CN102444660A - Rotating shaft structure - Google Patents
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- CN102444660A CN102444660A CN2010102983786A CN201010298378A CN102444660A CN 102444660 A CN102444660 A CN 102444660A CN 2010102983786 A CN2010102983786 A CN 2010102983786A CN 201010298378 A CN201010298378 A CN 201010298378A CN 102444660 A CN102444660 A CN 102444660A
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Abstract
The invention provides a rotating shaft structure which comprises a base body, a spring piece and a rotating shaft, wherein the base body is axially provided with a cylindrical hole and an axially extended guide groove connected to the bottom of the cylindrical hole; the spring piece is in close fit with the base body, and comprises a cylindrical tube which is provided with a notch and which is adjacent to the inner wall of the cylindrical hole; the cylindrical tube is provided with at least one hollowed-out zone; a guide locating plate connected with the cylindrical tube is in close fit with the guide groove; at least one flat zone is formed on the surface of the rotating shaft; the one end, provided with the flat zone, of the rotating shaft is arranged in the cylindrical tube of the spring piece, and the other end of the rotating shaft is provided with shaft shoulder gears used for limiting the axial movement of the spring piece; when the rotating shaft rotates relative to the spring piece, under the combined action of the hollowed-out zone and the flat zone, the contact area of the inner surface of the cylindrical tube and the outer surface of the rotating shaft changes along with the rotating angle of the cylindrical tube and the rotating shaft, thereby generating different friction torques. According to the invention, the torque change is realized through the change of the contact area, thus the regularity of the torque changing along with the rotating angle is easy to control and implement.
Description
Technical field
The invention belongs to the rotating shaft field, relate in particular to a kind of turning shaft structure with auto-closing function.
Background technique
In daily life, be able to smooth folding, usually can between two relative swivel assembly, install turning shaft structure in order to make collapsible object.In existing turning shaft structure, cladding type rotary shaft is widely used on the collapsible object because of its relatively low fabricating cost, so that certain moment of torsion to be provided.
At present, the realization of rotating shaft auto-closing function mainly relies on two class formations.One type is the spring-piece type structure that adopts the cam interference component, produces axial displacement through rotation axial between cam, and shell fragment extruding degree rapid change causes the output torque drastic change of rotating shaft, realizes auto-closing and the anti-auto-closing function of opening automatically.Another kind of is to improve in the diameter of axle direction of existing cladding type rotary shaft; The interference deformation amount between the diameter of axle and the shell fragment (or axle sleeve) that makes changes with rotary angle position, and when going to the auto-closing position, the interference displacement amount reduces; Cause output torque to reduce sharply, realize the auto-closing function.
Theoretically, these two kinds of structures all can ideally realize the auto-closing function of rotating shaft, but can know according to actual production and use condition, and also there are many shortcoming and defect in these two kinds of structures.As when the auto-closing angular orientation, because moment of torsion sharply reduces, the rotational acceleration when auto-closing falls is very big, and striking velocity is very big when being incorporated into the zero degree position, very easily electronic products such as notebook is produced impact failure.Impact in order to slow down this potential stronger lid that closes at present, often the auto-closing angular range with rotating shaft limits very for a short time, such as below 20 degree.For the rotating shaft of cam spring-piece type; When the auto-closing angle is opened rotating shaft, because the transition characteristics of cam convex platform cause a great moment of torsion can occurring in the rotating shaft opening procedure; Exceed normal output torque value far away, increase the risk of this body support frame of electronic product and outer casing rupture; And on moment of torsion angle curve, be presented as a very high spike, thereby can cause the wearing and tearing aggravation of peak location, directly influence the working life of rotating shaft.For the cladding type rotary shaft that improves the interference deformation amount; Because frictional force and output torque are very responsive to amount of interference; The amount of interference in actual production after the very difficult assurance rotating shaft assembling and the relation of angle of swing cause rotating shaft moment of torsion poor stability, and not having volume production basically maybe.
Summary of the invention
The present invention has cladding type rotary shaft now because frictional force and output torque are very responsive to amount of interference for solving; The amount of interference in actual production after the very difficult assurance rotating shaft assembling and the relation of angle of swing; The technical problem that causes rotating shaft moment of torsion poor stability provides a kind of cladding type rotary shaft structure with auto-closing function.
Technical problem of the present invention solves through following technological scheme:
A kind of turning shaft structure comprises:
Base body, said base body is axially offered a cylindrical hole, is connected and axially extended guiding groove with this cylindrical hole bottom;
Spring sheet closely cooperates with base body, comprises that the inwall that is adjacent to cylindrical hole is provided with the cylindrical tube of fluting, offers at least one vacancy section on the said cylindrical tube, and the guide-localization sheet and the guiding groove that are connected with cylindrical tube closely cooperate; And
Running shaft, the surface of this running shaft offers at least one flat zone, and an end of offering flat zone is sheathed in the cylindrical tube of spring sheet, and the other end of running shaft is provided with the axially movable shaft shoulder gear of restraining spring sheet;
When running shaft rotated with respect to spring sheet, under the acting in conjunction of vacancy section and flat zone, the area of contact of the internal surface of cylindrical tube and running shaft outer surface changed with both angle of swing, thereby forms different friction torques.
Turning shaft structure provided by the invention adopts the variation of area of contact to realize the variation of moment of torsion, because moment of torsion and rubbing contact area size are linear relationship, makes moment of torsion control more easily with the Changing Pattern of angle of swing and realize.Simultaneously, no matter in design, still produce, can both guarantee well that the continous-stable of area of contact changes, make also smooth change continuously of output torque.In the auto-closing angular range,, close the function of closing in the time of reaching friction torque and be reduced to external torque automatically through the trend that reduces of appropriate design area of contact.Because its moment of torsion is to reduce gently, the potential destruction that can effectively avoid the intense impact of general rotating shaft when auto-closing to bring, the restriction of respective closed angular range is also littler, more meets the hommization requirement.
Description of drawings
Fig. 1 is a turning shaft structure assembly structural representation provided by the invention.
Fig. 2 is the exploded perspective view of first embodiment of the invention shaft structure.
Fig. 3 is the structural representation of base body in the first embodiment of the invention.
Fig. 4 is the be hit by a bullet structural representation of reed of first embodiment of the invention.
Fig. 5 is the be hit by a bullet deployed configuration schematic representation of reed of Fig. 4.
Fig. 6 is the structural representation of running shaft in the first embodiment of the invention.
Fig. 7 is the first embodiment of the invention shaft at Phase I be hit by a bullet reed and running shaft position view.
Fig. 8 is the first embodiment of the invention shaft at Phase be hit by a bullet reed and running shaft position view.
Fig. 9 is the first embodiment of the invention shaft at Phase I be hit by a bullet reed and running shaft position view.
Figure 10 is friction area in the first embodiment of the invention-angle of swing curve synoptic diagram.
Figure 11 is friction torque in the first embodiment of the invention, gravity torque, angle of swing curve synoptic diagram.
Figure 12 is the exploded perspective view of second embodiment of the invention shaft structure.
Figure 13 is the be hit by a bullet structural representation of reed of second embodiment of the invention.
Figure 14 is the structural representation of running shaft during the present invention second implements.
Spring sheet and running shaft position view when Figure 15 is second embodiment of the invention shaft initial position.
Figure 16 is the second embodiment of the invention shaft at Phase I be hit by a bullet reed and running shaft position view.
Figure 17 is the second embodiment of the invention shaft at Phase be hit by a bullet reed and running shaft position view.
Figure 18 is friction area in the second embodiment of the invention-angle of swing curve synoptic diagram.
Figure 19 is friction torque in the second embodiment of the invention, gravity torque, angle of swing curve synoptic diagram.
Figure 20 is the structure exploded perspective view of third embodiment of the invention shaft.
Figure 21 is the be hit by a bullet structural representation of reed of third embodiment of the invention.
Figure 22 is the structural representation of running shaft in the third embodiment of the invention.
Spring sheet and running shaft position view when Figure 23 is third embodiment of the invention shaft initial position.
Figure 24 is the third embodiment of the invention shaft at Phase I be hit by a bullet reed and running shaft position view.
Figure 25 is the third embodiment of the invention shaft at Phase be hit by a bullet reed and running shaft position view.
Figure 26 is the third embodiment of the invention shaft at Phase I be hit by a bullet reed and running shaft position view.
Figure 27 is friction area in the third embodiment of the invention-angle of swing curve synoptic diagram.
Figure 28 is friction torque in the third embodiment of the invention, gravity torque, angle of swing curve synoptic diagram.
Embodiment
Clearer for technical problem, technological scheme and beneficial effect that the present invention is solved, below in conjunction with accompanying drawing and embodiment, the present invention is further elaborated.Should be appreciated that specific embodiment described herein only in order to explanation the present invention, and be not used in qualification the present invention.
To the serial problem of existing auto-closing function rotating shaft, the inventor when amount of interference is constant basically, changes the local shape of spring sheet and running shaft through discovering, rubbing contact area size can change along with the variation of angle of swing.And the proportional relation of rubbing contact area and output torque; Therefore can be through reasonably designing the auto-closing angular range; And in this angular range the relation between rubbing contact area and the angle of swing, realize the relation between desired output torque of auto-closing function and angle of swing.
Relevant theoretical formula is following:
Friction torque M=f * L
Frictional force f=μ * N
Frictional force is to the arm of force L ≈ r in axle center
Lateral extrusion power N=σ * S
Area of contact S=θ * r * h
M=μσθ×r×h×r
Wherein, μ is a friction factor; σ is the extrusion stress on the surface of contact, and when amount of interference was constant, σ remained unchanged basically; θ is the corresponding angle of area of contact; R is the rubbing surface radius corresponding; H is the axial length of frictional contact surface; S is the rubbing contact area.
Please refer to shown in Figure 1ly, on the basis of aforementioned theory, the invention provides a kind of turning shaft structure, comprise base body 1, said base body 1 is axially offered a cylindrical hole, is connected also axially extended guiding groove with this cylindrical hole bottom;
Running shaft 3, the surface of this running shaft offers at least one flat zone, and an end of offering flat zone is sheathed in the cylindrical tube of spring sheet, and the other end of running shaft is provided with the axially movable shaft shoulder gear of restraining spring sheet;
When running shaft rotated with respect to spring sheet, under the acting in conjunction of vacancy section and flat zone, the area of contact of the internal surface of cylindrical tube and running shaft outer surface changed with both angle of swing, thereby forms different friction torques.
Turning shaft structure provided by the invention adopts the variation of area of contact to realize the variation of moment of torsion, because moment of torsion and rubbing contact area size are linear relationship, makes moment of torsion control more easily with the Changing Pattern of angle of swing and realize.Simultaneously, no matter in design, still produce, can both guarantee well that the continous-stable of area of contact changes, make also smooth change continuously of output torque.In the auto-closing angular range,, close the function of closing in the time of reaching friction torque and be reduced to external torque automatically through the trend that reduces of appropriate design area of contact.Because its moment of torsion is to reduce gently, the potential destruction that can effectively avoid the intense impact of general rotating shaft when auto-closing to bring, the restriction of respective closed angular range is also littler, more meets the hommization requirement.
Please refer to shown in Fig. 2-6 the turning shaft structure schematic representation that provides for first embodiment of the invention.Turning shaft structure in the present embodiment comprises base body 10, and said base body 10 is axially offered a cylindrical hole 101, is connected with these cylindrical hole 101 bottoms and axially extended guiding groove 102.
In the present embodiment, offer four vacancy sections 203 on the cylindrical tube 201 of said spring sheet 20, per two vacancy sections are located at the two ends of cylindrical tube respectively, the interlaced setting of the vacancy section of adjacent both ends.Please refer to shown in Figure 4ly, the two ends of said cylindrical tube are meant: after said spring sheet 20 launches, two parts about being divided into it along center line 206 vertical directions of Fig. 4, said about two two ends that part promptly is a cylindrical tube.Can be seen that by this figure the right ends of said cylindrical tube is respectively equipped with two vacancy sections 203, the vacancy section of the right and left is crisscross arranged basically, and the below of the top of left end cylindrical tube and right-hand member cylindrical tube is connected with guide-localization sheet 202 respectively.
And running shaft 30; These running shaft 30 base shapes are circular shaft; The surface 301 of running shaft 30 offers flat zone 302; An end of offering flat zone is sheathed in the cylindrical tube 201 of spring sheet 20, closely cooperates with the internal surface of cylindrical tube 201, and the other end of running shaft 30 is provided with restraining spring sheet 20 axially movable shaft shoulder gears 303.After the assembling, spring sheet 20 can keep relative rotation with running shaft 30, and shaft shoulder gear 303 can prevent that spring sheet 20 from moving axially.
In the present embodiment, the surface 301 of said running shaft 30 offers four flat zones 302, and per two flat zones are located at two sections of running shaft respectively, two flat zone positioned opposite on every section, the interlaced setting of adjacent two sections flat zone.Two sections of said running shaft are meant: vertically be divided into two sections to that end that does not have shaft shoulder gear 303 along the center line of this end; Every section is respectively arranged with two flat zones 302; Two flat zone positioned opposite (becoming 180 degree symmetries basically), its whole design is similar with the layout of vacancy section among Fig. 4.
In the opening procedure of the said turning shaft structure of present embodiment, moment of torsion output is designed to example by three phase scheme, curve is shown in figure 11, and wherein, curve 40 is the output torque of rotating shaft, and curve 50 is a gravity torque.Three stages were followed successively by Phase I: output torque is constant, less than gravity torque, does not change with angle of swing; Phase: output torque increases with angle of swing is linear; Phase I: output torque is constant, greater than gravity torque, does not change with angle of swing.In present design; Output torque curve 40 is higher than in the arbitrarily angled scope of gravity torque curve 50; Rotating shaft all can freely be stopped; And output torque curve 40 is lower than in the arbitrarily angled scope of gravity torque curve 50, because the rotating shaft moment of torsion can't overcome gravity torque, and the equal auto-closing of rotating shaft in this scope.According to the linear resolution relation of above-mentioned frictional contact surface corresponding angle and moment of torsion, design the relation curve between desirable friction area-angle of swing, shown in figure 10.Please refer to shown in Fig. 7-9, the pairing central angle of each vacancy section is designated as α on the needs design this moment cylindrical tube 201, and the size of its α is the 30-150 degree; Each flat zone 302 pairing central angle is designated as β on the running shaft 30, and the size of its β is the 30-150 degree; The initial setting angle of cylindrical tube and running shaft is designated as ψ, and the size of its ψ is the 10-60 degree.After comprehensive Design α, β and ψ relation, the friction area between spring sheet 20 and the running shaft 30 and the Changing Pattern of angle of swing are following:
In the rotating shaft opening process, Phase I: in this scope, friction area is constant, and this moment, friction torque was constant and less than gravity torque, needs the effect of external force could continue unlatching; Phase: in this scope, friction area increases with angle of swing gradually, in the time of near the P point; Friction torque and gravity torque are suitable, cross P point corresponding angle after, friction area increases with angle of swing and continues increase; This II is in the stage, and output torque can't support foreign object and auto-closing less than gravity torque before the P point; Need the external force effect could continue to open, after the P point, output torque is greater than gravity torque; Make rotating shaft can in this scope, freely support foreign object, P point corresponding angle is the maximum auto-closing angle of rotating shaft; Phase I: during this angular range, it is maximum and constant that friction area reaches, and friction torque is also maximum, constant and greater than gravity torque, ability freely support foreign object in this scope.
The rotating shaft pass closes process and opening process is opposite, and particularly: during Phase I, friction area is constant, and friction torque is constant and greater than gravity torque, ability freely support foreign object in this scope; Phase, angle is little to P point angle process, and the friction area linearity reduces; Friction torque is decreased to the gravity torque size gradually by the maximum constant moment of torsion, and friction torque can freely support foreign object greater than gravity torque in this scope; When angle continues to reduce; Friction area continues to reduce, and friction torque reduces and less than gravity torque, can't freely support foreign object and realizes the auto-closing function of auto-closing; Phase I: friction area is constant, and friction torque no longer reduces, and the transition that can well avoid moment of torsion reduces and causes rotating shaft intense impact of closed moment.
Please refer to shown in Figure 12-14 the turning shaft structure schematic representation that provides for second embodiment of the invention.Turning shaft structure in the present embodiment comprises base body 11, spring sheet 21 and running shaft 31.Wherein, structure division identical with first embodiment in the present embodiment repeats no more, and its difference part mainly is:
In the present embodiment, offer the staggered respectively two ends of being located at cylindrical tube of 213, two vacancy sections of two vacancy sections on the cylindrical tube 211 of said spring sheet 21, the two ends of said cylindrical tube are identical with implication among first embodiment.Correspondingly, the right ends of said cylindrical tube 211 only is provided with a vacancy section 213 respectively, and the vacancy section of the right and left is crisscross arranged basically.
In the present embodiment, the surface 311 of said running shaft 31 offers 312, two flat zones 312 of two flat zones and is located at two sections of running shaft respectively, the flat zone positioned opposite on two sections, two sections of said running shaft with first embodiment in implication identical.From the surface 311 of the running shaft 31 of Figure 14, can see, flat zone be positioned at left section surface above, another flat zone be positioned at right section surface below.
In the opening procedure of the said turning shaft structure of present embodiment, be example with moment of torsion output by the two-stage conceptual design, curve is shown in figure 19, and wherein, curve 41 is the output torque of rotating shaft, and curve 51 is a gravity torque.Two-stage is followed successively by Phase I: the friction torque of rotating shaft output increases with angle of swing; Phase: output torque is constant.In present design; Output torque curve 41 is higher than in the arbitrarily angled scope of gravity torque curve 51; Rotating shaft all can freely be stopped; And output torque curve 41 is lower than in the arbitrarily angled scope of gravity torque curve 51, because the rotating shaft moment of torsion can't overcome gravity torque, and the equal auto-closing of rotating shaft in this scope.According to the linear resolution relation of above-mentioned frictional contact surface corresponding angle and moment of torsion, design the relation curve between desirable friction area-angle of swing, shown in figure 18.Please refer to shown in Figure 13-17, the pairing central angle of each vacancy section is designated as α on the needs design this moment cylindrical tube 211, and the size of its α is the 30-150 degree; Each flat zone 312 pairing central angle is designated as β on the running shaft 31, and the size of its β is the 30-150 degree; The initial setting angle of cylindrical tube and running shaft is designated as ψ, and the size of its ψ is the 0-90 degree.After comprehensive Design α, β and ψ relation, the friction area between spring sheet 21 and the running shaft 31 and the Changing Pattern of angle of swing are following.
In the present embodiment, rotating shaft realizes that the function of closing the position automatically occurs in Phase I, closes in the closed procedure in rotating shaft; Along with reducing of angle, the moment of torsion of output tapers to Phase I by the stationary value of Phase, when angle continues to be reduced to P point position; The output torque of this moment is not enough to overcome the heavy moment of torsion of screen; Even do not apply external force, last screen realizes closing automatically bit function with auto-closing.
The rotating shaft opening process: Phase I, output torque increases with angle of swing, and before reaching the P point, all less than gravity torque, in this process, if the external force of removing, screen will close the position automatically; After surpassing the P point, moment of torsion increases with angle of swing and continues to increase, and until the stationary value that reaches Phase, in this process, if the external force of removing, the output torque of rotating shaft all can guarantee freely supporting of screen.
Phase, the output torque of rotating shaft do not change with angle of swing, reach a stationary value, and are higher than the gravity torque of screen, realize going up in this angular range freely supporting of screen.
With shown in Figure 19 is example, and the angular range that Phase I, II are corresponding respectively is θ 1, θ 2, please refer to shown in Figure 15, θ 1≤(180-α)-ψ, θ 2≤(360-β)-α.
Please refer to shown in Figure 20-22 the turning shaft structure schematic representation that provides for third embodiment of the invention.Turning shaft structure in the present embodiment comprises base body 12, spring sheet 22 and running shaft 32.Wherein, structure division identical with first embodiment in the present embodiment repeats no more, and its difference part mainly is:
In the present embodiment, offer 223, two vacancy sections of two vacancy sections order on cylindrical tube on the cylindrical tube 221 of said spring sheet 22 and arrange; Among this embodiment; No longer distinguish the right ends of cylindrical tube 221, said two vacancy sections 223 across cylindrical tube 221 about end, order arrange to form.When spring sheet 22 coilings be processed into cylindrical after, two vacancy sections, the 223 basic positioned opposite on the cylindrical tube 221.
In the present embodiment; The surface 321 of said running shaft 32 offers two flat zones 322; Two flat zones 322 are oppositely arranged on the surface 321 of running shaft, in this embodiment, no longer include the differentiation of two sections on running shaft; Said two flat zones 322 do not have that end of shaft shoulder gear 323 across running shaft 32, and both are oppositely arranged.
In the opening procedure of the said turning shaft structure of present embodiment, be example with moment of torsion output by the five-stage conceptual design, curve is shown in figure 28, and wherein, curve 42 is the output torque of rotating shaft, and curve 52 is a gravity torque.Five-stage is followed successively by Phase I: output torque is constant; Phase: output torque increases with angle of swing and reduces; Phase I: output torque is constant; Phase IV: output torque increases with angle of swing; Stage V: output torque is constant.In present design; Output torque curve 42 is higher than gravity torque curve 52 always, i.e. rotating shaft can freely be stopped arbitrarily angled, and the friction torque of output is along with angle of swing reduces earlier; After increase again; Can guarantee the function that the rotating shaft support screen is heavy, can reduce the complexity of external force unlatching and closed rotating shaft again, realize certain labor-saving effect.According to the linear resolution relation of above-mentioned frictional contact surface corresponding angle and moment of torsion, design the relation curve between desirable friction area-angle of swing, shown in figure 27.Please refer to shown in Figure 23-26, the pairing central angle of each vacancy section is designated as α on the needs design this moment cylindrical tube 221, and the size of its α is the 30-150 degree; Each flat zone 322 pairing central angle is designated as β on the running shaft 32, and the size of its β is the 30-150 degree; The initial setting angle of cylindrical tube and running shaft is designated as ψ, and the size of its ψ is the 0-90 degree.
With shown in Figure 28 is example, and the angular range that Phase I, II, III, IV, V are corresponding respectively is θ 1, θ 2, θ 3, θ 4, θ 5, wherein: θ 1=ψ, θ 2=β, θ 3=(180-α)-β, θ 4=θ 2, θ 5=θ 1.Under external force, open in the rotating shaft process, the output torque M (f) of moment of face M (outward), the heavy moment of torsion M (g) of screen, rotating shaft needs to satisfy relation: M (outward) >=M (g)+M (f); M (g)=G * L * COS (x), G is the gravity of screen, L arrives the distance in axle center for the center of gravity of screen; L * COS (x): effective arm of force of gravity when angle is x.When removing external force, the moment of torsion of rotating shaft must support screen weigh M (f) >=M (g).Close a rotating shaft for non-automatic, when any angular position, all must satisfy M (f) >=M (g), could guarantee the normal function of rotating shaft.Because M (g) changes with the variation of angle of swing, therefore under the condition that satisfies M (f) >=M (g), reduce the output torque M (f) of rotating shaft, be easy to the unlatching and the closure of rotating shaft.
After comprehensive Design α, β and ψ relation, the friction area between spring sheet 22 and the running shaft 32 and the Changing Pattern of angle of swing are following:
In the present embodiment, the rotating shaft in each stage output friction torque is all greater than gravity torque, and promptly in any angular position, rotating shaft all can guarantee freely supporting of screen.In each stage of rotating shaft open and close, need provide moment of face just can carry out, according to above-mentioned mechanical equilibrium condition, when gravity torque and moment of face in the same way the time, the moment of face of this moment must be greater than the output torque of rotating shaft and the difference of gravity torque; When gravity torque and moment of face were reverse, moment of face must be greater than the output torque and the gravity torque sum of rotating shaft.Therefore guaranteeing to reduce the output torque of rotating shaft under the condition of rotating shaft output torque greater than gravity torque, can reduce the moment of face size in rotating shaft unlatching and the closing course, making that promptly unlatching and closure are easier.Because gravity torque and angle are cosine absolute value relation, promptly gravity torque reduces earlier with angle of swing, reaches minimum value at 90 degree annexes; After increase with angle of swing again, satisfying under the prerequisite of rotating shaft output torque greater than gravity torque, unlatching and closing course with rotating shaft in the present embodiment are divided into 5 stages; Wherein moment of torsion is constant among Phase I, III, the V; Do not change with angle, in the Phase, the rotating shaft output torque increases with angle of swing and reduces; In the Phase IV, the rotating shaft output torque increases with the increase of angle of swing.In 5 stages, the output torque of Phase I is minimum, but still greater than the gravity torque in this angular range, could guarantee freely supporting of screen.
The above is merely preferred embodiment of the present invention, not in order to restriction the present invention, all any modifications of within spirit of the present invention and principle, being done, is equal to and replaces and improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. a turning shaft structure is characterized in that, comprising:
Base body, said base body is axially offered a cylindrical hole, is connected and axially extended guiding groove with this cylindrical hole bottom;
Spring sheet closely cooperates with base body, comprises that the inwall that is adjacent to cylindrical hole is provided with the cylindrical tube of fluting, offers at least one vacancy section on the said cylindrical tube, and the guide-localization sheet and the guiding groove that are connected with cylindrical tube closely cooperate; And
Running shaft, the surface of this running shaft offers at least one flat zone, and an end of offering flat zone is sheathed in the cylindrical tube of spring sheet, and the other end of running shaft is provided with the axially movable shaft shoulder gear of restraining spring sheet;
When running shaft rotated with respect to spring sheet, under the acting in conjunction of vacancy section and flat zone, the area of contact of the internal surface of cylindrical tube and running shaft outer surface changed with both angle of swing, thereby forms different friction torques.
2. turning shaft structure according to claim 1 is characterized in that, offers four vacancy sections on the said cylindrical tube, and per two vacancy sections are located at the two ends of cylindrical tube respectively, the interlaced setting of the vacancy section of adjacent both ends; The surface of running shaft offers four flat zones, and per two flat zones are located at two sections of running shaft respectively, two flat zone positioned opposite on every section, the interlaced setting of adjacent two sections flat zone.
3. turning shaft structure according to claim 2; It is characterized in that; The pairing central angle of each vacancy section is the 30-150 degree on the said cylindrical tube, and the pairing central angle of each flat zone is the 30-150 degree on the running shaft, and the initial setting angle of cylindrical tube and running shaft is the 10-60 degree.
4. turning shaft structure according to claim 3 is characterized in that, when opening said turning shaft structure, moment of torsion output was divided into for three stages, and three stages were followed successively by Phase I: output torque is constant, does not change with angle of swing; Phase: output torque increases with angle of swing is linear; Phase I: output torque is constant, does not change with angle of swing.
5. turning shaft structure according to claim 1 is characterized in that, offers two vacancy sections on the said cylindrical tube, two staggered respectively two ends of being located at cylindrical tube of vacancy section; The surface of running shaft offers two flat zones, and two flat zones are located at respectively on two sections of running shaft relatively.
6. turning shaft structure according to claim 5; It is characterized in that; The pairing central angle of each vacancy section is the 30-150 degree on the said cylindrical tube, and the pairing central angle of each flat zone is the 30-150 degree on the running shaft, and the initial setting angle of cylindrical tube and running shaft is the 0-90 degree.
7. turning shaft structure according to claim 6 is characterized in that, when opening said turning shaft structure, moment of torsion output is divided into the two-stage, and the two-stage is followed successively by Phase I: the friction torque of rotating shaft output increases with angle of swing; Phase: output torque is constant.
8. turning shaft structure according to claim 1 is characterized in that, offers two vacancy sections on the said cylindrical tube, and two vacancy sections are arranged relatively; The surface of running shaft offers two flat zones that are oppositely arranged.
9. turning shaft structure according to claim 8; It is characterized in that; The pairing central angle of each vacancy section is the 30-150 degree on the said cylindrical tube, and the pairing central angle of each flat zone is the 30-150 degree on the running shaft, and the initial setting angle of cylindrical tube and running shaft is the 0-90 degree.
10. turning shaft structure according to claim 9 is characterized in that, when opening said turning shaft structure, moment of torsion output is divided into five-stage, and five-stage is followed successively by Phase I: output torque is constant; Phase: output torque increases with angle of swing and reduces; Phase I: output torque is constant; Phase IV: output torque increases with angle of swing; Stage V: output torque is constant.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010298378.6A CN102444660B (en) | 2010-09-30 | 2010-09-30 | Rotating shaft structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010298378.6A CN102444660B (en) | 2010-09-30 | 2010-09-30 | Rotating shaft structure |
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| CN102444660A true CN102444660A (en) | 2012-05-09 |
| CN102444660B CN102444660B (en) | 2014-07-02 |
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| CN201010298378.6A Expired - Fee Related CN102444660B (en) | 2010-09-30 | 2010-09-30 | Rotating shaft structure |
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| CN (1) | CN102444660B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104977988A (en) * | 2014-04-07 | 2015-10-14 | 苹果公司 | Variable Friction Clutch For A Portable Computer |
| CN108242906A (en) * | 2016-12-26 | 2018-07-03 | 丰田自动车株式会社 | Electric machine control system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US3909077A (en) * | 1973-08-20 | 1975-09-30 | Leco Corp | Pivot assembly mounting apparatus |
| JPH10294572A (en) * | 1997-04-21 | 1998-11-04 | Kato Electrical Mach Co Ltd | Opening/closing device of opening closing body |
| CN1471287A (en) * | 2002-07-24 | 2004-01-28 | ���ǵ�����ʽ���� | Flip-cover drive device for portable apparatus |
| CN201103611Y (en) * | 2007-05-09 | 2008-08-20 | 蔡泳明 | Torsion axis structure |
| CN101435460A (en) * | 2007-11-15 | 2009-05-20 | 兆利科技工业股份有限公司 | Cladding type rotary shaft structure |
| CN201391535Y (en) * | 2009-04-09 | 2010-01-27 | 元镫金属股份有限公司 | Pivot structure with flexible torque force adjusting arm |
| CN101684839A (en) * | 2008-09-25 | 2010-03-31 | 鸿富锦精密工业（深圳）有限公司 | Hinge structure |
| CN201496395U (en) * | 2009-08-24 | 2010-06-02 | 昆山前端电子有限公司 | Pivot device structure |
-
2010
- 2010-09-30 CN CN201010298378.6A patent/CN102444660B/en not_active Expired - Fee Related
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3909077A (en) * | 1973-08-20 | 1975-09-30 | Leco Corp | Pivot assembly mounting apparatus |
| JPH10294572A (en) * | 1997-04-21 | 1998-11-04 | Kato Electrical Mach Co Ltd | Opening/closing device of opening closing body |
| CN1471287A (en) * | 2002-07-24 | 2004-01-28 | ���ǵ�����ʽ���� | Flip-cover drive device for portable apparatus |
| CN201103611Y (en) * | 2007-05-09 | 2008-08-20 | 蔡泳明 | Torsion axis structure |
| CN101435460A (en) * | 2007-11-15 | 2009-05-20 | 兆利科技工业股份有限公司 | Cladding type rotary shaft structure |
| CN101684839A (en) * | 2008-09-25 | 2010-03-31 | 鸿富锦精密工业（深圳）有限公司 | Hinge structure |
| CN201391535Y (en) * | 2009-04-09 | 2010-01-27 | 元镫金属股份有限公司 | Pivot structure with flexible torque force adjusting arm |
| CN201496395U (en) * | 2009-08-24 | 2010-06-02 | 昆山前端电子有限公司 | Pivot device structure |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104977988A (en) * | 2014-04-07 | 2015-10-14 | 苹果公司 | Variable Friction Clutch For A Portable Computer |
| CN108242906A (en) * | 2016-12-26 | 2018-07-03 | 丰田自动车株式会社 | Electric machine control system |
| CN108242906B (en) * | 2016-12-26 | 2021-01-12 | 丰田自动车株式会社 | Motor control system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102444660B (en) | 2014-07-02 |
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