CN113883184A - Magneto-rheological clutch with groove structure transmission disc - Google Patents
Magneto-rheological clutch with groove structure transmission disc Download PDFInfo
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- CN113883184A CN113883184A CN202111080498.3A CN202111080498A CN113883184A CN 113883184 A CN113883184 A CN 113883184A CN 202111080498 A CN202111080498 A CN 202111080498A CN 113883184 A CN113883184 A CN 113883184A
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- transmission disc
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D37/00—Clutches in which the drive is transmitted through a medium consisting of small particles, e.g. centrifugally speed-responsive
- F16D37/02—Clutches in which the drive is transmitted through a medium consisting of small particles, e.g. centrifugally speed-responsive the particles being magnetisable
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D37/00—Clutches in which the drive is transmitted through a medium consisting of small particles, e.g. centrifugally speed-responsive
- F16D2037/002—Clutches in which the drive is transmitted through a medium consisting of small particles, e.g. centrifugally speed-responsive characterised by a single substantially axial gap in which the fluid or medium consisting of small particles is arranged
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/02—Overheat protection, i.e. means for protection against overheating
- F16D2300/021—Cooling features not provided for in group F16D13/72 or F16D25/123, e.g. heat transfer details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/10—Surface characteristics; Details related to material surfaces
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention discloses a magneto-rheological clutch with a groove structure transmission disc, which comprises a main transmission disc and a driven transmission disc, wherein a liquid medium with internal iron magnetic suspension particles is arranged between the main transmission disc and the driven transmission disc; the opposite surfaces of the main driving disc and the driven driving disc are inner surfaces, grooves are machined on the inner surface of one of the main driving disc and the driven driving disc, and the inner surface of the other opposite driving disc is not provided with the grooves. Has the advantages that: the ditching groove on the transmission disc can effectively enhance the shearing stress of the magnetorheological clutch and simultaneously increase the surface heat dissipation area of the transmission disc, thereby achieving the comprehensive optimization effects of enhancing the shearing torque, strengthening the heat dissipation capacity and reducing the highest temperature rise.
Description
Technical Field
The invention relates to a clutch, in particular to a magneto-rheological clutch with a groove structure transmission disc, and belongs to the technical field of mechanical transmission.
Background
In recent years, with the development of "intelligent materials", the physical properties of the magnetorheological fluid, such as heat conductivity, mechanical properties, and particularly the rheological properties under the action of a magnetic field, are rapidly and reversibly changed under the action of an external magnetic field, so that the magnetorheological fluid is widely applied to the fields of mechanical transmission, aerospace, construction, medical treatment and the like. The magnetorheological fluid is a liquid formed by mixing ferromagnetic particles with high magnetic conductivity, carrier fluid, additives and the like according to a certain proportion, has good fluidity when no magnetic field exists outside, and when a magnetic field exists outside, the ferromagnetic particles in the magnetorheological fluid are connected with each other under the action of the magnetic field to form a magnetic chain, so that a 'curing effect' can be generated.
The magneto-rheological clutch is a novel transmission device which realizes the engagement and the disengagement of the clutch by controlling the magnetic field intensity between a driving disc and a driven disc of the magneto-rheological clutch by means of electromagnetic induction, thereby achieving the purpose of controlling the clutch to transmit power outwards. Compared with the traditional power transmission device, the magneto-rheological clutch has the advantages of small noise, quick response, simple control, small abrasion of transmission parts, stepless speed change realization and the like, overcomes the defects of large noise, unstable torque and the like of the traditional clutch, and is a novel electromechanical transmission control device. However, the lack of strong shear force of the magnetorheological clutch has been an important reason to limit the development thereof. In order to solve the problems, the prior art adopts a mode of increasing the number of the annular coils, and the shearing force is increased by improving the magnetic field intensity, so that the increase of the torque and the high-power transmission are realized. However, the addition of the ring coil also brings new problems, such as large energy consumption, high temperature of the driving disc, the driven disc and the magnetorheological fluid of the clutch, and the like. How to effectively enhance the shearing moment of the magnetorheological clutch, ensure the power transmission of a transmission part, reduce energy consumption and increase heat dissipation has become a focus of increasing attention in the industry.
Disclosure of Invention
The purpose of the invention is as follows: the invention aims to solve the problems in the prior art and provides a magnetorheological clutch with a groove structure transmission disc, which can enhance the shearing moment of the magnetorheological clutch in an engagement state and enhance the surface heat dissipation of the transmission disc. When the magnetorheological clutch is in an engaged state, a magnetic mechanical barrier is formed by utilizing the groove structure on the transmission disc, so that the sliding of the microfluidic medium on the surface of the microfluidic medium is inhibited, the shear stress transmitted to the surface of the transmission disc by the magnetorheological fluid is further enhanced, and the transmission torque is improved. Meanwhile, the surface of the transmission disc of the magnetorheological clutch is provided with the grooves, so that the heat convection area between the transmission disc and the magnetorheological fluid is increased, the heat dissipation capability is improved, the highest temperature rise is reduced, and further the comprehensive optimization effects of enhancing the shearing torque, strengthening the heat dissipation and reducing the temperature rise are achieved.
The technical scheme is as follows: a magneto-rheological clutch with a groove structure transmission disc comprises a main transmission disc and a driven transmission disc, wherein a liquid medium with internal iron magnetic suspension particles is arranged between the main transmission disc and the driven transmission disc; the opposite surfaces of the main driving disc and the driven driving disc are inner surfaces, grooves are machined on the inner surface of one of the main driving disc and the driven driving disc, and the inner surface of the other opposite driving disc is not provided with the grooves.
Compared with a plane disc, the ditching grooves in the transmission disc of the magnetorheological clutch can effectively enhance the shearing stress of the magnetorheological clutch, and simultaneously increase the surface heat dissipation area of the transmission disc, so that the comprehensive optimization effects of enhancing the shearing torque, strengthening the heat dissipation capacity and reducing the highest temperature rise are achieved.
Preferably, in order to improve the distribution uniformity of ferromagnetic particles on the surface of the transmission disc and make the distribution of the shearing moment on the surface of the disc more balanced, the grooves are elongated radial grooves extending in the radial direction of the transmission disc from the center of the transmission disc or the main transmission disc, the number of the elongated radial grooves is at least 3, and the radial grooves are uniformly distributed on the inner surface of the transmission disc or the auxiliary transmission disc at equal angles in the circumferential direction.
Preferably, the radial grooves are elongated grooves with equal width, and the width of the radial grooves is 4-10 mm.
Preferably, the width of the radial slot decreases from the main drive disc or from the centre of the drive disc towards the outside in the radial direction, with a maximum width of 10mm and a minimum width of 4 mm.
Preferably, the depth of the radial grooves is equal, and the depth of the radial grooves is 1-5 mm.
Preferably, the depth of the radial groove decreases gradually from the main drive disc or from the center of the drive disc to the outside in the radial direction, and the maximum depth is 5mm and the minimum depth is 1 mm.
Preferably, the grooves are concentric circular ring grooves which are distributed at equal intervals along the radial direction from the center of the main driving disc or the driving disc, and the center distance between adjacent circular ring grooves ranges from 10mm to 40 mm.
Preferably, the width of the circular ring grooves is equal, and the width of the circular ring grooves is 4-10 mm.
Preferably, the width of the circular ring groove is reduced by the width of the circular ring groove outside the inner ring by equal variation one by one, the range of the width of the circular ring groove is 4-10mm, and the variation of the width of the circular ring groove is the maximum difference of the width of the circular ring groove divided by the number of the circular ring grooves.
Preferably, the depth of the circular ring grooves is equal, and the depth of the circular ring grooves is 1-5 mm.
Preferably, the depth of the circular ring groove is reduced by the depth of the circular ring groove outside the inner ring by equal variation one by one, the range of the depth of the circular ring groove is 1-5mm, and the variation of the depth of the circular ring groove is the maximum difference of the depth of the circular ring groove divided by the number of the circular ring grooves.
According to the functional requirement of insufficient shearing torque in the working process, a groove structure is processed on the working surface of the steel pipe; the surfaces of the transmission discs are uniformly distributed in the equal-depth groove structures, and the shapes of the equal-depth groove structures comprise radial grooves and circumferential circular grooves; according to the centrifugal force effect and the linear velocity difference of different radial positions of the magnetorheological clutch transmission disc in a high-speed running state, the difference of heat dissipation requirements of different positions of the surface of the transmission disc is considered, the groove structure with the gradient change of depth and width is arranged along the radial direction, the distribution uniformity of ferromagnetic particles on the surface of the transmission disc is improved, the distribution of the shearing moment of the surface of the disc is more balanced, and the comprehensive optimization effects of enhancing the shearing moment of the magnetorheological clutch, increasing the transmission torque and enhancing the heat dissipation are achieved.
Has the advantages that: according to the invention, the grooves are formed in the transmission disc, so that the shearing stress of the magnetorheological clutch can be effectively enhanced, and the surface heat dissipation area of the transmission disc is increased, thereby achieving the comprehensive optimization effects of enhancing the shearing torque, strengthening the heat dissipation capability and reducing the highest temperature rise. When the magnetorheological clutch is in an engaged state, a magnetic mechanical barrier is formed by utilizing the groove structure on the transmission disc, so that the sliding of a microfluid medium on the surface of the microfluid medium is inhibited, the shear stress transmitted from the magnetorheological fluid to the surface of the transmission disc is further enhanced, and the transmission torque is improved; the depth and the width gradient that gradually reduce from the center to the outside are set up and groove structure is changed to the width gradient for driven disc center department stores more magnetorheological suspensions, when increasing shear torque, compromises different positions heat dissipation demands, reduces the surperficial biggest temperature rise of driving disc and makes temperature distribution more even. Therefore, the invention can effectively enhance the shearing stress between the transmission discs of the magnetorheological clutch and simultaneously meet the comprehensive effect of optimizing the surface heat dissipation of the transmission discs.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.
FIG. 1 is a schematic diagram of the operation of a first embodiment of a magnetorheological clutch in accordance with the present invention;
FIG. 2 is a schematic diagram of the operation of a second embodiment of a magnetorheological clutch in accordance with the invention;
FIG. 3 is a front view of first and second embodiments of the trench structure of the present invention;
FIG. 4 is a cross-sectional view of first and third embodiments of the trench structure of the present invention;
FIG. 5 is a cross-sectional view of a second embodiment of a trench structure in accordance with the present invention;
FIG. 6 is a front view of a third embodiment of a trench structure in accordance with the present invention;
FIG. 7 is a front view of a fourth and fifth embodiment of the trench structure of the present invention;
FIG. 8 is a cross-sectional view of a fourth embodiment of a trench structure in accordance with the present invention;
FIG. 9 is a cross-sectional view of a fifth embodiment of the trench structure of the present invention;
FIG. 10 is a front view of a sixth embodiment of a trench structure in accordance with the present invention;
fig. 11 is a cross-sectional view of a sixth embodiment of a trench structure in accordance with the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
First embodiment of a magnetorheological clutch
As shown in FIG. 1, the magnetorheological clutch with the transmission disc with the groove structure comprises a main transmission disc 1 and a secondary transmission disc 2, wherein a liquid medium with internal iron magnetic suspension particles is arranged between the main transmission disc 1 and the secondary transmission disc 2; the opposite surfaces of the main transmission disc 1 and the driven transmission disc 2 are inner surfaces, grooves 3 are machined in the inner surfaces of the main transmission disc 1, and no grooves 3 are machined in the inner surfaces of the driven transmission discs 2.
Second embodiment of a magnetorheological clutch
As shown in fig. 2, the magnetorheological clutch with the transmission disc with the groove structure comprises a main transmission disc 1 and a secondary transmission disc 2, wherein a liquid medium with internal iron magnetic suspension particles is arranged between the main transmission disc 1 and the secondary transmission disc 2; the opposite surfaces of the main driving disc 1 and the driven driving disc 2 are inner surfaces, grooves 3 are machined in the inner surfaces of the driven driving discs 2, and the inner surfaces of the main driving disc 1 are not provided with the grooves 3.
First embodiment of Trench Structure
As shown in fig. 3 and 4, the grooves 3 are elongated radial grooves extending in the radial direction from the center of the main transmission disc 1 or the transmission disc 2, and the number of the elongated radial grooves is at least 3, and preferably 4 to 12; the radial grooves are uniformly distributed on the inner surface of the main drive disc 1 or the auxiliary drive disc 2 at equal angles along the circumferential direction. The radial grooves are long-strip-shaped grooves with equal width, and the width of each radial groove is 4-10 mm. The depths of the radial grooves are equal, and the depth of the radial grooves is 1-5 mm.
Second embodiment of Trench Structure
As shown in fig. 3 and 5, the grooves 3 are elongated radial grooves extending in the radial direction from the center of the main transmission disc 1 or the transmission disc 2, and the number of the elongated radial grooves is at least 3, and preferably 4 to 12; the radial grooves are uniformly distributed on the inner surface of the main drive disc 1 or the auxiliary drive disc 2 at equal angles along the circumferential direction. The radial grooves are long-strip-shaped grooves with equal width, and the width of each radial groove is 4-10 mm. The depth of the radial groove is gradually reduced from the center of the main driving disc (1) or the driving disc (2) to the outer side along the radial direction, the maximum depth is 5mm, and the minimum depth is 1 mm.
Third embodiment of trench Structure
As shown in fig. 4 and 6, the grooves 3 are elongated radial grooves extending in the radial direction from the center of the main transmission disc 1 or the transmission disc 2, and the number of the elongated radial grooves is at least 3, and preferably 4 to 12; the radial grooves are uniformly distributed on the inner surface of the main drive disc 1 or the auxiliary drive disc 2 at equal angles along the circumferential direction. The width of the radial groove is gradually reduced from the center of the main driving disc 1 or the driving disc 2 to the outer side along the radial direction, the maximum width is 10mm, and the minimum width is 4 mm. The depths of the radial grooves are equal, and the depth of the radial grooves is 1-5 mm.
Fourth embodiment of Trench Structure
As shown in fig. 7 and 8, the grooves 3 are concentric circular grooves which are distributed at equal intervals in the radial direction from the center of the main transmission disc 1 or the transmission disc 2, and the center distance between the adjacent circular grooves ranges from 10mm to 40 mm. The width of the circular ring grooves is equal, and the width of the circular ring grooves is 4-10 mm. The depth of the circular ring grooves is equal, and the depth of the circular ring grooves is 1-5 mm.
Fifth embodiment of Trench Structure
As shown in fig. 7 and 9, the grooves 3 are concentric circular grooves which are distributed at equal intervals in the radial direction from the center of the main driving disk 1 or the driving disk 2, and the center distance between adjacent circular grooves ranges from 10mm to 40 mm. The width of the circular ring grooves is equal, and the width of the circular ring grooves is 4-10 mm. The depth of the circular ring groove is reduced by the depth of the circular ring groove on the outer side of the inner ring one by one and the like, the depth range of the circular ring groove is 1-5mm, and the variation of the depth of the circular ring groove is the maximum difference of the depth of the circular ring groove divided by the number of the circular ring grooves.
Sixth embodiment of Trench Structure
As shown in fig. 10 and 11, the grooves 3 are concentric circular grooves which are distributed at equal intervals in the radial direction from the center of the main driving disk 1 or the driving disk 2, and the center distance between adjacent circular grooves ranges from 10mm to 40 mm. The width of the circular ring groove is reduced by the width of the circular ring groove on the outer side of the inner ring in an equal variable quantity one by one, the width range of the circular ring groove is 4-10mm, and the variable quantity of the width of the circular ring groove is the maximum difference value of the width of the circular ring groove divided by the number of the circular ring grooves. The depth of the circular ring grooves is equal, and the depth of the circular ring grooves is 1-5 mm.
By adopting the magnetorheological clutch with the groove structure transmission disc, the shear stress of the magnetorheological clutch can be effectively enhanced by arranging the groove structure, the surface heat dissipation area of the transmission disc is increased, and the comprehensive optimization effects of enhancing the shear torque, strengthening the heat dissipation capacity and reducing the highest temperature rise are achieved. When the magnetorheological clutch is in an engaged state, a magnetic mechanical barrier is formed by utilizing the groove structure on the transmission disc, so that the sliding of a microfluid medium on the surface of the microfluid medium is inhibited, the shear stress transmitted from the magnetorheological fluid to the surface of the transmission disc is further enhanced, and the transmission torque is improved; according to the magneto-rheological clutch transmission disc, under the high-speed running state, centrifugal force action and linear velocity difference of different radial positions are achieved, the difference of heat dissipation requirements of different positions on the surface of the transmission disc is considered, the groove structure with the gradient change of depth and width is arranged along the radial direction, the distribution uniformity of ferromagnetic particles on the surface of the transmission disc is improved, the distribution of the surface shearing moment of the disc is more balanced, the heat dissipation requirements of different positions are considered while the shearing moment is increased, the maximum temperature rise of the surface of the transmission disc is reduced, and the temperature distribution is more uniform. Therefore, the invention can effectively enhance the shearing stress between the transmission discs of the magnetorheological clutch and simultaneously meet the comprehensive effect of optimizing the surface heat dissipation of the transmission discs.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other. The device disclosed by the embodiment corresponds to the method disclosed by the embodiment, so that the description is simple, and the relevant points can be referred to the method part for description.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (11)
1. A magneto-rheological clutch with a groove structure transmission disc comprises a main transmission disc (1) and a slave transmission disc (2), wherein a liquid medium with internal iron magnetic suspension particles is arranged between the main transmission disc (1) and the slave transmission disc (2); the method is characterized in that: the opposite surfaces of the main transmission disc (1) and the auxiliary transmission disc (2) are inner surfaces, a groove (3) is machined in the inner surface of one of the main transmission disc (1) or the auxiliary transmission disc (2), and the inner surface of the other opposite transmission disc is not provided with the groove (3).
2. The magnetorheological clutch having a grooved drive plate of claim 1, wherein: the groove (3) is a long-strip-shaped radial groove which takes the center of the main transmission disc (1) or the center of the auxiliary transmission disc (2) as a starting point and extends along the radial direction of the main transmission disc, the number of the long-strip-shaped radial grooves is at least 3, and the radial grooves are uniformly distributed on the inner surface of the main transmission disc (1) or the auxiliary transmission disc (2) along the circumferential direction at equal angles.
3. The magnetorheological clutch having a grooved drive plate of claim 2, wherein: the radial grooves are long-strip-shaped grooves with equal width, and the width of each radial groove is 4-10 mm.
4. The magnetorheological clutch having a grooved drive plate of claim 2, wherein: the width of the radial groove is gradually reduced from the center of the main driving disc (1) or the driving disc (2) to the outer side along the radial direction, the maximum width is 10mm, and the minimum width is 4 mm.
5. The magnetorheological clutch having a grooved drive plate according to claim 3 or 4, wherein: the depths of the radial grooves are equal, and the depth of the radial grooves is 1-5 mm.
6. The magnetorheological clutch having a grooved drive plate of claim 3, wherein: the depth of the radial groove is gradually reduced from the center of the main driving disc (1) or the driving disc (2) to the outer side along the radial direction, the maximum depth is 5mm, and the minimum depth is 1 mm.
7. The magnetorheological clutch having a grooved drive plate of claim 1, wherein: the grooves (3) are concentric circular grooves which are distributed at equal intervals along the radial direction from the center of the main driving disc (1) or the driven disc (2), and the center distance range of the adjacent circular grooves is 10-40 mm.
8. The magnetorheological clutch having a grooved drive plate of claim 7, wherein: the width of the circular ring grooves is equal, and the width of the circular ring grooves is 4-10 mm.
9. The magnetorheological clutch having a grooved drive plate of claim 7, wherein: the width of the circular ring groove is reduced by the width of the circular ring groove on the outer side of the inner ring in an equal variable quantity one by one, the width range of the circular ring groove is 4-10mm, and the variable quantity of the width of the circular ring groove is the maximum difference value of the width of the circular ring groove divided by the number of the circular ring grooves.
10. The magnetorheological clutch having a grooved drive plate according to claim 8 or 9, wherein: the depth of the circular ring grooves is equal, and the depth of the circular ring grooves is 1-5 mm.
11. The magnetorheological clutch having a grooved drive plate of claim 8, wherein: the depth of the circular ring groove is reduced by the depth of the circular ring groove on the outer side of the inner ring one by one and the like, the depth range of the circular ring groove is 1-5mm, and the variation of the depth of the circular ring groove is the maximum difference of the depth of the circular ring groove divided by the number of the circular ring grooves.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111080498.3A CN113883184A (en) | 2021-09-15 | 2021-09-15 | Magneto-rheological clutch with groove structure transmission disc |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111080498.3A CN113883184A (en) | 2021-09-15 | 2021-09-15 | Magneto-rheological clutch with groove structure transmission disc |
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| Publication Number | Publication Date |
|---|---|
| CN113883184A true CN113883184A (en) | 2022-01-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111080498.3A Pending CN113883184A (en) | 2021-09-15 | 2021-09-15 | Magneto-rheological clutch with groove structure transmission disc |
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Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1079210A (en) * | 1953-04-21 | 1954-11-26 | Eaton Mfg Co | Advanced electromagnetic disc clutch |
| CH329486A (en) * | 1954-03-25 | 1958-04-30 | Smith & Sons Ltd S | Electromagnetic clutch |
| US5823309A (en) * | 1997-05-23 | 1998-10-20 | General Motors Corporation | Magnetorheological transmission clutch |
| US20020166745A1 (en) * | 2001-05-11 | 2002-11-14 | Visteon Global Technologies, Inc. | Multiple disc clutch pack having rheological film layer |
| CN101004196A (en) * | 2006-06-05 | 2007-07-25 | 倪平涛 | Controllable coupler of magnetic rheologic coupling wheel pair |
| US20080236976A1 (en) * | 2004-04-30 | 2008-10-02 | Magna Drivetrain Ag & Co Kg | Magnetorheological Clutch |
| JP2010242945A (en) * | 2009-04-09 | 2010-10-28 | Kurimoto Ltd | Magnetic viscous fluid device |
| CN205533876U (en) * | 2016-01-31 | 2016-08-31 | 宿州学院 | Magnetic current becomes permanent soft starting drive with higher speed with control system |
| CN111623056A (en) * | 2020-06-30 | 2020-09-04 | 厦门理工学院 | Braking device based on magneto-rheological effect |
| CN112032216A (en) * | 2020-09-18 | 2020-12-04 | 重庆理工大学 | Electromagnetic force extruded cross arc groove magneto-rheological clutch |
| CN112503113A (en) * | 2020-12-15 | 2021-03-16 | 吉林大学 | Self-adjusting rectangular limiting clutch based on magnetorheological fluid |
-
2021
- 2021-09-15 CN CN202111080498.3A patent/CN113883184A/en active Pending
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1079210A (en) * | 1953-04-21 | 1954-11-26 | Eaton Mfg Co | Advanced electromagnetic disc clutch |
| CH329486A (en) * | 1954-03-25 | 1958-04-30 | Smith & Sons Ltd S | Electromagnetic clutch |
| US5823309A (en) * | 1997-05-23 | 1998-10-20 | General Motors Corporation | Magnetorheological transmission clutch |
| US20020166745A1 (en) * | 2001-05-11 | 2002-11-14 | Visteon Global Technologies, Inc. | Multiple disc clutch pack having rheological film layer |
| US20080236976A1 (en) * | 2004-04-30 | 2008-10-02 | Magna Drivetrain Ag & Co Kg | Magnetorheological Clutch |
| CN101004196A (en) * | 2006-06-05 | 2007-07-25 | 倪平涛 | Controllable coupler of magnetic rheologic coupling wheel pair |
| JP2010242945A (en) * | 2009-04-09 | 2010-10-28 | Kurimoto Ltd | Magnetic viscous fluid device |
| CN205533876U (en) * | 2016-01-31 | 2016-08-31 | 宿州学院 | Magnetic current becomes permanent soft starting drive with higher speed with control system |
| CN111623056A (en) * | 2020-06-30 | 2020-09-04 | 厦门理工学院 | Braking device based on magneto-rheological effect |
| CN112032216A (en) * | 2020-09-18 | 2020-12-04 | 重庆理工大学 | Electromagnetic force extruded cross arc groove magneto-rheological clutch |
| CN112503113A (en) * | 2020-12-15 | 2021-03-16 | 吉林大学 | Self-adjusting rectangular limiting clutch based on magnetorheological fluid |
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