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CN1121556C - 螺杆机械 - Google Patents

螺杆机械 Download PDF

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Publication number
CN1121556C
CN1121556C CN00137460A CN00137460A CN1121556C CN 1121556 C CN1121556 C CN 1121556C CN 00137460 A CN00137460 A CN 00137460A CN 00137460 A CN00137460 A CN 00137460A CN 1121556 C CN1121556 C CN 1121556C
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rotor
screw rod
rod mechanism
face
clearance
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CN1300904A (zh
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亚历山大·利夫森
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Carrier Corp
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Carrier Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/08—Axially-movable sealings for working fluids
    • F01C19/085—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or engines, e.g. gear machines or engines
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/086—Carter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines 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
    • F01C1/16—Rotary-piston machines or engines 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

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

Abstract

一螺杆机械(10)具有界定了重叠孔(13、15)的一转子壳体(12)。凹形转子(14)位于孔(13)中，而凸形转子(16)位于孔(15)中。排放箱(53)的相面对表面(51)或阴性和凸形转子的端面(24、26)中的任一个或两者都具有由互连壁构件(80)的网络分隔的多个分离的腔体(70)所形成的一表面。

Description

螺杆机械
在传统的螺杆机械中，设置在界定于一转子壳体中的各个平行的重叠孔中的一凸形转子和一凹形转子相互协作以封闭且压缩气体的体积。尽管这样的两个转子的结构是最普遍的设计，但具有三个或更多容纳在各个重叠孔中的转子以成对协作的螺杆机械在本领域中也是已知的。成对的阳性和凹形转子在它们的凸角外形和凸角及凹槽的数量方面是不同的。例如，凹形转子可具有被六个凹槽分隔的六个凸角；而共轭的凸形转子可具有被五个凹槽分隔的五个凸角。因此，转子之间凸角和凹槽协同作用的每一可能组合会周期性地发生。
典型螺杆机械的转子安装在每端的轴承中，以提供径向和轴向的约束。然而，在传统的实践中，在转子的端面和壳体的相面对表面之间必须设置沿轴向的一定量的余隙。需要设置端部运行余隙主要是因为压缩过程中被加热的气体所导致的转子的热膨胀。保持足量的所需端部余隙以确保在转子的端面和壳体的相面对表面之间不发生接触，这对于螺杆机械的可靠运作非常重要。此外，在运作中，在被压缩的流体中变化的压力通常沿轴向作用在转子上，这就会迫使转子向着螺杆机械的吸入端移动，从而增加端部运行余隙。
如果端部余隙太大，则在螺杆机械的排放端压缩流体通过运行余隙会发生过量的周向和径向泄漏，由此显著降低螺杆机械的总效率。在传统的注油螺杆机械中，通常向转子端面和壳体端板之间的端部运行余隙所界定的界面区域供油，来作为减小通过界面区域的气体泄漏的流体密封手段。但是，当端部运行余隙被减小时，因为转子端面和壳体端板之间的油中的粘滞摩擦力趋于增大，所以会降低效率。
如前面已指出，在运作中，因压缩过程中被加热的流体所导致的热量增加，转子沿轴向向着壳体的排放端处的端部壳体膨胀。转子的热膨胀趋于减小端部运行余隙。但是，在运作中，前面指出的轴向压力变化趋于沿轴向向着螺杆机械的吸入端推动转子，由此增加端部运行余隙。
因此，在传统的注油螺杆机械中，通常保持一定量的端部余隙以使摩擦损耗最小，并且在极端情况下防止转子滞塞故障。该滞塞可以是压缩过程中转子的热膨胀所导致的结果。而且，当端部运行余隙减小时，粘滞的摩擦力增加，并导致压缩机运行效率的降低。
如前面所指出，保持较大端部运行余隙的代价是压缩流体泄漏的随之增加。为了在传统的注油螺杆机械中保持较大的端部运行余隙，已知道可在转子的端面增加材料以给周边的气体泄漏提供物理阻碍。例如，细长杆可焊接在转子端面上，以沿着凸角的中心线或转子的焊接区径向延伸，由此伸过并桥接端部运行余隙的主要部分。
本发明的一目的是改进螺杆机械的运行效率。
本发明的另一目的是减小螺杆机械中通过转子端部运行余隙的泄漏。
在本发明的螺杆机械中，通过给穿越端部运行余隙的泄漏气体提供一连续的扩张和收缩路径来减小通过螺杆机械的端部运行余隙所造成的压缩气体的泄漏。在本发明的一个实施例中，转子端面的表面和/或壳体端板的相面对表面包含有被蜂窝状的各个腔体壁结构分隔的小型的分离的腔体表面，该蜂窝状的腔体壁结构被互连壁构件的网络所分隔。在穿越该表面时，当泄漏气体通过腔体和腔体壁时，泄漏气体必定重复地扩张和收缩，该过程可起到减小泄漏气流的作用。与传统的迷宫型密封件不同，传统的密封件仅沿一个方向提供密封，且实际上会导致通过迷宫型密封件所形成的沟槽而引起沿周向泄漏的增加，该表面的蜂窝状腔体结构给沿径向和周向的气体泄漏都提供了有效的密封。
本发明对于带有减量回流油运行的螺杆机械特别重要。在这些机械中，因为缺少密封泄漏路径的足量的油，所以难以获得良好的密封控制。
为了更完整地理解本发明，现参见以下对其各个实施例的详尽描述和附图，在附图中：
图1是横过一螺杆机械的横剖视图；
图2是图1所示螺杆机械的局部剖视图；
图3是图1所示螺杆机械的排放端的一部分的放大的视图；
图4是沿图3中的线4-4的转子的端视图，示出了转子端面的一个实施例；
图5是蜂窝状表面结构的一具体实施例的放大的视图；以及
图6是沿图3中的线6-6的壳体的端板的一端视图，示出本发明的另一实施例。
参见图1，其所示的是一螺杆机械10，例如螺杆式压缩机，它具有一转子壳体或外壳12，壳体12带有位于其内的重叠孔13和15。孔13和15分别沿平行的轴线A和B延伸。
在所示的实施例中，凹形转子14具有被六个凹槽分隔的六个凸角14A，而凸形转子16具有被五个凹槽分隔的五个凸角。凹形转子14和凸形转子16中的任一个可连接于一个发动机(图未示)且作为驱动转子。也可以使用其他数目的凸角和凹槽的组合。
现参见图2和图3，转子14具有一轴部23，轴部23带有沿径向向外形成在转子14的端部上的一端面24。转子14的轴部23被一个或多个轴承30支承在排放箱53中。相似地，转子16具有一轴部25，轴部25带有沿径向向外形成在转子16的端面上的一端面26。转子16的轴部25被一个或多个轴承31支承在排放箱53中。转子14和16的吸入侧的轴部27和29分别通过滚柱轴承32和33支承地接纳在转子壳体12中。
在运作中，例如作为制冷剂压缩机，假定凸形转子16为驱动转子，转子16转动啮合的转子14且致使其转动。设置在各个孔13和15中的转动的转子14和16的协作将制冷气体通过吸入进口18吸入到转子16和14的沟槽中，转子16和14的沟槽啮合以封闭和压缩气体的体积，并将压缩后的热气传送到排放口19。由于此前所讨论的原因，在转子14和16的排放端处的端面24和26分别与排放箱53的端板55的相面对表面51之间必须保持一端部运行余隙60。该端部运行余隙60被定义为转子端面24和26的最近界面与端板55的相面对表面51之间的区域。该端部运行余隙60在转子端面24和26与排放箱53的端板55之间沿周向和径向建立起潜在的气体泄漏路径。在传统的注油压缩机中，自然流入到端部运行余隙60中的润滑油起到密封的作用，能够减少通过端部运行余隙的气体泄漏。
在本发明的螺杆机械中，通过提供一迂回曲折的泄漏路径来减少通过螺杆式压缩机的端部运行余隙所造成的压缩气体的泄漏，在该迂回曲折的泄漏路径中通过端部运行余隙发生连续的扩张和收缩。在图4所示的本发明实施例中，转子端面24和26的表面包括一蜂窝状的表面65。如图5所示，表面65包括被各个腔体壁构件80分隔开的多个小型的分离的腔体70。在横穿端部运行余隙60时，泄漏的气体必须越过转子表面24和26上的蜂窝状表面65。这样做时，当泄漏气体越过腔体和腔体壁时，泄漏气体反复地扩张和收缩，该过程起到减小泄漏气流的作用。
在图6所示的本发明实施例中，排放箱53的端板55的相面对表面51包括一蜂窝状的表面65，如同图5所示，该表面65包括被各个腔体壁80分隔开的多个小型的分离的腔体70。当横穿端部运行余隙60时，泄漏的气体必须越过排放箱53的端板55的相面对表面51上的蜂窝状表面65。这样做时，当泄漏气体越过腔体70和腔体壁80时，泄漏气体反复地扩张和收缩，该过程起到减小泄漏气流的作用。
与仅沿一个方向提供密封的传统的迷宫型密封件不同，该表面的蜂窝状图案的腔体结构对于沿径向和周向的气体泄漏都提供了有效的密封。应理解到，蜂窝状的结构是指被互连的壁构件80的网络所分隔的多个分离的开放腔体70。实际上腔体不一定要与蜂窝相关的六边形蜂房相象。对于本发明，不论腔体70的开放区域的深度，还是其形状和尺寸要求都不严格，这些应当是设计时所要选择的事情。
尽管已通过两相似转子的螺杆机械对本发明作了具体描述，但本发明也可应用于使用三个或更多转子的螺杆机械。因此，本发明仅被所附权利要求书的范围限制。

Claims (3)

1.一种螺杆机械，它包括界定了至少一对平行的重叠孔的一壳体、具有一相面对表面的一排放箱、以及位于至少一对孔中的一对共轭的相互啮合的转子，每个所述转子具有一端面，所述转子的所述端面与排放箱的所述相面对表面分隔开，并在此界定了一端部运行余隙；其特征在于：所述转子端面和排放箱的所述相面对表面中至少一个表面包括被互连壁构件的网络分隔的多个分离的腔体。
2.如权利要求1所述的螺杆机械，其特征在于：被互连壁构件的网络分隔的所述多个分离的腔体形成在每个所述转子端面上。
3.如权利要求1所述的螺杆机械，其特征在于：被互连壁构件的网络分隔的所述多个分离的腔体形成在排放箱的相面对表面上。
CN00137460A 1999-12-20 2000-12-20 螺杆机械 Expired - Fee Related CN1121556C (zh)

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US09/467,266 US6290480B1 (en) 1999-12-20 1999-12-20 Screw machine
US09/467,266 1999-12-20

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CN1121556C true CN1121556C (zh) 2003-09-17

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EP (1) EP1111187A3 (zh)
JP (1) JP2001193678A (zh)
KR (1) KR100378933B1 (zh)
CN (1) CN1121556C (zh)
AU (1) AU744102B2 (zh)
BR (1) BR0005950B1 (zh)
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US6290480B1 (en) 2001-09-18
KR100378933B1 (ko) 2003-04-08
AU744102B2 (en) 2002-02-14
EP1111187A2 (en) 2001-06-27
KR20010067412A (ko) 2001-07-12
CN1300904A (zh) 2001-06-27
EP1111187A3 (en) 2002-05-02
JP2001193678A (ja) 2001-07-17
TW482877B (en) 2002-04-11
BR0005950A (pt) 2001-07-17
AU7234200A (en) 2001-06-21
BR0005950B1 (pt) 2008-11-18

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