CN109441825B - Crankshaft and rotor type compressor - Google Patents
Crankshaft and rotor type compressor Download PDFInfo
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- CN109441825B CN109441825B CN201811517510.0A CN201811517510A CN109441825B CN 109441825 B CN109441825 B CN 109441825B CN 201811517510 A CN201811517510 A CN 201811517510A CN 109441825 B CN109441825 B CN 109441825B
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- 238000005461 lubrication Methods 0.000 abstract description 22
- 230000000694 effects Effects 0.000 abstract description 11
- 238000013461 design Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
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Abstract
The invention provides a crankshaft and a rotor type compressor. The crankshaft comprises a central oil hole (1) and a radial side hole (2) which are communicated, wherein the diameter of the central oil hole (1) is a, the diameter of the radial side hole (2) is r, the distance between the central axis of the radial side hole (2) and the end face of the eccentric part of the crankshaft is h, and the relation between the central oil hole (1) and the radial side hole (2) is as follows: a is more than or equal to 4mm and less than or equal to 7mm, and c is more than or equal to 0.07 and less than or equal to 0.13; or a is more than or equal to 7mm and less than or equal to 10mm, and c is more than or equal to 0.05 and less than or equal to 0.11; or a is more than or equal to 10mm and less than or equal to 13mm, and c is more than or equal to 0.04 and less than or equal to 0.1; where c=r/h. According to the crankshaft provided by the invention, the lubrication effect of each part can be effectively improved, and the reliability and performance of the compressor can be improved.
Description
Technical Field
The invention belongs to the technical field of compressors, and particularly relates to a crankshaft and rotor type compressor.
Background
The working principle of the existing rolling rotor compressor is as follows: the crankshaft of the pump body is driven by the motor to do rotary motion, and the roller is driven by the rotation of the crankshaft to do eccentric circular motion, so that the cold coal is compressed. The crankshaft is continuously rotating at high speed, so that friction of moving parts is most intense. The main kinematic pairs in the compressor are the long and short axes of the crank shaft, the inner walls of the upper flange and the lower flange, the eccentric parts of the crank shaft and the inner circles of the rollers, and meanwhile, the parts between the kinematic pairs are the most needed lubrication parts, the excessive oil lubrication can cause the hydraulic condition, and how to improve the lubrication effect of each part so as to improve the reliability and the performance of the compressor is a technical problem to be solved urgently by each compressor manufacturer.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to provide a crankshaft and rotor type compressor, which can effectively improve the lubrication effect of each part and improve the reliability and performance of the compressor.
In order to solve the above problems, the present invention provides a crankshaft, which comprises a central oil hole and a radial side hole which are communicated, wherein the diameter of the central oil hole is a, the diameter of the radial side hole is r, the distance between the central axis of the radial side hole and the end face of the eccentric part of the crankshaft is h, and the relationship between the central oil hole and the radial side hole satisfies:
A is more than or equal to 4mm and less than or equal to 7mm, and c is more than or equal to 0.07 and less than or equal to 0.13; or alternatively, the first and second heat exchangers may be,
A is more than or equal to 7mm and less than or equal to 10mm, and c is more than or equal to 0.05 and less than or equal to 0.11; or alternatively, the first and second heat exchangers may be,
A is more than or equal to 10mm and less than or equal to 13mm, and c is more than or equal to 0.04 and less than or equal to 0.1;
Where c=r/h.
Preferably, the crankshaft comprises a short shaft, a first connecting shaft, a first eccentric part, a second connecting shaft and a long shaft which are sequentially connected along the axial direction, and the radial side holes are positioned on the first connecting shaft, the first eccentric part, the second eccentric part and the second connecting shaft.
Preferably, the diameter of the central oil hole corresponding to the first connecting shaft is a1, the diameter of the radial side hole corresponding to the first connecting shaft is r1, the distance between the central axis of the radial side hole corresponding to the first connecting shaft and the end face of the eccentric part of the crankshaft is h1, c1=r1/h 1, wherein a1 and c1 satisfy: a1 is more than or equal to 4mm and less than or equal to 7mm, and c1 is more than or equal to 0.07 and less than or equal to 0.13.
Preferably, the diameter of the central oil hole corresponding to the first eccentric portion is a2, the diameter of the radial side hole corresponding to the first eccentric portion is r2, the distance between the central axis of the radial side hole corresponding to the first eccentric portion and the end face of the eccentric portion of the crankshaft is h2, c2=r2/h 2, wherein a2 and c2 satisfy:
A2 is more than or equal to 4mm and less than or equal to 7mm, c2 is more than or equal to 0.07 and less than or equal to 0.13; or alternatively, the first and second heat exchangers may be,
A2 is more than or equal to 7mm and less than or equal to 10mm, and c2 is more than or equal to 0.05 and less than or equal to 0.11.
Preferably, the diameter of the central oil hole corresponding to the second eccentric portion is a3, the diameter of the radial side hole corresponding to the second eccentric portion is r3, the distance between the central axis of the radial side hole corresponding to the second eccentric portion and the end face of the eccentric portion of the crankshaft is h3, c3=r3/h 3, wherein a3 and c3 satisfy:
a3 is more than or equal to 7mm and less than or equal to 10mm, and c3 is more than or equal to 0.05 and less than or equal to 0.11; or alternatively, the first and second heat exchangers may be,
A3 is more than or equal to 10mm and less than or equal to 13mm, and c3 is more than or equal to 0.04 and less than or equal to 0.1.
Preferably, the diameter of the central oil hole corresponding to the second connecting shaft is a4, the diameter of the radial side hole corresponding to the second connecting shaft is r4, the distance between the central axis of the radial side hole corresponding to the second connecting shaft and the end face of the eccentric part of the crankshaft is h4, c4=r4/h 4, wherein a4 and c4 satisfy: a4 is more than or equal to 10mm and less than or equal to 13mm, and c4 is more than or equal to 0.04 and less than or equal to 0.1.
Preferably, the crankshaft includes a short shaft, a first eccentric portion, a second eccentric portion, and a long shaft connected in sequence in an axial direction, and the radial side holes are located on the first eccentric portion and the second eccentric portion.
Preferably, the radial side hole is provided on a side wall of the first eccentric portion having the smallest distance from the central axis of the central oil hole.
Preferably, the radial side hole is provided on a side wall of the second eccentric portion having the smallest distance from the central axis of the central oil hole.
Preferably, the central oil holes are distributed in a stepped hole along the axial direction, and the hole diameter is increased gradually along the direction away from the end face of the end where the eccentric part of the crankshaft is located.
According to another aspect of the present invention, there is provided a rotor compressor including a crankshaft, which is the above-described crankshaft.
The crankshaft provided by the invention is provided with the communicated central oil hole and the radial side hole, wherein the diameter of the central oil hole is a, the diameter of the radial side hole is r, the distance between the central axis of the radial side hole and the end face of the eccentric part of the crankshaft is h, and the relationship between the central oil hole and the radial side hole is as follows: a is more than or equal to 4mm and less than or equal to 7mm, and c is more than or equal to 0.07 and less than or equal to 0.13; or a is more than or equal to 7mm and less than or equal to 10mm, and c is more than or equal to 0.05 and less than or equal to 0.11; or, 10 mm.ltoreq.a.ltoreq.13 mm, and 0.04.ltoreq.c.ltoreq.0.1, where c=r/h. Through limiting the proportional relation between the diameter of the radial side hole and the axial distance in the diameter range of different central oil holes, the lubrication effect between the moving parts can be guaranteed to be optimal when the compressor works, the hydraulic pressure of the pump body can be reduced, heat generated by compression of the pump body can be taken away, the problems of design difficulty of a crankshaft oil way and insufficient lubrication of the moving parts of the compressor are solved, the hydraulic pressure is reduced, and the reliability and performance of the compressor are improved.
Drawings
FIG. 1 is a schematic view of a crankshaft according to an embodiment of the present invention;
fig. 2 is a schematic structural view of a compressor according to an embodiment of the present invention;
FIG. 3 is a graph of compressor friction power consumption w versus c for 4 mm.ltoreq.a.ltoreq.7 mm;
FIG. 4 is a graph of compressor friction power consumption w versus c for a 7 mm.ltoreq.a.ltoreq.10 mm;
FIG. 5 is a graph of compressor friction power consumption w versus c for 10 mm.ltoreq.a.ltoreq.13 mm.
The reference numerals are expressed as:
1. A central oil hole; 2. radial side holes; 3. a short shaft; 4. a first connecting shaft; 5. a first eccentric portion; 6. a second eccentric portion; 7. a second connecting shaft; 8. a long axis; 9. a first bearing; 10. a second bearing; 11. a housing; 12. and a drive assembly.
Detailed Description
Referring to fig. 1 to 5 in combination, according to an embodiment of the present invention, a crankshaft includes a central oil hole 1 and a radial side hole 2 which are communicated, the diameter of the central oil hole 1 is a, the diameter of the radial side hole 2 is r, the distance between the central axis of the radial side hole 2 and the end face of the eccentric portion of the crankshaft is h, and the relationship between the central oil hole 1 and the radial side hole 2 satisfies: a is more than or equal to 4mm and less than or equal to 7mm, and c is more than or equal to 0.07 and less than or equal to 0.13; or a is more than or equal to 7mm and less than or equal to 10mm, and c is more than or equal to 0.05 and less than or equal to 0.11; or a is more than or equal to 10mm and less than or equal to 13mm, and c is more than or equal to 0.04 and less than or equal to 0.1; where c=r/h.
Through limiting the proportional relation between the diameter r of the radial side hole 2 and the axial distance h in different central oil hole diameter ranges, the best lubrication effect between the moving parts during the operation of the compressor can be ensured, the hydraulic pressure of the pump body can be reduced, the heat generated by the compression of the pump body can be taken away, the problems of the design difficulty of a crankshaft oil way and the insufficient lubrication of the moving parts of the compressor are solved, the hydraulic pressure is reduced, and the reliability and the performance of the compressor are improved.
In general, there is a larger relationship between the diameter of the central oil hole 1 and the oil transportation capability, the larger the diameter of the central oil hole 1 is, the stronger the oil transportation capability is, and the smaller the diameter of the central oil hole 1 is, the worse the oil transportation capability is; meanwhile, when the diameter of the central oil hole 1 is fixed, the diameter of the radial side hole 2 is related to the axial distance between the radial side hole 2 and the oil inlet, namely, the distance h between the end faces of the eccentric part of the crankshaft is related, and the further the axial distance between the radial side hole 2 and the oil inlet is, the more difficult the oil transportation is, so that if sufficient oil transportation is required, the diameter of the radial side hole 2 needs to be increased. By setting the reasonable ratio of the diameter of the radial side hole 2 to the distance in the diameter range of the specific central oil hole 1, the lubrication effect of parts during the working of the compressor can be ensured to be optimal, the minimum mutual friction and abrasion is ensured, and meanwhile, the occurrence of hydraulic pressure is reduced.
Preferably, the central oil holes 1 are distributed in stepped holes along the axial direction, and the hole diameters of the central oil holes 1 are gradually increased along the direction away from the end face of the eccentric part of the crankshaft, so that the oil feeding capacity of the central oil holes 1 is gradually increased along the direction away from the oil feeding end, the problem that the oil feeding capacity of the central oil holes 1 is poor due to the increase of the distance between the central oil holes 1 and the oil feeding end is solved, and the oil feeding capacity of the central oil holes 1 away from the oil feeding end is improved.
In a first embodiment of the invention, the crankshaft comprises a long axis 8, a short axis 3 and a first eccentric portion 5 connected between the long axis 8 and the short axis 3, the radial side hole 2 being located on the first eccentric portion 5. In this embodiment, the main motion friction is located between the first eccentric portion 5 and the inner wall of the first cylinder and between the inner walls of the upper and lower flanges and the long and short shafts, so that the oil delivery amount can be ensured by arranging the radial side holes 2 on the first eccentric portion 5, and meanwhile, the motion pairs between the upper and lower flanges and the long and short shafts can be lubricated by the radial side holes 2 on the first eccentric portion 5. Of course, the long and short shafts may be provided with radial side holes 2 communicating with the central oil hole 1, respectively, to carry out oil transportation.
In a second embodiment of the invention, the crankshaft comprises a short shaft 3, a first connecting shaft 4, a first eccentric portion 5 and a long shaft 8 connected in sequence in the axial direction, the radial side holes 2 being located on the first connecting shaft 4 and the first eccentric portion 5. In this embodiment, a first connecting shaft 4 is added between the short shaft 3 and the first eccentric portion 5, a first bearing 9 is sleeved on the first connecting shaft 4, and a crankshaft is mounted on a lower flange through the first bearing 9, so that the rotation friction of the crankshaft can be further reduced through the first bearing 9, the friction loss is reduced, and the working energy efficiency of the compressor is improved.
In the third embodiment of the present invention, the crankshaft includes a short shaft 3, a first connecting shaft 4, a first eccentric portion 5, a second eccentric portion 6, and a long shaft 8, which are sequentially connected in the axial direction, and the radial side hole 2 is located on the first connecting shaft 4, the first eccentric portion 5, and the second eccentric portion 6. In this embodiment, the first connecting shaft 4 is sleeved with the first bearing 9, the first bearing 9 and the kinematic pair of the lower flange and the short shaft 3 are supplied with oil through the radial side hole 2 on the first connecting shaft 4, the kinematic pair between the first eccentric part 5 and the first cylinder is lubricated by oil through the radial side hole 2 on the first eccentric part 5, and the kinematic pair between the second eccentric part 6 and the second cylinder and the kinematic pair between the upper flange and the long shaft 8 are lubricated by oil through the radial side hole 2 on the second eccentric part 6.
In the fourth embodiment of the present invention, the crankshaft includes a short shaft 3, a first eccentric portion 5, a second eccentric portion 6, a second connecting shaft 7, and a long shaft 8, which are sequentially connected in the axial direction, and the radial side hole 2 is located on the second eccentric portion 6 and the second connecting shaft 7. In the embodiment, the second connecting shaft 7 is sleeved with the second bearing 10, the crankshaft is mounted on the upper flange through the second bearing 10, the rotation friction of the crankshaft can be further reduced through the second bearing 10, the friction loss is reduced, and the working energy efficiency of the compressor is improved.
In the fifth embodiment of the present invention, the crankshaft includes a short shaft 3, a first connecting shaft 4, a first eccentric portion 5, a second eccentric portion 6, a second connecting shaft 7, and a long shaft 8, which are sequentially connected in the axial direction, and the radial side hole 2 is located on the first connecting shaft 4, the first eccentric portion 5, the second eccentric portion 6, and the second connecting shaft 7.
Preferably, the diameter of the central oil hole corresponding to the first connecting shaft 4 is a1, the diameter of the radial side hole corresponding to the first connecting shaft 4 is r1, the distance between the central axis of the radial side hole corresponding to the first connecting shaft 4 and the end face where the eccentric part of the crankshaft is located is h1, c1=r1/h 1, wherein a1 and c1 satisfy: a1 is more than or equal to 4mm and less than or equal to 7mm, and c1 is more than or equal to 0.07 and less than or equal to 0.13.
Preferably, the diameter of the central oil hole corresponding to the first eccentric portion 5 is a2, the diameter of the radial side hole corresponding to the first eccentric portion 5 is r2, the distance between the central axis of the radial side hole corresponding to the first eccentric portion 5 and the end face of the eccentric portion of the crankshaft is h2, c2=r2/h 2, wherein a2 and c2 satisfy:
A2 is more than or equal to 4mm and less than or equal to 7mm, c2 is more than or equal to 0.07 and less than or equal to 0.13; or alternatively, the first and second heat exchangers may be,
A2 is more than or equal to 7mm and less than or equal to 10mm, and c2 is more than or equal to 0.05 and less than or equal to 0.11.
Preferably, the diameter of the central oil hole corresponding to the second eccentric portion 6 is a3, the diameter of the radial side hole corresponding to the second eccentric portion 6 is r3, the distance between the central axis of the radial side hole corresponding to the second eccentric portion 6 and the end face of the eccentric portion of the crankshaft is h3, c3=r3/h 3, wherein a3 and c3 satisfy:
a3 is more than or equal to 7mm and less than or equal to 10mm, and c3 is more than or equal to 0.05 and less than or equal to 0.11; or alternatively, the first and second heat exchangers may be,
A3 is more than or equal to 10mm and less than or equal to 13mm, and c3 is more than or equal to 0.04 and less than or equal to 0.1.
Preferably, the diameter of the central oil hole corresponding to the second connecting shaft 7 is a4, the diameter of the radial side hole corresponding to the second connecting shaft 7 is r4, the distance between the central axis of the radial side hole corresponding to the second connecting shaft 7 and the end face where the eccentric part of the crankshaft is located is h4, c4=r4/h 4, wherein a4 and c4 satisfy: a4 is more than or equal to 10mm and less than or equal to 13mm, and c4 is more than or equal to 0.04 and less than or equal to 0.1.
In the above embodiments, a1 is greater than a2 and less than a3 is greater than a4, so that the oil delivery capacity of the central oil hole 1 is continuously enhanced along with the increase of the distance from the oil inlet end, the oil delivery capacity of the central oil hole 1 to the radial side hole 2 is improved, and the oil delivery capacity of the radial side hole 2 is further improved.
In the above embodiments, according to the different positions of the central oil hole 1, the diameters of the central oil hole 1 are selected, so that the central oil hole 1 can be designed according to the variable diameter, and the diameter of the central oil hole 1 and the diameter of the radial side hole 2 can be reasonably designed according to the distance between the radial side hole 2 and the oil inlet end, so that the influence of the distance between the radial side hole 2 and the oil inlet end on the oil conveying capacity of the radial side hole 2 is reduced, the oil conveying capacity of the radial side hole 2 at each position is ensured, the lubrication effect of each part is effectively improved, and the reliability and performance of the compressor are improved.
In the sixth embodiment of the present invention, the crankshaft includes a short shaft 3, a first eccentric portion 5, a second eccentric portion 6, and a long shaft 8, which are connected in order in the axial direction, and the radial side hole 2 is located on the first eccentric portion 5 and the second eccentric portion 6.
In the above embodiments, when the setting parameters of the radial side hole 2 can meet the limiting requirements of the present invention, the radial side hole 2 may be arranged on the short shaft 3 and the long shaft 8, so that lubrication oil supply of the kinematic pair between the short shaft 3 and the inner wall of the lower flange is realized through the radial side hole 2 on the short shaft 3, and lubrication oil supply of the kinematic pair between the long shaft 8 and the inner wall of the upper flange is realized through the radial side hole 2 on the long shaft 8.
Preferably, the radial side hole 2 is arranged on the side wall of the first eccentric part 5, which has the smallest distance with the central axis of the central oil hole 1, so that the length of the oil supply path of the first eccentric part 5 can be shortened, the oil supply efficiency can be improved, and the oil supply difficulty can be reduced.
Preferably, the radial side hole 2 is arranged on the side wall of the second eccentric part 6, which has the smallest distance with the central axis of the central oil hole 1, so that the length of the oil supply path of the second eccentric part 6 can be shortened, the oil supply efficiency can be improved, and the oil supply difficulty can be reduced.
The first connecting shaft 4 is sleeved with a first bearing 9.
The second connecting shaft 7 is sleeved with a second bearing 10.
Referring to fig. 1 to 5 in combination, according to an embodiment of the present invention, the rotor type compressor includes a pump body assembly including the above-described crankshaft, a driving assembly 12, a housing 11, a dispenser, and upper and lower covers, and when the rotor type compressor is a single stage compressor, the pump body assembly further includes a first cylinder, an upper flange, and a lower flange, in which the crankshaft is inserted. When the rotor type compressor is a two-stage compressor, the pump body assembly further comprises a first cylinder, a second cylinder, an upper flange and a lower flange, and the crankshaft is arranged in the first cylinder, the second cylinder, the upper flange and the lower flange in a penetrating mode.
During operation, the crankshaft is driven by the driving assembly to perform high-speed rotation, so that the kinematic pairs in the compressor are extremely violently rubbed with each other, lubrication of the kinematic pairs is extremely important, proper lubrication can reduce mutual friction loss between the kinematic pairs and take away heat, and reliability and performance of the compressor can be greatly improved. The main mode of lubrication in the pump body is that the oil suction pipe sucks the frozen oil in the oil pool at the bottom of the compressor and then conveys the frozen oil to each part through the oil guide plate, and the radial side hole 2 of the crankshaft can bring the frozen oil to the position with the strongest friction, so that lubrication between kinematic pairs is ensured.
When the central oil hole 1 is designed with equal diameter, as shown in fig. 1, the value of a is a certain, and the value of c can be different due to different arrangement positions of the radial side holes 2, in this embodiment, four radial side holes 2 are arranged, when a is a certain value, c1=r1/h 1, c2=r2/h 2, c3=r3/h 3, and c4=r4/h 4, and the arrangement of the four radial side holes 2 meets the above limitation, namely, when a is 4mm less than or equal to 7mm, the values of c1, c2, c3 and c4 are all in the range of 0.07-0.13, and when a is 7mm less than or equal to 10mm, the values of c1, c2, c3 and c4 are all in the range of 0.05-0.11, and when a is 10mm less than or equal to 13mm, the values of c1, c2, c3 and c4 are all in the range of 0.04-0.10. Under the condition of meeting the above limitation, the values of r1, r2, r3 and r4 can be reasonably designed, so that the oil transportation capacity of the radial side hole 2 is improved within a certain range.
The power Fn of pumping oil mainly comes from the pressure difference Fv between the inside and outside of the side hole and the centrifugal force Fa during rotation of the crankshaft, and the pumping oil quantity of the radial side hole 2 is determined by the diameter of the radial side hole, the distance from the central oil hole and the diameter of the central oil hole of the crankshaft. The larger the distance, the smaller the diameter of the radial side hole 2, the larger the required pumping power Fn. As shown in fig. 3 to 5, the graphs of the friction loss and the ratio c of the compressor have a tendency to decrease and increase at the same diameter of the central oil hole, that is, there is an optimum value between the friction power consumption and the lubrication effect of the moving parts. According to the research, when a1 is more than or equal to 4 and less than or equal to 7, the friction loss of the compressor is smaller and the lubrication effect is better under the condition that c1 is more than or equal to 0.07 and less than or equal to 0.13; when a2 is more than or equal to 7 and less than or equal to 10, the friction loss of the compressor is smaller and the lubrication effect is better under the condition that c2 is more than or equal to 0.05 and less than or equal to 0.11; when a3 is more than or equal to 10 and less than or equal to 13, the friction loss of the compressor is smaller and the lubrication effect is better under the condition that c3 is more than or equal to 0.04 and less than or equal to 0.1.
By monitoring the oil discharge rate of the refrigerating oil in the running process of the compressor, when the design of the central oil hole and the side hole of the crankshaft meets the above-mentioned limit of the invention, the oil discharge rate of the compressor is lower, and the condition that a large amount of refrigerating oil is discharged along with the refrigerant is avoided, namely, the hydraulic pressure of the compressor is reduced, and the refrigerating capacity and the lubrication of the compressor are better.
It will be readily appreciated by those skilled in the art that the above advantageous ways can be freely combined and superimposed without conflict.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention. The foregoing is merely a preferred embodiment of the present invention, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present invention, and these modifications and variations should also be regarded as the scope of the invention.
Claims (11)
1. The utility model provides a bent axle, its characterized in that includes the central oilhole (1) and the radial side opening (2) of intercommunication, the diameter of central oilhole (1) is a, the diameter of radial side opening (2) is r, the distance between the central axis of radial side opening (2) and the terminal surface that the eccentric part of bent axle is located is h, the relation between central oilhole (1) with radial side opening (2) satisfies:
A is more than or equal to 4mm and less than or equal to 7mm, and c is more than or equal to 0.07 and less than or equal to 0.13; or alternatively, the first and second heat exchangers may be,
A is more than or equal to 7mm and less than or equal to 10mm, and c is more than or equal to 0.05 and less than or equal to 0.11; or alternatively, the first and second heat exchangers may be,
A is more than or equal to 10mm and less than or equal to 13mm, and c is more than or equal to 0.04 and less than or equal to 0.1;
Where c=r/h.
2. The crankshaft according to claim 1, characterized in that it comprises a short shaft (3), a first connecting shaft (4), a first eccentric portion (5), a second eccentric portion (6), a second connecting shaft (7) and a long shaft (8) connected in sequence in the axial direction, said radial side holes (2) being located on said first connecting shaft (4), said first eccentric portion (5), said second eccentric portion (6) and said second connecting shaft (7).
3. The crankshaft according to claim 2, wherein the diameter of the central oil hole corresponding to the first connecting shaft (4) is a1, the diameter of the radial side hole corresponding to the first connecting shaft (4) is r1, the distance between the central axis of the radial side hole corresponding to the first connecting shaft (4) and the end face where the eccentric portion of the crankshaft is located is h1, c1=r1/h 1, wherein a1 and c1 satisfy: a1 is more than or equal to 4mm and less than or equal to 7mm, and c1 is more than or equal to 0.07 and less than or equal to 0.13.
4. A crankshaft according to claim 2, characterized in that the diameter of the central oil hole corresponding to the first eccentric portion (5) is a2, the diameter of the radial side hole corresponding to the first eccentric portion (5) is r2, the distance between the central axis of the radial side hole corresponding to the first eccentric portion (5) and the end face of the eccentric portion of the crankshaft is h2, c2=r2/h 2, where a2 and c2 satisfy:
A2 is more than or equal to 4mm and less than or equal to 7mm, c2 is more than or equal to 0.07 and less than or equal to 0.13; or alternatively, the first and second heat exchangers may be,
A2 is more than or equal to 7mm and less than or equal to 10mm, and c2 is more than or equal to 0.05 and less than or equal to 0.11.
5. A crankshaft according to claim 2, characterized in that the diameter of the central oil hole corresponding to the second eccentric portion (6) is a3, the diameter of the radial side hole corresponding to the second eccentric portion (6) is r3, the distance between the central axis of the radial side hole corresponding to the second eccentric portion (6) and the end face of the eccentric portion of the crankshaft is h3, c3=r3/h 3, where a3 and c3 satisfy:
a3 is more than or equal to 7mm and less than or equal to 10mm, and c3 is more than or equal to 0.05 and less than or equal to 0.11; or alternatively, the first and second heat exchangers may be,
A3 is more than or equal to 10mm and less than or equal to 13mm, and c3 is more than or equal to 0.04 and less than or equal to 0.1.
6. The crankshaft according to claim 2, characterized in that the diameter of the central oil hole corresponding to the second connecting shaft (7) is a4, the diameter of the radial side hole corresponding to the second connecting shaft (7) is r4, the distance between the central axis of the radial side hole corresponding to the second connecting shaft (7) and the end face where the eccentric portion of the crankshaft is located is h4, c4=r4/h 4, wherein a4 and c4 satisfy: a4 is more than or equal to 10mm and less than or equal to 13mm, and c4 is more than or equal to 0.04 and less than or equal to 0.1.
7. A crankshaft according to claim 1, characterized in that it comprises a short shaft (3), a first eccentric portion (5), a second eccentric portion (6) and a long shaft (8) connected in sequence in the axial direction, said radial side holes (2) being located on said first eccentric portion (5) and on said second eccentric portion (6).
8. A crankshaft according to any one of claims 2 to 7, wherein the radial side hole (2) is provided on a side wall of the first eccentric portion (5) where a distance from a central axis of the central oil hole (1) is smallest.
9. A crankshaft according to any one of claims 2 to 7, wherein the radial side hole (2) is provided on a side wall of the second eccentric portion (6) where a distance from a central axis of the central oil hole (1) is smallest.
10. A crankshaft according to any one of claims 1 to 7, wherein the central oil holes (1) are distributed in stepped holes along the axial direction, and the hole diameter increases in the direction away from the end face of the eccentric portion of the crankshaft.
11. A rotor compressor comprising a crankshaft, characterized in that the crankshaft is a crankshaft according to any one of claims 1 to 10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811517510.0A CN109441825B (en) | 2018-12-12 | Crankshaft and rotor type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811517510.0A CN109441825B (en) | 2018-12-12 | Crankshaft and rotor type compressor |
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| Publication Number | Publication Date |
|---|---|
| CN109441825A CN109441825A (en) | 2019-03-08 |
| CN109441825B true CN109441825B (en) | 2024-07-02 |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN209458123U (en) * | 2018-12-12 | 2019-10-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Crankshaft and rotor-type compressor |
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN209458123U (en) * | 2018-12-12 | 2019-10-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Crankshaft and rotor-type compressor |
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