WO2016187848A1 - 旋转式压缩机 - Google Patents

旋转式压缩机 Download PDF

Info

Publication number
WO2016187848A1
WO2016187848A1 PCT/CN2015/079958 CN2015079958W WO2016187848A1 WO 2016187848 A1 WO2016187848 A1 WO 2016187848A1 CN 2015079958 W CN2015079958 W CN 2015079958W WO 2016187848 A1 WO2016187848 A1 WO 2016187848A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
hole
exhaust
communication
chamber
Prior art date
Application number
PCT/CN2015/079958
Other languages
English (en)
French (fr)
Inventor
黎法运
高斌
郭小龙
汤立宽
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 PCT/CN2015/079958 priority Critical patent/WO2016187848A1/zh
Publication of WO2016187848A1 publication Critical patent/WO2016187848A1/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
    • 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
    • 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

Definitions

  • the present invention relates to the field of compressors, and more particularly to a rotary compressor.
  • the high-temperature and high-pressure refrigerant gas discharged from the compression chamber of the rotary compressor is directly discharged into the compressor casing through the exhaust passage of the upper bearing, which causes the temperature in the compressor casing to be higher to the motor and the refrigeration. Oil reliability has an impact.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent.
  • the present invention needs to provide a rotary compressor in which a cylinder is provided with an exhaust chamber, which can solve the problem that high-temperature and high-pressure refrigerant gas is discharged into the compressor casing to the motor and the refrigeration oil.
  • the impact of the compressor can make the compressor structure simple and compact, and the performance is good.
  • a rotary compressor includes: a casing; a compression mechanism provided in the casing, the compression mechanism including: a cylinder having a height penetrating along a central axis thereof a cylinder bore; an upper bearing, the upper bearing is disposed at an upper end of the cylinder; a lower bearing, the lower bearing is disposed at a lower end of the cylinder, an inner wall of the cylinder bore, the upper bearing, and the lower bearing Cooperating with a cylinder chamber for accommodating a piston, the cylinder is provided with an intake port and an exhaust port communicating with the cylinder chamber, and the cylinder is further provided with an exhaust chamber, the exhaust chamber and the exhaust chamber The interior of the casing or the exterior of the casing communicates, wherein the compression mechanism is provided with a communication passage for communicating the exhaust port and the exhaust chamber.
  • the rotary compressor of the embodiment of the present invention is provided with an exhaust chamber in the cylinder, which can solve the influence of the high-temperature high-pressure refrigerant gas discharged into the compressor casing on the motor and the refrigerating oil in the background art, and can make the compressor structure Simple and compact, with good performance.
  • rotary compressor according to the present invention may have the following additional technical features:
  • the cylinder is provided with a through groove extending through the height thereof, the upper bearing covers the upper end of the through slot and the lower bearing covers the lower end of the through slot, the upper end
  • the exhaust chamber is defined between the bearing, the lower bearing and the inner wall of the through slot.
  • the through groove is disposed around at least a portion of the circumferential direction of the cylinder chamber.
  • At least one reinforcing rib is disposed in the through groove, the reinforcing rib is arranged substantially in a radial direction of the cylinder, and the reinforcing rib is configured to be provided on both sides of the reinforcing rib
  • the through slots are in communication.
  • a sidewall of the cylinder is provided with an exhaust passage communicating with the exhaust chamber, and a sidewall of the casing is provided with a through hole of the casing, and the exhaust passage is The through holes of the casing are opposite and connected.
  • the upper bearing is provided with an exhaust through hole extending through its height and communicating with the exhaust chamber, the exhaust through hole communicating with the interior of the casing.
  • the communication passage is provided on the upper bearing and/or the lower bearing.
  • the upper bearing is provided with: an upper through hole vertically disposed, the upper through hole communicating with the exhaust port on the cylinder; an upper receiving cavity having a predetermined volume, The upper receiving cavity communicates with the upper through hole; the upper connecting hole is obliquely disposed, the axis of the upper communicating hole is inclined with respect to a vertical direction, and the upper communicating hole is configured to communicate with the upper receiving cavity and the The exhaust chamber; wherein the upper through hole, the upper receiving chamber, and the upper communication hole constitute the communication passage.
  • the lower bearing is provided with: a vertically disposed lower through hole, the lower through hole communicating with an exhaust port on the cylinder; a lower receiving cavity having a predetermined volume, a lower receiving cavity communicating with the lower through hole; a downwardly disposed lower communicating hole, an axis of the lower communicating hole being inclined with respect to a vertical direction, the lower communicating hole for communicating the lower receiving cavity and the row An air cavity; wherein the lower through hole, the lower receiving cavity, and the lower communicating hole constitute the communication passage.
  • the communication passage is provided in the cylinder.
  • FIG. 1 is a schematic structural view of a rotary compressor according to an embodiment of the present invention.
  • Figure 2 is a schematic structural view of a compression mechanism of the rotary compressor shown in Figure 1;
  • FIG. 3 is a schematic structural view of a rotary compressor according to another embodiment of the present invention.
  • Figure 4 is a schematic structural view of a compression mechanism of the rotary compressor shown in Figure 3;
  • Figure 5 is a schematic structural view of a cylinder according to an embodiment of the present invention.
  • Figure 6 is a schematic structural view of a cylinder according to another embodiment of the present invention.
  • Figure 7 is a schematic structural view of a cylinder according to still another embodiment of the present invention.
  • Figure 8 is a schematic structural view of an upper bearing according to an embodiment of the present invention.
  • Figure 9 is a schematic view showing the structure of a lower bearing according to an embodiment of the present invention.
  • Cylinder 21 Cylinder 21; cylinder bore 211; cylinder chamber 212; intake port 213; exhaust port 214; exhaust chamber 215; through slot 216; stiffener 217; exhaust passage 218; slide slot 219;
  • Lower bearing 23 lower through hole 232; lower receiving cavity 233; lower communicating hole 234;
  • 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 integrally; can be directly connected, or indirectly connected through an intermediate medium, which can be the internal communication of two elements or the interaction of two elements. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • a rotary compressor 100 according to an embodiment of the present invention will be described below with reference to Figs.
  • a rotary compressor 100 includes: a casing 1 and a compressor Structure 2.
  • the compression mechanism 2 is provided in the casing 1, and the compression mechanism 2 includes a cylinder 21, an upper bearing 22, and a lower bearing 23.
  • the upper bearing 22 is provided at the upper end of the cylinder 21, and the lower bearing 23 is provided at the lower end of the cylinder 21.
  • the cylinder 21 has a cylinder bore 211 extending through its height (the "height" according to the present invention, that is, the up and down direction in Figs. 1 to 4) along its central axis, and the center axis of the cylinder bore 211 coincides with the central axis of the cylinder 21.
  • the inner wall of the cylinder bore 211, the upper bearing 22 and the lower bearing 23 together define a cylinder bore 212 for receiving the piston 25.
  • the cylinder 21 is provided with a sliding slot 219, and the sliding slot 219 is provided with a sliding piece.
  • the cylinder chamber 212 is divided by the piston 25 or the vane into an intake chamber and a compression chamber.
  • the cylinder 21 is provided with an intake port 213 and an exhaust port 214 which communicate with the cylinder chamber 212.
  • the intake port 213 communicates with the intake chamber
  • the exhaust port 214 communicates with the compression chamber.
  • the cylinder 21 is provided with an exhaust chamber 215.
  • the exhaust chamber 215 communicates with the inside of the casing 1 or the outside of the casing 1.
  • the compression mechanism 2 is provided with a communication passage 24 for communication.
  • the passage 24 is for communicating the exhaust port 214 and the exhaust chamber 215.
  • the refrigerant outside the rotary compressor 100 enters the suction chamber, and the high-speed rotation of the piston 25 in the cylinder chamber 212 causes the refrigerant gas to gradually enter the compression chamber for compression, thereby becoming a high-temperature and high-pressure refrigerant gas, and finally from the refrigerant gas.
  • the exhaust port 214 discharges the cylinder 21. Since the exhaust chamber 215 is provided in the cylinder 21 according to the embodiment of the present invention, and the communication passage 24 is used to communicate the exhaust port 214 and the exhaust chamber 215, the high-temperature high-pressure refrigerant gas enters the cylinder 21 via the communication passage 24.
  • the exhaust chamber 215 has a certain buffering effect on the high-temperature and high-pressure refrigerant gas, so that the running noise of the entire rotary compressor 100 can be reduced. Moreover, by providing the exhaust chamber 215, the inner wall of the exhaust chamber 215 can be used for the condensation of the refrigerating oil, which also contributes to the separation of the oil and gas of the refrigerant gas.
  • the exhaust chamber 215 can communicate with the inside of the casing 1 or the outside of the casing 1.
  • the exhaust chamber 215 communicates with the interior of the casing 1
  • the high-temperature and high-pressure refrigerant gas in the exhaust chamber 215 is first discharged to the machine.
  • the inside of the casing 1 is discharged to the outside of the rotary compressor 100 via the exhaust pipe 12 at the top of the casing 1 to participate in the circulation of the refrigeration system. Since the exhaust chamber 215 is provided in the cylinder 21, it is passed in relation to the background art.
  • the structure of the rotary compressor 100 is simple and compact, and the cost is low; when the exhaust chamber 215 communicates with the outside of the casing 1, the high-temperature and high-pressure refrigerant gas in the exhaust chamber 215 It can be directly discharged to the outside of the rotary compressor 100 without passing through the internal space of the casing 1, and further participates in the circulation of the refrigeration system, and is directly discharged from the exhaust chamber 215 to the outside of the casing 1, so that the refrigerant gas does not pass through the casing 1.
  • the internal motor thereby reducing the impact of high temperature and high pressure gas on the motor and the refrigeration oil, can improve the reliability of the motor and the refrigeration oil.
  • the cylinder 21 of the rotary compressor 100 is provided with an exhaust chamber 215, which makes the compressor structure simple and compact, has good performance, and the running noise of the rotary compressor 100 is low.
  • the gas-liquid separating device 3 may not be disposed outside the casing 1, and the refrigerant gas may directly enter the inside of the casing 1 of the rotary compressor 100 due to the cylinder 21
  • the exhaust gas does not pass through the internal space of the casing 1, so the internal space of the casing 1 is a low-temperature and low-pressure environment, and the casing 1 can serve as a gas-liquid separation structure, and the refrigerant gas can enter the cylinder chamber 212 from the suction port 213 of the cylinder 21. .
  • the cylinder 21 may be provided with a through slot 216 extending through its height.
  • the shape of the through slot 216 may be arbitrary.
  • the top view of the through groove 216 is generally curved and the through groove 216 is disposed around at least a portion of the circumferential direction of the cylinder chamber 212, wherein the through groove 216 is not in communication with the intake port 213 of the cylinder 21.
  • the upper bearing 22 covers the upper end of the through groove 216 and the lower bearing 23 covers the lower end of the through groove 216.
  • the upper bearing 22, the lower bearing 23 and the inner wall of the through groove 216 collectively define an exhaust chamber 215. That is, the upper bearing 22 is for sealing the upper end of the through groove 216, and the lower bearing 23 is for sealing the lower end of the through groove 216, whereby the exhaust chamber 215 can be formed as a relatively closed cavity to avoid unnecessary gas leakage. . Moreover, such a cylinder 21 has a simple structure, the exhaust chamber 215 is easy to manufacture, and the compression mechanism 2 has a compact structure.
  • At least one reinforcing rib 217 may be disposed in the through groove 216, and the reinforcing rib 217 may be arranged substantially in the radial direction of the cylinder 21, since the through groove 216 has a certain radial direction.
  • the size and the through groove 216 occupy a large area on the end surface of the cylinder 21, so that the structural strength of the cylinder 21 can be improved by providing the reinforcing rib 217, and the high-pressure refrigerant gas can be ensured to enter the exhaust chamber 215 to the exhaust chamber 215.
  • the inner wall generates an overpressure to deform the wall of the cylinder 21.
  • the reinforcing ribs 217 are configured to be connected to the through grooves 216 on both sides of the reinforcing ribs 217, that is, the reinforcing ribs 217 are provided to have a spacing effect on the through grooves 216, so that the refrigerant gas is in the entire through grooves 216. Flow can be performed therein, and the reinforcing ribs 217 can be disposed such that the through grooves 216 on both sides communicate with each other.
  • the ribs 217 may be provided with rib through holes such that the refrigerant gas may communicate with the through grooves 216 located at both sides of the ribs 217 through the rib through holes; or in another example of the present invention,
  • the dimension of the rib 217 in the height direction may be set smaller than the dimension in the height direction of the through groove 216, so that the refrigerant may be communicated on both sides of the rib 217 by the gap between the top of the rib 217 and the lower end surface of the upper bearing 22.
  • the through groove 216 or the refrigerant may communicate with the through groove 216 located at both sides of the rib 217 through a gap between the bottom of the rib 217 and the upper end surface of the lower bearing 23.
  • the ribs 217 can be plural and spaced apart within the through slot 216, whereby the structural strength of the cylinder 21 can be further increased and the cylinder 21 can be more evenly stressed during operation.
  • the exhaust chamber 215 is in communication with the exterior of the cabinet 1 in accordance with an embodiment of the present invention as shown in FIGS. 1 and 2.
  • the side wall of the cylinder 21 is provided with an exhaust passage 218 communicating with the exhaust chamber 215, and both ends of the exhaust passage 218 are respectively formed on the inner wall of the exhaust chamber 215 and
  • the side wall of the casing 1 is provided with a through hole of the casing, and the exhaust passage 218 is opposite to and communicates with the through hole of the casing, and the arrangement is simplified by arranging the exhaust passage 218 opposite to the through hole of the casing.
  • the communication structure between the gas passage 218 and the through hole of the casing is simplified by arranging the exhaust passage 218 opposite to the through hole of the casing.
  • the exhaust chamber 215 is in communication with the interior of the cabinet 1.
  • the exhaust chamber 215 may communicate with the interior of the casing 1 through the upper bearing 22, and specifically, as shown in FIGS. 3 and 4, the upper bearing 22 may be provided with a height therethrough and communicated with the exhaust chamber 215.
  • the exhaust through hole 221 and the exhaust through hole 221 communicate with the inside of the casing 1.
  • the structure is simple and easy to implement. Further, the refrigerant gas discharged into the inside of the casing 1 can be discharged to the outside of the rotary compressor 100 through the exhaust pipe 12 at the top of the casing 1.
  • a communication passage 24 according to an embodiment of the present invention is described below.
  • the communication passage 24 may be provided on the upper bearing 22 and/or the lower bearing 23. That is, the communication passage 24 may be provided only on the upper bearing 22, the communication passage 24 may be provided only on the lower bearing 23, or the communication passage 24 may be provided on both the upper bearing 22 and the lower bearing 23. In the example shown in FIGS. 2 and 4, the communication passage 24 is simultaneously provided on the upper bearing 22 and the lower bearing 23.
  • the structure of the communication passage 24 on the upper bearing 22 and the lower bearing 23 will be specifically described below with reference to Figs. 2, 4, 8, and 9.
  • the upper bearing 22 is provided with an upper through hole 222, an upper receiving cavity 223 and an upper communicating hole 224, wherein the upper through hole 222 is disposed in a vertical direction, and the upper through hole 222 is The exhaust port 214 on the cylinder 21 communicates.
  • the upper through hole 222 may face and communicate with the exhaust port 214 of the cylinder 21 in the up and down direction.
  • the upper receiving chamber 223 may have a predetermined volume, and the upper receiving chamber 223 is in communication with the upper through hole 222, and the upper receiving chamber 223 may function to diffuse and buffer the high temperature and high pressure refrigerant gas.
  • the upper communication hole 224 is disposed obliquely, that is, the axis of the upper communication hole 224 is inclined with respect to the vertical direction, and the upper communication hole 224 is for communicating the upper accommodation chamber 223 and the exhaust chamber 215.
  • the upper through hole 222, the upper receiving chamber 223, and the upper communicating hole 224 constitute a communication passage 24. That is, the high-temperature high-pressure refrigerant gas discharged from the exhaust port 214 of the cylinder 21 sequentially enters the exhaust chamber 215 through the upper through hole 222, the upper housing chamber 223, and the upper communication hole 224.
  • the upper communication hole 224 has a larger aperture than the upper through hole 222.
  • the lower bearing 23 is provided with a lower through hole 232, a lower receiving cavity 233 and a lower communication hole 234, wherein the lower through hole 232 is arranged in the vertical direction,
  • the through hole 232 communicates with the exhaust port 214 under the cylinder 21, and optionally, the lower through hole 232 can face and communicate with the exhaust port 214 of the cylinder 21 in the up and down direction.
  • the lower housing chamber 233 may have a predetermined volume, the lower housing chamber 233 is in communication with the lower through hole 232, and the lower housing chamber 233 may function to diffuse the high temperature and high pressure refrigerant gas.
  • the lower communication hole 234 is disposed obliquely, that is, the axis of the lower communication hole 234 is inclined with respect to the vertical direction, and the lower communication hole 234 is for communicating the lower accommodation chamber 233 and the exhaust chamber 215.
  • the lower through hole 232, the lower receiving cavity 233, and the lower communication hole 234 constitute a communication passage 24. That is, from the cylinder 21
  • the high-temperature high-pressure refrigerant gas discharged from the exhaust port 214 sequentially enters the exhaust chamber 215 through the lower through hole 232, the lower receiving chamber 233, and the lower communication hole 234.
  • the aperture of the lower communication hole 234 is larger than the aperture of the lower through hole 232.
  • the communication passage 24 may be disposed in the cylinder 21, specifically, the cylinder 21 is provided with a direct communication exhaust port 214 and a row.
  • the passage of the air chamber 215 can thereby make the structure of the communication passage 24 simpler and easier to implement.

Landscapes

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

Abstract

一种旋转式压缩机，包括：机壳（1）；压缩机构（2），压缩机构（2）包括：气缸（21），气缸（21）沿其中心轴线贯穿其高度的气缸孔（211）；上轴承（22），上轴承（22）设在气缸（21）的上端；下轴承（23），下轴承（23）设在气缸（21）的下端，气缸孔（211）的内壁、上轴承（22）和下轴承（23）共同限定出用于容纳活塞的气缸腔（212），气缸（21）上设有与气缸腔（212）连通的吸气口（213）和排气口（214），气缸（21）内还设有排气腔（215），排气腔（215）与机壳（1）的内部或者机壳（1）的外部连通，其中压缩机构（2）内设有连通通道（24），连通通道（24）用于连通排气口（214）和排气腔（215）。该旋转式压缩机的气缸内设置有排气腔可以减小高温高压的冷媒气体排到压缩机壳体内部对电机和冷冻油的影响，使压缩机结构简单紧凑，性能好。

Description

旋转式压缩机 技术领域
本发明涉及压缩机领域，尤其是涉及一种旋转式压缩机。
背景技术
相关技术中，旋转式压缩机从气缸的压缩腔排出的高温高压的冷媒气体会直接通过上轴承的排气通道排到压缩机壳体内，这样会造成压缩机壳体内温度较高对电机和冷冻油可靠性有影响。
为了解决上述问题，有些压缩机结构会将从气缸的压缩腔排出的高温高压的冷媒气体排到上下轴承内的空腔中，但是这样会造成泵体结构庞大，压缩机的重量大，制造难度高。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本发明需要提出一种旋转式压缩机，该旋转式压缩机的气缸内设置有排气腔，可以解决背景技术中高温高压的冷媒气体排到压缩机壳体内部对电机和冷冻油的影响，而且可以使压缩机结构简单紧凑，性能好。
根据本发明实施例的旋转式压缩机，包括：机壳；压缩机构，所述压缩机构设在所述机壳内，所述压缩机构包括：气缸，所述气缸具有沿其中心轴线贯穿其高度的气缸孔；上轴承，所述上轴承设在所述气缸的上端；下轴承，所述下轴承设在所述气缸的下端，所述气缸孔的内壁、所述上轴承和所述下轴承共同限定出用于容纳活塞的气缸腔，所述气缸上设有与所述气缸腔连通的吸气口和排气口，所述气缸内还设有排气腔，所述排气腔与所述机壳的内部或者所述机壳的外部连通，其中所述压缩机构内设有连通通道，所述连通通道用于连通所述排气口和所述排气腔。
根据本发明实施例的旋转式压缩机的气缸内设置有排气腔，可以解决背景技术中高温高压的冷媒气体排到压缩机壳体内部对电机和冷冻油的影响，而且可以使压缩机结构简单紧凑，性能好。
另外，根据本发明的旋转式压缩机还可具有如下附加技术特征：
根据本发明的一个实施例，所述气缸上设有贯穿其高度的贯通槽，所述上轴承封盖所述贯通槽的上端且所述下轴承封盖所述贯通槽的下端，所述上轴承、所述下轴承与所述贯通槽的内壁之间共同限定出所述排气腔。
根据本发明的一个实施例，所述贯通槽围绕所述气缸腔周向的至少一部分设置。
根据本发明的一个实施例，所述贯通槽内设有至少一个加强筋，所述加强筋大致沿所述气缸的径向方向布置，所述加强筋被构造成可供所述加强筋两侧的所述贯通槽连通。
根据本发明的一个实施例，所述气缸的侧壁上设有与所述排气腔连通的排气通道，所述机壳的侧壁上设有机壳通孔，所述排气通道与所述机壳通孔相对且连通。
根据本发明的一个实施例，所述上轴承上设有贯穿其高度且与所述排气腔连通的排气通孔，所述排气通孔与所述机壳的内部连通。
根据本发明的一个实施例，所述连通通道设在所述上轴承和/或所述下轴承上。
根据本发明的一个实施例，所述上轴承上设有：竖直设置的上通孔，所述上通孔与所述气缸上的所述排气口连通；具有预定容积的上容纳腔，所述上容纳腔与所述上通孔连通；倾斜设置的上连通孔，所述上连通孔的轴线相对于竖直方向倾斜设置，所述上连通孔用于连通所述上容纳腔和所述排气腔；其中所述上通孔、所述上容纳腔和所述上连通孔构成所述连通通道。
根据本发明的一个实施例，所述下轴承上设有：竖直设置的下通孔，所述下通孔与所述气缸上的排气口连通；具有预定容积的下容纳腔，所述下容纳腔与所述下通孔连通；倾斜设置的下连通孔，所述下连通孔的轴线相对于竖直方向倾斜设置，所述下连通孔用于连通所述下容纳腔和所述排气腔；其中所述下通孔、所述下容纳腔和所述下连通孔构成所述连通通道。
根据本发明的一个实施例，所述连通通道设在所述气缸内。
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是根据本发明一个实施例的旋转式压缩机的结构示意图；
图2是图1所示的旋转式压缩机的压缩机构的结构示意图；
图3是根据本发明另一个实施例的旋转式压缩机的结构示意图；
图4是图3所示的旋转式压缩机的压缩机构的结构示意图；
图5是根据本发明一个实施例的气缸的结构示意图；
图6是根据本发明另一个实施例的气缸的结构示意图；
图7是根据本发明再一个实施例的气缸的结构示意图；
图8是根据本发明一个实施例的上轴承的结构示意图；
图9是根据本发明一个实施例的下轴承的结构示意图。
附图标记：
旋转式压缩机100；
机壳1；吸气管11；排气管12；
压缩机构2；
气缸21；气缸孔211；气缸腔212；吸气口213；排气口214；排气腔215；贯通槽216；加强筋217；排气通道218；滑片槽219；
上轴承22；排气通孔221；上通孔222；上容纳腔223；上连通孔224；
下轴承23；下通孔232；下容纳腔233；下连通孔234；
连通通道24；活塞25；
气液分离装置3。
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”、“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”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。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。
下面参考图1-图9描述根据本发明实施例的旋转式压缩机100。
如图1-图9所示，根据本发明实施例的旋转式压缩机100，包括：机壳1和压缩机 构2。具体地，压缩机构2设在机壳1内，压缩机构2包括：气缸21、上轴承22和下轴承23，上轴承22设在气缸21的上端，下轴承23设在气缸21的下端。
气缸21具有沿其中心轴线贯穿其高度(本发明所述的“高度”即附图1-图4中的上下方向)的气缸孔211，气缸孔211的中心轴线与气缸21的中心轴线重合。气缸孔211的内壁、上轴承22和下轴承23共同限定出用于容纳活塞25的气缸腔212。可知的是，气缸21内设置有滑片槽219，滑片槽219内设置有滑片，活塞25在气缸腔212内偏心转动时，滑片的自由端始终止抵在活塞25的外壁上，由此，气缸腔212由活塞25或滑片分隔成吸气腔和压缩腔。气缸21上设有与气缸腔212连通的吸气口213和排气口214，具体地，吸气口213与吸气腔连通，排气口214与压缩腔连通。
其中，在本发明的实施例中，气缸21内设有排气腔215，排气腔215与机壳1的内部或者机壳1的外部连通，其中压缩机构2内设有连通通道24，连通通道24用于连通排气口214和排气腔215。
下面参考附图描述冷媒在旋转式压缩机100内的流动路径：
旋转式压缩机100外部的冷媒进入到吸气腔内，通过活塞25在气缸腔212内的高速转动，冷媒气体再逐渐进入到压缩腔内进行压缩，从而成为高温高压的冷媒气体，最后再从排气口214排出气缸21。由于根据本发明实施例的气缸21内设有排气腔215，并且连通通道24用于连通排气口214和排气腔215，从而高温高压的冷媒气体经由连通通道24进入到气缸21内的排气腔215中，排气腔215对高温高压的冷媒气体起到一定的缓冲作用，从而可以降低整个旋转式压缩机100的运行噪音。而且通过设置排气腔215，排气腔215的内壁可以供冷冻油凝结，这样还有利于冷媒气体的油气分离的作用。
其中排气腔215可以与机壳1的内部或者机壳1的外部连通，当排气腔215与机壳1的内部连通时，排气腔215内的高温高压的冷媒气体，首先排到机壳1的内部，再经由机壳1顶部的排气管12排向旋转式压缩机100的外部从而参与制冷系统的循环，由于气缸21内设置有排气腔215，相对于背景技术中通过在上下轴承23内设置空腔的结构而言，旋转式压缩机100的结构简单紧凑，成本低廉；当排气腔215与机壳1的外部连通时，排气腔215内的高温高压的冷媒气体可以不经机壳1的内部空间而直接排到旋转式压缩机100的外部，进而参与制冷系统的循环，从排气腔215直接排出到壳体1外部，这样冷媒气体不经过壳体1的内部的电机，由此减小高温高压的气体对电机和冷冻油冲击，从而可以提高电机和冷冻油的可靠性。
综上，根据本发明实施例的旋转式压缩机100的气缸21内设置有排气腔215，可以使压缩机结构简单紧凑，性能好，旋转式压缩机100的运行噪音低。
需要说明的是，当排气腔215与机壳1的内部连通时，外部的冷媒气体可以经设在 机壳1外部的气液分离装置3的气液分离后，从吸气管11流向气缸21的吸气口213处，进而进入到气缸腔212内。当排气腔215直接与机壳1的外部连通时，机壳1的外部可以不设置气液分离装置3，冷媒气体可以直接进入到旋转式压缩机100的壳体1内部，由于气缸21的排气不经过壳体1内部空间，因此壳体1的内部空间为低温低压的环境，壳体1可以作为气液分离结构，冷媒气体可以从气缸21的吸气口213进入到气缸腔212内。
下面参考图1-图7描述根据本发明一个实施例的气缸21的结构。如图1-图7所示，气缸21上可以设有贯穿其高度的贯通槽216，可选地，贯通槽216的俯视图形状可以是任意的，在本发明的一个实施例中，如图5-图7所示，贯通槽216的俯视图大体为弧形且贯通槽216围绕气缸腔212周向的至少一部分设置，其中贯通槽216与气缸21的吸气口213不连通。上轴承22封盖贯通槽216的上端且下轴承23封盖贯通槽216的下端，上轴承22、下轴承23与贯通槽216的内壁之间共同限定出排气腔215。也就是说，上轴承22用于密封贯通槽216的上端，下轴承23用于密封贯通槽216的下端，由此可以使排气腔215构成相对封闭的一个空腔，避免不必要的气体泄漏。而且这样的气缸21结构简单，排气腔215容易制造，压缩机构2的结构紧凑。
优选地，如图5-图7所示，贯通槽216内可以设有至少一个加强筋217，加强筋217可以大致沿气缸21的径向方向布置，由于贯通槽216在径向方向上具有一定尺寸，且贯通槽216在气缸21的端面上所占面积较大，因此通过设置加强筋217可以提高气缸21的结构强度，可以保证高压的冷媒气体进入到排气腔215内对排气腔215的内壁产生过压作用而使气缸21的壁产生变形。
其中，加强筋217被构造成可供加强筋217两侧的贯通槽216连通，也就是说，所设置的加强筋217对贯通槽216起到了间隔的作用，为了使冷媒气体在整个贯通槽216内可以进行流动，可以将加强筋217设置为使其两侧的贯通槽216连通。在本发明的一个示例中，加强筋217上可以设置加强筋通孔，这样冷媒气体可以通过加强筋通孔连通位于加强筋217两侧的贯通槽216；或者在本发明的另一个示例中，加强筋217的高度方向上的尺寸可以设置成小于贯通槽216的高度方向上的尺寸，这样冷媒可以通过加强筋217的顶部与上轴承22的下端面之间的间隙连通位于加强筋217两侧的贯通槽216，或者冷媒可以通过加强筋217的底部与下轴承23的上端面之间的间隙连通位于加强筋217两侧的贯通槽216。由此可以提高贯通槽216的利用率，提高排气腔215对高压冷媒气体的扩压缓冲效果。
有利地，该加强筋217可以是多个且间隔开设置在贯通槽216内，由此可以进一步提高气缸21的结构强度，而且可以使气缸21在工作过程中受力更加均匀。
如图1和图2所示的根据本发明的一个实施例，排气腔215与机壳1的外部连通。具体地，如图1和图2所示，气缸21的侧壁上设有与排气腔215连通的排气通道218，排气通道218的两端分别形成在排气腔215的内壁上和气缸21的外侧壁上，机壳1的侧壁上设有机壳通孔，排气通道218与机壳通孔相对且连通，通过将排气通道218与机壳通孔相对设置可以简化排气通道218与机壳通孔之间的连通结构。
如图3和图4所示的根据本发明的另一个实施例，排气腔215与机壳1的内部连通。可选地，排气腔215可以通过上轴承22与机壳1的内部连通，具体地，如图3和图4所示，上轴承22上可以设有贯穿其高度且与排气腔215连通的排气通孔221，排气通孔221与机壳1的内部连通。该结构简单，容易实现。进一步地，排入到机壳1内部的冷媒气体可以通过机壳1顶部的排气管12排出至旋转式压缩机100的外部。
下面描述根据本发明实施例的连通通道24。可选地，连通通道24可以设在上轴承22和/或下轴承23上。也就是说，连通通道24可以仅设在上轴承22上，连通通道24可以仅设在下轴承23上，或者连通通道24还可以同时设在上轴承22和下轴承23上。其中图2和图4所示的示例中，连通通道24同时设置在上轴承22和下轴承23上。下面参考图2、图4、图8和图9，具体描述位于上轴承22和下轴承23上的连通通道24的结构。
如图2、图4和图8所示，上轴承22上设有上通孔222、上容纳腔223和上连通孔224，其中，上通孔222沿竖直方向设置，上通孔222与气缸21上的排气口214连通，可选地，上通孔222在上下方向上可以与气缸21的排气口214相对且连通。上容纳腔223可以具有预定容积，上容纳腔223与上通孔222连通，上容纳腔223可以起到对高温高压的冷媒气体扩压缓冲的作用。上连通孔224为倾斜设置的，即上连通孔224的轴线相对于竖直方向倾斜设置，上连通孔224用于连通上容纳腔223和排气腔215。其中上通孔222、上容纳腔223和上连通孔224构成连通通道24。也就是说，从气缸21的排气口214排出的高温高压的冷媒气体，依次经过上通孔222、上容纳腔223和上连通孔224进入到排气腔215内。可选地，上连通孔224的孔径大于上通孔222的孔径。
相对应地，如图2、图4和图9所示，下轴承23上设有下通孔232、下容纳腔233和下连通孔234，其中，下通孔232沿竖直方向设置，下通孔232与气缸21下的排气口214连通，可选地，下通孔232在上下方向上可以与气缸21的排气口214相对且连通。下容纳腔233可以具有预定容积，下容纳腔233与下通孔232连通，下容纳腔233可以起到对高温高压的冷媒气体扩压缓冲的作用。下连通孔234为倾斜设置的，即下连通孔234的轴线相对于竖直方向倾斜设置，下连通孔234用于连通下容纳腔233和排气腔215。其中下通孔232、下容纳腔233和下连通孔234构成连通通道24。也就是说，从气缸21 的排气口214排出的高温高压的冷媒气体，依次经过下通孔232、下容纳腔233和下连通孔234进入到排气腔215内。可选地，下连通孔234的孔径大于下通孔232的孔径。
如图7所示的实施例中，根据本发明实施例的旋转式压缩机100中，连通通道24还可以设在气缸21内，具体地，气缸21内设有直接连通排气口214和排气腔215的通道，由此可以使连通通道24的结构更加简单，容易实现。
根据本发明实施例的旋转式压缩机100的其他构成例如气缸21、上轴承22、下轴承23等的具体结构以及操作对于本领域普通技术人员而言都是已知的，这里不再详述。
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 (10)

  1. 一种旋转式压缩机，其特征在于，包括：
    机壳；
    压缩机构，所述压缩机构设在所述机壳内，所述压缩机构包括：
    气缸，所述气缸具有沿其中心轴线贯穿其高度的气缸孔；
    上轴承，所述上轴承设在所述气缸的上端；
    下轴承，所述下轴承设在所述气缸的下端，所述气缸孔的内壁、所述上轴承和所述下轴承共同限定出用于容纳活塞的气缸腔，所述气缸上设有与所述气缸腔连通的吸气口和排气口，
    所述气缸内设有排气腔，所述排气腔与所述机壳的内部或者所述机壳的外部连通，其中所述压缩机构内设有连通通道，所述连通通道用于连通所述排气口和所述排气腔。
  2. 根据权利要求1所述的旋转式压缩机，其特征在于，所述气缸上设有贯穿其高度的贯通槽，所述上轴承封盖所述贯通槽的上端且所述下轴承封盖所述贯通槽的下端，所述上轴承、所述下轴承与所述贯通槽的内壁之间共同限定出所述排气腔。
  3. 根据权利要求2所述的旋转式压缩机，其特征在于，所述贯通槽围绕所述气缸腔周向的至少一部分设置。
  4. 根据权利要求2所述的旋转式压缩机，其特征在于，所述贯通槽内设有至少一个加强筋，所述加强筋大致沿所述气缸的径向方向布置，所述加强筋被构造成可供所述加强筋两侧的所述贯通槽连通。
  5. 根据权利要求1-4中任一项所述的旋转式压缩机，其特征在于，所述气缸的侧壁上设有与所述排气腔连通的排气通道，所述机壳的侧壁上设有机壳通孔，所述排气通道与所述机壳通孔相对且连通。
  6. 根据权利要求1-5中任一项所述的旋转式压缩机，其特征在于，所述上轴承上设有贯穿其高度且与所述排气腔连通的排气通孔，所述排气通孔与所述机壳的内部连通。
  7. 根据权利要求1-6中任一项所述的旋转式压缩机，其特征在于，所述连通通道设在所述上轴承和/或所述下轴承上。
  8. 根据权利要求7所述的旋转式压缩机，其特征在于，所述上轴承上设有：
    竖直设置的上通孔，所述上通孔与所述气缸上的所述排气口连通；
    具有预定容积的上容纳腔，所述上容纳腔与所述上通孔连通；
    倾斜设置的上连通孔，所述上连通孔的轴线相对于竖直方向倾斜设置，所述上连通孔用于连通所述上容纳腔和所述排气腔；
    其中所述上通孔、所述上容纳腔和所述上连通孔构成所述连通通道。
  9. 根据权利要求7所述的旋转式压缩机，其特征在于，所述下轴承上设有：
    竖直设置的下通孔，所述下通孔与所述气缸上的排气口连通；
    具有预定容积的下容纳腔，所述下容纳腔与所述下通孔连通；
    倾斜设置的下连通孔，所述下连通孔的轴线相对于竖直方向倾斜设置，所述下连通孔用于连通所述下容纳腔和所述排气腔；
    其中所述下通孔、所述下容纳腔和所述下连通孔构成所述连通通道。
  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，所述连通通道设在所述气缸内。
PCT/CN2015/079958 2015-05-27 2015-05-27 旋转式压缩机 WO2016187848A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2015/079958 WO2016187848A1 (zh) 2015-05-27 2015-05-27 旋转式压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2015/079958 WO2016187848A1 (zh) 2015-05-27 2015-05-27 旋转式压缩机

Publications (1)

Publication Number Publication Date
WO2016187848A1 true WO2016187848A1 (zh) 2016-12-01

Family

ID=57393713

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/079958 WO2016187848A1 (zh) 2015-05-27 2015-05-27 旋转式压缩机

Country Status (1)

Country Link
WO (1) WO2016187848A1 (zh)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001280277A (ja) * 2000-03-31 2001-10-10 Sanyo Electric Co Ltd 回転型圧縮機構ならびにその利用装置
CN1793658A (zh) * 2005-12-31 2006-06-28 西安交通大学 旋叶式压缩机排量自动调节机构
CN101235818A (zh) * 2008-02-29 2008-08-06 江苏益昌投资有限公司 同步旋转流体压缩装置
CN103867439A (zh) * 2014-01-01 2014-06-18 周汉忠 旋片真空泵
CN103967788A (zh) * 2013-02-05 2014-08-06 珠海格力节能环保制冷技术研究中心有限公司 压缩组件、压缩机、空调器及热泵热水器
CN104929933A (zh) * 2015-05-27 2015-09-23 广东美芝制冷设备有限公司 旋转式压缩机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001280277A (ja) * 2000-03-31 2001-10-10 Sanyo Electric Co Ltd 回転型圧縮機構ならびにその利用装置
CN1793658A (zh) * 2005-12-31 2006-06-28 西安交通大学 旋叶式压缩机排量自动调节机构
CN101235818A (zh) * 2008-02-29 2008-08-06 江苏益昌投资有限公司 同步旋转流体压缩装置
CN103967788A (zh) * 2013-02-05 2014-08-06 珠海格力节能环保制冷技术研究中心有限公司 压缩组件、压缩机、空调器及热泵热水器
CN103867439A (zh) * 2014-01-01 2014-06-18 周汉忠 旋片真空泵
CN104929933A (zh) * 2015-05-27 2015-09-23 广东美芝制冷设备有限公司 旋转式压缩机

Similar Documents

Publication Publication Date Title
JP4730317B2 (ja) 両頭ピストン式圧縮機
KR101431183B1 (ko) 스크롤 압축기
WO2019024562A1 (zh) 压缩机以及具有它的制冷设备
WO2018094914A1 (zh) 喷气增焓涡旋压缩机及制冷系统
EP3196467B1 (en) Compressor exhaust structure, screw compressor and air-conditioning unit having same
US10012232B2 (en) Compressor
CN104806522B (zh) 旋转式压缩机及具有其的冷冻装置
JP2015034536A (ja) 圧縮機
JP6776377B2 (ja) ロータリーシリンダ・エンタルピー増加・ピストン式圧縮機及びそれを備えるエアコンシステム
US9695825B2 (en) Rotary compressor
CN104929934A (zh) 旋转式压缩机
JP2015531846A (ja) 冷媒充填型回転式圧縮機
CN104929933B (zh) 旋转式压缩机
WO2016187848A1 (zh) 旋转式压缩机
WO2023236499A1 (zh) 泵体组件、压缩机以及具有其的空调器
US9518680B2 (en) Compressor and valve assembly thereof for reducing pulsation and/or noise
JP6257806B2 (ja) 多気筒密閉型圧縮機
JP2012132408A (ja) 冷媒圧縮機
JPWO2019049226A1 (ja) 密閉型圧縮機及び冷凍サイクル装置
JP2013015069A (ja) オイルセパレータ、及び、オイルセパレータを備えた圧縮機
CN109595166B (zh) 压缩机
CN109595165B (zh) 高低压分割的多级压缩机
WO2016179813A1 (zh) 旋转式压缩机及具有其的冷冻装置
CN205136030U (zh) 旋转式压缩机
WO2016165114A1 (zh) 旋转式压缩机

Legal Events

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

Ref document number: 15892929

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15892929

Country of ref document: EP

Kind code of ref document: A1