CN211288421U - Crankshaft and roller matching structure, compressor and air conditioner - Google Patents
Crankshaft and roller matching structure, compressor and air conditioner Download PDFInfo
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- CN211288421U CN211288421U CN201922061747.9U CN201922061747U CN211288421U CN 211288421 U CN211288421 U CN 211288421U CN 201922061747 U CN201922061747 U CN 201922061747U CN 211288421 U CN211288421 U CN 211288421U
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Abstract
The utility model provides a bent axle and roller cooperation structure, compressor, 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 portionA first gap m is formed between the inner hole and the outer hole, and when the temperature of the matching structure rises, the outer diameter D of the eccentric part after thermal expansion2Is smaller than the diameter D of the inner hole of the roller after thermal expansion1. The utility model provides a pair of bent axle and roller cooperation structure, compressor, air conditioner when the compressor temperature risees, the external diameter behind the eccentric portion thermal energy of bent axle is less than the hole diameter behind the roller thermal energy, stops both locking of bent axle and roller, the emergence of the dead phenomenon of card at compressor operation in-process.
Description
Technical Field
The utility model belongs to the technical field of air conditioning, concretely relates to bent axle and roller cooperation structure, compressor, 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, jamming and the like, is easily caused by unreasonable gaps because only the material is replaced and the deformation difference caused by the thermodynamic property is ignored. 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.
SUMMERY OF THE UTILITY MODEL
Therefore, the to-be-solved technical problem of the utility model is to provide a bent axle and roller cooperation structure, compressor, air conditioner, when the compressor temperature risees, the external diameter behind the eccentric portion thermal energy of bent axle is less than the hole diameter behind the roller thermal energy, stops both locking of bent axle and roller, the emergence of the dead phenomenon of card in compressor operation process.
In order to solve the problem, the utility model provides a 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, work as when cooperation structure temperature risees, external diameter D behind the eccentric portion thermal energy2Is 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 alpha 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 utility model also provides a compressor, including foretell bent axle and roller cooperation structure.
The utility model also provides an air conditioner, including foretell compressor.
The utility model provides a pair of bent axle and roller cooperation structure, compressor, air conditioner when the compressor temperature risees, the external diameter behind the eccentric portion thermal energy of bent axle is less than the hole diameter behind the roller thermal energy, stops both locking of bent axle and roller, the emergence of the dead phenomenon of card at compressor operation in-process.
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 matching structure is provided, including 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 (unit is mm) therebetween, when the temperature of the matching structure rises, the 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 gap m (in mm) is related to the α, and it can be understood that the material of the roller 2 and the eccentric portion 11 is respectively selected to be different first material and second material, which can facilitate 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 compressor balance system, 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.
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 D1(in mm), △ 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＞△D2-ΔD1。
Assuming that the maximum temperature rise of the roller 2 and the crankshaft 1 at the mating position during the operation of the compressor is △ T respectively1And 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 △ D1/ΔD2＝αD1/D2。
When the alpha is more 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
△ 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 portion of the crankshaft are not locked due to deformation are as follows:
m＞△D2-ΔD1＝ΔD2-(αD1/D2)△D2＝(1-αD1/D2)ΔD2
＝ΔT2(1-αD1/D2)D2ξ2
i.e. m > △ 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＜△T2(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 △ T of the eccentric part 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
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 portion 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 the 3 horizontal isodiametric lines shown in FIG. 3, the temperature corresponding to each component is represented 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 portion of the crankshaft is up to about 75 ℃, the inner diameter of the roller is almost close to the outer diameter of the eccentric portion of the crankshaft, and there is a risk of seizure, when the local temperature rise of the eccentric portion of the crankshaft is up to more than 80 ℃, the inner diameter of the roller is inevitably larger than the outer diameter of the eccentric portion of the crankshaft, and the compressor is seized, according to theoretical calculation and experimental verification by utility model, preferably, when one of the roller of the ceramic roller of the pump body is adopted, the pump body, the design gap is 6335 μ2＜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 the utility model discloses an embodiment still provides a compressor, including foretell bent axle and roller cooperation structure, the compressor can be single cylinder rotor compressor for example, also can be double-cylinder or multi-cylinder rotor compressor.
According to the utility model discloses an embodiment still provides an air conditioner, including foretell 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 above description is only exemplary of the present invention and should not be construed as limiting the present invention, and any modifications, equivalents and improvements made within the spirit and principles of the present invention are intended to be included within the 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, a plurality of modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations 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 arrangement, as set forth in claim 1, characterized in that the material of the roller (2) is a first material, the material beingThe first material has 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 ≧ 1, 0.01mm ≦ m ≦ 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 has a density less than a density of FC 300.
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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922061747.9U CN211288421U (en) | 2019-11-25 | 2019-11-25 | Crankshaft and roller matching structure, compressor and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922061747.9U CN211288421U (en) | 2019-11-25 | 2019-11-25 | Crankshaft and roller matching structure, compressor and air conditioner |
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| Publication Number | Publication Date |
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| CN211288421U true CN211288421U (en) | 2020-08-18 |
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| CN201922061747.9U Active CN211288421U (en) | 2019-11-25 | 2019-11-25 | Crankshaft and roller matching structure, compressor and air conditioner |
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