Fluid compression apparatus and electronic device

Abstract

Provided in the present application are a fluid compression apparatus and an electronic device. The electronic device comprises a housing, and a heat dissipation system and a heat conduction assembly accommodated in the housing, wherein the housing is provided with an air inlet and an air outlet, the air inlet and the air outlet being arranged on side surfaces of the housing; the heat conduction assembly comprises a vapor chamber and heat dissipation fins; and in the direction perpendicular to the thickness of the electronic device, 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, the extension directions of the main channel and each slit channel being perpendicular to the thickness of the electronic device; the main channel is used for guiding air from the air inlet to the heat dissipation fins; an inlet of each slit channel is in communication with a gas outlet of the gas compression structure, and an outlet of each slit channel is in communication with the side wall of the main channel. The heat dissipation system in the electronic device has a relatively thin thickness, thereby facilitating miniaturization of the electronic device while ensuring heat dissipation performance.

Description

Fluid compression devices and electronic equipment

[0001] Cross-references to related applications

[0002] This application claims priority to Chinese Patent Application No. 202410970440.3, filed on July 18, 2024, entitled "Fluid Compression Apparatus and Electronic Equipment", the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of terminal technology, and in particular to a fluid compression device and electronic device. Background Technology

[0004] In recent years, with the upgrading of electronic product hardware and chip specifications, and users' increasing demand for improved electronic product performance, how to fully unleash the performance of electronic devices has become a key focus of product iteration and upgrading. At the same time, in order to improve the user experience, electronic devices are trending towards thinner and lighter designs, which in turn leads to a continuous reduction in heat dissipation space.

[0005] Traditional heat dissipation technologies can no longer meet the heat dissipation needs of current electronic devices, and the current heat dissipation structures are too large and will restrict further reduction in the thickness of the entire system. Summary of the Invention

[0006] This application provides a fluid compression device and an electronic device, wherein the heat dissipation system of the electronic device has a thin thickness, which is conducive to the miniaturization of the electronic device while ensuring heat dissipation performance.

[0007] In a first aspect, this application provides an electronic device, which 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 a direction perpendicular to the thickness of the electronic device, and the air inlet and air outlet are arranged on the side of the housing; the heat-conducting component includes a heat spreader and heat dissipation fins, the heat spreader being used to absorb heat emitted by the heat source of the electronic device and guide it to the heat dissipation fins, the heat dissipation fins being disposed at the air outlet of the housing; along a direction perpendicular to the thickness of the electronic device, the heat dissipation system includes a fluid amplifier and a gas compression structure arranged adjacent to each other; the fluid amplifier includes a main channel and at least one slit channel, the extension direction of the main channel and each slit channel being 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 side wall of the main channel. When the heat dissipation system of this electronic device is working, the gas compression structure can draw in air from the air inlet, compress it, 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, which can form a negative pressure area in the main channel. This allows the main channel of the fluid amplifier to draw in a large amount of air from the air inlet and form a high-speed airflow that flows to the heat dissipation fins, accelerating the heat exchange between the heat dissipation fins and the air, and achieving heat dissipation for the electronic device.

[0008] The aforementioned electronic device's cooling system utilizes a gas compression structure to provide a small amount of compressed air to the fluid amplifier as a power source, driving the ambient airflow to form a high-pressure, high-flow-rate airflow that blows onto the heat sink fins, achieving excellent heat dissipation. The entire cooling system is relatively sealed, fully utilizing the airflow to enhance cooling efficiency. Both the air inlet and outlet are located on the side of the casing, eliminating the need for a pre-existing airflow gap in the thickness direction and avoiding any structural damage to the casing's strength or appearance, thus contributing to the trend towards thinner and lighter electronic products. This cooling system replaces the traditional centrifugal fan with a fluid amplifier and gas compression structure, avoiding the noise and clicking sounds associated with centrifugal fans and providing a better user experience.

[0009] In some possible implementations, at least one slit channel includes at least one first channel, the inlet of which is located on the same side of the fluid amplifier and 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 first channel via a conduit. In this heat dissipation system, the gas compression structure is located on the air intake side of the main channel of the fluid amplifier, the air intake space ensures that air from the air inlet can enter the main channel, and the conduit can deliver the high-pressure gas output from the gas compression structure to the slit channel.

[0010] In the case where the extension direction of the slit channel is a straight line, the extension direction of the main channel is set at an angle to the inner wall of each first channel.

[0011] In some possible implementations, at least one first channel is provided on each side of the main channel, along the arrangement direction of the main channel entrance and any one of the first channel entrances. The slit channels on both sides of the main channel can introduce high-pressure gas into both sides of the main channel, thereby creating a negative pressure area on both sides of the inner wall of the main channel.

[0012] In some possible implementations, at least one slit channel includes at least one second channel, with the inlet of each second channel and the main channel inlet located on different sides of the fluid amplifier. A gas compression structure avoids communication between the air inlet and the main channel inlet. In this heat dissipation system, the compression structure is positioned 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.

[0013] In some possible implementations, the electronic device may include other components such as audio equipment. To avoid interference with these components, a gap may exist between the cooling system and the heat sink fins. Specifically, a gap may exist between the fluid amplifier and the heat sink fins. In this case, the cooling system includes a flow guide with a channel, one end of which connects to the outlet of the main channel, and the other end of which faces the heat sink fins. The flow guide channel of the flow guide can deliver the airflow generated by the cooling system to the heat sink fins, increasing the utilization rate of the airflow.

[0014] In some possible implementations, the cross-sectional area of ​​the slit channel inlet is larger than the cross-sectional area of ​​the slit channel outlet along the extension direction of the slit channel, thereby further compressing the compressed gas.

[0015] In some possible implementations, the cross-sectional area of ​​the main channel is larger than that of any single slit channel, thus enabling a small amount of high-pressure gas to act as a power source, driving several times or even tens of times the volume of ambient gas to form a large airflow. The cross-sectional dimension of the main channel along the thickness direction of the electronic device is smaller than that 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.

[0016] In some possible implementations, there are two heat dissipation systems, arranged perpendicular to the thickness of the electronic device, on opposite sides of the vapor chamber, thereby dissipating heat more evenly on the electronic device.

[0017] Among some possible implementation methods, the gas compression structure can be a miniature air pump or a piezoelectric fan. Both miniature air pumps and piezoelectric fans can compress the air entering the housing to output high-pressure gas to the slit channel of the fluid amplifier. Both miniature air pumps and piezoelectric fans can be made with a small thickness, making them suitable for miniaturized electronic devices.

[0018] When a miniature air pump is selected for the gas compression structure, the miniature air pump can be selected with a structure similar to a Roots rotary pump. Specifically, the gas compression structure includes a housing, two rotors, at least one drive assembly, and a control assembly. The housing has an inner cavity, an inlet, and an outlet. Along a thickness direction perpendicular to the electronic device, the inlet and outlet connect the inner cavity and the outer surface of the housing, respectively, 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. The two rotors are arranged adjacent to each other along a thickness direction perpendicular to the electronic device, and the impeller surfaces of the two rotors are conjugately meshed. Along the thickness direction of the electronic device, the rotor has an axial groove on the side facing the housing. At least one rotor is driven by a drive assembly, each drive assembly including an annular drive magnet and multiple drive coils. Between one rotor and the drive assembly for driving the rotor, the drive magnet is coaxially fixed to the rotor, and the multiple drive coils are fixed to the housing and accommodated in the axial groove of the rotor. The multiple drive coils are spaced apart around the rotation axis of the rotor to form a magnetic field for driving the drive magnet. Along a thickness direction perpendicular to the electronic device, any one drive coil is arranged adjacent to the drive magnet. The control assembly is electrically connected to the multiple drive coils of the at least one drive assembly to supply power to the drive coils. The air inlet and outlet are arranged perpendicular to the arrangement direction of the two rotors, and are located between the two rotors. A chamber is formed between the circumferential inner wall of the air inlet and the impeller surfaces of the two rotors, and a chamber is formed between the circumferential inner wall of the air outlet and the impeller surfaces of the two rotors. During the meshing rotation of the two rotors, the impeller surfaces of the two rotors can transfer the gas entering through the air inlet to the air outlet. The volume change of the chambers connected to the air inlet and the air outlet enables gas compression. This gas compression structure achieves gas intake and exhaust through the meshing of the impeller surfaces of the two rotors, offering advantages in dynamic balance and minimizing vibration. The drive magnets and drive coils of the drive assembly are arranged perpendicular to the thickness direction of the electronic device, with no overlap in the thickness direction, making it suitable for miniaturized electronic devices.

[0019] In some possible implementations, two rotors can be driven to rotate around their respective axes by two drive components. To maintain synchronous movement of the two rotors, the control component includes an angle detection device for detecting the rotation angle of the two rotors. The control component can adjust the current supplied to the corresponding drive components of the two rotors based on the detection data from the angle detection device. Synchronous movement of the two rotors is achieved through the angle detection device in conjunction with the control component, preventing the two rotors from jamming. The angle detection device includes at least one or more combinations of Hall effect sensors, eddy current encoders, magnetic encoders, and photoelectric sensors. Alternatively, one rotor may have multiple first magnets distributed circumferentially along the rotor's axis, and the other rotor may have multiple second magnets distributed circumferentially along the rotor's axis. The first and second magnets repel each other, achieving synchronous movement of the two rotors through mutual repulsion. Another option is that one rotor may have multiple permanent magnets distributed circumferentially along the rotor's axis, and the other rotor may have magnetic coils distributed circumferentially along the rotor's axis. The multiple magnetic coils are used for charging to form a magnetic field, and the magnetic field formed by the magnetic coils dynamically fine-tunes the synchronous movement of the two rotors.

[0020] Secondly, embodiments of this application provide a fluid compression device, which includes a housing, a rotor assembly, at least one drive assembly, and a control assembly. The housing has an inner cavity, an inlet, and an outlet. Along the thickness direction of the fluid compression device, the inlet and outlet respectively connect the inner cavity and the outer surface of the housing and are spaced apart. 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 at least one rotor, the volume of at least two chambers changes. Each drive assembly is used to drive a rotor to rotate about its own rotation axis. Each drive assembly includes an annular drive magnet and a plurality of drive coils. The drive magnet is coaxially fixed to the rotor, and the plurality of drive coils are spaced apart and fixed to the housing around the rotation axis of the rotor 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 assembly is electrically connected to the drive coil of at least one drive assembly to supply power to the drive coil.

[0021] In this fluid compression device, each chamber can achieve air intake and exhaust during the rotor's rotation around its own axis. Furthermore, during rotation, the rotor can transfer the gas entering through the intake port to the exhaust port. The volume of different chambers varies from large to small due to the interaction between the rotor's outer surface and the outer casing, thereby compressing the gas and ultimately expelling high-pressure gas. The drive unit of the fluid compression device can be integrated into the casing and rotor, resulting in a smaller thickness. The drive magnets and drive coils are arranged perpendicular to the thickness direction of the fluid compression device, with no overlap in the thickness direction, further reducing the device's thickness. This fluid compression device can be used in the heat dissipation system of the electronic device provided in the first aspect, replacing the gas compression structure of the heat dissipation system. It can also be used to compress liquids. When the fluid compression device is used to compress liquids, the intake port can be used for liquid inlet, and the exhaust port can be used for liquid outlet; the intake port can be called the liquid inlet, and the exhaust port can be called the liquid outlet.

[0022] In some possible implementations, 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 outlet are arranged perpendicular to the arrangement direction of the two impellers, and the air inlet and outlet are located between the two rotors. At least one rotor is driven by a drive assembly. Along the thickness direction of the fluid compression device, the rotor has an axial groove on the side facing the housing, and multiple drive coils are fixed to the housing and accommodated within the axial groove. This fluid compression device achieves gas intake and exhaust through the meshing of the impeller surfaces of the two rotors, offering advantages in dynamic balance during movement and minimizing vibration.

[0023] In some possible implementations, the two rotors are each driven by a separate drive assembly. The control assembly includes angle detection devices to detect the rotational angle of the two rotors. The control assembly adjusts the current supplied to the corresponding drive assemblies of the two rotors based on the detection data from the angle detection devices. The two rotors move synchronously through the angle detection devices and the control assembly, preventing them from jamming.

[0024] The angle detection device includes at least one or more combinations of Hall sensors, eddy current encoders, magnetic encoders, and photoelectric sensors.

[0025] In some possible implementations, one rotor 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. The first magnets and the second magnets repel each other, and the two rotors move synchronously through the mutual repulsion of the first magnets and the second magnets.

[0026] In some possible implementations, one rotor is equipped with multiple permanent magnets distributed circumferentially along the rotor, and the other rotor is equipped with magnetic coils distributed circumferentially along the rotor. The multiple magnetic coils are used to charge and form a magnetic field, and the magnetic field formed by the magnetic coils is used to dynamically fine-tune the synchronous movement of the two rotors.

[0027] In some possible implementations, 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 with a cam surface surrounding a rotation axis. The furthest radial end of the rotor contacts the circumferential inner wall. A movable slider is provided between the housing and the rotor. The housing includes a groove with an opening located on the circumferential inner wall. Along the rotation axis perpendicular to the rotor, one end of the movable slider extends into and slides into the groove, while the other end protrudes from the circumferential inner wall and contacts the cam surface of the rotor. An air inlet and an air outlet are arranged on opposite sides of the groove along the circumferential direction of the inner wall. On either side of the movable slider, the cam surface of the rotor forms two chambers with the circumferential inner wall of the housing. Along the thickness direction of the fluid compression device, the rotor has an axial groove on the side facing the housing, and multiple drive coils are fixed to the housing and accommodated within the axial groove. As the rotor rotates around its own axis of rotation, the radially furthest end of the movable slide cam surface slides along the circumferential inner wall of the outer casing, which can change the volume of the two chambers mentioned above, thereby enabling the intake and exhaust of gas. By controlling the exhaust, the gas can be compressed.

[0028] In some possible implementations, the rotor has a counterweight cutout so that the rotor's center of gravity coincides with the rotor's axis of rotation. The counterweight cutout is located between the rotor's axis of rotation and the radially furthest end of the cam surface to maintain vibration balance during the operation of the fluid compression device.

[0029] In some possible implementations, the fluid compression device also includes a pressure valve located at the outlet. The pressure valve is used to adjust the timing of the exhaust to compress the gas.

[0030] In some possible implementations, each drive assembly includes a fixed shaft, a bearing, and a coil holder. The fixed shaft is fixed to the housing and is coaxial with the rotor's rotation axis. The coil holder includes a central sleeve and multiple supports, which are fixed at intervals around the rotor's rotation axis on the outer circumference of the central sleeve. Each support is used to wind a 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 central sleeve. This fixed shaft, bearing, and coil holder, together with the drive magnet and drive coil, can form a motor that drives the rotor to rotate. The drive assembly is essentially integrated into the rotor and housing, saving space in the fluid compression device.

[0031] In some possible implementations, 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 outer circumferential surface of the rotor includes three circumferential sidewalls, with an apex formed between any two adjacent circumferential sidewalls. Each apex contacts the circumferential inner wall, and each circumferential sidewall can form a chamber with one of the circumferential inner walls. The rotor has a central gear ring coaxial with the rotor's rotation axis. A drive magnet is fixed to the rotor around the central gear ring, and multiple drive coils are fixed to the housing at intervals around the circumferential inner wall. The drive assembly also 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 coaxially, and the second shaft is rotatably connected to the rotor coaxially. This fluid compression device allows the rotor to move relative to the housing in a planetary gear manner. During the rotor's movement, there are no large-stroke sliding moving parts, resulting in a more reliable and stable structure.

[0032] In some possible implementations, there are two air inlets and two air outlets. 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, while 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 the other facing another air inlet. During one revolution of the rotor around its own axis, each chamber can achieve two gas intake and exhaust cycles, resulting in higher efficiency.

[0033] Thirdly, embodiments of this application provide a fluid compression device, which includes a housing, two rotors, at least one drive assembly, and a control assembly. The housing has an inner cavity, an inlet, and an outlet. Along a thickness direction perpendicular to the fluid compression device, the inlet and outlet communicate with the outer surface of the inner cavity 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. The two rotors are arranged adjacent to each other along a thickness direction perpendicular to the fluid compression device, and the impeller surfaces of the two rotors are conjugately meshed. Each drive assembly includes an annular drive magnet and multiple drive coils. The drive magnet is coaxially fixed to the rotor. Along the thickness direction of the fluid compression device, the rotor has an axial groove on the side facing the housing. The multiple drive coils are fixed to the housing and accommodated within the axial groove. The multiple drive coils are spaced apart around the rotation axis of the rotor to form a magnetic field for driving the drive magnet. Along a thickness direction perpendicular to the fluid compression device, any one drive coil is arranged adjacent to the drive magnet. The control assembly is electrically connected to the multiple drive coils to supply power to the drive coils. Each drive assembly can correspondingly drive one rotor to rotate around its own rotation axis. The air inlet and outlet are arranged perpendicular to the arrangement of the two rotors, and are located between the two rotors. A chamber is formed between the circumferential inner wall on one side of the air inlet and the impeller surfaces of the two rotors, and a chamber is formed between the circumferential inner wall on the other side of the air outlet and the impeller surfaces of the two rotors. During the meshing rotation of the two rotors, the impeller surfaces of the two rotors can transfer the gas entering through the air inlet to the air outlet side. The volume change of the chambers connected to the air inlet and the air outlet enables gas compression. This fluid compression device achieves gas intake and exhaust through the meshing of the impeller surfaces of the two rotors, exhibiting advantages in dynamic balance during operation and minimizing vibration.

[0034] Each drive assembly includes a fixed shaft, a bearing, and a coil frame. The fixed shaft is fixed to the housing and is coaxial with the rotor's rotation axis. The coil frame includes a central sleeve and multiple supports, which are fixed at intervals around the rotor's rotation axis on the outer circumference of the central sleeve. Each support is used to wind a 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 central sleeve. This fixed shaft, bearing, and coil frame, together with the drive magnet and drive coil, can form a motor that drives the rotor to rotate. The drive assembly is essentially integrated into the rotor and housing, saving space in the fluid compression device.

[0035] In some possible implementations, one rotor can be driven to rotate around its own axis by a drive component, and the meshing of the two rotors can drive the other rotor to rotate around its own axis, thereby compressing the gas.

[0036] In some possible implementations, two rotors can be driven to rotate around their respective axes by two drive components. To maintain synchronous movement of the two rotors, the control component includes an angle detection device for detecting the rotational angle of the two rotors. The control component can adjust the current supplied to the corresponding drive components of the two rotors based on the detection data from the angle detection device. Synchronous movement of the two rotors through the angle detection device and the control component prevents the two rotors from jamming. The angle detection device includes at least one or a combination of Hall effect sensors, eddy current encoders, magnetic encoders, and photoelectric sensors.

[0037] Alternatively, one rotor may have multiple first magnets distributed circumferentially along its length, while the other rotor may have multiple second magnets distributed circumferentially along its length. The first and second magnets repel each other, achieving synchronous movement of the two rotors through this mutual repulsion. Or, one rotor may have multiple permanent magnets distributed circumferentially along its length, while the other rotor may have magnetic coils distributed circumferentially along its length. The magnetic coils are used to charge and generate a magnetic field, which dynamically fine-tunes the synchronous movement of the two rotors.

[0038] Fourthly, embodiments of this application provide a fluid compression device, which includes a housing, a rotor, a drive assembly, and a control assembly. The housing has an inner cavity, an inlet, and an outlet. Along a thickness direction perpendicular to the fluid compression device, the inlet and outlet communicate with the outer surfaces of the inner cavity and are spaced apart. The rotor is housed within the inner cavity, and the rotor's rotation axis is parallel to the thickness direction of the fluid compression device. The housing includes a circumferential inner wall surrounding the rotor's rotation axis. The rotor includes a cam surface surrounding its own rotation axis, and the radially furthest end of the cam surface contacts the axial inner wall. The drive assembly includes an annular drive magnet and multiple drive coils. The drive magnet is coaxially fixed to the rotor. Along the thickness direction of the fluid compression device, the rotor has an axial groove on the side facing the housing. The multiple drive coils are fixed to the housing and housed within the axial groove. The multiple drive coils are spaced apart around the rotor's rotation axis to form a magnetic field for driving the drive magnet. Along a thickness direction perpendicular to the fluid compression device, any one drive coil is arranged adjacent to the drive magnet. The control assembly is electrically connected to the multiple drive coils to supply power to the drive coils. A movable slider is provided between the outer casing and the rotor. The outer casing 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 into it. 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 circumferential inner wall, the air inlet and air outlet are arranged on both sides of the groove. The cam surface of the rotor located on both sides of the movable slider forms two chambers between it and the circumferential inner wall. During the rotation of the rotor around the rotation axis, the volume of the two chambers changes.

[0039] In some possible implementations, the fluid compression device also includes a pressure valve located at the outlet, which can be used to adjust the pressure of the gas in the chamber connected to the outlet.

[0040] In some possible implementations, the radial dimension of the outlet is smaller than that of the inlet. By designing a large intake and a small exhaust, the gas compression effect can be optimized.

[0041] In some possible implementations, in order to make the rotor's center of gravity coincide with the rotor's axis of rotation, the rotor is provided with a counterweight cutout, which is specifically located between the rotor's axis of rotation and the radially furthest end of the cam surface.

[0042] Fifthly, embodiments of this application provide a fluid compression device, which includes a housing, a rotor, a drive assembly, and a control assembly. The housing has an inner cavity, an inlet, and an outlet. Along a direction perpendicular to the thickness of the fluid compression device, the inlet and outlet communicate with the outer surface of the inner cavity and are spaced apart. The outer circumferential surface of the rotor includes three circumferential sidewalls, with an apex formed between any two adjacent circumferential sidewalls. Each apex contacts the inner circumferential wall, and a chamber can be formed between each circumferential sidewall and the inner circumferential wall. The rotor has a central gear ring coaxial with the rotor's rotation axis. Each drive assembly includes an annular drive magnet and multiple drive coils. The drive magnet is coaxially fixed to the rotor. The drive magnet is fixed to the rotor around the central gear ring, and the multiple drive coils are spaced apart and fixed to the housing around the inner circumferential wall to form a magnetic field for driving the drive magnet. Along a direction perpendicular to the thickness of the fluid compression device, any one drive coil is arranged adjacent to the drive magnet. The control assembly is electrically connected to the multiple drive coils to supply power to the drive coils. The drive assembly also includes a drive gear and a planetary carrier. The drive gear is fixed to the housing and meshes with a 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. This fluid compression device allows the rotor to move relative to the housing in a planetary gear manner. There are no large-stroke sliding moving parts during the rotor's movement, making the structure more reliable and stable.

[0043] In some possible implementations, there are two air inlets and two air outlets; 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. During one revolution of the rotor around its own rotation axis, each chamber can achieve two gas intake and exhaust cycles, resulting in higher efficiency.

[0044] In some possible implementations, each apex of the rotor is provided with a slot, into which a sealing strip is embedded. The sealing strip can be used with a spring to seal the gap between the apex of the rotor and the circumferential inner wall. To ensure that the sealing strip remains in contact with the circumferential inner wall, a spring can be embedded between the sealing strip and the slot. The spring can apply a certain preload to the sealing strip so that the sealing strip can be pressed against the circumferential inner wall.

[0045] In a sixth aspect, embodiments of this application provide an electronic device, which 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 a direction perpendicular to the thickness of the electronic device. The heat-conducting component includes a heat spreader and heat dissipation fins. The heat spreader absorbs heat emitted by the heat source of the electronic device and guides it to the heat dissipation fins, which 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 any of the fluid compression devices provided in the second aspect. The fluid amplifier includes a main channel and at least one slit channel, the extension directions of which are perpendicular to the thickness direction of the electronic device. The main channel guides air from the air inlet to the heat dissipation fins. The inlet of each slit channel 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. The fluid compression device provides high-pressure gas to the fluid amplifier, which helps to reduce the thickness of the electronic device and adapts to the miniaturization of electronic devices. Attached Figure Description

[0046] Figure 1a shows the structure of a centrifugal fan in the prior art;

[0047] Figure 1b is a schematic diagram of the heat dissipation principle of an electronic device in the prior art;

[0048] Figure 1c is a schematic diagram of the heat dissipation principle of an electronic device in the prior art;

[0049] Figure 1d is a schematic diagram of the working principle of a piezoelectric diaphragm pump in the prior art;

[0050] Figure 1e is a schematic diagram of the working principle of a piezoelectric diaphragm pump in the prior art;

[0051] Figure 2a is a schematic diagram of the structure of an electronic device provided in an embodiment of this application;

[0052] Figure 2b is a schematic diagram of the structure of an electronic device provided in an embodiment of this application;

[0053] Figure 3 is a partial structural schematic diagram of an electronic device provided in an embodiment of this application;

[0054] Figure 4a is a schematic diagram of the structure of a fluid amplifier for an electronic device provided in an embodiment of this application;

[0055] Figure 4b is a schematic diagram of the working principle of a fluid amplifier in an electronic device provided in an embodiment of this application;

[0056] Figure 5a is a schematic diagram of the structure of a heat dissipation system for an electronic device provided in an embodiment of this application;

[0057] Figure 5b is a schematic diagram illustrating the working principle of a heat dissipation system for an electronic device provided in an embodiment of this application;

[0058] Figure 6 is a partial structural schematic diagram of an electronic device provided in an embodiment of this application;

[0059] Figure 7a is a schematic diagram of the structure of a fluid amplifier for an electronic device provided in an embodiment of this application;

[0060] Figure 7b is a schematic diagram of the working principle of a fluid amplifier in an electronic device provided in an embodiment of this application;

[0061] Figure 8a is a schematic diagram of the structure of a heat dissipation system for an electronic device provided in an embodiment of this application;

[0062] Figure 8b is a schematic diagram illustrating the working principle of a heat dissipation system for an electronic device provided in an embodiment of this application;

[0063] Figure 9 is a schematic diagram of a fluid compression device provided in an embodiment of this application;

[0064] Figure 10a is an exploded view of a fluid compression device provided in an embodiment of this application;

[0065] Figure 10b is an exploded view of a fluid compression device provided in an embodiment of this application;

[0066] Figure 11a is a partial structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0067] Figure 11b is a partial structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0068] Figure 12a is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0069] Figure 12b is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0070] Figure 12c is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0071] Figure 13 is a schematic diagram of a fluid compression device provided in an embodiment of this application;

[0072] Figure 14a is an exploded view of a fluid compression device provided in an embodiment of this application;

[0073] Figure 14b is an exploded view of a fluid compression device provided in an embodiment of this application;

[0074] Figure 15a is a partial structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0075] Figure 15b is a partial structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0076] Figure 16a is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0077] Figure 16b is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0078] Figure 16c is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0079] Figure 16d is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0080] Figure 16e is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0081] Figure 16f is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0082] Figure 16g is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0083] Figure 17a is a partial structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0084] Figure 17b is a cross-sectional structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0085] Figure 17c is a cross-sectional structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0086] Figure 17d is a cross-sectional structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0087] Figure 18 is a schematic diagram of a fluid compression device provided in an embodiment of this application;

[0088] Figure 19a is an exploded view of a fluid compression device provided in an embodiment of this application;

[0089] Figure 19b is an exploded view of a fluid compression device provided in an embodiment of this application;

[0090] Figure 19c is a schematic diagram of the eccentric structure principle of a fluid compression device provided in an embodiment of this application;

[0091] Figure 20a is a cross-sectional structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0092] Figure 20b is a partial cross-sectional structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0093] Figure 21 is a partial structural schematic diagram of a fluid compression device provided in an embodiment of this application;

[0094] Figure 22a is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0095] Figure 22b is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0096] Figure 22c is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0097] Figure 22d is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0098] Figure 22e is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0099] Figure 22f is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0100] Figure 22g is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0101] Figure 22h is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0102] Figure 22i is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0103] Figure 22j is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0104] Figure 22k is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0105] Figure 221 is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0106] Figure 22m is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0107] Figure 23a is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0108] Figure 23b is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0109] Figure 23c is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0110] Figure 23d is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0111] Figure 23e is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0112] Figure 23f is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0113] Figure 23g is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0114] Figure 23h is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0115] Figure 23i is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0116] Figure 23j is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0117] Figure 23k is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0118] Figure 231 is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application;

[0119] Figure 23m is a schematic diagram of the working principle of a fluid compression device provided in an embodiment of this application.

[0120] Reference numerals: 00-Centrifugal fan; 001-Air inlet; 002-Air outlet; 01-Bottom shell; 02-Middle frame; 021-Frame; 022-Support plate; 03-Display module; 041-Cover; 042-Piezoelectric film; 043-Inlet valve; 044-Outlet valve; 10-Housing; 101-Side frame; 102-Bottom shell; 20-Display module; 30-Cooling system; 301-Fluorescent amplifier; 302-Gas compression structure; 303-Conduit; 304-Air guide; 401-Popularity plate; 402-Heat dissipation fins; 50-Audio equipment; 1-Fluid compression device; 11-Housing shell; 111-Base; 1111-Slide groove; 112-Top cover; 12-Rotor assembly; 121-Rotor; 1211-Counterweight cutout; 1212-Axial groove; 13-Drive assembly; 131-Drive magnet; 132-Drive coil; 133-Fixed shaft; 134-Bearing; 135-Coil bracket; 1351-Center sleeve; 1352-Bracket; 14-Control assembly; 141-Circuit board; 15-Pressure valve; 161-Modible slider; 162-Spring; 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; 3-Fluid compression device; 31-Housing; 311-Base; 312-Top cover; 32-Rotor assembly; 321-Rotor; 3211-Center gear ring; 3212- Annular groove; 3213-sealing strip; 3214-spring; 33-drive assembly; 331-drive magnet; 332, 332a, 332b-drive coil; 333-drive gear; 334-bearing; 335-planetary carrier; 3351-first shaft; 3352-second shaft. Detailed Implementation

[0121] 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.

[0122] As illustrated in Figure 1a, a 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 axial direction. The fan uses centrifugal force to throw air out circumferentially and discharge it radially from the air outlet 002. Applying this centrifugal fan 00 to an electronic device, as shown in Figure 1b, the electronic device includes a bottom shell 01, a middle frame 02, and a display module 03. The middle frame 02 specifically includes a side 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. The side frame 021 surrounds the bottom shell 01 and the support plate 022, thus forming a receiving space between the middle frame 02 and the bottom shell 01. The display module 03 is disposed on the side of the support plate 022 opposite to the bottom shell 01, and the support plate 022 provides support for the display module. The centrifugal fan 00 is housed within this receiving space, with its axial direction parallel to the thickness direction of the electronic device. When air enters and exits from the side of an electronic device, sufficient air intake space is required for the centrifugal fan 00. Along the thickness direction of the electronic device, an air intake gap G needs to be reserved between the centrifugal fan 00 and the base shell 01. This gap G is generally greater than or equal to 1.5mm. The presence of the air intake gap G increases the thickness of the electronic device, limiting its thinning. The thickness of the centrifugal fan 00 is generally between 3-5mm. The motor, blades, bearings, and other structures of the centrifugal fan 00 have certain thickness requirements. Reducing the thickness will lead to abnormal noise, increased noise, decreased bearing life, and decreased fan performance, affecting heat dissipation. Due to the size of the centrifugal fan 00, the distance between the air intake and exhaust positions of the electronic device is relatively short, which may cause hot air confluence, thus affecting heat dissipation efficiency. To avoid hot air confluence extending the air intake position to the base shell 01, the integrity and strength of the electronic device's casing would be affected. Furthermore, the centrifugal fan 00 has relatively low air pressure, placing high demands on the airflow design of the electronic device's cooling system, resulting in a more complex structure. The cooling system using a centrifugal fan 00 is an open-type air intake and exhaust system. Although the individual fan has a large airflow, due to factors such as the air duct design, the airflow at the outlet of the electronic device is relatively small, resulting in low utilization of the air source. Alternatively, as shown in Figure 1c, an air intake channel 011 can be formed in the opening of the bottom shell 01, allowing air to enter from the bottom of the electronic device and exit from the side. The centrifugal fan 00 rotates at high speed during operation. If the centrifugal fan 00 is too close to the bottom shell 01, pressing the bottom shell 01 will cause abnormal noise from the centrifugal fan 00. Therefore, a certain air intake gap G, approximately 0.5mm, still needs to be maintained between the centrifugal fan 00 and the bottom shell 01. Although this reduces the air intake gap G to some extent, the opening in the bottom shell 01 will compromise the integrity and strength of the bottom shell 01 and also affect the product's appearance.

[0123] Figures 1d and 1e illustrate a piezoelectric diaphragm pump, which includes a housing 041, a piezoelectric diaphragm 042, an inlet valve 043, and an outlet valve 044. This piezoelectric diaphragm pump utilizes the vibration of a piezoelectric element to agitate the piezoelectric diaphragm 042, thereby controlling the volume change of the pump chamber Q to draw in and expel gas. As shown in Figure 1d, when the piezoelectric diaphragm 042 moves upward, the volume of the pump chamber Q increases, and the gas pressure inside the pump chamber Q becomes lower than the external air pressure, causing the inlet valve 043 to open and allow air to enter. As shown in Figure 1e, when the piezoelectric diaphragm 042 moves downward, it compresses the gas inside the pump chamber Q, causing the outlet valve 044 to open and allow air to exit. In this design, the piezoelectric diaphragm 042 exhibits a high vibration frequency, small amplitude, and low noise. However, the amplitude of the piezoelectric element is in the micrometer range, making it difficult to cause significant changes in the piezoelectric diaphragm 042. This results in a small airflow rate, which is insufficient to meet the heat dissipation requirements of electronic equipment.

[0124] Based on this, embodiments of this application provide a fluid compression device and an electronic device. The heat dissipation system of the electronic device combines heat dissipation performance with a thin and light size, which can adapt to the development of thinner and lighter electronic products and high performance, bringing a better user experience to consumers.

[0125] To make the objectives, technical solutions, and advantages of this application clearer, the application will now be described in further detail with reference to the accompanying drawings.

[0126] The electronic devices provided in this application include, but are not limited to, consumer electronic products carried by consumers, such as mobile phones, tablets, laptops, wearable electronic devices, headphones, e-readers, etc., which can bring a more convenient and comfortable experience to consumers' lives. Figures 2a and 2b illustrate the structure of an electronic device using a tablet as an example. For ease of understanding, the X, Y, and Z directions are defined, where the Z direction is the thickness direction of the electronic device, the X direction is the length direction of the electronic device, and the Y direction is the width direction of the electronic device. As shown in Figures 2a and 2b, the electronic device includes a housing 10 and a display module 20. The display module 20 is assembled into the housing 10, and there is space between the display module 20 and the housing 10 for accommodating structural components such as circuit boards. The housing 10 includes a side frame 101 and a back shell 102, with the side frame 101 surrounding and connected to the back shell 102, and the two can be an integral structure. The air inlet K1 and air outlet K2 of the electronic device are provided on the side frame 101. Outside air can enter the electronic device through the air inlet K1, and the gas inside the electronic device can be discharged through the air outlet K2. For example, air inlet K1 and air outlet K2 are respectively located on different sides of the electronic device. Specifically, air inlet K1 is located on the side of the side frame 101 in the width direction, and air outlet K2 is located on the side of the side frame 101 in the length direction. There is a large distance between air inlet K1 and air outlet K2, which can reduce the impact of heat recirculation. Here, there are two air outlets K2 distributed along the length direction of the side frame 101. The airflow path from air inlet K1 to air outlet K2 can pass through more areas inside the electronic device as much as possible, achieving more comprehensive and uniform heat dissipation. The location of air inlet K1 and air outlet K2 on the side frame 101 can ensure the integrity and strength of the back cover 102.

[0127] Figure 3 shows a partial structure of the electronic device. The electronic device also includes a heat-conducting component 40 disposed within the housing 10. Specifically, the heat-conducting component 40 includes a heat spreader 401 and heat sink fins 402. The heat spreader 401 absorbs heat from heat sources such as the circuit board of the electronic device, and the heat sink fins 402 are arranged at the air outlet K2. The electronic device includes a cooling system 30 for providing airflow to the electronic device. The cooling system 30 can guide air from the air inlet K1 to the air outlet K2, thereby forming airflow within the electronic device. The movement of the airflow allows heat from the heat spreader 401 to be quickly transferred to the heat sink fins 402 and discharged through the air outlet K2, achieving heat dissipation and cooling of the electronic device. In some embodiments, the electronic device also includes devices such as an audio device 50.

[0128] Referring to Figure 3, 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.

[0129] Figure 4a shows the structure of a fluid amplifier 301. This fluid amplifier 301 has a relatively thin thickness, meaning its length-to-thickness ratio or width-to-thickness ratio is considered large. The fluid amplifier 301 has a hollow structure, including a main channel T1 and at least one slit channel T2. Here, the slit channel T2 is an example where the inlet is 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 side wall 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 the inlet and outlet of the main channel T1 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.

[0130] For example, the main channel T1 is hourglass-shaped, specifically referring to the gray area shown in Figure 4a. The dimension of the inlet t11 ​​of the main channel T1 along the X direction is smaller than the dimension of the outlet t12 of the main channel T1 along the X direction, and the dimension of the cross-section of the main channel T1 at any point along the Y direction along the X direction is smaller than the dimension of the outlet t12 of the main channel T1 along the X direction. The slit channel T2 is connected to the inner wall at the smallest cross-section of the main channel T1. Two slit channels T2 are provided, and the two slit channels T2 are symmetrically arranged on both sides of the main channel T1 along the X direction. It can be considered that the inlet of the main channel T1 and the inlet of the slit channel T2 are arranged alternately along the X direction on the same side of the fluid amplifier 301, and the arrangement of the slit channels T2 in the main channel T1 does not increase the thickness of the fluid amplifier 301. As can be seen from Figure 4a, the cross-section of the main channel T1 used for gas flow is larger than the cross-section of the slit channel T2 used for gas flow, and the gas capacity of the main channel T1 is larger than the gas capacity 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 the angle range can be between 0-90°. The radial dimension of the main channel T2 is between 0-3mm.

[0131] When the fluid amplifier 301 shown in Figure 4a is applied to the heat dissipation system 30 of an electronic device, the high-pressure gas from the gas compression structure 302 can enter the inlet t21 of the slit channel T2 and then enter the main channel T1 through the slit channel T2. The slit channel T2 is exemplarily designed as a radially varying structure; specifically, along the airflow direction, the radial dimension of the slit channel T2 decreases, further compressing the gas entering the slit channel T2 and increasing its pressure. Exemplarily, the extension direction of the slit channel T2 is straight, and the slit channel T2 is conical. The cross-section of the slit channel T2 perpendicular to the gas flow direction is, for example, rectangular, but it can also be oval, elliptical, polygonal, or other irregular shapes. It is understood that the shape of the slit channel T2 along its extension direction can also be other shapes, as long as the radial dimension of the inlet t21 is greater than the radial dimension of the outlet t22. Changing the shape and structure of the slit channel T2 alters the flow parameters of the airflow within the slit channel T2, allowing for adaptive structural adjustments to the slit channel T2 according to heat dissipation requirements.

[0132] Figure 4b illustrates the working principle of the fluid amplifier 301. The structure shown in Figure 4b is a cross-sectional structure obtained by cutting the fluid amplifier 301 along a direction perpendicular to Z. As shown in Figure 4b, when a small amount of high-pressure gas is introduced into the inlet t21 of the slit channel T2, the high-pressure gas enters the main channel T1 from the outlet t22 through the slit channel T2 and flows along the side wall of the main channel T1 towards the outlet direction of the main channel T1. According to the wall effect, a negative pressure region will be formed near the two opposite side walls of the main channel T1 along the X direction. The fluid amplifier 301 will draw a large amount of ambient air into the main channel T1 from the inlet t11 ​​and flow through the main channel T1 to the outlet t12. The high-pressure gas introduced into the main channel T1 by the slit channel T2 serves as a power source, which can drive the gas in the main channel T1 to form a high-pressure, high-speed airflow. Because the radial dimension of the main channel T1 is several to tens of times larger than that of the slit channel T2, the volume of gas discharged from the outlet T12 of the main channel T1 can be several to tens of times larger than the volume of high-pressure gas entering the main channel T2, thus forming a large airflow. By directing the outlet T12 of the main channel T1 of the fluid amplifier 301 toward the heat sink 402 of the electronic device, the airflow output from the main channel T1 can accelerate the heat exchange between the heat sink 402 and the external environment, improving heat dissipation efficiency.

[0133] Two slit channels T2 are provided on both sides of the main channel T1 along the X direction. When high-pressure gas enters the main channel T1 through the slit channels T2, a negative pressure area is formed on both sides of the main channel T1. In some embodiments, an annular air guide groove can also be provided in the main channel T1 to guide the high-pressure gas along the inner wall of the main channel T1 along the X direction to the middle position of the main channel T1, thereby forming a negative pressure area in the middle position of the main channel T1, further improving the intensity of ambient air suction. Of course, there can be more slit channels T2, so that at least one slit channel T2 is provided on each side of the main channel T1.

[0134] Figure 5a illustrates the structure of a heat dissipation system 30. A gas compression structure 302 delivers high-pressure gas to the slit channel T2 of a fluid amplifier 301 via a conduit 303. As shown in Figure 5a, the fluid amplifier 301 and the gas compression structure 302 are arranged at intervals along the Y-direction, with a certain space between them. The inlet of the main channel T1 and the inlet of the slit channel T2 are both located on the side of the fluid amplifier 301 facing the gas compression structure 302. 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 from the gas compression structure 302 is delivered to the two slit channels T2 respectively via two conduits 303. The two ends of the conduits 303 can be sealed and connected to the slit channels T2 and the gas compression structure 302 respectively to prevent high-pressure gas leakage and improve the utilization rate of the high-pressure gas. The conduit 303 is located within the gap between the fluid amplifier 301 and the gas compression structure 302. The dimension of the conduit 303 along the Z-direction is smaller than that of both the fluid amplifier 301 and the gas compression structure 302 along the Z-direction. This means that ambient air can bypass the conduit 303 and enter the main channel T1 without affecting the gas guidance of the main channel T1. When this heat dissipation system 30 is modularly applied in different electronic devices, the conduit 303 can be a telescopic tube or a flexible tube to facilitate adjustment of the gap between the fluid amplifier 301 and the gas compression structure 302. Here, the gas compression structure 302 can be a miniature air pump or a small piezoelectric fan. When a piezoelectric fan is selected, its thickness along the Z-direction should be less than 2.8 mm.

[0135] Figure 5b shows a schematic diagram of the structure of the electronic device using the two sets of heat dissipation systems 30 shown in Figure 5a. Two air inlets K1 are respectively provided on the short sides of the two opposing side frames 101 along the X direction of the housing 10, and one air inlet K2 is provided on the long side of one side frame 101 perpendicular to the Y direction. Along the Y direction, the distance between the sides where the air inlets K1 and K2 are located is greater than the distance between the side opposite the air inlet K1 and the air outlet K2, ensuring a large distance between the air inlets K1 and K2. Heat dissipation fins 402 are located inside the housing 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 frame 101 where the air outlet K2 is located covers both air outlets K2. A rectangular heat spreader 401 is disposed within the housing 10 along the Y-direction, with one end of its length contacting the heat dissipation fins 402. In practice, the heat spreader 401 and the heat dissipation fins 402 may have structural overlap or intersection. The heat spreader 401 can contact heat source structures such as circuit boards of electronic devices, thereby absorbing heat from these structures and rapidly dissipating and guiding it to the heat dissipation fins 402. Along the X-direction, the heat dissipation fins 402 fan out from the heat spreader 401, and the heat dissipation fins 402 and the heat spreader 401 can cooperate with the side frame 101 to form two spaces for housing the heat dissipation system 30. The fluid amplifier 301 of the heat dissipation system 30 is disposed adjacent to the heat dissipation fins 402 along the Y-direction. Along the Y-direction, a gas compression structure 302 is disposed on the side of the fluid amplifier 301 away from the heat dissipation fins 402, with an air intake space between them. The high-pressure gas outlet of the gas compression structure 302 is connected to the slit channel T2 of the fluid amplifier 301 via a 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.

[0136] Referring to Figure 5b, taking a heat dissipation system 30 as an example, when the gas compression structure 302 is working, it draws in a small amount of ambient air through the air inlet K1 and compresses it into high-pressure gas, which is then transported 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 towards the heat dissipation fins 402, forming a negative pressure area on both sides of the main channel T1. The main channel T1 draws in a large amount of ambient air through the air inlet K1 and transports it to the heat dissipation fins 402, quickly directing the heat from the heat dissipation fins 402 to the outside through the air outlet K2. The two heat dissipation systems 30 are symmetrically arranged on both sides of the heat spreader 401, enabling more uniform and comprehensive heat dissipation for electronic equipment and improving heat dissipation efficiency.

[0137] 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.

[0138] Figure 6 shows a partial structure of another electronic device provided in an embodiment of this application. The arrangement of the heat spreader 401, heat sink fins 402, and audio device 50 in the electronic device is similar to that in Figure 3, and will not be described again here. Along the X direction, a space for accommodating the heat dissipation system 30 is formed between the audio device 50 and the heat spreader 401. The electronic device includes two sets of heat dissipation systems 30, which are arranged symmetrically on both sides of the heat spreader 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. To avoid obstructing the audio device 50, the fluid amplifier 301 and the gas compression structure 302 are moved away from the heat sink 402 along the Y direction until the gas compression structure 302 and the audio device 50 are arranged adjacent to each other along the Y direction, maintaining a certain gap between the fluid amplifier 301 and the heat sink 402. A guide 304 is connected between the fluid amplifier 301 and the heat sink 402 along the Y direction to guide the airflow discharged from the fluid amplifier 301 to the heat sink 402. Specifically, the guide 304 can be a hollow structure with a channel to guide airflow from the fluid amplifier 301 to the heat sink 402. One end of this channel is connected to the air outlet 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 airflow utilization.

[0139] Figure 7a shows the structure of the fluid amplifier 301 in Figure 6. The fluid amplifier 301 has a relatively thin thickness, and can 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, the main channel T1 of the fluid amplifier 301 shown in Figure 7a has the same structure and distribution as the main channel T1 of the fluid amplifier 301 shown in Figure 4a. The slit channel T2 of the fluid amplifier 301 shown in Figure 7a has a similar structure but a different distribution than the slit channel T2 of the fluid amplifier 301 shown in Figure 4a. The main channel T1 extends through the fluid amplifier 301 along the Y direction, with the inlet and outlet of the main channel T1 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. Unlike the slit channel T2 of the fluid amplifier shown in Figure 4a, this slit channel T2 can be referred to as the second channel. The inlet t21 of this 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 minimum 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 arranged alternately on different sides of the fluid amplifier 301 along the X-direction, and the arrangement of the slit channels T2 in the main channel T1 does not increase the thickness of the fluid amplifier 301. As can be seen from Figure 7a, the cross-section of the main channel T1 used for gas flow is larger than that of the slit channel T2 used for gas flow, and the gas capacity of the main channel T1 is larger 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 0-3mm.

[0140] Figure 7b illustrates the working principle of the fluid amplifier 301. The structure shown in Figure 7b is a cross-sectional structure obtained by cutting the fluid amplifier 301 perpendicular to the Z direction. As shown in Figure 7b, when a small amount of high-pressure gas is introduced into the inlet t21 of the slit channel T2, the high-pressure gas enters the main channel T1 from the outlet t22 through the slit channel T2 and flows along the side wall of the main channel T1 towards the outlet t12. Due to the wall adhesion effect, a negative pressure region is formed near the left side wall of the main channel T1. The fluid amplifier 301 will draw a large amount of ambient air from the inlet t11 ​​of the main channel T1 into the main channel T1 and flow through the main channel T1 towards the outlet t12. The high-pressure gas introduced into the main channel T1 by the slit channel T2 serves as a power source, which can drive the gas in the main channel T1 to form a high-pressure, high-speed airflow. Because the radial dimension of the main channel T1 is several to tens of times larger than that of the slit channel T2, the volume of gas discharged from the outlet T12 of the main channel T1 can be several to tens of times larger than the volume of high-pressure gas entering the main channel T2, thus forming a large airflow. By directing the outlet T12 of the main channel T1 of the fluid amplifier 301 toward the heat sink 402 of the electronic device, the airflow output from the main channel T1 can accelerate the heat exchange between the heat sink 402 and the external environment, improving heat dissipation efficiency.

[0141] Figure 8a shows the structure of a heat dissipation system 30. A gas compression structure 302 is arranged adjacent to a fluid amplifier 301. The high-pressure gas discharged from the gas compression structure 302 can directly enter the slit channel T2 of the fluid amplifier 301, reducing intake resistance and increasing airflow. The guide member 304 is a funnel-shaped cylindrical structure, with a guide channel W formed inside for airflow guidance. Along the Y direction, one end of the guide channel W is connected to the outlet t12 side of the main channel T1 of the gas compression structure 302. Along the X direction, the dimension of the end of the guide channel W connected to the gas compression structure 302 is smaller than the dimension of the end of the guide channel W facing the heat dissipation fins 402.

[0142] Figure 8b shows a schematic diagram of the structure of two sets of heat dissipation systems 30 shown in Figure 8a for use in electronic devices. As shown in Figure 8b, the fluid amplifier 301 of the heat dissipation system 30 is spaced apart from the heat dissipation fins 402 along the Y direction, and the two are connected by a flow guide 304. Along the X direction, the gas compression structure 302 is located on the side of the fluid amplifier 301 away from the heat spreader 401 and is adjacent to it. The high-pressure gas outlet of the gas compression structure 302 is directly connected to the slit channel T2 of the fluid amplifier 301. Along the Y direction, the gas compression structure 302 is connected and arranged with the audio device 50. Along the X direction, the orthographic projection of the gas compression structure 302 on the side frame 101 overlaps with the air inlet K1. Taking one set of heat dissipation systems 30 as an example, when the gas compression structure 302 is working, it draws in a small amount of ambient air through the air inlet K1 and compresses it into high-pressure gas, which is then delivered to the slit channel T2 of the fluid amplifier 301. High-pressure gas enters the main channel T1 through the slit channel T2 and flows along the inner wall of one side of the main channel T1 in the X direction towards the heat dissipation fins 402, forming a negative pressure area on one side of the main channel T1. The main channel T1 draws in a large amount of ambient air through the air inlet K1 and delivers it to the heat dissipation fins 402 through the guide element 304, quickly directing the heat from the heat dissipation fins 402 to the outside through the air outlet K2. The two sets of heat dissipation systems 30 are symmetrically arranged on both sides of the heat spreader 401, enabling more uniform and comprehensive heat dissipation for the electronic equipment and improving heat dissipation efficiency. In the heat dissipation system of this electronic equipment, the gas compression structure 302, the fluid amplifier 301, and the guide element 304 can form a relatively closed air intake system between the air inlet K1 and the heat dissipation fins 402, which can improve the utilization rate of the air source air volume and enhance the air cooling effect of the electronic equipment.

[0143] It should be noted that in the electronic devices provided in this application embodiment, the two different slit channels T2 in the fluid amplifier 301 and the connection method between the slit channel T2 and the gas compression structure 302 can be used simultaneously in some applications with relatively large spaces. That is, if the space of the electronic device allows, the fluid amplifier 301 may include the slit channel T2 shown in FIG. 4a or the slit channel shown in FIG. 7a, and the heat dissipation system 30 can be configured with at least one suitable gas compression structure 302 for such fluid amplifier 301. Of course, the heat dissipation system 30 in the electronic devices provided in this application embodiment may also have other layout methods, and the structure can be adjusted according to different electronic devices, resulting in high layout flexibility.

[0144] In conjunction with the electronic device provided in the above embodiments, the heat dissipation system 30 of the electronic device needs to compress a portion of the air through a gas compression structure 302 to form high-pressure gas, which works in conjunction with the fluid amplifier 301 to achieve air cooling. To adapt to the thinner and lighter electronic device, the gas compression structure 302 also needs to have a thinner and lighter volume to facilitate adaptation to the heat dissipation system 30 of the aforementioned electronic device. Based on this, this application embodiment also provides a fluid compression device that can compress air into high-pressure gas and discharge it. This fluid compression device can be applied to the heat dissipation system 30 of the aforementioned electronic device, and can replace the gas compression structure 302 in the above embodiments.

[0145] The fluid compression device provided in this application embodiment achieves air compression by drawing in, compressing, and discharging gas through changes in the volume of an internal air chamber. As shown in Figure 9, a fluid compression device 1 includes a housing 11, a rotor assembly 12, and a drive unit. The housing 11 specifically includes a base 111 and a top cover 112. The base 111 and the top cover 112 can be fitted together along the thickness direction of the fluid compression device 1 to form the housing 11. The base 111 and the top cover 112 can be connected by screws or by adhesive. The rotor assembly 12 and the drive unit can be integrated within the housing 11. The drive unit includes at least one drive component 13, which, exemplarily, drives the rotor assembly 12 to rotate.

[0146] Figures 10a and 10b are exploded views of the fluid compression device 1. Referring to Figures 10a and 10b, the fluid compression device 1 specifically includes a housing 11, a rotor assembly 12, and a drive assembly 13. A groove A is provided on the side of the base 111 facing the top cover 112. After the base 111 mates with the top cover 112, the groove A and the top cover 112 form an inner cavity of the housing 11. The groove A includes 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 drive assembly 13 can be accommodated within the inner cavity of the housing 11. The rotor assembly 12 includes at least one rotor 121, exemplified here as a cam. The rotation axis of the rotor 121 is shown as a dashed line, and the rotor 121 can rotate about the rotation axis, which passes through the axis of rotation of the groove A. The rotor 121 includes a cam surface surrounding the rotation axis. The rotor 121 has a counterweight cutout 1211, such that the center of the cam coincides with the rotation axis of the rotor 121. Specifically, the counterweight cutout 1211 is located between the rotation axis of the rotor 121 and the radially furthest end of the cam surface. The distance between the radially furthest end of the cam surface and the rotation axis of the rotor 121 is greater than the distance between other locations on the cam surface and the rotation axis of the rotor 121. Each drive assembly 13 drives one rotor 121 to rotate about its rotation axis. Exemplarily, each drive assembly 13 includes an annular drive magnet 131, a plurality of drive coils 132, a fixed shaft 133, a bearing 134, and a coil holder 135. A drive magnet 131 is coaxially fixed to the rotor 121, and a fixed shaft 133 is fixed to the base 111 of the housing 11. The coil support 135 includes a central sleeve 1351 and multiple supports 1352. The central sleeve 1351 is coaxially fixed to the outer ring of the bearing 134. The multiple supports 1352 are spaced apart around the rotation axis of the rotor 121 and fixed to the outer circumferential surface of the central sleeve 1351. Each support 1352 extends radially along the rotor 121, and at least one drive coil 132 is wound on each support 1352, so that the multiple drive coils 132 can be spaced apart around the rotation axis of the rotor 121, thereby forming a magnetic field for driving the drive magnet 131 to rotate around the rotation axis of the rotor 121.

[0147] To control the drive unit 13, the fluid compression device 1 also includes a control component 14. Specifically, the control component 14 may include a circuit board 141, which is fixed to the base 111 and electrically connected to each drive coil 132. The circuit board 141 may integrate a control chip, which can control the magnitude and direction of the current flowing through the drive coil 132. Alternatively, the control component 14 may also include a control chip external to the housing 11. The circuit board 141 can act as an adapter to connect the drive coil 132 to an external control chip, which then controls the magnitude and direction of the current flowing through the drive coil 132. Furthermore, the fluid compression device 1 also includes a pressure valve 15, which controls the air output of the fluid compression device 1. A movable slider 161 is provided between the base 111 of the outer casing 11 and the rotor 121. The base 111 includes a groove 1111 with an opening located on the circumferential inner wall a1. Along the direction perpendicular to the rotation axis of the rotor 121, one end of the movable slider 161 is used to extend into the groove 1111 and slide in cooperation with the groove 1111. The other end of the movable slider 161 protrudes from the circumferential inner wall a1 and extends into the groove A. Exemplarily, one end of the movable slider 161 located in the groove 1111 is connected to the base 111 by a spring 162. As shown in FIG10b, an axial groove 1212 is formed on the side of the rotor 121 facing the base 111. After the rotor 121 and the base 111 are engaged, the axial groove 1212 can form a space between the axial groove 1212 and the groove A of the base 111 that can accommodate the drive magnet 131, multiple drive coils 132, fixed shaft 133, bearing 134, and coil support 135.

[0148] Figure 11a shows a partial structural schematic diagram of the fluid compression device 1, omitting the top cover 112 of the outer casing 11. As shown in Figure 11a, the outer ring of the bearing 134 is fixed to the base 111, and the coil support 135 is fixed to the base 111 via the outer ring of the bearing 134. The inner ring of the bearing 134 is coaxially fixed to the fixed shaft 133, the axis of the fixed shaft 133 is collinear with the rotation axis of the rotor 121, and the axis of the drive magnet 131 is collinear with the rotation axis of the rotor 121. The drive magnet 131 surrounds the coil support 135 and does not contact the coil support 135. Each drive coil 132 and the drive magnet 131 are adjacent to each other but not in contact along the thickness direction perpendicular to the fluid compression device 1, which saves space in the thickness direction of the fluid compression device 1. When the drive magnet 131 is driven by the magnetic field formed by the multiple drive coils 132 to rotate around the rotation axis of the rotor 121, the drive magnet 131 rotates around the rotation axis of the rotor 121, thereby driving the 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 that communicate 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. Pressure valve 15 is located at air outlet c. As shown in Figure 11a, air inlet j and air outlet c of outer casing 11 are respectively located on both sides of movable slider 161 along the circumference of base 111. Air inlet j can be normally open, and air outlet c can be controlled to open and close by pressure valve 15.

[0149] 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 a groove A of the base 111 and protrudes from the bottom wall a2. When the rotor 121 is assembled onto the base 111, the structure shown in Figure 11b is obtained. As shown in Figure 11b, the rotor 121 is housed within the groove A, and the drive magnet 131 is integrated into the rotor 121. The space between the rotor 121 and the bottom wall a2 of the base 111 can accommodate multiple drive coils 132, the fixed shaft 133, the bearing 134, the coil support 135, and the circuit board 141.

[0150] Referring to Figure 11b, the distance between the nearest radial end of the cam surface of rotor 121 and the rotation axis is r1, and the distance between the farthest radial end of the cam surface of 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 farthest radial end of the cam surface of rotor 121 can contact the circumferential inner wall a1. An air chamber can be formed between the cam surface of rotor 121 and the circumferential inner wall a1 of base 111, and between the base 111 and the top cover 112 of the housing 11. One end of the movable slider 161 located in the slide groove 1111 is connected to the base 111 by a spring 162. The other end of the movable slider 161 protrudes from the circumferential inner wall a1 and abuts against the cam surface of rotor 121. The movable slider 161 can divide the air chamber into a first chamber R1 and a second chamber R2. The air inlet j communicates with the first chamber R1, and the air outlet c communicates with the second chamber R2. For ease of understanding, the spaces of the first chamber R1 and the second chamber R2 are shown with different shades. The spring 162, under compression and possessing elastic potential energy, provides a preload force for the movable slider 161 to abut 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 furthest end of the cam surface of the rotor 121 and the axial inner wall a1, is sealed, ensuring the sealing effect of the first chamber R1 and the second chamber R2. It should be noted that when the radially furthest 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 close to 0, while the volume of the other can be considered equivalent to the space between the cam surface of the rotor 121 and the circumferential inner wall a1.

[0151] When the drive unit 13 drives the rotor 121 to rotate around the rotation axis, the radially furthest end of the cam surface of the rotor 121 will slide along the axial inner wall a1, thereby changing the volume of the first chamber R1 and the second chamber R2, realizing air intake and exhaust, and compressing the gas during the rotation of the rotor 121, and finally discharging high-pressure gas. As shown in Figures 12a to 12c, the initial position of the rotor 121 is set as shown in Figure 11a, at which time the volume of the first chamber R1 is smaller than the volume 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 Figure 12a to the position shown in Figure 11b, the volume of the first chamber R1 increases, and the first chamber R1 can draw in air through the air inlet j. The volume of the second chamber R2 decreases, and the gas in the first chamber R2 is compressed. During the clockwise rotation of rotor 121 from the position shown in Figure 12b to the position shown in Figure 12c, the volume of the first chamber R1 further increases, approaching the space between the cam surface of rotor 121 and the circumferential inner wall a1. The volume of the second chamber R2 further decreases to near its minimum value, and the gas pressure in the second chamber R2 is high enough to activate pressure valve 15 to open and discharge high-pressure gas from outlet c.

[0152] It should be noted that the timing of the exhaust from the fluid compression device 1 can be controlled by the pressure valve 15. When the gas pressure in the second chamber R2 is insufficient, the pressure valve 15 is closed. As the volume of the second chamber R2 decreases, the gas pressure inside the second chamber R2 increases to the point that the pressure valve 15 opens, allowing the high-pressure gas in the second chamber R2 to be discharged through the outlet c. Alternatively, the pressure valve 15 can be omitted, and the radial dimension of the outlet c can be reduced. In this case, the outlet c can be normally open, and the amount of gas discharged from the second chamber R2 through the outlet c is very small. As the gas pressure in the second chamber R2 increases, only a small amount of gas will be discharged from the outlet c. When the gas pressure in the second chamber R2 is sufficiently high, the high-pressure gas is rapidly discharged through the outlet c. When the fluid compression device 1 is applied to the heat dissipation system 30 of electronic equipment, the outlet c can work with the slit channel T2 of the fluid amplifier 301 to further compress the discharged gas, so that the airflow that finally enters the main channel T1 has a high pressure and velocity, thereby driving a large amount of ambient air to form an airflow that blows toward the heat dissipation fins 402, thereby achieving heat dissipation for electronic equipment.

[0153] As shown in Figure 13, a fluid compression device 2 includes a housing 21, a rotor assembly 22, and a drive unit. The drive unit includes at least one drive component 23. The housing 21 includes a base 211 and a top cover 212, which are connected and fixed along the thickness of the fluid compression device 2. The rotor assembly 22 and the drive unit can be accommodated within the housing 21. The housing 21 is racetrack-shaped, with arc-shaped ends along its length and parallel sides along its width. The rotor assembly 22 includes two rotors 221, whose rotation axes are parallel to the thickness direction of the fluid compression device 2. The two rotors 221 are arranged adjacent to each other along the length of the housing 21. Exemplarily, each rotor 221 can be configured with one drive component 23.

[0154] Figures 14a and 14b illustrate exploded views of the fluid compression device 2. Referring also to Figures 14a and 14b, the fluid compression device 1 specifically includes a housing 21, two rotor assemblies 22, and two drive assemblies 23, each rotor assembly 22 being driven by one drive assembly 23. The base 211 has a groove B on the side facing the top cover 212. After the base 211 mates with the top cover 212, the groove B and the top cover 212 form an inner cavity of the housing 21. The groove B includes a bottom wall b2 and a circumferential inner wall b1. The bottom wall b2 is racetrack-shaped, or can be considered oblong, and the circumferential inner wall b1 surrounds the edge of the bottom wall b2. To make the fit between the top cover 212 and the base 211 tighter, the housing 21 may also include a sealing ring 25 disposed between the top cover 212 and the base 211. When the top cover 212 and the base 211 are fixed together along the thickness direction of the fluid compression device 2, the sealing ring 25 is held between the base 211 and the top cover 212 around the groove B. The rotor assembly 22 includes two rotors 221, each exemplified as two identical impellers. Each rotor 221 includes an impeller surface surrounding a rotation shaft, and each rotor 221 is driven by a set of drive assemblies 23. Exemplarily, each drive assembly 23 includes an annular drive magnet 231, multiple drive coils 232, a fixed shaft 233, a bearing 234, and a coil holder 235. The structure of the drive assembly 23 here is similar to that of the drive assembly 13 in the fluid compression device 2 shown in Figures 11a and 11b, and will not be described again here. Of course, the fluid compression device 2 also includes a control assembly 24 for controlling the two sets of drive assemblies 23, each control assembly 24 including a circuit board 241. Between a set of corresponding circuit boards 241, drive assembly 23, and rotor 221, an axial groove 2211 is formed on the side of rotor 221 facing base 211. After rotor 221 and base 211 are engaged, the axial groove 2211 and the groove B of base 211 form a space that can accommodate drive magnet 231, multiple drive coils 232, fixed shaft 233, bearing 234, and coil support 235. Along the width direction of base 211 of housing 21, base 211 includes an air inlet j and an air outlet c communicating with the circumferential inner wall a1. Air inlet j and air outlet c are normally open. The inner diameter of air inlet j is larger than the inner diameter of air outlet c.

[0155] Figure 15a shows a partial structural schematic of the fluid compression device 2, omitting the top cover 212 of the outer casing 21. As shown in Figure 15a, taking a corresponding set of circuit boards 241, drive assembly 23, and rotor 221 as an example: The outer ring of the bearing 234 is fixed to the base 211, and the coil support 235 is fixed to the base 211 via the outer ring of the bearing 234. The inner ring of the bearing 234 is coaxially fixed to the fixed shaft 233, the axis of the fixed shaft 233 is collinear with the rotation axis of the rotor 221, and the axis of the drive magnet 231 is collinear with the rotation axis of the rotor 221. The drive magnet 231 surrounds the coil support 235 and does not contact the coil 235. When the drive magnet 231 is driven by the magnetic field formed by multiple drive coils 232 to rotate around the rotation axis of the rotor 221, the drive magnet 231 rotates around the rotation axis of the rotor 221, thereby driving the 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, as do multiple drive coils 232, coil support 235, outer ring of bearing 234, and base 211. When rotor 221 is assembled onto base 211, the structure shown in Figure 15b is obtained. Rotor 221 is accommodated in groove A, and drive magnet 231 is integrated into rotor 221. The space between rotor 221 and bottom wall b2 of base 211 can accommodate multiple drive coils 232, fixed shaft 233, bearing 234, coil support 235, and circuit board 241.

[0156] The assembly structure of each drive assembly 23 and rotor 221 shown in Figures 15a and 15b is similar to the assembly structure of drive assembly 13 and rotor 121 shown in Figures 11a and 11b. The difference lies in the structure of the rotor, the way rotor 221 is fitted with housing 21, the structure of rotor 121, and the way rotor 121 is fitted with housing 11.

[0157] Referring to Figures 15a and 15b, two impeller-shaped rotors 221 are respectively mounted in the 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 is used to contact 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 communicates with the air inlet j, and the second chamber R2 communicates 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. In addition, when two adjacent convex surfaces m1 of each rotor 221 contact 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.

[0158] 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.

[0159] Figures 16a to 16g illustrate the operation of the fluid compression device 2. To facilitate understanding of the rotation of the two rotors 221, a gray arrow is marked on one of the blades of each rotor 221, corresponding to that blade. The initial position of the rotors 221 is shown in Figure 16a. A portion of the impeller surface of the left rotor 221 and a portion of the impeller surface of the right rotor 221, in conjunction with the base 211, form the first chamber R1. Another portion of the impeller surface of the left rotor 221, in conjunction with another portion of the impeller surface of the right rotor 221, forms the second chamber R2. As the left rotor 221 rotates counterclockwise and the right rotor 221 rotates clockwise to the position shown in Figure 16b, the volume of the first chamber R1 further increases, thereby drawing in air through the inlet j as indicated by the arrow. As the two rotors 221 continue to rotate synchronously in opposite directions as shown in Figure 16b, through Figures 16c, 16d, 16e, 16f, and 16g, the gas in the first chamber R1 is carried by the two rotors 221 to the chamber between the outer circumference of each rotor 221 and the base 211, as indicated by the arrows, and finally transferred to the second chamber R2 shown in Figure 16g and compressed, and discharged as high-pressure gas through the outlet c.

[0160] The fluid compression device 2 provided in this embodiment requires the two rotors 221 to maintain synchronous movement; otherwise, there is a risk of jamming. Two drive components 23 can drive the two rotors 221 to rotate separately. Angle detection devices can be configured on the two control components 24 to detect the angles of the two rotors 221 and determine their meshing state. These angle detection devices include, but are not limited to, one or more of Hall effect sensors, eddy current encoders, magnetic encoders, and photoelectric sensors. Two angle detection devices can be used, each detecting the rotation angle of the two rotors 221. Based on this angle data, it can be determined whether the two rotors 221 are synchronized. If they are not synchronized, the control component 24 can adjust the current supplied to the drive coils 232 in the two drive components 23 to change the magnetic field, thereby changing the rotation of the drive magnet 231 to drive the rotors 221 and achieve adjustment of the rotors 221. Alternatively, the drive components 23 corresponding to the two rotors 221 can also be controlled by the same control component 24.

[0161] The Hall sensor can be either an analog Hall sensor or a digital Hall sensor. Taking an angle detection device including an analog Hall sensor 28 as an example, as shown in Figure 17a, each rotor 221 is equipped with a set of angle detection devices consisting of two analog Hall sensors 28, which are arranged opposite each other 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 drive magnet 231 and the circuit board 41, which is indicated by a dashed line.

[0162] The fluid compression device 2 is sectioned by a plane VV parallel to the rotation axis of rotor 221 in Figure 17a, resulting in the cross-sectional structure shown in Figure 17b. As shown in Figure 17b, along the thickness direction of the fluid compression device 2, the circuit board 241 is fixed to the base 211, with a certain gap between the circuit board 241 and the rotor 221. An analog Hall sensor 28 can be integrated on the surface of the circuit board 241 facing the rotor 221, with the analog Hall sensor 28 facing the drive magnet 231 along the thickness direction of the fluid compression device 2. When multiple drive coils 232 are energized, the magnetic field generated by the drive coils 232 drives the drive magnet 231 to rotate around the fixed axis 233, thus rotating the rotor 221. Two analog Hall sensors 28 can monitor changes in the magnetic field, and the rotation angle of the rotor 221 can be calculated based on this information. The circuit board 241 provides support for the analog Hall sensors 28. When the circuit board 241 integrates a control chip, it can directly receive the data detected by the analog Hall sensors 28 and analyze it to obtain the rotation angle of the rotor 221. By comparing the rotation angles of the two rotors 221, the current of the drive coils 232 corresponding to the two rotors 221 is adjusted to regulate the rotation angle of the rotors 221. Alternatively, the circuit board 241 acts as an intermediate adapter board to transmit the electrical signal from the analog Hall sensor 28 to an external control chip.

[0163] In some embodiments, if digital Hall sensors are selected, three digital Hall sensors can be provided for each rotor 221. The three digital Hall sensors are evenly distributed along the circumference of the rotor 221, and any two digital Hall sensors are at a 120° angle to each other. Along the thickness direction of the fluid compression device 2, the digital Hall sensors are also integrated on the surface of the circuit board 241 facing the rotor 221 and opposite to the drive magnet 231, similar to the illustration in Figure 17b.

[0164] Alternatively, in some embodiments as shown in Figure 17c, a first magnet 261 is provided on the impeller protrusion of one rotor 221, and a second magnet 262 is provided on the impeller protrusion of the other rotor 221. The first magnet 261 and the second magnet 262 have the same magnetism. Under the drive of the drive assembly 23, the synchronous rotation of the two rotors 221 is achieved by utilizing the principle of like poles repelling each other.

[0165] Alternatively, in some embodiments as shown in Figure 17d, a magnetic coil 27 is provided on the impeller protrusion of one rotor 221, while 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 synchronize them.

[0166] 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.

[0167] As shown in Figure 18, a fluid compression device 3 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.

[0168] Figures 19a and 19b are exploded views of the fluid compression device 3 described above. As shown in Figures 19a and 19b, the base 311 has a groove D on the side facing the top cover 312. After the base 311 and the top cover 312 are fitted together, the groove D and the top cover 312 form the inner cavity of the outer shell 31. The groove D includes a bottom wall d2 and a circumferential inner wall d1, with the circumferential inner wall d1 surrounding the edge of the bottom wall d2. The base 311 also includes a first air inlet j1, a second air inlet j2, a first air outlet c1, and a second air outlet c2 that communicate with the inner cavity of the outer shell 31. Specifically, the first air inlet j1, the second air inlet j2, the first air outlet c1, and the second air outlet c2 penetrate the base 311 along a direction perpendicular to the thickness of the fluid compression device 3 and communicate with the circumferential inner wall d1. The base 311 is racetrack-shaped, with arc-shaped ends in the length direction and parallel ends in the width direction. The first air inlet j1 and the second air outlet c2 are located on one side of the width direction of the base 311, and the second air inlet j2 and the first air outlet c1 are located on the other side of the width direction of the base 311. 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 housed within the inner cavity of the housing 31. The rotor assembly 32 includes a rotor 321, which is shaped like a Reichstag triangle, having three vertices and three circumferential sidewalls, with a circumferential sidewall between any two vertices. Each vertices of the rotor 321 is used to contact the circumferential inner wall d1 of the base 311. To enhance the sealing between the apex of the rotor 321 and the circumferential inner wall d1, a slit f can be provided at each apex, and a sealing strip 3213 is embedded in each slit f. The sealing strip 3213 can be pre-set within the slit f at the apex of the rotor 321 by a spring 3214. The spring 3214 provides a certain pre-tightening force to the sealing strip 3213, ensuring that the sealing strip 3213 remains in contact with the circumferential inner wall d1 and maintains a seal when the rotor 321 engages with it. The side of the rotor 321 facing the base 311 has a central gear ring 3211 coaxial with the rotor 321's rotation axis. The side of the rotor 321 facing the top cover 312 has an annular groove 3212 coaxial with the rotor 321's rotation axis. The drive assembly 33 is used to drive the rotor 321 to rotate around its rotation axis. Exemplarily, the drive assembly 33 includes an annular drive magnet 331, multiple drive coils 332, a drive gear 333, a bearing 334, and a planetary carrier 335. The drive magnet 331 is coaxially fixed to the rotor 321, specifically embedded in the annular groove 3212 of the rotor 321. The multiple drive coils 332 are fixed to the base 311 around the groove D, and the multiple drive coils 332 are spaced apart around the rotation axis of the rotor 321, thereby forming a magnetic field for driving the drive magnet 331 to rotate around the rotation axis of the rotor 321. The drive gear 333 is fixed to the base 311 of the housing 31, and the drive gear 333 meshes with the central gear ring 3211 of the rotor 321.The planetary carrier 335 has a first rotating shaft 3351 and a second rotating shaft 3352. The centerlines of the first rotating shaft 3351 and the second rotating shaft 3352 are parallel to the rotation axis of the rotor 321, respectively, and the first rotating shaft 3351 and the second rotating shaft 3352 are offset in a direction perpendicular to the rotation axis of the rotor 321. The first rotating shaft 3351 is used to be coaxially rotatably connected to the drive gear 333 via a bearing 334, and the second rotating shaft 3352 is coaxially rotatably connected to the rotor 321. The structural principle of the connection between the rotor 321 and the drive gear 333 in this fluid compression device 3 via the planetary carrier 335 can be seen with reference to Figure 19c, where the dashed line represents the rotation axis of the rotor 321, which is eccentric relative to the centerline of the drive gear 333. When the rotor 321 rotates relative to the drive gear 333 around its rotation axis, the rotor 321 can rotate around the centerline of the drive gear 333 in conjunction with the planetary 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.

[0169] Figure 20a illustrates a cross-sectional structure of the fluid compression device 3, passing through the axis of the drive gear 333 and one apex and one circumferential sidewall of the rotor 321. As shown in Figure 17a, the drive gear 333 is embedded and fixed in the base 311. The first shaft 3351 of the planetary carrier 335 is rotatably connected to the center of the drive gear 333 via a bearing 334. The second shaft 3352 of the planetary carrier 335 is rotatably connected to the center of the rotor 321, and the axis of the second shaft 3352 is collinear with the rotation axis of the rotor 321. The central gear ring 3211 of the rotor 321 meshes with the drive gear 333. The drive magnet 331 is coaxially fixed in the annular groove 3212 of the rotor 321.

[0170] Figure 20b illustrates a partial cross-sectional structure of the fluid compression device 3, which is cut in half perpendicular to the rotation axis of the rotor 321. Taking the state shown in Figure 20b as an example, this cross-sectional structure represents the right half of the fluid compression device 3. The drive gear 333 is eccentrically connected to the rotor 321 via a planetary carrier 335, and meshes with the central gear ring 3211 of the rotor 321. The magnetic field formed by multiple drive coils 332 drives the drive magnet 331 to rotate the rotor 321 around the rotation axis. Simultaneously, the rotor 321 rotates around the axis of the drive gear 333, ultimately allowing the rotor 321 to rotate within the inner cavity of the housing 31, with the three apex angles of the rotor 321 always in contact with the circumferential inner wall d1 of the base 311. Referring to Figures 17a and 17b, the drive assembly 33 can be integrated into the housing 31 and the rotor 321, reducing the thickness of the fluid compression device 3.

[0171] Figure 21 shows a partial structural schematic diagram 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 the first chamber R1, the second chamber R2, and the 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, as shown in Figures 17a and 17b. 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 causing the rotor 321 to rotate. Each drive coil 332 can have a different magnitude and direction of current. The magnitude and direction of the current flowing through each drive coil 332 can be adjusted according to the state of the rotor 321, allowing the changing magnetic field formed by the multiple drive coils 332 to drive the drive magnet 331 to rotate in a predetermined direction and speed. For example, taking the apex of the rotor 321 marked with an arrow in Figure 21 as an example, there are drive coils 332a and 332b on either side of this apex. Currents flowing through drive coils 332a and 332b in different directions cause 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 the drive magnet 331, 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.

[0172] As shown in Figures 22a to 22m, during one revolution of the rotor 321 around the rotation axis, based on the shape of the circumferential inner wall d1 of the base 311, the volume of the chamber formed between each circumferential side wall and the circumferential inner wall b1 of the rotor 321 changes, thereby realizing the intake and exhaust of the fluid compression device 3. During the rotation of the rotor 321, the intake gas can also be compressed, and finally high-pressure gas is discharged.

[0173] The initial position of rotor 321 is set as shown in Figure 22a. At this time, one apex of rotor 321 contacts the circumferential inner wall d1 between the first air inlet j1 and the second air outlet c2. For ease of understanding, an arrow is marked at this apex of rotor 321. The position of the arrow is fixed relative to rotor 321 and rotates with rotor 321. Further defined, the space between the circumferential sidewall to the right of this apex and the circumferential inner wall d1 is the first chamber R1, the space between the circumferential sidewall to the left of this apex and the circumferential inner wall d1 is the third chamber R3, and the space between the circumferential sidewall opposite to this apex and the circumferential inner wall d1 is the second chamber R2. The first chamber R1 is connected to the first air inlet j1, the second chamber R2 is connected to the second air inlet j2 and the first air outlet c1, and the third chamber R3 is connected to the second air outlet c2. The intermediate states of rotor 321 rotating clockwise one revolution in the direction indicated by the thick arrow can be seen in Figures 22b to 22m. It can be observed that the volume of the three chambers changes during the rotation of rotor 321, and air is drawn in and exhausted through two inlets and two outlets. The discharged gas is high-pressure gas obtained by compressing the chambers as their volumes decrease. For ease of understanding, the direction of airflow is indicated by dashed arrows.

[0174] It should be understood that during operation, the rotor 321 of the fluid compression device 3 undergoes a continuous cyclic rotation process, which can be considered as the rotor 321 cyclically moving in the states shown in Figures 22a to 22m. During the rotation of the rotor 321, the intake and exhaust processes of each chamber are not synchronized. Therefore, the intake and exhaust processes of the three chambers are illustrated here as examples of approximately complete processes.

[0175] Taking the first chamber R1 as an example, during the clockwise rotation of the rotor 321 around the rotation axis, passing through the states shown in Figures 22l, 22m, 22a, 22b, 22c, 22d, and 22e, 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, the first chamber R1 can draw in air from the first air inlet j1. When the volume of the first chamber R1 decreases, the gas in the first chamber R1 is compressed into high-pressure gas and finally discharged from the first air outlet c1. During the clockwise rotation of the rotor 321 around the rotation axis, passing through the states shown in Figures 22f, 22g, 22h, 22i, 22j, and 22k, 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, the first chamber R1 can draw in air from the second air inlet j2. When the volume of the first chamber R1 decreases, the gas inside the first chamber R1 is compressed into high-pressure gas and finally discharged from the second outlet c2. During one rotation of the rotor 321, the first chamber R1 can achieve two intake and exhaust cycles.

[0176] Taking the second chamber R2 as an example, during the clockwise rotation of the rotor 321 around the rotation axis, passing through the states shown in Figures 22a, 22b, 22c, 22d, 22e, 22f, and 22g, 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 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. During the clockwise rotation of the rotor 321 around the rotation axis, passing through the states shown in Figures 22h, 22i, 22g, 22k, 22l, and 22m, 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 the second chamber R2 is compressed into high-pressure gas and eventually discharged from the first outlet c1. During one rotation of the rotor 321, the second chamber R2 can achieve two intake and exhaust cycles.

[0177] Taking the third chamber R3 as an example, during the clockwise rotation of the rotor 321 around the rotation axis, passing through the states shown in Figures 22d, 22e, 22f, 22g, 22h, and 22i, 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, air is drawn in through the first air 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 air outlet c1. During the clockwise rotation of the rotor 321 around the rotation axis, passing through the states shown in Figures 22j, 22k, 22l, 22m, 22a, 22b, and 22c, 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, the third chamber R3 can draw in air through the second air 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 from the second outlet c2. During one rotation of the rotor 321, the third chamber R3 can achieve two intake and exhaust cycles.

[0178] Figures 23a to 23m illustrate the relative motion between the rotor 321 and the drive wheel 333 during one clockwise rotation of the rotor 321 around the rotation axis. For clarity, Figures 23a to 23m are shown in cross-section along the thickness direction perpendicular to the fluid compression device 3, revealing the connection relationship between the rotor 321, the planetary gear 335, and the drive wheel 333.

[0179] In particular, Figure 23a corresponds to the state shown in Figure 22a, Figure 23b corresponds to the state shown in Figure 22b, Figure 23c corresponds to the state shown in Figure 22c, Figure 23d corresponds to the state shown in Figure 22d, Figure 23e corresponds to the state shown in Figure 22e, Figure 23f corresponds to the state shown in Figure 22f, Figure 23g corresponds to the state shown in Figure 22g, Figure 23h corresponds to the state shown in Figure 22h, Figure 23i corresponds to the state shown in Figure 22i, Figure 23j corresponds to the state shown in Figure 22j, Figure 23k corresponds to the state shown in Figure 22k, Figure 23l corresponds to the state shown in Figure 22l, and Figure 23m corresponds to the state shown in Figure 22m.

[0180] Referring to Figures 23a to 23m, o1 represents the position of the axis of the driving gear 333, and o2 represents the position of the rotation axis of the rotor 321. During one revolution of the rotor 321 relative to the circumferential inner wall d1 of the base 311, the rotation axis of the rotor 321 rotates one revolution relative to the axis of the driving gear 333, and the central gear ring 3211 of the rotor 321 meshes with the driving gear 333 and rotates one revolution, ultimately achieving the eccentric motion of the rotor 321 and the driving gear 333. Throughout the entire rotation of the rotor 321, the three apexes of the rotor 321 remain in contact with the circumferential inner wall d1 of the base 311.

[0181] The fluid compression device 3 provided in this embodiment of the application allows the three chambers to achieve two intake and exhaust cycles per revolution of the rotor 321, resulting in higher working efficiency. The two inlets and two outlets of this fluid compression device 3 do not require valves and can achieve stable pulsating flow output, making the structure more stable and reliable. The rotation of the rotor 321 is achieved through the attractive or repulsive forces between multiple drive coils 332 and drive magnets 331. Specifically, different currents can be applied to different drive coils 332 to change the magnetic attraction or repulsion, resulting in a smaller thickness dimension for the fluid compression device 3.

[0182] In summary, the three fluid compression devices provided in this application can all form at least two chambers through the cooperation of the rotor and the inner cavity of the housing. During the rotation of the rotor around its own rotation axis, each chamber can achieve air intake and exhaust. Furthermore, during rotor rotation, the volume of the chamber decreases due to the cooperation between the outer circumferential surface of the rotor and the circumferential inner wall of the housing, thereby compressing the gas and ultimately discharging high-pressure gas. The drive units of these three fluid compression devices can all be integrated into the housing and rotor, resulting in a smaller thickness for the fluid compression device. All three fluid compression devices can be applied to the heat dissipation system 30 of the electronic device shown in Figures 3 and 6 to provide high-pressure gas to the fluid amplifier 301, contributing to the reduction of the electronic device's thickness and adapting to the miniaturization development of electronic devices. The fluid compression devices provided in the above embodiments can also be used to compress liquids. When the fluid compression device is applied to compress liquids, the air inlet j can be used for liquid intake, and the air outlet c can be used for liquid discharge; the air inlet j can be called the liquid inlet, and the air outlet c can be called the liquid outlet.

[0183] The above are merely specific embodiments of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. An electronic device, comprising: The electronic device comprises a shell, 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 generated by the 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; The heat dissipation system comprises a fluid amplifier and a gas compression structure arranged adjacent to each other along the thickness direction perpendicular to the electronic device; the fluid amplifier comprises a main channel and at least one slit channel, 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 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.

2. The electronic device of claim 1, wherein, The at least one slit channel comprises 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 arranged along the thickness direction perpendicular to the electronic device; The gas compression structure and the fluid amplifier are connected through an air inlet space in communication with the air inlet, and the gas outlet of the gas compression structure is connected to the inlet of each first channel through a pipe.

3. The electronic device of claim 2, wherein, The extension direction of each first channel is arranged at an angle with the inner wall of the main channel.

4. The electronic device of claim 2 or 3, wherein, 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.

5. The electronic device of any one of claims 1-4, wherein, The at least one slit channel comprises at least one second channel, and the inlet of each second channel and the inlet of the main channel are located on different sides of the fluid amplifier; The gas compression structure avoids the communication between the air inlet and the inlet of the main channel.

6. The electronic device of claim 5, wherein, The heat dissipation system comprises a flow guide piece 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 to the heat dissipation fin.

7. The electronic device of any one of claims 1-6, wherein, Along the extension direction of the slit channel, the cross-sectional area of the inlet of the slit channel is greater than that of the outlet of the slit channel.

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

9. The electronic device of any of claims 1-8, wherein, The number of the heat dissipation systems is two, and the two heat dissipation systems are arranged on both sides of the vapor chamber along the thickness direction perpendicular to the electronic device.

10. The electronic device of any one of claims 1-9, wherein, The gas compression structure is a micro air pump or a piezoelectric fan.

11. The electronic device of claim 10, wherein, The gas compression structure is a micro air pump, and the gas compression structure comprises a shell, two rotors, at least one driving component and a control component; The shell has an inner cavity, an air inlet and an air outlet, and along a direction perpendicular to the thickness of the electronic device, the inner cavity of the shell comprises a circumferential inner wall, the air inlet and the air outlet are respectively connected with the circumferential inner wall and the outer surface of the shell and are arranged in parallel; each rotor comprises an impeller surface, and the convex surface of the impeller surface is used for contacting the circumferential inner wall; two rotors are arranged in parallel along a direction perpendicular to the thickness of the electronic device, and the impeller surfaces of the two rotors are conjugated and engaged; along the thickness direction of the electronic device, the rotors are provided with axial grooves on the side of the shell; 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 arranged between the two rotors; At least one of the rotors is driven by one of the drive assemblies, each drive assembly comprises an annular drive magnet and a plurality of drive coils; between one rotor and the drive assembly for driving the rotor, the drive magnet is coaxially fixed to the rotor, and the plurality of drive coils are arranged in parallel around the rotation axis of the rotor and accommodated in the axial groove of the rotor; along a direction perpendicular to the thickness of the electronic device, any one of the drive coils is arranged in parallel with the drive magnet; The control assembly is electrically connected with the drive coils of the at least one drive assembly to supply power to the drive coils.

12. A fluid compression device, characterized by, The fluid compression device comprises a shell, a rotor assembly, at least one drive assembly and a control assembly; The shell has an inner cavity, an air inlet and an air outlet, and along a direction perpendicular to the thickness of the fluid compression device, the air inlet and the air outlet are respectively connected with the inner cavity and the outer surface of the shell and are arranged in parallel; 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 shell; 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; during the rotation of the at least one rotor, the volume of the at least two chambers changes; Each drive assembly is used for driving one rotor to rotate around its rotation axis; each drive assembly comprises an annular drive magnet and a plurality of drive coils, the drive magnet is coaxially fixed to the rotor, and the plurality of drive coils are fixed to the shell around the rotation axis of the rotor to form a magnetic field for driving the drive magnet; Along a direction perpendicular to the thickness of the fluid compression device, any one of the drive coils is arranged in parallel with the drive magnet; The control assembly is electrically connected with the drive coils of the at least one drive assembly to supply power to the drive coils.

13. The fluid compression device of claim 12, wherein, The inner cavity of the shell comprises a circumferential inner wall along a direction perpendicular to the thickness direction of the fluid compression device, the rotor assembly comprises two rotors arranged adjacently, each of the rotors comprises an impeller face and the convex surface of the impeller face is used to contact the circumferential inner wall, the impeller faces of the two rotors are conjugate engaged; the arrangement direction of the air inlet and the air outlet is perpendicular to the arrangement direction of the two impeller faces, 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 driving assemblies, and the rotor has an axial recess on the side of the rotor facing the shell along the thickness direction of the fluid compression device, and the driving magnet is fixed to the shell and accommodated in the axial recess.

14. The fluid compression device of claim 13, wherein, The two rotors are respectively driven by one of the driving assemblies, the control assembly comprises 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.

15. The fluid compression device of claim 14, wherein, 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.

16. The fluid compression device of any one of claims 13-15, wherein, 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, and the first magnets and the second magnets repel each other.

17. The fluid compression device of any one of claims 13-16, wherein, 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, and the plurality of magnetic coils are used to form a magnetic field by charging.

18. The fluid compression device of claim 12, wherein, The inner cavity of the shell comprises a circumferential inner wall along a direction perpendicular to the thickness direction of the fluid compression device, the rotor assembly comprises one rotor, and the rotor comprises a cam surface surrounding the rotation axis of the rotor, and the radially farthest end of the cam surface contacts the circumferential inner wall. The shell and the rotor are provided with a movable slider, the shell comprises a sliding groove with an opening on the circumferential inner wall, and one end of the movable slider extends into the sliding groove and is in sliding fit with the sliding groove along a direction perpendicular to the rotation axis of the rotor, and the other end of the movable slider protrudes out of the circumferential inner wall and contacts the cam surface of the rotor. The air inlet and the air outlet are respectively arranged on both sides of the sliding groove along the circumference of the circumferential inner wall. The rotor has an axial recess on the side of the rotor facing the shell along the thickness direction of the fluid compression device, and the driving magnet is fixed to the shell and accommodated in the axial recess.

19. The fluid compression device of claim 18, wherein, The rotor has a counterweight hollow to make the center of gravity of the rotor coincide with the rotation axis of the rotor, and the counterweight hollow is located between the rotation axis of the rotor and the radially farthest end of the cam surface.

20. The fluid compression device of claim 18 or 19, wherein, The fluid compression device further comprises a pressure valve arranged at the air outlet.

21. The fluid compression device of any one of claims 18-20, wherein, The end of the movable slider extending into the sliding groove is connected to the shell by a spring, and the spring is in a compressed state.

22. The fluid compression device of any one of claims 12-21, wherein, The radial size of the air outlet is smaller than the radial size of the air inlet.

23. The fluid compression device of any one of claims 13-22, wherein, Each of the driving assemblies comprises 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 comprises a central sleeve and a plurality of supports, the plurality of supports are fixed to the outer circumferential surface of the central sleeve and spaced around the rotation axis of the rotor, and each of the supports is used for arranging one of the drive coils; The inner ring of the bearing is fixed to the fixed shaft, and the outer ring of the bearing is fixed coaxially to the central sleeve.

24. The fluid compression device of claim 12, wherein, Along the thickness direction perpendicular to the fluid compression device, the inner cavity of the shell comprises a circumferential inner wall, the rotor assembly comprises one rotor, and the outer circumferential surface of the rotor comprises three circumferential side walls, each of the circumferential side walls forms a top corner with any two adjacent circumferential side walls, and each of the top corners is in contact with the circumferential inner wall; The rotor has a central gear ring coaxial with the rotation axis of the rotor, the drive magnet is fixed to the rotor around the central gear ring, and the plurality of drive coils are fixed to the shell around the circumferential inner wall; The drive 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, the ratio of the number of teeth of the central gear ring to the number of teeth of the driving gear is 3:2, and the planet carrier comprises first and second rotation shafts parallel to each other, the first rotation shaft is coaxially connected in rotation with the driving gear, and the second rotation shaft is coaxially connected in rotation with the rotor.

25. The fluid compression device of claim 24, wherein, The number of the air inlets is two, and the number of the air outlets is two; Along the thickness direction perpendicular to the fluid compression device, one of the air outlets and one of the air inlets are arranged adjacent to each other on one side of the shell, the other of the air outlets and the other of the air inlets are arranged adjacent to each other on the other side of the shell, and one of the air outlets is opposite to one of the air inlets, and the other of the air outlets is opposite to the other of the air inlets.

26. The fluid compression device of claim 24 or 25, wherein, Each of the top corners of the rotor is provided with a clamping gap, the clamping gap is embedded with a sealing strip, and the sealing strip is used for sealing the gap between the top corner of the rotor and the circumferential inner wall.

27. The fluid compression device of claim 26, wherein, A spring sheet is embedded between the clamping gap and the sealing strip, and the spring sheet is used for providing a force to the sealing strip to press the sealing strip towards the circumferential inner wall.

28. An electronic device, comprising: The electronic device comprises a shell, a heat dissipation system and a heat conduction assembly accommodated in the shell; The shell has an air inlet and an air outlet, and along the thickness direction perpendicular to the electronic device, the air inlet and the air outlet respectively penetrate the outer surface and the inner surface of the shell; The heat conduction assembly 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; The heat dissipation system comprises fluid amplifiers and fluid compression devices arranged adjacently along a direction perpendicular to the thickness direction of the electronic device; the fluid amplifiers comprise a main channel and at least one slit channel, the extension direction of the main channel and each slit channel is perpendicular to the thickness direction of the electronic device; the main channel is used for guiding the air of the air inlet to the heat dissipation fins; 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.

Images