JP2966906B2 - Inclined coil spring device - Google Patents

Description

Description: FIELD OF THE INVENTION The present invention relates generally to canted coil springs, and more particularly to holding a spring in a cavity in a coherently oriented orientation for subsequent loading of the spring. To a tilted coil spring. By loading the spring with respect to the long or short axis, a particular selected resilience or load-deflection characteristic is obtained in response to subsequent spring loading.

[Prior Art and Its Problems] The voids described below can be circular or other predetermined linear shapes, that is, continuous. In the case of a circular void, the spring abuts the coils at both ends, overlaps the coils at both ends, or is joined by welding the coils at both ends to form a garter-type gradient coil spring.

A general discussion of these types of garter-type springs is provided in U.S. Pat. Nos. 3,323,735 and 3,468,527 to Mother.
The prior art springs disclosed in the above-mentioned U.S. patents have limited applications, and in particular, are limited to the angle of inclination of the coil as described in the above-mentioned U.S. patents.

Advances in the design of springs described in U.S. Patent Application No. 186,016 entitled "Internal Back Angle Tilted Coil Springs" and U.S. Patent No. 4,826,144 entitled "Outside Back Angle Tilted Coil Springs" It has become possible to design springs that have better operating characteristics than prior art springs.

The load-deflection characteristics of conventional garter-type axial springs have been changed by varying various spring parameters, examples of which include wire size, coil height, coil spacing, and the above-mentioned U.S. Pat. There is a front angle, etc., known as the tilt angle described in the specification, which defines the leading part of each tilt coil spring.
These parameters have been effectively used to design the load-deflection characteristics of the spring, but do not achieve the overall design possibilities of the spring.

A previously unrecognized parameterizer that inherently affects the properties of an axially loaded spring of the garter type is disclosed in U.S. Patent Application Nos. 180,016 and 186,018 (U.S. Patent No. 4,826,144). . The specifications of these U.S. patents or U.S. patent applications disclose coils that are interconnected to form a resilient garter-type coil spring, wherein the coils are axially resilient garter-type coil springs. It has a trailing portion along the outer diameter of the coil spring and a leading portion along the inner diameter of the garter-type coil spring having elasticity in the axial direction. Further, the following portion may be along the inner diameter, and the preceding portion may be along the outer diameter.

The selected arrangement of the back angles and the trailing part defined by this back angle allows for the design of garter-type elastic coil springs in a wider range than the conventional known garter-type elastic coil springs To

Consequently, the spring can be formed to have high load-deflection characteristics. That is, the spring can produce a greater force on any deflection as compared to a spring having the same dimensions and wire size and having a trailing portion along the inside diameter of the spring.

Ultimately, these springs can be formed from smaller diameter wires and have tight coil spacing to produce the same force as the prior art springs in response to deflection.

Means for Achieving the Object and Effects The feature of the present invention is to find other parameters that can be used to design a garter-type spring having a selected load-deflection characteristic.

First, an axially loaded garter type with higher load-deflection characteristics compared to conventional springs formed using the same wire diameter, using the winding angles defined and discussed below. Can be formed. The effect of high loading has been described above.

Also, the specific relationship and range of elasticity of use of a spring formed in accordance with the present invention can be exploited to provide a spring with custom load-deflection characteristics not heretofore possible. .

Second, as described below, when a load is applied to a garter-type spring along the long axis with or without changing the winding angle, the load-deflection characteristics of the spring can be set arbitrarily, and When a load is applied to such a spring, the spring can be inclined along the long axis from the inside toward the radial direction or from the outside toward the radial direction.

In order to tilt the spring when a radial load is applied along its long axis, the spring must be accommodated in a cavity. It has been found that when the spring is free and radially loaded along the long axis, the spring resists tilting or does not tilt at all.

It is also possible to house or provide the spring in place and apply both radial and axial forces to incline the spring radially along the long axis and radially along the short axis.

Many parameters that affect the load-deflection characteristics of garter-type springs, such as those described above in connection with the prior art, are dependent on the spring's ability to flex or bend freely in its unrestrained state. It is important to recognize that the elastic properties have little or no effect. For example, Bram discloses in U.S. Pat. No. 3,183,010 the reinforcement for a sealing element having the shape of a garter-type spring and the winding angle at the reinforcement element.

However, while the disclosed reinforcing element has the shape of a spring, it cannot be flexed freely because it is embedded in the sealing element so that the faces match. With such embedding, it is clear that this reinforcement element or spring cannot flex freely with the load-deflection characteristics that it would have in free space, i.e. in an unrestrained deflection under load.

The springs of the present invention provide load-deflection operating characteristics that can be effectively used in spring design for applications not heretofore enabled.

The tilted coil spring device of the present invention generally has a plurality of major axes and minor axes that are inclined in the direction of the centerline along a centerline defined by connecting intersections of the major and minor axes. Coil. A back angle is provided which defines the arrangement of the trailing portion of each coil with respect to a line perpendicular to the center line and which determines the load-deflection characteristics of the canted coil spring. A front angle is provided that defines an array of leading portions of each coil with respect to the perpendicular line and has an angle greater than the back angle. According to the present invention, there is provided support means for supporting the plurality of coil springs in a predetermined direction in a non-interfering manner to control elastic characteristics of a garter-type inclined coil spring having elasticity in the axial direction, However, it is characterized in that it comprises means defining a cavity for supporting and orienting the coil spring at a winding angle greater than 0 ° and less than 90 °.

More particularly, the coils are interconnected to form an axially elastic garter-type canted coil spring, and the support means deflects the spring along a short axis and has an elastic garter. Means may be provided for defining a cavity for loading a coil spring of the type along the longitudinal axis. Conversely, the cavity may provide a means for flexing the spring along its long axis and loading the elastic garter-type coil spring along its short axis.

Further, the trailing portion may be provided along an outer diameter of the yl spring, and the leading portion may be provided along an inner diameter of the coil spring. Conversely, the trailing portion may be provided along the inner diameter of the yl spring, and the leading portion may be provided along the outer diameter of the coil spring. The back angle is selected to provide a load-deflection characteristic such that the load is relatively constant within the range of use deflection. Further, the void means may have a width at most as high as the height of the coil, and in other embodiments the void means may have a width greater than the height of the coil means but less than the width of the coil. it can. In the present invention, the “leading portion” refers to a half of the winding of each coil that advances the coil spring in a clockwise or counterclockwise direction, and the “subsequent portion” refers to each coil. , The remaining half of the turn following the preceding part.

Embodiments Referring to FIGS. 1 to 6, various obliquely wound coil springs or inclined coil spring assemblies 1 of the present invention will be described.
0,12,14,16 are shown, each of which has a plurality of coils 18,20,22,28 inclined along and along the centerline 28,30,32,34, respectively. It has 24.

The springs 10,12 are interconnected to form circular springs and have a primary load-deflection characteristic along the axial direction of the circular springs 10,12. As shown in FIG. 2, the spring 10 having the coil inclined in the clockwise direction shown in FIG.
And a front angle 46 defining a leading portion 48 of the coil 18 is connected to the coil 18 so as to be along the outer diameter 50 of the spring 10.
have.

Referring to FIGS. 3 and 4, the axial spring 12 comprises
The back angle 54 defining the trailing portion 56 is along the outer diameter 64 of the spring 12,
A clockwise inclined coil 20 interconnected such that a front angle 60 defining a leading portion 62 is along the inner diameter 58 of the spring 12
have.

Referring to FIGS. 5 and 6, the springs 14, 16 have a plurality of coils 20, 24, which are indicated by arrows 6
They are interconnected to form a circular spring with radial primary load-deflection characteristics as indicated at 6, 68. As shown in FIG. 5, the coils are interconnected in a clockwise manner and are provided along a back angle 72 defining a trailing portion 74 along the top 76 and along the bottom of the spring 14. And a front angle 78 defining a leading portion 80.

Also, as shown in FIG. 6, the spring 16 has a coil 24 interconnected so as to incline counterclockwise,
The coils have a back angle 88 defining a trailing portion 90 along the bottom 92 of the spring 16 and a forward angle 96 defining a leading portion 98 provided along the top 100 of the spring 16.

As described below, all of the springs 10, 12, 14, 16 have a substantially constant load-deflection characteristic over the range of deflection used.

FIG. 7 shows load-deflection curves A and B showing characteristics of a garter-type elastic coil spring having a gradient coil.
It is shown. As shown by curve A, when a load is applied to the annular spring, the spring deflects substantially linearly until it reaches a minimum load point 102, as shown by line 100. Minimum load point 102 indicates the point at which the load begins to become relatively constant after the initial deflection.

Between the minimum load point 102 and the maximum load point 104, the seventh
As shown, the load-deflection curve tends to be constant or slightly increase. The area between the minimum load point 102 and the maximum load point 104 is known as the use deflection range 106. Normally, the spring is loaded for operation within this range, as shown at point 108 for a typical spring used in combination with a seal, gasket or the like used to seal. When a load is applied to the spring beyond the maximum load point, the spring reacts sharply until it reaches the butt point 110, and the overload causes permanent deformation of the spring. FIG. 7 also shows the total flexure area 112 defined as the flexure between the unloaded spring and the flexure at the point of maximum load 104.

FIG. 7 shows springs 10, 12, formed according to the invention.
A load-deflection curve B showing load-deflection characteristics of 14 and 16 is shown, and a linear load-deflection portion 116 is shown until a peak load point 118 is reached. Peak point 118
Thereafter, at portion 120, the load decreases with deflection. Thus, a saddle-type flexure region is formed between the peak point 118 and the butt point 110.

This type of load-deflection characteristic has a special effect on the spring seal, and the tension created by the spring locks the seal in place, such as in a groove. In this regard, the spring produces a relatively constant load over a given use deflection area 124, but exhibits a sharp increase in load beyond the use area limit at points 126,128. This results in self-centering in grooves or the like of the spring seal.

Another application that is effective with the springs of the present invention is in static applications where it is desirable to apply large loads without increasing the wire diameter of the spaced coils. Yet another application is where a high initial load is required, such as in seals exposed to low vacuum temperatures.

FIG. 8 schematically shows a cross section of the oblique coil springs 10, 12, 14, and 16 of the present invention. The coil spring has a free winding angle θ, a measurement coil width CW, a measurement coil height CH, and a measurement spring. It has a height H. In FIG. 8, the free winding angle θ can be clockwise (indicated by a solid line) or counterclockwise (indicated by a chain line).

As shown in FIG. 9a, an axially flat spring can be wound counterclockwise at 30 °, for example, as in FIG. 9b,
Also, as shown in FIGS. 9c and 9d, it is possible to wind clockwise at winding angles of 30 ° and 60 °, respectively. Although the springs are shown as being elliptical, other shapes, such as circular or rectangular, can be used depending on the shape of the cooperating components into which the springs 10, 12, 14, 16 are inserted.

As shown in FIG. 8, the free winding angle θ is defined as the angle formed by a substantially circular spring that forms a cone or inverted cone depending on the position of the spring, and the angle θ is defined as It is measured as the angle between the intersections passing through the centerline of the inverted cone. By changing the winding angle θ, different loads can be obtained and the degree of the load depends on the winding angle θ. That is, as described below, the load generated increases as the winding angle θ increases. The force generated by the load is not affected by whether the spring has a conical shape as shown in FIG. 9b or an inverted conical shape as shown in FIG. 9c. That is, 9th
The springs in the figures and FIG. 9c show the same behavior.

FIG. 10 shows the axial springs 10, 12 located in grooves 130 which bend the springs to an assembly winding angle α. When an axial load is applied, the springs 10, 12 exhibit a load winding angle α _L as shown in FIG.

Curves A, B, C and D in FIG. 12 show the load-deflection characteristics of a series of springs with the angle θ varying from 0 ° to 90 ° and with the spring specifications listed in Table 1. Each spring
A, B, C and D have the same requirements except for the winding angle θ.

As described in U.S. Patent Application Nos. 186,016 and 186,018, springs A, B, C, D are formed with specific trailing portions 40, 56 defined by back angles 38, 54, This back angle is defined between the trailing portions 40, 56 and a line perpendicular to the centerlines 28, 30 of the springs 10, 12 (see FIGS. 1 and 2). The front angles 46, 60 also define leading portions 48, 62 of the springs 10, 12, which are the angles that the leading portions 48, 62 make with lines perpendicular to the centerlines 28, 30. FIG. 1 shows the spring 10 with a trailing portion 40 along the inner diameter 42 of the spring, and FIG. 3 shows the spring 12 with a trailing portion 56 along the outer diameter 64 of the spring. As can be seen from FIGS. 1 and 2, when each coil is wound in a circle around the centerline, each turn has a trailing portion and a leading portion,
The leading portion advances further along the centerline as it is wrapped around the centerline following the trailing portion.

Details of canted coil springs having an inner diameter back angle and canted coil springs having an outer diameter back angle are disclosed in the above-mentioned U.S. patent application. The effect of positioning the trailing part on the inner or outer diameter of the inclined coil springs 10, 12 will be described in detail below.

Referring to FIG. 12, curve A shows a spring with a winding angle of 0 °, curve B shows a spring with a winding angle of 15 °, and a critical rise 136 of a spring formed in accordance with the present invention.
The characteristics of are specified. The appearance of this gradual rise showing peak load characteristics is shown in the curves corresponding to springs C, D and E in Table 1.
More clearly indicated by C, D and E.

As shown in FIG. 12, when the winding angle θ increases,
The load reaches its maximum at 90 ゜. The important point is 13
After the peak load shown at 8,140,142, respectively, the force drops sharply to near the force shown by springs A and B. Therefore, these springs are unwound springs A
Although the use areas 146, 148, and 150 are substantially the same as shown in FIG. 12, as shown in FIG. 12, these use areas are distinguished by abrupt load-deflection characteristics. The spring of the present invention has advantages in various applications as described above. As described above, the shape of the illustrated spring is substantially circular, but it can be formed into another shape and used for other purposes. That is, the spring can be easily formed into another shape outside the circle.

As shown in Table 1, the peak load is sufficiently larger than the reference load, and reaches 1725% when the winding angle is 90 °. Thus, a high load can be obtained by using the winding angle. Eventually, as described above, thin wires are used to increase the number of coils per unit length to reduce the stress on the seal when loaded. This makes the stress concentration across the spring more uniform so that a longer life spring can be obtained.

Also, as noted above, curves C, D and E in FIG.
The spring of the present invention, which exhibits a force-deflection curve represented by, can be used for self-locking and self-centering applications that could not be achieved with conventional springs exhibiting a force-deflection curve, represented by curve A. .

Curves A to E show the case where the trailing part is at the outside diameter or at the inside diameter. Curves F and G shown in FIG.
Corresponds to springs F and G having the characteristics shown in Table 2. As shown, curve F shows the load-deflection curve of spring 12 with trailing portion 56 along the outer diameter 64 of the spring, and also shows an annular loop having trailing portion 40 along the inner diameter 42 of the spring of curve G. 2 shows a spring. The winding angle of the spring G is the spring F
, The peak load point 152 appears.

Many spring tests were performed. The characteristics shown by curves A to G in FIGS. 12 and 13 show a spring whose back angle is between 1 ° and 45 °. In particular, these springs have a forward angle of less than 35 °. To determine the load-deflection characteristics of a spring formed in accordance with the present invention, fixtures or jigs 160, 162, 164, 166 whose cross-sections can be used in FIGS. 14, 15, 16 and 17 can be used.

In general, as shown in FIG.
And a piston 170 having a spacer 174, the thickness of which varies so as to compress the inner diameter of the spring 176 toward its outer diameter. The specific flexural load characteristics of such loaded springs are discussed below.

The fixture 162 shown in FIG. 15 is similar to the fixture 160,
The spring 180 is compressed in a groove 182 having a spacer 184, and the spacer radially compresses the spring 180. In addition, a spacer 186 having a variable thickness is used to press the spring 180 in the axial direction.

The fixture 164 shown in FIG. 16 uses a piston 190 to radially compress the spring 192 in the groove 194,
The spacer 196 compresses the spring 192 from the outer diameter to the inner diameter. The fixing tool 166 shown in FIG. 17 compresses the spring 202 in the radial direction
A piston 200 for applying a load in the axial direction is provided.

18 to 21 show the load-deflection characteristics of a spring formed according to the present invention. Representative examples of such springs are shown below.

Spring-Type A Wire diameter: 0.56mm Coil height: 4.09 / 4.14mm Back angle: 13/15 ゜ Front angle: 29/31 ゜ Coil spacing: 0.43 / 0.48mm The spring has 58 coils and the diameter is 19mm In some cases, various springs having a reverse angle on the inner diameter and a reverse angle on the outer diameter were used. Further, such a spring had the following general properties. That is, the winding angle 0
゜, 30 ゜, 55 ゜ and 90 ゜. The winding angle was changed according to each spring.

Spring type B Wire diameter: 0.56mm Coil height: 4.09 / 4.14mm Back angle: 15.5 / 17 ゜ Table angle: 37/39 ゜ Coil spacing: 0.81 / 0.86mm The spacing between coils of spring type B is spring of type A About 1.38 times the distance between coils. By increasing the spacing between the coils, other parameters can be determined based on load, deflection, and the like.

The spring is in the welding position, its inner diameter is 19 mm and the number of coils is 42. The spring formed a reverse angle on the inner diameter or a reverse angle on the outer diameter, and the winding angle was varied among these parameters at 0, 30, 55 and 90 °.

FIG. 18 shows a comparison between Type A and Type B springs, the curves of which show the average load deflection characteristics for various winding angles. Type A springs having a back angle at their inner diameters have a much greater degree of deflection than type B springs having a back angle at their outer diameters.

FIG. 19 shows that the winding angle (TA) is varied between 0, 36, 55 and 90 ° and inserted into the fixture 164 in FIG. 16 to radially load the spring along the main axis. , Is the load-deflection characteristic of a Type A spring in which the deflection is from the inner diameter to the outer diameter and occurs along the main axis in the axial direction. The degree of deflection obtained by radially and axially loading the spring is reduced, and the rate is generally about
You can see that it is 10 to 15%.

It has been found that the application of radial and axial loads to the spring significantly reduces the degree of deflection. A spring having a reverse angle on the outer diameter has a significantly smaller deflection than a spring having a reverse angle on the inner diameter.

FIG. 20 shows an axial spring having a reverse angle on the outer diameter (curve F).
FIG. 5 shows a load-deflection comparison between a spring having a reverse angle at the inner diameter (curve RF). As shown, a spring having a back angle at the inner diameter has about 40% greater degree of deflection than an identical spring having a back angle at the outer diameter.
FIG. 21 shows load-deflection curves for an axial spring (RF) having a reverse angle on the inner diameter and a spring (F) having a reverse angle on the outer diameter. These properties occur when the spring is simultaneously loaded in the axial and radial directions and the spring deflection occurs radially from the outer diameter to the inner diameter. Compare this with the same spring shown in FIG. 19 when loaded from the inside diameter.

By varying the parameters of the spring and the direction of loading of the spring, the spring of the present invention can be designed to accommodate a wide range of load deflection characteristics not previously possible. This is particularly useful where other factors limit the size of the wire and number of coils, such as, for example, the size of the cavity in which the spring is provided.

In general, there are several ways in which the springs 10, 12, 14, 16 are mounted in the cavity. For example, if the dimensions of the cavity create a clearance between the coil and the cavity, or, conversely, the spring has an inner diameter smaller than the inner diameter of the cavity in which the spring is provided, so that the spring is held in the cavity. Elongation, that is, a load may occur.

Also, the springs 10, 12, 14, 16 may be dimensioned so that they interfere between the spring coil and the cavity, and the springs may be held in the cavity. All of these spring cavity shapes are related to the loading of the spring after it has been provided in the cavity.

As mentioned above, the length or dimensions of the cavity will define a continuous path when the ends of the spring are joined, for example, circular, rectangular or other irregular shapes. The mounting of the spring produces a specific force within a certain range of deflection, as described above in connection with FIG.

Referring to FIGS. 22, 23 and 24, a radial spring 220 and a conical axial spring 222 according to an embodiment of the present invention are shown.
And inverted conical axial springs 224 are vacancies 226, 22 respectively.
8 and 230, grooves 226, 228, 230 are shown distorting springs 232, 234, 236 along short axes 240, 242, 244, respectively, while simultaneously loading along long axes 250, 252, 254.

That is, the axial spring 220 has an assembly winding angle α of 90 °, and the groove width 260 is less than or equal to the coil height CH defined in FIG. The spring coils 232 thus interfere, thereby retaining the spring 220 in the groove 226.

The conical axial spring 222 shown in FIG. 23 has an assembly winding angle α of less than 90 °, the spring 220 is distorted along its short axis 242, and the spring has a substantially long axis. Assembled while applying force along 252. In this example, the groove width 262 is larger than the coil height CH (see FIG. 8), but interferes with the coil and the spring 222
To keep the coil in the cavity 228, the width CW of the coil (eighth
(See the figure).

Referring to FIG. 24, the inverted conical axial spring 224 has 9
Has an assembly winding angle α smaller than 0 °,
The spring 224 is radially distorted along the short axis 244 and exerts a force substantially along the long axis 254. In this example,
Groove width 270 is greater than coil height CH, but coil 236
The coil width CW (see FIG. 8) is made smaller to hold the spring 224 in the cavity 230 by interfering with the above.

Shown in FIGS. 25, 26 and 27 are axial springs 250 ', 252' and 254 'provided in cavities 256', 258 'and 260', respectively. Spring deflects its coils 260 ', 262' and 264 'along their long axes 266', 268 'and 270', respectively, and applies a primary load along their short axes 274 ', 276' and 278 '. providing. More specifically, the spring 250 'shown in FIG. 25 is an axial array having an assembly winding angle α of 0 ° (FIG. 10). Spring 250 'is distorted radially along long axis 266' and short axis
274 '. In this example, the groove width 280 'interferes with the coil 260' and places the spring 250 'in the cavity 25.
It is smaller than the coil width CW (FIG. 8) to keep it in 6 '.

As shown in FIG. 26, the conical axial spring 252 '
Has an assembly winding angle α smaller than ゜. The spring 252 'is radially distorted along the long axis 268',
The force acts substantially along the short axis 276 '. In this example, the groove width 282 'interferes with the coil 262'
Coil width CW so that 2 'is held in space 258'
(See FIG. 8). The inverted conical axial spring 254 'shown in FIG. 27 has an assembly winding angle α of less than 30 °. Spring 254 'is radially distorted along major axis 270' and is loaded substantially along minor axis 278 '. The width 284 'of the groove is equal to the width CW of the coil (eighth) in order to interfere with the coil 2647 and retain the spring 254'
Figure).

As shown in FIGS. 22 through 27, various void dimensions can generally be used to load the spring. No.
FIG. 22 shows a cavity having a groove width equal to or smaller than the coil height. Voids having a groove width larger than the coil height and smaller than the coil width are shown in FIGS. 23 and 24, while cavities having a groove width smaller than the coil width are shown in FIG. It is shown in the figure. 26 and 27 show a cavity having a groove width smaller than the cosine of the load angle α _L (see FIG. 11).

Generally, radial springs are used when such springs are incorporated into a cavity at or below the height of the coil to distort the coil along the short axis and apply a load along the long axis. Has many limitations. In any case, the coil does not flex or bend easily, and a very large initial force occurs, after which such force decreases rapidly. Therefore, in order to use the radial spring appropriately, it is necessary to make the width of the groove larger than the height of the coil when the spring is axially loaded along the long axis. This is shown in FIGS. 23 and 24.
It is shown in the figure. Eventually, to provide a useful spring, the width of the groove must be large enough to allow an assembly wrap angle of less than 80 °. As the groove width increases, the assembly wrap angle decreases, reducing the likelihood of spring fatigue when loaded or flexed.

As mentioned above, the radial spring has a winding angle of 90 °,
When such a spring is provided in a cavity, applying force along the long axis will cause the spring to fatigue. The degree of fatigue depends on the amount of winding and the deflection of the spring coil, and the greater these are, the greater the fatigue. Of course, the degree of fatigue depends on the axial force,
It is also affected by other factors such as back angle, coil diameter ratio, wire diameter and coil spacing.

The axial spring of the present invention loaded into a cavity to form a winding angle of 90 ° with a reverse angle on the inner diameter and loaded along the long axis, the spring coil is reversed and distorted along the long axis, and is used. Provides a nearly constant force within the deflection range. The constant force in the deflection is affected by the winding angle, back angle, ratio of coil diameter to wire diameter and other parameters. This axial spring is significantly different from a radial spring which always experiences excessive fatigue under the same load conditions.

Axial spring with an outside diameter with a reverse angle (F type spring)
Has many limitations, especially when the assembly wrap angle is
It is remarkable when it becomes larger than 60 mm. F-type springs having a back angle on the outside diameter do not have high coil deflection because the coil has a tendency to abut rapidly to limit deflection. Thus, the degree of fatigue is always greater when using an F-type spring that has an incorporated winding angle of 60 ° to 90 ° and is axially loaded along the long axis. The greater the winding angle of the assembly, the greater the fatigue. Become.

Axial springs with a reverse angle on the inner diameter (RF type) have a sufficiently large degree of deflection and therefore from 0 °
It is a preferred embodiment of the present invention because of its versatile use including a 90 ° winding angle. An RF type spring is installed in a cavity with a groove equal to or smaller than the coil height CH, and when the assembly winding angle is 90 °, it operates with minimal fatigue. The spring is the only reliable type of spring. RF type spring fatigue occurs when the assembly wrap angle is between 80 ° and 90 °, especially at 90 °.

Although grooves of the type shown in FIGS. 22-27 are rectangular in shape, many differently shaped grooves can be used to incorporate the spring into the cavity and retain the spring in the cavity. The spring can be loaded. An example of such a groove is the groove shown in FIGS. 22 to 27 having side walls orthogonal to the horizontal plane, but other shapes of grooves having angled side walls and angled bottom surfaces (see FIGS. (Not shown) can be used to further affect the load deflection characteristics of the spring.

Examples of factors that affect the force deflection characteristics of an axially wound spring include wire diameter, coil back angle, assembly winding angle, coil diameter to wire diameter ratio (Wd), coil spacing and coil spacing. And the like.
More specifically, as the wire diameter increases, the back angle decreases and the force generated for a given deflection increases.

As the assembly wrap angle increases, the resulting force increases and the deflection increases. As the D / d ratio increases, the resulting force decreases and the likelihood that a constant force will occur within the use deflection range increases. The greater the spacing between the coils, the lower the force and the greater the deflection, and the greater the number of coils, the greater the resulting force.

Generally, the spring has a tilted direction that is determined by whether it is wound clockwise or counterclockwise. RF axial springs are clockwise wound and have a reverse angle on the inside diameter of the spring, while F type springs are counterclockwise wound but have a reverse angle on the outside diameter of the spring.

While the specific spring assembly of the present invention has been described above to illustrate aspects of using the present invention effectively, the present invention is not limited to these examples. Therefore,
It should be understood that modifications, corrections, or the adoption of equivalent configurations for the above embodiments by those skilled in the art are within the scope of the present invention.

[Brief description of the drawings]

FIG. 1 is a plan view of a spring of the present invention having a coil tilted clockwise. FIG. 2 is a diagram relating to line 2-2 of the spring of FIG. 1,
This shows a state where the back angle is at the inner diameter of the spring and the front angle is at the outer diameter of the spring. FIG. 3 is a plan view of the spring of the present invention in which the coil is inclined counterclockwise. FIG. 4 is a view relating to line 4-4 of the spring of FIG. 3,
This shows a state in which the back angle is at the outer diameter of the spring and the front angle is at the inner diameter of the spring. FIG. 5 is a plan view showing the radial spring of the present invention, which is inclined clockwise around the center line, and has a back angle at the top. FIG. 6 is a plan view showing a gradient coil radial spring of the present invention, wherein the coil is tilted counterclockwise around a center line;
This shows a state where the back angle is at the bottom. FIG. 7 is a diagram showing a load-deflection curve for a spring assembled according to the present invention. FIG. 8 is a diagram schematically illustrating an axially inclined coil spring having a winding angle θ in order to show how the winding angle θ is calculated. FIGS. 9a, b, c, d and e are schematic diagrams showing axial and radial springs with various winding angles. FIG. 10 is a cross-sectional view of the axial spring showing a winding angle position when the spring is mounted in the groove. FIG. 11 is a cross-sectional view of the axial spring showing a position of a load winding angle under a load. FIG. 12 is a diagram showing a plurality of load-deflection curves respectively corresponding to annular coil springs having elasticity in the axial direction having various winding angle directions. FIG. 13 is a diagram showing a load-deflection curve showing the effect of a plurality of deflections on the load-deflection characteristics of an annular coil spring having elasticity in the axial direction having a preselected winding angle. FIG. 14 shows the load of a spring formed according to the present invention.
It is sectional drawing which shows the jig | tool for determining a bending characteristic. FIG. 15 shows the load of a spring formed according to the present invention.
It is sectional drawing which shows the jig | tool for determining a bending characteristic. FIG. 16 shows the load of a spring formed according to the present invention.
Sectional drawing which shows the jig | tool for determining a bending characteristic. FIG. 17 shows the load of the spring formed according to the present invention.
It is sectional drawing which shows the jig | tool for determining a bending characteristic. FIG. 18 is a diagram showing load-deflection characteristics for a spring formed according to the present invention. FIG. 19 is a diagram showing load-deflection characteristics for a spring formed according to the present invention. FIG. 20 is a diagram showing load-deflection characteristics for a spring formed according to the present invention. FIG. 21 is a diagram showing load-deflection characteristics for a spring formed according to the present invention. 22 to 27 are cross-sectional views showing various embodiments of the inclined coil spring assembly of the present invention, in which the coil is supported non-interferingly in a direction for controlling the elastic characteristic of the coil. ing. [Explanation of Main Symbols] 10, 12, 14, 46: Inclined coil spring assembly, 18, 20, 22, 24: Coil, 28, 30, 32, 34: Center line, 38: Back angle, 40: Trailing part, 42: inside diameter, 46: front angle, 48: leading part, 50: outside diameter.

Continuation of the front page (56) References JP-A-61-165035 (JP, A) JP-B-48-9286 (JP, B1) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16F 1 / 00-6/00

Claims (10)

(57) [Claims] A tilted coil spring device having a major axis and a minor axis and inclined in the direction of the centerline along a centerline defined by a continuous intersection of the major and minor axes. A plurality of coils interconnected so as to form a garter-type gradient coil spring having elasticity in the axial direction of the gradient coil spring; and an arrangement of a trailing portion of each coil with respect to a line perpendicular to the center line. A back angle that defines and determines the load-deflection characteristics of the canted coil spring; and a front angle that defines an array of leading portions of each coil with respect to the perpendicular line and has an angle greater than the back angle; Supporting means for supporting the garter-type coil spring having elasticity in the axial direction non-interferingly in a predetermined direction to control the elastic characteristic of the garter-type inclined coil spring having elasticity in the axial direction. A tilt coil spring device, wherein the supporting means includes means for defining a cavity for supporting and orienting the coil spring at a winding angle of greater than 0 ° and less than 90 °. 2. The invention of claim 1 wherein said support means includes means defining a cavity such that said coil spring is loaded and tilted along said longitudinal axis. And a gradient coil spring device. 3. The gradient coil according to claim 1, wherein said support means includes means defining a cavity for loading said coil spring along both the major and minor axes. Spring device. 4. The method according to claim 1, wherein
The trailing portion is provided along an outer diameter of the coil spring,
The inclined coil spring device, wherein the leading portion is provided along an inner diameter of the coil spring. 5. The method according to claim 1, wherein
The trailing portion is provided along an inner diameter of the coil spring,
The inclined coil spring device, wherein the leading portion is provided along an outer diameter of the coil spring. 6. A canted coil spring assembly, having a major axis and a minor axis, inclined in a direction of the centerline along a centerline defined by a continuation of the intersection of the major and minor axes. A plurality of coils; a back angle defining an array of trailing portions of each coil with respect to a line perpendicular to the centerline and determining the load-deflection characteristics of the gradient coil assembly; and a leading of each coil with respect to the perpendicular line. A front angle having an angle larger than the back angle, and a support means for supporting the plurality of coils in a non-interfering manner and controlling elastic characteristics of the plurality of coils; A canted coil spring assembly, wherein the support means includes means defining a cavity for supporting and orienting the coil spring at a winding angle greater than 0 ° and less than 90 °. 7. The tilt coil spring according to claim 6, wherein the plurality of coils are connected to each other to form a garter type tilt coil spring having elasticity in the axial direction of the tilt coil spring. A canted coil spring assembly comprising means for flexing the spring along a short axis and defining a cavity for loading the resilient garter-type coil spring along a long axis. . 8. The apparatus of claim 6, wherein said support means defines a cavity for flexing said spring along a short axis and for loading said resilient garter-type coil spring along a long axis. A coil spring assembly comprising: 9. The method according to claim 6, wherein
The trailing portion is provided along an outer diameter of the coil spring,
A canted coil spring assembly wherein the leading portion is provided along an inner diameter of the coil spring. 10. The method according to claim 6, wherein the trailing portion is provided along an inner diameter of the coil spring, and the leading portion is provided along an outer diameter of the coil spring. And a gradient coil spring assembly.