WO2015096017A1 - 压缩机、空调器和热水机 - Google Patents

压缩机、空调器和热水机 Download PDF

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Publication number
WO2015096017A1
WO2015096017A1 PCT/CN2013/090260 CN2013090260W WO2015096017A1 WO 2015096017 A1 WO2015096017 A1 WO 2015096017A1 CN 2013090260 W CN2013090260 W CN 2013090260W WO 2015096017 A1 WO2015096017 A1 WO 2015096017A1
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WO
WIPO (PCT)
Prior art keywords
cylinder
mass
compressor
crankshaft
compressor according
Prior art date
Application number
PCT/CN2013/090260
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English (en)
French (fr)
Inventor
李华明
郑立宇
郭宏
向卫民
喻继江
杨泾涛
张�诚
Original Assignee
广东美芝制冷设备有限公司
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Publication date
Application filed by 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to PCT/CN2013/090260 priority Critical patent/WO2015096017A1/zh
Publication of WO2015096017A1 publication Critical patent/WO2015096017A1/zh

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Classifications

    • 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
    • F04C18/3564—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 the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • 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
    • 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
    • F04C23/008—Hermetic pumps

Definitions

  • the present invention relates to the field of refrigeration equipment, and more particularly to a compressor, an air conditioner, and a water heater. Background technique
  • the rotary compressor has a refrigerating machine oil in the sealed casing, and the compression device is immersed in the refrigerating machine oil.
  • the ordinary compressor is operated under high temperature and high pressure conditions. Unsatisfactory reliability, compression device wear is severe, resulting in compressor necrosis. Summary of the invention
  • the present invention aims to solve at least one of the technical problems existing in the prior art. Accordingly, it is an object of the present invention to provide a compressor which is less prone to wear and necrosis, thereby prolonging the service life of the compressor and improving the reliability of the compressor.
  • Another object of the present invention is to provide an air conditioner having the above compressor.
  • Still another object of the present invention is to provide a water heater having the above compressor.
  • a compressor comprising: a casing, a bottom portion of the casing is provided with a refrigerating machine oil; and a compression device provided in the casing and including a crankshaft, a main bearing, a sub-bearing and a cylinder, the main bearing and the sub-bearing being respectively disposed at a top and a bottom of the cylinder and defining a compression chamber together with the cylinder, a lower end of the crankshaft extending through the main bearing In the compression chamber, the ratio of the eccentricity e of the eccentric portion of the crankshaft relative to the central axis of the cylinder to the inner diameter ⁇ of the cylinder satisfies: 0.05 eAD 0.12.
  • the compressor of the present invention by setting the ratio of the eccentric amount e to the inner diameter ⁇ of the cylinder to be between 0.05 eAD 0.12, the degree of wear failure of the sliding piece and the crankshaft in the compression device of the compressor during high temperature and high pressure operation can be improved. Therefore, the compressor is less prone to wear, which effectively extends the service life of the compressor and improves the reliability and overall performance of the compressor.
  • the refrigerator oil is an ester oil
  • the ester oil has a kinematic viscosity at 40 ° C of 70.5 to 76.0 mm 2 /s and a kinematic viscosity at 100 ° C of 8.4 to 9.0 mm 2 /s.
  • the refrigerator oil contains a sulfur-containing extreme pressure anti-wear agent.
  • At least one of the main bearing and the sub-bearing is formed with a venting hole, and the venting hole is covered with an exhaust valve piece, and the exhaust valve piece is made of a stainless steel material.
  • the stainless steel material comprises: 0.25 to 0.45 mass% of carbon; 0.3 to 0.5 mass% of silicon; 0.3 to 0.7 Mass% of manganese; 0 to 0.03 mass% of phosphorus; 0 to 0.015 mass% of sulfur; 12 to 14 mass% of chromium; 0.5 to 2.0 mass% of molybdenum; and balance of iron, wherein the stainless steel material
  • the tensile strength is 1850 ⁇ 2000MPa.
  • the exhaust hole is a circular hole and has a diameter D
  • a side of the exhaust hole adjacent to the exhaust valve piece is provided with a valve seat boss, and the valve seat boss is adjacent to the row
  • One side surface of the gas valve piece is formed as a circular arc surface having a radius of 1 1.3 1 ⁇ and 0.12 R/D 0.38.
  • An air conditioner according to a second aspect of the invention includes the compressor according to the above first aspect of the invention.
  • the compressed refrigerant used in the air conditioner is R410A or R32 refrigerant.
  • a water heater according to a third aspect of the invention comprises the compressor according to the above first aspect of the invention.
  • the compressed refrigerant used in the water heater is R410A or R32 refrigerant.
  • FIG. 1 is a schematic view of a compressor in accordance with an embodiment of the present invention
  • Figure 2 is a plan view of the compressor shown in Figure 1;
  • Figure 3 is an enlarged view of a portion A circled in Figure 1;
  • Figure 4 is a graph showing the relationship between the degree of wear of the compression device, the valve seat boss and the exhaust valve piece of the compressor and the ratio of e/ ⁇ ;
  • Fig. 5 is a view showing the remaining thickness of the surface treatment layer of the slider of the conventional compressor and the slider of the compressor of the embodiment of the present invention after the abrasion resistance test.
  • venting hole 1 1 : exhaust valve piece; 101 : valve seat boss;
  • connection In the description of the present invention, it should be noted that the terms “installation”, “connected”, and “connected” are to be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined. Connected, or connected in one piece; can be directly connected, or indirectly connected through an intermediate medium, and can be internal to the two elements.
  • the specific meanings of the above terms in the present invention can be understood in the specific circumstances by those skilled in the art.
  • a compressor according to an embodiment of the first aspect of the present invention which may be a rotary compressor, will be described below with reference to Figs.
  • a compressor as a rotary compressor will be described as an example.
  • the compressor in accordance with the present invention may also be other types of compressors.
  • a compressor according to an embodiment of the first aspect of the present invention includes a housing 1 and a compression device.
  • a refrigerant oil 12 is provided at the bottom of the casing 1
  • a compression device is provided in the casing 1
  • the compression device includes a crankshaft 4, a main bearing 8, a sub-bearing 9 and a cylinder 5, a main bearing 8 and a sub
  • the bearings 9 are respectively disposed at the top and the bottom of the cylinder 5, and the main bearing 8, the sub-bearing 9 and the cylinder 5 together define a compression chamber, and the lower end of the crankshaft 4 extends through the main bearing 8 into the compression chamber.
  • the sealed housing 1 is provided with a motor and a compression device, the compression device is immersed in the refrigeration oil 12, the motor is disposed in the upper portion of the housing 1, and the compression device is located in the motor Below, the motor comprises a stator 2 and a rotor 3, the stator 2 is fixed on the inner wall of the casing 1, and the rotor 3 is fixed on the crankshaft 4 in the compression device, so that the rotation of the crankshaft 4 can be driven when the rotor 3 rotates, and the compression device includes The crankshaft 4, the cylinder 5, the piston 6 and the slider 7, the piston 6 is sleeved outside the crankshaft 4 and rotates in the cylinder 5, and the cylinder 5 is provided with a slide groove 51 slidably coupled to the slider 7, in other words, formed on the cylinder 5.
  • the cylinders 5 collectively enclose a compression chamber.
  • the crankshaft 4 can be driven to rotate, thereby driving the piston 6 sleeved on the eccentric portion of the crankshaft 4 to roll along the inner wall of the compression chamber to compress the refrigerant.
  • the ratio of the eccentric portion e of the eccentric portion of the crankshaft 4 with respect to the central axis of the cylinder 5 to the inner diameter ⁇ of the cylinder 5 satisfies: 0.05 eAD 0.12.
  • the eccentric amount e is the distance between the central axis of the eccentric portion and the central axis of the cylinder 5
  • the ratio of the eccentric amount e of the crankshaft 4 with respect to the central axis of the cylinder 5 to the cylinder bore diameter ⁇ of the cylinder 5 satisfies the condition: 0.05
  • ⁇ / ⁇ 0.12 the degree of wear failure of the vane 7 and the crankshaft 4 in the compression device of the compressor such as the rotary compressor at high temperature and high pressure can be improved.
  • the abscissa is the ratio of the eccentric amount e to the cylinder bore diameter ⁇ of the cylinder 5
  • the ordinate is the degree of wear of the compression device
  • the degree of wear of the valve seat boss 101 and the exhaust valve plate 1 of the compressor It can be seen that the wear of each part reaches the optimum value when 0.05 ⁇ e/O ⁇ 0.12 is satisfied.
  • a compressor such as a rotary compressor according to an embodiment of the present invention can improve compressor compression at high temperature and high pressure by setting the ratio of the eccentric amount e to the inner diameter ⁇ of the cylinder 5 to be between 0.05 ⁇ / ⁇ 0.12 .
  • the wear of the sliding piece 7 and the crankshaft 4 is invalid, so that the compressor is less prone to wear, thereby effectively prolonging the service life of the compressor and improving the reliability of the compressor.
  • the refrigerating machine oil 12 is an ester oil
  • the kinematic viscosity of the ester oil is 70.5 to 76.0 mm 2 /s at 40 ° C, and the kinematic viscosity at 100 ° C. It is 8.4 ⁇ 9.0mm 2 /s.
  • the refrigerator oil 12 contains a sulfur-containing extreme pressure anti-wear agent.
  • the vent hole 10 may be formed only on the main bearing 8, or only on the sub-bearing 9, or simultaneously formed on the main bearing 8 and the sub-bearing 9.
  • the vent hole 10 is formed only on the main bearing 8, and the vent hole 10 penetrates the main bearing 8 in the up and down direction, and the vent hole 10 is covered with the compressed exhaust gas.
  • the exhaust valve piece 1 1 is such that the compressed gas can be discharged from the vent hole 10.
  • a side of the vent hole 10 adjacent to the exhaust valve plate 11 is provided with a valve seat boss 101.
  • valve seat boss 101 is disposed at a contact of the vent hole 10 with the exhaust valve plate 1 1 .
  • the valve seat boss 101 may be generally annular and disposed coaxially with the venting opening 10, specifically, the inner peripheral wall and row of the valve seat boss 101
  • the inner peripheral wall of the air hole 10 is connected or disposed adjacent to the inner peripheral wall of the vent hole 10.
  • the vent hole 10 is a circular hole, and the diameter of the vent hole 10 is D, and the adjacent row of the valve seat boss 101
  • One side surface of the gas valve piece 11 (for example, the upper surface shown in FIGS.
  • the radius R is 1.3 mm, and 0.12 R/D 0.38, so that the exhaust valve piece 1 1 can be supported on the valve seat boss 101, in accordance with this condition, and in the immersion environment of the refrigerating machine oil 12 of the present invention and the eccentricity e
  • the ratio of the inner diameter ⁇ of the cylinder 5 satisfies 0.05 eAD 0.12, the contact wear of the valve seat boss 101 itself and the exhaust valve plate 11 is optimal, thereby further reducing the wear of the exhaust valve plate 1 1 . .
  • the exhaust valve piece 1 1 is made of a stainless steel material, and the stainless steel material comprises:
  • the tensile strength of the stainless steel material is 1850 MPa to 2000 MPa.
  • the exhaust valve piece 1 1 can be made of a stainless steel material which has been subjected to a quenching and tempering process, and its chemical composition is as follows: 0.25 to 0.45 mass% of carbon, 0.3 to 0.5 mass% of silicon, 03 to 0.7 mass % of manganese, 0 to 0.03 mass% of phosphorus, 0 to 0.015 mass% of sulfur, 12 to 14 mass% of chromium, 0.5 to 2.0 mass% of molybdenum, the balance of iron, etc., and the exhaust valve piece 1 1 should be The tensile strength is 1850 MPa to 2000 MPa.
  • the chemical composition of the stainless steel material may contain other chemical components in addition to carbon, silicon, manganese, phosphorus, sulfur, chromium, molybdenum and iron.
  • the surface treatment layer of the compression device of the compressor according to the present invention is greatly improved, as shown in Fig. 5, the left side is the slide 7 of the conventional compressor after the abrasion test Schematic diagram of the surface treatment layer, the right side is a schematic view of the surface treatment layer of the sliding sheet 7 of the compressor of the present invention after the abrasion test, and it can be seen that the surface treatment layer of the conventional sliding sheet 7 (for example, as shown in FIG. 5) The vertical white bright layer) after the abrasion resistance test, the remaining thickness is ⁇ ⁇ , the surface treatment layer of the sliding sheet 7 of the present invention (for example, the vertical white bright layer shown in FIG. 5) is subjected to the abrasion resistance test. The thickness is 9 ⁇ , and the improvement is obvious.
  • the four curves are in order: In the conventional refrigeration oil 12 immersion environment, the wear degree and eccentricity e of the conventional valve seat boss 101 and the exhaust valve piece 1 and the cylinder bore diameter ⁇ The relationship between the ratio of the ratio; the relationship between the degree of wear of the slider 7 and the crankshaft 4 of the compression device and the ratio of the eccentricity e to the cylinder bore ⁇ of the cylinder 5 in the conventional refrigerating machine oil 12 immersion environment; The relationship between the degree of wear of the sliding piece 7 and the crankshaft 4 of the compression device and the ratio of the eccentric amount e to the cylinder bore diameter ⁇ of the cylinder 5 in the immersion environment of the invention; in the immersion environment of the refrigerating machine oil 12 of the present invention, A relationship between the degree of wear of the valve seat boss 101 of the present invention, the exhaust valve piece 11 of the present invention, and the ratio of the eccentric amount e to the cylinder bore diameter ⁇ of the cylinder 5.
  • An air conditioner (not shown) according to an embodiment of the second aspect of the present invention includes the compressor according to the above first embodiment of the present invention.
  • the compressed refrigerant used in the air conditioner may be R410A refrigerant or R32 refrigerant.
  • R410A refrigerant and R32 refrigerant are well known to those skilled in the art and will not be described in detail herein.
  • a water heater (not shown) according to an embodiment of the third aspect of the present invention includes the compressor according to the above first embodiment of the present invention.
  • the compressed refrigerant used in the hot water machine may be R410A refrigerant or R32 refrigerant.
  • the compressor according to the embodiment of the present invention can be widely used in various refrigeration or hot water machine systems, and the system uses R410A or R32 refrigerant, which can be widely applied to high temperature and high pressure operating environments. in.

Abstract

一种压缩机，包括：壳体（1）和压缩机构，压缩机构设在壳体（1）内且包括曲轴（4）、主轴承（8）、副轴承（9）和气缸（5），主轴承（8）和副轴承（9）分别设在气缸（5）的顶部和底部且与汽缸（5）共同限定出压缩腔，曲轴（4）的下端穿过主轴承（8）伸入压缩腔内，其中曲轴（4）的偏心部相对于汽缸（5）的中轴线的偏心量e与气缸（5）的内径Φ的比值满足：0.05≤e/Φ≤0.12。此外，还公开了一种包括上述压缩机的空调和热水机。

Description

压缩机、 空调器和热水机
技术领域
本发明涉及制冷设备领域， 尤其是涉及一种压縮机、 空调器和热水机。 背景技术
相关技术中，旋转式压縮机的密封壳体内有冷冻机油，压縮装置浸泡于冷冻机油中， 然而， 由于 R410A冷媒及新型 R32环保冷媒的使用， 在高温高压运行条件下， 普通压 縮机无法满足可靠性， 压縮装置磨损严重， 导致压縮机坏死。 发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。 为此， 本发明的一个目的在 于提出一种压縮机， 所述压縮机不易磨损坏死， 从而延长了压縮机的使用寿命， 提高了 压縮机的可靠性。
本发明的另一个目的在于提出一种具有上述压縮机的空调器。
本发明的再一个目的在于提出一种具有上述压縮机的热水机。
根据本发明第一方面的压縮机， 包括： 壳体， 所述壳体内的底部设有冷冻机油； 和 压縮装置， 所述压縮装置设在所述壳体内且包括曲轴、 主轴承、 副轴承和气缸， 所述主 轴承和所述副轴承分别设在所述气缸的顶部和底部且与所述气缸共同限定出压縮腔，所 述曲轴的下端穿过所述主轴承伸入所述压縮腔内，其中所述曲轴的偏心部相对于所述气 缸的中轴线的偏心量 e与所述气缸的内径 Φ的比值满足： 0.05 eAD 0.12。
根据本发明的压縮机， 通过将偏心量 e与气缸的内径 Φ的比值设置在 0.05 eAD 0.12之间， 可以改善压縮机高温高压运行时压縮装置中滑片、 曲轴的磨损失效程度， 从 而压縮机不易出现磨损的情况， 进而有效地延长了压縮机的使用寿命， 提高了压縮机的 可靠性以及整体性能。
进一步地， 所述冷冻机油为酯类油， 且所述酯类油在 40 °C时运动粘度为 70.5〜76.0mm2/s、 在 100°C时运动粘度为 8.4〜9.0mm2/s。
更进一步地， 所述冷冻机油内含有含硫极压抗磨剂。
可选地， 所述主轴承和所述副轴承中的至少一个上形成有排气孔， 所述排气孔上覆 盖有排气阀片， 所述排气阀片由不锈钢材料制成。
具体地， 所述不锈钢材料包含： 0.25〜0.45质量％的碳； 0.3〜0.5质量％的硅； 0.3〜0.7 质量％的锰； 0〜0.03质量％的磷； 0〜0.015质量％的硫； 12〜14质量％的铬； 0.5〜2.0质量％ 的钼； 以及余量的铁， 其中， 所述不锈钢材料的抗拉强度为 1850〜2000MPa。
进一步地， 所述排气孔为圆孔且直径为 D， 所述排气孔的邻近所述排气阀片的一侧 设有阀座凸台， 所述阀座凸台的邻近所述排气阀片的一侧表面形成为圆弧面， 所述圆弧 面的半径1 1.3 1^ 且 0.12 R/D 0.38。
根据本发明第二方面的空调器， 包括根据本发明上述第一方面的压縮机。
可选地， 所述空调器使用的压縮制冷剂为 R410A或 R32冷媒。
根据本发明第三方面的热水机， 包括根据本发明上述第一方面的压縮机。
可选地， 所述热水机使用的压縮制冷剂为 R410A或 R32冷媒。
本发明的附加方面和优点将在下面的描述中部分给出， 部分将从下面的描述中变得 明显， 或通过本发明的实践了解到。 附图说明
本发明的上述和 /或附加的方面和优点从结合下面附图对实施例的描述中将变得明 显和容易理解， 其中：
图 1是根据本发明实施例的压縮机的示意图；
图 2是图 1中所示的压縮机的俯视图；
图 3是图 1中圈示的 A部的放大图；
图 4是压縮机的压縮装置、 阀座凸台和排气阀片的磨损程度与 e/Φ的比值之间的关 系曲线图；
图 5是传统的压縮机的滑片与本发明实施例的压縮机的滑片经过耐磨试验后表面处 理层的剩余厚度的示意图。
附图标记：
1： 壳体； 2: 定子； 3 : 转子； 4 : 曲轴；
5： 气缸； 51 : 滑片槽；
6： 活塞； 7: 滑片； 8 : 主轴承； 9: 副轴承；
10： 排气孔； 1 1 : 排气阀片； 101 : 阀座凸台；
12： 冷冻机油。 具体实施方式
下面详细描述本发明的实施例， 所述实施例的示例在附图中示出， 其中自始至终相 同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附 图描述的实施例是示例性的， 仅用于解释本发明， 而不能理解为对本发明的限制。
在本发明的描述中， 需要理解的是， 术语"中心"、 "横向"、 "长度"、 "宽度"、 "上"、 "下"、 "左"、 "右"、 "竖直"、 "水平"、 "顶"、 "底"、 "内"、 "外"、 "轴向"、 "径向"、 "周 向"等指示的方位或位置关系为基于附图所示的方位或位置关系， 仅是为了便于描述本 发明和简化描述， 而不是指示或暗示所指的装置或元件必须具有特定的方位、 以特定的 方位构造和操作， 因此不能理解为对本发明的限制。 此外， 术语"第一"、 "第二"仅用于 描述目的， 而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数 量。 由此， 限定有 "第一"、 "第二 "的特征可以明示或者隐含地包括一个或者更多个该特 征。 在本发明的描述中， 除非另有说明， "多个"的含义是两个或两个以上。
在本发明的描述中， 需要说明的是， 除非另有明确的规定和限定， 术语"安装"、 "相 连"、 "连接 "应做广义理解， 例如， 可以是固定连接， 也可以是可拆卸连接， 或一体地 连接； 可以是直接相连， 也可以通过中间媒介间接相连， 可以是两个元件内部的连通。 对于本领域的普通技术人员而言， 可以具体情况理解上述术语在本发明中的具体含义。
下面参考图 1-图 5描述根据本发明第一方面实施例的压縮机，压縮机可以为旋转式 压縮机。 在本申请下面的描述中， 以压縮机为旋转式压縮机为例进行说明。 当然， 本领 域的技术人员可以理解， 根据本发明的压縮机还可以是其它类型的压縮机。
如图 1-图 3所示， 根据本发明第一方面实施例的压縮机， 包括壳体 1和压縮装置。 参照图 1， 壳体 1内的底部设有冷冻机油 12， 压縮装置设在壳体 1内， 且压縮装置 包括曲轴 4、 主轴承 8、 副轴承 9和气缸 5， 主轴承 8和副轴承 9分别设在气缸 5的顶 部和底部， 且主轴承 8、 副轴承 9与气缸 5共同限定出压縮腔， 曲轴 4的下端穿过主轴 承 8伸入压縮腔内。
例如在图 1和图 2的示例中， 密封的壳体 1内设置有电机和压縮装置， 压縮装置浸 泡于冷冻机油 12中， 电机设在壳体 1 内的上部， 压縮装置位于电机的下方， 电机包括 定子 2和转子 3，定子 2固定在壳体 1的内壁上，转子 3固定在压縮装置中的曲轴 4上， 从而转子 3转动时可以带动曲轴 4旋转， 压縮装置包括曲轴 4、 气缸 5、 活塞 6和滑片 7， 活塞 6套在曲轴 4外并在气缸 5内旋转， 气缸 5上设置有与滑片 7滑动连接的滑片 槽 51， 换言之， 气缸 5上形成有沿其径向延伸的滑片槽 51， 滑片 7可移动地设在滑片 槽 51 内， 气缸 5的两端分别设置有主轴承 8、 副轴承 9， 主轴承 8、 副轴承 9与气缸 5 共同围成压縮腔， 当电机工作时， 可以驱动曲轴 4转动， 从而带动套设在曲轴 4的偏心 部上的活塞 6沿着压縮腔的内壁滚动以压縮冷媒。 其中， 曲轴 4的偏心部相对于气缸 5的中轴线的偏心量 e与气缸 5的内径 Φ的比值 满足： 0.05 eAD 0.12。 如图 2所示， 偏心量 e为偏心部的中心轴线与气缸 5的中轴线 之间的距离， 当曲轴 4相对于气缸 5中轴线的偏心量 e与气缸 5缸径 Φ的比值满足条 件： 0.05 ε/Φ 0.12 时， 可以改善压縮机例如旋转式压縮机高温高压运行时压縮装置 中滑片 7、 曲轴 4的磨损失效程度。
参照图 4， 横坐标为偏心量 e与气缸 5缸径 Φ的比值、 纵坐标为压縮装置的磨损程 度以及压縮机的阀座凸台 101、排气阀片 1 1的磨损程度， 从图中可以看出，在满足 0.05 ^ e/O^ 0.12时各部分磨损达到最优值。
根据本发明实施例的压縮机例如旋转式压縮机， 通过将偏心量 e与气缸 5的内径 Φ 的比值设置在 0.05 ε/Φ 0.12之间， 可以改善压縮机高温高压运行时压縮装置中滑片 7、 曲轴 4的磨损失效程度， 从而压縮机不易出现磨损的情况， 进而有效地延长了压縮 机的使用寿命， 提高了压縮机的可靠性。
在本发明的一个实施例中， 如图 1所示， 冷冻机油 12为酯类油， 且酯类油在 40°C 时运动粘度为 70.5〜76.0mm2/s、 在 100°C时运动粘度为 8.4〜9.0mm2/s。 进一步地， 冷冻 机油 12内含有含硫极压抗磨剂。 由此， 通过采用 40°C时运动粘度为 70.5〜76.0mm2/s、 在 100°C时运动粘度为 8.4〜9.0mm2/s的冷冻机油 12， 可以保证高温高压且有冷媒溶解 时的润滑性， 大幅改善压縮装置的磨损， 延长压縮机例如旋转式压縮机的使用寿命， 且 按照偏心量 e与气缸 5缸径 Φ比值为 0.05 eAD 0.12设计的压縮装置， 在上述冷冻机 油 12环境下运行， 可以大幅度改善高温高压运行时压縮装置中滑片 7、 曲轴 4的磨损 失效程度。
可选地， 主轴承 8和副轴承 9中的至少一个上形成有排气孔 10， 排气孔 10上覆盖 有排气阀片 1 1。 也就是说， 排气孔 10可以仅形成在主轴承 8上， 或者仅形成在副轴承 9上， 或者同时形成在主轴承 8和副轴承 9上。 例如在图 1和图 2的示例中， 排气孔 10 仅形成在主轴承 8上， 排气孔 10沿上下方向贯穿主轴承 8， 排气孔 10上覆盖有随压縮 排气而开启的排气阀片 1 1， 从而压縮后的气体可以由排气孔 10排出。 进一步地， 排气 孔 10的邻近排气阀片 1 1的一侧设有阀座凸台 101， 换言之， 阀座凸台 101设置在排气 孔 10的与排气阀片 1 1接触的一侧表面（例如图 1和图 3中所示的上表面）上， 阀座凸 台 101可以大体为环形且与排气孔 10同轴布置， 具体地， 阀座凸台 101的内周壁与排 气孔 10的内周壁相接， 或者邻近排气孔 10的内周壁设置， 可选地， 排气孔 10为圆孔， 且排气孔 10的直径为 D， 阀座凸台 101的邻近排气阀片 1 1的一侧表面（例如图 1和图 3中所示的上表面） 形成为圆弧面， 此时阀座凸台 101的横截面为圆弧形式， 圆弧面的 半径 R 1.3mm， 且 0.12 R/D 0.38， 从而排气阀片 1 1可以支撑在阀座凸台 101上， 符合这一条件时， 且在本发明的冷冻机油 12浸泡环境下以及偏心量 e与气缸 5的内径 Φ的比值满足 0.05 eAD 0.12时，阀座凸台 101本身与排气阀片 1 1的接触磨损达到最 佳状态， 从而进一步减小了排气阀片 1 1出现磨损的情况。
进一步地， 排气阀片 1 1 由不锈钢材料制成， 不锈钢材料包含：
0.25-0.45质量％的碳； 0.3〜0.5质量％的硅； 0.3〜0.7质量％的锰； 0〜0.03质量％的磷； 0〜0.015质量％的硫； 12〜14质量％的铬； 0.5〜2.0质量％的钼； 以及余量的铁。
其中， 不锈钢材料的抗拉强度为 1850MPa〜2000MPa。
也就是说， 排气阀片 1 1 可以由经过淬火和回火工艺处理的不锈钢材料制成， 其化 学成分如下： 0.25〜0.45 质量％的碳、 0.3〜0.5 质量％的硅、 03〜0.7 质量％的锰、 0〜0.03 质量％的磷、 0〜0.015质量％的硫、 12〜14质量％的铬、 0.5〜2.0质量％的钼、其余为铁等， 且排气阀片 1 1应达到的抗拉强度为 1850MPa〜2000MPa， 这里， 需要说明的是， 不锈钢 材料的化学成分除了包含碳、 硅、 锰、 磷、 硫、 铬、 钼和铁外， 还可以含有其他化学成 分。
通过耐磨试验可以看出， 根据本发明的压縮机的压縮装置表面处理层得到大幅度改 善， 如图 5所示， 左侧是传统的压縮机的滑片 7经过耐磨试验后表面处理层的示意图， 右侧是本发明的压縮机的滑片 7经过耐磨试验后表面处理层的示意图， 可以看出， 传统 的滑片 7的表面处理层（例如图 5中所示的竖直的白亮层）经过耐磨试验后的剩余厚度 为 Ι μηι, 本发明的滑片 7的表面处理层（例如图 5中所示的竖直的白亮层）经过耐磨试 验后的剩余厚度为 9μηι， 改善明显。
参照图 4， 从上到下、 四条曲线依次为： 在传统的冷冻机油 12浸泡环境下， 传统的 阀座凸台 101、 排气阀片 1 1的磨损程度与偏心量 e与气缸 5缸径 Φ的比值之间的关系 曲线； 在传统的冷冻机油 12浸泡环境下， 压縮装置的滑片 7、 曲轴 4的磨损程度与偏 心量 e与气缸 5缸径 Φ的比值之间的关系曲线； 在本发明的冷冻机油 12浸泡环境下， 压縮装置的滑片 7、曲轴 4的磨损程度与偏心量 e与气缸 5缸径 Φ的比值之间的关系曲 线； 在本发明的冷冻机油 12浸泡环境下， 本发明的阀座凸台 101、 本发明的排气阀片 1 1的磨损程度与偏心量 e与气缸 5缸径 Φ的比值之间的关系曲线。从图 4中可以看出， 在上述冷冻机油 12环境下工作时， 压縮装置的滑片 7、 曲轴 4、 阀座凸台 101、 排气阀 片 1 1的磨损量大幅减小， 从而极大地改善高温高压运行时压縮装置的滑片 7、 曲轴 4、 阀座凸台 101 以及排气阀片 1 1的失效损坏程度， 并且磨损程度在本发明的偏心量与其 缸径比值范围内总体达到较优值。 根据本发明第二方面实施例的空调器 （图未示出） ， 包括根据本发明上述第一方面 实施例的压縮机。 可选地， 空调器使用的压縮制冷剂可以为 R410A冷媒或 R32冷媒。 这里， 需要说明的是， R410A冷媒和 R32冷媒已为本领域的技术人员所熟知， 这里不 再详细描述。
根据本发明第三方面实施例的热水机 （图未示出） ， 包括根据本发明上述第一方面 实施例的压縮机。 可选地， 热水机使用的压縮制冷剂可以为 R410A冷媒或 R32冷媒。
综上所述， 根据本发明实施例的压縮机， 可以广泛运用于各种制冷或热水机系统中， 该 系统使用 R410A或 R32制冷剂， 该系统可以广泛应用到高温、 高压的运行环境中。
在本说明书的描述中，参考术语"一个实施例"、 "一些实施例"、 "示意性实施例"、 "示例"、 "具体示例"、 或"一些示例"等的描述意指结合该实施例或示例描述的具体特征、 结构、 材料 或者特点包含于本发明的至少一个实施例或示例中。 在本说明书中， 对上述术语的示意性 表述不一定指的是相同的实施例或示例。 而且， 描述的具体特征、 结构、 材料或者特点可 以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例， 本领域的普通技术人员可以理解： 在不脱 离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、 修改、 替换和变型， 本发明的范围由权利要求及其等同物限定。

Claims

权利要求书
1、 一种压縮机， 其特征在于， 包括：
壳体， 所述壳体内的底部设有冷冻机油； 和
压縮装置， 所述压縮装置设在所述壳体内且包括曲轴、 主轴承、 副轴承和气缸， 所 述主轴承和所述副轴承分别设在所述气缸的顶部和底部且与所述气缸共同限定出压縮 腔， 所述曲轴的下端穿过所述主轴承伸入所述压縮腔内， 其中所述曲轴的偏心部相对于 所述气缸的中轴线的偏心量 e与所述气缸的内径 Φ的比值满足：
0.05 eAD 0.12。
2、 根据权利要求 1 所述的压縮机， 其特征在于， 所述冷冻机油为酯类油， 且所述 酯类油在 40°C时运动粘度为 70.5〜76.0mm2/s、 在 100°C时运动粘度为 8.4〜9.0mm2/s。
3、 根据权利要求 2所述的压縮机， 其特征在于， 所述冷冻机油内含有含硫极压抗 磨剂。
4、根据权利要求 1-3中任一项所述的压縮机， 其特征在于， 所述主轴承和所述副轴 承中的至少一个上形成有排气孔， 所述排气孔上覆盖有排气阀片， 所述排气阀片由不锈 钢材料制成。
5、 根据权利要求 4所述的压縮机， 其特征在于， 所述不锈钢材料包含：
0.25-0.45质量％的碳；
0.3〜0.5质量％的硅；
0.3〜0.7质量％的锰；
0-0.03质量％的磷；
0-0.015质量％的硫；
12〜14质量％的铬；
0.5〜2.0质量％的钼； 以及
余量的铁
其中， 所述不锈钢材料的抗拉强度为 1850〜2000MPa。
6、 根据权利要求 4所述的压縮机， 其特征在于， 所述排气孔为圆孔且直径为 D， 所述排气孔的邻近所述排气阀片的一侧设有阀座凸台， 所述阀座凸台的邻近所述排 气阀片的一侧表面形成为圆弧面， 所述圆弧面的半径 R 1.3mm， 且 0.12 R/D 0.38。
7、 一种空调器， 其特征在于， 包括根据权利要求 1 -6中任一项所述的压縮机。
8、 根据权利要求 7所述的空调器， 其特征在于， 所述空调器使用的压縮制冷剂为 R410A或 R32冷媒。
9、 一种热水机， 其特征在于， 包括根据权利要求 1 -6中任一项所述的压縮机。
10、 根据权利要求 9所述的热水机， 其特征在于， 所述热水机使用的压縮制冷剂为 R410A或 32冷媒。
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