CN212508820U - Flexible eccentric mechanism of scroll compressor - Google Patents
Flexible eccentric mechanism of scroll compressor Download PDFInfo
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- CN212508820U CN212508820U CN202020475390.9U CN202020475390U CN212508820U CN 212508820 U CN212508820 U CN 212508820U CN 202020475390 U CN202020475390 U CN 202020475390U CN 212508820 U CN212508820 U CN 212508820U
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Abstract
The utility model provides a flexible eccentric mechanism of a scroll compressor, which relates to the technical field of scroll compressors and comprises an eccentric wheel, an eccentric shaft and a driving pin; the eccentric wheel comprises a driving shaft, wherein first eccentric holes distributed along the axial direction of the driving shaft are formed in the driving shaft; the eccentric shaft is provided with second eccentric holes which are distributed along the axial direction of the eccentric shaft; one end of the driving pin is inserted into the first eccentric hole, and the other end of the driving pin is inserted into the second eccentric hole; the connecting lines of the first central point O1 of the driving shaft, the second central point O2 of the first eccentric hole and the third central point O3 of the eccentric shaft form a triangle, and the included angles of the triangle are all constant values. The utility model provides a scroll compressor's flexible eccentric mechanism, on guaranteeing the moderate basis of contact force between conjugate point department's driving disk vortex line and the quiet dish vortex line, simplify flexible eccentric mechanism's design process, raise the efficiency.
Description
Technical Field
The utility model relates to a scroll compressor technical field particularly, relates to a flexible eccentric mechanism of scroll compressor.
Background
The radial seal between the movable and fixed disks of the existing electric scroll compressor usually adopts a flexible eccentric mechanism, and the flexible eccentric mechanism has the advantage of reducing pressing force on the basis of ensuring the radial seal and stability of the movable and fixed disks on a scroll line, thereby reducing abrasion and power consumption.
Specifically, the compression mechanism of the electric scroll compressor is that a sealed cavity is formed by a movable disc vortex line on a movable disc and a fixed disc vortex line on a fixed disc, and in the operation process of the compressor, the fixed disc is static, and the movable disc makes translation along the circumferential direction, so that the volume of the sealed cavity is reduced along with the circumferential translation, and refrigerant gas is compressed and then discharged; the movable disc vortex line and the fixed disc vortex line which are mutually contacted are both rigid structures, and in the translation process of the movable disc, the movable disc vortex line and the fixed disc vortex line are mutually contacted at a conjugate point and then a gap between the movable disc vortex line and the fixed disc vortex line is eliminated, so that the sealing effect is achieved.
The contact force between the movable plate vortex line and the fixed plate vortex line at the conjugate point is moderate, and when the contact force is too small, pressure relief is generated due to a gap between the movable plate vortex line and the fixed plate vortex line, and radial impact between the movable plate and the fixed plate is caused; excessive contact force is easy to generate abrasion, and the input power of the compressor is increased, namely the radial contact force between the movable plate vortex line and the fixed plate vortex line determines the working performance of the compressor.
The contact force between the movable plate vortex line and the fixed plate vortex line at the conjugate point is determined by the flexible eccentric mechanism, and the flexible eccentric mechanism needs to be designed in a complex and fussy mode at present to ensure that the contact force between the movable plate vortex line and the fixed plate vortex line is moderate.
SUMMERY OF THE UTILITY MODEL
The utility model provides a problem how to simplify flexible eccentric mechanism's design process.
In order to solve the above problems, the utility model provides a flexible eccentric mechanism of a scroll compressor, which comprises an eccentric wheel, an eccentric shaft and a driving pin; wherein the content of the first and second substances,
the eccentric wheel comprises a driving shaft, and first eccentric holes distributed along the axial direction of the driving shaft are formed in the driving shaft;
the eccentric shaft is provided with second eccentric holes which are distributed along the axial direction of the eccentric shaft;
one end of the driving pin is inserted into the first eccentric hole, and the other end of the driving pin is inserted into the second eccentric hole;
the connecting lines of the first central point O1 of the driving shaft, the second central point O2 of the first eccentric hole and the third central point O3 of the eccentric shaft form a triangle, and the included angles of the triangle are all constant values.
Optionally, the value of the first included angle α in the triangle ranges from 30 ° to 32 °.
Optionally, the value of the second included angle β in the triangle ranges from 102 ° to 103 °.
Optionally, the drive pin is in interference fit with the second eccentric hole
Compared with the prior art, the utility model provides a scroll compressor's flexible eccentric mechanism has following advantage:
the utility model provides a scroll compressor's flexible eccentric mechanism, the contained angle through the triangle-shaped that will constitute by first central point O1, second central point O2 and third central point O3 line is fixed for when designing flexible eccentric mechanism, simplify loaded down with trivial details calculation optimization process, on the moderate basis of contact force between assurance conjugate point department's driving disk vortex line and the quiet dish vortex line, simplify flexible eccentric mechanism's design process, raise the efficiency.
Drawings
FIG. 1 is a schematic view of the front structure of the movable plate of the present invention;
FIG. 2 is a schematic view of the back structure of the movable plate according to the present invention;
FIG. 3 is a cross-sectional view of the movable plate according to the present invention;
fig. 4 is a schematic structural diagram of the stationary disc of the present invention;
fig. 5 is a cross-sectional view of the stationary plate according to the present invention;
FIG. 6 is an assembly view of the movable and stationary plates according to the present invention;
fig. 7 is a schematic structural diagram of the flexible eccentric mechanism according to the present invention;
fig. 8 is a cross-sectional view of the flexible eccentric mechanism according to the present invention;
fig. 9 is a schematic structural diagram of the eccentric wheel of the present invention;
fig. 10 is a cross-sectional view of the eccentric wheel according to the present invention;
fig. 11 is a first assembly view of the eccentric shaft and the driving pin according to the present invention;
fig. 12 is a second assembly view of the eccentric shaft and the driving pin according to the present invention.
Description of reference numerals:
1-eccentric wheel; 11-a drive shaft; 111-a first eccentric orifice; 2-eccentric shaft; 21-a first eccentric orifice; 3-driving the pin; 4-a movable disc; 41-orbiting plate vortex line; 42-spin limiting hole; 43-bearing bore; 44-a bearing; 5-a static disc; 51-stationary plate vortex line.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention more comprehensible, embodiments accompanied with figures are described in detail below.
Referring to fig. 1 to 3, a central point of a top view of the movable disk 4 is a fifth central point O5, and a front surface of the movable disk 4 is provided with a movable disk vortex line 41; the back of the movable disc 4 is provided with six rotation limiting holes 42, and the movable disc 4 can only do horizontal circumferential movement but can not rotate through the limitation of the rotation limiting holes 42; the back of the movable disc 4 is also provided with a bearing hole 43 and a bearing 44 arranged in the bearing hole 43; during the operation of the compressor, the driving shaft of the eccentric wheel in the flexible eccentric mechanism is matched with the bearing to drive the movable disc 4 to horizontally and circumferentially translate.
Referring to fig. 4 and 5, the fixed disk 5 is provided with a fixed disk spiral line 51, and a center point in a plan view of the fixed disk 5 is a sixth center point O6.
During the operation of the compressor, referring to fig. 6, the movable plate vortex line 41 is upward, the fixed plate vortex line 51 is downward, and the fifth central point O5 on the movable plate 4 makes a circumferential translation along the track D; wherein D is a circular structure; the movable plate vortex line 41 and the fixed plate vortex line 51 are meshed with each other, and the movable plate vortex line 41 and the fixed plate vortex line 51 are the same in height, so that axial sealing is realized; in the process of the translation of the movable disc 4, the radial conjugate points of the movable disc vortex line 41 and the fixed disc vortex line 51 are a first conjugate point P1, a second conjugate point P2, a third conjugate point P3, a fourth conjugate point P4, a fifth conjugate point P5 and a sixth conjugate point P6 in sequence, four independent compression cavities are formed through the conjugate points and are a first compression cavity M1, a second compression cavity M2, a third compression cavity M3 and a fourth compression cavity M4 in sequence, wherein the first compression cavity M1 corresponds to the second compression cavity M2 and the third compression cavity M3 corresponds to the fourth compression cavity M4 in a pairwise mode, the volumes of the four compression cavities are gradually reduced along with the counterclockwise circumferential translation of the movable disc 4, the internal gas pressure is gradually increased and then discharged, and the purpose of compression is achieved.
Wherein the contact force between the orbiting plate spiral line 41 and the stationary plate spiral line 51 at the conjugate point is determined by the flexible eccentric mechanism.
In order to ensure that the contact force between the movable plate vortex line 41 and the fixed plate vortex line 51 is kept at a moderate level, the utility model provides a flexible eccentric mechanism of a scroll compressor, which is shown in figures 7 and 8 and comprises an eccentric wheel 1, an eccentric shaft 2 and a driving pin 3; as shown in fig. 9 and 10, the eccentric wheel 1 includes a driving shaft 11, a first eccentric hole 111 is disposed on the driving shaft 11, the first eccentric hole 111 is distributed along an axial direction of the driving shaft 11, and a second central point O2 of the first eccentric hole 111 does not coincide with a first central point O1 of the driving shaft 11; the first center point O1 and the second center point O2 are the center point of the driving shaft 11 and the center point of the first eccentric hole 111 respectively.
Herein, an offset angle between the second center point O2 on the first eccentric hole 111 with respect to the first center point O1 on the drive shaft 1 is referred to as an offset angle γ, and an offset amount between the second center point O2 with respect to the first center point O1 is referred to as a first eccentric amount e 1; specifically, the first included angle β is an angle rotated when the horizontal line passing through the first center point O1 rotates clockwise to a connection line between the first center point O1 and the second center point O2; the first eccentricity e1 refers to a straight distance between the second center point O2 and the first center point O1.
Referring to fig. 11 and 12, the eccentric shaft 2 is provided with second eccentric holes 21, the second eccentric holes 21 are distributed along the axial direction of the eccentric shaft 2, and a fourth central point O4 of the second eccentric holes 21 is not coincident with a third central point O3 of the eccentric shaft 2; the third center point O3 is the center of rotation of the eccentric shaft 2, the third center point O3 is the center point of the eccentric shaft 2 in plan view, and the fourth center point O4 is the center point of the second eccentric hole 21 in plan view.
The offset of the fourth centerpoint O4 with respect to the third centerpoint O3 is herein denoted as a second eccentricity e 2; specifically, the second eccentricity e2 is a straight-line distance between the fourth center point O4 and the third center point O3.
One end of the drive pin 3 is inserted into the first eccentric hole 111 so that the center point of the drive pin 3 coincides with the second center point O2; the other end of the driving pin 3 is inserted into the second eccentric hole 21; the present application prefers that the drive pin 3 has an interference fit with the second eccentric hole 21.
Referring to fig. 7, the third center point O3 is the center of rotation of the eccentric shaft 2, the first center point O1 is the center of the drive shaft 11, the eccentric wheel 1 can rotate around the drive pin 3 within a minute range, the equivalent eccentric amount e of the drive shaft 11 is determined by the second eccentric amount e2, the first eccentric amount e1 and the offset angle γ, and the theoretical equivalent eccentric amount e is equal to the radius of the trajectory D in fig. 6; specifically, the equivalent eccentricity e of the drive shaft 11 refers to a straight distance between the first center point O1 on the drive shaft 11 and the third center point O3 of the center of gyration of the eccentric shaft 2.
In the running process of the compressor, the flexible eccentric mechanism is subjected to a driving force F1 and a load F2 at the same time, wherein the driving force F1 and the load F2 are the same in size and are marked as F, the directions are opposite and parallel, and the distance between two stress points is L; the eccentric wheel 1 generates a counterclockwise turning moment due to the existence of the distance L, and the moment is F multiplied by L; under the action of the moment, after the eccentric wheel 1 rotates around the driving pin 3 anticlockwise, the equivalent eccentric amount e of the driving shaft 11 is increased, so that the contact point between the movable disc vortex line 41 and the fixed disc vortex line 51 can eliminate the gap, and a reasonable contact force can be kept, namely, the contact force can be realized by adjusting the offset angle gamma and the first eccentric amount e 1.
Referring to fig. 7, the connection lines of the first center point O1, the second center point O2 and the third center point O3 form a triangle; wherein the first eccentricity e1 is a length of a connection line between the first center point O1 and the second center point O2 in the triangle, i.e., the first eccentricity e1 is a side length of the triangle; the angle of the offset angle gamma is an angle value obtained by subtracting 90 degrees from the angle of & lt O3O1O2 in the triangle; therefore, by adjusting the triangular configuration, the contact force between the movable plate scroll line 41 and the fixed plate scroll line 51 can be adjusted.
In order to simplify the design process of the flexible eccentric mechanism, the structure of the triangle and the relation of the contact force between the movable plate vortex line 41 and the fixed plate vortex line 51 are researched and optimized, the included angle in the triangle is fixed, that is, the included angle in the triangle is designed, so that the flexible eccentric mechanism with the triangle structure can adapt to different equivalent eccentric quantities e, under the condition of different equivalent eccentric quantities e, the triangle formed by connecting lines of the first central point O1, the second central point O2 and the third central point O3 is a similar triangle, and the flexible eccentric mechanism can enable the contact force between the movable plate vortex line 41 and the fixed plate vortex line 51 at the conjugate point to be moderate.
The utility model provides a scroll compressor's flexible eccentric mechanism, the contained angle through the triangle-shaped that will constitute by first central point O1, second central point O2 and third central point O3 line is fixed for when designing flexible eccentric mechanism, simplify loaded down with trivial details calculation optimization process, on the moderate basis of contact force between assurance conjugate point department's driving disk vortex line 41 and quiet dish vortex line 51, simplify flexible eccentric mechanism's design process, raise the efficiency.
The included angle of the triangle is further optimized, specifically, in the triangle formed by connecting a first central point O1, a second central point O2 and a third central point O3, an included angle between a connecting line of the first central point O1 and the third central point O3 and a connecting line of the second central point O2 and the third central point O3, namely × O1O3O2 is recorded as a first included angle α; an included angle between a connecting line of the third central point O3 and the first central point O1 and a connecting line of the second central point O2 and the first central point O1 is a second included angle beta which is ^ O3O1O 2; the first included angle alpha and the second included angle beta are both constant values.
Through optimization screening, the value range of the first included angle alpha is further preferably 30-32 degrees, and the value range of the second included angle beta is preferably 102-103 degrees.
The angle of the offset angle γ is obtained by subtracting 90 degrees from the angle of the second included angle β, and therefore, the angle range of the offset angle γ is 12 ° to 13 °.
According to the flexible eccentric mechanism with the triangular structure, the included angle in the triangle formed by connecting lines of the first central point O1, the second central point O2 and the third central point O3 is specifically set, so that the contact force between the movable disc vortex line 41 and the fixed disc vortex line 51 at the conjugate point can be guaranteed to be moderate, and the working performance of the compressor is improved.
Although the present disclosure has been described above, the scope of the present disclosure is not limited thereto. Those skilled in the art can make various changes and modifications without departing from the spirit and scope of the present disclosure, and such changes and modifications will fall within the scope of the present invention.
Claims (4)
1. A flexible eccentric mechanism of a scroll compressor is characterized by comprising an eccentric wheel (1), an eccentric shaft (2) and a driving pin (3); wherein the content of the first and second substances,
the eccentric wheel (1) comprises a driving shaft (11), wherein first eccentric holes (111) distributed along the axial direction of the driving shaft (11) are formed in the driving shaft (11);
the eccentric shaft (2) is provided with second eccentric holes (21) which are distributed along the axial direction of the eccentric shaft (2);
one end of the driving pin (3) is inserted into the first eccentric hole (111), and the other end of the driving pin is inserted into the second eccentric hole (21);
the connecting lines of the first central point O1 of the driving shaft (11), the second central point O2 of the first eccentric hole (111) and the third central point O3 of the eccentric shaft (2) form a triangle, and the included angles of the triangle are all constant values.
2. The flexible eccentric mechanism of scroll compressor as claimed in claim 1, wherein the first included angle α in the triangle is in the range of 30 ° to 32 °.
3. The flexible eccentric mechanism of scroll compressor as claimed in claim 1, wherein the second included angle β in the triangle is in the range of 102 ° to 103 °.
4. The flexible eccentric mechanism of scroll compressor according to claim 1, characterized in that the driving pin (3) is interference fitted with the second eccentric hole (21).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020475390.9U CN212508820U (en) | 2020-04-03 | 2020-04-03 | Flexible eccentric mechanism of scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020475390.9U CN212508820U (en) | 2020-04-03 | 2020-04-03 | Flexible eccentric mechanism of scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN212508820U true CN212508820U (en) | 2021-02-09 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202020475390.9U Active CN212508820U (en) | 2020-04-03 | 2020-04-03 | Flexible eccentric mechanism of scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN212508820U (en) |
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2020
- 2020-04-03 CN CN202020475390.9U patent/CN212508820U/en active Active
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