CN216383336U - Laser radar and rotation driving assembly - Google Patents
Laser radar and rotation driving assembly Download PDFInfo
- Publication number
- CN216383336U CN216383336U CN202122761292.9U CN202122761292U CN216383336U CN 216383336 U CN216383336 U CN 216383336U CN 202122761292 U CN202122761292 U CN 202122761292U CN 216383336 U CN216383336 U CN 216383336U
- Authority
- CN
- China
- Prior art keywords
- bearing
- drive assembly
- rotary drive
- laser radar
- central shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
The utility model provides a laser radar and a rotary driving component, wherein the rotary driving component is used for driving a detection device in the laser radar to rotate, and the rotary driving component comprises: a support part connected with the detecting device; the bearing is used for axially supporting the detecting device and comprises an inner ring, an outer ring and rolling bodies matched with the inner ring and the outer ring respectively, the outer ring is connected with the supporting part, and the rolling bodies are ceramic ball rolling bodies; the central shaft is connected with the inner ring and is suitable for driving the detection device to rotate. Because the ceramic ball rolling body has the characteristic of oil-free self-lubrication, lubricating grease is not needed between the ceramic ball rolling body and the inner and outer raceways of the bearing for lubrication, the risk of bearing failure caused by failure of the lubricating grease of the laser radar can be reduced, the situation that the rotary driving assembly cannot drive the detection device to rotate is avoided, and the service life of the laser radar is prolonged; furthermore, as the bearing does not need to be added with lubricating grease, the risk that the laser radar is difficult to start at low temperature due to the fact that the lubricating grease has too large viscous moment at low temperature can be avoided.
Description
Technical Field
The utility model relates to the field of laser detection, in particular to a laser radar and a rotary driving assembly.
Background
The laser radar is used for acquiring the distance between the laser radar and an object. In order to acquire target information around the radar in an all-round mode, the mechanical laser radar is characterized in that a light emitting device and a light receiving device are installed on a support capable of rotating 360 degrees, the support is connected with a central shaft through a bearing, and a rotating driving assembly drives the support to rotate. A deep groove ball bearing is generally adopted to connect the bracket and the central shaft.
However, on one hand, the viscous torque of the lubricating grease is too large at low temperature (-40 ℃ to 0 ℃) to cause the difficulty in starting the laser radar at low temperature, and on the other hand, after the lubricating grease runs for a period of time, the lubricating grease of the bearing can age and lose the lubricating function, and a bearing rolling body and a bearing raceway rub with each other when the support rotates at high speed, so that abnormal sound is generated, and the service life of the laser radar is influenced.
Therefore, how to improve the reliability of the rotation driving component of the laser radar is a technical problem which needs to be solved urgently.
SUMMERY OF THE UTILITY MODEL
The utility model provides a laser radar and a rotary driving assembly, which are used for improving the reliability of the rotary driving assembly.
In order to solve the above problem, an embodiment of the present invention provides a rotation driving assembly for driving a detection device in a laser radar to rotate, including:
a support connected to the probe;
the bearing is used for axially supporting the detection device and comprises an inner ring, an outer ring and rolling bodies matched with the inner ring and the outer ring respectively, the outer ring is connected with the supporting part, and the rolling bodies are ceramic ball rolling bodies;
and the central shaft is connected with the inner ring and is suitable for driving the detection device to rotate.
Optionally, the bearing includes a first bearing and a second bearing, the first bearing and the second bearing are both sleeved on the central shaft, and the second bearing and the first bearing are respectively located at two axial ends of the central shaft.
Optionally, the first bearing and the second bearing are symmetrical about an axially central cross-section of the central shaft.
Optionally, the outer ring is in interference fit with the support portion, and the material of the outer ring is the same as that of the support portion.
Optionally, the central shaft is clearance fit with the inner race.
Optionally, the material of the ceramic ball rolling element comprises any one of silicon nitride, zirconium oxide and silicon carbide.
Optionally, the ceramic ball rolling body has a coefficient of thermal expansion in the range of 0.6 × 10-6/℃～12.6×10-6/℃。
Optionally, the compressive strength of the ceramic ball rolling body is greater than or equal to 3500MPa, and the bending rigidity is greater than or equal to 900 MPa.
Optionally, the material of the inner ring and/or the outer ring of the bearing is bearing steel.
Optionally, the material of the outer ring and the support portion is a ceramic material.
Optionally, the bearing has a minimum radial play in the range of 7-23 um.
Optionally, the bearing has a minimum radial play in the range 11um-16 um.
Optionally, the minimum radial play range of the bearing is determined according to the accuracy of the bearing.
Optionally, the maximum interference between the support and the bearing is in the range of 14um-21 um.
Optionally, the maximum interference range is determined according to the minimum radial play range to avoid the bearing from rotating.
In order to solve the above problem, an embodiment of the present invention further provides a laser radar, including the above rotation driving assembly;
and the detection device is fixedly connected with the rotary driving component.
Optionally, the detecting means comprises light emitting means and light receiving means,
the light emitting device is used for emitting a detection light beam to a three-dimensional space;
the light receiving device is used for receiving an echo light beam formed by reflecting the probe light beam by a target in a three-dimensional space;
the bearing is used for axially supporting the light emitting device and the light receiving device.
Compared with the prior art, the technical scheme of the embodiment of the utility model has the following advantages:
the rotary driving component provided by the embodiment of the utility model is used for driving a detection device in a laser radar to rotate, and comprises: a support connected to the probe; the bearing is used for axially supporting the detection device and comprises an inner ring, an outer ring and rolling bodies matched with the inner ring and the outer ring respectively, the outer ring is connected with the supporting part, and the rolling bodies are ceramic ball rolling bodies; and the central shaft is connected with the inner ring and is suitable for driving the detection device to rotate. Because the ceramic ball rolling body has the characteristic of oil-free self-lubrication, lubricating grease is not needed between the ceramic ball rolling body and the inner and outer raceways of the bearing for lubrication, the risk of bearing failure caused by failure of the lubricating grease of the laser radar can be reduced, the situation that the rotary driving assembly cannot drive the detection device to rotate is avoided, and the service life of the laser radar is prolonged; further, because of the bearing need not to add lubricating grease, can avoid starting the difficult risk of difficulty when the low temperature because of lubricating grease viscous torque is too big when the low temperature leads to laser radar, reduce the risk that laser radar does not reach standard in the time that starts rotatory when the low temperature starts.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, it is obvious that the drawings in the following description are only embodiments of the present application, 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 structural diagram of a rotary drive assembly according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a partial structure of a rotary drive assembly according to an embodiment of the present invention;
fig. 3 is a schematic structural diagram of a laser radar according to an embodiment of the present invention;
FIG. 4 is another schematic diagram of the lidar shown in FIG. 3;
fig. 5 is a schematic structural diagram of another lidar provided by an embodiment of the present invention.
Detailed Description
In order to improve the reliability of the rotation driving component, an embodiment of the present invention provides a laser radar and a rotation driving component thereof, wherein the rotation driving component is used for driving a detection device in the laser radar to rotate, and includes: a support connected to the probe; the bearing is used for axially supporting the detection device and comprises an inner ring, an outer ring and rolling bodies matched with the inner ring and the outer ring respectively, the outer ring is connected with the supporting part, and the rolling bodies are ceramic ball rolling bodies; and the central shaft is connected with the inner ring and is suitable for driving the detection device to rotate.
Because the ceramic ball rolling body has the characteristic of oil-free self-lubrication, lubricating grease is not needed between the ceramic ball rolling body and the inner and outer raceways of the bearing for lubrication, the risk of bearing failure caused by failure of the lubricating grease of the laser radar can be reduced, the situation that the rotary driving assembly cannot drive the detection device to rotate is avoided, and the service life of the laser radar is prolonged; further, because of the bearing need not to add lubricating grease, can avoid starting the difficult risk of difficulty when the low temperature because of lubricating grease viscous torque is too big when the low temperature leads to laser radar, reduce the risk that laser radar does not reach standard in the time that starts rotatory when the low temperature starts.
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.
It should be noted that the indication of the direction or the positional relationship referred to in the present specification is based on the direction or the positional relationship shown in the drawings, and is only for convenience of description and simplification of description, and it is not intended to indicate or imply that the indicated device must have a specific direction, be configured in a specific direction, and thus, should not be construed as limiting the present invention.
Referring to fig. 1-3, fig. 1 is a schematic structural diagram of a rotation driving assembly according to an embodiment of the present invention; FIG. 2 is a schematic diagram of a partial structure of a rotary drive assembly according to an embodiment of the present invention; fig. 3 is a schematic structural diagram of a laser radar according to an embodiment of the present invention.
As shown in the drawings, a rotary driving assembly 1 according to an embodiment of the present invention is used for driving a detection device in a laser radar to rotate, and includes:
a support 10 connected to the probe 8;
the bearing 20 is used for axially supporting the detecting device, the bearing 20 comprises an inner ring 22, an outer ring 21 and a rolling body 23 respectively matched with the inner ring 22 and the outer ring 21, the outer ring 21 is connected with the supporting part 10, and the rolling body 23 is a ceramic ball rolling body;
a central shaft 30 connected to the inner ring 22, wherein the central shaft 30 is adapted to rotate the detecting device.
The ceramic ball rolling body has the characteristics of high temperature resistance, cold resistance, wear resistance, corrosion resistance, magnetoelectric insulation resistance, oil-free self-lubrication, high rotating speed and the like, and replaces the steel ball rolling body with lubricating grease, so that the risk of bearing failure caused by failure of the lubricating grease of the laser radar can be reduced, the situation that the rotary driving assembly cannot drive the detection device to rotate is avoided, and the service life of the laser radar is prolonged; the risk that the laser radar is difficult to start at low temperature due to overlarge viscous moment of lubricating grease at low temperature can be avoided, and the risk that the time for starting the laser radar to rotate at low temperature is not up to standard is reduced.
In a specific embodiment, the material of the ceramic ball rolling element 23 may be selected from silicon nitride (Si3N 4). The silicon nitride rolling element 23 has the characteristics of low density, high hardness, low friction coefficient, magneto-electric insulation resistance, wear resistance, self-lubrication and the like. Of course, in other embodiments, the material of the ceramic ball rolling element may also be zirconia or silicon carbide.
In order to prevent the bearing 20 and the inner surface of the support portion 10 from being deformed by expansion and contraction due to temperature change, it is necessary that the temperature coefficients of the bearing outer ring material and the support portion inner surface material are kept as uniform as possible, and therefore, the material of the outer ring 21 is the same as that of the support portion 10. In a specific embodiment, the material of the outer ring 21 and the support portion 10 may be both bearing steel. Of course, in other embodiments, the material of the bearing outer ring and the material of the inner surface of the support part may be the same. In another embodiment, the material of the outer ring 21 and the support portion 10 is a ceramic material.
Under the harsh scene of laser radar service condition, in order to satisfy the demands of high rotational speed, anti strong impact and high load, in a specific embodiment, bearing 20 can adopt mixed ceramic bearing: the material of the inner ring 22 and/or the outer ring 21 of the bearing 20 is bearing steel, for example, the material may be GCr15, the material of the rolling element 23 is ceramic, for example, the material may be silicon nitride (Si3N4), and the mixed ceramic bearing has strong loading capacity, is suitable for high rotation speed, resists strong impact, and has the advantages of low cost, good corrosion resistance, and the like. Of course, in other embodiments, the bearing 20 may also be an all-ceramic bearing, that is, the inner ring 22, the outer ring 21 and the rolling elements 23 are made of ceramic, and accordingly, the material of the support portion 10 engaged with the outer ring 21 is also made of ceramic material.
It is easily understood that, in order to prevent the bearing 20 from failing to operate normally due to the change of the bearing play during the temperature change, the thermal expansion coefficient of the ceramic ball rolling elements 23 is preferably not too large or too small to be close to that of the inner ring 22 or the outer ring 21, and therefore, in one embodiment, the thermal expansion coefficient of the ceramic ball rolling elements 23 may be in the range of 0.6 × 10-6/℃～12.6×10-6The coefficient of thermal expansion of the ceramic ball rolling element 23 may be 3.2X 10/. degree.C, for example-6/℃。
Of course, the strength of the ceramic ball rolling elements 23 should satisfy the supporting effect of the bearing 20, and therefore, in a specific embodiment, the compressive strength of the ceramic ball rolling elements 23 may be not less than 3500Mpa, and the bending rigidity may be not less than 900 Mpa.
It can be seen that, in the rotary drive assembly 1 provided by the embodiment of the present invention, since the bearing employs the ceramic ball rolling element, and the ceramic ball rolling element has the oil-free self-lubricating property, lubricating grease is not required between the rolling element and the inner and outer raceways of the bearing for lubrication, and the use of the ceramic ball rolling element can reduce the risk of bearing failure caused by grease failure, avoid that the rotary drive assembly 1 cannot drive the detection device to rotate, and prolong the service life of the laser radar; further, as the bearing of the rotary driving assembly 1 provided by the embodiment of the utility model does not need to be added with lubricating grease, the risk that the laser radar is difficult to start at low temperature due to the fact that the viscous torque of the lubricating grease is too large at low temperature can be avoided, and the risk that the time for the laser radar to start to rotate at low temperature does not reach the standard is reduced.
With continued reference to fig. 1 and fig. 2, in order to ensure the supporting effect, the bearing 20 may include a first bearing 201 and a second bearing 202, the first bearing 201 and the second bearing 202 are both sleeved on the central shaft 30, and the first bearing 201 and the second bearing 202 are respectively located at two axial ends of the central shaft 30.
Specifically, the bearing 20 is sleeved between the central shaft 30 and the support portion 10, the support portion 10 includes a first shoulder surface (not shown by reference numerals in the drawings) and a second shoulder surface (not shown by reference numerals in the drawings), the central shaft 30 is disposed inside the support portion 10 and includes a fixing portion (not shown by reference numerals in the drawings) and an axial support portion 50 respectively located at two end portions thereof, two end surfaces (including flange end surfaces) of the first bearing 201 are axially supported on the first shoulder surface and an end surface of the bearing fixing member 40 respectively, and two end surfaces (including flange end surfaces) of the second bearing 202 are axially supported on the second shoulder surface and a support surface of the axial support portion 50 respectively.
When assembling, firstly, the second bearing 202 is sleeved on the central shaft 30, the second bearing 202 is in clearance fit with the central shaft 30, the end face of the second bearing 202 is supported on the supporting face of the axial supporting portion 50, then the supporting portion 10 is sleeved on the central shaft 30 with a first thrust, the second shoulder face of the supporting portion is supported on the flange end face of the second bearing 202, the second bearing 202 is in interference fit with the supporting portion 10, then the first bearing 201 is sleeved on the central shaft 30 with a second thrust until the flange end face of the first bearing 201 is supported on the first shoulder face of the supporting portion 10, the first bearing 201 is in clearance fit with the central shaft 30, is in interference fit with the supporting portion 10, and is fixed through the bearing fixing component 40, so that the end face of the bearing fixing component 40 is connected with the other end face of the first bearing 201.
Specifically, the first bearing 201 may be a 608 type bearing, and the second bearing 202 may be a 698 type bearing, so as to improve the supporting function of the bearings. Of course, in other embodiments, the type of the first bearing 201 and the type of the second bearing 202 may be the same, and may be both 608 bearings, or 698 bearings or other bearings.
It can be seen that, by supporting the two first bearings 201 and the two second bearings 202 on the first shoulder surface and the second shoulder surface of the support 10, respectively, and further limiting the axial positions of the first bearing 201 and the second bearing 202 through the bearing fixing component 40 and the axial support 50, not only the rotational support between the central shaft 30 and the support 10 can be realized, but also the support can be provided in the axial direction of the bearing 20, the damage of the bearing 20 is reduced, the stability and reliability of the rotary drive assembly 1 are further improved, and the service life of the rotary drive assembly is prolonged.
It should be noted that the fixing portion described herein is a portion where the upper end portion of the central shaft 30 is assembled with the bearing fixing part 40 in the drawing, and the axial supporting portion 50 not only supports the second bearing 202 and provides an axial supporting force for the second bearing 202, but also is adapted to be connected with a housing portion of the rotary drive assembly 1. In fig. 2, the direction a represents the axial direction, and the direction R represents the radial direction.
In a specific embodiment, the bearing 20 may be a thin-walled deep-groove ball bearing, the thin-walled deep-groove ball bearing is integrally embedded between the central shaft 30 and the support portion 10, and the radial thickness of the thin-walled deep-groove ball bearing is relatively thin, so that the requirement of gap installation between the central shaft 30 and the support portion 10 can be met, and the thin-walled deep-groove ball bearing can be supported on the first shoulder surface and the second shoulder surface to bear an axial force (the axial force is shown as F in fig. 2), and of course, in order to ensure the balance of the forces applied to the upper end and the lower end, the first bearing 201 and the second bearing 202 are configured to have the same shape. Of course, in another embodiment, the bearing may also be a flange outer ring deep groove ball bearing, that is, a flange bearing, and a flange portion of the flange bearing is supported on the first shoulder surface or the second shoulder surface and bears the axial acting force.
Of course, in other embodiments, the bearing 20 may be a single-row deep groove ball bearing.
Further, in order to improve the stability of the bearing 20 to support the support portion 10, in a specific embodiment, the first bearing 201 and the second bearing 202 are symmetrical with respect to the axial center cross section of the central shaft 30.
It is understood that the axial center cross section of the center shaft 30 refers to a cross section in which the center of the center shaft 30 is located in the axial direction of the center shaft 30.
In order to prevent the inner ring 22 from slipping relative to the central shaft 30 and the outer ring 21 from slipping relative to the support portion 10, so-called "bouncing" is generated during rotation, and abnormal noise is generated, so that the service life of the radar is affected, in a specific embodiment, the support portion 10 and the outer ring 21 are in interference fit, the increase of the play caused by collision and abrasion between the rolling bodies 23 and the raceways is reduced, the outer ring 21 is in close contact with the inner surface of the support portion 10, and the outer ring 21 is prevented from slipping relative to the support portion 10.
The central shaft 30 and the inner ring 22 may adopt a clearance fit, in order to avoid the inner ring 22 from slipping relative to the central shaft 30, in a specific embodiment, an instant adhesive may be applied to the installation position of the inner ring 22 and the central shaft 30 to bond the bearing 20 and the central shaft 30 together, so as to enhance the adhesive force between the inner ring 22 and the central shaft 30, effectively prevent the bearing 20 from slipping relative to the central shaft 30, and improve the installation stability of the bearing 20.
It will be appreciated by those skilled in the art that when the outer race 21 is mounted with an interference fit with the support portion 10, the outer race 21 will contract. After the interference fit, the reduction of the diameter of the outer ring groove bottom should not be larger than the minimum radial play of the bearing, so as to ensure that the bearing does not rotate due to the interference fit between the outer ring 21 and the support portion 10, that is, the maximum interference between the support portion 10 and the bearing 20 needs to be matched with the minimum radial play of the bearing 20.
In particular, in order to guarantee a minimum radial play of the bearing 20, the support 10 may be chosen as a bearing seat of SUS630 type.
In a specific embodiment, the minimum radial play of the bearing 20 is in the range of 7um to 23 um. The minimum radial play range of the bearing 20 is determined according to the accuracy and temperature of said bearing 20.
In a specific embodiment, the minimum radial play of the bearing 20 is in the range of 11um to 16 um.
Because the Young modulus and the Poisson ratio of the material of the outer ring and the material of the supporting part are the same, the reduction amount of the diameter of the groove bottom of the outer ring of the bearing is obtained according to the following formula:
wherein dE is the diameter of the groove bottom of the outer ring; d-bearing outer ring diameter; dh-diameter of the inner ring of the support part; Δ f — maximum interference; δ E is the outer ring groove bottom diameter reduction amount.
Based on the above formula, in combination with the maximum allowable reduction of the outer ring groove bottom diameter, that is, the minimum radial play of the bearing, the maximum interference between the support portion and the bearing can be calculated.
Obtaining the maximum interference amount delta f according to the following formula:
in a specific embodiment, the maximum interference between the support 10 and the bearing 20 is in the range of 14um-21 um.
According to the above calculation formula, the maximum interference is in a positive correlation with the minimum radial play of the bearing, that is, the larger the minimum radial play is, the larger the maximum interference is.
And, since the minimum radial play is related to the operating temperature of the bearing, the maximum interference is also related to the operating temperature of the bearing,
such as: when the temperature is normal, the range of the minimum radial play can be 11um-16um, when the temperature is minus 40 degrees, the range can be 7um-12um, when the temperature is 110 degrees, the range can be 18-23um, correspondingly, the maximum interference can be 17um, when the temperature is minus 40 degrees, the range can be 14.5um-15um, and when the temperature is 110 degrees, the range can be 20.1um-21.5 um.
Based on the experimental result, the value of the maximum interference can be referred to the following table, wherein the model of the first bearing is 608 bearings, and the model of the second bearing is 698 bearings.
In a specific embodiment, the maximum interference range is determined according to the minimum radial play range to avoid the bearing from locking, and specifically, based on the minimum radial play and the corresponding maximum interference range set in different temperature ranges, the bearing can be prevented from locking in the whole temperature range.
Of course, the tolerance of the outer diameter of the bearing outer ring can be determined according to the bearing precision, and the tolerance of the supporting part and the bearing matching surface can be determined according to the maximum interference.
In addition to the fact that it is to be noted that, during the aforesaid assembly, the first thrust and the second thrust are associated with a maximum interference range and with said minimum radial play range, both of which can be calculated by the following equations:
Fpush＝μπDhPf
wherein: fpush-a thrust force; μ — coefficient of friction between bearing and central shaft; d-the diameter of the outer ring surface of the bearing outer ring; h- -bearing height; pfThe interference fit surface pressure may be obtained by the following formula:
wherein dE is the diameter of the groove bottom of the outer ring; d-bearing outer ring diameter; dh-diameter of the inner ring of the support part; Δ f — maximum interference; e ═ young's modulus.
In order to solve the foregoing problem, an embodiment of the present invention further provides a laser radar, including:
the aforementioned rotary drive assembly 1;
and the detection device is fixedly connected with the rotary driving assembly 1.
Specifically, the detection means includes light emitting means and light receiving means;
the light emitting device is used for emitting a detection light beam to a three-dimensional space;
the light receiving device is used for receiving an echo light beam formed by reflecting the probe light beam by a target in a three-dimensional space;
the bearing is used for axially supporting the light emitting device and the light receiving device.
Of course, since the rotary drive assembly 1 includes the aforementioned first bearing 201 and second bearing 202, the laser radar provided in the embodiment of the present application also includes the aforementioned first bearing 201 and second bearing 202.
Specifically, referring to fig. 4 and fig. 5, fig. 4 is another schematic structural diagram of the laser radar shown in fig. 3, and fig. 5 is a schematic structural diagram of another laser radar provided in the embodiment of the present invention.
The lidar provided by the embodiment of the application may have a structure as shown in fig. 4, the lidar includes a central shaft 30 and a bearing 20, the bearing 20 may include a first bearing 201 and a second bearing 202, and the central shaft 30 is only located at a lower portion of the lidar and does not penetrate through the whole of the lidar; of course, the laser radar provided in the embodiment of the present application may have a structure as shown in fig. 5, which is different from the laser radar of fig. 4 in that the central shaft 30 penetrates the whole of the laser radar.
According to the laser radar provided by the embodiment of the utility model, as the bearing of the rotation driving component 1 adopts the ceramic ball rolling body, the ceramic ball rolling body has the oil-free self-lubricating property, lubricating grease is not needed between the rolling body and the inner and outer raceways of the bearing for lubrication, the risk of bearing failure caused by failure of the lubricating grease can be reduced by adopting the ceramic ball rolling body, the rotation driving component 1 can not drive the detection device to rotate, and the service life of the laser radar is prolonged; further, as the bearing of the rotary driving assembly 1 provided by the embodiment of the utility model does not need to be added with lubricating grease, the risk that the laser radar is difficult to start at low temperature due to the fact that the viscous torque of the lubricating grease is too large at low temperature can be avoided, and the risk that the time for the laser radar to start to rotate at low temperature does not reach the standard is reduced.
Although the embodiments of the present invention have been disclosed, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the utility model as defined in the appended claims.
Claims (17)
1. A rotary drive assembly for driving rotation of a lidar detection device, comprising:
a support connected to the probe;
the bearing is used for axially supporting the detection device and comprises an inner ring, an outer ring and rolling bodies matched with the inner ring and the outer ring respectively, the outer ring is connected with the supporting part, and the rolling bodies are ceramic ball rolling bodies;
and the central shaft is connected with the inner ring and is suitable for driving the detection device to rotate.
2. The rotational drive assembly as claimed in claim 1, wherein the bearing comprises a first bearing and a second bearing, the first bearing and the second bearing are both sleeved on the central shaft, and the second bearing and the first bearing are respectively located at two axial ends of the central shaft.
3. The rotary drive assembly as recited in claim 2, wherein the first bearing and the second bearing are symmetrical about an axially central cross-section of the central shaft.
4. The rotary drive assembly as recited in claim 1, wherein the outer race is an interference fit with the support portion and the material of the outer race is the same as the material of the support portion.
5. The rotary drive assembly as recited in claim 1, wherein the central shaft is clearance fit with the inner race.
6. A rotary drive assembly as claimed in any one of claims 1 to 5, wherein the material of the ceramic ball rolling elements comprises any one of silicon nitride, zirconia, silicon carbide.
7. A rotary drive assembly as claimed in any one of claims 1 to 5, wherein the ceramic ball rolling elements have a coefficient of thermal expansion in the range 0.6 x 10-6/℃～12.6×10-6/℃。
8. A rotary drive assembly according to any one of claims 1 to 5, wherein the ceramic ball rolling elements have a compressive strength of at least 3500MPa and a bending stiffness of at least 900 MPa.
9. A rotary drive assembly according to any one of claims 1 to 5, wherein the material of the inner and/or outer race of the bearing is bearing steel.
10. A rotary drive assembly according to any one of claims 1 to 5, wherein the material of the outer race and the support portion is a ceramic material.
11. A rotary drive assembly according to any one of claims 1 to 5, wherein the bearing has a minimum radial play in the range 7um to 23 um.
12. A rotary drive assembly according to claim 11, wherein the minimum radial play of the bearing is in the range 11um-16 um.
13. A rotary drive assembly as claimed in claim 11, wherein the minimum radial play range of the bearing is determined in dependence on the accuracy of the bearing.
14. The rotary drive assembly as recited in claim 11, wherein a maximum interference between the support and the bearing is in a range of 14um to 21 um.
15. The rotary drive assembly as recited in claim 14, wherein the maximum interference range is determined based on the minimum radial play range to avoid the bearing from seizing.
16. A lidar, comprising:
the rotary drive assembly of any one of claims 1-15;
and the detection device is fixedly connected with the rotary driving component.
17. Lidar according to claim 16, wherein said detection means comprises light emitting means and light receiving means,
the light emitting device is used for emitting a detection light beam to a three-dimensional space;
the light receiving device is used for receiving an echo light beam formed by reflecting the probe light beam by a target in a three-dimensional space;
the bearing is used for axially supporting the light emitting device and the light receiving device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122761292.9U CN216383336U (en) | 2021-11-11 | 2021-11-11 | Laser radar and rotation driving assembly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122761292.9U CN216383336U (en) | 2021-11-11 | 2021-11-11 | Laser radar and rotation driving assembly |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN216383336U true CN216383336U (en) | 2022-04-26 |
Family
ID=81251775
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122761292.9U Active CN216383336U (en) | 2021-11-11 | 2021-11-11 | Laser radar and rotation driving assembly |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN216383336U (en) |
-
2021
- 2021-11-11 CN CN202122761292.9U patent/CN216383336U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6669368B2 (en) | Spindle motor and bearing assembly | |
| US5210665A (en) | Floppy disk apparatus having an improved disk rotating mechanism | |
| JP2006525466A (en) | Vacuum pump | |
| JPH1047357A (en) | Rolling bearing | |
| US6273230B1 (en) | Ball bearing and electromagnetic clutch having the same | |
| JPH11117942A (en) | Rolling bearing | |
| CN216383336U (en) | Laser radar and rotation driving assembly | |
| JPH02271106A (en) | Sliding bearing device | |
| WO2006117515A1 (en) | Vacuum pump | |
| JP2014159869A (en) | Rolling bering device | |
| KR20040088068A (en) | Pulley bearing for engine auxiliaries | |
| CN116105033A (en) | Laser radar and rotary driving assembly | |
| JP2007092863A (en) | Bearing device | |
| JP3490074B2 (en) | Magnetic bearing device | |
| JP2004011801A (en) | Deep groove ball bearing and fan coupling device | |
| JP2004308735A (en) | Electric corrosion-proof bearing | |
| US11859661B2 (en) | Deep groove ball bearing and applications thereof | |
| JP2002139048A (en) | Electric corrosion preventive rolling bearing | |
| JPH10159579A (en) | Rolling bearing for engine auxiliary machine | |
| JPH10176714A (en) | Magnetic bearing device | |
| JP3061168B2 (en) | Magnetic bearing device | |
| JP2003074545A (en) | Designing method of ball bearing and ball bearing therewith | |
| US7073947B2 (en) | Bearing structure of a motor | |
| JPH02493Y2 (en) | ||
| Tanimoto et al. | Evaluation of extra-small ceramic ball bearings |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |