JP2001255238A - Spring force detecting method and device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To accurately estimate spring force with a spring and a functional part assembled to a structure and to ensure that the spring force in practical use is within a set range. SOLUTION: This spring force detecting device externally applies load to the spring 210 and the functional component 100 in the spring force operation direction with structural bodies 150 and 200 connected thereto, measures the load and displacement of the spring 210 and the functional component 100, calculates the spring constant of the spring 210 and the spring constant of the structural bodies 150 and 200 based on the load and the displacement, estimates the spring force of the spring 210 with the load set to 0 taking account of the displacement of the structural bodies 150 and 200 in the spring force operation direction with the load set to 0, and determines whether the estimated spring force is within the set range or not.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an assembly in which a spring and a functional component are sandwiched between at least two divided structural members, and the structural members are joined to apply the spring force of the spring to the functional component. The present invention relates to a three-dimensional spring force inspection method and apparatus.

[0002]

2. Description of the Related Art In the apparatus described in Japanese Patent No. 2697261, the characteristics (plate thickness, spring constant, etc.) of a disc spring are measured before assembly, and the thickness of the shim is selected based on the measurement result. Then, the set length of the coned disc spring after assembly is set to a predetermined length, thereby reducing the variation in the spring force acting on the functional component.

[0003]

However, in the above-mentioned conventional apparatus, when the disc spring and the functional component are assembled to the structure, the structure also receives a spring force, so that the structure slightly expands. Therefore, after assembling (that is, during actual use), the set length of the disc spring and, consequently, the spring force change by the extension of the structure, and the actual spring force during actual use is within the set range. It was unknown whether or not.

SUMMARY OF THE INVENTION The present invention has been made in view of the above points, and it is an object of the present invention to accurately estimate an actual spring force after assembling and to assure that the spring force in actual use is within a set range. With the goal.

[0005]

In order to achieve the above object, according to the first aspect of the present invention, a structure (150, 20) is provided.
0), a load (F) is externally applied to the spring (210) and the functional component (100) in the direction in which the spring force acts, and the load (F) and the spring (210).
And the displacement (S) of the functional component (100) are measured,
Based on the load (F) and the displacement (S), the spring (21)
0) and the spring constant of the structure (150, 200) are calculated, taking into account the amount of deformation of the structure (150, 200) in the direction of the spring force when the load (F) is set to 0. Then, the spring force of the spring (210) when the load (F) is set to 0 is estimated, and it is determined whether or not the estimated spring force is within a set range.

According to this, the spring force of each assembly in the actual use condition is accurately determined by taking into account the variation in the spring constant of the spring for each assembly and the spring constant of the structure and the amount of deformation of the structure. Can be estimated. Therefore, it is possible to guarantee that the spring force in the actual use state is within the set range for all the assemblies.

The amount of deformation of the structures (150, 200) and the spring force of the spring (210) when the load (F) is set to zero are determined by the load (F). The reaction force (Fh) of the structures (150, 200) when gradually increasing
(F) at which is zero is determined as the inflection point load (F0), the inflection point load (F0), the spring constant (ks) of the spring (210), and the structure (150, 200) It can be estimated based on the spring constant (kh).

According to the third aspect of the present invention, the structure (15)
(300) for externally applying a load (F) to the spring (210) and the functional component (100) in the direction in which the spring force acts, with the load (F)
Load measuring means (320) for measuring the pressure, and a spring (210)
And displacement amount measuring means (330) for measuring the displacement amount (S) of the functional component (100), the load (F) and the displacement amount (S)
, The spring constant of the spring (210) and the spring constant of the structure (150, 200) are calculated, and the load (F)
Structure in the direction of action of the spring force when
Taking into account the deformation amount of (0), the spring force of the spring (210) when the load (F) is set to 0 is estimated, and the spring force for determining whether or not the estimated spring force is within a set range. Judgment means (4
00).

According to this, the same effect as the first aspect of the invention can be obtained.

According to the fourth aspect of the present invention, the pump body (100) for pressurizing and discharging the fluid and the spring (210) are housed in the recess (150a) of the housing (150).
A method for testing a spring force of a pump in which a screw member (200) is screwed into an opening end side of a concave portion (150a) to compress a spring (210), wherein the screw member (200) is screwed. Then, the pump body (100) and the spring (21)
0), a load (F) is applied from the outside in the direction of action of the spring force, and the load (F) and the displacement (S) of the pump body (100) and the spring (210) are measured. And the displacement (S), the spring constant of the spring (210), the housing (150) and the screw member (2).
00) and calculate the load (F) to 0 by taking into account the deformation of the housing (150) and the screw member (200) in the direction of the spring force when the load (F) is set to 0. The spring force of the spring (210) at this time is estimated, and it is determined whether or not the estimated spring force is within a set range.

According to this, the variation of the spring constant of the spring for each pump, the variation of the spring constant of the housing and the screw member of each pump, and the amount of deformation of the housing and the screw member are taken into consideration. The spring force in the actual use state can be accurately estimated. Therefore, it is possible to guarantee that the spring force in the actual use state is within the set range for all the pumps.

Also, by guaranteeing the spring force in the actual use state, the axial force can be stabilized, and the axial force applied to the pump body can be minimized.

The reference numerals in parentheses of the above means indicate the correspondence with specific means described in the embodiments described later.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows the overall configuration of a pump body to which the present invention is applied, FIG. 2 shows the configuration of the pump section in the pump body (section AA in FIG. 1), and FIG. Is shown.

FIG. 1 shows a pump body (functional component) 100 as A
It shows a state in which it is mounted on a housing (structure) 150 of the BS actuator, and is mounted so that the vertical direction in the drawing is the vertical direction. Since the brake device is composed of two systems, a first piping system and a second piping system, the pump body 100 includes a rotary pump 10 for the first piping system.
And a rotary pump 13 for the second piping system. And these rotary pumps 10 and 13 are 1
Driven by the drive shaft 54, the brake fluid is increased in pressure and discharged to the first piping system and the second piping system, respectively.

The casing constituting the outer shape of the pump body 100 includes first, second, third, and fourth cylinders (side plates) 71a, 71b, 71c, 71d and cylindrical first and second central plates 73a, 73b.

The first cylinder 71a, the first center plate 73a, the second cylinder 71b, the third cylinder 71
c, the second center plate 73b and the fourth cylinder 71d are sequentially stacked, and the outer periphery of the overlapping portion is welded to form the pump body 100 having an integral structure. The pump body 100 having such an integrated structure is
It is inserted into a substantially cylindrical recess 150a formed in the ABS housing 150.

The entrance (open end) of the recess 150a
The ring-shaped male screw member (structure) 200 is screwed into the female screw groove 150b formed in the
Are fixed to the housing 150.

Further, between the tip of the pump body 100 in the insertion direction and the bottom of the recess 150a, two disc springs 2 are provided.
10 are arranged. And male screw member (structure)
The disc spring 210 is compressed and deformed by the screw tightening of 200,
Due to the spring force of the disc spring 210, the pump body 100
Axial force (force applied in the insertion direction of the pump body 100)
Is secured.

The case 211 disposed between the disc spring 210 and the bottom of the concave portion 150a is configured so that one end of the disc spring 210 is in contact with the case 211, and the first cylinder 71a of the pump body 100. The hollow circular plate 212 disposed between the disc spring 210 and the
0 is configured to be in contact with one end.

The tip of the drive shaft 54 is inserted into the hollow portion 212a of the plate 212. And the drive shaft 5
4, the ring-shaped stopper 21 fitted to the drive shaft 54 is located on the bottom side of the concave portion 150a with respect to the plate 212.
3 are provided. The diameter of the stopper 213 is larger than the diameter of the hollow portion 212a of the plate 212, so that even if the drive shaft 54 moves to the right side of the drawing, the stopper 213 contacts the plate 212 to restrict the movement. . A groove 214 provided in the circumferential direction is formed at the tip of the drive shaft 54.
A C-ring 215 is disposed in the inside 14. The C-ring 215 prevents the stopper 213 from coming off the tip of the drive shaft 54.

The first, second, third and fourth cylinders 7
1a, 71b, 71c, and 71d have first, second, third, and fourth center holes 72a, 72b, 72c, and 72d, respectively.
Are formed. The bearing 51 is provided on the inner periphery of the first center hole 72a formed in the first cylinder 71a, and the fourth center hole 72 formed in the fourth cylinder 71d is provided.
A bearing 52 is provided on the inner periphery of c. First to first
A drive shaft 54 is fitted in the fourth center holes 72a to 72d, and is supported by bearings 51 and 52. Thus, bearings 51 and 52 are arranged on both sides of rotary pumps 10 and 13.

Next, the structure of the rotary pumps 10 and 13 will be described with reference to FIGS. The rotary pump 10
It is arranged in a rotor chamber 50a formed by sandwiching both sides of a cylindrical first central plate 73a between a first cylinder 71a and a second cylinder 71b. Rotary pump 10
Is constituted by an internal gear pump driven by a drive shaft 54. The rotary pump 10 includes a rotating portion including an outer rotor 10a having an inner tooth portion formed on the inner circumference and an inner rotor 10b having an outer tooth portion formed on the outer circumference, and is driven in a hole of the inner rotor 10b. The configuration is such that the shaft 54 is inserted. Then, the key 54b is inserted into an elongated hole 54a having an axial direction formed on the drive shaft 54 and extending in the longitudinal direction.
The key 54b transmits torque to the inner rotor 10b.

Outer rotor 10a and inner rotor 1
In the case of Ob, a plurality of gaps 10c are formed by meshing the internal teeth and the external teeth formed respectively. The rotation of the drive shaft 54 changes the size of the gap 10c so that the brake fluid can be sucked and discharged.

The rotary pump 13 is disposed in a pump chamber 50b formed by sandwiching both sides of a second cylindrical central plate 73b between a third cylinder 71c and a fourth cylinder 71d. The rotary pump 13 is also a rotary pump 1
The rotary pump 10 is formed by rotating the rotary pump 10 by 180 ° about the drive shaft 54.

The first cylinder 71a has a rotary pump 10
, A suction port 60 communicating with the gap 10c on the suction side, and a discharge port 61 communicating with the gap 10c on the discharge side. The suction port 60 is formed so as to penetrate from the end face of the first cylinder 71a on the rotary pump 10 side to the end face on the opposite side, and is further drawn out from the end face on the opposite side to the outer peripheral face toward the top. The brake fluid is introduced with the outer peripheral surface side of the suction port 60 as an inlet.

The suction port 60 is connected to the housing 150
An annular groove 161 formed on the entire circumference of the inner peripheral surface of the concave portion 150a where the distal end position of the pump body 100 is disposed.
Through the suction pipe 1 formed in the housing 150
51.

The discharge port 61 is connected to the first cylinder 71a.
And the second cylinder 71b extends from the end face on the rotating part side of the rotary pump 10 to the outer peripheral face. This discharge port 61 is specifically configured as follows.

First cylinder 71a and second cylinder 71
b, an annular groove (first annular groove) formed so as to surround the drive shaft 54 on the end face on the rotating portion side of the rotary pump 10.
61a are provided.

A ring-shaped seal member 171 is provided in the annular groove 61a so as to sandwich the outer rotor 10a and the inner rotor 10b.
The seal member 171 is composed of a resin member 171a disposed on the rotating part side and a rubber member 171b pressing the resin member 171a on the rotating part side. The inner peripheral side of the seal member 171 includes a gap between the central plate 73a and the outer periphery of the outer rotor 10a opposed to the suction-side gap 10c and the suction-side gap 10c. The center plate 73a includes a gap 10c on the discharge side and a gap between the outer periphery of the outer rotor 10a facing the gap 10c on the discharge side and the center plate 73a. That is, the relatively low-pressure portion and the relatively high-pressure portion on the inner and outer circumferences of the seal member 171 are sealed by the seal member 171.

Further, the sealing member 171 is provided with an annular groove 61a.
Is configured so as to be in contact with the inner periphery and not the outer periphery. Therefore, the outer circumferential side of the annular groove 61a with respect to the seal member 171 is a gap. Further, a pipe line 61b is drawn from the uppermost position of the annular groove 61a to the first cylinder 71a in a ceiling direction. The discharge port 61 is formed by the gap of the annular groove 61a thus configured and the pipe line 61b.
Is configured.

The discharge port 61 is connected to the housing 150
Is connected to a discharge pipe 152 formed in the housing 150 via an annular groove 162 formed on the entire circumference of the inner peripheral surface of the concave portion facing the center plate 73a.

On the other hand, the fourth cylinder 71d has a suction port 62 communicating with the gap 10c on the suction side of the rotary pump 13,
And a discharge port 63 communicating with the discharge-side gap 10c. The suction port 62 is formed to penetrate the end face of the fourth cylinder 71d on the rotary pump 13 side and the outer peripheral face. Specifically, the suction port 62 is configured to extend in the horizontal direction from the gap 10c on the suction side and then be drawn out at least in the top direction. Also, the suction port 62
Is configured to communicate with a center hole 72c in which the drive shaft 54 is disposed. The brake fluid is introduced through the inlet 62 on the outer peripheral surface side of the fourth cylinder 71d. The suction port 62 is formed in the housing 150 through an annular groove 163 formed on the entire inner peripheral surface of the recess 150 a of the housing 150 so as to include the position of the inlet of the suction port 62. Road 15
3 is connected.

The discharge port 63 is formed so as to extend from the end face on the rotating part side of the rotary pump 13 of the third cylinder 71c and the fourth cylinder 71d to the outer peripheral face. The discharge port 63 has the same structure as the above-described discharge port 61, and has an annular groove 63a that accommodates a ring-shaped seal member 172 including a resin member 172a and a rubber member 172b.
And a conduit 63b drawn from the uppermost position of the annular groove 63a. This discharge port 63
Is connected to the discharge pipe 154 via an annular groove 164 formed on the entire inner peripheral surface of the recess 150a of the housing 150 facing the outer periphery of the central plate 73b.

The diameter of the second central hole 72b of the second cylinder 71b and the inner diameter of the third cylinder 71c are partially
The seal member 80 for shutting off the first rotary pump 10 and the second rotary pump 13 is accommodated in the portion having the larger diameter. This sealing member 8
Numeral 0 denotes a ring-shaped elastic member O-ring 81 fitted into a ring-shaped resin member 82 having a groove formed in the radial direction as a depth direction. The member 82 is pressed and comes into contact with the drive shaft 54.

The resin member 82 and the third cylinder 71
Both of the cross-sectional shapes of the inner circumference of c are arc-shaped with a partially cutout circular shape, and are configured so that the resin member 82 is fitted into the inner circumference of the third cylinder 71c.
For this reason, the cutout portion of the resin member 82 functions as a key, and the seal member 80 is configured to be unable to rotate relative to the third cylinder 71c.

The fourth cylinder 71d is concave on the surface opposite to the surface to be welded to the second central plate 73a,
The drive shaft 54 projects from this recess.
The drive shaft 54 has a connection portion 54c that is partially recessed at the protruding end, and the drive shaft 11a of the motor 11 is inserted into the connection portion 54c.
Then, one drive shaft 54 is rotated by the motor 11 via the drive shaft 11a, and the rotary pumps 10 and 13 are driven. Also, the fourth cylinder 71
The diameter of the entrance of the recessed part of d is equal to the hole formed in the holder of the motor 11, and the fourth cylinder 71d
The bearing 180 is disposed by reducing the gap between the recessed portion of the motor 11 and the hole of the holder 11b of the motor 11, and the drive shaft 1
1a is pivotally supported.

In the recess formed in the fourth cylinder 71d, an oil seal 90 and an oil seal 91 are arranged and fitted in the axial direction of the drive shaft 54 so as to cover the outer periphery of the drive shaft 54. . Further, O-rings 74a, 74b, 74c and 74d are arranged on the outer peripheral surfaces of the first, second and fourth cylinders 71a, 71b and 71d.

The front end of the recessed portion of the fourth cylinder 71d on the inlet side is reduced in diameter to form a stepped portion. The above-mentioned ring-shaped male screw member 200 is fitted in the reduced diameter portion, and the pump body 100 is fixed.

Next, the pump body 1 constructed as described above will be described.
The operation of 00 will be briefly described. The brake device is
At the time of the ABS control in which the wheels tend to lock, or when a large braking force is required, for example, when a braking force corresponding to the brake depression force cannot be obtained, or when the operation amount of the brake pedal 1 is large, the pump body 100 is moved. It drives and sucks and discharges brake fluid in the reservoir. Then, the pressure of the wheel cylinder is increased by the discharged brake fluid.

At this time, in the pump body 100, the rotary pumps 10 and 13 suck the brake fluid through the suction pipes 151 and 153 and discharge the brake fluid through the discharge pipes 152 and 154. Perform pump operation.

At this time, in the rotary pump, the pressure on the discharge side becomes extremely large. Therefore, brake fluid pressure acts in a direction in which the pump main body 100 comes out of the housing 150. However, as described above, the axial force of the pump main body 100 is secured by the disc spring 210 and the male screw member 200. 100 can be prevented from falling out of the housing 150.

Next, a spring force inspection method after assembling the pump body will be described with reference to FIGS. In this spring force test, the disc spring 210 and the pump body 100 are connected to the housing 15.
This is carried out in an assembly in which the male screw member 200 is housed in the housing 0 and screwed and fixed. This assembly is in a state before the motor 11 (including the drive shaft 11a and the holder 11b) and the bearing 180 are assembled to the housing 150 in FIG.

In FIG. 3, a hydraulically driven piston 310
Press device 300 having the piston 310 abuts on the end of the pump body 100 (the end on the side of the male screw member 200), and the spring force acting direction of the disc spring 210 against the disc spring 210 and the pump body 100. Externally acting as a load means. The press device 300 includes a disc spring 210 and a pump body 100.
Load meter (load measuring means) that measures the load applied to
320, and a stroke sensor (displacement amount measuring means) 330 that measures the position of the end of the pump body 100 by detecting the stroke position of the piston 310.

The control device 400 outputs a command for controlling the hydraulic pressure of the press device 300 to the press device 300, and performs calculations and determinations to be described later based on signals from the load meter 320 and the stroke sensor 330. It functions as load control means and spring force determination means.

In FIG. 3, F is a press load for pressing the pump body 100 by the press device 300, and Fs is a disc spring 2
The spring force Fh generated at 10 is a housing reaction force generated at the housing 150 and the male screw member 200.

By the way, the housing 150 and the male screw member 200, particularly the threaded portion of the male screw member 200, are elongated in accordance with the housing reaction force Fh. Therefore, the set length of the disc spring 210 and the spring force F are equivalent to the extension.
s changes.

Therefore, in the present embodiment, the spring force of the disc spring 210 in the actual use state is determined by the method described below, taking into account the effects of the extension of the housing 150 and the male screw member 200 for each assembly. That is, the set load Fset is estimated, and it is determined whether the estimated set load Fset is within the set range.

Calculation of Belleville Spring Constant ks and Housing Spring Constant kh First, the pressing device 300 presses the pump body 100. At this time, the press load F is set slightly higher than the target value of the set load Fset. Under this pressurized state, the male screw member 200 is tightened to a position where the male screw member 200 contacts the pump body 100.

Next, while increasing the press load F,
The changes in the press load F and the end position of the pump body 100 are measured. From the measurement results of the press load F and the end position change amount (stroke) S of the pump body 100 at this time, a characteristic diagram as shown in FIG. 4 is obtained, and the spring constant of the disc spring 210 (hereinafter, referred to as the disc spring constant). ks and housing 150
The controller 400 calculates a spring constant (hereinafter referred to as a housing spring constant) kh of the male screw member 200.

In FIG. 4, F0 is the press load (hereinafter, referred to as “following”) when the press load F is increased and the reaction force Fh of the housing becomes 0 (ie, when the pump body 100 and the male screw member 200 are separated). F0 is called the inflection point load), and S0 is the pressing load F from 0 to the inflection point load F
This corresponds to the amount of deformation of the housing 150 and the male screw member 200 when changed to zero.

Therefore, when the stroke S is between 0 and S0, both the spring force Fs and the housing reaction force Fh change, so that the characteristic line in FIG. 4 has a slope corresponding to the disc spring constant ks and the housing spring constant kh. become. Further, when the stroke S exceeds S0, the housing reaction force Fh remains 0, and the inclination corresponds to only the disc spring constant ks. Therefore, the disc spring constant ks can be obtained from the relationship between the press load F and the stroke S in a range where the stroke S exceeds S0. When the disc spring constant ks is obtained, the housing spring constant kh can be obtained from the relationship between the press load F and the stroke S when the stroke S is between 0 and S0.

Estimation and Determination of Set Load Fset Next, the pump body 100 is pressed again by the press device 300 with a constant press load. The set press load F 'at this time is the set load Fs of the disc spring 210 in the actual use state.
Set to a value expected when et falls within the setting range.

Next, in a state where the set press load F ′ is applied, the male screw member 2 is observed while observing a change in the press load F.
Tighten 00. As soon as the press load F starts to decrease (that is, the male screw member 200 is
00), the fastening of the male screw member 200 is stopped. At this time, the housing reaction force Fh can be regarded as substantially zero, and therefore, it can be considered that the set press load F ′ = the inflection point load F0.

Next, the pressurization of the pump body 100 by the press device 300 is stopped, that is, the press load F is set to zero.

Next, the disc spring constant k calculated above is calculated.
s and the housing spring constant kh, and based on the set press load F ′ (= inflection point load F0)
The set load Fset of the disc spring 210 in the actual use state is calculated, and further, it is determined whether or not the calculated set load Fset is within a set range.

FIG. 5 shows the relationship between the spring force Fs and the housing reaction force Fh, and the stroke S of the end of the pump body 100. The inflection point load F is applied to the pump body 100.
In a state where 0 is applied, the housing reaction force Fh is 0, and the extension of the housing 150 and the male screw member 200 is also 0. Therefore, the spring force Fs = the inflection point load F0
It is.

Then, as the press load F is reduced, the housing reaction force Fh increases, and the housing 15
The 0 and the male screw member 200 elongate according to the housing reaction force Fh. Further, since the set length of the disc spring 210 is increased by the extension of the housing 150 and the male screw member 200, the spring force Fs decreases as the press load F decreases. Then, when the press load F is set to 0, the point where the spring force Fs = the housing reaction force Fh, that is, the load Fset at the point where both the characteristic lines of the spring force Fs and the housing reaction force Fh in FIG.
The set load Fset of the disc spring 210 in the actual use state is obtained.

Therefore, based on the relationship shown in FIG. 5, the set load F of the disc spring 210 in the actual use state is determined based on the disc spring spring constant ks, the housing spring constant kh, and the inflection point load F0.
set can be determined.

As described above, according to the present embodiment, the disc spring spring constant ks and the housing spring constant kh for each assembly are determined, and the disc spring 210 in the actual use state for each assembly.
In order to estimate the set load Fset of each assembly, in consideration of the variation of the disc spring spring constant ks and the housing spring constant kh of each assembly and the extension of the housing 150 and the male screw member 200, the actual use condition of each assembly is considered. Disc spring 21
The set load Fset of 0 can be accurately estimated. Therefore, it is possible to guarantee that the set load Fset of the disc spring 210 in the actual use state is within the set range for all the assemblies.

Although the axial force of the pump body 100 is ensured by the spring force of the disc spring 210, according to the present embodiment, the set load Fset of the disc spring 210 in the actual use state is guaranteed. By stabilizing the axial force,
The axial force applied to the pump body 100 can be minimized.

(Other Embodiments) In the above embodiment, the disc spring 210 is disposed between the tip of the pump body 100 in the insertion direction and the bottom of the concave portion of the housing 150. A coned disc spring 210 may be arranged between the male screw member 200 and the male screw member 200.

Even with such a configuration, the male screw member 200
The force acting when the screw is tightened is balanced by the disc spring 210, and the male screw member 20 is secured while maintaining a desired axial force.
The pump main body 100 can be reliably fixed to the housing 150 by the screw tightening of 0. And also in such a configuration, by the method described above,
It is possible to accurately estimate the set load Fset of the disc spring 210 in the actual use state for each assembly. Therefore, it is possible to guarantee the set load Fset of the disc spring 210 in the actual use state for all the assemblies. it can.

[Brief description of the drawings]

FIG. 1 shows a pump body 100 according to an embodiment of the present invention.
FIG. 3 is a diagram showing a cross-sectional configuration in the vicinity of FIG.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a view showing an apparatus for testing a spring force of the pump body 100 of FIG. 1;

FIG. 4 is a characteristic diagram used to explain the operation of the device of FIG. 3;

FIG. 5 is a characteristic diagram used to explain the operation of the device of FIG. 3;

[Explanation of symbols]

100: pump body (functional parts), 150: housing (structure), 200: male screw member (structure), 210:
Spring.

Claims (6)

[Claims] A structure (1) divided into at least two parts
A spring (210) and a functional component (100) are sandwiched between the structural members (150, 200).
A spring force test method for an assembly, wherein the spring force of the spring (210) is applied to the functional component (100), wherein the structural bodies (150, 200) are combined, A load (F) is externally applied to the spring (210) and the functional component (100) in a spring force acting direction, and displacement of the load (F) and the spring (210) and the functional component (100) is performed. The amount (S) is measured, and a spring constant (ks) of the spring (210) and the structure (1) are determined based on the load (F) and the displacement (S).
50, 200), and taking into account the amount of deformation of the structure (150, 200) in the direction of the spring force when the load (F) is set to 0, the load (F) is calculated. A spring force inspection method comprising: estimating a spring force of the spring (210) when F) is set to 0; and determining whether the estimated spring force is within a set range. 2. The load (F) when the reaction force (Fh) of the structure (150, 200) becomes 0 when the load (F) is gradually increased is determined as an inflection point load (F0). The structure (150, 2) when the load (F) is set to 0
00) and the spring force of the spring (210)
The estimation is performed based on the inflection point load (F0), a spring constant (ks) of the spring (210), and a spring constant (kh) of the structure (150, 200). 2. The spring force inspection method according to 1. 3. A structure (1) divided into at least two parts.
A spring (210) and a functional component (100) are sandwiched between the structural members (150, 200).
A spring force testing device for an assembly, wherein the spring force of the spring (210) is applied to the functional component (100), wherein the structures (150, 200) are combined, Load means (300) for externally applying a load (F) to the spring (210) and the functional component (100) in the direction of action of the spring force; load measurement means (320) for measuring the load (F); A displacement amount measuring unit (330) for measuring a displacement amount (S) of the spring (210) and the functional component (100); and the spring based on the load (F) and the displacement amount (S). (210) and the structure (1)
50, 200), and taking into account the amount of deformation of the structure (150, 200) in the direction in which the spring force acts when the load (F) is set to 0, the load (F) is calculated. A spring force determining means (400) for estimating a spring force of the spring (210) when F) is set to 0 and determining whether or not the estimated spring force is within a set range. Spring force inspection device. 4. A housing (150) comprising a pump body (100) for discharging a fluid at a high pressure and a spring (210).
And a screw member (200) is screwed into an opening end of the concave portion (150a) to compress the spring (210). In a state where the screw member (200) is screwed, a load (F) is externally applied to the pump body (100) and the spring (210) in a direction in which a spring force acts, and the pump body (100) and the spring (210) are combined with the load (F). A displacement (S) of the pump body (100) and the spring (210) is measured, and a spring constant (ks) of the spring (210) is determined based on the load (F) and the displacement (S). ) And the spring constant (kh) of the housing (150) and the screw member (200), and the housing (150) and the screw in the spring force acting direction when the load (F) is set to 0. Member (200) Taking into account the amount of deformation, the spring force of the spring (210) when the load (F) is set to 0 is estimated, and it is determined whether or not the estimated spring force is within a set range. Spring force inspection method. 5. The pump body (100) includes an inner rotor (10b) having outer teeth formed on an outer periphery and an outer rotor (10a) having inner teeth formed on an inner periphery. A rotating part formed by forming a plurality of gaps (10c) by meshing a part with the external tooth part, a suction port (60, 62) for sucking a fluid into the rotating part, A rotary pump (10, 13) having a discharge port (61, 63) for discharging a fluid, wherein the inner rotor (10b) is driven by a drive shaft (54); The spring force inspection method according to claim 4, wherein: 6. The method or apparatus according to claim 1, wherein the spring is a disc spring (210).