WO2011134261A1 - 螺杆压缩机 - Google Patents

螺杆压缩机 Download PDF

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Publication number
WO2011134261A1
WO2011134261A1 PCT/CN2010/079353 CN2010079353W WO2011134261A1 WO 2011134261 A1 WO2011134261 A1 WO 2011134261A1 CN 2010079353 W CN2010079353 W CN 2010079353W WO 2011134261 A1 WO2011134261 A1 WO 2011134261A1
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WO
WIPO (PCT)
Prior art keywords
air supply
screw compressor
air
male rotor
economizer
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
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PCT/CN2010/079353
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English (en)
French (fr)
Inventor
汤炎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shanghai Power Technology Screw Machinery Co Ltd
Original Assignee
Shanghai Power Technology Screw Machinery Co Ltd
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Publication date
Application filed by Shanghai Power Technology Screw Machinery Co Ltd filed Critical Shanghai Power Technology Screw Machinery Co Ltd
Priority to US13/148,943 priority Critical patent/US20120058001A1/en
Priority to EP10850592.6A priority patent/EP2565456B1/en
Publication of WO2011134261A1 publication Critical patent/WO2011134261A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet

Definitions

  • the invention belongs to the technical field of compressors, relates to a screw compressor, and more particularly to a screw compressor including an economizer. Background technique
  • the screw compressor consists of a pair of parallel, intermeshing male and female screws, which is the most widely used type of rotary compressor.
  • a power-saving circulation system with an economizer is usually used. See Figure 1 and Figure 2 for the refrigeration cycle with economizer.
  • Figure 1 discloses a heat exchanger-type economizer refrigeration cycle system; wherein, the left diagram in Figure 1 is a schematic diagram of the composition of a heat exchanger-type economizer refrigeration cycle system, and the right-hand diagram shows the pressure of a heat exchanger-type economizer refrigeration cycle system. - Cut the map.
  • Figure 2 shows the flash-type economizer refrigeration cycle system; wherein, the left picture in Figure 2 is the composition diagram of the flash-type economizer refrigeration cycle system, and the right picture shows the pressure- ⁇ diagram of the flash-type economizer refrigeration cycle system. .
  • FIG 4 is a schematic diagram of the primary air supply of the economizer of the existing radial setting ventilator.
  • dl is the width of the plenum
  • al is the distance between the spirals of the two adjacent rotor tips, corresponding to the corner of a groove. It can be seen that the angle of rotation of the radial intake is always greater than the angle of rotation of a groove.
  • the technical problem to be solved by the present invention is to provide a screw compressor which can add a gaseous refrigerant to the current compression chamber in a shorter time, and eliminate or reduce the potential reverse return flow.
  • the present invention adopts the following technical solutions:
  • the compressor is connected to an economizer; the economizer is connected with at least one air supply hole, and the air supply hole is disposed on a compressor exhaust end seat; the economizer is from a rotor exhaust end surface, Fill the air along the axial direction of the rotor.
  • the contour of the air vent is coincident with the rotor tooth shape and the root circle.
  • the two sides of the cross section of the air plenum are respectively matched with a part of the sides of the compressor rotor; the first side of the male rotor is rotated to the first boundary of the air vent, When the air supply is about to start, the first boundary of the air plenum is mostly coincident with the corresponding portion of the first side of the male rotor; the second side of the male rotor is rotated to the second boundary of the air vent, which is about to be disconnected from the air vent.
  • the second boundary of the air vent is mostly coincident with the corresponding portion of the second side of the male rotor.
  • the air venting holes are triangular or circular or rectangular or flat stripe.
  • the economizer is provided with a plurality of air supply holes, and the plurality of air supply holes are evenly disposed on the compressor exhaust end seat.
  • the screw compressor is a twin screw compressor or a three screw compressor.
  • the qi process of the screw compressor includes:
  • the male rotor tooth groove is disconnected from the compressor air supply hole
  • the male rotor rotates to a boundary of the air supply hole, and the air supply is about to start, that is, the male rotor tooth groove is about to communicate with the economical air supply hole;
  • the male rotor rotates to the other boundary of the air supply hole, and the air supply ends, and the male rotor tooth groove and the economizer air supply hole are disengaged;
  • step Sl the screw compressor proposed by the invention can be in a shorter time
  • the gaseous refrigerant is replenished into the current compression chamber to eliminate or reduce the potential for reverse flow; thereby artificially improving the performance of the economizer system.
  • Figure 1 is a schematic diagram of a heat exchanger type economizer refrigeration cycle system.
  • Figure 2 is a schematic diagram of a flashing economizer refrigeration cycle system.
  • Fig. 3 is a structural schematic view of the radial enrichment of the air inlet of the existing economizer.
  • FIG. 4 is a schematic view showing the primary air supply process of the economizer of the existing radial setting air purifying hole.
  • FIG. 5 is a schematic view showing the outline of a gas filling hole according to an embodiment of the present invention.
  • FIG. 6 is a schematic view showing the outline of a gas filling hole according to another embodiment of the present invention.
  • Fig. 7 is a schematic view showing the position of the male rotor tooth groove and the suction hole.
  • Fig. 8 is a schematic view showing the position of the male rotor tooth groove when it is in communication with the suction hole.
  • Fig. 9 is a schematic view showing the position of the male rotor cogging in communication with the suction hole.
  • Fig. 10 is a schematic view showing the position of the male rotor tooth groove and the suction hole being disengaged.
  • Figure 11 is a schematic diagram of the rotational distance of the aerator's primary air-filled rotor.
  • Figure 12 is a partial structural view of a screw compressor of the present invention.
  • Figure 13 is a schematic view showing the position of the suction hole of the screw compressor of the present invention. detailed description
  • the present invention discloses a screw compressor which mainly includes a body 20, and a male rotor 30 and a female rotor 40 in the body 20.
  • the compressor is connected to an economizer; the economizer is connected to at least one air supply hole 10, and the air supply hole 10 is disposed on the compressor exhaust end seat 50.
  • the economizer is ventilated from the exhaust end face of the male rotor 30 and axially along the male rotor 30.
  • the screw compressor is a twin screw compressor or a three screw compressor.
  • the contour of the air vent is matched with the rotor tooth shape and the root circle.
  • the two sides of the cross section of the venting hole are respectively matched with a part of the sides of the compressor rotor; the first side of the male rotor is rotated to the first boundary of the venting hole, and the venting hole is about to start.
  • a boundary 101 is mostly coincident with a corresponding portion of the first side of the male rotor; when the second side of the male rotor is rotated to the second boundary of the air filling hole, that is, when the air filling hole is to be disconnected, the second boundary 102 of the air filling hole is large.
  • the portion coincides with the corresponding portion of the second side of the male rotor; the majority of the bottom edge 103 of the air vent is coincident with the root of the male rotor.
  • the air venting holes may also be substantially triangular or circular or rectangular or flat strip. See Figure 6, Figure 6 for a profile of the air vent.
  • the economizer may be provided with a plurality of air supply holes, and the plurality of air supply holes are evenly disposed on the compressor exhaust end seat.
  • the qi process of the screw compressor includes:
  • the male rotor rotates to a boundary of the air supply hole, and the air supply is about to start, that is, the male rotor tooth groove is about to communicate with the economizer air hole (as shown in Fig. 8);
  • the male rotor gradually rotates to the other boundary of the air supply hole (as shown in Fig. 10). At this time, the air supply is closed, and the male rotor tooth groove is disengaged from the economizer air supply hole;
  • the rotation angle of the air inlet hole is not smaller than the rotor tooth area, and the rotation angle is always smaller than the rotation angle of the rotor end.
  • Kal, al corresponds to the corner of a groove); and the angle of the radial intake is always greater than the angle of a groove. Therefore, compared to the radial intake, the axial intake can fill the current compression chamber in the shortest time, thus optimizing the performance.
  • the screw compressor proposed by the present invention can replenish the gaseous refrigerant into the current compression chamber in a shorter time, eliminating or less potential reverse flow; thereby artificially improving the performance of the economizer system.
  • the description and application of the present invention are intended to be illustrative, and not intended to limit the scope of the invention. Variations and modifications of the embodiments disclosed herein are possible, and various alternative and equivalent components of the embodiments are well known to those of ordinary skill in the art. It is apparent to those skilled in the art that the present invention may be embodied in other forms, configurations, arrangements, ratios, and other components, materials and components without departing from the spirit or essential characteristics of the invention. Other variations and modifications of the embodiments disclosed herein may be made without departing from the scope and spirit of the invention.

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

Description

螺杆压缩机 技术领域
本发明属于压缩机技术领域， 涉及一种螺杆压缩机， 尤其涉及一种包括 经济器的螺杆压缩机。 背景技术
螺杆压缩机由一对平行、 互相啮合的阴、 阳螺杆构成， 是回转压缩机中 应用最广泛的一种。 为了提高压缩机的工作效率， 通常使用带经济器的节电 循环系统。 带有经济器的制冷循环系统可参阅图 1、 图 2。 图 1揭示了换热器 式经济器制冷循环系统； 其中， 图 1 中的左图为换热器式经济器制冷循环系 统的组成示意图， 右图为换热器式经济器制冷循环系统的压-焓图。 图 2揭示 了闪发式经济器制冷循环系统； 其中， 图 2 中的左图为闪发式经济器制冷循 环系统的组成示意图， 右图为闪发式经济器制冷循环系统的压-焓图。
请参阅图 3， 现有的螺杆式压缩机的经济器补气孔都是径向设置的。 图 4 为现有径向设置经济器补气孔的经济器一次补气的示意图。
由图 4可知， 转子完成一次补气， 需要旋转的角度为图 4中转子末端旋 转 dl+al距离对应的中心角。 其中， dl为补气孔宽度； al为两相邻转子齿顶 螺旋线之间的距离， 对应一个螺槽的转角。 由此可见， 径向进气的转角总是 会大于一个螺槽的转角。
上述经济器补气孔径向设置的缺陷在于： 螺杆式压缩机补气过程时间长， 会导致气体的潜在回流， 从而造成管道震动、 补气口位置发热、 噪声高等一 系列影响性能的不利结果。 发明内容
本发明所要解决的技术问题是： 提供一种螺杆压缩机， 可以在更短时间 内将气态制冷工质补入当前压缩腔， 消除或减少潜在反向回流的气流。 为解决上述技术问题， 本发明采用如下技术方案：
一种螺杆压缩机， 所述压缩机连接一经济器； 所述经济器连有至少一补 气孔， 所述补气孔设置于压缩机排气端座上； 所述经济器从转子排气端面、 沿转子轴向补气。
作为本发明的一种优选方案， 所述补气孔的轮廓与转子齿形、 齿根圆相 吻合。
作为本发明的一种优选方案， 所述补气孔横截面的两侧边分别与压缩机 阳转子两侧边的一部分相吻合； 使得阳转子的第一侧边旋转到补气孔的第一 边界、 即将开始补气时， 补气孔的第一边界大部分与阳转子的第一侧边的相 应部分吻合； 阳转子的第二侧边旋转到补气孔的第二边界、 即将与补气孔断 开时， 补气孔的第二边界大部分与阳转子的第二侧边的相应部分吻合。
作为本发明的一种优选方案， 所述补气孔为三角形或圆形或矩形或扁条 形。
作为本发明的一种优选方案， 所述经济器设置多个补气孔， 所述多个补 气孔均匀地设置于压缩机排气端座上。
作为本发明的一种优选方案， 所述螺杆压缩机为双螺杆压缩机或三螺杆 压缩机。
作为本发明的一种优选方案， 所述螺杆压缩机的补气过程包括：
51、 阳转子齿槽与压缩机补气孔断开；
52、 阳转子旋转到补气孔的一边界， 即将开始补气， 即阳转子齿槽即将 与经济器补气孔联通；
53、 阳转子继续旋转， 到达补气孔最大面积补气；
54、 阳转子旋转到补气孔的另一边界， 补气结束， 阳转子齿槽与经济器 补气孔脱开；
55、 转歩骤 Sl， 直至补气结束。 本发明的有益效果在于： 本发明提出的螺杆压缩机， 可以在更短时间内 将气态制冷工质补入当前压缩腔， 消除或将少潜在的反向气流； 从而人为改 进经济器系统的性能。 附图说明
图 1为换热器式经济器制冷循环系统示意图。
图 2为闪发式经济器制冷循环系统示意图。
图 3为现有经济器补气孔径向补气的结构示意图。
图 4为现有径向设置经济器补气孔的经济器一次补气过程的示意图。 图 5为本发明一种实施方式下补气孔的外形轮廓示意图。
图 6为本发明另一种实施方式下补气孔的外形轮廓示意图。
图 7为阳转子齿槽与吸气孔断开时的位置示意图。
图 8为阳转子齿槽即将与吸气孔联通时的位置示意图。
图 9为阳转子齿槽与吸气孔联通时的位置示意图。
图 10为阳转子齿槽与吸气孔脱开时的位置示意图。
图 11为经济器一次补气阳转子旋转距离的示意图。
图 12为本发明螺杆压缩机局部的结构示意图。
图 13为本发明螺杆压缩机吸气孔的位置示意图。 具体实施方式
下面结合附图详细说明本发明的优选实施例。
实施例一
请参阅图 12、 图 13， 本发明揭示了一种螺杆压缩机， 所述螺杆压缩机主 要包括机体 20， 以及机体 20内的阳转子 30、 阴转子 40。 所述压缩机连接一 经济器； 所述经济器连有至少一补气孔 10， 所述补气孔 10设置于压缩机排气 端座 50上。 所述经济器从阳转子 30排气端面、 沿阳转子 30轴向补气。 所述 螺杆压缩机为双螺杆压缩机或三螺杆压缩机。
请参阅图 5， 所述补气孔的轮廓与转子齿形、 齿根圆相吻合。 具体地， 所 述补气孔横截面的两侧边分别与压缩机阳转子两侧边的一部分相吻合； 使得 阳转子的第一侧边旋转到补气孔的第一边界、 即将开始补气时， 补气孔的第 一边界 101 大部分与阳转子的第一侧边的相应部分吻合； 阳转子的第二侧边 旋转到补气孔的第二边界、 即将与补气孔断开时， 补气孔的第二边界 102大 部分与阳转子的第二侧边的相应部分吻合； 补气孔的底边 103 的大部分与阳 转子的齿根圆吻合。
当然， 所述补气孔还可以大致呈三角形或圆形或矩形或扁条形。 请参阅 图 6， 图 6揭示了补气孔的一种外形轮廓图。
此外， 所述经济器可以设置多个补气孔， 所述多个补气孔均匀地设置于 压缩机排气端座上。
所述螺杆压缩机的补气过程包括：
51、 阳转子齿槽与压缩机补气孔断开 （如图 7所示）；
52、 阳转子旋转到补气孔的一边界， 即将开始补气， 即阳转子齿槽即将 与经济器补气孔联通 （如图 8所示）；
53、 阳转子继续旋转， 到达补气孔最大面积补气 （如图 9所示）；
54、 阳转子逐渐旋转到补气孔的另一边界 （如图 10所示）， 本次补气结 束， 阳转子齿槽与经济器补气孔脱开；
55、 转歩骤 Sl， 直至补气结束。
请参阅图 11， 由于是从阳转子排气端面补气， 即轴向补气， 在补气孔孔 口面积不大于转子齿形面积时其转角总小于一个螺槽的转角 （转子末端的旋 转距离 Kal， al 则对应一个螺槽的转角）； 而径向进气的转角总是会大于一 个螺槽的转角。 因此相比于径向进气， 轴向进气就能够在最短的时间内将气 体补入当前压缩腔， 从而使得性能最优。 综上所述， 本发明提出的螺杆压缩机， 可以在更短时间内将气态制冷工 质补入当前压缩腔， 消除或将少潜在的反向气流； 从而人为改进经济器系统 的性能。 这里本发明的描述和应用是说明性的， 并非想将本发明的范围限制在上 述实施例中。 这里所披露的实施例的变形和改变是可能的， 对于那些本领域 的普通技术人员来说实施例的替换和等效的各种部件是公知的。 本领域技术 人员应该清楚的是， 在不脱离本发明的精神或本质特征的情况下， 本发明可 以以其它形式、 结构、 布置、 比例， 以及用其它组件、 材料和部件来实现。 在不脱离本发明范围和精神的情况下， 可以对这里所披露的实施例进行其它 变形和改变。

Claims

权利 要 求书 、 一种螺杆压缩机， 其特征在于， 所述压缩机连接一经济器； 所述经济器连 有至少一补气孔， 所述补气孔设置于压缩机排气端座上； 所述经济器从转 子排气端面、 沿转子轴向补气。 、 根据权利要求 1所述的螺杆压缩机， 其特征在于：
所述补气孔的轮廓与转子齿形、 齿根圆相吻合。 、 根据权利要求 1所述的螺杆压缩机， 其特征在于：
所述补气孔横截面的两侧边分别与压缩机阳转子两侧边的一部分相 吻合；
使得阳转子的第一侧边旋转到补气孔的第一边界、 即将开始补气时， 补气孔的第一边界大部分与阳转子的第一侧边的相应部分吻合；
阳转子的第二侧边旋转到补气孔的第二边界、 即将与补气孔断开时， 补气孔的第二边界大部分与阳转子的第二侧边的相应部分吻合。 、 根据权利要求 1所述的螺杆压缩机， 其特征在于：
补气孔的底边的大部分与阳转子的齿根圆吻合。 、 根据权利要求 1所述的螺杆压缩机， 其特征在于：
所述补气孔为三角形或圆形或矩形或扁条形。 、 根据权利要求 1或 2或 3或 4或 5所述的螺杆压缩机， 其特征在于： 所述经济器设置多个补气孔，所述多个补气孔均匀地设置于压缩机排 气端座上。 、 根据权利要求 1或 2或 3或 4或 5所述的螺杆压缩机， 其特征在于： 所述螺杆压缩机为双螺杆压缩机或三螺杆压缩机。 、 根据权利要求 1所述的螺杆压缩机， 其特征在于：
所述螺杆压缩机的补气过程包括：
51、 阳转子齿槽与压缩机补气孔断开；
52、 阳转子旋转到补气孔的一边界， 即将开始补气， 即阳转子齿槽即 将与经济器补气孔联通；
53、 阳转子继续旋转， 到达补气孔最大面积补气；
54、 阳转子旋转到补气孔的另一边界， 补气结束， 阳转子齿槽与经济 器补气孔脱开；
55、 转歩骤 Sl， 直至补气结束。
PCT/CN2010/079353 2010-04-26 2010-12-01 螺杆压缩机 Ceased WO2011134261A1 (zh)

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