WO2013043373A1 - Mécanisme de commande de la force de ressort de tensionneur d'entraînement de chaîne - Google Patents

Mécanisme de commande de la force de ressort de tensionneur d'entraînement de chaîne Download PDF

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Publication number
WO2013043373A1
WO2013043373A1 PCT/US2012/053830 US2012053830W WO2013043373A1 WO 2013043373 A1 WO2013043373 A1 WO 2013043373A1 US 2012053830 W US2012053830 W US 2012053830W WO 2013043373 A1 WO2013043373 A1 WO 2013043373A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
sleeve
housing
hollow
tensioner
Prior art date
Application number
PCT/US2012/053830
Other languages
English (en)
Inventor
Kevin B. Todd
Original Assignee
Borgwarner Inc.
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
Priority to RU2014113136/11A priority Critical patent/RU2014113136A/ru
Priority to JP2014531848A priority patent/JP6189846B2/ja
Priority to CN201280042785.8A priority patent/CN103765044B/zh
Priority to DE112012003408.2T priority patent/DE112012003408T5/de
Priority to KR1020147009242A priority patent/KR101939967B1/ko
Application filed by Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2013043373A1 publication Critical patent/WO2013043373A1/fr
Priority to US14/196,229 priority patent/US9360088B2/en
Priority to US14/196,261 priority patent/US9377088B2/en
Priority to US14/196,191 priority patent/US9377087B2/en
Priority to US15/146,472 priority patent/US10125849B2/en
Priority to US15/146,311 priority patent/US9879764B2/en
Priority to US15/850,600 priority patent/US10677325B2/en
Priority to US16/144,676 priority patent/US11078992B2/en

Links

Classifications

    • 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
    • F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H7/0836—Means for varying tension of belts, ropes, or chains with vibration damping means of the fluid and restriction type, e.g. dashpot
    • 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
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • 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
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • 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
    • F16H2007/0876—Control or adjustment of actuators
    • F16H2007/0882—Control or adjustment of actuators the tension being a function of temperature
    • 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
    • F16H2007/0876—Control or adjustment of actuators
    • F16H2007/0885—Control or adjustment of actuators the tension being a function of engine running condition
    • 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
    • F16H2007/0876—Control or adjustment of actuators
    • F16H2007/0887—Control or adjustment of actuators the tension being a function of load

Definitions

  • the invention pertains to the field of tensioners. More particularly, the invention pertains to chain drive tensioner spring force control mechanisms.
  • a piston of the tensioner presses against the chain to maintain tension in the chain.
  • tension in the chain increases during operation due to resonance of a chain span, a high load from the chain acts on the piston of the tensioner, causing the piston to retract into the housing of the tensioner.
  • Chain drive tensioner spring force is often too high for most operating conditions so that the spring force is sufficient to handle worst case operating conditions of the tensioner system.
  • the effectiveness of the tensioner and the overall system behavior and efficiency could be improved if the tensioner spring force could be varied with operating conditions taking into account wear and stretching that occurs in the chain during the life of the chain.
  • a tensioner in which an inward force acting to push a piston into a housing creates a fluid pressure in a hydraulic chamber formed by a cylindrical bore of the housing and a moveable sleeve, causing a movable sleeve to exert an outward force on the piston through a piston spring, opposing the inward force.
  • Fig. 2 shows a schematic of a tensioner of a passive tensioner system of a second
  • Fig. 3 shows a schematic of a tensioner of a passive tensioner system of a third
  • Fig. 4 shows a schematic of a tensioner of a passive tensioner system of a fourth
  • Fig. 5 shows a schematic of a tensioner of a passive tensioner system of a fifth
  • Fig. 6 shows a schematic of a tensioner of a passive tensioner system of a sixth
  • Fig. 7 shows a schematic of a tensioner of a passive tensioner system of a seventh
  • Fig. 8 shows a schematic of a tensioner of a passive tensioner system of an eighth
  • FIG. 9 shows a schematic of a tensioner of an active tensioner system of a ninth
  • Fig. 10 shows a schematic of a tensioner of an active tensioner system of a tenth
  • the tensioner systems of the present invention include a tensioner (described in further detail below) for a closed loop chain drive system used in an internal combustion engine. It may be utilized on a closed loop power transmission system between a driveshaft and at least one camshaft or on a balance shaft system between the driveshaft and a balance shaft.
  • the tensioner system may also include an oil pump and be used with fuel pump drives. Additionally, the tensioner systems of the present invention may also be used with belt drives.
  • Figures la-lc show the tensioner of a first embodiment tensioning under various chain conditions;
  • Figure la is tensioning a new chain;
  • Figure lb is tensioning a worn chain without high loads;
  • Figure lc is tensioning a worn chain under high load.
  • the tensioner is comprised of a housing 2 having an axially extending piston bore
  • the piston bore 2a has an interior with first diameter portion Dl and a second diameter portion D2, with the second diameter portion D2 being larger than the first diameter portion Dl .
  • the moveable sleeve 18 has an outer circumferential flange 20, which increases the diameter of the moveable sleeve 18 to be approximately equal to the diameter of the second diameter portion D2, but allowing the flange 20 to slide within the second diameter portion D2 of the bore 2a and to form a fluid chamber 14 between the bottom surface 27 of the outer circumferential flange 20 and the second diameter portion D2 of the bore 2a.
  • the fluid chamber 14 is in fluid communication with an oil pressure supply 7 through a supply line 12 containing a check valve 10.
  • the supply 7 supplies fluid to the fluid chamber 14 to make up for any leakage that may occur.
  • the check valve 10 prevents any fluid in the fluid chamber 14 from entering back into the supply 7. It should be noted that fluid pressure is not supplied to the area between top surface 29 of the outer
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • the supply 7 providing fluid to the fluid chamber 14 may be the same as the supply providing fluid to inlet supply line 6.
  • the supply supplying fluid to the inlet supply line 6 may be different than the supply 7 in fluid communication with fluid chamber 14.
  • supply 7 supplies fluid through the check valve 10 and supplies fluid to the fluid chamber 14 to fill the fluid chamber 14 and compensate for the movement of the sleeve 18 relative to the piston 3 and to maintain the position of the sleeve 18 relative to the piston 3.
  • the tensioner is comprised of a housing 2 having an axially extending piston bore 2a.
  • the piston bore 2a has an interior with a first diameter portion Dl and a second diameter portion D2, with the second diameter portion D2 being larger than the first diameter portion D 1.
  • a hollow moveable sleeve 33 is received within the bore 2a of the housing 2.
  • a hollow fixed sleeve 30 Received within the hollow moveable sleeve 33 is a hollow fixed sleeve 30.
  • sleeve spring 5 Within the hollow fixed sleeve 30 is sleeve spring 5.
  • the first end 5a of the sleeve spring 5 is in contact with a bottom surface 36 of an inner flange 34 of the moveable sleeve 33 and the second end 5b of the sleeve spring 5 is in contact with a bottom surface 32 of an inner flange 31 of the hollow fixed sleeve 30 or bottom of the bore 29a, if no flange 31 is present.
  • the sleeve spring 5 provides a bias force to reduce the control force required to keep the moveable sleeve 33 in the desired position relative to the piston 3.
  • a pressure chamber 16 is formed between an inner diameter portion 38 of the fixed sleeve 30, the inner diameter portion 17 of the hollow interior of the hollow moveable sleeve 33, and the interior 3a of
  • At least a portion of the moveable sleeve 33 is slidably received within the hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 35 of the inner flange 34 of the moveable sleeve 33.
  • a through hole 25 is present in the inner flange 34 allowing fluid from the inlet supply line 6 to the interior 3a of the piston and the top surface 35 of the inner flange 34 of the moveable sleeve 33.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • the supply 7 providing fluid to the fluid chamber 37 may be the same as the supply providing fluid to inlet supply line 6.
  • the supply supplying fluid to the inlet supply line 6 may be different than the supply 7 in fluid communication with fluid chamber 37.
  • a vent or pressure relief valve may be present within the hollow piston 3.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve (not shown) to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain similar to Figure la.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain.
  • the piston 3 has to be biased further outwards from the housing 2 in order to adequately tension the chain.
  • supply 7 supplies fluid through the check valve 10 and supplies fluid to the fluid chamber 37 to fill the fluid chamber 37 and compensate for the movement of the sleeve 33 relative to the piston 3 and to maintain the position of the sleeve 33 relative to the piston 3.
  • Seals may be present between the moveable sleeve 33 and the between the second diameter portion D2 of the bore 2a and the second diameter portion D2 and the first diameter of the bore Dl or any other place within the tensioner as necessary.
  • Hydraulic stiffness of the tensioner is created by pressure chamber 16 and fluid chamber 37 of the tensioner and substantially prevents inward movement of piston 3 and the moveable sleeve 33 towards the housing 2 when the chain span is under load.
  • Figure 3 shows a tensioner for a passive tensioner system using supply pressure to move a moveable sleeve 40 which receives a hollow piston 3 of a third embodiment.
  • the tensioner is comprised of a housing 2 having an axially extending piston bore 2a. Received within the bore 2a of the housing 2 is a moveable sleeve 40.
  • the moveable sleeve 40 has a first opening 46a defined by a top inner diameter portion 46 and a top surface 43 of central inner flange 41 and a second opening 45a defined by a bottom inner diameter portion 45 and a bottom surface 42 of central inner flange 41.
  • a through hole 47 of the central inner flange 41 connects the first opening 46a to the second opening 45a of the moveable sleeve 40.
  • a top surface 48 of the moveable sleeve 40 is exposed to atmospheric pressure.
  • a hollow piston 3 Received within the first opening 46a of the moveable sleeve 40, defined by the top inner diameter portion 46 and the top surface 43 of the central inner flange 41 is a hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 43 of the central inner flange 41 of the moveable sleeve 40.
  • a hollow fixed sleeve 30 Received within the second opening 45a of the moveable sleeve 40, defined by the bottom inner diameter portion 45 and the bottom surface 42 of the central inner flange 41 is a hollow fixed sleeve 30.
  • sleeve spring 5 Within the hollow fixed sleeve 30 is sleeve spring 5.
  • the first end 5a of the sleeve spring 5 is in contact with a bottom surface 42 of the central inner flange 41 of the moveable sleeve 40 and the second end 5b of the sleeve spring 5 is in contact with a bottom surface 32 of an inner flange 31 of the hollow fixed sleeve 30.
  • the sleeve spring 5 provides a bias force to reduce the control force required to keep the moveable sleeve 40 in the desired position relative to the piston 3.
  • a pressure chamber 16 is formed between an inner portion 38 of the fixed sleeve 30, or bottom of the bore if a flange 31 is not present, the inner diameter portion 17 of the second opening 45a of the moveable sleeve 40, and the interior 3a of piston 3.
  • the through hole 47 is present in the central inner flange 41 allows fluid from the inlet supply line 6 to the interior 3a of the piston and the top surface 43 of the central inner flange 41 of the moveable sleeve 40.
  • a fluid chamber 37 is formed between a bottom of the bore 2a, the fixed sleeve 30 and a bottom end surface 39 of the moveable sleeve 40.
  • the fluid chamber 37 is in fluid communication with an oil pressure supply 7 through a supply line 12 containing a check valve 10.
  • the check valve 10 prevents any fluid in the fluid chamber 37 from entering back into the supply 7.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • the supply 7 providing fluid to the fluid chamber 37 may be the same as the supply providing fluid to inlet supply line 6.
  • the supply supplying fluid to the inlet supply line 6 may be different than the supply 7 in fluid communication with fluid chamber 37.
  • a vent or pressure relief valve (not shown) may be present within the hollow piston 3.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain similar to Figure la.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain.
  • the piston 3 has to be biased further outwards from the housing 2 in order to adequately tension the chain.
  • supply 7 supplies fluid through the check valve 10 and supplies fluid to the fluid chamber 37 to fill the fluid chamber 37 and compensate for the movement of the sleeve 40 relative to the piston 3 and to maintain the position of the sleeve 40 relative to the piston 3.
  • Movement of the moveable sleeve 40 moves the second end 4b of the piston spring 4 biasing the piston 3 outwards from the housing 2, and therefore the spring force acting on the piston 3 is variable and the piston 3 continually tensions the chain, even when the chain becomes worn and stretched.
  • Seals may be present between the bore 2a and the moveable sleeve 40 or any other place within the tensioner as necessary.
  • Hydraulic stiffness of the tensioner is created by pressure chamber 16, and fluid chamber 37 of the tensioner and substantially prevents inward movement of piston 3 and the moveable sleeve 40 towards the housing 2 when the chain span is under load.
  • the tensioner is comprised of a housing 2 having an axially extending piston bore 2a.
  • the piston bore 2a has an interior with a first diameter portion Dl and a second diameter portion D2, with the second diameter portion D2 being larger than the first diameter portion Dl .
  • a bore flange 150 separates a second diameter portion D2 of the bore 2a that receives the piston 3 and another second diameter portion D2 of the bore that receives an outer circumferential flange 141 of the moveable sleeve 140.
  • a moveable sleeve 140 Received within the bore 2a of the housing 2 is a moveable sleeve 140.
  • the moveable sleeve 140 is hollow and forms a pressure chamber 16 with the bore 2a of the housing 2, the inner diameter portion 17 of the hollow moveable sleeve 140, and the interior 3a of the piston 3.
  • a sleeve spring 5 is present within the bore 2a and is received within the inner diameter portion 17 of the moveable sleeve 140, with a first end 5a of the spring 5 in contact with a bottom surface 147 of the inner flange 145 of the moveable sleeve 140 and second end 5b of the spring 5 in contact with the bottom 2c of the bore 2a.
  • the sleeve spring 5 provides a bias force to reduce the control force required to keep the moveable sleeve 140 in the desired position relative to the piston 3.
  • the moveable sleeve 140 has an outer circumferential flange 141 with a top surface 142 with an area A2 and a bottom surface 143 with an area Al .
  • the area A2 of the top surface 142 is less than the area Al of the bottom surface 143.
  • a first fluid chamber 58 is formed between a top surface 142 of the outer circumferential flange 141 and the bottom surface 152 of the bore flange 150 and a second fluid chamber 57 between the bottom surface 143 of the outer circumferential flange 141 and another wall 73 of the second diameter portion D2.
  • the first fluid chamber 58 is connected to a supply 7 through line 55, which preferably has a check valve 53 and the second fluid chamber 57 is connected to a supply 7 through line 56, which also preferably has a check valve 54.
  • the check valves 53, 54 prevent any fluid in the fluid chambers 58, 57 from entering back into supply 7.
  • the supply 7 supplies fluid to the fluid chambers 58, 57 to make up for any leakage that may occur.
  • At least a portion of the moveable sleeve 140 forward of the outer circumferential flange 141 is slidably received within the hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 146 of the inner flange 145 of the moveable sleeve 140.
  • a through hole 144 is present in the inner flange 145 allowing fluid from the inlet supply line 6 to the interior 3a of the piston and the top surface 146 of the inner flange 145 of the moveable sleeve 140.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain similar to Figure la.
  • the movable sleeve 140 is moved outwards mostly by oil from supply 7 and not the oil from hydraulic chamber 16. Since a bottom surface 143 of the outer circumferential flange 141 has a greater area Al than the area A2 of the top surface 142 of the outer circumferential flange 141, chamber 57 requires less fluid pressure to move the moveable sleeve 140 outwards from the housing similar to Figure lb, than chamber 58 to move the moveable sleeve 140 in the opposite direction.
  • the pressurization of the fluid chamber 57 causes the inner flange 145 of the moveable sleeve 33 to be "pumped” up or move the moveable sleeve 140 outward from the housing 2 and exert an outward force on the piston 3 through the piston spring 4, opposing the inward force.
  • supply 7 supplies fluid through the check valve 54 and supplies fluid to the fluid chamber 57 to fill the fluid chamber 57 and compensates for the movement of the sleeve 140 relative to the piston 3 and to maintain the position of the sleeve 140 relative to the piston 3.
  • Movement of the moveable sleeve 140 moves the second end 4b of the piston spring 4 biasing the piston 3 outwards from the housing 2, and therefore the spring force acting on the piston 3 is variable and the piston 3 continually tensions the chain, even when the chain becomes worn and stretched.
  • fluid chamber 57 when fluid chamber 57 is depressurizing, fluid chamber 58 is pressurizing.
  • the filling of fluid chamber 57 with fluid from supply 7 moves the moveable sleeve 140.
  • the movement of the moveable sleeve 140 beyond or greater than the travel necessary to maintain the position of the piston 3 relative to the chain is resisted by the fluid in fluid chamber 58 since the check valve 53, in supply line 55 block fluid from exiting the fluid chamber 58, essentially pressurizing the chamber 58.
  • the chamber 58 depressurizes and supply 7 supplies fluid through the check valve 53 and supplies fluid to the fluid chamber 58 to fill the chamber 58 and compensates for movement of the sleeve 140 relative to the piston 3 and maintains the position of the sleeve 140 relative to the piston regardless of other forces acting on sleeve.
  • Seals may be present between the bore 2a and the moveable sleeve
  • Hydraulic stiffness of the tensioner is created by pressure chamber 16 and fluid chambers 57, 58 of the tensioner and substantially prevents inward movement of piston 3 and the moveable sleeve 140 towards the housing 2 when the chain span is under load.
  • Figure 5 shows a tensioner for a passive tensioner system using supply pressure to move a moveable sleeve received by a piston of a fifth embodiment.
  • the tensioner is comprised of a housing 2 having an axially extending piston bore
  • the moveable sleeve 163 is hollow and forms a pressure chamber 16 with the bore 2a of the housing 2, the inner diameter portion 169 of the hollow moveable sleeve 163, and the interior 3a of the piston 3.
  • a sleeve spring 5 is present within the bore 2a and is received within the inner diameter portion 169 of the moveable sleeve 163, with a first end 5a of the spring 5 in contact with a bottom surface 166 of the inner flange 164 of the moveable sleeve 163 and second end 5b of the spring 5 in contact with the bottom 2c of the bore 2a.
  • the sleeve spring 5 provides a bias force to reduce the control force required to keep the moveable sleeve 163 in the desired position relative to the piston 3.
  • the cutout 168 of the moveable sleeve 163 slidably receives a bore flange 160.
  • the bore flange 160 has a top surface 161 with an area Al and a bottom surface 162 with an area A2.
  • the area Al of the top surface 161 of the bore flange 160 is greater than the area A2 of the bottom surface 162 of the bore flange 160.
  • a first fluid chamber 58 is formed between a top surface 161 of the bore flange 160 and the cutout 168 surface of the moveable sleeve 163 and a second fluid chamber 57 is formed between the bottom surface 162 of the bore flange 160 and another surface of the cutout 168 of the moveable sleeve 163.
  • the first fluid chamber 58 is connected to a supply 7 through line 55, which preferably has a check valve 53 and the second fluid chamber 57 is connected to a supply 7 through line 56, which also preferably has a check valve 54.
  • the check valves 53, 54 prevent any fluid in the fluid chambers 58, 57 from entering back into supply 7.
  • Supply 7 provides fluid to the fluid chambers 57, 58 to make up for any leakage that occurs.
  • At least a portion of the moveable sleeve 163 forward of the cutout 168 is slidably received within the hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the interior 3a of the hollow piston 3 and a second end 4b in contact with a top surface 165 of the inner flange 164 of the moveable sleeve 163.
  • a through hole 144 is present in the inner flange 164 allowing fluid from the inlet supply line 6 to the interior 3a of the piston and the top surface 165 of the inner flange 164 of the moveable sleeve 163.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • the supply 7 providing fluid to the fluid chambers 57, 58 may be the same as the supply providing fluid to inlet supply line 6.
  • the supply supplying fluid to the inlet supply line 6 may be different than the supply 7 in fluid communication with fluid chambers 57, 58.
  • a vent or pressure relief valve (not shown) may be present within the hollow piston 3.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain.
  • the piston 3 has to be biased further outwards from the housing 2 in order to adequately tension the chain.
  • some of the fluid supplied to the hydraulic chamber 16 leaks to the fluid chambers 57, 58 between the moveable sleeve 163 and bore 2a of the housing.
  • the pressurization of the fluid chamber 58 causes the inner flange 164 of the moveable sleeve 163 to be "pumped" up or move outwards from the housing 2 and exert an outward force on the piston 3 through the piston spring 4, opposing the inward force.
  • supply 7 supplies fluid through the check valve 53 and supplies fluid to the fluid chamber 58 to fill the fluid chamber 58 and compensate for the movement of the sleeve 163 relative to the piston 3 and to maintain the position of the sleeve 163 relative to the piston 3.
  • the fluid chamber 57 depressurizes and supply 7 supplies fluid through the check valve 54 and supplies fluid to the fluid chamber 57 to fill the chamber 57 and compensates for movement of the sleeve 163 relative to the piston 3 and maintains the position of the sleeve 163 relative to the piston regardless of other forces acting on sleeve.
  • Hydraulic stiffness of the tensioner is created by the chamber 16, and fluid chambers 57, 58 of the tensioner and substantially prevents inward movement of piston 3 and the moveable sleeve 163 towards the housing 2 when the chain span is under load.
  • Figure 6 shows a passive tensioner system using internal pressure areas and flange pressures to move a moveable sleeve received by a piston of a sixth embodiment.
  • a hollow piston 3 Received within the first opening 89a of the moveable sleeve 80, defined by the top inner diameter portion 89 and the top surface 81 of the central inner flange 82 is a hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 81 of the central inner flange 82 of the moveable sleeve 80.
  • a sleeve spring 5 Received within the second opening 96a of the moveable sleeve 80, defined by the bottom inner diameter portion 96 and the bottom surface 83 of the central inner flange 82 is a sleeve spring 5.
  • the first end 5a of the sleeve spring 5 is in contact with a bottom surface 83 of the central flange 82 of the moveable sleeve 80 and the second end 5b of the sleeve spring 5 is in contact with a bottom 2c of the bore 2a.
  • the sleeve spring 5 provides a bias force to reduce the control force required to keep the moveable sleeve 80 in the desired position relative to the piston 3.
  • a pressure chamber 16 is formed the top inner diameter portion 89 of the sleeve 80, the bottom inner diameter portion 96 of the sleeve 80, the bore 2a of the housing, and the interior 3a of the piston.
  • the through hole 97 is present in the central inner flange 81 and allows fluid from the inlet supply line 6 to flow from the second opening 96a to the first opening 89a.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • the supply 7 providing fluid to the fluid chambers 94, 95 may be the same as the supply providing fluid to inlet supply line 6.
  • the supply supplying fluid to the inlet supply line 6 may be different than the supply 7 in fluid communication with fluid chambers 94, 95.
  • a vent or pressure relief valve (not shown) may be present within the ho How piston 3.
  • the moveable sleeve 80 has an outer circumferential flange 84 which is approximately equal to the width of the second diameter portion D2, but allowing the flange 84 to slide within the second diameter portion D2 of the bore 2a and to form a first fluid chamber 95 and a second fluid chamber 94.
  • the first fluid chamber 95 is connected to a supply 7 through line 93, which preferably has a check valve 92 and the second fluid chamber 94 is connected to a supply 7 through line 91, which also preferably has a check valve 90.
  • the check valves 92, 90 prevent any fluid in the fluid chambers 95, 94 from entering back into supply 7.
  • Supply 7 provides fluid to the fluid chambers 94, 95 as necessary to make up for leakage.
  • the outer diameter of the moveable sleeve 80 below the outer circumferential flange 84 is received by a first diameter portion Dl of the bore 2a,
  • the second diameter portion D2 is greater than the first diameter portion Dl .
  • the piston 3 has to be biased further outwards from the housing 2 in order to adequately tension the chain.
  • some of the fluid supplied to the hydraulic chamber 16 leaks to the fluid chambers 94, 95 between the moveable sleeve 80 and bore 2a of the housing and the fluid pressure in chamber 16 on a bottom surface 99 of the sleeve 80 and on the bottom surface 83 of the central inner flange 82 moves the sleeve 80 outwards from the housing similar to Figure la.
  • the movable sleeve is moved outwards mostly by oil from supply and not the oil from hydraulic chamber 16.
  • supply 7 supplies fluid through the check valve 10 and supplies fluid to the fluid chamber 94 to fill the fluid chamber 94 and compensate for the movement of the sleeve 80 relative to the piston 3 and to maintain the position of the sleeve 80 relative to the piston 3.
  • Movement of the moveable sleeve 80 moves the second end 4b of the piston spring 4 biasing the piston 3 outwards from the housing 2, and therefore the spring force acting on the piston 3 is variable and the piston 3 continually tensions the chain, even when the chain becomes worn and stretched.
  • fluid chamber 95 when fluid chamber 94 is depressurizing, fluid chamber 95 is pressurizing.
  • the filling of fluid chamber 94 with fluid from supply 7 moves the moveable sleeve 80.
  • the movement of the moveable sleeve beyond or greater than the travel necessary to maintain the position of the piston 3 relative to the chain is resisted by the fluid in fluid chamber 95 since the check valve 92, in supply line 93 blocks fluid from exiting the fluid chamber 95, essentially pressurizing the chamber 95.
  • the chamber 95 depressurizes and supply 7 supplies fluid through the check valve 92 and supplies fluid to the fluid chamber 95 to fill the chamber 95 and compensates for movement of the sleeve 80 relative to the piston 3 and maintains the position of the sleeve 80 relative to the piston regardless of other forces acting on sleeve.
  • Seals may be present between the bore 2a and the moveable sleeve 80 or any other place within the tensioner as necessary.
  • Figure 7 shows a tensioner for a passive tensioner system of a seventh
  • the tensioner is comprised of a housing 2 having an axially extending piston bore 2a.
  • the piston bore 2a has an interior with a first diameter portion Dl and a second diameter portion D2, with the second diameter portion D2 being larger than the first diameter portion Dl .
  • a bore flange 52 separates a second diameter portion D2 of the bore 2a that receives the piston 3 and another second diameter portion D2 of the bore that receives an outer circumferential flange 20 of a moveable sleeve 18.
  • a moveable sleeve 18 Received within the bore 2a of the housing is a moveable sleeve 18.
  • the moveable sleeve 18 is hollow and forms a pressure chamber 16 with the bore 2a of the housing 2, the inner diameter portion 17 of the hollow moveable sleeve 18 and the interior of the piston 3.
  • a sleeve spring 5 is present within the bore 2a and is received within the inner diameter portion 17 of the moveable sleeve 18, with a first end 5a of the spring 5 in contact with a bottom surface 24 of the inner flange 22 of the moveable sleeve 18 and second end 5b of the spring 5 in contact with the bottom 2c of the bore 2a.
  • the sleeve spring 5 provides a bias force to reduce the control force required to keep the moveable sleeve 18 in the desired position relative to the piston 3.
  • the moveable sleeve 18 has an outer circumferential flange 20 with a top surface 29 and a bottom surface 27.
  • the outer circumferential flange 20 separates a second diameter portion D2 of the housing 2 into first and second fluid chambers 58, 57.
  • a first fluid chamber 58 is formed between a top surface 29 of the outer circumferential flange 20 and the bottom surface 51 of the bore flange 52 and a second fluid chamber 57 between the bottom surface 27 of the outer circumferential flange 20 and another wall 73 of the second diameter portion D2.
  • the first fluid chamber 58 is connected to a supply 7 through line 101 and a control valve 108.
  • the second fluid chamber 57 is connected to a supply 7 through line 100 and control valve 108.
  • Supply 7 supplies fluid to the fluid chambers 57, 58 to make up for leakage from the chambers only.
  • the control valve, 108 preferably a spool valve, includes a spool 109 with at least two cylindrical lands 109a, 109b slidably received within a bore 106.
  • the bore 106 may be in the tensioner housing 2 or located remotely from the tensioner housing in the engine.
  • One end of the spool is in contact with a spring 110 that biases the spool in a first direction.
  • At least a portion of the moveable sleeve 18 forward of the outer circumferential flange 20 is slidably received within the hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 26 of the inner flange 22 of the moveable sleeve 18.
  • a through hole 47 is present in the inner flange 22 allowing fluid from the inlet supply line 6 to interior 3a of the piston and the top surface 26 of the inner flange 22 of the moveable sleeve 18.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • the supply 7 providing fluid to the fluid chambers 57, 58 may the same as the supply providing fluid to inlet supply line 6.
  • the supply supplying fluid to the inlet supply line 6 may be different than the supply 7 in fluid communication with fluid chambers 57, 58.
  • a vent or pressure relief valve (not shown) may be present within the hollow piston 3.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain similar to Figure la.
  • supply 7 supplies fluid through the spool valve 108 to fluid chamber 57 and compensates for movement of the sleeve 40 relative to the piston 3 and to maintain the position of the sleeve 40 relative to the piston 3.
  • Movement of the moveable sleeve 18 moves the second end 4b of the piston spring 4 biasing the piston 3 outwards from the housing 2, and therefore the spring force acting on the piston 3 is variable and the piston 3 continually tensions the chain, even when the chain becomes worn and stretched.
  • the chamber 58 depressurizes and supply 7 supplies fluid through the spool 108 and supplies fluid to the fluid chamber 58 to fill the chamber 58 and compensates for movement of the sleeve 18 relative to the piston 3 and maintains the position of the sleeve 18 relative to the piston regardless of other forces acting on sleeve.
  • Seals may be present between the bore 2a and the moveable sleeve 18 or any other place within the tensioner as necessary.
  • Hydraulic stiffness of the tensioner is created by the chamber 16, and pressure chambers 57, 58 of the tensioner and substantially prevents inward movement of piston 3 and the moveable sleeve 40 towards the housing 2 when the chain span is under load.
  • Figure 8 is an alternate embodiment of Figure 7 in which the control valve 108 is in fluid communication with an accumulator 114.
  • the accumulator 114 is also in fluid communication with the pressure chamber 16 formed by the bore 2a of the housing 2, the inner diameter portion 17 of the hollow moveable sleeve 18, and the interior 3a of the piston 3 through a check valve 125.
  • the accumulator 114 stores or accumulates fluid from the pressure chamber 16 to supply to fluid chambers 57, 58 in case of leakage.
  • the moveable sleeve 18 is hollow and forms a pressure chamber 16 with the bore 2a of the housing 2, the interior of the piston 3 and the inner diameter portion 17 of the hollow moveable sleeve 18.
  • a sleeve spring 5 is present within the bore 2a and is received within the inner diameter portion 17 of the moveable sleeve 18, with a first end 5a of the spring 5 in contact with a bottom surface 24 of the inner flange 22 of the moveable sleeve 18 and second end 5b of the spring 5 in contact with the bottom 2c of the bore 2a.
  • the sleeve spring 5 provides a bias force to reduce the control force required to keep the moveable sleeve 18 in the desired position relative to the piston 3.
  • the first fluid chamber 58 is connected to accumulator 114 through line 101, control valve 108 and line 112.
  • the second fluid chamber 57 is connected to accumulator 114 through line 100, control valve 108 and line 112.
  • the accumulator 114 supplies fluid to chambers 57, 58 for make up purposes due to leakage only.
  • the control valve, 108 preferably a spool valve, includes a spool 109 with at least two cylindrical lands 109a, 109b slidably received within a bore 106.
  • the bore 106 may be in the tensioner housing 2 or located remotely from the tensioner housing in the engine.
  • One end of the spool is in contact with a spring 110 that biases the spool valve in a first direction.
  • At least a portion of the moveable sleeve 18 forward of the outer circumferential flange 20 is slidably received within the hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 26 of the inner flange 22 of the moveable sleeve 18.
  • a through hole 47 is present in the inner flange 22 allowing fluid from the inlet supply line 6 to the interior 3a of the piston and the top surface 26 of the inner flange 22 of the moveable sleeve 18.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • a vent or pressure relief valve may be present within the hollow piston 3.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain similar to Figure la.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4, to bias a span of the closed loop chain.
  • the piston 3 has to be biased further outwards from the housing 2 in order to adequately tension the chain.
  • accumulator 114 supplies fluid through the spool valve 108 to fluid chamber 57 to fill the fluid chamber 57 and compensate for the movement of the sleeve 40 relative to the piston 3.
  • fluid chamber 58 when fluid chamber 57 is depressurizing, fluid chamber 58 is pressurizing.
  • the filling of fluid chamber 57 with fluid from supply 7 moves the moveable sleeve 40.
  • the movement of the moveable sleeve 40 beyond or greater than the travel necessary to maintain the position of the piston 3 relative to the chain is resisted by fluid in fluid chamber 58 since spool valve 108 blocks fluid from exiting the fluid chamber 58, essentially pressurizing the chamber 57.
  • fluid chamber 58 depressurizes and fluid chamber 57 pressurizes.
  • Seals may be present between the bore 2a and the moveable sleeve 40 or any other place within the tensioner as necessary.
  • Figure 9 shows an active tensioner control system of a ninth embodiment.
  • the tensioner is comprised of a housing 2 having an axially extending piston bore
  • the piston bore 2a has an interior with a first diameter portion Dl and a second diameter portion D2, with the second diameter portion D2 being larger than the first diameter portion Dl .
  • a bore flange 52 separates a second diameter portion D2 of the bore 2a that receives the piston 3 and another second diameter portion D2 of the bore that receives an outer circumferential flange 20 of the moveable sleeve 18 through a check valve 125.
  • the moveable sleeve 18 has an outer circumferential flange 20 with a top surface 29 and a bottom surface 27.
  • the outer circumferential flange 20 separates a second diameter portion D2 of the housing 2 into first and second fluid chambers 58, 57.
  • a first fluid chamber 58 is formed between a top surface 29 of the outer circumferential flange 20 and the bottom surface 51 of the bore flange 50 and a second fluid chamber 57 between the bottom surface 27 of the outer circumferential flange 20 and another wall 73 of the second diameter portion D2.
  • the first fluid chamber 58 is in fluid communication with an accumulator 114 through line 101, a control valve 108, and line 112.
  • the second fluid chamber 57 is in fluid communication with an accumulator 114 through line 100, a control valve 108 and line 112.
  • the accumulator 114 is also preferably in fluid communication with the pressure chamber 16 formed by the bore 2a of the housing 2 and the inner diameter portion 17 of the hollow moveable sleeve 18.
  • the control valve, 108 preferably a spool valve, includes a spool 109 with at least two cylindrical lands 109a, 109b slidably received within a bore 106 that can block or allow flow from the accumulator 114 to the fluid chambers 57, 58.
  • the bore 106 may be in the tensioner housing 2 or located remotely from the tensioner housing in the engine.
  • One end of the control valve 108 is in contact with an actuator 116.
  • the actuator 116 is a position setting actuator or linear actuator in which the actuator sets a specific position of the control valve 108.
  • the actuator 116 may also be a force actuator in which a force is present on one side of the control valve. It should be noted that if the actuator 116 is a force actuator a spring would be present on the opposite side of control valve influenced by the actuator 116.
  • At least a portion of the moveable sleeve 18 forward of the outer circumferential flange 20 is slidably received within the hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 26 of the inner flange 22 of the moveable sleeve 18.
  • a through hole 47 is present in the inner flange 22 allowing fluid from the inlet supply line 6 to the inner portion 3 a of the piston 3.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • a vent or pressure relief valve may be present within the hollow piston 3.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and the chamber 9 formed within the inner portion 3a of the piston and bias the piston outward from the housing 2 with the spring force from piston spring 4 to bias a span of the closed loop chain.
  • a sensor (not shown) provides position feedback 120 of the moveable sleeve 18 to the controller 118.
  • the controller 118 compares the position feedback of the moveable sleeve to the set point 122 from the set point algorithm or map 124 based on different engine parameters 126.
  • the control valve 108 is actuated by the actuator 116 to a position in which fluid flows from the accumulator 114 to the fluid chambers 57, 58 to move the moveable sleeve 18 relative to the piston 3 and the bore 2a of the housing.
  • the movement of the moveable sleeve 18 moves the location of the second end 4b of the piston spring 4 which is in contact with a top surface 26 of the inner flange 22 of the moveable sleeve 18, biasing the piston 3 outwards from the housing 2 and into contact with a span of a chain or belt (not shown).
  • the spring force acting on the piston 3 is variable and the piston 3 continually tensions the chain, even when the chain becomes worn and stretched.
  • Hydraulic stiffness of tensioner created by the chamber 16, and fluid chambers 57 and 58 of the tensioner and substantially prevents inward movement of piston 3 and the moveable sleeve 18 towards the housing 2 when the chain span is under load. Seals (not shown) may be present between the bore 2a and the moveable sleeve 40 or any other place within the tensioner as necessary.
  • Figure 10 an active control tensioner system of a tenth embodiment.
  • a hollow piston 3 Received within the first opening 89a of the moveable sleeve 80, defined by the top inner diameter portion 89 and the top surface 82 of the central inner flange 81 is a hollow piston 3.
  • a piston spring 4 biasing the piston 3 outwards from the housing 2.
  • the piston spring 4 has a first end 4a in contact with the inner portion 3a of the hollow piston 3 and a second end 4b in contact with a top surface 82 of the central inner flange 81 of the moveable sleeve 80.
  • an inlet check valve may be present (not shown) as well as an inlet supply line 6 to provide oil pressure to the pressure chamber 16.
  • the moveable sleeve 80 has an outer circumferential flange 84 which is approximately equal to the width of the second diameter portion D2, but allowing the flange 84 to slide within the second diameter portion D2 of the bore 2a and to form a first fluid chamber 95 and a second fluid chamber 94.
  • the first fluid chamber 95 is connected to an accumulator 114 through line 101, a control valve 108 and line 112.
  • the second fluid chamber 94 is connected to the accumulator 114 through line 100, the control valve 108 and line 112.
  • the accumulator 114 is also preferably in fluid communication with the pressure chamber 16 formed by the bore 2a of the housing 2 and the bottom inner surface 96a of the second opening 96 of the moveable sleeve 80 through a check valve 125.
  • the actuator position is controlled by a controller 118 which receives a set point input 122 from a set point algorithm or map 124.
  • the controller 118 also receives position feedback 120 of the moveable sleeve 80 of the tensioner via a sensor (not shown).
  • the set point algorithm or map 124 receives input from different engine parameters 126, such as, but not limited to cam timing, engine speed, throttle, temperature, age, and tensioner position.
  • fluid is supplied to the hydraulic chamber 16 from an inlet supply line 6 and optionally through an inlet check valve to pressurize the hydraulic chamber 16 and bias the piston outward from the housing 2 with the spring force from piston spring 4 to bias a span of the closed loop chain.
  • a sensor (not shown) provides position feedback 120 of the moveable sleeve 80 to the controller 118.
  • the controller 118 compares the position feedback of the moveable sleeve to the set point 122 from the set point algorithm or map 124 based on different engine parameters 126.
  • the control valve 108 is actuated by the actuator to a position in which fluid flows from the accumulator 114 to the fluid chambers 94, 95 to move the moveable sleeve 80 relative to the piston 3 and the bore 2a of the housing.
  • the movement of the moveable sleeve 80 moves the location of the second end 4b of the piston spring 4 which is in contact with a top surface 81 of the central inner flange 81 of the moveable sleeve 80, biasing the piston 3 outwards from the housing 2 and into contact with a span of a chain or belt (not shown).
  • the spring force acting on the piston 3 is variable and the piston
  • Hydraulic stiffness of tensioner created by the chamber 16, and fluid chambers 94 and 95 of the tensioner substantially prevents inward movement of piston 3 and the moveable sleeve 80 towards the housing 2 when the chain span is under load.
  • Seals may be present between the bore 2a and the moveable sleeve 80 or any other place within the tensioner as necessary.

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

Abstract

La présente invention se rapporte à un tensionneur, pour lequel une force dirigée vers l'intérieur, qui agit pour pousser un piston dans un boîtier, crée une pression de fluide dans une chambre hydraulique formée par un alésage cylindrique du boîtier et un manchon mobile, ce qui amène un manchon mobile à exercer une force dirigée vers l'extérieur sur le piston au moyen d'un ressort de piston, à l'opposé de la force dirigée vers l'intérieur.
PCT/US2012/053830 2011-09-22 2012-09-06 Mécanisme de commande de la force de ressort de tensionneur d'entraînement de chaîne WO2013043373A1 (fr)

Priority Applications (12)

Application Number Priority Date Filing Date Title
RU2014113136/11A RU2014113136A (ru) 2011-09-22 2012-09-06 Механизм регулирования усилия пружины натяжителя цепного привода
JP2014531848A JP6189846B2 (ja) 2011-09-22 2012-09-06 チェーンドライブテンショナばね力制御機構
CN201280042785.8A CN103765044B (zh) 2011-09-22 2012-09-06 链条驱动张紧器弹簧力控制机构
DE112012003408.2T DE112012003408T5 (de) 2011-09-22 2012-09-06 Federkraftsteuerungsmechanismus für eine Kettenantriebsspannvorrichtung
KR1020147009242A KR101939967B1 (ko) 2011-09-22 2012-09-06 체인 구동부 텐셔너 스프링력 제어 기구
US14/196,229 US9360088B2 (en) 2011-09-22 2014-03-04 Chain drive tensioner spring force control mechanism
US14/196,191 US9377087B2 (en) 2011-09-22 2014-03-04 Chain drive tensioner spring force control mechanism
US14/196,261 US9377088B2 (en) 2011-09-22 2014-03-04 Chain drive tensioner spring force control mechanism
US15/146,472 US10125849B2 (en) 2011-09-22 2016-05-04 Chain drive tensioner spring force control mechanism
US15/146,311 US9879764B2 (en) 2011-09-22 2016-05-04 Chain drive tensioner spring force control mechanism
US15/850,600 US10677325B2 (en) 2011-09-22 2017-12-21 Chain drive tensioner spring force control mechanism
US16/144,676 US11078992B2 (en) 2011-09-22 2018-09-27 Chain drive tensioner spring force control mechanism

Applications Claiming Priority (2)

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US201161537651P 2011-09-22 2011-09-22
US61/537,651 2011-09-22

Related Parent Applications (1)

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PCT/US2014/019329 Continuation-In-Part WO2014137790A1 (fr) 2011-09-22 2014-02-28 Mécanisme de commande de force de rappel de tensionneur à entraînement par chaîne

Related Child Applications (4)

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PCT/US2014/019329 Continuation-In-Part WO2014137790A1 (fr) 2011-09-22 2014-02-28 Mécanisme de commande de force de rappel de tensionneur à entraînement par chaîne
US14/196,261 Continuation-In-Part US9377088B2 (en) 2011-09-22 2014-03-04 Chain drive tensioner spring force control mechanism
US14/196,191 Continuation-In-Part US9377087B2 (en) 2011-09-22 2014-03-04 Chain drive tensioner spring force control mechanism
US14/196,229 Continuation-In-Part US9360088B2 (en) 2011-09-22 2014-03-04 Chain drive tensioner spring force control mechanism

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KR (1) KR101939967B1 (fr)
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US9683637B2 (en) 2012-12-18 2017-06-20 Borgwarner Inc. Tensioner with spring force control in a second bore
US9879764B2 (en) 2011-09-22 2018-01-30 Borgwarner Inc. Chain drive tensioner spring force control mechanism
US10077825B2 (en) 2013-03-07 2018-09-18 Borgwarner Inc. Tensioner with spring force control
US10094449B2 (en) 2015-04-15 2018-10-09 Tsubakimoto Chain Co. Chain tensioner
CN109458365A (zh) * 2018-12-24 2019-03-12 江苏徐工工程机械研究院有限公司 工程机械液压系统以及工程机械

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WO2017019037A1 (fr) * 2015-07-28 2017-02-02 Borgwarner Inc. Piston assemblé à évacuation
US9739348B2 (en) * 2015-10-21 2017-08-22 GM Global Technology Operations LLC Variable tensioner for cam drive
WO2019164525A1 (fr) * 2018-02-26 2019-08-29 Borgwarner Inc Tendeur à force variable avec alésage primaire de technologie de réservoir interne
CN108397525B (zh) * 2018-03-15 2019-11-29 温州职业技术学院 一种皮带涨紧装置
CN110925369B (zh) * 2019-12-05 2020-12-18 宁波吉利罗佑发动机零部件有限公司 一种正时紧链器

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US9879764B2 (en) 2011-09-22 2018-01-30 Borgwarner Inc. Chain drive tensioner spring force control mechanism
US10125849B2 (en) 2011-09-22 2018-11-13 Borgwarner Inc. Chain drive tensioner spring force control mechanism
US10677325B2 (en) 2011-09-22 2020-06-09 Borgwarner Inc. Chain drive tensioner spring force control mechanism
US11078992B2 (en) 2011-09-22 2021-08-03 Borgwarner Inc. Chain drive tensioner spring force control mechanism
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US10077825B2 (en) 2013-03-07 2018-09-18 Borgwarner Inc. Tensioner with spring force control
US10094449B2 (en) 2015-04-15 2018-10-09 Tsubakimoto Chain Co. Chain tensioner
CN109458365A (zh) * 2018-12-24 2019-03-12 江苏徐工工程机械研究院有限公司 工程机械液压系统以及工程机械
CN109458365B (zh) * 2018-12-24 2024-02-02 江苏徐工工程机械研究院有限公司 工程机械液压系统以及工程机械

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CN103765044A (zh) 2014-04-30
JP2014528047A (ja) 2014-10-23
JP6189846B2 (ja) 2017-08-30
JP6609603B2 (ja) 2019-11-20
KR101939967B1 (ko) 2019-01-18
JP2017215046A (ja) 2017-12-07
DE112012003408T5 (de) 2014-05-08
KR20140065437A (ko) 2014-05-29
RU2014113136A (ru) 2015-10-27

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