CN106762645B - Method for determining viscosity grade of lubricating oil of rotary compressor - Google Patents

Method for determining viscosity grade of lubricating oil of rotary compressor Download PDF

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CN106762645B
CN106762645B CN201611007944.7A CN201611007944A CN106762645B CN 106762645 B CN106762645 B CN 106762645B CN 201611007944 A CN201611007944 A CN 201611007944A CN 106762645 B CN106762645 B CN 106762645B
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lubricating oil
rotary compressor
viscosity
oil
viscosity grade
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CN106762645A (en
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吴建华
李佳宸
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Xian Jiaotong University
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Xian Jiaotong University
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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
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/40—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member
    • F04C18/44—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member with vanes hinged to the inner member
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/40—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member
    • F04C18/46—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member with vanes hinged to the outer member
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2210/00—Fluid
    • F04C2210/14—Lubricant
    • 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
    • F04C2210/00—Fluid
    • F04C2210/24—Fluid mixed, e.g. two-phase fluid
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2210/00—Fluid
    • F04C2210/40—Properties
    • F04C2210/44—Viscosity

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubricants (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

A rotary compressor using R600a or R600 as main refrigerant and using R600a or R600 refrigerant as main compressed medium comprises a closed shell, a motor and a pump body, wherein the bottom space of the shell is stored with lubricating oil; in order to reduce the viscous resistance loss generated by lubricating oil in each friction pair of the rotary compressor and ensure the lubricating performance and the sealing performance of the rotary compressor, the invention combines the working condition and the specific structure of the rotary compressor for analysis and provides an effective lubricating scheme: the lubricating oil has a viscosity grade of ISO8-ISO32, i.e. a viscosity in the range of 8-32cSt at 40 ℃; the lubricating oil viscosity scheme with a specific structure is optimized and optimized according to the suction and exhaust pressure difference and different back pressure structures in the working condition of a specific circulating system; the invention provides an efficient rotary compressor which can effectively lubricate a system such as a refrigerator, a freezer, a refrigeration display rack or a beverage machine and can reduce the viscous resistance loss of lubricating oil.

Description

Method for determining viscosity grade of lubricating oil of rotary compressor
Technical Field
The invention relates to a rotary compressor, in particular to an efficient rotary compressor which is used for a refrigerator or a freezer system, mainly takes an R600a or R600 refrigerant as a compressed medium, can effectively ensure the lubrication and the sealing of a moving part of the compressor, and simultaneously reduces the viscous resistance loss of lubricating oil, and an application thereof.
Background
At present, due to the influence of industrial discharge of Freon refrigerants, the world is suffering from a plurality of serious environmental problems such as ozone layer holes, greenhouse effect and the like. In order to reduce the discharge of chlorine and fluorine atoms in refrigerants and to relieve the pressure of ozone holes, various worldwide circles are trying to develop refrigerant replacement work. Among them, various refrigeration systems such as refrigerators, freezers, cold storage shelves, beverage machines, etc. have adopted hydrocarbons working media such as isobutane R600a or normal butane R600, etc. as main refrigerants, instead of working media such as freon R12 and R134a, etc., to make a staged progress.
Meanwhile, the rotary compressor is widely applied to a vapor compression refrigeration system due to the advantages of compact structure, good dynamic balance performance, high stability and reliability and the like. Particularly, in an air conditioning system with a medium-low cooling capacity (1 p, 1.5 p, etc.), the compressor has become the most important compressor model. And air conditioning systems with high cooling capacity are also actively improved and applied. The electrical appliances such as refrigerators and freezers are common refrigeration appliances like air conditioners, so that the refrigeration system is expected to introduce a rotary compressor as a power core.
To design a rotary compressor suitable for a refrigeration system of a refrigerator, a freezer, etc. in which R600a or R600 is the main refrigerant, it is necessary to optimize for many factors in addition to the design of the mechanical structure. The most prominent factors are: in a refrigeration cycle in which R600a and R600 are refrigerants, the pressure of the refrigerant at the operating pressure of the compressor is much lower than the pressure of a refrigerant that is used in a conventional air conditioner such as R12 and R134a instead of R22 or R410 a. The pressure of the compressor is only about 0.55MPa at the high pressure side, about 0.05MPa at the low pressure side, and the suction pressure is lower than the atmospheric pressure. For the lubricating oil used by the compressor, the selection or the development of the lubricating oil needs to be comprehensively considered according to the load, the rotating speed, the fit clearance and the oil supply mode of the lubricating oil.
While the viscosity grade of the lubricating oil used by the rotary compressor in the prior art is above ISO50, even a lot of lubricating oil exceeds ISO100, and the viscosity is higher. The lubricating oil of the rotary compressor for the air conditioning system was directly used in the rotary compressor using R600a or R600 as the main refrigerant, and the mechanical efficiency was found to be low. This would cause the moving parts inside the compressor to suffer excessive viscous drag of the lubricating oil due to the excessive viscosity, resulting in a large loss of viscous drag, thus reducing the mechanical efficiency of the compressor.
However, if the viscosity of the lubricating oil is reduced blindly, the viscosity of the lubricating oil may be too low. If the viscosity is too low, a lubricating oil film with enough thickness cannot be formed between the friction pairs, effective lubrication cannot be realized, the friction wear of the friction pairs is increased, the mechanical efficiency is reduced, and meanwhile, the leakage of refrigerant is caused, and the volumetric efficiency of the compressor is reduced.
Therefore, the rotary compressor is optimized according to the working conditions of the R600a and R600 systems, and the rotary compressor has high practical significance for the application of the rotary compressor in the systems of refrigerators, freezers and the like.
The excessive viscosity of the lubricating oil can effectively separate two friction surfaces, but can cause excessive viscous resistance loss and reduce the mechanical efficiency; if the viscosity is too low, a lubricating oil film with enough thickness cannot be formed between the friction pairs, effective lubrication cannot be realized, the friction wear of the friction pairs is increased, the mechanical efficiency is reduced, and meanwhile, the leakage of refrigerant is caused, and the volumetric efficiency of the compressor is reduced.
Disclosure of Invention
In order to solve the problems in the prior art, the invention aims to provide a method for determining the viscosity grade of the lubricating oil of the rotary compressor, which determines the viscosity grade range of the lubricating oil suitable for the rotary compressor, can ensure the oil film thickness of a key lubricating position, can reduce the viscous resistance loss of the lubricating oil, ensures that the compressor reaches the highest mechanical efficiency level, and ensures the stability of the compressor.
In order to achieve the purpose, the invention adopts the following technical scheme:
a method for determining the viscosity grade of lubricating oil of a rotary compressor comprises a shell 10, a motor 20 accommodated in the inner space of the shell 10 and a pump body 30 driven by the motor 20, wherein the bottom space of the shell 10 stores lubricating oil 40;
using an R600a or R600 refrigerant as the main compressed medium or a mixed refrigerant as the compressed medium, wherein the total mass fraction of R600a and R600 refrigerants is 60% or more if a mixed refrigerant is used as the compressed medium;
the lubricating oil 40 has a viscosity grade of ISO8-ISO32, i.e., a viscosity of 8cSt-32cSt at 40 ℃.
The viscosity range of the lubricating oil 40 subdivides the suction and exhaust pressure difference interval according to different working conditions of the compressor, and the viscosity grades of the subdivided lubricating oil are shown in the following table:
Figure GDA0002458571000000031
Figure GDA0002458571000000041
the base oil of the lubricating oil is polyester POE oil, polyethylene glycol PAG oil or polyvinyl ether PVE oil.
When the rotary compressor is in a high back pressure structure, the viscosity grade of the lubricating oil is as follows: ISO15-ISO 30.
When the rotary compressor is in a low back pressure structure, the viscosity grade of the lubricating oil is as follows: ISO10-ISO 25.
If a mixed refrigerant is used as the medium to be compressed, the total mass fraction of the R600a and R600 refrigerants is 80% or more.
The control of the viscosity resistance loss generated by the lubricating oil, namely the restriction of the viscosity grade of the lubricating oil, and the pump body structure of the rotary compressor is not limited, and the control method is characterized in that:
the cylinder component is in a rolling piston type, a swinging sliding sheet type, a piston hinge type or a cylinder hinge type;
the pump body structure is a single cylinder structure, a multi-stage cylinder structure or a multi-cylinder parallel structure.
The rotary compressor adopting the method for determining the viscosity grade of the lubricating oil of the rotary compressor.
Compared with the prior art, the invention has the following advantages:
1. the invention analyzes the working condition and the internal condition of the R600a or R600 rotary compressor, determines the viscosity grade range of the lubricating oil suitable for the compressor, can ensure the oil film thickness of the key lubricating position, can reduce the viscous resistance loss of the lubricating oil, ensures that the compressor reaches the highest mechanical efficiency level, and ensures the stability of the compressor.
2. The invention analyzes the different working conditions of the R600a or R600 rotary compressor under different circulation conditions in detail to obtain the applicable viscosity range table related to the pressure difference of suction and exhaust, thereby providing more reference basis for the rotary compressor under different circulation systems when designing lubricating oil.
3. The invention carries out the optimization design of the viscosity grade range of the lubricating oil aiming at different air suction and exhaust structures of the rotary compressor, thereby ensuring that the rotary compressors with different air suction and exhaust structures can efficiently run under the lubrication of proper lubricating oil.
4. The invention optimizes the application range of the lubricating oil of the R600a or the R600 rotary compressor, does not limit the structure and the form of the rotary compressor cylinder component and has wide practicability.
Drawings
FIG. 1 is a diagram of the adaptive value range of the Somofield number.
Fig. 2 is a longitudinal sectional view of a main portion of a single cylinder type high back pressure rotary compressor according to an embodiment of the present invention.
Fig. 3 is a top view of various forms of cylinder assemblies suitable for use in the invention, wherein fig. 3a is a rolling piston type, fig. 3b is a rocking slider type, fig. 3c is a piston hinge type, and fig. 3d is a cylinder hinge type.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
The invention obtains each working condition of the rotary compressor by carrying out thermodynamic calculation on the refrigeration cycle systems of the refrigerator, the freezer and the like. Then, aiming at the obtained working condition and the basic structure of the rotary compressor, the pressure distribution analysis is carried out on each position in the rotary compressor by utilizing a finite element method, and the load P of each friction pair is obtainedb. Then combined with dimensionless minimum oil film thickness
Figure GDA0002458571000000061
Graph relating to Sommerfeld number S through minimum oil film thickness HminThe viscosity range of the applicable lubricating oil was analyzed.
Firstly, the minimum oil film thickness H is determined by ensuring that the ratio Λ of the minimum oil film thickness to the roughness of two friction surfaces is more than or equal to 3min. Then passing through the dimensionless minimum oil film thickness
Figure GDA0002458571000000062
The adaptive value range of the Sommerfeld number is obtained from a relation curve (shown in figure 1) of the Sommerfeld number and the S, and the value range of the viscosity of the lubricating oil is deduced from a formula of the Sommerfeld number.
The Somofield number is obtained from the following equation:
Figure GDA0002458571000000063
wherein D is the diameter of the crankshaft, c is the radial clearance of the bearing, N is the rotation speed, mu is the dynamic viscosity of the lubricating oil, P isbIs a friction pair load.
And finally, checking the result by combining the lubricating oil condition of the rotary compressor of other working mediums through the relation of delta P ^ v (wherein delta P is the pressure difference of suction and discharge of the compressor, and v is the kinematic viscosity of the lubricating oil).
Through the research process, the technical scheme of the invention is obtained.
As shown in fig. 2, the single cylinder type high back pressure rotary compressor according to an embodiment of the present invention, which uses R600a or R600 refrigerant as a medium to be compressed mainly, includes a housing 10, a motor 20 accommodated in an inner space of the housing 10, and a pump body 30 driven by the motor 20, wherein a bottom space of the housing 10 stores lubricating oil 40.
The compressed medium of the rotary compressor is R600a or R600 refrigerant. If a mixed refrigerant is used as the medium to be compressed, the total mass fraction of the R600a plus R600 refrigerant should be 60% or more, preferably 80% or more.
The pump body 30 includes a crankshaft 31 extending in a vertical direction at the center of the pump body 30, a cylinder assembly 32, an upper bearing 33 and a lower bearing 34; the cylinder assembly 32 is covered at its upper end by an upper bearing 33 and at its lower end by a lower bearing 34.
The crankshaft is mainly divided into a main shaft 41, a curved part 42 and an auxiliary shaft 43; the main shaft 41 is sleeved inside the upper bearing 33 and forms a sliding friction pair with the upper bearing 33, and the tail end of the main shaft 41 is in transmission connection with the motor 20; the curved part 42 is sleeved in the piston 12 and forms a sliding friction pair with the piston 12; the auxiliary shaft 43 is sleeved inside the lower bearing 34 and forms a sliding friction pair with the lower bearing 34.
In order to reduce the viscous resistance loss generated by the lubricating oil in each friction pair of the rotary compressor and ensure the lubricating performance and the sealing performance, the lubricating oil used by the compressor is required to be as follows, which is characterized in that:
the lubricating oil has a viscosity grade of ISO8-ISO32, i.e. a viscosity in the range of 8-32cSt at 40 ℃.
In addition, aiming at different working conditions of the rotary compressor in different cycles, the rotary compressor is subdivided into the following suction and exhaust pressure difference intervals, and the viscosity grade of the subdivided lubricating oil is preferably as follows:
group number Pressure difference between suction and discharge delta P (bar) Lubricating oil viscosity grade ISO
1 3.0-4.0 8-20
2 4.0-5.0 12-24
3 5.0-6.0 15-27
4 6.0-7.0 18-30
5 7.0-8.0 20-32
The base oil of the lubricating oil is: polyester POE oil, polyethylene glycol PAG oil or polyvinyl ether PVE oil.
Because the embodiment is a rotary compressor with a high back pressure structure, the gas pressure in the inner cavity of the shell is the exhaust pressure, and the working load of the lubricating oil is higher, according to the scheme of the invention, the viscosity grade range of the lubricating oil is preferably as follows: ISO15-ISO 30.
If the rotary compressor is in a low back pressure structure, that is, the gas pressure in the cavity inside the housing is the suction pressure, and the working load of the lubricating oil is low, the viscosity grade range of the lubricating oil is preferably obtained according to the above research process: ISO10-ISO 25.
Fig. 3 is a top view of various forms of the cylinder assembly to which the present invention is applicable.
The invention controls the viscous resistance loss generated by the lubricating oil, does not limit the pump body structure of the rotary compressor, and is embodied as follows:
the cylinder assembly may be in the form of: rolling piston (fig. 3a), rocking slide (fig. 3b), piston hinge (fig. 3c), cylinder hinge (fig. 3d), etc.;
the cylinder assembly in several forms is shown as comprising a cylinder 35, a slide 11 and a piston 12 (or the like). The interior of the cylinder component is also provided with a sliding friction pair of the piston 12, an upper bearing 33 and a lower bearing 34, and a friction pair of the cylinder 35, the sliding sheet 11, the piston 12, the sliding friction pair between every two of the sliding friction pairs and the like. These friction pairs are all factors to be considered in the optimization calculation process of the invention. However, because the types of the internal friction pairs of the cylinder assemblies in different forms are similar and the losses are similar, the influence of the cylinder assemblies in different forms on the final optimization scheme is not obvious, and therefore, the scheme provided by the invention is suitable for rotary compressors in various cylinder forms.
Furthermore, the pump body structure may be: single cylinder structure, multi-stage cylinder structure or multi-cylinder parallel structure.
The invention is also suitable for the rotary compressor with the method for determining the viscosity grade of the lubricating oil of the rotary compressor.

Claims (5)

1. A method for determining the viscosity grade of lubricating oil of a rotary compressor comprises a shell (10), a motor (20) accommodated in the inner space of the shell (10) and a pump body (30) driven by the motor (20), wherein the bottom space of the shell (10) is stored with the lubricating oil (40); the method is characterized in that: using either R600a or R600 refrigerant as the primary compressed medium or a mixed refrigerant as the compressed medium, wherein the total mass fraction of R600a and R600 refrigerant is 60% or more; the lubricating oil (40) has a viscosity grade of ISO8-ISO32, i.e. a viscosity at 40 ℃ of 8cSt-32 cSt;
the viscosity range of the lubricating oil (40) is subdivided into suction and exhaust pressure difference intervals according to different working conditions of the compressor, and the viscosity grades of the subdivided lubricating oil are shown in the following table:
group number Pressure difference between suction and discharge delta P (bar) Lubricating oil viscosity grade ISO 1 3.0-4.0 8-20 2 4.0-5.0 12-24 3 5.0-6.0 15-27 4 6.0-7.0 18-30 5 7.0-8.0 20-32
The rotary compressor is of a high back pressure structure, and the viscosity grade of the lubricating oil is as follows: ISO15-ISO 30;
the method for calculating the value range of the viscosity grade of the lubricating oil comprises the following steps:
thermodynamic calculation is carried out on a refrigeration cycle system of a refrigerator and a freezer to obtain each working condition of the rotary compressor, then pressure distribution analysis is carried out on each position in the rotary compressor by utilizing a finite element method according to the obtained working condition and the basic structure of the rotary compressor, so as to obtain the load Pb of each friction pair, and then the dimensionless minimum oil film thickness is combined
Figure FDA0002458570990000011
Graph relating to Sommerfeld number S through minimum oil film thickness HminAnalyzing the viscosity range of the applicable lubricating oil;
firstly, the minimum oil film thickness H is determined by ensuring that the ratio Λ of the minimum oil film thickness to the roughness of two friction surfaces is more than or equal to 3minThen passing through the dimensionless minimum oil film thickness
Figure FDA0002458570990000021
Obtaining the adaptive value range of the Sommerfeld number by a relation curve of the Sommerfeld number and the Sommerfeld number S, and deducing the value range of the viscosity of the lubricating oil from a formula of the Sommerfeld number;
the Somofield number is obtained from the following equation:
Figure FDA0002458570990000022
d is the diameter of the crankshaft, c is the clearance in the radial direction of the bearing, N is the rotating speed, mu is the dynamic viscosity of lubricating oil, and Pb is the friction pair load;
and finally, checking the result through the condition that the delta P is combined with the lubricating oil of the rotary compressor of other working mediums, wherein the delta P is the pressure difference of suction and discharge of the compressor, and the nu is the relation of the kinematic viscosity of the lubricating oil.
2. The method for determining the viscosity grade of the lubricating oil of the rotary compressor as claimed in claim 1, wherein: the base oil of the lubricating oil is polyester POE oil, polyethylene glycol PAG oil or polyvinyl ether PVE oil.
3. The method for determining the viscosity grade of the lubricating oil of the rotary compressor as claimed in claim 1, wherein: the refrigerant mixture is used as a compressed medium, wherein the total mass fraction of R600a and R600 refrigerants is more than 80%.
4. The method for determining the viscosity grade of the lubricating oil of the rotary compressor as claimed in claim 1, wherein: the control of the viscosity resistance loss generated by the lubricating oil, namely the restriction of the viscosity grade of the lubricating oil, and the pump body structure of the rotary compressor is not limited, and the control method is characterized in that:
the cylinder component is in a rolling piston type, a swinging sliding sheet type, a piston hinge type or a cylinder hinge type;
the pump body structure is a single cylinder structure, a multi-stage cylinder structure or a multi-cylinder parallel structure.
5. A rotary compressor using a method for determining a viscosity grade of a lubricant for a rotary compressor according to any one of claims 1 to 4.
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