CN206206378U - Two-stage Compression machine crankshaft and double-stage compressor - Google Patents
Two-stage Compression machine crankshaft and double-stage compressor Download PDFInfo
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- CN206206378U CN206206378U CN201621089821.8U CN201621089821U CN206206378U CN 206206378 U CN206206378 U CN 206206378U CN 201621089821 U CN201621089821 U CN 201621089821U CN 206206378 U CN206206378 U CN 206206378U
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- stage compression
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Abstract
The utility model discloses a kind of Two-stage Compression machine crankshaft and double-stage compressor, belong to Compressor Technology field, for solve existing apparatus needed for balance weight quality increase, compressor operating when bent axle amount of deflection become it is big the problems such as and design.The utility model Two-stage Compression machine crankshaft includes bent axle main body, low-pressure stage eccentric part and hiigh pressure stage eccentric part are provided with bent axle main body, low-pressure stage eccentric part outside is arranged with low-pressure stage roller, hiigh pressure stage eccentric part outside is arranged with hiigh pressure stage roller, and the eccentric rotary inertia force of low-pressure stage compression unit is equal to the eccentric rotary inertia force of hiigh pressure stage compression unit；Low-pressure stage compression unit includes low-pressure stage eccentric part and low-pressure stage roller, and hiigh pressure stage compression unit includes hiigh pressure stage eccentric part and hiigh pressure stage roller.The utility model Two-stage Compression machine crankshaft and double-stage compressor reduce the balance weight weight of double-stage compressor, the amount of deflection of bent axle when reducing compressor operating, improve the reliability of huge discharge double-stage compressor, while also reducing compressor cost.
Description
Technical field
The utility model is related to Compressor Technology field, more particularly to a kind of Two-stage Compression machine crankshaft and including the bent axle
Double-stage compressor.
Background technology
For the efficiency of guarantee Dual-level enthalpy adding compressor, the design volumetric ratio of its hiigh pressure stage and low-pressure stage is less than 1, i.e. hiigh pressure stage
Discharge capacity is less than low-pressure stage discharge capacity.Therefore, the eccentric mass and low-pressure stage pressure of Dual-level enthalpy adding compressor bent axle hiigh pressure stage compression unit
Can there is certain difference in the eccentric mass in contracting portion.
In Dual-level enthalpy adding compressor balance system design is carried out, low-pressure stage compression unit eccentric rotary inertia force is more than high pressure
Level compression unit eccentric rotary inertia force is, it is necessary to ensure compressor operating by setting balance weight steady.
In order to solve the problems, such as that heating capacity decay is, it is necessary to reduce the volumetric ratio of double-stage compressor during compressor assembly low temperature
To lift efficiency during low-temperature heating, cause the hiigh pressure stage compression unit eccentric mass of double-stage compressor and low-pressure stage compression unit eccentric
The difference of quality can increase, and then the amount of deflection of bent axle becomes big, compressor when causing required balance weight quality increase, compressor operating
Less reliable, compressor high cost.
Utility model content
A purpose of the present utility model is to propose a kind of Two-stage Compression that can reduce double-stage compressor balance weight weight
Machine crankshaft.
Another purpose of the present utility model is to propose that one kind solves huge discharge double-stage compressor low-pressure stage and high pressure
The double-stage compressor of the out-of-balance force problem of level compression unit eccentric mass.
It is up to this purpose, on the one hand, the utility model uses following technical scheme：
A kind of Two-stage Compression machine crankshaft, including bent axle main body, low-pressure stage eccentric part and height are provided with the bent axle main body
Arbitrarily downgrade eccentric part, the low-pressure stage eccentric part outside is arranged with low-pressure stage roller, the hiigh pressure stage eccentric part outside is arranged with height
Arbitrarily downgrade roller, the eccentric rotary inertia force of low-pressure stage compression unit is equal to the eccentric rotary inertia force of hiigh pressure stage compression unit；It is described low
Compression unit of arbitrarily downgrading includes the low-pressure stage eccentric part and the low-pressure stage roller, and the hiigh pressure stage compression unit includes the hiigh pressure stage
Eccentric part and the hiigh pressure stage roller.
Particularly, the axis direction of the bent axle main body is provided with least one through hole on the low-pressure stage eccentric part
And/or blind hole.
Further, the through hole and/or the blind hole are crescent hole, and the crescent hole is along perpendicular to the bent axle main body
Section on axis direction is in crescent shape.
Further, reinforcement is provided with the middle part of the crescent hole, one end of the reinforcement is connected to the moon
On the side arcwall face in tooth hole, the other end is connected on the opposite side arcwall face of the crescent hole.
Particularly, the through hole and/or the blind hole are circular hole.
Particularly, it is formed with bias on the lateral surface of the axis away from the bent axle main body of the low-pressure stage eccentric part
Portion's groove.
Particularly, it is formed with roller groove on the inwall of the low-pressure stage roller.
Further, the roller groove surround the low-pressure stage roller on the axis direction perpendicular to the bent axle main body
Inwall at least enclose.
On the other hand, the utility model uses following technical scheme：
A kind of double-stage compressor, including above-mentioned Two-stage Compression machine crankshaft.
Particularly, the double-stage compressor also includes rotor, and main balance weight and secondary balance weight are provided with the rotor, by
The rotor-support-foundation system that low-pressure stage compression unit, hiigh pressure stage compression unit, main balance weight and secondary balance weight are constituted meets static balance and moves simultaneously
The condition of balance；During static balance, the eccentric rotary of the eccentric rotary inertia force of the low-pressure stage compression unit and the secondary balance weight
Inertia force sum is equal to the eccentric rotary inertia force of the hiigh pressure stage compression unit and the eccentric rotary inertia force of the main balance weight
Sum, the eccentric rotary inertia force be equal to quality, eccentric throw and angular speed square product；During dynamic balancing, the low-pressure stage
The eccentric rotary moment of inertia sum of the eccentric rotary moment of inertia of compression unit and the main balance weight is equal to the hiigh pressure stage pressure
The eccentric rotary moment of inertia sum of the eccentric rotary moment of inertia in contracting portion and the secondary balance weight, the eccentric rotary inertia force
Square be equal to the distance between quality, eccentric throw, center of gravity and specified point and angular speed square product.
The eccentric rotary inertia force of the low-pressure stage compression unit of the utility model Two-stage Compression machine crankshaft compresses equal to hiigh pressure stage
The eccentric rotary inertia force in portion, reduces the balance weight weight of double-stage compressor, the amount of deflection of bent axle when reducing compressor operating,
The reliability of huge discharge double-stage compressor is improve, while also reducing compressor cost；Low-pressure stage compression unit includes low-pressure stage
Eccentric part and low-pressure stage roller, hiigh pressure stage compression unit include hiigh pressure stage eccentric part and hiigh pressure stage roller, calculate eccentric rotary inertia
The quality of roller, eccentric throw and angular speed are also contemplated for wherein during power, resulting structures more meet reality, counterbalance effect is more preferable.
The utility model double-stage compressor includes above-mentioned Two-stage Compression machine crankshaft, solves huge discharge double-stage compressor low
The problem arbitrarily downgraded with the out-of-balance force of hiigh pressure stage compression unit eccentric mass, so that the balance weight weight of double-stage compressor can be reduced,
The amount of deflection of bent axle when reducing compressor operating, improves the reliability of huge discharge double-stage compressor.
Brief description of the drawings
Fig. 1 is the schematic diagram of the first structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment one is provided；
Fig. 2 is the broken section of the first structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment one is provided
Figure；
Fig. 3 is the schematic diagram of second structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment one is provided；
Fig. 4 is the top view of second structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment one is provided；
Fig. 5 is the schematic diagram of the third structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment one is provided；
Fig. 6 is the top view of the third structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment one is provided；
Fig. 7 is the eccentric rotary inertia force of the calculating Two-stage Compression machine crankshaft that the utility model preferred embodiment one is provided
Schematic diagram；
Fig. 8 is the structural representation of the Two-stage Compression machine crankshaft that the utility model preferred embodiment two is provided；
Fig. 9 is the broken section of the first structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment three is provided
Figure；
Figure 10 is the sectional view of the low-pressure stage roller that the utility model preferred embodiment three is provided；
Figure 11 is the partial cutaway of second structure of the Two-stage Compression machine crankshaft that the utility model preferred embodiment three is provided
View；
Figure 12 is the sectional view of the double-stage compressor that the utility model preferred embodiment four is provided；
Figure 13 is the eccentric rotary inertia force of the calculating Two-stage Compression machine crankshaft that the utility model preferred embodiment four is provided
With the schematic diagram of eccentric rotary moment of inertia.
In figure：
1st, bent axle main body；2nd, low-pressure stage eccentric part；3rd, hiigh pressure stage eccentric part；4th, low-pressure stage roller；5th, hiigh pressure stage roller；6、
Rotor；21st, through hole；22nd, crescent hole；23rd, reinforcement；24th, eccentric part groove；41st, roller groove；61st, main balance weight；62nd, it is secondary
Balance weight.
Specific embodiment
Further illustrate the technical solution of the utility model below in conjunction with the accompanying drawings and by specific embodiment.
Preferred embodiment one：
This preferred embodiment discloses a kind of Two-stage Compression machine crankshaft.As shown in Figures 1 to 7, the Two-stage Compression machine crankshaft bag
Bent axle main body 1 is included, low-pressure stage eccentric part 2 and hiigh pressure stage eccentric part 3, the outer sheath of low-pressure stage eccentric part 2 are provided with bent axle main body 1
Low-pressure stage roller 4 is provided with, the outside of hiigh pressure stage eccentric part 3 is arranged with hiigh pressure stage roller 5, the eccentric rotary inertia of low-pressure stage compression unit
Power is equal to the eccentric rotary inertia force of hiigh pressure stage compression unit, and eccentric rotary inertia force is equal to quality m, eccentric throw r and angular velocity omega
Square product, i.e.,：m1r1ω2=m2r2ω2, divide out ω2Obtain：m1r1=m2r2.Wherein, low-pressure stage compression unit includes that low-pressure stage is inclined
Center portion 2 and low-pressure stage roller 4, hiigh pressure stage compression unit include hiigh pressure stage eccentric part 3 and hiigh pressure stage roller 5.
The eccentric rotary inertia force of low-pressure stage compression unit is made equal to the eccentric rotary inertia force of hiigh pressure stage compression unit, so that can
Reduce the weight that double-stage compressor uses balance weight, the amount of deflection of bent axle, improves huge discharge twin-stage pressure when reducing compressor operating
The reliability of contracting machine, reduces compressor cost；By the quality m of roller, eccentric throw r and angular speed during calculating eccentric rotary inertia force
ω is also contemplated for wherein, and resulting structures more meet reality, and counterbalance effect is more preferable.
The eccentric rotary inertia force of hiigh pressure stage compression unit is equal to for the eccentric rotary inertia force for making low-pressure stage compression unit, can
To increase the eccentric rotary inertia force (including quality or eccentric throw of increase hiigh pressure stage compression unit) of hiigh pressure stage compression unit, it is also possible to
Reduce the eccentric rotary inertia force (including reducing the quality or eccentric throw of low-pressure stage compression unit) of low-pressure stage compression unit, preferably subtract
The quality of small low-pressure stage compression unit, can not so change the overall structure of compressor.
The concrete mode for reducing low-pressure stage compression unit quality is not limited, it is preferred that along bent axle main body on low-pressure stage eccentric part 2
1 axis direction is provided with least one through hole 21 and/or blind hole.As depicted in figs. 1 and 2, the through hole 21 and/or blind hole can be with
It is circular hole；Can also be other shapes, as shown in Figure 3 and Figure 4, through hole 21 and/or blind hole are crescent hole 22, and crescent hole 22 is along vertical
Straight is in crescent shape in the section on the axis direction of bent axle main body 1, and weight loss effect is obvious；As shown in Figure 5 and Figure 6, in crescent hole
22 middle part is provided with reinforcement 23, and one end of reinforcement 23 is connected on the side arcwall face of crescent hole 22, other end connection
On the opposite side arcwall face of crescent hole 22, the structural strength of low-pressure stage eccentric part 2 is increased in the case where loss of weight is not influenceed, kept away
Exempt from low-pressure stage eccentric part 2 to be damaged when by external force collision or vibration.
Preferred embodiment two：
This preferred embodiment discloses a kind of Two-stage Compression machine crankshaft, and its structure is essentially identical with preferred embodiment one.It is different
Part is, as shown in figure 8, being formed with eccentric part on the lateral surface of the axis away from bent axle main body 1 of low-pressure stage eccentric part 2
Groove 24.
Preferred embodiment three：
This preferred embodiment discloses a kind of Two-stage Compression machine crankshaft, and its structure is essentially identical with preferred embodiment one.It is different
Part is as shown in Figs. 9 to 11, roller groove 41 to be formed with the inwall of low-pressure stage roller 4.Preferably, roller groove
41 inwall at least around low-pressure stage roller 4 on the axis direction perpendicular to bent axle main body 1 is enclosed.Wherein it is possible to such as Fig. 9 institutes
Show that low-pressure stage roller 4 is located at the position of the lower end of bent axle main body 1, hiigh pressure stage roller 5 is located at the top of low-pressure stage roller 4；
Hiigh pressure stage roller 5 can also be located at the position of the lower end of bent axle main body 1 as shown in figure 11, low-pressure stage roller 4 is located at high pressure
The top of level roller 5, does not influence the balance of the Two-stage Compression machine crankshaft.
Preferred embodiment four：
This preferred embodiment discloses a kind of double-stage compressor.As shown in figure 12, the double-stage compressor includes such as being preferable to carry out
Any described Two-stage Compression machine crankshaft in example one to three.Double-stage compressor also includes rotor 6, is provided with rotor 6 main flat
Weighing apparatus block 61 and secondary balance weight 62, by turning that low-pressure stage compression unit, hiigh pressure stage compression unit, main balance weight 61 and secondary balance weight 62 are constituted
Subsystem meets static balance and dynamically balanced condition simultaneously.
As shown in figure 13, during static balance, the eccentric rotation of the eccentric rotary inertia force of low-pressure stage compression unit and secondary balance weight 62
Turn inertia force sum equal to the eccentric rotary inertia force of hiigh pressure stage compression unit and the eccentric rotary inertia force sum of main balance weight 61,
Eccentric rotary inertia force be equal to quality m, eccentric throw r and angular velocity omega square product, i.e.,：
m1r1ω2+m4r4ω2=m2r2ω2+m3r3ω2
Divide out ω2Obtain：m1r1+m4r4=m2r2+m3r3。
Wherein, m1It is the quality of low-pressure stage eccentric part 2, r1It is the eccentric throw of low-pressure stage eccentric part 2；m2For hiigh pressure stage is eccentric
The quality in portion 3, r2It is the eccentric throw of hiigh pressure stage eccentric part 3；m3It is the quality of main balance weight 61, r3It is the bias of main balance weight 61
Away from；m3It is the quality of secondary balance weight 62, r3It is the eccentric throw of secondary balance weight 62.
During dynamic balancing, the eccentric rotary moment of inertia of low-pressure stage compression unit and the eccentric rotary moment of inertia of main balance weight 61
Sum is equal to the eccentric rotary moment of inertia of hiigh pressure stage compression unit and the eccentric rotary moment of inertia sum of secondary balance weight 62, eccentric
Rotatory inertia torque be equal to the distance between quality m, eccentric throw r, center of gravity and specified point L (specified point can be any position,
As long as the Two-stage Compression machine crankshaft at a certain position relative to that can reach dynamic balancing, then it puts down relative to any position all in dynamic
Weighing apparatus) and angular velocity omega square product, i.e.,：
m1r1L1ω2+m3r3L3ω2=m2r2L2ω2+m4r4L4ω2。
Wherein, m1It is the quality of low-pressure stage eccentric part 2, r1It is the eccentric throw of low-pressure stage eccentric part 2, L1For low-pressure stage is eccentric
The distance between the center of gravity and specified point in portion 2；m2It is the quality of hiigh pressure stage eccentric part 3, r2It is the eccentric throw of hiigh pressure stage eccentric part 3,
L2The distance between center of gravity and specified point for hiigh pressure stage eccentric part 3；m3It is the quality of main balance weight 61, r3It is main balance weight 61
Eccentric throw, L3The distance between center of gravity and specified point for main balance weight 61；m3It is the quality of secondary balance weight 62, r3For pair is flat
The eccentric throw of weighing apparatus block 62, L4The distance between center of gravity and specified point for secondary balance weight 62.
Note, above are only preferred embodiment of the present utility model and the know-why used.Those skilled in the art
It will be appreciated that the utility model is not limited to specific embodiment described here, can carry out for a person skilled in the art various
Significantly change, readjust and substitute without departing from protection domain of the present utility model.Therefore, although implement more than
Example is described in further detail to the utility model, but the utility model is not limited only to above example, is not taking off
In the case of conceiving from the utility model, more other Equivalent embodiments can also be included, and scope of the present utility model is by institute
Attached right is determined.
Claims (10)
1. a kind of Two-stage Compression machine crankshaft, including bent axle main body (1), low-pressure stage eccentric part is provided with the bent axle main body (1)
(2) and hiigh pressure stage eccentric part (3), low-pressure stage eccentric part (2) outside is arranged with low-pressure stage roller (4), and the hiigh pressure stage is inclined
Center portion (3) outside is arranged with hiigh pressure stage roller (5), it is characterised in that the eccentric rotary inertia force of low-pressure stage compression unit is equal to height
Arbitrarily downgrade the eccentric rotary inertia force of compression unit；
The low-pressure stage compression unit includes the low-pressure stage eccentric part (2) and the low-pressure stage roller (4), the hiigh pressure stage compression
Portion includes the hiigh pressure stage eccentric part (3) and the hiigh pressure stage roller (5).
2. Two-stage Compression machine crankshaft according to claim 1, it is characterised in that the edge on the low-pressure stage eccentric part (2)
The axis direction of the bent axle main body (1) is provided with least one through hole (21) and/or blind hole.
3. Two-stage Compression machine crankshaft according to claim 2, it is characterised in that the through hole (21) and/or the blind hole
It is crescent hole (22) that the crescent hole (22) is in crescent shape along the section on the axis direction of the bent axle main body (1).
4. Two-stage Compression machine crankshaft according to claim 3, it is characterised in that set at the middle part of the crescent hole (22)
There is a reinforcement (23), one end of the reinforcement (23) is connected on the side arcwall face of the crescent hole (22), the other end connects
It is connected on the opposite side arcwall face of the crescent hole (22).
5. Two-stage Compression machine crankshaft according to claim 2, it is characterised in that the through hole (21) and/or the blind hole
It is circular hole.
6. Two-stage Compression machine crankshaft according to claim 1, it is characterised in that in the remote of the low-pressure stage eccentric part (2)
Eccentric part groove (24) is formed with the lateral surface of the axis of the bent axle main body (1).
7. Two-stage Compression machine crankshaft according to claim 1, it is characterised in that in the inwall of the low-pressure stage roller (4)
On be formed with roller groove (41).
8. Two-stage Compression machine crankshaft according to claim 7, it is characterised in that the roller groove (41) is perpendicular to institute
The inwall at least one on the axis direction of bent axle main body (1) around the low-pressure stage roller (4) is stated to enclose.
9. a kind of double-stage compressor, it is characterised in that bent including the double-stage compressor as any one of claim 1 to 8
Axle.
10. double-stage compressor according to claim 9, it is characterised in that the double-stage compressor also includes rotor (6),
Main balance weight (61) and secondary balance weight (62) are provided with the rotor (6), by low-pressure stage compression unit, hiigh pressure stage compression unit, master
The rotor-support-foundation system that balance weight (61) and secondary balance weight (62) are constituted meets static balance and dynamically balanced condition simultaneously；
During static balance, the eccentric rotary inertia of the eccentric rotary inertia force of the low-pressure stage compression unit and the secondary balance weight (62)
Power sum is equal to the eccentric rotary inertia force of the hiigh pressure stage compression unit and the eccentric rotary inertia force of the main balance weight (61)
Sum, the eccentric rotary inertia force be equal to quality, eccentric throw and angular speed square product；
During dynamic balancing, the eccentric rotary of the eccentric rotary moment of inertia of the low-pressure stage compression unit and the main balance weight (61) is used to
Property torque sum be equal to the eccentric rotary moment of inertia of the hiigh pressure stage compression unit and the eccentric rotary of the secondary balance weight (62)
Moment of inertia sum, the eccentric rotary moment of inertia be equal to the distance between quality, eccentric throw, center of gravity and specified point and
Angular speed square product.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621089821.8U CN206206378U (en) | 2016-09-28 | 2016-09-28 | Two-stage Compression machine crankshaft and double-stage compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621089821.8U CN206206378U (en) | 2016-09-28 | 2016-09-28 | Two-stage Compression machine crankshaft and double-stage compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206206378U true CN206206378U (en) | 2017-05-31 |
Family
ID=58762608
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621089821.8U Expired - Fee Related CN206206378U (en) | 2016-09-28 | 2016-09-28 | Two-stage Compression machine crankshaft and double-stage compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206206378U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286573A (en) * | 2016-09-28 | 2017-01-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Two-stage Compression machine crankshaft and double-stage compressor |
| CN109307499A (en) * | 2018-11-02 | 2019-02-05 | 常州大学 | A method of calculating the eccentric distance of motor eccentric shaft using Hookean spring |
| WO2019134364A1 (en) * | 2018-01-08 | 2019-07-11 | 瑞智精密股份有限公司 | Compressor crankshaft and compressor having same |
| CN110873051A (en) * | 2018-08-31 | 2020-03-10 | 广东美芝精密制造有限公司 | Double-cylinder rotary compressor and crankshaft thereof |
-
2016
- 2016-09-28 CN CN201621089821.8U patent/CN206206378U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286573A (en) * | 2016-09-28 | 2017-01-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Two-stage Compression machine crankshaft and double-stage compressor |
| WO2019134364A1 (en) * | 2018-01-08 | 2019-07-11 | 瑞智精密股份有限公司 | Compressor crankshaft and compressor having same |
| CN110873051A (en) * | 2018-08-31 | 2020-03-10 | 广东美芝精密制造有限公司 | Double-cylinder rotary compressor and crankshaft thereof |
| CN109307499A (en) * | 2018-11-02 | 2019-02-05 | 常州大学 | A method of calculating the eccentric distance of motor eccentric shaft using Hookean spring |
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Granted publication date: 20170531 |