WO2015154726A1 - 压缩机及空调器 - Google Patents

压缩机及空调器 Download PDF

Info

Publication number
WO2015154726A1
WO2015154726A1 PCT/CN2015/078115 CN2015078115W WO2015154726A1 WO 2015154726 A1 WO2015154726 A1 WO 2015154726A1 CN 2015078115 W CN2015078115 W CN 2015078115W WO 2015154726 A1 WO2015154726 A1 WO 2015154726A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
stage
primary
partition
disposed
Prior art date
Application number
PCT/CN2015/078115
Other languages
English (en)
French (fr)
Inventor
黄辉
胡余生
魏会军
任丽萍
徐嘉
吴健
杨欧翔
梁社兵
罗惠芳
朱红伟
Original Assignee
珠海格力节能环保制冷技术研究中心有限公司
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=51330864&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2015154726(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by 珠海格力节能环保制冷技术研究中心有限公司 filed Critical 珠海格力节能环保制冷技术研究中心有限公司
Priority to EP15777249.2A priority Critical patent/EP3130807B1/en
Priority to US15/303,096 priority patent/US10465685B2/en
Priority to KR1020167031402A priority patent/KR20170020742A/ko
Priority to JP2017504233A priority patent/JP6246977B2/ja
Publication of WO2015154726A1 publication Critical patent/WO2015154726A1/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
    • 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
    • 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
    • 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
    • F04C23/003—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 having complementary function
    • 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
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • 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
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the invention relates to the field of refrigeration, in particular to a multi-cylinder two-stage reinforced variable-capacity compressor and an air conditioner.
  • Rolling rotor type two-stage compressor is generally a two-cylinder two-stage booster compressor. Due to the limitation of displacement, this compressor needs to use electric auxiliary heat to improve the heat capacity of the compressor under low temperature conditions. Machine displacement, the compressor series needs to be increased, so that the compressor volume increases and the cost increases. In addition, the two-cylinder two-stage booster compressor can not meet the high volume ratio operation and the large displacement and small volume ratio operation of the refrigeration condition.
  • the object of the present invention is to provide a compressor and an air conditioner.
  • the compressor realizes multi-mode operation, and different modes can be selected according to different application occasions, thereby improving heating capacity and increasing rated point and intermediate point.
  • the technical solution of the present invention is as follows:
  • a compressor comprising a first stage cylinder, a second stage cylinder, a second stage cylinder and a lower flange, a first stage cylinder, a second stage cylinder, a second stage cylinder stacking arrangement, adjacent two cylinders a partition is disposed between the second stage cylinder and the second stage cylinder, or the second stage cylinder is placed in the first stage cylinder and Between the second stage cylinders, the lower flange is disposed on a lower side of the first primary cylinder, the second primary cylinder, and the secondary cylinder;
  • the first stage cylinder has a first suction port and a first vane groove, a first sliding piece is disposed in the first sliding piece groove, and the second first stage cylinder has a second suction port and a first a second sliding vane, wherein a second sliding vane is disposed in the second sliding vane, the secondary cylinder has an exhaust port and a third vane slot, and a third sliding vane is disposed in the third vane slot
  • the first stage cylinder and the second stage cylinder are arranged in parallel, and the first stage cylinder and the second stage cylinder connected in parallel are connected in series with the second stage cylinder to enter the first
  • the refrigerant of the suction port and the second suction port is discharged from the exhaust port after being compressed by the first stage or/and the second stage;
  • the two partitions are respectively a first partition and a second partition, and any one or both of the first partition, the second partition and the lower flange are provided with slide control for controlling the action of the slide
  • the device each of the slider control devices corresponding to one of the sliders.
  • the first primary cylinder and the second primary cylinder are both disposed on a lower side of the secondary cylinder, and the first partition or/and the second partition are provided with a slide control device
  • the first stage cylinder or/and the second stage cylinder act as an unloadable cylinder.
  • the first primary cylinder and the second primary cylinder are both disposed on a lower side of the secondary cylinder, and the sliding control device is disposed on the lower flange, the first one The cylinders placed on the lower side of the stage cylinders and the second stage cylinders serve as unloadable cylinders.
  • first baffle or the second baffle is provided with the slide control device, and the cylinders placed on the upper side of the first primary cylinder and the second primary cylinder are unloadable
  • the cylinder or the secondary cylinder acts as an unloadable cylinder.
  • the secondary cylinder is disposed between the first primary cylinder and the second primary cylinder, and the sliding plate is disposed on the first partition or/and the second partition.
  • the secondary cylinder is disposed between the first primary cylinder and the second primary cylinder, the lower flange is provided with the slide control device, the first primary cylinder and The cylinder placed on the lower side of the second stage cylinder serves as an unloadable cylinder.
  • the first baffle control device is disposed on the first baffle or the second baffle, and the cylinders disposed on the upper side of the first primary cylinder and the second primary cylinder are The cylinder or the secondary cylinder is unloaded as an unloadable cylinder.
  • the first primary cylinder and the second primary cylinder are both disposed on an upper side of the secondary cylinder, and the first partition or/and the second partition are disposed on the second partition A slide control device, the first stage cylinder or/and the second stage cylinder as an unloadable cylinder.
  • the first primary cylinder and the second primary cylinder are both disposed on an upper side of the secondary cylinder, and the sliding control device is disposed on the lower flange, the secondary cylinder As a downloadable cylinder.
  • first partition or the second partition is provided with the slide control device, and the first primary cylinder or the second primary cylinder is an unloadable cylinder.
  • the slider control device comprises a pin and an elastic returning element, the elastic restoring element being disposed at a tail of the pin, any one of the first sliding piece, the second sliding piece and the third sliding piece Or any two of them are provided with a locking groove for engaging with the locking groove, when the pin is placed in the locking groove, the sliding piece is locked, and the pin is disengaged from the After the lock groove is locked, the slide is unlocked.
  • 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 compressor has a secondary volume to first volume ratio of 0.3-0.6 or 0.8-1.3 in the two-stage compression mode.
  • the lower flange is provided with an intermediate cavity.
  • an air conditioner including a compressor which is a compressor of any of the above aspects.
  • the compressor and the air conditioner of the invention realize multi-mode operation, and can select different modes according to different application occasions, thereby improving the heating capacity, improving the rated point and the intermediate point, and being free from structural constraints and amplifying the displacement.
  • the two first-stage cylinders can realize the large-displacement compressor without the series limitation;
  • the variable capacity is realized by the change of the working and unloading state of the cylinder, and the energy efficiency and capability under different compressor working conditions are ensured.
  • the requirements can greatly improve the heat production under low-temperature heating conditions, single-cylinder operation can improve the energy efficiency at the intermediate point, and the two-cylinder two-stage increase or double-cylinder operation can improve and guarantee the rated point. Energy efficiency.
  • FIG. 1 to 6 are schematic views showing the structure of a compressor having a variable capacity cylinder according to the present invention.
  • FIG. 7 to FIG. 9 are schematic structural views of the compressor of the present invention in the case where the secondary cylinder is unloadable;
  • FIG. 10 to FIG. 12 are schematic structural views of the compressor of the present invention in a state in which two primary cylinders are unloadable;
  • FIG. 13 to 18 are structural views showing the compressor of the present invention in the case where a primary cylinder and a secondary cylinder can be simultaneously unloaded.
  • an embodiment of the compressor of the present invention includes a first stage cylinder 1, a second stage cylinder 2, a secondary cylinder 3, a lower flange 7, an upper flange 4, and a crankshaft 5, first
  • the first stage cylinder 1, the second stage cylinder 2, the second stage cylinder 3 are stacked, the partition between the adjacent two cylinders is arranged, and the second stage cylinder 3 is placed in the first stage cylinder 1 and the second stage cylinder 2
  • the ipsilateral side, or secondary cylinder 3 is placed between the first stage cylinder 1 and the second stage cylinder 2.
  • the lower flange 7 is placed on the lower side of the first stage cylinder 1, the second stage cylinder 2 and the second stage cylinder 3, the lower flange 7 is provided with the intermediate chamber 8, and the lower end of the lower flange 7 is provided with the lower cover 9 .
  • the first stage cylinder 1 has a first intake port and a first vane slot (not shown), a first vane 11 is disposed in the first vane slot, and the second stage cylinder 2 has a second intake port And a second vane slot (not shown), in the second vane slot, a second vane 21 is provided, the secondary cylinder 3 having an exhaust port and a third vane slot (not shown), in the third slide A third sliding piece 31 is disposed in the groove; the first primary cylinder 1 and the second primary cylinder 2 are arranged in parallel, and the first primary cylinder 1 and the second primary cylinder 2 connected in parallel are connected in series with the secondary cylinder 3 to enter The refrigerant of the first suction port and the second suction port is discharged from the exhaust port after being compressed by the first or second and second stages.
  • the two partitions are respectively a first partition and a second partition, and any one or both of the first partition, the second partition and the lower flange 7 are provided with a slide for controlling the action of the slider
  • the slider control device 6 includes a pin and an elastic returning member, the elastic restoring member is disposed at the tail of the pin, the first slider 11, the second slider 21, and the third slider Any one or both of the 31s are provided with a locking groove for engaging with the locking groove, the sliding piece being locked when the pin is placed in the locking groove, After the pin is disengaged from the lock groove, the slide is unlocked.
  • the resilient return element can be a spring.
  • a first partition or/and a second partition is provided with a through hole corresponding to the lock groove; or the first partition or/and the lower flange is provided with a through hole corresponding to the lock groove; or,
  • the two baffles or/and the lower flange are provided with through holes corresponding to the lock grooves; the pins are placed in the through holes, and the pins are sealingly engaged with the through holes, and the pins are movable in the axial direction of the through holes.
  • the first primary cylinder 1 and the second primary cylinder 2 are both placed on the lower side of the secondary cylinder 3, on the first partition or the second partition.
  • a slide control device 6, a first stage cylinder 1 or a second stage cylinder 2, is provided as an unloadable cylinder.
  • the first stage cylinder 1 and the second stage cylinder 2 are both placed on the lower side of the secondary cylinder 3, and the lower flange 7 is provided with a slider control device 6,
  • the cylinders placed on the lower side of the first-stage cylinder 1 and the second-stage cylinder 2 serve as the unloadable cylinders.
  • the secondary cylinder 3 is placed between the first primary cylinder 1 and the second primary cylinder 2, placed in the first separator and the second separator.
  • the upper partition is provided with a slide control device 6, and the second primary cylinder 2 serves as an unloadable cylinder.
  • the secondary cylinder 3 is disposed between the first primary cylinder 1 and the second primary cylinder 2, and the lower flange 7 is provided with the slider control device 6, the first stage The cylinder (the first stage cylinder 1 in Fig. 4) placed on the lower side of the cylinder 1 and the second stage cylinder 2 serves as an unloadable cylinder.
  • the first primary cylinder 1 and the second primary cylinder 2 are both placed on the upper side of the secondary cylinder 3, on the first partition or the second partition.
  • a slide control device 6, a first stage cylinder 1 or a second stage cylinder 2, is provided as an unloadable cylinder.
  • the second-stage cylinder 2 is an unloadable cylinder.
  • the flow of the refrigerant is shown in the direction of the arrow in the figure.
  • the compressor sucks the refrigerant of the pressure Ps from the liquid separator through the first suction port and the second suction port, and is compressed and discharged into the intermediate chamber 8.
  • the refrigerant discharged from the first-stage cylinder 1 is reinforced by the air supply.
  • the mixed refrigerant After the refrigerant sucked from the flasher is mixed in the intermediate chamber 8, the mixed refrigerant enters the secondary cylinder 3, is compressed by the secondary cylinder 3, and is discharged through the exhaust port to enter a closed chamber, thereby realizing the three-cylinder two-stage. Increased operation, at this time the volume ratio of the secondary to the first stage can achieve 0.3-0.6.
  • the compressor When the second-stage cylinder 2 is unloaded, the compressor sucks the refrigerant of the pressure Ps from the liquid separator through the first suction port, performs first-stage compression through the first-stage cylinder, and then discharges into the intermediate chamber 8, and discharges
  • the refrigerant and the refrigerant sucked from the flash evaporator through the qi and suffocating port are mixed in the intermediate chamber 8, and then mixed into the secondary cylinder 3, and after being compressed by the secondary cylinder 3, the pressure is formed as Pd refrigerant is discharged through the exhaust port, and enters A closed chamber, thus achieving a two-cylinder two-stage enthalpy operation, in which the volume ratio of the secondary to the first stage can be achieved by 0.8-1.3.
  • the first stage cylinder 1 and the second stage cylinder 2 are both placed on the lower side of the secondary cylinder 3, and the first diaphragm or the second partition is provided with slide control.
  • the device 6, the first stage cylinder 1 or/and the second stage cylinder 2 acts as an unloadable cylinder.
  • the secondary cylinder 3 is placed between the first primary cylinder 1 and the second primary cylinder 2, and the first partition and the second partition are placed on the lower side.
  • the partition plate is provided with a slide control device 6, and the secondary cylinder 3 serves as an unloadable cylinder.
  • the first stage cylinder 1 and the second stage cylinder 2 are both placed on the upper side of the secondary cylinder 3, and the lower flange 7 is provided with the slider control device 6, 2
  • the stage cylinder 3 serves as a downloadable cylinder.
  • the secondary cylinder 3 is an unloadable cylinder.
  • the compressor The refrigerant sucking the pressure Ps from the liquid separator through the first suction port and the second suction port is first-stage compressed by the first-stage cylinder 1 and the second-stage cylinder 2, and then discharged into the intermediate chamber 8, the first one After the refrigerant discharged from the stage cylinder 1 and the second stage cylinder 2 is mixed with the refrigerant sucked from the flasher through the air supply suffocating port, the mixed refrigerant enters the secondary cylinder 3 through the secondary cylinder.
  • 3 Compression is discharged through the exhaust port and enters a closed chamber, thereby achieving a three-cylinder two-stage boosting operation. At this time, the volume ratio of the second stage to the first stage can be realized by
  • the compressor When the secondary cylinder 3 is unloaded, the compressor sucks the refrigerant of the pressure Ps from the liquid separator through the first suction port and the second suction port, and is compressed by the first stage cylinder 1 and the second stage cylinder 2
  • the Pd refrigerant is discharged into the intermediate chamber 8, and then subjected to the secondary compression by the secondary cylinder 3, and then discharged from the exhaust port to enter a closed chamber, thereby realizing the two-cylinder operation.
  • the three-cylinder two-stage reinforced variable-capacity compressor can simultaneously unload the first-stage cylinder 1 and the second-stage cylinder 2 as follows:
  • the first stage cylinder 1 and the second stage cylinder 2 are both placed on the lower side of the secondary cylinder 3, and the lower flange 7 is provided with a slider control device 6,
  • the cylinder placed on the lower side of the first-stage cylinder 1 and the second-stage cylinder 2 (the first-stage cylinder 1 in the figure) is an unloadable cylinder; the first partition (the first-stage cylinder 1 in the figure)
  • a slide control device 6 is also disposed on the partition between the second-stage cylinders 2, and the cylinders on the upper side of the first-stage cylinder 1 and the second-stage cylinder 2 (the second-stage cylinder in the figure) 2) As an unloadable cylinder.
  • the secondary cylinder 3 is disposed between the first primary cylinder 1 and the second primary cylinder 2, and the lower flange 7 is provided with the slider control device 6, the first stage
  • the cylinder placed on the lower side of the cylinder 1 and the second stage cylinder 2 serves as an unloadable cylinder; the second partition (the partition between the second stage cylinder 2 and the secondary cylinder 3 in the figure) is also provided with slippage.
  • the sheet control device 6, the cylinders placed on the upper side of the first stage cylinder 1 and the second stage cylinder 2 (the second stage cylinder 2 in the drawing) also function as an unloadable cylinder.
  • the first stage cylinder 1 and the second stage cylinder 2 are both placed on the upper side of the secondary cylinder 3, and the first partition and the second partition are provided with slides.
  • the control device 6, the first primary cylinder 1 and the second primary cylinder 2 serve as an unloadable cylinder.
  • the first primary cylinder 1 and the second primary cylinder 2 are unloadable cylinders.
  • the refrigerant flows toward the direction of the arrow in the figure, and the compressor draws the pressure Ps from the liquid separator through the first suction port 11 and the second suction port.
  • the refrigerant is compressed by the first stage cylinder 1 and the second stage cylinder 2 and discharged into the intermediate chamber 8.
  • the refrigerant discharged from the first stage cylinder 1 and the second stage cylinder 2 is passed through the venting port.
  • the volume ratio of the stage to the first stage can be achieved by 0.3-0.6.
  • the compressor draws the refrigerant of the pressure Ps from the liquid separator through the first suction port, and is compressed by the first stage cylinder 1 to form a Pd.
  • the refrigerant is discharged into the intermediate chamber 8, and the refrigerant discharged from the first-stage cylinder 1 and the refrigerant sucked from the flash evaporator through the air-filling port are mixed in the intermediate chamber 8, and after mixing, enter the secondary cylinder 3, and pass through the secondary cylinder.
  • the Pd refrigerant is discharged through the exhaust port and enters a closed chamber, thereby realizing the two-stage two-stage enthalpy operation.
  • the volume ratio of the second stage to the first stage can be realized by 0.8-1.3.
  • the compressor sucks the refrigerant of the pressure Ps from the liquid separator through the second suction port, and is compressed by the second stage cylinder 2 to form a Pd.
  • the refrigerant is discharged into the intermediate chamber 8, and the refrigerant discharged from the second-stage cylinder 2 is mixed with the refrigerant sucked from the flash evaporator through the qi-enhanced vent, and is mixed into the secondary cylinder 3 through the secondary cylinder 3
  • Pd refrigerant is discharged through the exhaust port and enters a closed chamber, thereby realizing a two-cylinder two-stage enthalpy operation.
  • the volume ratio of the second stage to the first stage can be 0.8-1.3.
  • the compressor draws the refrigerant of the pressure Ps from the liquid separator through the first suction port and the second suction port, and passes through the first stage cylinder. 1 and the second stage cylinder 2, and the intermediate chamber 8, and then enter the secondary cylinder 3, after being compressed by the secondary cylinder 3, the Pd refrigerant is discharged through the exhaust port and enters a closed chamber, thereby achieving single cylinder operation.
  • the three-cylinder two-stage reinforced variable-capacity compressor can simultaneously unload one primary cylinder and one secondary cylinder as follows:
  • the first primary cylinder 1 and the second primary cylinder 2 are both placed on the lower side of the secondary cylinder 3, and the first partition and the second partition are provided with slides.
  • the control device 6, the first stage cylinder 1 or/and the second stage cylinder 2 serves as an unloadable cylinder.
  • the first stage cylinder 1 and the second stage cylinder 2 are both placed on the lower side of the secondary cylinder 3, and the lower flange 7 is provided with a slider control device 6,
  • the cylinder placed on the lower side of the first stage cylinder 1 and the second stage cylinder 2 serves as the unloadable cylinder;
  • the second partition (the second stage cylinder 3 and the second in the figure)
  • a slide control device 6 is also provided on the partition between the primary cylinders 1, and the secondary cylinder 3 also serves as an unloadable cylinder.
  • the secondary cylinder 3 is disposed between the first primary cylinder 1 and the second primary cylinder 2, and the lower flange 7 is provided with the slider control device 6, the first stage A cylinder placed on the lower side of the cylinder 1 and the second stage cylinder 2 serves as an unloadable cylinder; and a slide control device is also disposed on the second partition (a partition between the first stage cylinder 1 and the secondary cylinder 3) 6.
  • the secondary cylinder 3 also acts as an unloadable cylinder.
  • the secondary cylinder 3 is disposed between the first primary cylinder 1 and the second primary cylinder 2, and the first diaphragm and the second diaphragm are each provided with a slider control.
  • the first stage cylinder 1 and the second stage cylinder 2 are both placed on the upper side of the secondary cylinder 3, and the slide control device is disposed on the lower flange 7. 6.
  • the secondary cylinder 3 serves as a downloadable cylinder; the first partition or the second partition is also provided with a slide control device 6, and the first primary cylinder 1 or the second primary cylinder 2 also serves as an unloadable cylinder.
  • the second primary cylinder 2 and the secondary cylinder 3 are unloadable cylinders.
  • the compressor sucks the refrigerant of the pressure Ps from the liquid separator through the first suction port and the second suction port, After being compressed by the first-stage cylinder 1 and the second-stage cylinder 2, the refrigerant is discharged into the intermediate chamber 8, and the refrigerant discharged from the first-stage cylinder 1 and the second-stage cylinder 2 is sucked from the flash evaporator through the venting port.
  • the refrigerant is mixed in the intermediate chamber 8, and after mixing, it enters the secondary cylinder 3. After being compressed by the secondary cylinder 3, it is discharged through the exhaust port and enters a closed chamber, thereby realizing the three-cylinder two-stage enhanced operation.
  • the volume ratio to the first stage can be achieved by 0.3-0.6.
  • the compressor draws the refrigerant of the pressure Ps through the first suction port 11 and compresses the first stage cylinder 1 to form a Pd refrigerant discharge.
  • the intermediate chamber 8 is configured such that the refrigerant discharged from the first stage cylinder 1 and the refrigerant sucked from the flash unit through the venting port are in the intermediate chamber 8. After mixing and mixing, it enters the secondary cylinder 3, and after being compressed by the secondary cylinder 3, the Pd refrigerant is discharged through the exhaust port and enters a closed chamber, thereby realizing the two-cylinder two-stage enhanced operation, and the secondary and first-stage volume at this time
  • the ratio can be achieved by 0.8-1.3.
  • the compressor draws the refrigerant of the pressure Ps from the liquid separator through the first suction port and the second suction port, and passes through the first stage cylinder 1
  • the second-stage cylinder 2 is discharged into the intermediate chamber 8, and then discharged through the exhaust port through the secondary cylinder 3 to enter a closed chamber, thereby realizing the two-cylinder operation.
  • the compressor sucks the refrigerant of the pressure Ps from the liquid separator through the first suction port, is compressed by the first stage cylinder, and is discharged into the intermediate chamber 8, and then After passing through the secondary cylinder 3, it is discharged through the exhaust port and enters a closed chamber, thereby achieving a single operation.
  • 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 above compressor, it will not be further described herein.
  • the compressor realizes multi-mode operation, and different modes can be selected according to different application occasions, thereby improving the heating capacity, improving the rated point and the intermediate point, without structural limitation, and amplifying the displacement. , thereby reducing the volume of the compressor and reducing the cost; the two primary cylinders can realize the large displacement compressor without the series limitation; the variable capacity is realized by the change of the working and unloading state of the cylinder, and the energy efficiency under different compressor conditions is ensured.
  • Capability requirements such as three-cylinder two-stage operation, can greatly improve the heat production under low-temperature heating conditions, single-cylinder operation can improve the energy efficiency at the intermediate point, and the two-cylinder two-stage or two-cylinder operation can improve and guarantee the rated capacity. Point of energy efficiency.

Landscapes

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

Abstract

一种压缩机，包括叠放设置的第一一级气缸（1）、第二一级气缸（2）和二级气缸（3），相邻的两气缸之间设置隔板；第一一级气缸（1）设置第一吸气口，第二一级气缸（2）设置第二吸气口，二级气缸（3）设置排气口；第一一级气缸（1）和第二一级气缸（2）并联设置，并联后的第一一级气缸（1）和第二一级气缸（2）与二级气缸（3）串联，进入第一吸气口和第二吸气口的冷媒经一级或/和二级压缩后从排气口排出；两个隔板分别为第一隔板和第二隔板，第一隔板、第二隔板和下法兰中的任一个或任意两个设有滑片控制装置。具有该压缩机的空调器。该压缩机实现多模式运行，根据不同的运用场合选择不同模式，提高制热能力，提高额定点和中间点的能力。

Description

压缩机及空调器 技术领域
本发明涉及制冷领域，尤其涉及一种多缸双级增焓变容压缩机及空调器。
背景技术
滚动转子式双级压缩机一般为双缸双级增焓压缩机,此压缩机因受排量的限制，在低温工况下需采用电辅热来提高压缩机的制热量，如要增加压缩机排量，需增大压缩机系列，从而使压缩机体积增大，成本上升。另外双缸双级增焓压缩机无法满足制冷工况高容积比运行和制冷工况大排量小容积比运行。
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及空调器，压缩机实现多模式运行，可根据不同的运用场合选择不同模式，从而提高制热能力，提高额定点和中间点的能力。为实现上述目的，本发明的技术方案如下：
一种压缩机，包括第一一级气缸、第二一级气缸、二级气缸和下法兰，第一一级气缸、第二一级气缸、二级气缸叠放设置，相邻的两气缸之间设置隔板，所述二级气缸置于所述第一一级气缸和所述第二一级气缸的同侧，或所述二级气缸置于所述第一一级气缸和所述第二一级气缸之间，所述下法兰置于所述第一一级气缸、所述第二一级气缸和所述二级气缸的下侧；
所述第一一级气缸具有第一吸气口和第一滑片槽，在所述第一滑片槽内设置第一滑片，所述第二一级气缸具有第二吸气口和第二滑片槽，在所述第二滑片槽内设置第二滑片，所述二级气缸具有排气口和第三滑片槽，在所述第三滑片槽内设置第三滑片；所述第一一级气缸和所述第二一级气缸并联设置，并联后的所述第一一级气缸和所述第二一级气缸与所述二级气缸串联，进入所述第一吸气口和所述第二吸气口的冷媒经一级或/和二级压缩后从所述排气口排出；
两个所述隔板分别为第一隔板和第二隔板，第一隔板、第二隔板和下法兰中的任意一个或任意两个设置有用于控制滑片动作的滑片控制装置，每个所述滑片控制装置对应一个所述滑片。
较优地，所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的下侧，所述第一隔板或/和第二隔板上设置滑片控制装置，所述第一一级气缸或/和所述第二一级气缸作为可卸载气缸。
较优地，所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的下侧，所述下法兰上设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于下侧的气缸作为可卸载气缸。
进一步地，所述第一隔板或所述第二隔板上设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于上侧的气缸作为可卸载气缸或所述二级气缸作为可卸载气缸。
较优地，所述二级气缸置于所述第一一级气缸和所述第二一级气缸之间，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，所述第一一级气缸或/和所述二级气缸作为可卸载气缸，或者，所述第二一级气缸或/和所述二级气缸作为可卸载气缸。
较优地，所述二级气缸置于所述第一一级气缸和所述第二一级气缸之间，所述下法兰设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于下侧的气缸作为可卸载气缸。
较优地，所述第一隔板或所述第二隔板上设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于上侧的气缸作为可卸载气缸或所述二级气缸作为可卸载气缸。
较优地，所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的上侧，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，所述第一一级气缸或/和所述第二一级气缸作为可卸载气缸。
较优地，所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的上侧，所述下法兰上设置所述滑片控制装置，所述二级气缸作为可下载气缸。
进一步地，所述第一隔板或所述第二隔板设置所述滑片控制装置，所述第一一级气缸或所述第二一级气缸作为可卸载气缸。
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、第二滑片和第三滑片中的任一个或任意两个设有止锁槽，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内时，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。
较优地，所述压缩机在双级压缩模式下，二级容积与一级容积比为0.3-0.6或0.8-1.3。
较优地，所述下法兰设置有中间腔。
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：
本发明的压缩机及空调器，压缩机实现多模式运行，可根据不同的运用场合选择不同模式，从而提高制热能力，提高额定点和中间点的能力，不受结构限制，放大排量，从而缩小压缩机体积，降低成本；两个一级气缸可不受系列限制实现大排量压缩机；通过气缸的工作与卸载状态的改变而实现变容，保证不同压缩机工况下的能效和能力的要求，如三缸双级增焓运行，可大大提高低温制热情况下的制热量，单缸运行可提高中间点的能效，双缸双级增焓或双缸运行可提高及保证额定点的能效。
附图说明
图1-图6为本发明的压缩机具有一个可变容气缸的结构示意图；
图7-图9为本发明的压缩机在二级气缸可卸载情形下的结构示意图；
图10-图12为本发明的压缩机在两个一级气缸可卸载情形下的结构示意图；
图13-图18为本发明的压缩机在一个一级气缸和一个二级气缸可同时卸载情形下的结构示意图。
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以三缸转子压缩机为例对本发明的压缩机及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18，本发明的压缩机一实施例包括第一一级气缸1、第二一级气缸2、二级气缸3、下法兰7、上法兰4和曲轴5，第一一级气缸1、第二一级气缸2、二级气缸3叠放设置，相邻的两气缸之间设置隔板，二级气缸3置于第一一级气缸1和第二一级气缸2的同侧，或二级气缸3置于第一一级气缸1和第二一级气缸2之间。下法兰7置于第一一级气缸1、第二一级气缸2和二级气缸3的下侧，下法兰7设置有中间腔8，下法兰7的下端部设置下盖板9。
第一一级气缸1具有第一吸气口和第一滑片槽(未示出)，在第一滑片槽内设置第一滑片11，第二一级气缸2具有第二吸气口和第二滑片槽(未示出)，在第二滑片槽内设置第二滑片21，二级气缸3具有排气口和第三滑片槽(未示出)，在第三滑片槽内设置第三滑片31；第一一级气缸1和第二一级气缸2并联设置，并联后的第一一级气缸1和第二一级气缸2与二级气缸3串联，进入所述第一吸气口和所述第二吸气口的冷媒经一级或/和二级压缩后从所述排气口排出。
两个所述隔板分别为第一隔板和第二隔板，第一隔板、第二隔板和下法兰7中的任意一个或任意两个设置有用于控制滑片动作的滑片控制装置6，每个滑片控制装置6对应一个所述滑片。
作为一种可实施方式，滑片控制装置6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11、第二滑片21和第三滑片31中的任一个或任意两个设有止锁槽，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内时，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。弹性复位元件可为弹簧。
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/和下法兰设置有与止锁槽相对应的通孔；销钉置于通孔中，销钉与通孔密封配合，销钉能够在所述通孔的轴向方向移动。
实施例一
三缸双级增焓变容压缩机可卸载其中一个一级缸的情形如下：
作为一种可实施方式，如图1或图7所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的下侧，第一隔板或第二隔板上设置滑片控制装置6，第一一级气缸1或第二一级气缸2作为可卸载气缸。
作为一种可实施方式，如图2所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的下侧，下法兰7上设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于下侧的气缸(图2中为第一一级气缸1)作为可卸载气缸。
作为一种可实施方式，如图3和图8所示，二级气缸3置于第一一级气缸1和第二一级气缸2之间，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6，第二一级气缸2作为可卸载气缸。
作为一种可实施方式，如图4所示，二级气缸3置于第一一级气缸1和第二一级气缸2之间，下法兰7设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于下侧的气缸(图4中为第一一级气缸1)作为可卸载气缸。
作为一种可实施方式，如图5和图6所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的上侧，第一隔板或第二隔板上设置滑片控制装置6，第一一级气缸1或第二一级气缸2作为可卸载气缸。
以图1为例对可卸载一个低压缸的情形进行描述，图1中第二一级气缸2为可卸载缸，当第二一级气缸2正常工作时，冷媒流向如图中箭头方向所示，压缩机通过第一吸气口和第二吸气口从分液器吸入压力Ps的冷媒，经压缩后排入中间腔8，第一一级气缸1排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔8内进行混合后，混合后的冷媒进入二级气缸3，经二级气缸3压缩后通过排气口排出，进入一个密闭腔，从而实现三缸双级增焓运行，此时二级与一级的容积比可实现0.3-0.6。
当第二一级气缸2卸载不工作时，压缩机通过第一吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸进行一级压缩后排入中间腔8，排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔8内进行混合后，混合后进入二级气缸3，经二级气缸3压缩后形成压力为Pd冷媒通过排气口排出，进入一个密闭腔，从而实现双缸双级增焓运行，此时二级与一级的容积比可实现0.8-1.3。
实施例二
三缸双级增焓变容压缩机可卸载二级气缸的情形如下：
作为一种可实施，如图7所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的下侧，第一隔板或第二隔板上设置滑片控制装置6，第一一级气缸1或/和第二一级气缸2作为可卸载气缸。
作为一种可实施方式，如图8所示，二级气缸3置于第一一级气缸1和第二一级气缸2之间，第一隔板和第二隔板中置于下侧的隔板设置滑片控制装置6，二级气缸3作为可卸载气缸。
作为一种可实施方式，如图9所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的上侧，下法兰7上设置滑片控制装置6，二级气缸3作为可下载气缸。
以图7为例对可卸载二级气缸3的情形进行描述，图7中二级气缸3为可卸载缸，当二级气缸3正常工作时，冷媒流向如图中箭头方向所示，压缩机通过第一吸气口和第二吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸1和第二一级气缸2进行一级压缩后排入中间腔8，第一一级气缸1和第二一级气缸2排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔8内进行混合后，混合后的冷媒进入二级气缸3，经二级气缸3压缩通过排气口排出，进入一个密闭腔，从而实现三缸双级增焓运行，此时二级与一级的容积比可实现0.8-1.3。
当二级气缸3卸载不工作时，压缩机通过第一吸气口和第二吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸1和第二一级气缸2压缩后形成Pd冷媒排入中间腔8，然后经二级气缸3进行二级压缩后由排气口排出，进入一个密闭腔，从而实现双缸运行。
实施例三
三缸双级增焓变容压缩机可同时卸载第一一级气缸1和第二一级气缸2的情形如下：
作为一种可实施方式，如图10所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的下侧，下法兰7上设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于下侧的气缸(图中为第一一级气缸1)为可卸载气缸；第一隔板(图中为第一一级气缸1与第二一级气缸2之间的隔板)上也设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于上侧的气缸(图中为第二一级气缸2)作为可卸载气缸。
作为一种可实施方式，如图11所示，二级气缸3置于第一一级气缸1和第二一级气缸2之间，下法兰7设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于下侧的气缸作为可卸载气缸；第二隔板(图中为第二一级气缸2与二级气缸3之间的隔板)上也设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于上侧的气缸(图中为第二一级气缸2)也作为可卸载气缸。
作为一种可实施方式，如图12所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的上侧，第一隔板和第二隔板上设置滑片控制装置6，第一一级气缸1和第二一级气缸2作为可卸载气缸。
以图10为例对可同时卸载两个低压缸的情形进行描述，图10中，第一一级气缸1和第二一级气缸2为可卸载缸。当第一一级气缸1和第二一级气缸2正常工作时，冷媒流向如图中箭头方向所示，压缩机通第一吸气口11和第二吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸1和第二一级气缸2压缩后排入中间腔8，第一一级气缸1和第二一级气缸2排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔8进行混合后，进入二级气缸3，经二级气缸3压缩后通排气口排出，进入一个密闭腔，从而实现三缸双级增焓运行，此时二级与一级的容积比可实现0.3-0.6。
当第二一级气缸2卸载不工作，第一一级气缸1正常工作时，压缩机通过第一吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸1压缩后形成Pd冷媒排入中间腔8，第一一级气缸1排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔8内进行混合，混合后进入二级气缸3，经二级气缸3压缩后形成Pd冷媒通过排气口排出，进入一个密闭腔，从而实现双缸双级增焓运行，此时二级与一级的容积比可实现0.8-1.3。
当第一一级气缸1卸载不工作、第二一级气缸2正常工作时，压缩机通过第二吸气口从分液器吸入压力Ps的冷媒，经第二一级气缸2压缩后形成Pd冷媒排入中间腔8，第二一级气缸2排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔内进行混合，混合后进入二级气缸3，经二级气缸3压缩后形成Pd冷媒通过排气口排出，进入一个密闭腔，从而实现双缸双级增焓运行，此时二级与一级的容积比可实现0.8-1.3。
当第一一级气缸1和第二一级气缸2均卸载不工作时，压缩机通过第一吸气口和第二吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸1和第二一级气缸2，以及中间腔8，后进入二级气缸3，经二级气缸3压缩后形成Pd冷媒通过排气口排出，进入一个密闭腔，从而实现单缸运行。
实施例四
三缸双级增焓变容压缩机可同时卸载一个一级气缸和一个二级气缸的情形如下：
作为一种可实施方式，如图13所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的下侧，第一隔板和第二隔板上设置滑片控制装置6，第一一级气缸1或/和第二一级气缸2作为可卸载气缸。
作为一种可实施方式，如图14所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的下侧，下法兰7上设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于下侧的气缸(图中为第一一级气缸1)作为可卸载气缸；第二隔板(图中为二级气缸3与第二一级气缸1之间的隔板)上也设置滑片控制装置6，二级气缸3也作为可卸载气缸。
作为一种可实施方式，如图15所示，二级气缸3置于第一一级气缸1和第二一级气缸2之间，下法兰7设置滑片控制装置6，第一一级气缸1和第二一级气缸2中置于下侧的气缸作为可卸载气缸；第二隔板(第一一级气缸1与二级气缸3之间的隔板)上也设置滑片控制装置6，二级气缸3也作为可卸载气缸。
作为一种可实施方式，如图16所示，二级气缸3置于第一一级气缸1和第二一级气缸2之间，第一隔板和第二隔板上均设置滑片控制装置6，第一一级气缸1和第二一级气缸2均作为可卸载气缸。
作为一种可实施方式，如图17和图18所示，第一一级气缸1和第二一级气缸2均置于二级气缸3的上侧，下法兰7上设置滑片控制装置6，二级气缸3作为可下载气缸；第一隔板或第二隔板也设置滑片控制装置6，第一一级气缸1或第二一级气缸2也作为可卸载气缸。
以图13为例对可同时卸载一个一级气缸和一个二级气缸的情形进行描述，图10中，第二一级气缸2和二级气缸3为可卸载缸。当第二一级气缸2和二级气缸3正常工作时，冷媒流向如图中箭头方向所示，压缩机通过第一吸气口和第二吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸1和第二一级气缸2压缩后排入中间腔8，第一一级气缸1和第二一级气缸2排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔8内进行混合，混合后进入二级气缸3，经二级气缸3压缩后通过排气口排出，进入一个密闭腔，从而实现三缸双级增焓运行，此时二级与一级的容积比可实现0.3-0.6。
当第二一级气缸2卸载不工作、二级气缸3正常工作时，压缩机通过第一吸气口11液器吸入压力Ps的冷媒，经第一一级气缸1压缩后形成Pd冷媒排入中间腔8，第一一级气缸1排出后的冷媒与通过补气增焓口从闪蒸器吸入的冷媒在中间腔8内进行 混合，混合后进入二级气缸3，经二级气缸3压缩后形成Pd冷媒通过排气口排出，进入一个密闭腔，从而实现双缸双级增焓运行，此时二级与一级的容积比可实现0.8-1.3。
当二级气缸3卸载不工作、第二一级气缸2正常工作时，压缩机通过第一吸气口和第二吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸1和第二一级气缸2压缩后排入中间腔8，再经二级气缸3后通过排气口排出，进入一个密闭腔，从而实现双缸运行。
当第二一级气缸2和二级气缸3卸载不工作时，压缩机通过第一吸气口从分液器吸入压力Ps的冷媒，经第一一级气缸压缩后排入中间腔8，再经二级气缸3后通过排气口排出，进入一个密闭腔，从而实现单运行。
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，由于空调器除上述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及空调器，压缩机实现多模式运行，可根据不同的运用场合选择不同模式，从而提高制热能力，提高额定点和中间点的能力，不受结构限制，放大排量，从而缩小压缩机体积，降低成本；两个一级气缸可不受系列限制实现大排量压缩机；通过气缸的工作与卸载状态的改变而实现变容，保证不同压缩机工况下的能效和能力的要求，如三缸双级增焓运行，可大大提高低温制热情况下的制热量，单缸运行可提高中间点的能效，双缸双级增焓或双缸运行可提高及保证额定点的能效。
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 (17)

  1. 一种压缩机，其特征在于：
    包括第一一级气缸、第二一级气缸、二级气缸和下法兰，第一一级气缸、第二一级气缸、二级气缸叠放设置，相邻的两气缸之间设置隔板，所述二级气缸置于所述第一一级气缸和所述第二一级气缸的同侧，或所述二级气缸置于所述第一一级气缸和所述第二一级气缸之间，所述下法兰置于所述第一一级气缸、所述第二一级气缸和所述二级气缸的下侧；
    所述第一一级气缸具有第一吸气口和第一滑片槽，在所述第一滑片槽内设置第一滑片，所述第二一级气缸具有第二吸气口和第二滑片槽，在所述第二滑片槽内设置第二滑片，所述二级气缸具有排气口和第三滑片槽，在所述第三滑片槽内设置第三滑片；所述第一一级气缸和所述第二一级气缸并联设置，并联后的所述第一一级气缸和所述第二一级气缸与所述二级气缸串联，进入所述第一吸气口和所述第二吸气口的冷媒经一级或/和二级压缩后从所述排气口排出；
    两个所述隔板分别为第一隔板和第二隔板，第一隔板、第二隔板和下法兰中的任意一个或任意两个设置有用于控制滑片动作的滑片控制装置，每个所述滑片控制装置对应一个所述滑片。
  2. 根据权利要求1所述的压缩机，其特征在于：
    所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的下侧，所述第一隔板或/和第二隔板上设置滑片控制装置，所述第一一级气缸或/和所述第二一级气缸作为可卸载气缸。
  3. 根据权利要求1所述的压缩机，其特征在于：
    所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的下侧，所述下法兰上设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于下侧的气缸作为可卸载气缸。
  4. 根据权利要求3所述的压缩机，其特征在于：
    所述第一隔板或所述第二隔板上设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于上侧的气缸作为可卸载气缸或所述二级气缸作为可卸载气缸。
  5. 根据权利要求1所述的压缩机，其特征在于：
    所述二级气缸置于所述第一一级气缸和所述第二一级气缸之间，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，所述第一一级气缸或/和所述二级气缸作为可卸载气缸，或者，所述第二一级气缸或/和所述二级气缸作为可卸载气缸。
  6. 根据权利要求1所述的压缩机，其特征在于：
    所述二级气缸置于所述第一一级气缸和所述第二一级气缸之间，所述下法兰设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于下侧的气缸作为可卸载气缸。
  7. 根据权利要求6所述的压缩机，其特征在于：
    所述第一隔板或所述第二隔板上设置所述滑片控制装置，所述第一一级气缸和所述第二一级气缸中置于上侧的气缸作为可卸载气缸或所述二级气缸作为可卸载气缸。
  8. 根据权利要求1所述的压缩机，其特征在于：
    所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的上侧，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，所述第一一级气缸或/和所述第二一级气缸作为可卸载气缸。
  9. 根据权利要求1所述的压缩机，其特征在于：
    所述第一一级气缸和所述第二一级气缸均置于所述二级气缸的上侧，所述下法兰上设置所述滑片控制装置，所述二级气缸作为可下载气缸。
  10. 根据权利要求9所述的压缩机，其特征在于：
    所述第一隔板或所述第二隔板设置所述滑片控制装置，所述第一一级气缸或所述第二一级气缸作为可卸载气缸。
  11. 根据权利要求1-10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、第二滑片和第三滑片中的任一个或任意两个设有止锁槽，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内时，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。
  12. 根据权利要求11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。
  13. 根据权利要求1-10任一项所述的压缩机，其特征在于：
    所述压缩机在双级压缩模式下，二级容积与一级容积比为0.3-0.6或0.8-1.3。
  14. 根据权利要求1-10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。
  15. 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1-14任一项所述的压缩机。
  16. 一种压缩机，其特征在于：
    包括第一一级气缸、第二一级气缸、二级气缸和下法兰，第一一级气缸、第二一级气缸、二级气缸叠放设置，相邻的两气缸之间设置隔板，所述二级气缸置于所述第一一级气缸和所述第二一级气缸的同侧，或所述二级气缸置于所述第一一级气缸和所述第二一级气缸之间，所述下法兰置于所述第一一级气缸、所述第二一级气缸和所述二级气缸的下侧。
  17. 根据权利要求16所述的压缩机，其特征在于：所述第一一级气缸具有第一吸气口和第一滑片槽，在所述第一滑片槽内设置第一滑片，所述第二一级气缸具有第二吸气口和第二滑片槽，在所述第二滑片槽内设置第二滑片，所述二级气缸具有排气口和第三滑片槽，在所述第三滑片槽内设置第三滑片；所述第一一级气缸和所述第二一级气缸并联设置，并联后的所述第一一级气缸和所述第二一级气缸与所述二级气缸串联，进入所述第一吸气口和所述第二吸气口的冷媒经一级或/和二级压缩后从所述排气口排出。
PCT/CN2015/078115 2014-04-10 2015-04-30 压缩机及空调器 WO2015154726A1 (zh)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP15777249.2A EP3130807B1 (en) 2014-04-10 2015-04-30 Compressor and air conditioner
US15/303,096 US10465685B2 (en) 2014-04-10 2015-04-30 Air conditioner with stacked parallel and serial compressor cylinders
KR1020167031402A KR20170020742A (ko) 2014-04-10 2015-04-30 압축기 및 에어컨
JP2017504233A JP6246977B2 (ja) 2014-04-10 2015-04-30 圧縮機及びエアコン

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410144072.3 2014-04-10
CN201410144072.3A CN103953545B (zh) 2014-04-10 2014-04-10 压缩机及空调器

Publications (1)

Publication Number Publication Date
WO2015154726A1 true WO2015154726A1 (zh) 2015-10-15

Family

ID=51330864

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/078115 WO2015154726A1 (zh) 2014-04-10 2015-04-30 压缩机及空调器

Country Status (6)

Country Link
US (1) US10465685B2 (zh)
EP (1) EP3130807B1 (zh)
JP (1) JP6246977B2 (zh)
KR (1) KR20170020742A (zh)
CN (1) CN103953545B (zh)
WO (1) WO2015154726A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018531347A (ja) * 2015-11-23 2018-10-25 グリー エレクトリック アプライアンスィズ，インコーポレーテッド オブ ジュハイ 多シリンダ２段式ｅｖｉ圧縮機および空気調和装置、ヒートポンプ給湯機ならびに制御方法

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
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
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
CN105201838A (zh) * 2015-10-28 2015-12-30 珠海格力节能环保制冷技术研究中心有限公司 转子压缩机
CN105736377A (zh) * 2016-04-11 2016-07-06 珠海格力节能环保制冷技术研究中心有限公司 一种压缩机结构
CN107956687B (zh) * 2017-10-10 2024-01-26 珠海凌达压缩机有限公司 压缩机及其运行控制方法、空调器
CN108506213A (zh) * 2018-05-25 2018-09-07 珠海格力节能环保制冷技术研究中心有限公司 压缩机及空调系统
CN110630503B (zh) * 2018-06-25 2024-06-28 上海海立电器有限公司 压缩机及其排气结构与排气方法
CN109026697A (zh) * 2018-08-03 2018-12-18 天津商业大学 三缸双级滑槽平行布置的滚动转子压缩机
CN109026692B (zh) * 2018-08-27 2024-05-14 珠海凌达压缩机有限公司 一种多缸泵体结构及压缩机
CN109113996B (zh) * 2018-10-12 2023-03-10 珠海凌达压缩机有限公司 一种旋转式压缩机、制冷系统及具有其的空调器
CN109113994A (zh) * 2018-10-29 2019-01-01 珠海格力节能环保制冷技术研究中心有限公司 泵体组件、变容压缩机、空气调节系统
CN109519379B (zh) * 2018-12-12 2024-10-01 珠海凌达压缩机有限公司 一种压缩机及包括该压缩机的电器
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
CN110159532B (zh) * 2019-06-21 2024-10-18 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
CN115750353B (zh) * 2022-11-19 2023-07-28 上海阿波罗机械股份有限公司 一种屏蔽多级自冷却式压缩机

Citations (7)

* 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
JPH05106576A (ja) * 1991-08-05 1993-04-27 Daikin Ind Ltd 多気筒密閉形回転圧縮機
US5871342A (en) * 1997-06-09 1999-02-16 Ford Motor Company Variable capacity rolling piston compressor
CN1950611A (zh) * 2004-06-15 2007-04-18 东芝开利株式会社 多缸旋转式压缩机
CN103953545A (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 压缩机及空调器
CN203809296U (zh) * 2014-04-10 2014-09-03 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

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2957426A (en) * 1956-12-17 1960-10-25 Ralph C Miller Series-parallel pump
JPS516576A (ja) 1974-07-05 1976-01-20 Citizen Watch Co Ltd Keitaidokei
JPS5190792A (en) 1975-02-08 1976-08-09 Eaa taorutsukijidokaiheikyabinetsuto
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
JPH051686A (ja) * 1991-06-27 1993-01-08 Daikin Ind Ltd 多気筒回転圧縮機
JP2003328972A (ja) * 2002-05-09 2003-11-19 Hitachi Home & Life Solutions Inc 密閉形２シリンダロータリ圧縮機及びその製造方法
JP4045154B2 (ja) * 2002-09-11 2008-02-13 日立アプライアンス株式会社 圧縮機
JP4797715B2 (ja) * 2006-03-09 2011-10-19 ダイキン工業株式会社 冷凍装置
JP5070097B2 (ja) * 2007-08-28 2012-11-07 東芝キヤリア株式会社 ２シリンダ回転式圧縮機およびこれを用いた冷凍サイクル装置
EP2295720B1 (en) * 2008-05-19 2016-01-27 Panasonic Intellectual Property Management Co., Ltd. Two-stage rotary expander, expander-integrated compressor, and refrigeration cycle device
US20140094727A1 (en) * 2012-09-28 2014-04-03 Covidien Lp Compression device pumping
DE102012112720B4 (de) * 2012-12-20 2017-01-12 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pumpe
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
CN103954064B (zh) * 2014-04-15 2016-04-13 珠海格力电器股份有限公司 制冷装置

Patent Citations (7)

* 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
JPH05106576A (ja) * 1991-08-05 1993-04-27 Daikin Ind Ltd 多気筒密閉形回転圧縮機
US5871342A (en) * 1997-06-09 1999-02-16 Ford Motor Company Variable capacity rolling piston compressor
CN1950611A (zh) * 2004-06-15 2007-04-18 东芝开利株式会社 多缸旋转式压缩机
CN103953545A (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 压缩机及空调器
CN203809296U (zh) * 2014-04-10 2014-09-03 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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3130807A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018531347A (ja) * 2015-11-23 2018-10-25 グリー エレクトリック アプライアンスィズ，インコーポレーテッド オブ ジュハイ 多シリンダ２段式ｅｖｉ圧縮機および空気調和装置、ヒートポンプ給湯機ならびに制御方法

Also Published As

Publication number Publication date
US20170030355A1 (en) 2017-02-02
EP3130807A1 (en) 2017-02-15
JP6246977B2 (ja) 2017-12-13
EP3130807B1 (en) 2019-03-06
EP3130807A4 (en) 2018-03-28
CN103953545A (zh) 2014-07-30
US10465685B2 (en) 2019-11-05
JP2017514066A (ja) 2017-06-01
KR20170020742A (ko) 2017-02-24
CN103953545B (zh) 2016-01-27

Similar Documents

Publication Publication Date Title
WO2015154726A1 (zh) 压缩机及空调器
WO2015154717A1 (zh) 压缩机和空调器
CN110374876B (zh) 双温并行独立的压缩机及空调系统
WO2017063588A1 (zh) 双级变容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
CN106321433A (zh) 压缩机及空调系统
CN105221421A (zh) 压缩机及空调器
CN103727034A (zh) 压缩机
EP3217013B1 (en) Compressor, air-conditioning system and compressor control method
WO2015131313A1 (zh) 双级旋转式压缩机及具有其的制冷循环装置
CN202483880U (zh) 两级压缩式旋转压缩机
CN107084133B (zh) 压缩机和具有其的制冷装置
CN109026691A (zh) 一种多缸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
CN209164088U (zh) 一种压缩机及制冷循环装置
CN203809296U (zh) 压缩机及空调器
CN107228070A (zh) 压缩机以及具有它的制冷系统
CN112302901B (zh) 多级压缩结构及控制方法、多级压缩机
CN204003467U (zh) 空调系统
CN209783060U (zh) 制冷系统和制冷设备
CN106382760B (zh) 压缩机及具有其的制冷系统
CN107218740B (zh) 冷媒循环系统及具有其的空调器
CN105332919B (zh) 空调系统
CN203822589U (zh) 一种空调以及双缸变容压缩机
CN217082969U (zh) 一种双机双级压缩制冷机组

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: 15777249

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2017504233

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 15303096

Country of ref document: US

REEP Request for entry into the european phase

Ref document number: 2015777249

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2015777249

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 20167031402

Country of ref document: KR

Kind code of ref document: A