CN109829258A - Consider the main and auxiliary type constant force spring design of cam profile curve method of roller radius - Google Patents
Consider the main and auxiliary type constant force spring design of cam profile curve method of roller radius Download PDFInfo
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Abstract
The main and auxiliary type constant force spring design of cam profile curve method for considering roller radius, belongs to main and auxiliary type constant-force spring hanger technical field.It is characterized by comprising the following steps: step 1001, determines the energy transfer relationship in motion process；Step 1002, the spring force of main spring and auxiliary spring is determined；Step 1003, the corner of blade type cam and the differential equation of load pipe vertical displacement are established；Step 1004, corresponding elliptic equation is established according to step 1003；Step 1005~1006 establish suspension and support respectively and directly do not consider roller radius and consider the design equation of the blade type cam profile curve of roller radius；Step 1007, obtain considering the blade type cam profile curve of roller radius.In the main and auxiliary type constant force spring design of cam profile curve method of this consideration roller radius, directly consider roller radius to the quantitative effect of blade type cam profile curve, accurately and reliably blade type cam profile curve is obtained, design level, reliability and the support invariance degree of suspension and support product are improved.
Description
Technical field
The main and auxiliary type constant force spring design of cam profile curve method for considering roller radius, belongs to main and auxiliary type constant force spring support
Hanger technical field.
Background technique
Thermal power plant, nuclear power station, petrochemical industry and heating enterprise etc. are required to short then hundreds of meters, long then hundred kilometers
Conveyance conduit realizes gas and water, cigarette, the materials conveying such as wind, and need the internal temperature of complicated alternation, pressure, fluid-load and
External wind, rain, shock loading descend sustaining reliable operation.Carrying fluctuation and tube wall due to conveyance conduit are expanded with heat and contract with cold, pipeline
The vertical deformation of tens or even hundreds of millimeters can be generated.According to rigid carrier supports, pipeline can be interfered to deform vertically, generated very
Big additional primary, secondary stress and stress raisers, and by pipe-line system by this power be transmitted to fixed bracket with
In connected equipment, the safety of these equipment is constituted and is destroyed, pipe-line equipment and safety of surrounding environment are seriously affected；According to general
Logical spring supporting, although additional stress can be reduced to a certain extent, pipeline branch point load is directly proportional to vertical displacement, can not
It is inherently eliminated pipeline additional stress.Currently, conveyance conduit is largely propped up using various main and auxiliary type constant-force spring hanger
Support avoids load transfer, reduces pipeline and interface stress to guarantee that pipeline rationally deforms.
Currently, the main and auxiliary type constant-force spring hanger of LISEGA company, Germany exploitation is high-precision main and auxiliary type constant force in recent years
The canonical form of spring support hanging frame.Blade type cam is the core component of main and auxiliary type constant-force spring hanger, the design essence of curve
Degree directly affects the invariance degree of suspension and support support force.It is all based on not directly for blade type design of cam profile curve method at present
Consider the idealized design of load pipe both ends roller radius, however in main and auxiliary type constant-force spring hanger practical work process, it is
It reduces friction between load pipe and blade type cam and slides, load pipe left and right ends pass through idler wheel and blade type cam contact.
Traditional main and auxiliary type constant-force spring hanger designs processing method, does not consider rolling directly when calculating cam profile curve substantially
The influence of radius is taken turns, but the strategy of post-compensation is used to carry out contour curve amendment, this method can bring additional design to miss
Therefore difference establishes a kind of design method of accurate, reliable blade type cam profile curve, be main and auxiliary type constant-force spring hanger
The design of blade type cam profile curve provides reliable technical method, with improve the design level of suspension and support product, reliability and
Invariance degree is supported, is this field technical problem urgently to be resolved.
Summary of the invention
The technical problem to be solved by the present invention is overcoming the deficiencies of the prior art and provide a kind of directly consideration roller radius
To the quantitative effect of blade type cam profile curve, accurately and reliably blade type cam profile curve is obtained, it is ensured that constant force spring support is hung
The considerations of frame cam profile curve meets design requirement, improves design level, reliability and the support invariance degree of suspension and support product
The main and auxiliary type constant force spring design of cam profile curve method of roller radius.
The technical solution adopted by the present invention to solve the technical problems is: the main and auxiliary type constant force spring of the consideration roller radius
Design of cam profile curve method, which comprises the steps of:
Step 1001, the energy transfer relationship in main and auxiliary type constant-force spring hanger motion process is determined；
Step 1002, the spring force of main spring and auxiliary spring in main and auxiliary type constant-force spring hanger motion process is determined respectively；
Step 1003, the corner of blade type cam and the differential equation of load pipe vertical displacement are established；
Step 1004, the differential equation obtained in step 1003 is integrated, obtains the corner and load pipe of blade type cam
The elliptic equation of vertical displacement；
Step 1005, the design equation that suspension and support does not consider the blade type cam profile curve of roller radius directly is established；
Step 1006, the design equation for considering the blade type cam profile curve of roller radius is established；
Step 1007, the considerations of established in solution procedure 1006 roller radius blade type cam profile curve design side
Journey obtains the blade type cam profile curve for considering roller radius.
Preferably, the expression formula of energy transfer relationship described in step 1001 are as follows:
Wherein, F is output loads, F1For the spring force of main spring, F2Supplemented by spring spring force, spring connects with blade type cam supplemented by h
Point arrives the vertical range of cam shaft,For from global coordinate system XOY along clockwise direction to the corner of satellite coordinate system ξ o η, y
Indicate load pipe vertical displacement.
Preferably, the expression formula of the spring force of main spring and auxiliary spring described in step 1002 is respectively as follows:
F1=k1(h-y)
Wherein, F1For the spring force of main spring, F2Supplemented by spring spring force, k1For the rigidity of main spring, k2Supplemented by spring rigidity, h
Supplemented by the vertical range of spring and blade type cam tie point to cam shaft, the reduction length of a is cam angle when being zero auxiliary spring,
For from global coordinate system XOY along clockwise direction to the corner of satellite coordinate system ξ o η, y expression load pipe vertical displacement.
Preferably, the expression formula of the differential equation described in step 1003 are as follows:
Wherein, k1For the rigidity of main spring, k2Supplemented by spring rigidity, FhFor the sum of the horizontal force of two auxiliary springs, FvIt is carried for outside
The difference of the spring force of lotus and main spring.
Preferably, the expression formula of elliptic equation described in step 1004 are as follows:
Wherein, FvFor the difference of external load and the spring force of main spring, FhFor the sum of the horizontal force of two auxiliary springs, γ=k1/
2k2, for the rigidity of main spring and the ratio between the rigidity of 2 times of auxiliary spring；k1For the rigidity of main spring, k2Supplemented by spring rigidity, C2It is normal to integrate
Number, C2=(1.1~1.5) max (Fv 2)。
Preferably, the design equation of the blade type cam profile curve of roller radius is not considered described in step 1005 directly
Are as follows:
Wherein, (ξ, η) is the curvilinear coordinate of the required blade type cam for not considering roller radius directly,For from world coordinates
It is the corner that XOY arrives satellite coordinate system ξ o η along clockwise direction, y indicates load pipe vertical displacement, and d is that load pipe and blade type are convex
Horizontal distance of the contact point of wheel to cam shaft.
Preferably, described in step 1006 the considerations of roller radius blade type cam profile curve design equation are as follows:
Wherein, (ξ1,η1) it is the required blade type cam profile curve coordinate for considering roller radius, r indicates the half of idler wheel
Diameter.
Compared with prior art, the present invention has the beneficial effects that
In the main and auxiliary type constant force spring design of cam profile curve method of this consideration roller radius, idler wheel half is directly considered
Diameter does not consider for the prior art knife for simplifying design and obtaining of idler wheel directly to the quantitative effect of blade type cam profile curve
Type cam is adding man-hour requirement that post-compensation strategy is used to carry out the amendment of contour curve, and causes the defect of extra error, institute
It is smaller to obtain result design error, is more able to satisfy the use demand of constant-force spring hanger.It can be obtained accurately and reliably using this method
Blade type cam profile curve, it is ensured that constant-force spring hanger cam profile curve meets design requirement, improves suspension and support product
Design level, reliability and support invariance degree.
The Curve Design and simulation analysis obtained simultaneously by example is it is found that the main and auxiliary type for passing through this consideration roller radius
The blade type cam loads deviation that constant force spring design of cam profile curve method obtains is about 0.8%, and the prior art that compares is negative
Carrying deviation is about 6%, and precision greatly improves, and can preferably meet the requirement of constant-force spring hanger.
Detailed description of the invention
Fig. 1 is the main and auxiliary type constant force spring design of cam profile curve method flow diagram for considering roller radius.
Fig. 2 is main and auxiliary type constant-force spring hanger structural schematic diagram.
Fig. 3 is the blade type for considering main and auxiliary type the constant force spring design of cam profile curve method and the prior art of roller radius
Cam profile curve comparison diagram.
Fig. 4 be consider roller radius main and auxiliary type constant force spring design of cam profile curve method and the prior art it is major-minor
The constant force effect contrast figure of formula constant-force spring hanger.
Wherein: 1, load pipe 2, idler wheel 3, main spring 4, blade type cam 5, auxiliary spring 6, cam shaft 7, central load pipe
8, spring bearer plate 9, shell.
Specific embodiment
Fig. 1~4 are highly preferred embodiment of the present invention, and 1~4 the present invention will be further described with reference to the accompanying drawing.
In the structural schematic diagram of main and auxiliary type constant-force spring hanger (hereinafter referred to as suspension and support) shown in Fig. 2, center is negative
The bottom center for carrying pipe 7 from shell 9 is pierced by, and spring bearer plate 8 is fixed on shell 9 by the way that multiple bolts of its border are arranged in
The bottom of lower section, central load pipe 7 is passed down through spring bearer plate 8 simultaneously, and the top of central load pipe 7 is provided with load pipe 1,
Main spring 3 is arranged between load pipe 1 and spring bearer plate 8, and is sleeved on the outer ring of central load pipe 7.
It is respectively arranged with an idler wheel 2 at the both ends of load pipe 1, is respectively arranged with a knife in the outside of two idler wheels 2
Type cam 4, idler wheel 2 and the inner surface of blade type cam 4 are in rolling contact.It is mounted with one respectively on the lateral surface of blade type cam 4
The other end of auxiliary spring 5, auxiliary spring 5 is fixed on the inner face of shell 9, is respectively arranged with a cam in the bottom of blade type cam 4
Shaft 6, blade type cam 4 are axis rotation with the cam shaft 6.
During the motion, main spring 3 provides vertical support force to main and auxiliary type constant-force spring hanger, and auxiliary spring 5 passes through blade type
The deflecting effect of cam 4 provides vertical support force, is mentioned in certain stroke range by the interaction of main spring 3 and auxiliary spring 5
It is supported for constant force.The present invention carries out the cam profile curve for not considering roller radius directly acquired using generation method linear
The contour curve for considering the main and auxiliary type constant-force spring hanger blade type cam of roller radius is established in transformation.
In the main and auxiliary type constant force spring design of cam profile curve method of this consideration roller radius, it is with cam shaft 6
Origin, with 6 center of cam shaft to the line of auxiliary spring 5 and 4 tie point of blade type cam for η axis, is established using vertical direction as Y-axis
Global coordinate system XOY and satellite coordinate system ξ o η, satellite coordinate system ξ o η are rotated with blade type cam 4 around cam shaft 6, angle
For from global coordinate system XOY along clockwise direction to the corner of satellite coordinate system ξ o η, F is output loads, F1For the bullet of main spring 3
Spring force, F2Supplemented by spring 5 spring force.k1For the rigidity of main spring 3, k2Supplemented by spring 5 rigidity, d is load pipe 1 and blade type cam 4
Horizontal distance of the contact point to cam shaft 6, spring 5 and vertical range of 4 tie point of blade type cam to cam shaft 6, a supplemented by h
The reduction length of auxiliary spring 5, h when for 4 corner of blade type cam being 01To cam shaft when moving to extreme higher position for main 3 upper extreme point of spring
6 vertical range, r are the radius of idler wheel 2.
As shown in Figure 1, considering the main and auxiliary type constant force spring design of cam profile curve method of roller radius, including walk as follows
It is rapid:
Step 1001, the energy transfer relationship in main and auxiliary type constant-force spring hanger motion process is determined；
Under output load F effect, frictional dissipation is disregarded, acting and its internal main spring 3,5 energy of auxiliary spring are carried outside suspension and support
Variable quantity is identical, obtains the energy transfer relationship expression formula in suspension and support motion process:
Wherein, F is output loads, F1For the spring force of main spring 3, F2Supplemented by spring 5 spring force, spring 5 and blade type are convex supplemented by h
Take turns 4 tie points to cam shaft 6 vertical range.
Step 1002, spring force is determined；
When the load pipe 1 of constant-force spring hanger moves to any position, 5 spring force of main 3 spring force of spring and auxiliary spring
Expression formula is respectively as follows:
F1=k1(h-y)
Wherein, F1For the spring force of main spring 3, F2Supplemented by spring 5 spring force, k1For the rigidity of main spring 3, k2Supplemented by spring 5 it is rigid
Degree, spring 5 and 4 tie point of blade type cam are to the vertical range of cam shaft 6 supplemented by h, a is 4 corner of blade type cam auxiliary spring 5 when being zero
Reduction length,For from global coordinate system XOY along clockwise direction to the corner of satellite coordinate system ξ o η, y expression load pipe 1
Vertical displacement.
Step 1003, the corner of blade type cam and the differential equation of load pipe vertical displacement are established；
The expression formula obtained according to step 1001~step 1002, while substitution of variable is done, enable Fv=F-F1, Fh=2F2,
The available corner about blade type cam 4With the differential equation of the vertical displacement y of load pipe 1, it may be assumed that
Wherein, k1For the rigidity of main spring 3, k2Supplemented by spring 5 rigidity.
Step 1004, the corner of blade type cam and the elliptic equation of load pipe vertical displacement are established；
The differential equation obtained in step 1003 is integrated, the corner of blade type cam 4 is obtainedPosition vertical with load pipe 1
Move the elliptic equation of y:
Wherein, FvFor the difference of external load and the spring force of main spring 3, namely by the way that two auxiliary springs 5 are equivalent it is applied to load
Vertical force on pipe 1, the referred to as equivalent vertical force of auxiliary spring 5；FhFor the sum of the horizontal force of two auxiliary springs 5, referred to as auxiliary spring horizontal force；γ
=k1/2k2, for the rigidity of main spring 3 and the ratio between the rigidity of 2 times of auxiliary spring 5；C2For integral constant, it is generally taken as C2=(1.1~
1.5)max(Fv 2)。
Step 1005, the blade type cam profile curve that suspension and support does not consider roller radius directly is established；
In constant force spring motion process, 1 blade type of load pipe and the horizontal distance perseverance of 4 contact point of cam to cam shaft 6 are
The design equation of cam curve can be obtained by coordinate transform by d:
Wherein, (ξ, η) is the curvilinear coordinate of the required blade type cam 4 for not considering 2 radius of idler wheel directly.
Step 1006, the blade type cam profile curve for considering roller radius is established；
Gained each coordinate points of cam profile curve in step 1005 are put into one to away from load pipe 1 in its normal direction
Side is retracted 2 radius length of idler wheel, and the design equation for considering the blade type cam profile curve of roller radius can be obtained:
Wherein, (ξ1,η1) it is the required blade type cam profile curve coordinate for considering 2 radius of idler wheel.
Step 1007, the blade type cam profile curve solution to roller radius is considered；
Give the rigidity of main spring 3, auxiliary spring 5, output loads, stroke range and installation geometric parameter, solution procedure 1006
Obtained in design equation, can be obtained and consider that the profile of the main and auxiliary type constant-force spring hanger blade type cam of roller radius is bent
Line.
Below by embodiment, invention is further described in detail:
If certain main and auxiliary type constant-force spring hanger external support load F is 10000N, 1 constant force stroke of load pipe is 400mm,
Main 3 rigidity k of spring1For 50N/mm, auxiliary 5 rigidity of spring is k2For 75N/mm, the contact point of load pipe 1 and blade type cam 4 to cam shaft
6 horizontal distance d is 60mm, and the vertical range h of auxiliary spring 5 and tie point to the cam shaft 6 of blade type cam 4 is 400mm, main spring
3 load pipes 1 when not stressing arrive the vertical range h of cam shaft 61For 600mm, the compression of 4 corner of blade type cam auxiliary spring 5 when being 0
Length a is 80mm, and 2 radius r of idler wheel is 20mm.According to above-mentioned parameter, in conjunction with 1001~1007 pairs of main and auxiliary type constant force of above-mentioned steps
Spring support hanging frame cam profile curve is calculated, and through the above steps 1005 and step 1006 respectively obtain and do not examine directly
Consider the cam profile curve of roller radius and considers the cam profile curve of roller radius, the contrast effect of two curves such as Fig. 3
It is shown.
Constant force spring is carried out in simulation software for the cam profile curve for considering roller radius obtained in Fig. 3
Modeling analysis, the constant force Contrast on effect results of two models as shown in figure 4, curve as shown in Figure 4 it is found that being obtained by the prior art
To main and auxiliary type constant-force spring hanger model load deviation be about 6%, and the main and auxiliary type constant force bullet that this specification technology obtains
Spring bearing hanger model load deviation is about 0.8%, therefore design accuracy is higher, can preferably meet main and auxiliary type constant force spring support
The requirement of hanger.
The above described is only a preferred embodiment of the present invention, being not that the invention has other forms of limitations, appoint
What those skilled in the art changed or be modified as possibly also with the technology contents of the disclosure above equivalent variations etc.
Imitate embodiment.But without departing from the technical solutions of the present invention, according to the technical essence of the invention to above embodiments institute
Any simple modification, equivalent variations and the remodeling made, still fall within the protection scope of technical solution of the present invention.
Claims (7)
1. considering the main and auxiliary type constant force spring design of cam profile curve method of roller radius, which is characterized in that including walking as follows
It is rapid:
Step 1001, the energy transfer relationship in main and auxiliary type constant-force spring hanger motion process is determined；
Step 1002, the spring force of main spring and auxiliary spring in main and auxiliary type constant-force spring hanger motion process is determined respectively；
Step 1003, the corner of blade type cam and the differential equation of load pipe vertical displacement are established；
Step 1004, the differential equation obtained in step 1003 is integrated, the corner for obtaining blade type cam is vertical with load pipe
The elliptic equation of displacement；
Step 1005, the design equation that suspension and support does not consider the blade type cam profile curve of roller radius directly is established；
Step 1006, the design equation for considering the blade type cam profile curve of roller radius is established；
Step 1007, the considerations of established in solution procedure 1006 roller radius blade type cam profile curve design equation,
Obtain considering the blade type cam profile curve of roller radius.
2. the main and auxiliary type constant force spring design of cam profile curve method according to claim 1 for considering roller radius,
It is characterized in that: the expression formula of energy transfer relationship described in step 1001 are as follows:
Wherein, F is output loads, F1For the spring force of main spring, F2Supplemented by spring spring force, spring is arrived with blade type cam contact supplemented by h
The vertical range of cam shaft,For from global coordinate system XOY along clockwise direction to the corner of satellite coordinate system ξ o η, y expression
Load pipe vertical displacement.
3. the main and auxiliary type constant force spring design of cam profile curve method according to claim 1 for considering roller radius,
Be characterized in that: the expression formula of the spring force of main spring and auxiliary spring described in step 1002 is respectively as follows:
F1=k1(h-y)
Wherein, F1For the spring force of main spring, F2Supplemented by spring spring force, k1For the rigidity of main spring, k2Supplemented by spring rigidity, supplemented by h
Spring and blade type cam tie point are to the vertical range of cam shaft, the reduction length of a is cam angle when being zero auxiliary spring,For from
Global coordinate system XOY arrives the corner of satellite coordinate system ξ o η along clockwise direction, and y indicates load pipe vertical displacement.
4. the main and auxiliary type constant force spring design of cam profile curve method according to claim 1 for considering roller radius,
It is characterized in that: the expression formula of the differential equation described in step 1003 are as follows:
Wherein, k1For the rigidity of main spring, k2Supplemented by spring rigidity, FhFor the sum of the horizontal force of two auxiliary springs, FvFor external load with
The difference of the spring force of main spring.
5. the main and auxiliary type constant force spring design of cam profile curve method according to claim 1 for considering roller radius,
It is characterized in that: the expression formula of elliptic equation described in step 1004 are as follows:
Wherein, FvFor the difference of external load and the spring force of main spring, FhFor the sum of the horizontal force of two auxiliary springs, γ=k1/2k2, it is
The ratio between the rigidity of the rigidity of main spring and 2 times of auxiliary spring；k1For the rigidity of main spring, k2Supplemented by spring rigidity, C2For integral constant, C2
=(1.1~1.5) max (Fv 2)。
6. the main and auxiliary type constant force spring design of cam profile curve method according to claim 1 for considering roller radius,
It is characterized in that: not considering the design equation of the blade type cam profile curve of roller radius described in step 1005 directly are as follows:
Wherein, (ξ, η) is the curvilinear coordinate of the required blade type cam for not considering roller radius directly,For from global coordinate system XOY
Arrive the corner of satellite coordinate system ξ o η along clockwise direction, y indicates load pipe vertical displacement, and d is load pipe and blade type cam connects
Horizontal distance of the contact to cam shaft.
7. the main and auxiliary type constant force spring design of cam profile curve method according to claim 1 for considering roller radius,
It is characterized in that: the design equation of the blade type cam profile curve of roller radius the considerations of described in step 1006 are as follows:
Wherein, (ξ1,η1) it is the required blade type cam profile curve coordinate for considering roller radius, r indicates the radius of idler wheel.
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| CN113919087A (en) * | 2021-09-09 | 2022-01-11 | 华电电力科学研究院有限公司 | Main and auxiliary spring type constant-force hanger cam curve design method suitable for variable-load pipeline |
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