Fluid compression device and electronic equipment

Abstract

The invention provides a fluid compression device and electronic equipment. The electronic equipment comprises a shell, a heat dissipation system and a heat conduction assembly, wherein the heat dissipation system and the heat conduction assembly are contained in the shell. The shell is provided with an air inlet and an air outlet, and the air inlet and the air outlet are distributed in the side face of the shell. The heat conduction assembly comprises a uniform temperature plate and heat dissipation fins. The heat dissipation system comprises a fluid amplifier and a gas compression structure which are adjacently arranged in the thickness direction perpendicular to the electronic equipment. The fluid amplifier comprises a main channel and at least one slit channel, and the extending directions of the main channel and each slit channel are perpendicular to the thickness direction of the electronic equipment; the main channel is used for guiding air of the air inlet to the cooling fins. An inlet of each slit channel is communicated with a gas outlet of the gas compression structure, and an outlet of each slit channel is communicated with the side wall of the main channel. The heat dissipation system in the electronic equipment has a relatively thin thickness, so that the miniaturization development of the electronic equipment is facilitated while the heat dissipation performance is ensured.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of terminal, in particular to a fluid compression device and electronic equipment. BACKGROUND

[0002] In recent years, with the upgrading of electronic product hardware and chip specifications and the increasing demand of users for performance improvement of electronic products, how to fully release the performance of electronic equipment has become a key point in product iteration and upgrading. At the same time, in order to improve the use experience, electronic equipment tends to be thin and light, and the heat dissipation space is also continuously compressed.

[0003] The heat dissipation mode of the traditional technology cannot meet the heat dissipation demand of the existing electronic equipment, and the current heat dissipation structure will also restrict the further thinning of the whole machine system due to the large size. SUMMARY

[0004] The present application provides a fluid compression device and electronic equipment, and the heat dissipation system in the electronic equipment has a relatively thin thickness, which is beneficial to the miniaturization development of the electronic equipment while ensuring the heat dissipation performance.

[0005] In a first aspect, the present application provides an electronic equipment, which comprises a shell, and a heat dissipation system and a heat conduction assembly accommodated in the shell; the shell has an air inlet and an air outlet, the air inlet and the air outlet respectively penetrate the outer surface and the inner surface of the shell along the thickness direction perpendicular to the electronic equipment, and the arrangement of the air inlet and the air outlet is located on the side surface of the shell; the heat conduction assembly comprises a uniform plate and a heat dissipation fin, the uniform plate is used for absorbing the heat emitted by the heat source of the electronic equipment and guiding to the heat dissipation fin, and the heat dissipation fin is arranged at the air outlet of the shell; along the thickness direction perpendicular to the electronic equipment, the heat dissipation system comprises a fluid amplifier and a gas compression structure arranged adjacent to each other; the fluid amplifier comprises a main channel and at least one slit channel, and the extension directions of the main channel and each slit channel are perpendicular to the thickness direction of the electronic equipment; the main channel is used for guiding the air of the air inlet to the heat dissipation fin; the inlet of each slit channel is in communication with the gas outlet of the gas compression structure, and the outlet of the slit channel is in communication with the side wall of the main channel. When the heat dissipation system of the electronic equipment works, the gas compression structure can suck in the air from the air inlet, compress the air and provide a small amount of compressed gas to the fluid amplifier, the compressed gas enters the main channel through the slit channel and flows along the inner wall of the main channel, a negative pressure area can be formed in the main channel, so that the main channel of the fluid amplifier can suck a large amount of air from the air inlet and form a high-speed airflow to the heat dissipation fin, accelerate the heat exchange between the heat dissipation fin and the air, and realize the heat dissipation of the electronic equipment.

[0006] The heat dissipation system of the electronic device uses the gas compression structure to provide a small amount of compressed air to the fluid amplifier as a power source to drive the ambient air to flow, forming a high-pressure and high-flow air flow blowing to the heat dissipation fins, so that a good heat dissipation effect can be achieved. The entire heat dissipation system is relatively sealed, and the air volume of the air source can be fully utilized to improve the heat dissipation effect. The air inlet and the air outlet of the electronic device are located on the side surface of the shell, and no air inlet gap needs to be reserved in the thickness direction of the electronic device, and the structure in the thickness direction of the shell is not damaged, which does not affect the strength and appearance of the shell, and is beneficial to the light and thin development of electronic products. The heat dissipation system uses the fluid amplifier and the gas compression structure to replace the traditional centrifugal fan, which can avoid the noise and pressing abnormal sound caused by the centrifugal fan, and bring better user experience to consumers.

[0007] In some possible implementations, the at least one slit channel includes at least one first channel, and the inlet of the first channel and the inlet of the main channel are located on the same side surface of the fluid amplifier and arranged in a direction perpendicular to the thickness direction of the electronic device; the gas compression structure and the fluid amplifier are connected through an air inlet space connected to the air inlet, and the gas outlet of the gas compression structure is connected to the inlet of each first channel through a conduit. In the heat dissipation system, the gas compression structure is arranged on the air inlet side of the main channel of the fluid amplifier, the air inlet space can ensure that the air of the air inlet can enter the main channel, and the conduit can transport the high-pressure gas output by the gas compression structure to the slit channel.

[0008] In the case where the extension direction of the slit channel is a straight line, the extension direction of the main channel is arranged at an angle between the inner walls of each first channel.

[0009] In some possible implementations, along the arrangement direction of the inlet of the main channel and the inlet of any first channel, at least one first channel is arranged on each side of the main channel. The slit channels on both sides of the main channel can guide the high-pressure gas to the two sides of the main channel, so as to form a negative pressure area on the two sides of the inner wall of the main channel.

[0010] In some possible implementations, the at least one slit channel includes at least one second channel, and the inlet of each second channel and the inlet of the main channel are located on different side surfaces of the fluid amplifier, and the gas compression structure avoids the communication between the air inlet and the inlet of the main channel. In the heat dissipation system, the compression structure is arranged on the air inlet side of the main channel of the fluid amplifier, and the gas outlet of the gas compression structure can be directly connected to each second channel.

[0011] In some possible implementation manners, the electronic device can include other devices such as an audio device, and the heat dissipation system can be provided with a gap between the heat dissipation fins and the heat dissipation system. Specifically, the gap is between the fluid amplifier and the heat dissipation fins. In this case, the heat dissipation system includes a flow guide member with a flow guide channel, one end of the flow guide channel is in communication with the outlet of the main channel, and the other end of the flow guide channel is directed towards the heat dissipation fins. The flow guide channel of the flow guide member can deliver the airflow formed by the heat dissipation system to the heat dissipation fins, and increase the utilization rate of the airflow.

[0012] In some possible implementation manners, the cross-sectional area of the slit channel inlet is greater than the cross-sectional area of the slit channel outlet along the extension direction of the slit channel, and the compressed gas is further compressed.

[0013] In some possible implementation manners, the cross-sectional area of the main channel is greater than the cross-sectional area of any one of the slit channels, so that a small amount of high-pressure gas can drive several times or tens of times of ambient gas to form a large airflow as a power source. The cross-sectional dimension of the main channel along the thickness direction of the electronic device is less than the cross-sectional dimension along the direction perpendicular to the thickness direction of the electronic device, and the main channel is a flat cavity, which can reduce the thickness of the fluid amplifier.

[0014] In some possible implementation manners, the number of heat dissipation systems is two, and the two heat dissipation systems are arranged on the two sides of the vapor chamber along the direction perpendicular to the thickness direction of the electronic device, so that the electronic device can be more uniformly cooled.

[0015] In some possible implementation manners, the gas compression structure can be a micro air pump or a piezoelectric fan. Both the micro air pump and the piezoelectric fan can compress the air entering the shell to output high-pressure gas to the slit channel of the fluid amplifier. Both the micro air pump and the piezoelectric fan can have a small thickness, and can be suitable for small electronic devices.

[0016] When the gas compression structure selects a micro air pump, the micro air pump can select a structure similar to a Roots rotary pump. Specifically, the gas compression structure includes a housing, two rotors, at least one driving assembly, and a control assembly; the housing has an inner cavity, an air inlet, and an air outlet, and the air inlet and the air outlet are respectively connected to the inner cavity and the outer surface of the housing and are arranged in parallel along the thickness direction of the electronic device; each rotor includes an impeller surface, and the convex surface of the impeller surface is used to contact the circumferential inner wall; the two rotors are arranged in parallel along the thickness direction of the electronic device, and the impeller surfaces of the two rotors are conjugate meshing; along the thickness direction of the electronic device, the side of the rotor facing the housing has an axial groove; at least one of the rotors is driven by a driving assembly, and each driving assembly includes an annular driving magnet and a plurality of driving coils; between the rotor and the driving assembly for driving the rotor, the driving magnet is coaxially fixed to the rotor, the plurality of driving coils are fixed to the housing and are accommodated in the axial groove of the rotor, and the plurality of driving coils are arranged in parallel around the rotation axis of the rotor to form a magnetic field for driving the driving magnet; along the thickness direction of the electronic device, any one of the driving coils is arranged in parallel with the driving magnet; the control assembly is electrically connected to the plurality of driving coils of the at least one driving assembly to supply power to the driving coils. The arrangement direction of the air inlet and the air outlet is perpendicular to the arrangement direction of the two rotors, and the air inlet and the air outlet are respectively located between the two rotors; the circumferential inner wall on one side of the air inlet and the impeller surfaces of the two rotors form a chamber, and the circumferential inner wall on one side of the air outlet and the impeller surfaces of the two rotors form a chamber; during the meshing rotation of the two rotors, the impeller surfaces of the two rotors can transfer the gas entering the air inlet to the side of the air outlet, and the volume change of the chamber connected to the air inlet and the chamber connected to the air outlet can realize the compression of the gas. The gas compression structure realizes the suction and discharge of the gas through the meshing of the impeller surfaces of the two rotors, and the dynamic balance of the movement process has advantages and less vibration. The arrangement of the driving magnet and the driving coil of the driving assembly is perpendicular to the thickness direction of the electronic device, and there is no overlap in the thickness direction between the two, which can be applied to small electronic devices.

[0017] In some possible implementations, the two rotors can be driven to rotate around their respective rotation axes by two driving assemblies respectively. In order to keep the two rotors in synchronous motion, the control assembly comprises an angle detection device for detecting the rotation angles of the two rotors, and the control assembly can adjust the currents supplied to the driving assemblies corresponding to the two rotors according to the detection data of the angle detection device. The two rotors can be kept in synchronous motion through the cooperation of the angle detection device and the control assembly, so that the two rotors can be prevented from being stuck. In this case, the angle detection device comprises at least one or a combination of multiple of a Hall sensor, an eddy current encoder, a magnetic encoder, and a photoelectric sensor. Alternatively, one of the two rotors is provided with a plurality of first magnets distributed along the circumferential direction of the rotor, and the other rotor is provided with a plurality of second magnets distributed along the circumferential direction of the rotor, the first magnets and the second magnets repel each other, and the synchronous motion of the two rotors is realized through the repulsion of the first magnets and the second magnets. Alternatively, one of the two rotors is provided with a plurality of permanent magnets distributed along the circumferential direction of the rotor, and the other rotor is provided with a plurality of magnetic coils distributed along the circumferential direction of the rotor, the plurality of magnetic coils are used to charge to form a magnetic field, and the synchronous motion of the two rotors is dynamically fine-tuned through the magnetic field formed by the magnetic coils.

[0018] In a second aspect, the embodiments of the present application provide a fluid compression device, which comprises a housing, a rotor assembly, at least one driving assembly, and a control assembly. The housing has an inner cavity, an air inlet, and an air outlet, and the air inlet and the air outlet are arranged in parallel and spaced apart along the thickness direction of the fluid compression device. The rotor assembly is accommodated in the inner cavity, and at least two chambers are formed between the outer surface of the rotor assembly and the inner cavity of the housing. The rotor assembly comprises at least one rotor, and the rotation axis of each rotor is parallel to the thickness direction of the fluid compression device. The volume of the at least two chambers changes during the rotation of the at least one rotor. Each driving assembly is used to drive one rotor to rotate around its own rotation axis. Each driving assembly comprises an annular driving magnet and a plurality of driving coils. The driving magnet is coaxially fixed to the rotor, and the plurality of driving coils are fixed to the housing in a spaced-apart manner around the rotation axis of the rotor to form a magnetic field for driving the driving magnet. Any one of the driving coils is arranged adjacent to the driving magnet along a direction perpendicular to the thickness direction of the fluid compression device. The control assembly is electrically connected to the driving coils of the at least one driving assembly to supply power to the driving coils.

[0019] The fluid compression device can realize gas intake and discharge for each chamber during rotation of the rotor around its rotation axis. During rotation of the rotor, the rotor can transport the gas entering the gas inlet to the gas outlet, the volume of different chambers changes from large to small due to cooperation of the outer surface of the rotor and the shell, thereby compressing the gas and finally discharging high-pressure gas. The driving units of the fluid compression device can be integrated on the shell and the rotor, so that the fluid compression device has a small thickness size. The arrangement of the driving magnets and the driving coils is perpendicular to the thickness direction of the fluid compression device, and there is no thickness direction overlap between the two, which can reduce the thickness of the device. The fluid compression device can be used in the heat dissipation system of the electronic device provided in the first aspect to replace the gas compression structure of the heat dissipation system, and the fluid compression device can also be used to compress liquid. When the fluid compression device is applied to compress liquid, the gas inlet can be used to introduce liquid, and the gas outlet can be used to discharge liquid. The gas inlet can be referred to as a liquid inlet, and the gas outlet can be referred to as a liquid outlet.

[0020] In some possible implementations, along the direction perpendicular to the thickness direction of the fluid compression device, the inner cavity of the shell includes a circumferential inner wall, the rotor assembly includes two adjacent rotors, each rotor includes an impeller surface, and the convex surface of the impeller surface is used to contact the circumferential inner wall. The impeller surfaces of the two rotors are conjugate meshing. The arrangement direction of the gas inlet and the gas outlet is perpendicular to the arrangement direction of the two impellers, and the gas inlet and the gas outlet are located between the two rotors, respectively. At least one of the rotors is driven by a driving assembly. Along the thickness direction of the fluid compression device, the side of the rotor facing the shell has an axial groove, and a plurality of driving coils are fixed to the shell and accommodated in the axial groove. The fluid compression device realizes gas intake and discharge through the meshing of the impeller surfaces of the two rotors, and the dynamic balance of the movement process has an advantage of smaller vibration.

[0021] In some possible implementations, the two rotors are respectively driven by a driving assembly, the control assembly includes an angle detection device for detecting the rotation angle of the two rotors, and the control assembly is used to adjust the current supplied to the corresponding driving assembly of the two rotors according to the detection data of the angle detection device. The two rotors realize synchronous movement through cooperation of the angle detection device and the control assembly, which can prevent the two rotors from being stuck.

[0022] The angle detection device includes at least one or a combination of multiple of a Hall sensor, an eddy current encoder, a magnetic encoder, and a photoelectric sensor.

[0023] In some possible implementations, one of the rotors is provided with a plurality of first magnets distributed along the circumference of the rotor, and the other rotor is provided with a plurality of second magnets distributed along the circumference of the rotor. The first magnets repel the second magnets, and synchronous movement of the two rotors is realized through repulsion of the first magnets and the second magnets.

[0024] In some possible implementations, one of the rotors is provided with a plurality of permanent magnets distributed along the circumference of the rotor, and the other rotor is provided with a plurality of magnetic coils distributed along the circumference of the rotor, the plurality of magnetic coils are used to charge to form a magnetic field, and the magnetic field formed by the magnetic coils dynamically fine-tunes the synchronous movement of the two rotors.

[0025] In some possible implementations, along a thickness direction perpendicular to the fluid compression device, the inner cavity of the shell includes a circumferential inner wall, the rotor assembly includes one rotor, the rotor includes a cam surface surrounding the rotation axis of the rotor, and the farthest end of the radius of the rotor is in contact with the circumferential inner wall; a movable slider is arranged between the shell and the rotor, the shell includes a sliding groove with an opening located on the circumferential inner wall, along a direction perpendicular to the rotation axis of the rotor, one end of the movable slider extends into the sliding groove and is in sliding cooperation with the sliding groove, and the other end of the movable slider protrudes from the circumferential inner wall and is in contact with the cam surface of the rotor; along the circumference of the circumferential inner wall, the gas inlet and the gas outlet are arranged on two sides of the sliding groove, respectively. On both sides of the movable slider, the cam surface of the rotor and the circumferential inner wall of the shell form two chambers, respectively. Along the thickness direction of the fluid compression device, the side of the rotor facing the shell has an axial groove, and a plurality of drive coils are fixed to the shell and accommodated in the axial groove. When the rotor rotates around its rotation axis, the radially farthest end of the movable slider cam surface slides along the circumferential inner wall of the shell, which can change the volume of the above two chambers, realize the inhalation and exhalation of the gas, and realize the compression of the gas by controlling the exhaust.

[0026] In some possible implementations, the rotor has a counterweight hollowed out so that the center of gravity of the rotor coincides with the rotation axis of the rotor, and the counterweight hollowed out is located between the rotation axis of the rotor and the radially farthest end of the cam surface, so as to maintain the vibration balance during the operation of the fluid compression device.

[0027] In some possible implementations, the fluid compression device further includes a pressure valve arranged at the gas outlet, and the timing of the exhaust is adjusted through the pressure valve to realize the compression of the gas.

[0028] In some possible implementations, each drive assembly includes a fixed shaft, a bearing and a coil holder; the fixed shaft is fixed to the shell, and the fixed shaft is coaxial with the rotation axis of the rotor; the coil holder includes a central sleeve and a plurality of supports, the plurality of supports are fixed to the outer circumferential surface of the central sleeve at intervals around the rotation axis of the rotor, and each support is used to wind one drive coil; the inner ring of the bearing is fixed to the fixed shaft, and the outer ring of the bearing is fixed to the central sleeve coaxially. The fixed shaft, the bearing and the coil holder cooperate with the drive magnet and the drive coil to form a motor that drives the rotor to rotate. The drive assembly is equivalent to being integrated on the rotor and the shell, which can save the thickness space of the fluid compression device.

[0029] In some possible implementation manners, the inner cavity of the shell comprises a circumferential inner wall in a direction perpendicular to the thickness direction of the fluid compression device; the rotor assembly comprises a rotor, and an outer circumferential surface of the rotor comprises three circumferential side walls, each of the circumferential side walls forms a vertex angle with any two adjacent circumferential side walls, each of the vertex angles is in contact with the circumferential inner wall, and each of the circumferential side walls can form a chamber with the circumferential inner wall; the rotor has a central gear ring coaxial with the rotation axis of the rotor; a driving magnet is fixed to the rotor around the central gear ring, and a plurality of driving coils are fixed to the shell around the circumferential inner wall at intervals; the driving assembly further comprises a driving gear and a planet carrier, the driving gear is fixed to the shell, and the driving gear is engaged with the central gear ring, and the ratio of the number of teeth of the central gear ring to the number of teeth of the driving gear is 3:2; the planet carrier comprises a first rotation shaft and a second rotation shaft, the first rotation shaft and the second rotation shaft are coaxial with each other, the first rotation shaft is rotationally connected to the driving gear coaxially, and the second rotation shaft is rotationally connected to the rotor coaxially. The fluid compression device can enable the rotor to move relative to the shell in the manner of a planetary gear, and there is no large-stroke sliding movement part in the movement process of the rotor, and the structure is more reliable and stable.

[0030] In some possible implementation manners, the number of the gas inlets is two, and the number of the gas outlets is two; one gas outlet and one gas inlet are arranged adjacent to each other on one side of the shell in a direction perpendicular to the thickness direction of the fluid compression device, the other gas outlet and the other gas inlet are arranged adjacent to each other on the other side of the shell, and the one gas outlet is opposite to the one gas inlet, and the other gas outlet is opposite to the other gas inlet. In the process of one rotation of the rotor around the rotation axis thereof, each of the chambers can realize gas suction and discharge twice, and the efficiency is higher.

[0031] In a third aspect, the embodiments of the present application provide a fluid compression device, which comprises a housing, two rotors, at least one driving assembly and a control assembly; the housing has an inner cavity, an air inlet and an air outlet, and the air inlet and the air outlet are respectively connected to the inner cavity and the outer surface of the housing and are arranged in parallel along the thickness direction of the fluid compression device; each rotor comprises an impeller surface, and the convex surface of the impeller surface is used to contact the circumferential inner wall; the two rotors are arranged in parallel along the thickness direction of the fluid compression device, and the impeller surfaces of the two rotors are conjugate meshing; each driving assembly comprises a driving magnet and a plurality of driving coils, and the driving magnet is coaxially fixed to the rotor; along the thickness direction of the fluid compression device, the side of the rotor facing the housing has an axial groove, and the plurality of driving coils are fixed to the housing and accommodated in the axial groove, and the plurality of driving coils are arranged in parallel around the rotation axis of the rotor to form a magnetic field for driving the driving magnet; along the thickness direction of the fluid compression device, any one of the driving coils is arranged in parallel with the driving magnet; the control assembly is electrically connected to the plurality of driving coils to supply power to the driving coils. Each driving assembly can drive one rotor to rotate around its rotation axis. The arrangement direction of the air inlet and the air outlet is perpendicular to the arrangement direction of the two rotors, and the air inlet and the air outlet are respectively located between the two rotors; the circumferential inner wall on one side of the air inlet and the impeller surfaces of the two rotors form a chamber, and the circumferential inner wall on one side of the air outlet and the impeller surfaces of the two rotors form a chamber, and in the process of meshing rotation of the two rotors, the impeller surfaces of the two rotors can transfer the gas entering the air inlet to the side of the air outlet, and the volume change of the chamber connected to the air inlet and the chamber connected to the air outlet can realize the compression of the gas. The fluid compression device realizes the suction and discharge of the gas through the meshing of the impeller surfaces of the two rotors, and has the advantages of dynamic balance in the movement process and small vibration.

[0032] In the third aspect, each driving assembly comprises a fixed shaft, a bearing and a coil holder; the fixed shaft is fixed to the housing, and the fixed shaft is coaxial with the rotation axis of the rotor; the coil holder comprises a center sleeve and a plurality of supports, and the plurality of supports are fixed to the outer circumferential surface of the center sleeve around the rotation axis of the rotor, and each support is used to wind one driving coil; the inner ring of the bearing is fixed to the fixed shaft, and the outer ring of the bearing is coaxially fixed to the center sleeve. The fixed shaft, the bearing and the coil holder cooperate with the driving magnet and the driving coil to form a motor for driving the rotor to rotate. The driving assembly is integrated on the rotor and the housing, which can save the thickness space of the fluid compression device.

[0033] In some possible implementations, one of the rotors can be driven to rotate around its rotation axis by one driving assembly, and the other rotor can be driven to rotate around its rotation axis by the meshing of the two rotors, so as to realize the compression of the gas.

[0034] In some possible implementations, the two rotors can be driven to rotate around their respective rotation axes by two driving assemblies respectively. In order to keep the synchronous movement of the two rotors, the control assembly includes an angle detection device for detecting the rotation angles of the two rotors, and the control assembly can adjust the currents supplied to the corresponding driving assemblies of the two rotors according to the detection data of the angle detection device. The synchronous movement of the two rotors is achieved by the cooperation of the angle detection device and the control assembly, and the two rotors can be prevented from being stuck. The angle detection device includes at least one or a combination of multiple kinds of sensors, such as a Hall sensor, an eddy current encoder, a magnetic encoder, and a photoelectric sensor.

[0035] Alternatively, one of the rotors is provided with a plurality of first magnets distributed along the circumferential direction of the rotor, and the other rotor is provided with a plurality of second magnets distributed along the circumferential direction of the rotor. The first magnets and the second magnets repel each other, and the synchronous movement of the two rotors is achieved by the repulsion between the first magnets and the second magnets. Alternatively, one of the rotors is provided with a plurality of permanent magnets distributed along the circumferential direction of the rotor, and the other rotor is provided with a plurality of magnetic coils distributed along the circumferential direction of the rotor. The plurality of magnetic coils are used to charge to form a magnetic field, and the synchronous movement of the two rotors is dynamically fine-tuned by the magnetic field formed by the magnetic coils.

[0036] In a fourth aspect, the embodiments of the present application provide a fluid compression device, which includes a housing, a rotor, a driving assembly, and a control assembly. The housing has an inner cavity, an air inlet, and an air outlet. The air inlet and the air outlet are respectively connected to the inner cavity and the outer surface of the housing and are arranged in parallel along the thickness direction of the fluid compression device. The rotor is accommodated in the inner cavity, and the rotation axis of the rotor is parallel to the thickness direction of the fluid compression device. The housing includes a circumferential inner wall around the rotation axis of the rotor. The rotor includes a cam surface around the rotation axis of the rotor. The radially farthest end of the cam surface is in contact with the circumferential inner wall. The driving assembly includes a driving magnet in the shape of a ring and a plurality of driving coils. The driving magnet is coaxially fixed to the rotor. Along the thickness direction of the fluid compression device, the side of the rotor facing the housing has an axial groove. The plurality of driving coils are fixed to the housing and accommodated in the axial groove. The plurality of driving coils are arranged in parallel around the rotation axis of the rotor to form a magnetic field for driving the driving magnet. Along the thickness direction of the fluid compression device, any one of the driving coils is arranged adjacent to the driving magnet. The control assembly is electrically connected to the plurality of driving coils to supply power to the driving coils. The housing and the rotor are provided with a movable slider. The housing includes a sliding groove with an opening on the circumferential inner wall. Along the direction perpendicular to the rotation axis of the rotor, one end of the movable slider extends into the sliding groove and is in sliding cooperation with the sliding groove. The other end of the movable slider protrudes from the circumferential inner wall and is in contact with the cam surface of the rotor. Along the circumferential direction of the circumferential inner wall, the air inlet and the air outlet are arranged on the two sides of the sliding groove, respectively. The cam surfaces of the rotors on the two sides of the movable slider and the circumferential inner wall form two chambers. During the rotation of the rotor around the rotation axis, the volumes of the two chambers change.

[0037] In some possible implementations, the fluid compression device further comprises a pressure valve arranged at the gas outlet, and the pressure of the gas in the chamber connected to the gas outlet can be adjusted through the pressure valve.

[0038] In some possible implementations, the radial dimension of the gas outlet is smaller than the radial dimension of the gas inlet, and the design of large gas inlet and small gas outlet can optimize the gas compression effect.

[0039] In some possible implementations, in order to make the center of gravity of the rotor coincide with the rotation axis of the rotor, the rotor is provided with a counterweight hollow, which is specifically located between the rotation axis of the rotor and the radially farthest end of the cam surface.

[0040] In the fifth aspect, an embodiment of the present application provides a fluid compression device, which comprises a housing, a rotor, a driving assembly and a control assembly; the housing has an inner cavity, a gas inlet and a gas outlet, and the gas inlet and the gas outlet are respectively connected to the inner cavity and the outer surface of the housing and are arranged in parallel along the thickness direction of the fluid compression device; the outer circumferential surface of the rotor comprises three circumferential side walls, and each top angle is formed between any two adjacent circumferential side walls, each top angle is in contact with the circumferential inner wall, and a chamber can be formed between each circumferential side wall of the rotor and the circumferential inner wall; the rotor has a central gear ring coaxial with the rotation axis of the rotor; each driving assembly comprises an annular driving magnet and a plurality of driving coils, and the driving magnet is coaxially fixed to the rotor; the driving magnet is fixed to the rotor around the central gear ring, and the plurality of driving coils are fixed to the housing around the circumferential inner wall to form a magnetic field for driving the driving magnet; any one driving coil is arranged in parallel with the driving magnet along the thickness direction of the fluid compression device; and the control assembly is electrically connected to the plurality of driving coils to supply power to the driving coils. The driving assembly further comprises a driving gear and a planet carrier, the driving gear is fixed to the housing, and the driving gear is engaged with the central gear ring, and the ratio of the number of teeth of the central gear ring to the number of teeth of the driving gear is 3:2; the planet carrier comprises a first rotating shaft and a second rotating shaft, the first rotating shaft and the second rotating shaft are coaxially and rotatably connected to the driving gear and the rotor respectively; and the fluid compression device can make the rotor move relative to the housing in the manner of a planetary gear, and there is no large-stroke sliding movement part in the movement process of the rotor, and the structure is more reliable and stable.

[0041] In some possible implementations, the number of gas inlets is two, and the number of gas outlets is two; one gas outlet and one gas inlet are arranged in parallel on one side of the housing along the thickness direction of the fluid compression device, the other gas outlet and the other gas inlet are arranged in parallel on the other side of the housing, and one gas outlet is opposite to one gas inlet, and the other gas outlet is opposite to the other gas inlet. In the process of rotating one circle around the rotation axis of the rotor, each chamber can realize the suction and discharge of gas twice, and the efficiency is higher.

[0042] In some possible implementations, each vertex angle of the rotor is provided with a clamping gap, and a sealing strip is embedded in the clamping gap. The sealing strip can be provided with an elastic piece for sealing the gap between the vertex angle of the rotor and the circumferential inner wall. In order to ensure that the sealing strip keeps in contact with the circumferential inner wall, an elastic piece can be embedded between the sealing strip and the clamping gap, and the elastic piece can exert a certain pre-tightening force on the sealing strip so that the sealing strip can be pressed against the circumferential inner wall.

[0043] In a sixth aspect, the embodiments of the present application provide an electronic device, which comprises a shell, and a heat dissipation system and a heat conduction component accommodated in the shell; the shell has an air inlet and an air outlet, and the air inlet and the air outlet respectively penetrate the outer surface and the inner surface of the shell along the thickness direction perpendicular to the electronic device; the heat conduction component comprises a vapor chamber and a heat dissipation fin, the vapor chamber is used for absorbing heat emitted by a heat source of the electronic device and guiding the heat to the heat dissipation fin, and the heat dissipation fin is arranged at the air outlet of the shell; along the thickness direction perpendicular to the electronic device, the heat dissipation system comprises fluid amplifiers arranged in an adjacent manner and any one of the fluid compression devices provided in the second aspect; the fluid amplifiers comprise a main channel and at least one slit channel, and the extension directions of the main channel and each slit channel are perpendicular to the thickness direction of the electronic device; the main channel is used for guiding the air at the air inlet to the heat dissipation fin; the inlet of each slit channel is in communication with the air outlet of the fluid compression device, and the outlet of the slit channel is in communication with the side wall of the main channel. The fluid compression device is used for providing high-pressure gas for the fluid amplifiers, which is helpful for reducing the thickness of the electronic device and can adapt to the miniaturization development of the electronic device. BRIEF DESCRIPTION OF DRAWINGS

[0044] Figure 1a A structure of a centrifugal fan in the prior art;

[0045] Figure 1b A heat dissipation principle schematic diagram of an electronic device in the prior art;

[0046] Figure 1c A heat dissipation principle schematic diagram of an electronic device in the prior art;

[0047] Figure 1d A working principle schematic diagram of a piezoelectric diaphragm pump in the prior art;

[0048] Figure 1e A working principle schematic diagram of a piezoelectric diaphragm pump in the prior art;

[0049] Figure 2a A structure schematic diagram of an electronic device provided by the embodiments of the present application;

[0050] Figure 2b A structure schematic diagram of an electronic device provided by the embodiments of the present application;

[0051] Figure 3A partial structure schematic diagram of an electronic device provided by an embodiment of the present application;

[0052] Figure 4a A structure schematic diagram of a fluid amplifier of an electronic device provided by an embodiment of the present application;

[0053] Figure 4b A working principle schematic diagram of a fluid amplifier of an electronic device provided by an embodiment of the present application;

[0054] Figure 5a A structure schematic diagram of a heat dissipation system of an electronic device provided by an embodiment of the present application;

[0055] Figure 5b A working principle schematic diagram of a heat dissipation system of an electronic device provided by an embodiment of the present application;

[0056] Figure 6 A partial structure schematic diagram of an electronic device provided by an embodiment of the present application;

[0057] Figure 7a A structure schematic diagram of a fluid amplifier of an electronic device provided by an embodiment of the present application;

[0058] Figure 7b A working principle schematic diagram of a fluid amplifier of an electronic device provided by an embodiment of the present application;

[0059] Figure 8a A structure schematic diagram of a heat dissipation system of an electronic device provided by an embodiment of the present application;

[0060] Figure 8b A working principle schematic diagram of a heat dissipation system of an electronic device provided by an embodiment of the present application;

[0061] Figure 9 A structure schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0062] Figure 10a An exploded view of a fluid compression device provided by an embodiment of the present application;

[0063] Figure 10b An exploded view of a fluid compression device provided by an embodiment of the present application;

[0064] Figure 11a A partial structure schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0065] Figure 11b A partial structure schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0066] Figure 12aA working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0067] Figure 12b A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0068] Figure 12c A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0069] Figure 13 A structure schematic view of a fluid compression device provided by the embodiment of the present application;

[0070] Figure 14a An explosion view of a fluid compression device provided by the embodiment of the present application;

[0071] Figure 14b An explosion view of a fluid compression device provided by the embodiment of the present application;

[0072] Figure 15a A partial structure schematic view of a fluid compression device provided by the embodiment of the present application;

[0073] Figure 15b A partial structure schematic view of a fluid compression device provided by the embodiment of the present application;

[0074] Figure 16a A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0075] Figure 16b A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0076] Figure 16c A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0077] Figure 16d A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0078] Figure 16e A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0079] Figure 16f A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0080] Figure 16g A working principle schematic view of a fluid compression device provided by the embodiment of the present application;

[0081] Figure 17aA partial structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0082] Figure 17b A cross-sectional structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0083] Figure 17c A cross-sectional structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0084] Figure 17d A cross-sectional structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0085] Figure 18 A structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0086] Figure 19a An exploded view of a fluid compression device provided by an embodiment of the present application;

[0087] Figure 19b An exploded view of a fluid compression device provided by an embodiment of the present application;

[0088] Figure 19c An eccentric structural principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0089] Figure 20a A cross-sectional structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0090] Figure 20b A partial cross-sectional structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0091] Figure 21 A partial structural schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0092] Figure 22a A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0093] Figure 22b A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0094] Figure 22c A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0095] Figure 22d A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0096] Figure 22eA working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0097] Figure 22f A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0098] Figure 22g A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0099] Figure 22h A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0100] Figure 22i A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0101] Figure 22j A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0102] Figure 22k A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0103] Figure 22l A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0104] Figure 22m A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0105] Figure 23a A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0106] Figure 23b A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0107] Figure 23c A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0108] Figure 23d A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0109] Figure 23e A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0110] Figure 23f A working principle schematic diagram of a fluid compression device provided for an embodiment of the present application;

[0111] Figure 23gA working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0112] Figure 23h A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0113] Figure 23i A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0114] Figure 23j A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0115] Figure 23k A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0116] Figure 23l A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application;

[0117] Figure 23m A working principle schematic diagram of a fluid compression device provided by an embodiment of the present application.

[0118] Reference signs:

[0119] 00 - centrifugal fan; 001 - air inlet; 002 - air outlet; 01 - bottom shell; 02 - middle frame; 021 - side frame; 022 - support plate; 03 - display module; 041 - cover shell; 042 - piezoelectric film; 043 - air inlet valve; 044 - air outlet valve;

[0120] 10 - shell; 101 - side frame; 102 - bottom shell; 20 - display module; 30 - heat dissipation system; 301 - fluid amplifier; 302 - gas compression structure; 303 - conduit; 304 - flow guide; 401 - uniform temperature plate; 402 - heat dissipation fin; 50 - audio device;

[0121] 1 - fluid compression device; 11 - shell; 111 - base; 1111 - sliding groove; 112 - top cover; 12 - rotor assembly; 121 - rotor; 1211 - counterweight hollow; 1212 - axial groove; 13 - drive assembly; 131 - drive magnet; 132 - drive coil; 133 - fixed shaft; 134 - bearing; 135 - coil support; 1351 - center sleeve; 1352 - support; 14 - control assembly; 141 - circuit board; 15 - pressure valve; 161 - movable slider; 162 - spring;

[0122] 2-Fluid compression device; 21-Housing; 211-Base; 212-Top cover; 22-Rotor assembly; 221-Rotor; 2211-Axial groove; 23-Drive assembly; 231-Drive magnet; 232-Drive coil; 233-Fixed shaft; 234-Bearing; 235-Coil bracket; 24-Control assembly; 241-Circuit board; 25-Sealing ring; 261-First magnet; 262-Second magnet; 27-Magnetic coil; 28-Analog Hall sensor;

[0123] 3-Fluid compression device; 31-Housing shell; 311-Base; 312-Top cover; 32-Rotor assembly; 321-Rotor; 3211-Central gear ring; 3212-Annular groove; 3213-Sealing strip; 3214-Spring; 33-Drive assembly; 331-Drive magnet; 332, 332a, 332b-Drive coils; 333-Drive gear; 334-Bearing; 335-Planetary carrier; 3351-First shaft; 3352-Second shaft. Detailed Implementation

[0124] Consumer electronics are indispensable necessities in modern life. These devices need to consider portability and aesthetics, and in recent years, electronic devices have been trending towards thinner and lighter designs to meet consumer demands. With technological advancements, electronic devices have become more functionally integrated, leading to increased heat dissipation issues. Currently, the industry's main heat dissipation solutions for electronic devices include centrifugal fan cooling and piezoelectric diaphragm pump cooling. These solutions use centrifugal fans or piezoelectric diaphragm pumps to drive airflow and remove heat dissipated by the electronic devices. Centrifugal fan cooling, in particular, uses forced convection by rotating fan blades to drive airflow and achieve heat dissipation.

[0125] like Figure 1a The example centrifugal fan 00 has an axial air inlet 001 and a radial air outlet 002. The air inlet direction is parallel to the fan's axis. The fan uses centrifugal force to throw air out circumferentially and discharge it radially from the air outlet 002. This centrifugal fan 00 can be applied to electronic devices, such as... Figure 1bAs shown, the electronic device includes a bottom shell 01, a middle frame 02, and a display module 03. The middle frame 02 specifically includes a frame 021 and a support plate 022, the support plate 022 is opposite to the bottom shell 01 along the thickness direction of the electronic device, and the frame 021 is arranged between the bottom shell 01 and the support plate 022, thereby forming an accommodation space between the middle frame 02 and the bottom shell 01, and the display module 03 is arranged on the side of the support plate 022 away from the bottom shell 01, and the support plate 022 provides support for the display module. The centrifugal fan 00 is accommodated in the accommodation space, and the axial direction of the centrifugal fan is parallel to the thickness direction of the electronic device. When the air enters and exits from the side of the electronic device, the electronic device needs to be arranged with sufficient air inlet space for the centrifugal fan 00 to enter the air, and an air inlet gap G needs to be reserved between the centrifugal fan 00 and the bottom shell 01 along the thickness direction of the electronic device. The air inlet gap G is generally greater than or equal to 1.5 mm. The existence of the air inlet gap G increases the thickness of the electronic device and limits the thickness reduction of the electronic device. The thickness of the centrifugal fan 00 is generally between 3-5 mm, and the motor, blade, bearing and other structures of the centrifugal fan 00 have certain thickness requirements. A decrease in thickness will cause abnormal noise, increased noise, decreased bearing life, and decreased fan performance, thereby affecting the heat dissipation effect. Based on the size of the centrifugal fan 00, the distance between the air inlet position and the air outlet position of the electronic device is relatively close, and there may be a problem of hot air convergence, thereby affecting the heat dissipation efficiency. In order to avoid hot air convergence, the air inlet position is extended to the bottom shell 01, which will affect the integrity and strength of the outer shell of the electronic device. In addition, the air pressure of the centrifugal fan 00 is relatively low, and the air duct design of the electronic device heat dissipation system has high requirements and the structure is more complex. The heat dissipation system using the centrifugal fan 00 is an open air inlet and outlet system. Although the fan has a large air volume, the air outlet volume at the air outlet position of the electronic device is small and the utilization rate of the air source is low due to the influence of the air duct design and other factors. Alternatively, as shown in Figure 1c As shown, the electronic device includes a bottom shell 01, a middle frame 02, and a display module 03. The middle frame 02 specifically includes a frame 021 and a support plate 022, the support plate 022 is opposite to the bottom shell 01 along the thickness direction of the electronic device, and the frame 021 is arranged between the bottom shell 01 and the support plate 022, thereby forming an accommodation space between the middle frame 02 and the bottom shell 01, and the display module 03 is arranged on the side of the support plate 022 away from the bottom shell 01, and the support plate 022 provides support for the display module. The centrifugal fan 00 is accommodated in the accommodation space, and the axial direction of the centrifugal fan is parallel to the thickness direction of the electronic device. When the air enters and exits from the side of the electronic device, the electronic device needs to be arranged with sufficient air inlet space for the centrifugal fan 00 to enter the air, and an air inlet gap G needs to be reserved between the centrifugal fan 00 and the bottom shell 01 along the thickness direction of the electronic device. The air inlet gap G is generally greater than or equal to 1.5 mm. The existence of the air inlet gap G increases the thickness of the electronic device and limits the thickness reduction of the electronic device. The thickness of the centrifugal fan 00 is generally between 3-5 mm, and the motor, blade, bearing and other structures of the centrifugal fan 00 have certain thickness requirements. A decrease in thickness will cause abnormal noise, increased noise, decreased bearing life, and decreased fan performance, thereby affecting the heat dissipation effect. Based on the size of the centrifugal fan 00, the distance between the air inlet position and the air outlet position of the electronic device is relatively close, and there may be a problem of hot air convergence, thereby affecting the heat dissipation efficiency. In order to avoid hot air convergence, the air inlet position is extended to the bottom shell 01, which will affect the integrity and strength of the outer shell of the electronic device. In addition, the air pressure of the centrifugal fan 00 is relatively low, and the air duct design of the electronic device heat dissipation system has high requirements and the structure is more complex. The heat dissipation system using the centrifugal fan 00 is an open air inlet and outlet system. Although the fan has a large air volume, the air outlet volume at the air outlet position of the electronic device is small and the utilization rate of the air source is low due to the influence of the air duct design and other factors. Alternatively, as shown in

[0126] As shown in Figure 1d and Figure 1e A piezoelectric diaphragm pump, which comprises a cover shell 041, a piezoelectric film 042, an air inlet valve 043 and an air outlet valve 044. The piezoelectric diaphragm pump uses the vibration of the piezoelectric element to drive the piezoelectric film 042 to pump, and realizes the suction and discharge of gas through the volume change of the pump chamber Q. As shown in Figure 1dAs shown, the piezoelectric film 042 moves upward to increase the volume of the pump chamber Q, the pressure of the gas in the pump chamber Q is less than the ambient air pressure, the intake valve 043 is opened to realize air intake. As shown, Figure 1e As shown, the piezoelectric film 042 moves downward to compress the gas in the pump chamber Q, the exhaust valve 044 is opened to realize exhaust. In this scheme, the piezoelectric film 042 has high vibration frequency, small amplitude and low noise, but the amplitude of the piezoelectric element is microns, which is difficult to cause large changes in the piezoelectric film 042, the air pushing flow is not large, and it is difficult to meet the heat dissipation demand of electronic equipment.

[0127] Based on this, the embodiment of the present application provides a fluid compression device and an electronic equipment. The heat dissipation system of the electronic equipment has both heat dissipation performance and thin volume, can adapt to the light and thin development and high performance of electronic products, and brings better use experience for consumers.

[0128] In order to make the purpose, technical scheme and advantages of the present application clearer, the present application will be further described in detail below with reference to the drawings.

[0129] The electronic equipment provided by the embodiment of the present application includes but is not limited to consumer electronic products carried by consumers, such as mobile phones, tablet computers, notebook computers, wearable electronic devices, earphones, e-books and the like. These electronic equipment can bring more convenient and comfortable experience to consumers' life. Figure 2a And Figure 2b A structure of an electronic equipment is illustrated by taking a tablet computer as an example. For the convenience of understanding, X direction, Y direction and Z direction are set, the Z direction is the thickness direction of the electronic equipment, the X direction is the length direction of the electronic equipment, and the Y direction is the width direction of the electronic equipment. As shown, Figure 2a And Figure 2bAs shown, the electronic device includes a housing 10 and a display module 20, the display module 20 is assembled to the housing 10, and the display module 20 and the housing 10 have a space for accommodating circuit boards and other structural devices. The housing 10 includes a side frame 101 and a back shell 102, the side frame 101 surrounds the back shell 102, and the two can be an integral structure. The air inlet K1 and the air outlet K2 of the electronic device are arranged on the side frame 101, and the air in the external environment can enter the electronic device through the air inlet K1, and the gas in the electronic device can be discharged through the air outlet K2. Exemplarily, the air inlet K1 and the air outlet K2 are arranged on different sides of the electronic device, the air inlet K1 is arranged on the side of the width direction of the side frame 101, and the air outlet K2 is arranged on the side of the length direction of the side frame 101, and the air inlet K1 and the air outlet K2 are far away from each other, which can reduce the influence of heat backflow. The air outlet K2 here is an example of two and is distributed along the length direction of the side frame 101, and the path of the air flow entering from the air inlet K1 and the air outlet K2 can pass through more areas in the electronic device as much as possible, and more comprehensive and uniform heat dissipation can be achieved. The air inlet K1 and the air outlet K2 are located on the side frame 101, which can ensure the integrity and strength of the back shell 102.

[0130] Figure 3 As part of the structure of the electronic device, the electronic device further includes a heat conduction assembly 40 arranged in the housing 10, the heat conduction assembly 40 specifically includes a vapor chamber 401 and a heat dissipation fin 402, the vapor chamber 401 is used to absorb heat of heat sources such as circuit boards of the electronic device, and the heat dissipation fin 402 is arranged at the position of the air outlet K2. The electronic device includes a heat dissipation system 30 for providing air flow for the electronic device, the heat dissipation system 30 can guide the air at the air inlet K1 to the air outlet K2, so as to form an air flow in the electronic device, and the movement of the air flow can quickly transfer the heat on the vapor chamber 401 to the heat dissipation fin 402 and then be discharged through the air outlet K2, thereby achieving heat dissipation and cooling of the electronic device. In some embodiments, the electronic device further includes an audio device 50 and the like.

[0131] Please continue to refer to Figure 3As shown, the electronic device includes two sets of heat dissipation systems 30, which are symmetrically arranged on both sides of the heat spreader 401. Each heat dissipation system 30 corresponds to an air outlet K2, enabling more uniform heat dissipation for the electronic device. Of course, one or more sets of heat dissipation systems 30 can be provided depending on the structure of the electronic device; this application does not impose any limitations on this. The heat dissipation system 30 includes a fluid amplifier 301 and a gas compression structure 302. The gas compression structure 302 provides high-pressure air to the fluid amplifier 301. The negative pressure area formed within the fluid amplifier 301 by the high-pressure air draws in a large amount of ambient air from the air inlet K1 and guides it to the heat dissipation fins 402, accelerating heat exchange between the heat dissipation fins 402 and the environment, thus achieving heat dissipation for the electronic device. The fluid amplifier 301 and the gas compression structure 302 are distributed along the Y-direction of the electronic device, ensuring that the main structures of the fluid amplifier 301 and the gas compression structure 302 do not overlap along the thickness direction of the electronic device. There is no overlapping portion between them, and the thickness dimension of the electronic device is not increased.

[0132] like Figure 4a The diagram illustrates the structure of a fluid amplifier 301. This fluid amplifier 301 has a relatively thin profile, meaning it has a large length-to-thickness ratio or width-to-thickness ratio. The fluid amplifier 301 is a hollow structure, comprising a main channel T1 and at least one slit channel T2. Here, the slit channel T2 is exemplified by having its inlet located on the same side as the inlet of the main channel T1; this slit channel T2 can be referred to as the first channel. The slit channel T2 is connected to the sidewall of the main channel T1. Referring to the structure of an electronic device, the main channel T1 extends through the fluid amplifier 301 along the Y-direction, with its inlet and outlet facing each other along the Y-direction. The inlet t11 ​​of the main channel T1 is used for gas entry, and the outlet t12 of the main channel T1 is used for gas exit. The airflow within the main channel T1 is perpendicular to the Z-direction. The inlet t21 of the slit channel T1 and the inlet t11 ​​of the main channel T1 are located on the same side of the fluid amplifier 301. The outlet t22 of the slit channel T2 is connected to the inner wall of the main channel T1. The gas in the slit channel T2 can be guided to the main channel T1.

[0133] For example, the main channel T1 is hourglass-shaped, as can be seen in the following example. Figure 4aThe size of the inlet t11 of the main channel T1 along the X direction is smaller than the size of the outlet t12 of the main channel T1 along the X direction, and the size of the cross section of the main channel T1 along the Y direction at any position is smaller than the size of the outlet t12 of the main channel T1 along the X direction. The slit channel T2 is connected to the inner wall of the main channel T1 at the position of the minimum cross section. The slit channel T2 is provided in two, and the two slit channels T2 are symmetrically arranged along the X direction on both sides of the main channel T1. It can be considered that the inlet of the main channel T1 and the inlet of the slit channel T2 are arranged on the same side of the fluid amplifier 301 along the X direction, and the arrangement of the slit channel T2 of the main channel T1 will not increase the thickness of the fluid amplifier 301. From Figure 4a It can be seen that the cross section of the main channel T1 for gas flow is larger than the cross section of the slit channel T2 for gas flow, and the gas capacity of the main channel T1 is larger than the gas capacity of the slit channel T2. For example, the extension direction of the slit channel T2 is a straight line, and the extension direction of the main channel T2 is arranged at an angle with the extension direction of the main channel T1, and the angle can be between 0-90°. The radial dimension of the main channel T2 is between 0-3mm.

[0134] In the application of the fluid amplifier 301 shown in the heat dissipation system 30 of the electronic equipment, Figure 4a When the fluid amplifier 301 shown is applied to the heat dissipation system 30 of the electronic equipment, the high-pressure gas of the gas compression structure 302 can enter the inlet t21 of the slit channel T2 and enter the main channel T1 through the slit channel T2. The slit channel T2 is exemplarily designed as a radially variable structure, specifically along the flow direction of the gas flow, the radial dimension of the slit channel T2 becomes smaller and smaller, and the gas entering the slit channel T2 can be further compressed to increase the pressure of the gas. Exemplarily, the extension direction of the slit channel T2 is a straight line, and the slit channel T2 is conical. The cross section of the slit channel T2 perpendicular to the gas flow direction is exemplarily rectangular, and can also be a polygon or other irregular shape. It can be understood that the shape of the slit channel T2 along the extension direction can also be other shapes, as long as the radial dimension of the inlet t21 is larger than the radial dimension of the outlet t22. When the shape and structure of the slit channel T2 are changed, the flow parameters of the gas flow in the slit channel T2 will be changed, and the structure of the slit channel T2 can be adjusted adaptively according to the heat dissipation requirements.

[0135] Figure 4b The working principle of the fluid amplifier 301 is exemplified, Figure 4b The structure shown is the cross-sectional structure obtained by cutting the fluid amplifier 301 along the direction perpendicular to the Z direction. As shown in the figure, Figure 4bAs shown, when a small amount of high-pressure gas is introduced into the inlet t21 of the slit passage T2, the high-pressure gas enters the main passage T1 from the outlet t22 of the slit passage T2 and flows along the side wall of the main passage T1 to the outlet direction of the main passage T1. According to the Coanda effect, a negative pressure area is formed near the two opposite side walls of the main passage T1 along the X direction. The fluid amplifier 301 will suck a large amount of ambient air into the main passage T1 from the inlet t11 of the main passage T1 and flow to the outlet t12 of the main passage T1. The high-pressure gas introduced into the main passage T1 by the slit passage T2 serves as a power source to drive the gas in the main passage T1 to form a high-pressure and high-speed airflow. Since the radial dimension of the main passage T1 is several or tens of times larger than the radial dimension of the slit passage T2, the amount of gas finally discharged from the outlet T12 of the main passage T1 can be several or tens of times larger than the amount of high-pressure gas introduced into the main passage T2, thereby forming a larger airflow. The outlet t12 of the main passage T1 of the fluid amplifier 301 is directed towards the heat dissipation fins 402 of the electronic device, and the airflow output by the main passage T1 can accelerate the heat exchange between the heat dissipation fins 402 and the external environment, thereby improving the heat dissipation efficiency.

[0136] In some embodiments, the slit passage T2 is arranged on both sides of the main passage T1 along the X direction. When high-pressure gas enters the main passage T1 through the slit passage T2, a negative pressure area can be formed on both sides of the main passage T1. In some embodiments, a ring-shaped gas guide groove can also be arranged in the main passage T1 to guide the high-pressure gas along the inner wall of the main passage T1 in the X direction to the central position of the main passage T1, thereby forming a negative pressure area at the central position of the main passage T1 to further improve the strength of the ambient air suction. Of course, there can be more slit passages T2, so that at least one slit passage T2 is arranged on each side of the main passage T1.

[0137] Figure 5a A structure of a heat dissipation system 30 is shown, and the gas compression structure 302 delivers high-pressure gas to the slit passage T2 of the fluid amplifier 301 through the conduit 303. As shown in FIG. 3B, the gas compression structure 302 is a compressor, and the conduit 303 is a pipe. The compressor 302 is connected to the pipe 303, and the pipe 303 is connected to the slit passage T2 of the fluid amplifier 301. Figure 5aAs shown, the fluid amplifier 301 and the gas compression structure 302 are arranged along the Y direction with a certain space between them. The main channel T1 inlet and the slit channel T2 inlet are both located on the side of the fluid amplifier 301 facing the gas compression structure 302, and the space between the fluid amplifier 301 and the gas compression structure 302 needs to ensure that sufficient ambient air can enter the main channel T1. Since the fluid amplifier 301 has two slit channels T2, the high-pressure gas of the gas compression structure 302 is delivered to the two slit channels T2 through two conduits 303, respectively. The two ends of the conduit 303 can be in sealed communication with the slit channel T2 and the gas compression structure 302, respectively, to prevent high-pressure gas leakage and improve the utilization rate of high-pressure gas. The conduit 303 is located in the gap between the fluid amplifier 301 and the gas compression structure 302, and the size of the conduit 303 along the Z direction is smaller than the size of the fluid amplifier 301 along the Z direction and the size of the gas compression structure 302 along the Z direction, that is, ambient air can bypass the conduit 303 to enter the main channel T1, and the presence of the conduit 303 will not affect the guidance of the main channel T1 to the gas. When the heat dissipation system 30 is modularly applied to different electronic devices, the conduit 303 can be a telescopic tube or a flexible tube, which facilitates the adjustment of the gap between the fluid amplifier 301 and the gas compression structure 302. Here, the gas compression structure 302 can be a micro gas pump or a small piezoelectric fan. When a piezoelectric fan is selected, the thickness of the piezoelectric fan along the Z direction is selected to be less than or equal to 2.8 mm.

[0138] Figure 5b Two groups of heat dissipation systems 30 are shown to be applied to an electronic device Figure 5aA structure diagram of the heat dissipation system 30 is shown. The two short sides of the two opposite side frames 101 of the shell 10 are respectively provided with two air inlets K1, and the long side of the side frame 101 perpendicular to the Y direction is provided with an air inlet K2. Along the Y direction, the distance between the side where the air inlets K1 and the air outlets K2 are located is greater than the distance between the side where the air inlets K1 are located and the side opposite to the air outlet K2, so as to ensure that the air inlets K1 and the air outlets K2 have a larger distance. The heat dissipation fins 402 are located in the shell 10 and close to the air outlet K2. Along the X direction, the length of the heat dissipation fins 402 is greater than the sum of the lengths of the two air outlets K2. Along the Y direction, the orthographic projection of the heat dissipation fins 402 on the side where the side frame 101 is provided with the air outlet K2 covers the two air outlets K2. The vapor chamber 401 is rectangular and is arranged in the shell 10 along the Y direction. One end of the length direction of the vapor chamber 401 is in contact with the heat dissipation fins 402. In a specific arrangement, there can be structural intersection and overlap between the vapor chamber 401 and the heat dissipation fins 402. The vapor chamber 401 can be in contact with the heat source structure such as the circuit board of the electronic device, so as to absorb the heat of the heat source structure and quickly spread and guide the heat to the heat dissipation fins 402. Along the X direction, the heat dissipation fins 402 fan out the vapor chamber 401, and the heat dissipation fins 402 and the vapor chamber 401 can cooperate with the side frame 101 to form two spaces for arranging the heat dissipation system 30. The fluid amplifier 301 of the heat dissipation system 30 is arranged adjacent to the heat dissipation fins 402 along the Y direction. Along the Y direction, the gas compression structure 302 is arranged on the side of the fluid amplifier 301 away from the heat dissipation fins 402, and there is an air inlet space between the two. The high-pressure gas outlet of the gas compression structure 302 is communicated with the slit channel T2 of the fluid amplifier 301 through the conduit 303. Along the X direction, the orthographic projection of the gas compression structure 302 on the side frame 101 overlaps with the air inlet K1, and the orthographic projection of the air inlet space between the gas compression structure 302 and the fluid amplifier 301 on the side frame 101 overlaps with the air inlet K1.

[0139] Please continue to refer to Figure 5b As shown, taking a group of heat dissipation systems 30 as an example, the gas compression structure 302 sucks a small amount of ambient air through the air inlet K1 and compresses it into high-pressure gas when working, and delivers it to the slit channel T2 of the fluid amplifier 301 through the conduit 303. The high-pressure gas enters the main channel T1 through the slit channel T2, and flows along the inner wall of the main channel T1 to the heat dissipation fins 402, forming a negative pressure area on both sides of the main channel T1. The main channel T1 sucks a large amount of ambient air through the air inlet K1 and delivers it to the heat dissipation fins 402, quickly guiding the heat of the heat dissipation fins 402 to the outside through the air outlet K2. Two groups of heat dissipation systems 30 are symmetrically arranged on both sides of the vapor chamber 401, which can more uniformly and comprehensively dissipate heat for the electronic device and improve the heat dissipation efficiency.

[0140] In summary, the electronic device provided in this application embodiment utilizes a heat dissipation system 30 that can replace a fan to accelerate heat exchange between the heat sink fins 402 and the external environment, thereby achieving heat dissipation for the electronic device. The heat dissipation system 30 operates without fan blades, reducing noise and eliminating issues such as pressing noises. Both the air inlet K1 and air outlet K2 of the electronic device are located on the side of the housing 10. The airflow path of the heat dissipation system 30 is perpendicular to the thickness direction of the electronic device, eliminating the need for an air inlet gap between the heat dissipation system 30 and the back cover 102, thus reducing the thickness of the electronic device. Based on the structural arrangement of the heat dissipation system 30, the air inlet K1 and air outlet K2 can be spaced far apart, reducing the impact of heat recirculation on heat dissipation. The gas compression structure 302 is connected to the slit channel T2 of the fluid amplifier 301 via a conduit 303. High-pressure gas can carry ambient gas into the main channel T1 of the fluid amplifier 301 and guide it to the heat sink fins 402. The entire heat dissipation system 30 can be considered a relatively closed air intake system, fully utilizing the airflow and improving the air-cooling effect.

[0141] Figure 6 This application provides a partial structure of another electronic device, in which the arrangement of the heat spreader 401, heat sink 402, and audio device 50 is similar to that of the present application. Figure 3 Similar to the previous method, it will not be repeated here. Along the X direction, a space is formed between the audio device 50 and the vapor chamber 401 to accommodate the heat dissipation system 30. The electronic device includes two sets of heat dissipation systems 30, which are arranged symmetrically on both sides of the vapor chamber 401. The heat dissipation system 30 includes a fluid amplifier 301, a gas compression structure 302, and a flow guide 304. In each heat dissipation system, the fluid amplifier 301 and the gas compression structure 302 are arranged adjacent to each other along the X direction. The fluid amplifier 301 is opposite to the air inlet K1 along the X direction. The fluid amplifier 301 can compress a small amount of air entering through the air inlet K1 and deliver high-pressure gas to the gas compression structure 302. In order to avoid the audio device 50, the fluid amplifier 301 and the gas compression structure 302 are moved away from the heat dissipation fins 402 along the Y direction, so that the gas compression structure 302 and the audio device 50 are arranged adjacent to each other along the Y direction, and a certain gap is maintained between the fluid amplifier 301 and the heat dissipation fins 402. The airflow guide 304 is connected along the Y direction between the fluid amplifier 301 and the heat sink 402, and is used to guide the airflow discharged from the fluid amplifier 301 to the heat sink 402. Specifically, the airflow guide 304 can be a hollow structure with a channel to guide the airflow from the fluid amplifier 301 to the heat sink 402. One end of the channel is connected to the air outlet port of the fluid amplifier 301, and the other end faces the heat sink 402, preventing the airflow discharged from the fluid amplifier 301 from diffusing to other locations, and guiding as much of the gas discharged from the fluid amplifier 301 as possible to the heat sink 402, thereby improving the airflow utilization rate.

[0142] Figure 7a It shows Figure 6 The structure of the fluid amplifier 301 is described. This fluid amplifier 301 has a relatively thin thickness, and can also be considered to have a large length-to-thickness ratio or width-to-thickness ratio. The fluid amplifier 301 has a hollow structure, including a main channel T1 and a slit channel T2, with the slit channel T2 connected to the sidewall of the main channel T1. Referring to the structure of an electronic device, Figure 7a The main channel T1 of the fluid amplifier 301 shown is... Figure 4a The structure and distribution of the main channel T1 of the fluid amplifier 301 shown are the same. Figure 7a The slit channel T2 of the fluid amplifier 301 shown is with Figure 4a The slit channel T2 of the fluid amplifier 301 shown has a similar structure but a different distribution. The main channel T1 penetrates the fluid amplifier 301 along the Y-direction, with its inlet and outlet facing each other along the Y-direction. The inlet t11 ​​of the main channel T1 is for gas entry, and the outlet t12 is for gas exit. The airflow within the main channel T1 is perpendicular to the Z-direction. This differs from... Figure 4a The fluid amplifier shown has a slit channel T2, which can be referred to as the second channel. The inlet t21 of the slit channel T2 and the inlet t11 ​​of the main channel T1 are located on different sides of the fluid amplifier 301, respectively. The outlet t22 of the slit channel T2 is connected to the inner wall of the main channel T1, allowing gas within the slit channel T2 to be guided to the main channel T1. One slit channel T2 is provided along the X-direction, located on the side of the main channel T1 away from the heat spreader 401 and connected to the inner wall at the smallest cross-section of the main channel T1. It can be considered that the inlets of the main channel T1 and the slit channel T2 are spaced apart along the X-direction on different sides of the fluid amplifier 301, and this arrangement of the slit channel T2 in the main channel T1 does not increase the thickness of the fluid amplifier 301. Figure 7a It can be seen that the cross-section of the main channel T1 used for gas flow is larger than that of the slit channel T2, and the gas capacity of the main channel T1 is greater than that of the slit channel T2. Taking the extension direction of the slit channel T2 as a straight line as an example, the extension direction of the main channel T2 is set at an angle to the extension direction of the main channel T1, and this angle can be around 90°. The radial dimension of the main channel T2 is between 0-3 mm.

[0143] Figure 7b The working principle of the fluid amplifier 301 is illustrated. Figure 7b The structure shown is a cross-sectional structure obtained by cutting the fluid amplifier 301 along a direction perpendicular to the Z-axis. For example... Figure 7bAs shown, when a small amount of high-pressure gas is introduced into the entrance t21 of the slit passage T2, the high-pressure gas enters the main passage T1 from the exit t22 of the slit passage T2 and flows along the side wall of the main passage T1 to the exit t12 of the main passage T1. According to the Coanda effect, a negative pressure area is formed near the left side wall of the main passage T1. The fluid amplifier 301 will suck a large amount of ambient air into the main passage T1 from the entrance t11 of the main passage T1 and flow through the main passage T1 to the exit t12 of the main passage T1. The high-pressure gas introduced into the main passage T1 by the slit passage T2 serves as a power source to drive the gas in the main passage T1 to form a high-pressure and high-speed airflow. Since the radial dimension of the main passage T1 is several or tens of times larger than the radial dimension of the slit passage T2, the amount of gas finally discharged from the exit T12 of the main passage T1 can be several or tens of times larger than the amount of high-pressure gas introduced into the main passage T2, thereby forming a larger airflow. The exit t12 of the main passage T1 of the fluid amplifier 301 is directed towards the heat dissipation fins 402 of the electronic device, and the airflow output by the main passage T1 can accelerate the heat exchange between the heat dissipation fins 402 and the external environment, thereby improving the heat dissipation efficiency.

[0144] Figure 8a A structure of a heat dissipation system 30 is shown, in which the gas compression structure 302 is arranged adjacent to the fluid amplifier 301. The high-pressure gas discharged by the gas compression structure 302 can be directly introduced into the slit passage T2 of the fluid amplifier 301, thereby reducing the air intake resistance and increasing the air volume. The flow guide 304 is a cylindrical structure in the shape of a horn, and the flow guide passage W for guiding flow is formed inside the flow guide 304. In the Y direction, one end of the flow guide passage W is connected to the exit t12 side of the main passage T1 of the gas compression structure 302. In the X direction, the size of the end of the flow guide passage W connected to the gas compression structure 302 is smaller than the size of the end of the flow guide passage W directed towards the heat dissipation fins 402.

[0145] Figure 8b Two groups of heat dissipation systems 30 are shown as applied to an electronic device. Figure 8a A structural schematic diagram of the heat dissipation system 30 is shown. As shown in the figure, the heat dissipation system 30 is applied to an electronic device. Figure 8bAs shown, the fluid amplifier 301 of the heat dissipation system 30 is arranged in the Y direction and spaced apart from the heat dissipation fins 402, and the two are communicated through the flow guide 304. In the X direction, the gas compression structure 302 is arranged adjacent to the fluid amplifier 301 on the side away from the heat dissipation plate 401, and the high-pressure gas outlet of the gas compression structure 302 is communicated with the slit channel T2 of the fluid amplifier 301. In the Y direction, the gas compression structure 302 is arranged in the same row as the audio equipment 50. In the X direction, the orthogonal projection of the gas compression structure 302 on the side wall frame 101 overlaps the air inlet K1. The orthogonal projection of the gas compression structure 302 on the side wall frame 101 overlaps the air inlet K1. Taking a group of heat dissipation systems 30 as an example, when the gas compression structure 302 works, a small amount of ambient air is sucked through the air inlet K1 and compressed into high-pressure gas and delivered to the slit channel T2 of the fluid amplifier 301. The high-pressure gas enters the main channel T1 through the slit channel T2, and flows along the single-side inner wall of the main channel T1 in the X direction to the heat dissipation fins 402, forming a negative pressure area on the single side of the main channel T1. The main channel T1 sucks a large amount of ambient air through the air inlet K1 and delivers it to the heat dissipation fins 402 through the flow guide 304, quickly guiding the heat of the heat dissipation fins 402 to the outside through the air outlet K2. Two groups of heat dissipation systems 30 are symmetrically arranged on both sides of the heat dissipation plate 401, which can more evenly and comprehensively dissipate heat from the electronic equipment and improve the heat dissipation efficiency. In the heat dissipation system of the electronic equipment, the gas compression structure 302, the fluid amplifier 301, and the flow guide 304 can form a relatively closed air inlet system between the air inlet K1 and the heat dissipation fins 402, which can improve the utilization rate of the air source and improve the air cooling effect of the electronic equipment.

[0146] It should be noted that in the electronic equipment provided by the embodiments of the present application, the slit channels T2 in the two different fluid amplifiers 301 and the connection mode of the slit channels T2 and the gas compression structure 302 can be used simultaneously in some application scenarios with relatively large space. That is, if the size of the space of the electronic equipment allows, the fluid amplifier 301 can include Figure 4a the slit channel T2 as shown, or can include Figure 7a the slit channel as shown, and the heat dissipation system 30 can be configured with a suitable at least one gas compression structure 302 for such a fluid amplifier 301. Of course, the heat dissipation system 30 in the electronic equipment provided by the embodiments of the present application can also have other layout modes, and the structure can be adjusted according to different electronic equipment, and the layout flexibility is high.

[0147] In combination with the electronic device provided in the above embodiment, the heat dissipation system 30 of the electronic device needs to compress part of the air by the air compression structure 302 to form high-pressure air, and cooperate with the fluid amplifier 301 to realize air cooling heat dissipation. In order to adapt to the thin and light electronic device, the air compression structure 302 also needs to have a thin and light volume, so as to facilitate the adaptation of the heat dissipation system 30 of the electronic device. Based on this, the embodiment of the present application further provides a fluid compression device which can compress air into high-pressure air and discharge. The fluid compression device can be applied to the heat dissipation system 30 of the electronic device, and the fluid compression device can replace the air compression structure 302 in the above embodiment.

[0148] The fluid compression device provided in the embodiment of the present application realizes the air compression effect by the volume change of the internal air cavity to inhale, compress and discharge the air. As shown in Figure 9 A fluid compression device 1, which includes a housing 11, a rotor assembly 12 and a driving unit, the housing 11 specifically includes a base 111 and a top cover 112, the base 111 and the top cover 112 can cooperate with each other to form the housing 11 along the thickness direction of the fluid compression device 1, and the base 111 and the top cover 112 can be connected by screw thread or bonded by adhesive. The rotor assembly 12 and the driving unit can be integrated in the housing 11. The driving unit includes at least one driving assembly 13, and one driving assembly 13 is exemplarily used to drive the rotation of the rotor assembly 12.

[0149] Figure 10a And Figure 10b is an exploded view of the fluid compression device 1. Referring to Figure 10a And Figure 10bAs shown, the fluid compression device 1 specifically comprises a housing 11, a rotor assembly 12 and a driving assembly 13. The base 111 has a recess A on the side facing the top cover 112, and the recess A and the top cover 112 form an inner cavity of the housing 11 after the base 111 is coupled with the top cover 112. The recess A comprises a bottom wall a2 and a circumferential inner wall a1, the bottom wall a2 is circular, and the circumferential inner wall a1 surrounds the edge of the bottom wall a2. The rotor assembly 12 and the driving assembly 13 can be accommodated in the inner cavity of the housing 11. The rotor assembly 12 comprises at least one rotor 121, which is exemplified as a cam in this case. The rotation axis of the rotor 121 is shown by a dashed line, and the rotor 121 can rotate around the rotation axis. The rotation axis of the rotor 121 passes through the axial center line of the recess A. The rotor 121 comprises a cam surface surrounding the rotation axis. The rotor 121 has a counterweight hollow 1211, so that the center of the cam coincides with the rotation axis of the rotor 121. Specifically, the counterweight hollow 1211 is located between the rotation axis of the rotor 121 and the radially farthest end of the cam surface. The distance between the radially farthest end of the cam surface and the rotation axis of the rotor 121 is greater than the distance between other positions of the cam surface and the rotation axis of the rotor 121. Each driving assembly 13 drives one rotor 121 to rotate around the rotation axis. Each driving assembly 13 exemplarily comprises an annular driving magnet 131, a plurality of driving coils 132, a fixed shaft 133, a bearing 134 and a coil support 135. The driving magnet 131 is used to be coaxially fixed to the rotor 121, the fixed shaft 133 is used to be fixed to the base 111 of the housing 11, and the coil support 135 comprises a central sleeve 1351 and a plurality of supports 1352. The central sleeve 1351 is coaxially fixed to the outer ring of the bearing 134, and the plurality of supports 1352 are distributed at intervals around the rotation axis of the rotor 121 and are fixed to the outer circumferential surface of the central sleeve 1351. Each support 1352 extends in the radial direction of the rotor 121, and at least one driving coil 132 is wound on each support 1352, so that the plurality of driving coils 132 can be distributed at intervals around the rotation axis of the rotor 121, thereby forming a magnetic field for driving the driving magnet 131 to rotate around the rotation axis of the rotor 121.

[0150] In order to control the driving units 13, the fluid compression device 1 further comprises a control assembly 14, which can specifically include a circuit board 141 for being fixed to the base 111, and the circuit board 141 is electrically connected with each driving coil 132. The circuit board 141 can be integrated with a control chip, through which the current flowing through the driving coil 132 can be controlled in size and direction. Alternatively, the control assembly 14 can further include a control chip outside the shell 11, and the circuit board 141 can serve as an adapter board to adapt the driving coil 132 to the external control chip, so that the current flowing through the driving coil 132 is controlled in size and direction by the external control chip. In addition, the fluid compression device 1 further comprises a pressure valve 15 for controlling the air outlet of the fluid compression device 1. An active slider 161 is arranged between the base 111 and the rotor 121 of the shell 11, and the base 111 comprises a sliding groove 1111 opening in the circumferential inner wall a1. In the direction perpendicular to the rotation axis of the rotor 121, one end of the active slider 161 is used to extend into the sliding groove 1111 and slide with the sliding groove 1111, and the other end of the active slider 161 protrudes from the circumferential inner wall a1 and extends into the groove A. Exemplarily, the end of the active slider 161 in the sliding groove 1111 is connected with the base 111 through a spring 162. As shown in Figure 10b the rotor 121 is formed with an axial groove 1212 on the side facing the base 111, and after the rotor 121 is matched with the base 111, the axial groove 1212 can form a space between the groove A of the base 111, which can accommodate the driving magnet 131, the plurality of driving coils 132, the fixed shaft 133, the bearing 134 and the coil support 135.

[0151] Figure 11a A partial structure diagram of the fluid compression device 1 is shown, and the top cover 112 of the shell 11 is omitted here. As shown in Figure 11aAs shown, the outer ring of bearing 134 is fixed to base 111, and coil support 135 is fixed to base 111 via the outer ring of bearing 134. The inner ring of bearing 134 is coaxially fixed to fixed shaft 133, the axis of fixed shaft 133 is collinear with the rotation axis of rotor 121, and the axis of drive magnet 131 is collinear with the rotation axis of rotor 121. Drive magnet 131 surrounds coil support 135 and does not contact coil support 135. Each drive coil 132 and drive magnet 131 are adjacent to each other but do not contact each other along the thickness direction perpendicular to fluid compression device 1, which can save space in the thickness direction of fluid compression device 1. When drive magnet 131 is driven by the magnetic field formed by multiple drive coils 132 to rotate around the rotation axis of rotor 121, drive magnet 131 rotates around the rotation axis of rotor 121, thereby driving rotor 121 to rotate around the rotation axis. During the rotation of rotor 121, rotor 121, drive magnet 131, inner ring of bearing 134, and fixed shaft 133 remain relatively fixed, as do multiple drive coils 132, coil support 135, outer ring of bearing 134, and base 111. The outer casing 11 includes an air inlet j and an air outlet c communicating with the inner cavity. Specifically, air inlet j communicates with the circumferential inner wall a1 of base 111 along a direction perpendicular to the rotation axis of rotor 121, and air outlet c communicates with the circumferential inner wall a1 of base 111 along a direction perpendicular to the rotation axis of rotor 121. A pressure valve 15 is located at air outlet c. Figure 11a As shown, the air inlet j and air outlet c of the outer casing 11 are respectively arranged on both sides of the movable slider 161 along the circumference of the base 111. The air inlet j can be in a normally open state, and the air outlet c can be controlled to open and close by the pressure valve 15.

[0152] The drive assembly 13, consisting of a drive magnet 131, multiple drive coils 132, a fixed shaft 133, a bearing 134, and a coil support 135, is housed within the groove A of the base 111 and protrudes from the bottom wall a2. When the rotor 121 is assembled onto the base 111, it can achieve... Figure 11b The structure shown. (As illustrated) Figure 11b As shown, rotor 121 is housed in groove A, and drive magnet 131 is integrated into rotor 121. The space between rotor 121 and bottom wall a2 of base 111 can accommodate multiple drive coils 132, fixed shaft 133, bearing 134, coil support 135, and circuit board 141.

[0153] Please continue to refer to Figure 11bAs shown, the distance between the radially nearest end of the cam surface of the rotor 121 and the rotation axis is r1, and the distance between the radially farthest end of the cam surface of the rotor 121 and the rotation axis is r2, r2 is greater than r1, and r2 is equal to the radius of the circumferential inner wall a1. The radially farthest end of the cam surface of the rotor 121 can be in contact with the circumferential inner wall a1, and the base 111 and the top cover 112 of the housing 11 can form an air cavity between the cam surface of the rotor 121 and the circumferential inner wall a1 of the base 111. One end of the movable slider 161 in the sliding groove 1111 is connected to the base 111 by a spring 162, and the other end of the movable slider 161 protrudes from the circumferential inner wall a1 and abuts against the cam surface of the rotor 121. The movable slider 161 can divide the air cavity into a first chamber R1 and a second chamber R2. The air inlet j is in communication with the first chamber R1, and the air outlet c is in communication with the second chamber R2. For the convenience of understanding, the space of the first chamber R1 and the space of the second chamber R2 are shown by different shadows respectively. Among them, the spring 162 is in a compressed state and has elastic potential energy, which can provide the movable slider 161 with a pre-tightening force abutting against the cam surface of the rotor 121. The contact between the movable slider 161 and the cam surface of the rotor 121, and between the radially farthest end of the cam surface of the rotor 121 and the axial inner wall a1, is sealed, which can ensure the sealing effect of the first chamber R1 and the second chamber R2. It should be noted that when the radially farthest end of the cam surface of the rotor 121 abuts against the movable slider 161, the volume of one of the first chamber R1 and the second chamber R2 can be considered to be close to 0, and the volume of the other can be considered to be equivalent to the space between the cam surface of the rotor 121 and the circumferential inner wall a1.

[0154] When the driving unit 13 drives the rotor 121 to rotate around the rotation axis, the radially farthest end of the cam surface of the rotor 121 will slide along the axial inner wall a1, thereby changing the volumes of the first chamber R1 and the second chamber R2, realizing air intake and air exhaust, and compressing the gas during the rotation of the rotor 121, and finally discharging high-pressure gas. As shown in FIG. 6, when the rotor 121 rotates clockwise around the rotation axis, the radially farthest end of the cam surface of the rotor 121 will slide along the axial inner wall a1, thereby changing the volumes of the first chamber R1 and the second chamber R2, realizing air intake and air exhaust, and compressing the gas during the rotation of the rotor 121, and finally discharging high-pressure gas. Figure 12a to Figure 12c As shown, the initial position of the rotor 121 is set as shown in FIG. 7. Figure 11a At this time, the volume of the first chamber R1 is smaller than that of the second chamber R2. Taking the clockwise rotation of the rotor 121 around the rotation axis as an example, during the clockwise rotation of the rotor 121 from the position shown in FIG. 7 to the position shown in FIG. 8, the volume of the first chamber R1 increases, and the first chamber R1 can inhale air through the air inlet j. The volume of the second chamber R2 decreases, and the gas in the first chamber R2 is compressed. Figure 12a As shown, the initial position of the rotor 121 is set as shown in FIG. 7. Figure 11b During the clockwise rotation of the rotor 121 from the position shown in FIG. 8 to the position shown in FIG. 9, the volume of the first chamber R1 increases, and the first chamber R1 can inhale air through the air inlet j. The volume of the second chamber R2 decreases, and the gas in the first chamber R2 is compressed. Figure 12b As shown, the initial position of the rotor 121 is set as shown in FIG. 7. Figure 12cDuring the position shown, the volume of the first chamber R1 is further increased, and the volume of the first chamber R1 approaches the space between the cam surface of the rotor 121 and the circumferential inner wall a1. The volume of the second chamber R2 is further decreased to approach the minimum value, and the gas pressure in the second chamber R2 is large enough to start the pressure valve 15 to open to discharge the high-pressure gas from the gas outlet c.

[0155] It should be noted that the exhaust timing of the fluid compression device 1 can be controlled by the pressure valve 15, and when the pressure of the gas in the second chamber R2 is not large enough, the pressure valve 15 is in a closed state. As the volume of the second chamber R2 decreases, the pressure of the gas in the second chamber R2 increases to a value that can open the pressure valve 15, and the high-pressure gas in the second chamber R2 can be discharged through the gas outlet c. Alternatively, the pressure valve 15 can be omitted, and the radial size of the passage of the gas outlet c can be reduced, so that the gas outlet c can be in a normally open state, and the amount of gas discharged from the second chamber R2 through the gas outlet c is very small. During the process in which the pressure of the gas in the second chamber R2 increases from small to large, only a small amount of gas is discharged through the gas outlet c. When the pressure of the gas in the second chamber R2 is large enough, the high-pressure gas is quickly discharged through the gas outlet c. When the fluid compression device 1 is applied to the heat dissipation system 30 of the electronic device, the gas outlet c can cooperate with the slit passage T2 of the fluid amplifier 301 to further compress the discharged gas, so that the gas flow finally entering the main passage T1 has a high pressure and speed, thereby driving a large amount of ambient air to form a gas flow blowing to the heat dissipation fins 402, thereby achieving heat dissipation of the electronic device.

[0156] As Figure 13 shown, a fluid compression device 2 includes a housing 21, a rotor assembly 22, and a driving unit including at least one driving assembly 23. The housing 21 includes a base 211 and a cover 212, which can be connected and fixed along the thickness of the fluid compression device 2, and the rotor assembly 22 and the driving unit can be accommodated in the housing 21. Among them, the housing 21 is in the shape of a racetrack, the two ends of the housing 21 in the length direction are in the shape of a circular arc, and the two side surfaces of the housing 21 in the width direction are parallel to each other. The rotor assembly 22 includes two rotors 221, the rotation axes of the two rotors 221 are parallel to the thickness direction of the fluid compression device 2, and the two rotors 221 are arranged adjacent to each other along the length direction of the housing 21. Exemplarily, each rotor 221 can be configured with one driving assembly 23.

[0157] Figure 14a and Figure 14b An exploded view of the fluid compression device 2 is shown. Referring to Figure 14a and Figure 14bAs shown, the fluid compression device 1 specifically comprises a housing 21, two rotor assemblies 22 and two drive assemblies 23, each rotor assembly 22 is driven by one drive assembly 23. The base 211 has a groove B on the side facing the top cover 212, and the groove B and the top cover 212 form the inner cavity of the housing 21 after the base 211 is matched with the top cover 212. The groove B comprises a bottom wall b2 and a circumferential inner wall b1, the bottom wall b2 is a runway type, which can also be considered as an oblong, and the circumferential inner wall b1 surrounds the edge of the bottom wall b2. In order to make the top cover 212 and the base 211 match more closely, the housing 21 can further comprise a sealing ring 25 arranged between the top cover 212 and the base 211. When the top cover 212 and the base 211 are matched and fixed along the thickness direction of the fluid compression device 2, the sealing ring 25 is clamped between the base 211 and the top cover 212 around the groove B. The rotor assembly 22 comprises two rotors 221, which are respectively exemplified as two structurally identical impellers, each rotor 221 comprises an impeller surface surrounding a rotation axis, and each rotor 221 is driven by a set of drive assemblies 23. Exemplarily, each drive assembly 23 comprises an annular drive magnet 231, a plurality of drive coils 232, a fixed shaft 233, a bearing 234 and a coil holder 235, and the structure of the drive assembly 23 here is similar to that of the drive assembly 13 shown in the fluid compression device 2, which will not be described here again. Of course, the fluid compression device 2 further comprises control assemblies 24 for controlling the two sets of drive assemblies 23, and each control assembly 24 comprises a circuit board 241. Between a set of corresponding circuit boards 241, drive assemblies 23 and rotors 221, the side of the rotor 221 facing the base 211 is formed with an axial groove 2211, and after the rotor 221 is matched with the base 211, the axial groove 2211 can form a space capable of accommodating the drive magnet 231, the plurality of drive coils 232, the fixed shaft 233, the bearing 234 and the coil holder 235 between the groove B of the base 211. Along the width direction of the base 211 of the housing 21, the base 211 comprises an air inlet j and an air outlet c in communication with the circumferential inner wall a1, and the air inlet j and the air outlet c are in a normally open state. Among them, the inner diameter size of the air inlet j is larger than that of the air outlet c. Figure 11a and Figure 11b The structure of the drive assembly 13 in the fluid compression device 2 shown is similar, which will not be described here again. Of course, the fluid compression device 2 further comprises control assemblies 24 for controlling the two sets of drive assemblies 23, and each control assembly 24 comprises a circuit board 241. Between a set of corresponding circuit boards 241, drive assemblies 23 and rotors 221, the side of the rotor 221 facing the base 211 is formed with an axial groove 2211, and after the rotor 221 is matched with the base 211, the axial groove 2211 can form a space capable of accommodating the drive magnet 231, the plurality of drive coils 232, the fixed shaft 233, the bearing 234 and the coil holder 235 between the groove B of the base 211. Along the width direction of the base 211 of the housing 21, the base 211 comprises an air inlet j and an air outlet c in communication with the circumferential inner wall a1, and the air inlet j and the air outlet c are in a normally open state. Among them, the inner diameter size of the air inlet j is larger than that of the air outlet c.

[0158] Figure 15a The partial structure diagram of the fluid compression device 2 is shown, and the top cover 212 of the housing 21 is omitted here. As shown, Figure 15aAs shown, taking a corresponding circuit board 241, drive assembly 23, and rotor 221 as an example, the outer ring of bearing 234 is fixed to base 211, and coil support 235 is fixed to base 211 via the outer ring of bearing 234. The inner ring of bearing 234 is coaxially fixed to fixed shaft 233, the axis of fixed shaft 233 is collinear with the rotation axis of rotor 221, and the axis of drive magnet 231 is collinear with the rotation axis of rotor 221. Drive magnet 231 surrounds coil support 235 and does not contact coil 235. When drive magnet 231 is driven by the magnetic field formed by multiple drive coils 232 to rotate around the rotation axis of rotor 221, drive magnet 231 rotates around the rotation axis of rotor 221, thereby driving rotor 221 to rotate around the rotation axis. During the rotation of rotor 221, rotor 221, drive magnet 231, inner ring of bearing 234, and fixed shaft 233 remain relatively fixed, while multiple drive coils 232, coil support 235, outer ring of bearing 234, and base 211 remain relatively fixed. When rotor 221 is assembled onto base 211, the following can be obtained: Figure 15b The structure shown is as follows. The rotor 221 is housed in the groove A, and the drive magnet 231 is integrated into the rotor 221. The space between the rotor 221 and the bottom wall b2 of the base 211 can accommodate multiple drive coils 232, a fixed shaft 233, a bearing 234, a coil support 235, and a circuit board 241.

[0159] Figure 15a as well as Figure 15b The assembly structure of each drive assembly 23 and rotor 221 shown is similar to Figure 11a as well as Figure 11b The drive assembly 13 shown is similar to the rotor 121 in terms of assembly structure, but the rotor structure is different, as are the mating methods of rotor 221 and housing 21, rotor 121 and housing 11.

[0160] Please refer to the above as well. Figure 15a and Figure 15bAs shown, two impeller-shaped rotors 221 are respectively mounted in grooves B of the base 211, with the impeller surfaces of the two rotors 221 engaging in conjugate meshing. The impeller surfaces of the rotors 221 include multiple convex surfaces m1 and concave surfaces m2 alternately connected along the circumference of the rotor 221, each convex surface m1 contacting the circumferential inner wall b1 of the groove B. When the rotors 221 rotate about their rotation axis, the multiple convex surfaces m1 of the rotors 221 slide relative to the circumferential inner wall b1 and maintain contact. The impeller surfaces of the two rotors 221, the circumferential inner wall b1 of the base 211, the base 211 of the mating housing 21, and the top cover 212 can form an air chamber. Specifically, due to the impeller shape of the rotors 221, this air chamber can include a first chamber R1 and a second chamber R2, the first chamber R1 communicating with the air inlet j, and the second chamber R2 communicating with the air outlet c. For ease of understanding, the spaces of the first chamber R1 and the second chamber R2 are shown with different shades. Furthermore, when two adjacent convex surfaces m1 of each rotor 221 come into contact with the circumferential inner wall b1, a chamber can also be formed between the impeller surface between the two convex surfaces m1 and the circumferential inner wall b1.

[0161] When the two sets of drive units 23 drive their corresponding rotors 221 to rotate around the rotation axis, the impeller surfaces of the two rotors 221 mesh to achieve synchronous counter-rotation. The volume of the first chamber R1 and the second chamber R2 changes, enabling air intake and exhaust. The gas entering the first chamber R1 of the fluid compression device 2 is carried by the two rotors 221 to the second chamber R2 and compressed there, ultimately discharging high-pressure gas. It should be understood that this fluid compression device 2 is equivalent to a Roots rotary pump.

[0162] like Figure 16a to Figure 16g The working process of the fluid compression device 2 is described below. To facilitate understanding of the rotation process of the two rotors 221, a gray arrow is marked on one of the blades of each rotor 221, and the gray arrow corresponds to that blade. The initial position of the rotor 221 is set as follows: Figure 16a As shown, a portion of the impeller surface of the left rotor 221 and a portion of the impeller surface of the right rotor 221, mating with the base 211, form a first chamber R1. Another portion of the impeller surface of the left rotor 221 and another portion of the impeller surface of the right rotor 221, mating with the base 211, form a second chamber R2. When the left rotor 221 rotates counterclockwise and the right rotor 221 rotates clockwise... Figure 16b During the process shown in the diagram, the volume of the first chamber R1 further increases, thus drawing in air through the inlet j as indicated by the arrow. As the two rotors 221 continue to move synchronously in opposite directions... Figure 16b Rotation Figure 16c , Figure 16d , Figure 16e , Figure 16f , Figure 16gThe gas in the first chamber R1 is carried by the two rotors 221 to the chamber between the outer circumferential surface of each rotor 221 and the base 211 along the arrows shown, and is finally transferred to the second chamber R2. Figure 16g The gas in the second chamber R2 shown is compressed and high-pressure gas is discharged through the gas outlet c.

[0163] The two rotors 221 included in the fluid compression device 2 provided by the embodiments of the present application need to keep synchronous movement, otherwise there is a risk of jamming. Two driving assemblies 23 are adopted to respectively drive the two rotors 221 to rotate, and angle detection devices can be configured for the two control assemblies 24 to detect the angles of the two rotors 221 and determine the meshing state of the two rotors 221 through the angles. The angle detection devices herein include, but are not limited to, one or more of a Hall sensor, an eddy current encoder, a magnetic encoder, and a photoelectric sensor. The angle detection devices can be provided in two, and the two angle detection devices are respectively used to detect the rotation angles of the two rotors 221, and whether the two rotors 221 are synchronous can be determined according to the angle data. If they are not synchronous, the current supplied to the driving coils 232 in the two driving assemblies 23 can be adjusted by the control assemblies 24 to change the magnetic field, and then the rotation of the driving magnets 231 is changed to drive the rotors 221 to realize the adjustment of the rotors 221. Of course, the driving assemblies 23 corresponding to the two rotors 221 can also be controlled by the same control assembly 24.

[0164] The Hall sensor can be an analog Hall sensor or a digital Hall sensor. Taking the angle detection device including an analog Hall sensor 28 as an example, as shown in Figure 17a Each rotor 221 is correspondingly configured with a set of angle detection devices composed of two analog Hall sensors 28, and the two analog Hall sensors 28 are oppositely arranged along the radial direction of the rotor 221. Along the axial direction of the rotation axis of the rotor 221, the analog Hall sensor 28 is located between the driving magnet 231 and the circuit board 41, which is shown by a dashed line shadow here.

[0165] Taking Figure 17a the plane V-V parallel to the rotation axis of the rotor 221 to cut the fluid compression device 2, a cross-sectional structure as shown in Figure 17b can be obtained. As shown in Figure 17bAs shown, along the thickness direction of the fluid compression device 2, the circuit board 241 is fixed on the base 211, and there is a certain gap between the circuit board 241 and the rotor 221. The analog Hall sensor 28 can be integrated on the surface of the circuit board 241 facing the rotor 221, and the analog Hall sensor 28 is opposite to the driving magnet 231 along the thickness direction of the fluid compression device 2. When the plurality of driving coils 232 are energized, the magnetic field formed by the driving coils 232 can drive the driving magnet 231 to rotate around the fixed shaft 233 to drive the rotor 221 to rotate, and the two analog Hall sensors 28 can monitor the change of the magnetic field, and the rotation angle of the rotor 221 can be calculated according to the information of the change of the magnetic field. Among them, the circuit board 241 can provide support for the analog Hall sensor 28. When the circuit board 241 is integrated with a control chip, the circuit board 241 can directly receive the data detected by the analog Hall sensor 28 and analyze the rotation angle of the rotor 221. By comparing the rotation angles of the two rotors 221, the currents of the driving coils 232 corresponding to the two rotors 221 are adjusted to adjust the rotation angle of the rotor 221. Alternatively, the circuit board 241 acts as an intermediate adapter board to transmit the electrical signals of the analog Hall sensor 28 to an external control chip.

[0166] In some embodiments, if a digital Hall sensor is selected, three digital Hall sensors can be arranged corresponding to each rotor 221, and the three digital Hall sensors are uniformly distributed along the circumference of the rotor 221, and any two digital Hall sensors form an angle of 120°. Along the thickness direction of the fluid compression device 2, the digital Hall sensor is also integrated on the surface of the circuit board 241 facing the rotor 221 and opposite to the driving magnet 231, which is similar to the analog Hall sensor 28. Figure 17b As shown.

[0167] Alternatively, in some embodiments as shown in Figure 17c , a first magnet 261 is arranged on the impeller protrusion of one of the rotors 221, and a second magnet 262 is arranged on the impeller protrusion of the other rotor 221, the first magnet 261 and the second magnet 262 have the same magnetism, and under the driving of the driving assembly 23, the synchronous rotation of the two rotors 221 is realized by the principle of same polarity repelling each other.

[0168] Alternatively, in some embodiments as shown in Figure 17d , a magnetic coil 27 is arranged on the impeller protrusion of one of the rotors 221, and the other rotor 221 is made of a permanent magnet. The magnetic field generated by the energized magnetic coil 27 can dynamically fine-tune the rotation state of the two rotors 221 to make them synchronous.

[0169] The fluid compression device 2 uses two impeller-shaped rotors 221 to compress air. This structure has advantages in dynamic balance during operation and less vibration, which helps to improve the service life of various mechanical parts. When applied to the heat dissipation system 30 of electronic equipment, it provides a better user experience.

[0170] like Figure 18 The fluid compression device 3 shown includes a housing 31, a rotor assembly 32, and a drive unit. The rotor assembly 32 includes a rotor 321, and the drive unit includes a drive assembly 33. The housing 31 includes a base 311 and a top cover 312, which can be connected and fixed along the thickness of the fluid compression device 3. The rotor assembly 32 and the drive assembly 33 can be accommodated within the housing 31.

[0171] Figure 19a and Figure 19b This is an exploded view of the fluid compression device 3 described above. Figure 19a and Figure 19bAs shown, the base 311 has a recess D on the side facing the top cover 312, and the recess D and the top cover 312 form the inner cavity of the shell 31 after the base 311 is matched with the top cover 312. The recess D includes a bottom wall d2 and a circumferential inner wall d1 surrounding the edge of the bottom wall d2. The base 311 further includes a first air inlet j1, a second air inlet j2, a first air outlet c1, and a second air outlet c2 communicating with the inner cavity of the shell 31. Specifically, the first air inlet j1, the second air inlet j2, the first air outlet c1, and the second air outlet c2 respectively penetrate the base 311 along the thickness direction perpendicular to the fluid compression device 3 and communicate with the circumferential inner wall d1. The base 311 is in a shape similar to a racetrack, and the length direction ends are arc-shaped, and the width direction ends are parallel to each other. The first air inlet j1 and the second air outlet c2 are located on one side of the base 311 in the width direction, and the second air inlet j2 and the first air outlet c1 are located on the other side of the base 311 in the width direction. Along the width direction of the base 311, the first air inlet j1 is opposite to the second air outlet c2, and the second air inlet j2 is opposite to the first air outlet c1. The rotor assembly 32 is accommodated in the inner cavity of the shell 31, and the rotor assembly 32 includes a rotor 321 in a shape similar to a Reuleaux triangle, having three vertices and three circumferential side walls between any two vertices. Each vertex of the rotor 321 is used to contact the circumferential inner wall d1 of the base 311. In order to strengthen the sealing performance of the contact between the vertex of the rotor 321 and the circumferential inner wall d1, a gap f can be provided at each vertex, and a sealing strip 3213 is embedded in each gap f. The sealing strip 3213 can be pre-installed in the gap f of the vertex of the rotor 321 by a spring 3214, and the spring 3214 can provide a certain pre-tightening force for the sealing strip 3213, so that when the rotor 321 is matched with the circumferential inner wall d1, the sealing strip 3213 can always contact the circumferential inner wall d1 and maintain sealing. The side of the rotor 321 facing the base 311 has a central gear ring 3211 coaxial with the rotation axis of the rotor 321. The side of the rotor 321 facing the top cover 312 has an annular recess 3212 coaxial with the rotation axis of the rotor 321. The drive assembly 33 is used to drive the rotor 321 to rotate around the rotation axis.The planet carrier 335 has a first rotating shaft 3351 and a second rotating shaft 3352, the axis of the first rotating shaft 3351 and the second rotating shaft 3352 are parallel to the rotating axis of the rotor 321 respectively, and the first rotating shaft 3351 and the second rotating shaft 3352 are offset in the direction perpendicular to the rotating axis of the rotor 321. The first rotating shaft 3351 is used to be coaxially connected with the driving gear 333 through the bearing 334, and the second rotating shaft 3352 is coaxially connected with the rotor 321. The structure principle of the connection between the rotor 321 and the driving gear 333 in the fluid compression device 3 through the planet carrier 335 can be referred to. Figure 19c As shown in the figure, the dashed line represents the rotating axis of the rotor 321, and the rotating axis of the rotor 321 is eccentric relative to the axis of the driving gear 333. When the rotor 321 rotates around the rotating axis of the rotor 321 relative to the driving gear 333, the rotor 321 can rotate around the axis of the driving gear 333 in cooperation with the planet carrier 335. The ratio of the number of teeth of the central gear ring 3211 to the number of teeth of the driving gear 333 is 3:2.

[0172] Figure 20a The cross-sectional structure of the fluid compression device 3 is shown, which passes through the axis of the driving gear 333 and one of the top corners and one of the circumferential side walls of the rotor 321. Figure 17a As shown in the figure, the driving gear 333 is embedded and fixed in the base 311, the first rotating shaft 3351 of the planet carrier 335 is coaxially connected with the center of the driving gear 333 through the bearing 334, the second rotating shaft 3352 of the planet carrier 335 is coaxially connected with the center of the rotor 321, and the axis of the second rotating shaft 3352 is collinear with the rotating axis of the rotor 321. The central gear ring 3211 of the rotor 321 is engaged with the driving gear 333. The driving magnet 331 is coaxially fixed in the annular groove 3212 of the rotor 321.

[0173] Figure 20b The partial cross-sectional structure of the fluid compression device 3 is shown, which is cut in half in the direction perpendicular to the rotating axis of the rotor 321. As shown in the figure, Figure 20b The state shown is an example of the cross-sectional structure of the right half of the fluid compression device 3. The driving gear 333 is eccentrically connected with the rotor 321 through the planet carrier 335, and the driving gear 333 is engaged with the central gear ring 3211 of the rotor 321. When the driving magnet 331 is driven to rotate around the rotating axis by the magnetic field formed by the plurality of driving coils 332, the rotor 321 rotates around the axis of the driving gear 333, and finally the rotor 321 can rotate in the inner cavity of the shell 31, and the three top corners of the rotor 321 are always in contact with the circumferential inner wall d1 of the base 311. Combined with Figure 17a and Figure 17b As shown in the figure, the driving assembly 33 can be integrated on the shell 31 and the rotor 321, reducing the thickness of the fluid compression device 3.

[0174] like Figure 21 The diagram shows a partial structural representation of the fluid compression device 3, omitting the top cover 312. The rotor 321 is housed within a groove D in the base 311. Each apex of the rotor 321 contacts the circumferential inner wall d1 of the groove D. Each circumferential sidewall of the rotor 321 forms a chamber with the circumferential inner wall d1, namely, a first chamber R1, a second chamber R2, and a third chamber R3. For ease of understanding, the spaces of the three chambers are indicated by different shades. The rotor 321 is connected to the base 311 via a planetary carrier 335. Figure 17a and Figure 17b The connection is shown. The drive magnet 331 of the drive assembly 33 is coaxially fixed to the rotor 321, and multiple drive coils 332 are embedded in the base 311 around the groove D. When the multiple drive coils 332 are energized, the magnetic field formed by the multiple drive coils 332 can drive the drive magnet 331 to rotate around the rotation axis of the rotor 321, thereby driving the rotor 321 to rotate. The magnitude and direction of the current flowing through each drive coil 332 can be different, and the magnitude and method of the current flowing through different drive coils 332 can be adjusted according to the state of the rotor 321, so that the changing magnetic field formed by the multiple drive coils 332 can drive the drive magnet 331 to rotate in a set direction and speed. For example, with... Figure 21 Taking the apex of the rotor 321 marked with an arrow as an example, there are drive coils 332a and 332b on either side of this apex. Currents in different directions are supplied to drive coils 332a and 332b, causing the magnetic fields generated by them to exert opposite forces on the drive magnet 331. When the magnetic field generated by drive coil 332a attracts the drive magnet 331, and the magnetic field generated by drive coil 332b repels it, the drive magnet 331 can drive the rotor 321 to rotate clockwise. During the operation of the fluid compression device 3, the magnitude and direction of the current in the multiple drive coils 332 can be adjusted as needed to change the magnetic field in real time, thereby driving the rotor 321 to rotate according to a predetermined rule. Due to the connection between the planetary carrier 335 and the drive gear 333 and the rotor 321, the rotor 321 can rotate eccentrically relative to the base 311 during the rotation around the rotation axis. The drive gear 333 and the planetary carrier 335 can constrain the movement of the rotor 321, so that each apex of the rotor 321 remains in contact with the circumferential inner wall d1 during the rotation.

[0175] like Figure 22a to Figure 22mAs shown, during the rotation of the rotor 321 around the rotation axis, the volume of the cavity formed between each circumferential side wall of the rotor 321 and the circumferential inner wall d1 based on the shape of the circumferential inner wall d1 of the base 311 changes, so as to realize the suction and exhaust of the fluid compression device 3. During the rotation of the rotor 321, the inhaled gas can also be compressed, and finally high-pressure gas is exhausted.

[0176] It is assumed that the initial position of the rotor 321 is Figure 22a As shown, at this time, one of the vertices of the rotor 321 contacts the circumferential inner wall d1 between the first gas inlet j1 and the second gas outlet c2. For the convenience of understanding, an arrow is marked at the vertex of the rotor 321, and the position of the arrow is fixed relative to the rotor 321 and rotates with the rotor 321. It is further assumed that the space between the circumferential side wall on the right side of the vertex of the rotor 321 and the circumferential inner wall d1 is the first cavity R1, the space between the circumferential side wall on the left side of the vertex of the rotor 321 and the circumferential inner wall d1 is the third cavity R3, and the space between the circumferential side wall opposite to the vertex and the circumferential inner wall d1 is the second cavity R2. The first cavity R1 is connected with the first gas inlet j1, the second cavity R2 is connected with the second gas inlet j2 and the first gas outlet c1, and the third cavity R3 is connected with the second gas outlet c2. The intermediate states of the rotor 321 rotating one circle clockwise along the thick arrow can be referred to 22b to 22i. Figure 22m It can be seen that the volumes of the three cavities change during the rotation of the rotor 321, and the suction and exhaust are realized through the two gas inlets and the two gas outlets. The exhausted gas is high-pressure gas obtained by compression due to the decrease of the cavity volume. For the convenience of understanding, the directions of the gas flows are indicated by dashed arrows.

[0177] It should be understood that, in the working process of the fluid compression device 3, the rotor 321 is in a continuous rotation cycle, and it can be considered that the rotor 321 rotates at a constant speed. Figure 22a to Figure 22m As shown, the rotor 321 rotates one circle clockwise along the thick arrow. During the rotation of the rotor 321, the suction and exhaust processes of each cavity are also not synchronized. Therefore, the approximately complete suction and exhaust processes of the three cavities are exemplarily described respectively.

[0178] Taking the first cavity R1 as an example, during the rotation of the rotor 321 around the rotation axis, the rotor 321 successively passes through Figure 22l , Figure 22m , Figure 22a , Figure 22b , Figure 22c , Figure 22d , Figure 22eDuring the process shown, the volume of the first chamber R1 undergoes a complete process from its minimum value to its maximum value, then shrinks back to its minimum value. When the volume of the first chamber R1 increases, it can draw in air through the first inlet j1. When the volume of the first chamber R1 decreases, the gas inside is compressed into high-pressure gas and finally discharged through the first outlet c1. This process occurs sequentially as the rotor 321 rotates clockwise around its axis. Figure 22f , Figure 22g , Figure 22h , Figure 22i , Figure 22j , Figure 22k During the process shown, the volume of the first chamber R1 undergoes a complete process from minimum to maximum and then to minimum. When the volume of the first chamber R1 increases, it can draw in air through the second inlet j2. When the volume of the first chamber R1 decreases, the gas inside is compressed into high-pressure gas and finally discharged through the second outlet c2. During one revolution of the rotor 321, the first chamber R1 can achieve two intake and exhaust cycles.

[0179] Taking the second chamber R2 as an example, as the rotor 321 rotates clockwise around the rotation axis, it passes through the chamber in sequence. Figure 22a , Figure 22b , Figure 22c , Figure 22d , Figure 22e , Figure 22f , Figure 22g During the process shown, the volume of the second chamber R2 undergoes a complete process from its minimum value to its maximum value, then shrinks back to its minimum value. When the volume of the second chamber R2 increases, it can draw in air through the second inlet j2. When the volume of the second chamber R2 decreases, the gas inside is compressed into high-pressure gas and finally discharged from the second outlet c2. This process occurs as the rotor 321 rotates clockwise around its axis. Figure 22h , Figure 22i , Figure 22g , Figure 22k , Figure 22l , Figure 22m During the process shown, the volume of the second chamber R2 undergoes a complete process from minimum to maximum and then to minimum. When the volume of the second chamber R2 increases, it can draw in air from the first inlet j1. When the volume of the second chamber R2 decreases, the gas inside is compressed into high-pressure gas and finally discharged from the first outlet c1. During one revolution of the rotor 321, the second chamber R2 can achieve two intake and exhaust cycles.

[0180] Taking the third chamber R3 as an example, as the rotor 321 rotates clockwise around the rotation axis, it passes through the chamber in sequence. Figure 22d , Figure 22e , Figure 22f ,Figure 22g , Figure 22h , Figure 22i During the process shown, the volume of the third chamber R3 undergoes a complete process from minimum to maximum and then to minimum again. When the volume of the third chamber R3 increases, air is drawn in through the first inlet j1. When the volume of the third chamber R3 decreases, the gas inside is compressed into high-pressure gas and finally discharged from the first outlet c1. This process occurs sequentially as the rotor 321 rotates clockwise around its axis. Figure 22j , Figure 22k , Figure 22l , Figure 22m , Figure 22a , Figure 22b , Figure 23a to Figure 23m During the process shown, the volume of the third chamber R3 undergoes a complete process from minimum to maximum and then to minimum. When the volume of the third chamber R3 increases, it can draw in air through the second inlet j2. When the volume of the third chamber R3 decreases, the gas inside the third chamber R3 is compressed into high-pressure gas and finally discharged through the second outlet c2. During one rotation of the rotor 321, the third chamber R3 can achieve two intake and exhaust cycles.

[0181] Figure 23a to Figure 23m This illustrates the relative motion between rotor 321 and drive wheel 333 during one clockwise rotation of rotor 321 around the rotation axis. For ease of illustration, Figure 23a By taking a cross-sectional view along the thickness direction perpendicular to the fluid compression device 3, the connection relationship between the rotor 321, the planetary gear 335 and the drive gear 333 can be seen.

[0182] in, Figure 22a and Figure 23b The states shown correspond to, Figure 22b and Figure 23c The states shown correspond to, Figure 22c and Figure 23d The states shown correspond to, Figure 22d and Figure 23e The states shown correspond to, Figure 22e and Figure 23f The states shown correspond to, Figure 22f and Figure 23g The states shown correspond to, Figure 22g and Figure 23h The states shown correspond to, Figure 22h and Figure 23i The states shown correspond to, Figure 22i and Figure 23j The states shown correspond to, Figure 22j and Figure 23k The states shown correspond to, Figure 22k and Figure 23l The states shown correspond to,Figure 22l corresponds to the state shown in FIG. 2B, Figure 23m corresponds to the state shown in FIG. 2B, Figure 22m corresponds to the state shown in FIG. 2B. Figure 23a to Figure 23m corresponds to the state shown in FIG. 2B.

[0183] Referring to FIG. 3A and FIG. 3B together, Figure 3 o1 is the axial position of the driving gear 333, and o2 is the rotating shaft position of the rotor 321. During the rotation of the rotor 321 relative to the circumferential inner wall d1 of the base 311, the rotating shaft of the rotor 321 rotates relative to the axial line of the driving gear 333, the central gear ring 3211 of the rotor 321 meshes with the driving gear 333 and rotates one circle, and finally the eccentric motion of the rotor 321 and the driving gear 333 is realized. During the entire rotation of the rotor 321, the three top corners of the rotor 321 are always in contact with the circumferential inner wall d1 of the base 311.

[0184] The fluid compression device 3 provided by the embodiment of the present application can realize twice suction and exhaust of each chamber during one rotation of the rotor 321, and has higher working efficiency. The two gas inlets and the two gas outlets of the fluid compression device 3 do not need to be provided with valves, and can also realize stable pulsating flow output, and the structure is more stable and reliable. The rotation of the rotor 321 is realized by the attraction or repulsion between the driving coils 332 and the driving magnets 331, and different currents can be input into different driving coils 332 to change the magnetic attraction or repulsion, so that the fluid compression device 3 has a smaller size in the thickness direction.

[0185] In summary, the three kinds of fluid compression devices provided by the embodiment of the present application can all form at least two chambers by cooperation of the rotor and the inner cavity of the shell. During the rotation of the rotor around its rotating shaft, each chamber can realize gas suction and exhaust. During the rotation of the rotor, the volume of the chamber is changed from large to small by cooperation of the outer circumferential surface of the rotor and the circumferential inner wall of the shell, so as to compress the gas and finally discharge high-pressure gas. The driving unit of the three kinds of fluid compression devices can be integrated on the shell and the rotor, so that the fluid compression device has a smaller thickness size. The above three kinds of fluid compression devices can be applied to Figure 6 and ​ The fluid compression device can be applied to the heat dissipation system 30 of the electronic device shown in FIG. 4, to provide high-pressure gas for the fluid amplifier 301, which is helpful for the thickness reduction of the electronic device and can adapt to the miniaturization development of the electronic device. The fluid compression device provided by the above embodiment can also be used to compress liquid. When the fluid compression device is applied to compress liquid, the gas inlet j can be used to introduce liquid, and the gas outlet c can be used to discharge liquid. The gas inlet j can be called a liquid inlet, and the gas outlet c can be called a liquid outlet.

[0186] The above merely provides the specific implementation of the present application, but the protection scope of the present application is not limited to this. Any person skilled in the art can easily think of the changes or replacements within the technical range disclosed by the present application, which should be covered in the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. An electronic device, characterized in that, The electronic device includes a housing and a heat dissipation system and a heat-conducting component housed within the housing; The housing has an air inlet and an air outlet, which penetrate the outer and inner surfaces of the housing respectively along the thickness direction perpendicular to the electronic device. The heat-conducting component includes a heat spreader and heat dissipation fins. The heat spreader is used to absorb the heat emitted by the heat source of the electronic device and guide it to the heat dissipation fins. The heat dissipation fins are disposed at the air outlet of the housing. Along a direction perpendicular to the thickness of the electronic device, the heat dissipation system includes adjacently arranged fluid amplifiers and gas compression structures; the fluid amplifier includes a main channel and at least one slit channel, the main channel and each of the slit channels extending perpendicular to the thickness direction of the electronic device; the main channel is used to guide air from the air inlet to the heat dissipation fins; the inlet of each slit channel is connected to the gas outlet of the gas compression structure, and the outlet of the slit channel is connected to the sidewall of the main channel.

2. The electronic device as claimed in claim 1, characterized in that, The at least one slit channel includes at least one first channel, the inlet of the first channel and the inlet of the main channel are located on the same side of the fluid amplifier and are arranged along a direction perpendicular to the thickness of the electronic device; An air intake space communicating with the air inlet exists between the gas compression structure and the fluid amplifier, and the gas outlet of the gas compression structure is connected to the inlet of each of the first channels via a conduit.

3. The electronic device as described in claim 2, characterized in that, The extension direction of each of the first channels is set at an angle to the inner wall of the main channel.

4. The electronic device as described in claim 2 or 3, characterized in that, Along the arrangement direction of the entrance of the main channel and the entrance of any one of the first channels, at least one first channel is provided on each side of the main channel.

5. The electronic device according to any one of claims 1-4, characterized in that, The at least one slit channel includes at least one second channel, the inlet of each second channel and the inlet of the main channel being located on different sides of the fluid amplifier; The gas compression structure avoids connection between the air inlet and the entrance of the main channel.

6. The electronic device as claimed in claim 5, characterized in that, The heat dissipation system includes a flow guide with a flow channel, one end of which is connected to the outlet of the main channel, and the other end of which faces the heat dissipation fins.

7. The electronic device according to any one of claims 1-6, characterized in that, Along the extension direction of the slit channel, the cross-sectional area of ​​the slit channel inlet is larger than the cross-sectional area of ​​the slit channel outlet.

8. The electronic device according to any one of claims 1-7, characterized in that, The cross-sectional area of ​​the main channel is greater than the cross-sectional area of ​​any one of the slit channels; The cross-sectional dimension of the main channel along the thickness direction of the electronic device is smaller than the dimension along the direction perpendicular to the thickness direction of the electronic device.

9. The electronic device according to any one of claims 1-8, characterized in that, The heat dissipation system comprises two systems, which are respectively disposed on both sides of the heat exchange plate along the thickness direction perpendicular to the electronic device.

10. The electronic device according to any one of claims 1-9, characterized in that, The gas compression structure is a miniature air pump or a piezoelectric fan.

11. The electronic device as claimed in claim 10, characterized in that, The gas compression structure is a miniature gas pump, which includes a housing, two rotors, at least one drive component, and a control component. The housing has an inner cavity, an air inlet, and an air outlet. Along a direction perpendicular to the thickness of the electronic device, the inner cavity includes a circumferential inner wall. The air inlet and air outlet connect the circumferential inner wall to the outer surface of the housing and are spaced apart. Each rotor includes an impeller surface, and the convex surface of the impeller surface is used to contact the circumferential inner wall. Two rotors are arranged adjacent to each other along a direction perpendicular to the thickness of the electronic device, and the impeller surfaces of the two rotors are conjugately meshed. Along the thickness of the electronic device, the rotor has an axial groove on the side facing the housing. The air inlet and air outlet are arranged perpendicular to the arrangement direction of the two rotors, and the air inlet and air outlet are located between the two rotors. At least one of the rotors is driven by one of the drive components, each drive component including an annular drive magnet and a plurality of drive coils; between one rotor and the drive component for driving the rotor, the drive magnet is coaxially fixed to the rotor, and the plurality of drive coils are spaced apart around the rotation axis of the rotor and accommodated in the axial groove of the rotor; along the thickness direction perpendicular to the electronic device, any one of the drive coils is arranged adjacent to the drive magnet; The control component is electrically connected to a plurality of the drive coils of the at least one drive component to supply power to the drive coils.

12. A fluid compression device, characterized in that, The fluid compression device includes a housing, a rotor assembly, at least one drive assembly, and a control assembly; The outer casing has an inner cavity, an air inlet, and an air outlet. Along the thickness direction perpendicular to the fluid compression device, the air inlet and the air outlet respectively connect the inner cavity and the outer surface of the outer casing and are arranged at intervals. The rotor assembly is housed within the inner cavity, and at least two chambers are formed between the outer surface of the rotor assembly and the inner cavity of the housing; the rotor assembly includes at least one rotor, and the rotation axis of each rotor is parallel to the thickness direction of the fluid compression device; during the rotation of the at least one rotor, the volume of the at least two chambers changes; Each of the drive components is used to drive one of the rotors to rotate about its own rotation axis; each of the drive components includes an annular drive magnet and a plurality of drive coils, the drive magnet being coaxially fixed to the rotor, and the plurality of drive coils being fixed at intervals around the rotation axis of the rotor to the housing to form a magnetic field for driving the drive magnet; Along the thickness direction perpendicular to the fluid compression device, any one of the drive coils is arranged adjacent to the drive magnet; The control component is electrically connected to the drive coil of the at least one drive component to supply power to the drive coil.

13. The fluid compression device as claimed in claim 12, characterized in that, Along the thickness direction perpendicular to the fluid compression device, the inner cavity of the housing includes a circumferential inner wall; the rotor assembly includes two adjacent rotors, each rotor including an impeller surface with a convex surface for contacting the circumferential inner wall; the impeller surfaces of the two rotors are conjugately meshed; the air inlet and the air outlet are arranged perpendicular to the arrangement direction of the two impellers, and the air inlet and the air outlet are respectively located between the two rotors; At least one of the rotors is driven by one of the drive components, and the rotor has an axial groove on the side facing the housing along the thickness direction of the fluid compression device, and the drive magnet is fixed to the housing and accommodated in the axial groove.

14. The fluid compression device as claimed in claim 13, characterized in that, The two rotors are each driven by one of the drive components. The control component includes an angle detection device for detecting the rotation angle of the two rotors. The control component is used to adjust the current supplied to the drive components corresponding to the two rotors based on the detection data of the angle detection device.

15. The fluid compression device as claimed in claim 14, characterized in that, The angle detection device includes at least one or more combinations of Hall sensors, eddy current encoders, magnetic encoders, and photoelectric sensors.

16. The fluid compression device according to any one of claims 13-15, characterized in that, One of the rotors is provided with a plurality of first magnets distributed circumferentially along the rotor, and the other rotor is provided with a plurality of second magnets distributed circumferentially along the rotor, wherein the first magnets and the second magnets repel each other.

17. The fluid compression device according to any one of claims 13-16, characterized in that, One of the rotors is provided with a plurality of permanent magnets distributed circumferentially along the rotor, and the other rotor is provided with magnetic coils distributed circumferentially along the rotor, the plurality of magnetic coils being used for charging to form a magnetic field.

18. The fluid compression device as claimed in claim 12, characterized in that, Along the thickness direction perpendicular to the fluid compression device, the inner cavity of the housing includes a circumferential inner wall, and the rotor assembly includes a rotor, the rotor including a cam surface surrounding the rotation axis, the radially furthest end of the cam surface contacting the circumferential inner wall; A movable slider is provided between the outer shell and the rotor. The outer shell includes a groove with an opening located on the circumferential inner wall. Along the direction perpendicular to the rotation axis of the rotor, one end of the movable slider extends into the groove and slides in cooperation with the groove, while the other end of the movable slider protrudes from the circumferential inner wall and contacts the cam surface of the rotor. Along the circumferential direction of the inner wall, the air inlet and the air outlet are respectively arranged on both sides of the slide groove; Along the thickness direction of the fluid compression device, the rotor has an axial groove on the side facing the housing, and the drive magnet is fixed to the housing and accommodated in the axial groove.

19. The fluid compression device as claimed in claim 18, characterized in that, The rotor has a counterweight cutout so that the center of gravity of the rotor coincides with the rotation axis of the rotor, and the counterweight cutout is located between the rotation axis of the rotor and the radially furthest end of the cam surface.

20. The fluid compression device as claimed in claim 18 or 19, characterized in that, The fluid compression device further includes a pressure valve, which is located at the outlet.

21. The fluid compression device according to any one of claims 18-20, characterized in that, One end of the movable slider that extends into the groove is connected to the outer shell via a spring, which is in a compressed state.

22. The fluid compression device according to any one of claims 12-21, characterized in that, The radial dimension of the air outlet is smaller than the radial dimension of the air inlet.

23. The fluid compression device according to any one of claims 13-22, characterized in that, Each of the drive components includes a fixed shaft, bearings, and a coil frame; The fixed shaft is fixed to the outer casing, and the fixed shaft is coaxial with the rotation axis of the rotor; The coil frame includes a central sleeve and multiple supports. The multiple supports are fixed at intervals around the rotation axis of the rotor on the outer circumferential surface of the central sleeve. Each support is used to wind one drive coil. The inner ring of the bearing is fixed to the fixed shaft, and the outer ring of the bearing is coaxially fixed to the center sleeve.

24. The fluid compression device as claimed in claim 12, characterized in that, Along the thickness direction perpendicular to the fluid compression device, the inner cavity of the housing includes a circumferential inner wall, the rotor assembly includes a rotor, the outer circumferential surface of the rotor includes three circumferential sidewalls, an apex angle is formed between any two adjacent circumferential sidewalls, and each apex angle contacts the circumferential inner wall; The rotor has a central gear ring coaxial with the rotor's rotation axis; the drive magnet is fixed to the rotor around the central gear ring, and the plurality of drive coils are fixed to the outer shell at intervals around the circumferential inner wall; The drive assembly further includes a drive gear and a planetary carrier. The drive gear is fixed to the housing and meshes with the central gear ring. The ratio of the number of teeth on the central gear ring to the number of teeth on the drive gear is 3:

2. The planetary carrier includes a first shaft and a second shaft with parallel axes. The first shaft is rotatably connected to the drive gear on the same axis, and the second shaft is rotatably connected to the rotor on the same axis.

25. The fluid compression device as claimed in claim 24, characterized in that, The number of air inlets is two, and the number of air outlets is two; Along the thickness direction perpendicular to the fluid compression device, one air outlet and one air inlet are arranged adjacent to each other on one side of the housing, and another air outlet and another air inlet are arranged adjacent to each other on the other side of the housing, with one air outlet facing one air inlet and another air outlet facing another air inlet.

26. The fluid compression device as claimed in claim 24 or 25, characterized in that, Each apex of the rotor is provided with a slit, and a sealing strip is embedded in the slit. The sealing strip is used to seal the gap between the apex of the rotor and the circumferential inner wall.

27. The fluid compression device as claimed in claim 26, characterized in that, A spring is embedded between the gap and the sealing strip, and the spring is used to provide a force to the sealing strip to press against the circumferential inner wall.

28. An electronic device, characterized in that, The electronic device includes a housing and a heat dissipation system and heat-conducting components housed within the housing; The housing has an air inlet and an air outlet, which penetrate the outer and inner surfaces of the housing respectively along the thickness direction perpendicular to the electronic device. The heat-conducting component includes a heat spreader and heat dissipation fins. The heat spreader is used to absorb the heat emitted by the heat source of the electronic device and guide it to the heat dissipation fins. The heat dissipation fins are disposed at the air outlet of the housing. Along a direction perpendicular to the thickness of the electronic device, the heat dissipation system includes adjacently arranged fluid amplifiers and a fluid compression device as described in any one of claims 12-27; the fluid amplifier includes a main channel and at least one slit channel, the main channel and each of the slit channels extending in a direction perpendicular to the thickness of the electronic device; the main channel is used to guide air from the air inlet to the heat dissipation fins; the inlet of each of the slit channels is connected to the outlet of the fluid compression device, and the outlet of the slit channel is connected to the sidewall of the main channel.

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