CN111059136A - Crankshaft and roller matching structure, compressor and air conditioner - Google Patents

Crankshaft and roller matching structure, compressor and air conditioner Download PDF

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Publication number
CN111059136A
CN111059136A CN201911167446.2A CN201911167446A CN111059136A CN 111059136 A CN111059136 A CN 111059136A CN 201911167446 A CN201911167446 A CN 201911167446A CN 111059136 A CN111059136 A CN 111059136A
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China
Prior art keywords
roller
compressor
crankshaft
thermal expansion
eccentric
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Inventor
魏会军
徐嘉
张心爱
胡文祥
王珺
吴健
孙成龙
闫鹏举
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Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
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Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
    • F16C3/12—Crankshafts assembled of several parts, e.g. by welding by crimping releasably connected
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/20—Shape of crankshafts or eccentric-shafts having regard to balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/24—Compensation of inertia forces of crankshaft systems by particular disposition of cranks, pistons, or the like
    • 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
    • F04C2240/20—Rotors
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/20—Thermal properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/20—Thermal properties
    • F16C2202/22—Coefficient of expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2204/00—Metallic materials; Alloys
    • F16C2204/60—Ferrous alloys, e.g. steel alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2206/00—Materials with ceramics, cermets, hard carbon or similar non-metallic hard materials as main constituents
    • F16C2206/40—Ceramics, e.g. carbides, nitrides, oxides, borides of a metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/46—Gap sizes or clearances
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/43—Screw compressors

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The invention provides a crankshaft and roller matching structure, a compressor and an air conditioner. Wherein bent axle and roller cooperation structure, including bent axle, roller, the bent axle has eccentric portion, the roller has the hole, eccentric portion is in the hole and form first clearance m between the two, works as when cooperation structure temperature risees, external diameter D after the eccentric portion thermal expansion2Is smaller than the diameter D of the inner hole of the roller after thermal expansion1. According to the crankshaft and roller matching structure, the compressor and the air conditioner, when the temperature of the compressor rises, the eccentric part of the crankshaft thermally expandsThe outer diameter of the crank shaft is smaller than the diameter of the inner hole of the roller after thermal expansion, so that the phenomena of locking and blocking of the crank shaft and the roller in the running process of the compressor are avoided.

Description

Crankshaft and roller matching structure, compressor and air conditioner
Technical Field
The invention belongs to the technical field of air conditioning, and particularly relates to a crankshaft and roller matching structure, a compressor and an air conditioner.
Background
The rotary compressor shell is mainly composed of a pump body assembly and a motor assembly, the pump body assembly comprises a cylinder, a roller, a crankshaft, a sliding vane and upper and lower bearing assemblies, all parts are matched with each other to form a closed air suction cavity and an air exhaust cavity, and the motor assembly comprises a stator assembly and a rotor assembly. The long axle head of the crankshaft of the pump body assembly is in interference fit with the rotor in the motor assembly, the rotary compressor generates driving force for rotating the crankshaft of the pump body through the action of electromagnetic force generated between the motor rotor assembly and the stator assembly, and the volume of the suction cavity and the exhaust cavity of the compressor is constantly changed under the action of the rotation driving of the crankshaft, so that the periodic suction, compression and exhaust processes of the compressor are realized. The rotary compressor utilizes the eccentric portion of bent axle to realize the periodic compression process of cylinder cavity internal gas flow, because the eccentric design of bent axle, the eccentric portion of bent axle and with the eccentric portion complex roller of bent axle have constituted compressor pump body rotating part's unbalanced mass jointly, lead to the unbalance nature of compressor pump body structure, and then make whole rotating part (electric motor rotor, pump body bent axle, pump body roller) be in the unbalanced state, in order to ensure compressor steady operation, need arrange the main of different counter weights, vice balancing piece with the unbalance nature of balanced compressor rotating part at electric motor rotor core both ends usually. The larger the unbalanced mass of the rotating part of the pump body is, the larger the mass of the main balance block and the auxiliary balance block which need to balance the unbalanced mass is.
With the trend of miniaturization and high-speed development of compressors, the compressors need to be designed in a descending series, and the performance, noise and reliability levels of the compressors can be guaranteed when the compressors are operated at higher frequency. Wherein, the miniaturization of the compressor means that the cylinder diameter is limited under the same discharge capacity, correspondingly inevitably leads to the increase of the cylinder height, the integral height of the pump body-rotor assembly is increased, and the calculation formula F is rm omega according to the inertia moment2l, the rotational inertia moment caused by the eccentric mass increases linearly with the increase of the height of the pump body, and the formula F is rm omega2The centrifugal force of the main balance block and the auxiliary balance block of the motor rotor is increased in power direction due to the high-speed operation of the compressor, the deflection of a pump body crankshaft is greatly increased when the compressor operates at high frequency, noise and vibration of the compressor operating at high frequency are increased sharply, meanwhile, the friction loss is increased, the performance is greatly reduced, the abrasion of parts of the compressor is further increased, the risk of a plurality of reliability problems such as the motor sweeping caused by the contact of the outer circular surface of the motor and the inner circular surface of the stator is further increased, and the bottleneck problem which needs to be solved urgently in the process of the small-sized high-speed design and.
According to the calculation formula of the inertia force and the inertia moment, on the premise of ensuring the high-speed operation of the compressor, the eccentric rotating radius is fixed, the rotating inertia force and the rotating inertia moment of the compressor can be effectively reduced by reducing the eccentric mass m, so that a balance system of the compressor is optimized, the deflection of a crankshaft of a pump body of the compressor is reduced, the problems of performance and noise caused by the high-speed operation balance problem of the compressor are effectively solved or optimized, and the problems of the reliability of the compressor such as abrasion of parts of the pump body and the sweeping of a motor are solved, which is the problem of the current light weight research.
The eccentric parts are made of light materials, which is one of the important methods for reducing the eccentric mass, and the thermal deformation of the eccentric parts is greatly different due to different physical properties of different materials, namely different thermodynamic parameters such as thermal conductivity, specific heat capacity, thermal expansion coefficient and the like. The heat conductivity reflects the heat transfer speed of materials, on one hand, an inner circular surface of a roller in a rotary compressor pump body assembly continuously absorbs heat due to frictional heat and conducts heat to the interior of the roller and parts on an outer circular surface of the roller, on the other hand, one part of the outer circular surface of the roller is in contact with low-pressure low-temperature gas of a gas suction cavity of a cylinder, and the other part of the outer circular surface of the roller is in contact with high-temperature high-pressure gas of a compression cavity of the cylinder, so that a temperature gradient exists, and heat flow changes along. The specific heat capacity reflects the temperature difference caused by the absorption or emission of specific heat of the part, and the larger the specific heat capacity, the smaller the temperature difference. While the coefficient of thermal expansion reflects part deformation at a particular temperature difference. When the heat conductivity of the roller material is smaller than that of the crankshaft material matched with the roller material, according to the heat conduction characteristic, the heat generated by the friction pair is conducted on the crankshaft material more quickly, and the heat conducted on the roller is relatively slower, so that the temperature of the crankshaft is raised quickly, the temperature rise of the roller is slower, the temperature difference of the roller-crankshaft friction pair is further larger, when the thermal expansion coefficients of the two are relatively close, the thermal expansion deformation of the crankshaft is far larger than that of the roller, the eccentric part of the crankshaft is blocked with the roller, and when the heat conductivity of the roller material is larger than that of the crankshaft material matched with the roller, the opposite is realized, and the matching gap between the roller and the eccentric part of the crankshaft is larger. Therefore, the problem of abnormal reliability of the compressor, such as large leakage, unsmooth operation, blockage and the like, is easily caused by unreasonable gaps only by replacing materials and neglecting the deformation difference caused by the thermodynamic characteristics. Based on the defects existing in the research process of light weight and small size and high speed of the compressor material, the necessary research needs to be carried out on the material selection basis of the crankshaft, particularly the eccentric part of the crankshaft and the roller matched with the eccentric part of the crankshaft so as to ensure that the crankshaft and the roller are not locked or jammed in the operation process of the compressor.
Disclosure of Invention
Therefore, the technical problem to be solved by the present invention is to provide a matching structure of a crankshaft and a roller, a compressor, and an air conditioner, wherein when the temperature of the compressor rises, the outer diameter of the eccentric portion of the crankshaft after thermal expansion is smaller than the inner hole diameter of the roller after thermal expansion, so as to prevent the phenomena of locking and jamming of the crankshaft and the roller during the operation of the compressor.
To solve the above problems, the present inventionThe invention provides a crankshaft and roller matching structure, which comprises a crankshaft and a roller, wherein the crankshaft is provided with an eccentric part, the roller is provided with an inner hole, the eccentric part is positioned in the inner hole, a first gap m is formed between the eccentric part and the inner hole, and when the temperature of the matching structure rises, the outer diameter D of the eccentric part after thermal expansion is larger than the outer diameter D of the eccentric part2Is smaller than the diameter D of the inner hole of the roller after thermal expansion1。
Preferably, the material of the roller is a first material having a thermal conductivity λ1Specific heat capacity of C1A coefficient of thermal expansion of ξ1The material of the eccentric part is a second material, and the thermal conductivity of the second material is lambda2Specific heat capacity of C2A coefficient of thermal expansion of ξ2Thermodynamic relation parameter α ═ C (C)2λ1ξ1)/(C1λ2ξ2) Said first gap m being associated with said α.
Preferably, when α is more than or equal to 1, m is more than or equal to 0.01mm and less than or equal to 0.03 mm.
Preferably, 0.015 mm. ltoreq. m.ltoreq.0.025 mm.
Preferably, when α < 1, k (1- α D)1/D2)D2ξ2< m, where k is the maximum temperature rise of the eccentric.
Preferably, k is 20 ℃ to 150 ℃.
Preferably, k (1- α D)1/D2)D2ξ2+ b > m, where b is the upper gap limit constant in mm.
Preferably, 0.01mm < b < 0.03 mm.
Preferably, the first material is a lightweight material.
The invention also provides a compressor, which comprises the crankshaft and the roller matching structure.
The invention also provides an air conditioner which comprises the compressor.
According to the crankshaft and roller matching structure, the compressor and the air conditioner, when the temperature of the compressor rises, the outer diameter of the eccentric part of the crankshaft after thermal expansion is smaller than the diameter of the inner hole of the roller after thermal expansion, and the phenomena that the crankshaft and the roller are locked and stuck in the running process of the compressor are avoided.
Drawings
Fig. 1 is a schematic view of an internal structure of a compressor according to an embodiment of the present invention;
FIG. 2 is an enlarged view of a portion of FIG. 1 at A;
FIG. 3 is a thermal deformation curve of the inner diameter of the ceramic roller and the outer diameter of the eccentric portion of the ductile iron crankshaft according to an embodiment of the present invention.
The reference numerals are represented as:
1. a crankshaft; 11. an eccentric portion; 2. a roller; 21. an inner bore.
Detailed Description
Referring to fig. 1 to 3 in combination, according to an embodiment of the present invention, a crankshaft and roller mating structure is provided, which includes a crankshaft 1 and a roller 2, the crankshaft 1 has an eccentric portion 11, the roller 2 has an inner hole 21, the eccentric portion 11 is located in the inner hole 21 and forms a first gap m (in mm) therebetween, and when the mating structure is heated, an outer diameter D of the eccentric portion 11 after thermal expansion is increased2(in mm) is smaller than the diameter D of the inner hole 21 of the roller 2 after thermal expansion1(in mm). In the technical scheme, when the temperature of the compressor rises, the outer diameter of the eccentric part of the crankshaft after thermal expansion is smaller than the diameter of the inner hole of the roller after thermal expansion, and the phenomena of locking and blocking of the crankshaft and the roller in the running process of the compressor are avoided.
In order to realize that the outer diameter of the eccentric part of the crankshaft after thermal expansion is smaller than the diameter of the inner hole 21 of the roller after thermal expansion, the roller 2 is preferably made of a first material, and the thermal conductivity (in W/(m DEG C)) of the first material is lambda1The specific heat capacity (in J/(kg. DEG C)) is C1Coefficient of thermal expansion (unit 10)-6/deg.C) ξ1The material of the eccentric part 11 is a second material, and the thermal conductivity (unit is W/(m DEG C)) of the second material is lambda2The specific heat capacity (in J/(kg. DEG C)) is C2Coefficient of thermal expansion (unit 10)-6/deg.C) ξ2Thermodynamic relation parameter α ═ C (C)2λ1ξ1)/(C1λ2ξ2) The first mentionedA gap m (in mm) is associated with the α, and it can be understood that the material of the roller 2 and the eccentric portion 11 is selected to be different first material and second material, respectively, which facilitates the lightweight design of the roller 2, for example, the density of the first material is selected to be greater than the density of the second material, so as to effectively reduce the rotational inertia force and the rotational inertia moment of the compressor, thereby optimizing the balance system of the compressor, reducing the flexibility of the crankshaft of the compressor pump body, and effectively solving or optimizing the performance and noise problems caused by the high-speed operation balance problem of the compressor, and the reliability problems of the compressor such as the abrasion of pump body parts and the sweeping of the motor chamber.
Specifically, in order to ensure that the roller and the eccentric part of the crankshaft are not locked, the following requirements are met: d1+ΔD1＞D2+ΔD2Wherein, Δ D1In mm,. DELTA.D2(in mm) represents the inner diameter deformation of the roller and the outer diameter deformation of the eccentric portion 11, and m is D1-D2＞ΔD2-ΔD1。
Assuming that the maximum temperature rises of the roller 2 and the crankshaft 1 at the mating place are respectively Δ T in the compressor operation1And Δ T2Then, according to a thermodynamic calculation formula:
ΔD1/ΔD2＝(ΔT1D1ξ1)/(ΔT2D2ξ2)＝((D1ξ1)/(D2ξ2))·(ΔT1/ΔT2)
＝((D1ξ1)/(D2ξ2))·(C2λ1)/(C1λ2)
＝((C2λ1ξ1)/(C1λ2ξ2))·(D1/D2)
let α be (C)2λ1ξ1)/(C1λ2ξ2)，
The ratio of the deformation of the inner diameter of the roller to the deformation of the outer diameter of the eccentric part of the crankshaft is as follows: delta D1/ΔD2＝αD1/D2。
When α is greater than or equal to 1,
at this time, the roller inner diameter D is determined1Outer diameter D of eccentric part of crankshaft2The ratio between (i.e. D)1/D2＞1
Then Δ D1/ΔD2More than 1, that is, the inner diameter deformation of the roller is greater than the outer diameter deformation of the eccentric portion of the crankshaft, and locking and blocking phenomena certainly do not occur, at this time, only a fit clearance needs to be designed reasonably, for example, 0.01mm is greater than or equal to m is less than or equal to 0.03mm, at this time, it can be understood that, when α is equal to 1, the first material and the second material may be the same material, and certainly, at this time, the roller 2 is not designed to be light in a strict sense, further, 0.015 is greater than or equal to m is less than or equal to 0.025, that is, when α is greater than or equal to 1, the original installation clearance between the roller 2 and the eccentric portion 11 is controlled to be within a reasonable range after the temperature rises, and the range can enable the compressor to operate normally, and the phenomenon that the pump body leaks seriously to affect the energy.
When α < 1, the most basic conditions for ensuring that the inner diameter of the roller and the outer diameter of the eccentric part of the crankshaft are not locked due to deformation are as follows:
m＞ΔD2-ΔD1＝ΔD2-(αD1/D2)ΔD2＝(1-αD1/D2)ΔD2
＝ΔT2(1-αD1/D2)D2ξ2
i.e. m > Δ T2(1-αD1/D2)D2ξ2In time, the utility model can ensure that the utility model is not locked,
in order to ensure that the clearance is not too large to cause leakage risk during operation of the compressor, the upper limit of the clearance is further limited not to exceed a certain range, wherein a constant b (in mm) is introduced, namely
m＜ΔT2(1-αD1/D2)D2ξ2+b，0.01≤b≤0.03；
I.e., k (1- α D)1/D2)D2ξ2＜m＜k(1-αD1/D2)D2ξ2+b。
As can be seen from the above formula, k represents the maximum temperature rise Δ T of the eccentric portion of the crankshaft2The exhaust temperature is positively correlated with the exhaust temperature when the compressor operates, the larger the exhaust temperature is, the larger the local temperature rise of the matched friction pair part is, and when the compressor operates at high frequency under heavy working conditions, the exhaust temperature does not exceed 150 ℃ at most, therefore, k is within the range of 20 ℃ to 150 ℃, when the exhaust temperature is larger, the temperature rise is relatively larger, so k is biased to an upper limit value within a limited value range.
Preferably, the first material is a lightweight material, preferably having a density less than the prior art roller material FC300, such as zirconia ZrO2Ceramics, alumina Al2O3The crankshaft is made of steel materials with relatively high hardness, such as 40Cr, 20Cr and the like, so that the wear resistance of the compressor is improved, and the high-frequency deflection of the crankshaft can be further reduced because the rigidity of the steel materials is higher than that of ductile iron (nodular cast iron) in the prior art.
As a specific embodiment, as shown in fig. 3, when a ceramic roller component is used, it is matched with a conventional nodular iron crankshaft, the thermal conductivity and linear expansion coefficient of the ceramic roller component are shown in table 1, and as can be seen from the thermal conductivity parameters of the ceramic roller component and the nodular iron crankshaft, the ceramic thermal conductivity is much smaller than that of the nodular iron crankshaft and is only 6.7% of that of the nodular iron crankshaft, according to the thermal conductivity characteristics, the heat generated by the friction pair is conducted on the crankshaft material faster and conducted on the roller relatively slower, so that the crankshaft is heated up quickly, the temperature rise of the roller is relatively slow, further the temperature difference between the roller and the crankshaft friction pair is large, when the thermal expansion coefficients of the two are relatively close, the thermal expansion deformation of the crankshaft is much larger than that of the roller, and if the design of the gap between the roller and the crankshaft is not reasonable, the eccentric part.
TABLE 1 thermodynamic parameters of ceramic and ductile iron materials
Figure BDA0002287832500000061
As shown in FIG. 3, according to the linear expansion coefficients of ceramic and ductile iron materials in Table 1, a curve of the change of the inner diameter of the ceramic roller and the outer diameter of the eccentric part of the ductile iron crankshaft along with the temperature rise is drawn, and it can be seen that the ceramic roller has slow temperature rise and slow increase of the inner diameter along with the temperature rise (the ceramic linear expansion coefficient is smaller than that of the ductile iron material), and according to 3 horizontal isodiametric lines shown in FIG. 3, the temperature corresponding to each part is shown when the outer diameter of the crankshaft is equal to the inner diameter of the roller, so that it can be known that, when the local temperature rise of the friction pair surface of the ceramic roller is up to 30 ℃, the local temperature rise of the eccentric part of the crankshaft is up to about 75 ℃, the inner diameter of the roller is basically close to the outer diameter of the eccentric part of the crankshaft, and the risk of seizure exists, when the local temperature rise of the eccentric part of the crankshaft is up to more than 80 ℃, the inner diameter of the eccentric part of the crankshaft is inevitably caused to be larger than the outer diameter of the eccentric part of the crankshaft, and the compressor is seized according to theoretical calculation and experimental verification of the inventor, preferably, when one of the roller of the pump body of the compressor is adopted, the ceramic roller, the pump2＜m＜k(1-αD1/D2)D2ξ2+ b, and reasonably selecting the values of k and b.
On the one hand, ceramic roller hardness is far higher than current roller material (FC300) structure, can reduce roller wearing and tearing volume, reduces frictional loss, and on the other hand, ceramic roller's thermal conductivity is about 2.2W/(m. ° C), is far less than current roller material FC 300's thermal conductivity (about 47.5mm), and its thermal-insulated effect is showing, is favorable to promoting the instruction efficiency of the compressor pump body, further promotes the compressor energy efficiency.
According to an embodiment of the present invention, there is also provided a compressor including the above-mentioned crankshaft and roller cooperating structure, and the compressor may be, for example, a single-cylinder rotor compressor, or a double-cylinder or multi-cylinder rotor compressor.
According to an embodiment of the invention, an air conditioner is also provided, which comprises the compressor.
It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.
The present invention is not limited to the above preferred embodiments, and any modifications, equivalent substitutions and improvements made within the spirit and principle of the present invention should be included in the protection scope of the present invention. The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several improvements and modifications can be made without departing from the technical principle of the present invention, and these improvements and modifications should also be regarded as the protection scope of the present invention.

Claims (11)

1. The utility model provides a bent axle and roller cooperation structure, characterized in that, includes bent axle (1), roller (2), bent axle (1) has eccentric portion (11), roller (2) have hole (21), eccentric portion (11) are in hole (21) and form first clearance m between the two, when cooperation structure temperature risees, external diameter D after eccentric portion (11) the thermal expansion2Is smaller than the diameter D of the inner hole (21) of the roller (2) after thermal expansion1。
2. The mating structure according to claim 1, characterized in that the material of the roller (2) is a first material having a thermal conductivity λ1Specific heat capacity of C1A coefficient of thermal expansion of ξ1The material of the eccentric part (11) is a second material, and the thermal conductivity of the second material is lambda2Specific heat capacity of C2A coefficient of thermal expansion of ξ2Thermodynamic relation parameter α ═ C (C)2λ1ξ1)/(C1λ2ξ2) Said first gap m being associated with said α.
3. The fitting structure according to claim 2, wherein when α is not less than 1, m is not less than 0.01mm and not more than 0.03 mm.
4. The mating structure of claim 3, wherein 0.015mm ≦ m ≦ 0.025 mm.
5. The mating structure of claim 2, wherein k (1- α D) is when α < 11/D2)D2ξ2< m, where k is the maximum temperature rise of the eccentric (11).
6. The mating structure of claim 5, wherein k is 20 ℃ ≦ 150 ℃.
7. The mating structure of claim 5, wherein k (1- α D)1/D2)D2ξ2+ b > m, where b is the upper gap limit constant in mm.
8. The mating structure of claim 7, wherein 0.01mm ≦ b ≦ 0.03 mm.
9. The mating structure of claim 7, wherein the first material is a lightweight material.
10. A compressor comprising a crankshaft and roller mating structure, wherein said crankshaft and roller mating structure is as claimed in any one of claims 1 to 9.
11. An air conditioner comprising a compressor, wherein the compressor is the compressor of claim 10.
CN201911167446.2A 2019-11-25 2019-11-25 Crankshaft and roller matching structure, compressor and air conditioner Pending CN111059136A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114320914A (en) * 2021-12-23 2022-04-12 珠海格力电器股份有限公司 Pump body subassembly and compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114320914A (en) * 2021-12-23 2022-04-12 珠海格力电器股份有限公司 Pump body subassembly and compressor

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