WO2015154717A1 - 压缩机和空调器 - Google Patents

压缩机和空调器 Download PDF

Info

Publication number
WO2015154717A1
WO2015154717A1 PCT/CN2015/076290 CN2015076290W WO2015154717A1 WO 2015154717 A1 WO2015154717 A1 WO 2015154717A1 CN 2015076290 W CN2015076290 W CN 2015076290W WO 2015154717 A1 WO2015154717 A1 WO 2015154717A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure stage
stage cylinder
cylinder
partition
low
Prior art date
Application number
PCT/CN2015/076290
Other languages
English (en)
French (fr)
Inventor
黄辉
胡余生
魏会军
吴健
杨欧翔
梁社兵
任丽萍
罗惠芳
朱红伟
徐嘉
Original Assignee
珠海格力电器股份有限公司
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=51330863&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2015154717(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Priority to JP2016561371A priority Critical patent/JP6244478B2/ja
Priority to US15/301,072 priority patent/US11067083B2/en
Priority to EP15777291.4A priority patent/EP3130806B1/en
Priority to KR1020167031181A priority patent/KR101797424B1/ko
Publication of WO2015154717A1 publication Critical patent/WO2015154717A1/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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type

Definitions

  • the invention relates to the field of refrigeration, and in particular relates to a rolling rotor type three-cylinder two-stage variable-capacity increasing compressor and an air conditioner.
  • Electric auxiliary heat is usually used to increase the heat capacity of the compressor or the two-stage booster compressor to solve the problem of low temperature heating capability.
  • the method of using electric auxiliary heat to increase the heat of the compression mechanism has lower energy efficiency; since the displacement of the ordinary two-stage enhanced boring compressor cannot be adjusted, the adaptability to the operating condition is poor, and the system under the low temperature condition of the compressor is ensured. Thermal capacity and energy efficiency, energy efficiency under normal operating conditions has dropped significantly.
  • a compressor comprising a low pressure stage cylinder, a first high pressure stage cylinder, a second high pressure stage cylinder and a lower flange;
  • a low-pressure stage cylinder, a first high-pressure stage cylinder, and a second high-pressure stage cylinder are stacked, and a partition is disposed between the adjacent two cylinders, wherein the first high-pressure stage cylinder and the second high-pressure stage cylinder are disposed
  • the same side of the low pressure stage cylinder or the first high pressure stage cylinder and the second high pressure stage cylinder are respectively placed at the low pressure Two sides of the cylinder, the lower flange is disposed on a lower side of the low pressure stage cylinder, the first high pressure stage cylinder and the second high pressure stage cylinder;
  • the first high pressure stage cylinder has a first sliding vane, a first sliding vane is disposed in the first sliding vane, and the second high pressure stage cylinder has a second sliding vane in the second sliding vane a second sliding piece is disposed in the groove, the low-pressure stage cylinder has a third sliding piece groove, and a third sliding piece is disposed in the third sliding piece groove;
  • the first high pressure stage cylinder is disposed in parallel with the second high pressure stage cylinder, and the parallel first high pressure stage cylinder and the second high pressure stage cylinder are connected in series with the low pressure stage cylinder, the first high pressure stage
  • the cylinder or/and the second high pressure stage cylinder are variable capacity cylinders that act as primary compression cylinders.
  • the two partitions are respectively a first partition and a second partition, and the first partition or/and the second partition are provided with a slide control device for controlling the action of the slider Or the first partition or/and the lower flange is provided with the slide control device; or the second partition or/and the lower flange is provided with the slide control device
  • the first partition or/and the lower flange is provided with the slide control device
  • the second partition or/and the lower flange is provided with the slide control device
  • Each of the slider control devices corresponds to one of the sliders.
  • the first high pressure stage cylinder and the second high pressure stage cylinder are both disposed on an upper side of the low pressure stage cylinder, and the first partition or/and the second partition are disposed on the second partition A slide control device, the first high pressure stage cylinder or/and the second high pressure stage cylinder as an unloadable cylinder.
  • the first high pressure stage cylinder and the second high pressure stage cylinder are both placed on a lower side of the low pressure stage cylinder, and the first partition and the second partition are placed on a lower side.
  • the baffle is provided with the slide control device or/and the lower flange is provided with the slide control device, and the first high pressure stage cylinder or/and the second high pressure stage cylinder are used as an unloadable cylinder.
  • the low-pressure stage cylinder is disposed between the first high-pressure stage cylinder and the second high-pressure stage cylinder, and the first partition and the second partition are placed on the upper side
  • the baffle control device or/and the lower flange is provided with the slide control device, and the first high pressure stage cylinder or/and the second high pressure stage cylinder serve as an unloadable cylinder.
  • the lower flange is provided with an intermediate cavity.
  • the slider control device comprises a pin and an elastic returning element, the elastic restoring element being disposed at a tail of the pin;
  • the first sliding piece or/and the second sliding piece are provided with a locking groove, the pin is for cooperating with the locking groove, and when the pin is placed in the locking groove, the sliding piece is Locking, the slide is unlocked after the pin is disengaged from the locking groove.
  • first baffle or/and the second baffle are provided with through holes corresponding to the lock grooves; or the first baffle or/and the lower flange are provided with a through hole corresponding to the lock groove; or the second partition or/and the lower flange is provided with a through hole corresponding to the lock groove; the pin is placed in the through hole In the hole, the pin is sealingly engaged with the through hole, and the pin is movable in an axial direction of the through hole.
  • the low-pressure stage cylinder, the first high-pressure stage cylinder or the second high-pressure stage cylinder is further provided with a groove corresponding to the through hole, and the groove communicates with the through hole to form a cavity The cavity is used to connect the control line.
  • the compressor has a first operating mode, a second operating mode, and a third operating mode;
  • the first sliding piece, the second sliding piece and the third sliding piece are all in a free state, and the low-pressure stage cylinder performs one-stage compression, the first high-pressure stage cylinder and The second high pressure stage cylinders are all subjected to secondary compression;
  • the first sliding piece or the second sliding piece is in a locked state
  • the low-pressure stage cylinder performs one-stage compression
  • the second high-pressure stage cylinder or the first high-pressure stage cylinder performs Secondary compression
  • the first sliding piece and the second sliding piece are both in a locked state
  • the low-pressure stage cylinder performs one-stage compression
  • the first high-pressure stage cylinder and the second high-pressure stage cylinder are both in Uninstall status.
  • an air conditioner including a compressor which is a compressor of any of the above aspects.
  • the first high-pressure stage cylinder or/and the second high-pressure stage cylinder are variable-capacity cylinders, which facilitates flexible adjustment of the number of working cylinders of the multi-cylinder compressor, thereby improving the operating condition thereof.
  • adaptability Under normal working conditions (lighter load), unload one or more high-pressure cylinders to improve the energy efficiency of the compressor and improve the overall energy efficiency of the compressor; increase the operation of the high-pressure cylinder under low-temperature conditions (heavier load) The quantity can greatly improve the heating capacity of the compressor.
  • FIG. 6 are schematic diagrams showing different arrangement of pump cylinders of a compressor of the present invention.
  • Figure 7 is a schematic view showing the flow direction of the refrigerant in the first embodiment of the pump body of the compressor shown in Figure 1;
  • Figure 8 is a schematic view showing the flow direction of the refrigerant in the second embodiment of the pump body of the compressor shown in Figure 1;
  • Figure 9 is a cross-sectional view showing the compressor body of Figure 8 in a locked state of the first slide
  • Figure 10 is a cross-sectional view showing the compressor body of Figure 8 in another direction in which the first sliding piece is in a locked state;
  • Figure 11 is a partially enlarged cross-sectional view showing the compressor body of Figure 8 in a locked state of the first sliding piece
  • Figure 12 is a partially enlarged cross-sectional view showing the compressor body of Figure 8 in a free state of the first slide;
  • FIG. 13 to 15 are schematic structural views showing the arrangement of two slide control devices for the pump body of the compressor shown in Figs. 1 to 6;
  • Figure 16 is a schematic view showing the structure of the pump body of the compressor of Figure 13 in a state in which both the first sliding piece and the second sliding piece are in a free state;
  • Figure 17 is a schematic view showing the structure of the pump body of the compressor shown in Figure 13 in a locked state at the first sliding piece and the second sliding piece in a free state;
  • Figure 18 is a schematic view showing the structure of the pump body of the compressor of Figure 13 in a free state at the first sliding piece and the second sliding piece in a locked state;
  • Fig. 19 is a structural schematic view showing the pump body of the compressor of Fig. 13 in a state in which the first sliding piece and the second sliding piece are both in a locked state.
  • a pump body of an embodiment of a compressor of the present invention includes a crankshaft 1, an upper flange, a low pressure stage cylinder 8, a first high pressure stage cylinder 3, a second high pressure stage cylinder 6 and a lower flange 9,
  • the low-pressure stage cylinder 8, the first high-pressure stage cylinder 3, and the second high-pressure stage cylinder 6 are stacked, and a partition is disposed between the adjacent two cylinders, and the first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6 are placed at a low pressure.
  • the same side of the stage cylinder 8 or the first high pressure stage cylinder 3 and the second high pressure stage cylinder 6 are respectively placed on both sides of the low pressure stage cylinder 8, and the lower flange 9 is placed in the low pressure stage cylinder 8, the first high pressure stage cylinder 3 and the
  • the lower side of the second high pressure stage cylinder 6 is provided with an intermediate chamber, and the lower end of the lower flange 9 is provided with a cover 10.
  • the first high pressure stage cylinder 3 has a first vane slot (not shown), a first vane 15 is disposed in the first vane slot, and the second high pressure stage cylinder 6 has a second vane slot (not shown).
  • a second sliding vane 17 is disposed in the second vane slot
  • the low-pressure stage cylinder 8 has a third vane slot (not shown), and a third vane is disposed in the third vane slot.
  • the first high-pressure stage cylinder 3 is disposed in parallel with the second high-pressure stage cylinder 6, and the parallel first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6 are connected in series with the low-pressure stage cylinder 8, the first high-pressure stage cylinder 3 or/and the second
  • the high pressure stage cylinder 6 is a variable capacity cylinder, and the low pressure stage cylinder 8 is used as a primary compression cylinder.
  • the two partitions are respectively a first partition and a second partition, and the first partition or/and the second partition are provided with a slide control device for controlling the action of the slide;
  • the first partition or/and the lower flange 9 are provided with slide control means;
  • the second partition or/and the lower flange 9 are provided with slide control means; each slide control means corresponds to a slide .
  • the slider control device comprises a pin 14 and an elastic restoring element 13 which is disposed at the tail of the pin 14.
  • the elastic return element 13 is a spring.
  • the first sliding piece 15 or/and the second sliding piece 17 are provided with a locking groove (not shown) for engaging the locking groove, and the corresponding sliding piece of the pin 14 when the pin 14 is placed in the locking groove After being locked, the pin 14 is released from the lock groove, and the corresponding slider of the pin 14 is unlocked to be in a free state.
  • first baffle or/and the second baffle are provided with through holes corresponding to the lock grooves; or the first baffle or/and the lower flange are provided with through holes corresponding to the lock grooves;
  • the second partition or/and the lower flange 9 are provided with a through hole corresponding to the lock groove; the pin 14 is placed in the through hole, and the pin 14 is sealingly fitted with the through hole, and the pin 14 can be The axial direction of the through hole is moved.
  • the low-pressure stage cylinder 8, the first high-pressure stage cylinder 3 or the second high-pressure stage cylinder 6 is further provided with a groove corresponding to the through hole, and the groove communicates with the through hole to form a cavity, the cavity
  • the body is used to connect the control line, and the refrigerant in the control line can change the pressure difference between the two sides of the pin 14, thereby causing the pin 14 to operate.
  • the first high pressure stage cylinder 3 and the second high pressure stage cylinder 6 are both placed on the upper side of the low pressure stage cylinder 8
  • the first partition or/and A slide control device is provided on the second partition
  • the first high pressure stage cylinder 3 or/and the second high pressure stage cylinder 6 serve as an unloadable cylinder.
  • the first partition here is a partition between the first high pressure stage cylinder 3 and the second high pressure stage cylinder 6, where the second partition is a gap between the second high pressure stage cylinder 6 and the low pressure stage cylinder 8. board.
  • the first high pressure stage cylinder 3 and the second high pressure stage cylinder 6 are both placed on the lower side of the low pressure stage cylinder 8, the first partition and the second.
  • the baffle control device disposed on the lower side of the partition plate or/and the lower flange 9 is provided with a slide control device, and the first high pressure stage cylinder 3 or/and the second high pressure stage cylinder 6 are Unload the cylinder.
  • the first partition plate is a partition between the low pressure stage cylinder 8 and the first high pressure stage cylinder 3
  • the second partition is a partition between the first high pressure stage cylinder 3 and the second high pressure stage cylinder 6,
  • the separator disposed on the lower side of the separator and the second separator is the second separator.
  • first partition here may also be a partition between the first high pressure stage cylinder 3 and the second high pressure stage cylinder 6, and the second partition may also be a low pressure stage cylinder 8 and a first high pressure stage cylinder 3.
  • the partition between the first partition and the second partition is the first partition.
  • the low-pressure stage cylinder 8 is placed between the first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6, and the low-pressure stage cylinder is disposed under the cylinder.
  • the roller 11, the upper roller 16 is disposed in the first high-pressure stage cylinder, the middle roller 12 is disposed in the second high-pressure stage cylinder 6, and the partition plate disposed on the upper side of the first partition plate and the second partition plate is provided with the slide control
  • a slide control device is provided on the device or/and the lower flange 9, and the first high pressure stage cylinder 3 or/and the second high pressure stage cylinder 6 serve as an unloadable cylinder.
  • the first partition plate here is a partition between the first high pressure stage cylinder 3 and the low pressure stage cylinder 8 (the upper partition plate 4 is integrated with the middle partition plate 5), and the second partition plate is the second high pressure stage.
  • the partition between the cylinder 6 and the low-pressure stage cylinder 8 (the lower partition 7), and the partition placed on the upper side of the first partition and the second partition is the first partition.
  • the first partition here may also be a partition between the second high-pressure stage cylinder 6 and the low-pressure stage cylinder 8
  • the second partition may be a gap between the first high-pressure stage cylinder 3 and the low-pressure stage cylinder 8. The plate, then the partition placed on the upper side of the first partition and the second partition is the second partition.
  • the compressor of the above embodiment has a first working mode, a second working mode, and a third operating mode
  • the first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6 are both placed on the upper side of the low-pressure stage cylinder 8, as shown in FIG.
  • the sheet 15, the second vane 17 and the third vane are all in a free state
  • the low-pressure stage cylinder 8 performs one-stage compression
  • the first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6 are both subjected to secondary compression.
  • the refrigerant coming out of the evaporator enters the liquid separator and enters the low-pressure stage cylinder 8.
  • the first compression in the low-pressure stage cylinder 8 After the first compression in the low-pressure stage cylinder 8, it is discharged to the intermediate chamber, and the refrigerant which is flashed to the intermediate pressure with the flasher is mixed in the intermediate chamber.
  • the mixed refrigerant enters the first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6 for the second compression, and then directly discharged into the casing of the compressor, thereby realizing three-cylinder two-stage motion, and the direction of the arrow in the figure indicates the refrigerant. Flow direction.
  • the first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6 are both placed on the upper side of the low-pressure stage cylinder 8, as shown in FIGS. 17 and 18,
  • the first slide 15 or the second slide 17 is in a locked state
  • the low pressure stage cylinder 8 performs one stage compression
  • the second high pressure stage cylinder 6 or the first high pressure stage cylinder 3 performs secondary compression.
  • the refrigerant coming out of the evaporator enters the liquid separator and enters the low-pressure stage cylinder 8 for the first compression. After compression, it is discharged to the intermediate chamber, which is mixed with the intermediate pressure refrigerant flashed by the flasher, and the refrigerant enters the first high pressure after mixing.
  • the second stage compression is performed in the stage cylinder 3 or the second high pressure stage cylinder 6, and then directly discharged into the compressor casing to realize two-stage two-stage operation, and the direction of the arrow in the figure indicates the flow direction of the refrigerant.
  • the first high-pressure stage cylinder 3 and the second high-pressure stage cylinder 6 are both placed on the upper side of the low-pressure stage cylinder 8, as shown in FIG. Both the sheet 15 and the second sliding sheet 17 are in a locked state, the third sliding sheet is in a free state, and the low-pressure stage cylinder 8 is subjected to one-stage compression. Both the first high pressure stage cylinder 3 and the second high pressure stage cylinder 6 are in an unloaded state.
  • the present invention also relates to an air conditioner, including the compressor of any of the above technical solutions. Since the air conditioner is a prior art except for the compressor, it will not be further described herein.
  • the first high-pressure stage cylinder or/and the second high-pressure stage cylinder are variable-capacity cylinders, which facilitates flexible adjustment of the number of working cylinders of the multi-cylinder compressor, thereby improving the adaptation to the operating conditions. ability.
  • Under normal working conditions (lighter load) unload one or more high-pressure cylinders to improve the energy efficiency of the compressor and improve the overall energy efficiency of the compressor; increase the operation of the high-pressure cylinder under low-temperature conditions (heavier load)
  • the quantity can greatly improve the heating capacity of the compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

提供一种压缩机，低压级气缸（8）、第一高压级气缸（3）、第二高压级气缸（6）叠放设置，相邻的两气缸之间设置隔板，第一高压级气缸（3）和第二高压级气缸（6）均置于低压级气缸（8）的同侧或分别置于低压级气缸（8）的两侧，下法兰（9）置于低压级气缸（8）、第一高压级气缸（3）和第二高压级气缸（6）的下侧；第一高压级气缸（3）内设置第一滑片（15），第二高压级气缸（6）内设置第二滑片（17），低压级气缸（8）内设置第三滑片；第一高压级气缸（3）与第二高压级气缸（6）并联设置，并联后的第一高压级气缸（3）和第二高压级气缸（6）与低压级气缸（8）串联，第一高压级气缸（3）或／和第二高压级气缸（6）为可变容气缸，低压级气缸（8）作为一级压缩缸。还涉及一种空调器。提供的压缩机和空调器，方便调节多缸压缩机工作气缸的数量。

Description

压缩机和空调器
本申请要求于2014年04月10日提交中国专利局、申请号为201410143626.8、发明名称为“压缩机和空调器”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及制冷领域，尤其涉及一种滚动转子式三缸双级变容增焓压缩机和空调器。
背景技术
随着环境温度下降，制冷剂的比容增大，压缩机的单位吸气量减小，造成压缩机的制热能力大幅下降。通常采用电辅热来提高压缩机的制热量或双级增焓压缩机来解决低温制热能力低的问题。采用电辅热提高压缩机制热量的方法能效较低；由于普通双级增焓压缩机的排量无法进行调节，其对运行工况的适应能力较差，若保证压缩机低温工况下的制热能力和能效，普通工况下运行的能效大幅下降。
发明内容
鉴于现有技术的现状，本发明的目的在于提供一种压缩机和空调器，可灵活调节多缸压缩机工作气缸的数量，从而提高其对运行工况的适应能力。为实现上述目的，本发明的技术方案如下：
一种压缩机，包括低压级气缸、第一高压级气缸、第二高压级气缸和下法兰；
低压级气缸、第一高压级气缸、第二高压级气缸叠放设置，相邻的两气缸之间设置隔板，所述第一高压级气缸和所述第二高压级气缸均置于所述低压级气缸的同侧或所述第一高压级气缸和所述第二高压级气缸分别置于所述低压 级气缸的两侧，所述下法兰置于所述低压级气缸、所述第一高压级气缸和所述第二高压级气缸的下侧；
所述第一高压级气缸具有第一滑片槽，在所述第一滑片槽内设置第一滑片，所述第二高压级气缸具有第二滑片槽，在所述第二滑片槽内设置第二滑片，所述低压级气缸具有第三滑片槽，在所述第三滑片槽内设置第三滑片；
所述第一高压级气缸与所述第二高压级气缸并联设置，并联后的所述第一高压级气缸和所述第二高压级气缸与所述低压级气缸串联，所述第一高压级气缸或/和第二高压级气缸为可变容气缸，所述低压级气缸作为一级压缩缸。
较优地，两个所述隔板分别为第一隔板和第二隔板，所述第一隔板或/和所述第二隔板上设置有用于控制滑片动作的滑片控制装置；或者，所述第一隔板或/和所述下法兰设置有所述滑片控制装置；或者，所述第二隔板或/和所述下法兰设置有所述滑片控制装置；每个所述滑片控制装置对应一个所述滑片。
较优地，所述第一高压级气缸和所述第二高压级气缸均置于所述低压级气缸的上侧，所述第一隔板或/和所述第二隔板上设置所述滑片控制装置，所述第一高压级气缸或/和所述第二高压级气缸作为可卸载气缸。
较优地，所述第一高压级气缸和所述第二高压级气缸均置于所述低压级气缸的下侧，所述第一隔板与所述第二隔板中置于下侧的所述隔板设置所述滑片控制装置或/和所述下法兰上设置所述滑片控制装置，所述第一高压级气缸或/和所述第二高压级气缸作为可卸载气缸。
较优地，所述低压级气缸置于所述第一高压级气缸和所述第二高压级气缸之间，所述第一隔板和所述第二隔板中置于上侧的所述隔板设置所述滑片控制装置或/和所述下法兰上设置所述滑片控制装置，所述第一高压级气缸或/和所述第二高压级气缸作为可卸载气缸。
较优地，所述下法兰设置有中间腔。
较优地，所述滑片控制装置包括销钉和弹性复位元件，所述弹性复位元件设置在所述销钉的尾部；
所述第一滑片或/和第二滑片设有止锁槽，所述销钉用于与所述止锁槽相配合，所述销钉置于所述止锁槽时，所述滑片被锁定，所述销钉脱离所述止锁槽后，所述滑片解锁。
进一步地，所述第一隔板或/和所述第二隔板上设置与所述止锁槽相对应的通孔；或者，所述第一隔板或/和所述下法兰设置有与所述止锁槽相对应的通孔；或者，所述第二隔板或/和所述下法兰设置有与所述止锁槽相对应的通孔；所述销钉置于所述通孔中，所述销钉与所述通孔密封配合，所述销钉能够在所述通孔的轴向方向移动。
进一步地，所述低压级气缸、所述第一高压级气缸或所述第二高压级气缸还设置有与所述通孔对应的凹槽，所述凹槽与所述通孔连通形成腔体，所述腔体用于连通控制管路。
较优地，所述压缩机具有第一工作模式、第二工作模式和第三工作模式；
在第一工作模式下，所述第一滑片、所述第二滑片和所述第三滑片均处于自由状态，所述低压级气缸进行一级压缩，所述第一高压级气缸和所述第二高压级气缸均进行二级压缩；
在第二工作模式下，所述第一滑片或所述第二滑片处于锁定状态，所述低压级气缸进行一级压缩，所述第二高压级气缸或所述第一高压级气缸进行二级压缩；
在第三工作模式下，所述第一滑片和第二滑片均处于锁定状态，所述低压级气缸进行一级压缩，所述第一高压级气缸和所述第二高压级气缸均处于卸载状态。
还涉及一种空调器，包括压缩机，所述压缩机为上述任一技术方案的压缩机。
本发明的有益效果是：
本发明的压缩机和空调器，第一高压级气缸或/和第二高压级气缸为可变容气缸，方便灵活调节多缸压缩机工作气缸的数量，从而提高其对运行工况的 适应能力。在常规工况下(负载较轻)，卸载一个或多个的高压级气缸，提高压缩机的能效，提升压缩机的综合能效；在低温工况下(负载较重)增加高压级气缸的工作数量，能大幅提高压缩机的制热能力。
附图说明
图1至图6为本发明的压缩机的泵体气缸不同排布示意图；
图7为图1所示压缩机的泵体实施例一的冷媒流向示意图；
图8为图1所示压缩机的泵体实施例二的冷媒流向示意图；
图9为图8所示压缩机泵体在第一滑片处于锁定状态的剖视示意图；
图10为图8所示压缩机泵体在第一滑片处于锁定状态的另一方向剖视示意图；
图11为图8所示压缩机泵体在第一滑片处于锁定状态的局部放大剖视示意图；
图12为图8所示压缩机泵体在第一滑片处于自由状态的局部放大剖视示意图；
图13至15为图1至图6所示压缩机的泵体设置两个滑片控制装置的结构示意图；
图16为图13所示压缩机的泵体在第一滑片和第二滑片均处于自由状态的结构示意图；
图17为图13所示压缩机的泵体在第一滑片处锁定状态、第二滑片处于自由状态的结构示意图；
图18为图13所示压缩机的泵体在第一滑片处自由状态、第二滑片处于锁定状态的结构示意图；
图19为图13所示压缩机的泵体在第一滑片、第二滑片均处于锁定状态的结构示意图。
具体实施方式
为了使本发明的目的、技术方案及优点更加清楚明白，以下结合附图及实施例对本发明的压缩机和空调器进行进一步详细说明。应当理解，此处所描述的具体实施例仅用于解释本发明，并不用于限定本发明。
参照图1至图19，本发明的压缩机一实施例的泵体包括曲轴1、上法兰、低压级气缸8、第一高压级气缸3、第二高压级气缸6和下法兰9，低压级气缸8、第一高压级气缸3、第二高压级气缸6叠放设置，相邻的两气缸之间设置隔板，第一高压级气缸3和第二高压级气缸6均置于低压级气缸8的同侧或第一高压级气缸3和第二高压级气缸6分别置于低压级气缸8的两侧，下法兰9置于低压级气缸8、第一高压级气缸3和第二高压级气缸6的下侧，下法兰9设置有中间腔，下法兰9的下端设置盖板10。第一高压级气缸3具有第一滑片槽(未示出)，在第一滑片槽内设置第一滑片15，第二高压级气缸6具有第二滑片槽(未示出)，在第二滑片槽内设置第二滑片17，低压级气缸8具有第三滑片槽(未示出)，在第三滑片槽内设置第三滑片。第一高压级气缸3与第二高压级气缸6并联设置，并联后的第一高压级气缸3和第二高压级气缸6与低压级气缸8串联，第一高压级气缸3或/和第二高压级气缸6为可变容气缸，低压级气缸8作为一级压缩缸。
作为一种可实施方式，两个所述隔板分别为第一隔板和第二隔板，第一隔板或/和第二隔板上设置有用于控制滑片动作的滑片控制装置；或者，第一隔板或/和下法兰9设置有滑片控制装置；或者，第二隔板或/和下法兰9设置有滑片控制装置；每个滑片控制装置对应一个滑片。优选地，滑片控制装置包括销钉14和弹性复位元件13，弹性复位元件13设置在销钉14的尾部。弹性复位元件13为弹簧。
第一滑片15或/和第二滑片17设有止锁槽(未标示)，销钉14用于与止锁槽相配合，销钉14置于止锁槽内时，销钉14对应的滑片被锁定，销钉14脱离止锁槽后，销钉14对应的滑片解锁而呈自由状态。
进一步地，第一隔板或/和第二隔板上设置与止锁槽相对应的通孔；或者，第一隔板或/和下法兰设置有与止锁槽相对应的通孔；或者，第二隔板或/和下法兰9设置有与止锁槽相对应的通孔；销钉14置于所述通孔中，销钉14与所述通孔密封配合，销钉14能够在所述通孔的轴向方向移动。
其中，低压级气缸8、第一高压级气缸3或第二高压级气缸6还设置有与所述通孔对应的凹槽，所述凹槽与所述通孔连通形成腔体，所述腔体用于连通控制管路，控制管路内的冷媒可改变销钉14两侧的压差，从而使销钉14动作。
作为一种可实施方式，如图1、图2和图13所示，第一高压级气缸3和第二高压级气缸6均置于低压级气缸8的上侧，第一隔板或/和第二隔板上设置滑片控制装置，第一高压级气缸3或/和第二高压级气缸6作为可卸载气缸。此处的第一隔板为第一高压级气缸3与第二高压级气缸6之间的隔板，此处的第二隔板为第二高压级气缸6与低压级气缸8之间的隔板。
作为一种可实施方式，如图5、图6和图15所示，第一高压级气缸3和第二高压级气缸6均置于低压级气缸8的下侧，第一隔板与第二隔板中置于下侧的所述隔板设置滑片控制装置或/和下法兰9上设置滑片控制装置，第一高压级气缸3或/和所述第二高压级气缸6作为可卸载气缸。此处的第一隔板为低压级气缸8与第一高压级气缸3之间的隔板，第二隔板为第一高压级气缸3与第二高压级气缸6之间的隔板，第一隔板与第二隔板中置于下侧的隔板即为第二隔板。当然，此处的第一隔板也可为第一高压级气缸3与第二高压级气缸6之间的隔板，第二隔板也可为低压级气缸8与第一高压级气缸3之间的隔板，那么第一隔板与第二隔板中置于下侧的隔板就为第一隔板。
作为一种可实施方式，如图3、图4、图9和图14所示，低压级气缸8置于第一高压级气缸3和第二高压级气缸6之间，低压级气缸内设置下滚子11，第一高压级气缸内设置上滚子16，第二高压级气缸6内设置中滚子12，第一隔板和第二隔板中置于上侧的隔板设置滑片控制装置或/和下法兰9上设置滑片控制装置，第一高压级气缸3或/和第二高压级气缸6作为可卸载气缸。 此处的第一隔板为第一高压级气缸3与低压级气缸8之间的隔板(上隔板4与中隔板5为一体的隔板)，第二隔板为第二高压级气缸6与低压级气缸8之间的隔板(下隔板7)，第一隔板和第二隔板中置于上侧的隔板即为第一隔板。当然，此处的第一隔板也可为第二高压级气缸6与低压级气缸8之间的隔板，第二隔板可为第一高压级气缸3与低压级气缸8之间的隔板，那么第一隔板和第二隔板中置于上侧的隔板就为第二隔板。
以上实施例的压缩机具有第一工作模式、第二工作模式和第三工作模式；
在第一工作模式下(三缸双级模式)，以第一高压级气缸3和第二高压级气缸6均置于低压级气缸8的上侧为例，如图16所示，第一滑片15、第二滑片17和第三滑片均处于自由状态，低压级气缸8进行一级压缩，第一高压级气缸3和第二高压级气缸6均进行二级压缩。从蒸发器出来的冷媒进入分液器后进入低压级气缸8，在低压级气缸8内进行第一次压缩后排出至中间腔，其与闪蒸器闪发为中间压力的冷媒在中间腔内混合，混合后的冷媒进入第一高压级气缸3和第二高压级气缸6进行第二次压缩，然后直接排出至压缩机的壳体内，从而实现三缸双级运动，图中的箭头方向表示冷媒流向。
在第二工作模式下(双缸双级模式)，以第一高压级气缸3和第二高压级气缸6均置于低压级气缸8的上侧为例，如图17和图18所示，第一滑片15或第二滑片17处于锁定状态，低压级气缸8进行一级压缩，第二高压级气缸6或第一高压级气缸3进行二级压缩。从蒸发器出来的冷媒进入分液器后进入低压级气缸8进行第一次压缩，压缩后排出至中间腔，其与闪蒸器闪发出来的中间压力的冷媒混合，混合后冷媒进入第一高压级气缸3或第二高压级气缸6内进行第二次压缩，然后直接排出这压缩机壳体内，实现双缸双级运行，图中的箭头方向表示冷媒流向。
在第三工作模式下(单缸单级模式)，以第一高压级气缸3和第二高压级气缸6均置于低压级气缸8的上侧为例，如图19所示，第一滑片15和第二滑片17均处于锁定状态，第三滑片处于自由状态，低压级气缸8进行一级压缩， 第一高压级气缸3和第二高压级气缸6均处于卸载状态。
本发明还涉及一种空调器，包括上述任一技术方案的压缩机，由于空调器除压缩机外均为现有技术，此处不再一一赘述。
以上实施例的压缩机和空调器，第一高压级气缸或/和第二高压级气缸为可变容气缸，方便灵活调节多缸压缩机工作气缸的数量，从而提高其对运行工况的适应能力。在常规工况下(负载较轻)，卸载一个或多个的高压级气缸，提高压缩机的能效，提升压缩机的综合能效；在低温工况下(负载较重)增加高压级气缸的工作数量，能大幅提高压缩机的制热能力。
以上所述实施例仅表达了本发明的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对本发明专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本发明构思的前提下，还可以做出若干变形和改进，这些都属于本发明的保护范围。因此，本发明专利的保护范围应以所附权利要求为准。

Claims (11)

  1. 一种压缩机，其特征在于：
    包括低压级气缸、第一高压级气缸、第二高压级气缸和下法兰；
    低压级气缸、第一高压级气缸、第二高压级气缸叠放设置，相邻的两气缸之间设置隔板，所述第一高压级气缸和所述第二高压级气缸均置于所述低压级气缸的同侧或所述第一高压级气缸和所述第二高压级气缸分别置于所述低压级气缸的两侧，所述下法兰置于所述低压级气缸、所述第一高压级气缸和所述第二高压级气缸的下侧；
    所述第一高压级气缸具有第一滑片槽，在所述第一滑片槽内设置第一滑片，所述第二高压级气缸具有第二滑片槽，在所述第二滑片槽内设置第二滑片，所述低压级气缸具有第三滑片槽，在所述第三滑片槽内设置第三滑片；
    所述第一高压级气缸与所述第二高压级气缸并联设置，并联后的所述第一高压级气缸和所述第二高压级气缸与所述低压级气缸串联，所述第一高压级气缸或/和第二高压级气缸为可变容气缸，所述低压级气缸作为一级压缩缸。
  2. 根据权利要求1所述的压缩机，其特征在于：
    两个所述隔板分别为第一隔板和第二隔板，所述第一隔板或/和所述第二隔板上设置有用于控制滑片动作的滑片控制装置；或者，所述第一隔板或/和所述下法兰设置有所述滑片控制装置；或者，所述第二隔板或/和所述下法兰设置有所述滑片控制装置；每个所述滑片控制装置对应一个所述滑片。
  3. 根据权利要求2所述的压缩机，其特征在于：
    所述第一高压级气缸和所述第二高压级气缸均置于所述低压级气缸的上侧，所述第一隔板或/和所述第二隔板上设置所述滑片控制装置，所述第一高压级气缸或/和所述第二高压级气缸作为可卸载气缸。
  4. 根据权利要求2所述的压缩机，其特征在于：
    所述第一高压级气缸和所述第二高压级气缸均置于所述低压级气缸的下 侧，所述第一隔板与所述第二隔板中置于下侧的所述隔板设置所述滑片控制装置或/和所述下法兰上设置所述滑片控制装置，所述第一高压级气缸或/和所述第二高压级气缸作为可卸载气缸。
  5. 根据权利要求2所述的压缩机，其特征在于：
    所述低压级气缸置于所述第一高压级气缸和所述第二高压级气缸之间，所述第一隔板和所述第二隔板中置于上侧的所述隔板设置所述滑片控制装置或/和所述下法兰上设置所述滑片控制装置，所述第一高压级气缸或/和所述第二高压级气缸作为可卸载气缸。
  6. 根据权利要求1-5任一项所述的压缩机，其特征在于：
    所述下法兰设置有中间腔。
  7. 根据权利要求2-5任一项所述的压缩机，其特征在于：
    所述滑片控制装置包括销钉和弹性复位元件，所述弹性复位元件设置在所述销钉的尾部；
    所述第一滑片或/和第二滑片设有止锁槽，所述销钉用于与所述止锁槽相配合，所述销钉置于所述止锁槽时，所述滑片被锁定，所述销钉脱离所述止锁槽后，所述滑片解锁。
  8. 根据权利要求7所述的压缩机，其特征在于：
    所述第一隔板或/和所述第二隔板上设置与所述止锁槽相对应的通孔；或者，所述第一隔板或/和所述下法兰设置有与所述止锁槽相对应的通孔；或者，所述第二隔板或/和所述下法兰设置有与所述止锁槽相对应的通孔；所述销钉置于所述通孔中，所述销钉与所述通孔密封配合，所述销钉能够在所述通孔的轴向方向移动。
  9. 根据权利要求8所述的压缩机，其特征在于：
    所述低压级气缸、所述第一高压级气缸或所述第二高压级气缸还设置有与所述通孔对应的凹槽，所述凹槽与所述通孔连通形成腔体，所述腔体用于连通控制管路。
  10. 根据权利要求2-5任一项所述的压缩机，其特征在于：
    所述压缩机具有第一工作模式、第二工作模式和第三工作模式；
    在第一工作模式下，所述第一滑片、所述第二滑片和所述第三滑片均处于自由状态，所述低压级气缸进行一级压缩，所述第一高压级气缸和所述第二高压级气缸均进行二级压缩；
    在第二工作模式下，所述第一滑片或所述第二滑片处于锁定状态，所述低压级气缸进行一级压缩，所述第二高压级气缸或所述第一高压级气缸进行二级压缩；
    在第三工作模式下，所述第一滑片和第二滑片均处于锁定状态，所述低压级气缸进行一级压缩，所述第一高压级气缸和所述第二高压级气缸均处于卸载状态。
  11. 一种空调器，包括压缩机，其特征在于：
    所述压缩机为权利要求1-10任一项所述的压缩机。
PCT/CN2015/076290 2014-04-10 2015-04-10 压缩机和空调器 WO2015154717A1 (zh)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2016561371A JP6244478B2 (ja) 2014-04-10 2015-04-10 圧縮機及び空気調和装置
US15/301,072 US11067083B2 (en) 2014-04-10 2015-04-10 Compressor and air conditioner
EP15777291.4A EP3130806B1 (en) 2014-04-10 2015-04-10 Compressor and air conditioner
KR1020167031181A KR101797424B1 (ko) 2014-04-10 2015-04-10 압축기 및 공기 조화 장치

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410143626.8 2014-04-10
CN201410143626.8A CN103953544B (zh) 2014-04-10 2014-04-10 压缩机和空调器

Publications (1)

Publication Number Publication Date
WO2015154717A1 true WO2015154717A1 (zh) 2015-10-15

Family

ID=51330863

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/076290 WO2015154717A1 (zh) 2014-04-10 2015-04-10 压缩机和空调器

Country Status (6)

Country Link
US (1) US11067083B2 (zh)
EP (1) EP3130806B1 (zh)
JP (1) JP6244478B2 (zh)
KR (1) KR101797424B1 (zh)
CN (1) CN103953544B (zh)
WO (1) WO2015154717A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107878154A (zh) * 2017-10-24 2018-04-06 珠海格力电器股份有限公司 一种双级增焓车用空调系统和控制方法
CN109322828A (zh) * 2018-11-16 2019-02-12 珠海格力节能环保制冷技术研究中心有限公司 滑片结构、泵体组件及压缩机

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103953544B (zh) * 2014-04-10 2016-01-27 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器
CN103953545B (zh) * 2014-04-10 2016-01-27 珠海格力节能环保制冷技术研究中心有限公司 压缩机及空调器
CN103982426B (zh) * 2014-05-15 2016-08-17 珠海格力节能环保制冷技术研究中心有限公司 滚动转子式压缩机及其泵体结构
CN105508249B (zh) * 2014-09-24 2017-09-22 珠海格力节能环保制冷技术研究中心有限公司 空调系统及其压缩机
JP6734624B2 (ja) * 2014-09-30 2020-08-05 ダイキン工業株式会社 空気調和装置の室内ユニット
CN105626523B (zh) * 2014-11-05 2018-02-02 珠海格力节能环保制冷技术研究中心有限公司 压缩机、空调系统和压缩机控制方法
CN104632581B (zh) * 2014-11-28 2017-02-01 珠海格力节能环保制冷技术研究中心有限公司 双缸两级压缩机和空调系统
CN105987657B (zh) 2015-02-12 2018-12-07 珠海格力电器股份有限公司 用于转轴的电涡流传感器和转轴装置
CN105840500A (zh) * 2015-04-02 2016-08-10 熵零股份有限公司 一种三缸共轴流体机构
CN106704189A (zh) * 2015-08-10 2017-05-24 珠海格力节能环保制冷技术研究中心有限公司 压缩机和换热系统
CN105114320B (zh) * 2015-08-18 2018-07-24 广东美芝制冷设备有限公司 旋转式变容喷气增焓压缩机
CN105545745B (zh) * 2015-12-07 2018-09-25 珠海格力节能环保制冷技术研究中心有限公司 压缩机及降低压缩机泄漏量的方法
CN105464978A (zh) * 2015-12-18 2016-04-06 珠海格力节能环保制冷技术研究中心有限公司 变容气缸的滑片控制结构、变容气缸及变容压缩机
CN105485012B (zh) * 2016-01-11 2018-05-22 珠海格力节能环保制冷技术研究中心有限公司 一种旋转压缩机及其变容控制方法
CN107435628B (zh) * 2016-05-25 2019-05-10 北京星旋世纪科技有限公司 定位密封组件及应用其的转动装置、转动系统和流体机械
DE102017004361A1 (de) * 2017-05-05 2018-11-08 Wabco Gmbh Verfahren zum Betreiben einer Druckregelanlage mit einem mehrstufigen Kompressor, sowie Druckregelanlage
CN107489619B (zh) * 2017-08-28 2023-07-14 广东美芝制冷设备有限公司 旋转式压缩机和具有其的空调系统
CN108087278B (zh) * 2017-12-06 2023-11-03 珠海格力节能环保制冷技术研究中心有限公司 压缩机及空调器
CN111287974B (zh) * 2018-12-06 2022-01-18 安徽美芝精密制造有限公司 四缸压缩机及具有其的制冷装置
CN111287973B (zh) * 2018-12-06 2022-01-18 安徽美芝精密制造有限公司 三缸压缩机及具有其的制冷装置
CN109958625B (zh) * 2018-12-20 2020-01-07 珠海格力电器股份有限公司 销钉弹性部变形控制方法及控制系统、变容压缩机
CN111594443B (zh) * 2020-05-12 2024-05-14 珠海凌达压缩机有限公司 一种压缩机组件及包括其的空调系统及控制方法
CN111622950B (zh) * 2020-05-22 2022-05-31 珠海格力节能环保制冷技术研究中心有限公司 压缩机及其控制方法、空调器
CN113982926A (zh) * 2021-10-19 2022-01-28 珠海格力节能环保制冷技术研究中心有限公司 一种单双级切换的压缩机、空调系统和控制方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002303284A (ja) * 2001-04-09 2002-10-18 Matsushita Electric Ind Co Ltd ロータリ式多段圧縮機
JP2003286981A (ja) * 2002-03-28 2003-10-10 Sanyo Electric Co Ltd 横型多段圧縮式ロータリコンプレッサ
CN202946381U (zh) * 2012-11-30 2013-05-22 珠海格力节能环保制冷技术研究中心有限公司 压缩机及具有其的制冷系统
CN202954971U (zh) * 2012-10-12 2013-05-29 珠海格力电器股份有限公司 双缸变容量压缩机
CN103953544A (zh) * 2014-04-10 2014-07-30 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器
CN203906282U (zh) * 2014-04-10 2014-10-29 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5612085A (en) * 1979-07-12 1981-02-05 Sanyo Electric Co Ltd Capacity controller for multicylinder rotary compressor
JPS5910792A (ja) * 1982-07-09 1984-01-20 Hitachi Ltd ロ−タリ式圧縮機
JPS5928694U (ja) 1982-08-17 1984-02-22 三菱電機株式会社 多気筒形回転圧縮機の容量制御
JPH05106576A (ja) * 1991-08-05 1993-04-27 Daikin Ind Ltd 多気筒密閉形回転圧縮機
US6672065B1 (en) * 1999-09-15 2004-01-06 Ewan Choroszylow Multiple stage compressor with rotors using rollers
JP2005155540A (ja) * 2003-11-27 2005-06-16 Aisin Seiki Co Ltd 多段ドライ真空ポンプ
CN100447424C (zh) * 2004-06-15 2008-12-31 东芝开利株式会社 多缸旋转式压缩机
KR100595766B1 (ko) 2005-02-23 2006-07-03 엘지전자 주식회사 로터리 압축기의 용량 가변 장치 및 이를 적용한 에어콘
JP4796073B2 (ja) * 2005-02-23 2011-10-19 エルジー エレクトロニクス インコーポレイティド 容量可変型ロータリ圧縮機
JP4856091B2 (ja) * 2005-02-23 2012-01-18 エルジー エレクトロニクス インコーポレイティド 容量可変型ロータリ圧縮機及びこれを備える冷却システム
WO2007052569A1 (ja) * 2005-10-31 2007-05-10 Matsushita Electric Industrial Co., Ltd. 膨張機およびこれを用いたヒートポンプ
JP4797715B2 (ja) 2006-03-09 2011-10-19 ダイキン工業株式会社 冷凍装置
EP2075405B1 (en) 2007-12-25 2015-10-14 Calsonic Kansei Corporation Vane-type compressor
KR101023351B1 (ko) * 2008-07-16 2011-03-18 엘지전자 주식회사 용량 가변형 압축기 및 이를 구비하는 공기 조화 시스템
JP5040907B2 (ja) * 2008-09-30 2012-10-03 ダイキン工業株式会社 冷凍装置
KR101268612B1 (ko) * 2008-11-17 2013-05-29 엘지전자 주식회사 주파수 가변 압축기 및 그 제어 방법
KR101679860B1 (ko) * 2010-07-14 2016-11-25 엘지전자 주식회사 압축기
KR101708310B1 (ko) 2010-12-29 2017-02-20 엘지전자 주식회사 밀폐형 압축기
WO2013005568A1 (ja) 2011-07-01 2013-01-10 東芝キヤリア株式会社 多気筒回転式圧縮機及び冷凍サイクル装置
US9512841B2 (en) * 2011-11-16 2016-12-06 Panasonic Intellectual Property Management Co., Ltd. Rotary compressor with oil retaining portion
CN103185007B (zh) * 2011-12-29 2015-11-04 珠海格力节能环保制冷技术研究中心有限公司 旋转压缩机的气缸、旋转压缩机及空调器
GB2499217A (en) * 2012-02-08 2013-08-14 Edwards Ltd Vacuum pump with recirculation valve
CN202833168U (zh) 2012-10-12 2013-03-27 珠海格力节能环保制冷技术研究中心有限公司 压缩机
DK2976225T3 (en) * 2013-03-21 2018-01-02 Carrier Corp CAPACITY MODULATION OF TRANSPORT COOLING SYSTEM
CN203335401U (zh) 2013-03-26 2013-12-11 珠海格力节能环保制冷技术研究中心有限公司 双级增焓转子压缩机及具有其的空调器、热泵热水器
CN111373152B (zh) * 2017-08-08 2021-01-15 日立江森自控空调有限公司 旋转压缩机及其组装方法
WO2019142408A1 (ja) * 2018-01-18 2019-07-25 東芝キヤリア株式会社 圧縮機および冷凍サイクル装置
WO2019186695A1 (ja) * 2018-03-27 2019-10-03 東芝キヤリア株式会社 ロータリコンプレッサおよび冷凍サイクル装置
WO2019193697A1 (ja) * 2018-04-04 2019-10-10 東芝キヤリア株式会社 ロータリコンプレッサおよび冷凍サイクル装置
EP3920374A4 (en) * 2019-07-02 2022-03-16 Samsung Electronics Co., Ltd. ENGINE AND COMPRESSOR WITH SUCH ENGINE

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002303284A (ja) * 2001-04-09 2002-10-18 Matsushita Electric Ind Co Ltd ロータリ式多段圧縮機
JP2003286981A (ja) * 2002-03-28 2003-10-10 Sanyo Electric Co Ltd 横型多段圧縮式ロータリコンプレッサ
CN202954971U (zh) * 2012-10-12 2013-05-29 珠海格力电器股份有限公司 双缸变容量压缩机
CN202946381U (zh) * 2012-11-30 2013-05-22 珠海格力节能环保制冷技术研究中心有限公司 压缩机及具有其的制冷系统
CN103953544A (zh) * 2014-04-10 2014-07-30 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器
CN203906282U (zh) * 2014-04-10 2014-10-29 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3130806A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107878154A (zh) * 2017-10-24 2018-04-06 珠海格力电器股份有限公司 一种双级增焓车用空调系统和控制方法
CN107878154B (zh) * 2017-10-24 2023-09-08 珠海格力电器股份有限公司 一种双级增焓车用空调系统和控制方法
CN109322828A (zh) * 2018-11-16 2019-02-12 珠海格力节能环保制冷技术研究中心有限公司 滑片结构、泵体组件及压缩机
CN109322828B (zh) * 2018-11-16 2024-04-16 珠海格力节能环保制冷技术研究中心有限公司 滑片结构、泵体组件及压缩机

Also Published As

Publication number Publication date
US11067083B2 (en) 2021-07-20
JP6244478B2 (ja) 2017-12-06
EP3130806A1 (en) 2017-02-15
CN103953544A (zh) 2014-07-30
CN103953544B (zh) 2016-01-27
KR20170009851A (ko) 2017-01-25
JP2017516009A (ja) 2017-06-15
EP3130806B1 (en) 2018-11-07
KR101797424B1 (ko) 2017-11-13
EP3130806A4 (en) 2017-11-08
US20170022988A1 (en) 2017-01-26

Similar Documents

Publication Publication Date Title
WO2015154717A1 (zh) 压缩机和空调器
WO2015154726A1 (zh) 压缩机及空调器
US10724523B2 (en) Compressor and refrigeration system having same
KR101986965B1 (ko) 압축기와 열교환 시스템
WO2015172612A1 (zh) 空调系统
CN204851640U (zh) 压缩机和换热系统
CN202579193U (zh) 双级变容量压缩机
WO2017063588A1 (zh) 双级变容压缩机及具有其的空调系统
CN103423164A (zh) 双级变容量压缩机及其控制方法
CN105221421A (zh) 压缩机及空调器
CN106321433A (zh) 压缩机及空调系统
US10465683B2 (en) Compressor, air conditioning system, and a method of controlling a compressor
CN110578689A (zh) 压缩机及具有其的空调系统
CN110762017B (zh) 进气结构、排气结构、压缩机、控制方法及空调器
CN205689429U (zh) 多级压缩机及空调系统
WO2017031669A1 (zh) 旋转式压缩机和具有其的冷冻循环装置
CN203906282U (zh) 压缩机和空调器
CN204003467U (zh) 空调系统
CN112412787B (zh) 变容压缩机和空调器
CN218627339U (zh) 换热系统
CN107218740B (zh) 冷媒循环系统及具有其的空调器
CN204061180U (zh) 一种可变内容积比涡旋压缩机
CN115977954A (zh) 旋转式压缩机及其空调系统

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: 15777291

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 15301072

Country of ref document: US

ENP Entry into the national phase

Ref document number: 2016561371

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

REEP Request for entry into the european phase

Ref document number: 2015777291

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2015777291

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 20167031181

Country of ref document: KR

Kind code of ref document: A