CN215059345U - Novel gear corner transmission - Google Patents

Abstract

The utility model relates to a corner derailleur technical field discloses a novel gear corner derailleur, including well transmission case, the right part of well transmission case is equipped with power input helical angle pinion, sun gear axle upper portion cover is equipped with spiral basin tooth flange, be equipped with on the spiral basin tooth flange with input helical angle pinion meshing spiral basin tooth, the bottom of well transmission case is connected with fixed ring gear, the inboard of well transmission bottom of the case portion is connected with the planet carrier, the inboard of planet carrier and the sub-unit connection of sun gear axle, be equipped with a plurality of planet overgear axles on the planet carrier, it crosses the ferryboat all to be equipped with the planet on a plurality of planet overplanes, be equipped with the external tooth on the sun gear axle, the ferryboat meshing is crossed with the planet to the external tooth, fixed ring gear also crosses the ferryboat meshing with the planet, the bottom of planet carrier is connected with the power take off main shaft. The device's operation has realized little big reduction ratio of volume, and reduction gear assembly space is also compacter simultaneously, and stability can promote to the life of derailleur has been increased.

Description

Novel gear corner transmission

Technical Field

The utility model relates to a derailleur technical field specifically is a novel gear corner derailleur.

Background

In the building industry, the dual-purpose lift transmission of people goods is widely used, and because the frequency of use of lift is higher, and operating time is longer, consequently to the life and the performance requirement of reduction gear just higher, if change and maintain the reduction gear in the life cycle, can cause long-time shut down or the waste of manpower and materials, also probably change in the high altitude, still can cause bigger potential safety hazard like this.

The prior art has the defects that 1, in a right-angle steering transmission planetary reducer, the interval of support bearings of an output main shaft is too short, the main shaft has poor stability and is easy to swing when being subjected to impact force and large force, the abrasion is also large, the noise is also large, and the factor causing short service life is one of the factors. 2. In addition, in order to reduce the structure of the planetary reducer in the prior art, a planetary disk and a cantilever shaft are adopted, a planetary transition gear is arranged on the cantilever shaft, the gear is also large in swing and poor in stability, is easy to wear and short in service life, and further increases of noise are aggravated. 3. The reduction ratio realized on the premise of the same volume and weight is smaller, and the application is not wide. 4. In the conventional speed reducer, because in the power transmission of the gear, the next-stage transmission ratio of the modulus is larger than the previous-stage transmission ratio, the size and the weight are increased, and the dead weight can be increased when a plurality of speed reducers are used simultaneously, so that the dead weight is not beneficial to the improvement of the load tonnage of the lifter under the same power and is reduced to some extent.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a novel gear corner derailleur to thereby the reduction gear ratio is less, the noise is great, the big unstability of swing leads to the big problem of wearing and tearing when passing power to the variable speed that proposes in solving above-mentioned background art.

In order to realize the purpose of the utility model, the utility model adopts the technical proposal that: a novel gear corner transmission comprises a middle transmission case, wherein an input spiral angle gear shaft connected with an inner cavity and an outer cavity is arranged at the right part of the middle transmission case, a spiral basin gear end cover is detachably connected to the top of the middle transmission case, a sun gear shaft extending out of the bottom of the middle transmission case is connected to the spiral basin gear end cover, a spiral basin gear connecting flange is sleeved on the upper part of the sun gear shaft, spiral basin gears meshed with the input spiral angle gear shaft are arranged on the spiral basin gear connecting flange, a fixed inner gear ring is connected to the bottom of the middle transmission case, an output bearing box is connected to one end, far away from the middle transmission case, of the fixed inner gear ring, a planet carrier is connected to the inner side of the bottom of the middle transmission case through a first rolling bearing, the inner side of the planet carrier is connected with the lower part of the sun gear shaft through a second rolling bearing, a plurality of planet passing shafts are arranged on the planet carrier, and planet passing ferryboards are arranged on the planet passing shafts, and the sun gear shaft is provided with external teeth close to the second rolling bearing, the external teeth are meshed with the planet transition wheel, the fixed inner gear ring is also meshed with the planet transition wheel, and the bottom end of the planet carrier is detachably connected with an output main shaft penetrating through the output bearing box.

Preferably, the input spiral angle gear shaft and the spiral basin gear form right-angle transmission.

Preferably, the input helical angle gear shaft and the middle transmission case are supported by an input angle gear shaft support bearing; the sun gear shaft and the middle transmission case are supported by a spiral basin tooth supporting bearing; the output main shaft and the output bearing box are supported by an output stress bearing.

Preferably, one end of the fixed inner gear ring, which is far away from the middle transmission case, is connected with a connection box, a second fixed inner gear ring is arranged at the bottom of the connection box, an output bearing box is connected at the bottom of the second fixed inner gear ring, the inner side of the connection box is connected with a second planet carrier through a third rolling bearing, the inner side of the second planet carrier is connected to a second sun gear shaft through a fourth rolling bearing, a plurality of second planet wheel shafts are arranged on the second planet carrier, second planet transition wheels are arranged on the second planet wheel shafts, second outer teeth are arranged on the second sun gear shaft and meshed with the second planet transition wheels, the second fixed inner gear ring is also meshed with the second planet transition wheels, and a second output main shaft penetrating through the output bearing box is detachably connected to the bottom end of the second planet carrier.

The beneficial effects of the utility model are concentrated and are embodied in: 1. the transmission can be performed at a corner of 90 degrees, so that the installation is convenient and the occupied space of the installation is reduced. 2. The reduction ratio is large, because of multi-path gear transmission (multi-path, namely engagement of a plurality of planet transition wheels with the sun gear shaft and the fixed inner gear ring), the module of the gear can be reduced, the number of teeth of the gear is increased under the same size, and the transmission ratio is increased. 3. Ultra-low noise: when the front input high-speed rotation is carried out, external tooth transmission (ultra-silence) with relatively high precision is adopted, and finally, when the output is carried out (at low rotating speed), gear ring transmission with relatively low precision is adopted, and in addition, all transmission shafts are positioned by mounting bearings as far as possible and as far as possible (the second-stage sun gear and the more than second-stage sun gear of the existing heavy planetary transmission have no bearings, the gear shaft is freely suspended in the middle up and down), so that the stability is improved, and the noise is reduced to some extent. The noise can be relatively reduced in the similar planetary speed reducer under the double action. 4. High torque: under the condition of the same size, the larger the reduction ratio is (the output mechanical torque is approximately equal to the input moment x of the motor by the reduction multiple (namely the reduction ratio)), the larger the output reduction ratio is, and the larger the output torque is. 6. High stability and high durability: all shafts adopt the largest wheelbase and heavy-duty bearings as far as possible, so that the shafts have good stability, and the service lives of the gears and the shafts are prolonged; meanwhile, the low noise can reduce the abrasion of the gear or the bearing and can also prolong the service life of the gear and the shaft.

Drawings

Fig. 1 is a cross-sectional view of the present invention;

FIG. 2 is a schematic diagram of a transmission according to a second embodiment of the present invention;

FIG. 3 is a schematic diagram of a transmission according to a third embodiment of the present invention;

FIG. 4 is a schematic diagram of a transmission according to a fourth embodiment of the present invention;

FIG. 5 is a cross-sectional view of the present invention with increased number of transmission stages;

in the attached drawings, 1, a middle transmission case; 2. inputting a helical angular gear shaft; 3. a spiral bevel gear end cover; 4. a sun gear shaft; 5. the spiral bevel gear is connected with a flange; 6. spiral basin teeth; 8. fixing the inner gear ring; 9. an output bearing housing; 10. a first rolling bearing; 11. a planet carrier; 12. a second rolling bearing; 13. a planet wheel shaft; 14. a planet transition wheel; 15. an output spindle; 16. inputting a sealed bearing cap; 17. an output sealed bearing cap; 18. a seal member; 19. an input angle gear shaft support bearing; 20. the spiral basin teeth support the bearing; 21. an output stressed bearing; 22. a connecting box; 23. a second fixed ring gear; 24. a second planet carrier; 25. a second sun gear shaft; 26. a second planetary wheel shaft; 27. a second planetary transition wheel.

Detailed Description

All of the features disclosed in this specification, or all of the steps in any method or process so disclosed, may be combined in any combination, except combinations of features and/or steps that are mutually exclusive.

Any feature disclosed in this specification (including any accompanying claims, abstract and drawings), may be replaced by alternative features serving equivalent or similar purposes, unless expressly stated otherwise. That is, unless expressly stated otherwise, each feature is only an example of a generic series of equivalent or similar features.

In the description of the present invention, it is to be understood that the terms "one end", "the other end", "the outside", "upper", "inside", "horizontal", "coaxial", "central", "end", "length", "outer end", etc. indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention.

Furthermore, in the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present invention, unless otherwise explicitly specified or limited, the terms "set", "coupled", "connected", "penetrating", "plugging", and the like are to be understood in a broad sense, and may be, for example, fixedly connected, detachably connected, or integrated; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

Example 1:

referring to fig. 1, a novel gear rotation angle transmission includes a middle transmission case 1, an input helical angle gear shaft 2 connected to an inner cavity and an outer cavity is disposed at the right portion of the middle transmission case 1, an end portion of the input helical angle gear shaft 2 located outside the middle transmission case 1 transmits input power through external teeth, and a bevel gear is disposed at an end portion of the input helical angle gear shaft 2 located inside the inner cavity of the middle transmission case 1 to output power. The top of the middle transmission case 1 is detachably connected with a spiral bevel gear end cover 3, and a plurality of screws are preferably connected in the detachable connection mode. The spiral basin tooth end cover 3 is connected with a sun gear shaft 4 extending out of the bottom of the middle transmission case 1, the connection can be realized by adopting a rolling bearing, and the sun gear shaft 4 adopts a shaft with a long wheelbase. The upper portion of the sun gear shaft 4 is sleeved with a spiral basin-shaped tooth connecting flange 5, spiral basin-shaped teeth 6 meshed with the input spiral angle gear shaft 2 are arranged on the spiral basin-shaped tooth connecting flange 5, and the spiral basin-shaped teeth 6 are driven bevel gears matched with bevel gears on the input spiral angle gear shaft 2. The arrangement of the spiral bevel gear connecting flange 5 enables the transmission to realize 90-degree corner transmission, and meanwhile, the convenience of equipment disassembly is improved. The bottom of the middle transmission case 1 is connected with a fixed inner gear ring 8, one end of the fixed inner gear ring 8, which is far away from the middle transmission case 1, is connected with an output bearing case 9, and the middle transmission case 1, the fixed inner gear ring 8 and the output bearing case 9 are fastened into a whole through a plurality of bolts. The inboard of well transmission case 1 bottom is connected with planet carrier 11 through first antifriction bearing 10, the inboard of planet carrier 11 passes through the sub-unit connection of second antifriction bearing 12 with sun gear shaft 4, and the connection effect can be realized to the use of first antifriction bearing 10 and second antifriction bearing 12, still can realize relative rotation simultaneously. According to the stress requirement, a plurality of planet wheel shafts 13 are arranged on the planet carrier 11, planet transition wheels 14 are arranged on the planet wheel shafts 13, external teeth are arranged on the sun gear shaft 4 and close to the second rolling bearing 12, the external teeth are meshed with the planet transition wheels 14, the fixed inner gear ring 8 is also meshed with the planet transition wheels 14, the planet transition wheels 14 rotate on the planet wheel shafts 13 due to the rotation of the sun gear shaft 4, and the planet wheel shafts 13 and the planet wheel carrier 11 are driven to make planet surrounding around the fixed inner gear ring 8 and the sun gear shaft 4 together due to the rotation of the planet transition wheels 14 because the fixed inner gear ring 8 is not moved, so that the speed reduction is realized. The bottom end of the planet carrier 11 is detachably connected with an output main shaft 15 penetrating through the output bearing box 9, so that the rotation of a planet transition wheel 14 on the planet carrier 11 drives the output main shaft 15 to rotate, and further, the power output is realized; the detachable connection is preferably a bolt connection; in addition, the carrier 11 and the output main shaft 15 may be formed as an integral structure for easy disassembly.

Specifically, in order to achieve output of relatively small torque, save gear cost and reduce installation space of the speed reducer, according to stress requirements, a planet carrier shaft 13 is arranged on the planet carrier 11, and a planet transition wheel 14 is arranged on the planet carrier shaft 13.

Specifically, for realizing the right angle transmission, better ensure the stability of equipment operation, the rational utilization assembly space, input spiral angle tooth axle 2 constitutes the right angle transmission with spiral basin tooth 6.

Specifically, in order to seal the transmission, an input sealing bearing cover 16 is arranged between the input helical angular gear shaft 2 and the middle transmission case 1, and an output sealing bearing cover 17 is arranged between the output main shaft 15 and the output bearing case 9. Further, the input seal bearing cover 16 and the output seal bearing cover 17 are provided with a sealing member 18. The sealed transmission can ensure good lubrication, so that the abrasion and the noise are further reduced, and the performance of the sealed transmission is more stable.

Specifically, the input helical angular gear shaft 2 and the middle transmission case 1 are supported by an input angular gear shaft support bearing 19; the sun gear shaft 4 and the middle transmission case 1 are supported by a spiral basin-shaped tooth supporting bearing 20; the output main shaft 15 and the output bearing box 9 are supported by an output force bearing 21. The transmission is better loaded by the input angle gear shaft support bearing 19, the spiral basin gear support bearing 20 and the output stressed bearing 21.

Specifically, referring to fig. 5, if necessary, under the original condition, the end of the fixed ring gear 8 away from the middle transmission case 1 is connected to a connection box 22, further, a second fixed ring gear 23 is disposed at the bottom of the connection box 22, the bottom of the second fixed ring gear 23 is connected to an output bearing box 9, the inner side of the connection box 22 is connected to a second planet carrier 24 through a third rolling bearing, the inner side of the second planet carrier 24 is connected to a second sun gear shaft 25 through a fourth rolling bearing, a plurality of second planet through-wheel shafts 26 are disposed on the second planet carrier 24, a plurality of second planet through-wheel shafts 26 are disposed on the second planet through-wheel shafts 27, second outer teeth are disposed on the second sun gear shaft 25, the second outer teeth are engaged with the second planet through-wheel 27, the second fixed ring gear 23 is also engaged with the second planet through-wheel 27, the bottom end of the second planet carrier 24 is detachably connected with a second output main shaft penetrating through the output bearing box 9, and an output stressed bearing 21 is arranged between the output bearing box 9 and the second output main shaft in a replaceable manner for supporting. The transmission ratio can be enlarged by replacing and newly adding components on the original basis.

The gear transmission and speed reduction principle of the embodiment is as follows:

1 level transmission speed reduction, the rotation of input helix angle tooth axle 2 drives spiral basin tooth 6 rotatory, and this level transmission makes the rotational speed of spiral basin tooth 6 reduce 2 ~ 6 times for the rotational speed of input helix angle tooth axle 2, has realized first speed reduction.

The 2-stage transmission is used for speed reduction, the spiral bevel gear 6 drives the sun gear shaft 4 to coaxially rotate, the sun gear shaft 4 drives the planet transition wheel 14 to do planet rotation in the fixed inner gear ring 8, the planet rotation of the planet transition wheel 14 enables the planet transition wheel shaft 13 to do planet rotation in the fixed inner gear ring 8, and meanwhile, the planet transition wheel shaft 13 also drives the output main shaft 15 to rotate, so that the secondary speed reduction is realized.

3-stage or more transmission speed reduction, referring to fig. 5 as a mode of increasing transmission ratio, the principle of 3-stage transmission speed reduction is the same as that of 2-stage transmission, and a second planetary transition wheel 27, a second planetary wheel shaft 26, a second fixed inner gear ring 23 and a second output main shaft which are matched with the output main shaft 15 are newly added at the lower part of the output main shaft to realize the speed reduction effect the same as that of 2-stage transmission, so that the principle and the structure are continuously superposed, 4-stage transmission or even more-stage transmission can be realized, and the transmission ratio is infinitely increased through the principle, so that third, fourth or even more speed reduction is realized.

Example 2:

referring to fig. 2, the present embodiment is a second transmission in two-stage transmission, and in the present embodiment, under the condition that other conditions (see embodiment 1) are not changed, in order to achieve output of medium torque, two planetary wheel shafts 13 are arranged on the planet carrier 11, and a planetary wheel transition 14 is arranged on each of the two planetary wheel shafts 13.

Example 3:

referring to fig. 3, the present embodiment is a third transmission in the two-stage transmission, and in the present embodiment, under the condition that other conditions (see embodiment 1) are not changed, in order to realize output of a large torque, three planetary transition wheels 13 are arranged on the planet carrier 11, and one planetary transition wheel 14 is arranged on each of the three planetary transition wheels 13.

Example 4:

referring to fig. 4, the present embodiment is a fourth transmission in two-stage transmission, and in the present embodiment, under the condition that other conditions (see embodiment 1) are not changed, in order to realize output of a large torque, four planetary transition wheels 13 are arranged on the planet carrier 11, and a planetary transition wheel 14 is arranged on each of the four planetary transition wheels 13.

In conclusion, the gear transmission can realize the simultaneous parallel transmission of multiple paths of gears through the implementation of each embodiment, thereby meeting the output power of different torques, ensuring heavy load and overload, reducing the occupied space for installation, realizing larger reduction ratio, and having lower noise and good stability. It should be noted that the embodiments only describe the deceleration implementation steps, and the acceleration requires the reverse operation.

The above, only be the specific implementation of the utility model discloses, nevertheless the utility model discloses a protection scope is not limited to this, and the shape and the structure of box and bearing are not only limited and only the form and the structure that mention in this patent, and what focus in this implementation case is mechanical transmission principle structure, and the box also can realize the transmission structure principle of this patent with bearing shape and connected mode suitable change. Any changes or substitutions which are not imaginable by the inventive work are intended to be covered by the scope of protection of the present invention. Therefore, the protection scope of the present invention should be subject to the protection scope defined by the claims.

Claims (4)

1. The novel gear corner transmission is characterized by comprising a middle transmission case (1), wherein an input spiral angle gear shaft (2) connected with an inner cavity and an outer cavity is arranged at the right part of the middle transmission case (1), a spiral basin gear end cover (3) is detachably connected to the top of the middle transmission case (1), a solar gear shaft (4) extending out of the bottom of the middle transmission case (1) is connected onto the spiral basin gear end cover (3), a spiral basin gear connecting flange (5) is sleeved on the upper part of the solar gear shaft (4), spiral basin gears (6) meshed with the input spiral angle gear shaft (2) are arranged on the spiral basin gear connecting flange (5), a fixed inner gear ring (8) is connected to the bottom of the middle transmission case (1), one end, far away from the middle transmission case (1), of the fixed inner gear ring (8) is connected with an output bearing case (9), and the inner side of the bottom of the middle transmission case (1) is connected with a planet carrier (11) through a first rolling bearing (10), the inner side of the planet carrier (11) is connected with the lower portion of the sun gear shaft (4) through a second rolling bearing (12), a plurality of planet wheel passing shafts (13) are arranged on the planet carrier (11), planet wheel passing shafts (14) are arranged on the planet wheel passing shafts (13), external teeth are arranged on the sun gear shaft (4) and close to the second rolling bearing (12), the external teeth are meshed with the planet wheel passing shafts (14), the fixed inner gear ring (8) is also meshed with the planet wheel passing shafts (14), and an output main shaft (15) penetrating through the output bearing box (9) is detachably connected to the bottom end of the planet carrier (11).

2. A new gear angle transmission according to claim 1, characterized in that the input helical angle shaft (2) and the helical bevel ring gear (6) form a right angle drive.

3. The novel gear angle transmission according to claim 1, characterized in that the input helical-pitch shaft (2) and the intermediate transmission case (1) are supported by an input helical-pitch shaft support bearing (19); the sun gear shaft (4) and the middle transmission case (1) are supported by a spiral bevel gear support bearing (20); the output main shaft (15) and the output bearing box (9) are supported by an output stress bearing (21).

4. The novel gear corner transmission according to any one of claims 1-3, wherein one end of the fixed ring gear (8) away from the middle transmission case (1) is connected with a connecting box (22), a second fixed ring gear (23) is arranged at the bottom of the connecting box (22), an output bearing box (9) is connected at the bottom of the second fixed ring gear (23), the inner side of the connecting box (22) is connected with a second planet carrier (24) through a third rolling bearing, the inner side of the second planet carrier (24) is connected with a second sun gear shaft (25) through a fourth rolling bearing, a plurality of second planet through gear shafts (26) are arranged on the second planet through gear shaft (24), a plurality of second planet through gear shafts (26) are provided with second planet through-wheels (27), and second outer teeth are arranged on the second sun gear shaft (25), the second outer teeth are meshed with a second planet transition wheel (27), the second fixed inner gear ring (23) is also meshed with the second planet transition wheel (27), and the bottom end of the second planet carrier (24) is detachably connected with a second output main shaft penetrating through an output bearing box (9).

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