JPH074336A - Continuous fluid acceleration axial-flow impeller - Google Patents

Abstract

PURPOSE: To provide an impeller for a turbine machine corresponding to the pressure difference of a wide range. CONSTITUTION: This paper provides an impeller 10 which forms a continuously changing fluid passing region 20 in cooperation between an inner core 12 and a jacket 16. The continuous change of the fluid passing range 20 provides the fluid with continuous axial-flow acceleration or generates the pressure gradient corresponding thereto. At the same time, a blade 14 provided in the fluid passing range 20 and having a continuously changing angle is provided. The inclination angle of the continuously changing blade 14 continuously and angularly accelerates the fluid and provides a torque. The blade 14 with a continuously changing inclination angle rotates with the inner core 12 to provide a torque.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates generally to turbine machine technology, and more particularly to impellers for combined pressure differentials in different states, including fluid pressure differentials and pressure differentials associated with a wide range of specific velocities.

[0002]

2. Description of the Related Art The layout of a Kaplan turbine or the like is very special and cannot be used for various purposes. The Kaplan turbine cannot be used, for example, when the head is less than 100 m. Furthermore, modern turbine machine technology has not been able to design a multi-blade impeller that compresses air in a single stage to the pressure required by a jet engine.

[0003]

SUMMARY OF THE INVENTION An object of the present invention is to provide a blade that continuously responds to the action of the flow rate and pressure under different conditions such as pressure, fluid density, compressibility, viscosity and temperature. Is to provide a car.

[0004]

SUMMARY OF THE INVENTION In accordance with the present invention, an impeller is provided which provides a continuously variable fluid passage area with cooperation of an inner core and a jacket. This continuous change in the area of the fluid passage region causes continuous axial flow acceleration of the fluid, and a corresponding pressure gradient is obtained. Further, according to the present invention, blades provided in the fluid passage area and having continuously changing angles can be obtained at the same time. Such a continuously changing blade tilt angle results in a continuous angular acceleration of the fluid and a corresponding torque. The vanes whose inclination angle changes continuously rotate with the inner core to generate torque.

A set of different embodiments of the invention is disclosed using an impeller according to the invention described above. In addition to the feature of producing continuous axial and angular acceleration, the inner core with axial extension provided by the present invention has blades extending axially beyond the entire length of the impeller. This is an important distinction from prior art arrangements such as screws or typical turbine designs.

According to the present invention, in order to efficiently exchange energy between the fluid and the impeller, there must be a change in velocity (both in the axial flow direction and in the rotational direction), which requires a continuous change in the fluid passage area. Is based on the understanding that you need. The continuous deformation of this region causes acceleration, which creates a torque on the blade due to the pressure difference created. With this technology, the rotational speed of the fluid can be kept low and at the same time the pressure difference between the input and the output can be highly utilized. This technique also prevents the occurrence of cavity phenomena in applications where the fluid is a liquid.

The role of the area ratio (input to output) is very important, as is clear from the embodiments described here.

The controlled simultaneous rotational and axial acceleration of the fluid allows very efficient energy exchange between the fluid and the impeller. Since the fluid is rotated before entering the impeller, some energy is rotational kinetic energy and some axial flow kinetic energy when first contacted. The amount of angular velocity imparted to the fluid prior to entering the impeller is selected to produce a given torque, while the axial velocity determines the mass flowing through the impeller. There is also a pressure difference between the inlet and outlet, which couples with the flow-through mass to determine energy. A continuous change in the axial and rotational acceleration of the fluid creates a gentle pressure gradient. If the fluid leaves the impeller with rotational kinetic energy, it is necessary to provide a fixed vane at the outlet to straighten the flow and recover the energy in the form of a negative pressure differential.

To form an impeller based on the above-mentioned beneficial features, the principles set forth above have been applied in accordance with the present invention.
As mentioned above, one of the key features of this new technology is to internally create an axial acceleration of the fluid to obtain a pressure differential that helps generate torque. Therefore, the impeller is manufactured according to the present invention based on the above principles, and also with a selection as to how much axial fluid acceleration occurs in the impeller. According to the invention, this choice determines the shape of the inner core. When a shape other than a straight cylinder is selected for the outer jacket, the factors of this shape play an important role not only in the acceleration of the fluid in the rotational direction but also in the acceleration of the axial flow. Therefore, the pressure gradient distribution along the impeller is also increased. Plays an important role in.

In applications such as propellers where it is difficult to equip a fixed separate jacket, the outer jacket can be designed to rotate with the impeller.

Once the criterion for axial flow acceleration is established, the mathematical function is determined and the instantaneous axial flow velocity of the fluid is known at all points along the impeller. This function determines the shape of the inner core.

"Area" of fluid passage used in the text
Is the area remaining between the outer jacket and the inner core,
Set as a function of flow rate and velocity. If the fluid is incompressible, the flow is steady and this region is determined by the ratio of flow rate to instantaneous velocity at all points along the axis. On the other hand, if the fluid is compressible, the change in density as a function of pressure and temperature must also be considered.
That is, the area calculation is a function of the selected acceleration evaluation criteria and the instantaneous value of the flow rate which is also a function of the variable density.

The change of the radius of the inner core is one of the important features of the present invention. From the description of the fluid passage area, the formula for calculating the radius of the inner core at all points along the axis of the impeller is obtained. This formula is established by subtracting the range left for fluid passage from the range drawn by the circle corresponding to the outer jacket. The result of this subtraction is the area of the circle drawn by the inner core,
This in turn determines its radius.

According to the present invention, the angular velocity of the fluid can be maintained in a controlled distribution state. As shown in the examples given here, some of the energy of the fluid must take the form of rotational speed as it enters and leaves the impeller. The criteria for exchanging this rotational energy within the impeller must be selected by the designer to make effective use of it.

Therefore, the designer must select a rotation acceleration handling method that he / she considers and determine a mathematical formula representing it.
It is important to minimize turbulence on the flow at the inlet and outlet to prevent turbulence and / or cavity formation.

As the diameter of the inner core changes continuously, fluids of different mass rotate around the axis of the impeller with changing radii but at the same rotational speed. By the law of conservation of rotational momentum, any torque received or produced by the impeller must take the form of rotational energy outside the impeller. This means that in our turbine, if the rotational energy of the fluid at the outlet is zero, then all the rotational speeds needed to produce the desired torque must be present at the inlet. This relationship can be used to calculate the total torque.

According to the present invention, the inclination angle of the blade can be obtained. The combination of the usable angular velocity of the impeller, the angle of the fluid, and the axial flow acceleration is the value of the angle (tilt angle) between the blade and the plane perpendicular to the axis measured at all points along the axis of rotation of the impeller. To decide. This angle can be calculated as the arctangent of the ratio of the algebraic subtraction of the angular velocity to the angular velocity times the radius of the outer jacket. This is the angle of inclination of the blade between all designated points on the axis and the outermost diameter of the blade at that point. This calculation is done for structure determination purposes.

The invention provides the rotational advance angle of the blade, that is, the angle from the point of start to any point on the impeller axis indicating how far the measured blade has rotated. This value is calculated as the integral of the angular velocity divided by the axial velocity and is used for structural determination purposes.

Torque is a function that is directly proportional to energy and inversely proportional to angular velocity. It is also a function of the force exerted on the vanes by the fluid mass when the fluid is rotationally accelerated. This can be calculated as the integral value of the force acting on the projected area of the blade in the radial direction on its average diameter along the length of the impeller.

Since the shape of the impeller is smooth and abrupt changes in speed are not forced, it is unlikely that a significant deviation from reality will occur when this method is used for ordinary applications. Since it is considered that there is no large relative velocity difference between the various flows of the fluid, it is possible to know the behavior of the fluid in detail by these equations in advance.

The designer can choose different approaches to the distribution of torque. For example, the designer may decide to smoothly change the angular velocity of the fluid. In that case, either a constant distribution of the torque along the length of the impeller or any other suitable distribution for the application can be used. The shape of the blade is determined by the distribution of the angular acceleration.

The fluid must enter and / or exit the impeller with a certain amount of angular velocity required to produce torque. This angular velocity is produced and / or regulated by fixed vanes arranged in front of and / or behind the impeller. The input and output angular velocities are calculated as the integral value of the acceleration of the fluid produced by the blades over the length of the impeller, which is used to calculate the length of the impeller. The angular velocity at any position along the axis of rotation of the impeller can be calculated as described above.

The total angular velocity is calculated as a similar integral over the length of the impeller, allowing the designer to determine the distribution according to the needs of a particular application. For example, if you attach importance to the cavity as an evaluation criterion as shown in the example given here,
It is desirable that there is no angular velocity at the impeller exit, so we must create all the required fluid rotation speeds with fixed vanes in front of the impeller.

As mentioned above, if the angular velocity of the fluid is known, the impeller length can be calculated in accordance with the present invention, and it can be modified by changing the number of vanes.

The area projected by the blade on the plane perpendicular to the rotation axis is the area that determines the solidity of the impeller and supports the suction force. For example, in the case of a hydraulic turbine, this area supports the suction created by the head of water between the turbine and the spill and the suction created by axial and angular deceleration of the fluid.

The fixed blades are preferably provided upstream and downstream of the impeller. These fixed vanes, which are placed in front of the impeller to impart an angular velocity to the fluid before it enters the impeller and straighten the flow behind the impeller, are made on a cylindrical hub through which the shaft can pass.

The shape of these vanes must be determined by the designer based on the compromises that exist between friction and turbulence. Longer vanes reduce the likelihood of turbulence, but increasing vane length also increases friction losses.

It is noted that in applications involving steam or any other gas, these vanes can also be used as liquid separators.

The angle at the end of the fixed blade close to the impeller is calculated according to the invention in the manner outlined below.

The losses can be kept very low as the fluid is handled smoothly during axial movement in the impeller.

As can be seen by the preferred embodiment disclosed, the number of vanes can be reduced, and if the impeller is made to the proper length, the radial movement of the fluid will also be slow.

Since unavoidable losses are only losses due to energy leaving the system in the form of fluid velocity, other energy losses are also lost as turbulence and / or friction, so careful design will improve efficiency. Can be greatly enhanced.

The energy corresponding to the outgoing velocity can be made much lower than the energy of the entire system by increasing the diameter of the impeller. Turbulence and friction will not be significant because there is no abrupt change in flow velocity and almost no relative velocity difference between the layers of flow can be eliminated.

In most applications, the loss corresponding to the energy leaving the system as the escape rate can be kept below 1% of the total energy, so efficiencies near 98% are easily achieved.

The pressure at every point in the impeller can be determined by Bernoulli's equation, as described further below.

The various features of novelty which characterize the invention are pointed out with particularity in the claims annexed to and forming a part of this disclosure. For a better understanding of the content of the present invention, and the advantages and special objectives of the invention which can be achieved by the use thereof, reference should be made to the accompanying drawings and the description which sets forth preferred embodiments of the invention.

[0037]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the drawings and in particular to FIG. The present invention comprises a continuous fluid accelerating axial flow impeller, generally indicated at 10, including an inner core 12, one or more vanes 14 and an outer jacket 16. FIG. 5 is a schematic diagram generally intended to illustrate the features of the present invention. The shaft 18 transmits generated torque (or supplies torque used as a propeller). This axis 1
8 can be connected only to the inner core and the vanes connected to it, or to the outer jacket, or fixed and rotatable with the inner core and the vanes.

According to the invention, the radius R of the inner core is a function of the length along the centerline of the arrangement, ie the X axis. This radius varies continuously so that the fluid passage area between the outer jacket and the inner core (region 20) varies continuously. Between outer jacket 16 and inner core 12 (region 20)
This continuously changing fluid passage area of the inlet 22
The fluid passing from the outlet to the outlet 24 is continuously accelerated by the axial flow. The axial flow acceleration of the present invention can also be provided by varying the outer jacket radius R ₀ with respect to the X axis. That is, the radius R _{0 of the} outer jacket is the X axis R _0.
It can be said to be a function of the distance x along x.

According to the present invention, it is possible to obtain the torque for continuously accelerating the fluid flowing from the intake port 22 to the outlet 24. This can be accomplished in accordance with the present invention by continuously changing the tilt angle of the vanes 14. Therefore, the angle Γ with a constant change in the blade angle (continuously changing inclination angle of the blade 14)
Gives a continuous angular acceleration and a torque corresponding thereto to the fluid.

The following are terms used in future discussions.

[Table 1]

The exact form of fluid acceleration is selected in accordance with design constraints including volumetric flow rate Q and axial flow velocity V (x) of the fluid along the X axis. The continuous fluid acceleration axial flow impeller of the present invention can be designed in accordance with the following matters.

In designing the impeller of the present invention, one must first consider how axial acceleration of the fluid in the impeller occurs. Once the axial velocity of the impeller is determined, the radius of the inner core is determined based on the equation that is established by subtracting the area of the fluid passage portion from the area drawn by the circle corresponding to the outer jacket.
The area obtained as a result of the subtraction is the area of the circle drawn by the inner core.
Next, this is used to determine the radius.

[0043]

[Equation 5]

The next important consideration according to the invention is the angle Γ (x between the blade and the plane perpendicular to the axis, measured at any point along the axis of rotation of the impeller (in the X-axis direction). )
Is the value of. This angle (the angle of inclination of the blades) varies continuously, the state of which shows this angle for a two-blade impeller, FIG.
You can see best by looking at.

This angle Γ (x) can be calculated as the arctangent of the ratio of the axial flow velocity to the algebraic subtraction of the angular velocity times the radius of the outer jacket. This is the blade tilt angle between any given point along the axis and the outermost diameter of the blade there. This is calculated for structural purposes.
The following equation is used for the calculation of the blade tilt angle Γ (x).
As mentioned above, the vanes extend the entire length of the inner core from the leading end to the trailing end of the inner core.

[0046]

[Equation 6]

Another important feature of the present invention is the rotational advance angle of the vanes. This angle represents how much the blade advances by rotation from the starting point of the blade (starting location on the inner core) to any point along the X axis (axial direction of the impeller). This is best understood by looking at FIG. 6 which shows that the blades are rotationally advanced based on the change in angular position from the angular start position of the blade to the angular end point at the opposite axial end. Ah

The difference between the angular start position and the angular end point is the rotational advance angle. Since the blade tilt angle Γ (x) varies continuously, the rotational advance angle Θ (x) is calculated as the integrated value of the total angular velocity divided by the axial velocity and is used for structural purposes. This rotation advance angle Θ (x) is calculated by the following equation (3).
Given in.

[0049]

[Equation 7]

Torque is a function which is directly proportional to the power and inversely proportional to the working angular velocity expressed by the equation (4).

[0051]

[Equation 8]

Due to the law of conservation of rotational momentum, if the rotational energy of the fluid at the turbine outlet (or the inlet side of the pump) is zero, the torque can still be calculated. The torque in this case can be calculated by the following equation.

[0053]

[Equation 9]

Here, MF is the fluid mass, r (x) is the average radius of the fluid mass, and W (x) is the angular velocity of the fluid.

Torque is also a function of the force exerted on the vanes when the fluid mass is rotationally accelerated. The torque can be calculated as an integral value of the force acting on the radial projection of the blade area at the average radius point given by the following equations 5a and 5b along the length of the impeller.

[0056]

[Equation 10]

Equation 4b can be modified as follows to calculate the torque at any point X along the impeller.

[0058]

[Equation 11]

The input and output angular velocities can be calculated as an integral value of the acceleration of the fluid blocked by the blades over the entire length of the impeller. These angular velocities can then be used to calculate the impeller length. Equation (6) gives the angular velocity at any point along the axis of rotation of the impeller.

[0060]

[Equation 12]

The area projected by the blades on the plane perpendicular to the rotation axis is the area that supports the suction pressure, and is calculated by the following equation (7).

[0062]

[Equation 13]

As described above, it is desirable to provide the fixed blade upstream of the impeller. The upstream vanes create an angular velocity in the fluid before entering the impeller, and the downstream vanes straighten the flow. The exact shape of the vanes will be determined by the designer based on a compromise between friction and turbulence, based on several considerations. The longer the blades, the less likely turbulence is, but the longer the length, the greater the friction. The angle of the downstream portion of the fixed blade near the impeller is calculated by the following equation (8).

[0064]

[Equation 14]

The efficiency of this arrangement is calculated by the equation (9).

[0066]

[Equation 15]

The pressure at an arbitrary point along the X axis (axial direction of the impeller) can be determined by Bernoulli's equation, and the following equation (1)
0).

[0068]

[Equation 16]

As shown in FIG. 11, if the energy of the axial velocity of the fluid at point 2 is greater than the energy corresponding to the rotational velocity, the fluid leaves the impeller at a rotational velocity in the opposite direction to the rotation of the impeller. Go. On the other hand, if the energy corresponding to the rotation speed is larger than the energy of the axial speed, the fluid leaves the impeller at a rotation speed in the same direction as the rotation of the impeller. This adds a fixed blade, point 3
It can be controlled by straightening the subsequent flow,
The amount of rotation we can control in this respect is limited due to cavity considerations. Quenching the rotational speed at this point with a fixed vane results in a reduction in pressure, which is not allowed to decrease beyond the limits imposed by the cavity phenomenon.

The ideal condition is that there is no rotational speed of the fluid at the exit point 2. This can be controlled by adjusting the rotational speed between points 1 and 2 so that the axial flow and rotational energy remain balanced at point 2 when the impeller is operating according to design parameters. When we liberate above or below the design parameters, vortices occur that are critical to loss, which is typical of turbines with fixed blades. Maximum efficiency is achieved under design conditions. However, since most applications require a constant working speed, the axial flow and rotational energy at point 2 are rarely equal. Therefore, it is very often necessary to adjust the fluid rotation speed between points 1 and 2. This adjustment can be calculated as follows by averaging the axial and rotational dynamic pressures and finding the difference between the required dynamic rotational pressure and the pressure that would occur if not adjusted.

Without adjustment, the rotational speed of the fluid at point 2 is

[0072]

[Equation 17]

If the two dynamic pressures at point 2 are equal,

[0074]

[Equation 18]

The actual angular velocity of the fluid that should be

[0076]

[Formula 19]

The adjustment of the angular velocity between points 1 and 2 is as follows.

[0078]

[Equation 20]

As shown in FIGS. 1 to 6, an example of the present invention will be described based on a three-blade impeller developed according to the present invention.

The following assumptions are made to simplify the description. 1. The compressibility of the fluid is not considered. 2. Disregard the losses due to friction, viscosity and turbulence. 3. The rate of change of axial flow velocity along the axis of rotation is constant and radial acceleration due to the shape of the inner core is not considered. 4. The fluid is water having a density of 1000 kg / m ³ .

It should be noted that different evaluation criteria can be used for angular acceleration as well as radial and axial acceleration. In this example, on the basis of the evaluation criteria described above, it was chosen as the evaluation criteria that the velocity changes were evenly distributed along the length of the impeller. The designer may choose to have a uniform distribution of torque along the length of the impeller, or may choose different criteria for the particular application for the distribution of axial flow and / or angular acceleration. You can also do it. The pressure at any point within the impeller can be calculated by equation (10), which corresponds to Bernoulli's equation, and this analysis deals with absolute pressure.

As an example, the impeller was designed to produce a total of 20 MW at a water head of 150 m and a rotation speed of 600 RPM. The turbine operates at 2 m above the spill, and the minimum permissible absolute pressure estimated in extreme conditions of temperature and dissolved gas due to the limitation of the cavity is 42000 Pa (minimum permissible value at P ₃ point, see FIG. 6).

Since this is a theoretical example, the cross-sectional area of the shaft 18 and the thickness of the blades 14 are ignored for simplification.

Consider the case of two inner cores 12 having the same cross-sectional area which are arranged back to back on the same axis and are continuously integrated. As will be seen later, the cross-sectional areas of both inner cores selected are the same, but the vanes 14, 14 'have different shapes. The reason for this is that we choose that the angular velocity of the fluid is zero at the end of the impeller 10 and the tilt angle of the vanes changes according to the angular velocity of the fluid. The angular velocity at the outlet is selected to be 0 in order to prevent suction due to the fluid rotation speed at the end of the impeller where the cavity is important. This also means that no fixed vanes are required at the end for the fluid deflection.

It is assumed that the atmospheric pressures at both ends of the water channel at the power generation site are equal and the value is 94000 Pa.

A very important factor chosen by the designer is the velocity V ₃ at the exit end. For this particular case, we choose V ₃ = 3.0 m / s to maintain high efficiency and keep emissions within a reasonable range.

First, the discharge (outflow) rate is determined. It should be noted that, through this example, the values obtained from the calculation by the formula are in agreement with the final results of the calculation shown in Table 1 calculated by the computer using the approximation method.

[0088]

[Equation 21]

If the angular velocity of water at the end of the impeller is 0
If we wish to obtain, all the energy leaving the impeller is in the form of an axial velocity, so by choosing a value of V ₃ = 8 m / s we obtain:

[0090]

[Equation 22]

P ₃ should always be greater than the minimum permissible pressure (42000 Pa in this case) to avoid cavities.

From the value of V ₃ we can also calculate the area of the outer jacket.

[0093]

[Equation 23]

Therefore, the radius is

[0095]

[Equation 24]

The torque that needs to be produced is

[0097]

[Equation 25]

This is equal to the reaction force applied to the blade when water is rotationally accelerated. In this example, this reaction force is evenly distributed to both halves of the impeller. Therefore, for each category,

[0099]

[Equation 26]

This means the following matters.

[0101]

[Equation 27]

The distribution of changes in axial flow velocity along the impeller can be obtained by the following equation. From 1 to 2:

[0103]

[Equation 28]

From 2 to 3:

[0105]

[Equation 29]

Therefore, the rate of change of V _x with respect to _x is

From 1 to 2:

[0108]

[Equation 30]

From 2 to 3:

[0110]

[Equation 31]

For this example, a uniform distribution of angular velocities along the X-axis is assumed, and for both sections:

[0112]

[Equation 32]

Therefore, its rate of change with respect to x is

[0114]

[Expression 33]

However, since dx = dV (x) dt, the angular acceleration for this case is

[0116]

[Equation 34]

The value of W ₁ is obtained by integrating this acceleration over the entire length (see equation (6)). Torque can be calculated by using the equations for angular acceleration along with equations 5a, 5b.

[0118]

[Equation 35]

As a first trial, if the area (Ra) ratio is 6, Kt can be calculated, but this calculation is exactly the same as the formula for obtaining the torque. This calculation can be obtained by an integration method or a numerical calculation method using a computer.

By knowing the value of Ra, the following equation is obtained.

[0121]

[Equation 36]

By making the torque calculated from energy equal to the torque calculated by integration, W ₂ = 2
We get 7.95.

Here, half of the total net energy is the point 2
The fact that all are available as kinetic energy (axis and angular velocity) is used.

[0124]

[Equation 37]

V ₂₁ is a point 2 calculated by V ₂ = V ₀ Ra
When compared to the axial flow velocity of, the error value that can be used to determine the new value of Ra is known. This method is repeated until an appropriate value of the area ratio is found by the approximation method.

The final value of Ra we obtained in this example is: Ra = 4.126.

We can improve the design by choosing a higher V ₃ value. This means smaller and cheaper impellers can be made. The minimum size of our product is point 3
Is determined by the pressure conditions at, and in this case the pressure must never be less than 42000 Pa.

The impeller can also be made smaller by lowering the turbine height above spill and / or by increasing the axial flow velocity at point 5. If V
Increasing the value of ₅ will incur a penalty of reduced efficiency, but the energy loss due to V ₅ is loss =
σV ₅ ² /2=0.31%. That is, the expected efficiency without considering friction and turbulence is 99.69%. Efficiency can also be calculated as:

[0129]

[Equation 38]

The area projected by the blades on a plane perpendicular to the axis is integrated and, together with the selected number of blades (3 in this case), is equalized with the area of the outer jacket at point 3 to determine the length of the impeller. Can be estimated (using equation (7)). The area at point 5 is

A ₅ = Q / V ₅ = 4.56 m ² and the radius is R ₅ = A ₅ / π = 120 m

Cost can be reduced by increasing V ₅ to reduce efficiency and reduce the radius of the impeller.

The shapes of the blade and the inner core are expressed by the equation (1),
Calculation is performed using (2) and (3). The results of the computer estimation are included here as Tables I and II. Table I
Includes data that is consistent with this example, and Table II shows that the angular velocity used is 3
The reader knows how the vane shape, the angular velocity of the water and the pressure at points 1 and 2 change, as it provides data for another example using the same data except that it was decelerated to 60 RPM. Will be possible. With a slow impeller,
Note how the W ₁ increases because the vane takes the shape of a bucket (water receiver) and produces the required torque.

The conditions in Table I (TABLE I) are as follows.

[0135]

[Table 2]

[0136]

[Table 3]

The conditions in Table II (TABLE II) are as follows.

[0138]

[Table 4]

[0139]

[Table 5]

The axial flow velocity at point 3 is from 8 m / s to 7.5 in the first example (Table I) in order to balance the pressure produced by the axial acceleration of water with the pressure required to produce the extra torque.
You must decelerate to m / s (Table II).

As mentioned above, the present invention can be used in a variety of different applications. FIG. 7 shows an impeller of the present invention used as a propeller. In this case, the outer jacket 16 shall be able to rotate with the impeller for simplicity. Impeller 1
0 has one or more vanes 14 in the propeller embodiment. A constant velocity exhaust duct 30 is provided which cooperates with the interior surface 32 to achieve a steady velocity of exhaust fluid.
A preceding vane deflection element 34 is also provided to impart a rotational speed to the fluid. Shown in the arrangement is a shaft 18, which either rotatably supports the filter screen 36 (the filter screen rotates with the shaft) or suitable bearings are provided for mutual rotational movement.

A turbine or pump arrangement is shown in FIG. 8 (a turbine arrangement for receiving energy from a flowing fluid or a pump arrangement for pumping a fluid with energy supplied from a shaft 18). In this arrangement, the outer jacket 16 is shown, in which fluid flows from the intake 22 to the exhaust 24. A suitable leading deflector vane 34 is provided, and a similar suitable trailing deflector vane 38 is also provided. In this embodiment, two impeller cores 12 and 12 'are illustrated in the same manner as shown in FIG. Feather 14
Are provided in the same way as in the example of FIG. 1c.

The impeller of the present invention is also effective as a jet engine as shown in FIG. This arrangement also includes the outer jacket 16 and the trailing portion 30 cooperates with the inner surface 32 to provide a steady velocity of fluid at the outlet 24. A front or leading deflection vane 34 is provided adjacent the intake 22. The surface of the inner core 12 is made equivalent to that described in the example, and the blades 14 are provided in the same manner as the illustrated one. The burner 40 is installed downstream of the intake impeller 10 ', upstream of the exhaust impeller 10 ", and the leading or intake deflection vane 34' is installed upstream of the exhaust impeller 10 '. The exhaust impeller 10" is front. Of inner core 12 and vanes 14 made in a manner similar to the example of FIG.

A turbine machine (engine) is disclosed as shown in FIG. This arrangement has a forward or leading deflector vane 34 and a trailing or ejector deflector vane 38.
Rotors 10a and 10b include inner cores 12 and vanes 14 made in a manner similar to that described in the examples. An outer jacket 16 is provided to cooperate with the impeller to form a fluid passage area and a burner 40 is provided. Each impeller is connected to a shaft 18 and rotates.

The impeller can be manufactured by shaving a shape from a material using a computer-controlled machine.

Alternatively, the inner core is molded, punched according to the advancing angle of the blade, the pin of the blade of suitable shape is inserted into the hole, the blade is molded with plastic excipient and the desired finish is obtained. You can build them into a state finished with sandpaper and finish polish.

The shape of the inner core may be cut out from the material or may be pasted with discs of different diameters and sanded to the desired finish before sanding to the desired finish, as before. Can be created.

Once the model is complete, the manufacturing mold can be made of any suitable material. A copy of the impeller can be made directly from the mould, or the lost wax or foaming method can be used to obtain the braze or foam molding used to metal cast the product.

The impeller can be made solid or hollow depending on the requirements of the application. The shape of the pin that assembles the vane is calculated based on the strength of the material selected and the stress the vane must withstand under extreme operating conditions.

While specific embodiments of the present invention have been presented and described in detail to demonstrate the justification of the principles of the invention, the invention can be embodied in other forms without departing from such principles.

[Brief description of drawings]

FIG. 1 is a perspective view of a 3-blade continuous fluid accelerating axial flow impeller according to the present invention.

FIG. 2 is a sectional perspective view showing a maximum diameter portion of an inner core of a three-blade type continuous fluid accelerating axial flow impeller according to the present invention.

FIG. 3 is a perspective view showing a cross section of a core and a blade of a three-blade type continuous fluid accelerating axial flow impeller according to the present invention.

FIG. 4 is a schematic diagram in the simplest form of a continuous fluid accelerating axial flow impeller according to the present invention.

FIG. 5 is a book that has two impellers placed back-to-back for use as a turbine, showing a continuously variable fluid passage region between an outer jacket and an inner core and a continuously variable blade angle; 1 is a schematic view of an impeller according to the invention.

FIG. 6 is a schematic diagram of a continuous fluid accelerating axial flow impeller according to the present invention showing the angle of advance of the blades.

FIG. 7 is a schematic diagram of a continuous fluid accelerating axial flow impeller according to the present invention used as a propeller.

FIG. 8 is a schematic diagram of a continuous fluid accelerating axial flow impeller according to the present invention used as a turbine or pump.

FIG. 9 is a schematic diagram of a continuous fluid accelerating axial flow impeller according to the present invention used as a jet engine.

FIG. 10 is a schematic diagram of a continuous fluid accelerating axial flow impeller according to the present invention used as a turbine machine.

FIG. 11 is a schematic diagram of a continuous fluid accelerating axial flow impeller according to the present invention used as a turbine in a hydraulic turbine arrangement.

[Explanation of symbols]

 10 Impeller 12 Inner Core 14 Blade 16 Outer Jacket 18 Shaft 20 Area 22 Intake 24 Discharge Port

Claims (16)

[Claims] 1. An impeller having an inner core having an axial extension, and a jacket cooperating with the inner core and having at least the same axial size as the axial extension. The inner core and the jacket cooperate to define a fluid passage that varies continuously from the intake end to the discharge end and provide a means for producing a continuous axial flow acceleration of the fluid and a corresponding pressure gradient. An axial flow impeller characterized in that the vanes connected to the core and arranged in the fluid passages have a continuously varying inclination angle and are means for producing continuous angular acceleration of the fluid. 2. Each of the vanes has a first end to a second end of the inner core.
The impeller according to claim 1, wherein the impeller extends in the axial direction toward the end. 3. The impeller according to claim 2, wherein a driven shaft is connected to the inner core and drives the inner core and the blade as a propeller. 4. An impeller according to claim 2, wherein a shaft is connected to the inner core to drive the inner core and the vanes, pump fluids and / or compress gases. 5. The fluid at the intake end has a pressure head and the discharge end is provided with a fluid outlet and comprises a hydraulic turbine,
The impeller according to claim 2, wherein a torque corresponding to the continuous angular acceleration of the fluid in the turbine is generated. 6. The intake end is connected to a high pressure steam source and the discharge end is connected to a fluid outlet, the high pressure steam is continuously accelerated in the axial direction, and the continuous angular acceleration produces a torque corresponding thereto. The impeller according to claim 2, which is generated. 7. A burner is provided upstream of the inner core and the vanes constituting a turbine, and an additional impeller having the vanes is provided upstream of the turbine to operate as a compressor. The impeller according to claim 2, wherein thrust is generated at the outlet end of the jet engine type. 8. The impeller according to claim 2, wherein the impeller is formed as a blower or a fan. 9. Impeller according to claim 2, characterized in that the impeller is formed as a gas or air motor. 10. A fixed deflector plate is provided upstream of the inner core to impart a rotational speed to the fluid by the deflector plate before the fluid acts on the inner core and the vanes. The impeller described in. 11. An impeller comprising an inner core, a plurality of vanes, and an outer jacket, the vanes extending from a first axial end to a second axial end of the inner core, the impeller passing through the impeller, and flowing the fluid. Is used to cause continuous axial flow acceleration in the fluid, and flow through the impeller to flow the fluid to cause continuous angular acceleration in the fluid to generate torque corresponding thereto. 12. A fluid head at the intake end is provided with a head pressure and a deflector is provided to impart a rotational speed to the fluid before it passes through the impeller. Energy usage. 13. An impeller having an inner core having an axial extension, and a jacket cooperating with the inner core and having at least the same axial dimension as the axial extension. The inner core and the jacket cooperate to define a continuously changing fluid passage, and a vane connected to the inner core and disposed in the fluid passage has an axial extension of a size equal to the axial extension. In an axial flow impeller having a section and having a continuously varying tilt angle, Q (x) is the flow rate at a given position as a function of position along the X axis, and V (x) is along the X axis. Assuming that the fluid has an axial velocity, the radius R (x) of the core is expressed by the following equation: And an axial flow impeller resulting in continuous axial flow acceleration of the fluid. 14. W (x) is the angular velocity of the fluid along the X axis, W ₀ is the angular velocity of the impeller, and R ₀ (x) is the radius of the vane, where R ₀ (x) is the radius of the outer jacket along the X axis. Γ is the following equation The axial flow impeller according to claim 13, characterized in that: 15. The angle Θ between the starting point of each blade at one axial end of the impeller and the ending point of each blade at the other axial end of the impeller is given by the following equation: The axial flow impeller according to claim 13, characterized in that: 16. The projected area of each blade on a plane perpendicular to the axis of rotation is expressed by the following equation: Impeller according to claim 14, characterized in that it is provided by: