TW201723449A - Gear type torque sensing device including an input shaft gear, an output shaft gear, and a planetary gear unit - Google Patents
Gear type torque sensing device including an input shaft gear, an output shaft gear, and a planetary gear unit Download PDFInfo
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- TW201723449A TW201723449A TW104142794A TW104142794A TW201723449A TW 201723449 A TW201723449 A TW 201723449A TW 104142794 A TW104142794 A TW 104142794A TW 104142794 A TW104142794 A TW 104142794A TW 201723449 A TW201723449 A TW 201723449A
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- 238000004364 calculation method Methods 0.000 claims abstract description 9
- 230000006698 induction Effects 0.000 claims description 23
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims 2
- 229910052742 iron Inorganic materials 0.000 claims 1
- 230000008859 change Effects 0.000 description 8
- 238000004519 manufacturing process Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000007246 mechanism Effects 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 230000004907 flux Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 210000000078 claw Anatomy 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
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Classifications
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
- G01L3/02—Rotary-transmission dynamometers
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
- G01L3/02—Rotary-transmission dynamometers
- G01L3/04—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft
- G01L3/06—Rotary-transmission dynamometers wherein the torque-transmitting element comprises a torsionally-flexible shaft involving mechanical means for indicating
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L19/00—Details of, or accessories for, apparatus for measuring steady or quasi-steady pressure of a fluent medium insofar as such details or accessories are not special to particular types of pressure gauges
- G01L19/14—Housings
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Abstract
Description
本發明是有關於一種齒輪式扭力感測裝置,特別是指一種可線性放大扭桿轉角範圍的齒輪式扭力感測裝置。 The invention relates to a gear type torque sensing device, in particular to a gear type torque sensing device capable of linearly amplifying a torsion bar angle range.
參閱圖1,為了使駕駛人輕鬆操控車輛,因此在車輛轉向系統皆會具備動力輔助的功能,而現有市場上車輛大多配置電動馬達型式的動力輔助轉向系統91,依電動馬達安裝位置不同會產生不同型式的轉向系統,但皆統稱為電動輔助轉向系統(Electric Power Steering,EPS),其中扭力感測器92為電動輔助轉向系統中的一個關鍵組件。 Referring to Figure 1, in order to make the driver easily control the vehicle, the vehicle steering system will have the power assist function, and the existing vehicles on the market are mostly equipped with an electric motor type power assist steering system 91, which may be generated depending on the electric motor installation position. Different types of steering systems, but collectively referred to as Electric Power Steering (EPS), wherein the torque sensor 92 is a key component in the electric assisted steering system.
扭力感測器92的主要功能為感測駕駛者轉動方向盤93的轉向力矩,其實現方法為將感測器92架設在扭桿(圖未示)位置來感測扭桿的扭轉角度變化,進而輸出對應變化的訊號。 The main function of the torsion sensor 92 is to sense the steering torque of the driver turning the steering wheel 93. The method is implemented by locating the sensor 92 at a position of a torsion bar (not shown) to sense a change in the torsion angle of the torsion bar. Output a signal corresponding to the change.
目前市面上的扭力感測器,架構上大都以霍爾感應方式呈現,參閱圖2,為一種運用霍爾感應原理的扭力角度感測器,該扭力角度感測器具有一轉子95、二定子96及一霍爾元件97,該 轉子95固定在一內部具有扭桿的扭力傳遞裝置(圖未示)的一端,其外環上佈滿磁鐵,N-S極接連排列,該等定子96各具爪形,且固定在該扭力傳遞裝置的另一端,其材質具導磁性,該霍爾元件97固定在感測器殼上,可感應磁通的大小,該扭力傳遞裝置受扭力而使輸入軸桿相對輸出軸桿產生角度差,以致該轉子95及該等定子96產生相對位移,因而產生磁通變化,該霍爾元件97即可感測磁通量變化,以此判讀扭力值。 At present, the torsion sensor on the market is mostly represented by Hall induction. Referring to FIG. 2, it is a torsion angle sensor using the Hall induction principle. The torsion angle sensor has a rotor 95 and two stators 96. And a Hall element 97, the The rotor 95 is fixed to one end of a torsion transmitting device (not shown) having a torsion bar, the outer ring is covered with magnets, and the NS poles are arranged in series. The stators 96 each have a claw shape and are fixed to the torque transmitting device. The other end of the material is magnetically conductive. The Hall element 97 is fixed on the sensor shell to sense the magnitude of the magnetic flux. The torque transmitting device is subjected to a torsion force to cause an angular difference between the input shaft and the output shaft. The rotor 95 and the stators 96 are relatively displaced, thereby causing a change in magnetic flux, and the Hall element 97 can sense the change in the magnetic flux to thereby interpret the torque value.
雖然利用該霍爾元件97能夠根據該扭力傳遞裝置的輸入軸桿相對輸出軸桿的角度差而判讀扭力,然而,由於該扭力傳遞裝置的輸入軸桿相對輸出軸桿的角度差的角度變化非常微小,因此對於霍爾元件97及配合的零件的精密度要求非常高。 Although the Hall element 97 can be used to interpret the torque according to the angular difference of the input shaft of the torsion transmitting device with respect to the output shaft, the angular difference of the angular difference of the input shaft of the torque transmitting device with respect to the output shaft is very It is so small that the precision of the Hall element 97 and the mating parts is very high.
現有另一種扭力感測器,如專利號碼CN101825425B專利所示,是將兩組行星齒輪組的太陽輪分別由扭桿的兩相反端帶動後,分別連動至兩個齒數不同的感應齒輪,藉由量測該等感應齒輪各自的轉動角度變化以及自身齒輪比的差異,進而計算出該扭桿的扭轉角度,而可得知扭力的變化。 Another type of torsion sensor, as shown in the patent number CN101825425B, is that the sun gears of the two sets of planetary gear sets are respectively driven by opposite ends of the torsion bar, and then respectively linked to two induction gears with different numbers of teeth. The change of the rotation angle of each of the induction gears and the difference of the gear ratios thereof are measured, and the torsion angle of the torsion bar is calculated, and the change of the torsion force can be known.
然而,前述的扭力感測器應用了兩組的行星齒輪,不僅結構複雜,造成成本無法下降,且藉由該等感應齒輪各自的轉動角度變化以及自身齒輪比的差異的計算方式也相當複雜,導致使用上非常不便。 However, the aforementioned torsion sensor uses two sets of planetary gears, which are not only complicated in structure, but also can not reduce the cost, and the calculation method of the difference of the rotation angle of the induction gears and the difference of the gear ratios thereof is also quite complicated. It is very inconvenient to use.
因此,本發明之目的,即在提供一種方便使用並可使感測範圍線性放大以提高感測精度的齒輪式扭力感測裝置。 Accordingly, it is an object of the present invention to provide a gear type torque sensing device that is convenient to use and that can linearly amplify the sensing range to improve sensing accuracy.
於是,本發明齒輪式扭力感測裝置,應用於一扭力傳遞裝置,該扭力傳遞裝置包括一可轉動的輸入軸桿,及一可相對該輸入軸桿轉動的輸出軸桿,該扭力感測裝置包含一輸入軸齒輪、一輸出軸齒輪,及一行星齒輪單元。 Accordingly, the gear type torque sensing device of the present invention is applied to a torque transmitting device including a rotatable input shaft and an output shaft rotatable relative to the input shaft, the torque sensing device The utility model comprises an input shaft gear, an output shaft gear, and a planetary gear unit.
該輸入軸齒輪套設於該輸入軸桿,該輸出軸齒輪套設於該輸出軸桿,該行星齒輪單元包括一與該輸入軸齒輪相互嚙合的環齒輪、一位於該環齒輪內的太陽齒輪、一與該輸出軸齒輪相互嚙合的行星架齒輪,及複數可轉動地設置於該行星架齒輪且分別設置於該環齒輪及該太陽齒輪間並嚙合該環齒輪及該太陽齒輪的行星齒輪,該環齒輪具有一與該輸入軸齒輪嚙合的外環齒,及一與該等行星齒輪嚙合的內環齒,其中,當該輸入軸齒輪相對該輸出軸齒輪產生一相對轉動角度時,受連動的該太陽齒輪的轉動角度為該相對轉動角度的一預設倍數,且轉動方向為反向。 The input shaft gear is sleeved on the input shaft, the output shaft gear is sleeved on the output shaft, the planetary gear unit includes a ring gear meshing with the input shaft gear, and a sun gear located in the ring gear a carrier gear that meshes with the output shaft gear, and a plurality of planetary gears rotatably disposed on the carrier gear and respectively disposed between the ring gear and the sun gear and meshing the ring gear and the sun gear, The ring gear has an outer ring tooth that meshes with the input shaft gear, and an inner ring tooth that meshes with the planetary gears, wherein when the input shaft gear generates a relative rotation angle with respect to the output shaft gear, The rotation angle of the sun gear is a predetermined multiple of the relative rotation angle, and the rotation direction is reverse.
本發明之功效在於:藉由該行星齒輪單元的設置,以及該環齒輪的內環齒、該太陽齒輪、該行星架齒輪、該輸入軸齒輪及該輸出軸齒輪之間的齒數的匹配,能將該輸入軸桿及該輸出軸桿 之間的轉動角度經由該太陽齒輪進行放大,而使感測範圍線性放大,以提升感測精度,進而方便計算扭力。 The effect of the present invention is that, by the arrangement of the planetary gear unit, and the matching of the number of teeth between the inner ring gear of the ring gear, the sun gear, the carrier gear, the input shaft gear and the output shaft gear, The input shaft and the output shaft The angle of rotation between the two is amplified by the sun gear, and the sensing range is linearly amplified to improve the sensing accuracy, thereby facilitating the calculation of the torque.
200‧‧‧齒輪式扭力感測裝置 200‧‧‧Gear type torque sensing device
2‧‧‧輸入軸齒輪 2‧‧‧Input shaft gear
21‧‧‧第一安裝孔 21‧‧‧First mounting hole
22‧‧‧第一凸部 22‧‧‧First convex
3‧‧‧輸出軸齒輪 3‧‧‧ Output shaft gear
31‧‧‧第二安裝孔 31‧‧‧Second mounting hole
32‧‧‧第二凸部 32‧‧‧second convex
4‧‧‧行星齒輪單元 4‧‧‧ planetary gear unit
41‧‧‧環齒輪 41‧‧‧ring gear
411‧‧‧外環齒 411‧‧‧ outer ring teeth
412‧‧‧內環齒 412‧‧‧ Inner ring teeth
42‧‧‧太陽齒輪 42‧‧‧Sun Gear
43‧‧‧行星架齒輪 43‧‧‧ planet carrier gear
44‧‧‧行星齒輪 44‧‧‧ planetary gear
5‧‧‧轉角量測單元 5‧‧‧ Corner measuring unit
51‧‧‧第一磁鐵 51‧‧‧First magnet
52‧‧‧第一磁感應模組 52‧‧‧First magnetic induction module
6‧‧‧計算單元 6‧‧‧Computation unit
7‧‧‧角度量測單元 7‧‧‧ Angle measuring unit
71‧‧‧第一齒輪 71‧‧‧First gear
72‧‧‧第二齒輪 72‧‧‧second gear
73‧‧‧第二磁鐵 73‧‧‧Second magnet
74‧‧‧第三磁鐵 74‧‧‧ Third magnet
75‧‧‧第二磁感應模組 75‧‧‧Second magnetic induction module
76‧‧‧第三磁感應模組 76‧‧‧ Third magnetic induction module
8‧‧‧扭力傳遞裝置 8‧‧‧Torque transmission device
81‧‧‧輸入軸桿 81‧‧‧Input shaft
811‧‧‧第一桿體 811‧‧‧first body
812‧‧‧第一導槽 812‧‧‧First channel
82‧‧‧輸出軸桿 82‧‧‧ Output shaft
821‧‧‧第二桿體 821‧‧‧Second body
822‧‧‧第二導槽 822‧‧‧Second guiding channel
83‧‧‧可撓扭桿 83‧‧‧Flexible torsion bar
本發明之其他的特徵及功效,將於參照圖式的實施方式中清楚地呈現,其中:圖1是一示意圖,說明一現有的扭力感測器的設置位置;圖2是一運用霍爾感應原理的一扭力感測器的立體分解圖;圖3是本發明齒輪式扭力感測裝置的一實施例的示意圖;圖4是該實施例的一立體圖;圖5是該實施例的一立體分解圖;圖6是該實施例的一示意圖,說明各齒輪間的連接關係;圖7是該實施例的一剖視圖;及圖8是一示意圖,說明一第一齒輪及一第二齒輪的設置位置。 Other features and effects of the present invention will be apparent from the following description of the drawings, wherein: FIG. 1 is a schematic diagram showing a set position of a conventional torsion sensor; FIG. 2 is a Hall sensing 3 is an exploded perspective view of a torque sensor of the present invention; FIG. 3 is a perspective view of an embodiment of the gear type torque sensing device of the present invention; FIG. 4 is a perspective view of the embodiment; Figure 6 is a schematic view of the embodiment, illustrating the connection relationship between the gears; Figure 7 is a cross-sectional view of the embodiment; and Figure 8 is a schematic view showing the position of a first gear and a second gear .
參閱圖3、4、5,本發明齒輪式扭力感測裝置200之一實施例,是應用於一扭力傳遞裝置8,該扭力傳遞裝置8包括一可轉動的輸入軸桿81、一可相對該輸入軸桿81轉動的輸出軸桿82,及一連接於該輸入軸桿81及該輸出軸桿82間的可撓扭桿83,該輸入 軸桿81具有一第一桿體811,及二位於該第一桿體811的第一導槽812,該輸出軸桿82具有一第二桿體821,及二位於該第二桿體821的第二導槽822。 Referring to Figures 3, 4 and 5, an embodiment of the gear type torque sensing device 200 of the present invention is applied to a torque transmitting device 8, the torque transmitting device 8 including a rotatable input shaft 81, An output shaft 82 for inputting the rotation of the shaft 81, and a flexible torsion bar 83 connected between the input shaft 81 and the output shaft 82, the input The shaft 81 has a first rod body 811, and two first guiding grooves 812 of the first rod body 811. The output shaft rod 82 has a second rod body 821, and two of the second rod bodies 821. Second guiding groove 822.
該可撓扭桿83可視為扭力彈簧,其具有與扭力彈簧相同的物理特性,即扭力等於剛性及扭轉角度的乘積,該輸入軸桿81及該輸出軸桿82間具有一止擋機構(圖未示),該止擋機構限制該可撓扭桿83的轉動角度,一般運用設計在+/-5度間。 The flexible torsion bar 83 can be regarded as a torsion spring, which has the same physical characteristics as the torsion spring, that is, the torque is equal to the product of the rigidity and the torsion angle, and the input shaft 81 and the output shaft 82 have a stop mechanism (Fig. Not shown), the stop mechanism limits the angle of rotation of the flexible torsion bar 83, and is generally designed to be between +/- 5 degrees.
假如該輸出軸桿82不受負荷時,此時旋轉該輸入軸桿81,該可撓扭桿83不產生形變,該輸入軸桿81及該輸出軸桿82同步旋轉。 If the output shaft 82 is not under load, the input shaft 81 is rotated at this time, the flexible torsion bar 83 is not deformed, and the input shaft 81 and the output shaft 82 rotate synchronously.
當該輸出軸桿82受負荷時,此時旋轉該輸入軸桿81,該可撓扭桿83產生形變,該輸入軸桿81及該輸出軸桿82會依扭力之大小產生扭轉角度,並受限於該止擋機構,角度差在+/-5度間,扭力和扭轉角度之間關係呈線性比例。 When the output shaft 82 is under load, the input shaft 81 is rotated at this time, and the flexible torsion bar 83 is deformed. The input shaft 81 and the output shaft 82 are twisted according to the magnitude of the torque, and are subjected to the deformation. Limited to the stop mechanism, the angular difference is between +/- 5 degrees, and the relationship between the torque and the torsion angle is linear.
該齒輪式扭力感測裝置200包含一輸入軸齒輪2、一輸出軸齒輪3、一行星齒輪單元4、一轉角量測單元5、一計算單元6,及一角度量測單元7。 The gear type torque sensing device 200 includes an input shaft gear 2, an output shaft gear 3, a planetary gear unit 4, a corner measuring unit 5, a calculating unit 6, and an angle measuring unit 7.
該輸入軸齒輪2套設於該輸入軸桿81,且包括一供該第一桿體811穿設的第一安裝孔21,及二相鄰該第一安裝孔21且卡制於該等第一導槽812的第一凸部22。 The input shaft gear 2 is sleeved on the input shaft 81 and includes a first mounting hole 21 through which the first rod body 811 is bored, and two adjacent first mounting holes 21 are engaged in the first shaft A first convex portion 22 of a guide groove 812.
該輸出軸齒輪3套設於該輸出軸桿82,且包括一供該第二桿體821穿設的第二安裝孔31,及二卡制於該第二導槽822的第二凸部32。 The output shaft gear 3 is sleeved on the output shaft 82 and includes a second mounting hole 31 through which the second rod body 821 is inserted, and a second protrusion 32 that is inserted into the second guiding groove 822. .
參閱圖5、6、7,該行星齒輪單元4包括一與該輸入軸齒輪2相互嚙合的環齒輪41、一位於該環齒輪41內的太陽齒輪42、一與該輸出軸齒輪3相互嚙合的行星架齒輪43,及二可轉動地設置於該行星架齒輪43且分別設置於該環齒輪41及該太陽齒輪42間並嚙合該環齒輪41及該太陽齒輪42的行星齒輪44。 Referring to Figures 5, 6, and 7, the planetary gear unit 4 includes a ring gear 41 that meshes with the input shaft gear 2, a sun gear 42 located in the ring gear 41, and a meshing engagement with the output shaft gear 3. The carrier gears 43 and the two are rotatably disposed on the carrier gears 43 and are respectively disposed between the ring gear 41 and the sun gear 42 and mesh with the ring gear 41 and the planetary gears 44 of the sun gear 42.
該環齒輪41具有一與該輸入軸齒輪2嚙合的外環齒411,及一與該等行星齒輪44嚙合的內環齒412。 The ring gear 41 has an outer ring tooth 411 that meshes with the input shaft gear 2, and an inner ring tooth 412 that meshes with the planetary gears 44.
該環齒輪41的外環齒411的齒數與該輸入軸齒輪2的齒數相同,即滿足T(E)=T(I),其中,T(E)為該環齒輪41的外環齒411的齒數、T(I)為該輸入軸齒輪2的齒數。於本實施例中,該環齒輪41的外環齒411的齒數與該輸入軸齒輪2的齒數同為六十二齒。 The number of teeth of the outer ring gear 411 of the ring gear 41 is the same as the number of teeth of the input shaft gear 2, that is, T (E) = T (I) is satisfied, where T (E) is the outer ring tooth 411 of the ring gear 41 The number of teeth and T (I) are the number of teeth of the input shaft gear 2. In the present embodiment, the number of teeth of the outer ring gear 411 of the ring gear 41 is sixty-two teeth equal to the number of teeth of the input shaft gear 2.
該環齒輪41的內環齒412的齒數是該太陽齒輪42的齒數的一預設倍數,即滿足T(R)=T(S)×K,其中,T(R)為該環齒輪41的內環齒412的齒數、T(S)為該太陽齒輪42的齒數、K為該預設倍數。於本實施例中,該預設倍數為十五倍,該太陽齒輪42的齒數為六齒,該環齒輪41的內環齒412的齒數為九十齒。 The number of teeth of the inner ring gear 412 of the ring gear 41 is a predetermined multiple of the number of teeth of the sun gear 42, that is, T (R) = T (S) × K, where T (R) is the ring gear 41 The number of teeth of the inner ring teeth 412, T (S) is the number of teeth of the sun gear 42, and K is the predetermined multiple. In this embodiment, the preset multiple is fifteen times, the number of teeth of the sun gear 42 is six teeth, and the number of teeth of the inner ring teeth 412 of the ring gear 41 is ninety teeth.
該行星架齒輪43的齒是位於外周緣,且齒數乘以該預設倍數是等於該輸出軸齒輪3的齒數乘以該預設倍數後再加上該輸出軸齒輪3的齒數的和,即滿足T(P)×K=T(O)×(K+1),其中,T(P)為該行星架齒輪的齒數、T(O)為該輸出軸齒輪的齒數。於本實施例中,該行星架齒輪43的齒數為六十四齒,該輸出軸齒輪3的齒數為六十齒。 The teeth of the carrier gear 43 are located at the outer circumference, and the number of teeth multiplied by the predetermined multiple is equal to the sum of the number of teeth of the output shaft gear 3 multiplied by the predetermined multiple and the number of teeth of the output shaft gear 3, that is, T (P) × K = T (O) × (K + 1) is satisfied, where T (P) is the number of teeth of the carrier gear, and T (O) is the number of teeth of the output shaft gear. In the present embodiment, the number of teeth of the carrier gear 43 is sixty-four teeth, and the number of teeth of the output shaft gear 3 is sixty teeth.
該轉角量測單元5包括一設置於該太陽齒輪42的第一磁鐵51,及一對應該第一磁鐵51設置以量測該第一磁鐵51的轉動角度的第一磁感應模組52。 The corner measuring unit 5 includes a first magnet 51 disposed on the sun gear 42 and a pair of first magnetic induction modules 52 that are disposed on the first magnet 51 to measure the rotation angle of the first magnet 51.
該計算單元6電連接該轉角量測單元5,並根據該第一磁感應模組52量測的該第一磁鐵51的轉動角度計算該輸入軸桿81相對該輸出軸桿82的扭力。 The calculating unit 6 is electrically connected to the corner measuring unit 5, and calculates the torque of the input shaft 81 relative to the output shaft 82 according to the rotation angle of the first magnet 51 measured by the first magnetic sensing module 52.
參閱圖5、6、8,該角度量測單元7包括嚙合於該行星架齒輪43的一第一齒輪71及一第二齒輪72、分別設置於該第一齒輪71及該第二齒輪72的一第二磁鐵73及一第三磁鐵74、一電連接該計算單元6且對應該第二磁鐵73設置以量測該第二磁鐵73的轉動角度的第二磁感應模組75,及一電連接該計算單元6且對應該第三磁鐵74設置以量測該第三磁鐵74的轉動角度的第三磁感應模組76。 Referring to FIGS. 5, 6, and 8, the angle measuring unit 7 includes a first gear 71 and a second gear 72 that are engaged with the carrier gear 43 and are respectively disposed on the first gear 71 and the second gear 72. a second magnet 73 and a third magnet 74, a second magnetic sensor module 75 electrically connected to the computing unit 6 and corresponding to the second magnet 73 for measuring the rotation angle of the second magnet 73, and an electrical connection The calculating unit 6 and the third magnetic induction module 76 corresponding to the third magnet 74 for measuring the rotation angle of the third magnet 74.
該第一齒輪71的齒數與該第二齒輪72的齒數不相同。於本實施例中,該第一齒輪71的齒數為十九齒,該第二齒輪72的齒數為十七齒。 The number of teeth of the first gear 71 is different from the number of teeth of the second gear 72. In the embodiment, the number of teeth of the first gear 71 is nineteen teeth, and the number of teeth of the second gear 72 is seventeen teeth.
參閱圖5、6、7,該計算單元6根據該第二磁感應模組75及該第三磁感應模組76量測的該第二磁鐵73及該第三磁鐵74的轉動角度計算該扭力傳遞裝置8的轉動角度。 Referring to FIGS. 5 , 6 , and 7 , the calculating unit 6 calculates the torque transmitting device according to the rotation angles of the second magnet 73 and the third magnet 74 measured by the second magnetic sensing module 75 and the third magnetic sensing module 76 . The angle of rotation of 8.
參閱圖3、5、6,使用時,該扭力傳遞裝置8一般是用於車輛,該輸入軸桿81是連接於一方向盤(圖未示),該輸出軸桿82是連接於一方向機(圖未示),假如該輸出軸桿82未受到負載時,轉動該方向盤會使該輸入軸桿81及該輸出軸桿82同時轉動,此時該輸入軸桿81及該輸出軸桿82並不會產生相對轉動角度,而當該輸出軸桿82受到負載時,此時,該可撓扭桿83產生形變,該輸入軸桿81相對該輸出軸桿82產生相對轉動角度C,該相對轉動角度C即是該可撓扭桿83形變而產生的扭轉角度,根據扭力等於剛性及扭轉角度的乘積的物理特性,藉由量測該相對轉動角度C即可得知該可撓扭桿83所受到的扭力。 Referring to Figures 3, 5 and 6, in use, the torque transmitting device 8 is generally for a vehicle, the input shaft 81 is coupled to a steering wheel (not shown), and the output shaft 82 is coupled to a steering machine ( If the output shaft 82 is not subjected to a load, rotating the steering wheel causes the input shaft 81 and the output shaft 82 to rotate simultaneously. At this time, the input shaft 81 and the output shaft 82 are not A relative rotation angle is generated, and when the output shaft 82 is subjected to a load, the flexible torsion bar 83 is deformed at this time, and the input shaft 81 generates a relative rotation angle C with respect to the output shaft 82. The relative rotation angle is C is the torsion angle generated by the deformation of the flexible torsion bar 83. According to the physical property of the product of the torsion force equal to the stiffness and the torsion angle, the relative torsion bar C can be obtained by measuring the relative rotation angle C. Torque.
要說明的是,該輸入軸齒輪2套設於該輸入軸桿81時,是以該輸入軸齒輪2的等第一凸部22卡制於該輸入軸桿81的該等第一導槽812,而該輸出軸齒輪3套設於該輸出軸桿82時,是以該輸出軸齒輪3的該等第二凸部32卡制於該輸出軸桿82的該等第二 導槽822,因此在安裝上能夠非常方便地達到固定的效果,且由於該等第一凸部22及該等第二凸部32是簡單的凸出結構,因此在加工上也非常容易,而能減少製作成本。 It should be noted that when the input shaft gear 2 is sleeved on the input shaft 81, the first convex portion 22 of the input shaft gear 2 is engaged with the first guiding groove 812 of the input shaft 81. When the output shaft gear 3 is sleeved on the output shaft 82, the second protrusions 32 of the output shaft gear 3 are locked to the second of the output shaft 82. The guide groove 822 can be easily fixed to achieve a fixed effect on the mounting, and since the first convex portion 22 and the second convex portion 32 are simple protruding structures, it is also very easy to process. Can reduce production costs.
當該輸入軸桿81及該輸出軸桿82各自轉動時,會分別帶動該環齒輪41及該行星架齒輪43轉動,進而使該等行星齒輪44轉動,最後由該等行星齒輪44連動該太陽齒輪42轉動。 When the input shaft 81 and the output shaft 82 rotate, respectively, the ring gear 41 and the carrier gear 43 are respectively rotated to rotate the planetary gears 44, and finally the planetary gears 44 are linked by the sun. The gear 42 rotates.
根據行星齒輪的運動公式:ψ(S)=((T(R)/T(S))+1)ψ(P)-(T(R)/T(S))ψ(R) (1) According to the equation of motion of the planetary gear: ψ (S) = ((T (R) / T (S) ) +1) ψ (P) - (T (R) / T (S) ) ψ (R) (1)
其中T(S)為太陽齒輪42的齒數、T(R)為環齒輪41的內環齒412的齒數、ψ(S)為太陽齒輪42的轉動角度、ψ(P)為行星架齒輪43的轉動角度、ψ(R)為環齒輪41的轉動角度。 Where T (S) is the number of teeth of the sun gear 42, T (R) is the number of teeth of the inner ring gear 412 of the ring gear 41, ψ (S) is the angle of rotation of the sun gear 42, and ψ (P) is the carrier gear 43 The angle of rotation, ψ (R), is the angle of rotation of the ring gear 41.
假如該輸入軸桿81及該輸出軸桿82同時轉動且並無產生相對轉動角度時,此時該可撓扭桿83不會變形,由於該太陽齒輪42的齒數為六齒,該環齒輪41的內環齒412的齒數為九十齒,因此可以得到ψ(S)=16 ψ(P)-15 ψ(R) (2)的結果。 If the input shaft 81 and the output shaft 82 rotate simultaneously and there is no relative rotation angle, the flexible torsion bar 83 does not deform at this time. Since the number of teeth of the sun gear 42 is six teeth, the ring gear 41 The number of teeth of the inner ring teeth 412 is ninety teeth, so that ψ (S) = 16 ψ (P) -15 ψ (R) (2) can be obtained.
由於該行星架齒輪43的齒數為六十四齒,該輸出軸齒輪3的齒數為六十齒,因此根據轉動角度與齒數成反比的關係可以得出ψ(P)/ψ(R)=15/16 (3),帶入公式(2)可以得到ψ(S)=0的結果,即該太陽齒輪42不會轉動,此時該第一磁鐵51不轉動,該第 一磁感應模組52感應到該第一磁鐵51為不轉動,因此可以得知該輸入軸桿81及該輸出軸桿82之間並無扭力發生。 Since the number of teeth of the carrier gear 43 is sixty-four teeth, the number of teeth of the output shaft gear 3 is sixty teeth, so that the relationship between the rotation angle and the number of teeth can be obtained as ψ (P) / ψ (R) = 15 /16 (3), brought into the formula (2), the result of ψ (S) =0, that is, the sun gear 42 does not rotate, and the first magnet 51 does not rotate, the first magnetic induction module 52 senses Since the first magnet 51 does not rotate, it can be known that no torque is generated between the input shaft 81 and the output shaft 82.
而當該輸入軸桿81相對該輸出軸桿82產生該相對轉動角度C時,此時該可撓扭桿83產生變形,該輸入軸齒輪2相對該輸出軸齒輪3產生該相對轉動角度C,則可以得到ψ(S)=16 ψ(P)-15(ψ(R)+C) (4)的結果,進一步將公式(3)代入公式(4),則可以得到ψ(S)=-15C (5)的公式,也就是說,受連動的太陽齒輪42的轉動角度為十五倍的該相對轉動角度C,且轉動方向為反向,因此該輸入軸桿81及該輸出軸桿82之間的該相對轉動角度C就可被放大,此時該第一磁鐵51隨著該太陽齒輪42而轉動,該第一磁感應模組52感應到該第一磁鐵51的轉動角度後,即可經由該計算單元6計算該輸入軸桿81及該輸出軸桿82之間的扭力。於本實施例中,該太陽齒輪42可以轉動的範圍為+/-120度,也就是可容許的該相對轉動角度C為+/-8度,由於該可撓扭桿83的扭轉角度是被限制在+/-5度間,因此符合設計需求。 When the input shaft 81 generates the relative rotation angle C with respect to the output shaft 82, the flexible torsion bar 83 is deformed at this time, and the input shaft gear 2 generates the relative rotation angle C with respect to the output shaft gear 3. Then you can get the result of ψ (S) =16 ψ (P) -15(ψ (R) +C) (4). Further substituting the formula (3) into the formula (4), you can get ψ (S) =- The formula of 15C (5), that is, the relative rotation angle C of the linked sun gear 42 is fifteen times, and the rotation direction is reversed, so the input shaft 81 and the output shaft 82 The relative rotation angle C between the two magnets 51 can be enlarged, and the first magnet 51 rotates with the sun gear 42. After the first magnetic induction module 52 senses the rotation angle of the first magnet 51, The torque between the input shaft 81 and the output shaft 82 is calculated via the calculation unit 6. In this embodiment, the sun gear 42 can be rotated in a range of +/- 120 degrees, that is, the relative rotation angle C is +/- 8 degrees, because the torsion angle of the flexible torsion bar 83 is Limited to +/- 5 degrees, so meet the design needs.
另外,當該扭力傳遞裝置8轉動時,由於該行星架齒輪43轉動時會帶動該第一齒輪71及該第二齒輪72轉動,由於該第一齒輪71及該第二齒輪72的齒數不相同,因此分別受到連動的該第二磁鐵73及該第三磁鐵74的轉動角度會不相同,透過該第二磁感應模組75及該第三磁感應模組76分別量測該第二磁鐵73及該第三 磁鐵74的轉動角度後,該計算單元6即可根據該第二磁鐵73及該第三磁鐵74的轉動角度差及該第一齒輪71及該第二齒輪72的齒輪比計算出該扭力傳遞裝置8的轉動角度。 In addition, when the torsion transmitting device 8 rotates, the first gear 71 and the second gear 72 rotate when the carrier gear 43 rotates, because the number of teeth of the first gear 71 and the second gear 72 are different. Therefore, the rotation angles of the second magnets 73 and the third magnets 74 that are respectively linked are different, and the second magnets 73 and the third magnetic sensor modules 76 are respectively measured by the second magnetic sensor module 75 and the third magnetic sensor module 76. third After the rotation angle of the magnet 74, the calculating unit 6 can calculate the torque transmitting device according to the difference of the rotation angle of the second magnet 73 and the third magnet 74 and the gear ratio of the first gear 71 and the second gear 72. The angle of rotation of 8.
簡單來說,由於該第一齒輪71的齒數為十九齒,該第二齒輪72的齒數為十七齒,因此當該第一齒輪71轉動十七圈時,該第二齒輪72會轉動十九圈,此時該第一齒輪71與該第二齒輪72各自可轉回至原點重合的位置,因此藉由該第二磁鐵73及該第三磁鐵74的轉動角度差就能計算該扭力傳遞裝置8的轉動角度。 In short, since the number of teeth of the first gear 71 is nineteen teeth, the number of teeth of the second gear 72 is seventeen teeth, so when the first gear 71 rotates seventeen turns, the second gear 72 will rotate ten Nine laps, at this time, the first gear 71 and the second gear 72 can each be rotated back to the position where the origin coincides, so the torque can be calculated by the difference of the rotation angles of the second magnet 73 and the third magnet 74. The angle of rotation of the transfer device 8.
於本實施例中,由於該行星架齒輪43和該輸出軸齒輪3的齒數比是64/60,因此轉速比是60/64,即0.9375,設定該輸出軸齒輪3的轉動角度範圍至少為±800度,即總角度範圍至少為1600度,因此即可接著定義所欲量測該輸出軸齒輪3的最大轉動角度範圍在1900~3000度之間,故該行星架齒輪43的最大轉角範圍是在(1900×0.9375)~(3000×0.9375)度之間,即1781~2812度之間,進一步以轉動圈數表示,則為(1781/360)~(2812/360)圈之間,即4.9~7.8圈之間。 In this embodiment, since the gear ratio of the carrier gear 43 and the output shaft gear 3 is 64/60, the rotation ratio is 60/64, that is, 0.9375, and the rotation angle of the output shaft gear 3 is set to at least ± 800 degrees, that is, the total angle range is at least 1600 degrees, so that it can be defined that the maximum rotation angle of the output shaft gear 3 is between 1900 and 3000 degrees, so the maximum rotation angle of the carrier gear 43 is Between (1900 × 0.9375) ~ (3000 × 0.9375) degrees, that is, between 1781 ~ 2812 degrees, further expressed by the number of turns, then between (1781/360) ~ (2812/360) circle, that is, 4.9 ~ 7.8 laps.
因此,該第一齒輪71及該第二齒輪72的齒數的最小公倍數應在(4.9×64~7.8×64)之間,即314~499之間,以最小公倍數323為基準,即可得出該第一齒輪71的齒數為十九齒,該第二齒輪72的齒數為十七齒。 Therefore, the least common multiple of the number of teeth of the first gear 71 and the second gear 72 should be between (4.9×64 and 7.8×64), that is, between 314 and 499, based on the least common multiple 323. The number of teeth of the first gear 71 is nineteen teeth, and the number of teeth of the second gear 72 is seventeen teeth.
要說明的是,該輸入軸齒輪2及該環齒輪41的搭配,以及該輸出軸齒輪3及該行星架齒輪43的搭配,除了是以齒輪的方式配合之外,也可改為使用皮帶輪或鏈輪的方式進行配合,而同樣可獲得相類似的效果。 It should be noted that the combination of the input shaft gear 2 and the ring gear 41, and the combination of the output shaft gear 3 and the carrier gear 43 can be replaced by a pulley or by using a gear. The manner of the sprocket is matched, and similar effects can be obtained.
另外,每一對相互配合的齒輪的齒數除了是本案所揭露的數目外,也可以改以其他倍數的齒數相互配合。於本實施例中,所有的齒輪是以塑膠材質製成,但並不以此為限。 In addition, the number of teeth of each pair of cooperating gears can be matched with the number of teeth of other multiples in addition to the number disclosed in the present case. In this embodiment, all the gears are made of plastic material, but not limited thereto.
在實際應用上,本發明是可應用於各種電子輔助動力載具,例如電動腳踏車、電動輪椅等等。 In practical applications, the present invention is applicable to various electronically assisted power vehicles, such as electric bicycles, electric wheelchairs, and the like.
因此,本發明相較於現有的扭力感測器,具有以下優點: Therefore, the present invention has the following advantages over the existing torsion sensor:
一、本發明可以放大該相對轉動角度C,使能夠用以感測的角度線性放大十五倍,因此感測範圍線性擴大,而使感測精度大幅提升,因此相較於霍爾元件式的扭力感測器,本發明的精度更高。 1. The present invention can enlarge the relative rotation angle C so that the angle that can be sensed is linearly amplified by fifteen times, so that the sensing range is linearly expanded, and the sensing precision is greatly improved, so that compared with the Hall element type Torque sensors, the accuracy of the present invention is higher.
二、本發明是以機械結構的方式放大該相對轉動角度C,因此可以避免霍爾元件式的扭力感測器容易遭到外來電氣的干擾問題。 2. The present invention amplifies the relative rotation angle C in a mechanical manner, thereby avoiding the problem that the Hall element type torsion sensor is susceptible to external electrical interference.
三、霍爾元件式的扭力感測器由於是對原始的轉動角度進行量測,因此可量測角度非常小,故在機構組配以及霍爾元件 的精度上的要求較高,加上爪形定子的設計需要經過磁路分析及在製造上是屬於加工難度高的零件,且爪形定子還有生產組裝時容易變形的缺點,而本發明是以塑膠齒輪方式進行連動,由於齒輪的製作已是非常成熟的技術,因此生產設計上相對容易。 Third, the Hall element type torque sensor measures the original rotation angle, so the measurement angle is very small, so the mechanism assembly and the Hall element The accuracy requirement is high, and the design of the claw-shaped stator needs to be subjected to magnetic circuit analysis and manufacturing parts which are difficult to process, and the claw-shaped stator has the disadvantage of being easily deformed during production and assembly, and the present invention is Linking with plastic gears, because the production of gears is a very mature technology, production design is relatively easy.
四、相較於現有的另一種扭力感測器,除了利用兩組的行星齒輪而造成成本無法下降的缺點外,且兩個感應齒輪還必須再搭配兩個感測轉動角度變化的感測器來量測角度變化,並根據自身齒輪比的差異來計算轉動角度,計算方式相當複雜,而本發明僅使用了一組行星齒輪,且將該相對轉動角度C進行線性放大後會更便於量測轉動角度,因此結構更為簡便而能降低成本。 4. Compared with the existing torque sensor, in addition to the disadvantage that the cost of the two sets of planetary gears cannot be reduced, the two induction gears must be combined with two sensors that sense the change of the rotation angle. To measure the angle change and calculate the rotation angle according to the difference of the gear ratio, the calculation method is quite complicated, and the present invention only uses a set of planetary gears, and linearly amplifying the relative rotation angle C is more convenient to measure. The angle of rotation makes the structure simpler and reduces costs.
綜上所述,藉由該行星齒輪單元4的設置,以及該環齒輪41的內環齒412、該太陽齒輪42、該行星架齒輪43、該輸入軸齒輪2及該輸出軸齒輪3之間的齒數的匹配,能將該輸入軸桿81及該輸出軸桿82之間的該相對轉動角度C經由該太陽齒輪42進行放大,而方便計算扭力,相較於現有運用霍爾感應原理的扭力感測器,本發明可以放大該相對轉動角度C,因此可避免需要高精密度的霍爾元件及配合零件而所帶來的高成本問題,另外,再相較於現有的另一種扭力感測器,本發明僅使用了一組行星齒輪,且將該相對轉動角度C進行放大後會更便於量測轉動角度,因此結構更為簡便而能降低成本,且更容易計算扭力,故確實能達成本發明之目的。 In summary, the arrangement of the planetary gear unit 4, and the inner ring gear 412 of the ring gear 41, the sun gear 42, the carrier gear 43, the input shaft gear 2 and the output shaft gear 3 The matching of the number of teeth can enlarge the relative rotation angle C between the input shaft 81 and the output shaft 82 via the sun gear 42, thereby conveniently calculating the torque, compared with the existing torque using the Hall induction principle. The sensor can enlarge the relative rotation angle C, thereby avoiding the high cost problem caused by the high-precision Hall element and the matching component, and further comparing with another existing torque sensing In the present invention, only one set of planetary gears is used, and the relative rotation angle C is enlarged to make it easier to measure the rotation angle, so that the structure is simpler and the cost can be reduced, and the torque is more easily calculated, so that it can be achieved. The object of the invention.
惟以上所述者,僅為本發明之實施例而已,當不能以此限定本發明實施之範圍,凡是依本發明申請專利範圍及專利說明書內容所作之簡單的等效變化與修飾,皆仍屬本發明專利涵蓋之範圍內。 However, the above is only the embodiment of the present invention, and the scope of the invention is not limited thereto, and all the equivalent equivalent changes and modifications according to the scope of the patent application and the patent specification of the present invention are still The scope of the invention is covered.
200‧‧‧齒輪式扭力感測裝置 200‧‧‧Gear type torque sensing device
2‧‧‧輸入軸齒輪 2‧‧‧Input shaft gear
21‧‧‧第一安裝孔 21‧‧‧First mounting hole
22‧‧‧第一凸部 22‧‧‧First convex
3‧‧‧輸出軸齒輪 3‧‧‧ Output shaft gear
31‧‧‧第二安裝孔 31‧‧‧Second mounting hole
32‧‧‧第二凸部 32‧‧‧second convex
4‧‧‧行星齒輪單元 4‧‧‧ planetary gear unit
41‧‧‧環齒輪 41‧‧‧ring gear
42‧‧‧太陽齒輪 42‧‧‧Sun Gear
43‧‧‧行星架齒輪 43‧‧‧ planet carrier gear
44‧‧‧行星齒輪 44‧‧‧ planetary gear
5‧‧‧轉角量測單元 5‧‧‧ Corner measuring unit
51‧‧‧第一磁鐵 51‧‧‧First magnet
52‧‧‧第一磁感應模組 52‧‧‧First magnetic induction module
6‧‧‧計算單元 6‧‧‧Computation unit
7‧‧‧角度量測單元 7‧‧‧ Angle measuring unit
71‧‧‧第一齒輪 71‧‧‧First gear
72‧‧‧第二齒輪 72‧‧‧second gear
73‧‧‧第二磁鐵 73‧‧‧Second magnet
74‧‧‧第三磁鐵 74‧‧‧ Third magnet
75‧‧‧第二磁感應模組 75‧‧‧Second magnetic induction module
76‧‧‧第三磁感應模組 76‧‧‧ Third magnetic induction module
Claims (10)
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TW104142794A TWI579546B (en) | 2015-12-18 | 2015-12-18 | Gear type torque sensing device |
KR1020160171649A KR101932820B1 (en) | 2015-12-18 | 2016-12-15 | Torque detecting device |
DE102016225337.9A DE102016225337B4 (en) | 2015-12-18 | 2016-12-16 | Torque detection device |
JP2016244122A JP6280980B2 (en) | 2015-12-18 | 2016-12-16 | Torque detection device |
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FR1440883A (en) * | 1964-05-02 | 1966-06-03 | Zahnradfabrik Friedrichshafen | Transmission system |
CA1151903A (en) * | 1980-03-10 | 1983-08-16 | Frans P. Gillade | Power transmission |
JPS6283631A (en) * | 1985-10-09 | 1987-04-17 | Honda Motor Co Ltd | Torque sensor |
JP2580865B2 (en) * | 1990-10-17 | 1997-02-12 | 三菱自動車工業株式会社 | Vehicle steering control device |
JPH04358987A (en) * | 1991-06-04 | 1992-12-11 | Yamaha Motor Co Ltd | Motorbike |
DE19506938A1 (en) * | 1995-02-28 | 1996-08-29 | Bosch Gmbh Robert | Method and device for measuring the angle of a rotatable body |
JP2004020370A (en) * | 2002-06-17 | 2004-01-22 | Matsushita Electric Ind Co Ltd | Torque detection system |
DE102008008835B4 (en) | 2008-02-13 | 2010-04-22 | Zf Friedrichshafen Ag | Device for determining a torque |
DE102009011352B3 (en) * | 2009-03-05 | 2010-07-15 | Bourns, Inc., Riverside | Torsion angle sensor for measuring torsion angle of two shafts coupled with each other, has torsion bar, by which two shafts are connected with each other, housing and rotational position sensor |
JP2013096930A (en) * | 2011-11-04 | 2013-05-20 | Jtekt Corp | Rotation angle detection apparatus and torque sensor |
JP5923002B2 (en) * | 2012-07-09 | 2016-05-24 | アズビル株式会社 | Torque detector and electric actuator |
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