CN109958622A - A kind of rolling rotor compressor - Google Patents
A kind of rolling rotor compressor Download PDFInfo
- Publication number
- CN109958622A CN109958622A CN201711422203.XA CN201711422203A CN109958622A CN 109958622 A CN109958622 A CN 109958622A CN 201711422203 A CN201711422203 A CN 201711422203A CN 109958622 A CN109958622 A CN 109958622A
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- Prior art keywords
- cylinder
- compressor
- crankshaft
- diameter
- rolling rotor
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/10—Stators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/601—Shaft flexion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2250/00—Geometry
- F04C2250/30—Geometry of the stator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/12—Vibration
- F04C2270/125—Controlled or regulated
Abstract
The present invention relates to a kind of rolling rotor compressor, including shell, motor, crankshaft, cylinder, the ratio between the internal diameter d of the cylinder and the outer diameter D of motor: 0.41≤d/D < 1.The ratio of the internal diameter d of the eccentricity Q and cylinder of the crankshaft are as follows: 0.05≤Q/d≤0.11.Compared with prior art, the present invention is able to satisfy the duplex cylinder compressor of EMC requirement in small shell diameter and large shell caliber, moreover it is possible to meet the EMC requirement of single cylinder compressor, and good compression property, at low cost.
Description
Technical field
The present invention relates to rolling rotor compressors, are applicable in the refrigerating fields such as air-conditioning, refrigerator.
Background technique
Rolling rotor type cold compressor is also referred to as rolling piston type refrigerating compressor, is a kind of rotary compression of displacement type
Machine.It is to make rolling movement and one and rolling-rotor in cylindrical cylinder by the eccentric rolling-rotor being installed in cylinder
The refrigeration compressor of gas compression is realized in the reciprocating motion for the slide plate being in contact.
Compressor first has to determine its discharge capacity, and discharge capacity is exactly that crankshaft turns around the refrigerating capacity of discharge, refrigerating capacity and compressor
Delivery space V it is directly related, can be calculated by following formula, set cylinder bore diameter as d, cylinder height is H, the bias of eccentric shaft
Amount is Q,
Then V=π × Q × (d-e) × H,
In the formula, delivery space V and cylinder bore d are proportional, if wanting to increase delivery space, pass through increase
Cylinder bore d or increase cylinder height, change eccentricity may be implemented.
In current rolling rotor type cold compressor design, increases cylinder height and often result in leakage loss increase, with
And compression efficiency reduces, therefore is not intended to increase delivery space V by increasing cylinder height.But when increasing cylinder bore diameter,
But it is limited by the outer diameter D of rolling rotor type cold compressor motor, the cylinder bore diameter size of rotary compressor is very
Hardly possible expands, the two factors can lead to the unstable of compressor operating, cause the nonlinear object of electric current, to generate humorous
Wave causes Electro Magnetic Compatibility poor.
Seven state of Middle East bay, which pushes forward compressor Electro Magnetic Compatibility (EMC) comprehensively, improves requirement, and second harmonic need to meet certification
It is required that.The basic reason that harmonic wave generates is due to caused by nonlinear load.When electric current flows through load, it is not in added voltage
Linear relationship just forms non-sinusoidal current, to generate harmonic wave.Harmonic current generates harmonic voltage drop on electric network impedance, makes
Voltage waveform deviates sine wave.Endangered after harmonic current vector addition from different harmonic sources it is very big, moment influence be by
In the offset of voltage waveform zero-acrross ing moment, make equipment control failure protection, it is long-term to influence mainly to generate heat but do not do work, cause
Capacitor and rotating electric machine premature aging even damage.In order to improve drawbacks described above, general material following methods in the prior art:
The harmonic wave that EMC filter or reactor etc. generate compressor operating is arranged to be filtered, is wanted to improve EMC
It asks, such as patent ZL201621219319.4 discloses a kind of compressor Control Cprant and air conditioner, passes through the confession in compressor
Reactor with multiple taps is set in electrical circuit, by multiple sub-control units in access control unit, can be opened in compressor
When dynamic, control in some or all of winding access compressor electronic control circuit of reactor, what is generated when to compressor operating is humorous
Wave is filtered, and is avoided in the lower situation of input voltage, and compressor is produced since reactor whole winding accesses on startup
The operating voltage that pressure estranged leads to load on compressor reduces, and causes the abnormal problem of compressor start, while on startup
The winding of reactor also acts as the harmonic wave generated to compressor operating and is filtered effect, improves the reliable of compressor Control Cprant
Property.Patent ZL201520188701.2 discloses a kind of frequency converter of on-off control compressor operation using temperature controller, has
Closed cabinet is equipped with control module in cabinet, it is characterized in that: control module include main control chip, signal input unit,
EMC filter unit, rectification unit, inversion unit, driving unit, busbar voltage detection unit and inverter current detection unit, it is main
Temperature control module, micro control unit, driving engine and the quenched unit of pulsewidth are integrated in control chip, wherein signal input unit will test
To the switching signal of temperature controller be conveyed to temperature control module, temperature control module calculates the practical booting frequency of compressor with this, and will
Practical booting frequency is made comparisons with target booting frequency, adjusts the running frequency of compressor in real time.
But the above method requires additional and needs component, increased costs, and is unfavorable for the miniaturization of compressor
Design.
Summary of the invention
That it is an object of the present invention to overcome the above-mentioned drawbacks of the prior art and provide a kind of constitutional balances is stable,
The good rolling rotor compressor of Electro Magnetic Compatibility.
The purpose of the present invention can be achieved through the following technical solutions: a kind of rolling rotor compressor, including shell,
Motor, crankshaft, cylinder, which is characterized in that the ratio between the internal diameter d of the cylinder and the outer diameter D of motor: 0.41≤d/D < 1.
Preferably, the ratio between the internal diameter d of the cylinder and the outer diameter D of motor: 0.41≤d/D < 0.48.
Preferably, the ratio of the internal diameter d of the eccentricity Q and cylinder of the crankshaft are as follows: 0.05≤Q/d≤0.11.
The compressor for meeting above-mentioned requirements can be large-scale duplex cylinder compressor:
Preferably, the compressor is duplex cylinder compressor, and cylinder includes upper cylinder and lower cylinder, is all provided in each cylinder
There is piston, each piston is separately connected the crankshaft.
Preferably, the crankshaft includes crankshaft body and two eccentric parts being arranged on crankshaft body, two bias
Portion is separately connected the piston in upper cylinder and lower cylinder.
Preferably, the eccentricity of two eccentric parts on the crankshaft body and the ratio of cylinder bore diameter are all larger than or are equal to
0.05, and it is less than or equal to 0.11.
Preferably, the compressor is large-scale compressor, diameter >=130mm of the shell of compressor.Such as it is compressing
The discharge capacity of machine is 19~29cc, and in industry the diameter of the shell of compressor is generally 132mm, and is single cylinder compressor, and
It is not able to satisfy EMC requirement, is duplex cylinder compressor by compressor design according to above-mentioned requirements of the present invention, can satisfy EMC requirement,
Compressor performance such as compression efficiency is attained by a more satisfactory effect simultaneously.
The compressor for meeting above-mentioned requirements can also be small-size double cylinder compressor, diameter < 130mm of the shell of compressor.
Duplex cylinder compressor is made on small shell diameter compressor, piston, the cylinder bore of twin-tub machine are small, crankshaft, quality also phase
It should want light, the stroke of piston is short, so even being in the case where piston keeps identical linear speed, twin-tub machine can be by mentioning
High revolving speed increases the maximum power of compressor, and vibrates more small than single cylinder engine, and exhaust noise is also significantly lower than single cylinder engine,
It is compared under the conditions of same displacement with twin-tub, the movement parts inertia force of single cylinder cannot offset each other, and therefore, the vibration of single cylinder engine is big,
Especially high revolving speed when, this problem shows especially prominent.In addition, single cylinder engine cylinder diameter is larger under conditions of same displacement,
The size of each movement parts is also larger, for example piston, etc..Also it is unfavorable for improving power.Above-mentioned this tendency can increase with discharge capacity
And it is obvious, so as to cause being difficult to meet EMC requirement.Therefore, according to the internal diameter d of cylinder of the present invention and the outer diameter of motor
The ratio between D carrys out the light duty compressor that design diameter is less than 130mm, can be made duplex cylinder compressor (this be current light duty compressor without
What method was accomplished, light duty compressor is single cylinder compressor at present), it is able to satisfy EMC requirement, and compressor performance is excellent.
Small-sized single cylinder compressor, the i.e. shell of single cylinder compressor can also be made in the compressor for meeting above-mentioned requirements of the present invention
Diameter < 130mm under the conditions of the present invention, EMC requirement can be better met, pressed simultaneously and since single cylinder compressor size is small
Contracting efficiency can be also improved.
Although large-scale single cylinder compressor, cylinder diameter is larger, and the size of each movement parts is also larger, for example piston 0 etc., ordinary circumstance
Under be difficult to meet EMC requirement, but if the compressor meets the ratio between internal diameter d and outer diameter D of motor of cylinder of the present invention: 0.41
The condition of≤d/D < 1 also can satisfy EMC requirement.
Compared with prior art, the invention has the following advantages that
1. the present invention can satisfy and be got at present to EMC by the ratio between the internal diameter d of optimization compressor cylinder and outer diameter D of motor
Carry out higher requirement, while cooperating the ratio of the eccentricity Q of optimization crankshaft and the internal diameter d of the cylinder, moreover it is possible to meet compressor
It can require.Various compressors are all suitable for, it is applied widely.
2. the rolling rotor compressor that the present invention designs especially is able to satisfy the requirement currently for compressor miniaturization,
Be less than 130mm in shell diameter may be implemented under conditions of meeting cylinder bore diameter/motor outer diameter >=0.41, develops and meets on small shell diameter
The duplex cylinder compressor that EMC is required, performance and cost all have advantage.Because meeting under above-mentioned condition, the size of cylinder and motor
Reduce, to be installed into the outer diameter of small shell, and will not be because of being reduced in size the injustice for leading to compressor operating
Surely, to improve EMC performance (this is that general small-size double cylinder compressor is difficult to meet and realize).
3. eccentricity/cylinder bore diameter >=0.05~0.11 of the control crankshaft for the duplex cylinder compressor that the present invention uses, guarantees
For compressor motor and cylinder dimensions reduce while, determination can guarantee discharge capacity in 19~29cc.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of rolling rotor compressor of the present invention；
Fig. 2 is the cross-sectional view of crankshaft of the present invention and cylinder.
Specific embodiment
Example embodiment is described more fully with reference to the drawings.However, example embodiment can be with a variety of shapes
Formula is implemented, and is not understood as limited to embodiment set forth herein；On the contrary, thesing embodiments are provided so that the present invention will
Fully and completely, and by the design of example embodiment comprehensively it is communicated to those skilled in the art.It is identical attached in figure
Icon note indicates same or similar structure, thus will omit repetition thereof.
Embodiment 1
As shown in Figure 1, a kind of rolling rotor compressor, including shell 1, motor 2, crankshaft 3 and cylinder, wherein cylinder packet
Upper cylinder 4 and lower cylinder 5 are included, piston is equipped in each cylinder, each piston is separately connected the crankshaft 3.The crankshaft 3 includes
Crankshaft body and two eccentric parts being arranged on crankshaft body, two eccentric parts are separately connected in upper cylinder 4 and lower cylinder 5
Piston.
The diameter of the shell 1 of above-mentioned compressor is 120mm, and discharge capacity is in 19~29cc.
In order to guarantee to install motor 2, crankshaft 3, upper cylinder 4 and lower cylinder 5 in above-mentioned small shell compressor, need to each
The size of building block is reduced, while guaranteeing that meeting discharge capacity while size reduction does not reduce.
Therefore, designing the ratio between the internal diameter d of cylinder (including upper cylinder 4 and lower cylinder 5) and the outer diameter D of motor is 0.41, this
Sample meets each size of components and reduces, while the power between each component maintains the performance of large scale duplex cylinder compressor, and meets EMC
It is required that.
Meanwhile the eccentricity Q (including two respective eccentricity of eccentric part) of the crankshaft 3 and the cylinder (including
Upper cylinder 4 and lower cylinder 5) the ratio of internal diameter d be 0.05, both met size in this way and reduced the compressor that does not reduce of discharge capacity simultaneously
Small form factor requirements.
Above-mentioned eccentricity Q refers to two respective eccentricity of eccentric part, and equal two eccentricity are Q, above-mentioned cylinder
Internal diameter refers to that upper cylinder 4 is equal with the internal diameter of lower cylinder 5, is d.
Embodiment 2
The ratio between the internal diameter d of the cylinder and the outer diameter D of motor: 0.41.
The ratio of the internal diameter d of the eccentricity Q and cylinder of the crankshaft are as follows: 0.11.
Remaining is the same as embodiment 1.
Embodiment 3
The ratio between the internal diameter d of the cylinder and the outer diameter D of motor: 0.5.
The ratio of the internal diameter d of the eccentricity Q and cylinder of the crankshaft are as follows: 0.1.
Remaining is the same as embodiment 1.
Embodiment 4
A kind of rolling rotor compressor, for large-scale duplex cylinder compressor, diameter >=130mm of the shell of compressor.Compression
The discharge capacity of machine is 19~29cc, and in industry the diameter of the shell of compressor is generally 132mm, and is single cylinder compressor, and
It is not able to satisfy EMC requirement, compressor design is duplex cylinder compressor by the present invention, including shell, motor, crankshaft and cylinder, wherein
Cylinder includes upper cylinder and lower cylinder, and piston is equipped in each cylinder, and each piston is separately connected the crankshaft.The crankshaft packet
Two eccentric parts for including crankshaft body and being arranged on crankshaft body, two eccentric parts are separately connected in upper cylinder and lower cylinder
Piston.
The ratio between the internal diameter d of two cylinders and the outer diameter D of motor: 0.41.The eccentricity Q of the crankshaft and the cylinder
The ratio of internal diameter d are as follows: 0.05.Can satisfy EMC requirement, while compressor performance such as compression efficiency be attained by one it is more satisfactory
Effect.
Embodiment 5
The ratio between the internal diameter d of two cylinders and the outer diameter D of motor: < 1.The eccentricity Q of the crankshaft is interior with the cylinder
The ratio of diameter d are as follows: 0.11.Can satisfy EMC requirement, at the same compressor performance such as compression efficiency be attained by one it is more satisfactory
Effect.Remaining is the same as embodiment 4.
Embodiment 6
A kind of rolling rotor compressor, is small-sized single cylinder compressor, and compressor size is less than 130mm, including shell, electricity
Machine, crankshaft and cylinder, the ratio between the internal diameter d of the cylinder and the outer diameter D of motor: 0.43.The eccentricity Q of the crankshaft and institute
State the ratio of the internal diameter d of cylinder are as follows: 0.1.
Embodiment 7
A kind of rolling rotor compressor, for large-scale single cylinder compressor, compressor size is greater than 130mm, including shell, electricity
Machine, crankshaft and cylinder, the ratio between the internal diameter d of the cylinder and the outer diameter D of motor: 0.8.The eccentricity Q of the crankshaft and institute
State the ratio of the internal diameter d of cylinder are as follows: 0.08.
The compressor performance of the various embodiments described above is as shown in the table:
It is particularly shown and described exemplary embodiments of the present invention above.It should be understood that the present invention is not limited to institute
Disclosed embodiment, on the contrary, it is intended to cover comprising various modifications within the scope of the appended claims and equivalent set
It changes.
Claims (9)
1. a kind of rolling rotor compressor, including shell, motor, crankshaft, cylinder, which is characterized in that the cylinder it is interior
The ratio between diameter d and the outer diameter D of motor: 0.41≤d/D < 1.
2. a kind of rolling rotor compressor according to claim 1, which is characterized in that the internal diameter d of the cylinder with
The ratio between outer diameter D of motor: 0.41≤d/D < 0.48.
3. a kind of rolling rotor compressor according to claim 1, which is characterized in that the eccentricity Q of the crankshaft
With the ratio of the internal diameter d of the cylinder are as follows: 0.05≤Q/d≤0.11.
4. a kind of rolling rotor compressor according to claim 1, which is characterized in that the compressor is twin-tub pressure
Contracting machine, cylinder include upper cylinder and lower cylinder, piston are equipped in each cylinder, each piston is separately connected the crankshaft.
5. a kind of rolling rotor compressor according to claim 4, which is characterized in that the crankshaft includes crankshaft sheet
Body and two eccentric parts being arranged on crankshaft body, two eccentric parts are separately connected the piston in upper cylinder and lower cylinder.
6. a kind of rolling rotor compressor according to claim 5, which is characterized in that two on the crankshaft body
The eccentricity of a eccentric part and the ratio of cylinder bore diameter are all larger than or are equal to 0.05, and are less than or equal to 0.11.
7. a kind of rolling rotor compressor according to claim 4, which is characterized in that the compressor is large-scale pressure
Contracting machine, diameter >=130mm of the shell of compressor.
8. a kind of rolling rotor compressor according to claim 4, which is characterized in that the compressor is small-sized pressure
Contracting machine, diameter < 130mm of the shell of compressor.
9. a kind of rolling rotor compressor according to claim 1, which is characterized in that the compressor can also be
Single cylinder compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711422203.XA CN109958622B (en) | 2017-12-25 | 2017-12-25 | Rolling rotor type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711422203.XA CN109958622B (en) | 2017-12-25 | 2017-12-25 | Rolling rotor type compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109958622A true CN109958622A (en) | 2019-07-02 |
| CN109958622B CN109958622B (en) | 2021-06-08 |
Family
ID=67021052
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711422203.XA Active CN109958622B (en) | 2017-12-25 | 2017-12-25 | Rolling rotor type compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109958622B (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110821833A (en) * | 2019-11-29 | 2020-02-21 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
| CN110905812A (en) * | 2019-12-11 | 2020-03-24 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and heat exchange working equipment |
| CN110925200A (en) * | 2019-12-11 | 2020-03-27 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and refrigerating and heating equipment |
| CN110985375A (en) * | 2019-12-11 | 2020-04-10 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and refrigerating and heating equipment |
| CN111043006A (en) * | 2019-12-11 | 2020-04-21 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and heat exchange working equipment |
| CN114370399A (en) * | 2021-12-09 | 2022-04-19 | 珠海格力电器股份有限公司 | Pump body subassembly and doublestage compressor |
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| CN110925200B (en) * | 2019-12-11 | 2021-09-03 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and refrigerating and heating equipment |
| CN110985375B (en) * | 2019-12-11 | 2021-09-03 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and refrigerating and heating equipment |
| CN114370399A (en) * | 2021-12-09 | 2022-04-19 | 珠海格力电器股份有限公司 | Pump body subassembly and doublestage compressor |
| CN114370399B (en) * | 2021-12-09 | 2023-01-17 | 珠海格力电器股份有限公司 | Pump body subassembly and doublestage compressor |
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