WO2011018005A1 - 低压缩比的离心式压缩机及应用该压缩机的空调机组 - Google Patents

低压缩比的离心式压缩机及应用该压缩机的空调机组 Download PDF

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Publication number
WO2011018005A1
WO2011018005A1 PCT/CN2010/075688 CN2010075688W WO2011018005A1 WO 2011018005 A1 WO2011018005 A1 WO 2011018005A1 CN 2010075688 W CN2010075688 W CN 2010075688W WO 2011018005 A1 WO2011018005 A1 WO 2011018005A1
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Prior art keywords
blade
compression ratio
impeller
curved
centrifugal compressor
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PCT/CN2010/075688
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English (en)
French (fr)
Inventor
苏玉海
刘华
张治平
李宏波
谢艳群
钟瑞兴
王晨光
程旭
王彦川
刘怀灿
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珠海格力电器股份有限公司
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Publication of WO2011018005A1 publication Critical patent/WO2011018005A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the present invention relates to a centrifugal compressor of low compression ratio. Background technique
  • Waste is the goal of air conditioning equipment product development.
  • the purpose of air conditioning is to remove the residual heat and residual moisture from the room and provide a fresh air that meets the hygienic requirements.
  • the current domestic air conditioning system generally uses both cooling and dehumidification methods. In order to ensure better dehumidification effect, the air conditioning chilled water inlet temperature (5 ⁇ 7 °C) is required in summer, which limits the air conditioning host performance coefficient ( COP) is further improved.
  • the sensible heat load of more than half of the total load the heat that can be taken away by the high temperature cold source (12 ⁇ 20 °C) is treated by the low temperature cold source sharing the 5 ⁇ 7 °C together with the dehumidification. , causing waste in energy utilization.
  • the existing conventional centrifugal chillers in China are developed based on this "cooling and dehumidifying" mode.
  • the compressors are generally designed to have a high compression ratio.
  • the chilled water of the unit is 5 ⁇ 7 °C.
  • the highest COP value is less than 6.0, causing a great waste of energy.
  • the object of the present invention is to provide a centrifugal compressor with a low compression ratio and an air conditioning unit using a low compression ratio centrifugal compressor.
  • the present invention redesigns the important components of the compressor and reduces the compression ratio of the compressor. It satisfies the high-efficiency operation of the air-conditioning unit (ie, 30°C cooling water inlet and 12-20°C frozen water), improves the performance coefficient of the unit, and has better energy-saving effect.
  • a low compression ratio centrifugal compressor including an impeller, a rotating shaft, a motor, a driving gear and a driven gear,
  • the moving gear is disposed on the output shaft of the motor
  • the driven gear is disposed on the rotating shaft and meshes with the driving gear
  • the rotating shaft is connected with the axial portion of the impeller;
  • the impeller includes a wheel and a plurality of curved blades, and the plurality of curved blades are along the wheel
  • the disk is circumferentially evenly distributed.
  • the radially inner end of the curved blade is an inlet end, and the radially outer end is an outlet end.
  • the side of the curved blade near the wheel is the side of the wheel, and the side away from the wheel is The inner side; the angle between the exit end of the curved blade relative to the line connecting the outlet end and the axis is 50 to 60 degrees, and the line between the outer side and the inner side of the exit end of the curved blade is opposite to the axis of the wheel The angle is 17 to 23 degrees.
  • the invention redesigns the blade, so that the compression of the impeller is relatively low, and the work is also more stable, the compression ratio of the compressor is low, and the compression efficiency is high. After the compressor is installed in the air conditioning system, the performance coefficient of the air conditioner can be effectively improved.
  • a further structure of the invention is:
  • the angle between the exit end of the curved blade relative to the line connecting the outlet end and the axis is preferably 55 degrees, and the line connecting the outer side and the inner side of the exit end of the curved blade is opposite to the axis of the wheel The angle between them is preferably 20 degrees.
  • the curved blade includes a long blade and a short blade, and the number of the long blade and the short blade is equal, and the long blade and the short blade are spaced apart from each other.
  • the present invention also improves the gear ratio of the speed increasing gear, wherein the ratio of the gear ratio of the driving gear to the driven gear is 2.5:1 to 3:1, preferably 128:43, that is, the driving gear
  • the number of teeth is 128, and the number of teeth of the driven gear is 43.
  • an air conditioning unit comprising:
  • a low compression ratio centrifugal compressor as described above for compressing a low temperature and low pressure refrigerant gas from an evaporator to a high temperature and high pressure state
  • a condenser for condensing high temperature and high pressure refrigerant gas from the compressor into a high temperature and high pressure liquid refrigerant
  • a throttling device for throttling high temperature and high pressure liquid refrigerant from the condenser to a low temperature and low pressure liquid refrigerant
  • the evaporator, the low-temperature low-pressure liquid refrigerant from the throttling device absorbs heat in the chilled water in the evaporator and evaporates into a low-temperature low-pressure refrigerant gas, and the chilled water also lowers the temperature by releasing heat.
  • the compressor, the evaporator, the condenser and the throttling device are connected by a pipe.
  • the advantages of the present invention are: Since the transmission ratio of the impeller and the speed increasing gear of the compressor is redesigned, the compression of the compressor is relatively low, the compression efficiency of the compressor is higher, and the compression is installed in the air conditioning system. After the machine, the temperature of the frozen water is between 12 and 20 °C, which has better energy saving effect and effectively improves the performance coefficient of the air conditioner.
  • Figure 1 is a system flow diagram of an air conditioning unit incorporating the compressor of the present invention
  • Figure 2 is a partial enlarged view of Figure 1;
  • Figure 3 is a perspective view of the impeller
  • Figure 4 is an end view of the impeller
  • Figure 5 is a side view of the impeller
  • a low compression ratio centrifugal compressor includes an impeller 4, a rotating shaft 5, a motor 8, a driving gear 6 and a driven gear 7, and the driving gear 6 is disposed on an output shaft of the motor 8.
  • the driven gear 7 is disposed on the rotating shaft 5 and meshes with the driving gear 6, and the rotating shaft 5 is connected with the axial portion of the impeller 4;
  • the impeller 4 includes a wheel 9 and a plurality of curved blades 10, and the plurality of curved blades 10 are along the wheel
  • the disk 9 is circumferentially uniform, the radially inner end of the curved blade 10 is the inlet end 11, and the radially outer end is the outlet end 12, and the curved blade 10 is adjacent to the side of the wheel 9 as the outer side 1 3, away from One side of the wheel 9 is the inner side 14; the angle between the outlet end 12 of the curved blade 10 with respect to the line connecting the outlet end 12 and the axis is 50 to 60 degrees, and the outer side of the exit end 12 of the
  • the angle between the outlet end 12 of the curved blade 10 and the line connecting the outlet end 12 and the axis is 55 degrees.
  • the angle between the line connecting the outer side 13 and the inner side 14 of the outlet end 12 of the curved blade 10 with respect to the axis of the wheel 9 is 20 degrees;
  • the curved blade 10 includes long and short blades, long blades and short The number of blades is equal, and the long blades and the short blades are spaced apart from each other;
  • the number of teeth of the driving gear 6 is 128, and the number of teeth of the driven gear 7 is 43, that is, the gear ratio of the driving gear 6 to the driven gear 128 is 128:43.
  • the invention redesigns the transmission ratio of the blade and the speed increasing gear, so that the compression of the impeller 4 is relatively low, and the work is also more stable, and the compressor 1 has a low compression ratio and a high compression efficiency.
  • an air conditioning unit equipped with the compressor 1 is configured. After the compressor 1 is compressed, the heat exchange medium enters the condenser 3 to condense and release heat, and the condensed heat exchange medium passes through the throttling device. After the throttling action of the throttle plate 15 and the electronic expansion width 16 , the evaporator 1 is evaporated and absorbs the heat of the chilled water. Since the compression of the compressor 1 is relatively low, the temperature of the entire unit at the frozen outlet water is satisfied. High and stable operation under high working conditions (12 ⁇ 20 °C), energy saving effect is good, and the performance coefficient of air conditioner can be effectively improved.
  • the above is only the preferred embodiment of the present invention, and the scope of the present invention is not limited thereto; any substitutions and improvements made without departing from the inventive concept are within the scope of the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

低压缩比的离心式压缩机及应用该压缩机的空调机组 技术领域
本发明涉及一种低压缩比的离心式压缩机。 背景技术
当前， 由于能源的紧缺， 建筑节能作为国家能源战略的一个重要组成部分， 受到了 越来越多的关注， 特别是占据了建筑能耗 60%以上的空调能耗， 提高能源利用效率和减 少能源浪费成为空调设备产品开发的目标。空调的目的是把室内的余热、余湿排出室夕卜， 并提供满足卫生要求的新风。 国内现行的空调系统普遍釆用既冷却又除湿的方式， 为了 保证具有较好的除湿效果， 要求夏季较低的空调冷冻水进水温度（ 5 ~ 7 °C ), 限制了空 调主机性能系数（COP )的进一步提高。 在空调系统中， 占总负荷一半以上的显热负荷， 本可以釆用高温冷源 （12 ~ 20°C ) 带走的热量却因为与除湿一起共用 5 ~ 7 °C的低温冷 源进行处理，造成能量利用品位上的浪费。 国内现有的普通离心式冷水机组都是基于这 种 "既供冷又除湿" 的模式开发的， 其压缩机一般都设计具有较高的压缩比， 机组冷 冻水出水为 5 ~ 7 °C , 最高 COP值低于 6. 0, 造成能源的极大浪费。
为了与前述空调设计思路相适应， 现有的离心式空调压缩机需要具有较高的压缩 比， 所以现有离心式压缩机的叶片设计、 增速齿轮传动比均是为了满足该设计思路。 发明内容
本发明的目的在于提供一种低压缩比的离心式压缩机和应用了低压缩比离心式压 缩机的空调机组， 本发明对压缩机的重要部件进行重新设计， 降低了压缩机的压缩比， 满足空调机组在高温工况（即冷却进水 30°C , 冷冻出水 12 ~ 20°C ) 高效稳定运行， 提 高机组性能系数， 具有更好的节能效果。
其技术方案如下：
一种低压缩比的离心式压缩机， 包括叶轮、 转轴、 电机、 主动齿轮及从动齿轮， 主 动齿轮设于电机的输出轴上，从动齿轮设于转轴上且与主动齿轮啮合， 转轴与叶轮的轴 心部位连接； 叶轮包括轮盘及多个曲形叶片， 多个曲形叶片沿轮盘周向均布， 该曲形叶 片径向靠内的一端为进口端、径向靠外的一端为出口端， 该曲形叶片靠近轮盘的一侧为 夕卜侧、远离轮盘的一侧为内侧； 曲形叶片出口端相对于该出口端与轴心的连线之间的夹 度为 50至 60度，曲形叶片出口端的外侧与内侧的连线相对于轮盘的轴线之间的夹角为 17至 23度。
本发明由于对叶片进行重新设计， 使得叶轮的压缩比较低， 同时工作也更稳定， 压 缩机的压缩比低， 压缩效率高。 在空调系统中装设该压缩机之后， 可以有效的提高空调 主机性能系数。
本发明的进一步结构是：
所述曲形叶片出口端相对于该出口端与轴心的连线之间的夹度优选为 55度， 所述 曲形叶片出口端的外侧与内侧的连线相对于所述轮盘的轴线之间的夹角优选为 20度。
所述曲形叶片包括长叶片及短叶片， 长叶片及短叶片的数量相等， 且长叶片与短叶 片相互间隔设置。
本发明还对增速齿轮的传动比进行改进，所述主动齿轮与从动齿轮的齿数比齿数比 为 2. 5 : 1至 3: 1 , 优选为 128 : 43 , 即， 所述主动齿轮的齿数为 128 , 所述从动齿轮 的齿数为 43。
同时本发明还提供一种空调机组， 包括：
如前所述的低压缩比的离心式压缩机，用于将来自蒸发器的低温低压制冷剂气体压 缩至高温高压状态；
冷凝器， 用于将来自压缩机的高温高压制冷剂气体冷凝成为高温高压的液态制冷 剂；
节流装置，用于将来自冷凝器的高温高压的液态制冷剂节流至低温低压的液态制冷 剂；
蒸发器，来自节流装置的低温低压的液态制冷剂在蒸发器中吸收冷冻水中的热量而 蒸发成为低温低压的制冷剂气体， 同时冷冻水也因为释放热量而降低温度。 压缩机、 蒸发器、 冷凝器及节流装置之间通过管路连接。
综上所述， 本发明的优点是： 由于对压缩机的叶轮及增速齿轮的传动比进行重新设 计， 压缩机的压缩比较低， 压缩机工作时压缩效率更高， 空调系统装设该压缩机之后， 冷冻出水温度在 12 ~ 20 °C之间， 节能效果更好， 有效的提高空调主机性能系数。 附图说明
图 1是装有本发明所述压缩机的空调机组的系统流程图；
图 2是图 1的局部放大图；
图 3是叶轮的立体图；
图 4是叶轮的端部视图；
图 5是叶轮的侧视图；
附图标记说明：
1、 压缩机、 2、 蒸发器， 3、 冷凝器， 4、 叶轮， 5、 转轴， 6、 主动齿轮， 7、 从动 齿轮， 8、 电机， 9、 轮盘， 10、 曲形叶片， 11、 进口端， 12、 出口端， 1 3、 外侧， 14、 内侧， 15、 节流板， 16、 电子膨胀阔。 具体实施方式
如图 2至图 5所示， 一种低压缩比的离心式压缩机， 包括叶轮 4、 转轴 5、 电机 8、 主动齿轮 6及从动齿轮 7 , 主动齿轮 6设于电机 8的输出轴上， 从动齿轮 7设于转轴 5 上且与主动齿轮 6啮合， 转轴 5与叶轮 4的轴心部位连接； 叶轮 4包括轮盘 9及多个曲 形叶片 10 , 多个曲形叶片 10沿轮盘 9周向均布， 该曲形叶片 10径向靠内的一端为进 口端 11、 径向靠外的一端为出口端 12 , 该曲形叶片 10靠近轮盘 9的一侧为外侧 1 3、 远离轮盘 9的一侧为内侧 14 ; 曲形叶片 10出口端 12相对于该出口端 12与轴心的连线 之间的夹度为 50至 60度，曲形叶片 10出口端 12的外侧 1 3与内侧 14的连线相对于轮 盘 9的轴线之间的夹角为 17至 23度。
其中，曲形叶片 10出口端 12相对于该出口端 12与轴心的连线之间的夹度为 55度， 曲形叶片 10出口端 12的外侧 1 3与内侧 14的连线相对于轮盘 9的轴线之间的夹角为 20度； 所述曲形叶片 10包括长叶片及短叶片， 长叶片及短叶片的数量相等， 且长叶片 与短叶片相互间隔设置； 主动齿轮 6的齿数为 128 , 从动齿轮 7的齿数为 43 , 即主动齿 轮 6与从动齿轮 Ί的齿数比为 128 : 43。
本发明由于对叶片及增速齿轮的传动比进行重新设计， 使得叶轮 4的压缩比较低， 同时工作也更稳定， 压缩机 1的压缩比低， 压缩效率高。
如图 1所示为装设有该压缩机 1的空调机组，换热工质在经压缩机 1压缩后进入到 冷凝器 3内冷凝并释放热量， 经冷凝的换热工质经节流装置 （即节流板 15和电子膨胀 阔 16 )的节流作用后， 再进入到蒸发器 1蒸发并吸收其中冷冻水的热量， 由于压缩机 1 的压缩比较低，满足整个机组在冷冻出水温度较高（ 12 ~ 20 °C )的工况下高效稳定运行， 节能效果好， 并可有效的提高空调的主机性能系数。 以上仅为本发明的较佳实施例， 并不以此限定本发明的保护范围； 在不违反本发明 构思的基础上所作的任何替换与改进， 均属本发明的保护范围。

Claims

权利要求 、 一种低压缩比的离心式压缩机， 包括叶轮、 转轴、 电机、 主动齿轮及从动齿轮， 主 动齿轮设于电机的输出轴上，从动齿轮设于转轴上且与主动齿轮啮合， 转轴与叶轮 的轴心部位连接； 叶轮包括轮盘及多个曲形叶片， 多个曲形叶片沿轮盘周向均布， 该曲形叶片径向靠内的一端为进口端、径向靠外的一端为出口端， 该曲形叶片靠近 轮盘的一侧为外侧、 远离轮盘的一侧为内侧， 其特征在于， 曲形叶片出口端相对于 该出口端与轴心的连线之间的夹度为 50至 60度，曲形叶片出口端的外侧与内侧的 连线相对于轮盘的轴线之间的夹角为 17至 23度。 、 如权利要求 1所述低压缩比的离心式压缩机， 其特征在于， 所述曲形叶片出口端相 对于该出口端与轴心的连线之间的夹度为 55度， 所述曲形叶片出口端的外侧与内 侧的连线相对于所述轮盘的轴线之间的夹角为 20度。 、 如权利要求 1或 2所述低压缩比的离心式压缩机， 其特征在于， 所述曲形叶片包括 长叶片及短叶片， 长叶片及短叶片的数量相等， 且长叶片与短叶片相互间隔设置。 、 如权利要求 1或 2所述低压缩比的离心式压缩机， 其特征在于， 所述主动齿轮与从 动齿轮的齿数比为 2. 5 : 1至 3: 1。 、 如权利要求 4所述低压缩比的离心式压缩机， 其特征在于， 所述主动齿轮的齿数为 128 , 所述从动齿轮的齿数为 43。 、 一种空调机组， 其特征在于包括：
如权利要求 1至 5任意一项所述的低压缩比的离心式压缩机、 冷凝器、 节流装置、 蒸发器， 各部分之间通过管路连接。
PCT/CN2010/075688 2009-08-11 2010-08-04 低压缩比的离心式压缩机及应用该压缩机的空调机组 WO2011018005A1 (zh)

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CN200910041765.9 2009-08-11

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CN109209927A (zh) * 2018-08-06 2019-01-15 黄华 一种离心压缩机

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CN102889237B (zh) * 2012-06-12 2015-04-22 中国科学院工程热物理研究所 一种应用带尖角前缘的大小叶片叶轮及压气机

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