WO2010135988A1

WO2010135988A1 - Direct-connection low-speed small-scale mixed-flow hydroturbine seat ring applied in hydrodynamic energy-saving cooling tower

Info

Publication number: WO2010135988A1
Application number: PCT/CN2010/073240
Authority: WO
Inventors: 顾星康
Original assignee: 南京星飞冷却设备有限公司
Priority date: 2009-05-27
Filing date: 2010-05-25
Publication date: 2010-12-02
Also published as: CN101560937B; CN101560937A

Abstract

A direct-connection low-speed small-scale mixed-flow water turbine seat ring applied in a hydrodynamic energy-saving cooling tower, mainly consisting of an upper ring plate (1), a lower ring plate (3) and guide vanes (2) arranged between the upper ring plate (1) and the lower ring plate (3). The seat ring is characterized in that the guide vanes (2) are negative curvature guide vanes, the height of the negative curvature guide vane (2) is 0.07-0.09 times of the diameter D1 of the water inlet side thereof, the length L is 0.16-0.2 times of the diameter D1 of the water inlet side thereof; the diameter D2 of the water outlet side of the negative curvature guide vane (2) is 0.75-0.95 times of the diameter D1 of the water inlet side thereof, the diameters D3 of outer circles of the upper ring plate (1) and the lower ring plate (3) are both 1.0-1.25 times of the diameter D1 of the water inlet side of the negative curvature guide vane (2), the diameters D4 of inner circles of the upper ring plate (1) and the lower ring plate (3) are 0.7-0.9 times of the diameter D1 of the water inlet side of the negative curvature guide vane (2). The seat ring has a simple structure and convenient design, and is beneficial to improve the energy conversion efficiency of the hydroturbine.

Description

Instruction manual

Direct-coupled low-speed small Francis turbine seat ring for hydrodynamic energy-saving cooling tower

Technical field

The invention relates to a cooling tower, in particular to a water inlet seat ring of a cooling tower driven water turbine, in particular to a waterless turbine output shaft by rationally designing a water inlet seat guide vane and an impeller without a reduction gear box. It is a direct-coupled low-speed small mixed-flow turbine seat ring for the hydro-powered energy-saving cooling tower, which is the rated speed of the fan and thus eliminates the gearbox used in the traditional counter-turbine.

Background technique

As is known, in order to achieve energy saving, the existing air conditioning cooling tower has begun to use a water turbine to drive the cooling fan, which fully utilizes the energy of the cooling tower circulating water flow to convert it into the driving force of the water turbine, and converts the water energy into Rotating machinery can be used to drive cooling fans, eliminating the need for traditional high-power cooling motors, and the energy savings are significant.

According to the Applicant's knowledge, the current counter-turbine turbines require a speed reducer to reduce the output speed of the turbine to a reasonable speed to drive the blades to rotate, thereby achieving cooling of the circulating water. Since the working condition of the reduction gearbox is poor, it is not only noisy, but also has a short life and is prone to failure. At the same time, since the reduction gearbox is a large reduction gearbox, the manufacturing cost is accordingly increased.

Therefore, if the gearbox can be removed by reasonable design, the above problem can be solved well. The applicant has calculated through a large number of calculations that the turbine output speed can be as long as the shape and size of the inlet ring and the impeller of the turbine are properly designed. Control is within the desired range. Therefore, it is imperative to design a seat ring that meets the low speed requirements of the turbine of a hydro-cooling tower. It is the key to achieving gearless transmission of the cooling tower turbine.

Summary of the invention

The object of the present invention is to solve the problems of large noise, easy failure and high manufacturing cost of the output shaft of the existing cooling tower counter-turbine that needs to be driven by the reduction gear box, and is designed to be applied to hydrodynamic cooling. The tower's direct-coupled low-speed small Francis turbine seat ring lays the foundation for the final elimination of the gear reduction transmission mechanism. The technical solution of the present invention is:

The utility model relates to a direct-coupled low-speed small mixed flow turbine seat ring applied to a hydrodynamic energy-saving cooling tower, which mainly comprises an upper ring plate 1, a lower ring plate 3 and a guide vane 2 installed between the upper ring plate 1 and the lower ring plate 3 The composition is characterized in that the vane 2 is a negative curvature vane, and the height of the negative curvature vane 2 is 0.07 to 0.09 times the diameter D1 of the inlet side, and the length L is 0.16 of the diameter D1 of the inlet side. ~0.2 times; the diameter of the water outlet side D2 of the negative curvature vane 2 is 0.75~0.95 times of the diameter D1 of the inlet water; the diameter of the outer circle D3 of the upper ring plate 1 and the lower ring plate 3 are both the negative curvature The guide vane 2 has a water inlet diameter D1 of 1.0 to 1.25 times, and the inner ring diameter D4 of the upper ring plate 1 and the lower ring plate 3 is 0.7 to 0.9 times the diameter D1 of the water inlet side of the negative curvature guide vane 2.

The number of the vanes 2 is 15-19.

The curve equation of the water-facing surface of the vane (2) is y = A _lX ⁴ + B _lX ³ + C _lX ² + Di x + E where Af XlO - ⁸ ~ - 9X10 - 8, BfS XlO - ⁵ 5.5X10 ^{- 5} , d=-6.5 X 10 ^-5 ~- 8.5 X10 ^-5 , D^JXIO - ¹ ~ 2.6X10 ^-1 , Ei=-9X 10 ^-2 ~- 1.3 X 10 ^-1 , the curve equation of the back surface is y =A ₂ x ⁴ +B ₂ x ³ +C ₂ x ² +D ₂ x+E ₂ , where A ₂ =1.9X 10 ^-9 ~2.3 X 10 ^-9 , B ₂ =-1.7 X 10 ^-6 ~- 2.1 X 10 ^-6 , C ₂ =-9.5X 10 ^-4 ~- l.OX 10 ^-3 , D ₂ =2.5 X 10 - ¹ ~ 3.0 X 10 , E ₂ =3.1~3.7, x, y in the equation The unit is millimeter, and the head of the vane (2) is smoothly connected between the water-facing surface and the back surface, and the tail of the vane (2) is connected by a fold line between the water-facing surface and the back surface.

The relationship between the inlet diameter D1 of the negative curvature vane 2 and the rotor speed n of the cooling fan is: Dl=KlXnllX>/ /n, where Kl=l.15-1.25, nil is the unit speed, The value is between 28 and 42, and H is the water pressure of the tower (in water column: m).

The beneficial effects of the invention:

The invention lays a foundation for the cooling tower water turbine to finally save the reduction gear box, and the seat ring designed by the invention can fully meet the use requirements, and the test proves that the turbine with the seat ring of the invention has the output speed fully satisfying the use. Required, and the pulsation range of the speed is small.

The invention has simple structure and is convenient to install and use.

The invention is directed to the characteristics of the cooling tower water turbine, and creatively reduces the unit rotation speed nil from not less than 80 to 28-42 of the actual application of the counter-attack turbine, and at the same time, according to the unit rotation speed, the key components affecting the efficiency of the turbine are determined. The curve equation of the leaf, after a lot of calculations and experiments The relationship between the size of the seat ring and the water inlet side dimension Dl is given, and the relationship between the D1 and the cooling fan speed is given, which provides a quick and convenient way for rational design of the seat ring.

It has been experimentally confirmed that the size of the seat wheel determined by the water inlet side dimension D1 determined when the unit speed is between 28 and 42 can maintain the overall efficiency of the turbine at about 86%, and the efficiency is greater than 42 or less than 28. It is a straight line in a straight line.

DRAWINGS

1 is a schematic perspective view of a seat ring of the present invention.

2 is a schematic view showing the installation layout of the seat ring guide vanes of the present invention.

Figure 3 is a diagram showing the position of a single vane curve equation of the present invention.

4 is a schematic perspective view of a guide vane of the present invention.

Figure 5 is a three-view projection view of the vane of the present invention.

detailed description

The invention will now be further described with reference to the accompanying drawings and embodiments.

As shown in Figure 1-5.

The utility model relates to a direct-coupled low-speed small mixed flow turbine seat ring applied to a hydrodynamic energy-saving cooling tower, which mainly comprises an upper ring plate 1, a lower ring plate 3 and a guide vane 2 installed between the upper ring plate 1 and the lower ring plate 3 Composition, the number of vanes can be between 15-19, as shown in Figure 1. The vane 2 is a negative curvature guide vane (Fig. 3), the height of the negative curvature vane 2 is 0.07~0.09 times the diameter D1 of the inlet water, and the length L is 0.16~ of the diameter D1 of the inlet side. 0.2 times, as shown in FIG. 5; the diameter D2 of the water outlet side of the negative curvature guide vane 2 is 0.75 to 0.95 times of the diameter D1 of the inlet water; the outer diameter D3 of the upper ring plate 1 and the lower ring plate 3 are both For the negative curvature guide vane 2, the water inlet diameter D1 is 1.0 to 1.25 times, and the inner ring diameter D4 of the upper ring plate 1 and the lower ring plate 3 is 0.7 to 0.9 times the diameter D1 of the water inlet side of the negative curvature guide vane 2. , wherein the relationship between the inlet diameter D1 and the fan speed n of the cooling fan is: Dl=KlXnll x H/n, where Kl=l.15-1.25, nil is the unit speed, and the value is between 28~ Between 42 and H is the inlet water pressure (in water column: m), as shown in Figure 2.

In specific implementation, the curve equation of the water-facing surface of the vane 2 is y=A _lX ⁴ +B _lX ³ +C _lX ² +D _{l X}

+E where A^- XlCr ⁸ ~- 9X10 ^-8 , BfS XlO ^-5 5.5X10 ^-5 , d=-6.5 X 10 ^-5 ~

-8.5Χ1 (Γ ⁵ , D^JXIO - ¹ ~ 2.6X10 ^-1 , Ei=-9X 1 (T ² ~- 1.3 X 10 ^-1 , curve of the back surface) The equation is y = A ₂ x ⁴ + B ₂ x ³ + C ₂ x ² + D ₂ x + E ₂ , where A ₂ = 1.9 X 10 ^-9 ~ 2.3 X 10 ^-9 , B ₂ = -1.7 X 10 ^{- 6} ~- 2.1 X 10 ^-6 , C ₂ =-9.5 X 10 ^-4 ~- 1.0 X 10 ^-3 , D ₂ =2.5 X 10 - ¹ ~ 3.0 X 10 E ₂ =3.1~3.7, x, y in the equation The unit is millimeter, and the head of the vane (2) is smoothly connected between the water-facing surface and the back surface, and the tail of the vane (2) is connected by a fold line between the water-facing surface and the back surface.

The following table is a table of the dimensions of the seat ring calculated from the above relationship:

It can be seen from the above that the efficiency can only meet the requirements when the unit speed is selected between 28 and 42. Otherwise, it is difficult to achieve the expected cooling effect, because the relationship between the cooling fan speed and the turbine efficiency is substantially cubic power. Therefore, when the efficiency is lower than 85%, it will be difficult to obtain the desired rotational speed. The parts not covered by the present invention are the same as the prior art or can be implemented by the prior art.

Claims

Claim

1. A direct-coupled low-speed small mixed-flow turbine seat ring for a hydrodynamic cooling tower, which is mainly composed of an upper ring plate (1), a lower ring plate (3) and a lower ring plate (1) and a lower ring. The vane (2) between the plates (3) is characterized in that the vane (2) is a negative curvature vane, and the height of the negative curvature vane (2) is the diameter D1 of the influent side 0.07~0.09 times, the length L is 0.16~0.2 times of the diameter D1 of the inlet water; the diameter D2 of the water outlet side of the negative curvature guide vane (2) is 0.75~0.95 times of the diameter D1 of the inlet side; The annular plate (1) and the lower ring plate (3) have an outer diameter D3 which is the negative curvature guide vane

(2) 1.0 to 1.25 times the diameter D1 of the inlet water, the inner diameter D4 of the upper ring plate (1) and the lower ring plate (3) is 0.7 to 0.9 of the diameter of the inlet of the negative curvature guide vane (2) The curve equation of the water-facing surface of the vane (2) is

-9 X 10 ^-8 , Bi=3.5 X 10 ^-5 ～5.5 X 10 ^-5 , d=-6.5 X 10 ^-5 ～ 8.5 X 10 ^-5 , Dj ' =2.2 X 10 - ¹ ~ 2.6X lO^ ^{Ef ^ X 10-2~- 1.3 X 10- 1} , the back surface curve equation is _{^{y = a 2 x 4 + B}} 2 x 3 + C 2 x 2 + Ό 2 'x + E 2, where a ₂ = 1.9 X 10 ^-9 ~2.3 X 10 ^-9 , B ₂ =-1.7X 10 ^-6 ~- 2.1 X 10 ^-6 , C ₂ =-9.5 X10 ^-4 ~- 1.0Χ10 ^-3 , Ό ₂ ' =2.5 10 〜 3. (^10 ^-1 , Ε ₂ =3.1~3.7, where χ, y are in millimeters, and the head of the vane (2) is smoothly connected between the water-facing surface and the back surface, the vane (2) The tail line between the tail water surface and the back water surface is connected; the relationship between the inlet diameter D1 of the negative curvature guide vane (2) and the fan speed n of the cooling fan is: Dl=KlXnllX>/ ^/n, where D1 is the negative curvature guide vane (2) inlet water diameter, the unit is m, Kl=1.15~1.25, nil is the unit speed, the value is between 28~42, H is the tower water pressure , in m, n is the speed of the blade, the unit is r/mino

2. The seat ring of claim 1 wherein said number of vanes (2) is 15-19