CN209977163U - Large-torque-diameter gear needle roller speed reducer - Google Patents
Large-torque-diameter gear needle roller speed reducer Download PDFInfo
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- CN209977163U CN209977163U CN201920801049.5U CN201920801049U CN209977163U CN 209977163 U CN209977163 U CN 209977163U CN 201920801049 U CN201920801049 U CN 201920801049U CN 209977163 U CN209977163 U CN 209977163U
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Abstract
The utility model provides a big moment of torsion footpath gear kingpin speed reducer, including the casing, input shaft, footpath gear, kingpin apical wheel, ring gear, kingpin, the interior accuse circle output shaft of setting in the casing drive footpath gear rotation and drive output shaft through the kingpin. Compared with the traditional cycloid speed reducer, the pressure angle of the stress of the roller pins is small, so that the stress of the roller pins is greatly reduced, the deformation of the roller pins is reduced, the part can bear larger torque, the service life of the part is prolonged, and the speed reducer is more durable; compared with the traditional cycloidal speed reducer, the cycloidal speed reducer can transmit larger torque and power; different transmission ratios can be obtained by changing the reference circle and the modulus of the radial gear, and compared with the traditional cycloidal reducer, the device can obtain a larger range of the transmission ratios.
Description
Technical Field
The utility model belongs to the technical field of the speed reducer, a big moment of torsion footpath gear kingpin speed reducer is related to.
Background
The cycloidal pin gear speed reducer belongs to the planetary gear transmission speed reducer, and is widely applied to the fields of textile printing and dyeing, light industrial food, metallurgical mines, petrochemical industry, hoisting transportation and engineering machinery; the weak link of the planetary transmission of the cycloidal speed reducer is a tumbler bearing (a new edition of mechanical design manual 3-17-82), because the pressure angle of a cycloidal wheel to a roller pin is too large, the generated radial component force is too large, and the force acting on the roller pin is also very large, so that the contact stress of a tooth-shaped curved surface of the cycloidal wheel and the roller pin is too large, the roller pin and the cycloidal wheel, particularly the tumbler bearing, are easy to deform or damage, the torque with higher power cannot be transmitted, and the service life of equipment can be influenced when the torque is larger.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to the problem that prior art exists, it is little to provide a kingpin pressure angle, and normal direction component is big, can provide the big moment of torsion footpath gear kingpin speed reducer of great moment of torsion.
Therefore, the utility model adopts the following technical scheme:
a large-torque-diameter gear needle roller speed reducer comprises a machine shell and
the input shaft is arranged in the shell, one end of the input shaft extends out of the shell, a first eccentric shaft sleeve and two second eccentric shaft sleeves are mounted on the input shaft, the eccentricity of the second eccentric shaft sleeves is larger than that of the first eccentric shaft sleeves, the eccentricity directions of the second eccentric shaft sleeves are the same, and the first eccentric shaft sleeves are positioned between the two second eccentric shaft sleeves;
the radial gear is mounted on the first eccentric shaft sleeve through a bearing, and a plurality of first pin shaft holes are uniformly formed in the radial gear along the circumferential direction;
the two needle roller top wheels are respectively arranged on the two second eccentric shaft sleeves through bearings, the diameter of each needle roller top wheel is smaller than that of the addendum circle of the radial gear, second pin shaft holes corresponding to the first pin shaft holes are uniformly formed in the needle roller top wheels along the circumferential direction, and the first pin shaft holes are not overlapped with the second pin shaft holes;
the two inner gear rings are fixed on the inner wall of the machine shell and are respectively positioned between the radial gear and the needle roller top gear, and the number of teeth of the inner gear rings is one more than that of the radial gear;
the number of the rolling needles is the same as that of the teeth of the radial gear, one rolling needle is correspondingly arranged in one tooth groove of the radial gear, and two ends of the rolling needles are in contact with the outer edge of the rolling needle top wheel;
the inner control ring is sleeved on the needle roller top wheel and can move along with the needle roller top wheel, and the needle roller is positioned in a gap between the inner control ring and the needle roller top wheel;
the output shaft and the input shaft are coaxially arranged, the output shaft is positioned in the shell, one end of the output shaft extends out of the shell, an output shaft end plate perpendicular to the output shaft is fixed at the inner end of the output shaft, pin shafts corresponding to the pin shaft holes are uniformly arranged on the output shaft end plate along the circumferential direction, and the pin shafts penetrate through the pin shaft holes.
Furthermore, the number of the pin shaft holes is 3-6.
Further, a pin shaft sleeve is sleeved on the pin shaft.
Further, the diameter of the pin shaft hole is larger than that of the pin shaft sleeve.
Further, the tooth groove width of the diameter gear is the same as the diameter of the needle roller.
The beneficial effects of the utility model reside in that:
1. compared with the traditional cycloid speed reducer, the roller pin has the advantages that the pressure angle of the roller pin stressed by the traditional cycloid speed reducer is too large, the pressure angle of the roller pin stressed by external force is very small, the stress of the roller pin is greatly reduced, the deformation of the roller pin is reduced, the part can bear larger torque, the service life of the part is prolonged, and the speed reducer is more durable.
2. Compared with the traditional cycloidal speed reducer, the cycloidal speed reducer can transmit larger torque and power; the speed reducer with the same volume and the same speed ratio transmits the same torque through theoretical analysis, the radial force component of the speed reducer is reduced by 71 percent compared with that of a cycloidal speed reducer, the radial force component of the speed reducer is reduced by 57 percent, and the transmittable torque is 1.8 times of that of a pendulum reduction under the condition of the same contact stress.
3. The transmission ratio is the same as the tooth number of the radial gear, different transmission ratios can be obtained by changing the reference circle and the modulus of the radial gear, and the device has a wider range of the obtained transmission ratio compared with the traditional cycloidal speed reducer.
Drawings
FIG. 1 is a schematic view of a novel planar assembly structure of the present invention;
FIG. 2 is an exploded view of the three-dimensional structure of the present invention;
FIG. 3 is a schematic structural view of the radial gear of the present invention;
FIG. 4 is a schematic structural view of the inner positioning ring of the present invention;
fig. 5 is a schematic structural view of the ring gear of the present invention;
fig. 6 is a schematic structural view of the inside of the casing in the direction of the output shaft of the present invention;
FIG. 7 is a schematic diagram of the outline of the internal components of the output shaft direction casing of the present invention;
FIG. 8 is a displacement diagram of the needle rollers during operation according to the present invention;
fig. 9 is a schematic view of the stress of the roller pins during operation of the present invention;
in the figure, 1-machine shell, 2-input shaft, 3-first eccentric shaft sleeve, 4-second eccentric shaft sleeve, 5-diameter gear, 6-roller pin top wheel, 7-first pin shaft hole, 8-second pin shaft hole, 9-inner gear ring, 10-roller pin, 11-inner control ring, 12-output shaft, 13-output shaft end plate, 14-pin shaft, 15-bearing and 16-pin shaft sleeve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. The components of embodiments of the present invention, as generally described and illustrated in the figures herein, may be arranged and designed in a wide variety of different configurations. Thus, the following detailed description of the embodiments of the present invention, presented in the accompanying drawings, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
As shown in fig. 1-5, a large torque diameter gear needle roller speed reducer comprises a machine shell 1;
the input shaft 2 is arranged in the machine shell 1, one end of the input shaft 2 extends out of the machine shell 1, the end is used for being connected with a motor, a first eccentric shaft sleeve 3 and two second eccentric shaft sleeves 4 are installed on the input shaft 2, the eccentricity of the second eccentric shaft sleeves 4 is larger than that of the first eccentric shaft sleeve 3, the eccentric directions of the first eccentric shaft sleeve 3 and the second eccentric shaft sleeve 4 are the same, and the first eccentric shaft sleeve 3 is positioned between the two second eccentric shaft sleeves 4;
the radial gears 5 are mounted on the first eccentric shaft sleeve 3 through bearings 15, a plurality of first pin shaft holes 7 are uniformly formed in the radial gears 5 along the circumferential direction, the specific number of the first pin shaft holes can be 3-6, and the radial gears 5 can perform circular revolution motion around the central line of the input shaft 2 under the driving of the first eccentric shaft sleeve 3;
the two needle roller top wheels 6 are respectively arranged on the two second eccentric shaft sleeves 4 through bearings 15, the diameter of each needle roller top wheel 6 is smaller than the diameter of the addendum circle of the corresponding radial gear 5, second pin shaft holes 7 corresponding to the first pin shaft holes 7 are uniformly arranged on the needle roller top wheels 6 along the circumferential direction, and the first pin shaft holes 7 are not overlapped with the second pin shaft holes 8;
and two inner gear rings 9 (the tooth form of the inner gear rings 9 is shown in fig. 5), the two inner gear rings 9 are fixed on the inner wall of the machine shell 1, the two inner gear rings 9 are respectively positioned between the radial gear 5 and the needle roller top wheel 6, and the number of teeth of the inner gear rings 9 is one more than that of the radial gear 5.
The number of the needle rollers 10 is the same as the number of teeth of the radial gear 5, one needle roller 10 is correspondingly arranged in one tooth groove of the radial gear 5, the outer edges of the needle roller top wheels 6 on two sides of the radial gear 5 at two ends of the needle rollers 10 are contacted, namely, the needle rollers 10 are uniformly distributed at intervals along the circumferential direction of the needle roller top wheels 6 (as shown in fig. 6), the needle rollers 10 are uniformly stressed and cannot be skewed, the width of the tooth groove of the radial gear 5 is the same as the diameter of the needle roller 10, a certain tolerance gap is reserved during actual matching, and the needle rollers 10 can move in the tooth groove along the length direction of the tooth groove;
in addition, the distance between the edge of the needle roller top wheel 6 and the tooth top of the inner gear ring 9 and the edge of the needle roller top wheel 6 is the diameter of the needle roller 10, and the arrangement can ensure that the needle roller 10 can smoothly move from one tooth space of the inner gear ring 9 to an adjacent tooth space without blocking;
the two inner control rings 11 are respectively sleeved on the needle roller top wheel 6 and can move along with the needle roller top wheel 6, the needle rollers 10 are positioned at a gap between the inner control rings 11 and the needle roller top wheel 6, the needle rollers 10 and the inner control rings 11 form a structure similar to a bearing, so that the needle rollers 10 can revolve along with the needle roller top wheel 6 when the needle roller top wheel 6 revolves, and the inner control rings 11 are used for keeping the needle rollers 10 in contact with the edge of the needle roller top wheel 6 and preventing the needle rollers 10 from being separated;
an output shaft 12, the output shaft 12 and the input shaft 2 are coaxially arranged, the output shaft 12 is positioned in the casing 1, one end of the output shaft 12 extends out of the casing 1, an output shaft end plate 13 perpendicular to the output shaft 12 is fixed at the inner end of the output shaft 12, a pin shaft 14 corresponding to the first pin shaft hole 7 is uniformly arranged on the output shaft end plate 13 along the circumferential direction, the pin shaft 14 penetrates through the first pin shaft hole 7 and the second pin shaft hole 8, a pin shaft sleeve 16 is sleeved on the pin shaft 14, the pin shaft sleeve 16 can rotate and is used for protecting the pin shaft 14 to reduce the friction of the first pin shaft hole 7 and the second pin shaft hole 8 to the pin shaft, in addition, the diameters of the first pin shaft hole 7 and the second pin shaft hole 8 are larger than the diameter of the pin shaft sleeve 16, so that a large enough gap is formed between the pin shaft sleeve 16 and the first pin shaft hole 7 and the second pin shaft hole 8, and simultaneously, the first pin, and the connecting line of the tangent point and the center of the circle of the pin bush 16 is the stress direction of the pin bush 16 at that time.
In addition, bearings of corresponding types are arranged between contact parts of the input shaft 2 and the output shaft 12 and the shell 1 in a conventional mode.
The working principle and process of the utility model are as follows, when in use, the motor is connected with the input shaft 2, the motor rotates to drive the input shaft 2 to rotate (assuming that the rotation direction of the motor is clockwise at the moment), the input shaft 2 drives the first eccentric sleeve 3 and the two second eccentric sleeves 4 to rotate, the radial gear 5 and the roller pin top wheel 6 are driven by the first eccentric sleeve 3 and the two second eccentric sleeves 4 to revolve clockwise around the central line of the input shaft 2, the roller pin 10 is extruded by the roller pin top wheel 6 at one side of the radial gear 5 and the inner gear ring 9 to the direction of the radial gear 5 far away from the tooth space, the roller pin 10 is simultaneously applied with the roller pin top wheel 6 and the inner gear ring 9 (as shown in figure 9), concretely, the force B applied by the roller pin top wheel 6 to the roller pin 10 and the force C applied by the inner gear ring 9 to the roller pin 10, the resultant force of the two is equal to the force A applied by the side wall of the, under the action of resultant force, the tooth space side wall of the cycloid wheel 5 is subjected to reaction force exerted by the roller pin 10, under the action of the reaction force, the radial gear 5 rotates anticlockwise, the first pin shaft hole 7 on the radial gear 5 exerts action force on the pin shaft 14 through the pin shaft sleeve 16 while the radial gear 5 rotates anticlockwise, the action force is transmitted to the output shaft end plate 13, and finally the output shaft end plate 13 drives the output shaft 12 to rotate anticlockwise.
In the operation process (as shown in fig. 7), taking any one of the needle rollers 10 as an example, the needle roller 10 rotates and displaces under the common acting force of the radial gear 5, the inner ring gear 9, the needle roller top wheel 6 and the inner control ring 11, specifically, when the radial gear 5 and the needle roller top wheel 6 revolve from the initial position close to the side wall of the inner ring gear 9 to the side wall far away from the side wall, the corresponding needle roller 10 moves towards the inner direction of the tooth socket of the radial gear 5, the needle roller 10 clings to the tooth trace of the inner ring gear 9 in the movement process, and when the radial gear 5 and the needle roller top wheel 6 revolve to the side far away from the initial position, the needle roller 10 moves to the innermost end of the tooth socket of the corresponding radial gear 5 and leaves the inner part of the; when the radial gear 5 and the needle roller top wheel 6 return to the initial position along the revolution circle of the pointer, the needle roller 10 moves to the direction far away from the tooth groove of the radial gear 5 where the needle roller is located and enters the tooth groove of one inner gear ring 9 adjacent to the counterclockwise direction of the needle roller, the displacement motion of the needle roller 10 is in a curve (as shown in figure 8), namely, the radial gear 5 and the roller pin top wheel 6 revolve along the pointer for a circle, the roller pin 10 moves anticlockwise by the pitch of the radial gear 5, the movement of the roller pin 10 drives the radial gear 5 to rotate anticlockwise correspondingly, when the roller pin 10 revolves for one circle, the radial gear 5 is driven to rotate for one circle, when the input shaft 2 drives the radial gear 5 and the roller pin top wheel 6 to revolve for the number of turns equal to the number of teeth of the radial gear 5, the roller pin 10 revolves for one circle, and the roller pin 10 revolves to drive the radial gear 5 to rotate for one circle, so that the transmission ratio of the speed reducer is equal to the number of teeth of the radial gear 5 and the number of the roller pins 10.
Claims (5)
1. The large-torque-diameter gear needle roller speed reducer is characterized by comprising a machine shell (1) and
the input shaft (2) is arranged in the machine shell (1), one end of the input shaft (2) extends out of the machine shell (1), the input shaft (2) is provided with a first eccentric shaft sleeve (3) and two second eccentric shaft sleeves (4), the eccentricity of the second eccentric shaft sleeves is larger than that of the first eccentric shaft sleeves, the eccentricity directions are the same, and the first eccentric shaft sleeve (3) is positioned between the two second eccentric shaft sleeves (4);
the radial gear (5) is mounted on the first eccentric shaft sleeve (3) through a bearing (15), and a plurality of first pin shaft holes (7) are uniformly formed in the radial gear (5) along the circumferential direction;
the two needle roller top wheels (6) are respectively arranged on the two second eccentric shaft sleeves (4) through bearings (15), the diameter of each needle roller top wheel (6) is smaller than that of the addendum circle of the radial gear (5), second pin shaft holes (8) corresponding to the first pin shaft holes (7) are uniformly formed in the needle roller top wheels (6) along the circumferential direction, and the first pin shaft holes (7) are not overlapped with the second pin shaft holes (8);
the two inner gear rings (9) are fixed on the inner wall of the machine shell (1), the two inner gear rings (9) are respectively positioned between the radial gear (5) and the needle roller top wheel (6), and the number of teeth of the inner gear rings (9) is one more than that of the radial gear (5);
the number of the rolling needles (10) is the same as the number of teeth of the radial gear (5), one rolling needle (10) is correspondingly arranged in one tooth groove of the radial gear (5), and two ends of the rolling needle (10) are in contact with the outer edge of the rolling needle top wheel (6);
the inner control ring (11) is sleeved on the roller pin top wheel (6) and can move along with the roller pin top wheel (6), and the roller pin (10) is positioned in a gap between the inner control ring (11) and the roller pin top wheel (6);
the output shaft (12) and the input shaft (2) are coaxially arranged, the output shaft (12) is located in the shell (1), one end of the output shaft (12) extends out of the shell (1), an output shaft end plate (13) perpendicular to the output shaft is fixed to the inner end of the output shaft (12), pin shafts (14) corresponding to the first pin shaft holes (7) are evenly arranged on the output shaft end plate (13) in the circumferential direction, and the pin shafts (14) penetrate through the first pin shaft holes (7) and the second pin shaft holes (8).
2. The large-torque-diameter gear needle roller speed reducer according to claim 1, wherein the number of the first pin shaft holes (7) is 3-6.
3. The large-torque-diameter gear needle roller speed reducer according to claim 1, wherein the pin shaft (14) is sleeved with a pin shaft sleeve (16).
4. A large torque diameter gear needle roller reducer according to claim 3, wherein the diameters of the first pin shaft hole (7) and the second pin shaft hole (8) are larger than the diameter of the pin bush (16).
5. A large-torque-diameter gear needle roller reducer according to claim 1, wherein the width of the tooth space of the diameter gear (5) is the same as the diameter of the needle roller (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920801049.5U CN209977163U (en) | 2019-05-30 | 2019-05-30 | Large-torque-diameter gear needle roller speed reducer |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920801049.5U CN209977163U (en) | 2019-05-30 | 2019-05-30 | Large-torque-diameter gear needle roller speed reducer |
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| Publication Number | Publication Date |
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| CN209977163U true CN209977163U (en) | 2020-01-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201920801049.5U Active CN209977163U (en) | 2019-05-30 | 2019-05-30 | Large-torque-diameter gear needle roller speed reducer |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110067834A (en) * | 2019-05-30 | 2019-07-30 | 兰州西腾润工装备制造有限公司 | A kind of large torque diameter gear needle roller speed reducer |
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2019
- 2019-05-30 CN CN201920801049.5U patent/CN209977163U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110067834A (en) * | 2019-05-30 | 2019-07-30 | 兰州西腾润工装备制造有限公司 | A kind of large torque diameter gear needle roller speed reducer |
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