WO2022245143A1 - 링기어 없는 자동체결 기능을 갖는 감속장치 및 그 감속장치의 자동체결 방법 - Google Patents
링기어 없는 자동체결 기능을 갖는 감속장치 및 그 감속장치의 자동체결 방법 Download PDFInfo
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- WO2022245143A1 WO2022245143A1 PCT/KR2022/007159 KR2022007159W WO2022245143A1 WO 2022245143 A1 WO2022245143 A1 WO 2022245143A1 KR 2022007159 W KR2022007159 W KR 2022007159W WO 2022245143 A1 WO2022245143 A1 WO 2022245143A1
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- sun gear
- gear
- teeth
- carrier
- input
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- 238000000034 method Methods 0.000 title claims abstract description 15
- 239000003638 chemical reducing agent Substances 0.000 title abstract description 9
- 230000009467 reduction Effects 0.000 claims description 55
- 230000008859 change Effects 0.000 description 18
- 238000004519 manufacturing process Methods 0.000 description 17
- 230000000694 effects Effects 0.000 description 6
- 238000005516 engineering process Methods 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 238000004458 analytical method Methods 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 230000002265 prevention Effects 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
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- 230000004043 responsiveness Effects 0.000 description 1
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Classifications
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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
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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
- F16H1/36—Toothed gearings for conveying rotary motion with gears having orbital motion with two central gears coupled by intermeshing 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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
Definitions
- the present invention relates to a reduction device having an automatic fastening function without a ring gear and an automatic fastening method of the reduction device, and in particular, first, second, and third planetary gears are supported at different positions on one side of a carrier, which is an input side, to rotate. And it is configured to be able to revolve and is arranged in n sets, and when either the first sun gear or the second sun gear is fixed and the other sun gear is rotated by changing the input shaft, the self-locking function does not increase speed and the speed increase ratio is 0 (Zero ) (a sun gear used as an input is in a stop state in which the sun gear itself cannot rotate) and thus becomes inoperable.
- Zero a sun gear used as an input is in a stop state in which the sun gear itself cannot rotate
- the planetary gear reduction device has a structure in which a sun gear is installed on a central axis, a plurality of planetary gears that engage with the sun gear and orbit and rotate around it are arranged, and rotate by supporting the planetary gear with a carrier. It consists of a ring gear that meshes with the
- Patent Documents 1 to 3 One example of such technology is disclosed in Patent Documents 1 to 3 and the like.
- an internal gear is formed and a housing in which a planetary gear and a sun gear are sequentially geared in the direction of its axis, a drive shaft penetrated into the housing and coupled to the sun gear, and a planetary gear arranged in parallel with the internal gear It consists of an output shaft connected to a drive gear with a different dimension than the internal gear that is engaged with the gear, and even when a load is applied to the drive shaft, the internal gear and the tooth groove of the drive gear are engaged with the teeth of the planetary gear, so it is driven by the internal gear fixed to the housing.
- a reduction gear in which a gear is self-locked is disclosed.
- a sun gear installed on the rotating shaft of a motor, a plurality of planetary gears arranged around the sun gear to mesh with the sun gear, a carrier connected to the shaft of the planetary gears and rotating, and a carrier on the outside of the planetary gears
- An internal gear unit having a fixed internal gear spaced apart from each other at a predetermined interval and a rotational internal gear that rotates while being engaged with the planetary gear and the outside of the carrier, and provided in the fixed internal gear to supply and cut off power to the rotary internal gear unit.
- a reducer having a moving means for advancing and retracting a gear in the longitudinal direction of a rotating shaft.
- Patent Document 3 uses a Ravigneaux gear train in which a single pinion planetary gear is integrated with a double pinion planetary gear including a carrier in which two pinion gears are combined, two or more clutches, and the like, engine output Disclosed is a power transmission device for a hybrid vehicle that can improve fuel efficiency by implementing two or more types of engine fixed gear stages capable of distributing .
- Patent Document 1 when a high rate of deceleration or a low rate of deceleration or speed increase is required, it must be configured in multiple stages, and there is a problem that the number of teeth of the gears is restricted.
- Patent Document 2 the responsiveness during braking can be improved by amplifying and transmitting the rotational force of the motor, but there is a problem in that the number of teeth of the gears is limited, as in Patent Document 1.
- Patent Document 3 uses a Ravigneaux gear train in which a single pinion planetary gear and a double pinion planetary gear are integrated and two or more clutches are used, but there is a problem that high ratio deceleration cannot be performed.
- the simple planetary gear, double planetary gear, and Ravigneaux planetary gear method used in the prior art as described above do not have a high ratio reduction, and the reduction ratio that can be obtained in one layer is about 1/11 at most, and the high ratio When deceleration is required, there was a problem of using a two-layer (double) or more coupling method.
- the present invention as described above is a reduction device capable of realizing various gear ratios from high-rate deceleration to low-rate deceleration. Since the element of the ring gear is eliminated and consists of only external gears, difficulties in manufacturing are eliminated and space is reduced. On the other hand, the effect of reducing the manufacturing cost is obtained, and the effect of being suitable for mass production due to the ease of processing is obtained. In addition, it is to provide a reduction gear having an automatic locking function without a ring gear and an automatic fastening method of the reduction gear that can be easily controlled and used in various ways because the self-locking function prevents reversal.
- a carrier rotating by input, a first sun gear provided concentrically with the carrier, a first planet gear meshed with the first sun gear, a second planet gear meshed with the first planet gear, and a third planet gear meshed with the second planet gear , a second sun gear concentric with the carrier, provided in parallel to the first sun gear, and meshed with the third planetary gear;
- the number of teeth of the first sun gear and the number of teeth of the second sun gear are different by one or more, and the first, second, and third planetary gears are supported at different positions on one side of the carrier to enable rotation and revolution. is arranged in n sets,
- the carrier is an input, the first sun gear is fixed, and the second sun gear is an output, Z1 is defined as the number of teeth of the first sun gear, Z2 is defined as the number of teeth of the second sun gear,
- the self-locking function does not increase speed and the speed increase ratio becomes 0 (Zero) (the sun gear itself used as input cannot rotate) It is achieved by a reduction device having an automatic fastening function without a ring gear, characterized in that.
- Another structure of the present invention is a speed reduction device, a carrier rotating by input, a first sun gear provided concentrically with the carrier, a first planetary gear meshed with the first sun gear, and a second planetary gear meshed with the first planetary gear , a third planetary gear meshed with the second planetary gear, and a second sun gear concentric with the carrier, provided in parallel to the first sun gear, and meshed with the third planetary gear, wherein the number of teeth of the first sun gear and the first sun gear The number of teeth of the two sun gears is different by one or more, and the first, second, and third planetary gears are supported at different positions on one side of the carrier and configured to rotate and revolve, and are arranged in n sets.
- the carrier is an input, the second sun gear is fixed, the first sun gear is an output, Z1 is defined as the number of teeth of the first sun gear, and Z2 is defined as the number of teeth of the second sun gear;
- the self-locking function does not increase the speed and the speed increase ratio becomes 0 (Zero) (the sun gear itself used as an input is in a stopped state that cannot rotate) It is achieved by a reduction device having an automatic fastening function without a ring gear, characterized in that.
- the automatic fastening method of the reduction device includes a carrier rotating by input, a first sun gear provided concentrically with the carrier, a first planetary gear meshed with the first sun gear, and a second planetary gear meshed with the first planetary gear.
- the number of teeth of the second sun gear is different by one or more, and the first, second, and third planetary gears are supported at different positions on one side of the carrier to rotate and rotate, and are arranged in n sets.
- the carrier is an input
- the first sun gear is fixed
- the second sun gear is an output
- Z1 is defined as the number of teeth of the first sun gear
- Z2 is defined as the number of teeth of the second sun gear
- the self-locking function does not increase speed and the speed increase ratio becomes 0 (Zero) (the sun gear itself used as input cannot rotate) It is achieved by the automatic fastening method of the reduction gear, characterized in that.
- the automatic fastening method of the reduction device includes a carrier rotating by input, a first sun gear provided concentrically with the carrier, a first planetary gear meshed with the first sun gear, and a third gear meshed with the first planetary gear.
- the number of teeth of the second sun gear differs by one or more, and the first, second, and third planetary gears are supported at different positions on one side of the carrier to rotate and rotate, and are arranged in n sets.
- the carrier is an input, the second sun gear is fixed, the first sun gear is an output, Z1 is defined as the number of teeth of the first sun gear, and Z2 is defined as the number of teeth of the second sun gear;
- the self-locking function does not increase the speed and the speed increase ratio becomes 0 (Zero) (the sun gear itself used as an input is in a stopped state that cannot rotate) It is achieved by the automatic fastening method of the reduction device, characterized in that.
- the present invention is a reduction device capable of realizing various gear ratios from high-rate reduction to low-rate reduction, and since the element of the ring gear is eliminated and consists of only external gears, difficulties in manufacturing are eliminated and space is eliminated.
- it has the effect of reducing the production cost by reducing the number of times, and it has the effect of being suitable for mass production due to the ease of processing, and it is easy to control and can be used in various ways because the self-locking function prevents reversal. advantage is gained.
- FIG. 1 is a perspective view of a reduction gear having an automatic fastening function without a ring gear according to the present invention.
- Figure 2 is a perspective view showing the configuration of the number of n sets of planetary gears having a straight toothed portion according to an embodiment of the present invention.
- Figure 3a is a cross-sectional view showing a first type gear speed ratio and self-locking function according to an embodiment of the present invention.
- Figure 3b is a cross-sectional view taken along V-V according to Figure 3a.
- Figure 4a is a cross-sectional view showing a second type gear speed ratio and self-locking function according to an embodiment of the present invention.
- Fig. 4b is a cross-sectional view taken along line II according to Fig. 4a;
- FIG. 5 is an exemplary diagram showing rotation and revolution analysis in the present invention.
- Figure 6 is an exemplary diagram for interpreting the principle of the automatic fastening method, which is the technical subject matter of the present invention.
- FIG. 7 is a front view showing the arrangement of n planetary gears at regular intervals according to an embodiment of the present invention.
- Figure 8b is a front view showing the impossibility of gear teeth engagement before changing the engagement angle according to an embodiment of the present invention.
- Fig. 8c is a side view according to Fig. 8a;
- Fig. 8d is a cross-sectional view taken along line P-P according to Fig. 8c;
- Figure 8e is a cross-sectional view taken along the line W-W according to Figure 8c.
- Figure 8f is a front view showing the position of the intersection angle according to an embodiment of the present invention.
- 9A is an exemplary diagram for explaining a general leverage principle
- 9B is an exemplary diagram showing the operation of a general planetary gear set and a ring gear
- FIG. 1 is a perspective view of a reduction device having an automatic fastening function without a ring gear according to the present invention
- FIG. 2 is a perspective view showing the number configuration of n sets of planetary gears having a straight toothed portion according to an embodiment of the present invention.
- the reduction device according to the present invention is a reduction device realized from a high ratio to a low ratio without a ring gear, and as shown in FIGS. 1 and 2, a carrier 200 rotating by input and concentric with the carrier 200
- the number of teeth of the first sun gear 300 and the number of teeth of the second sun gear 400 are prepared to have a difference of one or more, and the first, second, and third planetary gears 500 on one side of the carrier 200 , 600, 700) are supported at different positions to be able to rotate and revolve and are arranged in n sets, and the tooth end circle of the second planetary gear 600 is the first sun gear 300 and the second sun gear It is provided separately from the end circle of (400).
- the first, second, and third planetary gears 500, 600, and 700 are provided in three sets, but are not limited thereto, and may be provided in two or four or more sets. have.
- the carrier 200 may function as an input, the first sun gear 300 may be fixed, and the second sun gear 400 may function as an output.
- the carrier 200 is an input, the second sun gear 400 is fixed, and the first sun gear 300 functions as an output.
- first and second sun gears 300 and 400 and the first, second and third planetary gears 500, 600 and 700 may be provided as the same module.
- the first and second sun gears 300 and 400 and the first, second and third planetary gears 500, 600 and 700 have involute teeth, It may be provided in the form of any one of a cycloidal tooth, a straight toothed portion, and a spiral toothed portion.
- FIG. 3A is a cross-sectional view showing a first type gear speed ratio and self-locking function according to an embodiment of the present invention
- FIG. 3B is a cross-sectional view taken along the line V-V shown in FIG. 3A
- 4a is a cross-sectional view showing a second type gear speed ratio and self-locking function according to an embodiment of the present invention
- FIG. 4b is a cross-sectional view taken along the line II shown in FIG. 4a.
- the reduction device includes a carrier 200, a first sun gear 300, a second sun gear 400, and a first planetary gear 500 ,
- the second planetary gear 600 and the third planetary gear 700 are included, and the carrier 200, the first sun gear 300, and the second sun gear 400 are at input, output, and fixed positions. Accordingly, it is divided into gear speed ratios of the first type 800 shown in FIG. 3 and the second type 900 shown in FIG. 4, and the number of teeth of the first sun gear 300 and the number of teeth of the second sun gear 400 Depending on the output, the direction and speed are different.
- the gear speed ratio of the first type 800 rotates when the carrier 200 connected to the input gear 190 rotates, the first planet supported by the carrier 200
- the second planetary gear 600 engaged while rotating and revolving around the first sun gear 300 fastened to the housing 101 to which the gear 500 is fixed with bolts 950 rotates, 2
- the planetary gear 600 rotates the meshed third planetary gear 700
- the third planetary gear 700 rotates the meshed second sun gear 400 to rotate the second sun gear 400.
- the shaft 103 rotates with the output.
- reference numeral 201 is a carrier rotation support.
- the gear speed ratio of the first type 800 shown in FIG. 3 is expressed as Equation (1-1) below.
- the number of teeth of the second sun gear (400) is greater than the number of teeth of the first sun gear (300), and the number of teeth (400) of the second sun gear is the first sun gear (300). If the value obtained by subtracting the number of teeth of is less than the number of teeth of the first sun gear 300, the output direction and speed are reduced in the same direction, and the number of teeth of the second sun gear 400 is equal to the number of teeth of the first sun gear 300. If the value obtained by subtracting the number of teeth of the second sun gear 400 from the number of teeth of the first sun gear 300 is less than the number of teeth of the second sun gear 400, the direction and output speed are decelerated in the opposite direction.
- Table 1 shows the high and low ratios of the first type according to an embodiment of the present invention.
- the '-' sign means that the output relative to the input rotation direction is reverse rotation.
- Table 1 even if the number of teeth of the gear is slightly changed, various gear ratios of high and low ratio reduction are obtained.
- the third planetary gear 700 meshed with the second sun gear 400 rotates, and the third planetary gear ( 700 rotates the meshed second planetary gear 600, the second planetary gear 600 rotates the meshed first planetary gear 500, and the first planetary gear 500 meshes with The first sun gear 300 is rotated.
- the sun gear when one of the first or second sun gear is changed to an input, the sun gear is in a stationary state in which rotation is not possible even if a rotation input is received.
- the first sun gear 300 of the present invention is fixed and the second sun gear 400 is input to rotate and rotate direction), as shown in FIG. 5, the third planetary gear 700 and the first planetary gear 500 rotate counterclockwise, and the counterclockwise rotation of the first planetary gear 500 By orbiting around the first sun gear 300, the supported carrier 200 also rotates counterclockwise.
- the carrier 200 is an input, the first sun gear 300 is fixed, and the second sun gear 400 is an output, and Z1 is the first 1 is defined as the number of teeth of the sun gear 300, and Z2 is defined as the number of teeth of the second sun gear 400, and if Z1 ⁇ Z2 and (Z2-Z1) ⁇ Z1, the output of the second sun gear is decelerated in the same direction Therefore, the clockwise rotation of the carrier 200 becomes the clockwise rotation of the second sun gear 400.
- the principle analysis of the self-locking of the present invention is that when the second sun gear 400 is fixed, as the first sun gear 300 rotates, the first planetary gear ( 500) is about to be rotated. Since the second sun gear 400 is fixed, the meshed point between the first planetary gear 500 and the second sun gear 400 becomes the instantaneous center of rotation A, and the direction of the tangential force of the first planetary gear 500 is the instantaneous center of rotation. There is a separation tangential force F1 rotating based on A and a rotating tangential force F2 meshed with the second planetary gear 600.
- Z1 is the number of teeth of the first sun gear 300
- Z2 is the number of teeth of the second sun gear 400
- Z5 is the number of teeth of the first planetary gear 500
- Z6 is the number of teeth of the second planetary gear 600
- the number of revolutions of the first planetary gear 500 is 1+(Z2/Z5), 4 revolutions,
- the number of rotations of the second planetary gear 600 is 1-(Z2/Z6) (-) 2 rotations,
- the number of revolutions of the third planetary gear 700 is 1+(Z2/Z7), 4 revolutions,
- the number of rotations of the first sun gear 300 is 1-(Z2/Z1), which is 1/10 rotation.
- the rotation of the first planetary gear 500 is increased to 40 rotations
- the rotation of the second planetary gear 600 is increased to (-) 20 rotations
- the rotation of the third planetary gear 700 is about to be increased to 40 rotations.
- the first planetary gear 500 does not rotate and stops, and the carrier 200 also cannot rotate because there is a deviation phenomenon in which the supporting point moves away from the center, so the self-locking function is achieved. will be.
- the third planetary gear 700 supported by the carrier 200 is fixed. While rotating and revolving around the second sun gear 400 fastened to the housing cover 102 with bolts 950, the second planetary gear 600 engaged is rotated, and the second planetary gear 600 rotates the meshed first planetary gear 500, and the first planetary gear 500 rotates the meshed first sun gear 300 to rotate the shaft 103 together with the first sun gear 300 This output will rotate.
- the gear speed ratio of the second type 900 is expressed as Equation (1-2) below.
- the number of teeth of the first sun gear 300 is greater than the number of teeth of the second sun gear 400, and the number of teeth of the first sun gear 300 is the second sun gear 400. If the value obtained by subtracting the number of teeth of is less than the number of teeth of the second sun gear 400, the output direction and speed are reduced in the same direction, and the number of teeth of the second sun gear 400 is equal to the number of teeth of the first sun gear 300. If the value obtained by subtracting the number of teeth of the first sun gear 300 from the number of teeth of the second sun gear 400 is less than the number of teeth of the first sun gear 300, the direction and speed of the output represent the decelerated contents in the reverse direction. In short,
- the output of the first sun gear 300 outputs a low-ratio reduction ratio that rotates one rotation, and (-) means the reverse direction, so the direction and speed are decelerated in the reverse direction. .
- Table 2 shows examples of high and low ratios of the second type according to an embodiment of the present invention.
- Example 6 Z1 100 51 Z2 99 100 gear ratio R2 100 -1.0408 result co-direction deceleration reverse deceleration compare high rate low rate
- the first sun gear 300 when the first sun gear 300 is rotated by input, the first planetary gear 500 meshed with the first sun gear 300 rotates, and the first planetary gear 500 meshes with the first planetary gear 500.
- the second planetary gear 600 rotates, the second planetary gear 600 rotates the meshed third planetary gear 700, and the third planetary gear 700 meshes with the second sun gear ( 400) rotate.
- the third planetary gear 700 tries to get out of engagement with the second sun gear 400 and is supported by the carrier 200.
- the phenomenon of wanting to break away from occurs.
- this phenomenon is caused by the fact that the third planetary gear 700 cannot escape from the supporting point of the carrier 200 and cannot escape from meshing with the second sun gear 400, so the fixed second sun gear 400 rotation is stopped at , and rotation of the first sun gear 300 by input is not realized, and the speed increase ratio is 0 (Zero) in a state where the stopped rotation 0 (Zero) cannot be increased (the sun gear itself used as an input rotates) It becomes a self-locking function of reverse prevention, which is an impossible stop state).
- the sun gear when one of the first or second sun gear is changed to an input, the sun gear is in a stationary state in which rotation is not possible even if a rotation input is received.
- the above-described gears 300, 400, 500, 600, and 700 can adjust the center distances, so that both standard gears and forward gears can be manufactured without any constraints, and they are composed of only external gears. It represents something that anyone skilled in the art can easily manufacture. That is, the number of teeth of each of the gears is selected to manufacture the gears, and the number of sets of the first, second, and third planetary gears 500, 600, and 700 to be arranged at equal intervals can be selected. .
- the gear speed ratio is determined according to the number of teeth of the first sun gear 300 and the number of teeth of the second sun gear 400, and there is a correlation with the number of sets of planetary gears arranged at equal intervals. If the value obtained by subtracting the number of teeth of the second sun gear 400 from the number of teeth of the first sun gear 300 is designated as a multiple of the number n of planetary gear sets, the number of teeth of the first sun gear 300 and the number of teeth of the second sun gear 400 The number of teeth of can be determined as shown in Equation (1-3) below.
- the number of teeth Z1 of the first sun gear 300 is set to an arbitrary value, and the number of planetary gears
- the number of teeth Z2 of the second sun gear 400 is determined by Equation (1-3), and the first, second,
- the number of teeth of the third planetary gears 500, 600, and 700 may be freely selected so as not to overlap between sets.
- n 3
- n 3
- -6, -9, and -12 negative multiples.
- 7 is a front view illustrating an arrangement of n planetary gears set at equal intervals according to an embodiment of the present invention.
- the number of teeth of the second sun gear 400 is selected based on a positive multiple, there are 53, 56, 59, 62, etc., and when selected based on a negative multiple, there are 47, 44, 41, 38, etc. .
- the number of teeth suitable for the approximate value of the target gear ratio can be selected.
- the number of teeth of the second sun gear 400 was selected to be 41, and the number of teeth of the first, second, and third planetary gears 500, 600, and 700 of the first set were 15, respectively.
- 15, 21 were randomly selected, and the number of teeth of the first, second, and third planetary gears 500, 600, and 700 of the second set was similar to that of the planetary gears 500, 600, and 700 of the first set. Since they must be the same, 15, 15, and 21 are selected, respectively, and the number of teeth of the first, second, and third planetary gears 500, 600, and 700 of the third set is also set to 15, 15, and 21, respectively.
- the number of teeth of the planetary gears is 12, 13 14, 15,... 20, 21, . . .
- the positive multiples of the set number 5 are equal to 5, 10, 15, etc., and the negative multiples are -5, -10, -15 according to the above equation (1-3).
- the number of teeth of the first sun gear 300 is selected by applying a positive multiple, 56, 61, 66, ... 46, 41, 36, . . . etc., and select the number of teeth that fits the approximate value of the target gear ratio.
- the number of teeth of the planetary gear may be freely selected as described above.
- FIG. 8A is a front view showing the arrangement of n planetary gear sets after changing the engagement angle according to an embodiment of the present invention
- FIG. 8B is a front view showing the impossibility of gear teeth engagement before changing the engagement angle according to an embodiment of the present invention
- FIG. 8C is a side view of the side according to Figure 8a
- Figure 8d is a cross-sectional view taken along P-P according to Figure 8c
- Figure 8e is a cross-sectional view taken along W-W according to Figure 8c
- Figure 8f is this It is a front view showing the position of the sandwich angle according to the embodiment of the present invention.
- A represents a normal position of gear teeth engagement
- B represents a position where gear teeth cannot be engaged
- C represents a position where gear teeth cannot be engaged.
- the number of sets of planetary gears should be 1 according to Equation (1-3). As shown in FIG. 8B, if three sets are arranged at equal intervals, only the A position of the first set has no problem in meshing of the gear teeth, and the B position of the second set and the C position of the third set have no gear teeth meshing. It is impossible to assemble, resulting in problems that cannot be assembled.
- gear speed ratio is maximum when the number of teeth of the sun gear differs by one, if only one planetary gear set is arranged, there will be no problem at low speed, but excessive vibration occurs when rotating at high speed Poor durability can lead to problems.
- the condition of Equation (1-3) and The description includes determining the number n of irrelevant planetary gear sets.
- 'change in angle' is an angle between the straight lines connecting the centers of the gears at the first, second, or third set position in the carrier 200.
- A01 is the angle between the straight line connecting the center of the third planet gear at the first set position to the center of the carrier and the straight line connecting the center of the first planet gear to the center of the carrier
- A02 is the angle between the first set The angle between the straight line connecting the center of the carrier at the position to the center of the first planetary gear and the straight line connecting the center of the first planetary gear to the center of the carrier
- A03 is the angle between the center of the first planetary gear at the first set position and the second The angle between the straight line connected to the center of the planetary gear and the straight line connected from the center of the third planetary gear to the center of the second planetary gear
- A04 is the angle between the straight line connected from the center of the carrier at the first set position to the center of the third planetary gear
- It represents the angle between the straight lines connecting the center of the second planetary gear to the center of the third planetary gear.
- B01 is the angle between the straight line connecting the center of the third planet gear at the second set position to the center of the carrier and the straight line connecting the center of the first planet gear to the center of the carrier
- B02 is the angle between the second set position
- B03 is the angle between the center of the first planetary gear at the second set position and the center of the second planetary gear It is the angle between the straight line connected to the center and the straight line connected from the center of the third planetary gear to the center of the second planetary gear
- B04 is the angle between the straight line connected from the center of the carrier at the second set position to the center of the third planetary gear and the second planetary gear. It represents the angle between the straight lines connecting the center of the planetary gear to the center of the third planetary gear.
- C01 is an angle between a straight line connecting the center of the third planetary gear at the third set position to the center of the carrier and a straight line connecting the center of the first planetary gear to the center of the carrier
- C02 is the angle between the third set position
- C03 is the angle between the center of the first planetary gear at the third set position and the center of the second planetary gear
- C04 is the angle between the straight line connected from the center of the carrier at the third set position to the center of the third planet gear and It represents the angle between the straight lines connecting the center of the planetary gear to the center of the third planetary gear.
- the problem of impossible gear teeth engagement can be solved by changing one of the four angles in the set where gear teeth cannot be engaged. Also, the number of planetary gear sets can be increased or decreased regardless of the number of teeth of the first sun gear 300 and the second sun gear 400 in Equation (1-3).
- the B part of the second set position is the second set position in FIG. 8F. It is only necessary to change one of the angles between B01 or B02 or B03 or B04 of the position, and in FIG. 8B, part C of the third set position is one of the angles of C01 or C02 or C03 or C04 of the third set position in FIG. 8F. just make a change
- the center of the second planetary gear 600 at the third set position supported by the carrier 200 is the center of the carrier 200.
- a straight line connecting from the center of the first planet gear 500 to the center of the second planet gear 600 and the second planet gear ( 600) the second planetary gear 600 rotates around the first planetary gear 500, and the meshed third planetary gear ( 700) is also rotated to rotate and move as much as the thickness of the tooth, which was impossible to engage the gear teeth, so that the teeth are meshed according to the tooth space of the opposing gear.
- the values of 97 degrees before the interception angle change, 98.6 degrees and 95.4 degrees after the interception angle change are not limited to the values of the embodiments, and the number of teeth of the sun gears and the number of planetary gear sets increase or decrease, the planetary Since it is a value that varies according to a change in the position of gears, it is not limited to the embodiment.
- the technology of the present invention is a reduction device with a self-locking function that can be realized from a high ratio to a low ratio without a ring gear.
- a carrier rotating by input, a first sun gear provided concentrically with the carrier, A first planetary gear meshed with a sun gear, a second planetary gear meshed with the first planetary gear, a third planetary gear meshed with the second planetary gear, concentric with the carrier and provided in parallel to the first sun gear, the third planetary gear A second sun gear meshed with a gear, wherein the number of teeth of the first sun gear and the number of teeth of the second sun gear are different by one or more, and the first, second, and third planetary gears are provided on one side of the carrier to be different from each other.
- the carrier is an input
- the first sun gear is fixed
- the second sun gear is an output
- Z1 is defined as the number of teeth of the first sun gear
- Z2 is the number of teeth of the second sun gear.
- the self-locking function does not increase the speed and the speed increase ratio becomes 0 (Zero).
- the carrier is an input
- the second sun gear is fixed
- the first sun gear is an output
- Z1 is defined as the number of teeth of the first sun gear
- Z2 is defined as the number of teeth of the second sun gear
- the speed reducer of the structure in which the speed reduction of the present invention is performed if the output side is changed to the input side and used, the self-locking function does not increase the speed, so the speed increase ratio becomes 0 (Zero), that is, it becomes an inoperable device.
- the present invention is a reduction device capable of realizing various gear ratios from high-rate reduction to low-rate reduction, and since the element of the ring gear is eliminated and consists of only external gears, difficulties in manufacturing are eliminated and space is eliminated.
- the effect of reducing the manufacturing cost is obtained by reducing the manufacturing cost, and the effect of being suitable for mass production due to the ease of processing is obtained.
- the self-locking function prevents reversal, it is easy to control and can be used in various ways.
- the present invention has as a basic technical idea to provide a self-locking speed reduction device that can be realized from a high ratio to a low ratio without a ring gear.
- a self-locking speed reduction device that can be realized from a high ratio to a low ratio without a ring gear.
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Abstract
Description
도 8f는 본 발명의 실시 예에 따른사잇각의 위치를 도시한 정면도. 도 9a는 일반적인 지렛대 원리를 설명하기 위한 예시도. 도 9b는 일반적인 유성기어세트와 링기어의 작동을 보여주는 예시도.
제1 형식 | 예 1 | 예 2 |
Z1 | 49 | 50 |
Z2 | 50 | 26 |
기어속비 R1 | 50 | -1.08333 |
결과 | 동방향 감속 | 역방향 감속 |
비고 | 고비율 | 저비율 |
일반 유성기어 세트의 자전 및 공전 회전의 지렛대 원리는 도 9a과 같다.
상기 도 9a에서 F는 힘, W는 작용점, A는 받침점이며, r1과 r2는 거리다. 3가지 지렛대 원리의 관계식은 W x r1 = F x r2 이다.
여기서 일반 유성기어세트의 캐리어 회전은 아래 도 9b와 같다.
도 9b의 일반유성기어세트에서 링기어는 고정시키고 선기어를 시계방향으로 회전시키면, 도 9b의 F지점은 오른쪽으로 이동하게 되며 , F지점의 이동은 유성기어를 자전(반시계방향)시킴과 동시에 링기어의 둘레와동심으로 시계방향으로 공전되면서 감속된다.
상기 유성기어의 공전은 도 9b와 같이 유성기어에 지지되어 있는 캐리어가 회전하게 되는 것이며,상기 유성기어의 공전 회전은 제 2종지렛대 원리에서 찾을수 있으며, 도 9b에서 유성기어의 순간회전중심은 A점으로, 이는 제 2종 지렛대에서 받침점 A와 같으며, 도 9b에서 유성기어의 F점은 제 2종지렛대에서 힘점 F와 같고, 도 9b에서 유성기어의 W점은 제 2종 지렛대에서 작용점 W와 같은 것이다.
제2 형식 | 예 5 | 예 6 |
Z1 | 100 | 51 |
Z2 | 99 | 100 |
기어속비 R2 | 100 | -1.0408 |
결과 | 동방향 감속 | 역방향 감속 |
비교 | 고비율 | 저비율 |
Claims (4)
- 감속장치의 자동체결 방법에 있어서,입력으로 회전하는 캐리어, 상기 캐리어와 동심으로 마련된 제1 선기어, 상기 제1 선기어와 맞물린 제1 유성기어, 상기 제1 유성기어와 맞물린 제2 유성기어, 상기 제2 유성기어와 맞물린 제3 유성기어, 상기 캐리어와 동심이며 상기 제1 선기어에 병렬로 마련되고 상기 제3 유성기어와 맞물린 제2 선기어를 포함하고,상기 제1 선기어의 잇수와 상기 제2 선기어의 잇수는 1개 이상 차이가 나며, 상기 캐리어의 일측에 상기 제1, 제2, 제3 유성기어가 서로 다른 위치에 지지되어 자전 및 공전 가능하게 구성되어 n개 세트로 배치되고,상기 캐리어는 입력이고, 상기 제1 선기어는 고정이고, 상기 제2 선기어는 출력으로 하고 Z1을 상기 제1 선기어의 잇수로 정의하고, Z2를 상기 제2 선기어의 잇수로 정의하며,Z1 < Z2이고 (Z2-Z1) < Z1이면 상기 제2 선기어의 출력은 동방향 감속Z1 > Z2이고 (Z1-Z2) < Z2이면 상기 제2 선기어의 출력은 역방향 감속이 되며,상기 감속이 실행되는 조건 중 하나만 만족하면서 제2 선기어를 입력으로 바꾸어 회전시키면 Self-locking 기능으로 증속이 되지 않고 증속비가 0(Zero)(입력으로 사용되는 선기어 자체가 회전할 수 없는 정지 상태)이 되는 것을 특징으로 하는 링기어 없는 감속장치의 자동체결 방법.
- 감속장치의 자동체결 방법에 있어서,입력으로 회전하는 캐리어, 상기 캐리어와 동심으로 마련된 제1 선기어, 상기 제1 선기어와 맞물린 제1 유성기어, 상기 제1 유성기어와 맞물린 제2 유성기어, 상기 제2 유성기어와 맞물린 제3 유성기어, 상기 캐리어와 동심이며 상기 제1 선기어에 병렬로 마련되고 상기 제3 유성기어와 맞물린 제2 선기어를 포함하고,상기 제1 선기어의 잇수와 상기 제2 선기어의 잇수는 1개 이상 차이가 나며, 상기 캐리어의 일측에 상기 제1, 제2, 제3 유성기어가 서로 다른 위치에 지지되어 자전 및 공전 가능하게 구성되어 n개 세트로 배치되고,상기 캐리어가 입력이고, 상기 제2 선기어가 고정이고, 상기 제1 선기어를 출력으로 하고 Z1을 상기 제1 선기어의 잇수로 정의하고, Z2를 상기 제2 선기어의 잇수로 정의하며,Z1 > Z2이고 (Z1-Z2) < Z2이면, 상기 제1 선기어의 출력은 동방향의 감속,Z1 < Z2이고 (Z2-Z1) < Z1이면, 상기 제1 선기어의 출력은 역방향 감속이 되며,상기 감속이 실행되는 조건 중 하나만 만족하면서 제1 선기어를 입력으로 바꾸어 회전시키면 Self-locking 기능으로 증속되지 않고 증속비가 0(Zero)(입력으로 사용되는 선기어 자체가 회전할 수 없는 정지 상태)이 되는 것을 특징으로 하는 링기어 없는 감속장치의 자동체결 방법.
- 감속장치에 있어서,입력으로 회전하는 캐리어, 상기 캐리어와 동심으로 마련된 제1 선기어, 상기 제1 선기어와 맞물린 제1 유성기어, 상기 제1 유성기어와 맞물린 제2 유성기어, 상기 제2 유성기어와 맞물린 제3 유성기어, 상기 캐리어와 동심이며 상기 제1 선기어에 병렬로 마련되고 상기 제3 유성기어와 맞물린 제2 선기어를 포함하고,상기 제1 선기어의 잇수와 상기 제2 선기어의 잇수는 1개 이상 차이가 나며, 상기 캐리어의 일측에 상기 제1, 제2, 제3 유성기어가 서로 다른 위치에 지지되어 자전 및 공전 가능하게 구성되어 n개 세트로 배치되고,상기 캐리어는 입력이고, 상기 제1 선기어는 고정이고, 상기 제2 선기어는 출력으로 하고 Z1을 상기 제1 선기어의 잇수로 정의하고, Z2를 상기 제2 선기어의 잇수로 정의하며,Z1 < Z2이고 (Z2-Z1) < Z1이면 상기 제2 선기어의 출력은 동방향 감속Z1 > Z2이고 (Z1-Z2) < Z2이면 상기 제2 선기어의 출력은 역방향 감속이 되며,상기 감속이 실행되는 조건 중 하나만 만족하면서 제2 선기어를 입력으로 바꾸어 회전시키면 Self-locking 기능으로 증속이 되지 않고 증속비가 0(Zero)(입력으로 사용되는 선기어 자체가 회전할 수 없는 정지 상태)이 되는 것을 특징으로 하는 링기어 없는 자동체결 기능을 갖는 감속장치.
- 감속장치에 있어서,입력으로 회전하는 캐리어, 상기 캐리어와 동심으로 마련된 제1 선기어, 상기 제1 선기어와 맞물린 제1 유성기어, 상기 제1 유성기어와 맞물린 제2 유성기어, 상기 제2 유성기어와 맞물린 제3 유성기어, 상기 캐리어와 동심이며 상기 제1 선기어에 병렬로 마련되고 상기 제3 유성기어와 맞물린 제2 선기어를 포함하고,상기 제1 선기어의 잇수와 상기 제2 선기어의 잇수는 1개 이상 차이가 나며, 상기 캐리어의 일측에 상기 제1, 제2, 제3 유성기어가 서로 다른 위치에 지지되어 자전 및 공전 가능하게 구성되어 n개 세트로 배치되고,상기 캐리어가 입력이고, 상기 제2 선기어가 고정이고, 상기 제1 선기어를 출력으로 하고 Z1을 상기 제1 선기어의 잇수로 정의하고, Z2를 상기 제2 선기어의 잇수로 정의하며,Z1 > Z2이고 (Z1-Z2) < Z2이면, 상기 제1 선기어의 출력은 동방향의 감속,Z1 < Z2이고 (Z2-Z1) < Z1이면, 상기 제1 선기어의 출력은 역방향 감속이 되며,상기 감속이 실행되는 조건 중 하나만 만족하면서 제1 선기어를 입력으로 바꾸어 회전시키면 Self-locking 기능으로 증속되지 않고 증속비가 0(Zero)(입력으로 사용되는 선기어 자체가 회전할 수 없는 정지 상태)이 되는 것을 특징으로 하는 링기어 없는 자동체결 기능을 갖는 감속장치.
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GB2317665.4A GB2621086A (en) | 2021-05-20 | 2022-05-19 | Speed reducer having self-locking function without ring gear, and self-locking method of speed reducer |
JP2023569798A JP2024519762A (ja) | 2021-05-20 | 2022-05-19 | リング歯車のないセルフロック機能を有する減速装置及びその減速装置のセルフロック方法 |
CN202280035239.5A CN117321317A (zh) | 2021-05-20 | 2022-05-19 | 无环形齿轮的具有自锁功能的减速装置以及所述减速装置的自锁方法 |
EP22804996.1A EP4343170A1 (en) | 2021-05-20 | 2022-05-19 | Speed reducer having self-locking function without ring gear, and self-locking method of speed reducer |
US18/471,045 US20240011541A1 (en) | 2021-05-20 | 2023-09-20 | Speed reducer having self-locking function without ring gear, and self-locking method of speed reducer |
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KR1020210064515A KR102400973B1 (ko) | 2021-05-20 | 2021-05-20 | 링기어 없는 자동체결 기능을 갖는 감속장치 |
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JP2010060095A (ja) * | 2008-09-05 | 2010-03-18 | Hiroshi Mizuno | 遊星歯車減速装置 |
JP6004876B2 (ja) * | 2012-10-03 | 2016-10-12 | 三菱重工業株式会社 | 舵取機及びこれを備えた船舶 |
JP2018506003A (ja) * | 2015-02-03 | 2018-03-01 | 志林 王 | 噛合して押動しながら回動する方式を利用するギアレバー装置 |
JP2020008062A (ja) * | 2018-07-06 | 2020-01-16 | 株式会社広島精機 | 不思議遊星歯車減速機構 |
US10794460B2 (en) * | 2017-06-21 | 2020-10-06 | Jtekt Corporation | Differential device |
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JPS604876Y2 (ja) * | 1981-10-26 | 1985-02-13 | 三菱重工業株式会社 | ウインドデフレクタ装置 |
KR100505017B1 (ko) | 2003-08-07 | 2005-08-05 | 김승문 | 큰 감속비를 가지는 감속장치 |
KR101270459B1 (ko) | 2011-07-12 | 2013-06-04 | 주식회사 만도 | 변속 가능한 감속기 및 이를 구비하는 전자식 주차 브레이크 |
KR101491251B1 (ko) | 2013-05-22 | 2015-02-11 | 현대자동차주식회사 | 하이브리드 차량용 동력전달장치 |
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JP2010060095A (ja) * | 2008-09-05 | 2010-03-18 | Hiroshi Mizuno | 遊星歯車減速装置 |
JP6004876B2 (ja) * | 2012-10-03 | 2016-10-12 | 三菱重工業株式会社 | 舵取機及びこれを備えた船舶 |
JP2018506003A (ja) * | 2015-02-03 | 2018-03-01 | 志林 王 | 噛合して押動しながら回動する方式を利用するギアレバー装置 |
US10794460B2 (en) * | 2017-06-21 | 2020-10-06 | Jtekt Corporation | Differential device |
JP2020008062A (ja) * | 2018-07-06 | 2020-01-16 | 株式会社広島精機 | 不思議遊星歯車減速機構 |
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US20240011541A1 (en) | 2024-01-11 |
KR102400973B1 (ko) | 2022-05-20 |
GB2621086A (en) | 2024-01-31 |
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