JP2016038036A - Load application device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a versatile load application device which attains good cushioning function, has durability, and does not need design change to a tensioner.SOLUTION: A load application device includes: a spiral spring 3 formed by winding a thin plate material several times; and a holding member 4 which holds the spiral spring 3. The holding member 4 is attached to a mating member 240 or a tensioner 300 so that the spiral spring 3 is sandwiched between the mating member 240 provided at a moving member and the tensioner 300 which presses the mating member 240.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a load applying device for assisting operation of a tensioner used in an automobile engine or the like.

  An automobile engine such as a two-wheeled vehicle or a four-wheeled vehicle transmits power to an axle using an endless moving member such as a timing chain or a timing belt. These moving members need to travel (move) with appropriate tension. For this reason, the tensioner is assembled to the engine, and when the tensioner presses the moving member with a predetermined force and the moving member is stretched or loosened, the tension is kept constant.

  FIG. 12 shows the inside of the engine body 200 of the automobile. A pair of cam sprockets 210 and 210 that are driven shafts and a crank sprocket 220 that is a drive shaft are disposed inside the engine body 200, and timing as a moving member is between these sprockets 210, 210, and 220. The chain 230 is stretched over an endless shape. The timing chain 230 moves (runs) between the sprockets 210, 210, and 220 by the rotation of the crank sprocket 220. A guide arm 240 such as a chain guide as a counterpart member is disposed on the moving path of the timing chain 230 so as to contact the timing chain 230, and the timing chain 230 slides along the front surface (right surface) 241 of the guide arm 240. It is supposed to be. A guide arm 240 such as a chain guide can swing around a support shaft 250, and the tension of the timing chain 230 is adjusted by this swing.

  Reference numeral 300 denotes a tensioner provided inside the engine body 200 in order to press the guide arm 240 against the timing chain 230. The tensioner 300 generally has a structure in which the guide arm 240 is pressed by an expansion and contraction operation in the axial direction.

  FIG. 13 shows the general structure of the tensioner 300. A cylindrical propelling member 320, a shaft-like rotating member 340 screwed to the propelling member 320 by a screw portion 330, a coil spring 350 that applies rotational torque to the rotating member 340, and a case 310 that accommodates these are provided. The case 310 is fixed to the engine body 200 by bolting or the like. The rotation of the propelling member 320 is restricted by a bearing member 360 attached to the tip portion of the case 310, so that the propelling member 320 advances relative to the case 310 by the rotational force of the rotating member 340 transmitted through the screw portion 330. Then, the timing chain 230 is pressed through the guide arm 240. On the other hand, when the tension of the timing chain 230 increases, the guide arm 240 pushes back the propelling member 320, so that the propelling member 320 moves backward while rotating the rotating member 340 in the reverse direction. By these operations, the tension of the timing chain 230 is kept constant.

  The tensioner 300 and the guide arm 240 are repeatedly subjected to the tension fluctuation of the timing chain 230 due to vibration from the engine. When the engine vibration is large, abnormal noise is generated or each component of the tensioner 300 is The parts may be damaged due to excessive load. Therefore, it is necessary to absorb engine vibration. Patent Documents 1 and 2 describe structures for this purpose.

In Patent Document 1, an arc-shaped projecting portion is formed at a portion of the guide arm facing the tensioner, and a cap made of resin or metal is attached to the tip portion of the propulsion member of the tensioner, and this cap contacts the projecting portion. It has a structure that absorbs vibration by the buffering action.
In Patent Document 2, the entire swinging guide arm is made of resin, and a pad portion made of rubber is provided in a portion of the guide arm facing the tensioner, and vibration is absorbed by a buffering action of the pad portion. Yes.

JP-A-11-201245 JP 2013-83279 A

When the cap or pad used for the conventional buffer described in Patent Documents 1 and 2 is made of resin or rubber, thermal degradation in high-temperature oil occurs, or it cannot be able to withstand the high load during vibration, causing collapse There is. On the other hand, when metal is used for the cap or pad, it can be durable in high-temperature oil, but on the other hand, it is difficult to obtain the necessary deflection for high loads and also exhibits a buffering function. There is a problem that it is not possible to obtain the hysteresis characteristic (deflection-load characteristic) necessary for this.
In order to deal with the above problems, it has been studied to change the characteristics of the tensioner itself so that the tensioner has a good buffer function against vibration from the engine, but the tensioner inherently adjusts the tension. At present, it is difficult to develop a tensioner having a structure and a characteristic having a wide range of functions such as a buffer function in addition to the tension adjusting function.

  The present invention has been made in consideration of the above-described problems, and is capable of obtaining a good buffer function, having durability, and having a versatile load that does not require a design change to the tensioner. An object is to provide an additional device.

  In order to achieve the above object, a load applying device according to a first aspect of the present invention includes a mainspring spring in which a thin plate material is wound a plurality of times, and a holding member that holds the mainspring spring, and is provided on a movable member. The holding member is attached to the mating member or the tensioner so that the spring is sandwiched between the member and a tensioner that presses the mating member.

The invention according to claim 2 is the load applying device according to claim 1, wherein the holding member is attached to the mating member or the tensioner in a state in which the expansion and contraction operation of the mainspring spring is allowed. To do.

The invention according to claim 3 is the load applying device according to claim 1 or 2, wherein the recess for accommodating the spring is formed in the mating member or the tensioner, and the outer periphery of the spring is in the recess. It is attached to the mating member or the tensioner in the abutted accommodated state.

The invention according to claim 4 is the load applying device according to any one of claims 1 to 3, wherein the mainspring spring has an outer peripheral portion directly or indirectly through the holding member or the holding member. It is characterized by being in contact.

A load applying device according to a fifth aspect of the present invention includes a mainspring spring in which a thin plate material is wound a plurality of times, and a tensioner having a propelling member that moves forward and backward to press a mating member provided on the moving member, The mainspring spring is arranged in the tensioner so as to be positioned on the backward direction side of the propulsion member.

A sixth aspect of the present invention is the load applying device according to the fifth aspect, wherein the tensioner includes a case for accommodating the propulsion member so as to be movable forward and backward, and the mainspring spring is provided on a retreat direction side of the propulsion member. The rotating member is disposed between the case and the case.

A seventh aspect of the present invention is the load applying device according to any one of the first to sixth aspects, wherein the moving member is a timing chain or a timing belt that moves endlessly in an automobile engine. The mating member is a guide arm that is swingably provided in the engine and on which the moving member slides.

  ADVANTAGE OF THE INVENTION According to this invention, it can be set as the versatile load addition apparatus which can obtain a favorable buffer function, has durability, and does not require the design change to a tensioner.

It is sectional drawing which shows the state which applied the load addition apparatus of 1st Embodiment of this invention to the engine of the motor vehicle. It is a side view which shows the load addition apparatus of 1st Embodiment, and its periphery. It is the EE sectional view taken on the line of FIG. It is the FF sectional view taken on the line of FIG. It is a side view which shows the load addition apparatus of 2nd Embodiment of this invention, and its periphery. It is the GG sectional view taken on the line of FIG. It is a side view which shows the load addition apparatus of 3rd Embodiment of this invention, and its periphery. It is a side view which shows the load addition apparatus of 4th Embodiment of this invention, and its periphery. It is sectional drawing which shows the load addition apparatus of 4th Embodiment. It is a cross section of the load addition apparatus of 5th Embodiment of this invention, and is the II sectional view taken on the line of FIG. It is a cross section of the load addition apparatus of 5th Embodiment, and is the HH sectional view taken on the line of FIG. It is sectional drawing which shows the inside of the engine main body of the motor vehicle incorporating the general tensioner. It is sectional drawing which shows a general tensioner.

  Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments. In each embodiment, the same member is attached with the same reference numeral. Moreover, in each embodiment, it demonstrates as the arrow direction which illustrates an up-down direction and the front-back direction.

(First embodiment)
1 to 4 show a load applying device 1 according to a first embodiment of the present invention, and shows an embodiment applied to an automobile engine. The load applying device 1 is used by being attached to the guide arm 240 using a guide arm 240 such as a chain guide used in the engine as a counterpart member.

  FIG. 1 shows an engine main body 200 in which the load applying device 1 of this embodiment is incorporated, and a reference numeral corresponding to FIG. 12 is given. That is, a pair of cam sprockets 210 and 210 that are driven shafts and a crank sprocket 220 that is a drive shaft are arranged inside the engine main body 200, and the sprockets 210, 210, and 220 serve as moving members. The timing chain 230 is stretched over an endless shape. The timing chain 230 serves as a moving member of the present invention, and the timing chain 230 as a moving member moves (runs) between the sprockets 210, 210, and 220 by the rotation of the crank sprocket 220. A guide arm 240 such as a chain guide as a counterpart member is arranged on the moving path of the timing chain 230 so as to contact the timing chain 230, and the timing chain 230 slides along the front surface 241 of the guide arm 240. It has become. A guide arm 240 such as a chain guide can swing around a support shaft 250, and the tension of the timing chain 230 is adjusted by this swing.

  In order to adjust the tension of the timing chain 230, a tensioner 300 is attached inside the engine body 200. A general tensioner shown in FIG. 13 is used as the tensioner 300, and the case 310 is fixed to the engine body 200 by bolting or the like. Inside the case 310, there are provided a rotating member that is rotationally biased by a coil spring and a propelling member that is screwed into the rotating member and whose rotation is constrained (all not shown). The front end portion of the propelling member 320 protrudes from the case 310 and faces the guide arm 240. In this embodiment, the load applying device 1 is attached to the guide arm 240 so as to face the propelling member 320 of the tensioner 300.

  2 is an enlarged view showing the load applying device 1 and its peripheral portion, FIG. 3 is a cross-sectional view taken along the line EE of FIG. 2, and FIG. 4 is a cross-sectional view taken along the line FF of FIG.

  As shown in FIG. 2, the load applying device 1 is formed by a mainspring 3 and a holding member 4 that holds the mainspring 3, and the whole is attached to the back surface 242 of the guide arm 240. A concave portion 243 that accommodates the mainspring spring 3 is formed in a portion of the back surface 242 of the guide arm 240 that faces the tensioner 300 (propulsion member 320). As shown in FIG. 4, the concave portion 243 of the guide arm 240 is formed by slope portions 244 on both sides in the vertical direction and a bottom portion 245 continuously provided so as to be recessed between the slope portions 244. Three outer peripheral portions 31 abut. When the outer peripheral portion 31 of the mainspring spring 3 abuts on the inclined surface portion 244, a load acts between the guide arm 240 and the mainspring spring 3. Note that the outer peripheral portion 31 of the mainspring 3 is not in contact with the bottom portion 245.

  As shown in FIGS. 2 and 3, the holding member 4 has a holding portion 41 and an arm portion 42, and the arm portion 42 is attached to the guide arm 240 by being locked to the back surface 242 of the guide arm 240. By this attachment, the holding member 4 is in a state of holding the mainspring 3, and the mainspring 3 is provided so as to be sandwiched between the guide arm 240 as a counterpart member and the tensioner 300 that presses the guide arm 240.

  The holding portion 41 of the holding member 4 has an umbrella shape curved in the direction of the mainspring spring 3 with a predetermined thickness, and a concave portion 45 is formed on the front surface facing the mainspring spring 3. The concave portion 45 is formed by slope portions 46 on both sides in the vertical direction and a bottom portion 47 continuously provided so as to be recessed between the slope portions 46, and the slope portion 46 abuts on the outer peripheral portion 31 of the mainspring spring 3. 47 becomes a non-contact state with the outer peripheral part 31 of the mainspring spring 3. A load acts between the mainspring spring 3 and the holding member 4 by the outer peripheral portion 31 of the mainspring spring 3 coming into contact with the inclined surface portion 46. The holding portion 41 is provided so as to cover the mainspring spring 3, and the back portion thereof serves as an abutting portion 41 that abuts against the propelling member 320 of the tensioner 300.

  The arm portion 42 extends from the left and right sides of the holding portion 41 in the direction of the guide arm 240, and the extended end portion (front end portion) is bent to form a locking claw portion 43. The locking claw portion 43 is locked to a locking recess 246 formed in the guide arm 240, whereby the holding member 4 is attached to the guide arm 240 with the arm portion 42 sandwiching both end surfaces of the mainspring spring 3. The thickness of the locking claw 43 is smaller than the width of the locking recess 246. When the locking claw 43 is locked to the locking recess 246, the locking claw 43 and the locking recess 246 A gap is formed between them. For this reason, the holding member 4 can be displaced in the thickness direction (front-rear direction) of the guide arm 240. Accordingly, since the holding member 4 is displaced in the front-rear direction in accordance with the expansion / contraction operation of the mainspring spring 3, the expansion / contraction operation of the mainspring spring 3 can be permitted.

  The mainspring spring 3 is formed by winding a thin plate material having spring properties into a spiral shape a plurality of times, and the spiral inner end portion is a winding portion 32. The spiral outer end portion is an outer end locking portion 33, and the outer end locking portion 33 is locked to the end portion of the holding portion 41 of the holding member 4. A window portion 44 is opened in the arm portion 42 of the holding member 4, and a spring member 3 is appropriately wound up (reduced in diameter) by inserting and rotating a winding member (not shown) from the window portion 44. Can do. The mainspring spring 3 has a frictional resistance between the thin plate members when expanding the diameter, so that the force for expanding the diameter is relatively small. On the other hand, there is a frictional resistance between the thin plate members when reducing the diameter, so that the force necessary for the diameter reduction is obtained. Has a large characteristic, and a good buffering function can be exhibited by this characteristic.

  The load applying device 1 of this embodiment sets the mainspring spring 3 in a tensioned state, and stores the mainspring spring 3 in the recess 243 of the guide arm 240 in this tensioned state, and attaches the holding member 4 to the guide arm 240. As a result, the mainspring 3 is sandwiched between the guide arm 240 and the tensioner 300. In this state, the abutting portion 41 a of the holding portion 41 in the holding member 4 is in contact with the propelling member 320 of the tensioner 300, and the tension spring 3 biases the holding member 4 in the direction of the tensioner 300. .

  Upon receiving vibration from the engine, an alternating load acts on the guide arm 240 from the timing chain 230 as a moving member, and the mainspring spring 3 receives the alternating load between the guide arm 240 and the tensioner 300 via the holding member 4. . The spring spring 3 is wound with a thin plate material in close contact with it a plurality of times, and the spring spring 3 is repeatedly bent and returned to the opposite direction by an alternating load. Since friction is generated between the thin plate materials by this repeated operation, a hysteresis characteristic is generated in the load characteristic diagram of the longitudinal movement of the holding member 4. For this reason, even if intense vibration is applied from the guide arm 240, this vibration can be buffered and received, and resonance and the like can be suppressed.

  Since the mainspring spring 3 absorbs vibrations, it is not necessary to provide the tensioner 300 with a buffering characteristic, and it is not necessary to select a design or specification for imparting the buffering characteristic. Thus, a great degree of freedom can be given to the selection of the tensioner 300. it can. In this embodiment, the buffering characteristic of the spring spring 3 can be easily set to a required spring constant by selecting the thickness, width, length and outer diameter of the thin plate material. The degree of freedom increases. Furthermore, since the load applying device 1 is attached to the guide arm 240 in a state where the mainspring spring 3 is housed in the recess 243 of the guide arm 240, the height space for attachment is reduced, and the attachment state is prevented from becoming bulky. be able to. In addition, since the mainspring 3 and the holding member 4 are made of metal, there is no occurrence of thermal deterioration and it can withstand high loads, thereby improving durability.

(Second Embodiment)
5 and 6 show a load applying device 1A according to a second embodiment of the present invention. Also in this embodiment, the load applying device 1 </ b> A is applied to the engine body 200.

  In this embodiment, the arm portion 42 of the holding member 4 extends from the upper and lower ends of the holding portion 41 along the length direction of the guide arm 240, and the extended arm end portion 42 a is bent in the direction of the guide arm 240. doing. A locking claw portion 43 is formed on the arm end portion 42a. The guide arm 240 is formed with a locking recess 246 corresponding to each arm end 42a, and the locking claw 43 of the arm end 42a is locked to each locking recess 246. Thus, the holding member 4 (load adding device 1A) is attached to the guide arm 240. The arm portion 42 of the holding member 4 is long in the longitudinal direction (vertical direction), and the entire holding member 4 including the arm portion 42 is formed of a resin such as polyamide resin (for example, nylon). For this reason, since the holding member 4 expands and contracts according to the expansion / contraction operation of the mainspring spring 3, the expansion / contraction operation of the mainspring spring 3 can be permitted. The holding portion 41 is formed with a pinching piece portion 48 that sandwiches both end faces of the mainspring spring 3, and the mainspring spring 3 is accommodated in the concave portion 243 of the guide arm 240 while being held by the holding portion 41 and the pinching piece portion 48. The In this embodiment, the outer end locking portion 33 of the mainspring spring 3 is locked to one (lower) arm portion 42.

  Also in this embodiment, the load applying device 1A is attached to the guide arm 240 in a tension state in which the mainspring spring 3 is reduced in diameter. Thereby, the mainspring spring 3 is sandwiched between the guide arm 240 and the tensioner 300. In such a structure, as with the first embodiment, by receiving an alternating load from the engine, the mainspring spring 3 repeatedly operates to bend and return to the opposite direction, and friction is generated between the thin plate materials by this repeated operation. Therefore, a hysteresis characteristic is generated in the load characteristic diagram of the longitudinal movement of the holding member 4. For this reason, even if intense vibration is applied from the guide arm 240, this vibration can be buffered and received, and resonance and the like can be suppressed. Therefore, it is not necessary to provide the buffering characteristic to the tensioner 300, and it is not necessary to select a design or specification for providing the buffering characteristic, and a great degree of freedom can be given to the selection of the tensioner 300. Further, the shape and size of the holding member 4 can be appropriately changed in accordance with the guide arm 240 which is a counterpart member.

(Third embodiment)
FIG. 7 shows a load applying device 1B according to a third embodiment of the present invention. Also in this embodiment, the load applying device 1 </ b> B is applied to the engine body 200.

  In this embodiment, the holding member 4 in which the holding portion 41 facing the tensioner 300 is omitted is used. The holding member 4 has a curved triangular shape and is formed by a pair of plate-like holding bodies 49 extending from the guide arm 240 toward the spring 3, and the pair of holding bodies 49 are fixed to the guide arm 240 by screws 50. By doing so, both end surfaces of the mainspring spring 3 are sandwiched.

  The mainspring spring 3 is accommodated in the concave portion 243 of the back surface 242 of the guide arm 240 while being sandwiched between the pair of plate-like holding bodies 49, and the outer end locking portion 33 is locked to the back surface 242 of the guide arm 240. The spring 3 is in direct contact with the propulsion member 320 of the tensioner 300, and a recess 320 a corresponding to the outer peripheral portion 31 of the spring 3 is formed on the front surface of the propulsion member 320. Note that the front surface of the propelling member 320 may be a flat surface without forming the recess 320a.

Also in this embodiment, the load applying device 1B is attached to the guide arm 240 in a tension state in which the mainspring spring 3 is reduced in diameter. The mainspring spring 3 is sandwiched between the guide arm 240 and the tensioner 300 in a state where the spring 3 directly contacts the propelling member 320 of the tensioner 300. In such a structure, by receiving an alternating load from the engine, the mainspring spring 3 repeatedly operates to bend and return to the opposite direction, and friction is generated between the thin plate materials by this repeated operation. A hysteresis characteristic occurs in the load characteristic diagram of the longitudinal movement of the holding body 49). For this reason, even if intense vibration is applied from the guide arm 240, this vibration can be buffered and received, and resonance and the like can be suppressed. Therefore, it is not necessary to provide the buffering characteristic to the tensioner 300, and it is not necessary to select a design or specification for providing the buffering characteristic, and a great degree of freedom can be given to the selection of the tensioner 300.

(Fourth embodiment)
8 and 9 show a load applying device 1C according to a fourth embodiment of the present invention. The load applying device 1 </ b> C of this embodiment is attached to the tensioner 300, and the mainspring spring 3 is sandwiched between the tensioner 300 and the guide arm 240 as a counterpart member in the attached state to the tensioner 300.

  As shown in FIG. 9, the tensioner 300 includes a cylindrical propelling member 320, a shaft-like rotating member 340 that is screwed with the propelling member 320 by the screw portion 330, and a coil spring 350 that applies rotational torque to the rotating member 340. And a case 310 for housing them, and the case 310 is fixed inside the engine body 200 by bolting or the like. The rotation of the propelling member 320 is restrained by a bearing member 360 attached to the tip portion of the case 310, whereby the propelling member 320 is moved to the right with respect to the case 310 by the rotational force of the rotating member 340 transmitted through the screw portion 330. It advances in the direction and presses the timing chain 230 via the guide arm 240. On the other hand, when the tension of the timing chain 230 increases and the guide arm 240 pushes back the propelling member 320, the propelling member 320 moves backward while rotating the rotating member 340 in the reverse direction. Reference numeral 370 is a tightening jig inserted from the rear end of the case 310 in order to wind the coil spring 350 via the rotating member 340 by rotating the rotating member 340.

  The load applying device 1 </ b> C is attached to the tip (left end) portion of the propulsion member 320 of the tensioner 300. In order to attach the load applying device 1 </ b> C, a recess 321 is formed at the tip of the propelling member 320. The concave portion 321 is formed by a bottom portion 323 and slope portions 322 on both sides of the bottom portion 323, and the outer peripheral portion 31 of the spring 3 is brought into contact with the slope portion 322, and the spring spring 3 is brought into contact with the concave portion 321 by this contact. It becomes the accommodation state. When the outer peripheral portion 31 of the mainspring spring 3 abuts on the inclined surface portion 322, a load acts between the propelling member 320 and the mainspring spring 3.

The load applying device 1 </ b> C has the same structure as that of the first embodiment, and is formed by a holding member 4 having a holding portion 41 and an arm portion 42, and a spring spring 3 held by the holding member 4. As in the first embodiment, the holding portion 41 is provided with slope portions 46 from both sides of the bottom portion 47, and the outer peripheral portion 31 of the spring 3 abuts against the slope portion 46. As shown in FIG. 8, the abutting portion 41 a of the holding portion 41 abuts on a guide arm 240 as a counterpart member. A locking claw portion 43 is formed at the rear end portion (right end portion) of the arm portion 42. The locking claw portion 43 is locked to a locking recess 324 formed in the propelling member 320, and load is applied by this locking. The device 1C is attached to the propelling member 320.
Also in this embodiment, as in the first embodiment, the thickness of the locking claw 43 is smaller than the width of the locking recess 324, and the locking claw 43 is locked to the locking recess 324. A gap is formed between the locking claw 43 and the locking recess 324. For this reason, the holding member 4 can be displaced in the axial direction of the propelling member 320 in the left-right direction), and the holding member 4 is displaced in the front-rear direction in accordance with the expansion / contraction operation of the mainspring spring 3. In this state, the expansion / contraction operation 3 can be permitted.

The load applying device 1C of this embodiment can also operate in the same manner as in the first embodiment. That is, an alternating load from the engine acts on the holding member 4 from the guide arm 240, and the mainspring 3 receives the alternating load between the guide arm 240 and the propelling member 320. The spring spring 3 is wound with a thin plate material in close contact with it a plurality of times, and the spring spring 3 is repeatedly bent and returned to the opposite direction by an alternating load. Since friction is generated between the thin plate members by this repeated operation, a hysteresis characteristic is generated in the load characteristic diagram of the longitudinal movement of the holding member 4, and this vibration is buffered and received even when a strong vibration is applied from the guide arm 240. Therefore, resonance and the like can be suppressed.
In particular, in this embodiment, since the load applying device 1C is attached to the tensioner 300, processing such as forming a recess in the guide arm 240 is unnecessary, and a general guide arm can be used. Expands. Further, the tensioner 300 may have a structure incorporating a ratchet that locks forward / backward movement of the propelling member 320 in addition to the coil spring 350, or other structure.

(Fifth embodiment)
10 and 11 show a load applying device 1D according to a fifth embodiment of the present invention. The load applying device 1 </ b> D is formed by incorporating the mainspring 3 into the tensioner 300. That is, the load applying device 1 </ b> D is formed by the mainspring 3 and the tensioner 300.

  9 and 13 is used as the tensioner 300. The tensioner 300 includes a case 310 fixed in the engine main body 200 by bolting or the like, and further includes a rotating member 340 that is urged to rotate by a coil spring 350. And a cylindrical propelling member 320 that is screwed to the rotating member 340 via a screw portion 330 and whose rotation is restricted by the bearing member 260. The propelling member 320 advances from the case 310 and presses the guide arm 240 when the rotating member 340 is rotated by the spring force of the coil spring 350, and moves backward when a load is input from the guide arm 240.

Two springs 3 are arranged in the case 310 so that the springs 3 are located on the backward side of the propelling member 320. A rotating member 340 is coaxially connected in the retracting direction of the propelling member 320, and the two springs 3 are disposed between the rotating member 340 and the case 310. In order to arrange the two springs 3, the receiving member 6 is arranged at the rear end of the rotating member 340. The receiving member 6 is provided so as to abut on a receiving recess 341 formed on the rear end surface of the rotating member 340, and has a bottom portion 61 and a slope portion 62 around the bottom portion 61. Three outer peripheral portions 31 abut. On the other hand, on the inner surface of the bottom wall portion 310 a corresponding to the rotating member 340 of the case 310, a receiving recess 313 including a bottom portion 311 and a slope portion 312 around the bottom portion 311 is formed, and a spring spring is formed on the slope portion 312 of the receiving recess 313. Three outer peripheral portions 31 are in contact with each other. Further, a partition wall 314 for partitioning and arranging the two springs 3 is formed on the bottom wall 310a of the case 310 so as to protrude (FIG. 10). In such a structure, the mainspring spring 3 is disposed between the rotating member 340 and the case 310.

In such a structure, the alternating load from the engine body is transmitted from the propelling member 320 to the rotating member 340, and the alternating load acts on each spring 3 via the receiving member 6 from the rotating member 340. The spring spring 3 is wound with a thin plate material in close contact with it a plurality of times, and the spring spring 3 is repeatedly bent and returned to the inside in the case 310. Since friction is generated between the thin plate materials by this repeated operation, a hysteresis characteristic is generated in the load characteristic diagram of the forward and backward movement of the rotating member 340, and even if a strong vibration is applied from the guide arm 240, this vibration is buffered and received. Therefore, resonance and the like can be suppressed.
In this embodiment, the mainspring spring 3 constitutes a part of the tensioner 300 by incorporating the mainspring spring 3 into the tensioner 300, and it is not necessary to separately attach the mainspring spring 3 to the outside of the guide arm 240 or the tensioner. The structure for buffering can be simplified and the assembly to the engine body is facilitated. The tensioner 300 may have a structure incorporating a ratchet that locks the forward / backward movement of the propelling member 320 in addition to the coil spring 350, or other structure.

  In the above embodiment, the load applying device used for the automobile engine is shown. However, the present invention is not limited to this, and the same applies to the intake valve of the automobile engine that opens and closes, other opening / closing mechanisms, and linear movement mechanisms. Can be applied.

1A, 1B, 1C, 1D Load applying device 3 Spring spring 31 Outer peripheral portion 4 Holding member 200 Engine body 230 Timing chain (moving member)
240 Guide arm (mating member)
300 Tensioner

Claims (7)

A mainspring spring in which a thin plate material is wound a plurality of times, and a holding member that holds the mainspring spring,
A load application, wherein the holding member is attached to the counterpart member or the tensioner so that the mainspring spring is sandwiched between a counterpart member provided on the moving member and a tensioner that presses the counterpart member. apparatus. The load applying device according to claim 1,
The load applying device according to claim 1, wherein the holding member is attached to the mating member or the tensioner in a state where the expansion and contraction operation of the mainspring spring is permitted. The load applying device according to claim 1 or 2,
A concave portion for accommodating the mainspring is formed in the mating member or the tensioner, and the mainspring is attached to the mating member or the tensioner with the outer peripheral portion being in contact with the concave portion. apparatus. The load applying device according to any one of claims 1 to 3,
An outer peripheral portion of the mainspring spring is in direct contact with the mating member or tensioner or indirectly through the holding member. A spiral spring in which a thin plate material is wound a plurality of times, and a tensioner having a propelling member that moves forward and backward to press the mating member provided on the moving member,
The load applying device, wherein the mainspring is disposed on the tensioner so as to be positioned on the backward direction side of the propulsion member. The load applying device according to claim 5, wherein
The tensioner includes a case that accommodates the propelling member so as to be movable back and forth, and the mainspring is disposed between a rotating member and a case provided on the retreat direction side of the propelling member. apparatus. The load applying device according to any one of claims 1 to 6,
The moving member is a timing chain or timing belt that moves endlessly in an automobile engine, and the counterpart member is a guide arm that is swingably provided in the engine and on which the moving member slides. A load applying device characterized by.

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