TWI811833B - Harmonic speed reducer - Google Patents
Harmonic speed reducer Download PDFInfo
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Abstract
Description
本發明涉及一種減速裝置,特別是一種具有兩個剛輪的諧波減速裝置。 The invention relates to a deceleration device, in particular to a harmonic deceleration device with two rigid wheels.
請參閱圖1,其顯示為習知的雙剛輪諧波減速裝置的局部剖面示意圖。習知的雙剛輪諧波減速裝置的柔輪F,安裝於波產生器WG的外圍後,柔輪F的外齒狀結構F1將會變形,而變形後的外齒狀結構F1與兩個剛輪R1、R2所分別具有的內齒狀結構R11、R21的內側將產生干涉(即圖1中圈選處A)的問題,如此,將導致柔輪F與兩剛輪R1、R2的嚙合效率降低,進而會導致雙剛輪諧波減速裝置的使用壽命下降。 Please refer to Figure 1, which shows a partial cross-sectional schematic diagram of a conventional double rigid wheel harmonic reduction device. After the flexspline F of the conventional double rigid wheel harmonic reduction device is installed on the periphery of the wave generator WG, the external tooth-shaped structure F1 of the flexspline F will be deformed, and the deformed external tooth-shaped structure F1 is connected with the two The inner sides of the internal tooth structures R11 and R21 of the rigid sprockets R1 and R2 respectively will cause interference (i.e. the circled area A in Figure 1). This will lead to the meshing of the flex spline F with the two rigid sprockets R1 and R2. The efficiency is reduced, which in turn will lead to a reduction in the service life of the double rigid wheel harmonic reduction device.
本發明公開一種諧波減速裝置,主要用以改善習知的雙剛輪諧波減速裝置,所存在的嚙合效率不佳及使用壽命低的問題。 The invention discloses a harmonic deceleration device, which is mainly used to improve the problems of poor meshing efficiency and low service life of the conventional double rigid wheel harmonic deceleration device.
本發明的其中一實施例公開一種諧波減速裝置包含:一波產生器、一柔輪及兩剛輪。波產生器用以連接一驅動單元,波產生器能被驅動單元帶動,而以一中心軸為中心旋轉;柔輪與波產生器的外圍相連接,柔輪的外圍具有多個第一外齒狀結構、多個第二外齒狀結構及一分隔槽,分隔槽位於各個第一外齒狀結構及各個第二外齒狀結構之間;兩剛輪分別定義為一第一剛輪及一第二剛輪,第一剛輪包含多個第一內齒狀結構,第二剛輪包含多個第二內齒狀結構,多個第一內齒狀結構用以與多個第一外齒狀結構嚙合,多個第二內齒狀結構用以與多個第二外齒狀結構嚙合;第一剛輪包含的多個第一內齒狀結構的數量與柔輪所包含的多個第一外齒狀結構的數量相 同,第二剛輪包含的多個第二內齒狀結構的數量大於柔輪所包含的多個第二外齒狀結構的數量;第一剛輪的彼此相反的兩側分別定義為一內側及一外側,第二剛輪的彼此相反的兩側分別定義為一內側及一外側,第一剛輪與第二剛輪彼此相鄰地設置,且第一剛輪的內側與第二剛輪的內側彼此相面對地設置;第一剛輪的各個第一內齒狀結構包含一第一頂面及四個第一連接面,四個第一連接面與第一頂面的四邊線相連接;各個第一頂面與一截面的一第一交線,與平行於中心軸的一第一水平線的一第一夾角介於0.1~5度,且於截面中,第一交線與中心軸之間的直線距離是由第一剛輪的內側向第一剛輪的外側逐漸變小,截面的一法線方向與中心軸相互垂直,且中心軸通過截面;其中,所述第二剛輪的各個所述第二內齒狀結構包含一第二頂面及四個第二連接面,四個所述第二連接面與所述第二頂面的四邊線相連接;各個所述第二頂面與所述截面的一第二交線,與平行於所述中心軸的一第二水平線的一第二夾角介於0.1~5度,且於所述截面中,所述第二交線與所述中心軸之間的直線距離是由所述第二剛輪的所述內側向所述第二剛輪的所述外側逐漸變小。其中,柔輪被波產生器帶動而變形的最大徑向尺寸定義為一柔輪長軸,柔輪被波產生器帶動而變形的最小徑向尺寸定義為一柔輪短軸,柔輪長軸定義為CL,柔輪短軸定義為CS,各個第一內齒狀結構的一第一齒面寬定義為L1,第一夾角定義為θ1,各個第二內齒狀結構的一第二齒面寬定義為L2,第二夾角定義為θ2;其中,CL、CS、L1、θ1符合θ1=C1*tan-1((CL-CS)/(4*L1))的關係式,且0.08≦C1≦0.45;或者,CL、CS、L2、θ2符合θ2=C2*tan-1((CL-CS)/(4*L2))的關係式,且0.08≦C2≦0.45。 One embodiment of the present invention discloses a harmonic deceleration device including: a wave generator, a flexspline and two rigid splines. The wave generator is used to connect to a driving unit. The wave generator can be driven by the driving unit and rotate around a central axis. The flexspline is connected to the periphery of the wave generator. The periphery of the flexspline has a plurality of first external teeth. structure, a plurality of second external tooth-shaped structures and a separation groove, the separation groove is located between each first external tooth-shaped structure and each second external tooth-shaped structure; the two rigid wheels are respectively defined as a first rigid wheel and a first Two rigid wheels, the first rigid wheel includes a plurality of first internal tooth-shaped structures, the second rigid wheel includes a plurality of second internal tooth-shaped structures, and the plurality of first internal tooth-shaped structures are used to communicate with the plurality of first external tooth-shaped structures. Structural meshing, a plurality of second internal tooth-like structures are used to mesh with a plurality of second external tooth-like structures; the number of the plurality of first internal tooth-like structures included in the first rigid wheel is equal to the number of the plurality of first internal tooth-like structures included in the flexspline. The number of external tooth-like structures is the same, and the number of multiple second internal tooth-like structures included in the second rigid wheel is greater than the number of multiple second external tooth-like structures included in the flexspline; the two opposite sides of the first rigid wheel are opposite to each other. The sides are respectively defined as an inner side and an outer side, the opposite sides of the second rigid wheel are respectively defined as an inner side and an outer side, the first rigid wheel and the second rigid wheel are arranged adjacent to each other, and the first rigid wheel The inner side and the inner side of the second rigid wheel are arranged facing each other; each first internal tooth structure of the first rigid wheel includes a first top surface and four first connecting surfaces, and the four first connecting surfaces are connected to the first The four sides of the top surface are connected; a first intersection between each first top surface and a cross section and a first horizontal line parallel to the central axis range from 0.1 to 5 degrees, and in the cross section, The straight-line distance between the first intersection line and the central axis gradually decreases from the inside of the first rigid wheel to the outside of the first rigid wheel, a normal direction of the section is perpendicular to the central axis, and the central axis passes through the section; where , each second internal tooth-like structure of the second rigid wheel includes a second top surface and four second connection surfaces, and the four second connection surfaces are opposite to the four sides of the second top surface. Connection; a second intersection line of each second top surface and the cross section, and a second included angle between a second horizontal line parallel to the central axis, ranging from 0.1 to 5 degrees, and in the cross section , the linear distance between the second intersection line and the central axis gradually becomes smaller from the inner side of the second rigid wheel toward the outer side of the second rigid wheel. Among them, the maximum radial dimension of the flexspline driven by the wave generator and deformed is defined as a flexspline long axis, the minimum radial dimension of the flexspline driven by the wave generator is defined as a flexspline short axis, and the flexspline long axis is defined as C L , the minor axis of the flexspline is defined as CS , a first tooth surface width of each first internal tooth-like structure is defined as L 1 , a first included angle is defined as θ 1 , a first tooth surface width of each second internal tooth-like structure is defined as θ 1 The second tooth surface width is defined as L 2 , and the second included angle is defined as θ 2 ; among them, C L , C S , L 1 , and θ 1 comply with θ 1 =C 1 *tan -1 ((C L -C S )/ (4*L 1 )), and 0.08≦C 1 ≦0.45; or, C L , C S , L 2 , θ 2 are consistent with θ 2 =C 2 *tan -1 ((C L -C S ) /(4*L 2 )), and 0.08≦C 2 ≦0.45.
綜上所述,本發明的諧波減速裝置通過第一夾角、第二夾角及分隔槽的設計,可以有效地提升柔輪的第一外齒狀結構與第一剛輪的第一內齒狀結構的嚙合效率,以及柔輪的第二外齒狀結構與第二剛輪的第二內齒狀結構的嚙合效率,進而可以提升諧波減速裝置的使用壽命。 To sum up, the harmonic deceleration device of the present invention can effectively improve the first external tooth structure of the flexspline and the first internal tooth structure of the first rigid sprocket through the design of the first included angle, the second included angle and the separation groove. The meshing efficiency of the structure, as well as the meshing efficiency of the second external tooth-shaped structure of the flexspline and the second internal tooth-shaped structure of the second rigid wheel, can thereby increase the service life of the harmonic reduction device.
為能更進一步瞭解本發明的特徵及技術內容,請參閱以下有關本發明的詳細說明與附圖,但是此等說明與附圖僅用來說明本發明,而非對本發明的保護範圍作任何的限制。 In order to further understand the characteristics and technical content of the present invention, please refer to the following detailed description and drawings of the present invention. However, these descriptions and drawings are only used to illustrate the present invention and do not make any reference to the protection scope of the present invention. limit.
習知:Common knowledge:
Q:諧波減速裝置 Q: Harmonic reduction device
F:柔輪 F:flexspline
F1:外齒狀結構 F1: External tooth-like structure
WG:波產生器 WG: Wave Generator
R1、R2:剛輪 R1, R2: rigid wheel
R11、R21:內齒狀結構 R11, R21: Internal tooth-like structure
A:圈選處 A: Circle selection place
本發明:The present invention:
100:諧波減速裝置 100: Harmonic reduction device
1:波產生器 1: Wave generator
2:柔輪 2: Flexspline
2A:環狀本體 2A: Ring body
2A1:第一環狀部 2A1: First ring part
2A2:第二環狀部 2A2: Second ring part
2A3:連接環狀部 2A3: Connecting ring part
2B:分隔槽 2B: Separation tank
21:第一外齒狀結構 21: First external tooth-like structure
22:第二外齒狀結構 22: Second external tooth-like structure
3:第一剛輪 3: The first round
3A:內側 3A:Inside
3B:外側 3B: Outside
31:第一內齒狀結構 31: First internal tooth-like structure
311:頂面 311:Top surface
3111:交線 3111: Intersection
312:連接面 312:Connection surface
4:第二剛輪 4: The second round
4A:內側 4A:Inside
4B:外側 4B:Outside
41:第二內齒狀結構 41: Second internal tooth-like structure
411:頂面 411:Top surface
4111:交線 4111: Intersection
412:連接面 412:Connection surface
CP:中心軸 CP: central axis
S:截面 S: Section
N:法線方向 N: normal direction
H1:第一水平線 H1: first horizontal line
H2:第二水平線 H2: The second horizontal line
θ1:第一夾角 θ1: the first included angle
θ2:第二夾角 θ2: The second included angle
D1:直線距離 D1: Straight line distance
D2:直線距離 D2: Straight line distance
CL:柔輪長軸 C L : Long axis of flexspline
CS:柔輪短軸 C S : Flexspline short shaft
Db:柔輪的內徑 D b : inner diameter of flexspline
Da1:第一外齒狀結構的齒頂圓直徑 D a1 : Tip circle diameter of the first external tooth structure
Df1:第一外齒狀結構的齒根圓直徑 D f1 : Root circle diameter of the first external tooth structure
Da2:第二外齒狀結構的齒頂圓直徑 D a2 : Tip circle diameter of the second external tooth structure
Df2:第二外齒狀結構的齒根圓直徑 D f2 : Root circle diameter of the second external tooth-like structure
L1:第一齒面寬 L 1 : First tooth surface width
L2:第二齒面寬 L 2 : Second tooth surface width
t1:第一環狀部的厚度 t 1 :Thickness of the first annular part
t2:第二環狀部的厚度 t 2 : Thickness of the second annular part
t3:連接環狀部的厚度 t3 :Thickness of connecting ring part
WG:分隔槽的寬度 W G : Width of dividing groove
圖1為習知的雙剛輪諧波減速裝置的局部剖面示意圖。 Figure 1 is a partial cross-sectional schematic diagram of a conventional double rigid wheel harmonic reduction device.
圖2為本發明的諧波減速裝置的示意圖。 Figure 2 is a schematic diagram of the harmonic reduction device of the present invention.
圖3為本發明的諧波減速裝置的剖面示意圖。 Figure 3 is a schematic cross-sectional view of the harmonic reduction device of the present invention.
圖4為本發明的諧波減速裝置的分解示意圖。 Figure 4 is an exploded schematic diagram of the harmonic reduction device of the present invention.
圖5為沿圖2的剖線V-V的剖面示意圖。 FIG. 5 is a schematic cross-sectional view along the cross-section line V-V in FIG. 2 .
圖6為圖5的局部放大示意圖。 FIG. 6 is a partially enlarged schematic diagram of FIG. 5 .
圖7為本發明的諧波減速裝置的第一剛輪及第二剛輪的局部剖面示意圖。 Figure 7 is a partial cross-sectional schematic view of the first rigid wheel and the second rigid wheel of the harmonic reduction device of the present invention.
圖8為本發明的諧波減速裝置的第一剛輪的局部截面示意圖。 Figure 8 is a partial cross-sectional schematic view of the first rigid wheel of the harmonic reduction device of the present invention.
圖9為本發明的諧波減速裝置的第二剛輪的局部截面示意圖。 Figure 9 is a partial cross-sectional schematic view of the second rigid wheel of the harmonic reduction device of the present invention.
圖10為本發明的諧波減速裝置的柔輪的局部剖面示意圖。 Figure 10 is a partial cross-sectional schematic view of the flexspline of the harmonic reduction device of the present invention.
圖11為本發明的諧波減速裝置的柔輪變形前、後的示意圖。 Figure 11 is a schematic diagram of the flexspline before and after deformation of the harmonic reduction device of the present invention.
圖12為本發明的諧波減速裝置的柔輪的局部剖面示意圖。 Figure 12 is a partial cross-sectional schematic view of the flexspline of the harmonic reduction device of the present invention.
圖13為本發明的諧波減速裝置的柔輪的剖面示意圖。 Figure 13 is a schematic cross-sectional view of the flexspline of the harmonic reduction device of the present invention.
於以下說明中,如有指出請參閱特定圖式或是如特定圖式所示,其僅是用以強調於後續說明中,所述及的相關內容大部份出現於該特定圖式中,但不限制該後續說明中僅可參考所述特定圖式。 In the following description, if it is pointed out that please refer to a specific diagram or as shown in a specific diagram, it is only used to emphasize that in the subsequent explanation, most of the relevant content mentioned appears in the specific diagram. However, this is not limited to the specific drawings that can only be referred to in the subsequent description.
請一併參閱圖2至圖6,本發明的諧波減速裝置100包含一波產生器1、一柔輪2及兩剛輪。波產生器1的外圍設置有柔輪2,柔輪2的外圍設置有兩剛輪。為利說明,於以下說明中,將兩剛輪分別定義為一第一剛輪3
及一第二剛輪4,並將第一剛輪3及第二剛輪4所分別包含的多個內齒狀結構,分別定義為第一內齒狀結構31及第二內齒狀結構41。
Please refer to Figures 2 to 6 together. The
波產生器(Wave Generator)1用以連接一驅動單元(例如馬達的轉軸、馬達的轉子等),波產生器1能被驅動單元帶動,而以一中心軸CP為中心旋轉。 The wave generator (Wave Generator) 1 is used to connect a driving unit (such as a motor shaft, a motor rotor, etc.). The Wave Generator 1 can be driven by the driving unit and rotate around a central axis CP.
柔輪2與波產生器1的外圍相連接,柔輪2定義有一環狀本體2A,各個第一外齒狀結構21是形成於環狀本體2A的外圍,各個第二外齒狀結構22是形成於環狀本體2A的外圍,而多個第一外齒狀結構21與多個第二外齒狀結構22之間形成有一分隔槽2B。
The
在其中一個實施例中,各個第一外齒狀結構21的外型可以是與各個第二外齒狀結構22的外型完全相同,且柔輪2所包含的所有第一外齒狀結構21的數量及柔輪2所包含的所有第二外齒狀結構22的數量可以是完全相同,但不以此為限。在不同的實施例中,各個第一外齒狀結構21的外型,也可以是與各個第二外齒狀結構22的外型不相同,舉例來說,多個第一外齒狀結構21可以是直齒設計,而多個第二外齒狀結構22則可以是非直齒設計。
In one embodiment, the appearance of each first external tooth-
第一剛輪3包含多個第一內齒狀結構31,第一剛輪3所包含的多個第一內齒狀結構31用以與柔輪2的多個第一外齒狀結構21相互嚙合。第二剛輪4包含多個第二內齒狀結構41,第二剛輪4所包含的多個第二內齒狀結構41用以與柔輪2的多個第二外齒狀結構22相互嚙合。在實際應用中,第二剛輪4可以是與外部輸出構件相連接,舉例來說,第二剛輪4可以是直接或間接連接至輪子、手臂等構件。
The first
第一剛輪3與第二剛輪4是相鄰地設置,且第一剛輪3的彼此相反的兩側分別定義為一內側3A及一外側3B,第二剛輪4的彼此相反的兩側分別定義為一內側4A及一外側4B,且第一剛輪3的內側3A與第二剛輪4的內側4A相面對地設置。
The first
依上所述,在其中一個具體應用中,柔輪2所包含的多個第一外齒狀結構21的數量,可以是與柔輪2所包含的多個第二外齒狀結構22的數量相同,且第一剛輪3所包含的多個第一內齒狀結構31的數量,可以是與柔輪2的多個第一外齒狀結構21的數量相同,而第二剛輪4所包含的多個第二內齒狀結構41的數量大於柔輪2所包含的多個第二外齒狀結構22的數量。
As mentioned above, in one specific application, the number of the plurality of first external tooth-
承上,當驅動單元帶動波產生器1作動時,波產生器1將帶動柔輪2反覆地撓性變形,而柔輪2的多個第一外齒狀結構21的一部分將與第一剛輪3的多個第一內齒狀結構31的一部分相互嚙合,由於第一剛輪3所包含的第一內齒狀結構31的數量與柔輪2所包含的第一外齒狀結構21的數量相同,因此,柔輪2反覆地撓性變形時,柔輪2不會相對於第一剛輪3旋轉,而反覆地撓性變形的柔輪2的部分第二外齒狀結構22將會與第二剛輪4的部分第二內齒狀結構41相互嚙合,由於柔輪2所包含的第二外齒狀結構22的數量與第二剛輪4的第二內齒狀結構41的數量不相同,因此,第二剛輪4將被反覆地撓性變形的柔輪2帶動而旋轉,如此,驅動單元所輸入的高轉速動力,將由第二剛輪4以相對較低的轉速輸出。
Following the above, when the driving unit drives the wave generator 1 to operate, the wave generator 1 will drive the
請一併參閱圖4至圖8,第一剛輪3的各個第一內齒狀結構31包含一頂面311及四個連接面312,四個連接面312與頂面311的四邊線相連接。各個頂面311與一截面S的一交線3111,與平行於中心軸CP的一第一水平線H1的一第一夾角θ1介於0.1~5度,且於截面S中交線3111與中心軸CP之間的直線距離是由內側3A向外側3B逐漸變小;其中,截面S的一法線方向N與中心軸CP相互垂直,且中心軸CP通過截面S。
Please refer to Figures 4 to 8 together. Each first
相同地,第二剛輪4的各個第二內齒狀結構41包含一頂面411及四個連接面412,四個連接面412與頂面411的四邊線相連接。各個頂面411與截面S的一交線4111,與平行於中心軸CP的一第二水平線H2的一第二夾角
θ2介於0.1~5度,且於截面S中交線4111與中心軸CP之間的直線距離D2是由內側4A向外側4B逐漸變小。
Similarly, each second
依上所述,通過第一夾角θ1、第二夾角θ2及分隔槽2B等設計,可以使柔輪2保持軸向定位,而可有效地提升柔輪2與兩剛輪彼此間的嚙合效率(Mesh Efficiency)及諧波減速裝置100的承載能力,且還可以進一步延長諧波減速裝置100整體的使用壽命。
As mentioned above, through the design of the first included angle θ1, the second included angle θ2 and the
如圖1、圖2、圖4及圖5所示,在習知的諧波減速裝置Q中,柔輪F的外圍不具有本發明的柔輪2所具有的分隔槽2B,而習知的柔輪F安裝於波產生器WG的外圍時,柔輪F的外齒狀結構F1將發生相對明顯的變形的情況,且兩個剛輪R1、R2與柔輪F相互組合後,因為,柔輪F的外齒狀結構F1已經變形,所以柔輪F容易軸向位移,為此,將造成兩個剛輪R1、R2的內齒狀結構R11、R21與柔輪F的外齒狀結構F1的嚙合效率不佳的問題,進而可能導致諧波減速裝置Q整體的使用壽命下降。
As shown in Figures 1, 2, 4 and 5, in the conventional harmonic reduction device Q, the periphery of the flexspline F does not have the
另外,習知的諧波減速裝置Q由於柔輪F的外齒狀結構F1發生相對明顯的變形的情況,因此,習知的諧波減速裝置Q在運作時,柔輪F將容易發生左右晃動的問題。反觀,本發明的諧波減速裝置100,通過使柔輪2具有分隔槽2B、第一夾角θ1(如圖8所示)及第二夾角θ2(如圖9所示)等設計,在諧波減速裝置100在運作時,柔輪2相對不容易發生左右晃動的問題。
In addition, the external tooth-like structure F1 of the flexspline F of the conventional harmonic reduction device Q is relatively significantly deformed. Therefore, when the conventional harmonic reduction device Q is operating, the flexspline F will easily shake left and right. problem. On the other hand, the
請一併參閱圖7至圖12,在較佳的實施例中,柔輪2被波產生器帶動而變形的最大徑向尺寸定義為一柔輪長軸,柔輪2被波產生器帶動而變形的最小徑向尺寸定義為一柔輪短軸;假設柔輪長軸定義為CL,柔輪短軸定義為CS,各個第一內齒狀結構31的一第一齒面寬定義為L1,第一夾角定義為θ1,各個第二內齒狀結構41的一第二齒面寬定義為L2,第二夾角定義為θ2,則CL、CS、L1、θ1符合θ1=C1*tan-1((CL-CS)/(4*L1))的關係式,其中,0.08≦C1≦0.45;CL、CS、L2、θ2符合θ2=C2*tan-1((CL-CS)/(4*L2))的關係式,其中0.08
≦C2≦0.45,如此,將可以使柔輪2、第一剛輪3及第二剛輪4能夠達到相對較佳的嚙合效率。
Please refer to Figures 7 to 12 together. In the preferred embodiment, the maximum radial dimension of the
請一併參閱圖7至圖13,在較佳的實施例中,柔輪2的環狀本體2A可以定義有一第一環狀部2A1、一第二環狀部2A2及一連接環狀部2A3,第一環狀部2A1的一側與連接環狀部2A3相連接,連接環狀部2A3的另一側與第二環狀部2A2相連接,多個第一外齒狀結構21形成於第一環狀部2A1的外圍,多個第二外齒狀結構22形成於第二環狀部2A2的外圍,連接環狀部2A3的外圍、多個第一外齒狀結構21及多個第二外齒狀結構22共同形成分隔槽2B。第一外齒狀結構21的齒頂圓(Addendum Circle)直徑定義為Da1,第一外齒狀結構21的齒根圓(Dedendum Circle)直徑定義為Df1,第二外齒狀結構22的齒頂圓(Addendum Circle)直徑定義為Da2,第二外齒狀結構22的齒根圓(Dedendum Circle)直徑定義為Df2,分隔槽2B的寬度定義為WG;其中,在Df1<Df2時,Df1、Da2、WG符合以下關係式:,3.5≦R≦20.8;其中,在Df1>Df2時,Df2、Da1、WG符合以下關係式:,3.5≦R≦20.8;其中,第一環狀部2A1的厚度定義為t1,第二環狀部2A2的厚度定義為t2,連接環狀部2A3的厚度定義為t3,柔輪2的內徑定義為Db;其中,t1=(Df1-Db)/2,t2=(Df2-Db)/2;當t1<t2時,則t1≦t3≦t2;當t1>t2時,t2≦t3≦t1。
Please refer to Figures 7 to 13 together. In a preferred embodiment, the
依上所述,通過上述設計,可以使柔輪2、第一剛輪3及第二剛輪4能夠達到相對較佳的嚙合效率。
As mentioned above, through the above design, the
綜上所述,本發明的諧波減速裝置通過第一夾角、第二夾角及分隔槽的設計,可以有效地提升柔輪的第一外齒狀結構與第一剛輪的第一內齒狀結構的嚙合效率,以及柔輪的第二外齒狀結構與第二剛輪的第二內齒 狀結構的嚙合效率,進而可以提升諧波減速裝置的使用壽命。另外,通過使第一夾角、第二夾角及柔輪符合上述關係式,還可以更進一步地提升柔輪與第一剛輪的嚙合效率,以及柔輪與第二剛輪的嚙合效率。 To sum up, the harmonic deceleration device of the present invention can effectively improve the first external tooth structure of the flexspline and the first internal tooth structure of the first rigid wheel through the design of the first included angle, the second included angle and the separation groove. The meshing efficiency of the structure, as well as the second external tooth structure of the flexspline and the second internal tooth of the second rigid sprocket The meshing efficiency of the harmonic reduction device can be improved, thereby improving the service life of the harmonic reduction device. In addition, by making the first included angle, the second included angle and the flexspline conform to the above relational expression, the meshing efficiency of the flexspline and the first rigid spline, and the meshing efficiency of the flexspline and the second rigid spline can be further improved.
以上僅為本發明的較佳可行實施例,非因此侷限本發明的專利範圍,故舉凡運用本發明說明書及圖式內容所做的等效技術變化,均包含於本發明的保護範圍內。 The above are only the best possible embodiments of the present invention, and do not limit the patent scope of the present invention. Therefore, all equivalent technical changes made by using the description and drawings of the present invention are included in the protection scope of the present invention.
1:波產生器 1: Wave generator
2:柔輪 2: Flexspline
2A:環狀本體 2A: Ring body
2B:分隔槽 2B: Separation tank
21:第一外齒狀結構 21: First external tooth-like structure
22:第二外齒狀結構 22: Second external tooth-like structure
3:第一剛輪 3: The first round
3A:內側 3A:Inside
3B:外側 3B: Outside
31:第一內齒狀結構 31: First internal tooth-like structure
3111:交線 3111: Intersection
4:第二剛輪 4: The second round
4A:內側 4A:Inside
4B:外側 4B:Outside
41:第二內齒狀結構 41: Second internal tooth-like structure
4111:交線 4111: Intersection
Claims (8)
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EP22150665.2A EP4040017A1 (en) | 2021-02-04 | 2022-01-10 | Harmonic speed reducer |
JP2022006221A JP7355410B2 (en) | 2021-02-04 | 2022-01-19 | harmonic reduction device |
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Citations (5)
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JP2009133414A (en) * | 2007-11-30 | 2009-06-18 | Jtekt Corp | Wave gear sspeed reducer and variable transmission ratio steering device |
TW201612438A (en) * | 2014-07-23 | 2016-04-01 | Harmonic Drive Systems | Dual type strain wave gearing |
US9470301B2 (en) * | 2013-10-21 | 2016-10-18 | Hiwin Technologies Corp. | Harmonic drive gear reduction mechanism |
TW201920844A (en) * | 2017-09-07 | 2019-06-01 | 日商和諧驅動系統股份有限公司 | Wave bearing for strain wave gearing |
TWM625103U (en) * | 2021-02-04 | 2022-04-01 | 盟英科技股份有限公司 | Harmonic wave speed reduction device |
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Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2009133414A (en) * | 2007-11-30 | 2009-06-18 | Jtekt Corp | Wave gear sspeed reducer and variable transmission ratio steering device |
US9470301B2 (en) * | 2013-10-21 | 2016-10-18 | Hiwin Technologies Corp. | Harmonic drive gear reduction mechanism |
TW201612438A (en) * | 2014-07-23 | 2016-04-01 | Harmonic Drive Systems | Dual type strain wave gearing |
TW201920844A (en) * | 2017-09-07 | 2019-06-01 | 日商和諧驅動系統股份有限公司 | Wave bearing for strain wave gearing |
TWM625103U (en) * | 2021-02-04 | 2022-04-01 | 盟英科技股份有限公司 | Harmonic wave speed reduction device |
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