WO2017129080A1 - 双缸压缩机及空调器 - Google Patents

双缸压缩机及空调器 Download PDF

Info

Publication number
WO2017129080A1
WO2017129080A1 PCT/CN2017/072094 CN2017072094W WO2017129080A1 WO 2017129080 A1 WO2017129080 A1 WO 2017129080A1 CN 2017072094 W CN2017072094 W CN 2017072094W WO 2017129080 A1 WO2017129080 A1 WO 2017129080A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
vent
flange
partition
hole
Prior art date
Application number
PCT/CN2017/072094
Other languages
English (en)
French (fr)
Inventor
阙沛祯
杨欧翔
魏会军
翟元彬
黄建峰
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
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
Publication of WO2017129080A1 publication Critical patent/WO2017129080A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet

Definitions

  • the present invention relates to the field of compressor technology, and in particular to a two-cylinder compressor and an air conditioner.
  • the rotary compressor pump body assembly adopts a two-cylinder or multi-cylinder structure, and the displacement of a single cylinder is designed to be larger and larger.
  • the increase of cylinder displacement will inevitably require a larger exhaust port to meet the venting of the exhaust, reduce the exhaust loss of the compressor, and improve the performance of the compressor.
  • the single exhaust port cannot be designed to be large enough, and after the single exhaust port is increased to a certain extent, the clearance volume is also continuously increased, resulting in a decrease in performance. Therefore, the current two-cylinder large-displacement compressor has a four-exhaust structure. That is, one cylinder has two exhaust ports on the upper and lower end faces, and two double-layer partitions between the two cylinders.
  • the patent application number is 201020668869.0, 201420434597.6, 201280046586.4, 200510073056.0 and the like discloses a two-cylinder compressor having a double-layer partition and a four-exhaust structure exhausting mode.
  • the double-layer partition and the exhaust port is provided in the upper and lower flanges and the double-layer partition, the four-exhaust of the two-cylinder compressor can be realized, and the exhaust passage can be enlarged to reduce the exhaust loss.
  • the disclosed patented technology does not address the problem of reducing the exhaust noise problem of the two-cylinder four-exhaust structure compressor and the performance of the exhaust port size setting under different operating conditions.
  • the compressor with a two-cylinder four-exhaust port structure has two more exhaust ports than the conventional two-cylinder dual-exhaust compressor.
  • the exhaust port will be increased as much as possible, but increasing the exhaust port will also result in an increase in the clearance volume of the exhaust gas, a large loss of cooling capacity under the working condition of the compressor high pressure ratio, and a decrease in compressor performance.
  • a primary object of the present invention is to provide a two-cylinder compressor and an air conditioner to solve the problem of low performance of the prior art two-cylinder compressor.
  • a two-cylinder compressor including an upper cylinder and a lower cylinder, and a partition plate connected between the upper cylinder and the lower cylinder is provided, and an upper flange is disposed above the upper cylinder a lower flange is disposed under the lower cylinder, and a first upper cylinder exhaust hole is formed at an upper end of the upper cylinder toward the upper flange, and an upper flange is disposed at a position corresponding to the first upper cylinder exhaust hole on the upper flange a vent hole, a lower lower cylinder is formed with a first lower cylinder vent hole toward a lower end of the lower flange, and a lower flange vent hole is provided at a position corresponding to the first lower cylinder vent hole on the lower flange, the first upper portion a first notch is formed at an edge of the cylinder exhaust hole and/or the first lower cylinder exhaust hole, and an aperture of the upper flange exhaust hole and/or the lower flange exhaust
  • an upper cylinder resonant cavity is opened on the upper cylinder, and an upper cylinder resonant cavity communicates with the first upper cylinder exhausting hole through the upper tunnel.
  • a lower cylinder resonant cavity is opened on the lower cylinder, and a lower cylinder resonant cavity is communicated with the first lower cylinder exhausting hole through the lower tunnel.
  • a first valve piece is disposed at the upper flange vent hole and the lower flange vent hole, and the first valve piece is provided with a first blocking piece.
  • the partition plate includes an upper partition plate and a lower partition plate, the upper partition plate and the lower partition plate are disposed adjacent to each other, the upper partition plate is located below the upper cylinder, the lower partition plate is located above the lower cylinder, and the upper partition plate faces the upper partition plate
  • the lower end is formed with a second upper cylinder venting hole
  • the upper partition plate is provided with an upper partition venting opening corresponding to the second upper cylinder venting hole
  • the upper end of the lower cylinder facing the lower partition is formed with the second lower portion a cylinder vent hole
  • a lower partition vent hole is opened at a position corresponding to the lower cylinder vent hole on the lower partition.
  • a second valve plate is disposed at the upper partition vent hole and the lower partition vent hole, and the second valve sheet is provided with a second flap.
  • the apertures of the upper flange vent and the lower flange vent are D1
  • the apertures of the upper and lower diaphragm vents are D2
  • the volumes of the upper and lower cylinders are V1, wherein D2 ⁇ D1, 0.2 ⁇ D1/V1 ⁇ 0.3, 0.18 ⁇ D2 / V1 ⁇ 0.25.
  • the center of the first flap has a lift of H1
  • the center of the second flap has a lift of H2, wherein H2 ⁇ H1, 0.2 ⁇ H1/D1 ⁇ 0.25, and 0.2 ⁇ H2 / D2 ⁇ 0.25.
  • a second notch is formed at an edge of the second upper cylinder exhaust hole and the second lower cylinder exhaust hole, and the apertures of the upper partition hole and the lower partition air hole respectively correspond to the second upper cylinder row The maximum aperture of the vent and the second lower cylinder vent.
  • the upper flange vent hole, the lower flange vent hole, the upper partition vent hole and the lower partition vent hole have a diameter D3
  • the upper cylinder and the lower cylinder have a volume of V2, wherein 0.2 ⁇ D3 /V2 ⁇ 0.3.
  • center lift of the first flap and the second flap is H3, wherein 0.2 ⁇ H3 / D3 ⁇ 0.25.
  • first notch and/or the second notch are oblique cuts.
  • the two-cylinder compressor further includes a muffler, and the muffler is mounted on the lower flange.
  • an air conditioner including a two-cylinder compressor which is the above-described two-cylinder compressor is provided.
  • a first notch is opened at an edge of the first upper cylinder exhaust hole and the first lower cylinder exhaust hole, corresponding to the first upper cylinder exhaust hole and the first lower cylinder exhaust
  • the aperture is enlarged at the opening surface of the hole, and accordingly, the apertures of the upper flange vent hole and the lower flange vent hole are enlarged, so that the apertures of the upper flange vent hole and the lower flange vent hole correspond to the first The aperture of the upper cylinder vent and the first lower cylinder vent.
  • the aperture of the upper flange vent and the lower flange vent can be increased, thereby reducing exhaust loss.
  • the aperture is enlarged only at the opening faces of the first upper cylinder exhaust hole and the first lower cylinder exhaust hole, the first upper cylinder exhaust hole and the first lower cylinder row are not enlarged as a whole.
  • the volume of the air vent so the clearance volume of the first upper cylinder vent and the first lower cylinder vent is not greatly increased, so even under high pressure ratio conditions, the compressor's cooling capacity will not be lost. Large, to ensure the performance of the compressor.
  • Figure 1 is a schematic view showing the structure of a first embodiment of a two-cylinder compressor according to the present invention
  • Figure 2 is a partially enlarged schematic view showing the upper flange vent hole of the two-cylinder compressor of Figure 1;
  • Figure 3 is a schematic view showing the structure of the upper cylinder of the two-cylinder compressor of Figure 1;
  • Figure 4 is a schematic view showing the structure of a second embodiment of a two-cylinder compressor according to the present invention.
  • Figure 5 is a schematic view showing the energy efficiency of a pressure ratio of a two-cylinder compressor according to the present invention
  • Figure 6 shows a schematic diagram of the frequency noise of a two-cylinder compressor in accordance with the present invention.
  • FIG. 1 shows a two-cylinder compressor of a first embodiment of the present invention, which includes an upper cylinder 10 and a lower cylinder 20, and a partition 30 connected between the upper cylinder 10 and the lower cylinder 20.
  • An upper flange 40 is disposed above the upper cylinder 10, and a lower flange 50 is disposed below the lower cylinder 20.
  • the upper cylinder 10 is formed with a first upper cylinder exhaust hole 11 toward the upper end of the upper flange 40, and an upper flange exhaust hole 41 is formed at a position corresponding to the first upper cylinder exhaust hole 11 of the upper flange 40.
  • the lower cylinder 20 is formed with a first lower cylinder exhaust hole 21 toward the lower end of the lower flange 50, and a lower flange exhaust hole 51 is formed at a position of the lower flange 50 corresponding to the first lower cylinder exhaust hole 21.
  • a first notch is formed at an edge of the first upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21, and an aperture of the upper flange exhaust hole 41 and the lower flange exhaust hole 51 respectively corresponds to the first upper cylinder The maximum aperture of the vent hole 11 and the first lower cylinder vent hole 21.
  • a first notch is opened at the edge of the first upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21, corresponding to the opening of the first upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21
  • the aperture is enlarged at the surface, and accordingly, the apertures of the upper flange vent 41 and the lower flange vent 51 can be enlarged, so that the apertures of the upper flange vent 41 and the lower flange vent 51 correspond to the An aperture of the upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21. In this way, the apertures of the upper flange vent 41 and the lower flange vent 51 can be increased, thereby reducing exhaust loss.
  • the aperture is enlarged only at the opening faces of the first upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21, the first upper cylinder exhaust hole 11 and the first are not enlarged as a whole.
  • the volume of the lower cylinder exhaust hole 21, so the clearance volume of the first upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21 is not greatly increased, so even in the case of the high pressure ratio, the compressor is cold. The amount will not be lost, and the performance of the compressor is guaranteed.
  • the first notch and the second notch are oblique cuts.
  • the oblique slit is provided to effectively increase the aperture at the opening faces of the first upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21, and may be made to pass through the first upper cylinder exhaust hole 11 and the first lower cylinder.
  • the refrigerant of the vent hole 21 runs more smoothly, reducing the impact of the refrigerant.
  • rollers are disposed in the upper cylinder 10 and the lower cylinder 20, and the rollers are sleeved on the eccentric shaft of the crankshaft of the twin-cylinder compressor.
  • the roller is driven by the crankshaft to rotate, and the refrigerant entering the compressor is compressed.
  • a first valve piece 60 is disposed at both the upper flange vent hole 41 and the lower flange vent hole 51, and the first valve piece 60 is provided with a first flap 70.
  • the refrigerant will be the first valve on the first upper cylinder exhaust hole 11 and the first lower cylinder exhaust hole 21
  • the sheet 60 produces a greater impact force, which in turn causes a large amount of mechanical noise to be generated by the collision between the first flap 60 and the first flap 70.
  • the upper cylinder 10 is provided with an upper cylinder resonance chamber 12, and the upper cylinder resonance chamber 12 communicates with the first upper cylinder exhaust hole 11 through the upper passage.
  • a lower cylinder resonator chamber 22 is opened in the lower cylinder 20, and the lower cylinder resonator chamber 22 communicates with the first lower cylinder exhaust port 21 through the lower tunnel.
  • the noise generated by the impact between the first valve piece 60 and the first flap 70 can be effectively reduced by the upper cylinder cavity 12 and the lower cylinder cavity 22.
  • the upper cylinder resonator chamber 12 communicates with the oblique slit on the first upper cylinder exhaust hole 11 through the upper tunnel
  • the lower cylinder resonator chamber 22 communicates with the oblique slit on the first lower cylinder exhaust hole 21 through the lower tunnel.
  • the partition plate 30 includes an upper partition plate 31 and a lower partition plate 32, and the upper partition plate 31 and the lower partition plate 32 are disposed adjacent to each other.
  • the upper partition plate 31 is located below the upper cylinder 10
  • the lower partition plate 32 is located above the lower cylinder 20.
  • a second upper cylinder exhaust hole 13 is formed in the upper cylinder 10 toward the lower end of the upper partition 31, and an upper partition vent 311 is formed in the upper partition 31 at a position corresponding to the second upper cylinder exhaust hole 13.
  • a lower lower cylinder exhaust hole 23 is formed in the lower end of the lower cylinder 32 toward the lower partition 32, and a lower partition exhaust hole 321 is formed in the lower partition 32 at a position corresponding to the exhaust hole of the lower cylinder 20.
  • the exhaust loss can be further reduced by opening the vent hole in the partition plate 30.
  • a partitioning exhaust cavity is formed on one side of the partition plate 30 , and the partitioning exhaust cavity is connected to the upper partitioning venting hole 311 and the lower partitioning venting opening 321 . It is used to discharge the refrigerant and also has a good sound-absorbing effect.
  • the conventional double-cylinder compressor will increase the diameter of the cylinder vent hole and the flange vent hole as much as possible, thereby reducing the exhaust loss.
  • the diameters of the cylinder vent hole and the flange vent hole increase, the effect of reducing the exhaust resistance does not increase, and on the contrary, the clearance is increased, resulting in a decrease in the compression cooling capacity and a decrease in performance.
  • the increase in the diameter value of the cylinder vent hole and the flange vent hole the larger the acting surface acting on the valve plate, the greater the impact force on the valve plate, and the higher the lift of the flap, the valve plate impact The force of the flap is also greater.
  • the impact noise of the exhaust valve plate increases.
  • the direct and stop lift of the cylinder vent and flange vents should not be too small, otherwise the exhaust loss will increase.
  • the second diaphragm 80 is disposed at the upper partition vent 311 and the lower partition vent 321 , and the second flap 90 is disposed on the second valve 80.
  • the apertures of the upper flange vent 41 and the lower flange vent 51 are D1
  • the apertures of the upper partition vent 311 and the lower partition vent 321 are D2
  • the volumes of the upper cylinder 10 and the lower cylinder 20 are V1
  • the center of the first flap 70 is lifted to H1.
  • the inventors have found through research that when D2 ⁇ D1, 0.2 ⁇ D1/V1 ⁇ 0.3, 0.18 ⁇ D2/V1 ⁇ 0.25, the leakage resistance loss can be reduced while the clearance capacity is greatly reduced. Impact.
  • the inventors have also found that, among the above parameters, H2 ⁇ H1, 0.2 ⁇ H1/D1 ⁇ 0.25, and 0.2 ⁇ H2 / D2 ⁇ 0.25, the mechanical impact noise of the valve plate can also be significantly reduced.
  • the two-cylinder compressor further includes a muffler 100, and the muffler 100 is mounted on the lower flange 50.
  • the arrangement of the muffler 100 can further absorb the noise generated on the twin-cylinder compressor.
  • FIG. 4 shows a technical solution of the second embodiment of the present invention.
  • the technical solution of the second embodiment is different from the technical solution of the first embodiment, and the difference is the second upper cylinder exhaust hole 13 and the second lower cylinder exhaust hole 23 .
  • a second notch is also formed at the edge, and the apertures of the upper partition vent 311 and the lower partition vent 321 correspond to the maximum apertures of the second upper cylinder vent 13 and the second lower cylinder vent 23, respectively.
  • the upper flange vent hole 41, the lower flange vent hole 51, the upper partition vent hole 311, and the lower partition vent hole 321 have an aperture D3, the upper cylinder 10 and the lower
  • the volume of the cylinder 20 is V2
  • the center lift of the first flap 70 and the second flap 90 is H3.
  • the inventors have found through research that 0.2 ⁇ D3/V2 ⁇ 0.3 in the above parameters can reduce the influence of the clearance volume while ensuring the reduction of the exhaust resistance loss.
  • 0.2 ⁇ H3 / D3 ⁇ 0.25 the mechanical impact noise of the valve plate can also be significantly reduced.
  • the technical solution of the first embodiment has a better effect of reducing the clearance volume.
  • the present invention also provides an air conditioner comprising the above described two-cylinder compressor.
  • the air conditioner has low noise consumption and an excellent energy efficiency ratio.

Landscapes

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

Abstract

一种双缸压缩机，包括上气缸(10)和下气缸(20)以及连接在上气缸(10)和下气缸(20)之间的隔板(30)。上气缸(10)的上方设置有上法兰(40)，下气缸(20)的下方设置有下法兰(50)。上气缸(10)朝向上法兰(40)的上端形成有第一上气缸排气孔(11)，上法兰(40)上对应于第一上气缸排气孔(11)的位置处开设有上法兰排气孔(41)。下气缸(20)朝向下法兰(50)的下端形成有第一下气缸排气孔(21)，下法兰(50)上对应于第一下气缸排气孔(21)的位置处开设有下法兰排气孔(51)。第一上气缸排气孔(11)和第一下气缸排气孔(21)的边沿处开设有第一缺口，上法兰排气孔(41)和下法兰排气孔(51)的孔径分别对应于第一上气缸排气孔(11)和第一下气缸排气孔(21)的最大孔径。包括有该双缸压缩机的空调机。该双缸压缩机有效地解决了现有技术中双缸压缩机性能较低的问题。

Description

双缸压缩机及空调器 技术领域
本发明涉及压缩机技术领域，具体而言，涉及一种双缸压缩机及空调器。
背景技术
目前，为了实现大的制冷量，旋转式压缩机泵体组件采用双缸或多缸结构，并且单个气缸的排量设计得越来越大。而气缸排量的增大必然需要更大的排气口，以满足排气的通畅，减小压缩机的排气损失，提高压缩机性能。而因气缸结构的限制，单个排气口无法设计的得足够大，另外单个排气口增大到一定程度后，余隙容积也不断增大，导致性能降低。所以目前对双缸大排量压缩机有采用四排气结构。即一个气缸上下端面具有两个排气口，两个气缸之间有双层隔板。
比如专利申请号为201020668869.0，201420434597.6，201280046586.4，200510073056.0等专利公开了一种双缸压缩机具有双层隔板，四排气结构的排气方式。通过双层隔板，并且在上下法兰、双层隔板中都设置有排气口，实现双缸压缩机的四排气，能加大排气通道，降低排气损失。然而所公开的专利技术并未记载关于降低所述双缸四排气结构压缩机的排气噪声问题和排气口大小的设置在不同工况下性能提高的问题。双缸四排气口结构的压缩机，相对于普通双缸双排气压缩机，排气口增加了两个。为了降低排气损失，会尽量加大排气口，但是加大排气口也会导致排气的余隙容积增加，压缩机高压比的工况下冷量损失大，压缩机性能降低。
发明内容
本发明的主要目的在于提供一种双缸压缩机及空调器，以解决现有技术中双缸压缩机性能较低的问题。
为了实现上述目的，根据本发明的一个方面，提供了一种双缸压缩机，包括上气缸和下气缸以及连接在上气缸和下气缸之间的隔板，上气缸的上方设置有上法兰，下气缸的下方设置有下法兰，上气缸朝向上法兰的上端形成有第一上气缸排气孔，上法兰上对应于第一上气缸排气孔的位置处开设有上法兰排气孔，下气缸朝向下法兰的下端形成有第一下气缸排气孔，下法兰上对应于第一下气缸排气孔的位置处开设有下法兰排气孔，第一上气缸排气孔和/或第一下气缸排气孔的边沿处开设有第一缺口，上法兰排气孔和/或下法兰排气孔的孔径分别对应于第一上气缸排气孔和第一下气缸排气孔的最大孔径。
进一步地，上气缸上开设有上气缸共振腔，上气缸共振腔通过上孔道与第一上气缸排气孔连通。
进一步地，下气缸上开设有下气缸共振腔，下气缸共振腔通过下孔道与第一下气缸排气孔连通。
进一步地，上法兰排气孔和下法兰排气孔处均设置有第一阀片，第一阀片上设置有第一挡片。
进一步地，隔板包括上隔板和下隔板，上隔板和下隔板相邻设置，上隔板位于上气缸的下方，下隔板位于下气缸的上方，上气缸上朝向上隔板的下端形成有第二上气缸排气孔，上隔板对应于第二上气缸排气孔的位置处开设有上隔板排气孔，下气缸上朝向下隔板的上端形成有第二下气缸排气孔，下隔板上对应于下气缸排气孔的位置处开设有下隔板排气孔。
进一步地，上隔板排气孔和下隔板排气孔处均设置有第二阀片，第二阀片上设置有第二挡片。
进一步地，上法兰排气孔和下法兰排气孔的孔径为D1，上隔板排气孔和下隔板排气孔的孔径为D2，上气缸和下气缸的容积为V1，其中D2<D1，0.2<D1/V1<0.3，0.18<D2/V1<0.25。
进一步地，第一挡片的中心升程为H1，第二挡片的中心升程为H2，其中，H2<H1，0.2<H1/D1<0.25，0.2<H2/D2<0.25。
进一步地，第二上气缸排气孔和第二下气缸排气孔的边沿处开设有第二缺口，上隔板排气孔和下隔板排气孔的孔径分别对应于第二上气缸排气孔和第二下气缸排气孔的最大孔径。
进一步地，上法兰排气孔、下法兰排气孔、上隔板排气孔和下隔板排气孔的孔径为D3，上气缸和下气缸的容积为V2，其中，0.2<D3/V2<0.3。
进一步地，第一挡片和第二挡片的中心升程为H3，其中，0.2<H3/D3<0.25。
进一步地，第一缺口和/或第二缺口为斜切口。
进一步地，双缸压缩机还包括消音器，消音器安装在下法兰的上。
根据本发明的另一方面，提供了一种空调器，包括双缸压缩机，双缸压缩机为上述的双缸压缩机。
应用本发明的技术方案，通过在第一上气缸排气孔和第一下气缸排气孔的边沿处开设有第一缺口，相当于在第一上气缸排气孔和第一下气缸排气孔的开口面处扩大了孔径，相应地就可以扩大上法兰排气孔和下法兰排气孔的孔径，使得上法兰排气孔和下法兰排气孔的孔径对应于第一上气缸排气孔和第一下气缸排气孔的孔径。这样一来，就能增大上法兰排气孔和下法兰排气孔的孔径，从而降低排气损失。而与此同时，因为只在第一上气缸排气孔和第一下气缸排气孔的开口面处扩大了孔径，并没有从整体上扩大第一上气缸排气孔和第一下气缸排气孔的体积，因此第一上气缸排气孔和第一下气缸排气孔的余隙容积并没有大幅增加，所以即使在高压比的工况下，压缩机的冷量也不会损失很大，保障了压缩机的性能。
除了上面所描述的目的、特征和优点之外，本发明还有其它的目的、特征和优点。下面将参照图，对本发明作进一步详细的说明。
附图说明
构成本发明的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示出了根据本发明的双缸压缩机的实施例一的结构示意图；
图2示出了图1的双缸压缩机的上法兰排气孔处的局部放大示意图；
图3示出了图1的双缸压缩机的上气缸的结构示意图；
图4示出了根据本发明的双缸压缩机的实施例二的结构示意图；
图5示出了根据本发明的双缸压缩机的压比能效示意图；
图6示出了根据本发明的双缸压缩机的频率噪声示意图。
其中，上述附图包括以下附图标记：
10、上气缸；11、第一上气缸排气孔；12、上气缸共振腔；13、第二上气缸排气孔；20、下气缸；21、第一下气缸排气孔；22、下气缸共振腔；23、第二下气缸排气孔；30、隔板；31、上隔板；311、上隔板排气孔；32、下隔板；321、下隔板排气孔；40、上法兰；41、上法兰排气孔；50、下法兰；51、下法兰排气孔；60、第一阀片；70、第一挡片；80、第二阀片；90、第二挡片；100、消音器。
具体实施方式
需要说明的是，在不冲突的情况下，本发明中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
为了使本技术领域的人员更好地理解本发明方案，下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分的实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都应当属于本发明保护的范围。
需要说明的是，本发明的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本发明的实施例。此外，术语“包括”和“具有”以及他们的任何变形，意图在于覆盖不排他的包含，例如，包含了一系列步骤或单元的过程、方法、系统、产品或设备不必限于清楚地列出的那些步骤或单元，而是可包括没有清楚地列出的或对于这些过程、方法、产品或设备固有的其它步骤或单元。
图1示出了本发明的实施例一的双缸压缩机，该双缸压缩机包括上气缸10和下气缸20以及连接在上气缸10和下气缸20之间的隔板30。上气缸10的上方设置有上法兰40，下气缸20的下方设置有下法兰50。上气缸10朝向上法兰40的上端形成有第一上气缸排气孔11，上法兰40上对应于第一上气缸排气孔11的位置处开设有上法兰排气孔41。下气缸20朝向下法兰50的下端形成有第一下气缸排气孔21，下法兰50上对应于第一下气缸排气孔21的位置处开设有下法兰排气孔51。第一上气缸排气孔11和第一下气缸排气孔21的边沿处开设有第一缺口，上法兰排气孔41和下法兰排气孔51的孔径分别对应于第一上气缸排气孔11和第一下气缸排气孔21的最大孔径。
通过在第一上气缸排气孔11和第一下气缸排气孔21的边沿处开设有第一缺口，相当于在第一上气缸排气孔11和第一下气缸排气孔21的开口面处扩大了孔径，相应地就可以扩大上法兰排气孔41和下法兰排气孔51的孔径，使得上法兰排气孔41和下法兰排气孔51的孔径对应于第一上气缸排气孔11和第一下气缸排气孔21的孔径。这样一来，就能增大上法兰排气孔41和下法兰排气孔51的孔径，从而降低排气损失。而与此同时，因为只在第一上气缸排气孔11和第一下气缸排气孔21的开口面处扩大了孔径，并没有从整体上扩大第一上气缸排气孔11和第一下气缸排气孔21的体积，因此第一上气缸排气孔11和第一下气缸排气孔21的余隙容积并没有大幅增加，所以即使在高压比的工况下，压缩机的冷量也不会损失很大，保障了压缩机的性能。
可选的，只在第一上气缸排气孔11或第一下气缸排气孔21的边沿上开设第一缺口也是可行的，也能从一定程度上保障压缩机的性能。
可选的，如图2和图3所示，在实施例一中，第一缺口和第二缺口为斜切口。斜切口的设置既可以有效增大第一上气缸排气孔11和第一下气缸排气孔21的开口面处的孔径，又可以使得经由第一上气缸排气孔11和第一下气缸排气孔21的冷媒运行更加平稳，减小冷媒的冲击。
可选的，如图1所示，在上气缸10和下气缸20中设置有滚子，滚子套在双缸压缩机曲轴的偏心轴上。通过曲轴带动滚子旋转，进而对进入压缩机的冷媒进行压缩。
如图1和图2所示，在上法兰排气孔41和下法兰排气孔51处均设置有第一阀片60，第一阀片60上设置有第一挡片70。
在增大了第一上气缸排气孔11和第一下气缸排气孔21的孔径后，冷媒会对第一上气缸排气孔11和第一下气缸排气孔21上的第一阀片60产生更大的冲击力，进而引起第一阀片60和第一挡片70之间的碰撞产生大量的机械噪声。如图1所示，上气缸10上开设有上气缸共振腔12，上气缸共振腔12通过上孔道与第一上气缸排气孔11连通。下气缸20上开设有下气缸共振腔22，下气缸共振腔22通过下孔道与第一下气缸排气孔21连通。通过上气缸共振腔12和下气缸共振腔22可以有效降低，第一阀片60和第一挡片70之间因撞击而产生的噪音。可选的，上气缸共振腔12通过上孔道与第一上气缸排气孔11上的斜切口连通，下气缸共振腔22通过下孔道与第一下气缸排气孔21上的斜切口连通。
如图1所示，在实施例一中，可选的，隔板30包括上隔板31和下隔板32，上隔板31和下隔板32相邻设置。上隔板31位于上气缸10的下方，下隔板32位于下气缸20的上方。上气缸10上朝向上隔板31的下端形成有第二上气缸排气孔13，上隔板31对应于第二上气缸排气孔13的位置处开设有上隔板排气孔311。下气缸20上朝向下隔板32的上端形成有第二下气缸排气孔23，下隔板32上对应于下气缸20排气孔的位置处开设有下隔板排气孔321。通过在隔板30上开设排气孔，可以进一步降低排气损失。可选的，如图1所示，在隔板30的一侧形成有隔板排气空腔，该隔板排气空腔与上隔板排气孔311和下隔板排气孔321连通，用于排出冷媒，还可以起到良好的消音效果。
传统技术的双缸压缩机，为了降低排气损失，会尽可能的加大气缸排气孔和法兰排气孔的直径，从而降低排气损失。然而随着气缸排气孔和法兰排气孔直径值不断增大，对降低排气阻力的效果不会增加，相反会导致余隙的增加，导致压缩制冷量的降低，性能下降。尤其是在压比大的工况会表现得尤其明显。另外气缸排气孔和法兰排气孔的直径值的增大，作用于阀片的作用面也越大，阀片受到的冲击力也越大，同时挡片的升程越高，阀片撞击挡片的力也越大。最终导致排气阀片的撞击噪声随增大。但气缸排气孔和法兰排气孔的直接和挡片的升程也不能太小，否则排气损失会上升。
如图1所示，上隔板排气孔311和下隔板排气孔321处均设置有第二阀片80，第二阀片80上设置有第二挡片90。为了有效地减小余隙容积的同时而不增加排气阻力损失。上法兰排气孔41和下法兰排气孔51的孔径为D1，上隔板排气孔311和下隔板排气孔321的孔径为D2，上气缸10和下气缸20的容积为V1，第一挡片70的中心升程为H1。发明人经过研究发现，当上述参数中，D2<D1，0.2<D1/V1<0.3，0.18<D2/V1<0.25时，可以在保证减小排气阻力损失的同时，又大幅降低余隙容积的影响。发明人又发现，当上述参数中，H2<H1，0.2<H1/D1<0.25，0.2<H2/D2<0.25是，还可以明显地降低阀片的机械撞击噪声。
如图1所示，双缸压缩机还包括消音器100，消音器100安装在下法兰50的上。消音器100的设置可以进一步吸收双缸压缩机上产生的噪音。
图4示出了本发明实施例二的技术方案，实施例二的技术方案和实施例一的技术方案相比，区别在于第二上气缸排气孔13和第二下气缸排气孔23的边沿处也开设有第二缺口，上隔板排气孔311和下隔板排气孔321的孔径分别对应于第二上气缸排气孔13和第二下气缸排气孔23的最大孔径。通过在第二上气缸排气孔13和第二下气缸排气孔23的边沿处也开设有第二缺口，可以进一步降低排气损失，而在尽可能减小余隙容积增大程度的基础上，保证即使在高压比的工况下，压缩机的冷量也不会损失很大，保障了压缩机的性能。
在实施例二的技术方案中，上法兰排气孔41、下法兰排气孔51、上隔板排气孔311和下隔板排气孔321的孔径为D3，上气缸10和下气缸20的容积为V2，第一挡片70和第二挡片90的中心升程为H3。发明人经过研究发现，当上述参数中，0.2<D3/V2<0.3，可以在保证减小排气阻力损失的同时，又大幅降低余隙容积的影响。当上述参数中，0.2<H3/D3<0.25，还可以明显地降低阀片的机械撞击噪声。
实施一的技术方案和实施例二的技术方案相比较而言，实施一的技术方案降低余隙容积的效果更好。
如图5和图6所示，通过大量的试验证明，采用本发明的以上技术，对比现有技术的双缸压缩机，在大压比的工况下大幅提高了压缩机性能，同时在中压比的情况下与现有技术相当，只有在很小压比的的工况下性能有轻微下降，整体上压缩机性能得到大幅提升。同时各频率运行下噪声值相对以往技术得到了大幅降低，降低值在2dB以上。
本发明还提供了一种空调器，该空调器包括上述的双缸压缩机。该空调器的使用噪音较低，具有优良的能效比。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (14)

  1. 一种双缸压缩机，包括上气缸(10)和下气缸(20)以及连接在所述上气缸(10)和所述下气缸(20)之间的隔板(30)，所述上气缸(10)的上方设置有上法兰(40)，所述下气缸(20)的下方设置有下法兰(50)，所述上气缸(10)朝向所述上法兰(40)的上端形成有第一上气缸排气孔(11)，所述上法兰(40)上对应于所述第一上气缸排气孔(11)的位置处开设有上法兰排气孔(41)，所述下气缸(20)朝向所述下法兰(50)的下端形成有第一下气缸排气孔(21)，所述下法兰(50)上对应于所述第一下气缸排气孔(21)的位置处开设有下法兰排气孔(51)，其特征在于，所述第一上气缸排气孔(11)和/或所述第一下气缸排气孔(21)的边沿处开设有第一缺口，所述上法兰排气孔(41)和/或所述下法兰排气孔(51)的孔径分别对应于所述第一上气缸排气孔(11)和所述第一下气缸排气孔(21)的最大孔径。
  2. 根据权利要求1所述的双缸压缩机，其特征在于，所述上气缸(10)上开设有上气缸共振腔(12)，所述上气缸共振腔(12)通过上孔道与所述第一上气缸排气孔(11)连通。
  3. 根据权利要求1所述的双缸压缩机，其特征在于，所述下气缸(20)上开设有下气缸共振腔(22)，所述下气缸共振腔(22)通过下孔道与所述第一下气缸排气孔(21)连通。
  4. 根据权利要求1所述的双缸压缩机，其特征在于，所述上法兰排气孔(41)和所述下法兰排气孔(51)处均设置有第一阀片(60)，所述第一阀片(60)上设置有第一挡片(70)。
  5. 根据权利要求4所述的双缸压缩机，其特征在于，所述隔板(30)包括上隔板(31)和下隔板(32)，所述上隔板(31)和所述下隔板(32)相邻设置，所述上隔板(31)位于所述上气缸(10)的下方，所述下隔板(32)位于所述下气缸(20)的上方，所述上气缸(10)上朝向所述上隔板(31)的下端形成有第二上气缸排气孔(13)，所述上隔板(31)对应于所述第二上气缸排气孔(13)的位置处开设有上隔板排气孔(311)，所述下气缸(20)上朝向所述下隔板(32)的上端形成有第二下气缸排气孔(23)，所述下隔板(32)上对应于所述下气缸(20)排气孔的位置处开设有下隔板排气孔(321)。
  6. 根据权利要求5所述的双缸压缩机，其特征在于，所述上隔板排气孔(311)和所述下隔板排气孔(321)处均设置有第二阀片(80)，所述第二阀片(80)上设置有第二挡片(90)。
  7. 根据权利要求6所述的双缸压缩机，其特征在于，所述上法兰排气孔(41)和所述下法兰排气孔(51)的孔径为D1，所述上隔板排气孔(311)和所述下隔板排气孔(321)的孔径为D2，所述上气缸(10)和所述下气缸(20)的容积为V1，其中D2<D1，0.2<D1/V1<0.3，0.18<D2/V1<0.25。
  8. 根据权利要求7所述的双缸压缩机，其特征在于，所述第一挡片(70)的中心升程为H1，所述第二挡片(90)的中心升程为H2，其中，H2<H1，0.2<H1/D1<0.25，0.2<H2/D2<0.25。
  9. 根据权利要求6所述的双缸压缩机，其特征在于，所述第二上气缸排气孔(13)和所述第二下气缸排气孔(23)的边沿处开设有第二缺口，所述上隔板排气孔(311)和所述下 隔板排气孔(321)的孔径分别对应于所述第二上气缸排气孔(13)和所述第二下气缸排气孔(23)的最大孔径。
  10. 根据权利要求9所述的双缸压缩机，其特征在于，所述上法兰排气孔(41)、所述下法兰排气孔(51)、所述上隔板排气孔(311)和所述下隔板排气孔(321)的孔径为D3，所述上气缸(10)和所述下气缸(20)的容积为V2，其中，0.2<D3/V2<0.3。
  11. 根据权利要求10所述的双缸压缩机，其特征在于，所述第一挡片(70)和所述第二挡片(90)的中心升程为H3，其中，0.2<H3/D3<0.25。
  12. 根据权利要求9所述的双缸压缩机，其特征在于，所述第一缺口和/或所述第二缺口为斜切口。
  13. 根据权利要求1所述的双缸压缩机，其特征在于，所述双缸压缩机还包括消音器(100)，所述消音器(100)安装在所述下法兰(50)的上。
  14. 一种空调器，包括双缸压缩机，其特征在于，所述双缸压缩机为权利要求1至13中任一项所述的双缸压缩机。
PCT/CN2017/072094 2016-01-25 2017-01-22 双缸压缩机及空调器 WO2017129080A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201610053234.1 2016-01-25
CN201610053234.1A CN105485021B (zh) 2016-01-25 2016-01-25 双缸压缩机及空调器

Publications (1)

Publication Number Publication Date
WO2017129080A1 true WO2017129080A1 (zh) 2017-08-03

Family

ID=55672228

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2017/072094 WO2017129080A1 (zh) 2016-01-25 2017-01-22 双缸压缩机及空调器

Country Status (2)

Country Link
CN (1) CN105485021B (zh)
WO (1) WO2017129080A1 (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109519386A (zh) * 2018-11-19 2019-03-26 珠海凌达压缩机有限公司 一种压缩机用消音器组件及压缩机
CN111350667A (zh) * 2020-04-10 2020-06-30 黄石东贝电器股份有限公司 压缩机排气结构及压缩机
CN112229101A (zh) * 2020-10-26 2021-01-15 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调系统

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105485021B (zh) * 2016-01-25 2018-11-16 珠海格力节能环保制冷技术研究中心有限公司 双缸压缩机及空调器
CN105783137B (zh) * 2016-04-29 2019-02-15 广东美的制冷设备有限公司 冷暖型空调器的控制方法
CN107044422A (zh) * 2016-09-18 2017-08-15 珠海格力节能环保制冷技术研究中心有限公司 泵体结构和压缩机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59158396A (ja) * 1983-02-28 1984-09-07 Toshiba Corp 回転式圧縮機
CN1727685A (zh) * 2004-07-26 2006-02-01 乐金电子(天津)电器有限公司 压缩机排气通道内的消声装置
CN103452854A (zh) * 2013-08-19 2013-12-18 广东美芝制冷设备有限公司 旋转式压缩机
CN103827500A (zh) * 2011-09-29 2014-05-28 东芝开利株式会社 封闭式压缩机以及制冷循环装置
CN105485021A (zh) * 2016-01-25 2016-04-13 珠海格力节能环保制冷技术研究中心有限公司 双缸压缩机及空调器
CN205383084U (zh) * 2016-01-25 2016-07-13 珠海格力节能环保制冷技术研究中心有限公司 双缸压缩机及空调器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201902335U (zh) * 2010-12-20 2011-07-20 上海日立电器有限公司 一种用于双缸旋转式压缩机中间板的排气结构
CN105201836B (zh) * 2014-06-27 2018-01-02 珠海格力电器股份有限公司 空调系统、空调系统补气结构及双级压缩机
CN104564690B (zh) * 2015-01-08 2016-11-16 广东美芝制冷设备有限公司 压缩机构和具有其的压缩机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59158396A (ja) * 1983-02-28 1984-09-07 Toshiba Corp 回転式圧縮機
CN1727685A (zh) * 2004-07-26 2006-02-01 乐金电子(天津)电器有限公司 压缩机排气通道内的消声装置
CN103827500A (zh) * 2011-09-29 2014-05-28 东芝开利株式会社 封闭式压缩机以及制冷循环装置
CN103452854A (zh) * 2013-08-19 2013-12-18 广东美芝制冷设备有限公司 旋转式压缩机
CN105485021A (zh) * 2016-01-25 2016-04-13 珠海格力节能环保制冷技术研究中心有限公司 双缸压缩机及空调器
CN205383084U (zh) * 2016-01-25 2016-07-13 珠海格力节能环保制冷技术研究中心有限公司 双缸压缩机及空调器

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109519386A (zh) * 2018-11-19 2019-03-26 珠海凌达压缩机有限公司 一种压缩机用消音器组件及压缩机
CN109519386B (zh) * 2018-11-19 2024-06-11 珠海凌达压缩机有限公司 一种压缩机用消音器组件及压缩机
CN111350667A (zh) * 2020-04-10 2020-06-30 黄石东贝电器股份有限公司 压缩机排气结构及压缩机
CN112229101A (zh) * 2020-10-26 2021-01-15 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调系统
CN112229101B (zh) * 2020-10-26 2022-08-02 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调系统

Also Published As

Publication number Publication date
CN105485021B (zh) 2018-11-16
CN105485021A (zh) 2016-04-13

Similar Documents

Publication Publication Date Title
WO2017129080A1 (zh) 双缸压缩机及空调器
CN104214099B (zh) 滚动转子式压缩机泵体结构及空调器
JP2019516907A (ja) ポンプアセンブリ及びそれを備えた圧縮機
JP2000320479A (ja) 多気筒密閉型圧縮機
CN204783689U (zh) 一种压缩机
CN110360111A (zh) 气缸、泵体组件、压缩机和空调器
JP2015531846A (ja) 冷媒充填型回転式圧縮機
CN210829717U (zh) 气缸、泵体组件、压缩机和空调器
CN202520552U (zh) 旋转式压缩机
CN210397019U (zh) 一种消音器和压缩机
CN111005874A (zh) 消音结构、压缩机、空调器
CN104728084B (zh) 压缩机及其用于减少脉动和/或噪声的阀组件
CN203796573U (zh) 旋转式压缩机及其排气结构
CN102644597A (zh) 双缸式旋转压缩机
CN112412786B (zh) 一种高效压缩机排气结构
CN203756543U (zh) 压缩机排气结构及具有该排气结构的压缩机
CN201714676U (zh) 旋转式压缩机的排气装置
WO2019017248A1 (ja) 回転式圧縮機
CN107559204B (zh) 旋转式压缩机的压缩机构以及旋转式压缩机
CN112483396A (zh) 压缩机泵体及压缩机
CN218030629U (zh) 轴承、轴承组件及压缩机
CN111059056A (zh) 泵体组件、旋转式压缩机、空调器
CN110966203A (zh) 一种压缩机泵体及压缩机
CN216044402U (zh) 一种气缸、压缩机和空调器
CN211343367U (zh) 消音结构、压缩机、空调器

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: 17743695

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17743695

Country of ref document: EP

Kind code of ref document: A1