WO2021052117A1 - 一种移相器驱动装置及电调天线 - Google Patents

一种移相器驱动装置及电调天线 Download PDF

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Publication number
WO2021052117A1
WO2021052117A1 PCT/CN2020/111047 CN2020111047W WO2021052117A1 WO 2021052117 A1 WO2021052117 A1 WO 2021052117A1 CN 2020111047 W CN2020111047 W CN 2020111047W WO 2021052117 A1 WO2021052117 A1 WO 2021052117A1
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WIPO (PCT)
Prior art keywords
gear
clutch gear
clutch
central axis
transmission
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PCT/CN2020/111047
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English (en)
French (fr)
Inventor
吴晗
范雄辉
张申科
孙彦明
吴卫华
Original Assignee
武汉虹信科技发展有限责任公司
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Application filed by 武汉虹信科技发展有限责任公司 filed Critical 武汉虹信科技发展有限责任公司
Publication of WO2021052117A1 publication Critical patent/WO2021052117A1/zh

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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01Q—ANTENNAS, i.e. RADIO AERIALS
    • H01Q3/00—Arrangements for changing or varying the orientation or the shape of the directional pattern of the waves radiated from an antenna or antenna system
    • H01Q3/26—Arrangements for changing or varying the orientation or the shape of the directional pattern of the waves radiated from an antenna or antenna system varying the relative phase or relative amplitude of energisation between two or more active radiating elements; varying the distribution of energy across a radiating aperture
    • H01Q3/30—Arrangements for changing or varying the orientation or the shape of the directional pattern of the waves radiated from an antenna or antenna system varying the relative phase or relative amplitude of energisation between two or more active radiating elements; varying the distribution of energy across a radiating aperture varying the relative phase between the radiating elements of an array
    • H01Q3/32—Arrangements for changing or varying the orientation or the shape of the directional pattern of the waves radiated from an antenna or antenna system varying the relative phase or relative amplitude of energisation between two or more active radiating elements; varying the distribution of energy across a radiating aperture varying the relative phase between the radiating elements of an array by mechanical means

Definitions

  • This application relates to the field of mobile communication base station antennas, and in particular to a phase shifter driving device and a base station antenna.
  • phase shifter of the base station antenna In present, manual or electric methods are generally used to change the phase of the phase shifter of the base station antenna in the mobile communication system.
  • the traditional electric method is that each phase shifter adopts an independent phase adjustment device, but with the limitation of mobile base station resources, multi-frequency Antennas have increasingly become a demand trend.
  • the current mainstream electric adjustment method is to use a downtilt angle adjustment device for each frequency band antenna, that is, a multi-frequency antenna requires multiple downtilt angle adjustment devices.
  • antenna downtilt adjustment device As the frequency of antennas is more and more fusion, there are more and more adjustment devices, which leads to more and more pressures on the structural layout, weight, cost, and miniaturization of antennas.
  • the overall size of the antenna downtilt adjustment device is relatively large, which cannot meet the development trend of miniaturization.
  • the purpose of this application is to provide a phase shifter driving device and an electrically adjustable antenna, which are used to solve or partially solve the problem that the overall size of the current antenna downtilt adjustment device is large and cannot meet the development trend of miniaturization.
  • the first aspect of the present application provides a phase shifter drive device, which includes a drive gear, a shift mechanism, and a transmission mechanism.
  • the shift mechanism includes a push-pull component and at least one clutch gear.
  • the mechanism includes a transmission gear corresponding to the clutch gear one-to-one; the central axis of the clutch gear, the central axis of the drive gear, and the central axis of the drive gear are parallel to each other, and at least one of the clutch gears is in the drive
  • the four sides of the gears are arranged along the same circumference, and at least one of the transmission gears is arranged along the same circumference around the clutch gear; the clutch gear and the drive gear and/or the transmission gear are separated from each other along the direction of the central axis.
  • the clutch gear moves along the central axis to mesh with the drive gear and the transmission gear at the same time; the push-pull member is used to selectively push the clutch gear to reciprocate along the central axis.
  • an electrically adjustable antenna which includes the phase shifter driving device described in the above solution.
  • the clutch gear is arranged around the driving gear in a circumferential distribution, and the transmission gear is circumferentially distributed around the clutch gear, which can reduce the space required in the width direction, and
  • Each clutch gear can be meshed with the drive gear, and each clutch gear and transmission mechanism can be driven by one drive gear, which can adjust the phase of multiple phase shifters, and reduce the number of drive mechanisms.
  • the space required for installation; and the clutch gear and the transmission gear are respectively arranged on the same plane, which can avoid the space occupied by staggered arrangement in the length direction, thereby reducing the space required in the length direction; the drive device can be miniaturized under conventional technology , To achieve the purpose of miniaturization of the antenna and reduce the manufacturing cost.
  • FIG. 1 is a schematic diagram of disassembling a phase shifter driving device according to an embodiment of the application
  • phase shifter driving device is an overall schematic diagram of a phase shifter driving device according to an embodiment of the application
  • Fig. 3 is a schematic cross-sectional view of a shift mechanism in an embodiment of the application.
  • Fig. 4 is a schematic diagram of a turntable in an embodiment of the application.
  • Fig. 5 is a schematic diagram of a connecting piece in an embodiment of the application.
  • Fig. 6 is a schematic diagram of the connection structure of the shift mechanism in the embodiment of the application.
  • 104 connector
  • 105 clutch gear
  • 106 first elastic member
  • 103a Annular groove
  • 103b Protruding edge
  • 104a Protruding part
  • connection should be understood in a broad sense, unless otherwise clearly specified and limited.
  • it can be a fixed connection or a detachable connection.
  • Connected or integrally connected it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication between two components.
  • connection should be understood in a broad sense, unless otherwise clearly specified and limited.
  • it can be a fixed connection or a detachable connection.
  • Connected or integrally connected it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication between two components.
  • the specific meanings of the above-mentioned terms in this application can be understood under specific circumstances.
  • the phase shifter drive device includes: a drive gear 111, a shifting mechanism, and a transmission mechanism.
  • the shifting mechanism includes a push-pull component and at least A clutch gear 105
  • the transmission mechanism includes a transmission gear 112 corresponding to the clutch gear 105 one-to-one; the driving gear 111 rotates under the action of the input power.
  • the transmission gear 112 and the phase shifter are connected in a one-to-one correspondence, and the rotation of the transmission gear 112 drives the phase shifter to move for phase adjustment.
  • the central axis of the clutch gear 105, the central axis of the drive gear 111, and the central axis of the drive gear 112 are parallel to each other.
  • At least one clutch gear 105 is arranged around the drive gear 111 along the same circumference, and at least one drive gear 112 is in the clutch
  • the circumferences of the gears 105 are arranged along the same circumference; that is, the centers of all the clutch gears 105 are located on the same circumference, that is, all the clutch gears 105 are located on the same plane perpendicular to the axial direction.
  • the centers of all the transmission gears 112 are located on the same circumference, that is, all the transmission gears 112 are located on the same plane perpendicular to the axial direction.
  • the clutch gear 105 moves along the central axis to mesh with the drive gear 111 and the transmission gear 112 at the same time; the push-pull component is used to selectively push the clutch gear 105 Move back and forth along the central axis. That is, the clutch gear 105 and at least one of the driving gear 111 and the transmission gear 112 are misaligned in the direction of the central axis, that is, in the length direction of the phase shifter driving device. That is, the initial position clutch gear 105 does not mesh with the driving gear 111 and the transmission gear 112 at the same time, and there is no power transmission.
  • the wheel distance between the clutch gear 105 and the drive gear 111 and the transmission gear 112 meets the gear meshing size, so that the clutch gear 105 can mesh with the drive gear 111 and the transmission gear 112 at the same time when the clutch gear 105 slides in the axial direction.
  • At least one clutch gear 105 meshes with the drive gear 111 on the inner side and meshes with the transmission gear 112 on the outer side. The position where the clutch gear 105 meshes with the driving gear 111 and the transmission gear 112 at the same time is the working position of the clutch gear 105.
  • the driving gear 111 is used to drive the meshing clutch gear 105 to rotate, and then drive the corresponding transmission gear 112 to rotate, thereby adjusting the phase shifter connected to it.
  • the push-pull component is used to selectively push the clutch gear 105 to move along the central axis.
  • the push-pull component selectively pushes the clutch gear 105 to move to the working position and reset to the initial position, so as to realize the switching between different clutch gears 105.
  • the drive gear 111 and the transmission gear 112 corresponding to the clutch gear 105 mesh with the clutch gear 105 at the same time, so that the power can be transmitted to the transmission mechanism.
  • the mechanism drives the phase shifter to move for adjustment.
  • the push-pull component can push the clutch gear 105 in the working position to reset, that is, push the clutch gear 105 in the axial direction to the initial position, that is, a position where power transmission cannot be achieved. Then the push-pull component pushes the next clutch gear 105 to move in the axial direction to the working position, and adjust the next phase shifter.
  • the push-pull component can selectively push any clutch gear 105 to the working position in the axial direction, so that any phase shifter that needs to be adjusted can be adjusted.
  • the clutch gear 105 is arranged around the driving gear 111 in a circumferential distribution, and the transmission gear 112 is circumferentially distributed around the clutch gear 105, which can reduce the space required in the width direction.
  • each clutch gear 105 can be meshed with the drive gear 111, and each clutch gear 105 and the transmission mechanism can be driven by one drive gear 111, which can adjust the phase of multiple phase shifters and reduce the drive mechanism at the same time.
  • the number of installations reduces the space required for installation; and the clutch gear 105 and the transmission gear 112 are respectively arranged on the same plane, which can avoid the space occupied by staggered arrangement in the length direction, thereby reducing the space required in the length direction; the drive device can The miniaturization is achieved under the conventional process, achieving the purpose of miniaturizing the antenna and reducing the manufacturing cost.
  • this embodiment describes various setting structures of the initial position.
  • the clutch gear 105 meshes with the drive gear 111, is spaced from the drive gear 112 along the central axis, and the tooth width of the drive gear 111 is greater than or equal to the maximum travel path of the clutch gear 105; that is, when the clutch gear 105 is in the initial position
  • the clutch gear 105 and the drive gear 111 always maintain a meshing state.
  • the clutch gear 105 reaches the working position, it only needs to mesh with the transmission gear 112.
  • the clutch gear 105 meshes with the transmission gear 112 and is spaced from the drive gear 111 along the central axis direction, and the tooth width of the transmission gear 112 is greater than or equal to the maximum movement path of the clutch gear 105; that is, when the clutch gear 105 is in the initial position and the working position When reciprocating between, the clutch gear 105 and the transmission gear 112 always keep in meshing state. When the clutch gear 105 reaches the working position, it only needs to mesh with the driving gear 111.
  • the first two arrangement structures can be adopted, which can reduce the difficulty of meshing when the clutch gear 105 reaches the working position, and facilitate the smooth meshing with the driving gear 111 and the transmission gear 112 at the same time.
  • this embodiment proposes a specific push-pull component structure, which can realize the switching of different clutch gears 105.
  • the push-pull component includes an active part and a hollow cylindrical turntable 103 with at least one open end; the active part is used to drive the turntable 103 to rotate; each clutch gear 105 is sleeved on the switching shaft.
  • the central axis of the turntable 103 is parallel to the central axis of the clutch gear 105, and the open end of the turntable 103 faces the clutch gear 105.
  • the inner wall of the turntable 103 is provided with an annular groove 103a along the circumferential direction.
  • the first end of at least one switching shaft is plugged and slidably connected with the annular groove 103a, and a part of the annular groove 103a is offset in the axial direction to form a convex Along 103b.
  • the convex edge 103b and other parts of the annular groove 103a are misaligned in the direction of the central axis of the turntable 103; the convex edge 103b and other parts of the annular groove 103a are connected to form a ring shape. That is, when the turntable 103 rotates, the first end of the switching shaft will slide to the convex edge 103b in the other parts of the annular groove 103a, and it will also slide from the convex edge 103b to other parts, so that the switching shaft and the clutch gear 105 are in position. Displacement in the direction of the central axis.
  • the first end of the switching shaft is connected to the annular groove 103a through the connecting piece 104.
  • the side wall of the first end of the connecting piece 104 is provided with a convex
  • the raised portion 104a and the raised portion 104a are inserted into the annular groove 103a, and the second end 104b of the connecting piece is fixedly connected with the first end of the switching shaft in the axial direction.
  • the second end of the switching shaft is sleeved with a first elastic member 106.
  • One end of the first elastic member 106 is connected to the clutch gear 105 and the other end is fixedly arranged.
  • An elastic member 106 is initially in a natural state.
  • the first end of the connecting piece 104 is inserted into the inside of the turntable 103 from the open end of the turntable 103 to be connected to the annular groove 103a on the side wall of the turntable 103.
  • the annular groove 103a is on the inner wall of the turntable 103, and the notch faces the center axis of the turntable 103.
  • the two groove walls block and locate the protrusion 104a of the first end of the connecting member 104 in the direction of the center axis to realize the push-pull effect.
  • Each clutch gear 105 corresponds to a switching shaft, and each switching shaft corresponds to a connecting piece 104.
  • At least one end protrusion 104a of the connecting member 104 is inserted into the annular groove 103a and is slidably connected with the annular groove 103a.
  • the annular groove 103a is provided with groove protrusions 103b along the axial direction.
  • the specific switching operation process of the push-pull component is as follows: in the initial state, the protrusion 104a of one end of the connecting piece 104 is inserted into the groove protrusion of the annular groove 103a Outside 103b; the clutch gear 105 is located between the turntable 103 and the transmission gear 112.
  • the first input power sequentially drives the active shift gear 101, the driven shift gear 102, and the turntable 103 to rotate, and the protrusion 104a of one end of the connecting piece 104 slides in the annular sliding groove .
  • the clutch gear 105 moves in the axial direction to the transmission gear 112, meshes with the transmission gear 112, and adjusts the corresponding phase shifter.
  • the first elastic member 106 is in a compressed state.
  • the turntable 103 rotates so that the convex edge 103b of the top groove is disconnected from the connecting piece 104 of the clutch gear 105 corresponding to the last adjusted phase shifter, then the previous clutch gear 105 Under the action of pulling back the other end of the first elastic member 106 and the connecting member 104, it resets and returns to the initial state.
  • the switch can be realized by rotating the groove and convex edge 103b on the turntable 103 to the connecting piece 104 of the clutch gear 105 corresponding to the phase shifter to be adjusted.
  • the turntable 103 When the clutch gear 105 is located between the turntable 103 and the transmission gear 112 and the drive gear 111, the turntable 103 needs to push the clutch gear 105 to move toward the transmission gear 112 and the drive gear 111. At this time, the convex edge 103b is compared with the other of the annular groove 103a. The part can be offset toward the clutch gear 105 direction. Further, the transmission gear 112 and the driving gear 111 may be located between the turntable 103 and the clutch gear 105. At this time, the turntable 103 needs to pull the clutch gear 105 to move toward the transmission gear 112 and the driving gear 111. At this time, the convex edge 103b is opposite to each other.
  • the other parts of the annular groove 103a can be offset toward the direction away from the clutch gear 105; at this time, when the clutch gear 105 is in the working position, the first elastic member 106 is in a stretched state. After the adjustment is completed, the clutch gear 105 can be Under the pulling of the annular groove 103a and the first elastic member 106, it returns to the initial position.
  • the displacement difference between the top of the groove convex edge 103b and the annular groove 103a along the center axis of the turntable 103 is the same as the distance between the initial position and the working position of the clutch gear 105, so that the groove convex edge 103b Pushed, the clutch gear 105 can just move to the working position.
  • the annular groove 103a structure is used to pull back and the first elastic member 106 is assisted by the rebound.
  • the pull-back structure can effectively avoid the risk of failure of the elastic member.
  • the second end 104b of the connecting piece is rotatably connected with the first end of the switching shaft in the circumferential direction to smoothly realize the rotation of the switching shaft and the clutch gear 105; it can also be fixedly connected in the circumferential direction to make the clutch gear 105 rotatable Just set it on the switching axis.
  • a fixed connection in the circumferential direction that is, a connection that cannot be rotated in the circumferential direction
  • a rotatable connection in the circumferential direction that is, a connection that can be rotated in the circumferential direction
  • a fixed connection in the axial direction that is, a connection that cannot be rotated in the axial direction.
  • Relatively movable connection; sliding connection along the axial direction that is, the connection capable of relative sliding displacement along the axial direction.
  • the protruding edge 103b smoothly connects with other parts of the annular groove 103a.
  • the convex portion 104a of one end of the connecting piece 104 is cylindrical; it can facilitate smooth sliding in the annular groove 103a.
  • a second elastic member 113 is provided on one side of the driving gear 111 and/or the transmission gear 112, and the second elastic member 113 is initially in a natural state.
  • the second elastic member 113 is initially in a natural state.
  • the second elastic member 113 if the second elastic member 113 is arranged on the side facing the clutch gear 105, the second elastic member 113 will be elongated; if the second elastic member 113 is arranged on the side facing away from the clutch gear 105, the second elastic member 113 will be compressed; the specifics are not limited.
  • the insertion stroke is increased and the top dead resistance is reduced.
  • the driving gear 111 rotates, the facing teeth will be staggered, and the second elastic member 113 will return to its natural state to pull or push the transmission gear 112 and/or the driving gear 111 back to the original position to mesh with the clutch gear 105. This action can effectively avoid the occurrence of the non-engagement of the top, and ensure the smooth progress of the gear shift.
  • the arrangement of the second elastic member 113 solves the fatal problem of the tooth-to-tooth plug-in meshing during switching in the prior art, that is, during the tooth-to-tooth plug-in process, a probabilistic event of tip death will occur on the tooth end surface.
  • the end face is made of sharp corners to reduce this probability, but this fatal problem still exists in theory. Once it occurs, the top dead force will be so large that the motor cannot rotate, and the mechanism will be damaged and cannot work normally.
  • the second elastic member 113 is in a deformed state only during operation, and is in a natural state at other times, which can increase the service life of the second elastic member 113, prevent failure, and reduce manufacturing costs.
  • the first elastic member 106 is only in a deformed state during operation, and is in a natural state at other times, which can increase the service life of the first elastic member 106, prevent failure, and reduce manufacturing costs.
  • first elastic member 106 and the second elastic member 113 may be springs or the like.
  • the transmission mechanism further includes a screw 114, a slider 115 and a guide rod 116; the slider 115 is threadedly connected to the screw 114 on the outside of the screw 114, and the screw 114 One end is fixedly connected with the transmission gear 112 in the circumferential direction and slidingly connected in the axial direction; the two ends of the screw 114 are respectively provided with stop blocks 117; the guide rod 116 and the screw 114 are fixedly arranged in parallel, and the slider 115 is slidably connected with the guide rod 116 .
  • the transmission gear 112 drives the screw 114 to rotate, and then drives the sliding block 115 to move linearly along the screw 114.
  • the slider 115 is connected with the phase shifter, and the phase shifter is adjusted by movement.
  • the transmission gear 112 is directly connected with the screw 114 to drive the screw 114, which can reduce transmission components. Compared with the multi-stage transmission in the prior art, the transmission efficiency can be improved, the efficiency of power transmission can be ensured, and the space required for installation can be reduced.
  • a slot is provided at the center of the transmission gear 112, the end of the screw 114 connected with the transmission gear 112 is a non-circular shaft, and the inner surface of the slot is adapted to the non-circular shaft of the screw 114; it is convenient for the transmission gear 112 to move along the axial direction. When the displacement occurs, it can form a circumferential connection drive.
  • the non-circular shaft and the profiling shaft hole slot are used to prevent the shaft and the hole from rotating relative to each other.
  • This structure There are many cross-sectional forms of this structure, including but not limited to double D, triangle, polygon or a combination of these shapes; for example, one end of the screw 114 is non-rotating.
  • the round shaft is a square shaft
  • the slot at the center of the transmission gear 112 is a corresponding square shaft hole.
  • the sliding block 115 is sleeved on the screw 114 and slidably sleeved on the guide rod 116.
  • the screw 114 is parallel to the guide rod 116, that is, when the screw 114 rotates, the slider 115 moves linearly relative to the screw 114.
  • the guide rod 116 is used to limit the moving direction of the slider 115 to ensure the smooth movement of the slider 115.
  • a stop block 117 is fixed at both ends of the screw 114. When the transmission sliding block 115 moves to both ends, the stop block 117 can restrict the transmission sliding block 115 to continue to slide for stopping.
  • the drive gear 111 is sleeved on the drive shaft, one end of the drive shaft passes through the turntable 103 and is detachably connected to the second power output port 132; the drive gear 111 and the drive shaft should be fixed in the circumferential direction Connected so that the rotation of the drive shaft can drive the drive shaft to rotate integrally.
  • the axial connection between the drive gear 111 and the drive shaft is set according to the specific situation.
  • the clutch gear 105 When the clutch gear 105 is initially out of mesh with the drive gear 111, the clutch gear 105 can be movably connected along the axial direction of the drive shaft to avoid interference. Connect the top death phenomenon.
  • the clutch gear 105 initially meshes with the drive gear 111, the drive gear 111 and the drive shaft can be fixedly connected in the axial direction.
  • the driving part includes a driving gear 101 and a driven gear 102 that are engaged with each other.
  • the driving gear 101 is detachably connected to the first power output port 131; the driven gear 102 is fixedly connected to the turntable 103.
  • the driving member includes an active shift gear 101 and a driven shift gear 102 that mesh with each other; the active shift gear 101 is detachably and fixedly connected to the first power output port 131.
  • the driven shift gear 102 is fixedly connected to the turntable 103.
  • the first power output port 131 sequentially drives the active shift gear 101 and the driven shift gear 102 to rotate, and then controls the turntable 103 to intermittently rotate according to a preset angle.
  • the phase shifter driving device further includes a driving assembly 130 for external power input.
  • the driving assembly 130 includes a first power output port 131 and a second power output port 132.
  • the second power output port 132 and the first power output port 131 are respectively movably inserted into the drive shaft of the drive gear 111 and the shift mechanism.
  • the second power output port 132 is movably plugged into the driving gear 111 through an interface;
  • the first power output port 131 is movably plugged into one end of the active shift gear 101 through an interface.
  • the control component is used to drive the first power output port 131 and the second power output port 132 to rotate at a set angle, thereby driving the driving gear 111 and the shifting mechanism to rotate, and may be a controller.
  • the first power output port 131 and the second power output port 132 may be respectively connected to a motor, and the motor outputs rotational power.
  • a phase shifter driving device further includes: a base 120, a first support 122, a second support 123, and a third support 124; a driving gear 111, a switching mechanism, and a transmission The mechanisms are respectively arranged on the base 120; the first support 122 is arranged between the turntable 103 and the drive gear 111 and the clutch gear 105, and one end of the connecting piece 104 and the drive shaft respectively pass through the first support 122;
  • the second support 123 is arranged between the transmission gear 112 and the screw 114, and the second end of the switching shaft and the other end of the drive shaft are fixed by the second support 123.
  • One end of the screw 114 passes through the second support 123 and is connected to the transmission gear 112.
  • One end of the first elastic member 106 is connected with the clutch gear 105, and the other end can be fixed by the first support 122 or the second support 123; one end of the second elastic member 113 is connected with the driving gear 111 or the transmission gear 112, and the other end It can also be fixed by the first support 122 or the second support 123.
  • the other end of the screw 114 is fixed by the third support 124.
  • a fourth support 121 may be provided at the active shift gear 101 to support and fix one end of the active shift gear 101, the driven shift gear 102, and the drive shaft.
  • this embodiment provides an electrically adjustable antenna, including the phase shifter driving device described in any of the foregoing embodiments.
  • the multi-frequency fusion antenna designed and manufactured by the above embodiment can achieve the purpose of reducing the manufacturing cost of the antenna and miniaturizing the antenna.
  • this embodiment provides a phase shifter driving device for adjusting the downtilt angle of the antenna, including a shifting mechanism, a transmission mechanism and 6 sets of output parts.
  • a phase shifter driving device for adjusting the downtilt angle of the antenna, including a shifting mechanism, a transmission mechanism and 6 sets of output parts.
  • the output part is the screw 114 and the slider 115.
  • the shift mechanism includes an active shift gear 101, a driven shift gear 102 meshingly connected with the active shift gear 101, a turntable 103 relatively fixedly connected to the driven shift gear 102, six sets of clutch gears 105, and corresponding six sets of first gears.
  • An elastic member 106 and six sets of connecting members 104 whose one end is connected to the shaft of the clutch gear 105 and the other end is slidably connected to the annular groove 103 a of the turntable 103.
  • the transmission mechanism includes a driving gear 111, six sets of transmission gears 112, and a second elastic member 113; the output part includes a screw 114, a sliding block 115, a guide rod 116 and a stop block 117.
  • the clutch gear 105 is distributed in a circle with the shaft of the driving gear 111 as the center as a whole, and keeps meshing with the driving gear 111.
  • Each of the six sets of output parts includes a transmission gear 112, a second elastic member 113, a screw 114, a sliding block 115, a guide rod 116, and a stop block 117, respectively.
  • the clutch gear 105 and the transmission gear 112 are misaligned in the length direction of the phase shifter drive device, but in the projection of the length direction, the wheel distances of all the clutch gears 105 and the transmission gear 112 meet the gear meshing size, so that the clutch gear 105 slides into position in the axial direction to mesh with the transmission gear 112 for transmission.
  • the inner wall of the turntable 103 has an annular groove 103a, a groove convex edge 103b, and an inclined surface; one end of the protrusion 104a of the connecting member 104 is inserted into the annular groove 103a and is slidably connected with the annular groove 103a.
  • the other end of the connecting piece 104 is fixedly connected to the clutch gear 105 in the axial direction, that is, the axial direction is relatively fixed, and the circumferential direction is relatively slidable.
  • the tooth width of the drive gear 111 satisfies the axial movement dimension of the clutch gear 105, that is, the clutch gear 105 always keeps meshing with the drive gear 111 when it moves in the axial direction.
  • the advantage of this is that only the clutch gear 105 and the transmission are used.
  • the gear 112 is shifted and engaged, which reduces the difficulty and precision of the first-stage gear shaping.
  • the tooth width of the drive gear 111 can also be reduced, and the movement on the axis of the clutch gear 105 can also be used to simultaneously de-spin and engage the drive gear 111 and the transmission gear 112 when shifting gears.
  • phase shifter drive device The working principle of the phase shifter drive device is as follows:
  • the control component drives the first power output port 131 to rotate to a certain angle, which in turn drives the active shift gear 101, the driven shift gear 102, and the turntable 103 to rotate to a set angle, so that the groove and protruding edge 103b of the turntable 103 is selective Contact with the convex part 104a of one end of the first target connecting piece 104, and push the convex part 104a of one end of the connecting piece 104 to the convex edge 103b of the groove by the thrust of the convex edge 103b of the groove, so that the selected target
  • the connecting piece 104 advances in the axial direction for a linear distance while compressing the resistance spring, thereby causing the clutch gear 105 and the transmission gear 112 to mesh.
  • the control component drives the second power output port 132 to rotate, which in turn drives the target clutch gear 105 meshed with the drive gear 111 and the drive gear 111 to rotate, and then drives the target transmission gear 112 to rotate, thereby driving the target transmission gear 112 corresponds to the rotation of the screw 114 that is sleeved to achieve the purpose of driving the slider 115 to move linearly along the screw 114.
  • precise control of the linear movement distance of the slider 115 can be achieved by controlling the rotation angle of the first power output port 131.
  • the slider 115 is connected with the phase shifter of the antenna to realize the phase adjustment of the target phase shifter.
  • the control assembly drives the first power output port 131 to rotate again to the set angle, and one end of the first target connecting piece 104
  • the convex portion 104a is separated from the convex edge 103b of the groove, and is pulled back into the annular groove 103a by the resilient force of the resistance spring and the pulling force of the other end of the connecting piece 104, thereby making the first target clutch gear 105 and the transmission gear 112 Disengaged.
  • the groove protruding edge 103b of the turntable 103 is turned to neutral, all the clutch gear 105 and the transmission gear 112 return to their original positions, and the spring also returns to its natural state, which improves the service life of the spring.
  • the inner wall of the turntable 103 is provided with grooves, which can not only realize the pushing action of the clutch gear 105, but also realize the pulling back action, which can effectively avoid the rebound delay caused by the failure of the first elastic member 106.
  • a phase shifter multi-drive device can adjust the phases of multiple phase shifters on the antenna, and then realize the two-motor drive and adjust multiple phase shifters, which takes up a small space and is very Conducive to the miniaturization, cost reduction and layout requirements of multi-frequency fusion antennas; miniaturization can be achieved under conventional processes without jamming, and the purpose of reducing antenna manufacturing costs and antenna miniaturization can be achieved.

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Abstract

本申请涉及移动通信基站天线领域，公开了一种移相器驱动装置及电调天线，具体为：换挡机构包括推拉部件和至少一个离合齿轮，传动机构包括与离合齿轮一一对应的传动齿轮；离合齿轮的中心轴线、驱动齿轮的中心轴线以及传动齿轮的中心轴线相互平行，至少一个离合齿轮在驱动齿轮的四周沿同一圆周设置，至少一个传动齿轮在离合齿轮的四周沿同一圆周设置；离合齿轮与驱动齿轮和/或传动齿轮沿中心轴线方向存在间距且离合齿轮沿中心轴线移动能够同时与驱动齿轮和传动齿轮啮合；推拉部件用于选择性地推动离合齿轮沿中心轴线往复移动。本申请提供的一种移相器驱动装置及电调天线，可在常规工艺下实现小型化，达到天线小型化的目的且降低制造成本。

Description

一种移相器驱动装置及电调天线
相关申请的交叉引用
本申请要求于2019年9月17日提交的申请号为201910876741.9，发明名称为“一种移相器驱动装置及电调天线”的中国专利申请的优先权，其通过引用方式全部并入本文。
技术领域
本申请涉及移动通信基站天线领域，特别是涉及一种移相器驱动装置及基站天线。
背景技术
目前一般用手动或电动的方式来改变移动通信系统中基站天线的移相器相位，传统的电动方式是每个移相器采用独立的相位调节装置，但随着移动基站资源的限制，多频天线已越来越成为一种需求趋势。对于多频天线，目前主流的电动调节方式是每一个频段的天线分别采用一个下倾角调节装置，即一个多频天线需要多个下倾角调节装置。
随着天线频率融合越来越多，其调节装置也越来越多，导致天线的结构布局、重量、成本及小型化的设计压力越来越大。天线下倾角调节装置的整体尺寸较大，不能满足小型化的发展趋势。
发明内容
(一)要解决的技术问题
本申请的目的是提供一种移相器驱动装置及电调天线，用于解决或部分解决目前天线下倾角调节装置的整体尺寸较大，不能满足小型化发展趋势的问题。
(二)技术方案
为了解决上述技术问题，本申请第一方面，提供一种移相器驱动装置，包括：驱动齿轮、换挡机构和传动机构，所述换挡机构包括推拉部件和至少一个离合齿轮，所述传动机构包括与所述离合齿轮一一对应的传动齿轮；所述离合齿轮的中心轴线、所述驱动齿轮的中心轴线以及所述传动齿轮的 中心轴线相互平行，至少一个所述离合齿轮在所述驱动齿轮的四周沿同一圆周设置，至少一个所述传动齿轮在所述离合齿轮的四周沿同一圆周设置；所述离合齿轮与所述驱动齿轮和/或所述传动齿轮沿中心轴线方向存在间距且所述离合齿轮沿中心轴线移动能够同时与所述驱动齿轮和所述传动齿轮啮合；所述推拉部件用于选择性地推动所述离合齿轮沿中心轴线往复移动。
根据本申请第二方面，提供一种电调天线，包括上述方案所述的移相器驱动装置。
(三)有益效果
本申请提供的一种移相器驱动装置及电调天线，将离合齿轮设在驱动齿轮的四周呈圆周分布，传动齿轮在离合齿轮的四周呈圆周分布，可减少宽度方向所需的空间，且可将每个离合齿轮与驱动齿轮啮合，通过一个驱动齿轮即可驱动每一个离合齿轮和传动机构，既可实现对多个移相器的相位进行调节，同时可减少驱动机构的设置数量，减少安装所需空间；且离合齿轮和传动齿轮分别设置在同一平面上，可避免在长度方向交错设置而占用的空间，进而减少长度方向所需的空间；该驱动装置可在常规工艺下实现小型化，达到天线小型化的目的且降低制造成本。
附图说明
图1为本申请实施例的一种移相器驱动装置的拆解示意图；
图2为本申请实施例的一种移相器驱动装置的整体示意图；
图3为本申请实施例中换挡机构的截面示意图；
图4为本申请实施例中转盘的示意图；
图5为本申请实施例中连接件的示意图；
图6为本申请实施例中换挡机构的连接结构示意图。
附图标记说明：
101—主动换挡齿轮；    102—从动换挡齿轮；  103—转盘；
104—连接件；          105—离合齿轮；      106—第一弹性件；
103a—环形凹槽；       103b—凸沿；         104a—凸起部；
104b—连接件的第二端； 111—驱动齿轮；      112—传动齿轮；
113—第二弹性件；      114—螺杆；          115—滑块；
116—导向杆；          117—止位块；        120—底座；
121—第四支座；        122—第一支座；      123—第二支座；
131—第一动力输出口；  130—驱动组件；      124—第三支座；
132—第二动力输出口。
具体实施方式
下面结合附图和实施例，对本申请的具体实施方式作进一步详细描述。以下实例用于说明本申请，但不用来限制本申请的范围。
在本申请的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本申请中的具体含义。
本申请实施例提供一种移相器驱动装置，参考图1、图2和图3，该移相器驱动装置包括：驱动齿轮111、换挡机构和传动机构，换挡机构包括推拉部件和至少一个离合齿轮105，传动机构包括与离合齿轮105一一对应的传动齿轮112；驱动齿轮111在输入动力的作用下转动。传动齿轮112与移相器一一对应连接，通过传动齿轮112的转动带动移相器移动进行相位调节。
参考图3，离合齿轮105的中心轴线、驱动齿轮111的中心轴线以及传动齿轮112的中心轴线相互平行，至少一个离合齿轮105在驱动齿轮111的四周沿同一圆周设置，至少一个传动齿轮112在离合齿轮105的四周沿同一圆周设置；即所有离合齿轮105的圆心位于同一圆周上，也即所有离合齿轮105位于同一与轴向相垂直的平面上。同样的，所有传动齿轮112的圆心位于同一圆周上，也即所有传动齿轮112位于同一与轴向相垂直的平面上。
离合齿轮105与驱动齿轮111和/或传动齿轮112沿中心轴线方向存在间距且离合齿轮105沿中心轴线移动能够同时与驱动齿轮111和传动齿轮112啮合；推拉部件用于选择性地推动离合齿轮105沿中心轴线往复移动。即离合齿轮105与驱动齿轮111和传动齿轮112的至少一个在中心轴线方 向上，也即移相器驱动装置的长度方向上有错位。即初始位置离合齿轮105不与驱动齿轮111和传动齿轮112同时啮合，无动力传动。
但在长度方向的投影上，离合齿轮105与驱动齿轮111和传动齿轮112的轴距满足齿轮啮合尺寸，以使在离合齿轮105沿轴向滑动时可同时与驱动齿轮111和传动齿轮112啮合传动。至少一个离合齿轮105在内侧与驱动齿轮111啮合，在外侧与传动齿轮112啮合。离合齿轮105同时与驱动齿轮111和传动齿轮112啮合的位置为离合齿轮105的工作位置。
离合齿轮105位于工作位置时，驱动齿轮111用于带动相啮合的离合齿轮105转动、进而带动对应的传动齿轮112转动，进而调节与其相连的移相器。推拉部件用于选择性地推动离合齿轮105沿中心轴线移动。推拉部件选择性的推动离合齿轮105移动至工作位置以及复位至初始位置，以实现不同离合齿轮105间的切换。推拉部件在将其中一个离合齿轮105沿轴向推动至工作位置时，驱动齿轮111和与该离合齿轮105对应的传动齿轮112同时与该离合齿轮105啮合，进而可将动力传动至传动机构，传动机构带动移相器移动进行调节。
在需要对其他移相器进行调节时，推拉部件可推动位于工作位置的离合齿轮105复位，即将该离合齿轮105沿轴向推至初始位置，即无法实现动力传动的位置处。然后推拉部件推动下一个离合齿轮105沿轴向移动至工作位置，对下一个移相器进行调节。推拉部件可选择性的推动任何一个离合齿轮105沿轴向推动至工作位置，进而可对任何一个需要调节的移相器进行调节。
本实施例提供的一种移相器驱动装置，将离合齿轮105设在驱动齿轮111的四周呈圆周分布，传动齿轮112在离合齿轮105的四周呈圆周分布，可减少宽度方向所需的空间，且可将每个离合齿轮105与驱动齿轮111啮合，通过一个驱动齿轮111即可驱动每一个离合齿轮105和传动机构，既可实现对多个移相器的相位进行调节，同时可减少驱动机构的设置数量，减少安装所需空间；且离合齿轮105和传动齿轮112分别设置在同一平面上，可避免在长度方向交错设置而占用的空间，进而减少长度方向所需的空间；该驱动装置可在常规工艺下实现小型化，达到天线小型化的目的且降低制造成本。
在上述实施例的基础上，进一步地，本实施例对初始位置的多种设置结构进行了说明。初始位置时，离合齿轮105与驱动齿轮111啮合、与传动齿轮112沿中心轴线方向存在间距，且驱动齿轮111的齿宽大于等于离合齿轮105的最大移动路径；即在离合齿轮105在初始位置与工作位置之间往复移动时，离合齿轮105与驱动齿轮111始终保持啮合状态。在离合齿轮105到达工作位置时，只需和传动齿轮112啮合即可。
或者，离合齿轮105与传动齿轮112啮合、与驱动齿轮111沿中心轴线方向存在间距，且传动齿轮112的齿宽大于等于离合齿轮105的最大移动路径；即在离合齿轮105在初始位置与工作位置之间往复移动时，离合齿轮105与传动齿轮112始终保持啮合状态。在离合齿轮105到达工作位置时，只需和驱动齿轮111啮合即可。
或者，离合齿轮105与驱动齿轮111和传动齿轮112沿中心轴线方向均存在间距，且驱动齿轮111和传动齿轮112的齿在中心轴线方向上存在重合部位。即在推动离合齿轮105到达工作位置时，离合齿轮105需同时与驱动齿轮111和传动齿轮112实现啮合。
优选的，可采用前两种设置结构，可降低离合齿轮105到达工作位置时的啮合难度，有利于顺利实现同时与驱动齿轮111和传动齿轮112的啮合。
在上述实施例的基础上，进一步地，本实施例提出一种具体的推拉部件结构，能够实现不同离合齿轮105的切换。参考图1，推拉部件包括主动件和至少一端开口的中空柱状的转盘103；主动件用于驱动转盘103转动；每一离合齿轮105套设于切换轴。
转盘103的中心轴线与离合齿轮105的中心轴线平行，转盘103的开口端朝向离合齿轮105。参考图4，转盘103的内壁上沿周向设有环形凹槽103a，至少一个切换轴的第一端均与环形凹槽103a插接可滑动连接，环形凹槽103a的局部沿轴向偏移形成凸沿103b。即凸沿103b与环形凹槽103a的其他部位在转盘103的中心轴线方向上具有错位；凸沿103b与环形凹槽103a的其他部位是连通的，形成环状。即在转盘103转动时，切换轴的第一端在环形凹槽103a的其他部位会滑动至凸沿103b处，同样会从凸沿103b处滑动至其他部位，从而实现切换轴和离合齿轮105在中心 轴线方向上的位移。
在上述实施例的基础上，进一步地，参考图5，切换轴的第一端通过连接件104与环形凹槽103a相连，参考图6，连接件104的第一端的侧壁上设有凸起部104a，凸起部104a插入环形凹槽103a中，连接件的第二端104b与切换轴的第一端沿轴向固定连接。
在上述实施例的基础上，进一步地，参考图1，切换轴的第二端套设有第一弹性件106，第一弹性件106的一端与离合齿轮105相接、另一端固定设置，第一弹性件106初始处于自然状态。
连接件104的第一端从转盘103的开口端部插入转盘103内部与转盘103侧壁上的环形凹槽103a相连。环形凹槽103a在转盘103的内壁上，槽口朝向转盘103的中心轴线，两槽壁对连接件104的第一端的凸起部104a在中心轴线方向上进行阻挡定位，以实现推拉作用。每个离合齿轮105对应一个切换轴，每个切换轴对应一个连接件104。至少一个连接件104的一端凸起部104a均插入环形凹槽103a中且与环形凹槽103a可滑动连接。环形凹槽103a中沿轴线方向设有凹槽凸沿103b。
在离合齿轮105位于转盘103和传动齿轮112以及驱动齿轮111之间时，该推拉部件的具体切换操作过程为：初始状态连接件104的一端凸起部104a插入环形凹槽103a中凹槽凸沿103b以外的地方；离合齿轮105均位于转盘103与传动齿轮112之间。在需要对其中一个移相器进行调节时，第一输入动力依次驱动主动换挡齿轮101、从动换挡齿轮102、转盘103转动，连接件104的一端凸起部104a在环形滑槽内滑动。将转盘103上的凹槽凸沿103b转动至与该移相器相对应的离合齿轮105的连接件104处，随着转盘103的转动，凹槽凸沿103b会将该连接件104和离合齿轮105顶起，使得该连接件104的一端凸起部104a与凹槽凸沿103b的顶部相接。
使得该离合齿轮105沿轴向移动至传动齿轮112处，与传动齿轮112啮合，对相应的移相器进行调节。同时使得第一弹性件106处于压缩状态。当需要对其他移相器进行调节时，转盘103转动，使得顶位凹槽凸沿103b与上一个已调节的移相器所对应的离合齿轮105的连接件104脱离，则上一个离合齿轮105在第一弹性件106和连接件104另一端回拉的作用下复 位，恢复至初始状态。将转盘103上的凹槽凸沿103b转动至需要调节的移相器所对应的离合齿轮105的连接件104处即可实现切换。
在离合齿轮105位于转盘103和传动齿轮112以及驱动齿轮111之间时，转盘103需要推动离合齿轮105朝向传动齿轮112和驱动齿轮111移动，此时，凸沿103b相比环形凹槽103a的其他部位可朝向离合齿轮105方向偏移。进一步地，还可设置传动齿轮112和驱动齿轮111位于转盘103和离合齿轮105之间，此时，转盘103需要拉动离合齿轮105朝向传动齿轮112和驱动齿轮111移动，此时，凸沿103b相比环形凹槽103a的其他部位可朝向背离离合齿轮105的方向偏移；此时，在离合齿轮105位于工作位置时，第一弹性件106处于拉伸状态，调节完毕后，该离合齿轮105可在环形凹槽103a以及第一弹性件106的拉动下恢复至初始位置。
进一步地，凹槽凸沿103b的顶部与环形凹槽103a之间沿转盘103中心轴线方向上的位移差与离合齿轮105初始位置与工作位置之间的间距相同，使得在凹槽凸沿103b的推动下，离合齿轮105正好可移动至工作位置处。
同时，在离合齿轮105复位的过程中，采用环形凹槽103a结构回拉并以第一弹性件106回弹辅助，相比仅采用弹性件作为复位动力，由于弹性件的寿命和失效风险高，该回拉结构可有效避免弹性件失效的风险。
进一步地，连接件的第二端104b与切换轴的第一端沿周向可转动连接，以顺利实现切换轴和离合齿轮105的转动；也可沿周向固定连接，将离合齿轮105可转动设于切换轴即可。
进一步地，沿周向固定连接，即沿周向不能发生相对转动的连接；沿周向可转动连接，即沿周向能够发生相对转动的连接；沿轴向固定连接，即沿轴向不能发生相对移动的连接；沿轴向滑动连接，即沿轴向能够发生相对滑动位移的连接。
参考图4，凸沿103b与环形凹槽103a的其他部位平滑相接。连接件104的一端侧面凸起部104a为圆柱形；可便于在环形凹槽103a中顺利滑动。凹槽凸沿103b的两侧到环形凹槽103a均有平滑连接的斜面。便于在切换时，连接件104的凸起部104a沿着斜面顺利与凹槽凸沿103b相抵或者沿着斜面顺利滑入环形凹槽103a中实现切换，保证切换的顺利进行。
在上述实施例的基础上，进一步地，参考图2，驱动齿轮111和/或传动齿轮112的一侧设有第二弹性件113，第二弹性件113初始处于自然状态。离合齿轮105与传动齿轮112和/或驱动齿轮111啮合过程中，会出现小概率的对顶不啮合情况。当发生该情况，在离合齿轮105的推力作用下，传动齿轮112和/或驱动齿轮111沿着中心轴线方向移动，第二弹性件113会产生形变。具体的，第二弹性件113如果设置在朝向离合齿轮105的一侧，则第二弹性件113会拉长；第二弹性件113如果设置在背离离合齿轮105的一侧时，第二弹性件113会压缩；具体不做限定。
通过传动齿轮112和/或驱动齿轮111的移动增加插接行程，减小顶死阻力。当驱动齿轮111转动时，对顶的齿会错开，第二弹性件113会恢复自然状态将传动齿轮112和/或驱动齿轮111拉回或推回原位与离合齿轮105啮合。该动作能有效避免对顶不啮合的事件发生，确保档位切换的顺利进行。
第二弹性件113的设置解决了现有技术中在切换时齿与齿插接啮合的致命问题，即齿与齿插接过程中，齿端面会出现顶死概率性事件，虽然可以通过将齿端面做成尖角来减小这种概率，但是这个致命问题依然理论存在，一旦出现，该顶死力会很大，以致电机都无法转动，机构会出现破坏导致无法正常工作。
且第二弹性件113只有在工作时处于变形状态，其他时间均处于自然状态，可提高第二弹性件113使用寿命，防止失效，降低制造成本。同样的，第一弹性件106只有在工作时处于变形状态，其他时间均处于自然状态，可提高第一弹性件106使用寿命，防止失效，降低制造成本。
进一步地，第一弹性件106和第二弹性件113可为弹簧等。
在上述实施例的基础上，进一步地，参考图1和图2，传动机构还包括螺杆114、滑块115和导向杆116；滑块115在螺杆114的外侧与螺杆114螺纹连接，螺杆114的一端与传动齿轮112沿周向固定连接、沿轴向滑动连接；螺杆114的两端分别设有止位块117；导向杆116与螺杆114相平行固定设置，滑块115与导向杆116滑动连接。
传动齿轮112带动螺杆114转动，进而驱动滑块115沿着螺杆114进行直线移动。滑块115与移相器相连，通过移动对移相器进行调节。设置 传动齿轮112直接与螺杆114相连驱动螺杆114，可减少传递部件，相比现有技术中的多级传动，可提高传动效率，保证动力传递的高效性，且可减少安装所需空间。
进一步地，传动齿轮112的中心位置设有插槽，螺杆114与传动齿轮112连接的一端为非圆轴，插槽的内表面与螺杆114的非圆轴相适应；便于传动齿轮112沿轴向发生位移，又可形成周向连接驱动。
非圆轴及仿形轴孔插槽是为了使轴与孔不发生相对转动，该结构截面形式有很多，包括但不限于双D、三角、多边形或这些形状的组合；例如螺杆114的一端非圆轴为方轴时，传动齿轮112中心位置的插槽为对应方轴孔。
滑块115套旋于螺杆114上，并滑动套接于导向杆116上。螺杆114与导向杆116平行，即当螺杆114转动时，滑块115就相对螺杆114直线运动。导向杆116用于限定滑块115移动的方向，保证滑块115的顺利移动。进一步地，螺杆114两端的还各固定有一个止位块117，当传动滑块115运动到两端时，止位块117即可限制传动滑块115继续滑动，用于止位。
在上述实施例的基础上，进一步地，驱动齿轮111套设于驱动轴，驱动轴的一端穿过转盘103与第二动力输出口132可拆卸连接；驱动齿轮111与驱动轴应沿周向固定连接，以使得驱动轴的转动能够带动驱动轴一体转动。驱动齿轮111与驱动轴在轴向上的连接根据具体情况来设置，当离合齿轮105初始与驱动齿轮111不啮合时，可设置离合齿轮105沿驱动轴的轴向可移动连接，以避免出现插接顶死现象。当离合齿轮105与驱动齿轮111初始啮合时，可设置驱动齿轮111与驱动轴沿轴向固定连接。
主动件包括相啮合的主动换挡齿轮101和从动换挡齿轮102，主动换挡齿轮101与第一动力输出口131可拆卸连接；从动换挡齿轮102与转盘103固定连接。
主动件包括相啮合的主动换挡齿轮101和从动换挡齿轮102；主动换挡齿轮101与第一动力输出口131可拆卸固定连接。从动换挡齿轮102与转盘103固定连接。第一动力输出口131依次带动主动换挡齿轮101和从动换挡齿轮102转动，进而控制转盘103按照预设角度间歇性转动。
移相器驱动装置还包括驱动组件130用于外界动力输入。驱动组件130包括第一动力输出口131和第二动力输出口132。第二动力输出口132及第一动力输出口131分别与驱动齿轮111的驱动轴和换挡机构活动插接。具体的，第二动力输出口132与驱动齿轮111通过接口活动插接；第一动力输出口131与主动换挡齿轮101的一端通过接口活动插接。控制组件用于驱动第一动力输出口131及第二动力输出口132按设定角度转动，进而带动驱动齿轮111和换挡机构转动工作，可为控制器。第一动力输出口131和第二动力输出口132可分别与电机相连，通过电机输出转动动力。
在上述实施例的基础上，进一步地，一种移相器驱动装置还包括：底座120、第一支座122、第二支座123和第三支座124；驱动齿轮111、切换机构和传动机构分别设置在底座120上；第一支座122设在转盘103和驱动齿轮111以及离合齿轮105之间，连接件104以及驱动轴的一端分别穿过第一支座122；
第二支座123设置在传动齿轮112和螺杆114之间，切换轴的第二端和驱动轴的另一端通过第二支座123固定。螺杆114的一端穿过第二支座123与传动齿轮112相连。第一弹性件106的一端与离合齿轮105相连，另一端可通过第一支座122或第二支座123固定；第二弹性件113的一端与驱动齿轮111或传动齿轮112相接，另一端同样可通过第一支座122或第二支座123固定。螺杆114的另一端通过第三支座124固定。
进一步地，还可在主动换挡齿轮101处设置第四支座121，对主动换挡齿轮101、从动换挡齿轮102以及驱动轴的一端进行支撑固定。
在上述实施例的基础上，进一步地，本实施例提供一种电调天线，包括上述任一实施例所述的移相器驱动装置。通过上述实施例设计制造的多频融合天线，即可达到降低天线制造成本和天线小型化的目的。
在上述实施例的基础上，进一步地，本实施例提供一种移相器驱动装置，用于调节天线的下倾角，包括换挡机构、传动机构以及6组输出部，在其它实施例中的输出部可以是2个或2个以上。输出部即为螺杆114和滑块115。
换挡机构包括主动换挡齿轮101、与主动换挡齿轮101啮合连接的从动换挡齿轮102、与从动换挡齿轮102相对固定连接的转盘103、六组离 合齿轮105、对应六组第一弹性件106以及一端与离合齿轮105轴相连接另一端与转盘103的环形凹槽103a滑动连接的六组连接件104。传动机构包括驱动齿轮111和六组传动齿轮112、第二弹性件113；输出部包括螺杆114、滑块115、导向杆116及止位块117。
进一步地，离合齿轮105其整体以驱动齿轮111的轴为圆心呈圆周分布，并与驱动齿轮111保持啮合。六组输出部均分别包括传动齿轮112、第二弹性件113、螺杆114、滑块115、导向杆116及止位块117。离合齿轮105与传动齿轮112在移相器驱动装置的长度方向上有错位，但在长度方向的投影上，所有离合齿轮105均与传动齿轮112的轴距满足齿轮啮合尺寸，以使在离合齿轮105沿轴向滑动到位可与传动齿轮112啮合传动。
转盘103内壁侧有环形凹槽103a、凹槽凸沿103b及斜面；连接件104的一端凸起部104a均插入环形凹槽103a中且与环形凹槽103a可滑动连接。连接件104的另一端与离合齿轮105轴向固定连接，即轴向相对固定，周向可相对滑动。
本实施例中，驱动齿轮111齿宽满足离合齿轮105的轴线方向运动尺寸，即离合齿轮105在轴线方向运动时始终与驱动齿轮111保持啮合状态，这样做的好处是只用离合齿轮105与传动齿轮112换挡啮合，减少一级插齿的难度和精度。当然，其它实施例中也可减小驱动齿轮111的齿宽，换挡时亦可用离合齿轮105轴线上的运动同时去插齿啮合驱动齿轮111和传动齿轮112。
该移相器驱动装置的工作动作原理如下：
控制组件驱动第一动力输出口131转动一定角度，进而会依次驱动主动换挡齿轮101、从动换挡齿轮102和转盘103转动至设定角度，从而使转盘103的凹槽凸沿103b选择性的与第一目标连接件104的一端凸起部104a接触，并经凹槽凸沿103b斜面的推力，将连接件104的一端凸起部104a推至凹槽凸沿103b上，使选择的目标连接件104沿轴向推进一段直线距离，同时压缩了阻力弹簧，进而使离合齿轮105和传动齿轮112形成啮合。
此时，控制组件再驱动第二动力输出口132转动工作，进而会依次带动驱动齿轮111与驱动齿轮111啮合的目标离合齿轮105转动，再进而驱 动目标传动齿轮112转动，从而驱使与目标传动齿轮112对应套接的螺杆114转动，达到驱使滑块115沿所述螺杆114直线运动的目的。依据各齿轮之间的传动比和螺杆114的导程，即可通过控制第一动力输出口131转动角度实现滑块115直线运动距离的精确控制。滑块115与天线的移相器连接，即可实现目标移相器的相位调节。
进一步地，当第一目标移相器的相位调节完毕后，第二动力输出口132停止转动，控制组件再次驱动第一动力输出口131再次转动至设定角度，第一目标连接件104的一端凸起部104a脱离凹槽凸沿103b，并经阻力弹簧回弹弹力和连接件104另一端的回拉力将其回拉至环形凹槽103a内，进而使第一目标离合齿轮105与传动齿轮112脱离啮合。同时转盘103的凹槽凸沿103b斜面与连接件104的一端凸起部104a接触，并重复上述动作，实现第二目标螺杆114的转动和移相器的相位调节。
当所有目标螺杆114调节完后，转盘103的凹槽凸沿103b转至空挡，所有离合齿轮105和传动齿轮112均恢复原位，弹簧也恢复自然状态，提高弹簧的使用寿命。转盘103内壁设置凹槽，不仅可实现对离合齿轮105推进动作，又可实现回拉动作，能有效避免第一弹性件106失效造成回弹延迟现象。
通过上述换挡切换和调节动作，从而实现了一个移相器多驱动装置可以对天线上多个移相器的相位进行调节，进而实现两电机驱动调节多个移相器，占用空间小，非常利于多频融合天线的小型化、降本和布局需求；可以在常规工艺下实现小型化而不出现卡死现象，并达到降低天线制造成本和天线小型化的目的。
以上所述仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本申请的保护范围之内。

Claims (10)

  1. 一种移相器驱动装置，包括：驱动齿轮、换挡机构和传动机构，其特征在于，所述换挡机构包括推拉部件和至少一个离合齿轮，所述传动机构包括与所述离合齿轮一一对应的传动齿轮；
    所述离合齿轮的中心轴线、所述驱动齿轮的中心轴线以及所述传动齿轮的中心轴线相互平行，至少一个所述离合齿轮在所述驱动齿轮的四周沿同一圆周设置，至少一个所述传动齿轮在所述离合齿轮的四周沿同一圆周设置；
    所述离合齿轮与所述驱动齿轮和/或所述传动齿轮沿中心轴线方向存在间距且所述离合齿轮沿中心轴线移动能够同时与所述驱动齿轮和所述传动齿轮啮合；所述推拉部件用于选择性地推动所述离合齿轮沿中心轴线往复移动。
  2. 根据权利要求1所述的移相器驱动装置，其特征在于，所述离合齿轮与所述驱动齿轮啮合、与所述传动齿轮沿中心轴线方向存在间距，且所述驱动齿轮的齿宽大于等于所述离合齿轮的最大移动路径；
    或者，所述离合齿轮与所述传动齿轮啮合、与所述驱动齿轮沿中心轴线方向存在间距，且所述传动齿轮的齿宽大于等于所述离合齿轮的最大移动路径；
    或者，所述离合齿轮与所述驱动齿轮和所述传动齿轮沿中心轴线方向均存在间距，且所述驱动齿轮和所述传动齿轮的齿在中心轴线方向上存在重合部位。
  3. 根据权利要求1所述的移相器驱动装置，其特征在于，所述推拉部件包括主动件和至少一端开口的中空柱状的转盘；所述主动件用于驱动所述转盘转动；每一所述离合齿轮套设于切换轴；
    所述转盘的中心轴线与所述离合齿轮的中心轴线平行，所述转盘的开口端朝向所述离合齿轮，所述转盘的内壁上沿周向设有环形凹槽，至少一个所述切换轴的第一端均与所述环形凹槽插接可滑动连接，所述环形凹槽的局部沿轴向偏移形成有凸沿。
  4. 根据权利要求3所述的移相器驱动装置，其特征在于，所述切换轴的第一端通过连接件与所述环形凹槽相连，所述连接件的第一端的侧壁 上设有凸起部，所述凸起部插入所述环形凹槽中，所述连接件的第二端与所述切换轴的第一端沿轴向固定连接。
  5. 根据权利要求3所述的移相器驱动装置，其特征在于，所述切换轴的第二端套设有第一弹性件，第一弹性件的一端与离合齿轮相接、另一端固定设置，第一弹性件初始处于自然状态；
    所述凸沿与所述环形凹槽的其他部位平滑相接。
  6. 根据权利要求1所述的移相器驱动装置，其特征在于，所述驱动齿轮和/或所述传动齿轮的一侧设有第二弹性件，所述第二弹性件初始处于自然状态。
  7. 根据权利要求4所述的移相器驱动装置，其特征在于，所述传动机构还包括螺杆、滑块和导向杆；所述滑块在螺杆的外侧与螺杆螺纹连接，所述螺杆的一端与所述传动齿轮沿周向固定连接、沿轴向滑动连接；所述螺杆的两端分别设有止位块；所述导向杆与所述螺杆相平行固定设置，所述滑块与所述导向杆滑动连接。
  8. 根据权利要求7所述的移相器驱动装置，其特征在于，所述驱动齿轮套设于所述驱动轴，所述驱动轴的一端穿过所述转盘与第二动力输出口可拆卸连接；
    所述主动件包括相啮合的主动换挡齿轮和从动换挡齿轮，所述主动换挡齿轮与第一动力输出口可拆卸连接；所述从动换挡齿轮与所述转盘固定连接。
  9. 根据权利要求8所述的移相器驱动装置，其特征在于，还包括：底座、第一支座、第二支座和第三支座；所述驱动齿轮、换挡机构和传动机构分别设置在所述底座上；所述第一支座设在所述转盘和所述驱动齿轮以及离合齿轮之间，所述连接件以及驱动轴的一端分别穿过所述第一支座；
    所述第二支座设置在所述传动齿轮和所述螺杆之间，所述切换轴的第二端和所述驱动轴的另一端通过所述第二支座固定；所述螺杆的另一端通过第三支座固定。
  10. 一种电调天线，其特征在于，包括上述权利要求1-9任一所述的移相器驱动装置。
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