A method of manufacturing a set of cone pulleys

Abstract

To solve a problem that, in a conventional technology, a further free contour (shape) cannot be selected due to a limit of an integral calculation, and also, there is no guideline related to a necessary collection which actually occurs.SOLUTION: A set of skeleton data 70 composed of three variables of a moving distance S of a vertical load 10 of weight W being an invariable guideline for improving balance performance related to a spring balance mechanism, an elongation ξL of a spring 20 corresponding to the moving distance, and a rotation torque radius ratio P is acquired on the basis of an energy preservation law and a rotation torque balance law described in the present invention which should be satisfied by the spring balance mechanism. A correction caused by variation in a three-dimensional positional relation which is difficult to be treated in a lump, and actually occurs can be added with the set of skeleton data 70 as a correction guideline, and a method for manufacturing a pair of cone pulleys which is not constricted by a limit of an integral calculation, and formed into a desired contour (shape) at the vertical load 10 side or the spring 20 side can be established.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The present invention relates to a spring balance mechanism that enables manual movement of a vertical load via a set of cone pulleys (or cams) (hereinafter abbreviated as a set of cone pulleys), and particularly to a method for forming a set of cone pulleys in the balance mechanism. Here, the springs include generally springs having linear characteristics, such as tension coil springs, compression coil springs, spiral springs, etc. In the present invention, mainly, the tension coil spring with a wide application range of the present invention will be described.

Background Art

[0002] Conventionally, for example, in a device for manually moving an X-ray tube or the like, which is a vertical load, in the vertical direction, as in a mobile X-ray imaging device, generally, a counterweight having the same weight as the vertical load has been used. However, for medical devices such as mobile X-ray imaging devices, due to their portability and in order to easily move the vertical load, a spring balance mechanism using a spring that can eliminate the starting resistance associated with the inertial mass of the counterweight and can easily adapt to the use environment is used.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Non-Patent Documents

[0004]

Non-Patent Document 1

Non-Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0005] In the prior art, due to limitations in integral calculus, it is not possible to freely select a contour (shape), and there is no guidance regarding corrections related to fluctuations in the three-dimensional positional relationships that are actually necessary, and a method for forming the contour (shape) of the main body of a set of cone pulleys has not been established.

Means for Solving the Problems

[0006] However, in recent years, numerical integration has become available for various functions without restrictions, and the degree of freedom in determining the contour (shape) of the main body of a set of cone pulleys has been significantly improved. However, even though the degree of freedom in determining the contour (shape) of the main body of a set of cone pulleys increases due to numerical integration (as well as numerical differentiation), there are certain constraint conditions in order to establish a spring balance mechanism. Various corrections, including the pitch diameter, etc. of a set of cone pulleys, are required due to those constraint conditions and fluctuations in the three-dimensional positional relationships that are practically impossible to avoid. Therefore, the concept of a "set of skeleton data" is introduced as a guideline for various corrections.

Advantages of the Invention

[0007] An extensively applicable method for forming the contour (shape) of the main body of a set of cone pulleys is established. At the same time, various corrections that improve the balance performance and are actually not negligible due to fluctuations in the three-dimensional positional relationships become possible by using the "set of skeleton data" as a guideline, and it becomes possible to form the contour (shape) of the main body of a set of cone pulleys more precisely than in the prior art. And a spring balance mechanism using that set of cone pulleys is provided.

Brief Description of the Drawings

[0008]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Embodiments for Carrying Out the Invention

[0009] FIG. 1 shows a spring balance mechanism 100 in an initial balanced state where the vertical load 10 is at the lowest position, using a pair of cone pulleys 50 formed by a method for forming the contour (shape) of the main body 52 of a pair of cone pulleys 50. The spring balance mechanism 100 shown in FIG. 1 balances the weight W on the vertical load 10 side with the tension of the spring 20 and enables the vertical load 10 to be manually and smoothly moved. It is composed of the spring 20, a pair of cone pulleys 50 according to the present invention, and a wire rope 30 (hereinafter abbreviated as rope 30) with a diameter ρ (see FIG. 4), which is a tension transmission member that wraps around the outer periphery of the pair of cone pulleys 50 and transmits the tension between the vertical load 10 and the spring 20. One end of the rope 30 is connected to the vertical load 10, wound around the outer periphery of the pair of cone pulleys 50, and then connected to one end of the spring 20. The other end of the spring 20 is swingably supported by a spring fulcrum 40 on a support portion (not shown) of the spring balance mechanism 100.

[0010] Note that the present invention is not limited to the vertical load 10 vertically suspended from a set of cone pulleys 50 according to the present invention as shown in FIG. 1. For example, with respect to a load that rises and falls on an inclined plane, it can be applied by converting the moving distance on the inclined plane into a vertical moving distance.

[0011] A set of cone pulleys 50 in FIG. 2 includes a main body 52 having a rope groove 58 for accommodating and guiding a rope 30 wound around its outer periphery, and a support shaft 60 of the main body 52. However, it should be noted that FIG. 2 shows a set of cone pulleys 50 with a rope 30 wound around its outer periphery in the initial balanced state of the spring balance mechanism 100 shown in FIG. 1. Also, illustration of a bearing structure or the like that rotatably supports the support shaft 60 of the set of cone pulleys 50 is omitted.

[0012] FIG. 3 represents a virtual spiral curve 80 drawn by the center line of a rope 30 accommodated and guided in a rope groove 58 provided on the outer periphery of a main body 52 of a set of cone pulleys 50. Representing the contour (shape) of the main body 52 of the set of cone pulleys 50 by the virtual spiral curve 80 means assuming the tension transmitted by the rope 30, that is, the weight of the vertical load 10 and the tension of the spring 20, as the tension acting on the center line of the rope 30. This has the merit of not impairing the consistency with general physical handling and simplifying the derivation process of various relational expressions related to the set of cone pulleys 50.

[0013] That is, the virtual spiral curve 80 shall determine the contour (shape) of the main body 52 of the set of cone pulleys 50. Therefore, the method for forming the contour (shape) of the set of cone pulleys 50 of the present invention aims to specify the spiral curve 80. Also, the spiral curve 80 is indirectly specified by reducing the diameter of the bottom of the rope groove 58 provided for guiding the rope 30 on the main body 52 by the radius (ρ / 2) of the rope 30.

[0014] In this specification, the case where the rope groove 58, and thus the spiral curve 80, is left-handed will be described. Whether the rope groove 58 is left-handed or right-handed is selected from the perspective of, for example, the method of supporting a pair of cone pulleys 50 in the spring balance mechanism 100 using a pair of cone pulleys 50, or the selection may be arbitrary.

[0015] In this specification, the "pair of cone pulleys 50" means that the case where the main body 52 is not of the integral type as shown in FIGS. 1 and 2, but is a separable type that rotates around the axis of each support shaft 60 as if the vertical load 10 side and the spring 20 side were integral. is also included.

[0016] In this specification, as shown in FIG. 1, the orthogonal coordinates of the absolute coordinates (stationary coordinates) of the left-handed coordinate system that conform to the description of the rope groove 58, and the local coordinates (o-xyz) having the origins 54 and 56 of the left-handed coordinate system that conform to the description of the left-handed rope groove 58, and thus the spiral curve 80, associated with the pair of cone pulleys 50 shown in FIG. 2 are used. Note that the cylindrical polar coordinates specifying the spiral curve 80 are used as if there were two cylindrical polar coordinates having the origins 54 and 56 at a place where there should originally be one, in order to enable the spiral curves 80 on the vertical load 10 side and the spring 10 side to be handled separately, as shown in Equations 3 and 4 described later.

[0017] FIG. 4 shows only the rope 30 that spirally wraps along the rope groove 58 around the main body 52 on the spring 20 side of the pair of cone pulleys 50 in FIG. 2 near the origin 54 on the spring 20 side. Note that FIG. 4 is also a solid view of a part of the spiral curve 80 near the origin 54 on the spring 20 side. Further, FIG. 4 shows the orthogonal coordinates in the above-described absolute coordinates of an arbitrary point near the origin 54 (r x , r y , r z) shows the relationship with the radial distance r(θ) in cylindrical polar coordinates. Note that the solid figure of the rope 30 that encloses the spiral curve 80 and is wound along the rope groove 58 near the origin 56 (see Fig. 5) on the side of the vertical load 10 is omitted.

[0018] In the case of the initial balanced state shown in Fig. 1 and when a pair of cone pulleys 50 in the initial balanced state rotates by α in the rotational direction 62, the orthogonal coordinates (r x , r y , r z ) in the absolute coordinates of the shape of the spiral curve 80 are represented by Equation 1 using the radial distance r(θ) in cylindrical polar coordinates.

Equation

[0019] Similarly, the orthogonal coordinates (R X , R Y , R Z ) in the absolute coordinates of any point on the side of the vertical load 10 on the spiral curve 80 are represented by Equation 2 using the radial distance R(θ) in cylindrical polar coordinates.

Equation

[0020] When the vertical load 10 is manually moved upward by a distance S from the initial balanced state in Fig. 1, the rope 30 on the side of the vertical load 10 of the pair of cone pulleys 50 that is rotated in the rotational direction 62 is guided by the rope groove 58 and wound around the outer circumference along the spiral curve 80 of the pair of cone pulleys 50. The winding amount S W of the rope 30 around the pair of cone pulleys 50, taking the winding circumferential angle (hereinafter abbreviated as the winding angle) as α W (accurately, it is determined only after determining the engagement point 92 (see Fig. 5) that defines the winding start angle and end angle), is represented by Equation 3 in the local coordinates o-xyz associated with the pair of cone pulleys 50. The winding amount SW In principle, the vertical load 10 vertically rises upward by an amount corresponding to [Number]

[0021] Similarly, the amount of winding and unwinding s of the rope 30 unwound from a set of cone pulleys 50 in the initial balanced state of FIG. 1 is defined by the winding and unwinding circumferential angle (hereinafter abbreviated as the winding and unwinding angle) α around the cone pulley S (Precisely, it is determined only after determining the engagement point 90 (see FIG. 6) that defines the winding start angle and the end angle thereof. Assuming that the arc length element on the spring 20 side of the spiral curve 80 is ds, it is represented by Equation 4. In principle, the spring 20 contracts by an amount corresponding to the amount of winding and unwinding s of the rope 30, and the tension of the spring 20 weakens.) [Number]

[0022] In Equations 3 and 4, θei refers to the engagement angle, which will be described later, in the initial state of the spring balance mechanism 100 shown in FIG. 1.

[0023] Due to the development of numerical integration in recent years, the integration operations in Equations 3 and 4 can be widely performed regardless of the functional expressions of the radial distances R(θ) and r(θ). A major limitation in the prior art, where the integration was restricted to functions such as constants, linear expressions, or exponential functions for which integration was easy, is eliminated. Furthermore, in Equations 3 and 4, the lead e of the rope groove 58 of the main body 52 of a set of cone pulleys 50, which was not considered in the integration operations of the prior art, is taken into account, improving the balance performance of the spring balance mechanism 100.

[0024] FIG. 5 shows the engagement portion with the rope 30 on the vertical load 10 side in the initial balanced state of a set of cone pulleys 50, and shows the engagement point 92 that is also the contact point where the center line of the rope 30 contacts and is tangent to the spiral curve 80. In the initial balanced state shown in FIG. 5, the engagement point 92 is at a point very close to the origin 56 (R in Equation 2(a)) Z position), and defines an engagement radius Re, which is one of the radial vectors R(θ) that defines the Z-axis and the spiral curve 80, and an engagement angle θe (not shown because it is very small) formed between the engagement radius Re and the XZ plane on the -X side. The radial vector R(θ) is represented by the length of the perpendicular line between the Z-axis or z-axis of the straight line forming an angle θ with respect to the XZ plane on the -X side shown in FIG. 5 and the spiral curve 80 in the cylindrical polar coordinate representation.

[0025] The position of the engagement point 92 shown in FIG. 5 moves along the Z-axis direction in absolute coordinates as the vertical load 10 moves vertically, that is, as a pair of cone pulleys 50 rotates. The engagement angle θei corresponding to the engagement point 92 with the rope 30 in the initial balanced state defines the winding start angle of the rope 30, and the engagement point 92 with the rope 30 after α rotation of a pair of cone pulleys 50 W defines an engagement angle θeL corresponding to the winding angle α (therefore, defining the winding end angle). Therefore, the winding angle α shown in Equation 3 W is not the same as the rotation angle α unless the engagement angles θei and θeL are equal, and correction is required. The prior art lacks consideration in this regard.

[0026] On the vertical load 10 side, the engagement point 92 between the center line of the rope 30 and the spiral contour 80, and the related engagement angle θe, etc. are determined by obtaining the inclination angle of the tangent line represented by the center line of the rope 30 at an arbitrary point (angle coordinate θj) of the spiral contour 80 as shown in Equation 5, and ensuring that the inclination angle of the tangent line satisfies the condition of the vertical suspension of the vertical load 10. The angle coordinate θj has the counterclockwise direction as the + direction, and in the case of the side of the vertical load 10, the -X side of the XZ plane in the absolute coordinates is used as the reference (θ = 0).

Number

[0027] Equation 5(c) shows that the engagement point 92 and the engagement angle θe vary depending on the magnitude of the radial distance R(θ) in the cylindrical polar coordinate representation and the rotation angle α of the pair of cone pulleys 50. Due to this variation, the take-up angle α in Equation 3 W may need to be corrected as described above. In addition, the suspension point of the rope 30 indicated by the absolute coordinate RY in Equation 5(d), that is, the three-dimensional positional relationship varies. In the present invention, different from the prior art, the variation in the three-dimensional positional relationship related to the pair of cone pulleys 50, starting with the variation in the engagement point 92 with these ropes 30 (including the engagement point 90 described below), is targeted for correction to improve the balance of the spring balance mechanism 100.

[0028] FIG. 6 shows the engagement portion with the rope 30 on the spring 20 side in the initial balanced state of the pair of cone pulleys 50 corresponding to FIG. 5. In FIG. 6, the engagement point 90 is the contact point where the center line of the rope 30, which is a tangent to the spiral curve 80, contacts, similar to the above-described engagement point 92. The engagement point 90, similar to the case of the engagement point 92, is a point extremely close to the origin 54 (rz position in Equation 1(a)) in the initial balanced state, and the engagement radial distance r e of the spiral curve 80 connecting the z-axis and the engagement point 90 is determined. The engagement angle θe formed between the engagement radial distance r e and the xz plane on the +x side is determined. Therefore, there is an angular phase difference of 180° between the reference planes of the angular coordinates θ on the vertical load 10 side and the spring 20 side. This corresponds to, in principle, considering the shapes of the main bodies 52 on the vertical load 10 side and the spring 20 side of the pair of cone pulleys 50, which are integrated, with different origins and reference of the angular coordinates as shown in Equation 1 and Equation 2. Since the pair of cone pulleys 50 is constituted by the spring 20 side and the vertical load 10 side, the + direction of the angular coordinate θ on the spring 20 side is also in the clockwise direction.

[0029] On the spring 10 side, the engagement point 90 between the center line of the rope 30 and the spiral contour 80, and the related engagement angle θe, etc. are determined by obtaining the inclination angle of the tangent line represented by the center line of the rope 30 at an arbitrary point (let it be the angular coordinate θj) of the spiral contour 80 as shown in Equation 6, and satisfying the condition that the linear equation of the tangent line having that inclination angle passes through the absolute coordinates of the spring fulcrum 40.

Number

[0030] The engagement point 90 also determines the engagement angle θeL corresponding to the engagement point 90 with the rope 30 in the initial balance state and the engagement angle θeL corresponding to the engagement point 90 after α rotation of the set of cone pulleys 50 as described for the engagement point 92. Therefore, as described for the engagement point 92, the engagement point 90 may prompt a correction of the unwinding angle α that determines the unwinding amount s obtained by Equation 4 of the rope 30 of the spring 20. S of the correction.

[0031] Furthermore, the coordinates R of the engagement point 92, which is the suspension point on the vertical load 10 side Y Similarly, the orthogonal coordinates (r x , r y , r z ) of the engagement point 90, which is the suspension point of the spring 20, vary as shown in Equation 6(e) and affect the elongation ξL of the spring 20. This variation is also one of the objects of correction in the present invention as a variation in the three-dimensional positional relationship.

[0032] The spring balance mechanism 100 using a set of cone pulleys 50 constitutes an independent and mechanically closed system. Therefore, it can be considered that "when the vertical load 10 rises, the potential energy of the vertical load 10 increases, while the elastic energy of the spring, which is equal to the increase in the potential energy, is consumed (decreases)". That is, within the spring balance mechanism 100, which is a mechanically closed system, energy is conserved. In other words, a set of cone pulleys 50 that make up an ideal spring balance mechanism 100 must have a function that satisfies the law of conservation of energy.

[0033] When the vertical load 10 with a weight W is at the lowest position, in the initial balanced state of the spring balance mechanism 100 shown in Fig. 1, let the elongation of the spring 20 be ξm, the vertical movement distance of the vertical load 10 from the initial balanced state shown in Fig. 1 and the like be S, the elongation of the spring 20 at that time be ξL, the total vertical movement distance of the vertical load 10 be SE, the elongation of the spring 20 at that time be ξE, and applying the law of conservation of energy to the vertical movement of the vertical load 10, Equation 7 is obtained.

Equation

[0034] The law of conservation of energy is a necessary condition that an ideal spring balance mechanism 100 should naturally satisfy, and within the range of the total vertical movement distance SE of the vertical load 10, it complements the rotational torque balance law described later. However, it is not a sufficient condition such as the balance law described below that the spring balance mechanism 100 satisfies.

[0035] A set of cone pulleys 50 functions as a balance pulley that balances the rotational torque around the Z-axis via the rope 30 due to the vertical load 10 and the rotational torque via the rope 30 due to the force of the spring 20. That is, a set of cone pulleys 50 must satisfy the rotational torque balance law (hereinafter simply referred to as the balance law), which is a sufficient condition that an ideal spring balance mechanism 100 should naturally satisfy.

[0036] According to the balance principle, in the initial balanced state of the spring balance mechanism 100 shown in FIG. 1, the rotational torque radii of the vertical load 10 side and the spring 20 side of the weight W around the Z-axis, and thus around the axis of the support shaft 62, are respectively R T0 , r T0 . Then, Equation 8 is obtained.

Equation

[0037] Similarly, according to the balance principle, when a set of cone pulleys 50 rotates by α in the rotational direction 62 from the initial balanced state shown in FIG. 1, the rotational torque radii of the vertical load 10 side and the spring 20 side are respectively R T , r T . Then, Equation 9 is obtained.

Equation

[0038] In Equations 8 and 9, the magnitudes of the rotational torque radii R T0 , R T and r T0 , r T are respectively represented by the shortest distance from the Z-axis to the center line of the rope 30 (including its extension line) which is the tangent to the spiral curve 80, that is, the length of the common perpendicular between the two lines. In this regard, the present invention is different from the prior art that does not distinguish between the radial R(θ), r(θ) in the cylindrical polar coordinate representation and the rotational torque radii R T0 , r T0 etc., and improves the balance performance of the spring balance mechanism 100.

[0039] Substituting the results of Equations 8 and 9 obtained from the balance principle into Equation 7(a) derived from the law of conservation of energy, Equation 10 is obtained.

Equation

[0040] Selecting the initial rotation torque radius ratio Po means, as shown in Equation 8, selecting the spring constant k and the maximum elongation ξm of the spring 20. Further, through the above Equation 10, and thus through Po and P, as a result, the contour (shape) of a set of cone pulleys 50 on the vertical load 10 side and the spring 20 side will be indirectly determined.

[0041] The law of conservation of energy (and thus Equation 7), and the equilibrium law (and thus Equation 8 and Equation 9) hold in both the ascending process and the descending process of the vertical load 10, and in principle are not affected by whether the posture of the support shaft 60 is horizontal or vertical, etc.

[0042] The variables related to a set of cone pulleys 50 consist of the following given elements, selectable elements, and elements to be determined. The given elements given in advance are the weight W of the vertical load 10, its total moving distance (stroke) S E , and the accommodation space of a set of cone pulleys 50 and the spring 20, etc. The elements that should be selected or can be selected when forming the contour (shape) of a set of cone pulleys 50 are the initial rotation torque radius ratio Po, the spring constant k, and the lead e of the rope groove 58 of a set of cone pulleys 50, etc. The elements to be determined after setting when forming the contour (shape) of a set of cone pulleys 50 are the radial distance R(θ) on the vertical load 10 side and the radial distance r(θ) on the spring 20 side in the cylindrical polar coordinate representation that specifies the spiral curve 80.

[0043] In particular, from the above Equations 7 and 10, the set of three variables including the length ξL of the spring 20 and the rotation torque radius ratio P corresponding to the moving distance S of the vertical load 10 with weight W is determined corresponding to the moving distance S, and constitutes the "set of skeletal data 70" shown in Table 1 for a set of cone pulleys 50 used in the spring balance mechanism 100.

Table 1

[0044] Since the data set 70 in Table 1 is derived from Equation 7 and Equation 10, it enables the formation of an ideal set of cone pulleys 50 and an ideal spring balance mechanism 100. Therefore, it is important data in the method for forming a set of cone pulleys 50 of the present invention described later, and it is data that should be complied with as much as possible. By complying with it, a set of cone pulleys 50 and a spring balance mechanism 100 with high balance performance can be realized. However, as described in the flowchart 200 (see FIG. 7) of the method for forming the present invention described later, the data set 70 of the skeleton data in Table 1 does not directly specify the actual set of cone pulleys 50, that is, the radial diameters R(θ) and r(θ) of the spiral curve 80.

[0045] The "data set 70 of skeleton data" in Table 1 has the following characteristics (or properties) from the perspective of utilization Note that in order to utilize the data set 70 of skeleton data, it is a prerequisite that (k / W) is the same. For example, in order to utilize the data in Table 1, it is a prerequisite that (k / W) = 0.0024 (1 / mm).

[0046] 1. The "data set 70 of skeleton data" is data that a set of cone pulleys 50 should satisfy regardless of the functional expressions that define the contour (shape) of the main body 52 on the spring 20 side or the vertical load 10 side, that is, the radial diameters R(θ) and r(θ) of the spiral curve 80. That is, it is a data source that has the potential to form a set of cone pulleys 50 with various contours (shapes). 2. In reality, due to reasons such as the variation of the above-mentioned three-dimensional positional relationship, the engagement points 90 and 92 with the rope 30 when a set of cone pulleys 50 rotates by α are generally different from the engagement points 90 and 92 before rotation in absolute coordinates, that is, the engagement angle θe is different. The winding amount SW and unwinding amount s of the rope 30 related to a set of cone pulleys 50, the engagement radial diameters re and Re of the radial diameters r(θ) and R(θ) with the rope 30, and the rotation torque radius r T , R TModification is necessary, and the guideline for the modification is the "set 70 of skeletal data". That is, as long as the modification is in line with the "set 70 of skeletal data", a set of cone pulleys 5 that achieve precise balance performance The automatic realization of the formation of the contour (shape) of 0 is an important feature of using the "set 70 of skeletal data".

[0047] As a secondary effect, it becomes possible to select the contour (shape) on the vertical load 10 side or the spring 20 side of a set of cone pulleys 50 as desired. Note that the "set 70 of skeletal data" of a set of cone pulleys 50 conforms to a specific (k / W) ratio as shown in Formula 7 and Formula 10. When the (k / W) ratio is different, it is impossible to maintain the balance function within a certain moving distance S that is not short. 3. As long as the (k / W) ratio is the same, the cone pulley 50 formed based on the set 70 of skeletal data can of course be directly used within a narrow vertical movement range. For example, when the range of the vertical movement distance is 1000 mm, it is possible to form a set of cone pulleys 50 of the present invention by directly using the set 70 of skeletal data corresponding to, for example, the vertical movement distance of 500 mm to 1500 m in Table 1 within the range of the vertical movement distance. Therefore, for the formation of the contour (shape) of a set of cone pulleys 50, it is sufficient to devote efforts to the modification for the variation of the three-dimensional positional relationship referred to in the present invention without recalculating the set 70 of skeletal data. Alternatively, it is of course possible to directly use a set of cone pulleys 50 formed by the forming method of the present invention based on the set 70 of skeletal data in Table 1 where the range of the vertical movement distance S is 1500 mm.

[0048] Since the set 70 of skeletal data has the above characteristics, for each specific (k / W) and an appropriate movement distance S EThe data file of each set of skeleton data 70 derived each time serves not only as the above-described correction guideline for determining the respective radial diameters r(θ) and R(θ) on the vertical load 10 side and the spring 20 side of each set of cone pulleys 50 with a wide application range that form a set of cone pulleys of the spring balance mechanism 100, but also as a compliance data file of the spring balance mechanism 100.

[0049] In the above discussion, as described with respect to FIG. 1, it is assumed that the vertical load 10 is vertically suspended from a set of cone pulleys 50. However, in addition to the case where the load on the inclined plane described at the beginning moves, the present invention is applicable by performing the same processing as the processing for the restraint conditions of the spring 20 also when the vertical load 10 moves along a vertical rail (not shown) installed on a support portion (not shown) of the spring balance mechanism 100.

[0050] In the rope groove 58 of the main body 52 of a set of cone pulleys 50 of the spring balance mechanism 100 in FIG. 7 Each step constituting the flowchart 200 of the method of forming the spiral curve 8 formed by the radial diameters R(θ) and r(θ) in cylindrical polar coordinates will be described. In step 202, under the given elements W, SE, the selected elements P0, k are selected, and the maximum elongation ξm of the spring 20 of the set of skeleton data 70 is obtained by Equation 8. At this stage, a part of the basic elements of Equation 7 and Equation 10 in the next step 204 is determined.

[0051] In step 204, for each vertical movement distance S when the vertical load 10 is vertically moved upward from the initial balanced state at the lowest position in the spring balance mechanism 100, the elongation ξL of the spring 20 corresponding to the vertical movement distance S is obtained by Equation 7 and the rotation torque radius ratio P is obtained by Equation 10, and a set of skeleton data 70 (see Table 1) related to a set of cone pulleys 50 is created. The fact that the set 70 of skeletal data can be obtained even when the radial diameters R(θ) and r(θ) of the cylindrical polar coordinate representation of a set of cone pulleys 50 are undetermined is a very important feature of the present invention. Conversely, this indicates that the set 70 of skeletal data is the source enabling the formation of a set of cone pulleys 50 with various contours (shapes).

[0052] In the branch step 205 between step 206 and step 216, it branches depending on the order of setting the functional expressions of the radial diameters R(θ) and r(θ) in the cylindrical polar coordinate representation.

[0053] In step 206, the radial diameter R(θ) of the spiral curve 80 on the vertical load 10 side is set to a desired functional expression R(α) of the rotation angle α of a set of cone pulleys 50. In step 208, considering the variation of the three-dimensional positional relationship for each vertical movement distance S, using the vertical movement distance S as a pointer, the engagement point 92 with the rope 30, the engagement angle θe, and the winding angle α of the rope 30 are obtained and corrected by Equation 5 and Equation 3, and the rotation torque radius R W is obtained, and the rotation angle α of a set of cone pulleys 50 is determined. T In step 210, the rotation torque radius r on the spring 20 side is obtained as a function of the rotation angle α through the rotation torque radius ratio P of the set 70 of skeletal data corresponding to the vertical movement distance S. T In step 212, the radial diameter r(θ) on the spring 20 side is assumed to be a functional expression r(α) of the rotation angle α based on the obtained rotation torque radius r on the spring 20 side. T In step 214, using the elongation ξ of the spring of the set 70 of skeletal data as a pointer and considering the variation of the three-dimensional positional relationship, the engagement points 90 with the rope 30, the engagement angle θe, and the winding angle α of the rope 30 are obtained and corrected by Equation 6 and Equation 4 L respectively, and the assumed functional expression r(α) of the radial diameter r(θ) is corrected, and the rotation torque radius r on the spring 20 side is determined. S T

[0054] ​​​​​In step 216 of first setting the radial diameter r(θ) related to the contour (shape) on the spring 20 side, the radial diameter r(θ) of the spiral curve 80 on the spring 20 side is set to a desired functional expression r(α) of the rotation angle α of the set of cone pulleys 50. In step 218, the elongation ξ of the spring L Each time, considering the variation of the three-dimensional positional relationship, the elongation ξ of the spring L is used as a pointer, and according to Equation 6, the engagement point 90 with the rope 30, the engagement angle θe, and according to Equation 4, the winding and unwinding angle α of the rope 3 S are obtained and corrected, and the rotation torque radius r T and the rotation angle α of the set of cone pulleys 50 are determined. In step 220, through the rotation torque radius ratio P of the set of skeleton data 70 corresponding to the elongation ξ of the spring L the rotation torque radius R on the vertical load 10 side T is obtained as a function of the rotation angle α. In step 222, the functional expression R(α) of the radial diameter R(θ) on the vertical load 10 side is assumed as a function of the rotation angle α based on the obtained rotation torque radius R T In step 224, using the vertical movement distance S of the set of skeleton data 70 as a pointer and considering the variation of the three-dimensional positional relationship, according to Equation 5, the engagement point 92 with the rope 30 on the vertical load 10 side, the engagement angle θe, and according to Equation 3, the winding angle α of the rope 30 are obtained and corrected, and at the same time, the assumed functional expression R(α) of the radial diameter R(θ) is corrected to determine the rotation torque radius R W on the vertical load 10 side. T In the final step 226, based on the obtained data, it is verified that the balance rule holds according to Equations 8 and 9. Note that step 226 is not an essential step for the method of forming the contour (shape) of the set of cone pulleys 50 of the present invention, but a step for confirmation.

[0055] In the final step 226, based on the obtained data, it is verified that the balance rule holds according to Equations 8 and 9. Note that step 226 is not an essential step for the method of forming the contour (shape) of the set of cone pulleys 50 of the present invention, but a step for confirmation.

[0056] As shown in step 205 and subsequent steps 206 to 214, according to the method of forming the contour (shape) of a set of cone pulleys 50, the shape on the vertical load 10 side can be set by a desired functional expression, and then the shape on the spring 20 side can also be obtained. This is a feature of the present invention in addition to using the set of skeleton data 70 as a guide for modification, different from the conventional method of setting the shape on the spring 20 side first and then determining the shape on the vertical load 10 side.

Claims

[Claim 1] A method for manufacturing a set of cone pulleys formed by a pair of vertical load side shapes and a spring side shape, comprising: a) selecting three selection elements consisting of a spring constant ratio (k / W) to a vertical load W, an initial rotational torque radius ratio P0, and a maximum spring elongation ξm, which satisfy the total vertical travel distance SE of a given element and the following formula 8 of the rotational torque balance law; b. 1) A step of dividing the total vertical travel distance SE, with the lowest position of the vertical load W as the lowest section start point, into a plurality of continuous sections, and for each section end (upper end), calculating the spring extension ξL corresponding to the vertical travel distance S from the lowest section start point by the following formula 7 of the law of conservation of energy, and calculating the rotational torque radius ratio P by the following formula 10 derived from the law of conservation of energy and the law of rotational torque balance, to create a set 70 of skeleton data for a set of cone pulleys; b.2) A step of dividing the spring extension range, which is the difference between the maximum spring extension ξm and the minimum spring extension ξE, into a plurality of continuous spring extension sections, with the highest position of the spring extension as the start of the highest section, and calculating the vertical movement distance S defined in one step corresponding to the spring extension ξL from the following formula 7 and the rotational torque radius ratio P from the following formula 10 derived from the law of conservation of energy and the law of rotational torque balance, to create a set of skeleton data 70 for a set of cone pulleys; c. 1) Set the radius vector R(θ) on the vertical load side with a desired function including the lead e of the rotation angle θ, and for each section end of one step, assume a rotation angle α from the start of the lowest section of one step, and set the engagement point 92, engagement angle θel, and winding angle α with a tension transmission member that supports a vertical load at one end and is wound around the outer periphery of a set of cone pulleys, which represent the fluctuation of the three-dimensional positional relationship. W and determining the amount of winding SW from the start of the lowest section of the b.1 step of the tension transmission member using the following formula 3, correcting the rotation angle α until the actual vertical movement distance S based on the determined specifications matches the corresponding section end value in the skeleton data set 70, and after they match, determining the rotation angle α and the rotation torque radius RT, and further determining the rotation torque radius rT on the spring side using the rotation torque radius ratio P of the corresponding section end in the skeleton data set 70. c.2) A step of assuming the radius vector r(θ) on the spring side as a function including the lead e of the rotation angle θ, determining an engagement point 90 between a set of cone pulleys and a tension transmission member that transmits the tension of the spring at one end, an engagement angle θel, and a rotation torque radius rT, which represent the fluctuation of the three-dimensional positional relationship for each section of step b.1, correcting the function until the determined rotation torque radius rT coincides with the determined value in step c.1, and determining the function after the coincidence; d. 1) Set the radius vector r (θ) on the spring side in the desired function including the lead e of the rotation angle θ. Error! There is an error in the hyperlink reference. For each section end of b. 2 step, assume the rotation angle α from the start of the top section of b. 2 step, and use the engagement point 90 with the tension transmission member that wraps around the outer circumference of a set of cone pulleys and transmits the tension of the spring at one end, the engagement angle θel, the unwinding angle αS, and the following formula 4, which represent the fluctuation of the three-dimensional positional relationship, to obtain the unwinding amount s from the start of the top section of b. 2 step of the tension transmission member, and correct the rotation angle α until the actual spring elongation ξL based on the obtained specifications matches the corresponding section end value in the skeleton data set 70, and after matching, determine the rotation angle α and the rotation torque radius rT, and further determine the rotation torque radius RT on the vertical load side using the rotation torque radius ratio P of the corresponding section end in the skeleton data set 70; d.2) A step of assuming the radius vector R(θ) on the vertical load side as a function including the lead e of the rotation angle θ, and determining the engagement point 92, engagement angle θel, and rotation torque radius RT between a set of cone pulleys and a tension transmission member supporting the vertical load at one end at each section end in step b.2, which represent the fluctuation of the three-dimensional positional relationship, and correcting the assumed function until the rotation torque radius RT on the vertical load side coincides with the determined value in step d.1, and determining the function after the coincidence; e) At the end of each section, there is a step of machining the radius vectors based on the function formulas of the set radius vector R(θ) on the vertical load side in step c.1 and the determined radius vector r(θ) on the spring side in step c.2, or the set spring side radius vector r(θ) in step d.1 and the determined radius vector R(θ) on the vertical load side in step d.2, A method for manufacturing a set of cone pulleys, comprising steps a.a, b.1, c.1, c.2 and e, or comprising steps a, b.2, d.1, d.2 and e. [0030] [0045] [0070] [0080] [0089]

Images