CN218844675U - Axial flow fan - Google Patents

Axial flow fan Download PDF

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CN218844675U
CN218844675U CN202223385531.6U CN202223385531U CN218844675U CN 218844675 U CN218844675 U CN 218844675U CN 202223385531 U CN202223385531 U CN 202223385531U CN 218844675 U CN218844675 U CN 218844675U
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flow
hub
angle
blade
camber line
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连柽煜
符渡
黄建平
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

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Abstract

The application provides an axial flow fan, which comprises an impeller; the impeller comprises a hub and blades; the blades are arranged on the hub; on the cross section of the impeller, the diameter of the hub is Dh; the circle where the blades are located is a wheel rim, the diameter of the wheel rim is Ds, and the hub ratio D = Dh/Ds; wherein the hub ratio D =0.4-0.6. According to the axial flow fan, the Mach number of the fan blade top can be effectively reduced.

Description

Axial flow fan
Technical Field
This application is fan technical field, concretely relates to axial fan.
Background
At present, an axial flow fan is widely used as an impeller machine for conveying gas. But the rotating speed and the air pressure of the fan in general occasions are lower, and the density and the temperature of the air before and after the fan basically have no change. But for the high-rotating-speed axial flow fan with special application, the front-back pressure difference is large, and the gas state parameter change is obvious; and supersonic regions may appear at the blade tips under partial working conditions.
Therefore, how to provide an axial flow fan capable of effectively reducing the mach number of the fan blade top is a problem which needs to be solved by those skilled in the art urgently.
SUMMERY OF THE UTILITY MODEL
Therefore, the technical problem that this application will be solved lies in providing an axial fan, can effectual reduction fan blade top mach number.
In order to solve the above problems, the present application provides an axial flow fan including an impeller; the impeller comprises a hub and blades; the blades are arranged on the hub; on the cross section of the impeller, the diameter of the hub is Dh; the circle where the blades are located is a wheel rim, the diameter of the wheel rim is Ds, and the hub ratio D = Dh/Ds; wherein the hub ratio D =0.4-0.6.
Furthermore, in a meridian plane flow passage of the axial flow fan, the inner part of a shell of the axial flow fan is of a uniform cross-section structure from a gas inlet to a gas outlet.
Further, the blade profile of the blade is an asymmetric air blade profile; and/or the number of the blades is 7-11.
Further, the inlet geometry angle and the outlet angle of the blade are not equal.
Further, the cross-sectional radius at the inlet of the axial flow fan is 50mm.
Further, the distribution rule of the camber line installation angle of the hub along the flow direction follows a linear function: y is 1 ＝0.11x 1 +50; wherein x is 1 Relative position of camber line in the direction of flow, y, of the hub 1 The blade mounting angle is the blade mounting angle of the corresponding flow direction relative position of the camber line of the hub; the blade installation angle is an included angle between a blade camber line and the rotating direction of the impeller; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
Further, the camber line setting angle of the wheel rim follows a quadratic function along the distribution rule of the flow direction:
y 2 ＝-2.5e -4 x 2 2 +4.7e -2 x 2 +31; wherein x is 2 Relative position of camber line in the direction of flow, y, of the rim 2 The blade mounting angle is the blade mounting angle of the corresponding flow direction relative position of the camber line of the hub; blade mounting angleThe included angle between the camber line of the blade and the rotating direction of the impeller is formed; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
Further, the camber line setting angle of the hub follows a quartic function along the distribution law of the flow direction:
y 3 ＝-1.1e -7 x 3 4 +3e -5 x 3 3 -3.2e -3 x 3 2 +0.13x 3 +1.3; wherein x is 3 Is the relative position of the camber line in the direction of flow, y 3 The thickness of the blade corresponding to the relative position of the flow direction; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
Further, the camber line setting angle of the rim follows a quartic function along the distribution law of the flow direction:
y 4 ＝-6.2e -8 x 4 4 +1.9e -5 x 4 3 -2.3e -3 x 4 2 +0.1x 4 +0.45; wherein x is 4 Relative position of camber line of wheel rim in flow direction, y 4 The thickness of the blade corresponding to the relative position of the flow direction; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
According to still another aspect of the present application, there is provided a design method of the above axial flow fan, including the following steps:
step (1): determining the flow velocity Cm of the gas at the inlet of an axial fan 1 (ii) a The Mach number at the inlet of the axial flow fan is Ma;
step (2): calculating according to a basic gas dynamic equation to obtain the inlet area of the axial flow fan and the radius of a wheel rim;
and (3): by Cm 1 = nMa, calculating rim position relative speed W 1s ；
And (4): repeating the step (3) at least one time, and using different n values in at least two times of repetition processes to obtain different relative speeds W 1s Selecting the minimum relative velocity W 1s The corresponding hub ratio is used as the hub ratio of the impeller.
The application provides an axial fan. This application can effectually reduce fan blade top mach number.
Drawings
Fig. 1 is a schematic structural view of an axial flow fan in an embodiment of the present application;
FIG. 2 is a schematic structural diagram of an axial flow fan in an embodiment of the present application;
FIG. 3 is a schematic structural diagram of an axial flow fan in an embodiment of the present application;
FIG. 4 is a schematic structural diagram of an axial flow fan in an embodiment of the present application;
FIG. 5 is a schematic diagram of the impeller parameter structure in the embodiment of the present application;
FIG. 6 is a vane setting angle distribution profile along a flow direction in an embodiment of the present application;
FIG. 7 shows the blade thickness distribution along the flow direction in an embodiment of the present application;
FIG. 8 is a flow line distribution within the flow channel of the impeller in an embodiment of the present application;
fig. 9 shows the distribution of the entropy in the impeller flow channel in the embodiment of the present application.
1. A hub; 2. a blade.
Detailed Description
Referring to fig. 1-7 in combination, an axial flow fan includes an impeller; the impeller comprises a hub and blades; the blades are arranged on the hub; on the cross section of the impeller, the diameter of the hub is Dh; the circle where the blades are located is a wheel rim, the diameter of the wheel rim is Ds, and the hub ratio D = Dh/Ds; wherein the hub ratio D =0.4-0.6. The method can determine the optimal hub ratio suitable for most high-speed axial flow fan impellers, and can reduce the relative Mach number of the blade tips as much as possible, reduce the loss generated by shock waves and improve the pneumatic performance of the rotor; the high-rotating-speed axial flow fan rotor provided by combining the method has the following advantages: the inlet incoming flow of the rotor can be completely matched with the blade geometry, and the number of the blades can be reduced under the condition of meeting the performance requirement, so that the machining difficulty is reduced. D =0.5, is the optimum choice.
The application also discloses some embodiments, in the meridian plane runner of axial fan, from gas inlet to gas outlet, the inside constant cross section structure that is of axial fan's casing. The static pressure in the expanding flow channel increases along the flow direction, which may cause wall surface flow separation; in the convergent channel, the gas flow velocity is increased, and the flow loss is increased; the constant cross-section structure avoids the possible adverse effects of the two flow passages.
The application also discloses some embodiments, the blade profile of the blade is an asymmetric air blade profile; and/or the number of the blades is 7-11; further, the number of the blades is 9.
The present application also discloses embodiments where the inlet geometry angle and the outlet angle of the vanes are not equal.
The present application also discloses embodiments where the cross-sectional radius at the inlet of the axial flow fan is 50mm. The value of the radius, around 50mm, is calculated iteratively and is the optimum radius for the design that will maintain impeller inlet rim mach number at a minimum.
The application also discloses some embodiments, the camber line installation angle in the hub follows a linear function along the flow direction distribution rule: y is 1 ＝0.11x 1 +50; wherein x is 1 The relative position of the camber line of the hub along the flow direction, and y1 is a blade mounting angle of the camber line of the hub corresponding to the relative position of the flow direction; the blade installation angle is an included angle between a blade camber line and the rotating direction of the impeller; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
The application also discloses embodiments, and the mounting angle of the camber line of the wheel rim follows a quadratic function along the flow distribution rule: y is 2 ＝-2.5e -4 x 2 2 +4.7e -2 x 2 +31; wherein x is 2 Relative position of camber line of wheel rim in flow direction, y 2 The blade mounting angle is the blade mounting angle of the corresponding flow direction relative position of the camber line of the hub; the blade installation angle is an included angle between a blade camber line and the rotating direction of the impeller; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
The application also discloses some embodiments, the camber line installation angle of the hub follows a quartic function along the flow direction distribution rule:
y 3 ＝-1.1e -7 x 3 4 +3e -5 x 3 3 -3.2e -3 x 3 2 +0.13x 3 +1.3; wherein x is 3 Is the relative position of the camber line in the direction of flow, y 3 The thickness of the blade corresponding to the relative position of the flow direction; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
The present application also discloses embodiments in which the camber line setting angle of the rim follows a quartic function along the flow direction distribution law:
y 4 ＝-6.2e -8 x 4 4 +1.9e -5 x 4 3 -2.3e -3 x 4 2 +0.1x 4 +0.45; wherein x is 4 Relative position of camber line in the direction of flow, y 4 The thickness of the blade corresponding to the relative position of the flow direction; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
Fig. 8 shows the streamline distribution in the impeller flow channel under the design condition, the rotor inlet maintains a good flow state, the rotor can be tightly attached to the incoming air, and the air is not separated in the downstream flow process, which illustrates that the impact loss at the rotor inlet is controlled.
FIG. 9 shows the distribution of entropy in the flow channel of the impeller under the designed condition, and only a relatively high entropy value is generated in the wake region of the blade, which is unavoidable, and no high entropy region exists in the flow channel. Therefore, the impeller rotor can ensure that the incoming air is attached to the surface of the blade and enters the flow channel, and no turbulence is generated in the process of flowing downstream.
The application also discloses a design method of the axial flow fan, which comprises the following steps:
step (1): determining the flow velocity Cm of the gas at the inlet of an axial fan 1 (ii) a The Mach number at the inlet of the axial flow fan is Ma;
from Cm 1 Determining W 1s The formula of (1) is as follows:
1. giving Cm 1 An initial value;
2. static inlet temperature T Quiet ：T Quiet ＝T General assembly -Cm 1 2 /2/C p ；
3. Obtaining an inlet Mach number Ma: ma = (kRT) Quiet )^0.5。
Step (2): calculating according to a basic gas dynamic equation to obtain the inlet area of the axial flow fan and the radius of a wheel rim;
from Cm 1 Determining W 1S The formula of (1) is as follows:
1. obtaining an inlet Mach number Ma: ma = (kRT) Quiet )^0.5；
2. Static inlet pressure P Quiet ＝P General assembly /(1+0.2*Ma 2 ) 3.5 ；
3. Inlet density ρ: ρ = P Quiet /R/T Quiet ；
4. Inlet area a: a = m/ρ/Cm 1 ；
And (3): by Cm 1 = nMa, calculating rim position relative speed W 1s ；
And (4): repeating the step (3) at least twice, and using different n values in the repeating process of at least two times to obtain different relative speeds W 1S Selecting the smallest relative velocity W 1S The corresponding hub ratio serves as the hub ratio of the impeller.
From Cm 1 Determining W 1S The formula of (1) is as follows:
1. giving Cm 1 An initial value;
2. static inlet temperature T Quiet ：T Quiet ＝T General assembly -Cm 1 2 /2/C p ；
3. Obtaining an inlet Mach number Ma: ma = (kRT) Quiet )^0.5；
4. Static inlet pressure P Quiet ＝P General assembly /(1+0.2*Ma 2 ) 3.5 ；
5. Inlet density ρ: ρ = P Quiet /R/T Quiet ；
6. Inlet area a: a = m/ρ/Cm 1 ；
7. Radius of rim r 1s ＝(A/π+r 2 1h ) ^0.5, the stepStep (d) to obtain r 1s And D s ＝2*r 1s Ds is available because the hub radius is also given before and Dh =2*r 1h So that a hub ratio can be obtained
8. Rim rotation speed: u shape 1s ＝2πr 1s n/60；
9. Rim position relative speed: w 1S ＝(Cm 2 1 +U 2 1s ) 0.5, the step calculates to obtain r 1s Corresponding W 1S I.e. W corresponding to the respective hub ratio 1S The hub ratio is a dimensionless number, and is also often used as a design parameter in the design process.
From Cm 1 Determining W 1S The formula (c) is as follows:
1. giving Cm 1 An initial value (mach number of 0.3 times of the initial value can be given, and the selection of the multiple is free, because the multiple does not influence the size of the minimum relative speed obtained by the final iteration);
2. static inlet temperature T Quiet ：T Quiet = Ttotal-Cm 1 2 /2/C p ；
3. Obtaining an inlet Mach number Ma: ma = (kRT) Quiet )^0.5；
4. Static inlet pressure P Quiet ＝P General assembly /(1+0.2*Ma 2 ) 3.5 ；
5. Inlet density ρ: ρ = P Quiet /R/T Quiet ；
6. Inlet area a: a = m/ρ/Cm 1 ；
7. Radius of rim r 1s ＝(A/π+r 2 1h ) 0.5, the step of calculating to obtain r 1s And Ds =2*r 1s Ds is available because the hub radius is also given before and Dh =2*r 1h So that a hub ratio can be obtained
8. Rim rotation speed: u shape 1s ＝2πr 1s n/60；
9. Rim position relative speed: w 1s ＝(Cm 2 1 +U 2 1s ) 0.5, the step of calculating to obtain r 1s Corresponding to W 1s I.e. byW corresponding to corresponding hub ratio 1s The hub ratio is a dimensionless number, and is also often used as a design parameter in the design process.
As a high-speed axial flow fan, the pressure difference between the inlet and the outlet of the high-speed axial flow fan is large, and the design of the fan impeller is completed by reasonably calculating the aerodynamic and geometric parameters of the rotor, as shown in figure 3.
The application comprises the following implementation steps:
1. determining inlet gas state parameters and giving a rotor hub radius value; ( Here, the inlet gas state parameter refers to a state parameter such as gas pressure, temperature, mach number, and the like at the inlet of the fan. The radius of the hub is determined by the designer according to the specific structural requirements; while determining the hub radius value of the rotor. )
2. Selecting an impeller inlet flow velocity Cm 1 As iteration parameter, cm 1 The initial value can be selected to be about 0.3 times of the inlet Mach number; the flow velocity of the impeller inlet gas in the flow direction, which has been illustrated in the accompanying drawings.
3. Calculating according to a basic gas dynamic equation to obtain the area of a rotor inlet and the radius of a rim of the rotor inlet; the rotor inlet area here refers to the area of the annular region from the hub to the rim, and the formula is calculated as pi/4 (D) s 2 -D h 2 )。
As will be more readily understood when viewed in conjunction with FIG. 4, the rim position refers to the tip of the blade, which has a radius value of Ds/2.
4. Calculating the relative speed W of the rim position 1s ；
5. Returning to the step 2, changing Cm 1 The numerical value is continuously calculated to obtain different W 1s Until all W are obtained 1s When the minimum value occurs in the values, the calculation loop is exited, and W is selected 1s The ratio of the hub to the rim corresponding to the minimum value of (A) is used as the optimal hub ratio, and the optimal hub ratio corresponding to the invention is between 0.4 and 0.6, and is preferably about 0.5.
From Cm 1 Determining W 1s The formula (c) is as follows:
giving Cm 1 An initial value;
static inlet temperature T Quiet ：T Quiet ＝T General assembly -Cm 1 2 /2/C p ；
Obtaining an inlet Mach number Ma: ma = (kRT) Quiet )^0.5；
Static inlet pressure P Quiet ＝P General assembly /(1+0.2*Ma 2 ) 3.5 ；
Inlet density ρ: ρ = P Quiet /R/T Quiet ；
Inlet area a: a = m/ρ/Cm 1 ；
Radius of rim r 1s ＝(A/π+r 2 1h ) 0.5, calculated to r1s and Ds =2*r 1s Ds is available because the hub radius is also given before and Dh =2*r 1h So that a hub ratio can be obtained
Rim rotation speed: u shape 1s ＝2πr 1s n/60；
Rim position relative speed: w is a group of 1s ＝(Cm 2 1 +U 2 1s ) 0.5, the step calculates to obtain r 1s Corresponding W 1s I.e. W corresponding to the respective hub ratio 1s The hub ratio is a dimensionless number, and is also often used as a design parameter in the design process.
Relative velocity refers to the velocity of the airflow as viewed from the perspective of the impeller, with the impeller as a frame of reference.
From Cm 1 Determining W 1s The formula of (1) is as follows:
giving Cm 1 An initial value;
static inlet temperature T Quiet ：T Quiet ＝T General assembly -Cm 1 2 /2/C p ；
Obtaining an inlet Mach number Ma: ma = (kRT) Quiet )^0.5；
Static inlet pressure P Quiet ＝P General assembly /(1+0.2*Ma 2 ) 3.5 ；
Inlet density ρ: ρ = P Quiet /R/T Quiet ；
Inlet area a: a = m/ρ/Cm 1 ；
Radius of rim r 1s ＝(A/π+r 2 1h )^0.5；
Rim rotation speed: u shape 1s ＝2πr 1s n/60；
Rim position relative speed: w is a group of 1s ＝(Cm 2 1 +U 2 1s ) And 0.5, which can calculate the relative speed of the rim position.
FIG. 8 is a schematic view of a fan rotor setting angle and pitch, arc length and flow direction. In the present invention, the pitch and chord length are determined by determining the consistency of the blades and then selecting the number of blades (the number of blades selected in the present invention is 9). The included angle between the camber line of the blade and the rotating direction of the impeller is the installation angle beta of the blade, and the included angle between the camber line of the blade and the rotating direction of the impeller changes along with the flow direction.
FIG. 9 shows the blade rim, hub camber angle in the flow direction.
The camber line mounting angle of the hub follows a linear function along the flow direction distribution law: y is 1 ＝0.11x 1 +50；(x 1 Relative position in the flow direction, y 1 At a blade setting angle corresponding to the position of the opposite flow direction).
The camber line mount angle of the wheel rim follows a quadratic function along the distribution rule of the flow direction:
y 2 ＝-2.5e -4 x 2 2 +4.7e -2 x 2 +31。
the thickness of the blade in the flow direction from the blade rim, hub and its variation is given in figure 7.
Wherein,
the camber line installation angle of the hub follows a quartic function along the flow direction distribution rule:
y 3 ＝-1.1e -7 x 3 4 +3e -5 x 3 3 -3.2e -3 x 3 2 +0.13x 3 +1.3；。
the camber line setting angle of the wheel rim follows a quartic function along the distribution rule of the flow direction:
y 4 ＝-6.2e -8 x 4 4 +1.9e -5 x 4 3 -2.3e -3 x 4 2 +0.1x 4 +0.45. The arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan; the thickness of the blade is symmetrically distributed on two sides of the mean camber line by taking the mean camber line as a reference. Thereby, the blade thickness is determined. After the installation angle and the thickness of the camber line of the wheel rim and the hub are determined, the molded lines of the wheel rim and the hub of the blade are completely determined, the two molded lines are superposed to generate the surface of the blade, and finally the blade profile of the blade is determined.
The technical scheme of the application is that the meridian flow channel always keeps a constant area from the rotor inlet, and the chord length of the rotor blade is basically constant along the blade height; the hub ratio of the rotor is 0.5, and the number of blades is 9; and the front end of the rotor is not provided with a fluid director and is not driven by a motor. In the technical scheme of the application, the movable blades are asymmetric pneumatic blade types; the thicknesses of the front and the tail edges of the blades are different, and the thicknesses of the front and the tail edges are linearly changed along the height of the blades; as shown in fig. 6, the blade inlet and outlet geometrical angles are not consistent. The application scheme is a small-scale high-rotating-speed fan, and the inlet radius is about 50mm. The rotor hub ratio of the application scheme is 0.5.
It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.
The present invention is not intended to be limited to the particular embodiments shown and described, but is to be accorded the widest scope consistent with the principles and novel features herein disclosed. The foregoing is only a preferred embodiment of the present application, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present application, and these modifications and variations should also be considered as the protection scope of the present application.

Claims (9)

1. An axial flow fan, comprising an impeller; the impeller comprises a hub and blades; the blades are arranged on the hub; on the cross section of the impeller, the diameter of the hub is Dh; the circle where the blades are located is a wheel rim, the diameter of the wheel rim is Ds, and the hub ratio D = Dh/Ds; wherein the hub ratio D =0.4-0.6.
2. The axial flow fan according to claim 1, wherein the axial flow fan has a radial flow path in which the inner portion of the casing has a uniform cross-sectional structure from the gas inlet to the gas outlet.
3. The axial flow fan as claimed in claim 1, wherein the blade profile of the blade is an asymmetric air blade profile; and/or the number of the blades is 7-11.
4. The axial fan of claim 1, wherein the inlet geometry angle and the outlet angle of the blades are not equal.
5. The axial fan of claim 1, wherein a cross-sectional radius at an inlet of the axial fan is 50mm.
6. The axial fan of claim 1, wherein the hub mean camber line setting angle follows a linear function along a flow direction distribution law: y is 1 ＝0.11x 1 +50; wherein x is 1 The relative position of the camber line of the hub along the flow direction is shown, and y1 is the blade mounting angle of the camber line of the hub at the corresponding relative position of the flow direction; the blade installation angle is an included angle between the blade mean camber line and the rotating direction of the impeller; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
7. The axial fan of claim 1, wherein the camber line mount angle follows a quadratic function along the flow distribution law: y is 2 ＝-2.5e -4 x 2 2 +4.7e -2 x 2 +31; wherein x is 2 Is the relative position of the camber line in the direction of flow, y 2 Installing blades at the corresponding opposite positions of the flow direction of the camber line of the hubAn angle; the blade installation angle is an included angle between the blade mean camber line and the rotating direction of the impeller; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
8. The axial fan of claim 1, wherein the hub mean camber line setting angle follows a quartic function along the flow direction distribution law:
y 3 ＝-1.1e -7 x 3 4 +3e -5 x 3 3 -3.2e -3 x 3 2 +0.13x 3 +1.3; wherein x is 3 Is the relative position of the camber line in the direction of flow, y 3 The thickness of the blade corresponding to the relative position of the flow direction; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
9. The axial fan of claim 1, wherein the camber line setting angle follows a quartic function along the flow distribution law:
y 4 ＝-6.2e -8 x 4 4 +1.9e -5 x 4 3 -2.3e -3 x 4 2 +0.1x 4 +0.45; wherein x is 4 For the relative position of the camber line of the wheel rim in the direction of flow, y 4 The thickness of the blade corresponding to the relative position of the flow direction; the arc installation angle is an included angle between the tangential direction of the arc and the central axis direction of the axial flow fan.
CN202223385531.6U 2022-12-16 2022-12-16 Axial flow fan Active CN218844675U (en)

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