner circumferential of the 2nd gear, be folded with bearing.
Preferably, the 2nd gear is formed and the external tooth of the 1st gears meshing and the internal tooth with the 3rd gears meshing, the 3rd gear is formed with external tooth, a part for the internal tooth of the 2nd gear engages with a part for the external tooth of the 3rd gear.
Preferably, the internal tooth being formed at the 1st gear is for pin being inserted the groove being formed at inner peripheral surface and the tooth formed, the external tooth and the internal tooth that are formed at the 2nd gear are all the teeth being formed with pericycloid profile of tooth at outer circumferential face, being formed at the external tooth of the 3rd gear, is for pin being inserted the groove and the tooth that formed that are formed at outer circumferential face.
Preferably, the 2nd gear is formed and the external tooth of the 1st gears meshing and the external tooth with the 3rd gears meshing, the 3rd gear is formed with internal tooth, a part for the external tooth of the 2nd gear engages with a part for the internal tooth of the 3rd gear.
Preferably, be formed at the internal tooth of the 1st gear, for pin being inserted the groove and the tooth that formed that are formed at inner peripheral surface, be formed at two external tooths of the 2nd gear, it is the tooth being formed with pericycloid profile of tooth at outer circumferential face, being formed at the internal tooth of the 3rd gear, is for pin being inserted the groove and the tooth that formed that are formed at inner peripheral surface.
Preferably, the 2nd gear has the upper and lower utilizing bolt fixing, and the outer circumferential face on top and the outer circumferential face of bottom are all formed with pericycloid profile of tooth.
Another technological scheme of the present utility model is speed change gear, it is characterized in that, the 1st gear, and it is fixed on housing; 3rd gear, it is supported to can relative to housing rotation; Output shaft, it is fixed on the 3rd gear; Input shaft, it is supported to can relative to housing rotation; Eccentric swing body, it is fixed on input shaft, and when input shaft carries out time rotational, it revolves round the sun; 2nd gear, it utilizes eccentric swing body to locate, and engages with a part for the 1st gear and a part for the 3rd gear, and at least one party in " between the 1st gear and the 2nd gear " and " between the 2nd gear and the 3rd gear " is provided with number of teeth difference.
Preferably, be supported to can relative to the rotation freely of eccentric swing body for the 2nd gear.
Accompanying drawing explanation
Fig. 1 exemplifies the 1st example of speed change gear in the past.
Fig. 2 exemplifies the 2nd example of speed change gear in the past.
Fig. 3 exemplifies the 3rd example of speed change gear in the past.
Fig. 4 exemplifies the 4th example of speed change gear in the past.
Fig. 5 exemplifies an example of the speed change gear that this specification is recorded.
Fig. 6 exemplifies other examples of the speed change gear that this specification is recorded.
Fig. 7 represents the plan view of the speed change gear of the 1st embodiment.
Fig. 8 represents the sectional view of the speed change gear of the 1st embodiment.
Fig. 9 represents the plan view of the speed change gear of the 2nd embodiment.
Figure 10 represents the sectional view of the speed change gear of the 2nd embodiment.
Embodiment
Below, several technical characteristicss of embodiment disclosed in notebook specification.In addition, the item below recorded individually possesses skills the serviceability of aspect.
The revolution center of (feature 1) the 1st geometrical center of internal tooth of gear, the internal tooth of the 3rd gear or the geometrical center of external tooth, the axle center of output shaft and the 2nd gear on the same axis.
(feature 2), as illustrated in Fig. 5 and Fig. 6, the symmetry axis (axle through geometrical center) of input shaft 101, the 1st gear 107, the axis of rotation of the 3rd gear 118,120 and output shaft 109 are configured on the 1st axis that represents with reference character A.The axis of rotation of the 2nd gear 103 with the 1st axis A parallel the 2nd axis (representing with reference character B) that extends is configured in the position with the 1st axis A offset distance D.
(feature 3) is attached with the input shaft 101 extended on the same axis with output shaft 109 and the eccentric swing body 101a revolved round the sun around the axle center of input shaft 101.When the axle center revolution of eccentric swing body 101a around input shaft 101, the 2nd gear 103 carries out revolving round the sun (axis of rotation B of the 2nd gear rotates around the axle center A of input shaft 101).Eccentric swing body 101a can be the bent axle extended abreast in the position offset from input shaft 101 and input shaft 101, also can be the eccentric cam with the circumference being centrally located at the position offset from input shaft 101.Eccentric cam has the circumferential surface of the position be centrally located at from the skew of the axle center of input shaft 101, and therefore, eccentric cam is the component can revolved round the sun in center.
(feature 4) eccentric swing body 101a has the periphery of the position be centrally located at from the skew of the axle center of input shaft 101.Bearing is folded with between the periphery of eccentric swing body 101a and the inner circumferential of the 2nd gear 103.Utilize this bearing, the 2nd gear 103 can carry out rotation.2nd gear 103 freely can carry out rotation relative to housing 107.Namely, between the 2nd gear 103 and housing 107, there is not the relation of the rotation of constraint the 2nd gear 103.In addition, between the 2nd gear 103 and input shaft 101, there is not the relation of the rotation of constraint the 2nd gear 103 yet.And, between the 2nd gear 103 and output shaft 109, there is not the relation of the rotation of constraint the 2nd gear 103 yet.
(feature 5) as shown in Figure 5, the 2nd gear 103 is formed with external tooth 103f and internal tooth 103g.3rd gear 118 is formed with external tooth.The part engagement of a part of the internal tooth 103g of the 2nd gear 103 and the external tooth 118f of the 3rd gear 118.
(feature 6) as shown in Figure 6, the 3rd gear 120 is formed with internal tooth 120h.A part of the external tooth 103h of the 2nd gear 103 engages with a part of the internal tooth 120h of the 3rd gear 120.
(feature 7) as shown in Figure 6, the internal tooth 105 of the 1st gear 107 and the internal tooth 120h of the 3rd gear 120 are configured in different positions on the direction of the axis of rotation along the 3rd gear 120.
Both there is the number of teeth of the external tooth 103f of the 2nd gear 103 embodiment different from the number of teeth of the external tooth 103h of the 2nd gear 103 in (feature 8), also there is the embodiment that the number of teeth of the external tooth 103f of the 2nd gear 103 is identical with the number of teeth of the external tooth 103h of the 2nd gear 103, external tooth 103f engages with the internal tooth 105 of the 1st gear 107, and external tooth 103h engages with the internal tooth 120h of the 3rd gear 120.
(feature 9) the 2nd gear can be made up of 1 component, also multiple component can be fixed together and form.
(feature 10) the 1st gear be fixed on housing, the 3rd gear is fixed on output shaft.2nd gear is formed with the external tooth of the 1st gears meshing, with the external tooth of the 3rd gears meshing or internal tooth and the opening for receiving eccentric swing body (revolution body), they all configure on the same axis.2nd gear is relative to eccentric swing body (revolution body) rotation freely.
Embodiment
(the 1st embodiment)
Fig. 7 and Fig. 8 illustrates the embodiment corresponding with Fig. 5.Reference character 2 is motors, and it is fixed on the housing 20 of speed change gear 30.Reference character 6 is motor axis of rotation, and it is around the 1st axis A rotation.Reference character 8 is components that dual-purpose does input shaft and eccentric swing body (revolution body), has the cylindrical part 8a coaxial with the 1st axis A, eccentric cam 8b and the cylindrical part 8c coaxial with the 1st axis A.Cylindrical part 8a utilizes bearing 12 can be supported on to rotation output shaft described later (certainly turning) 24, cylindrical part 8c to utilize bearing 4 can be supported on housing 20 to rotation.Motor axis of rotation 6 is formed keyway 6a.Input shaft 8 is formed the raised line 8d for inserting keyway 6a.When motor axis of rotation 6 carries out time rotational around axis A, input shaft 8 carries out rotation around the 1st axis A.
Eccentric cam 8b has circular outer circumferential face.The center of eccentric cam 8b is on the 2nd axis B.2nd axis B is from the 1st axis A offset distance D.Namely the distance c, from B axis to the outer circumferential face of eccentric cam 8b is constant, has nothing to do with orientation.On the other hand, change as shown in " a " or " b " from A axis to the distance of the outer circumferential face of eccentric cam 8b according to orientation.
The plectane portion 16c of the 2nd gear 16 is positioned at around eccentric cam 8b.Be formed with opening 16f at the center of plectane portion 16c, between central opening 16f and eccentric cam 8b, be folded with bearing 10.When input shaft 8 is around axis A time rotational, the central shaft B of eccentric cam 8b revolves round the sun around axis A, and geometrical central axis (axis of rotation) B of the 2nd gear 16 also revolves round the sun around axis A.
2nd gear 16 is around geometrical central axis B Rotational Symmetry.The annular gear wheel 16b with external tooth and internal tooth is fixed on plectane portion 16c by bolt 16d.As shown in Figure 7, the outer circumferential face 16a of annular gear wheel 16b is formed with the profile of tooth of pericycloid.The inner peripheral surface 16e of annular gear wheel 16b is also formed the profile of tooth of pericycloid.The profile of tooth being formed at the outer circumferential face of annular gear wheel 16b is called as external tooth 16a, and the profile of tooth being formed at inner peripheral surface is called as internal tooth 16e.Annular gear wheel 16b can be called as the 2nd gear body.2nd gear 16 is housed in housing 20.
Housing 20 has base plate 20f, the 1st gear body 20d and upper plate 20a, utilizes bolt 20e, 20b etc. to come integrated.Reference character 27 is O RunddichtringOs, by airtight relative to air in housing.Hole 20g is the mounting hole for speed change gear 30 being fixed on robot etc.
As shown in Figure 7, the inner peripheral surface 20c of the 1st gear body 20d is the circumferential surface centered by axis A.Inner peripheral surface 20c is formed groove 20h that cross section is semicircle shape at predetermined intervals.Pin 18 is inserted with in each groove 20h.Pin 18 can rotation in half slot 20h.The outer circumferential face 16a of annular gear wheel 16b is close to the inner peripheral surface 20c of the 1st gear body 20d.Therefore, pin 18 can not depart from from groove 20h.Internal tooth 19 is formed by the inner peripheral surface 20c of pin 18 and the 1st gear body 20d.Housing 20 can be called as the 1st gear being formed with internal tooth 19 on inner peripheral surface.Housing 20 can be the 1st gear, also can be internal gear.Because entity is the same, so use common reference character 20 for housing, the 1st gear, internal gear.Even other components, be for identical component for entity, from function aspects, even if use different titles, also use common reference character.
As shown in Figure 7, the part being formed at the internal tooth 19 of the 1st gear 20 engages with a part of the external tooth 16a of the outer circumferential face being formed at annular gear wheel 16b.In the case of fig. 7, the central shaft B of the external tooth 16a of annular gear wheel 16b is eccentric to the right relative to the central shaft A of internal tooth 19.Therefore, on the right side of Fig. 7, internal tooth 19 and external tooth 16a engage darker.In the left side of Fig. 7, internal tooth 19 and external tooth 16 contact but do not engage.The part that can be referred to as internal tooth 19 engages with a part of external tooth 16a, and a part for internal tooth 19 does not engage with a part of external tooth 16a.In addition, " engagement " this term of this specification refer to outward appearance seem engagement." engagement " this term is different from the region of carrying out moment of torsion transmission between internal tooth and external tooth.The number of teeth being formed at the internal tooth 19 of the 1st gear 20 is inconsistent with the number of teeth of the external tooth 16a being formed at the 2nd gear 16.In the present embodiment, the former is 30, and the latter is 29.
As shown in Figure 8, contain in the inner side of annular gear wheel 16b to hold concurrently and certainly turn 24 as the 3rd gear and output shaft.24 there is the 3rd gear body 24b and output shaft 24c from turning, and utilize bolt 24a integration.24 utilize bearing 26,28 can be supported on housing 20 to rotation from turning.A axis is equal to from the axis of rotation of (dual-purpose does the 3rd gear and output shaft) 24 of turning.
Hole 24d be for not shown object is fixed on dual-purpose do output shaft certainly turn 24 mounting hole.Such as, when in advance the base portion side of the arm of robot to be fixed on housing 20 mounting hole 20g and the tip side of the arm of robot is fixed on from turn 24 mounting hole 24d, utilize motor 2 that input shaft 8 is rotated time, the tip side of arm is rotated relative to the base portion side of arm.Speed change gear 30 can make the rotational speed decelerates of motor 2 and the tip side of arm is rotated.Reference character 25 is oil sealings, for preventing from being closed in oil leakage in housing to outside housing.
The 1st axis A is equal to from the axis of rotation of (dual-purpose does the 3rd gear and output shaft) 24 of turning.As shown in Figure 7, the outer circumferential face 24e centered by the 1st axis A is formed with the groove 24f that cross section is semicircle shape at predetermined intervals.Pin 22 is inserted with in each groove 24f.Pin 22 can rotation in groove 24f.As shown in Figure 7, the inner peripheral surface 16e of annular gear wheel 16b is close to the outer circumferential face 24e of the 3rd gear body 24b.Therefore, pin 22 can not depart from from groove 24f.External tooth 23 is formed by the outer circumferential face 24e entirety of pin 22 and the 3rd gear body 24b.
As shown in Figure 7, the inner peripheral surface 16e of annular gear wheel 16b is formed with the profile of tooth of pericycloid.The part of the external tooth 23 of the 3rd gear body 24b engages with a part of internal tooth 16e for the inner peripheral surface being formed at annular gear wheel 16b.In the case of fig. 7, the central shaft B of the internal tooth 16e of annular gear wheel 16b is eccentric to the right relative to the central shaft A of external tooth 23.Therefore, in the left side of Fig. 7, internal tooth 16e and external tooth 23 engage darker.On the right side of Fig. 7, internal tooth 16e and external tooth 23 contact but do not engage.The number of teeth of the number of teeth of the external tooth 23 of the 3rd gear body 24b and the internal tooth 16e of annular gear wheel 16b is inconsistent.In the present embodiment, the former is 20, and the latter is 19.
The action of speed change gear 30 is described.Make motor axis of rotation 6 around axis A time rotational when drive motor 2, the central shaft B of eccentric cam 8b revolves round the sun around axis A, and the 2nd gear 16 follows these actions revolves round the sun.Between internal tooth 19 and external tooth 16a, be provided with number of teeth difference, therefore, when the 2nd gear 16 revolves round the sun relative to the 1st gear 20, the 2nd gear 16 also carries out rotation.Bearing 10 is inserted between the 2nd gear 16 and eccentric cam 8b, the 2nd gear 16 can be made to carry out rotation.
Between internal tooth 16e and external tooth 23, be provided with the number of teeth, when the 2nd gear 16 revolves round the sun, the 3rd gear 24 carries out rotation.When the 2nd gear 16 carries out time rotational, the 2nd gear 16 from revolution having an impact from revolution to the 3rd gear 24.In the present embodiment, the sense of rotation of the 3rd gear 24 produced by the revolution of the 2nd gear 16 is contrary with the sense of rotation of the 2nd gear 16.Namely, " speed of autorotation of the 3rd gear 24 "=" speed of autorotation of the 3rd gear 24 caused by the revolution of the 2nd gear 16 "-" speed of autorotation of the 2nd gear 16 ".Therefore, the speed of autorotation of the 3rd gear 24 slowly.Speed change gear 30 obtains larger gear ratio.
In the above-described embodiment, the number of teeth of the external tooth 23 of the 3rd gear 24 is different from the number of teeth of the internal tooth 16e of the 2nd gear 16.But, it is not indispensable that number of teeth difference is set, as long as make both consistent.Even if both are consistent, the 2nd gear 16 carrying out planetary motion also can be utilized to make the 3rd gear 24 rotation.In this case, the speed of autorotation of the 3rd gear 24 that the revolution due to the 2nd gear 16 causes is zero, becomes " absolute value of the speed of autorotation of the 3rd gear 24 "=the relation of " absolute value of the speed of autorotation of the 2nd gear 16 ".In addition, by selecting the number of teeth ,=the relation of " speed of autorotation that the revolution due to the 2nd gear 16 causes "+" speed of autorotation of the rotation of the 2nd gear 16 " can be obtained " speed of autorotation of the 3rd gear 24 ".In the present embodiment, the number of teeth selecting the symbol of the speed of autorotation of the 3rd gear 24 consistent with the symbol of the speed of autorotation of input shaft 8.By selecting the number of teeth, the symbol of the speed of autorotation of the 3rd gear 24 can be made different from the symbol of the speed of autorotation of input shaft 8.Namely, the sense of rotation of motor 2 can be made consistent with the sense of rotation of output shaft 24c, their direction also can be made contrary.
For above-mentioned speed change gear 30, rotating force can be transmitted to the 3rd gear body 24b integrated with output shaft 24c.Speed change gear 30 in order to rotating force is delivered to output shaft, without the need to bifurcated top 109c, 109d shown in Fig. 1, Fig. 2 and Fig. 3.When utilizing bifurcated top 109c, 109d to carry out the mode of transmitting torque, the problem of the strength deficiency of so-called bifurcated top 109c, 109d must be solved.Therefore, the miniaturization of speed change gear is hindered.What is called needs the structure self of bifurcated top 109c, 109d also to hinder miniaturization.And the existence of bifurcated top 109c, 109d will improve manufacture cost.In the present embodiment, rotating force is delivered to the 3rd gear body 24b of the axis of rotation (A axis) rotation around output shaft 24c.Therefore, speed change gear 30 does not need bifurcated top 109c, 109d, is therefore suitable for speed change gear miniaturization.
In addition, adopt the present embodiment, the internal tooth 16e of the internal tooth 19 of the 1st gear 20 and the external tooth 16a of the 2nd gear 16 engaged with internal tooth 19 and the external tooth 23 of the 3rd gear 24 and the 2nd gear 16 engaged with external tooth 23 can be placed in same plane.Can make along the lower thickness on the direction of the running shaft A of speed change gear 30.In the present embodiment, multiple component is utilized to form the 2nd gear 16.Because the 2nd gear self carries out moving integratedly, so 1 component also can be utilized to form the 2nd gear 16.
In the above-described embodiments, the number of teeth of the external tooth 23 of the 3rd gear body 24b is different from the number of teeth of the internal tooth 16e of the 2nd gear 16.But, it is not indispensable that number of teeth difference is set, both also can be made consistent.Even if make both consistent, the 2nd gear 16 carrying out planetary motion also can be utilized to make the 3rd gear 24 rotation.As long as there is number of teeth difference between the 1st gear and the 2nd gear, even if there is not number of teeth difference between the 2nd gear and the 3rd gear, just also speed change phenomenon can be obtained.As long as at least one party between the 1st gear and the 2nd gear and between the 2nd gear and the 3rd gear exists number of teeth difference, just can obtain speed change phenomenon, and the 3rd gear and output shaft rotation can be made.
(the 2nd embodiment)
Fig. 9 and Figure 10 represents the embodiment corresponding with Fig. 6.For the component identical with the component shown in Fig. 7 with Fig. 8, the reference character that the reference character that the component being used in Fig. 7 and Fig. 8 marks is added with 40 and obtains.Reference character 42 is motors, is fixed on the housing 60 of speed change gear 70.Reference character 46 is motor axis of rotation, around axis A rotation.Motor axis of rotation 46 is formed external tooth 46a.Reference character 44 is spur wheels.Spur wheel 44 is around the axis of rotation 47b rotation fixed by bolt 47a.
Reference character 48 is eccentric swing bodies.Eccentric swing body 48 has eccentric swing phosphor bodies 48b and upper plate 48c, and it is integrated to utilize bolt 48d to come.The inner peripheral surface 48e of upper plate 48c is formed with internal tooth, engages with the external tooth of spur wheel 44.When motor axis of rotation 46 is around axis A time rotational, eccentric swing body 48 is also around axis A rotation.The inner circumferential of eccentric swing phosphor bodies 48b is the circle centered by axis A, is supported by bearing 49a, 49b.Bearing 49a, 49b are configured in the position centered by axis A.
The outer circumferential face 48a of eccentric swing phosphor bodies 48b is circular, and its center is on B axis.B axis is from A axis only offset distance D.Namely, be constant from B axis to the distance c of outer circumferential face 48a, have nothing to do with orientation.On the other hand, change as shown in " a " or " b " from A axis to the distance of outer circumferential face 48a according to orientation.
2nd gear 56 is positioned at around eccentric swing phosphor bodies 48b.2nd gear 56 has top 56d and bottom 56f.Top 56d and bottom 56f utilizes bolt 56e to fix.The inner peripheral surface 56c of the 2nd gear 56 is circular.2nd gear 56 is can around the outer circumferential face 48a rotation of eccentric swing phosphor bodies 48b by bearing 50a, 50b supporting.2nd gear 56 is around axis B rotation.The upper outer circumferential face 56a of the 2nd gear 56 and lower outer circumferential face 56b is also centered by axis B.
When motor axis of rotation 46 is around axis A time rotational, eccentric swing body 48 is also around axis A rotation.The central shaft B of the outer circumferential face 48a of eccentric swing phosphor bodies 48b revolves round the sun around axis A.Its result, geometrical central axis (axis of rotation) B of the 2nd gear 56 also revolves round the sun around axis A.
The upper outer circumferential face 56a of the 2nd gear 56 is formed the profile of tooth of pericycloid, the lower outer circumferential face 56b of the 2nd gear 56 is also formed the profile of tooth of pericycloid.The profile of tooth being formed at outer circumferential face is called as external tooth 56a, and the profile of tooth being formed at lower outer circumferential face is called as external tooth 56b.
Housing 60 has base plate 60f, cylinder portion 60c and upper plate 60a, utilizes the integrations such as bolt 60e, 60b.Hole 60g is the mounting hole for speed change gear 70 being fixed on robot etc.The inner peripheral surface of cylinder portion 60c is the circumferential surface centered by axis A.As shown in Figure 9, the inner peripheral surface of cylinder portion 60c is formed with groove 60h that cross section is semicircle shape at predetermined intervals.Pin 58 is inserted with in each groove 60h.Pin 58 can rotation in half slot 60h.As shown in Figure 10, the lower outer circumferential face 56b of the 2nd gear 56 is close to the inner peripheral surface of cylinder portion 60c, and pin 58 can not depart from from groove 60h.Internal tooth 59 is formed by the inner peripheral surface of pin 58 and cylinder portion 60c.Housing 60 can be called as the 1st gear being formed with internal tooth 59 on inner peripheral surface.
As shown in Figure 10, the part being formed at the internal tooth 59 of the 1st gear 60 engages with a part of the external tooth 56b of the outer circumferential face being formed at the 2nd gear 56.In case of fig. 10, the central shaft B of the external tooth 56b of the 2nd gear 56 is eccentric to the left relative to the central shaft A of internal tooth 59.Therefore, in the left side of Figure 10, internal tooth 59 and external tooth 56b engage darker.On the right side of Figure 10, internal tooth 59 and external tooth 56b contact but do not engage.The number of teeth being formed at the internal tooth 59 of the 1st gear 60 is inconsistent with the number of teeth of the external tooth 56b being formed at the 2nd gear 56.In the present embodiment, the former is 71, and the latter is 70.
What be configured with in the outside of the upper outer circumferential face 56a of the 2nd gear 56 that dual-purpose does the 3rd gear and output shaft turns 64 certainly.From turn 64 utilize bolt 64c by the 3rd gear body 64b and upper plate 64d integration form.64 utilize bearing 66,68 can be supported on housing 60 to rotation from turning.A axis is equal to from the axis of rotation of (dual-purpose does the 3rd gear and output shaft) 64 of turning.
Hole 64e be for not shown object is fixed on dual-purpose do output shaft certainly turn 64 mounting hole.Such as, when in advance the base portion side of the arm of robot to be fixed on housing 60 mounting hole 60g and the tip side of the arm of robot is fixed on from turn 64 mounting hole 64e and motor 42 is driven time, the tip side of arm rotates relative to the base portion side of arm.Speed change gear 70 can reduce the rotating speed of motor 42, and the tip side of arm is rotated.
A axis is equal to from the axis of rotation of (dual-purpose does the 3rd gear and output shaft) 64 of turning.As shown in Figure 9, on the inner peripheral surface 64a centered by A axis, be formed with the groove 64f of semicircle shape at predetermined intervals.Pin 62 is inserted with in each groove 64f.Pin 62 can rotation in groove 64f.As shown in Figure 9, the 2nd gear 56 upper outer circumferential face 56a close to dual-purpose do the 3rd gear certainly turn 64 inner peripheral surface 64a.Therefore, pin 62 can not depart from from groove 64f.By pin 62 and certainly turn 64 inner peripheral surface 64a entirety form internal tooth 63.
The outer circumferential face 56a of the 2nd gear 56 is formed the profile of tooth of pericycloid.As shown in Figure 9, dual-purpose do the 3rd gear certainly turn 64 the part of internal tooth 63 engage with a part of external tooth 56a for the outer circumferential face being formed at the 2nd gear 56.In fig .9, the central shaft B of the external tooth 56a of the 2nd gear 56 is eccentric to the left relative to the central shaft A of internal tooth 63.Therefore, in the left side of Fig. 9, internal tooth 63 and external tooth 56a engage darker.On the right side of Fig. 9, internal tooth 63 and external tooth 56a contact but do not engage.The number of teeth of the external tooth 56a of the 2nd gear 56 with as the 3rd gear certainly turn 64 the number of teeth of internal tooth 63 inconsistent.In the present embodiment, the former is 70, and the latter is 69.
The action of above-mentioned speed change gear 70 is described.Make motor axis of rotation 46 around axis A time rotational when drive motor 42, make eccentric swing body 48 around axis A rotation by spur wheel 44, the central shaft B of the outer circumferential face 48a of eccentric swing phosphor bodies 48b revolves round the sun around axis A.Its result, geometrical central axis (axis of rotation) B of the 2nd gear 56 also revolves round the sun around axis A.Because the number of teeth of the 1st gear 60 is different with the number of teeth of the 2nd gear 56, so when the 2nd gear 56 revolves round the sun relative to the 1st gear 60, the 2nd gear 56 also carries out rotation.Between the 2nd gear 56 and eccentric swing phosphor bodies 48b, be inserted with bearing 50a, 50b, the 2nd gear 56 can rotation.
Because have the number of teeth poor between the 3rd gear 64 and the 2nd gear 56, when the 2nd gear 56 revolves round the sun, the 3rd gear 64 carries out rotation.When the 2nd gear 16 carries out time rotational, rotation the having an impact from revolution to the 3rd gear 64 of the 2nd gear 16.In the present embodiment, " speed of autorotation of the 3rd gear 64 "=" speed of autorotation of the 3rd gear 64 that the revolution due to the 2nd gear 56 causes "-" speed of autorotation of the 2nd gear 56 ".Therefore, the speed of autorotation of the 3rd gear 64 slowly.Speed change gear 70 can obtain larger gear ratio.
In the above-described embodiments, the number of teeth of the internal tooth 63 of the 3rd gear 64 is different from the number of teeth of the external tooth 56a of the 2nd gear 56.But it is not indispensable for arranging number of teeth difference between internal tooth 63 and external tooth 56a, and both also can be consistent.Even if both numbers of teeth are consistent, the 2nd gear 56 carrying out planetary motion also can be utilized to make the 3rd gear 64 rotation.In this case, the speed of autorotation of the 3rd gear 64 caused by the revolution of the 2nd gear 56 is zero, becomes " absolute value of the speed of autorotation of the 3rd gear 64 "=the relation of " absolute value of the speed of autorotation of the 2nd gear 56 ".
When using above-mentioned speed change gear 70, being delivered to by rotating force holds concurrently turns 64 certainly as output shaft and the 3rd gear.In order to rotating force is delivered to output shaft, without the need to bifurcated top 109c, 109d shown in Fig. 1, Fig. 2 and Fig. 3.When utilizing the mode of bifurcated top 109c, 109d transmitting torque, the miniaturization of speed change gear will be hindered.In the present embodiment, 64 are certainly turned, so without the need to bifurcated top 109c, 109d because be delivered to by rotating force to hold concurrently as output shaft and the 3rd gear.Therefore, be suitable for the speed change gear miniaturization of embodiment.
In the above-described embodiments, although be fixed housing (the 1st gear) (motionless), obtain from output shaft (the 3rd gear) and export (rotation), but also can be that output shaft (the 3rd gear) is fixed, obtain from housing (the 1st gear) and export (rotation).
Above, understand concrete example of the present utility model in detail, but these only illustrate, and do not limit claims.In the technology described in claims, comprise and various distortion, change and the technological scheme obtained are carried out to concrete example illustrated above.The technical characteristics illustrated in this specification or accompanying drawing plays technical serviceability by independent or various combination, is not limited to the combination described in claim when applying for.In addition, this specification or the technology illustrated in accompanying drawing can realize multiple object simultaneously, the serviceability on the technology itself realizing the object of one of them possesses skills.
Claims (12)
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012207791A JP2014062588A (en) | 2012-09-21 | 2012-09-21 | Gearshifter |
| JP2012-207791 | 2012-09-21 | ||
| PCT/JP2013/074870 WO2014046049A1 (en) | 2012-09-21 | 2013-09-13 | Transmission device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204610711U true CN204610711U (en) | 2015-09-02 |
Family
ID=50341362
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201390000767.3U Expired - Fee Related CN204610711U (en) | 2012-09-21 | 2013-09-13 | Speed change gear |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2014062588A (en) |
| CN (1) | CN204610711U (en) |
| TW (1) | TW201422945A (en) |
| WO (1) | WO2014046049A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107559388A (en) * | 2016-06-30 | 2018-01-09 | 兄弟工业株式会社 | Decelerator |
| CN108953499A (en) * | 2017-05-19 | 2018-12-07 | 丰田自动车株式会社 | Gear assembly |
| CN109780141A (en) * | 2019-01-26 | 2019-05-21 | 天津大学 | Conjugate cam hypocycloid reducer |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101990727B1 (en) * | 2015-06-02 | 2019-06-18 | 닛산 지도우샤 가부시키가이샤 | The variable compression ratio mechanism |
| CA2987707C (en) | 2015-06-02 | 2019-02-19 | Hitachi Automotive Systems, Ltd. | Variable compression ratio mechanism for internal combustion engine |
| JP2018087606A (en) * | 2016-11-29 | 2018-06-07 | 武蔵精密工業株式会社 | Transmission device for vehicle |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4212453Y1 (en) * | 1964-07-06 | 1967-07-13 | ||
| JPS63145842A (en) * | 1986-12-05 | 1988-06-17 | Muneharu Morozumi | Speed reducing mechanism |
| JP4171112B2 (en) * | 1998-09-04 | 2008-10-22 | 西部電機株式会社 | Gear reducer |
-
2012
- 2012-09-21 JP JP2012207791A patent/JP2014062588A/en active Pending
-
2013
- 2013-09-13 CN CN201390000767.3U patent/CN204610711U/en not_active Expired - Fee Related
- 2013-09-13 WO PCT/JP2013/074870 patent/WO2014046049A1/en active Application Filing
- 2013-09-17 TW TW102133704A patent/TW201422945A/en unknown
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107559388A (en) * | 2016-06-30 | 2018-01-09 | 兄弟工业株式会社 | Decelerator |
| CN108953499A (en) * | 2017-05-19 | 2018-12-07 | 丰田自动车株式会社 | Gear assembly |
| CN109780141A (en) * | 2019-01-26 | 2019-05-21 | 天津大学 | Conjugate cam hypocycloid reducer |
| CN109780141B (en) * | 2019-01-26 | 2021-09-28 | 天津大学 | Conjugate cam hypocycloid speed reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014046049A1 (en) | 2014-03-27 |
| JP2014062588A (en) | 2014-04-10 |
| TW201422945A (en) | 2014-06-16 |
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