WO2022118831A1 - Unité de tendeur pour courroies de machine auxiliaire - Google Patents

Unité de tendeur pour courroies de machine auxiliaire Download PDF

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Publication number
WO2022118831A1
WO2022118831A1 PCT/JP2021/043796 JP2021043796W WO2022118831A1 WO 2022118831 A1 WO2022118831 A1 WO 2022118831A1 JP 2021043796 W JP2021043796 W JP 2021043796W WO 2022118831 A1 WO2022118831 A1 WO 2022118831A1
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WO
WIPO (PCT)
Prior art keywords
swing arm
hydraulic
chamber
reservoir chamber
sub
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PCT/JP2021/043796
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English (en)
Japanese (ja)
Inventor
唯久 田中
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Ntn株式会社
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Publication of WO2022118831A1 publication Critical patent/WO2022118831A1/fr

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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

  • the present invention mainly relates to a tensioner unit for an auxiliary belt used for maintaining tension of a belt for driving an engine auxiliary such as an alternator or a water pump.
  • Auxiliary equipment for automobiles such as alternators, car air conditioners, and water pumps, has a rotating shaft connected to the crankshaft of the engine by an auxiliary belt and is driven via the auxiliary belt.
  • a tensioner unit for the auxiliary belt is generally used.
  • the tensioner unit for the auxiliary belt there is a conventional one provided with a hydraulic damper (for example, Patent Documents 1 and 2).
  • a reservoir chamber is formed around the cylinder, a hydraulic chamber is formed between the cylinder and the rod, and a leak gap is formed between the inner circumference of the cylinder and the rod.
  • the cylinder is provided with a hydraulic damper having a structure provided with a check valve that allows the inflow of hydraulic oil from the reservoir chamber to the hydraulic chamber, and a coil spring for return is arranged around the cylinder.
  • the tensioner unit of Patent Document 2 has a swing arm that is swingably supported around the fulcrum axis and moves integrally with the swing arm around the fulcrum axis when the swing arm swings.
  • the tension pulley supported by the swing arm, the first and second pins arranged so that the swing arm does not move even if the swing arm swings, and the reaction force attached to the swing arm and received from the first pin.
  • a spring that pushes the first pin so as to urge the swing arm in one swing direction, and a spring that is attached to the swing arm so as to contact the second pin, and the swing direction of the swing arm. Is equipped with a hydraulic damper, which cushions the swing in the opposite direction.
  • the hydraulic damper is slidably inserted into the cylinder provided in the swing arm so as to move integrally with the swing arm around the fulcrum axis when the swing arm swings, and the cylinder. It has a piston that divides the inside into a hydraulic chamber and a reservoir chamber, and a damper rod whose one end is connected to the piston and whose other end abuts on the second pin.
  • the hydraulic damper and the spring are arranged on the same plane orthogonal to the fulcrum axis.
  • a sub-reservoir chamber located adjacent to the reservoir chamber in a direction orthogonal to the longitudinal direction of the cylinder is formed.
  • the hydraulic damper is located above the fulcrum axis.
  • the sub-reservoir chamber is adjacent to the hydraulic damper on the upper side and protrudes toward the upper side.
  • the hydraulic chamber and reservoir chamber are filled with hydraulic oil so that there is no air. Air and hydraulic oil are housed in two upper and lower layers in the sub-reservoir chamber. The pressure change in the cylinder due to the movement of the piston is absorbed by the air layer in the sub-reservoir chamber. Since the hydraulic damper and the spring are incorporated in the swing arm in this way, the tensioner unit for the auxiliary belt of Patent Document 2 is attached to the tensioner unit as compared with the tensioner unit for the auxiliary belt of Patent Document 1. It is possible to reduce the space.
  • the tensioner unit for the auxiliary belt of Patent Document 2 has a structure in which a hydraulic damper is incorporated around the fulcrum shaft of the swing arm and a rod is interposed between the piston and the second pin outside the hydraulic chamber of the hydraulic damper. Therefore, unlike Patent Document 1, it is not possible to provide a relief valve inside the rod, and there is room for improvement in that it is not possible to prevent the pressure in the hydraulic chamber from becoming too high when the tension fluctuation of the belt is large. ..
  • the problem to be solved by the present invention is to limit the pressure in the hydraulic chamber by the relief valve in the tensioner unit for the auxiliary belt in which the hydraulic damper and the spring are attached around the fulcrum shaft of the swing arm supporting the tension pulley. To be able to do it.
  • the present invention has a swing arm that is swingably supported around a fulcrum shaft, and the swing so as to swing integrally with the swing arm around the fulcrum shaft.
  • the tension pulley supported by the arm, the first pin and the second pin arranged so as not to move with respect to the swing arm swinging about the fulcrum axis, and the first pin attached to the swing arm and described above.
  • a hydraulic damper for cushioning the swing of the swing arm in a direction opposite to the swing direction of the one is provided, and the hydraulic damper moves integrally with the swing arm about the fulcrum axis. It has a cylinder provided on the swing arm, a piston that divides the inside of the cylinder into a hydraulic chamber and a reservoir chamber, and a rod connected to the piston so as to abut on the second pin.
  • a sub-reservoir that communicates with the reservoir chamber is formed inside the swing arm, the hydraulic chamber and the reservoir chamber are filled with hydraulic oil, and air and hydraulic oil are above and below the sub-reservoir chamber.
  • an oil passage communicating between the hydraulic chamber and the sub-reservoir chamber is provided in the swing arm, and the pressure of the hydraulic chamber presses the set pressure.
  • a relief valve that opens the oil passage and releases the pressure of the hydraulic chamber to the sub-reservoir chamber is attached to the swing arm.
  • the oil passage is provided in the swing arm, it is possible to realize an oil passage that serves as a bypass flow path that communicates from the hydraulic chamber to the sub-reservoir chamber. Since a relief valve is attached to the swing arm, the oil passage can be opened and closed by the relief valve. The relief valve opens an oil passage when the pressure in the hydraulic chamber exceeds the set pressure of the relief valve to release the pressure in the hydraulic chamber, so that the pressure in the hydraulic chamber can be limited.
  • the sub-reservoir chamber, the oil passage, and the relief valve are adjacent to one side in the axial direction with respect to the hydraulic damper.
  • a large space can be obtained for arranging the oil passage, and the sub-reservoir chamber, the oil passage, and the relief valve can be arranged on the same side in the axial direction with respect to the hydraulic damper to suppress the passage length of the oil passage.
  • the spring and the hydraulic damper are arranged on the same plane orthogonal to the fulcrum axis. By doing so, it is possible to avoid further arranging the springs on the same plane orthogonal to the fulcrum axis, and to obtain a larger space for arranging the auxiliary reservoir chamber, the oil passage, and the relief valve.
  • the sub-reservoir chamber has a fitting hole portion that supports the relief valve, and the oil passage communicates from the fitting hole portion to the hydraulic pressure chamber, and a bore plug that seals the sub-reservoir chamber. Is preferably attached to the swing arm. By doing so, it is possible to eliminate the leakage path that directly leads from the oil passage or the relief valve to the outside of the swing arm, and to seal the flow path from the hydraulic chamber to the sub-reservoir chamber simply by attaching the bore plug.
  • the swing arm has a plurality of crimping portions plastically deformed so as to prevent the bore plug from coming off. By doing so, it is possible to surely prevent the bore plug from falling off.
  • Examples of the relief valve include a valve body, a valve seat supported by the fitting hole portion, a valve spring that urges the valve body toward the valve seat, and a valve retainer that receives the valve spring. It is possible to adopt the one consisting of.
  • the sub-reservoir chamber communicates with a long hole portion extending upward from a portion located below the fulcrum shaft through the periphery of the fulcrum shaft and from the long hole portion to the reservoir chamber. It has a penetrating portion, and the air and the hydraulic oil are housed in the elongated hole portion, and the penetrating portion is opened to the elongated hole portion at a position below the air and the fulcrum axis. It is preferable to have.
  • the elongated hole portion of the auxiliary reservoir chamber extends upward from the portion located below the fulcrum axis of the swing arm through the circumference of the fulcrum axis, the circumference of the fulcrum axis can be reached. It can be utilized to store a large amount of hydraulic oil and raise the oil level in the elongated hole. Since the penetrating part that communicates from the long hole part to the reservoir chamber is open to the long hole part at a position below the air in the long hole part and the fulcrum axis, the height difference between the oil level and the penetrating part can be reduced. Can be made larger.
  • the present invention relieves the pressure of the hydraulic chamber in the tensioner unit for the auxiliary belt in which the hydraulic damper and the spring are attached around the fulcrum shaft of the swing arm supporting the tension pulley. It can be limited by a valve.
  • FIG. 1 A front view showing a tensioner unit for an auxiliary belt according to an embodiment of the present invention.
  • Sectional drawing along the VI-VI line of FIG. Sectional drawing taken along the line VII-VII of FIG. Partially enlarged view showing the state where the bore plug of FIG. 1 is removed. Partial enlarged view showing a modified example in which the bore plug of FIG. 1 is prevented from coming off.
  • FIG. 2 shows an example of a belt transmission device using the auxiliary belt tensioner unit 1 according to the embodiment of the present invention.
  • This belt transmission device includes a crank pulley 3 attached to a crankshaft 2, a belt 4 wound around the crank pulley 3, an alternator 5 and a water pump 6 connected to the crank pulley 3 via the belt 4. It has a tensioner unit 1 for an auxiliary belt that pushes the belt 4 to apply tension to the belt 4.
  • the alternator 5 and the water pump 6 are auxiliary equipment of the automobile
  • the belt 4 is an auxiliary equipment belt that transmits the rotation of the crankshaft 2 to the auxiliary equipment (alternator 5 and water pump 6).
  • the auxiliary belt tensioner unit 1 includes a bracket 10 attached to the engine block 7, a swing arm 20 swingably supported with respect to the bracket 10, and a swing arm 20.
  • a tension pulley 30 attached to the swing arm 20 is provided.
  • a plurality of through holes 11 are formed in the bracket 10.
  • the through hole 11 is for fixing the bracket 10 to the engine block 7 with the bolt 8 as shown in FIG.
  • the swing arm 20 is supported so as to be swingable around the fulcrum shaft 40.
  • the tension pulley 30 is supported by the swing arm 20 so as to move integrally with the swing arm 20 around the fulcrum shaft 40 when the swing arm 20 swings.
  • a belt 4 is wound around the outer circumference of the tension pulley 30.
  • the direction along the axis of the fulcrum axis 40 is called the axial direction.
  • the circumferential direction around the axis of the fulcrum axis 40 is called the circumferential direction, and the direction orthogonal to the axis is called the radial direction.
  • the side far from the engine block 7 is the front side in the axial direction, and the side closer to the engine block 7 is the rear side in the axial direction.
  • the bracket 10 has a flat plate portion 12 orthogonal to the axial direction.
  • the flat plate portion 12 is formed with a shaft hole 13 that penetrates the flat plate portion 12 in the axial direction.
  • the swing arm 20 is formed with a shaft hole 21 facing the shaft hole 13 in the axial direction.
  • Cylindrical slide bearings 51 and 52 are fitted between the plate surface of the shaft hole 13 of the flat plate portion 12, the fulcrum shaft 40, and the swing arm 20.
  • the fulcrum shaft 40 is fixed to the bracket 10 by passing the slide bearings 51 and 52 through the shaft portion and pressing the shaft portion through the shaft hole 21 into the shaft hole 13.
  • the slide bearings 51 and 52 rotatably support the swing arm 20 with respect to the outer periphery of the fulcrum shaft 40 and the bracket 10 in the circumferential direction, and the head of the fulcrum shaft 40, the bracket 10 and the swing arm 20. Supports the axial load acting in between.
  • the tension pulley 30 is arranged so as to face the swing arm 20 in the axial direction.
  • the swing arm 20 is provided with a pulley shaft 22 that projects from the surface facing the tension pulley 30 toward the tension pulley 30.
  • the pulley shaft 22 is located at a position that faces the fulcrum shaft 40 in the radial direction.
  • a predetermined radial distance is provided between the fulcrum shaft 40 and the pulley shaft 22.
  • the fulcrum shaft 40 passes through one end side in the longitudinal direction of the swing arm 20, and the pulley shaft 22 is arranged on the other end side in the longitudinal direction of the swing arm 20.
  • the protruding direction of the pulley shaft 22 is set to be opposite to the protruding direction (front side in the axial direction) of the fulcrum shaft 40 with respect to the bracket 10 (rear side in the axial direction).
  • the tension pulley 30 has a pulley 31 and a rolling bearing 32.
  • the inner ring of the rolling bearing 32 is fitted to the outer circumference of the pulley shaft 22.
  • the outer ring of the rolling bearing 32 is integrated with the inner circumference of the pulley 31.
  • the inner ring of the rolling bearing 32 is fixed to the pulley shaft 22 by a bolt 33.
  • the bolt 33 is screwed into a screw hole formed in the pulley shaft 22.
  • the rolling bearing 32 is in a state of rotatably supporting the tension pulley 30 with respect to the pulley shaft 22, and the tension pulley 30 is attached to the swing arm 20.
  • a spring 60 and a hydraulic damper 70 are attached to the inside of the swing arm 20.
  • a compression coil spring is used as the spring 60.
  • a plurality of springs 60 are provided around the fulcrum shaft 40.
  • a first recess 23 for accommodating the spring 60 is formed around the fulcrum shaft 40 of the swing arm 20.
  • a plurality of first recesses 23 are formed at intervals in the circumferential direction.
  • One end of the spring 60 housed in the first recess 23 is supported by the inner surface of the first recess 23, and the other end of the spring 60 pushes the first pin 80 via the tubular cap 61.
  • the first pin 80 is arranged so as not to move even if the swing arm 20 swings.
  • the tubular cap 61 is slidably supported by a guide sleeve 62 provided in the first recess 23.
  • the first pin 80 is fixed to the bracket 10 by press-fitting into the pin hole 14 formed in the bracket 10 as shown in FIG.
  • the first pin 80 is provided in a state of protruding forward in the axial direction with respect to the axial front surface of the flat plate portion 12 of the bracket 10, and the protruding portion is inserted into the first recess 23. It has become.
  • a plurality of first pins 80 are provided corresponding to a plurality of springs 60. That is, the plurality of first pins 80 are provided in the same number as the number of springs 60, and the first pins 80 are arranged around the fulcrum shaft 40 at intervals in the circumferential direction.
  • the spring 60 urges the swing arm 20 in one swing direction by the reaction force received from the first pin 80.
  • the circumferential direction (leftward rotation direction in the figure) on the side of the spring 60 as viewed from the first pin 80 is the urging direction of the swing arm 20 by the spring 60.
  • the tension pulley 30 of FIG. 2 presses the belt 4 by the urging force of the spring 60.
  • the hydraulic damper 70 and the spring 60 are incorporated in the swing arm 20 so as to be located on the same plane orthogonal to the fulcrum axis 40.
  • the hydraulic damper 70 can slide on the cylinder 71 provided in the swing arm 20 and the cylinder 71 so as to move integrally with the swing arm 20 around the fulcrum shaft 40 when the swing arm 20 swings. It has a piston 74 which is inserted into the cylinder 71 and divides the inside of the cylinder 71 into a hydraulic chamber 72 and a reservoir chamber 73, and a rod 75 whose one end is connected to the piston 74 and whose other end abuts on the second pin 90.
  • the second pin 90 is arranged so as not to move even if the swing arm 20 swings.
  • the swing arm 20 is formed with a second recess 24 for incorporating the hydraulic damper 70.
  • Most of the second recess 24 is located on the same circumference as the first recess 23.
  • the second recess 24 is formed in the shape of a hole that is closed at one end side in the direction (string direction) along one string that does not pass through the center of the same circumference and is open at the other end side.
  • the closed end of the second recess 24 projects in the chord direction from the same circumference.
  • the hydraulic damper 70 is arranged below the fulcrum shaft 40.
  • the downward direction corresponds to the gravitational direction and corresponds to the downward direction in FIGS. 1 and 2.
  • the wear ring 76 is press-fitted into the inner circumference of the second recess 24.
  • the inner circumference of the wear ring 76 slidably supports the outer circumference of the rod 75.
  • an oil seal 77 is incorporated in a portion on the opening side of the second recess 24 with respect to the wear ring 76.
  • the rod 75 slidably penetrates the inside of the oil seal 77.
  • the oil seal 77 is for preventing leakage of hydraulic oil from between the rod 75 and the inner circumference of the second recess 24.
  • the cylinder 71 is composed of a portion of the second recess 24 on the closed end side of the second recess 24 with respect to the wear ring 76.
  • the cylinder can also be configured by using a cylinder member.
  • a cylinder member having one end open and the other end closed is fitted into the second recess and fixed in the second recess by wear ring. It may be provided inside the swing arm.
  • the piston 74 is housed in the cylinder 71 so as to be slidable in the longitudinal direction of the cylinder 71.
  • the piston 74 is provided with a check valve 78 that opens and closes an oil passage that communicates between the hydraulic chamber 72 and the reservoir chamber 73.
  • the check valve 78 only allows the flow of hydraulic oil from the reservoir chamber 73 side to the hydraulic chamber 72 side.
  • a minute leak gap is formed between the sliding surface of the piston 74 and the cylinder 71.
  • the hydraulic chamber 72 incorporates a damper spring 79 that pushes the piston 74 in a direction in which the volume of the hydraulic chamber 72 increases.
  • the second pin 90 is fixed to the bracket 10.
  • the bracket 10 is formed with a pin hole 15 for press-fitting and fixing the second pin 90.
  • the second recess 24 of the swing arm 20 is formed with a through hole for inserting the second pin 90 into the second recess 24.
  • the second pin 90 is provided in a state of protruding forward in the axial direction with respect to the front surface of the flat plate portion 12 of the bracket 10 in the axial direction, and the tip of the rod 75 is in contact with the protruding portion.
  • the hydraulic damper 70 and the second pin 90 have a spring 60 whose circumferential direction (counterclockwise rotation direction in the figure) on the side where the hydraulic damper 70 is viewed from the second pin 90 is viewed from the first pin 80. It is arranged so as to be in the same direction as the circumferential direction (left rotation direction in the figure) on a certain side.
  • the hydraulic damper 70 swings the swing arm 20 in the swing direction opposite to the direction in which the spring 60 urges the swing arm 20 (in the right direction in which the tension pulley 30 separates from the belt 4 in FIG. 2). It is designed to buffer the movement.
  • the inclination angle ⁇ of the swing arm 20 is an angle formed by a plane connecting the axis O1 of the fulcrum shaft 40 and the rotation center O2 of the tension pulley 30 and a horizontal plane.
  • the plane corresponds to the cut surface of the IV-IV line in FIG. 1
  • the horizontal plane corresponds to the oil surface of the hydraulic oil (Oil) in FIG. 1
  • the inclination angle ⁇ is from the axis O1 to the center of rotation O.
  • the tilt angle ⁇ is determined by a combination of the mounting angle of the swing arm 20 and the angle at which the swing arm 20 rotates about the fulcrum axis 40 during operation of the belt transmission device.
  • the mounting angle of the swing arm 20 corresponds to the tilt angle ⁇ when the swing arm 20 naturally settles down when tension does not act from the belt 4.
  • the tilt angle ⁇ of the swing arm 20 drawn in FIG. 1 corresponds to the mounting angle of the swing arm 20 in the belt transmission device shown in FIG.
  • the swing arm 20 swings in the counterclockwise direction due to the urging force of the spring 60 (see FIG. 6) to absorb the slack of the belt 4.
  • the piston 74 shown in FIGS. 6 and 7 moves in the direction in which the volume of the hydraulic chamber 72 increases due to the urging force of the damper spring 79.
  • the check valve 78 opens, and hydraulic oil flows from the reservoir chamber 73 to the hydraulic chamber 72.
  • an auxiliary reservoir chamber 25 is formed inside the swing arm 20 adjacent to the hydraulic damper 70 in a direction orthogonal to the longitudinal direction of the cylinder 71. Has been done.
  • the hydraulic chamber 72 and the reservoir chamber 73 are filled with hydraulic oil so that air does not exist.
  • the auxiliary reservoir chamber 25 contains air and hydraulic oil in two upper and lower layers.
  • the sub-reservoir chamber 25 is formed in a hole shape that is open toward one side in the axial direction at a portion adjacent to one side in the axial direction (front side in the drawing) with the hydraulic damper 70. .. As shown in FIGS. 1, 4, and 7, the sub-reservoir chamber 25 is sealed by the bore plug 100 attached to the swing arm 20.
  • the bore plug 100 is composed of a core metal and a sealing rubber attached to the peripheral edge of the core metal.
  • the rubber portion is a press-fitting portion for the inner circumference of the sub-reservoir chamber 25.
  • the bore plug 100 is attached to the swing arm 20 by press-fitting it into the inner circumference of the sub-reservoir chamber 25.
  • the swing arm 20 has a plurality of crimping portions 26 in which the end faces of the swing arm 20 are plastically deformed so as to prevent the bore plug 100 from coming off. You may have. After press-fitting the bore plug 100, the plurality of crimping portions 26 are plastically deformed so as to cover the bore plug 100 by striking a plurality of points around the bore plug 100 among the end faces on the front side in the axial direction of the swing arm 20 with a mold. Be made to. The bore plug 100 is surely prevented from coming off by these plurality of crimping portions 26.
  • an oil passage 27 communicating between the hydraulic chamber 72 and the sub-reservoir chamber 25 is formed inside the swing arm 20.
  • a relief valve 110 that opens and closes the oil passage 27 is attached to the swing arm 20.
  • the auxiliary reservoir chamber 25 has a long hole portion 25a that extends long in the circumferential direction, a fitting hole portion 25b that supports the relief valve 110, a groove portion 25c that connects the long hole portion 25a and the fitting hole portion 25b, and a long hole portion. It is formed by a penetrating portion 25d communicating from 25a to the reservoir chamber 73.
  • the elongated hole portion 25a is formed in an elongated hole shape having a hole width in the radial direction and extending in the circumferential direction longer than the hole width.
  • the elongated hole portion 25a extends upward from a portion located below the fulcrum shaft 40 through the periphery of the fulcrum shaft 40.
  • the inner wall surfaces on both the upper and lower sides connecting both ends in the circumferential direction are circularly isolated surfaces.
  • the bottom surface of the elongated hole portion 25a has a constant depth.
  • the penetrating portion 25d is open to the elongated hole portion 25a at a position below the air and the fulcrum shaft 40.
  • the penetrating portion 25d penetrates axially to the reservoir chamber 73 with a hole diameter smaller than the hole width of the elongated hole portion 25a.
  • the elongated hole portion 25a contains air and hydraulic oil in two upper and lower layers. Air is contained only in the upper region of the slot 25a.
  • the space in the fitting hole 25b that is, the flow path from the auxiliary reservoir chamber 25 side of the relief valve 110 to the groove 25c), the groove 25c, and the penetration portion 25d are also filled with hydraulic oil.
  • the total amount of hydraulic oil contained in these sub-reservoir chambers 25 is such that a height difference can be left between the oil level of the hydraulic oil in the sub-reservoir chamber 25 and the penetrating portion 25d within the possible swing range of the swing arm 20. It is set.
  • This height difference is such that even if the swing arm 20 swings when the tension of the belt 4 fluctuates, the air contained in the sub-reservoir chamber 25 stays in the upper region higher than the open position of the penetration portion 25d. It is for doing. Air is contained in the upper region of the sub-reservoir 25.
  • the hydraulic oil is not shown in FIG. 7.
  • the opening position of the penetrating portion 25d in the elongated hole portion 25a is set to a position at a distance from the inner wall surface on the upper side of the elongated hole portion 25a.
  • the oil passage 27 communicates from the fitting hole portion 25b of the sub-reservoir chamber 25 to the hydraulic chamber 72.
  • the oil passage 27 and the fitting hole portion 25b have a stepped hole shape extending in the axial direction so that the oil passage 27 is a small diameter hole portion and the fitting hole portion 25b is a large diameter hole portion.
  • the relief valve 110 includes a valve body 111, a valve seat 112, a valve spring 113 for urging the valve body 111 toward the valve seat 112, and a valve retainer 114 for receiving the valve spring 113. It is configured.
  • the valve body 111 is spherical.
  • the valve seat 112 has a seat surface on which the valve body 111 is seated, and a valve hole portion that is opened and closed by the valve body 111.
  • the valve retainer 114 has a bottomed cylinder shape and has a plurality of outlets on the cylinder wall thereof.
  • the valve seat 112 and the valve retainer 114 constitute a valve case that houses the valve body 111 and the valve spring 113.
  • the valve seat 112 and the valve retainer 114 are integrated by fitting each other.
  • the valve spring 113 is interposed between the valve body 111 and the valve retainer 114.
  • the valve body 111 is provided so as to be movable between a valve closing position (position shown in the drawing) that contacts the seat surface of the valve seat 112 and a valve opening position that separates from the seat surface of the valve seat 112.
  • the end face on the rear side in the axial direction of the valve seat 112 is supported in the axial direction by the fitting hole portion 25b.
  • the outer periphery of the valve seat 112 is supported in the hole radial direction of the fitting hole portion 25b by being fitted to the inner circumference of the fitting hole portion 25b.
  • the bore plug 100 restricts the movement of the valve retainer 114 to the front side in the axial direction so that the valve seat 112 does not rise from the bottom surface (step portion) of the fitting hole portion 25b. That is, the valve case including the valve seat 112 and the valve retainer 114 is fixed by the fitting hole portion 25b and the bore plug 100, and the relief valve 110 is attached to the swing arm 20 by this fixing.
  • the relief valve 110 is set in advance to open when the pressure of the hydraulic chamber 72 exceeds a predetermined value (set pressure).
  • set pressure of the relief valve 110 is appropriately determined based on the pressure on the oil passage 27 (hydraulic chamber 72) side acting on the valve body 111 and the urging force of the valve spring 113.
  • the valve body 111 When the pressure of the hydraulic chamber 72 is equal to or lower than the set pressure of the relief valve 110, as shown in FIG. 7, the valve body 111 is pressed against the seat surface of the valve seat 112 by the urging force of the valve spring 113 to close the valve hole. I'm out. That is, the relief valve 110 closes the oil passage 27 and cuts off the communication between the hydraulic chamber 72 and the sub-reservoir chamber 25.
  • the valve body 111 is pushed up against the urging force of the valve spring 113 by the pressure from the oil passage 27 side, and the seat surface of the valve seat 112.
  • the hydraulic oil is allowed to flow into the valve retainer 114 from the valve hole.
  • the hydraulic oil that has flowed into the valve retainer 114 from the valve hole of the valve seat 112 flows directly into the groove 25c from the outlet of the valve retainer 114, or passes through the gap between the outer periphery of the valve retainer 114 and the fitting hole 25b. Then, it reaches the groove portion 25c, and eventually reaches the elongated hole portion 25a. That is, when the pressure of the hydraulic chamber 72 exceeds the set pressure of the relief valve 110, the relief valve 110 opens the oil passage 27 and releases the pressure of the hydraulic chamber 72 to the sub-reservoir chamber 25.
  • the auxiliary belt tensioner unit 1 swings around the fulcrum shaft 40 and the swing arm 20 that is swingably supported around the fulcrum shaft 40.
  • the tension pulley 30 supported by the swing arm 20 so as to swing integrally with the moving arm 20, and the first pin arranged so as not to move with respect to the swing arm 20 swinging around the fulcrum shaft 40.
  • a hydraulic damper 70 which is attached to the swing arm 20 so as to come into contact with the second pin 90 and cushions the swing of the swing arm 20 in the direction opposite to the swing direction of the one, is provided.
  • the 70 is a cylinder 71 provided in the swing arm 20 so as to move integrally with the swing arm 20 around a fulcrum shaft 40, and a piston 74 that divides the inside of the cylinder 71 into a hydraulic chamber 72 and a reservoir chamber 73.
  • a rod 75 connected to the piston 74 so as to be in contact with the second pin 90, and a sub-reservoir chamber 25 communicating with the reservoir chamber 73 is formed inside the swing arm 20 and is a hydraulic chamber.
  • the mounting space for the tensioner unit 1 for the auxiliary belt is relatively large. It can be made smaller.
  • the tensioner unit 1 for an auxiliary machine belt is provided with an oil passage 27 communicating between the hydraulic chamber 72 and the sub-reservoir chamber 25 in the swing arm 20, and when the pressure of the hydraulic chamber 72 exceeds the set pressure, oil is provided.
  • An oil that serves as a bypass flow path that communicates from the hydraulic chamber 72 to the sub-reservoir chamber 25 by attaching a relief valve 110 to the swing arm 20 that opens the path 27 and releases the pressure of the hydraulic chamber 72 to the sub-reservoir chamber 25.
  • the passage 27 is realized, the oil passage 27 is opened and closed by the relief valve 110 attached to the swing arm 20, and when the pressure of the hydraulic chamber 72 exceeds the set pressure, the oil passage 27 is opened and the pressure of the hydraulic chamber 72 is used as a secondary reservoir.
  • the pressure in the hydraulic chamber 72 can be limited by letting it escape to the chamber 25. That is, the tensioner unit 1 for the auxiliary belt has the advantage of reducing the mounting space thereof, and when the tension fluctuation of the belt 4 is large, the pressure of the hydraulic chamber 72 becomes too high and the belt 4 becomes over-tensioned. It is possible to achieve both the advantages of prevention with the relief valve 110.
  • the auxiliary reservoir chamber 25, the oil passage 27, and the relief valve 110 are adjacent to one side in the axial direction with respect to the hydraulic damper 70. Avoid arranging the hydraulic damper 70, the auxiliary reservoir chamber 25, the oil passage 27 and the relief valve 110 on the same plane orthogonal to the fulcrum shaft 40, and utilize the circumference of the fulcrum shaft 40 to utilize the periphery of the fulcrum shaft 40 to utilize the auxiliary reservoir chamber 25 and the oil passage.
  • a large space for arranging the 27 and the relief valve 110 can be obtained, and the auxiliary reservoir chamber 25, the oil passage 27, and the relief valve 110 are arranged on the same side in the axial direction with respect to the hydraulic damper 70, and the oil passage 27 is arranged. It is also possible to suppress the path length of.
  • the spring 60 and the hydraulic damper 70 are arranged on the same plane orthogonal to the fulcrum axis 40, the spring 60 is further arranged on the same plane orthogonal to the fulcrum axis 40. This can be avoided and more space can be obtained for arranging the sub-reservoir 25, the oil passage 27 and the relief valve 110.
  • the auxiliary reservoir chamber 25 has a fitting hole portion 25b for supporting the relief valve 110, and the oil passage 27 hydraulically moves from the fitting hole portion 25b. Since the bore plug 100 that communicates to the chamber 72 and seals the sub-reservoir chamber 25 is attached to the swing arm 20, a leak path that directly leads from the oil passage 27 or the relief valve 110 to the outside of the swing arm 20 is provided. The flow path from the hydraulic chamber 72 to the sub-reservoir chamber 25 can be sealed simply by removing the bore plug 100 and attaching the bore plug 100.
  • the tensioner unit 1 for the auxiliary belt (see FIGS. 1 and 9) has a plurality of crimping portions 26 in which the swing arm 20 is plastically deformed so as to prevent the bore plug 100 from coming off, the bore plug 100 has a plurality of crimping portions 26. It is possible to surely prevent it from falling off.
  • the auxiliary reservoir chamber 25 extends upward from a portion located below the fulcrum shaft 40 through the periphery of the fulcrum shaft 40. Since the elongated hole portion 25a is provided, a large amount of hydraulic oil can be stored in the elongated hole portion 25a by utilizing the circumference of the fulcrum shaft 40, and the oil level in the elongated hole portion 25a can be raised. Further, the auxiliary belt tensioner unit 1 has a penetrating portion 25d in which the auxiliary reservoir chamber 25 communicates from the elongated hole portion 25a to the reservoir chamber 73, and air and hydraulic oil are contained in the elongated hole portion 25a and penetrates.
  • the portion 25d is open to the elongated hole portion 25a at a position below the air and the fulcrum shaft 40, the height difference between the oil level of the elongated hole portion 25a and the penetrating portion 25d is increased, and the swing arm Even if the inclination angle of 20 is large, air is retained in the upper region of the elongated hole portion 25a higher than the open position of the penetration portion 25d, and air is mixed from the penetration portion 25d into the reservoir chamber 73, and eventually the reservoir chamber 73. It is possible to prevent air from entering the hydraulic chamber 72.
  • the positional relationship between the shape and volume of the sub-reservoir 25 and the penetrating portion 25d is shown in a swing range acceptable to the swing arm 20 around the fulcrum shaft 40 during operation of the belt transmission device shown in FIG.
  • the air in the sub-reservoir 25 shown in 1 may be set so as to be able to be retained in the upper region higher than the open position of the penetration portion 25d.
  • tension pulley 30 is arranged at a position radially opposed to the fulcrum shaft 40, the hydraulic damper 70 and the spring 60 (see FIG. 4), but the auxiliary reservoir chamber is not formed around the fulcrum shaft. It is also possible to arrange the pulley shaft in the remaining angle region so that the tension pulley faces the spring or the like in the axial direction.
  • fulcrum shaft 40 is passed through the swing arm 20 and the fulcrum shaft 40 is fixed to the bracket 10, the fulcrum shaft may be integrally formed with the swing arm or the bracket. It is also possible to use rolling bearings instead of the sliding bearings 51 and 52 that support between the fulcrum shaft 40, the swing arm 20, and the bracket 10.
  • bracket 10 It is also possible to omit the bracket 10 and directly provide the fulcrum shaft, the first pin, and the second pin on the engine block 7.

Abstract

Cette unité de tendeur pour courroies de machine auxiliaire, qui comporte un amortisseur hydraulique et un ressort fixé autour d'un arbre de pivot d'un bras d'oscillation qui supporte un galet tendeur, est conçu pour pouvoir limiter la pression dans une chambre hydraulique à l'aide d'un clapet de décharge. Un passage d'huile (27) destiné à être raccordé entre une chambre hydraulique (72) d'un amortisseur hydraulique (70) et une chambre de sous-réservoir (25) est disposé sur un bras d'oscillation (20). Un clapet de décharge (110) pour ouvrir/fermer le passage d'huile (27) est fixé au bras d'oscillation (20). Le clapet de décharge (110) ouvre le passage d'huile (27) pour libérer la pression dans la chambre hydraulique (72) vers la chambre de sous-réservoir (25) lorsque la pression dans la chambre hydraulique (72) dépasse une pression définie.
PCT/JP2021/043796 2020-12-03 2021-11-30 Unité de tendeur pour courroies de machine auxiliaire WO2022118831A1 (fr)

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JP2020200932A JP2022088849A (ja) 2020-12-03 2020-12-03 補機ベルト用テンショナユニット
JP2020-200932 2020-12-03

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002156013A (ja) * 2000-11-22 2002-05-31 Ntn Corp チェーンテンショナ
JP2007333095A (ja) * 2006-06-15 2007-12-27 Ntn Corp チェーンテンショナの取付け装置
JP2019044941A (ja) * 2017-09-07 2019-03-22 Ntn株式会社 補機ベルト用テンショナユニット

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002156013A (ja) * 2000-11-22 2002-05-31 Ntn Corp チェーンテンショナ
JP2007333095A (ja) * 2006-06-15 2007-12-27 Ntn Corp チェーンテンショナの取付け装置
JP2019044941A (ja) * 2017-09-07 2019-03-22 Ntn株式会社 補機ベルト用テンショナユニット

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