WO2017057080A1 - 捩りばね - Google Patents
捩りばね Download PDFInfo
- Publication number
- WO2017057080A1 WO2017057080A1 PCT/JP2016/077606 JP2016077606W WO2017057080A1 WO 2017057080 A1 WO2017057080 A1 WO 2017057080A1 JP 2016077606 W JP2016077606 W JP 2016077606W WO 2017057080 A1 WO2017057080 A1 WO 2017057080A1
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- WIPO (PCT)
- Prior art keywords
- spring
- gap
- torsion spring
- torsion
- inter
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
- F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
- F16F1/06—Wound springs with turns lying in cylindrical surfaces
Definitions
- the present disclosure relates to a torsion spring used in a throttle valve device that increases or decreases the opening degree of an intake passage or an exhaust passage of an internal combustion engine.
- the intake passage is slightly opened while the operation of the internal combustion engine is stopped. That is, the opening degree of the intake passage is kept at a minute opening degree.
- a minute opening maintained while the operation of the internal combustion engine is stopped is referred to as a default opening.
- the throttle device of Patent Document 1 includes a valve body, an electric actuator, and a torsion coil spring.
- the valve body is rotatably accommodated in the intake passage and increases or decreases the opening degree of the intake passage.
- the actuator includes an electric motor and a speed reducer, and a torque generated by the electric motor is amplified by the speed reducer and transmitted to the valve body, so that the valve body can be driven to rotate on both sides of opening and closing.
- the coil spring has a return spring and a default spring. The return spring mainly biases the valve body to the closed side during operation of the internal combustion engine, and the default spring mainly biases the valve body to the open side when the operation of the internal combustion engine is stopped.
- torsion spring of Patent Document 2 two torsion type coil springs having functions of a return spring and a default spring are connected so that the torsion directions are opposite to each other.
- the two coil springs there is a U-shape between a coil spring called a one side spring arranged on one side in the axial direction and a coil spring called a other side spring arranged on the other side in the axial direction.
- An intermediate hook is provided.
- the axial direction is the direction of the axis of the torsion spring.
- one axial end of the one side spring is hooked and fixed to, for example, a locking portion provided on the housing, etc.
- the end is hooked on a rotating body that is rotationally driven by an actuator to be rotatable.
- the intermediate hook is rotatable or fixed depending on whether the rotation angle of the valve body is on the open side or the close side with respect to the rotation angle corresponding to the default opening.
- the intermediate hook When the rotation angle of the valve body is on the open side with respect to the rotation angle corresponding to the default opening, the intermediate hook can be rotated by being hooked by the engagement piece provided on the rotation body. When the rotation angle of the valve body is closer to the closing angle than the rotation angle corresponding to the default opening, the intermediate hook is hooked and fixed to a locking portion provided in the housing or the like.
- the intermediate hook functions as a torque switching unit that switches torque.
- the portion near the intermediate hook may be deteriorated in posture when the torsion spring is assembled to the throttle device. is there. For this reason, the gap between the lines becomes narrow in the vicinity of the intermediate hook, and there is a possibility that a line-to-line contact that is a contact between turns adjacent in the axial direction occurs.
- An object of the present disclosure is to be used in a throttle valve device that increases or decreases the opening degree of an intake passage or an exhaust passage of an internal combustion engine, so that a valve body is closed and opened so as to suppress contact between lines near an intermediate hook.
- the object is to provide a torsion spring that biases each.
- the torsion spring is formed by connecting two torsion type coil springs so that the torsion directions are opposite to each other, and having a hook between the two coil springs. It is used in a throttle valve device that increases or decreases the opening of an intake passage or an exhaust passage.
- the throttle valve device includes a valve body that is rotatably accommodated in the intake passage or the exhaust passage and increases or decreases the opening degree of the intake passage or the exhaust passage.
- the valve body is urged toward the closed side by the one side spring disposed on one side in the axial direction, and the valve body is opened on the other side with the other side spring disposed on the other side in the axial direction.
- the torsion spring is assembled to the throttle valve device so as to be biased.
- the size between the line gaps at the connection portion between the one coil spring and the hook is larger than the average value between the line gaps of the one coil spring.
- Example 1 which is the internal block diagram which removes the gear cover and shows the inside of a throttle valve apparatus.
- Example 1 which is a perspective view which shows the periphery of a torsion spring.
- A is explanatory drawing which shows a torsion spring
- (b) is a top view of a torsion spring (Example 1). It is explanatory drawing shown in the state which assembled
- (A) is a characteristic view which shows the distribution between the line gaps of one side spring
- (b) is a characteristic figure which shows the distribution between the line gaps of the other side spring (Example 1).
- (A) is explanatory drawing which shows a torsion spring
- (b) is a top view of a torsion spring (Example 2). It is explanatory drawing shown in the state which assembled
- Example 3) which is a figure which shows the state which assembled
- (A) is explanatory drawing which shows a torsion spring
- (b) is a top view of a torsion spring (Example 4).
- Example 4 which is a figure which shows the state which assembled
- (A) is explanatory drawing shown in the state assembled
- (A) is explanatory drawing shown in the state assembled
- (b) is a top view of a torsion spring (Example 6). It is explanatory drawing shown in the state which assembled
- (A) is explanatory drawing which shows the phenomenon in which one turn enters into the inside of another turn in a torsion spring
- (b) is an enlarged view of the area
- Example 1 The configuration of the torsion spring 1 according to the first embodiment will be described with reference to FIGS.
- the throttle valve device 2 is mounted, for example, in an engine room of a vehicle and increases or decreases the opening degree of an intake passage of an internal combustion engine (not shown).
- the throttle valve device 2 is controlled in operation by an electronic control device (not shown: hereinafter referred to as ECU) that controls the operation of the internal combustion engine.
- ECU mainly obtains a command value for the opening degree of the intake passage based on the accelerator operation amount of the vehicle, and the detected value of the rotation angle obtained from the rotation angle sensor 3 to be described later matches a numerical value corresponding to the command value.
- the throttle valve device 2 is controlled to operate.
- the throttle valve device 2 includes, in addition to the torsion spring 1, a body 4, a valve body 5, an electric actuator 6 and the like described below.
- the body 4 has a cylindrical bore 8, and the bore 8 forms a part of the intake passage.
- the body 4 is fastened to an intake manifold (not shown) of the internal combustion engine by a fastener such as a bolt.
- the valve body 5 is a disc-shaped butterfly type, and is rotatably accommodated in the bore 8 while being fixed to the shaft 9 to increase or decrease the opening of the intake passage.
- the shaft 9 is assembled so as to cross the bore 8 in the diameter direction ⁇ , and is rotatably supported by the body 4 by a so-called both-end support structure. That is, the shaft 9 is supported by the dry bearing 10 on one side in the diameter direction ⁇ and supported by the ball bearing 11 on the other side.
- the actuator 6 includes an electric motor 13 and a speed reducer 14.
- the torque generated by the electric motor 13 is amplified by the speed reducer 14 and transmitted to the valve body 5.
- the valve body 5 is driven to rotate mainly on the open side. To do.
- the body 4 is mainly provided with a gear case 15 that accommodates the speed reducer 14 on the other side in the diameter direction ⁇ of the bore 8 (that is, the right side of the bore 8 in FIG. 1). Closed by The body 4 is provided with a motor housing portion 17 that houses the electric motor 13. The motor housing portion 17 is provided so that the shaft of the housed electric motor 13 is parallel to the shaft 9, and the gear case 15 has an opening. is doing.
- the electric motor 13 can rotate the output shaft 19 in either the forward direction or the reverse direction by reversing the energization direction, and its operation is controlled by the ECU.
- the reduction gear 14 includes a valve gear 20 that is coaxially assembled to the shaft 9, a pinion gear 21 that is assembled to the output shaft 19, and an intermediate gear 22 that meshes with both the valve gear 20 and the pinion gear 21.
- the intermediate gear 22 is rotatably supported by a support shaft 23 installed between the gear case 15 and the gear cover 16.
- the intermediate gear 22 has a large-diameter gear portion 22 a that meshes with the pinion gear 21 and a small-diameter gear portion 22 b that is provided coaxially with the large-diameter gear portion 22 a and meshes with the valve gear 20.
- the valve gear 20 is a sector gear and has a gear portion that meshes with the small-diameter gear portion 22b on its outer periphery.
- the valve gear 20 is assembled with a split permanent magnet 25 that rotates together with the shaft 9.
- the permanent magnet 25 and the hall element 26 assembled to the gear cover 16 constitute the rotation angle sensor 3 that detects the rotation angle of the valve body 5.
- a signal generated by the rotation angle sensor 3 is output to the ECU, and the ECU controls the operation of the throttle valve device 2 by energizing the electric motor 13 based on the signal input from the rotation angle sensor 3.
- the valve gear 20 has locking portions 28 and 29 when fully closed and fully opened for mechanically setting the respective rotation angles of the valve body 5 to be fully closed and fully opened.
- the locking portions 28 and 29 are locked in contact with the fully closed and fully opened stoppers 30 and 31 when the valve body 5 rotates to the fully closed and fully opened rotation angle, respectively.
- the fully closed and fully opened stoppers 30 and 31 are both provided in the gear case 15, for example.
- the fully closed stopper 30 is, for example, an adjustment screw screwed into the inner wall of the gear case 15.
- the fully open stopper 31 is, for example, a step provided on the inner wall of the gear case 15.
- the torsion spring 1 has two torsion type coil springs 33 and 34 connected so that the torsion directions are opposite to each other, and has an intermediate hook 35 between the two coil springs 33 and 34. Then, with the torsion spring 1 assembled to the throttle valve device 2, the two coil springs 33 and 34 bias the valve body 5 as follows.
- a coil spring 33 disposed on one axial side biases the valve body 5 to the closed side and is disposed on the other axial side.
- a spring 34 biases the valve body 5 to the open side.
- the axial direction related to the torsion spring 1 coincides with the diameter direction ⁇ of the bore 8, and the axial direction one side and the other side related to the torsion spring 1 are each in the diameter direction ⁇ . Since it corresponds to the one side and the other side, the axial illustration of the torsion spring 1 is omitted.
- the torsion spring 1 is composed of one strand, and the intermediate hook 35 is provided by bending the strand into a U shape.
- the intermediate hook 35 forms a gap (hereinafter referred to as a hook gap A) in the axial direction by bending the wire (see FIGS. 4 and 5).
- One axial end of the intermediate hook 35 is connected to the other axial end of the one side spring 33, and the other axial end of the intermediate hook 35 is connected to one axial end of the other side spring 34.
- a hook 33a is also provided at one axial end of the one side spring 33, and the hook 33a is hooked and fixed to a locking portion 33b provided in the gear case 15, for example. Further, a hook 34 a is also provided at the other axial end of the other side spring 34, and the hook 34 a is hooked on an engagement piece 36 provided on the valve gear 20 and can be rotated together with the valve gear 20.
- the intermediate hook 35 can be rotated or fixed depending on whether the rotation angle of the valve body 5 is on the open side or the close side with respect to the rotation angle corresponding to the default opening. That is, when the rotation angle of the valve body 5 is on the open side with respect to the rotation angle corresponding to the default opening, the intermediate hook 35 is hooked by the engagement piece 36 and can be rotated. Moreover, when the rotation angle of the valve body 5 is closer to the rotation angle corresponding to the default opening, the intermediate hook 35 is hooked and fixed to a locking portion 37 provided on the housing or the like.
- the engagement piece 36 is provided with a guide 36a for preventing the lateral displacement of the intermediate hook 35.
- locking part 37 consists of an adjustment screw with an adjustment screw function assembled
- the intermediate hook 35 is assembled to the throttle valve device 2 in a state where the intermediate hook 35 is bent to the outer peripheral side of the one side and the other side springs 33 and 34.
- the one-side spring 33 mainly functions as a return spring that urges the valve body 5 to the closed side during operation of the internal combustion engine, and the actuator 6 resists the urging force of the one-side spring 33. 5 is rotated to the open side.
- the other side spring 34 mainly functions as a default spring that biases the valve body 5 to the open side while the operation of the internal combustion engine is stopped.
- the inner circumferences of the one-side and other-side springs 33 and 34 are respectively provided on the one-side and other-side bushes 39 and 40 that receive the contact of the inner circumference of the one-side and other-side springs 33 and 34 on their outer peripheral surfaces. Is arranged.
- the one side bush 39 is a part of the body 4 and is provided in a cylindrical shape, and protrudes to the other side in the axial direction in the gear case 15.
- the inner circumference of the one side bush 39 forms a space for accommodating the ball bearing 11.
- the other-side bush 40 is integral with the valve gear 20 and is coaxial and provided in a cylindrical shape.
- the other-side bush 40 bulges on one side in the axial direction in the gear case 15 and is axially spaced from the one-side bush 39 (hereinafter referred to as the axial bush). , Referred to as a gap B between the bushes) (see FIG. 5).
- the torsion spring 1 according to the first embodiment will be described in more detail with reference to FIGS. Note that the intermediate hook 35 in FIGS. 4 and 5 is depicted in a state before being bent to the outer peripheral side.
- the one side and the other side springs 33 and 34 form line gaps 42 and 43, respectively.
- the size of the inter-line gap 42a at the connecting portion between the one-side spring 33 and the intermediate hook 35 in the inter-line gap 42 of the one-side spring 33 is determined before and after the torsion spring 1 is assembled to the throttle valve device 2. Even in this state, it is larger than the average value of the gap 42 between the lines.
- connection portion between the one-side spring 33 and the intermediate hook 35 is the root of the rising of the intermediate hook 35 in a state where the intermediate hook 35 is bent to the outer peripheral side (see FIG. 3).
- the intermediate hook 35 In the state before the intermediate hook 35 is bent to the outer peripheral side (see FIG. 4), for example, the intermediate hook 35 extends linearly in a tangential direction from a circle formed by the one side spring 33. And the root of the rising of the intermediate hook 35, that is, the connection portion between the one side spring 33 and the intermediate hook 35 is a circle formed by the one side spring 33 in a state before the intermediate hook 35 is bent to the outer peripheral side, This is a contact point with a straight line formed by the intermediate hook 35.
- the size of the inter-line gap 42 has a continuous distribution with respect to the rotation angle ⁇ as shown in FIG.
- the size of the inter-line gap 42 is expressed by f ( ⁇ ) with the rotation angle ⁇ as a variable, and the average value of the inter-line gap 42 is expressed by fav
- the average value fav is the rotation angle of the root of the intermediate hook 35.
- the size of the inter-line gap 43a in the connection part between the other side spring 34 and the intermediate hook 35 in the inter-line gap 43 of the other side spring 34 is determined before and after the torsion spring 1 is assembled to the throttle valve device 2. In either state, the average value of the inter-line gap 43 is larger.
- connection portion between the other side spring 34 and the intermediate hook 35 can be described in the same manner as the connection portion between the one side spring 33 and the intermediate hook 35.
- the size of the inter-line gap 43 has a continuous distribution with respect to the rotation angle ⁇ as shown in FIG.
- the size of the inter-line gap 43 is represented by g ( ⁇ ) with the rotation angle ⁇ as a variable, and the average value of the inter-line gap 43 is represented by gav
- the average value gav is the root rotation angle of the intermediate hook 35.
- the number of turns is greater for the one side spring 33 than for the other side spring 34.
- the hook gap A is constant. That is, the hook gap A is constant even when moving along the intermediate hook 35 from the tip to the other axial end of the one side spring 33 and one axial end of the other side spring 34.
- f ( ⁇ ) has a maximum value at the root of the intermediate hook 35 (that is, fa has a maximum value of f ( ⁇ )).
- ⁇ may be set.
- the one side spring 33 when the first turn 45 located on the other side in the axial direction is the turn 451 and the turn 45 of the second turn is the turn 452, the one side spring 33 In this case, f ( ⁇ ) may be increased until halfway along the turn 451 toward the turn 452, and thereafter f ( ⁇ ) may be decreased.
- g ( ⁇ ) may be set so that g ( ⁇ ) has the maximum value at the root of the intermediate hook 35 (that is, ga has the maximum value of g ( ⁇ )).
- the other side spring 34 is provided. In this case, g ( ⁇ ) may be increased until halfway along the turn 461 toward the turn 462, and thereafter g ( ⁇ ) may be decreased.
- the size ga of the inter-line gap 43 a is larger than the average value gav of the inter-line gap 43 in the other side spring 34.
- the open side biased other side spring 34 is more likely to cause a line-to-line contact than the closed side biased one side spring 33, and the open side bias is caused by general mounting restrictions.
- the number of turns of the biased other side spring 34 is smaller than the number of turns of the closed side biased one side spring 33. Therefore, in the open side bias and the other side spring 34 with a small number of turns, the line gap 43a is made larger than the average value gav, whereby the effect of suppressing the line contact can be remarkably obtained.
- Example 2 A torsion spring 1 of Example 2 will be described with reference to FIGS. 7 and 8. Note that the intermediate hook 35 of FIGS. 7 and 8 is drawn in a state before being bent to the outer peripheral side.
- the inter-line gaps 42a and 43a are respectively before and after the torsion spring 1 is assembled to the throttle valve device 2, in either state. It is larger than the average values fav and gav of the gaps 42 and 43 between the lines.
- the inter-spring gap C is an axis formed between the turn 451 of the one side spring 33 and the turn 461 of the other side spring 34 in a state where the torsion spring 1 is assembled to the one side bush 39 and the other side bush 40. It is a gap in the direction.
- the inter-spring gap C is smaller than the inter-bush gap B until the rotation angle ⁇ reaches a predetermined magnitude ⁇ c when the one-side spring 33 circulates along the turn 451 toward the turn 452. If it exceeds, it will become larger than the clearance B between bushes (refer FIG. 8).
- the hook gap A gradually increases as it approaches the other end in the axial direction of the one-side spring 33 and one end in the axial direction of the other-side spring 34 from the tip.
- the hook gap A is equal to the minimum value of the inter-spring gap C at the other axial end of the one-side spring 33 and the other axial end of the other-side spring 34, and the inter-spring gap C is turned along the turn 451. As it goes around toward 452, it gradually increases, and when it exceeds ⁇ c, it becomes larger than the gap B between the bushes.
- the inter-spring gap C becomes larger than the inter-bush gap B in the middle of turning around the turn 451 toward the turn 452 in the one side spring 33.
- Example 3 The torsion spring 1 of Example 3 is demonstrated based on FIG. Note that the intermediate hook 35 in FIG. 9 is drawn in a state before being bent to the outer peripheral side.
- the inter-line gaps 42a and 43a are respectively in the state before and after the torsion spring 1 is assembled to the throttle valve device 2, respectively. It is larger than the average values fav and gav of the gaps 42 and 43.
- the inter-spring gap C is smaller than the inter-bush gap B until the rotation angle ⁇ reaches ⁇ c, and becomes larger than the inter-bush gap B beyond ⁇ c, as in the torsion spring 1 of the second embodiment.
- the diameter of the one side spring 33 is larger than the diameter of the other side spring 34.
- Example 4 The characteristics of the torsion spring 1 according to the fourth embodiment will be described with reference to FIGS. 10 and 11. Note that the intermediate hook 35 in FIGS. 10 and 11 is depicted in a state before being bent toward the outer peripheral side.
- the inter-line gaps 42a and 43a are respectively in the state before and after the torsion spring 1 is assembled to the throttle valve device 2, respectively. It is larger than the average values fav and gav of the gaps 42 and 43.
- the inter-spring gap C is expanded stepwise with the same ⁇ c as in the second embodiment (see FIG. 11).
- the hook gap A is constant and does not change from the tip to the other axial end of the one side spring 33.
- the inter-spring gap C is constant up to ⁇ c, equal to the hook gap A, and smaller than the inter-bush gap B.
- the inter-spring gap C expands stepwise at ⁇ c and becomes larger than the inter-bush gap B.
- the inner circumferences of the turns 451 and 461 are positioned so as not to contact the edges of the one side and the other side bushes 39 and 40, respectively. Becomes easier.
- Example 5 A torsion spring 1 of Example 5 will be described with reference to FIG.
- the inter-line gaps 42a and 43a are respectively before and after the torsion spring 1 is assembled to the throttle valve device 2, in either state. It is larger than the average values fav and gav of the gaps 42 and 43 between the lines.
- the inter-spring gap C is larger than the inter-bush gap B with the same ⁇ c as that of the torsion spring 1 of the second embodiment.
- the intermediate hook 35 is bent to the inner peripheral side of the one side and the other side springs 33 and 34 and protrudes into the gap B between the bushes.
- the intermediate spring 35 is bent to the inner peripheral side by making the inter-spring gap C larger than the inter-bush gap B in the middle of turning around the turn 452 along the turn 451 in the one-side spring 33, and between the bushes. It can be arranged in the gap B. For this reason, the physique of the radial direction of the torsion spring 1 can be reduced.
- Example 6 A torsion spring 1 of Example 6 will be described with reference to FIG.
- the inter-line gaps 42a and 43a are respectively before and after the torsion spring 1 is assembled to the throttle valve device 2 in either state. It is larger than the average values fav and gav of the gaps 42 and 43 between the lines.
- the inter-spring gap C expands stepwise and becomes larger than the inter-bush gap B as in the torsion spring 1 of the third embodiment.
- the position where the inter-spring gap C expands stepwise is the boundary between the intermediate hook 35 and one side, the other side springs 33, 34, that is, the other axial end of the one side spring 33 and the axis of the other side spring 34.
- the hook gaps A are all smaller than the inter-bush gaps B, and the inter-spring gaps C are larger than the inter-bush gaps B on the entire circumference.
- the intermediate hook 35 is bent to the inner peripheral side of the one side and the other side springs 33 and 34 and protrudes into the gap B between the bushes.
- the intermediate hook 35 is bent to the inner peripheral side and disposed in the inter-bush gap B. be able to. For this reason, the physique of the radial direction of the torsion spring 1 can be reduced.
- the gaps 42a and 43a between the lines are the average value fav of the gaps 42 and 43 between the lines before and after the torsion spring 1 is assembled to the throttle valve device 2, respectively.
- the inter-line gaps 42 and 43 are not limited to such a mode.
- the line gaps 42a and 43a may be set to be equal to the average values fav and gav of the line gaps 42 and 43, respectively.
- the diameter of the one side spring 33 is larger than the diameter of the other side spring 34 and the diameter of the one side bush 39 is larger than the diameter of the other side bush 40. You may make the diameter of the other side spring 34 larger than the diameter of the one side spring 33 (refer FIG. 14).
- the inter-spring gap C is larger than the inter-bush gap B by ⁇ c, and the hook gap A is smaller than the inter-bush gap B.
- the inter-bush gap B and the inter-spring gap C are not limited to such an embodiment.
- the hook gap A is smaller than the inter-bush gap B from the tip of the intermediate hook 35 to a predetermined position on the way to the other end in the axial direction of the one side spring 33.
- the gap C between the springs may be set to be larger than the gap B between the bushes on the entire circumference of the turn 451 so as to be larger than B.
- the hook gap A may be enlarged stepwise at a predetermined position.
- the number of turns of the one side and the other side springs 33 and 34 is set so that the one side spring 33 is larger than the other side spring 34.
- the magnitude of the number is not particularly limited, and the other side spring 34 may be set to be larger than the one side spring 33.
- the intermediate hook 35 is assembled to the throttle valve device 2 in a state of being bent to the outer peripheral side or the inner peripheral side, but the intermediate hook 35 is attached to the outer peripheral side or the inner peripheral side.
- the torsion spring 1 may be assembled to the throttle valve device 2 without bending it.
- the hook gap A is constant, and according to the torsion spring 1 of the second embodiment, the hook gap A extends from the tip to the other end in the axial direction of the one side spring 33 and the other. Although it gradually increased as it approached one end in the axial direction of the side spring 34, the aspect of the hook gap A is not limited to these aspects. For example, as shown in FIG. 16, the hook gap A may be gradually decreased from the tip toward the other axial end of the one side spring 33 and one axial end of the other side spring 34.
- the size of the inter-line gap 42 a in the inter-line gap 42 of the one side spring 33 is larger than the average value of the inter-line gap 42, and the other side spring 34.
- the size of the inter-line gap 43a is larger than the average value of the inter-line gap 43, but the mode of the torsion spring 1 is not limited to such a mode.
- the inter-line gap 42 existing on the other side in the axial direction may be larger than the other inter-line gaps 42.
- the inter-line gap 43 existing on the one side in the axial direction may be larger than the other inter-line gaps 43.
- the inter-line gap 42 existing on the other side in the most axial direction is made larger than the other inter-line gaps 42, and
- the inter-line gap 43 existing on the most axial side may be larger than the other inter-line gaps 43.
- the torsion spring 1 of the embodiment was used in the throttle valve device 2 that increases or decreases the opening degree of the intake passage of the internal combustion engine.
- the torsion spring 1 is a throttle valve that increases or decreases the opening degree of the exhaust path of the internal combustion engine. It may be used for the device 2.
- the exhaust path includes a reflux path for returning the exhaust gas to the intake path.
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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- Combustion & Propulsion (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
- Springs (AREA)
Abstract
Description
実施例1の捩りばね1の構成を図1~図5に基づき説明する。
実施例2の捩りばね1を、図7および図8に基づき説明する。なお、図7および図8の中間フック35は、外周側に折り曲げられる前の状態で描かれている。
実施例3の捩りばね1を、図9に基づき説明する。なお、図9の中間フック35は、外周側に折り曲げられる前の状態で描かれている。
実施例4の捩りばね1の特徴を、図10および図11に基づき説明する。なお、図10および図11の中間フック35は、外周側に折り曲げられる前の状態で描かれている。
実施例5の捩りばね1を、図12に基づき説明する。
実施例6の捩りばね1を、図13に基づき説明する。
本開示は、その要旨を逸脱しない範囲で様々な変形例を加えて実施できる。
Claims (13)
- 捩り式の2つのコイルばね(33、34)が、捩り方向が互いに逆となるように接続したものであって前記2つのコイルばねの間にフック(35)を有し、内燃機関の吸気路または排気路の開度を増減する絞り弁装置(2)に用いられ、
この絞り弁装置は、前記吸気路内または前記排気路内に回転自在に収容されて前記吸気路または前記排気路の開度を増減する弁体(5)を備え、
前記2つのコイルばねの内、軸方向一方側に配置される一方側ばね(33)によって前記弁体を閉側に付勢するように、かつ、軸方向他方側に配置される他方側ばね(34)によって前記弁体を開側に付勢するように組み付けられる捩りばね(1)において、
前記2つのコイルばねの内の少なくとも一方のコイルばねでは、この一方のコイルばねと前記フックとの接続部位における線間隙間(42a、43a)の大きさ(fa、ga)が、前記一方のコイルばねの線間隙間の平均値(fav、gav)よりも大きい捩りばね。 - 請求項1に記載の捩りばねにおいて、
前記一方のコイルばねは、他方のコイルばねよりも巻き数が少ない捩りばね。 - 請求項1または請求項2に記載の捩りばねにおいて、
前記一方のコイルばねは、他方のコイルばねよりも内径が小さい捩りばね。 - 請求項1または請求項2に記載の捩りばねにおいて、
前記一方のコイルばねは、他方のコイルばねよりも内径が大きい捩りばね。 - 請求項1ないし請求項4の内のいずれか1つに記載の捩りばねにおいて、
前記2つのコイルばねは、両方とも、各々のコイルばねと前記フックとの接続部位における線間隙間の大きさが、各々のコイルばねの線間隙間の平均値よりも大きい捩りばね。 - 請求項1ないし請求項5の内のいずれか1つに記載の捩りばねにおいて、
前記絞り弁装置は、
前記一方側ばねの内周に配置されて前記一方側ばねの内周の当接を外周面で受ける一方側ブッシュ(39)と、
前記他方側ばねの内周に配置されて前記他方側ばねの内周の当接を外周面で受け、前記一方側ブッシュとの間に軸方向の隙間を形成する他方側ブッシュ(40)とを備え、
前記捩りばねを前記一方側ブッシュおよび前記他方側ブッシュに組み付けた状態において、前記一方側ばねを構成する複数のターン(45)の内、最も軸方向他方側に位置する1周目のターン(451)と、前記他方側ばねを構成する複数のターン(46)の内、最も軸方向一方側に位置する1周目のターン(461)との間に形成される軸方向の隙間をばね間隙間(C)と定義し、
さらに、前記一方側ブッシュと前記他方側ブッシュとの間に形成される軸方向の隙間をブッシュ間隙間(B)と定義すると、
前記ばね間隙間は、前記一方側ばねにおいて1周目のターンに沿って2周目のターン(452)に向かい周回していくと、所定の周回位置(θc)までは前記ブッシュ間隙間よりも小さく、前記所定の周回位置を越えると前記ブッシュ間隙間よりも大きくなる捩りばね。 - 請求項6に記載の捩りばねにおいて、
前記ばね間隙間は、前記所定の周回位置で階段状に拡大する捩りばね。 - 請求項6または請求項7に記載の捩りばねにおいて、前記フックは、内周側に突き出ている捩りばね。
- 請求項1ないし請求項5の内のいずれか1つに記載の捩りばねにおいて、
前記フックは、素線の屈曲により軸方向にフック隙間(A)を形成し、前記フックの軸方向一端は前記一方側ばねの軸方向他端に接続するとともに、前記フックの軸方向他端は前記他方側ばねの軸方向一端に接続し、
前記絞り弁装置は、
前記一方側ばねの内周に配置されて前記一方側ばねの内周の当接を外周面で受ける一方側ブッシュと、
前記他方側ばねの内周に配置されて前記他方側ばねの内周の当接を外周面で受け、前記一方側ブッシュとの間に軸方向の隙間を形成する他方側ブッシュとを備え、
前記捩りばねを前記一方側ブッシュおよび前記他方側ブッシュに組み付けた状態において、前記一方側ばねを構成する複数のターンの内、最も軸方向他方側に位置する1周目のターンと、前記他方側ばねを構成する複数のターンの内、最も軸方向一方側に位置する1周目のターンとの間に形成される軸方向の隙間をばね間隙間(C)と定義し、
前記一方側ブッシュと前記他方側ブッシュとの間に形成される軸方向の隙間をブッシュ間隙間(B)と定義すると、
前記フック隙間は、先端から前記一方側ばねの軸方向他端に近付いていくと、所定の位置までは前記ブッシュ間隙間よりも小さく、前記所定の位置を越えると前記ブッシュ間隙間よりも大きくなり、
前記ばね間隙間は前記ブッシュ間隙間よりも大きい捩りばね。 - 請求項9に記載の捩りばねにおいて、
前記フック隙間は、前記所定の位置で階段状に拡大する捩りばね。 - 捩り方向が互いに逆となるように接続された捩り式の2つのコイルばね(33、34)と、
前記2つのコイルばねの間に設けられたフック(35)を備え、内燃機関の吸気路内に回転自在に収容されて前記吸気路の開度を増減する弁体(5)を有する絞り弁装置(2)に用いられる捩りばねであって、
前記2つのコイルばねの内、軸方向一方側に配置される一方側ばね(33)が前記弁体を閉側に付勢し、かつ、軸方向他方側に配置される他方側ばね(34)が前記弁体を開側に付勢し、
前記一方側ばねは、複数の線間隙間(42)を有し、
前記他方側ばねは、複数の線間隙間(43)を有し、
前記一方側ばねの複数の線間隙間の中で、最も軸方向他方側に存在する線間隙間(42a)は、他の線間隙間よりも大きい捩りばね。 - 捩り方向が互いに逆となるように接続された捩り式の2つのコイルばね(33、34)と、
前記2つのコイルばねの間に設けられたフック(35)を備え、内燃機関の吸気路内に回転自在に収容されて前記吸気路の開度を増減する弁体(5)を有する絞り弁装置(2)に用いられる捩りばねであって、
前記2つのコイルばねの内、軸方向一方側に配置される一方側ばね(33)が前記弁体を閉側に付勢し、かつ、軸方向他方側に配置される他方側ばね(34)によって前記弁体を開側に付勢し、
前記一方側ばねは、複数の線間隙間(42)を有し、
前記他方側ばねは、複数の線間隙間(43)を有し、
前記他方側ばねの複数の線間隙間の中で、最も軸方向一方側に存在する線間隙間(43a)は、他の線間隙間よりも大きい捩りばね。 - 請求項11に記載の捩りばねにおいて、
前記他方側ばねの複数の線間隙間の中で、最も軸方向一方側に存在する線間隙間(43a)は、他の線間隙間よりも大きい捩りばね。
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN109990027A (zh) * | 2019-04-08 | 2019-07-09 | 何至豪 | 一种自悬挂型夹子及其扭簧 |
JP2020148665A (ja) * | 2019-03-14 | 2020-09-17 | アイシン精機株式会社 | 回転角検出装置 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010156347A (ja) * | 2010-04-02 | 2010-07-15 | Mitsubishi Electric Corp | エンジン用吸気量制御装置 |
JP2011058408A (ja) * | 2009-09-09 | 2011-03-24 | Aisan Industry Co Ltd | 電子制御式スロットル制御装置 |
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Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2011058408A (ja) * | 2009-09-09 | 2011-03-24 | Aisan Industry Co Ltd | 電子制御式スロットル制御装置 |
JP2010156347A (ja) * | 2010-04-02 | 2010-07-15 | Mitsubishi Electric Corp | エンジン用吸気量制御装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020148665A (ja) * | 2019-03-14 | 2020-09-17 | アイシン精機株式会社 | 回転角検出装置 |
JP7205319B2 (ja) | 2019-03-14 | 2023-01-17 | 株式会社アイシン | 回転角検出装置 |
CN109990027A (zh) * | 2019-04-08 | 2019-07-09 | 何至豪 | 一种自悬挂型夹子及其扭簧 |
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