CN108457707A - A kind of turbine axle end sealing device applied to card Linne power circulation system - Google Patents
A kind of turbine axle end sealing device applied to card Linne power circulation system Download PDFInfo
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- CN108457707A CN108457707A CN201810210936.5A CN201810210936A CN108457707A CN 108457707 A CN108457707 A CN 108457707A CN 201810210936 A CN201810210936 A CN 201810210936A CN 108457707 A CN108457707 A CN 108457707A
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- 238000007789 sealing Methods 0.000 title claims abstract description 89
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 29
- 230000003068 static effect Effects 0.000 claims abstract description 27
- 230000001105 regulatory effect Effects 0.000 claims abstract description 22
- 238000005086 pumping Methods 0.000 claims description 22
- 230000007423 decrease Effects 0.000 claims description 8
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 abstract description 8
- 229910021529 ammonia Inorganic materials 0.000 abstract description 4
- 238000005260 corrosion Methods 0.000 abstract description 3
- 230000007797 corrosion Effects 0.000 abstract description 3
- 230000000694 effects Effects 0.000 description 5
- VHUUQVKOLVNVRT-UHFFFAOYSA-N Ammonium hydroxide Chemical compound [NH4+].[OH-] VHUUQVKOLVNVRT-UHFFFAOYSA-N 0.000 description 4
- 235000011114 ammonium hydroxide Nutrition 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000010248 power generation Methods 0.000 description 3
- 231100000331 toxic Toxicity 0.000 description 2
- 230000002588 toxic effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000008447 perception Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
- F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
- F01D11/06—Control thereof
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
Abstract
本发明提供一种应用于卡琳娜动力循环系统的透平轴端密封装置，包括螺旋密封系统和水密封系统；螺旋密封系统包括螺旋轴套、静套、集漏腔、密封腔和机械密封；螺旋轴套嵌在卡琳娜动力循环透平的主轴上，静套与螺旋轴套呈间隙套设在主轴的同一端形成螺旋密封，静套密封端与主轴端部形成密封腔，静套开口端内与主轴形成一个空腔作为集漏腔，静套和主轴之间设置的机械密封位于集漏腔内；主轴转动时，螺旋轴套转动向密封腔加压；水密封系统包括增压泵、调节阀和水箱；水箱的输入端与集漏腔连通，输出端依次经增压泵和调节阀连通设置在螺旋轴套和静套间隙末端。通过机械密封、水密封和螺旋密封三级密封，避免了富氨蒸汽与机械结构接触导致腐蚀的问题。
The invention provides a turbine shaft end sealing device applied to the Karina power cycle system, including a screw sealing system and a water sealing system; the screw sealing system includes a screw shaft sleeve, a static sleeve, a leakage chamber, a sealing chamber and a mechanical seal ;The screw shaft sleeve is embedded on the main shaft of the Karina power cycle turbine, and the static sleeve and the screw sleeve are set at the same end of the main shaft in a gap to form a spiral seal. The sealing end of the static sleeve and the end of the main shaft form a sealing cavity, and the static sleeve A cavity is formed between the open end and the main shaft as a leak collection chamber, and the mechanical seal provided between the static sleeve and the main shaft is located in the leakage collection chamber; when the main shaft rotates, the spiral sleeve rotates to pressurize the sealing chamber; the water sealing system includes a pressurized A pump, a regulating valve and a water tank; the input end of the water tank is communicated with the leakage chamber, and the output end is connected to the end of the gap between the spiral shaft sleeve and the static sleeve through the booster pump and the regulating valve in turn. Through mechanical seal, water seal and screw seal three-stage seal, the problem of corrosion caused by contact between rich ammonia vapor and mechanical structure is avoided.
Description
技术领域technical field
本发明涉及卡琳娜动力循环系统，具体为一种应用于卡琳娜动力循环系统的透平轴端密封装置。The invention relates to a Karina power cycle system, in particular to a turbine shaft end sealing device applied to the Karina power cycle system.
背景技术Background technique
卡琳娜低品位热源发电系统以氨水混合物代替传统的水或水蒸汽作为循环工质，将低品位热能转化为高品位电能。卡琳娜低品位热源发电系统主要由蒸发器，分离器，透平，发电机，冷凝器和增压泵组成。Kalina's low-grade heat source power generation system uses ammonia-water mixture instead of traditional water or steam as a circulating working medium to convert low-grade heat energy into high-grade electric energy. Karina low-grade heat source power generation system is mainly composed of evaporator, separator, turbine, generator, condenser and booster pump.
目前，限制卡琳娜循环发电技术推广的一大因素便是其工质泄漏问题。氨水具有毒性、腐蚀性和强挥发性，一旦发生泄漏，会极大影响系统的安全性。因此，卡琳娜动力循环对密封有着非常严苛的要求：能保持较低的泄漏量甚至零泄漏以及更长的使用寿命。传统的刷式密封、机械密封、迷宫密封都无法保障零泄漏，且会腐蚀密封结构。与传统机械密封相比，螺旋密封具有非接触型的特点，它通过在轴或静套上开矩形、三角形或圆形等规则与不规则槽来实现非接触性。采用螺旋密封结构时，主轴的高速旋转会带动动静套之间毫米甚至微米量级厚度的粘性流体一同旋转，由于粘性力的存在，不仅能在间隙间产生一定的液膜加强端面间的润滑和密封，更重要的是产生泵送效应，当泵送效应等于被密封介质的压力时，则实现了密封的效果。螺旋密封的非接触特点使其工作寿命大大延长，特别适用于易燃、易爆、剧毒、有腐蚀性工质的密封。在卡琳娜动力循环系统实际运行过程中，由于透平发生变工况运行会使得螺旋密封无法跟踪汽缸内压力变化。螺旋密封由于工作条件等因素的影响会使其密封能力降低甚至失效，导致氨水工质泄漏造成经济损失和环境污染等。At present, a major factor limiting the promotion of the Karina cycle power generation technology is the leakage of its working fluid. Ammonia water is toxic, corrosive, and highly volatile. Once leaked, it will greatly affect the safety of the system. Therefore, the Karina power cycle has very strict requirements on the seal: it can maintain a low leakage or even zero leakage and a longer service life. Traditional brush seals, mechanical seals, and labyrinth seals cannot guarantee zero leakage, and will corrode the sealing structure. Compared with the traditional mechanical seal, the spiral seal has the characteristics of non-contact type. It realizes non-contact by opening regular and irregular grooves such as rectangles, triangles or circles on the shaft or static sleeve. When the spiral seal structure is adopted, the high-speed rotation of the main shaft will drive the viscous fluid with a thickness of millimeter or even micron between the dynamic and static sleeves to rotate together. Due to the existence of viscous force, not only a certain liquid film can be generated in the gap to strengthen the lubrication between the end faces and Sealing, more importantly, produces a pumping effect. When the pumping effect is equal to the pressure of the sealed medium, the sealing effect is achieved. The non-contact feature of the spiral seal greatly prolongs the working life, and is especially suitable for the sealing of flammable, explosive, highly toxic and corrosive working fluids. During the actual operation of the Karina power cycle system, the screw seal cannot track the pressure change in the cylinder due to the variable operating conditions of the turbine. Due to the influence of working conditions and other factors, the screw seal will reduce its sealing ability or even fail, resulting in economic loss and environmental pollution caused by the leakage of ammonia working fluid.
发明内容Contents of the invention
针对现有技术中存在的问题，本发明提供一种应用于卡琳娜动力循环系统的透平轴端密封装置，结构简单，设计合理，不仅能依靠主轴的高速旋转产生泵送效应，并且其利用水作为密封介质，避免了富氨蒸汽与机械结构接触导致的腐蚀。Aiming at the problems existing in the prior art, the present invention provides a turbine shaft end sealing device applied to the Karina power cycle system. Using water as the sealing medium avoids the corrosion caused by the contact between the rich ammonia vapor and the mechanical structure.
本发明是通过以下技术方案来实现：The present invention is achieved through the following technical solutions:
一种应用于卡琳娜动力循环系统的透平轴端密封装置，包括螺旋密封系统和水密封系统；A turbine shaft end sealing device applied to the Karina power cycle system, including a screw sealing system and a water sealing system;
所述的螺旋密封系统包括螺旋轴套、静套、集漏腔、密封腔和机械密封；螺旋轴套嵌在卡琳娜动力循环透平的主轴上，静套与螺旋轴套呈间隙套设在主轴的同一端形成螺旋密封，静套密封端与主轴端部形成密封腔，静套开口端内与主轴形成一个空腔作为集漏腔，静套和主轴之间设置的机械密封位于集漏腔内；主轴转动时，螺旋轴套转动向密封腔加压；The spiral sealing system includes a spiral sleeve, a static sleeve, a leak collecting chamber, a sealing chamber and a mechanical seal; the spiral shaft sleeve is embedded on the main shaft of the Karina power cycle turbine, and the static sleeve and the spiral sleeve are set in a gap A spiral seal is formed at the same end of the main shaft, the sealing end of the static sleeve and the end of the main shaft form a sealing cavity, and a cavity is formed in the opening end of the static sleeve and the main shaft as a leak collection cavity, and the mechanical seal set between the static sleeve and the main shaft is located in the leakage collection In the cavity; when the main shaft rotates, the spiral sleeve rotates to pressurize the sealing cavity;
所述的水密封系统包括增压泵、调节阀和水箱；水箱的输入端与集漏腔连通，输出端依次经增压泵和调节阀连通设置在螺旋轴套和静套间隙末端。The water sealing system includes a booster pump, a regulating valve and a water tank; the input end of the water tank is communicated with the leakage chamber, and the output end is connected to the end of the gap between the spiral shaft sleeve and the static sleeve through the booster pump and the regulating valve in turn.
优选的，还包括增压泵伺服控制系统，其包括压力传感器和PI控制器；PI控制器用于根据压力传感器的测量值控制调节阀的开度，使螺旋密封的泵送压力与伺服增压泵的泵送压力之和等于密封腔压力。Preferably, it also includes a booster pump servo control system, which includes a pressure sensor and a PI controller; the PI controller is used to control the opening of the regulating valve according to the measured value of the pressure sensor, so that the pumping pressure of the screw seal and the servo booster pump The sum of the pumping pressures is equal to the seal chamber pressure.
进一步，压力传感器包括设置在密封腔和螺旋套尾端的第一、二压力传感器，分别输出的压力信号传输给PI控制器得到补偿压力对调节阀的开度进行调节控制。Further, the pressure sensor includes the first and second pressure sensors arranged at the end of the sealed cavity and the spiral sleeve, and the pressure signals respectively output are transmitted to the PI controller to obtain compensation pressure to adjust and control the opening of the regulating valve.
再进一步，当密封腔压力变化时，第一压力传感器接收密封腔的压力变化，并与密封压力进行比较得到压差信号，PI控制器接收压差信号来调节调节阀开度，通过调节流量，维持系统压力达到稳定；密封压力为螺旋密封的泵送压力与伺服增压泵的泵送压力之和。Furthermore, when the pressure of the sealing chamber changes, the first pressure sensor receives the pressure change of the sealing chamber and compares it with the sealing pressure to obtain a differential pressure signal. The PI controller receives the differential pressure signal to adjust the opening of the regulating valve. By adjusting the flow rate, Keep the system pressure stable; the sealing pressure is the sum of the pumping pressure of the screw seal and the pumping pressure of the servo booster pump.
进一步，当密封腔压力升高时，PI控制器控制调节阀开度逐渐减小，流量降低，增压泵动作增压，螺旋密封的泵送压力保持不变。Further, when the pressure of the sealing chamber increases, the PI controller controls the opening of the regulating valve to gradually decrease, the flow rate decreases, the booster pump acts to increase the pressure, and the pumping pressure of the screw seal remains unchanged.
再进一步，当密封腔压力保持不变，螺旋密封转速增大时，螺旋密封泵送压力突然升高，在PI控制器的控制的作用下调节阀开度增大，流量增大，增压泵供压减小。Further, when the pressure of the sealing chamber remains constant and the speed of the screw seal increases, the pumping pressure of the screw seal suddenly rises, and under the control of the PI controller, the opening of the regulating valve increases, the flow rate increases, and the booster pump The supply pressure is reduced.
与现有技术相比，本发明具有以下有益的技术效果：Compared with the prior art, the present invention has the following beneficial technical effects:
本发明所述的轴端密封装置不仅能依靠主轴的高速旋转通过螺旋密封产生泵送效应，并且其利用水作为密封介质实现水密封，由于水路由螺旋轴套和静套间隙末端开始，一部分经过螺旋泵送到达密封腔，另一部分经集液腔后流回到水箱，能够将集漏腔中经机械密封渗漏出的部分氨水通过水密封系统稀释并排出，从而使得后端的螺旋密封均处在水密封状态，不会被氨水腐蚀，从而通过机械密封、水密封和螺旋密封三级密封，避免了富氨蒸汽与机械结构接触导致腐蚀的问题。The shaft end sealing device of the present invention can not only rely on the high-speed rotation of the main shaft to produce a pumping effect through the spiral seal, but also use water as the sealing medium to realize water sealing. The screw pump reaches the sealing chamber, and the other part flows back to the water tank after passing through the liquid collecting chamber, which can dilute and discharge part of the ammonia water leaked from the mechanical seal in the leak collecting chamber through the water sealing system, so that the screw seal at the rear end is in good condition. In the water-sealed state, it will not be corroded by ammonia water, so through the three-stage seal of mechanical seal, water seal and screw seal, the problem of corrosion caused by the contact of rich ammonia vapor with the mechanical structure is avoided.
进一步的，通过监测密封装置内测点压力和应用可控增压泵伺服控制系统实现卡琳娜动力循环系统变工况下透平轴端的有效密封，满足工质零泄漏的要求，可以有效保障卡琳娜动力循环系统的安全服役，对于工程应用具有重要的现实意义。Further, by monitoring the pressure of the measuring point inside the sealing device and applying the servo control system of the controllable booster pump, the effective sealing of the turbine shaft end under the variable working conditions of the Karina power cycle system can be realized, which can meet the requirements of zero leakage of the working medium and can effectively guarantee The safe service of the Karina power cycle system has important practical significance for engineering applications.
进一步的，通过压力传感器对压力的感知，能够使得PI控制器立即对系统扰动后的动态偏差作出反应，减小了系统的稳态偏差和过调量，满足密封要求。Furthermore, through the pressure sensor's perception of the pressure, the PI controller can immediately respond to the dynamic deviation after the system disturbance, reducing the steady-state deviation and overshoot of the system, and meeting the sealing requirements.
附图说明Description of drawings
图1为本发明实例中所述轴端密封装置的结构示意图。Fig. 1 is a structural schematic diagram of the shaft end sealing device in the example of the present invention.
图2为本发明实例中所述轴端密封装置中增压泵的调节原理框图。Fig. 2 is a block diagram of the adjustment principle of the booster pump in the shaft end sealing device in the example of the present invention.
图3为本发明实例中所述轴端密封装置中螺旋轴套的几何尺寸示意图。Fig. 3 is a schematic diagram of the geometric dimensions of the helical sleeve in the shaft end sealing device in the example of the present invention.
图中：1为主轴；2为螺旋轴套；3为静套；4为集漏腔；5为密封腔；6为机械密封；7为增压泵；8为调节阀；9为水箱；P为压力传感器。In the figure: 1 is the main shaft; 2 is the screw sleeve; 3 is the static sleeve; 4 is the leakage chamber; 5 is the sealing chamber; 6 is the mechanical seal; 7 is the booster pump; 8 is the regulating valve; 9 is the water tank; P for the pressure sensor.
具体实施方式Detailed ways
下面结合具体的实施例对本发明做进一步的详细说明，所述是对本发明的解释而不是限定。The present invention will be further described in detail below in conjunction with specific embodiments, which are explanations of the present invention rather than limitations.
本发明一种应用于卡琳娜动力循环系统的透平轴端密封装置，如图1所示，包括螺旋密封系统、水密封系统和增压泵伺服控制系统。其中：螺旋密封系统包括螺旋轴套2、静套3、集漏腔4、密封腔5和机械密封6。水密封系统包括增压泵7、调节阀8和水箱9；增压泵伺服控制系统包括压力传感器和PI控制器。The present invention is a turbine shaft end sealing device applied to a Karina power cycle system, as shown in FIG. 1 , including a screw sealing system, a water sealing system and a booster pump servo control system. Among them: the spiral sealing system includes a spiral shaft sleeve 2, a static sleeve 3, a leakage chamber 4, a sealing chamber 5 and a mechanical seal 6. The water sealing system includes a booster pump 7, a regulating valve 8 and a water tank 9; the booster pump servo control system includes a pressure sensor and a PI controller.
螺旋轴套2嵌在卡琳娜动力循环透平的主轴1上，静套3与螺旋轴套2保持一定间隙套设在主轴1的同一端形成螺旋密封，静套3与主轴端部形成密封腔5。静套3内与密封腔5相对一端设置一个空腔形成集漏腔4，在主密封即螺旋密封的作用下，集漏腔4所需承受的密封压力小，集漏腔4与轴间隙处安装机械密封6作为次密封。如图1所示，从次级密封侧观测，也就是从图1的左侧看，主轴顺时针旋转，螺旋轴套为右旋槽；螺旋轴套2上刻有旋向固定的螺旋槽，使主轴1在高速旋转时产生泵送作用，螺旋密封几何结构如图3所示。采用克里斯公式作为该装置密封能力的计算公式，其表达式如下：The spiral bushing 2 is embedded on the main shaft 1 of the Karina power cycle turbine, the static bushing 3 and the spiral bushing 2 keep a certain gap, and are set on the same end of the main shaft 1 to form a spiral seal, and the static bushing 3 forms a seal with the end of the main shaft Cavity 5. A cavity is provided at the opposite end of the static sleeve 3 to the sealing chamber 5 to form a leak collecting chamber 4. Under the action of the main seal, that is, the spiral seal, the sealing pressure that the leak collecting chamber 4 needs to bear is small, and the gap between the leak collecting chamber 4 and the shaft Install mechanical seal 6 as secondary seal. As shown in Figure 1, viewed from the secondary seal side, that is, viewed from the left side of Figure 1, the main shaft rotates clockwise, and the helical sleeve is a right-handed groove; the helical sleeve 2 is engraved with a helical groove with a fixed direction of rotation, Make the main shaft 1 produce pumping action when it rotates at high speed, and the geometric structure of the spiral seal is shown in Figure 3. The Chris formula is used as the calculation formula for the sealing capacity of the device, and its expression is as follows:
式中：ΔP为密封压差/Pa，μ为液体动力粘度/Pa·s，L为螺旋长度/m，V为泵送速度/m·s-1，c为动静套3间隙/mm，K称之为密封系数，其表达式如下：In the formula: ΔP is the sealing pressure difference/Pa, μ is the dynamic viscosity of the liquid/Pa s, L is the screw length/m, V is the pumping speed/m s -1 , c is the gap between the dynamic and static sleeve 3/mm, K It is called the sealing coefficient, and its expression is as follows:
式中：α为螺旋角，K1和K2的计算分别如下所示：In the formula: α is the helix angle, and the calculations of K 1 and K 2 are as follows:
式中be和bg等参数均为螺旋密封几何尺寸。In the formula, parameters such as b e and b g are the geometric dimensions of the spiral seal.
增压泵7的调节目的是使螺旋密封的泵送压力与伺服增压泵7的泵送压力之和等于密封腔5压力，从而实现螺旋密封的完全密封和零泄漏，通过调节阀8门开度来实现对增压泵7的压力调节，如图2所示。The purpose of adjusting the booster pump 7 is to make the sum of the pumping pressure of the screw seal and the pumping pressure of the servo booster pump 7 equal to the pressure of the sealing chamber 5, so as to realize the complete sealing and zero leakage of the screw seal. To realize the pressure regulation of the booster pump 7, as shown in Fig. 2 .
如图1所示，其中P为压力传感器，增压泵伺服控制系统通过第一、二压力传感器将密封腔5和螺旋套尾端压力信号传输给增压泵伺服控制系统，求得补偿压力，最后通过PI控制器对增压泵7进行调节控制。水密封系统中由增压泵7抽取水箱9中的水，经过增压泵7的泵体、管路和调节阀8进入动静套3间隙末端处，然后一部分水会进入集漏腔4，流回水箱9，构成一个闭合密封水循环系统。As shown in Figure 1, where P is the pressure sensor, the servo control system of the booster pump transmits the pressure signals of the sealing chamber 5 and the tail end of the spiral sleeve to the servo control system of the booster pump through the first and second pressure sensors to obtain the compensation pressure, Finally, the booster pump 7 is adjusted and controlled by the PI controller. In the water-sealed system, the water in the water tank 9 is drawn by the booster pump 7, and enters the end of the gap between the dynamic and static sleeves 3 through the pump body of the booster pump 7, the pipeline and the regulating valve 8, and then a part of the water enters the leakage chamber 4 to flow The water return tank 9 constitutes a closed and sealed water circulation system.
当密封腔5压力变化时，第一压力传感器接受密封腔5的压力变化，并与密封压力(螺旋密封的泵送压力与伺服增压泵7的泵送压力之和)进行比较，PI控制器通过接受压差信号来调节调节阀8开度，通过调节流量，维持系统压力达到稳定。当密封腔5压力升高后，在PI控制器的控制作用下调节阀8开度逐渐减小，流量降低，增压泵7动作增压，螺旋密封的泵送压力保持不变。When the pressure of the sealing chamber 5 changes, the first pressure sensor receives the pressure change of the sealing chamber 5 and compares it with the sealing pressure (the sum of the pumping pressure of the screw seal and the pumping pressure of the servo booster pump 7), and the PI controller Adjust the opening degree of the regulating valve 8 by receiving the differential pressure signal, and maintain the system pressure to be stable by adjusting the flow rate. When the pressure of the sealing chamber 5 rises, under the control of the PI controller, the opening of the regulating valve 8 gradually decreases, the flow rate decreases, the booster pump 7 acts to increase the pressure, and the pumping pressure of the screw seal remains unchanged.
当密封腔5压力保持不变，螺旋密封转速增大时，螺旋密封泵送压力突然升高，而此时密封腔5压力不变，在PI控制器的控制的作用下调节阀8开度增大，流量增大，增压泵7供压减小。PI控制器立即对系统扰动后的动态偏差作出反应，减小了系统的稳态偏差和过调量，满足密封要求。When the pressure of the sealing chamber 5 remains constant and the rotation speed of the screw seal increases, the pumping pressure of the screw seal suddenly rises, and at this time the pressure of the sealing chamber 5 remains unchanged, and the opening of the regulating valve 8 increases under the control of the PI controller. Large, the flow increases, and the pressure supplied by the booster pump 7 decreases. The PI controller immediately responds to the dynamic deviation after the system disturbance, reduces the steady-state deviation and overshoot of the system, and meets the sealing requirements.
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| CN102220886A (en) * | 2011-05-16 | 2011-10-19 | 西安交通大学 | Device and method for automatically adjusting seal pressure of helical groove at shaft end of turbine |
| CN202017765U (en) * | 2011-03-11 | 2011-10-26 | 李廷伟 | Rotating shaft sealing device |
| CN203892237U (en) * | 2014-01-06 | 2014-10-22 | 东莞市华汇精密机械有限公司 | Mechanical sealing device used for hydrodynamic turbine |
| EP3073059A1 (en) * | 2015-03-25 | 2016-09-28 | Bosch Mahle Turbo Systems GmbH & Co. KG | Exhaust gas turbo charger |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202017765U (en) * | 2011-03-11 | 2011-10-26 | 李廷伟 | Rotating shaft sealing device |
| CN102220886A (en) * | 2011-05-16 | 2011-10-19 | 西安交通大学 | Device and method for automatically adjusting seal pressure of helical groove at shaft end of turbine |
| CN203892237U (en) * | 2014-01-06 | 2014-10-22 | 东莞市华汇精密机械有限公司 | Mechanical sealing device used for hydrodynamic turbine |
| EP3073059A1 (en) * | 2015-03-25 | 2016-09-28 | Bosch Mahle Turbo Systems GmbH & Co. KG | Exhaust gas turbo charger |
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