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WO2017043412A1 - Auto-tendeur hydraulique - Google Patents

Auto-tendeur hydraulique Download PDF

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Publication number
WO2017043412A1
WO2017043412A1 PCT/JP2016/075672 JP2016075672W WO2017043412A1 WO 2017043412 A1 WO2017043412 A1 WO 2017043412A1 JP 2016075672 W JP2016075672 W JP 2016075672W WO 2017043412 A1 WO2017043412 A1 WO 2017043412A1
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WO
WIPO (PCT)
Prior art keywords
plunger
rod
tensioner
valve
pressure chamber
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2016/075672
Other languages
English (en)
Japanese (ja)
Inventor
武博 高野
唯久 田中
洋生 森本
阿部　克史
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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 NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2017043412A1 publication Critical patent/WO2017043412A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/10—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes or chains  by adjusting the axis of a pulley of an idle pulley

Definitions

  • This invention relates to a hydraulic auto tensioner used for tension adjustment of an auxiliary machine drive belt for driving auxiliary machines such as an alternator, a water pump, and an air conditioner compressor.
  • ISG integrated starter generator
  • FIG. 4A and FIG. 4B show a belt transmission device for engine E provided with an idle stop mechanism of ISG 51 that achieves both driving of auxiliary machine 50 during normal operation and restart from the engine stop state.
  • the crank pulley P 1 provided on the crank shaft 52 of the engine E
  • the ISG pulley P 2 provided on the rotation shaft of the ISG 51
  • the rotation shaft of the auxiliary machine 50 such as a water pump
  • auxiliary spanned the accessory drive belt 53 between the pulleys P 3, (hereinafter, appropriately, simply. referred tensioner) hydraulic auto-tensioner a of this accessory drive belt 53 a tension pulley 54 provided on Press to adjust the belt tension.
  • the tension pulley 54 loosening tends to occur in the accessory drive belt 53, with the sign 53a between the belt advancing direction (crank pulley P 1 and ISG pulley P 2 crank pulley P 1 Provided).
  • the tension pulley 54 is rotatably supported by a pulley arm 55.
  • the pulley arm 55 is swingable by a tensioner A, and tension is applied to the accessory drive belt 53 via the tension pulley 54 by the urging force of the tensioner A.
  • the tension change of the accessory drive belt 53 during the driving of the belt transmission is absorbed.
  • the tensioner has a cylinder having a closed end formed on the inner bottom surface.
  • a sleeve fitting hole is formed in the inner bottom surface, and the sleeve is erected from the sleeve fitting hole.
  • a lower portion of the rod is slidably inserted into the sleeve, and a pressure chamber is formed between the sleeve and the lower end portion of the rod.
  • a spring seat is fixed to the upper end portion of the rod, and a return spring is provided between the spring seat and the inner bottom surface of the cylinder so as to urge the cylinder and the rod in the extending direction. .
  • a connecting piece connected to the pulley arm is provided at the upper end of the spring seat.
  • the spring seat is provided with a spring cover that covers the upper part of the return spring and a dust cover that covers the outer periphery of the upper part of the cylinder.
  • the outer periphery of the spring cover is covered with a cylindrical body.
  • An oil seal as a seal member is installed in the upper end opening of the cylinder. The inner periphery of the oil seal makes elastic contact with the outer peripheral surface of the cylinder, closes the upper opening of the cylinder, and fills the cylinder. This prevents the hydraulic fluid from leaking to the outside.
  • a sealed reservoir chamber is formed between the cylinder and the sleeve.
  • the reservoir chamber and the pressure chamber communicate with each other through a passage.
  • a check valve is provided at the end of the passage on the pressure chamber side. The check valve closes the passage when the pressure in the pressure chamber becomes higher than the pressure in the reservoir chamber.
  • the rod moves relative to the direction in which the rod is pushed into the cylinder against the biasing force of the return spring, and the tension of the accessory drive belt is reduced.
  • the pressure in the pressure chamber becomes larger than the pressure in the reservoir chamber, so the check valve closes the passage.
  • the hydraulic oil in the pressure chamber flows into the reservoir chamber through a minute gap formed between the inner diameter surface of the sleeve and the outer diameter surface of the rod.
  • a damper force (hydraulic damping force) is exerted by the flow resistance when the hydraulic oil flows through a minute gap. This damper force cushions the pushing force applied to the tensioner, while the pushing force and the biasing force of the return spring are reduced.
  • the rod is pushed into the cylinder to the balanced position.
  • the damper force of the tensioner is determined by the size of the minute gap.
  • the tension pulley 54 is provided in the belt traveling direction of the crank pulley P 1 is a drive source (between the crank pulley P 1 and ISG pulley P 2), usually The looseness of the accessory drive belt 53 during operation can be appropriately eliminated.
  • the mounting position of the tension pulley 54 is the opposite side of the belt traveling direction ISG pulley P 2 which is a driving source, the accessory drive belt 53 High tension is likely to occur.
  • the damper force of the tensioner A is increased in order to eliminate loosening of the auxiliary machine drive belt 53 at the time of ISG restart, the auxiliary machine drive belt 53 becomes over-tensioned during normal running, and each pulley P 1 , P 2 , P
  • the bearing that rotatably supports the bearing 3 is liable to be damaged, and the rotation resistance of the crankshaft 52 becomes a problem that the fuel consumption is reduced.
  • the common tensioner A compensates for both normal running and ISG start. It is considered difficult to properly adjust the belt tension of the machine drive belt 53.
  • an object of the present invention is to always adjust the belt tension of the accessory drive belt to an appropriate magnitude both during normal operation and when the engine is restarted by ISG.
  • a cylinder having a closed end at the bottom and filled with hydraulic oil therein, a cylindrical valve sleeve erected from the bottom of the cylinder, and the valve
  • a cylindrical plunger that is slidably inserted in the axial direction of the sleeve, a rod that is slidably inserted in the axial direction of the plunger, and the valve sleeve and the rod are attached in opposite directions.
  • a return spring that biases, a valve spring that biases the rod and the plunger in opposite directions, a pressure chamber formed between the valve sleeve, the plunger, and the rod; the cylinder and the valve sleeve; Between the reservoir chamber formed between the pressure chamber and the reservoir chamber, and the pressure of the hydraulic oil in the pressure chamber is A first check valve that closes the oil passage when the pressure of the hydraulic oil in the reservoir chamber is higher, a first constriction path formed between the rod and the plunger, and between the valve sleeve and the plunger. A second constriction path having a larger flow resistance than the first constriction path, and the first constriction path against the urging force of the valve spring as the pressure of the hydraulic oil in the pressure chamber increases.
  • a hydraulic auto-tensioner provided with a valve seat formed at the lower end of the rod and a second check valve formed by a seat surface formed at the lower end of the plunger.
  • the belt tension of the accessory drive belt can be adjusted to an appropriate size at all times during normal operation and when the engine is restarted by ISG.
  • the tension pulley is arranged on the opposite side of the belt traveling direction of the ISG pulley that is the drive source.
  • the tension of the machine drive belt increases rapidly.
  • the first check valve closes and the plunger rises against the urging force of the valve spring by the pressure of the hydraulic oil in the pressure chamber, and the second check valve causes the first constriction path to rise. Is closed.
  • the hydraulic oil in the pressure chamber flows into the reservoir chamber through the second constriction path.
  • the rod and plunger can be used even when the dimensional error between the rod and plunger is large or when a moment load is applied to the auto tensioner. And the second check valve can be reliably closed. For this reason, sufficient tension of the accessory drive belt can be ensured, and engine restart failure due to ISG can be reliably prevented. Further, since the second check valve is housed inside the plunger, the second check valve can be reduced in size and weight.
  • the rod may further include a limiting member on the outer peripheral surface of the rod for limiting the movable range in the axial direction of the plunger with respect to the rod within a predetermined range.
  • a limiting member on the outer peripheral surface of the rod for limiting the movable range in the axial direction of the plunger with respect to the rod within a predetermined range.
  • either the valve seat or the seat surface may be formed in a convex shape.
  • a contact area becomes small compared with the case where this valve seat and a sheet
  • the valve seat and the seat surface can be maintained in an annular shape. For this reason, it is possible to prevent the hydraulic oil from leaking from the second check valve (first constricted path), and it is possible to more reliably prevent engine restart failure due to ISG.
  • a cylinder having a closed end at the bottom and filled with hydraulic oil therein, a cylindrical valve sleeve erected from the bottom of the cylinder, and the valve sleeve are slid in the axial direction.
  • a cylindrical plunger that is movably inserted, a rod that is slidably inserted in the plunger in the axial direction thereof, a return spring that biases the valve sleeve and the rod in opposite directions, and the rod
  • a valve spring for urging the plunger in opposite directions, a pressure chamber formed between the valve sleeve, the plunger and the rod, and a reservoir chamber formed between the cylinder and the valve sleeve And an oil passage communicating the pressure chamber and the reservoir chamber, and the pressure of the hydraulic oil in the pressure chamber is the pressure of the hydraulic oil in the reservoir chamber
  • a first check valve that closes the oil passage when it is higher, a first constriction path formed between the rod and the plunger, and formed between the valve sleeve and the
  • the tensioner By configuring the tensioner in this way, the tension of the accessory drive belt can be adjusted to an appropriate magnitude at all times during normal operation and when the engine is restarted by ISG.
  • the durability and fuel efficiency of the bearing that is rotatably supported can be improved, and reliable restartability can be ensured when the engine is restarted.
  • the second check valve that controls the flow of hydraulic oil in the first constriction path is configured at the lower end of the rod by inserting the rod into the plunger. Even when a load is applied, the coaxiality between the rod and the plunger can be secured, and the second check valve can be reliably closed. For this reason, sufficient tension of the accessory drive belt can be ensured, and engine restart failure due to ISG can be reliably prevented. Further, since the second check valve is housed inside the plunger, the second check valve can be reduced in size and weight.
  • Partial longitudinal sectional view showing an embodiment of a hydraulic auto tensioner according to the present invention It is a longitudinal cross-sectional view of the principal part of the hydraulic auto tensioner shown in FIG. 1, and shows a state in which the second check valve is opened. It is a longitudinal cross-sectional view of the principal part of the hydraulic auto tensioner shown in FIG. 1, and shows a state in which the second check valve is closed.
  • the figure which shows the comparison of the reaction force characteristic of the hydraulic auto tensioner (implemented product) according to the present invention and the conventional hydraulic auto tensioner (conventional product) It is a front view which shows the belt transmission device of the engine by which the idle stop mechanism is mounted, Comprising: The normal driving state of an engine is shown It is a front view which shows the belt transmission apparatus of the engine by which the idle stop mechanism is mounted, Comprising: The state at the time of the engine restart by ISG is shown
  • FIG. 1 shows an embodiment of a hydraulic auto tensioner according to the present invention (hereinafter simply referred to as a tensioner as appropriate).
  • the cylinder 10 has a closed end at the bottom, and a connecting piece 11 connected to a pulley arm 55 (see FIGS. 4A and 4B) is provided on the lower surface side of the bottom.
  • the connecting piece 11 is formed with a shaft insertion hole 11a penetrating from one side surface to the other side surface.
  • a cylindrical fulcrum shaft 11b and a slide bearing 11c that rotatably supports the fulcrum shaft 11b are incorporated in the shaft insertion hole 11a.
  • the pulley arm 55 is swingably attached to the connecting piece 11 by a bolt (not shown) inserted through the fulcrum shaft 11b.
  • a valve sleeve fitting hole 12 is formed at the bottom of the cylinder 10, and a steel valve sleeve 13 is erected in the valve sleeve fitting hole 12.
  • a bottomed cylindrical plunger 14 is inserted into the valve sleeve 13 so as to be slidable in the axial direction with respect to the valve sleeve 13. The plunger 14 slides along a small-diameter inner diameter surface 13 a formed on the inner peripheral upper portion of the valve sleeve 13.
  • a radially outward flange 14 a is formed at the upper end of the plunger 14, an annular recess 14 b is formed at the inner peripheral surface, and a tapered groove 14 c having a larger outer diameter is formed at the lower portion of the outer peripheral portion.
  • Each of the through holes 14d is formed.
  • a taper groove 14c formed in the plunger 14 is provided with a retaining ring 15 having a cut in a part in the circumferential direction.
  • the retaining ring 15 has a natural outer diameter larger than the outer diameter of the plunger 14.
  • a rod 16 is inserted into the plunger 14 so as to be slidable in the axial direction with the plunger 14.
  • the lower end of the rod 16 is formed in a convex shape (hemispherical shape).
  • a taper groove 16a having an outer diameter larger toward the lower side is formed on the upper outer periphery of the rod 16.
  • the taper groove 16a is provided with a retaining ring 17 having a cut in a part in the circumferential direction.
  • the retaining ring 17 has an outer diameter in a natural state larger than the outer diameter of the rod 16.
  • a spring seat 18 is provided on the upper end of the rod 16 located outside the cylinder 10.
  • a return spring 19 that urges the valve sleeve 13 (cylinder 10) and the rod 16 (spring seat 18) in opposite directions is incorporated between the spring seat 18 and the inner bottom surface of the cylinder 10.
  • a connecting piece 20 connected to the engine E (see FIGS. 4A and 4B) is provided at the upper end of the spring seat 18.
  • the connecting piece 20 is formed with a sleeve insertion hole 20a penetrating from one side surface to the other side surface.
  • a sleeve 20b and a slide bearing 20c that rotatably supports the sleeve 20b are incorporated in the sleeve insertion hole 20a.
  • the connecting piece 20 is swingably attached to the engine E by a bolt (not shown) inserted through the sleeve 20b.
  • the spring seat 18 is formed of a molded product, and a cylindrical dust cover 21 that covers the upper outer periphery of the cylinder 10 and a cylindrical spring cover 22 that covers the upper part of the return spring 19 are integrally formed at the time of molding.
  • a cylindrical dust cover 21 that covers the upper outer periphery of the cylinder 10
  • a cylindrical spring cover 22 that covers the upper part of the return spring 19 are integrally formed at the time of molding.
  • an aluminum die-cast molded product or a resin molded product such as a thermosetting resin can be adopted.
  • the entire outer circumference of the spring cover 22 is covered with a cylindrical body 23 that is insert-molded when the spring seat 18 is molded.
  • a press-formed product of a steel plate can be adopted.
  • a valve spring 24 is incorporated between the opposed surfaces of the flange 14 a formed on the plunger 14 and the spring seat 18.
  • the valve spring 24 urges the plunger 14 downward with respect to the rod 16.
  • the retaining ring 17 provided on the rod 16 engages with the upper end portion of the annular recess 14b formed on the plunger 14 so that the movable range in the axial direction of the plunger 14 with respect to the rod 16 is within a predetermined range. Acts as a limiting member to limit. In this way, by restricting the movable range of the plunger 14 by the retaining ring 17, the plunger 14 can be prevented from coming off from the rod 16.
  • a pressure chamber 25 is formed between the valve sleeve 13 and the plunger 14 and the lower end of the rod 16.
  • the capacity of the pressure chamber 25 changes when the auto tensioner extends and contracts and at least one of the plunger 14 or the rod 16 moves relative to the valve sleeve 13 in the axial direction.
  • an oil seal (hereinafter denoted by the same reference numeral as the seal member 26) as a seal member 26 is incorporated.
  • the inner periphery of the oil seal 26 is in elastic contact with the outer peripheral surface of the cylinder 23 to close the upper opening of the cylinder 10 to prevent leakage of hydraulic oil filled in the cylinder 10 to the outside, and Prevents dust from entering the interior.
  • a sealed reservoir chamber 27 is formed between the cylinder 10 and the valve sleeve 13.
  • the reservoir chamber 27 and the pressure chamber 25 include an oil passage 28 formed between the fitting surfaces of the valve sleeve fitting hole 12 and the valve sleeve 13, and a circular recess formed in the center of the bottom surface of the valve sleeve fitting hole 12. It communicates via the oil sump 29 which consists of.
  • the first check valve 30 is incorporated at the lower end of the valve sleeve 13.
  • the first check valve 30 includes a steel check ball 30c that opens and closes the valve hole 30b of the valve seat 30a press-fitted into the lower end portion of the valve sleeve 13 from the pressure chamber 25 side, and the check ball 30c faces the valve hole 30b.
  • a cylindrical first constriction path 31 is formed between the sliding surfaces of the rod 16 and the plunger 14.
  • a cylindrical second constriction path 32 is formed between the sliding surfaces of the plunger 14 and the valve sleeve 13.
  • the gap amount of the second constriction path 32 is smaller than the gap amount of the first constriction path 31, and the flow resistance of the second constriction path 32 is larger than the flow resistance of the first constriction path 31 due to the difference in the gap amount. ing.
  • a damper action is exerted by the flow resistance when hydraulic oil flows from the pressure chamber 25 to the reservoir chamber 27 through the first constriction path 31 or the second constriction path 32.
  • the retaining ring 17 provided on the rod 16 is formed with a cut in a part in the circumferential direction, and the first narrow path 31 and the reservoir chamber 27 are in communication with each other by the cut.
  • the gap amount of the first constricted path 31 is set such that a damper force capable of absorbing the tension fluctuation of the auxiliary machine drive belt 53 is exhibited during the normal operation of the engine E shown in FIG. 4A.
  • the gap amount of the second constriction path 32 is such that a damper force capable of preventing the rod 16 from being pushed suddenly into the valve sleeve 13 when the engine E is restarted by the ISG 51 shown in FIG. 4B is exhibited.
  • a second check valve 35 that closes the first constricted passage 31 when the pressure rises when the engine is restarted.
  • the convex surface portion formed at the lower end portion of the rod 16 functions as a valve seat 35a, and the inner edge portion of the through hole 14d formed in the plunger 14 functions as a seat surface 35b.
  • the contact area becomes smaller than when the valve seat 35a and the seat surface 35b are in surface contact, and a large contact pressure is secured. can do.
  • the valve seat 35a and the seat surface 35b can be maintained in an annular contact. For this reason, it is possible to prevent the hydraulic oil from leaking from the second check valve 35 (first constricted path 31). For this reason, the engine restart failure by ISG51 can be prevented more reliably.
  • the valve seat 35a at the lower end of the rod 16 is convex, but the seat surface 35b at the inner edge of the through hole may be convex.
  • the retaining ring 15 provided on the plunger 14 comes into contact with the step 13b at the lower end of the small-diameter inner diameter surface 13a of the valve sleeve 13. By this contact, the plunger 14 can be prevented from coming off from the upper end of the valve sleeve 13.
  • FIG. 4A the belt drive system shown in FIG. 4B, the tension pulley 54, loosening tends to occur in the accessory drive belt 53, the crank pulley P 1 of belt travel direction (between the crank pulley P 1 and ISG pulley P 2 Between).
  • a pulley arm 55 for swingably supporting the tension pulley 54 is attached to the connecting piece 11 on the bottom side of the cylinder 10 of the tensioner, and the engine E is attached to the connecting piece 20 on the upper end side of the spring seat 18 of the tensioner.
  • the hydraulic oil in the pressure chamber 25 is compared with the case of flowing through the first constriction path 31. It flows slowly through the second constriction path 32. Therefore, without causing sudden pressure drop in the pressure chamber 25, sufficient damping action for maintaining the belt tension at the time of the engine E is restarted is exhibited, the accessory drive belt 53 and P 3 from the pulley P 1 It is possible to prevent slipping between the two.
  • the hydraulic oil in the pressure chamber 25 is caused to flow from the first constricted passage 31 having a small flow resistance to the reservoir chamber 27, and when the engine E is restarted, the operation in the pressure chamber 25 is performed. Since oil can flow from the second constriction path 32 having a large flow resistance to the reservoir chamber 27, an appropriate tension can be applied to the accessory drive belt 53 during normal operation and restart of the engine E. it can.
  • the rod 16 is inserted into the plunger 14 and the second check valve 35 is configured at the lower end of the rod 16, the dimensional error between the rod 16 and the plunger 14 is large, or the moment load is applied to the auto tensioner.
  • the coaxiality between the rod 16 and the plunger 14 can be secured, and the second check valve 35 can be reliably closed. For this reason, sufficient tension of the auxiliary machine drive belt 53 can be secured, and the engine restart failure due to the ISG 51 can be surely prevented. Further, since the second check valve 35 is housed inside the plunger 14, the second check valve 35 can be reduced in size and weight.
  • FIG. 3 shows a comparison between the reaction force characteristics of a tensioner according to this embodiment (hereinafter referred to as “implemented product”) and the reaction force characteristics of a conventional tensioner (hereinafter referred to as “conventional product”).
  • this tensioner As the implemented product, the tensioner described in the above embodiment was used. As shown in FIG. 1 and the like, this tensioner has a cylindrical cylinder 10 having a closed end at the bottom, a valve sleeve 13 erected from the bottom of the cylinder 10, and a valve sleeve 13 that slides in the axial direction thereof.
  • a cylindrical plunger 14 that is freely inserted; a rod 16 that is slidably inserted in the axial direction of the plunger 14; a return spring 19 that urges the valve sleeve 13 and the rod 16 in opposite directions;
  • a valve spring 24 for urging the rod 16 and the plunger 14 in opposite directions, a pressure chamber 25 formed between the valve sleeve 13, the plunger 14 and the rod 16, and a cylinder 10 and the valve sleeve 13 are formed.
  • the first check valve 30 that closes the oil passage 28 when the pressure of the hydraulic oil in the server chamber 27 is higher, the first constriction path 31 formed between the rod 16 and the plunger 14, the valve sleeve 13 and the plunger 14, the second constriction path 32 having a larger flow resistance than the first constriction path 31, and the urging force of the valve spring 24 as the pressure of the hydraulic oil in the pressure chamber 25 increases.
  • a second check valve 35 comprising a valve seat 35 a formed at the lower end of the rod 16 and a seat surface 35 b formed at the lower end of the plunger 14, which closes the first constricted path 31.
  • a tensioner (a tensioner having no member corresponding to the plunger 14 of the practical product.
  • the displacement of the spring seat 18 is changed so that the time change of the position of the spring seat 18 becomes a sine wave regardless of how the force (tensioner reaction force) acting on the spring seat 18 increases or decreases.
  • the control method was adopted.
  • the vibration amplitude was set to ⁇ 0.5 mm, which is larger than the general vibration amplitude (for example, about ⁇ 0.1 mm to ⁇ 0.2 mm) applied to the tensioner during normal operation of the engine E.
  • a return spring 19 having a spring constant of about 35 N / mm was used.
  • FIG. 3 shows the relationship between the tensioner displacement (downward displacement of the spring seat 18) and the tensioner reaction force (upward force acting on the spring seat 18) obtained by the above vibration test.
  • the tensioner reaction force changes in three steps: sudden, slow, and abrupt as the tensioner contracts.
  • the tensioner reaction force of the product is almost increased with the first stroke (points P1 to P2) that starts relatively rapidly from the minimum value of the tensioner reaction force (point P1).
  • the maximum value of the tensioner reaction force after passing through the second stroke (points P2 to P3) that maintains a substantially constant size without increasing and the third stroke (points P3 to P4) that increases relatively rapidly. It changes to (point P4).
  • the tensioner reaction force changes in four stages: sudden, slow, sudden and slow.
  • the tensioner reaction force of the product is almost reduced with the first stroke (points P4 to P5) where the maximum value of the tensioner reaction force (point P4) starts as a starting point.
  • the second stroke points P5 to P6 that maintains a substantially constant size without any reduction
  • the third stroke points P6 to P7 that decreases relatively abruptly.
  • the tensioner reaction force changes to the minimum value (point P1).
  • the tensioner reaction force generally increases monotonously from the minimum value (point Q1) to the maximum value (point Q2) during the process of contraction of the tensioner. Further, during the process of extending the tensioner, the tensioner reaction force changes in two steps of sudden and slow. In other words, in the process of tensioner extension, the tensioner reaction force of the conventional product is almost reduced with the first stroke (points Q2 to Q3) that decreases relatively rapidly starting from the maximum value of the tensioner reaction force (point Q2). Without going through the second stroke (points Q3 to Q1) maintaining a substantially constant magnitude, the tensioner reaction force changes to the minimum value (point Q1).
  • the reaction force characteristic is shown.
  • the tensioner of the practical product has a change point P5 where the rate of decrease of the tensioner reaction force changes from abrupt to moderate during the extension of the tensioner, a change point P6 where the rate of increase of the tensioner reaction force changes suddenly and suddenly, and the tensioner.
  • the reaction force characteristic which has the change point P7 in which the decreasing rate of reaction force changes from sudden to moderate is shown.
  • the plunger 14 rises to change the volume of the pressure chamber 25.
  • the tensioner reaction force becomes substantially constant (points P2 to P3 in FIG. 3).
  • the implemented product has a change point P2 at which the rate of increase in the tensioner reaction force changes from sudden to moderate, and a change point P3 at which the rate of increase in the tensioner reaction force changes from slow to sudden. Shows force characteristics.
  • the tensioner reaction force reaches a predetermined value (value at the point P5 in FIG. 3) in the process of extending the tensioner, the plunger 14 descends to absorb the change in the volume of the pressure chamber 25, The tensioner reaction force becomes substantially constant (points P5 to P6 in FIG. 3).
  • the implemented product has a change point P5 in which the rate of decrease in the tensioner reaction force changes from abrupt to moderate and a change point P6 in which the rate of increase in the tensioner reaction force changes from moderate to abrupt. Shows force characteristics.
  • the tension pulley 54 shown in FIG. 4A is applied to the accessory drive belt 53 while suppressing the magnitude of the tensioner reaction force during normal operation of the engine E. Tension can be kept small. On the other hand, at the time of restart of the engine E by ISG51, large tensioners to generate a reaction force, it is possible to reliably prevent slippage between the accessory drive belt 53 and the ISG pulley P 2 shown in Figure 4B.
  • the tensioner has an amplitude smaller than ⁇ 0.5 mm (for example, about ⁇ 0.1 mm to ⁇ 0.2 mm) obtained in the above vibration test. Displacement).
  • the tensioner reaction force increases from the point P1 to the value between the points P2 and P3 in the process where the tensioner contracts, and then increases to the value between the points P2 and P3, and then in the process where the tensioner extends. Starting from the value between point P3 and point P3, it decreases to a value between point P5 and point P6, and further passes through point P6 and point P7 in order and decreases to point P1.
  • the maximum value of the tensioner reaction force can be suppressed to a value between the points P2 and P3 during the normal operation of the engine E, and the tension pulley 54 shown in FIG.
  • the tension applied to the machine drive belt 53 can be kept small, and the fuel consumption of the engine E can be reduced.
  • the tensioner contracts to the maximum value of the amplitude of ⁇ 0.5 mm performed in the above vibration test or the vicinity thereof, as indicated by reference numeral S2 in FIG. .
  • the tensioner reaction force increases to the point P4 or the vicinity thereof.
  • the area tensioner displacement is large, large tensioner reaction force can be generated, ensuring a slippage between the belt 54 and the ISG pulley P 2 shown in FIG. 4B Can be prevented.
  • the tension of the auxiliary drive belt 53 tends to be excessive during the normal operation of the engine E. That is, when the tensioner is displaced with the amplitude indicated by S1 in FIG. 3, in the process in which the tensioner contracts, the tensioner reaction force increases from the point Q1 to a value between the points Q1 and Q2, and then In the process in which the tensioner contracts, the value between the point Q1 and the point Q2 is set as a starting point, the value is decreased to a value between the point Q3 and the point Q1, and further decreased to the point Q1. In this way, when the conventional tensioner is used, the maximum value of the tensioner reaction force increases to a value between the points Q1 and Q2 during normal operation. Therefore, the tension pulley 54 shown in FIG. The tension applied to the engine is likely to be excessive, and it is difficult to reduce the fuel consumption of the engine E.
  • the tensioner according to the above embodiment is merely an example, and the belt tension of the accessory drive belt 53 is always adjusted to an appropriate magnitude both during normal operation and when the engine is restarted by ISG.
  • the shape and arrangement of each member, particularly the valve seat 35a (the lower end portion of the rod 16) and the seat surface 35b (the inner edge of the through hole 14d formed in the plunger 14) constituting the second check valve 35. Part) can be changed as appropriate.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

La présente invention concerne un auto-tendeur hydraulique, comportant un cylindre (10), un manchon de vanne (13) disposé verticalement à l'intérieur du cylindre (10), un plongeur (14) inséré de manière à pouvoir coulisser à travers le manchon de vanne (13), une tige (16) insérée de manière à pouvoir coulisser à travers le plongeur (14), une chambre de pression (25) formée entre le manchon de vanne (13) et le plongeur (14) et la tige (16), et une chambre de réservoir (27) formée entre le cylindre (10) et le manchon de vanne (13). Pendant le fonctionnement normal d'un moteur (E), l'huile de travail s'écoule à partir de la chambre de pression (25) jusqu'à la chambre de réservoir (27) à travers un premier passage de rétrécissement (31) entre la tige (16) et le plongeur (14) et, pendant le redémarrage par un démarreur-générateur intégré (51), l'huile de travail s'écoule à partir de la chambre de pression (25) jusqu'à la chambre de réservoir (27) à travers un second passage de rétrécissement (32) entre le manchon de vanne (13) et le plongeur (14).
PCT/JP2016/075672 2015-09-08 2016-09-01 Auto-tendeur hydraulique Ceased WO2017043412A1 (fr)

Applications Claiming Priority (2)

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JP2015176477A JP6664910B2 (ja) 2015-09-08 2015-09-08 油圧式オートテンショナ
JP2015-176477 2015-09-08

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WO2017043412A1 true WO2017043412A1 (fr) 2017-03-16

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JP (1) JP6664910B2 (fr)
WO (1) WO2017043412A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012251629A (ja) * 2011-06-06 2012-12-20 Ntn Corp 油圧式オートテンショナ
JP2015068352A (ja) * 2013-09-26 2015-04-13 Ntn株式会社 油圧式オートテンショナ
JP2015155718A (ja) * 2014-02-20 2015-08-27 Ntn株式会社 油圧式オートテンショナ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012251629A (ja) * 2011-06-06 2012-12-20 Ntn Corp 油圧式オートテンショナ
JP2015068352A (ja) * 2013-09-26 2015-04-13 Ntn株式会社 油圧式オートテンショナ
JP2015155718A (ja) * 2014-02-20 2015-08-27 Ntn株式会社 油圧式オートテンショナ

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JP6664910B2 (ja) 2020-03-13
JP2017053390A (ja) 2017-03-16

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