JP7269102B2 - spring assembly - Google Patents

Description

The present invention relates to a spring assembly supporting a plurality of coil springs.

Conventionally, a spring assembly constructed by erecting a plurality of coil springs on an annular plate material is used as a spring for urging a piston incorporated in, for example, an automatic transmission (hereinafter also simply referred to as "AT") of an automobile. used.

For example, in Patent Document 1 below, at least one end is formed into an annular plate by forming a plurality of cut-and-raised holes on an annular plate and by caulking to widen cylindrical projections standing from the inner peripheral edge of each of the cut-and-raised holes. A spring assembly is described that includes a plurality of coil springs secured to a plate.

JP-A-10-311357

By the way, the spring assembly 120 described in Patent Document 1 is designed to be incorporated in, for example, an automatic transmission 100 (hereinafter also referred to as "AT100") of an automobile, as shown in FIG. This AT 100 has a case 101 and a shaft 102. A plurality of clutches 103, 104 are arranged on the inner circumference of the peripheral wall of the case 101, and a plurality of clutches 105, 106 are arranged on the outer circumference of the shaft 102. is provided. A pressing member 110 (piston) having a clutch pressing portion 111 is slidably arranged in the case 101, and hydraulic oil O is filled between the pressing member 110 and the case 101.

The spring assembly 120 described above is assembled inside the case 101 with the coil spring 125 slightly pressed by the pressing member 110 (the load at that time is referred to as the setting load). As shown in FIG. 7(a), the pressing member 110 is normally separated from the clutch 103 by the biasing force of the spring assembly 120. In this state, the plurality of clutches 103, 104, 105, 106 are far from each other.

Then, when a predetermined pressure is applied to the hydraulic oil O and the pressing member 110 is pressed against the biasing force of the spring assembly 120, as shown in FIG. 103 is pushed and the plurality of clutches 103 to 106 come into contact with each other, so torque is transmitted to the shaft 102 . At this time, the smaller the difference between the operating load of the spring assembly 120 (the load acting on the spring assembly 120 via the pressing member 110 pushed by the hydraulic pressure) and the setting load, the better. pressure is small.

By the way, it is known that in order to reduce the difference between the set load and the operating load of the spring assembly, it is necessary to lower the spring constant of the coil spring. In this case, it is conceivable to increase the free length of the coil spring, but this time the coil spring is likely to buckle.

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a spring assembly that can reduce the spring constant of the entire spring assembly while suppressing spring buckling.

In order to achieve the above object, the spring assembly of the present invention comprises a ring-shaped support member and a plurality of small-diameter springs arranged along the circumferential direction of the support member, one end of which is supported by the support member. and a wire diameter larger than the wire diameter of the small diameter spring, formed to have a diameter larger than the outer diameter of the small diameter spring, and having a free length longer than the free length of the small diameter spring, and one large-diameter spring supported by a support member, and the plurality of small-diameter springs are arranged on the inner diameter side or the outer diameter side of the large-diameter spring.

According to the spring assembly of the present invention, a plurality of small-diameter springs and a large-diameter spring having a wire diameter larger than that of the small-diameter spring and having a long free length are used in combination, so that a predetermined spring load can be obtained. It is possible to reduce the spring constant of the entire spring assembly while ensuring the same.

1 is an exploded perspective view showing a first embodiment of a spring assembly according to the invention; FIG. It is an assembly perspective view of the same spring assembly. FIG. 4 is a cross-sectional view of the same spring assembly in a free state in which no load is applied to the spring; FIG. 4 is a cross-sectional view of the spring assembly in a state in which it is set between a pair of members and a set load is applied. FIG. 5 is a cross-sectional view of the same spring assembly in a state where an operating load is applied from the state of FIG. 4 ; 4 is a graph showing the relationship between spring length and load in the same spring assembly. The same spring assembly or a conventional spring assembly is assembled in an automatic transmission, (a) is an explanatory diagram of the state in which a load is applied at the time of setting, and (b) is the state of (a). 1 is an explanatory diagram of a state in which an operating load is applied from . FIG. 5 is an exploded perspective view showing a second embodiment of a spring assembly according to the invention; It is an assembly perspective view of the same spring assembly. FIG. 4 is a cross-sectional view of the spring assembly in a state in which it is set between a pair of members and a set load is applied. FIG. 5 is an exploded perspective view showing a third embodiment of a spring assembly according to the invention; It is an assembly perspective view of the same spring assembly. FIG. 4 is a cross-sectional view of the spring assembly in a state in which it is set between a pair of members and a set load is applied. FIG. 11 is an exploded perspective view showing a fourth embodiment of a spring assembly according to the invention; It is an assembly perspective view of the same spring assembly. FIG. 4 is a cross-sectional view of the spring assembly in a state in which it is set between a pair of members and a set load is applied.

A first embodiment of a spring assembly according to the present invention will be described below with reference to FIGS.

As shown in FIGS. 1 to 3, the spring assembly 10 in this embodiment includes an annular support member 20, a plurality of support members 20 are arranged along the circumferential direction of the support member 20, and one end 31 of the support member It has a small-diameter spring 30 supported by 20 and one large-diameter spring 40 whose one end 41 is similarly supported by the support member 20 .

Further, as shown in FIG. 4, the spring assembly 10 in this embodiment is arranged between a pair of members 50 and 110, one member 50 having the supporting member 20 arranged thereon, and the other member 50 having the supporting member 20 arranged therebetween. The other end portions 33 of the plurality of small diameter springs 30 and the other end portions 43 of the large diameter springs 40 can abut against the member 110 (pressing member 110).

As shown in FIG. 7, the spring assembly 10 is incorporated in, for example, an AT 100 of an automobile to urge a pressure member 110 for hydraulic control, similarly to the spring assembly 120 of Patent Document 1 described above. It can be used as a spring for piston return for Note that the structure of the AT 100 has been described above and will be omitted. In addition, only one coil spring is shown in FIG. 7, but this is for the sake of convenience, and in this embodiment, it means a plurality of small-diameter springs 30 and one large-diameter spring 40. As shown in FIG.

This spring assembly may be used as a return spring for a clutch or a brake in addition to the piston return spring of the AT100, and the application location and installation location are not particularly limited.

One member 50 has a substantially annular plate shape, and a peripheral wall 51 is erected from the outer peripheral edge thereof (see FIG. 4). Also, the pressing member 110 that forms a piston can move toward and away from the one member 50 . Further, a circular hole 112 is formed in the center of the pressing member 110, and a spring pressing portion 113 protrudes from the peripheral edge of this circular hole 112. The outer peripheral edge of the spring pressing portion 113 on the proximal side Extends from the annular flange portion 115 . Although not shown, the pressing member 110 is provided with a clutch pressing portion 111 for pressing the clutch, as in FIG. The pressing member 110 shown in FIGS. 4 and 5 has a different shape from that shown in FIG. 7, but this is for convenience of illustration.

As shown in FIG. 4, the spring pressing portion 113 of the pressing member 110 can contact the other end portion 33 of the small-diameter spring 30 , and the flange portion 115 can contact the large-diameter spring 40 . It can contact the other end 43, and as shown in FIG. 5, biases the small diameter spring 30 and the large diameter spring 40 in the direction of compression. A support shaft 58 is inserted through the central portion of one member 50 and the circular hole 112 of the pressing member 110 .

Further, as shown in FIG. 3, the small-diameter spring 30 has a coil spring shape formed by winding a wire having a circular cross section with a predetermined wire diameter W1 at a predetermined pitch with a gap between the wires. ing. Each small-diameter spring 30 may be formed of a wire rod having a rectangular cross section, or may be formed in a tightly wound shape with no gaps between the wire rods.

On the other hand, the large-diameter spring 40 has a coil spring shape formed by winding a single wire having a circular cross section with a predetermined wire diameter W2 at a predetermined pitch with a gap between the wires. Further, as shown in FIG. 3, the wire diameter W2 of the wire material forming the large-diameter spring 40 is larger than the wire diameter W1 of the wire material forming the small-diameter spring 30, and the outer diameter D2 of the large-diameter spring 40 is It is formed to have a diameter larger than the outer diameter D<b>1 of the small diameter spring 30 .

Furthermore, as shown in FIG. 3, the other member (pressing member 110) is in a state in which it does not contact the plurality of small-diameter springs 30 and large-diameter springs 40, that is, in a state in which no load is applied to the springs. The free length L2 of the diameter spring 40 is formed longer than the free length L1 of each small diameter spring 30 in the same state. Further, as shown in FIG. 4, the length L2' of the large-diameter spring 40 when the pressing member 110 is in contact with the plurality of small-diameter springs 30 and the large-diameter springs 40 is equal to the length L2' of each small-diameter spring in the same state. It is formed longer than the length L1'.

The support member 20 is an annular plate material having circular inner and outer circumferences. The outer diameter of the support member 20 is approximately matched to the outer diameter D2 of the large-diameter spring 40. As shown in FIG. Therefore, when the large-diameter spring 40 is supported on the outer diameter side of the support member 20, the outer circumference of the large-diameter spring 40 does not protrude from the outer peripheral edge of the support member 20 (see FIG. 2). Further, the inner diameter of the support member 20 is large enough to support the plurality of small diameter springs 30 on the inner diameter side even when the large diameter springs 40 are supported on the outer diameter side.

A plurality of circular through-holes 21 are formed on the inner diameter side of the support member 20 at equal intervals in the circumferential direction. A first spring support portion 23 having an annular projection shape protrudes from the periphery of each through hole 21 of the support member 20 on the side of the spring support surface (the support surface of the small-diameter spring 30 and the large-diameter spring 40). It is

Then, as shown in FIG. 3 , each first spring support portion 23 is inserted into the inner circumference of one end portion 31 of each small diameter spring 30 , and one end portion 31 of each small diameter spring 30 is placed on the support surface of the support member 20 . While being supported, by crimping the tip of each first spring support portion 23 in a direction that spreads toward the small-diameter springs 30, the plurality of small-diameter springs 30 are retained in the support member 20. , are arranged along the circumferential direction on the inner diameter side of the support member 20 . The small-diameter springs 30 are erected so that their axial centers are perpendicular to the support surface of the support member 20 and parallel to each other (see FIG. 3).

A second spring support portion 27 is cut and raised through a notch portion 25 on the outer diameter side of the support member 20 . The second spring support portion 27 in this embodiment is formed by cutting and raising the notch portion 25 from the periphery of the support member 20 on the inner diameter side. A plurality of notch portions 25 are formed on the outer diameter side of the support member 20 and between the through holes 21 , 21 . As a result, the plurality of second spring support portions 27 are displaced from the plurality of first spring support portions 23 formed on the inner diameter side of the support member 20 so as not to overlap in the circumferential direction of the support member 20 . It is

2 and 3, one end portion 41 of the large-diameter spring 40 is brought into contact with and supported by the outer diameter side of the support member 20, and the distal end sides of the plurality of second spring support portions 27 are By bending toward the outer diameter side of the support member 20, the one end portion 41 of the large diameter spring 40 is pressed from the inner diameter side, and the large diameter spring 40 is bent toward the outer diameter side of the support member 20. 20 to prevent it from coming off. At this time, as described above, since the plurality of small-diameter springs 30 are arranged on the inner diameter side of the support member 20, the large-diameter spring 40 is arranged on the outer diameter side of the arrangement location of the plurality of small-diameter springs 30. (See FIGS. 2 and 3). In other words, the plurality of small-diameter springs 30 are arranged on the inner diameter side of the large-diameter spring 40 . One large-diameter spring 40 is erected so that its axis is perpendicular to the support surface of the support member 20 and parallel to the axes of the plurality of small-diameter springs 30. (see Figure 3).

Further, in the spring assembly 10 configured as described above, the states of the plurality of small-diameter springs 30 and the single large-diameter spring 40 change depending on the arrangement relationship with the pair of members 50 and 110 . That is, in the case shown in FIG. 3, the support member 20 is arranged on one member 50, and the pressing member 110, which is the other member, is in a state where the small diameter spring 30 and the large diameter spring 40 do not come into contact with each other. However, in this case, no load is applied to the small-diameter spring 30 and the large-diameter spring 40, and they extend in a free length.

On the other hand, in the case shown in FIG. 4, the spring assembly 10 is arranged between a pair of members 50 and 110, the supporting member 20 is arranged on one member 50, and the pressing member 110 is The small-diameter spring 30 and the large-diameter spring 40 are in contact with each other, and both the springs 30 and 40 are slightly pressed and contracted. In this state, the biasing force of both springs 30 and 40 of the spring assembly 10 is higher than the hydraulic pressure of the hydraulic fluid O. As shown in FIG. In this manner, the spring assembly 10 shown in FIG. 4 is set between the pair of members 50 and 110 and is in a state of being pushed by the pressing member 110, that is, the state shown in FIG. 7(a). This state is defined as a state in which the "set load" is applied.

Further, in the case shown in FIG. 5, a predetermined pressure is applied to the hydraulic oil O from the state shown in FIG. And the large-diameter spring 40 is further pressed and contracted. In this manner, the spring assembly 10 shown in FIG. 5 is further pushed through the pushed pressing member 110 against the biasing force of both the springs 30 and 40 by the predetermined hydraulic pressure of the hydraulic oil O. That is, the state shown in FIG. 7(b) is assumed to be the state in which the "operating load" is applied.

As described above, the plurality of small-diameter springs 30 in the spring assembly 10 of this embodiment are arranged on the inner diameter side of the large-diameter spring 40, but the plurality of small-diameter springs 30 are arranged on the outer diameter side of the large-diameter spring 40. (This will be explained later in third and fourth embodiments).

In this embodiment, the support member 20 is provided with the first spring support portions 23 having a plurality of annular projections and the second spring support portions 27 having a plurality of projections. The shape, number, position, and the like of the spring supporting portions are not particularly limited (for example, the first spring supporting portion may be shaped like a pair of claws, or shaped like three projecting pieces, etc.). However, the supporting member 20 is integrally formed with both a first spring supporting portion capable of supporting a plurality of small-diameter springs 30 and a second spring supporting portion capable of supporting a single large-diameter spring 40. It is preferable that Further, the support member 20 can be made of, for example, a metal material, but may also be made of a synthetic resin or the like.

Next, the effects of the spring assembly 10 having the above configuration will be described.

As described above, the spring assembly 10 of this embodiment is incorporated in, for example, an automobile AT 100. As shown in FIG. The small-diameter spring 30 and the large-diameter spring 40 are brought into contact with each other, and both springs 30 and 40 are set in a compressed state by being slightly pressed. Then, from the state shown in FIG. 4, a predetermined pressure is applied to the hydraulic oil O, and the pressing member 110 is pushed against the biasing force of the spring assembly 10 (the biasing force of the small-diameter spring 30 and the large-diameter spring 40). When pushed, as shown in FIG. 5, the large-diameter spring 40 is compressed and shrunk, and the plurality of small-diameter springs 30 are compressed and shrunk with their axial central portions slightly bulging like drums. As a result, as shown in FIG. 7B, the clutches 103 to 106 are in contact with each other, the case 101 and the shaft 102 are connected, and torque is transmitted to the shaft 102. As shown in FIG.

At this time, in the spring assembly 10, as shown in FIGS. 2 and 3, a plurality of small-diameter springs 30 are arranged along the circumferential direction of the support member 20, and the plurality of small-diameter springs 30 are combined into one large spring. It is arranged on the inner diameter side of the radial spring 40 . Thus, the plurality of small-diameter springs 30 and the wire diameter W2 larger than the wire diameter W1 of the small-diameter springs 30 are formed to have a larger diameter (outer diameter D2) than the outer diameter D1 of the small-diameter springs 30, and the small-diameter springs By using one large-diameter spring 40 having a free length L2 longer than the free length L1 of 30, the spring constant of the entire spring assembly 10 can be lowered while securing a predetermined spring load. .

That is, in order to reduce the spring constant while securing a predetermined spring load with only the small diameter spring 30, it is necessary to increase the free length L1 of the small diameter spring 30. In this case, however, the small diameter spring 30 will not buckle. easier. On the other hand, in this spring assembly 10, as described above, by using a plurality of small-diameter springs 30 and large-diameter springs 40 together, buckling occurs when a predetermined spring load is obtained by the small-diameter springs 30. Since the free length L2 of the large-diameter spring 40, which is difficult to bend, is increased, the buckling of the small-diameter spring 30 can be suppressed while reducing the spring constant of the spring assembly 10 as a whole.

To describe the above action in detail with reference to FIG. 6, FIG. 6 shows a graph showing the relationship between the spring length and the load (the load that can be received by the elastic repulsive force of the spring). The vertical line S1 in FIG. 6 indicates the spring length when the spring assembly 10 is set between the pair of members 50 and 110 (the state in FIG. 4), and the vertical line S2 in FIG. 5 shows spring lengths in a state where the small-diameter spring 30 and the large-diameter spring 40 are compressed by the pressing member 110 from the state (state shown in FIG. 5).

The example in FIG. 6 has the shape of the embodiment shown in FIGS. 1 to 5, and the comparative example in FIG. It has a shape without the spring 40 . The inclined straight line in FIG. 6 means the spring constant in the example and the comparative example (symbol B1 is the spring constant of the example, and symbol B2 is the spring constant of the comparative example). In addition, the smaller the difference between the load when the spring assembly is set (load when set: see S1) and the load when the spring assembly is actuated (load when actuated: see S2), the more the spring assembly absorbs the load. Good responsiveness when receiving is desirable (the spring assembly operates even if the applied load is small from the set load).

In the spring assembly 10 of this embodiment, by adopting the structure shown in FIGS. 1 to 5, as shown in FIG. 6, its spring constant B1 is set higher than the spring constant B2 of the spring assembly of the comparative example. It can be lowered and laid down (the angle of inclination can be reduced). As a result, the difference between the setting load and the operating load in the spring assembly 10 of the embodiment can be made smaller than the difference between the setting load and the operating load in the comparative example. Therefore, when the spring assembly 10 is used as a so-called return spring that urges the pressing member 110 incorporated in the AT 100 as described above, the spring assembly 10 can be returned to the position shown in FIG. Since the operation can be smoothly performed from the set state to the state shown in FIG. 5, there is no need to apply excessive hydraulic pressure, which contributes to improvement in fuel consumption.

In this embodiment, as shown in FIG. 3, the free length L2 of the large-diameter spring 40 when the other member (pressing member 110) does not contact the small-diameter spring 30 and the large-diameter spring 40 is Since it is formed longer than the free length L1 of the small-diameter spring 30, the spring constant of the entire spring assembly 10 can be made easier to lower.

Furthermore, as shown in FIG. 4, the length L2′ of the large-diameter spring 40 when the other member (pressing member 110) is in contact with the small-diameter spring 30 and the large-diameter spring 40 is equal to the length of the small-diameter spring 30. Since it is formed longer than the length L1′, it is possible to secure the distance between the pair of members 50 and 110 when the spring assembly 10 is arranged between the pair of members 50 and 110 (the pair of members 50 and 110). ), making it easier to compress the plurality of small-diameter springs 30 (if the length of the large-diameter spring 40 is shorter than that of the small-diameter spring 30, the wires of the large-diameter spring 40 contact each other, The member 110 on the other side cannot be pushed against the member 50 on the other side, and the small-diameter spring 30 does not generate a load).

In this embodiment, as shown in FIGS. 2 and 3, the plurality of small-diameter springs 30 are arranged on the inner diameter side of the large-diameter spring 40. Therefore, without changing the size of the support member 20, A large-diameter spring 40 having an outer diameter as large as possible can be used, and the spring constant of the entire spring assembly 10 can be further reduced.

8-10 show a second embodiment of the spring assembly according to the invention. In addition, the same code|symbol is attached|subjected to the substantially same part as said 1st Embodiment, and the description is abbreviate|omitted.

A spring assembly 10A according to the second embodiment has basically the same structure as the spring assembly 10 according to the first embodiment, but as shown in FIGS. 30 has a structure in which the other end 33 is supported by the contact member 60 .

As shown in FIG. 8, the contact member 60 has a substantially annular plate shape, and a number of through holes 61 matching the through holes 21 of the support member 20 are formed at equal intervals in the circumferential direction. A third spring support portion 63 projects from the inner peripheral edge thereof. The outer diameter of the contact member 60 is formed smaller than the inner diameter of the large diameter spring 40 so that the contact member 60 can be arranged inside the large diameter spring 40 . Then, as shown in FIG. 10, each of the third spring support portions 63 formed on the contact member 60 is inserted into the inner circumference of the other end portion 33 of the small diameter spring 30 and crimped to form a plurality of small diameter springs 30. A contact member 60 is fixed to the other end 33 of the to prevent it from coming off.

A spring pressing portion 113 provided in the pressing member 110 presses the contact member 60, thereby pressing the plurality of small-diameter springs 30. As shown in FIG. That is, the plurality of small-diameter springs 30 are indirectly biased by the pressing member 110 via the contact member 60 .

And also in this 2nd Embodiment, the effect similar to said 1st Embodiment can be obtained.

11-13 show a third embodiment of the spring assembly according to the invention. In addition, the same code|symbol is attached|subjected to the substantially same part as each said embodiment, and the description is abbreviate|omitted.

As shown in FIG. 12, in the spring assembly 10B of the third embodiment, the large-diameter spring 40 is arranged on the inner diameter side of the array of the plurality of small-diameter springs 30. In other words, the plurality of small-diameter springs 30 is arranged on the outer diameter side of the large diameter spring 40 .

As shown in FIG. 11, a support member 20B in this embodiment has a plurality of first spring support portions 23 protruding from the outer diameter side of the support member 20B via through holes 21 at equal intervals in the circumferential direction. In addition, a plurality of second spring support portions 27 are formed on the inner diameter side via notch portions 25 so as to be displaced in the circumferential direction with respect to the first spring support portion 23 . An annular spring pressing portion 113 is projected from the outer peripheral portion of the pressing member 110 , and this portion presses the other end portion 43 of the plurality of small-diameter springs 30 . portion presses the other end portion 43 of the large-diameter spring 40B. 12 and 13, one end portion 31 of each small diameter spring 30 is supported by each first spring support portion 23 on the outer diameter side of the support member 20B, and one large diameter spring 40B is supported. is supported on the inner diameter side of the support member 20B by the plurality of second spring support portions 27. As shown in FIG. The large-diameter spring 40B is formed to have a smaller outer diameter than those of the first and second embodiments, and does not protrude from the inner peripheral edge of the support member 20B while being supported by the support member 20B. It's like

And also in this 3rd Embodiment, the effect similar to said 1st, 2nd embodiment can be obtained.

14-16 show a fourth embodiment of the spring assembly according to the invention. In addition, the same code|symbol is attached|subjected to the substantially same part as each said embodiment, and the description is abbreviate|omitted.

A spring assembly 10C according to the fourth embodiment has basically the same structure as the spring assembly 10B according to the third embodiment, but as shown in FIGS. The other end 33 of 30 is structured to be supported by the contact member 60C.

The contact member 60C has a substantially annular plate shape, and a number of through holes 61 corresponding to the through holes 21 of the support member 20B are formed at equal intervals in the circumferential direction. , and a third spring support portion 63 are protruded. The inner diameter of the contact member 60C is formed to be larger than the outer diameter of the large diameter spring 40B so that the contact member 60C can be arranged outside the large diameter spring 40B. Then, as shown in FIG. 16, each of the third spring support portions 63 formed on the contact member 60C is inserted into the inner periphery of the other end portion 33 of the small-diameter spring 30 and crimped to form a plurality of small-diameter springs 30. The contact member 60C is fixed to the other end 33 of the .

Also, the spring pressing portion 113 provided in the pressing member 110 presses the contact member 60C, thereby pressing the plurality of small-diameter springs 30 . That is, the plurality of small-diameter springs 30 are indirectly biased by the pressing member 110 via the contact member 60C.

Also in this fourth embodiment, it is possible to obtain the same effects as those of the above-described first to third embodiments.

The present invention is not limited to the above-described embodiments, and various modified embodiments are possible within the scope of the present invention, and such embodiments are also included in the scope of the present invention. .

10, 10A, 10B, 10C Spring assembly 20, 20B Support member 30 Small diameter spring 31 One end 33 Other end 40 Large diameter spring 41 One end 43 Other end 50 Member (one member)
60, 60C contact member 110 pressing member (other member)

Claims (3)

an annular support member;
a plurality of small-diameter springs arranged along the circumferential direction of the support member and having one end supported by the support member;
It has a wire diameter larger than the wire diameter of the small-diameter spring, is formed to have a larger diameter than the outer diameter of the small-diameter spring, has a free length longer than the free length of the small-diameter spring, and has one end portion of the support member. has only one large diameter spring supported by
A spring assembly, wherein the plurality of small-diameter springs are arranged on the inner diameter side or the outer diameter side of the large-diameter spring. The spring assembly is arranged between a pair of members, one of which includes the support member, and the other member includes the plurality of small-diameter springs and the other end portion of the large-diameter spring. is allowed to abut,
a free length of the large-diameter spring in a state where the other member does not contact the small-diameter spring and the large-diameter spring is formed longer than a free length of the small-diameter spring,
2. The spring assembly according to claim 1, wherein the length of said large diameter spring in a state where said other member is in contact with said small diameter spring and said large diameter spring is formed longer than the length of said small diameter spring. . 3. The spring assembly according to claim 1, wherein the plurality of small-diameter springs are arranged on the inner diameter side of the large-diameter spring.

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