CN206159025U - Compressor crankshaft and rotary compressor - Google Patents
Compressor crankshaft and rotary compressor Download PDFInfo
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- CN206159025U CN206159025U CN201621116200.4U CN201621116200U CN206159025U CN 206159025 U CN206159025 U CN 206159025U CN 201621116200 U CN201621116200 U CN 201621116200U CN 206159025 U CN206159025 U CN 206159025U
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- compressor
- crank shaft
- length
- eccentric part
- ratio
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Abstract
The utility model provides a compressor crankshaft and rotary compressor, compressor crankshaft includes eccentric portion, off -centre portion is including the active section that is used for installing the compressing mechanism, the ratio of the length of active section and the total length of off -centre portion is between 0.5~0.9. Rotary compressor includes above -mentioned compressor crankshaft. The utility model discloses an establish the ratio of the total length of the length that is used for installing the active section of compressing mechanism in the off -centre portion and off -centre between 0.5 to 0.9, it is lubricated to guarantee can to form good fluid dynamic between off -centre portion and the compressing mechanism on the one hand, thereby reduce the inordinate wear consumption, on the other hand can also guarantee that the rotation velocity of compressing mechanism can not be too big, thereby make the relative slip speed between compressing mechanism and the blade head can not be too big, and then reduce the friction loss that arouses because of relative slip speed is too big.
Description
Technical field
The utility model is related to compressor field, more particularly to a kind of compressor crank shaft and rotary compressor.
Background technology
In refrigeration, air-conditioning system, topmost energy consumption comes from compressor, therefore, the raising of compressor efficiency has
Extremely important meaning, especially widely used rotary compressor.
In rotary compressor, rotor is installed on bent axle and drives bent axle to rotate, and at the same time, is installed on song
Piston on the eccentric part of axle does autobiography and revolution motion (wherein, between piston and the eccentric part of bent axle with the rotation of bent axle
Lubricating oil is full of, to form hydrodynamic lubrication).Rotary compressor by piston and cylinder, blade and upper and lower cylinder cap it
Between formed crescent-shaped space periodically increase and reduce, it is achieved thereby that the suction of cold-producing medium, compression and discharge.
But, in current rotary compressor structure, the frictional dissipation between all parts improves rotation than larger
The operation energy consumption of formula compressor.Therefore, in order to lift the efficiency of rotary compressor, it is necessary to the structure to rotary compressor
Be optimized, to reduce the rotary compressor course of work in frictional dissipation.
Utility model content
The purpose of this utility model is to provide a kind of compressor crank shaft and rotary compressor, to solve prior art
Middle rotary compressor frictional dissipation problems of too, lifts the efficiency of rotary compressor.
Further, the utility model provides a kind of compressor crank shaft, including eccentric part, and the eccentric part is included for installing
The ratio of the total length of the active section of compression mechanism, the length of the active section and the eccentric part is between 0.5～0.9.
Preferably, the invariablenes turning speed of the compressor crank shaft, and the overall length of the length of the active section and the eccentric part
The ratio of degree is between 0.7～0.85.
Preferably, the rotating speed of the compressor crank shaft is 3000rpm.
Preferably, the rotating speed of the compressor crank shaft is non-constant, and the length of the active section is total with the eccentric part
The ratio of length is between 0.75～0.9.
Preferably, the rotating speed of the compressor crank shaft is between 1000～4000rpm.
Preferably, the rotating speed of the compressor crank shaft is non-constant, and the length of the active section is total with the eccentric part
The ratio of length is between 0.65～0.75.
Preferably, the rotating speed of the compressor crank shaft is between 4000～7200rpm.
The utility model also provides a kind of rotary compressor, including the compressor crank shaft described in as above any one.
Preferably, the rotary compressor is also described on the active section of the compressor crank shaft including being socketed on
Compression mechanism.
Preferably, the rotary compressor is constant speed compressor or frequency-changeable compressor.
In sum, in the technical solution of the utility model, by being used to install pressure on the eccentric part by compressor crank shaft
The ratio of the length of the active section of contracting mechanism (compression mechanism is mainly piston) and the total length of eccentric part be located at 0.5 to 0.9 it
Between, on the one hand can ensure that and good hydrodynamic lubrication is formed between eccentric part and compression mechanism, so as to solve between the two
The inordinate wear problem of appearance, reduces inordinate wear power consumption, on the other hand can ensure that the rotational velocity of compression mechanism will not mistake
Greatly, so that the relative sliding velocity between compression mechanism and leaf head is not too large, and then reduce because of relative speed of sliding
The frictional dissipation for causing greatly is spent, in addition, within the above range, the difficulty of processing of compressor crank shaft is appropriate, and suitable for many
Plant refrigerant.
Description of the drawings
Fig. 1 is the schematic diagram of the compressor crank shaft of the embodiment of the utility model one；
Fig. 2 is the end view of the compression mechanism of the embodiment of the utility model one；
Fig. 3 is the compressor for different rotating speeds of the embodiment of the utility model one, the work of the eccentric part of compressor crank shaft
Make the length of section with the ratio of eccentric part total length and the graph of relation of the coefficient of performance of compressor.
Description of reference numerals is as follows：
1- compressor crank shafts；
11- major axis；12- short axles；13- eccentric parts；131- active sections；
2- compression mechanisms；
21- pistons；22- cylinders；23- blades；24- crescent-shaped spaces；
The length of h- active sections；The total length of H- eccentric parts.
Specific embodiment
Applicant's research finds, when piston is installed on the eccentric part of compressor crank shaft, its effective contact with eccentric part
Height has large effect with the ratio of the total height of eccentric part to the Performance And Reliability of compressor.Specifically, piston is worked as
When less with the effective contact of eccentric part height, hydrodynamic lubrication is hardly formed between piston and eccentric part, so as to cause
Inordinate wear between the two, increases abrasion power consumption.When the effective contact of piston and eccentric part is highly larger, piston is from rotating speed
Degree can be accelerated so that the relative sliding velocity of piston and leaf head increases, and friction power loss increases.Applicant further send out by research
It is existing, if piston is set in more than or equal to 0.4 and is less than with the effective contact height of eccentric part with the ratio of the total height of eccentric part
During 0.5 scope, the Energy Efficiency Ratio of compressor is relatively low, it can be seen that, the compressor crank shaft in the range of this is unsatisfactory.
Found based on the studies above, the utility model proposes a kind of compressor crank shaft, to solve prior art in rotate
The frictional dissipation of formula compressor is than larger problem.Below in conjunction with accompanying drawing 1 to Fig. 3 pair the utility model proposes compressor crank shaft make
Further describe.It should be noted that, accompanying drawing using very simplify in the form of and use non-accurately ratio, only to
Purpose that is convenient, lucidly aiding in illustrating the utility model embodiment.
As used in the specification and the appended claims, singulative "a", "an" and "the" includes
Plural reference, in addition to non-content is explicitly pointed out in addition.As used in the specification and the appended claims, term "or"
Typically used with including the implication of "and/or", in addition to non-content is explicitly pointed out in addition.
As shown in figure 1, it is the schematic diagram of the compressor crank shaft of the embodiment of the utility model one, the compressor of the present embodiment
Bent axle 1 is particularly the bent axle used on rotary compressor, and it includes major axis 11, short axle 12 and eccentric part 13, the eccentric part
13 are arranged on major axis 11, or are arranged in short axle 12, it is also possible to while being arranged on major axis 11 and short axle 12.The major axis
11 are used to install rotor, to rotate under the driving of rotor.
Wherein, the eccentric part 13 includes active section 131, and the active section 131 is overall diametrically to protrude from eccentric part 13,
For installing piston 21, (piston 21 is subordinated in the present embodiment compression mechanism 2, and is illustrated in Fig. 2, and Fig. 2 is that this practicality is new
The end view of the compression mechanism of the embodiment of type one).Wherein, the piston 21 does rotation and revolution under the driving of bent axle 1
Motion, and crescent-shaped space 24 is formed between cylinder 22, blade 23, upper cylinder cover and lower cylinder cap, and (crescent-shaped space 24 is commonly referred to as
For working chamber), periodically increase and reduce by crescent-shaped space 24, realize suction, compression and the discharge of cold-producing medium.It is described
Piston 21 has an endoporus, is socketed on active section 131 by the endoporus, and the length of the endoporus is more than or equal to active section
131 length (i.e. axial length).
Particularly, length h of the active section 131 is set in satisfaction with ShiShimonoseki with the ratio of the total length H of eccentric part 13
System：
0.5≤h/H≤0.9 (1)
In above-mentioned ratio range, when the timings of total length H mono- of eccentric part 13, in the length h satisfaction of the active section 131
After stating relation, then, in the case where the difficulty of processing for ensureing bent axle 1 is appropriate, it is possible to obtain preferably COP (compressor performances
Coefficient), and while the rotary compressor being suitable under various refrigerants.
Further, when the invariablenes turning speed of the compressor crank shaft 1, i.e., when compressor is constant speed compressor, the work
The ratio for making length h of section 131 and the total length H of eccentric part 13 is preferably set in and meets following relation：
0.7≤h/H≤0.85 (2)
In the ratio range of formula (2), constant speed compressor can obtain preferably COP.
Further, applicant through studying for a long period of time find obtain shown in Fig. 3 under different rotating speeds, the eccentric part 13
Active section 131 length h and eccentric part 13 total length H ratio and COP graph of a relation, in Fig. 3, what ordinate was indicated is
Coefficient of performance, what abscissa was indicated is the ratio h/H of length h with the total length H of eccentric part 13 of active section 131.
As seen from Figure 3, when compressor is constant speed compressor and rotating speed is, for example, 3000rpm, the length of the active section 131
When the ratio of the total length H of degree h and eccentric part 13 is between 0.7～0.85, preferably COP can be obtained.
In one embodiment, when the rotating speed of the compressor crank shaft 1 is non-constant, i.e., compressor is frequency-changeable compressor
When, length h of the active section 131 is preferably set in the ratio of the total length H of eccentric part 13 and meets following relation：
0.75≤h/H≤0.9 (3)
In the ratio range of formula (3), preferably select the rotating speed of compressor crank shaft 1 between 1000～4000rpm, make
Frequency-changeable compressor can obtain preferably COP, concrete example is as illustrated in FIG. 3.In Fig. 3, when compressor is frequency-changeable compressor
And rotating speed is when being, for example, 4000rpm, the ratio of length h of the active section 131 and the total length H of eccentric part 13 0.75～
When between 0.9, COP is preferable.
In another embodiment, when the rotating speed of the compressor crank shaft 1 is non-constant, i.e., compressor is frequency-changeable compressor
When, length h of the active section 131 is preferably set in the ratio of the total length H of eccentric part 13 and meets following relation：
0.65≤h/H≤0.75 (4)
In the ratio range of formula (4), preferably select the rotating speed of compressor crank shaft 1 between 4000～7200rpm, make
Frequency-changeable compressor can obtain preferably COP, concrete example is as illustrated in FIG. 3.In Fig. 3, when compressor is frequency-changeable compressor
And rotating speed is when being, for example, 5000rpm or 6000rpm, the ratio of length h of the active section 131 and the total length H of eccentric part 13
When between 0.75～0.9, COP is equally preferable.
In order to illustrate the performance of the compressor crank shaft 1 of the present embodiment, the present embodiment has made corresponding survey to compressor crank shaft 1
Examination, to verify the lifting situation of compressor efficiency.Implementation below will be explained in detail compressor crank shaft 1 and its corresponding test
As a result.
In the present embodiment, employ two kinds of rotary compressor to verify the lifting situation of compressor efficiency, its
Middle one kind is constant speed compressor, and another kind is frequency-changeable compressor, and frequency-changeable compressor sets three kinds of rotating speeds, specific as follows：
(a), in constant speed compressor, selection of speed 3000rpm, and the ratio of h/H is set between 0.7～0.85；
(b), in the first frequency-changeable compressor, selection of speed 4000rpm, and the ratio of h/H be set in 0.75～0.9 it
Between.
(c), in second frequency-changeable compressor：Selection of speed 5000rpm, and the ratio of h/H is set in 0.65～0.75
Between；
(d), in the third frequency-changeable compressor, selection of speed 6000rpm, and the ratio of h/H is set in 0.65～0.75
Between.
Further, applicant by compression efficiency to above-mentioned rotary compressor, (herein, compression efficiency is also referred to as
COP) measure, obtain：Rotary compressor within the above range, its COP is in optimum range, so as to compressor is total
Frictional dissipation it is smaller, efficiency is high.
Further, the present embodiment additionally provides a kind of rotary compressor including above-mentioned compressor bent axle 1.The pressure
Contracting machine crankshaft 1 is arranged in the compression case body of rotary compressor, can do high speed rotary motion under the support of metal (upper,
So that the acting of compression mechanism compressed gas.Because the rotary compressor of the present embodiment adopts the compressor crank shaft 1 of the present embodiment,
So the beneficial effect brought by compressor crank shaft 1, please accordingly refers to above-described embodiment.
It should be noted that " rotating speed " that refer in above-described embodiment can both refer to the rotating speed of compressor, it is also possible to finger pressure
The rotating speed of the rotating speed of contracting machine crankshaft 1, i.e. compressor is equal to the rotating speed of compressor crank shaft 1.
In sum, in the technical solution of the utility model, by being used to install work on the eccentric part by compressor crank shaft
The ratio of the length of the active section of plug and the total length of eccentric part is located between 0.5 to 0.9, on the one hand can ensure that eccentric part and
Good hydrodynamic lubrication is formed between piston, so as to the inordinate wear for solving the problems, such as to occur between the two, abnormal mill is reduced
Power consumption is damaged, on the other hand can ensure that the rotational velocity of piston will not be excessive, so that the phase between piston and leaf head
It is not too large to sliding speed, and then reduce the frictional dissipation caused because of relative sliding velocity increase, in addition, in above range
Interior, the difficulty of processing of compressor crank shaft is appropriate, and goes for the rotary compressor under various refrigerants.
Foregoing description is only the description to the utility model preferred embodiment, not to any limit of the utility model scope
Calmly, the those of ordinary skill in the utility model field does according to the disclosure above content any change, modification, belonging to right will
Seek the protection domain of book.
Claims (10)
1. a kind of compressor crank shaft, including eccentric part, it is characterised in that the eccentric part includes the work for installing compression mechanism
Make the ratio of total length of section, the length of the active section and the eccentric part between 0.5～0.9.
2. compressor crank shaft as claimed in claim 1, it is characterised in that the invariablenes turning speed of the compressor crank shaft, and it is described
The ratio of the total length of the length of active section and the eccentric part is between 0.7～0.85.
3. compressor crank shaft as claimed in claim 2, it is characterised in that the rotating speed of the compressor crank shaft is 3000rpm.
4. compressor crank shaft as claimed in claim 1, it is characterised in that the rotating speed of the compressor crank shaft is non-constant, and institute
The ratio of the length of active section and the total length of the eccentric part is stated between 0.75～0.9.
5. compressor crank shaft as claimed in claim 4, it is characterised in that the rotating speed of the compressor crank shaft 1000～
Between 4000rpm.
6. compressor crank shaft as claimed in claim 1, it is characterised in that the rotating speed of the compressor crank shaft is non-constant, and institute
The ratio of the length of active section and the total length of the eccentric part is stated between 0.65～0.75.
7. compressor crank shaft as claimed in claim 6, it is characterised in that the rotating speed of the compressor crank shaft 4000～
Between 7200rpm.
8. a kind of rotary compressor, it is characterised in that bent including compressor as claimed in any of claims 1 to 7 in one of claims
Axle.
9. rotary compressor as claimed in claim 8, it is characterised in that also including the institute for being socketed on the compressor crank shaft
State the compression mechanism on active section.
10. rotary compressor as claimed in claim 8, it is characterised in that the rotary compressor is constant speed compressor
Or frequency-changeable compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621116200.4U CN206159025U (en) | 2016-10-12 | 2016-10-12 | Compressor crankshaft and rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621116200.4U CN206159025U (en) | 2016-10-12 | 2016-10-12 | Compressor crankshaft and rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206159025U true CN206159025U (en) | 2017-05-10 |
Family
ID=58652861
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621116200.4U Active CN206159025U (en) | 2016-10-12 | 2016-10-12 | Compressor crankshaft and rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206159025U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109083923A (en) * | 2017-06-14 | 2018-12-25 | 上海海立电器有限公司 | Crankshaft, rolling rotor-type micro-compressor and refrigeration system |
| CN109899291A (en) * | 2017-12-11 | 2019-06-18 | 南昌海立电器有限公司 | Compressor and its support construction |
| CN111441944A (en) * | 2019-01-16 | 2020-07-24 | 上海海立电器有限公司 | Crankshaft eccentric part supporting structure and rotor type compressor |
-
2016
- 2016-10-12 CN CN201621116200.4U patent/CN206159025U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109083923A (en) * | 2017-06-14 | 2018-12-25 | 上海海立电器有限公司 | Crankshaft, rolling rotor-type micro-compressor and refrigeration system |
| CN109083923B (en) * | 2017-06-14 | 2024-03-08 | 上海海立电器有限公司 | Crankshaft, rolling rotor type micro compressor and refrigerating system |
| CN109899291A (en) * | 2017-12-11 | 2019-06-18 | 南昌海立电器有限公司 | Compressor and its support construction |
| CN111441944A (en) * | 2019-01-16 | 2020-07-24 | 上海海立电器有限公司 | Crankshaft eccentric part supporting structure and rotor type compressor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 201206 Pudong New Area Jinqiao Ning Road, Shanghai, No. 888 Patentee after: Shanghai Haili Electrical Appliance Co. Ltd. Address before: 201206 Pudong New Area Jinqiao Ning Road, Shanghai, No. 888 Patentee before: Rili Electric Appliance Co., Ltd., Shanghai |
|
| CP01 | Change in the name or title of a patent holder | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20180419 Address after: 621000 188 Mianyang Road, Mianyang economic and Technological Development Zone, Sichuan Co-patentee after: Shanghai Haili Electrical Appliance Co. Ltd. Patentee after: Mianyang Haili Electrical Appliance Co. Ltd. Address before: 201206 Pudong New Area Jinqiao Ning Road, Shanghai, No. 888 Patentee before: Shanghai Haili Electrical Appliance Co. Ltd. |
|
| TR01 | Transfer of patent right |