KR102016593B1 - Multistage Turbine System - Google Patents

Abstract

The present invention provides a multistage turbine system having a rotary shaft coupled with multiple radial blades, the multistage turbine system comprising: a housing configured to receive the rotary shaft and having an inlet for introducing a working fluid; A rotating shaft rotatably installed in the housing; A ball bearing installed to contact an end of the rotary shaft to support an end of the rotary shaft; And a cap installed at an end of the rotary shaft to contact the ball bearing, wherein the inlet is formed in a direction parallel to the longitudinal direction of the rotary shaft at an outer circumference of the rotary shaft.

Description

Multistage Turbine System

The present invention relates to a multistage turbine system, and more particularly, to a multistage turbine system for installing a cap and a guide bearing to protect a bearing at a housing inlet through which a working fluid enters.

Recently, the United States, Europe, and China are supporting the national development of technologies related to waste heat recovery and cogeneration in order to reduce greenhouse gas emissions, and the market related to greenhouse gas emission reduction is growing. For this reason, domestic and foreign companies are in constant competition with the power generation system for industrial waste heat and engine waste heat use due to the high interest and demand of the industry. Turbine technology using the Rankine cycle using steam and Organic Rankine Cycle (ORC) is most active, and axial and radial turbines are typically connected to generators for practical use. Among them, the radial flow turbine shows a high efficiency in the wet steam type working fluid and is the turbine type structure on which the present patent is applied.

Among the conventional turbines, a turbine of the radial type is disclosed. The radial type turbine is a turbine that converts the fluid energy of a working steam in the form of wet steam into electrical energy using a radial turbine. In addition, the radial type turbine is a method of rotating the turbine while passing through the stator and the blade installed in the rotor is fixed to the housing as the movement path of the working fluid spread radially unlike the axial turbine Is done. In order to improve the efficiency of the turbine, a method of radially repeating the stator blades and the rotor blades in a radial direction may be used to improve the efficiency of the turbine. This may result in excessive linear speed at the tip of the blade and excessive overload of the rotating shaft. There is a risk, so it is difficult to apply to large industrial sites.

Further, in order to avoid excessive lamination in the radial direction, a turbine of a type in which a turbine of a radial type and an axial type type is combined is known from Patent Document 1. Such a combined turbine produces a working fluid discharged from a conventional single stage turbine end blade in a multistage structure by combining an outlet path and an inlet path formed in an additional stator. Also, the working fluid delivered in the axial direction again rotates the rotor blades, creating a stronger load. Such coupled turbines can theoretically gain efficiency, but there is a problem that the inlet of the working fluid must be installed on the side of the housing to support both ends of the bearing.

Since the inlet of the working fluid is installed on the side of the housing, it first collides with the housing on the shaft or side before entering the rotor blades. At this time, when the working fluid collides, loss of fluid energy occurs primarily. In addition, when the direct force of the fluid in the radial direction to the shaft system has a great influence on the rotational stability. On the other hand, when the path of the fluid spreads out evenly in the radial direction of 360 °, stable operation is possible to the rotor blade, the fluid enters from the side of the housing, the stability is significantly reduced during operation.

That is, in order to reduce the loss of the fluid energy, the entry path of the working fluid to enter in the axial direction of the rotary shaft of the turbine can ensure the stability of the rotating body, such a structure is required.

Korean Unexamined Patent Publication No. 10-2015-0139309

The present invention has been made to solve the above problems, an object of the present invention is to form the entry path of the working fluid in the axial direction of the housing to reduce the loss of fluid energy to improve the efficiency of the turbine, It is to provide a multi-stage turbine system to ensure the stability.

In order to solve the above problems, the multi-stage turbine system of the present invention, the housing having a rotary shaft coupled to the multi-stage radial blades, the housing is configured to receive the rotary shaft, the inlet for introducing a working fluid; A rotating shaft rotatably installed in the housing; A ball bearing installed to contact an end of the rotary shaft to support an end of the rotary shaft; And a cap installed at an end of the rotating shaft to contact the ball bearing, wherein the inlet is formed in a direction parallel to the longitudinal direction of the rotating shaft at an outer circumference of the rotating shaft.

According to an example related to the present invention, the ball bearing is installed to surround the outer circumference of the rotary shaft end, the cap is coupled to the outer circumference of the ball bearing to receive the ball bearing, the outer circumference of the cap is the inlet It is arranged to be spaced apart from the inner circumference of the housing provided to enable the introduction of the working fluid.

A sealing member may be installed between the outer circumference of the end of the rotating shaft and the inner circumference of the cap end, and the sealing member may receive grease in the inner circumference of the cap to enable lubrication of the ball bearing.

Between the outer circumference of the cap and the inner circumference of the housing in which the inlet is provided, a plurality of support shafts configured to support the cap may be provided along the radial direction, and the inlet may be formed between the plurality of support shafts.

According to another example related to the present invention, the rotary shaft end includes a protrusion formed to protrude in the longitudinal direction of the rotary shaft along the circumferential direction, and a ball bearing is coupled to an inner circumference of the protrusion to support a load applied to the rotary shaft. do.

A cap for supporting the ball bearing is installed at one end of the ball bearing, and a hollow beam coupled to one end of the cap is installed at the other end of the ball bearing, and the ball bearing is lubricated inside the hollow beam. A flow path of lubricant can be formed that enables this.

The hollow beam is disposed to be in contact with the inner circumference of the ball bearing, one end of the hollow beam disposed on the inner circumference of the ball bearing protrudes, the one end of the cap may be screwed The screw coupling can be formed so as to.

The cap may be provided with an inflow passage for allowing the lubricating fluid to flow into the ball bearing and an outflow passage through which the lubricating fluid flows from the ball bearing.

The inflow passage, the first passage formed in a direction crossing the longitudinal direction of the rotary shaft; And a second flow passage communicating with the first flow passage and formed to intersect the first flow passage, wherein the outflow flow passage comprises: a third flow passage formed in a direction crossing the longitudinal direction of the rotation shaft; And a fourth flow passage communicating with the third flow passage and formed to intersect the third flow passage.

The multi-stage turbine system of the present invention can stably drive the overhang shaft structure and ensure the efficiency of the turbine.

In the multistage turbine system of the present invention, the ball bearing is installed on the rotating shaft and the hollow beam and the cap are coupled to each other so that the load transmitted to the rotating shaft is transferred in the order of the ball bearing, the hollow beam and the cap. The load to be distributed can be distributed.

Even in the absence of an additional oil lubrication device, grease is self-lubricated and the grease / oil seal can be completely isolated from external working fluid to ensure rotational stability of the rotor.

In addition, the multi-stage turbine system of the present invention is provided with an inflow and outflow path in the cap, and by providing an oil flow path in the hollow beam, it is possible to stably supply lubricant to the ball bearing.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross sectional view showing a structure of a first embodiment of a multistage turbine system and a flow of working fluid;
Figure 2 is an enlarged cross-sectional view showing a coupling structure of one end of the rotation shaft in FIG.
3 is a cross-sectional view showing the structure and flow of the working fluid of the second embodiment of the multistage turbine system;
Figure 4 is an enlarged cross-sectional view showing a coupling structure of one end of the rotating shaft in FIG.
5 is a graph showing the result of whirling amplitude versus rotational speed.

Hereinafter, exemplary embodiments disclosed herein will be described in detail with reference to the accompanying drawings, and the same or similar components will be given the same or similar reference numerals, and redundant description thereof will be omitted. The suffix "part" for components used in the following description is given or mixed in consideration of ease of specification, and does not have meanings or roles that are distinguished from each other. In addition, in describing the embodiments disclosed herein, when it is determined that the detailed description of the related known technology may obscure the gist of the embodiments disclosed herein, the detailed description thereof will be omitted. In addition, the accompanying drawings are intended to facilitate understanding of the embodiments disclosed herein, but are not limited to the technical spirit disclosed herein by the accompanying drawings, all changes included in the spirit and scope of the present invention. It should be understood to include equivalents and substitutes.

Terms including ordinal numbers such as first and second may be used to describe various components, but the components are not limited by the terms. The terms are used only for the purpose of distinguishing one component from another.

When a component is referred to as being "connected" to another component, it should be understood that there may be a direct connection to that other component, but other components may be present in between.

Singular expressions include plural expressions unless the context clearly indicates otherwise.

In this application, the terms "comprises" or "having" are intended to indicate that there is a feature, number, step, operation, component, part, or combination thereof described in the specification, and one or more other features. It is to be understood that the present invention does not exclude the possibility of the presence or the addition of numbers, steps, operations, components, components, or a combination thereof.

1 is a cross-sectional view showing the structure and flow of the working fluid of the first embodiment of the multi-stage turbine system 100, Figure 3 is a cross-sectional view showing the structure and flow of the working fluid of the second embodiment of the multi-stage turbine system 200. to be. With reference to FIG. 1 and FIG. 3, the structure of this invention is described.

The multistage turbine system (100, 200) of the present invention has a rotary shaft (120, 220) coupled with a multi-stage radial blade. A plurality of rotor blades 125 and 225 are formed on each rotor 123 and 223 coupled to the rotation shafts 120 and 220, and stator blades 115 and 215 are adjacent to the housing 110 and 210. It may be formed in plural. 1 and 3, two rotors 123 and 223 are provided on the rotation shafts 120 and 220, and rotor blades 125 and 225 are respectively formed on the rotors 123 and 223. An example formed of four or four is shown. In addition, stator blades 115 and 215 are formed on the inner circumference of the housings 110 and 210 so as to be spaced apart from the rotor blades 125 and 225. As a result, the resistance of the working fluid increases between the rotor blades 125 and 225 and the stator blades 115 and 215 when the rotation shafts 120 and 220 rotate, thereby further improving the pump output.

An example is shown in which a plurality of blades respectively formed on the rotor blades 125 and 225 and the housings 110 and 210 are formed twice to form the multistage turbine system 100 and 200.

The multistage turbine system 100, 200 of the present invention includes a housing 110, 210, a rotation shaft 120, 220, a ball bearing 130, 230, and a cap 140, 240.

The housings 110 and 210 are configured to receive the rotation shafts 120 and 220. In addition, the housings 110 and 210 are provided with inlets 113 and 213, and the inlets 113 and 213 are provided with inlet spaces 113a and 213a therein to allow the working fluid to be introduced therein. The working fluid in the present invention may be wet steam of 170 ~ 200 ℃. On the other hand, the housings 110 and 210 have outlets 116 and 216 to discharge the working fluid used for the turbine output.

The rotating shafts 120 and 220 are rotatably installed inside the housings 110 and 210. 1 and 3 illustrate examples of the rotation shafts 120 and 220 disposed in the left and right directions.

The ball bearings 130 and 230 are installed to contact the ends of the rotation shafts 120 and 220 to support the ends of the rotation shafts 120 and 220.

As described below, the ball bearings 130 and 230 may be installed at the outer circumference or the inner circumference of the ends of the rotation shafts 120 and 220 according to the shape of the ends of the rotation shafts 120 and 220, and the rotation of the rotation shafts 120 and 220. Supports the load generated by the rotation, and rotates the rotary shaft (120, 220).

Caps 140 and 240 are installed at the ends of the rotary shafts 120 and 220 to be in contact with the ball bearings 130 and 230. Caps 140 and 240 block the bearing from the entry path of the working fluid. That is, the wet steam of 160 ~ 200 ℃ generated during the recovery of waste heat can give a big obstacle to the lubrication of the ball bearing (130, 230), the ball bearing (130, 230) by the cap (140, 240) and the working fluid It can be completely blocked to contribute to the stability of the system of the present invention.

In the multi-stage turbine system (100, 200) of the present invention, the inlets (113, 213) of the housing (110, 210) is formed in a direction parallel to the longitudinal direction of the rotation shaft (120, 220) on the outer periphery of the rotation shaft (120, 220) do. 1 and 3 illustrate an example in which the inlets 113 and 213 are formed in a direction parallel to the longitudinal direction of the rotation shafts 120 and 220 at the left side of the housing 110 and 210, and through the inlets 113 and 213. The working fluid may be introduced into the housings 110 and 210.

For this reason, the multistage turbine systems 100 and 200 of the present invention can increase the efficiency of the entire system and stable driving of the overhanging rotary shafts 120 and 220.

Hereinafter, the structure of the multistage turbine system of the present invention will be described in more detail. The multistage turbine system of the present invention can be implemented in the first and second embodiments according to the coupling relationship between the rotating shaft, the ball bearing, and the cap.

1 and 2, a first embodiment of a multistage turbine system 100 of the present invention will be described. The multi-stage turbine system 100 of the first embodiment is installed so that the ball bearing 130 surrounds the outer circumference of the end of the rotary shaft 120, the cap 140 is coupled to the outer circumference of the ball bearing 130, the ball bearing 130 Is made to accommodate. In addition, the outer circumference of the cap 140 is spaced apart from the inner circumference of the housing 110 in which the inlet 113 is provided, whereby the working fluid is introduced between the outer circumference of the cap 140 and the inner circumference of the housing 110.

The multistage turbine system 100 according to the first embodiment may have a structure in which an outer ring of the ball bearing 130 is fixed and an inner ring rotates together with the rotation shaft 120.

In the multi-stage turbine system 100 of the first embodiment, the cap 140 may have a conical shape and may be installed concentrically with an end portion of the housing 110 in which the inlet 113 is formed. In addition, the cap 140 is preferably made so that the outer diameter is smaller than the diameter of the inner circumference of the housing 110 to ensure a sufficient flow path of the working fluid.

Meanwhile, a sealing member 150 may be installed between the outer circumference of the end of the rotation shaft 120 and the inner circumference of the end of the cap 140. The sealing member 150 allows grease to be received in the inner circumference of the cap 140 to enable lubrication of the ball bearing 130. The sealing member 150 may be, for example, a labyrinth seal.

A plurality of support shafts 160 may be installed between the outer circumference of the cap 140 and the inner circumference of the housing 110 provided with the inlet 113 to support the cap 140 along the radial direction of the inner circumference of the housing 110. 1, an inlet 113 is formed between six support shafts 160.

In addition, as shown in FIG. 1, the ball bearing 130a may be further installed on the other side of the inner circumference of the rotating shaft 120 and the housing 110.

Hereinafter, with reference to FIG. 3 and FIG. 4, 2nd Example of the multistage turbine system 200 of this invention is described.

The multi-stage turbine system 200 of the second embodiment has a protrusion 226 protruding in the longitudinal direction of the rotary shaft 220 along the circumferential direction of the end of the rotary shaft 220, and a ball bearing (260) in the inner circumference of the protrusion 226. 230 is coupled to support the load applied to the rotating shaft 220.

That is, unlike the multistage turbine system 100 of the first embodiment, the multistage turbine system 200 of the second embodiment is provided with a ball bearing 230 on the inner circumference of the protrusion 226 formed at the end of the rotation shaft 220. .

As shown in FIG. 4, the ball bearing 230 includes an inner ring 231 and an outer ring 235 which are made to rotate relative to each other, a cage 237 disposed between the inner ring 231 and the outer ring 235, and between them. It may comprise a ball 236 disposed in. The ball bearing 230 is fixed to the inner ring 231 to the hollow beam 270 to be described later, the outer ring 235 rotates together with the rotation shaft 220 to enable a stable drive.

In addition, a cap 240 supporting the ball bearing 230 is installed at one end of the ball bearing 230, and a hollow beam 270 is contacted to the other end of the ball bearing 230. Beam 270 may be coupled to one end of cap 240. In FIG. 4, an example in which the hollow beam 270 is in contact with the right side of the ball bearing 230 and the cap 240 is in contact with the left side is illustrated.

The hollow beam 270 allows the inflow hole 271 to allow the oil lubricated the ball bearing 230 to flow in, the oil flow passage 275 through which the lubricant can pass, and the lubricant to flow out into the ball bearing 230. The outflow hole 273 is provided. The lubricant that lubricates the ball bearing 230 may be, for example, lubricating oil or grease. In FIG. 4, an inflow hole 271 is formed in the upper portion of the hollow beam 270, and an outlet hole 273 is formed in the lower portion of the hollow beam 270, and an example in which an oil flow passage 275 is formed therebetween is shown. It is shown, thereby receiving a lubricant lubricating the ball bearing 230 and can supply the supplied lubricant back to the ball bearing 230 to facilitate lubrication of the ball bearing 230. Hollow beam 270 may be understood as a configuration that can serve as a nozzle to enable the movement of the lubricant.

The hollow beam 270 is disposed to be in contact with the inner circumference of the ball bearing 230, and a screw portion 277 protrudes from one end of the hollow beam 270 that penetrates the ball bearing 230. In addition, one end of the cap 240 is formed with a screw coupling portion 247 to which the screw portion 277 is screwed so that the hollow beam 270 is screwed to the cap 240. An inner circumference of the screw coupling portion 247 may be provided with a screw bone.

Therefore, the load is transmitted in the order of the rotating shaft 220, the ball bearing 230, the hollow beam 270 and the cap 240 to distribute it.

A sealing member 250 is installed between the cap 240 and the protrusion 226 of the rotating shaft 220 to enable sealing between the cap 240 and the rotating shaft 220. The sealing member 250 may be, for example, an O-ring or labyrinth seal.

Meanwhile, in the multistage turbine system 200 according to the second embodiment, an inflow passage 241 and an outlet passage 243 may be formed in the cap 240. The inflow passage 241 allows the lubricating fluid to flow into the ball bearing 230. 4 illustrates an example in which the inflow passage 241 includes a first passage 241a formed in a direction crossing the longitudinal direction of the rotation shaft 220 and a second passage 241b formed to intersect the first passage 241a. Shown. In addition, in FIG. 4, the outflow passage 243 is a fourth flow passage 243b formed to intersect the third flow passage 243a and the third flow passage 243a formed in a direction crossing the longitudinal direction of the rotation shaft 220. An example is made.

Between the outer circumference of the cap 240 and the inner circumference of the housing 210 having the inlet 213, a plurality of support shafts 260 supporting the cap 240 may be installed along the radial direction, see FIG. 3. An example in which the inlet 213 is formed between six support shafts 260 is illustrated.

Meanwhile, as shown in FIG. 3, two ball bearings 230a may be installed on the other side of the inner circumference of the rotating shaft 220 and the housing 210.

The inflow passage 241 and the outflow passage 243 may communicate with the support shaft 260 having a receiving space therein, respectively. The support shaft 260 communicated with the inflow flow path 241 enables lubrication of the ball bearing 230 by supplying a lubricant to the inflow flow path 241, and the support shaft 260 communicated with the outflow flow path 243 flows out. A lubricant is provided from the flow path 243 to enable the lubricant to be discharged.

Each of the inflow passage 241 and the outlet passage 243 may have a predetermined cross-section, and may be formed at the upper and lower portions of the cap 240, respectively. The inflow passage 241 and the outlet passage 243 may be respectively formed. It may consist of a circular cross section having a determined area.

Due to this structure, the lubricant is moved in the order of the housing 210, the inflow flow path 241 of the cap 240, the ball bearing 230, the hollow beam 270 and the outflow flow path 243 of the cap 240 Ball bearing 230 is completely isolated from the working fluid, so that lubrication can be achieved. On the other hand, the lubricant serves as a cooler to prevent overheating of the ball bearing 230 to ensure a stable driving of the ball bearing 230.

FIG. 5 is a graph showing the results of whirling amplitude versus rotational speed. FIG. Referring to FIG. 5, in the multi-stage turbine system of the present invention, when the ball bearing is not applied, the swing amplitude is about 7.50E-01 at the rotational speed of 20000 rpm, but the swing amplitude is about 2.30 at 25000 rpm by the ball bearing application. The improvement was confirmed with E-01.

The multi-stage turbine system 100 and 200 described above is not limited to the configuration and method of the above-described embodiments, but the embodiments may be configured by selectively combining all or some of the embodiments so that various modifications may be made. It may be.

It is apparent to those skilled in the art that the present invention can be embodied in other specific forms without departing from the spirit and essential features of the present invention. Accordingly, the above detailed description should not be construed as limiting in all aspects and should be considered as illustrative. The scope of the invention should be determined by reasonable interpretation of the appended claims, and all changes within the equivalent scope of the invention are included in the scope of the invention.

100, 200: multi-stage turbine system
110: housing 113: inlet 116: outlet
120: rotating shaft 123: rotor 125: rotor blade
130: ball bearing
140: Cap
150: sealing member
160: support shaft
210: housing 213: inlet 216: outlet
220: rotating shaft 223: rotor 225: rotor blade 226: protrusion
230: ball bearing 231: inner ring 235: outer ring 236: ball 237: cage
240: Cap 241: Inflow Euro 241a: First Euro 241b: Second Euro
243: outflow euro 243a: third euro 243b: fourth euro 247: screw coupling portion
250: sealing member
260: support shaft
270: hollow beam 271: inlet hole 273: outlet hole 275: oil flow path

Claims (9)

delete delete delete delete A multistage turbine system having a rotary shaft coupled with multiple radial blades,
A housing configured to receive the rotation shaft and having an inlet for introducing a working fluid;
A rotating shaft rotatably installed in the housing;
A ball bearing installed to contact an end of the rotary shaft to support an end of the rotary shaft;
A cap installed at an end of the rotating shaft to be in contact with the ball bearing,
The inlet is formed in a direction parallel to the longitudinal direction of the rotary shaft in the outer periphery of the rotary shaft,
The rotary shaft end has a protrusion that protrudes in the longitudinal direction of the rotary shaft along the circumferential direction, a ball bearing is coupled to the inner circumference of the protrusion to support the load applied to the rotary shaft,
And the cap is provided with an inlet flow passage through which the lubricating fluid can flow into the ball bearing and an outlet flow passage through which the lubricating fluid flows from the ball bearing.
The method of claim 5,
The cap supports the ball bearing at one end of the ball bearing, and a hollow beam coupled to one end of the cap is installed at the other end of the ball bearing, and lubrication of the ball bearing is provided inside the hollow beam. A multistage turbine system, wherein a flow path of lubricant is formed.
The method of claim 6,
The hollow beam is disposed to be in contact with the inner circumference of the ball bearing, one end of the hollow beam disposed on the inner circumference of the ball bearing protrudes, the one end of the cap may be screwed Multistage turbine system, characterized in that the screw coupling is formed so that.
delete The method of claim 5,
The inflow passage, the first passage formed in a direction crossing the longitudinal direction of the rotary shaft; And a second flow passage communicating with the first flow passage and formed to intersect the first flow passage,
The outflow passage, the third passage formed in a direction crossing the longitudinal direction of the rotation axis; And a fourth flow passage communicating with the third flow passage and formed to intersect the third flow passage.

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