CN109737187B - Speed reducer - Google Patents
Speed reducer Download PDFInfo
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- CN109737187B CN109737187B CN201910182874.6A CN201910182874A CN109737187B CN 109737187 B CN109737187 B CN 109737187B CN 201910182874 A CN201910182874 A CN 201910182874A CN 109737187 B CN109737187 B CN 109737187B
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- 239000003638 chemical reducing agent Substances 0.000 title claims abstract description 18
- 230000009467 reduction Effects 0.000 claims abstract description 29
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- 230000009347 mechanical transmission Effects 0.000 abstract description 3
- 230000005540 biological transmission Effects 0.000 description 26
- 230000033001 locomotion Effects 0.000 description 17
- 230000001050 lubricating effect Effects 0.000 description 4
- 238000012423 maintenance Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 3
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- 150000002632 lipids Chemical class 0.000 description 1
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Abstract
The invention discloses a speed reducer, and relates to the technical field of mechanical transmission. The gear comprises an inner gear ring, an input gear shaft, a first end cover, a second end cover, a bevel gear, a crank shaft and a swing gear, wherein the input gear shaft penetrates through central holes of the first end cover and the second end cover and is movably connected with the central holes of the first end cover and the second end cover, the bevel gear is fixedly connected with one end of the input gear shaft, the input gear shaft comprises a first gear tooth part, the crank shaft comprises a second gear tooth part and at least two eccentric wheels, the first gear tooth part is meshed with the second gear tooth part, the swing gear comprises a plurality of through holes, the through holes are uniformly distributed around the center circumference of the swing gear, the eccentric wheels are movably connected with the swing gear through the through holes respectively, two ends of the crank shaft are movably connected with the first end cover and the second end cover respectively, the swing gear and the inner gear ring form a gear pair with small tooth difference, and the second end cover comprises a connecting part for outputting torque and rotating speed. Has higher reduction ratio and more compact structure, and simultaneously enhances the running stability.
Description
Technical Field
The invention relates to the technical field of mechanical transmission, in particular to a speed reducer.
Background
The speed reducing device is an instrument which plays roles in matching the rotating speed and transmitting torque between a prime motor and a working machine or an actuating mechanism, and is widely applied to modern machines. At present, the industry of the speed reducing device is very specialized, and the speed reducing device is large-scale and standardized for different fields and different applications, so that great convenience is brought to production application. However, in industries requiring precise control, such as precise transmission and robots, the common speed reducing device cannot meet the application requirements. Therefore, the development of the speed reducer with excellent performance plays a great role in the production of mechanical equipment industry in China.
In the prior art, the speed reducer can not well meet the miniaturization of structural size and higher speed reduction ratio, and for the speed reducer meeting the high speed reduction ratio, the size is often larger, but the speed reduction ratio of the speed reducer with small size is insufficient, so that the development of mechanical transmission technology is limited to a certain extent. In addition, in the use process, particularly when the device is subjected to frequent impact load, the service life of the speed reducing device is shorter, the stable operation of transmission equipment is not facilitated, and the later maintenance burden is increased.
Therefore, there is a need for a reduction gear that is more compact in construction, has a higher gear ratio, and operates more stably to meet higher transmission demands.
Disclosure of Invention
The object of the present invention is to provide a reduction gear capable of having a higher reduction ratio and a more compact structure while enhancing the running stability.
Embodiments of the present invention are implemented as follows:
the embodiment of the invention provides a speed reducing device, which comprises an annular gear, an input gear shaft, a first end cover, a second end cover, a bevel gear, a crank shaft and a swing gear, wherein the input gear shaft penetrates through central holes of the first end cover and the second end cover and is movably connected with the central holes of the first end cover and the second end cover, the bevel gear is fixedly connected with one end of the input gear shaft, the input gear shaft comprises a first gear tooth part, the crank shaft comprises a second gear tooth part and at least two eccentric wheels, the first gear tooth part is meshed with the second gear tooth part, the swing gear comprises a plurality of through holes, the through holes are uniformly distributed around the central circumference of the swing gear, the eccentric wheels are respectively and movably connected with the swing gear through the through holes, two ends of the crank shaft are respectively and movably connected with the first end cover and the second end cover, the swing gear and the annular gear form a small-tooth-difference gear pair, and the second end cover comprises a connecting part for outputting torque and rotating speed.
Optionally, the first end cover includes a plurality of first mounting holes and a plurality of first connecting holes, first mounting holes with the interval sets up in turn in first connecting holes, the second end cover is provided with a plurality of second mounting holes and a plurality of second connecting holes, the second mounting holes with the interval sets up in the second is connected Kong Jiaoti, just first mounting holes with the second mounting holes are on same axis, first connecting holes with the second connecting holes are on same axis, first end cover with the second end cover is through wearing to establish first mounting holes with the round pin axle fixed connection of second mounting holes, the both ends of crank axle set up respectively first connecting holes with in the second connecting holes.
Optionally, the crankshaft is close to one end of first end cover with coaxial first bearing subassembly and the deep groove ball bearing of being provided with between the first connecting hole, first connecting hole inner wall is provided with first annular groove and first annular bulge, first annular groove sets up the protruding outside of first annular, be provided with the second annular groove on the crankshaft, just first annular groove with the second annular groove corresponds the setting, first annular groove first annular bulge with the second annular groove cooperatees and is used for right first bearing subassembly with the deep groove ball bearing axial positioning.
Optionally, the crankshaft is close to one end of second end cover with be provided with the second kingpin holder subassembly between the second connecting hole, second connecting hole inner wall is provided with third annular groove and second annular arch, third annular groove sets up the protruding outside of second annular, be provided with the fourth annular groove on the crankshaft, just third annular groove with the fourth annular groove corresponds the setting, third annular groove the protruding with the fourth annular groove cooperatees and is used for right second kingpin holder subassembly axial positioning.
Optionally, a third needle roller cage assembly is disposed between the eccentric and the through hole.
Optionally, the input gear shaft further includes a middle shaft section provided with the first gear tooth portion and a first shaft section coaxially connected with one end of the middle shaft section, the first shaft section is located on one side of the first end cover, the diameter of the first shaft section is smaller than that of the middle shaft section, a shaft sleeve is arranged on the first shaft section, a needle bearing is arranged between the shaft sleeve and a central hole of the first end cover, a bevel gear is sleeved on the first shaft section and abuts against the shaft sleeve, a threaded hole is formed in the end portion of the first shaft section, and the bevel gear is fixedly connected with the first shaft section through a fastening bolt.
Optionally, the input gear shaft further includes a second shaft section coaxially connected to the other end of the intermediate shaft section, the second shaft section is located at one side of the second end cover, the diameter of the second shaft section is smaller than that of the intermediate shaft section, angular contact ball bearings are disposed back to back or face to face on the second shaft section, and a fifth annular groove and a sixth annular groove are correspondingly disposed on the inner wall of the central hole of the second end cover and the second shaft section respectively and are used for axially positioning the angular contact ball bearings.
Optionally, the ring gear includes needle tooth portion, first spacing portion and second spacing portion, needle tooth portion with swing gear meshing, first spacing portion with be provided with first tapered roller bearing and mating grinding packing ring between the first end cover, second spacing portion with be provided with second tapered roller bearing and skeleton oil blanket between the second end cover, mating grinding packing ring sets up first tapered roller bearing inboard, the skeleton oil blanket sets up the second tapered roller bearing outside.
Optionally, tooth grooves are formed between adjacent needle teeth of the needle teeth part, the cross section of each tooth groove is in a concave circular arc shape, the tooth heights of two sides of the needle teeth are larger than those of the middle, and the teeth of the swing gear are concave teeth.
Optionally, the first end cover is provided with a grease injecting hole.
The beneficial effects of the embodiment of the invention include:
according to the speed reducer, the input gear shaft movably connected with the central holes of the first end cover and the second end cover enables the speed reducer to be capable of inputting torque well, and stability in operation is improved. The input gear shaft obtains the same rotating speed and torque as the bevel gear through the bevel gear fixedly connected with one end of the input gear shaft, and in addition, the first-stage speed reduction of the speed reduction device is realized through the meshing transmission of the bevel gear and the output end of the external motor. The first gear tooth part of the input gear shaft is meshed with the second gear tooth part of the crank shaft for transmission, so that the input torque is transmitted to the crank shaft, and the two-stage speed reduction of the speed reduction device is realized. Through holes uniformly distributed around the center circumference of the swing gear and eccentric wheels arranged through the through holes, the rotation motion of the crankshaft is converted into revolution motion of the swing gear, and then the small tooth difference transmission between the swing gear and the inner gear ring is realized. The manufacturing cost is reduced through the transmission of less tooth difference, the transmission ratio range is larger, the positioning precision and the transmission efficiency are higher, the structure is more compact, and the operation is stable and reliable. In addition, the crank axle is movably connected with the swing gear, the first end cover and the second end cover, and the rotation motion of the swing gear can drive the first end cover and the second end cover to do rotation motion around the central axis. And outputting the converted torque and rotation speed through the connecting part of the second end cover so as to obtain larger torque and smaller rotation speed.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are needed in the embodiments will be briefly described below, it being understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and other related drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of a speed reducer according to an embodiment of the present invention;
FIG. 2 is a cross-sectional view A-A of FIG. 1;
FIG. 3 is a cross-sectional view B-B of FIG. 2;
fig. 4 is a second schematic structural diagram of a speed reducer according to an embodiment of the present invention.
Icon: 100-speed reduction device; 110-an inner gear ring; 111-needle teeth; 112-a first limit part; 113-a second limit part; 114-a first tapered roller bearing; 115-mating the washers; 116-a second tapered roller bearing; 117-skeleton oil seal; 120-input gear shaft; 121-bevel gears; 122-a first gear tooth portion; 123-a first shaft section; 124-sleeve; 125-needle bearings; 126-fastening bolts; 127-second shaft section; 128-angular contact ball bearings; 129 A-A fifth annular groove; 129 b-a sixth annular groove; 130-a first end cap; 131-a first mounting hole; 133-first connection holes; 135 A-A first annular groove; 135 b-a second annular groove; 137-a first annular protrusion; 139-injecting a lipid hole; 140-a second end cap; 141-a connection; 143-a second mounting hole; 145-a second connection hole; 147 A-A third annular groove; 147 b-fourth annular groove; 149-a second annular projection; 150-crank shaft; 151-second gear tooth portions; 153-eccentric; 155-a first needle cage assembly; 157-deep groove ball bearings; 159-a second needle cage assembly; 160-a swing gear; 161-through holes; 163-third needle cage assembly; 165-gear teeth; 170-pin shaft.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. The components of the embodiments of the present invention 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 invention, as presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further definition or explanation thereof is necessary in the following figures.
In the description of the present invention, it should be noted that, directions or positional relationships indicated by terms such as "center", "upper", "lower", "left", "right", "inner", "outer", etc., are directions or positional relationships based on those shown in the drawings, or are directions or positional relationships conventionally put in use of the inventive product, are merely for convenience of describing the present invention and simplifying the description, and are not indicative or implying that the apparatus or element to be referred to must have a specific direction, be constructed and operated in a specific direction, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," "third," and the like are used merely to distinguish between descriptions and should not be construed as indicating or implying relative importance.
In the description of the present invention, it should also be noted that, unless explicitly specified and limited otherwise, the terms "disposed," "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Referring to fig. 1 and 2, an embodiment of the present invention provides a reduction gear 100, including an annular gear 110, an input gear shaft 120, a first end cap 130, a second end cap 140, a bevel gear 121, a crank shaft 150 and a swing gear 160, wherein the input gear shaft 120 passes through central holes of the first end cap 130 and the second end cap 140 and is movably connected with the central holes of the first end cap 130 and the second end cap 140, the bevel gear 121 is fixedly connected with one end of the input gear shaft 120, the input gear shaft 120 includes a first gear tooth portion 122, the crank shaft 150 includes a second gear tooth portion 151, and at least two eccentric gears 153, the first gear tooth portion 122 is meshed with the second gear tooth portion 151, the swing gear 160 includes a plurality of through holes 161, the through holes 161 are uniformly distributed around the central circumference of the swing gear 160 (as shown in fig. 3), the eccentric gears 153 are movably connected with the swing gear 160 through the through holes 161, two ends of the crank shaft 150 are movably connected with the first end cap 130 and the second end cap 140 respectively, the swing gear 160 and the annular gear 110 form a small gear difference pair, and the second end cap 140 includes a connecting portion 141 for outputting torque and rotation speed.
It should be noted that, in the first embodiment, the first gear tooth portion 122 of the input gear shaft 120 and the second gear tooth portion 151 of the crank shaft 150 may be detachably connected or integrally formed. In this way, the stability of the input gear shaft 120 and the crank shaft 150 during transmission can be enhanced, the probability of affecting normal transmission due to loosening of the first gear tooth portion 122 or the second gear tooth portion 151 is reduced, the assembly difficulty is also reduced, and the assembly efficiency is improved.
Second, the positional relationship, the number and the offset phase of the eccentric wheels 153 in the eccentric direction are not particularly limited in the embodiment of the present invention, as long as the required transmission requirement can be satisfied. For example, the number of eccentric wheels 153 may be two, and the phase difference between the eccentric wheels is 180 ° so as to better balance the stress of the crankshaft 150 and prolong the service life of the crankshaft 150. If there is only one eccentric wheel 153, the stability during transmission cannot be well ensured, and if the number of eccentric wheels 153 is large, the number of correspondingly assembled oscillating gears 160 is increased, so that the transmission load of the crankshaft 150 is increased intangibly, and the weight of the reduction gear 100 is increased. Therefore, the number of the eccentric wheels 153 is optimal when 2-3, and the two eccentric wheels 153 are adopted in the embodiment of the invention, so that the stability of transmission and the capability of bearing fatigue stress of the crankshaft 150 can be balanced better, and the stability of the speed reducer 100 is further improved. In addition, the meshing position of the first gear tooth portion 122 and the second gear tooth portion 151 is located between the second end cover 140 and the swing gear 160, so that the speed reducer 100 can better share load and prolong service life.
Third, the oscillating gear 160 and the ring gear 110 form a gear pair with small teeth difference, and the difference between the teeth numbers of the oscillating gear 160 and the ring gear 110 is not particularly limited in the embodiment of the present invention, and the teeth number of the oscillating gear 160 may be 2 to 4 teeth less than the teeth number of the ring gear 110, so long as the required stability and reduction ratio of the small teeth difference transmission can be satisfied.
According to the speed reducer 100 provided by the embodiment of the invention, through the input gear shaft 120 movably connected with the central holes of the first end cover 130 and the second end cover 140, the speed reducer 100 can better input torque, and the stability during operation is improved. The input gear shaft 120 is made to obtain the same rotation speed and torque as those of the bevel gear 121 by means of the bevel gear 121 fixedly connected to one end of the input gear shaft 120, and in addition, one-stage reduction of the reduction gear 100 is achieved by means of the meshed transmission of the bevel gear 121 and the output end of the external motor. By the meshing transmission of the first gear tooth portion 122 of the input gear shaft 120 and the second gear tooth portion 151 of the crank shaft 150, the input torque is transmitted to the crank shaft 150 while achieving the two-stage deceleration of the reduction gear 100. Through the through holes 161 uniformly distributed around the center circumference of the swing gear 160 and the eccentric wheels 153 arranged through the through holes 161, the rotation motion of the crank shaft 150 is converted into revolution motion of the swing gear 160, so that the small tooth difference transmission between the swing gear 160 and the inner gear ring 110 is realized. The manufacturing cost is reduced through the transmission of less tooth difference, the transmission ratio range is larger, the positioning precision and the transmission efficiency are higher, the structure is more compact, and the operation is stable and reliable. In addition, the crank shaft 150 is movably connected with the swing gear 160, the first end cover 130 and the second end cover 140, and the rotation of the swing gear 160 drives the first end cover 130 and the second end cover 140 to rotate around the central axis. The converted torque and rotation speed are outputted through the connection portion 141 of the second end cap 140 to obtain a larger torque and a smaller rotation speed.
As shown in fig. 1 and 4, the first end cap 130 includes a plurality of first mounting holes 131 and a plurality of first connection holes 133, the first mounting holes 131 and the first connection holes 133 are alternately arranged at intervals, the second end cap 140 is provided with a plurality of second mounting holes 143 and a plurality of second connection holes 145, the second mounting holes 143 and the second connection holes 145 are alternately arranged at intervals, the first mounting holes 131 and the second mounting holes 143 are on the same axis, the first connection holes 133 and the second connection holes 145 are on the same axis, and the first end cap 130 and the second end cap 140 are fixedly connected through pins 170 penetrating through the first mounting holes 131 and the second mounting holes 143 (as shown in fig. 2), and two ends of the crank shaft 150 are respectively arranged in the first connection holes 133 and the second connection holes 145.
Specifically, the pin 170 is a stepped shaft with a diameter greater than that of the two ends in the middle, and threaded holes are provided at the two ends of the pin 170. The first mounting hole 131 of the first end cap 130 is clamped at the stepped section of the pin 170, and the first end cap 130 is fixedly connected with the pin 170 through a locking screw. The screw hole of the pin shaft 170 at the second mounting hole 143 of the second end cap 140 may be fixedly connected with an external load as an auxiliary connection hole to improve the connection stability.
The first and second connection holes 133 and 145 are axially limited by both ends of the crank shaft 150 to fixedly connect the first and second end caps 130 and 140, and then form a planetary carrier structure by combining the pin shaft 170. It should be noted that, in the embodiment of the present invention, the number of the first mounting holes 131, the first connecting holes 133, the second mounting holes 143, and the second connecting holes 145 is not specifically limited, and the number of the first mounting holes 131, the first connecting holes 133, the second mounting holes 143, and the second connecting holes 145 may be set to 3, for example, to better meet the requirement of stable transmission.
As shown in fig. 2, a first needle roller cage assembly 155 and a deep groove ball bearing 157 are coaxially disposed between one end of the crank shaft 150 near the first end cap 130 and the first connecting hole 133, a first annular groove 135a and a first annular protrusion 137 are disposed on an inner wall of the first connecting hole 133, the first annular groove 135a is disposed outside the first annular protrusion 137, a second annular groove 135b is disposed on the crank shaft 150, and the first annular groove 135a and the second annular groove 135b are correspondingly disposed, and the first annular groove 135a, the first annular protrusion 137 and the second annular groove 135b are matched for axially positioning the first needle roller cage assembly 155 and the deep groove ball bearing 157.
Specifically, the retainer ring (e.g., inner snap spring) for the clamping hole in the first annular groove 135a, the retainer ring (e.g., outer snap spring) for the clamping hole in the second annular groove 135b, and the first annular groove 135a and the second annular groove 135b are correspondingly disposed, specifically, the first annular groove 135a and the second annular groove 135b are on the same assembly cross section, so as to axially locate the first needle roller cage assembly 155 and the first side of the deep groove ball bearing 157. A first annular projection 137 is formed through the inner wall of the first coupling bore 133 to axially locate the first needle cage assembly 155 and the second side of the deep groove ball bearing 157. In addition, an annular groove can be further formed on the crankshaft 150, and the axial positioning is assisted by the shaft retainer ring on the second side of the first needle roller cage assembly 155 and the deep groove ball bearing 157, so that the stability of connection is improved, the probability of axial movement is reduced, and the service lives of the first needle roller cage assembly 155 and the deep groove ball bearing 157 are further prolonged.
Because of the different radial thicknesses of the first needle cage assembly 155 and the deep groove ball bearing 157, concentric circumferential surfaces of different diameters may be employed to mate at the junction of the crankshaft 150 and the first needle cage assembly 155 and the deep groove ball bearing 157. An annular groove and a shaft retainer ring may also be provided between the first needle cage assembly 155 and the deep groove ball bearing 157 to reduce the chance of interaction between the first needle cage assembly 155 and the deep groove ball bearing 157. The deep groove ball bearing 157 can bear certain bidirectional axial load and has better dustproof performance, and the deep groove ball bearing 157 is arranged outside the first needle retainer assembly 155. The first needle roller cage assembly 155 is compact in radial configuration, has a minimum outer diameter when having the same inner diameter dimension and load carrying capacity as other types of bearings, and is particularly suitable for radially mounted limited size support structures, which facilitates compactness of the overall structure.
As shown in fig. 2, a second needle roller cage assembly 159 is disposed between one end of the crank shaft 150 near the second end cover 140 and the second connecting hole 145, a third annular groove 147a and a second annular protrusion 149 are disposed on the inner wall of the second connecting hole 145, the third annular groove 147a is disposed outside the second annular protrusion 149, a fourth annular groove 147b is disposed on the crank shaft 150, and the third annular groove 147a and the fourth annular groove 147b are disposed correspondingly, and the third annular groove 147a, the second annular protrusion 149 and the fourth annular groove 147b cooperate to axially position the second needle roller cage assembly 159.
Specifically, the third annular groove 147a is internally provided with a retainer ring for a clamping hole (such as an inner clamping spring), the fourth annular groove 147b is internally provided with a retainer ring for a clamping hole (such as an outer clamping spring), and the third annular groove 147a and the fourth annular groove 147b are correspondingly arranged, specifically, the third annular groove 147a and the fourth annular groove 147b are arranged on the same assembly section so as to axially position one side of the second needle roller cage assembly 159. The other side is axially positioned by means of the stepped section of the crank shaft 150 to promote stability of the crank shaft 150 when it rotates.
As shown in fig. 2 and 3, a third needle roller cage assembly 163 is provided between the eccentric 153 and the through hole 161.
Specifically, when the input gear shaft 120 rotates, a certain rotational speed and torque are transmitted to the crankshaft 150, and when the crankshaft 150 rotates around its own axis, the eccentric wheel 153 on the crankshaft 150 drives the oscillating gear 160 to rotate. By the third needle roller cage assembly 163 provided between the eccentric 153 and the through hole 161 of the swing gear 160, friction between the crank shaft 150 and the swing gear 160 is reduced, and lubrication maintenance and the like are also facilitated.
In addition, the swing gear 160 performs a revolution motion around the rotation axis of the first and second end caps 130 and 140, and as a result of the revolution, the swing gear 160 is brought into meshing contact with the pin gear portion 111 of the ring gear 110, and as a result of the ring gear 110 being fixedly secured to the outside, the pin gear portion 111 and the swing gear 160 reversely provide a force during the contact, which pushes the swing gear 160 to generate a force opposite to the revolution direction, that is, to generate a rotation motion around the own axis, and which is opposite to the revolution motion (that is, opposite to the direction in which the input gear shaft 120 is driven). When the swing gear 160 generates a rotation motion, the rotation motion is transmitted to the crank shaft 150 through an eccentric motion, resulting in the crank shaft 150 also generating a revolution motion around the rotation axes of the first and second end caps 130 and 140. The revolution motion of the crank shaft 150 drives the first and second end caps 130 and 140 to perform the rotation motion, and finally, the deceleration motion opposite to the input transmission direction is formed.
As shown in fig. 2, the input gear shaft 120 further includes a middle shaft section provided with a first gear tooth portion 122 and a first shaft section 123 coaxially connected to one end of the middle shaft section, the first shaft section 123 is located at one side of the first end cap 130, the diameter of the first shaft section 123 is smaller than that of the middle shaft section, a shaft sleeve 124 is provided on the first shaft section 123, a needle bearing 125 is provided between the shaft sleeve 124 and a central hole of the first end cap 130, a bevel gear 121 is sleeved on the first shaft section 123 and abuts against the shaft sleeve 124, a threaded hole is provided at an end of the first shaft section 123, and the bevel gear 121 is fixedly connected with the first shaft section 123 through a fastening bolt 126.
It should be noted that, the needle bearing 125 may be a needle bearing with a cage, or may be a needle bearing without a cage, which is not particularly limited in the embodiment of the present invention. In addition, the bevel gear 121 is fixedly connected with the first shaft section 123 through the fastening bolt 126, so that the bevel gear 121 is convenient to disassemble and assemble, and the bevel gears 121 with different types can be replaced according to different requirements, so that different reduction ratio requirements can be met.
As shown in fig. 2, the input gear shaft 120 further includes a second shaft section 127 coaxially connected to the other end of the intermediate shaft section, the second shaft section 127 is located at one side of the second end cap 140, the diameter of the second shaft section 127 is smaller than that of the intermediate shaft section, angular contact ball bearings 128 are disposed back-to-back or face-to-face on the second shaft section 127, and a fifth annular groove 129a and a sixth annular groove 129b are correspondingly disposed on the inner wall of the central hole of the second end cap 140 and the second shaft section 127, respectively, for axially positioning the angular contact ball bearings 128.
Specifically, the angular contact ball bearings 128 in a back-to-back or face-to-face pair are capable of bearing bi-directional axial loads, improving the stability of the input gear shaft 120. In addition, the inner wall of the central bore of the second end cap 140 is provided with a fifth annular groove 129a and the second shaft section 127 is provided with a sixth annular groove 129b. Wherein corresponding means that the fifth annular groove 129a and the sixth annular groove 129b are on the same assembly cross section so as to be axially positioned on one side of the diagonal contact ball bearing 128 and on the other side by means of the stepped cross section of the second shaft section 127 and the intermediate shaft section the diagonal contact ball bearing 128. In this way, the degree of freedom of the angular ball bearing 128 can be better limited by the self structure, the use of unnecessary parts is reduced, the cost is reduced, and the stability and the compactness of the reduction gear 100 are improved.
As shown in fig. 2, the ring gear 110 includes a pin gear portion 111, a first limiting portion 112 and a second limiting portion 113, the pin gear portion 111 is engaged with the swing gear 160, a first tapered roller bearing 114 and a mating washer 115 are provided between the first limiting portion 112 and the first end cap 130, a second tapered roller bearing 116 and a skeleton oil seal 117 are provided between the second limiting portion 113 and the second end cap 140, the mating washer 115 is provided inside the first tapered roller bearing 114, and the skeleton oil seal 117 is provided outside the second tapered roller bearing 116.
Specifically, as shown in fig. 2, the first tapered roller bearing 114 and the second tapered roller bearing 116 are disposed opposite to each other, so that a large axial load and a combined load (such as a bending moment generated by the self gravity of an external component or other acting force) mainly including a radial load can be received, and the stability of the reduction gear 100 is improved. In addition, the matched grinding washer 115 can better axially position the first tapered roller bearing 114, and the framework oil seal 117 provides a radial dynamic sealing function for the second end cover 140, so that the lubrication of internal components is more sufficient, and the influence of the external environment on the speed reducer 100 is reduced.
As shown in fig. 3, tooth grooves are formed between adjacent teeth of the needle tooth part 111, the cross section of the tooth grooves is in a concave circular arc shape, the tooth heights at two sides of the needle tooth are larger than the tooth heights in the middle, and the teeth 165 of the swing gear 160 are concave teeth.
Specifically, the tooth heights of two sides of each needle tooth are the same, the tooth heights of the middle are the same, the tooth heights of two sides are larger than the tooth heights of the middle, so that more lubricating grease can be stored on two sides of the needle tooth, more lubricating grease can be stored in the concave circular arc tooth grooves, and the lubrication in transmission and the reduction of the meshing temperature of tooth surfaces are facilitated. In addition, the teeth 165 of the swing gear 160 are concave teeth, so that the contact stress of the tooth surface can be effectively reduced, and the service life is longer than that of the traditional involute tooth profile.
As shown in fig. 1, the first end cap 130 is provided with a grease injection hole 139. Thus, the lubricating grease can more smoothly flow into the reduction gear 100, and the temperature during internal transmission can be effectively reduced. And maintenance operations such as adding lubricating grease in the later period are also facilitated, and maintenance time is saved.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (7)
1. The speed reducer is characterized by comprising an annular gear, an input gear shaft, a first end cover, a second end cover, a bevel gear, a crank shaft and a swing gear, wherein the input gear shaft penetrates through central holes of the first end cover and the second end cover and is movably connected with the central holes of the first end cover and the second end cover, the bevel gear is fixedly connected with one end of the input gear shaft, the input gear shaft comprises a first gear tooth part, the crank shaft comprises a second gear tooth part and at least two eccentric wheels, the first gear tooth part is meshed with the second gear tooth part, the swing gear comprises a plurality of through holes, the through holes are uniformly distributed around the center circumference of the swing gear, the eccentric wheels are respectively and movably connected with the swing gear through the through holes, two ends of the crank shaft are respectively and movably connected with the first end cover and the second end cover, the swing gear and the annular gear form a gear tooth difference less pair, and the second end cover comprises a connecting part for outputting torque and rotating speed; the input gear shaft further comprises a middle shaft section provided with a first gear tooth part and a first shaft section coaxially connected with one end of the middle shaft section, the first shaft section is positioned on one side of the first end cover, the diameter of the first shaft section is smaller than that of the middle shaft section, a shaft sleeve is arranged on the first shaft section, a needle bearing is arranged between the shaft sleeve and a central hole of the first end cover, a bevel gear is sleeved on the first shaft section and abuts against the shaft sleeve, a threaded hole is formed in the end part of the first shaft section, and the bevel gear is fixedly connected with the first shaft section through a fastening bolt;
the input gear shaft further comprises a second shaft section coaxially connected with the other end of the intermediate shaft section, the second shaft section is positioned on one side of the second end cover, the diameter of the second shaft section is smaller than that of the intermediate shaft section, angular contact ball bearings are arranged on the second shaft section back to back or face to face, and a fifth annular groove and a sixth annular groove are correspondingly arranged on the inner wall of a central hole of the second end cover and the second shaft section respectively and used for axially positioning the angular contact ball bearings; the first end cover is provided with a grease injection hole.
2. The reduction gear of claim 1, wherein the first end cap includes a plurality of first mounting holes and a plurality of first connecting holes, the first mounting holes are alternately spaced apart from the first connecting holes, the second end cap is provided with a plurality of second mounting holes and a plurality of second connecting holes, the second mounting holes are spaced apart from the second connection Kong Jiaoti, the first mounting holes are on the same axis as the second mounting holes, the first connecting holes are on the same axis as the second connecting holes, the first end cap and the second end cap are fixedly connected through pins penetrating through the first mounting holes and the second mounting holes, and two ends of the crank shaft are respectively arranged in the first connecting holes and the second connecting holes.
3. The reduction gear as claimed in claim 2, wherein a first needle roller cage assembly and a deep groove ball bearing are coaxially disposed between an end of the crank shaft adjacent to the first end cover and the first connecting hole, a first annular groove and a first annular protrusion are disposed on an inner wall of the first connecting hole, the first annular groove is disposed on an outer side of the first annular protrusion, a second annular groove is disposed on the crank shaft, the first annular groove and the second annular groove are correspondingly disposed, and the first annular groove, the first annular protrusion and the second annular groove are matched for axially positioning the first needle roller cage assembly and the deep groove ball bearing.
4. A reduction gear as claimed in claim 2 or claim 3, wherein a second needle roller cage assembly is provided between the end of the crank shaft adjacent the second end cap and the second connecting bore, a third annular groove and a second annular projection are provided on the inner wall of the second connecting bore, the third annular groove is provided on the outer side of the second annular projection, a fourth annular groove is provided on the crank shaft, and the third annular groove and the fourth annular groove are provided correspondingly, and the third annular groove, the second annular projection and the fourth annular groove cooperate to axially locate the second needle roller cage assembly.
5. The reduction gear as defined in claim 4, wherein a third needle roller cage assembly is disposed between the eccentric and the through bore.
6. The reduction gear according to claim 1, wherein the ring gear includes a pin tooth portion, a first limit portion, and a second limit portion, the pin tooth portion is engaged with the swing gear, a first tapered roller bearing and a mating washer are provided between the first limit portion and the first end cover, a second tapered roller bearing and a skeleton oil seal are provided between the second limit portion and the second end cover, the mating washer is provided inside the first tapered roller bearing, and the skeleton oil seal is provided outside the second tapered roller bearing.
7. The reduction gear according to claim 6, wherein tooth grooves are formed between adjacent needle teeth on the needle tooth portion, the cross section of each tooth groove is in a concave circular arc shape, tooth heights at two sides of the needle teeth are larger than tooth heights in the middle, and tooth teeth of the swing gear are concave teeth.
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| CN201910182874.6A CN109737187B (en) | 2019-03-11 | 2019-03-11 | Speed reducer |
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| CN201910182874.6A CN109737187B (en) | 2019-03-11 | 2019-03-11 | Speed reducer |
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|---|---|
| CN109737187A (en) | 2019-05-10 |
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Effective date of registration: 20210416 Address after: No.69, Feitian Avenue, Jiangning Airport Economic Development Zone, Nanjing City, Jiangsu Province Applicant after: Nanjing Nanchuan Intelligent Technology Co.,Ltd. Address before: No. 30 Houjiao Road, Jiangning District, Nanjing, Jiangsu Province, 210000 (Jiangning High-tech Park) Applicant before: NANJING HIGH SPEED GEAR MANUFACTURING Co.,Ltd. |
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