CN213017520U - Single-stage large-speed-ratio tower-type planet row speed reducer - Google Patents
Single-stage large-speed-ratio tower-type planet row speed reducer Download PDFInfo
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- CN213017520U CN213017520U CN202021304306.3U CN202021304306U CN213017520U CN 213017520 U CN213017520 U CN 213017520U CN 202021304306 U CN202021304306 U CN 202021304306U CN 213017520 U CN213017520 U CN 213017520U
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Abstract
The embodiment of the utility model discloses reduction gear is arranged to tower planet of big velocity ratio of single-stage, include: the planetary gear set comprises a sun gear, at least two pairs of tower-type planetary gears, an inner gear ring, a planetary frame, an input shaft, an output shaft and a shell; the sun gear is positioned in the center of the planetary frame and is parallel to the axis of the tower-type planetary gear; each tower-type planetary gear consists of a first planetary gear and a second planetary gear which are rigidly connected; each first planetary gear is arranged in layers and is meshed with the sun gear; the number of the first planet gears in each layer is the same; the second planet gears are arranged on the same layer and are meshed with the inner gear ring, and the reference circle diameter of the first planet gear is larger than that of the second planet gear; the sun wheel is used as a power input end and is rigidly connected with the input shaft, and the planet frame is used as a power output end and is connected with the output shaft. By adopting the technical scheme, the problem of interference in arrangement of the planetary gear of the large-speed-ratio single-stage planetary gear and the problem of overlarge stress on the sun gear caused by too small sun gear are solved.
Description
Technical Field
The utility model relates to a reduction gear technical field, concretely relates to tower planet row's reduction gear of big velocity ratio of single-stage.
Background
In the current industrial production, the demand for the speed reducer is higher and higher, and for the field of new energy commercial vehicle speed reducers, the requirements are that the speed reduction ratio is large, the weight is light, the bearing capacity is strong, the precision is high, the manufacturing is simple, and the price is moderate.
The speed reducer used by the commercial vehicle with the new energy source at present mainly comprises a planetary gear speed reducer and a parallel shaft speed reducer. The planetary reducer of the planetary gear reducer is widely applied to the field of new energy commercial vehicles due to the advantages of small volume, high transmission efficiency, wide reduction range, high precision, long service life and the like. However, the traditional planetary gear reducer usually selects a multi-stage transmission scheme at a large reduction ratio, and the multi-stage transmission scheme has the disadvantages of multiple parts, complex processing and large volume. The single-stage scheme is easy to cause the problem of planet wheel arrangement interference and the problem of overlarge stress on the sun wheel due to the fact that the sun wheel is too small and does not accord with adjacent conditions.
SUMMERY OF THE UTILITY MODEL
The embodiment of the utility model discloses reduction gear is arranged to tower planet of big velocity ratio of single-stage has solved big velocity ratio single-stage planetary gear planet wheel and has arranged interference problem and sun gear too little, the too big problem of sun gear teeth atress that leads to.
In a first aspect, the embodiment of the utility model discloses tower planet row's reduction gear of big velocity ratio of single-stage, this reduction gear includes: the planetary gear set comprises a sun gear, at least two pairs of tower-type planetary gears, an inner gear ring, a planetary frame, an input shaft, an output shaft and a shell; wherein the content of the first and second substances,
the sun gear is positioned in the center of the planetary frame and is parallel to the axis of the tower-type planetary gear;
each tower-type planetary gear consists of a first planetary gear and a second planetary gear which are rigidly connected;
each first planetary gear is arranged in layers and meshed with the sun gear; the number of the first planet gears in each layer is the same; the second planet gears are arranged on the same layer and are meshed with the inner gear ring, the number of teeth of the first planet gears is greater than that of teeth of the second planet gears, and the reference circle diameter of the first planet gears is greater than that of the second planet gears;
the inner gear ring is used as a fixed end and is rigidly connected with the shell,
the sun wheel is used as a power input end and is rigidly connected with the input shaft, and the planet frame is used as a power output end and is connected with the output shaft.
Optionally, in a direction along the output shaft, each of the first planetary gears is arranged in two staggered layers, and comprises a front first planetary gear close to the input shaft and a rear first planetary gear far away from the input shaft;
wherein at least one layer of first planet gears is located between the ring gear and the planet frame.
Optionally, each layer of the first planet gears is located between the inner gear ring and the planet frame;
the axial length of the tower-type planetary gear formed by the front first planetary gear and the corresponding second planetary gear is smaller than that of the tower-type planetary gear formed by the rear first planetary gear and the corresponding second planetary gear.
Optionally, the first planetary gear and the second planetary gear are distributed in a ring shape and are provided with four.
Optionally, the first planet gears are arranged on two sides of the inner gear ring;
the axial length of the tower-type planetary gear formed by the front first planetary gear and the corresponding second planetary gear is equal to the axial length of the tower-type planetary gear formed by the rear first planetary gear and the corresponding second planetary gear.
Optionally, the first planet gear and the second planet gear are distributed in a ring shape and are provided with six.
The embodiment of the utility model provides a technical scheme arranges through dividing into two-layer or multilayer with the first planetary gear in the tower planetary gear, has solved big velocity ratio single stage planetary gear planet wheel and has arranged the interference problem to and because the too big problem of sun gear teeth atress that the sun gear leads to too little, and the velocity ratio is too big, needs carry out multi-stage drive's problem. Furthermore, the embodiment of the utility model provides a multiple arrangement form can adapt to multiple reduction gear assembly installation condition.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained according to these drawings without creative efforts.
Fig. 1a is a side view of a single-stage large-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention;
fig. 1b is a front view of a single-stage large-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention;
fig. 1c is an axial view of a single-stage large-speed-ratio tower-type planetary gear reducer according to an embodiment of the present invention;
fig. 1d is a transmission diagram of a single-stage large-speed-ratio tower-type planetary gear reducer according to an embodiment of the present invention;
fig. 2a is a side view of another single-stage high-speed-ratio tower-type planetary reduction gear according to an embodiment of the present invention;
fig. 2b is a front view of another single-stage high-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention;
fig. 2c is an axial view of another single-stage large-speed-ratio tower-type planetary reduction gear according to an embodiment of the present invention;
FIG. 2d is a schematic transmission diagram of another single-stage high-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention;
fig. 3a is a side view of another single-stage high-speed-ratio tower-type planetary reduction gear according to an embodiment of the present invention;
fig. 3b is a front view of another single-stage high-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention;
fig. 3c is an axial view of another single-stage high-speed-ratio tower-type planetary reduction gear according to an embodiment of the present invention;
fig. 3d is a schematic transmission diagram of another single-stage high-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. 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.
Example one
Referring to fig. 1a to 1d, fig. 1a is a side view of a single-stage large-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention; fig. 1b is a front view of a single-stage large-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention; fig. 1c is an axial view of a single-stage large-speed-ratio tower-type planetary gear reducer according to an embodiment of the present invention; fig. 1d is a transmission diagram of a single-stage large-speed-ratio tower-type planetary gear reducer provided by the embodiment of the present invention. The embodiment of the utility model provides a reduction gear can be applied to on the new forms of energy commercial car.
As shown in fig. 1a, 1b, 1c and 1d, the embodiment of the present invention provides a speed reducer, including: a sun gear 1, at least two pairs of tower planet gears, an inner gear ring 4, a planet frame 5, an input shaft 6, an output shaft 7 and a housing (not shown in fig. 1a-1 d); wherein the content of the first and second substances,
the sun gear 1 is positioned in the center of the planet frame 5 and is parallel to the axis of the tower type planet gear; each tower planet gear is composed of a first planet gear and a second planet gear which are rigidly connected. Each first planetary gear is arranged in layers and is meshed with the sun gear 1; the number of the first planet gears in each layer is the same; the second planet gears are arranged in the same layer and are all meshed with the inner gear ring 4. The number of teeth of the first planetary gear is greater than that of the teeth of the second planetary gear, and the reference circle diameter of the first planetary gear is greater than that of the second planetary gear; the inner gear ring 4 is rigidly connected with the shell as a fixed end, the sun gear 1 is rigidly connected with the input shaft 6 as a power input end, and the planet frame 5 is connected with the output shaft 7 as a power output end.
For example, the first planetary gears may be arranged in a staggered manner in two layers or in multiple layers. Specifically, each first planetary gear is located on one side of the ring gear, and is arranged in two layers in front and back between the ring gear 4 and the planet frame 5 along the direction of the output shaft. All the second planet gears are arranged in the same layer and are meshed with the inner gear ring 4. As shown in fig. 1a to 1d, the first planetary gears include a front first planetary gear 21 close to the input shaft and a rear first planetary gear 22 far from the input shaft in a direction along the output shaft, and both the front first planetary gear 21 and the rear first planetary gear 22 are meshed with the sun gear 1. Of all the second planet gears, as shown in fig. 1a-1d, rigidly connected to the front first planet gear 21 is a second planet gear 31, both of which form a tower planet gear; rigidly connected to the rear first planet gears 22 are second planet gears 32, which form a planetary gear tower. The second planet gears 31 and the second planet gears 32 are both meshed with the inner gear ring, and the axial length of the tower-type planet gear formed by the rear first planet gear 22 and the corresponding second planet gear 32 is greater than the axial length of the tower-type planet gear formed by the front first planet gear 21 and the corresponding second planet gear 31. The embodiment is arranged to solve the problems of interference of a single-stage planetary gear and planet wheel arrangement with a large speed ratio, such as a ratio range of 16-25, and overlarge stress on the sun gear due to too small sun gear.
For example, the first planet gears and the second planet gears are distributed in a ring shape, and the number of the first planet gears and the second planet gears is not limited in this embodiment. As shown in fig. 1a, 1b, 1c and 1d, the number of second planet gears with which the first planet gears are rigidly coupled is preferably four, so that two pairs of planetary gears are formed.
As another alternative, on the basis of the above embodiment, the number of the tower type planetary gears can be increased to bear larger torque. For example, the number of first planet gears and second planet gears rigidly linked thereto can also be preferably set to six, thereby forming three pairs of planetary gears.
Referring to fig. 2a to 2d, in which, fig. 2a is a side view of another single-stage large-speed-ratio tower-type planetary gear set reducer provided in an embodiment of the present invention; fig. 2b is a front view of another single-stage high-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention; fig. 2c is an axial view of another single-stage large-speed-ratio tower-type planetary reduction gear according to an embodiment of the present invention; fig. 2d is a schematic transmission diagram of another single-stage large-speed-ratio tower-type planetary gear reducer according to an embodiment of the present invention. As shown in figures 2a to 2d,
the sun gear 1 is positioned in the center of the planet frame 5 and is parallel to the axis of the tower type planet gear; each tower planet gear is composed of a first planet gear and a second planet gear which are rigidly connected. The number of teeth of the first planetary gear is greater than that of the teeth of the second planetary gear, and the reference circle diameter of the first planetary gear is greater than that of the second planetary gear; the ring gear 4 is rigidly connected as a fixed end to a housing (not shown in fig. 2a to 2 d), the sun gear 1 as a power input is rigidly connected to an input shaft 6, and the planet carrier 5 as a power output is connected to an output shaft 7. The first planetary gears include a front first planetary gear 21 close to the input shaft and a rear first planetary gear 22 far from the input shaft in a direction along the output shaft, and both the front first planetary gear 21 and the rear first planetary gear 22 are meshed with the sun gear 1. Among all the second planet gears, shown in fig. 2a-2d, rigidly connected to the front first planet gear 21 is a second planet gear 31, both of which form a tower planet gear; rigidly connected to the rear first planet gears 22 are second planet gears 32, which form a planetary gear tower. The axial length of the stepped planetary gear formed by the rear first planetary gear 22 and the second planetary gear 32 corresponding thereto is longer than the axial length of the stepped planetary gear formed by the front first planetary gear 21 and the second planetary gear 31 corresponding thereto. The second planet gears 31 and the second planet gears 32 are arranged in the same layer, and are both meshed with the ring gear 4,
as another alternative, the first planetary gears may be disposed in a two-tiered arrangement on both sides of the ring gear. Referring to fig. 3a to 3d, in which, fig. 3a is a side view of another single-stage large-speed-ratio tower-type planetary gear set reducer provided in the embodiment of the present invention; fig. 3b is a front view of another single-stage high-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention; fig. 3c is an axial view of another single-stage high-speed-ratio tower-type planetary reduction gear according to an embodiment of the present invention; fig. 3d is a schematic transmission diagram of another single-stage high-speed-ratio tower-type planetary gear set reducer according to an embodiment of the present invention. As shown in figures 3a to 3d,
the sun gear 1 is positioned in the center of the planet frame 5 and is parallel to the axis of the tower type planet gear; each tower planet gear is composed of a first planet gear and a second planet gear which are rigidly connected. Each first planetary gear is arranged in layers and is meshed with the sun gear 1; the number of the first planet gears in each layer is the same; the second planet gears are arranged in the same layer and are all meshed with the inner gear ring 4. The number of teeth of the first planetary gear is greater than that of the teeth of the second planetary gear, and the reference circle diameter of the first planetary gear is greater than that of the second planetary gear; the ring gear 4 is rigidly connected as a fixed end to a housing (not shown in fig. 3a to 3 d), the sun gear 1 is rigidly connected as a power input to an input shaft 6, and the planet carrier 5 is connected as a power output to an output shaft 7. The first planet gears comprise, in the direction along the output shaft, a front first planet gear 21 close to the input shaft and a rear first planet gear 22 remote from the input shaft. The front first planet gears 21 and the rear first planet gears 22 are arranged in two layers on two sides of the internal gear ring 4, the front first planet gears 21 and the rear first planet gears 22 are in a symmetrical structure with the internal gear ring 4 as a symmetrical shaft, and both the front first planet gears and the rear first planet gears are meshed with the sun gear 1; the number of the front first planetary gears 21 and the rear first planetary gears 22 in each layer is the same. Among all the second planet gears, shown in fig. 3a-3d, rigidly connected to the front first planet gear 21 is a second planet gear 31, both of which form a tower planet gear; rigidly connected to the rear first planet gears 22 are second planet gears 32, which form a planetary gear tower. The second planet gears 31 and the second planet gears 32 are both meshed with an inner gear ring, and the axial length of the tower-type planet gear formed by the rear first planet gear 22 and the corresponding second planet gear 32 is equal to the axial length of the tower-type planet gear formed by the front first planet gear 21 and the corresponding second planet gear 31. In addition, each first planetary gear and each second planetary gear are distributed in a ring shape, and the number of the first planetary gears and the second planetary gears is not specifically limited herein. Preferably, as shown in fig. 3a, 3b, 3c and 3d, the number of the first planetary gears and the number of the second planetary gears rigidly linked therewith are six, respectively, so as to form three pairs of planetary gears of a planetary tower type.
The embodiment of the utility model provides a reduction gear, through dividing into two-layer or multilayer with the first planetary gear in the tower planetary gear and arranging, solved big velocity ratio single stage planetary gear planet wheel and arranged the interference problem to and because the too big problem of sun gear teeth atress that leads to of sun gear, and the velocity ratio is too big, need carry out multi-stage drive's problem. Furthermore, the embodiment of the utility model provides a multiple arrangement form can adapt to multiple reduction gear assembly installation condition.
It should be noted that the foregoing is only a preferred embodiment of the present invention and the technical principles applied. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail with reference to the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the scope of the present invention.
Claims (6)
1. The utility model provides a tower planet row of reduction gear of single-stage big velocity ratio which characterized in that includes: the planetary gear set comprises a sun gear, at least two pairs of tower-type planetary gears, an inner gear ring, a planetary frame, an input shaft, an output shaft and a shell; wherein the content of the first and second substances,
the sun gear is positioned in the center of the planetary frame and is parallel to the axis of the tower-type planetary gear;
each tower-type planetary gear consists of a first planetary gear and a second planetary gear which are rigidly connected;
each first planetary gear is arranged in layers and meshed with the sun gear; the number of the first planet gears in each layer is the same; the second planet gears are arranged on the same layer and are meshed with the inner gear ring, the number of teeth of the first planet gears is greater than that of teeth of the second planet gears, and the reference circle diameter of the first planet gears is greater than that of the second planet gears;
the inner gear ring is used as a fixed end and is rigidly connected with the shell,
the sun wheel is used as a power input end and is rigidly connected with the input shaft, and the planet frame is used as a power output end and is connected with the output shaft.
2. A reducer according to claim 1, in which the first planet gears are arranged staggered in two levels in a direction along the output shaft, including a forward first planet gear closer to the input shaft and a rearward first planet gear further from the input shaft;
wherein at least one layer of first planet gears is located between the ring gear and the planet frame.
3. A decelerator according to claim 2, wherein each of the layers of the first planet gears is located between the annulus gear and the planet frame;
the axial length of the tower-type planetary gear formed by the front first planetary gear and the corresponding second planetary gear is smaller than that of the tower-type planetary gear formed by the rear first planetary gear and the corresponding second planetary gear.
4. The reducer according to claim 1, wherein said first planetary gears and said second planetary gears are distributed in a ring shape and are provided in a number of four.
5. A decelerator according to claim 2, wherein the first planet gears are arranged on either side of the annulus gear;
the axial length of the tower-type planetary gear formed by the front first planetary gear and the corresponding second planetary gear is equal to the axial length of the tower-type planetary gear formed by the rear first planetary gear and the corresponding second planetary gear.
6. A reducer according to claim 5, in which the first and second planet gears are distributed in the shape of a ring, there being six each.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111734789A (en) * | 2020-07-06 | 2020-10-02 | 南京清研易为新能源动力有限责任公司 | Single-stage large-speed-ratio tower-type planet row speed reducer |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111734789A (en) * | 2020-07-06 | 2020-10-02 | 南京清研易为新能源动力有限责任公司 | Single-stage large-speed-ratio tower-type planet row speed reducer |
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