CN210859215U - Shaft system structure and electric scroll compressor with same - Google Patents
Shaft system structure and electric scroll compressor with same Download PDFInfo
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- CN210859215U CN210859215U CN201921568573.9U CN201921568573U CN210859215U CN 210859215 U CN210859215 U CN 210859215U CN 201921568573 U CN201921568573 U CN 201921568573U CN 210859215 U CN210859215 U CN 210859215U
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Abstract
A shaft system structure and an electric scroll compressor with the same are provided, wherein the shaft system structure comprises a motor rotor and a crankshaft penetrating and connected into the motor rotor; the motor rotor further comprises a first bearing, a second bearing and a third bearing, wherein the first bearing and the third bearing are respectively arranged at two ends of the crankshaft, and the second bearing is arranged between the first bearing and the motor rotor; the motor comprises a motor rotor, a crankshaft, a first bearing, a second bearing, a main balance block, an auxiliary balance block, an eccentric sleeve and a movable disc assembly, wherein the main balance block and the auxiliary balance block are arranged on two sides of the motor rotor respectively, the eccentric sleeve and the movable disc assembly are further arranged at one end of the crankshaft, the first bearing is sleeved in the eccentric sleeve, and the movable disc assembly is connected in the first bearing in. The beneficial effects of the utility model reside in that, the bent axle atress is even, and the compressor operation is stable, reduces the compressor and rotor swing phenomenon appears at the operation in-process. When the structural force balance and the moment balance of the shafting are within the range, the compressor runs stably, the noise and the vibration are small, the efficiency is low, and the reliability and the stability are high.
Description
Technical Field
The utility model relates to an electric scroll compressor technical field indicates a shafting structure and have this shafting structure's electric scroll compressor especially.
Background
The scroll compressor is a preferred compressor type in the present passenger vehicle due to the characteristics of small volume, light weight, high efficiency and the like, and is influenced by the structural characteristics of the scroll compressor, so that the requirement of the compressor on the whole shaft system in the operation process is extremely high. At present, the requirement of the compressor on the rotating speed is gradually increased, and particularly, the compressor has large noise vibration and high requirements on parts under high rotating speed. When the compressor runs, the shafting stress has great influence on the temperature property and the noise vibration of the compressor. When the shaft system is not designed properly, the life of the compressor is greatly reduced. Aiming at the problem of shafting stability, the electric scroll compressor and the shafting structure thereof are provided.
Most of the current electric scroll compressors have the following problems:
(1) the crankshaft and the rotor swing, which causes the compressor to have noise, large vibration, large power and poor performance;
(2) the shaft system is unreasonable in design, so that the stress of the crankshaft is uneven, the power of the compressor is high, and the service life of the compressor is reduced;
(3) the compressor shafting atress is improper, leads to compressor stability variation, and the reliability reduces.
SUMMERY OF THE UTILITY MODEL
The present invention is directed to a shaft system structure and an electric scroll compressor having the same, which can improve the compressor capacity and reduce the compressor power. The stability and the reliability of the compressor are improved. And greatly prolongs the service life of the compressor. The noise and vibration of the compressor are reduced.
In order to achieve the above purpose, the utility model adopts the following technical scheme:
a shafting structure comprises a motor rotor and a crankshaft penetrating through the motor rotor; the motor rotor further comprises a first bearing, a second bearing and a third bearing, wherein the first bearing and the third bearing are respectively arranged at two ends of the crankshaft, and the second bearing is arranged between the first bearing and the motor rotor; the motor comprises a motor rotor, a crankshaft, a first bearing, a second bearing, a main balance block, an auxiliary balance block, an eccentric sleeve and a movable disc assembly, wherein the main balance block and the auxiliary balance block are arranged on two sides of the motor rotor respectively, the eccentric sleeve and the movable disc assembly are further arranged at one end of the crankshaft, the first bearing is sleeved in the eccentric sleeve, and the movable disc assembly is connected in the first bearing in.
It should be noted that the first bearing, the second bearing and the third bearing are 3 stable points respectively.
The shafting structure is stressed to satisfy F1-m 1 × omega2r1；F2＝m2 ×ω2r2；F3＝m3×ω2r3；F4＝m4×ω2r4；
Wherein m1 is the mass of the movable disc assembly, m2 is the mass of the eccentric sleeve, m3 is the mass of the main balance weight 15, and m4 is the mass of the auxiliary balance weight; r1 is the distance from the center of mass of the movable disc assembly to the center of the shafting, r2 is the distance from the center of mass of the eccentric sleeve to the center of the shafting, r3 is the distance from the center of mass of the main balance weight to the center of the shafting, r4 is the distance from the center of mass of the auxiliary balance weight to the center of the shafting, and omega is the angular speed of the shafting.
The moment applied to the shafting structure satisfies the requirements of M1-F1 × L1, M2-F2 × L2, M3-F3 × L3, M4-F4 × L4;
wherein, L1 is the distance from the center of mass of the movable disc to the center of the bearing, and L2 is the distance from the center of mass of the eccentric sleeve to the center of the bearing; l3 is the distance from the main balance weight of the bearing to the center of the bearing, and L4 is the distance from the auxiliary balance weight to the center of the bearing.
It should be noted that the force balance of the shafting structure is as follows:
φ＝(F2+F3)/(F1+F4)；
the moment balance of the shafting structure is as follows:
η＝(M2+M4)/(M1+M3)。
it is noted that phi is not less than 0.3 and not more than 1.8, and η is not less than 0.3 and not more than η and not more than 1.8.
It should be noted that phi is 1, and η is 1.
The electric vortex compressor with shafting structure has the advantages of high stability, etc. phi is not less than 0.3 and not more than 1.8, and phi is not less than 0.3 and not more than η and not more than 1.8, and η is used in the electric vortex compressor.
It should be noted that phi is 1, and η is 1.
The beneficial effects of the utility model reside in that, the bent axle atress is even, and the compressor operation is stable, reduces the compressor and rotor swing phenomenon appears at the operation in-process. When the structural force balance and the moment balance of the shafting are within the range, the compressor runs stably, the noise and the vibration are small, the efficiency is low, and the reliability and the stability are high.
Drawings
FIG. 1 is a schematic view of the shafting structure of the present invention;
FIG. 2 is a schematic view of the shafting balance relationship of the present invention;
fig. 3 is a schematic structural view of an electric scroll compressor with a shafting structure according to the present invention.
Detailed Description
The present invention will be further described with reference to the accompanying drawings, and it should be noted that the following embodiments are based on the technical solution, and the detailed embodiments and the specific operation processes are provided, but the protection scope of the present invention is not limited to the embodiments.
As shown in fig. 1 and fig. 3, the present invention relates to a shafting structure, which includes a motor rotor 1 and a crankshaft 2 penetrating through the motor rotor 1; the motor rotor also comprises a first bearing 3, a second bearing 4 and a third bearing 5, wherein the first bearing 3 and the third bearing 5 are respectively arranged at two ends of the crankshaft 2, and the second bearing 4 is arranged between the first bearing 3 and the motor rotor 1; the two sides of the motor rotor 1 are respectively provided with a main balance weight 6 and an auxiliary balance weight 7, one end of the crankshaft 2 is further provided with an eccentric sleeve 8 and a movable disc assembly 9, the first bearing 3 is sleeved in the eccentric sleeve 8, and the movable disc assembly 9 is connected in the first bearing 3 in a penetrating mode.
Furthermore, the first bearing, the second bearing and the third bearing are respectively 3 stable points.
As shown in figure 2, the stress of the shafting structure satisfies F1-m 1 × omega2r1；F2＝m2×ω2r2；F3＝m3×ω2r3；F4＝m4×ω2r4；
Wherein m1 is the mass of the movable disc assembly, m2 is the mass of the eccentric sleeve, m3 is the mass of the main balance weight 15, and m4 is the mass of the auxiliary balance weight; r1 is the distance from the center of mass of the movable disc assembly to the center of the shafting, r2 is the distance from the center of mass of the eccentric sleeve to the center of the shafting, r3 is the distance from the center of mass of the main balance weight to the center of the shafting, and r4 is the distance from the center of mass of the auxiliary balance weight to the center of the shafting; omega is the angular speed of the shafting.
As shown in fig. 2, the moment applied to the shafting structure satisfies M1 ═ F1 × L1, M2 ═ F2 × L2, M3 ═ F3 × L3, M4 ═ F4 × L4;
wherein, L1 is the distance from the center of mass of the movable disc to the center of the bearing, and L2 is the distance from the center of mass of the eccentric sleeve to the center of the bearing; l3 is the distance from the main balance weight of the bearing to the center of the bearing, and L4 is the distance from the auxiliary balance weight to the center of the bearing.
It should be noted that the force balance of the shafting structure is as follows:
φ＝(F2+F3)/(F1+F4)；
the moment balance of the shafting structure is as follows:
η＝(M2+M4)/(M1+M3)。
it is noted that phi is not less than 0.3 and not more than 1.8, and η is not less than 0.3 and not more than η and not more than 1.8.
It should be noted that when the value of phi is 1, and when the value of η is 1, the preferred parameter of the shafting structure of the utility model is obtained.
The electric vortex compressor with shafting structure has the advantages of high stability, etc. phi is not less than 0.3 and not more than 1.8, and phi is not less than 0.3 and not more than η and not more than 1.8, and η is used in the electric vortex compressor.
Various corresponding changes and modifications can be made by those skilled in the art according to the above technical solutions and concepts, and all such changes and modifications should be included in the protection scope of the present invention.
Claims (8)
1. A shafting structure is characterized by comprising a motor rotor and a crankshaft penetrating through the motor rotor; the motor rotor further comprises a first bearing, a second bearing and a third bearing, wherein the first bearing and the third bearing are respectively arranged at two ends of the crankshaft, and the second bearing is arranged between the first bearing and the motor rotor; the motor comprises a motor rotor, a crankshaft, a first bearing, a second bearing, a main balance block, an auxiliary balance block, an eccentric sleeve and a movable disc assembly, wherein the main balance block and the auxiliary balance block are arranged on two sides of the motor rotor respectively, the eccentric sleeve and the movable disc assembly are further arranged at one end of the crankshaft, the first bearing is sleeved in the eccentric sleeve, and the movable disc assembly is connected in the first bearing in.
2. The shafting structure of claim 1, wherein the first bearing, the second bearing and the third bearing are 3 stable points respectively.
3. The shafting structure according to claim 1, wherein the shafting structure is stressed to satisfy:
F1＝m1×ω2r1；
F2＝m2×ω2r2；
F3＝m3×ω2r3；
F4＝m4×ω2r4；
wherein m1 is the mass of the movable disc assembly, m2 is the mass of the eccentric sleeve, m3 is the mass of the main balance weight 15, and m4 is the mass of the auxiliary balance weight; r1 is the distance from the center of mass of the movable disc assembly to the center of the shafting, r2 is the distance from the center of mass of the eccentric sleeve to the center of the shafting, r3 is the distance from the center of mass of the main balance weight to the center of the shafting, r4 is the distance from the center of mass of the auxiliary balance weight to the center of the shafting, and omega is the angular speed of the shafting.
4. The shafting structure according to claim 3, wherein the torque applied to said shafting structure satisfies the following requirements:
M1＝F1×L1；
M2＝F2×L2；
M3＝F3×L3；
M4＝F4×L4；
wherein, L1 is the distance from the center of mass of the movable disc to the center of the bearing, and L2 is the distance from the center of mass of the eccentric sleeve to the center of the bearing; l3 is the distance from the main balance weight of the bearing to the center of the bearing, and L4 is the distance from the auxiliary balance weight to the center of the bearing.
5. The shafting structure according to claim 4, wherein the force balance of the shafting structure is:
φ＝(F2+F3)/(F1+F4)；
the moment balance of the shafting structure is as follows:
η＝(M2+M4)/(M1+M3)。
6. the shafting structure according to claim 5, wherein phi is 0.3-1.8, and phi is η -0.3- η -1.8.
7. The shafting structure according to claim 6, wherein φ has a value of 1 and η has a value of 1.
8. An electric scroll compressor comprising a shafting structure according to any one of claims 1 to 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921568573.9U CN210859215U (en) | 2019-09-20 | 2019-09-20 | Shaft system structure and electric scroll compressor with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921568573.9U CN210859215U (en) | 2019-09-20 | 2019-09-20 | Shaft system structure and electric scroll compressor with same |
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| Publication Number | Publication Date |
|---|---|
| CN210859215U true CN210859215U (en) | 2020-06-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921568573.9U Active CN210859215U (en) | 2019-09-20 | 2019-09-20 | Shaft system structure and electric scroll compressor with same |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114183347A (en) * | 2021-12-17 | 2022-03-15 | 珠海格力电器股份有限公司 | Scroll compressor |
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2019
- 2019-09-20 CN CN201921568573.9U patent/CN210859215U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114183347A (en) * | 2021-12-17 | 2022-03-15 | 珠海格力电器股份有限公司 | Scroll compressor |
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