A magnetic repulsion transmission coupler

Abstract

The application discloses a magnetic repulsion transmission coupler and relates to the technical field of mechanical transmission. The coupler comprises a driving rotor assembly and a driven rotor assembly, and the driving rotor assembly and the driven rotor assembly are coaxially arranged. The driving rotor assembly comprises a driving rotor carrier, a positioning sleeve, a driving rotor magnetic steel, a driving rotor elastic body and a driving rotor magnetic claw. The driven rotor assembly comprises a driven rotor carrier, a driven rotor magnetic steel, a driven rotor elastic body and a driven rotor magnetic claw. Compared with the design that the magnetic steels are embedded on both sides of the magnetic claw, the design can reduce the magnetic resistance torque, so that the one-way transmission torque of the magnetic repulsion transmission coupler is large. On the other hand, when the magnetic repulsion transmission coupler does not transmit any load torque, the driving rotor magnetic claw and the driven rotor magnetic claw can be prevented from being rigidly collided together in the angular direction due to the magnetic repulsion, and the elastic body can play the role of elastic buffering.

Description

Technical Field

[0001] The invention relates to a mechanical transmission device, in particular to a magnetic repulsion transmission coupler. Background Art

[0002] Permanent magnetic couplings rely on the magnetic force of rare earth permanent magnets to achieve contactless transmission between the drive shaft and the load shaft. Synchronous permanent magnetic couplings, in particular, have been widely used in mechanical transmission systems. Common synchronous permanent magnetic couplings come in two main types: cylindrical and disc-type. Regardless of the design, they rely on permanent magnetic attraction to achieve transmission between the drive shaft and the load shaft, and the air gap between the driving and driven rotors is constant. Disc-type synchronous permanent magnetic couplings are rarely used in production due to the high axial force they experience. In cylindrical synchronous permanent magnetic couplings, the magnets participate in the magnetic coupling radially. Centrifugal force makes it difficult to secure the inner rotor's magnets. Coaxial positioning of the driving and driven rotors is also difficult, leading to eccentric adhesion and difficulty in separation. Furthermore, cylindrical synchronous permanent magnetic couplings have an unadjustable radial air gap, resulting in poor elastic buffering capacity and low torque transmission per unit volume. Summary of the Invention

[0003] The object of the present invention is to provide a magnetic repulsion transmission coupler to solve the problems in the background technology.

[0004] To achieve the above objectives, the present invention provides the following technical solutions: A magnetic repulsion transmission coupler comprising an active rotor assembly and a driven rotor assembly, the active rotor assembly and the driven rotor assembly being coaxially arranged. The active rotor assembly comprises an active rotor carrier, a positioning sleeve, an active rotor magnet, an active rotor elastomer, and an active rotor claw; the driven rotor assembly comprises a driven rotor carrier, a driven rotor magnet, a driven rotor elastomer, and a driven rotor claw; the active rotor magnet disposed in an open slot on one side of the active rotor claw and the driven rotor magnet disposed in an open slot on one side of the driven rotor claw have the same magnetic poles, such as NN or SS poles, arranged opposite each other; the active rotor elastomer is disposed in an open slot on the other side of the active rotor claw, and the driven rotor elastomer is disposed in an open slot on the other side of the driven rotor claw; a radial gap ΔR exists between the outer cylindrical surface of the positioning sleeve and the inner circumferential wall surface of the driven rotor claw.

[0005] On the basis of the above technical solutions, the present invention also provides the following optional technical solutions: In one optional solution: a plurality of identical active rotor magnetic claws are evenly arranged along the circumferential direction on the end face of the active rotor carrier, and open grooves are provided on the left and right sides of the active rotor magnetic claws. The cross-section of the open grooves is fan-shaped, and the active rotor magnets are embedded in the open grooves on one side of the plurality of active rotor magnetic claws in a certain order, and the active rotor elastomer is embedded in the other side.

[0006] In an optional solution: a plurality of identical driven rotor magnetic claws are evenly arranged along the circumferential direction on the end surface of the driven rotor carrier, and open grooves are provided on the left and right sides of the driven rotor magnetic claws. The cross-section of the open grooves is fan-shaped, and the driven rotor magnets are embedded in the open grooves on one side of the plurality of driven rotor magnetic claws in a certain order, and the driven rotor elastomer is embedded on the other side.

[0007] In an optional solution: the cross-sections of the active rotor magnet and the driven rotor magnet are both fan-shaped, and the two are respectively embedded in the open grooves of the fan-shaped cross-sections of the active rotor magnetic claws and the driven rotor magnetic claws, so that "positive locking" is formed between the active rotor magnet and the active rotor magnetic claws, and between the driven rotor magnet and the driven rotor magnetic claws.

[0008] In an optional solution, the cross-sections of the active rotor elastomer and the driven rotor elastomer are both fan-shaped, and both are embedded in the open grooves of the fan-shaped cross-sections on one side of the active rotor magnetic claw and the driven rotor magnetic claw, respectively. The active rotor elastomer and the active rotor magnetic claw, as well as the driven rotor elastomer and the driven rotor magnetic claw, also form a "positive lock".

[0009] The sector angles of the driving rotor elastic body and the driven rotor elastic body are respectively larger than the sector angles of the opening slots on one side of the driving rotor magnetic claw and the driven rotor magnetic claw.

[0010] In one optional solution, the active rotor magnetic claws and the driven rotor magnetic claws are evenly and alternately arranged along the circumferential direction. In one optional solution, the active rotor magnetic steel and the driven rotor magnetic steel are of the same size and made of the same material; the active rotor elastomer and the driven rotor elastomer are of the same size and made of the same material.

[0011] In an optional solution, in the working state, there is an axial gap ΔL between the right end surface of the active rotor carrier and the left end surface of the driven rotor magnetic claw, and between the left end surface of the driven rotor carrier and the right end surface of the active rotor magnetic claw.

[0012] In an optional solution: in a working state, there is an angular gap α between the active rotor magnetic steel of the active rotor magnetic claw and the driven rotor magnetic steel of the driven rotor magnetic claw; there is an angular gap β between the active rotor elastomer of the active rotor magnetic claw and the driven rotor elastomer of the driven rotor magnetic claw.

[0013] In an optional solution, in addition to the positive locking, the active rotor magnets, the active rotor elastic body, and the active rotor magnetic claws are bonded together using glue. In addition to the positive locking, the driven rotor magnets, the driven rotor elastic body, and the driven rotor magnetic claws are bonded together using glue.

[0014] In one optional solution, the active rotor magnets and the driven rotor magnets are made of high-performance permanent magnets, preferably neodymium iron boron; and the active rotor elastomers and the driven rotor elastomers are made of elastic materials, preferably rubber. Compared with the prior art, the present invention has the following beneficial effects:

[0015] 1. The active and passive rotor claws of this magnetic repulsion transmission coupler have magnets embedded on one side and an elastomer embedded on the other. Compared to designs with magnets embedded on both sides of the claws, this design reduces the magnetic drag torque, maximizing the torque value when the magnetic repulsion transmission coupler is transmitting in a single counterclockwise or clockwise direction. Furthermore, when the magnetic repulsion transmission coupler is not transmitting any load torque, it prevents the active and passive rotor claws from angularly "rigidly colliding" due to magnetic drive, and the elastomer acts as an elastic buffer.

[0016] 2. The magnetic repulsion transmission coupler has several identical active rotor claws and driven rotor claws that are evenly and alternately arranged along the circumferential direction, and the magnets and elastomers are installed in the fan-shaped opening slots on the left and right sides of the active rotor claws and the driven rotor claws through "form locking" and glue bonding. Therefore, during operation, the magnets and elastomers are accurately positioned and reliably fixed, and the magnets are not easy to fall off.

[0017] 3. Magnetic repulsion transmission is used to replace conventional magnetic attraction transmission, that is, the circumferential magnetic repulsion coupling transmission replaces the radial magnetic attraction coupling transmission. Obviously, the size of the magnetic repulsion coupling air gap value will vary with the size of the load. This makes it easy to set a larger angular gap α value between the active rotor and the driven rotor, thereby increasing the elastic buffering capacity of the magnetic repulsion transmission coupler. When the magnetic repulsion transmission coupler is working, as the load increases, the angular gap α value decreases. At this time, the magnetic repulsion torque, that is, the driving torque, will show a nonlinear and significant increase. That is, when the amount of magnetic steel used is the same, the torque value transmitted by the magnetic repulsion transmission coupler is greater than the torque value transmitted by the conventional magnetic attraction transmission coupler in the known technology.

[0018] 4. Before installation, the magnetic repulsion transmission coupler has a certain radial clearance ΔR between the outer cylindrical surface of the positioning sleeve and the inner circumferential wall of the driven rotor's magnetic claw. This allows for pre-positioning of the two components. Even in the presence of radially unbalanced forces, the maximum radial eccentricity of the active and passive rotor assemblies of the magnetic repulsion transmission coupler before installation does not exceed ΔR. Once the active and passive rotor assemblies are installed on the drive shaft and load shaft, respectively, the small eccentricity ΔR makes it very easy to align the centers of the two shafts, reducing the amount of alignment work and ultimately achieving a uniform radial clearance ΔR between the two rotors of the magnetic repulsion transmission coupler. Furthermore, a clearance ΔL is reserved on both axial left and right end faces of the magnetic repulsion transmission coupler, along with angular clearances α and β. This fully ensures non-contact transmission between the active and passive rotor assemblies.

[0019] 5. The magnetic repulsion transmission coupler has a relatively simple structure, is safe and reliable, has a reasonable magnetic circuit structure, and is easy to design and manufacture. Compared with other magnetic couplers, it can save a certain amount of magnetic steel and can be used in mechanical transmission systems with unidirectional transmission. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is a structural schematic diagram of the present invention.

[0021] Figure 2 It is a cross-sectional working state schematic diagram of the present invention.

[0022] Figure 3 It is a cross-sectional schematic diagram of the present invention in a non-working state.

[0023] Notes on the accompanying drawings: 11. Active rotor carrier; 12. Positioning sleeve; 13. Active rotor magnet; 14. Active rotor elastomer; 15. Active rotor magnetic claw; 21. Driven rotor carrier; 23. Driven rotor magnet; 24. Driven rotor elastomer; 25. Driven rotor magnetic claw. DETAILED DESCRIPTION

[0024] In order to make the objectives, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments.

[0025] In one embodiment, Figure 1-Figure 3As shown, a magnetic repulsion transmission coupling includes a driving rotor assembly and a driven rotor assembly, the driving rotor assembly and the driven rotor assembly being coaxially arranged. The driving rotor assembly includes a driving rotor carrier 11, a positioning sleeve 12, a driving rotor magnet 13, a driving rotor elastic body 14, and a driving rotor claw 15; the driven rotor assembly includes a driven rotor carrier 21, a driven rotor magnet 23, a driven rotor elastic body 24, and a driven rotor claw 25. The coupling is characterized in that the driving rotor magnet 13 disposed in an open slot on one side of the driving rotor claw 15 and the driven rotor magnet 23 disposed in an open slot on one side of the driven rotor claw 25 have the same magnetic poles, such as NN or SS poles, arranged opposite each other; the driving rotor elastic body 14 is disposed in an open slot on the other side of the driving rotor claw 15, and the driven rotor elastic body 24 is disposed in an open slot on the other side of the driven rotor claw 25; and a radial gap ΔR exists between the outer cylindrical surface of the positioning sleeve 12 and the inner circular wall surface of the driven rotor claw 25. A plurality of identical active rotor magnetic claws 15 are uniformly provided along the circumferential direction on the end surface of the active rotor carrier 11. Open slots are provided on the left and right sides of the active rotor magnetic claws 15. The cross-section of the open slots is fan-shaped. The active rotor magnets 13 are embedded in the open slots on one side of the plurality of active rotor magnetic claws 15 in a certain order, and the active rotor elastomer 14 is embedded in the open slots on the other side. A plurality of identical driven rotor magnetic claws 25 are uniformly provided along the circumferential direction on the end surface of the driven rotor carrier 21. Open slots are provided on the left and right sides of the driven rotor magnetic claws 25. The cross-section of the open slots is fan-shaped. The driven rotor magnets 23 are embedded in the open slots on one side of the plurality of driven rotor magnetic claws 25 in a certain order, and the driven rotor elastomer 24 is embedded in the open slots on the other side. The cross-sections of the active rotor magnet 13 and the driven rotor magnet 23 are both fan-shaped, and the two are respectively embedded in the open grooves of the fan-shaped cross-sections of the active rotor magnetic claw 15 and the driven rotor magnetic claw 25. The active rotor magnet 13 and the active rotor magnetic claw 15, as well as the driven rotor magnet 23 and the driven rotor magnetic claw 25, both form a "form lock". The cross-sections of the active rotor elastomer 14 and the driven rotor elastomer 24 are both fan-shaped, and the two are respectively embedded in the open grooves of the fan-shaped cross-sections on one side of the active rotor magnetic claw 15 and the driven rotor magnetic claw 25. The active rotor elastomer 14 and the active rotor magnetic claw 15, as well as the driven rotor elastomer 24 and the driven rotor magnetic claw 25, also form a "form lock".The sector angles of the active rotor elastic body 14 and the driven rotor elastic body 24 are respectively greater than the sector angles of the opening slots on one side of the active rotor claw 15 and the driven rotor claw 25; the active rotor claw 15 and the driven rotor claw 25 are evenly and alternately arranged in the circumferential direction; the active rotor magnets 13 and the driven rotor magnets 23 are of the same size and made of the same material; the active rotor elastic body 14 and the driven rotor elastic body 24 are of the same size and made of the same material; during operation, an axial gap ΔL exists between the right end face of the active rotor carrier 11 and the left end face of the driven rotor claw 25, and between the left end face of the driven rotor carrier 21 and the right end face of the active rotor claw 15; During operation, an angular gap α exists between the active rotor magnet 13 of the active rotor claw 15 and the driven rotor magnet 23 of the driven rotor claw 25; an angular gap β exists between the active rotor elastomer 14 of the active rotor claw 15 and the driven rotor elastomer 24 of the driven rotor claw 25. In addition to form-locking, the active rotor magnet 13, the active rotor elastomer 14, and the active rotor claw 15 are also bonded using glue. In addition to form-locking, the driven rotor magnet 23, the driven rotor elastomer 24, and the driven rotor claw 25 are also bonded using glue. The active rotor magnet 13 and the driven rotor magnet 23 are made of high-performance permanent magnet steel, preferably neodymium iron boron; the active rotor elastomer 14 and the driven rotor elastomer 24 are made of elastic material, preferably rubber.

[0026] The above description is merely a specific embodiment of the present disclosure, but the scope of protection of the present disclosure is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in this disclosure should be included in the scope of protection of the present disclosure. Therefore, the scope of protection of the present disclosure should be based on the scope of protection of the claims.

Claims

1. A magnetic repulsion transmission coupler, comprising an active rotor assembly and a driven rotor assembly, wherein the active rotor assembly and the driven rotor assembly are coaxially arranged, wherein the active rotor assembly comprises an active rotor carrier (11), a positioning sleeve (12), an active rotor magnetic steel (13), an active rotor elastic body (14), and an active rotor magnetic claw (15); and wherein the driven rotor assembly comprises a driven rotor carrier (21), a driven rotor magnetic steel (23), a driven rotor elastic body (24), and a driven rotor magnetic claw (25); wherein the driven rotor assembly comprises a driven rotor carrier (21), a driven rotor magnetic steel (23), a driven rotor elastic body (24), and a driven rotor magnetic claw (25); wherein the driven rotor assembly comprises a driven rotor carrier (21), a driven rotor magnetic steel (23), a driven rotor elastic body (24), and a driven rotor magnetic claw (25); The active rotor magnet (13) arranged in the open slot on one side of the active rotor magnetic claw (15) and the driven rotor magnet (23) arranged in the open slot on one side of the driven rotor magnetic claw (25) are arranged with the same magnetic poles opposite to each other; the active rotor elastic body (14) is arranged in the open slot on the other side of the active rotor magnetic claw (15), and the driven rotor elastic body (24) is arranged in the open slot on the other side of the driven rotor magnetic claw (25); a radial gap ΔR exists between the outer cylindrical surface of the positioning sleeve (12) and the inner cylindrical wall surface of the driven rotor magnetic claw (25); a plurality of identical active rotor magnetic claws (15) are evenly arranged along the circumferential direction on the end surface of the active rotor carrier (11), and open slots are arranged on the left and right sides of the active rotor magnetic claws (15), and the cross section of the open slot is fan-shaped. The active rotor magnet (13) is embedded in the open slot on one side of the plurality of active rotor magnetic claws (15) in a certain order, and the active rotor elastic body is embedded in the other side. The driven rotor carrier (21) comprises a plurality of identical driven rotor magnetic claws (25) uniformly arranged along the circumferential direction on the end surface thereof, and an open groove is arranged on the left and right sides of the driven rotor magnetic claws (25), and the cross section of the open groove is fan-shaped, and the driven rotor magnet (23) is sequentially embedded in the open groove on one side of the plurality of driven rotor magnetic claws (25), and the driven rotor elastic body (24) is embedded on the other side; the cross sections of the active rotor elastic body (14) and the driven rotor elastic body (24) are both fan-shaped, and the fan angles of the active rotor elastic body (14) and the driven rotor elastic body (24) are respectively larger than the fan angles of the open grooves on one side of the active rotor magnetic claws (15) and the driven rotor magnetic claws (25).

2. The magnetic repulsion transmission coupler according to claim 1, characterized in that: The cross-sections of the active rotor magnetic steel (13) and the driven rotor magnetic steel (23) are both fan-shaped, and the two are respectively embedded in the open grooves of the fan-shaped cross-sections of the active rotor magnetic claw (15) and the driven rotor magnetic claw (25), and a "form locking" is formed between the active rotor magnetic steel (13) and the active rotor magnetic claw (15), and between the driven rotor magnetic steel (23) and the driven rotor magnetic claw (25).

3. The magnetic repulsion transmission coupler according to claim 1, characterized in that: The active rotor elastic body (14) and the driven rotor elastic body (24) are respectively embedded in the open grooves of the fan-shaped cross-section on one side of the active rotor magnetic claw (15) and the driven rotor magnetic claw (25), and a "positive locking" is also formed between the active rotor elastic body (14) and the active rotor magnetic claw (15), and between the driven rotor elastic body (24) and the driven rotor magnetic claw (25).

4. The magnetic repulsion transmission coupler according to claim 3, characterized in that: The active rotor magnetic claws (15) and the driven rotor magnetic claws (25) are evenly and alternately arranged along the circumferential direction.

5. The magnetic repulsion transmission coupler according to any one of claims 1 to 4, characterized in that: In the working state, an axial gap ΔL exists between the right end face of the active rotor carrier (11) and the left end face of the driven rotor magnetic claw (25), and between the left end face of the driven rotor carrier (21) and the right end face of the active rotor magnetic claw (15).

6. The magnetic repulsion transmission coupler according to any one of claims 1 to 4, characterized in that: In a working state, an angular gap α exists between the active rotor magnetic steel (13) of the active rotor magnetic claw (15) and the driven rotor magnetic steel (23) of the driven rotor magnetic claw (25); and an angular gap β exists between the active rotor elastic body (14) of the active rotor magnetic claw (15) and the driven rotor elastic body (24) of the driven rotor magnetic claw (25).

7. The magnetic repulsion transmission coupler according to claim 6, characterized in that: The active rotor magnetic steel (13) and the driven rotor magnetic steel (23) are made of neodymium iron boron material; the active rotor elastic body (14) and the driven rotor elastic body (24) are made of rubber material.

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