WO2017049545A1 - 旋转式压缩机 - Google Patents

旋转式压缩机 Download PDF

Info

Publication number
WO2017049545A1
WO2017049545A1 PCT/CN2015/090608 CN2015090608W WO2017049545A1 WO 2017049545 A1 WO2017049545 A1 WO 2017049545A1 CN 2015090608 W CN2015090608 W CN 2015090608W WO 2017049545 A1 WO2017049545 A1 WO 2017049545A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotary compressor
rotor core
housing
end wall
dst
Prior art date
Application number
PCT/CN2015/090608
Other languages
English (en)
French (fr)
Inventor
杨恒
廖健生
刘丹伟
Original Assignee
广东美芝制冷设备有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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 JP2017516080A priority Critical patent/JP2017531755A/ja
Priority to US15/502,309 priority patent/US20180195512A1/en
Priority to PCT/CN2015/090608 priority patent/WO2017049545A1/zh
Priority to EP15899910.2A priority patent/EP3354902B1/en
Publication of WO2017049545A1 publication Critical patent/WO2017049545A1/zh

Links

Images

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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • 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
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • 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
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • 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
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • 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
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise
    • F04C2270/135—Controlled or regulated

Definitions

  • the present invention relates to the field of compressor equipment, and in particular to a rotary compressor.
  • a strong pressure pulsation occurs when the high-pressure gas refrigerant inside the compressor is discharged, and most of the noise is generated in the central cavity of the compressor, transmitted to the upper cavity through the rotor vent hole, and finally transmitted from the casing to the compression. Outside the machine.
  • the high-pressure refrigerant gas discharged from the compression pump body first reaches the central cavity.
  • the central cavity and the upper cavity mainly generate noise in the frequency band of 1000 Hz to 1250 Hz. This part of the noise can be eliminated by the sound insulation cotton, and the air conditioning system will be extremely harsh. , affecting the user experience.
  • the present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention is directed to a rotary compressor which has the advantages of low noise, simple and reasonable structure, and the like.
  • a rotary compressor includes: a housing, a motor, and a compression mechanism, the axial ends of the housing having a first end wall and a second end wall, respectively, the motor including a stator core and a rotor core, in the shell In the axial direction of the body, the maximum distance between the one end surface of the stator core adjacent to the first end wall and the first end wall is Dst, the compression mechanism is located on a side of the motor remote from the first end wall, and the compression mechanism includes a cylinder a component and a main bearing, the main bearing being coupled to a side end surface of the cylinder assembly adjacent to the motor, adjacent to a flange end of the main bearing in an axial direction of the housing and a side end of the rotor core adjacent to the first end wall
  • Drt The minimum distance between one end faces of the first end wall is Drt, where Dst and Drt satisfy the relationship: 0.335 ⁇ Dst / Drt ⁇ 0.838.
  • the noise during operation of the rotary compressor can be effectively reduced, so that the rotary compressor has a simple and reasonable structure, is simple to assemble, and is effective. Ground to reduce noise and other advantages.
  • the Dst and the Drt further satisfy a relationship: 0.568 ⁇ Dst / Drt ⁇ 0.680.
  • the rotor core is formed with a through hole through which a central axis is parallel to an axis of rotation of the rotor core.
  • the vent holes are axially symmetrically distributed with respect to a first diameter of the rotor core, and a width D of the vent holes in the first diameter direction satisfies: 0.204 mm ⁇ D ⁇ 0.480 mm .
  • the D further satisfies: 0.404 mm ⁇ D ⁇ 0.460 mm.
  • the outline of the cross section of the vent hole is formed as a curve or a knot of a straight line and a curve Hehe.
  • the cross-sectional shape and size of the vent holes are the same in the direction of the rotation axis of the rotor core.
  • the vent holes are plural and evenly spaced in the circumferential direction of the rotor core.
  • each of the vent holes has the same shape and size.
  • the rotor core is rotatably provided inside the stator core.
  • FIG. 1 is a cross-sectional view of a rotary compressor in accordance with an embodiment of the present invention
  • FIG. 2 is an axial schematic view of a rotor core according to an embodiment of the present invention.
  • FIG. 3 is an axial schematic view of a rotor core according to another embodiment of the present invention.
  • FIG. 4 is an axial schematic view of a rotor core according to still another embodiment of the present invention.
  • FIG. 5 is a graph showing a relationship between a Dst/Drt value and a noise value according to an embodiment of the present invention
  • Figure 6 is a graph of D values versus noise values in accordance with an embodiment of the present invention.
  • a housing 1 a housing 1; a first housing 11; a first end wall 111;
  • a second housing 13 a second housing 13; a second end wall 131;
  • Compression mechanism 3 cylinder assembly 31; main bearing 32; flange portion 321;
  • a rotary compressor 100 which can convert a low-temperature low-pressure refrigerant into a high-temperature high-pressure refrigerant discharge, will be described below with reference to Figs.
  • the rotary compressor 100 may be a vertical compressor or a bedroom compressor, and the following description will be made by taking the rotary compressor 100 as a vertical compressor as an example.
  • a rotary compressor 100 includes a housing 1, a motor 2, a compression mechanism 3, and a crankshaft 4.
  • the axial ends of the housing 1 respectively have a first end wall 111 and a second end wall 131.
  • the housing 1 may include a first housing 11, an intermediate housing 12, and a second housing.
  • the intermediate casing 12 may be formed in a cylindrical shape, so that the cylindrical intermediate casing 12 may define a certain accommodation space for facilitating components inside the rotary compressor 100 (for example, the motor shown in FIG. 1). 2 and the installation of the compression mechanism 3).
  • a first housing 11 (such as the upper housing shown in FIG. 1) and a second housing 13 (such as the lower housing shown in FIG. 1) are respectively coupled to the axial ends of the intermediate housing 12,
  • the first end wall 111 may be the bottom wall surface of the first housing 11
  • the second end wall 131 may be the top wall surface of the second housing 13.
  • any one of the first housing 11 and the second housing 13 may be integrally formed with the intermediate housing 12.
  • the first housing 11 may be integrally formed with the intermediate housing 12 so as to be assembled with zero. After the component, the intermediate casing 12 and the second casing 13 are fixed together to facilitate assembly of the rotary compressor 100, thereby improving production efficiency.
  • the second housing 13 can also be integrally formed with the intermediate housing 12, so that after the components are assembled, the intermediate housing 12 and the first housing 11 are fixed together to complete the assembly of the rotary compressor 100.
  • the motor 2 is disposed in the housing 1, and the motor 2 includes a stator core 21 and a rotor core 22 in the axial direction of the housing 1 (for example, the up and down direction shown in FIG. 1) of the stator core 21
  • the maximum distance between the one end surface adjacent to the first end wall 111 and the first end wall 111 is Dst.
  • the upper end surface of the stator core 21 and the first end wall 111 are in the up and down direction. The distance between them is Dst.
  • Dst is the maximum between the upper end surface of the stator core 21 and the inner side wall of the first casing 11. distance.
  • the compression mechanism 3 is disposed in the housing 1 and located on a side of the motor 2 remote from the first end wall 111.
  • the compression mechanism 3 may be disposed below the motor 2, so that the compression mechanism 3 is Motor 2 away from the first end wall 111, and facilitates the installation and cooperation of the motor 2 and the compression mechanism 3.
  • the compression mechanism 3 includes a cylinder assembly 31 and a main bearing 32 that is coupled to a side end surface of the cylinder assembly 31 adjacent to the motor 2 (for example, the upper end surface of the cylinder assembly 31 shown in FIG. 1).
  • the one end surface of the rotor core 22 adjacent to the first end wall 111 is adjacent to the flange portion 321 of the main bearing 32.
  • the minimum distance between one end faces of the end walls 111 is Drt, for example, in the example of Fig. 1, the distance between the upper end face of the rotor core 22 and the uppermost end of the flange portion 321 of the main bearing 32 is Drt.
  • Dst and Drt satisfy the relationship: 0.335 ⁇ Dst / Drt ⁇ 0.838.
  • the abscissa in FIG. 5 represents the value of Dst/Drt
  • the ordinate ⁇ in FIG. 5 represents the rotary compression.
  • the noise OA value of the machine 100 during operation specifically, as the Dst/Drt continues to increase, the operating noise OA value of the rotary compressor 100 is gradually reduced to a certain extent, and then gradually increased, through the rotary type
  • the different design of the Dst/Drt ratio of the compressor 100 causes the rotary compressor 100 to have different noises. For example, when the Dst/Drt is 0.4, 0.45, 0.55, 0.6, 0.75, the operating noise of the rotary compressor 100 will be It is effectively reduced.
  • the motor 2 and the compression mechanism 3 can both be disposed coaxially with the housing 1, that is, the central axis of the crankshaft 4 coincides with the central axis of the housing 1, so that the axis of rotation of the rotor core 22 and the shell
  • the central axes of the bodies 1 coincide, and the central axis of the main bearing 32 and the central axis of the cylinder assembly 31 also coincide with the central axis of the housing 1, so that the structure of the rotary compressor 100 can be simplified and rationalized, and the rotary compression is facilitated. Assembly of machine 100.
  • the noise during operation of the rotary compressor 100 can be effectively reduced, so that the rotary compressor 100 has a simple and reasonable structure. Simple assembly and effective noise reduction.
  • Dst and Drt further satisfy the relationship: 0.568 ⁇ Dst / Drt ⁇ 0.680, for example, when Dst / Drt is 0.58, 0.6 or 0.65, the operating noise of the rotary compressor 100 is near the minimum, thereby knowing that by rotating
  • the Dst/Drt value of the compressor 100 is set to 0.568 ⁇ Dst / Drt ⁇ 0.680, and the operating noise of the rotary compressor 100 can be further reduced.
  • the high temperature and high pressure refrigerant discharged from the compression mechanism 3 is driven upward, and the rotor core 22 is formed with a through hole 221 therein, thereby facilitating the high temperature and high pressure refrigerant.
  • the upward drive reduces noise.
  • the central axis of the vent hole 221 is parallel to the rotation axis of the rotor core 22, for example, in the example of FIG. 1, the rotation axis of the rotor core 22 is the up and down direction, so that the central axis of the vent hole 221 can also be the up and down direction. , Thereby, the upward transmission of the high temperature and high pressure refrigerant is further facilitated, and the noise is further effectively reduced.
  • the vent holes 221 are axially symmetrically distributed with respect to the first diameter of the rotor core 22, and the width D of the vent holes 221 in the first diameter direction satisfies: 0.204 mm ⁇ D ⁇ 0.480 mm, for example,
  • the venting holes 221 may be symmetrically disposed with respect to the first diameter k of the rotor core 22, and the width of the vent holes 221 at the first diameter k is D.
  • FIG. 6 it is to be noted that, in FIG.
  • the abscissa represents the value of D
  • the ordinate ⁇ in Fig. 6 represents the noise OA value at the time of operation of the rotary compressor 100.
  • the operating noise of the rotary compressor 100 is gradually increased. Decreasing to a certain extent, and then gradually increasing, by the different design of the D value of the vent hole 221 of the rotary compressor 100, the rotary compressor 100 is made to have different noise, for example, D is 0.25 mm, 0.35. At mm and 0.41 mm, the operating noise of the rotary compressor 100 is effectively reduced.
  • the operating noise of the rotary compressor 100 can be effectively reduced by setting the D value of the vent hole 221 of the rotary compressor 100 to 0.204 mm ⁇ D ⁇ 0.480 mm.
  • D further satisfies: 0.404 mm ⁇ D ⁇ 0.460 mm, for example, when D is 0.41 mm, 0.43 mm or 0.45 mm, the operating noise of the rotary compressor 100 is nearly the lowest, thereby knowing that by rotating the compression
  • the D value of the vent hole 221 of the machine 100 is set to 0.404 mm ⁇ D ⁇ 0.460 mm, and the operating noise of the rotary compressor 100 can be further reduced.
  • the outline of the cross section of the vent hole 221 may be formed as a curve or a combination of a straight line and a curved line.
  • the cross section of the vent hole 221 may be a hollow arc shape (as shown in FIG. 2). It may also be circular (as shown in FIG. 3), or may be a rounded rectangle (as shown in FIG. 4), thereby facilitating the circulation of the high-temperature and high-pressure refrigerant and reducing the operating noise of the rotary compressor 100.
  • the present invention is not limited thereto, and the cross section of the vent hole 221 may also be other curves or a combination of a straight line and a curved line to better meet the actual use requirements.
  • the cross-sectional shape and size of the vent holes 221 are the same in the direction of the rotation axis of the rotor core 22 (for example, the up-and-down direction shown in FIG. 1), thereby facilitating the vent holes 221 on the one hand.
  • the processing reduces the complexity of the production process of the rotary compressor 100, and on the other hand, makes the flow of the high-temperature and high-pressure refrigerant more uniform when passing through the vent 221, and further reduces the operating noise of the rotary compressor 100.
  • the vent holes 221 may be plural and evenly spaced in the circumferential direction of the rotor core 22, that is, the plurality of vent holes 221 are on the circumference of the rotor core 22.
  • the arrangement is evenly spaced upwards to facilitate the processing of the venting holes 221 and facilitate the circulation of high temperature and high pressure refrigerant.
  • each vent hole 221 has the same shape and size, thereby further facilitating the processing of the vent hole 221, improving the uniformity of circulation of the high temperature and high pressure refrigerant, and thereby effectively reducing the rotary compressor 100. Working noise.
  • the rotor core 22 is rotatably disposed inside the stator core 21, and specifically, the outer peripheral wall of the stator core 21 may be fixed to the inner peripheral wall of the casing 1.
  • the rotor core 22 can be thermally coupled to the crankshaft 4, thereby effectively improving the mating stability of the motor 2 and the compression mechanism 3, and facilitating assembly of the rotary compressor 100.
  • the present invention is not limited thereto, and the rotor core 22 may be rotatably provided outside the stator core 21.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features either explicitly or implicitly.
  • the meaning of "a plurality” is two or more unless specifically and specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. , or integrated; can be mechanical connection, electrical connection, or communication; can be directly connected, or indirectly connected through an intermediate medium, can be the internal connection of two components or the interaction of two components .
  • installation can be understood on a case-by-case basis.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

Landscapes

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

Abstract

一种旋转式压缩机（100），包括：壳体（1）、电机（2）以及压缩机构（3），电机（2）包括定子铁芯（21）和转子铁芯（22），压缩机构（3）包括气缸组件（31）和连接在气缸组件（31）的邻近电机（2）一侧的主轴承（32），定子铁芯（21）的邻近第一端壁（111）的一侧端面与第一端壁（111）之间的最大距离为Dst，转子铁芯（22）的邻近第一端壁（111）的一侧端面与主轴承（32）的法兰部（321）的邻近第一端壁（111）的一侧端面之间的最小距离为Drt，0.335≤Dst/Drt≤0.838。

Description

旋转式压缩机 技术领域
本发明涉及压缩机设备领域，具体而言，特别涉及一种旋转式压缩机。
背景技术
相关技术中指出，压缩机内部高压气体冷媒排出时会产生强烈的压力脉动，其中大部分噪音在压缩机的中部空腔产生，经转子通气孔传到上部空腔，最后由壳体传至压缩机外部。而压缩泵体排出的高压冷媒气体首先到达中部空腔，中部空腔与上部空腔主要产生了1000Hz至1250Hz频段噪音，这部分噪音由于无法被隔音棉消除，在空调系统上会表现得异常刺耳，影响用户体验。
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，本发明在于提出一种旋转式压缩机，所述旋转式压缩机具有噪音小、结构简单合理等优点。
根据本发明的旋转式压缩机，包括：壳体、电机以及压缩机构，壳体的轴向两端分别具有第一端壁和第二端壁，电机包括定子铁芯和转子铁芯，在壳体的轴向上、定子铁芯的邻近第一端壁的一侧端面与第一端壁之间的最大距离为Dst，压缩机构位于电机的远离第一端壁的一侧，压缩机构包括气缸组件和主轴承，主轴承连接在气缸组件的邻近电机的一侧端面上，在壳体的轴向上、转子铁芯的邻近第一端壁的一侧端面与主轴承的法兰部的邻近第一端壁的一侧端面之间的最小距离为Drt，其中，Dst和Drt满足关系：0.335≤Dst/Drt≤0.838。
根据本发明的旋转式压缩机，通过将Dst/Drt的值设置在合理的范围内，可有效地降低旋转式压缩机工作时的噪音，使得旋转式压缩机具有结构简单合理、装配简单以及有效地降低噪声等优点。
根据本发明的一个示例，所述Dst和所述Drt进一步满足关系：0.568≤Dst/Drt≤0.680。
根据本发明的一个示例，所述转子铁芯上形成有贯穿的通气孔，所述通气孔的中心轴线与所述转子铁芯的旋转轴线平行。
根据本发明的一个示例，所述通气孔关于所述转子铁芯的第一直径呈轴对称分布，所述通气孔在所述第一直径方向上的宽度D满足：0.204mm≤D≤0.480mm。
根据本发明的一个示例，所述D进一步满足：0.404mm≤D≤0.460mm。
根据本发明的一个示例，所述通气孔的横截面的轮廓线形成为曲线或直线与曲线的结 合。
根据本发明的一个示例，在所述转子铁芯的旋转轴线方向上、所述通气孔的横截面形状、尺寸均相同。
根据本发明的一个示例，所述通气孔为多个且在所述转子铁芯的周向上均匀地间隔开。
根据本发明的一个示例，每个所述通气孔的形状、尺寸均相同。
根据本发明的一个示例，所述转子铁芯可转动地设在所述定子铁芯的内侧。
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
图1是根据本发明实施例的旋转式压缩机的剖视图；
图2是根据本发明一个实施例的转子铁芯的轴向示意图；
图3是根据本发明另一个实施例的转子铁芯的轴向示意图；
图4是根据本发明再一个实施例的转子铁芯的轴向示意图；
图5是根据本发明实施例的Dst/Drt值与噪音值的关系曲线图；
图6是根据本发明实施例的D值与噪音值的关系曲线图。
附图标记：
旋转式压缩机100；
壳体1；第一壳体11；第一端壁111；
中间壳体12；
第二壳体13；第二端壁131；
电机2；定子铁芯21；
转子铁芯22；通气孔221；
压缩机构3；气缸组件31；主轴承32；法兰部321；
曲轴4。
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，旨在用于解释本发明，而不能理解为对本发明的限制。
下文的公开提供了许多不同的实施例或例子用来实现本发明的不同结构。为了简化本发明的公开，下文中对特定例子的部件和设置进行描述。当然，它们仅仅为示例，并且目的不在于限制本发明。此外，本发明可以在不同例子中重复参考数字和/或字母。这种重复是为了简化和清楚的目的，其本身不指示所讨论各种实施例和/或设置之间的关系。此外，本发明提供了的各种特定的工艺和材料的例子，但是本领域普通技术人员可以意识到其他工艺的可应用于性和/或其他材料的使用。
下面参考图1-图6描述根据本发明实施例的旋转式压缩机100，所述旋转式压缩机100可以将低温低压的冷媒转换成高温高压的冷媒排出。其中，旋转式压缩机100可以为立式压缩机或卧室压缩机等，下面仅以旋转式压缩机100为立式压缩机为例进行说明。
参考图1，根据本发明实施例的旋转式压缩机100，包括：壳体1、电机2、压缩机构3以及曲轴4。
其中，壳体1的轴向两端分别具有第一端壁111和第二端壁131，例如图1的示例中，壳体1可以包括第一壳体11、中间壳体12、第二壳体13，中间壳体12可以形成为圆筒形，从而圆筒形的中间壳体12可限定出一定的容纳空间，便于旋转式压缩机100内部的零部件(例如图1中所示的电机2和压缩机构3)的安装。
参考图1，第一壳体11(例如图1中所示上壳体)和第二壳体13(例如图1中所示下壳体)分别连接在中间壳体12的轴向两端，这样，第一端壁111可以为第一壳体11的底壁面，第二端壁131可以为第二壳体13的顶壁面。
进一步地，第一壳体11和第二壳体13中的任一个可以与中间壳体12一体成型，参考图1，第一壳体11可以与中间壳体12一体成型，从而在装配好零部件后，将中间壳体12与第二壳体13固定在一起，便于旋转式压缩机100的装配，提高生产效率。当然，第二壳体13也可以与中间壳体12一体成型，从而在装配好零部件后，将中间壳体12与第一壳体11固定在一起，完成旋转式压缩机100的装配。
具体地，电机2设在壳体1内，电机2包括定子铁芯21和转子铁芯22，在壳体1的轴向(例如图1中所示的上下方向)上、定子铁芯21的邻近第一端壁111的一侧端面与第一端壁111之间的最大距离为Dst，例如在图1的示例中，在上下方向上，定子铁芯21的上端面与第一端壁111之间的距离为Dst，这里需要说明的是，当第一壳体11为不规则形状的外形时，Dst则为定子铁芯21的上端面与第一壳体11的内侧壁之间的最大距离。
进一步地，压缩机构3设在壳体1内且位于电机2的远离第一端壁111的一侧，例如图1的示例中，压缩机构3可以设置在电机2的下方，从而压缩机构3较电机2远离第一端壁 111，且便于电机2和压缩机构3的安装和配合工作。
具体地，参考图1，压缩机构3包括气缸组件31和主轴承32，主轴承32连接在气缸组件31的邻近电机2的一侧端面(例如图1中所示的气缸组件31的上端面)上，在壳体1的轴向(例如图1中所示的上下方向)上、转子铁芯22的邻近第一端壁111的一侧端面与主轴承32的法兰部321的邻近第一端壁111的一侧端面之间的最小距离为Drt，例如在图1的示例中，转子铁芯22的上端面与主轴承32的法兰部321的最上端之间的距离为Drt。
其中，Dst和Drt满足关系：0.335≤Dst/Drt≤0.838，参考图5，这里需要说明的是，图5中的横坐标代表Dst/Drt的值，图5中的纵坐标α代表旋转式压缩机100工作时的噪音OA值，具体地，随着Dst/Drt的不断增大，旋转式压缩机100的工作噪音OA值先逐渐降低到一定程度，随后再逐渐的增大，通过对旋转式压缩机100的Dst/Drt比值的不同设计，会使得旋转式压缩机100具有不同的噪音，例如，Dst/Drt为0.4、0.45、0.55、0.6、0.75时，旋转式压缩机100的工作噪音都会得到有效地降低。
由此可知，通过将旋转式压缩机100的Dst/Drt值设置为：0.335≤Dst/Drt≤0.838，都会有效地降低旋转式压缩机100的工作噪音。
这里需要说明的是，电机2和压缩机构3可以均与壳体1同轴设置，也就是说，曲轴4的中心轴线与壳体1的中心轴线重合，从而转子铁芯22的旋转轴线与壳体1的中心轴线重合，主轴承32的中心轴线和气缸组件31的中心轴线也均与壳体1的中心轴线重合，这样，可使得旋转式压缩机100的结构简单合理，且便于旋转式压缩机100的装配。
根据本发明实施例的旋转式压缩机100，通过将Dst/Drt的值设置在合理的范围内，可有效地降低旋转式压缩机100工作时的噪音，使得旋转式压缩机100具有结构简单合理、装配简单以及有效地降低噪声等优点。
优选地，Dst和Drt进一步满足关系：0.568≤Dst/Drt≤0.680，例如，当Dst/Drt为0.58、0.6或0.65时，旋转式压缩机100的工作噪音接近最低，由此可知，通过将旋转式压缩机100的Dst/Drt值设置为：0.568≤Dst/Drt≤0.680，可进一步地降低旋转式压缩机100的工作噪音。
在本发明的一些实施例中，参考图1和图2，从压缩机构3排出的高温高压的冷媒会向上传动，转子铁芯22上形成有贯穿的通气孔221，从而可便于高温高压的冷媒的向上传动，降低噪音。
进一步地，通气孔221的中心轴线与转子铁芯22的旋转轴线平行，例如在图1的示例中，转子铁芯22的旋转轴线为上下方向，从而通气孔221的中心轴线也可以为上下方向， 从而进一步地便于高温高压的冷媒的向上传动，进一步有效地降低噪音。
在本发明的一些实施例中，通气孔221关于转子铁芯22的第一直径呈轴对称分布，通气孔221在第一直径方向上的宽度D满足：0.204mm≤D≤0.480mm，例如在图2的示例中，通气孔221可关于转子铁芯22的第一直径k对称设置，通气孔221在第一直径k上的宽度为D，参考图6，这里需要说明的是，图6中的横坐标代表D的值，图6中的纵坐标α代表旋转式压缩机100工作时的噪音OA值，具体地，随着D值的不断变大，转式压缩机100的工作噪音先逐渐降低到一定程度，随后再逐渐的增大，通过对旋转式压缩机100的通气孔221的D值的不同设计，会使得旋转式压缩机100具有不同的噪音，例如，D为0.25mm、0.35mm、0.41mm时，旋转式压缩机100的工作噪音都会得到有效地降低。
由此可知，通过将旋转式压缩机100的通气孔221的D值设置为：0.204mm≤D≤0.480mm，可以有效地降低旋转式压缩机100的工作噪音。
优选地，D进一步满足：0.404mm≤D≤0.460mm，例如，当D为0.41mm、0.43mm或0.45mm时，旋转式压缩机100的工作噪音接近最低，由此可知，通过将旋转式压缩机100的通气孔221的D值设置为：0.404mm≤D≤0.460mm，可进一步地降低旋转式压缩机100的工作噪音。
在本发明的一些实施例中，通气孔221的横截面的轮廓线可以形成为曲线或直线与曲线的结合，例如，通气孔221的横截面可以为空心弧形状(如图2中所示)，也可以为圆形(如图3中所示)，还可以为圆角矩形(如图4中所示)，从而便于高温高压的冷媒的流通，降低旋转式压缩机100的工作噪音。当然，本发明不限于此，通气孔221的横截面也可以是其他曲线或者直线与曲线的结合形状，以便更好地满足实际的使用需求。
在本发明的一些实施例中，在转子铁芯22的旋转轴线方向(例如图1中所示的上下方向)上、通气孔221的横截面形状、尺寸均相同，从而一方面便于通气孔221的加工，减少旋转式压缩机100的生产工艺复杂性，另一方面可使得高温高压的冷媒在通过通气孔221时的流动更加均匀，进一地降低旋转式压缩机100的工作噪音。
在本发明的一些实施例中，参考图2，通气孔221可以为多个且在转子铁芯22的周向上均匀地间隔开，也就是说，多个通气孔221在转子铁芯22的周向上均匀地间隔开设置，从而方便通气孔221的加工，且便于高温高压冷媒的流通。
进一步地，参考图2-图4，每个通气孔221的形状、尺寸均相同，从而进一步地方便通气孔221的加工，提高高温高压冷媒的流通均匀性，进而有效地降低旋转式压缩机100的工作噪音。
在本发明的一些实施例中，参考图1，转子铁芯22可转动地设在定子铁芯21的内侧，具体而言，定子铁芯21的外周壁可以与壳体1的内周壁固定，转子铁芯22可以与曲轴4热套相连，从而有效地提高电机2与压缩机构3的配合稳定性，且便于旋转式压缩机100的装配。当然，本发明不限于此，转子铁芯22也可以转动地设在定子铁芯21的外侧。
另外，根据本发明实施例的旋转式压缩机的其他构成、工作原理以及运转方式对于本领域普通技术人员而言都是已知的，这里不再详细描述。在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”、“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，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接，还可以是通信；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或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“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 表述不必须针对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一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
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 (10)

  1. 一种旋转式压缩机，其特征在于，包括：
    壳体，所述壳体的轴向两端分别具有第一端壁和第二端壁；
    电机，所述电机设在所述壳体内，所述电机包括定子铁芯和转子铁芯，在所述壳体的轴向上、所述定子铁芯的邻近所述第一端壁的一侧端面与所述第一端壁之间的最大距离为Dst；
    压缩机构，所述压缩机构设在所述壳体内且位于所述电机的远离所述第一端壁的一侧，所述压缩机构包括气缸组件和主轴承，所述主轴承连接在所述气缸组件的邻近所述电机的一侧端面上，在所述壳体的轴向上、所述转子铁芯的邻近所述第一端壁的一侧端面与所述主轴承的法兰部的邻近所述第一端壁的一侧端面之间的最小距离为Drt，
    其中，所述Dst和所述Drt满足关系：0.335≤Dst/Drt≤0.838。
  2. 根据权利要求1所述的旋转式压缩机，其特征在于，所述Dst和所述Drt进一步满足关系：0.568≤Dst/Drt≤0.680。
  3. 根据权利要求1所述的旋转式压缩机，其特征在于，所述转子铁芯上形成有贯穿的通气孔，所述通气孔的中心轴线与所述转子铁芯的旋转轴线平行。
  4. 根据权利要求3所述的旋转式压缩机，其特征在于，所述通气孔关于所述转子铁芯的第一直径呈轴对称分布，所述通气孔在所述第一直径方向上的宽度D满足：0.204mm≤D≤0.480mm。
  5. 根据权利要求4所述的旋转式压缩机，其特征在于，所述D进一步满足：0.404mm≤D≤0.460mm。
  6. 根据权利要求3-5中任一项所述的旋转式压缩机，其特征在于，所述通气孔的横截面的轮廓线形成为曲线或直线与曲线的结合。
  7. 根据权利要求3-6中任一项所述的旋转式压缩机，其特征在于，在所述转子铁芯的旋转轴线方向上、所述通气孔的横截面形状、尺寸均相同。
  8. 根据权利要求3-7中任一项所述的旋转式压缩机，其特征在于，所述通气孔为多个且在所述转子铁芯的周向上均匀地间隔开。
  9. 根据权利要求8所述的旋转式压缩机，其特征在于，每个所述通气孔的形状、尺寸均相同。
  10. 根据权利要求1-9中任一项所述的旋转式压缩机，其特征在于，所述转子铁芯可转动地设在所述定子铁芯的内侧。
PCT/CN2015/090608 2015-09-24 2015-09-24 旋转式压缩机 WO2017049545A1 (zh)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2017516080A JP2017531755A (ja) 2015-09-24 2015-09-24 回転式圧縮機
US15/502,309 US20180195512A1 (en) 2015-09-24 2015-09-24 Rotary compressor
PCT/CN2015/090608 WO2017049545A1 (zh) 2015-09-24 2015-09-24 旋转式压缩机
EP15899910.2A EP3354902B1 (en) 2015-09-24 2015-09-24 Rotary compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2015/090608 WO2017049545A1 (zh) 2015-09-24 2015-09-24 旋转式压缩机

Publications (1)

Publication Number Publication Date
WO2017049545A1 true WO2017049545A1 (zh) 2017-03-30

Family

ID=58385621

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/090608 WO2017049545A1 (zh) 2015-09-24 2015-09-24 旋转式压缩机

Country Status (4)

Country Link
US (1) US20180195512A1 (zh)
EP (1) EP3354902B1 (zh)
JP (1) JP2017531755A (zh)
WO (1) WO2017049545A1 (zh)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09144679A (ja) * 1995-11-20 1997-06-03 Hitachi Ltd ロータリ式圧縮機
JP2002295380A (ja) * 2001-03-29 2002-10-09 Mitsubishi Electric Corp 横形スクロール圧縮機
CN1626822A (zh) * 2003-12-12 2005-06-15 乐金电子(天津)电器有限公司 降低密封型旋转式压缩机噪音的遮蔽装置
CN1896528A (zh) * 2005-07-13 2007-01-17 乐金电子(天津)电器有限公司 具有两端支撑型旋转轴的旋转压缩机
CN104776029A (zh) * 2015-04-16 2015-07-15 广东美芝制冷设备有限公司 旋转式压缩机
CN104929938A (zh) * 2015-06-09 2015-09-23 安庆卡尔特压缩机有限公司 一种旋转式压缩机

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3395539B2 (ja) * 1996-09-18 2003-04-14 ダイキン工業株式会社 回転式圧縮機
JP2001342954A (ja) * 2000-05-31 2001-12-14 Sanyo Electric Co Ltd 電動圧縮機及びそれを用いた冷却装置
JP2008206358A (ja) * 2007-02-22 2008-09-04 Daikin Ind Ltd モータおよび圧縮機
US8740584B2 (en) * 2008-08-05 2014-06-03 Mitsubishi Electric Corporation Induction motor and hermetic compressor
JP4687810B2 (ja) * 2009-03-31 2011-05-25 株式会社富士通ゼネラル 電動機ロータ
JP5591099B2 (ja) * 2010-12-28 2014-09-17 三菱電機株式会社 圧縮機および冷凍サイクル装置
JP5786030B2 (ja) * 2011-10-31 2015-09-30 東芝キヤリア株式会社 密閉型回転式圧縮機と冷凍サイクル装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09144679A (ja) * 1995-11-20 1997-06-03 Hitachi Ltd ロータリ式圧縮機
JP2002295380A (ja) * 2001-03-29 2002-10-09 Mitsubishi Electric Corp 横形スクロール圧縮機
CN1626822A (zh) * 2003-12-12 2005-06-15 乐金电子(天津)电器有限公司 降低密封型旋转式压缩机噪音的遮蔽装置
CN1896528A (zh) * 2005-07-13 2007-01-17 乐金电子(天津)电器有限公司 具有两端支撑型旋转轴的旋转压缩机
CN104776029A (zh) * 2015-04-16 2015-07-15 广东美芝制冷设备有限公司 旋转式压缩机
CN104929938A (zh) * 2015-06-09 2015-09-23 安庆卡尔特压缩机有限公司 一种旋转式压缩机

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3354902A4 *

Also Published As

Publication number Publication date
EP3354902A4 (en) 2019-05-29
EP3354902B1 (en) 2024-05-01
US20180195512A1 (en) 2018-07-12
EP3354902A1 (en) 2018-08-01
JP2017531755A (ja) 2017-10-26

Similar Documents

Publication Publication Date Title
CN102828956B (zh) 压缩机吸气口结构
CN104481885B (zh) 压缩机
CN103511275B (zh) 低背压旋转式压缩机
CN203308712U (zh) 变螺距双头螺杆真空泵
JP2013525690A (ja) スクリュー式真空ポンプ
CN110410294A (zh) 气缸座组件、泵体组件和冰箱
WO2017049545A1 (zh) 旋转式压缩机
CN206000711U (zh) 双级空气压缩机
JP2016020657A (ja) ロータリ式圧縮機
CN201650740U (zh) 卧式旋转压缩机的内部气体导向机构
CN105114317B (zh) 旋转式压缩机
KR101166306B1 (ko) 응력완화부를 갖는 고정자 및 그를 포함하는 압축기
JP2011196297A (ja) 圧縮機
WO2019017248A1 (ja) 回転式圧縮機
CN210715113U (zh) 一种具有新型壳体的涡旋压缩机
CN201473739U (zh) 一种真空发生器
CN106168220B (zh) 压缩机及制冷循环装置
CN202840718U (zh) 空调压缩机转子
CN102691661A (zh) 旋转压缩机
CN105864037B (zh) 泵体结构及压缩机
JPH05993U (ja) 高圧ドーム形圧縮機
CN215890466U (zh) 旋转式压缩机及制冷设备
CN210118886U (zh) 压缩机组件及具有其的空调室外机
WO2018053943A1 (zh) 用于冰箱压缩机的上油组件和压缩机
CN105485020B (zh) 一种压缩机及其吸气端盖

Legal Events

Date Code Title Description
REEP Request for entry into the european phase

Ref document number: 2015899910

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2015899910

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2017516080

Country of ref document: JP

Kind code of ref document: A

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15899910

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE