WO2016019689A1 - 多级压缩机和空调器 - Google Patents

多级压缩机和空调器 Download PDF

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Publication number
WO2016019689A1
WO2016019689A1 PCT/CN2014/095185 CN2014095185W WO2016019689A1 WO 2016019689 A1 WO2016019689 A1 WO 2016019689A1 CN 2014095185 W CN2014095185 W CN 2014095185W WO 2016019689 A1 WO2016019689 A1 WO 2016019689A1
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Prior art keywords
stage
stage compressor
air
air supply
passage
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PCT/CN2014/095185
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English (en)
French (fr)
Inventor
钟瑞兴
张治平
刘华
蒋楠
王宏兴
蒋彩云
谢蓉
陈玉辉
刘建飞
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Publication of WO2016019689A1 publication Critical patent/WO2016019689A1/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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/14—Multi-stage pumps with means for changing the flow-path through the stages, e.g. series-parallel, e.g. side-loads

Definitions

  • the present invention relates to the field of air conditioner equipment, and more particularly to a multi-stage compressor and an air conditioner.
  • multi-stage centrifugal compressors In order to improve energy efficiency, multi-stage centrifugal compressors often use the technology of supplementing gas and increasing enthalpy, that is, adding a gas supply port to the compression stage bracket, and introducing the flash gas from the outside of the compressor into the compressor through the air supply port to achieve inter-stage gas supply.
  • the gas temperature is lowered before the gas enters the next-stage compression chamber, thereby reducing the power consumption of the next-stage compression and improving the energy efficiency of the compressor.
  • the structure of the multi-stage compressor is more and more compact, especially the volute adopts a forward-tilted structure, and the volute occupies a large space on the circumference, which makes the position of the air supply port more difficult, often
  • the wall surface of the supplementary air passage and the volute passage is too thin, which affects the strength and pressure bearing capacity of the compressor.
  • the air supply port is reduced, the compressor cannot be fully ventilated, and in some cases, the air supply may be caused.
  • the gas flow cannot be sufficiently mixed with the gas in the compression chamber, resulting in uneven temperature of the gas entering the second-stage compression chamber, which is not conducive to the compression of the gas.
  • the present invention is directed to a multi-stage compressor and an air conditioner to solve the problem that it is difficult to arrange an air supply passage in a compact multi-stage compressor structure of the prior art.
  • a multi-stage compressor including a first-stage compression chamber in which a first-stage impeller is located and a secondary compression chamber in which a secondary impeller is located, a first-stage compression chamber and a second-stage compression chamber.
  • the compression chambers are connected by an air passage
  • the multi-stage compressor further comprises: a casing, wherein at least a part of the first-stage compression chamber is formed in the casing; the casing body forms at least a part of the secondary compression chamber; the stage diffuser, and the shell Body connection; a gas supply passage for introducing a supplemental gas flow into the gas passage, a gas supply passage formed between the stage diffuser and the tank; an air supply chamber communicating with the gas supply passage and passing through the air inlet and the The air supply of the qi is connected, and the air chamber is enclosed between the casing, the box body and the stage diffuser.
  • the surface of the stage diffuser enclosing the air supply chamber has a rounded curved surface.
  • volume of the inflation chamber is greater than or equal to 10 times the volume of the supplemental passage.
  • the flow area of the supplemental gas passage gradually decreases along the flow direction of the supplemental gas flow.
  • the air inlet is opened on the casing in the axial or radial direction of the multi-stage compressor.
  • the air inlet is opened on the housing in the axial or radial direction of the multi-stage compressor.
  • the multi-stage compressor further includes a reflux baffle, the recirculation baffle has a U-shaped cross section of the air passage along the axial direction of the multi-stage compressor; and an air passage is formed between the stage diffuser and the return baffle; In the first stage, a second section of the air passage is formed between the box and the return baffle, and the first section and the second section are connected by a connecting section, and the supplemental air passage and the air passage are located radially outward of the return diaphragm. Connection segment connection.
  • the air supply passage is disposed obliquely inward with respect to the axis of the multi-stage compressor.
  • the angle between the air supply passage and the axis of the multi-stage compressor is less than or equal to 45 degrees.
  • an air conditioner comprising a multi-stage compressor which is the multi-stage compressor described above.
  • the multi-stage compressor of the present invention comprises a supplemental air passage for introducing a supplemental airflow into the air passage, and a supplemental air chamber for collecting the supplemental gas outside the multistage compressor.
  • the supplemental airflow is fully filled in the circumferential direction of the multistage compressor, the air supply pressure is kept uniform, and the air supply chamber is diffused by the casing, the casing and the stage.
  • the device is enclosed, and is not opened on the box or the casing.
  • the size of the air supply chamber is not limited by the wall thickness of the box or the casing, and the above-mentioned beneficial effects on the air supply flow can be fully utilized, so that the multi-stage compressor is Work efficiency is improved.
  • Figure 1 is a schematic cross-sectional view showing the two compression stages of the first multistage compressor of the present invention
  • Fig. 2 is a schematic cross-sectional view showing the two compression stages of the second multistage compressor of the present invention.
  • first stage impeller 10
  • first stage compression chamber 20
  • secondary impeller 20
  • secondary compression chamber 300
  • air passage 40
  • housing 50
  • box 50
  • Stage diffuser 400
  • air supply passage 500, air supply chamber; 501, first section; 502, second section; 600, air inlet; 30, return diaphragm.
  • a multi-stage compressor comprising a primary compression chamber 100 in which the primary impeller 10 is located and a secondary second stage in which the secondary impeller 20 is located.
  • the compression chamber 200, the first-stage compression chamber 100 and the secondary compression chamber 200 are connected through the air passage 300, wherein the multi-stage compressor further comprises: a housing 40, and at least a part of the first-stage compression chamber is formed in the housing 40. 100; a housing 50, at least a part of the secondary compression chamber 200 is formed in the housing 50; a stage diffuser 60 is connected to the housing 40; and a supplemental air passage 400 is provided for introducing a supplemental airflow into the air passage 300.
  • An air supply passage 400 is formed between the diffuser 60 and the tank 50; the air supply chamber 500 communicates with the air supply passage 400 and is connected to the air source for supplying air through the air inlet 600, and the housing 40 and the housing 50 An air supply chamber 500 is enclosed between the stage diffuser 60 and the stage diffuser 60.
  • the multi-stage compressor of the present invention includes a supplemental air passage 400 for introducing a supplemental airflow into the air passage 300, and an air supplementation chamber 500 for collecting a multi-stage compressor
  • the external supplemental gas is formed to form a supplemental airflow, and the supplemental airflow is decelerated, so that the supplemental airflow is fully filled in the circumferential direction of the multistage compressor, the supplemental air pressure is kept uniform, and the air supply chamber 500 is provided by the casing 50.
  • the casing 40 and the stage diffuser 60 are enclosed, and are not formed on the casing 50 or the casing 40.
  • the size of the air supply chamber 500 is not limited by the thickness of the casing 50 or the casing 40, and the above-mentioned
  • the beneficial effect on the makeup gas flow makes the working efficiency of the multi-stage compressor improved.
  • the surface of the stage diffuser 60 enclosing the air supply chamber 500 has a rounded curved surface.
  • the surface of the air supply chamber 500 includes a portion of the inner wall of the housing 40, a portion of the inner wall of the housing 50, and a portion or all of the outer wall of the stage diffuser 60.
  • the air supply chamber 500 includes a first section 501 and In the second segment 502, the supplemental airflow is decelerated and evenly distributed in the first segment 501, and the inner wall of the second segment 502 is rounded and curved, and the airflow is accelerated and enters the curve of the air passage 300 to reduce the air supply. The degree of interference between the airflow and the compressed airflow.
  • the supplemental air passage 400 is in a continuous annular shape along the circumference of the multi-stage compressor. This enables the air supply passage 400 to be in contact with the air passage 300 in the circumferential direction of the multi-stage compressor so that the makeup gas flow is sufficiently in contact with the compressed air flow in the circumferential direction, thereby causing the gas flowing into the secondary compression chamber 200. The temperature is even.
  • the flow area of the supplemental gas passage 400 gradually decreases along the flow direction of the supplemental gas flow.
  • the air supply passage 400 with a reduced flow area can accelerate and converge the air flow by utilizing the principle that the flow area is reduced and the speed is increased.
  • the volume of the supplemental air chamber 500 is greater than or equal to 10 times the volume of the supplemental air passage 400.
  • the air supply chamber 500 must have sufficient volume to ensure continuity and pressure stability of the supplemental airflow.
  • the air inlet 600 is formed in the housing 50 along the axial or radial direction of the multi-stage compressor.
  • the air inlet 600 is opened on the housing 40 in the axial or radial direction of the multi-stage compressor.
  • the position and orientation of the intake port 600 may vary depending on the overall arrangement of the multi-stage compressor. Since the air supply chamber 500 is no longer directly open in the various components of the multi-stage compressor, the intake port 600 can be more flexibly disposed.
  • the casing 40 and the casing 50 constitute part or all of the outer casing of the multi-stage compressor.
  • the casing 40 In the flow direction of the compressed gas, the casing 40 is located upstream of the casing 50, and the casing 40 is connected to the casing 50.
  • the gas passage 300 is located between the stage diffuser 60 and the tank 50.
  • the multi-stage compressor further includes a return baffle 30 which has a U-shaped cross section of the air passage 300 along the axial direction of the multi-stage compressor; the stage diffuser A first section of the air passage 300 is formed between the 60 and the return diaphragm 30, and a second section of the air passage 300 is formed between the box 50 and the return partition 30. The first section and the second section are connected by a connecting section.
  • the air supply passage 400 is connected to a connecting portion of the air passage 300 located radially outward of the return diaphragm 30.
  • the air supply passage 400 introduces the low temperature gas outside the compressor into the compressor and reduces the temperature of the original gas in the compressor.
  • the communication point of the air supply passage 400 is at the corner of the air passage 300, and the air passage 300 is in the air passage 300.
  • the gas is mixed with the gas in the air supply passage 400 at the corners, so that the two air flows can be mixed to the maximum extent, so that the airflow can be mixed as evenly as possible when flowing to the outlet of the air passage 300, thereby avoiding uneven temperature of the airflow. .
  • the supplemental air passage 400 is disposed inwardly obliquely with respect to the axis of the multi-stage compressor. Since the air supply passage 400 is disposed obliquely inward with respect to the axis of the multi-stage compressor, the air supply flow of the air supply passage 400 is also prevented from directly impinging the air flow in the air passage 300 to avoid turbulence.
  • the angle between the supplemental air passage 400 and the axis of the multi-stage compressor is less than or equal to 45 degrees. More preferably, the angle between the supplemental air passage 400 and the axis of the multi-stage compressor is 20 degrees for the sake of simple processing.
  • the above multistage compressor is preferably a multistage centrifugal compressor.
  • an air conditioner comprising a multi-stage compressor which is the multi-stage compressor described above. It is particularly noted that the air conditioner is preferably a centrifugal chiller.

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

Abstract

一种多级压缩机，包括一级叶轮（10）所在的一级压缩腔（100）和二级叶轮（20）所在的二级压缩腔（200），一级压缩腔（100）与二级压缩腔（200）之间通过过气通道（300）连接，该多级压缩机还包括：壳体（40），壳体（40）内形成至少一部分一级压缩腔（100）；箱体（50），箱体（50）内形成至少一部分二级压缩腔（200）；级扩压器（60），与壳体（40）连接；补气通道（400），用于向过气通道（300）内引入补气气流，级扩压器（60）与箱体（50）之间形成补气通道（400）；补气腔（500），与补气通道（400）连通并通过进气口（600）与用于补气的气源连接，壳体（40）、箱体（50）和级扩压器（60）之间围成补气腔（500）。具有该多级压缩机的空调器。由于补气腔由箱体、壳体和级扩压器围成，补气腔的大小不受箱体或壳体的壁厚限制，能够充分发挥补气气流的有益效果，使得多级压缩机的工作效率得到提高。

Description

多级压缩机和空调器 技术领域
本发明涉及空调器设备领域，更具体地，涉及一种多级压缩机和空调器。
背景技术
多级离心式压缩机为了提高能效，经常利用补气增焓技术，即在压缩级支架增加补气口，通过将压缩机的外部的闪发气体经过补气口引入压缩机内，实现级间补气，在气体进入下一级压缩腔之前将气体的温度降低，从而减小下一级压缩的功耗，提高压缩机的能效。
由于现代工艺的需求，多级压缩机的结构越来越紧凑，特别是蜗壳采用前倾的结构，蜗壳在圆周上占据很大的空间，造成补气口的位置布置变得更加困难，经常出现补气流道与蜗壳通道的壁面过薄，影响了压缩机的强度和承压能力，但补气口减小，则无法对压缩机进行充分的补气，某些情况下还会造成补气气流无法与压缩腔内的气体充分混合，导致进入第二级压缩腔的气体温度不均匀，不利于气体的压缩。
发明内容
本发明旨在提供一种多级压缩机和空调器，以解决现有技术的紧凑的多级压缩机结构难以布置补气通道的问题。
为解决上述技术问题，根据本发明的一个方面，提供了一种多级压缩机，包括一级叶轮所在的一级压缩腔和二级叶轮所在的二级压缩腔，一级压缩腔与二级压缩腔之间通过过气通道连接，多级压缩机还包括：壳体，壳体内形成至少一部分一级压缩腔；箱体，箱体内形成至少一部分二级压缩腔；级扩压器，与壳体连接；补气通道，用于向过气通道内引入补气气流，级扩压器与箱体之间形成补气通道；补气腔，与补气通道连通并通过进气口与用于补气的气源连接，壳体、箱体和级扩压器之间围成补气腔。
进一步地，级扩压器的围成补气腔的表面呈圆滑曲面。
进一步地，补气腔的容积大于或等于10倍的补气通道的容积。
进一步地，补气通道的流通面积沿补气气流的流通方向逐渐减小。
进一步地，进气口沿多级压缩机的轴向或径向开设在箱体上。
可替换地，进气口沿多级压缩机的轴向或径向开设在壳体上。
进一步地，多级压缩机还包括回流隔板，回流隔板使过气通道的沿多级压缩机的轴向的截面呈U形；级扩压器与回流隔板之间形成过气通道的第一段，箱体与回流隔板之间形成过气通道的第二段，第一段和第二段通过连接段连接，补气通道与过气通道的位于回流隔板的径向外侧的连接段连接。
进一步地，补气通道相对多级压缩机的轴线向内倾斜地设置。
进一步地，补气通道与多级压缩机的轴线间所呈角度小于或等于45度。
根据本发明的另一个方面，还提供了一种空调器，包括多级压缩机，多级压缩机是上述的多级压缩机。
本发明的多级压缩机包括补气通道和补气腔，其中补气通道用于向过气通道内通入补气气流，而补气腔则用于收集多级压缩机外部的补气气体以形成补气气流，并对补气气流进行降速，使补气气流在多级压缩机的圆周方向充分充盈，保持补气压力均匀，并且补气腔由箱体、壳体和级扩压器围成，并不是开设在箱体或壳体上，补气腔的大小不受箱体或壳体的壁厚限制，能够充分发挥上述对补气气流的有益效果，使得多级压缩机的工作效率得到提高。
附图说明
构成本申请的一部分的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示意性示出了本发明中的第一种多级压缩机的两个压缩级间的剖视图；
图2示意性示出了本发明中的第二种多级压缩机的两个压缩级间的剖视图。
图中附图标记：10、一级叶轮；100、一级压缩腔；20、二级叶轮；200、二级压缩腔；300、过气通道；40、壳体；50、箱体；60、级扩压器；400、补气通道；500、补气腔；501、第一段；502、第二段；600、进气口；30、回流隔板。
具体实施方式
以下结合附图对本发明的实施例进行详细说明，但是本发明可以由权利要求限定和覆盖的多种不同方式实施。
根据本发明的一个方面，提供了一种多级压缩机，如图1和2所示，该多级压缩机包括一级叶轮10所在的一级压缩腔100和二级叶轮20所在的二级压缩腔200，一级压缩腔100与二级压缩腔200之间通过过气通道300连接，其特征在于，多级压缩机还包括：壳体40，壳体40内形成至少一部分一级压缩腔100；箱体50，箱体50内形成至少一部分二级压缩腔200；级扩压器60，与壳体40连接；补气通道400，用于向过气通道300内引入补气气流，级扩压器60与箱体50之间形成补气通道400；补气腔500，与补气通道400连通并通过进气口600与用于补气的气源连接，壳体40、箱体50和级扩压器60之间围成补气腔500。
本发明的多级压缩机包括补气通道400和补气腔500，其中补气通道400用于向过气通道300内通入补气气流，而补气腔500则用于收集多级压缩机外部的补气气体以形成补气气流，并对补气气流进行降速，使补气气流在多级压缩机的圆周方向充分充盈，保持补气压力均匀，并且补气腔500由箱体50、壳体40和级扩压器60围成，并不是开设在箱体50或壳体40上，补气腔500的大小不受箱体50或壳体40的壁厚限制，能够充分发挥上述对补气气流的有益效果，使得多级压缩机的工作效率得到提高。
优选地，级扩压器60的围成补气腔500的表面呈圆滑曲面。如图1和2所示，补气腔500的表面包括壳体40的部分内壁、箱体50的部分内壁和级扩压器60的部分或全部外壁，补气腔500包括第一段501和第二段502，补气气流在第一段501内减速并均匀分布，而第二段502的内壁多成圆滑曲面，补气气流被加速并进入过气通道300的弯道处，降低补气气流与压缩气流的干扰程度。
优选地，补气通道400在沿多级压缩机的周向成连贯的环形。这样能够使得补气通道400能够在多级压缩机的周向与过气通道300均有接触，使得补气气流在圆周方向充分与压缩气流接触，从而使得流到二级压缩腔200内的气体温度均匀。
优选地，补气通道400的流通面积沿补气气流的流通方向逐渐减小。流通面积减小的补气通道400可以利用通流面积减小，提升速度的原理，对气流进行加速收敛。
优选地，补气腔500的容积大于或等于10倍的补气通道400的容积。补气腔500必须有足够的容积，以保障补气气流的连贯性与压力的稳定性。
优选地，在图1示出的实施例中，进气口600沿多级压缩机的轴向或径向开设在箱体50上。
可替换地，在图2示出的实施例中，进气口600沿多级压缩机的轴向或径向开设在壳体40上。
进气口600的位置和方向可以根据多级压缩机的整体设置而变化，由于补气腔500不再直接开设在多级压缩机的各个部件中，所以进气口600能够更加灵活的设置。
优选地，壳体40和箱体50构成多级压缩机的部分或全部外壳体，沿压缩气体的流通方向，壳体40位于箱体50的上游，壳体40与箱体50相连接，过气通道300位于级扩压器60与箱体50之间。
优选地，如图1和2所示，多级压缩机还包括回流隔板30，回流隔板30使过气通道300的沿多级压缩机的轴向的截面呈U形；级扩压器60与回流隔板30之间形成过气通道300的第一段，箱体50与回流隔板30之间形成过气通道300的第二段，第一段和第二段通过连接段连接，补气通道400与过气通道300的位于回流隔板30的径向外侧的连接段连接。
补气通道400以将压缩机外部的低温气体引入压缩机内部，并降低压缩机内原有气体的温度，补气通道400的连通点在过气通道300的弯角处，过气通道300内的气体在弯角处与补气通道400内的气体混合，能够最大程度地使两股气流混合，使得气流在流到过气通道300的出口时能够尽量混合均匀，避免出现气流温度不均匀的情况。
优选地，补气通道400相对多级压缩机的轴线向内倾斜地设置。由于补气通道400相对多级压缩机的轴线向内倾斜地设置，也避免补气通道400的补气气流直接冲击过气通道300内的气流，避免湍流的产生。
优选地，补气通道400与多级压缩机的轴线间所呈角度小于或等于45度。更优选地，出于加工工艺简单的考虑，补气通道400与多级压缩机的轴线间所呈角度为20度。
特别需要指出，上述多级压缩机优选地为多级离心式压缩机。
根据本发明的另一个方面，还提供了一种空调器，包括多级压缩机，多级压缩机是上述的多级压缩机。特别需要指出，该空调器优选地是离心式冷水机组。
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 (10)

  1. 一种多级压缩机，包括一级叶轮(10)所在的一级压缩腔(100)和二级叶轮(20)所在的二级压缩腔(200)，所述一级压缩腔(100)与所述二级压缩腔(200)之间通过过气通道(300)连接，其特征在于，所述多级压缩机还包括：
    壳体(40)，所述壳体(40)内形成至少一部分所述一级压缩腔(100)；
    箱体(50)，所述箱体(50)内形成至少一部分所述二级压缩腔(200)；
    级扩压器(60)，与所述壳体(40)连接；
    补气通道(400)，用于向所述过气通道(300)内引入补气气流，所述级扩压器(60)与所述箱体(50)之间形成所述补气通道(400)；
    补气腔(500)，与所述补气通道(400)连通并通过进气口(600)与用于补气的气源连接，所述壳体(40)、所述箱体(50)和所述级扩压器(60)之间围成所述补气腔(500)。
  2. 根据权利要求1所述的多级压缩机，其特征在于，所述级扩压器(60)的围成所述补气腔(500)的表面呈圆滑曲面。
  3. 根据权利要求1或2所述的多级压缩机，其特征在于，所述补气腔(500)的容积大于或等于10倍的所述补气通道(400)的容积。
  4. 根据权利要求1至3中任一项所述的多级压缩机，其特征在于，所述补气通道(400)的流通面积沿补气气流的流通方向逐渐减小。
  5. 根据权利要求1至4中任一项所述的多级压缩机，其特征在于，所述进气口(600)沿所述多级压缩机的轴向或径向开设在所述箱体(50)上。
  6. 根据权利要求1至5中任一项所述的多级压缩机，其特征在于，所述进气口(600)沿所述多级压缩机的轴向或径向开设在所述壳体(40)上。
  7. 根据权利要求1至6中任一项所述的多级压缩机，其特征在于，所述多级压缩机还包括回流隔板(30)，所述回流隔板(30)使所述过气通道(300)的沿所述多级压缩机的轴向的截面呈U形；所述级扩压器(60)与所述回流隔板(30)之间形成所述过气通道(300)的第一段，所述箱体(50)与所述回流隔板(30)之间形成所述过气通道(300)的第二段，所述第一段和所述第二段通过连接段 连接，所述补气通道(400)与所述过气通道(300)的位于所述回流隔板(30)的径向外侧的连接段连接。
  8. 根据权利要求7所述的多级压缩机，其特征在于，所述补气通道(400)相对所述多级压缩机的轴线向内倾斜地设置。
  9. 根据权利要求8所述的多级压缩机，其特征在于，所述补气通道(400)与所述多级压缩机的轴线间所呈角度小于或等于45度。
  10. 一种空调器，包括多级压缩机，其特征在于，所述多级压缩机是权利要求1至9中任一项所述的多级压缩机。
PCT/CN2014/095185 2014-08-07 2014-12-26 多级压缩机和空调器 Ceased WO2016019689A1 (zh)

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