Split motor frame cooling system

Abstract

The application discloses a split motor base cooling system, which is characterized in that the side surface of a motor heat dissipation base shell is integrated with a plurality of heat dissipation fins extending along the axial direction, and the heat dissipation fins are arranged in pairs in the up-down direction, and the heat dissipation fins are connected to each other to form a heat dissipation air duct extending along the front-back direction; the tail end of the motor heat dissipation base shell is provided with a flow guide air baffle, and the flow guide air baffle is internally provided with a centrifugal fan wheel; the centrifugal fan wheel rotates along with the motor shaft; and a ring-shaped air outlet is formed between the inner ring of the front end of the flow guide air baffle and the outer ring of the tail end of the motor heat dissipation base shell, and the air outlet faces forward; and the unique structure of the scheme makes the upper surface of the heat dissipation fin efficiently evaporate and absorb heat, the inside of the heat dissipation fin is efficiently liquid-cooled, and the lower surface of the heat dissipation fin is low-temperature and high-speed air-cooled, so that the cooling process of the heat dissipation fin is accelerated in all directions.

Description

Technical Field

[0001] This invention belongs to the field of electric motors. Background Technology

[0002] Traditional split-type motor cylindrical housing base, such as Figure 1 and 2 As shown, the motor housing is designed with dense fins, and the motor cooling method is a centrifugal forced air cooling structure; Its core principle is to utilize the directional airflow generated by a centrifugal impeller to achieve forced convection cooling through the air ducts formed by the heat dissipation fins. The centrifugal impeller is coaxially mounted at the tail of the motor and rotates synchronously with the motor shaft. Air is drawn in axially through the air inlet mesh at the tail end of the air guide shroud, accelerated by centrifugal force, and thrown out radially, forming a high-pressure airflow. The airflow is ejected forward through the annular air outlet (the annular gap between the front end of the air guide shroud and the casing), forming a cooling jet. The side of the motor casing is equipped with axially extending heat dissipation fins, and parallel heat dissipation air ducts are formed between adjacent fins. The airflow ejected from the annular air outlet surges forward along the air ducts under the guidance of the fins, directly scouring the fin surface and carrying away heat through forced convection.

[0003] When the airflow ejected from the annular air outlet of this structure enters the parallel air duct, the temperature of the fluid near the fin area of ​​the air outlet is lower, while the temperature at the far end is higher due to heat absorption over the extension, resulting in uneven heat dissipation. At the same time, the cooling efficiency of simple air cooling is limited and it is difficult to meet the heat dissipation requirements under high power conditions. Summary of the Invention

[0004] Purpose of the invention: In order to overcome the shortcomings of the existing technology, the present invention provides a split motor base cooling system. The unique structure of this solution enables efficient evaporation and heat absorption on the upper surface of the heat dissipation fins, efficient liquid cooling inside, and low-temperature high-speed air cooling on the lower surface, thereby accelerating the cooling process of the heat dissipation fins in all aspects.

[0005] Technical solution: To achieve the above objectives, the present invention provides a split-type motor base cooling system, wherein the side of the motor heat dissipation base housing has a plurality of heat dissipation fins extending along the axial direction, and heat dissipation air ducts extending along the front-back direction are formed between any two adjacent heat dissipation fins; the rear end of the motor heat dissipation base housing has a guide fan, and a centrifugal impeller is inside the guide fan. The centrifugal impeller rotates with the motor shaft, and a forward-facing annular air outlet is formed between the inner ring of the front end of the guide fan and the outer ring of the rear end of the motor heat dissipation base housing; An evaporator outlet is provided above the uppermost of the several heat dissipation fins on the side of the motor heat dissipation base housing. An evaporator outlet is provided below the evaporator outlet. The liquid evaporator discharged from the evaporator outlet is sprinkled onto the upper surface of the uppermost of the several heat dissipation fins.

[0006] Furthermore, the evaporating agent is water.

[0007] Furthermore, each heat dissipation fin has several parallel-spaced evaporator guide strips integrally arranged on its upper end along the length direction, and wind-driven evaporation grooves are formed between two adjacent evaporator guide strips.

[0008] Furthermore, each heat dissipation fin has an integrally formed rearwardly extending air pressure guide plate on its upper front end; a rearwardly extending air pressure port is formed on the lower side of the air pressure guide plate; a forwardly extending vortex guide plate is integrally formed on the lower rear end of each heat dissipation fin, and a forwardly extending vortex port is formed on the upper side of the vortex guide plate; several evaporator backflow channels are provided along the length of each heat dissipation fin; several evaporator pressure inlets are provided deep inside the air pressure port; several evaporator suction outlets are provided deep inside the vortex port; the front end of the evaporator backflow channel is connected to the evaporator pressure inlet, and the rear end of the evaporator backflow channel is connected to the evaporator suction outlet; The lower side of each vortex guide fin and the rear end of the heat dissipation fin below form an air inlet that gradually narrows forward and downward; the upper side of each wind pressure guide fin and the heat dissipation fin above form a steam outlet.

[0009] Furthermore, the wind pressure guide plate forms a 30° angle with the connected heat dissipation fins.

[0010] Furthermore, the eddy current guide plate forms a 30° angle with the connected heat dissipation fins.

[0011] Furthermore, as the gas ejected from the annular outlet is blown into the cooling duct through the gradually narrowing inlet, when the airflow impacts the lower surface of the vortex guide plate, it flows obliquely downward along the lower surface of the inclined plate. The flow velocity increases as the inlet narrows. The vortex orifice on the upper side of the vortex guide plate forms a low-speed separation zone due to the obstruction of the vortex guide plate, thus forming an airflow shear layer at the connection between the vortex orifice and the cooling duct. The gas in the vortex orifice generates a rotational torque under the action of the velocity difference at the airflow shear layer, forming a vortex. At the same time, when the airflow accelerates through the lower end of the vortex guide plate, according to Bernoulli's equation, the increased flow velocity leads to a decrease in static pressure, thereby forming a negative pressure in the vortex orifice. Meanwhile, the low-pressure vortex wake region formed on the upper side of the vortex guide plate due to airflow separation further strengthens the negative pressure in the vortex orifice.

[0012] Furthermore, as the gas surging forward in the cooling duct is discharged backward from the steam outlet, the airflow continuously impacts the lower side of the pressure guide plate, causing the airflow velocity to decrease sharply due to obstruction. According to Bernoulli's law: total pressure = static pressure + dynamic pressure, since the dynamic pressure decreases as it is proportional to the square of the velocity, the static pressure increases, thus forming a positive pressure zone at the pressure port. When the lower surface of the pressure guide plate comes into contact with the airflow, a boundary layer is formed due to viscosity. The airflow velocity is highest at the leading edge of the pressure guide plate, and as it flows backward along the slope, the boundary layer thickens due to the adverse pressure gradient, further converting the kinetic energy of the airflow into pressure energy, thus exacerbating the positive pressure.

[0013] Furthermore, the liquid in the evaporator backflow channel flows backward under the combined effect of the negative pressure suction of the evaporator at the vortex orifice and the pushing pressure of the air pressure orifice.

[0014] Beneficial effects: The present invention enables the airflow on the upper side of each heat dissipation fin to continuously cause high-speed evaporation of the liquid evaporator in the evaporation tank, thereby efficiently absorbing the heat on the upper side of each heat dissipation fin through the heat absorption of the evaporation phase change. Meanwhile, the liquid evaporator flows backward along the evaporator backflow channel in each heat dissipation fin, efficiently absorbing the heat inside each heat dissipation fin. At the same time, the lower surface of each heat dissipation fin is subjected to high-speed flow of the low-temperature gas after evaporation and heat absorption, thereby achieving efficient air cooling of the lower surface of each heat dissipation fin. The unique structure of this solution enables efficient evaporation and heat absorption on the upper surface of the heat dissipation fin, efficient liquid cooling inside, and low-temperature high-speed air cooling on the lower surface, thereby accelerating the cooling process of the heat dissipation fin in all aspects. Attached Figure Description

[0015] Figure 1 A schematic diagram of a cylindrical motor heat dissipation base structure for a typical existing centrifugal forced air cooling system; Figure 2 A schematic diagram of the newly designed high-efficiency cooling cylindrical motor heat dissipation base structure for this solution; Figure 3 A side view of the newly designed high-efficiency cooling cylindrical motor heat sink for this solution; Figure 4 This is a schematic diagram of several heat dissipation fins extending along the axial direction on the side of the motor heat dissipation base housing of this solution, with the base itself hidden. Figure 5 This is a schematic diagram of a single heat dissipation fin structure; Figure 6 This is a cross-sectional view showing the combination of three heat dissipation fins. Detailed Implementation

[0016] The invention will now be further described with reference to the accompanying drawings.

[0017] As attached Figures 2 to 6The illustrated split-type motor base cooling system includes a motor heat dissipation base housing 3. Several heat dissipation fins 6 extending along the axial direction are integrally formed on the side of the motor heat dissipation base housing 3. A heat dissipation air duct 8 extending in the front-back direction is formed between any two adjacent heat dissipation fins 6. A guide fan shroud 4 is detachably and coaxially mounted at the rear end of the motor heat dissipation base housing 3. A centrifugal impeller is coaxially mounted inside the guide fan shroud 4. The centrifugal impeller is coaxially and synchronously mounted at the rear end of the motor shaft and rotates synchronously with the motor shaft. A central feature is located at the rear end of the guide fan shroud 4. With an air inlet mesh, the inner ring at the front end of the air guide shroud 4 and the outer ring at the rear end of the motor heat dissipation base housing 3 form a forward-facing annular air outlet 5. The cooling air jet ejected from the annular air outlet 5 surges forward along the extension direction of several heat dissipation air channels 8 under the guidance of each heat dissipation fin 6, thereby carrying away the heat on each heat dissipation fin 6. The airflow direction of the centrifugal fan is perpendicular to the motor axis (radial airflow). However, this solution uses the design of the annular air outlet 5 to convert the airflow into axial flow, so that the cooling air is concentrated to cover the heat dissipation fin 6 area, thereby improving the heat dissipation efficiency.

[0018] like Figure 2 An evaporator outlet 1 is provided above the uppermost of one of the heat dissipation fins 6 on the side of the motor heat dissipation base housing 3. An evaporator outlet 7 is provided below the evaporator outlet 1. An evaporator supply pipe 2 is also provided, which is connected to the evaporator outlet 7. The liquid evaporator discharged from the evaporator outlet 7 is sprayed onto the upper surface of the uppermost of the heat dissipation fins 6 under the action of gravity.

[0019] The evaporating agent in this scheme is water, but it is not limited to water; it can also be other non-flammable volatile liquids.

[0020] like Figure 5 As shown, each heat dissipation fin 6 has a number of parallel evaporator guide strips 12 integrally arranged on its upper end along the length direction, and a wind-driven evaporation groove 30 is formed between two adjacent evaporator guide strips 12.

[0021] Each heat dissipation fin 6 has an integrally formed rearwardly extending air pressure guide fin 9 on its upper front end; a rearwardly extending air pressure port 10 is formed on the lower side of the air pressure guide fin 9; a forwardly extending vortex guide fin 14 is integrally formed on the lower rear end of the heat dissipation fin 6, and a forwardly extending vortex port 13 is formed on the upper side of the vortex guide fin 14; several evaporator backflow channels 18 are provided along the length direction inside each heat dissipation fin 6; several evaporator pressure inlets 16 are provided deep inside the air pressure port 10; several evaporator suction outlets 17 are provided deep inside the vortex port 13; the front end of the evaporator backflow channel 18 is connected to the evaporator pressure inlet 16, and the rear end of the evaporator backflow channel 18 is connected to the evaporator suction outlet 17.

[0022] The lower side of each vortex guide 14 and the rear end of the lower heat dissipation fin 6 form an air inlet guide 15 that gradually narrows forward and downward; the upper side of each wind pressure guide 9 and the upper heat dissipation fin 6 form a steam outlet 11.

[0023] The wind pressure guide plate 9 forms a 30° angle with the connected heat dissipation fin 6; the vortex guide plate 14 forms a 30° angle with the connected heat dissipation fin 6.

[0024] As shown in 3, 4, and 6, as the gas ejected from the annular air outlet 5 is blown into the heat dissipation duct 8 through the gradually narrowing air inlet 15, when the airflow impacts the lower surface of the vortex guide plate 14, the airflow will flow obliquely downward along the lower surface of the inclined plate, and the flow velocity will increase due to the gradual narrowing of the air inlet 15. The vortex port 13 on the upper side of the vortex guide plate 14 forms a low-speed separation zone due to the obstruction of the vortex guide plate 14, thereby forming an airflow shear layer at the connection between the vortex port 13 and the heat dissipation duct 8. The gas in the vortex port 13 generates a rotational torque under the action of the velocity difference at the airflow shear layer, forming a vortex. At the same time, under the Bernoulli effect, the airflow accelerates at the lower end of the vortex guide plate 14. Due to the narrowing of the flow channel, according to Bernoulli's equation, the increased flow velocity leads to a decrease in static pressure, thereby forming a negative pressure in the vortex port 13. Meanwhile, a low-pressure vortex wake region is formed on the upper side of the vortex guide plate 14 due to airflow separation, further strengthening the negative pressure of the vortex port 13. Meanwhile, as the gas surging forward in the heat dissipation duct 8 is discharged backward from the steam outlet 11, the airflow surging forward in the heat dissipation duct 8 continuously impacts the lower side of the air pressure guide plate 9, and the airflow velocity decreases sharply due to obstruction. According to Bernoulli's law (total pressure = static pressure + dynamic pressure), the decrease in dynamic pressure (proportional to the square of velocity) will lead to an increase in static pressure, thus forming a positive pressure zone at the air pressure outlet 10. Moreover, when the lower surface of the air pressure guide plate 9 comes into contact with the airflow, a boundary layer is formed due to viscosity. The airflow velocity is highest at the leading edge of the air pressure guide plate 9. When it flows backward along the slope, the boundary layer thickens due to the reverse pressure gradient (pressure increases along the flow direction), and the kinetic energy of the airflow is further converted into pressure energy, which intensifies the positive pressure.

[0025] Conventional cooling process: The cooling air jets ejected forward from the annular air outlet 5 are guided by each heat dissipation fin 6 and blown into the heat dissipation air duct 8 from the air inlet guide 15. They surge forward along the extension direction of each heat dissipation air duct 8 and are finally discharged backward through the steam outlet 11, thereby carrying away the heat of each heat dissipation fin 6. When the sensor detects that the temperature of the motor heat sink housing exceeds the threshold, it controls the evaporator supply pipe 2, causing the liquid evaporator discharged from the evaporator outlet 7 to continuously fall onto the upper surface of the uppermost strip of several heat dissipation fins 6 in the wind-driven evaporation tank 30. Driven by the high-speed forward-flowing gas above the liquid evaporator in the wind-driven evaporation tank 30, the evaporator undergoes accelerated evaporation and heat absorption, and ultimately flows forward into the air pressure port 10. The liquid evaporator entering the air pressure port 10 is further forced into the evaporator backflow channel 18 from the evaporator pressure inlet 16 under the action of air pressure. The liquid evaporator forced into the evaporator backflow channel 18 continuously flows backward under the negative pressure suction of the vortex port 13, directly... The liquid evaporator is continuously discharged diagonally downward from the vortex port 13 into the wind-driven evaporation tank 30 on the upper side of the front end of the heat dissipation fin 6 below. Driven by the high-speed forward flow of gas in the heat dissipation channel 8 above the liquid evaporator in the wind-driven evaporation tank 30, the liquid evaporator is accelerated to evaporate and absorb heat. Driven by the wind, it finally flows forward into the air pressure port 10. The liquid evaporator entering the air pressure port 10 is further forced into the evaporator backflow channel 18 from the evaporator pressure inlet 16 under the action of wind pressure. The liquid evaporator forced into the evaporator backflow channel 18 is continuously reversed backward under the negative pressure suction of the vortex port 13 until it is continuously discharged diagonally downward from the vortex port 13 into the wind-driven evaporation tank 30 on the upper side of the front end of the heat dissipation fin 6 below. Following the above pattern, the airflow on the upper side of each heat dissipation fin 6 drives the high-speed evaporation of the liquid evaporator in the evaporation tank 30, thereby efficiently absorbing the heat on the upper side of each heat dissipation fin 6 by means of evaporation phase change heat absorption. Meanwhile, the liquid evaporator flows backward along the evaporator backflow channel 18 in each heat dissipation fin 6, efficiently absorbing the heat inside each heat dissipation fin 6. At the same time, the lower surface of each heat dissipation fin 6 is subjected to high-speed flow of the low-temperature gas after evaporation heat absorption, thereby achieving efficient air cooling of the lower surface of each heat dissipation fin 6. In summary, the unique structure of this solution enables efficient evaporation and heat absorption on the upper surface of the heat dissipation fins 6, efficient liquid cooling inside, and low-temperature, high-speed air cooling on the lower surface, thereby accelerating the cooling process of the heat dissipation fins 6 in all aspects.

[0026] The above are merely preferred embodiments of the present invention. It should be noted that those skilled in the art can make various improvements and modifications without departing from the principle of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A split-type motor frame cooling system, characterized in that: The side of the motor heat dissipation base housing (3) has several heat dissipation fins (6) extending along the axial direction. A heat dissipation air duct (8) extending along the front-back direction is formed between any two adjacent heat dissipation fins (6). The rear end of the motor heat dissipation base housing (3) has a guide fan shroud (4). The guide fan shroud (4) contains a centrifugal impeller. The centrifugal impeller rotates with the motor shaft. The front inner ring of the guide fan shroud (4) and the rear outer ring of the motor heat dissipation base housing (3) form a forward-facing annular air outlet (5). An evaporator outlet (1) is provided above the uppermost strip of several heat dissipation fins (6) on the side of the motor heat dissipation base housing (3). An evaporator outlet (7) is provided on the lower side of the evaporator outlet (1). The liquid evaporator discharged from the evaporator outlet (7) is sprinkled onto the upper surface of the uppermost strip of several heat dissipation fins (6). Each heat dissipation fin (6) has a number of parallel evaporator guide strips (12) integrally arranged on the upper end along the length direction, and a wind-driven evaporation groove (30) is formed between two adjacent evaporator guide strips (12). Each heat dissipation fin (6) has an integrally arranged rearward-extending wind pressure guide plate (9) on the upper front side; a rearward-extending wind pressure port (10) is formed on the lower side of the wind pressure guide plate (9); a forward-extending vortex guide plate (14) is integrally arranged on the lower rear side of the heat dissipation fin (6), and a forward-extending vortex port (13) is formed on the upper side of the vortex guide plate (14); a number of evaporator backflow channels (18) are arranged along the length direction inside each heat dissipation fin (6); a number of evaporator pressure inlets (16) are arranged deep inside the wind pressure port (10); a number of evaporator suction outlets (17) are arranged deep inside the vortex port (13); the front end of the evaporator backflow channel (18) is connected to the evaporator pressure inlet (16), and the rear end of the evaporator backflow channel (18) is connected to the evaporator suction outlet (17). The lower side of each vortex guide fin (14) and the rear end of the heat dissipation fin (6) below form an air inlet guide (15) that gradually narrows forward and downward; the upper side of each wind pressure guide fin (9) and the upper heat dissipation fin (6) above form a steam outlet (11).

2. The split-type motor frame cooling system according to claim 1, characterized in that: The evaporating agent is water.

3. The split-type motor frame cooling system according to claim 2, characterized in that: The wind pressure guide plate (9) forms a 30° angle with the connected heat dissipation fins (6).

4. The split-type motor frame cooling system according to claim 3, characterized in that: The vortex guide plate (14) forms a 30° angle with the connected heat dissipation fins (6).

5. A split-type motor base cooling system according to claim 4, characterized in that: As the gas is ejected forward from the annular air outlet (5) and blown into the heat dissipation duct (8) through the gradually narrowing air inlet (15), when the airflow hits the lower surface of the vortex guide plate (14), the airflow will flow obliquely downward along the lower surface of the inclined plate, and the flow velocity will increase due to the gradual narrowing of the air inlet (15). The vortex port (13) on the upper side of the vortex guide plate (14) forms a low-speed separation zone due to the obstruction of the vortex guide plate (14), thereby causing the vortex port (13) to separate from the heat dissipation duct. (8) forms an airflow shear layer at the connection point. The gas in the vortex port (13) generates a rotational torque under the action of the velocity difference at the airflow shear layer, forming a vortex. At the same time, when the airflow accelerates through the lower end of the vortex guide plate (14), according to Bernoulli's equation, the increase in flow velocity leads to a decrease in static pressure, thereby forming a negative pressure in the vortex port (13). Meanwhile, a low-pressure vortex wake region is formed on the upper side of the vortex guide plate (14) due to airflow separation, further strengthening the negative pressure of the vortex port (13).

6. A split-type motor frame cooling system according to claim 5, characterized in that: As the gas surging forward in the heat dissipation duct (8) is discharged backward from the steam outlet (11), the airflow surging forward in the heat dissipation duct (8) continuously impacts the lower side of the wind pressure guide plate (9), and the airflow speed decreases sharply due to obstruction. According to Bernoulli's law: total pressure = static pressure + dynamic pressure, since the dynamic pressure decreases as it is proportional to the square of the velocity, the static pressure increases, thus forming a positive pressure zone at the wind pressure port (10). When the lower surface of the wind pressure guide plate (9) comes into contact with the airflow, a boundary layer is formed due to viscosity. The airflow has the highest speed at the leading edge of the wind pressure guide plate (9), and when it flows backward along the slope, the boundary layer thickens due to the reverse pressure gradient, and the airflow kinetic energy is further converted into pressure energy, which intensifies the positive pressure.

7. A split-type motor base cooling system according to claim 6, characterized in that: The liquid in the evaporator backflow channel (18) flows backward under the combined action of the negative pressure suction of the evaporator at the vortex port (13) and the pushing pressure at the air pressure port (10).

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