WO2018163701A1 - クッションピン - Google Patents

クッションピン Download PDF

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Publication number
WO2018163701A1
WO2018163701A1 PCT/JP2018/004336 JP2018004336W WO2018163701A1 WO 2018163701 A1 WO2018163701 A1 WO 2018163701A1 JP 2018004336 W JP2018004336 W JP 2018004336W WO 2018163701 A1 WO2018163701 A1 WO 2018163701A1
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WO
WIPO (PCT)
Prior art keywords
spring
main body
sleeve
springs
cushion pin
Prior art date
Application number
PCT/JP2018/004336
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English (en)
French (fr)
Japanese (ja)
Inventor
裕児 松元
Original Assignee
本田技研工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 本田技研工業株式会社 filed Critical 本田技研工業株式会社
Priority to JP2019504404A priority Critical patent/JP6739620B2/ja
Priority to CN201880016020.4A priority patent/CN110382219B/zh
Publication of WO2018163701A1 publication Critical patent/WO2018163701A1/ja

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/02—Die-cushions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/02—Dies; Inserts therefor; Mounting thereof; Moulds

Definitions

  • the present invention relates to a cushion pin used in a press molding apparatus that performs press molding on a workpiece.
  • Patent Literature 1 and Patent Literature 2 disclose techniques relating to a pressure control technique in this type of press molding.
  • Patent Document 1 is a die cushion of a press molding apparatus, which is composed of a plunger portion protruding from one opening of a cylindrical case by an elastic member, and the elastic member is formed by superposing a plurality of (disc) springs of the same type. The thing is described.
  • Patent Document 2 describes a method in which pressure control of a press is performed in a wide range from low pressure to high pressure, and a plurality of springs having different spring constants are connected in series via an intermediate body (sleeve). .
  • Patent Literature 1 and Patent Literature 2 an elastic member such as a spring is arranged inside the cushion pin so that a plurality (tens of) cushion pins abut against the blank holder before molding is started, and the cushion pin is blank.
  • a method for preventing the occurrence of a state in which the holder does not contact the holder is employed.
  • a wide range of stroke widths can be secured by using a plurality of different springs.
  • it is difficult to appropriately manage loads including load characteristics due to manufacturing variations of each spring, and strong springs. could not be initialized.
  • An object of the present invention is to provide a configuration capable of ensuring a large stroke width by a plurality of springs and appropriately managing load characteristics resulting from manufacturing errors of the spring in a cushion pin used in a press molding apparatus.
  • the present invention is a cushion pin (for example, a cushion pin 20 described later) that supports a blank holder (for example, a blank holder 12 described later) of a press molding apparatus (for example, a press molding apparatus 1 described later), and has a cylindrical shape.
  • a main body for example, a main body 21 described later
  • a bottom member for example, a bottom cap 22 described later
  • a lid member for example, a cap screw 30 described later
  • a piston member for example, a piston member 26 described later held on the main body by the lid member, and a load received via the piston member in stages.
  • a plurality of springs (for example, a first spring 51, a second spring 52, a first spring 251, a second spring 252, and a third spring 253 described later) arranged in series inside the main body so as to be received by
  • the plurality of springs is directed cushion pins which at least part of the respective spring is held in the main body portion so as to overlap the timing for receiving a load.
  • load characteristics due to manufacturing variations of each spring are added to the structure of the cushion pin, so that the load of each spring can be taken over seamlessly. Accordingly, even when a long stroke is required, a necessary load can be appropriately distributed by a plurality of springs, so that a cushion pin having excellent durability as compared with the case of using a single spring can be provided.
  • the cushion pin is disposed on the inner side of the main body, and is capable of pressing a bottom side spring (for example, a second spring 52 and a third spring 253 described later) located on the bottom member side among the plurality of springs.
  • a cylindrical member for example, a first sleeve 41, a first sleeve 241 and a second sleeve 242 to be described later
  • a second cylindrical member for example, a later-described first spring
  • a lid-side spring for example, a first spring 51, a first spring 251 and a second spring 252 described later
  • the lid member is The state assembled to the main body
  • the maximum contraction value of the cover-side spring can be accurately adjusted by the length of the second cylindrical member in the axial direction, and the cover member and the piston can also be adjusted for the minimum contraction value of the cover-side spring and the bottom-side spring. Since it can set with a member, the timing which takes over a load among several springs can be controlled correctly.
  • a weak spring for example, a small-diameter spring
  • the diameter of the entire cushion pin can be reduced, and the degree of freedom in layout can be improved.
  • the plurality of springs are preferably constituted by springs having different load characteristics, not the same type of spring. As a result, it is possible to more precisely design the range responsible for the load according to the device configuration and layout, and it is possible to further improve the durability according to the device configuration.
  • the cushion pin used in the press molding apparatus of the present invention it is possible to ensure a large stroke width with a plurality of springs and appropriately manage load characteristics resulting from manufacturing errors of the springs.
  • FIG. 1 is a diagram schematically showing a press molding apparatus 1 to which a cushion pin 20 according to an embodiment of the present invention is applied. First, the overall configuration of the press molding apparatus 1 will be described.
  • a press molding apparatus 1 shown in FIG. 1 includes an upper mold 2 fixed to a ram 11, a lower mold 3 fixed to a bolster 13, a die cushion device 14 disposed below the lower mold 3, and a lower mold 3.
  • a plurality of (several dozen) blank holders 12 configured to surround the outer periphery of the die cushion device 14 via the plate 15 and a plurality of cushion pins for transmitting the die cushion load from below to the blank holder 12 20.
  • the die cushion device 14 is configured by a hydraulic cylinder, and is configured to be able to move the blank holder 12 to a clamping position where the workpiece W is clamped via a plurality of cushion pins 20.
  • the ram 11 to which the upper mold 2 is fixed is configured to be movable in the vertical direction with respect to the lower mold 3 by a link device and a gib (both not shown).
  • the molded portion of the upper mold 2 and the molded portion of the lower mold 3 are subjected to press molding on the processed portion of the workpiece W. .
  • FIG. 2A is a diagram showing an internal structure of the cushion pin 20 of the present embodiment.
  • FIG. 2B is a diagram showing an internal structure of the cushion pin 20 in a state where the first spring 51 is elastically deformed together with the second spring 52 under the load of the present embodiment.
  • the term “axial direction” simply means the longitudinal direction of the cushion pin 20, and in this embodiment, the direction is parallel to the vertical direction.
  • the cushion pin 20 includes a main body 21, a first spring 51, a second spring 52, a bottom cap 22, an annular member 23, a first sleeve 41, and a second sleeve 42.
  • the rod 25, the piston member 26, and the cap screw 30 are provided.
  • the main body 21 is formed in a cylindrical shape whose inside is hollow.
  • a thread groove (not shown) for screwing the cap screw 30 is formed on the inner surface of the upper portion of the main body 21. Further, a screw groove (not shown) is also formed on the inner side surface of the lower portion of the main body portion 21 so that the bottom cap 22 can be screwed.
  • the bottom cap 22 is a member that is disposed at the lower end of the main body 21 and serves as the bottom of the main body 21.
  • the bottom cap 22 is disposed on the upper surface of the plate 15 positioned above the die cushion device 14, and the cushion pin 20 functions in a state where the upper surface of the plate 15 and the lower surface of the bottom cap 22 are in contact with each other.
  • An accommodation hole 45 for accommodating the lower end of the rod 25 is formed on the upper surface of the bottom cap 22.
  • a second spring 52 is disposed above the bottom cap 22.
  • the second spring 52 is arranged so that one end of the second spring 52 contacts the bottom cap 22 inside the main body 21.
  • the second spring 52 of the present embodiment is configured by arranging a plurality of disc springs 57 in series, and the disc spring 57 located at the lower end thereof is in contact with the upper surface of the bottom cap 22.
  • the disc spring 57 is formed with a through hole 58 through which the rod 25 is inserted.
  • the annular member 23 is disposed so as to contact the upper end of the second spring 52 inside the main body 21.
  • the annular member 23 is movable in the axial direction with respect to the main body portion 21.
  • a rod 25 is inserted into the through hole 24 inside the annular member 23.
  • the first sleeve 41 is a cylindrical member arranged above the annular member 23 inside the main body 21.
  • the first sleeve 41 is configured to be slidable in the axial direction with respect to the main body portion 21, and a lower end thereof is in contact with an upper surface of the annular member 23.
  • the second sleeve 42 is a cylindrical member disposed inside the first sleeve 41.
  • the second sleeve 42 is configured to be slidable in the axial direction with respect to the first sleeve 41, and the lower end thereof is in contact with the upper surface of the annular member 23.
  • the first spring 51 has a layout that is arranged in series on the same axis as the second spring 52 with the annular member 23 interposed therebetween.
  • the first spring 51 is in contact with the annular member 23 at one end on the inner side of the second sleeve 42.
  • the first spring 51 of the present embodiment is configured by arranging a plurality of disc springs 55 in series, and the disc spring 55 located at the lower end thereof is in contact with the upper surface of the annular member 23. Further, the disc spring 55 is formed with a through hole 56 through which the rod 25 is inserted.
  • the limit of the amount of contraction of the first spring 51 is configured to substantially match the length of the second sleeve 42. In terms of size (diameter), the relationship is disc spring 55 ⁇ disc spring 57.
  • the rod 25 is disposed along the central axis inside the main body 21 in a state of penetrating the second spring 52, the annular member 23 and the first spring 51.
  • the piston member 26 is slidable inside the first sleeve 41 and is disposed above the second sleeve 42.
  • the piston member 26 includes a large-diameter portion 27 located on the lower side and a small-diameter portion 28 located on the upper side.
  • the outer diameter of the large-diameter portion 27 of the piston member 26 is substantially the same as the outer diameter of the upper end of the second sleeve 42, so that the downward pressing of the second sleeve 42 by the piston member 26 is possible. As shown in FIG. 2A, a gap is formed between the lower surface 27a of the piston member 26 (large diameter portion 27) and the upper end surface 42a of the second sleeve 42.
  • An accommodation hole 29 for accommodating the upper end of the rod 25 is formed on the lower surface 27a of the piston member 26 (large diameter portion 27).
  • the small diameter portion 28 of the piston member 26 is formed in a columnar shape with a diameter smaller than that of the large diameter portion 27, and protrudes upward from the upper surface of the large diameter portion 27.
  • the cap screw 30 is a lid member disposed at the upper end of the main body 21.
  • the cap screw 30 includes a screw portion 31 that is screwed into a screw groove inside the upper portion of the main body portion 21, and a flange portion 32 that is formed in a flange shape on the upper portion of the screw portion 31.
  • the cap screw 30 is fixed to the main body portion 21 by screwing the screw portion 31 into the main body portion 21. When the flange portion 32 comes into contact with the main body portion 21, further tightening of the screw portion 31 is restricted.
  • an insertion hole 35 into which the small diameter portion 28 of the piston member 26 is inserted is formed in the center.
  • the piston member 26 has a large-diameter portion 27 biased by the first spring 51 and protrudes from the main body portion 21 through the insertion hole 35.
  • the lower surface 31 a of the cap screw 30 is capable of contacting the upper end surface 41 a of the first sleeve 41 while being in contact with the upper surface of the large diameter portion 27 of the piston member 26.
  • FIG. 2B is a diagram illustrating an internal structure of the cushion pin 20 in a state where the second spring 52 is elastically deformed together with the first spring 51 under the load of the present embodiment.
  • the first spring 51 that contacts the lower surface 27a of the piston member 26 starts to contract.
  • a gap is formed between the lower surface of the piston member 26 and the upper end surface 42 a of the second sleeve 42, and the initial load of the second spring 52 is set higher than that of the first spring 51.
  • the piston member 26 starts to be lowered, only the first spring 51 is contracted.
  • the annular member 23 is biased by the initial load of the second spring 52 in addition to the weight of the second sleeve 42.
  • the second sleeve 42 starts to move downward.
  • the pressing force of the second sleeve 42 is transmitted to the annular member 23, and the pressing force of the second sleeve 42 is also transmitted to the second spring 52.
  • the first spring 51 can continue to contract in the axial direction until the upper surface of the piston member 26 coincides with the upper surface of the flange portion 32 of the cap screw 30. Further, after the piston member 26 comes into contact with the second sleeve 42, the first spring 51 is not further contracted.
  • the shape and spring constant of each member are set so that the second spring 52 starts to contract before the first spring 51 that receives the load from the piston member 26 (blank holder 12) reaches its maximum value.
  • FIG. 3 is a graph showing an example of the relationship between the stroke of the cushion pin 20 and the generated load.
  • the first spring 51 is indicated by a broken line
  • the minimum contraction value of the first spring 51 corresponds to the starting end part of the broken line
  • the maximum contraction value corresponds to the terminal end part of the broken line.
  • the second spring 52 is indicated by a two-dot chain line
  • the minimum contraction value of the second spring 52 corresponds to the start end part of the two-dot chain line
  • the maximum contraction value corresponds to the end part of the two-dot chain line.
  • the load received by the cushion pin 20 is initially generated only in the first spring 51, and the load is also generated in the second spring 52 when the generated load exceeds a predetermined range.
  • the spring constants set for the first spring 51 and the second spring 52 are set values, respectively, and the load reception by the second spring 52 is smoothly shifted.
  • the minimum contraction value and the maximum contraction value are both contraction amounts with respect to the natural length of the spring.
  • FIG. 4 is a graph showing an example when a step is generated due to variations in the first spring 51 and the second spring 52 in the relationship between the stroke of the cushion pin 20 and the generated load.
  • the pressure by the die cushion device 14 is basically constant, and when the work W is sandwiched between the upper die 2 and the blank holder 12 in the initial stage of press molding, the cushion pin 20 is stroked by a certain amount according to the die cushion pressure. To do. At this time, the stroke amount of each cushion pin 20 differs due to the influence of wear / deflection or the like.
  • FIG. 5 is a graph showing the relationship between the stroke and the generated load of each of the first spring 51 and the second spring 52 in consideration of variation.
  • the start end portion of the solid line having a different slope corresponds to the contraction minimum value, and the end portion corresponds to the contraction maximum value.
  • the spring characteristics of the first spring 51 and the second spring 52 are set so that the point at which the load is applied to the second spring 52 overlaps the point at which the first spring 51 receives the load.
  • the lower region of the generated load is ⁇ 10% based on the variation width of a general spring
  • the upper region of the generated load is ⁇ 5% as a manufacturing error
  • the first spring 51 and the second spring 52 are The spring constant, the structure of the cushion pin 20 and the like were adjusted so that the ranges handled were overlapped.
  • FIG. 6 is a graph showing the relationship between the stroke and the generated load of the cushion pin 20 of the present embodiment in which the first spring 51 and the second spring 52 are incorporated in consideration of variations.
  • the alternate long and short dash line indicates a range in which the load is received by both the first spring 51 and the second spring 52.
  • the first spring 51 and the second spring 52 have variations, the variations are absorbed, and the occurrence of a step as shown in FIG. 4 can be reliably prevented.
  • the first sleeve 41, the second sleeve 42, the first spring 51 and the second spring 52, the piston member 26, and the cushion pin considering the manufacturing error by designing the axial length and shape of the cap screw 30. 20 was achieved.
  • FIG. 7A is a diagram showing an internal structure of the cushion pin 20 before the cap screw 30 is attached.
  • the second spring 52, the annular member 23, the first sleeve 41, the second sleeve 42, the first spring 51, and the rod 25 assembled in advance to the main body 21, the piston Installation of the member 26 and the cap screw 30 is performed.
  • the large diameter portion 27 of the piston member 26 is inserted into the first sleeve 41 and the small diameter portion 28 is inserted into the insertion hole 35 of the cap screw 30.
  • FIG. 7B is a diagram showing the internal structure of the cushion pin 20 at the start of screwing of the cap screw 30.
  • the screw portion 31 of the cap screw 30 is screwed into a screw groove formed inside the upper portion of the main body portion 21.
  • the lower surface 31 a of the cap screw 30 contacts the upper surface of the large diameter portion 27 of the piston member 26 (the surface around the small diameter portion 28), and the piston member 26 also moves downward integrally with the cap screw 30.
  • FIG. 7C is a view showing the internal structure of the cushion pin 20 in the middle of screwing the cap screw 30.
  • the lower surface 31 a of the cap screw 30 comes into contact with the upper end surface 41 a of the first sleeve 41.
  • the upper surface of the large diameter portion 27 of the piston member 26 and the upper end surface 41a of the first sleeve 41 are substantially flush. Since the piston member 26 is urged upward by the urging force of the first spring 51, the piston member 26 and the first sleeve 41 are moved integrally by the pressing force of the cap screw 30 thereafter. .
  • the minimum contraction value of the first spring 51 is determined by the position of the piston member 26.
  • FIG. 7D is a diagram showing an internal structure of the cushion pin 20 after the cap screw 30 is attached.
  • the lower surface 31 a of the cap screw 30 comes into contact with the upper end surface 41 a of the first sleeve 41.
  • the first sleeve 41 moves downward together with the cap screw 30, and the second spring 52 is pushed in via the annular member 23.
  • the cap screw 30 is in contact with the upper end surface 42a of the first sleeve 41 and is tightened to the end, the movement of the first sleeve 41 stops and the pushing of the second spring 52 is completed.
  • the minimum contraction value of the second spring 52 is determined by the position of the first sleeve 41.
  • the cap screw 30 is fastened and fixed to the main body 21, whereby the piston member 26 is held at the upper end of the main body 21.
  • the contraction minimum value of the 1st spring 51 and the 2nd spring 52 will be in the state controlled.
  • the maximum contraction value (upper limit) and the minimum contraction value (lower limit) of the first spring 51 and the second spring 52 are determined by the axial length of each member together with the spring constant. By adjusting the load characteristics can be accurately controlled.
  • the cushion pin 20 includes a cylindrical main body 21, a bottom cap (bottom member) 22 disposed at one end of the main body 21, and a cap screw disposed at the other end of the main body 21. (Lid member) 30, piston member 26 held by main body 21 by cap screw 30, and first arranged in series inside main body 21 so as to receive the load received via piston member 26 in stages.
  • a spring 51 and a second spring 52 (a plurality of springs). The first spring 51 and the second spring 52 are configured so that the timing of receiving the load is overlapped based on a manufacturing error (for example, lower region ⁇ 10% of the generated load, upper region ⁇ 5%) set for each spring. 21 is held.
  • the cushion pin 20 of the present embodiment is disposed inside the main body portion 21 and is disposed inside the first sleeve 41 and the first sleeve 41 that can press the second spring 52, and the first sleeve 41, And a second sleeve (second cylindrical member) 42 in which the first spring 51 arranged in series with the second spring 52 is accommodated.
  • the axial length of the second sleeve 42 is set to be shorter than that of the first spring 51, and the cap screw 30 is in contact with the first sleeve 41 in a state where it is assembled to the main body portion 21.
  • the minimum shrinkage value is regulated and the minimum shrinkage value of the first spring 51 is regulated via the piston member 26.
  • the maximum contraction value of the first spring 51 can be accurately adjusted by the length of the second sleeve 42 in the axial direction, and the cap screw 30 is also used for the minimum contraction value of the first spring 51 and the second spring 52. Since it can be set by the piston member 26, it is possible to accurately control the timing of taking over the load among the plurality of springs. As a result, design changes according to the specifications of the press molding apparatus 1 are facilitated.
  • the pressing force is smoothly increased by contracting from the first spring 51 having a long stroke width and a weak urging force at a constant load, and a strong urging force of the second spring 52 is applied when the constant load is exceeded. This configuration can be easily realized. Further, by arranging the weak first spring 51 inside the second sleeve 42 as in the present embodiment, the diameter of the cushion pin 20 as a whole can be reduced, and the degree of freedom in layout can be improved. .
  • first spring 51 and the second spring 52 of the present embodiment are constituted by a disc spring 55 and a disc spring 57, which are not the same type of spring, but have different load characteristics.
  • FIGS. 8A and 8B a cushion pin 220 of a modified example will be described with reference to FIGS. 8A and 8B.
  • components that are the same as or similar to those in the above-described embodiment may be denoted by the same reference numerals and description thereof may be omitted.
  • FIG. 8A is a diagram showing an internal structure of a cushion pin 220 according to a modification.
  • FIG. 8B is a diagram showing an internal structure of the cushion pin 220 in a state where the third spring 253 is elastically deformed together with the first spring 251 and the second spring 252 under the load of the modification.
  • the cushion pin 220 of this modification has a multiple sleeve structure different from the cushion pin 20 of the above embodiment.
  • the configuration of the modification will be described.
  • a third spring 253 is disposed above the bottom cap 22 of the main body 21.
  • the third spring 253 is configured by arranging in series a plurality of disc springs 259 in which a through hole 260 for inserting the rod 25 is formed at the center.
  • a second annular member 225 in which a through hole 226 for inserting the rod 25 is formed is disposed.
  • the first sleeve 241, the fourth sleeve 244, and the second spring 252 are disposed above the second annular member 225.
  • the fourth sleeve 244 has an outer diameter corresponding to the inner diameter of the first sleeve 241, and the second spring 252 is accommodated inside the fourth sleeve 244.
  • the second spring 252 is also configured by arranging in series a plurality of disc springs 257 in which a through hole 258 for inserting the rod 25 is formed in the center. The axial length of the second spring 252 is longer than that of the fourth sleeve 244.
  • the fourth sleeve 244 and the second spring 252 is disposed a first annular member 223 in which a through hole 224 for inserting the rod 25 is formed.
  • the upper end of the second spring 252 is in contact with the lower surface of the first annular member 223.
  • the upper end surface 244a of the fourth sleeve 244 is arranged such that a gap is provided between the upper end surface 244a and the first annular member 223 when no load is received. Therefore, the maximum contraction value of the second spring 252 is determined by the length of the fourth sleeve 244 in the axial direction.
  • the first spring 251 housed inside the third sleeve 243 is disposed.
  • the first spring 251 is also configured by arranging a plurality of disc springs 255 in which a through hole 256 for inserting the rod 25 in the center is arranged in series. It should be noted that in relation to the strength and size (diameter) of the urging force, the relationship is disc spring 255 ⁇ disc spring 257 ⁇ disc spring 259.
  • the upper end of the first spring 251 is in contact with the lower surface 27a of the piston member 26.
  • the upper end surface 243a of the third sleeve 243 is disposed such that a gap is provided between the upper surface 243a and the lower surface 27a of the piston member 26 in a state where no load is received. Therefore, the maximum contraction value of the first spring 251 is determined by the axial length of the third sleeve 243.
  • the upper end surface 241a of the first sleeve 241 and the upper end surface 242a of the second sleeve 242 are both in contact with the lower surface 31a of the cap screw 30.
  • the first sleeve 241 can press the third spring 253 via the second annular member 225, and the third spring 253 depends on the degree of tightening of the cap screw 30 and the length of the first sleeve 241 in the axial direction. The minimum value of shrinkage is determined.
  • the second sleeve 242 can press the second spring 252 via the first annular member 223, and the second sleeve 242 can be pressed according to the tightening amount of the cap screw 30 and the axial length of the second sleeve 242.
  • the minimum contraction value of the spring 252 is determined.
  • the piston member 26 receives a load
  • first the first spring 251 starts to contract
  • the second spring 252 starts to contract
  • the third spring 253 starts to contract
  • the first spring 251 begins to contract.
  • All of the spring 251, the second spring 252, and the third spring 253 are contracted.
  • the first spring 251 starts to contract before reaching the maximum contraction value
  • the first spring 251 starts to contract before the second spring 252 reaches the contraction maximum value.
  • the axial lengths of the first sleeve 241, the second sleeve 242, the third sleeve 243, the piston member 26, and the cap screw 30 in consideration of manufacturing errors set for the spring 251, the second spring 252, the third spring 253, and the like.
  • the shape, spring constant, etc. are adjusted, and seamless load transfer is realized. Also in this modified example, the same effects as those of the above embodiment can be obtained.
  • the present invention is not limited to this configuration.
  • the first spring and the second spring may be configured with the same spring constant.
  • the axial lengths and the like of the respective components such as the first sleeve, the second sleeve, the piston member, and the cap member are set so that a seam is not generated in taking over the load of the first spring and the second spring. It is preferable.
  • the example in which the first spring, the second spring, and the third spring are configured by a plurality of disc springs has been described, but other than the disc spring may be used.
  • the first spring, the second spring, and the third spring can be configured by arranging coil springs in series.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Springs (AREA)
  • Presses And Accessory Devices Thereof (AREA)
PCT/JP2018/004336 2017-03-09 2018-02-08 クッションピン WO2018163701A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2019504404A JP6739620B2 (ja) 2017-03-09 2018-02-08 クッションピン
CN201880016020.4A CN110382219B (zh) 2017-03-09 2018-02-08 缓冲销

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JP2017044637 2017-03-09
JP2017-044637 2017-03-09

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WO2018163701A1 true WO2018163701A1 (ja) 2018-09-13

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Publication number Priority date Publication date Assignee Title
CN114121519B (zh) * 2021-11-24 2023-06-20 西安西电高压开关有限责任公司 一种双稳态簧保持装置及其工作方法
CN115635037A (zh) * 2022-11-16 2023-01-24 山西大原机电科技有限公司 一种锻圆模具

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