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WO1999009331A1 - Systeme hydraulique de transmission rotative - Google Patents

Systeme hydraulique de transmission rotative Download PDF

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Publication number
WO1999009331A1
WO1999009331A1 PCT/KR1998/000251 KR9800251W WO9909331A1 WO 1999009331 A1 WO1999009331 A1 WO 1999009331A1 KR 9800251 W KR9800251 W KR 9800251W WO 9909331 A1 WO9909331 A1 WO 9909331A1
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WO
WIPO (PCT)
Prior art keywords
chamber
rotors
rotor
vanes
output shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/KR1998/000251
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English (en)
Inventor
Seong Joo Kim
Seong Joong Kim
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO1999009331A1 publication Critical patent/WO1999009331A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/04—Combined pump-turbine units
    • F16H41/22—Gearing systems consisting of a plurality of hydrokinetic units operating alternatively, e.g. made effective or ineffective by filling or emptying or by mechanical clutches
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D31/00—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution
    • F16D31/08—Control of slip
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D31/00—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution
    • F16D31/06—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution using pumps of types differing from those before-mentioned

Definitions

  • the present invention relates, in general, to power transmission systems used for transmitting power or rotational force from an input to an output shaft and, more particularly, to a hydraulic, rotary transmission system capable of transmitting the rotational force from the input shaft to the output shaft while controlling or changing the rotating speed of the output shaft using the hydraulic force of actuating fluid selectively pressurized by the rotational force of the input shaft.
  • Such transmission systems are typically classified into several types.
  • clutch systems, torque converter systems and hydraulic coupling systems are used as such transmission systems.
  • a clutch disk is mounted on each of the input and output shafts, so that the clutch disks of the two shafts are selectively brought into contact with each other, thus controllably transmitting the power from the input to the output shaft.
  • each of the typical torque converter transmission systems or the hydraulic coupling transmission systems comprises a pump impeller, a turbine rurmer and a stator, which are provided on the input and output shafts and are filled with actuating fluid for transmitting the power from the input to the output shaft.
  • hydrostatic transmission systems Another example of known transmission systems is a hydrostatic system, a chain or belt transmission system or a gear transmission system.
  • hydrostatic transmission systems the power is transmitted from an input to an output shaft due to a hydraulic reciprocating motion of a piston.
  • chain, belt or gear transmission systems preferably used with lathes or milling machines, the rotational force of a motor is transmitted to the spindle of a machine using a chain, a belt or a gear to rotate the spindle.
  • Torque converter transmission systems typically used as automatic transmission systems for automobiles, use a turbo-type impeller of which both the pump impeller and the power receiving turbine runner are opened during the operation.
  • the actuating fluid in the system is dynamically actuated. Therefore, such torque converter systems increase power consumption, complicate the system -3-
  • an object of the present invention is to provide a hydraulic, rotary transmission system which is capable of transmitting rotational force from an input shaft to an output shaft while controlling or changing the rotating speed of the output shaft using actuating fluid filling an oil chamber formed between two rotors respectively integrated with the input and output shafts.
  • the preferred embodiment of this invention provides a hydraulic, rotary transmission system for transmitting rotational force from an input shaft to an output shaft while controlling rotational speed of the output shaft, comprising: an outside rotor integrated with either one of the input and output shafts; an inside rotor integrated with a remaining one of the two shafts and fitted into the outside rotor, with an annular chamber being formed between the two rotors and being filled with actuating fluid; first means set on either one of the two rotors to project into the chamber and used for selectively moving the actuating fluid while pressurizing the fluid in the chamber; and second means set on a remaining one of the two rotors to be alternated with the first means and used for controlling an opening area of the chamber, thus selectively stopping a movement of the fluid in the chamber to transmit rotational force between the two rotors, with either one rotor, having relatively
  • FIG. 1 is a partially broken perspective view of a hydraulic, rotary transmission system in accordance with the primary embodiment of the present invention
  • Fig. 2 is a cross-sectioned view of the system of Fig. 1;
  • Fig. 3 is a longitudinal sectioned view of the above system taken along the line I-I of Fig. 2;
  • Fig. 4 is a cross-sectioned view of a hydraulic, rotary transmission system in accordance with the second embodiment of the present invention.
  • Fig. 5 is a longitudinal sectioned view of the system taken along the line II-II of Fig. 4;
  • Fig. 6 is a cross-sectioned view of a hydraulic, rotary transmission system in accordance with the third embodiment of the present invention.
  • Fig. 7 is a cross-sectioned view of a hydraulic, rotary transmission system in accordance with the fourth embodiment of the present invention.
  • Fig. 8 is a cross-sectioned view of a hydraulic, rotary transmission system in accordance with the fifth embodiment of the present invention
  • Fig. 9 is a longitudinal sectioned view of the system taken along the line III-III of Fig. 8;
  • Fig. 10 is a longitudinal sectioned view of a hydraulic, rotary transmission system in accordance with the sixth embodiment of the present invention.
  • Fig. 11 is a block diagram showing the operation of the control unit for the system of Fig. 1.
  • Figs. 1 to 3 show a hydraulic, rotary transmission system in accordance with the primary embodiment of this invention.
  • Fig. 1 is a partially broken perspective view showing the whole construction of the above system
  • Fig. 2 is a cross-sectioned view of the system of Fig. 1
  • Fig. 3 is a longitudinal sectioned view of the above system taken along the line I-I of Fig. 2.
  • the system of this invention comprises an input shaft 2, an output shaft 3 and two rotors, that is, outside and inside rotors 20 and 30.
  • the input shaft 2 is directly connected to a power source 1, such as a motor or an engine, thus being used as a driving shaft for outputting the power of the source 1.
  • the output shaft 3 receives the power from the input shaft 2 and transmits the power to a drive part of a machine.
  • the two rotors 20 and 30 are installed at the junction between the two shafts 2 and 3 with actuating fluid filling the annular chamber formed between the two rotors. The two rotors 20 and 30 thus transmit the power from the input shaft 2 to the output shaft 3 while ,.
  • the outside rotor 20, positioned around the inside rotor 30 with an annular oil chamber or main chamber "C" being formed between the two rotors 20 and 30, is integrated with the input shaft 2, thus being rotatable along with the shaft 2. Meanwhile, the inside rotor 30 is integrated with the output shaft 3 and transmits the power from input shaft 2 to the output shaft 3.
  • a plurality of planetary rotors 25 and spring-biased vanes 35 are provided in the annular oil chamber "C" formed between the two rotors 20 and 30.
  • the planetary rotors 25 are held by the outside rotor 20 and are brought into movable contact with the exterior surface of the inside rotor 30, while the vanes 35 are held by the inside rotor 30 and are brought into contact with the interior surface of the outside rotor 20.
  • the actuating fluid, filling the chamber "C" is incompressible fluid.
  • the rotational force, transmitted from the input shaft 2 to the outside rotor 20, is also transmitted to the incompressible actuating fluid through the planetary rotors 25 of the outside rotor 20, thus causing the fluid to flow in the chamber "C" .
  • the vanes 35 of the inside rotor 30 are thus rotated, so that the inside rotor 30 is rotated.
  • the system is designed for transmitting the power of the power source 1 to the output shaft 3 in a way such that the rotational force of the outside rotor 20 integrated with the input shaft 2 is hydraulically transmitted to both the inside rotor 30 and the output shaft 3.
  • a bypass passage 20L is formed on the outside rotor 20 with both ends of the bypass passage 20L opening into the main chamber "C" at opposite sides of each planetary rotor 25.
  • a check valve 21 is provided in each of the bypass passages 20L for controlling the amount of bypass fluid.
  • the hydraulic force, acting on the vanes 35 is in inverse proportion to the opening area of both the chamber "C” and the passages 20L. Meanwhile, the rotating speed of both the inside rotor 30 and the output shaft 3 is in proportion to the hydraulic force acting on the vanes 35. That is, when the opening areas of both the chamber “C” and the passages 20L are enlarged, the hydraulic force, acting on the vanes 35, is reduced and this reduces the rotating speed of the output shaft 30. On the contrary, when the opening areas of both the chamber "C” and the passages 20L are reduced, the hydraulic force, acting on the vanes 35, is increased and this increases the rotating speed of the output shaft 30.
  • the outside rotor 20 is integrated with the input shaft 2 and has an opening for receiving the inside rotor 30, thus having an annular configuration.
  • a groove 20a is formed along the interior surface of the outside rotor 20.
  • the above groove 20a forms the annular chamber "C" in cooperation with the external surface of the inside rotor 30.
  • the planetary rotors 25 are regularly set on the groove 20a.
  • the above rotors 25 are designed for being revolvable around the external surface of the inside rotor 30 and being rotatable around its central axis while moving the actuating fluid in the rotating direction of the input shaft 2.
  • a planetary gear 25G is fixed to an end of each planetary rotor 25 and engages with a rotor gear 30G which is fixed to an end Of the inside rotor 30.
  • the planetary rotors 25 are thus revolvable around the inside rotor 30 at the same speed while always coming into close contact with the inside rotor 30.
  • a groove 25a is axially formed on the outer surface of each planetary rotor 25 to receive the top edges of the vanes 35.
  • a check valve 21 is provided in each of the bypass passages 20L of the outside rotor 20.
  • a valve sleeve 22 for the check valve 21 axially moves along the input shaft 2. Therefore, a valve rod 22a, connected to the valve sleeve 22, moves the check valve 21, thus controlling the opening area of the bypass passage 20L.
  • a circular opening 20b is formed on a side wall of the outside rotor 20 at a position around the output shaft
  • Both an oil seal 45 and a bearing 46 are installed in the opening 20b.
  • the above seal 45 tightly closes the opening 20b.
  • An annular hole is formed around the circular opening 20b, while a vane sleeve 40, provided with a vane contact 40a, is led into the above annular hole at the contact 40a.
  • the above vane sleeve 40 is for selectively moving the vanes 35 of the inside rotor 30.
  • a plurality of spring-biased vanes 35 are set on the external surface of the inside rotor 30 to control the opening area of the main chamber "C".
  • the above vanes 35 are radially set in the vane holes formed on the inside rotor 30 and are individually and radially biased upwardly by a spring 36, thus being radially movable in opposite directions.
  • the vane contact 40a of the sleeve 40 is led to a side wall of the inside rotor 30 and selectively comes into contact with the side surfaces of the vanes 35 at inclined cams "D", thus moving the vanes 35 downwardly in the radial direction to gradually open the main chamber "C".
  • an annular slot 35b is formed on the side wall of the inside rotor 30.
  • a spring 36 is set in each vane hole of the inside rotor 30 at a position under each vane 35, thus normally biasing the vane 35 upwardly in the radial direction. That is, the above spring 36 biases an associated vane 35 in a direction opposite to the acting direction of the vane sleeve 40, thus allowing the vane 35 to be brought into elastic and close contact with the interior surface of the outside rotor 20.
  • each spring 36 it is preferable to set the elasticity of each spring 36 to a level at which the vanes 35 automatically move downwardly in the vane holes to open the chamber “C” when the inner pressure of the main chamber “C” becomes higher than a preset limit pressure due to an exceeding overload acting on the output shaft 3 with the chamber “C” being completely closed by the vanes 35.
  • the vane sleeve 40 Since the vane contact 40a of the sleeve 40 axially passes through the side wall of the outside rotor 20, the vane sleeve 40 is rotatable at the same speed as the rotating speed of the outside rotor 20. In order to prevent the rotational force of the vane sleeve 40 from being directly transmitted to the output shaft 3, the vane sleeve 40 is designed for being idle-rotatable around the output shaft 3.
  • the system of this invention is designed in that the rotational force of the input shaft 2 is normally and hydraulically transmitted to both the inside rotor 30 and the output shaft 3 through the outside rotor 20.
  • the actuating fluid in the chamber "C" practically transmits the rotational force from the outside rotor 20 to both the inside rotor 30 and the output shaft 3.
  • both the output shaft 3 and the vane sleeve 40 are provided with spline gears 3a and 40b, respectively.
  • the two gears 3a and 40b are set on the output shaft 3 and the vane sleeve 40, respectively, at positions where the vane sleeve 40 does not restrict the vanes 35.
  • the two gears 3a and- Ob. selectively engage with each other to bring the vane sleeve 40 into engagement with the output shaft 3.
  • the above vane sleeve 40 is designed for moving along the output shaft 3 by a second actuator 41 to move the vanes 35.
  • the above actuator 41 is operated under the control of the control unit 60.
  • the first and second actuators 23 and 41 are designed in that their actuating rods hydraulically move in an axial direction under the control of the control unit 60, thus operating the valve sleeve 22 and the vane sleeve 40, respectively.
  • the actuating rods of the two actuators 23 and 41 are actuated by both hydraulic force of a hydraulic mechanism and spring force of an internal spring.
  • conventional solenoid actuators which are operated in response to electric signals, may be used as the above actuators 23 and 41 in place of the above-mentioned hydraulic actuators.
  • the control unit 60 receives both a clutch signal from a clutch pedal 61 and a speed signal from a shift lever 62.
  • the clutch pedal 61 is selectively operated by a driver to controllably transmit the rotating force from the input shaft 2 to the output shaft 3.
  • the pedal 61 outputs such a clutch signal to the control unit 60.
  • the shift lever 62 is selectively operated by the driver to convert the position of the shafts 2 and 3 from a half-clutching position into a full-clutching position.
  • the lever 62 outputs such a speed signal to the control unit 60.
  • the control unit 60 controls the operation of the two actuators 23 and 41 to control both the opening area of the check valves 21 and the projecting height of the vanes 35 in the chamber "C".
  • the above control unit 60 also checks the operational condition of the system when receiving a signal from one or both the pedal and lever 61 and 62 with both rotating speed and torque of each shaft 2, 3 being received by the
  • control unit 60 controls the actuators 23 and 41 and a speed gear 50.
  • the operational effect of the system according to the primary embodiment will be described hereinbelow.
  • the above system is designed for selectively transmitting the rotational force from the input shaft 2 to the output shaft 3. That is, the system may stop the power transmission from the input shaft 2 to the output shaft 3. In addition, the system may transmit the rotational force from the input shaft 2 to the output haft 3 while converting the position of the two shafts 2 and 3 from a half-clutching position into a full- clutching position.
  • the actuator 41 pushes the vane sleeve 40 to the inside rotor 30.
  • the vane sleeve 40 slides along the output shaft 3, so that the vane contact 40a of the sleeve 40 is received into the annular slot 35b of the inside rotor 30.
  • the vane contact 40a thus comes into contact with the vanes 35 at the inclined cams "D", thus retracting the vanes 35 into the vane holes of the rotor 30. Therefore, the chamber "C" is fully opened.
  • the rotational force of both the power source 1 and the input shaft 2 is transmitted to the outside rotor 20.
  • the planetary rotors 25 revolve around the outer surface of the inside rotor 30 while moving the actuating fluid in the rotating direction of the outside rotor 20.
  • the vanes 35 are fully retracted into the vane holes of the inside rotor 30, the vanes 35 fail to receive the rotational force or the moving force of the fluid.
  • the rotational force of the outside rotor 20 is thus not transmitted to either the inside rotor 30 or the output shaft 3.
  • the first actuator 23 is operated in response to a signal from the control unit 60, thus pulling the valve sleeve 22.
  • the valve sleeve 22 moves along the input shaft 2 in a direction toward the end of the shaft 2, so that the check valves 21, coupled to the valve sleeve 22 through the valve rods 22a, moves in the same direction.
  • the bypass passages 20L are thus fully opened.
  • both the main chamber "C” and the bypass passages 20L are fully closed to allow the hydraulic force of the actuating fluid to act on the vanes 35.
  • the opening area of the chamber "C” is changed by the vanes 35.
  • both the check valves 21 and the valve sleeve 22 move forward along the input shaft 2 to close the bypass passages 20L.
  • the actuating fluid in the chamber "C” flows around the inside rotor 30 along with the planetary rotors 25 due to the rotational force of the outside rotor 20.
  • control unit 60 starts the second actuator 41 for the vanes 35, thus pulling the vane sleeve 40 in a direction toward the outside of the output shaft 3.
  • the above vanes 35 thus gradually project into the chamber “C” by the restoring force of the springs 36.
  • the rotational force of the power source 1 is primarily transmitted to the planetary rotors 25 through both the input shaft 2 and the outside rotor 20. Due to the rotational force of the planetary rotors 25, the actuating fluid in the chamber “C” is pressurized and moves in the chamber “C” to act on the vanes 35. Therefore, the inside rotor 30, with the vanes 35, is rotated along with the output shaft 3. The rotational force of the power source 1 is transmitted to the output shaft 3, thus rotating the output shaft 3.
  • the actuating fluid in the chamber “C” becomes free, so that it is possible to reduce the generation of heat from the actuating fluid pressurized between the planetary rotors 25 and the vanes 35.
  • the rotational speed of the output shaft 3 may be controlled by controlling the projecting height of the vanes 35 in the chamber “C”. Alternatively, such rotational speed of the output shaft 3 may be controlled by controlling the opening area of the bypass passages 20L with the vanes 35 completely closing the chamber "C".
  • a speed gear 50 such as a manual or automatic transmission system for automobiles
  • the system of this invention can transmit the rotational force from the input shaft 2 to the output shaft 3 while controlling or changing the rotational speed of the output shaft 3.
  • the system of this invention somewhat freely changes the rotational speed in the same manner as a conventional nonstop variable speed gear.
  • the outside rotor 20 is integrated with the input shaft 2, while the inside rotor 30 is integrated 'with the output shaft 3.
  • the system of this invention may be designed in that the outside and inside rotors 20 and 30 are integrated with the output and input shafts 3 and 2, respectively.
  • both the check valves 21 and the vanes 35 are mechanically operated by the actuators 23 and 41 and the sleeves 22 and 40 in the primary embodiment.
  • the system of this invention may be designed in that both the check valves 21 and the vanes 35 are operated by hydraulic pressure or electric signals.
  • either one rotor, having relatively higher rotational force acts as a conventional hydraulic pump, while a remaining rotor, having relatively lower rotational force, acts as a conventional hydraulic motor.
  • Figs. 4 to 10 show hydraulic, rotary transmission systems in accordance with the other embodiments of this invention, respectively.
  • a plurality of planetary rotors 135 are set on the inside rotor 130, while a plurality of vanes 125 are set on the outside rotor 120.
  • vanes 125 radially set on the interior surface of the outside rotor 120 integrated with the input shaft 102, are individually biased by a spring 126.
  • the above vanes 125 are thus elastically movable in a radial direction to control the opening area of the chamber "C".
  • the planetary rotors 135 are set on the exterior surface of the inside rotor 130 and are brought into close and movable contact with the interior surface of the outside rotor 120.
  • the above planetary rotors 135 are designed for being revolvable and rot ' atabie while moving the actuating fluid in the rotating direction of the input shaft 120.
  • the rotational force of the input shaft 102 is primarily transmitted to the actuating fluid through the outside rotor 120 integrated with the input shaft 102.
  • the hydraulic force of the actuating fluid is changed in accordance with the opening area of the chamber "C rt controlled by the spring-biased vanes 125.
  • the pressurized fluid thus pushes the planetary rotors 135 and rotates the inside rotor 130, so that the rotational force of the input shaft 102 is transmitted to the output shaft 103.
  • Fig. 6 is a cross-sectioned view of a hydraulic, rotary transmission system in accordance with the third embodiment of this invention.
  • the system is free from any gears or planetary rotors, but is provided with vanes 225 and 235 at the outside and inside rotors 220 and 230.
  • the vanes 235 of the inside rotor 230 are movable vanes capable of being radially movable to control the chamber "C" .
  • the vanes 225 of the outside rotor 220 are fixed vanes coming into close contact with the exterior surface of the inside rotor 230.
  • the movable vanes 235 are individually biased by a spring 236, so that the movable vanes 235 elastically retract into the vane holes when the vanes 235 come into contact with the fixed vanes 225.
  • the movable vanes 235 elastically return to the projecting position when the vanes 235 are free from the fixed vanes 225.
  • the top edge of each of the two types of vanes 225 and 235 is inclined, so that the fixed vanes 225 smoothly pass over the movable vanes 235 without interfering with the movable vanes 235.
  • both the check valves and bypass passages are formed in the system in the same manner as that described for the primary and second embodiments.
  • the movable vanes 235 may be designed for being mechanically movable in a radial direction by a vane sleeve or being hydraulically movable in the radial direction.
  • the system of the third embodiment is operated as a one way clutch, so that the system does not exert any effect on the input shaft.
  • Fig. 7 is a cross-sectioned view of a hydraulic, rotary transmission system in accordance with the fourth embodiment of this invention.
  • the general shape of the system remains the same as that of the third embodiment, but all vanes 325 and 335, provided on both rotors 320 and 330, are designed for being movable different from the system of the third embodiment.
  • each of the vanes 325 and 335 is biased by a spring 326 and 336 at its lower end.
  • Figs. 8 and 9 show a hydraulic, rotary transmission system in accordance with the fifth embodiment of this invention.
  • the outside rotor 420 is free from any planetary rotors or vanes, but the interior surface of the outside rotor 420 is shaped into an elliptical configuration capable of circumscribing the circular exterior surface of the inside rotor 430 at two variable points.
  • the inside rotor 430 has a circular configuration capable of being inscribed with the elliptical interior surface of the outside rotor 420, thus forming two variable crescent oil chambers "C" between the two rotors 420 and 430.
  • Two movable vanes 435 are set on the inside rotor 430 at diametrically opposite positions to control the two chambers "C", respectively.
  • the above movable vanes 435 of the inside rotor 430 have to be designed in that they are movable in a radial direction.
  • the vanes 435 are externally controlled in the same manner as that described for the primary embodiment.
  • Two bypass passages 420L are formed on the interior surface of the outside rotor 420 at positions around the inscribed points of the inside rotor 430.
  • a check valve 421 is set in each of the bypass passages 420L.
  • the system of the fifth embodiment selectively transmits the rotational force of the outside rotor 420 to the inside rotor 430 through the actuating fluid while changing the speed of the inside rotor 430 in accordance with the opening area of both the chambers "C" and the bypass passages 420L.
  • the movable vanes 435 are designed in that they are radially movable in accordance with the hydraulic pressure applied from the oil passages 403a and 430a of both the output shaft 403 and the inside rotor 430.
  • a solenoid valve 441 is installed on the oil line 440 for the first oil passage 403a, thus controlling the hydraulic pressure in response to an external signal.
  • FIG. 10 is a longitudinal sectioned view of a hydraulic, rotary transmission system in accordance with the sixth embodiment of this invention.
  • two rotors 520 and 530 used for controllably transmitting rotational force from an input shaft 502 to an output shaft 503, are oppositely and coaxially positioned on the input and output shafts 502 and 503, respectively, different from the primary to fifth embodiments where an outside rotor is fitted over an inside rotor.
  • the two rotors 520 and 530 are commonly cased by a casing 510 which is supported on the two shafts 502 and 503 by bearings 515.
  • An annular oil chamber “C” is externally formed at the junction between the two rotors 520 and 530.
  • First and second vanes 525 and 535 are respectively set on the two rotors 520 and 530 to controllably transmit the rotational force from the first rotor 520 to the second rotor 530 while controlling the opening area of the chamber "C".
  • the above vanes 525 and 535 are respectively biased by springs 526 and 536, thus being movable in a radial direction.
  • the casing 510 may be fixed to either rotor 520 or 530.
  • the present invention provides a hydraulic, rotary transmission system capable of transmitting rotational force from an input shaft to an output shaft while controlling or changing the rotating speed of the output shaft using the hydraulic force of actuating fluid filling an oil chamber formed between two rotors integrated with the input and output shafts.
  • the system thus easily transmits the rotational force of the input to the output shaft while changing the rotational speed of the output shaft.
  • Another advantage of the system resides in that the system has a simple construction.
  • the system of this invention is also designed in that the hydraulic force of the actuating fluid filling the oil ' chamber is hydrostaticfe'lly transmitted to the output shaft by a first means or a chamber closing means, such as vanes, without any flow loss of the fluid. Therefore, the system remarkably improves power transmission efficiency, thus effectively conserving energy in comparison with conventional torque converters or hydraulic couplings.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)

Abstract

Cette invention se rapporte à un système hydraulique de transmission rotative. Ce système transmet une force de rotation provenant d'une entrée (2) à un arbre mené (3) tout en régulant ou en modifiant la vitesse de rotation de l'arbre mené au moyen d'une force hydraulique exercée par un fluide d'actionnement qui remplit une chambre à huile 'C' formée entre deux rotors (20, 30) associés aux arbres menant et mené (2, 3). Ce système est également conçu de manière que la force hydraulique exercée par le fluide est transmise de manière hydrostatique à l'arbre mené au moyen d'un organe de fermeture de la chambre, tel que des aubes (35), sans aucune réduction d'écoulement du fluide. Ce système accroît considérablement l'efficacité de transmission de puissance et économise efficacement l'énergie par rapport aux convertisseurs de couple ou aux coupleurs hydrauliques classiques.
PCT/KR1998/000251 1997-08-13 1998-08-12 Systeme hydraulique de transmission rotative Ceased WO1999009331A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1019970038637A KR100259397B1 (ko) 1997-08-13 1997-08-13 유체를 이용한 로터리형 동력전달장치
KR1997/38637 1997-08-13

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WO1999009331A1 true WO1999009331A1 (fr) 1999-02-25

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PCT/KR1998/000251 Ceased WO1999009331A1 (fr) 1997-08-13 1998-08-12 Systeme hydraulique de transmission rotative

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WO (1) WO1999009331A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
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CN112392931A (zh) * 2020-12-01 2021-02-23 广西星云电机械制造有限公司 一种液压离心力变速器

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KR101346013B1 (ko) 2011-12-28 2013-12-31 주식회사평화발레오 전기구동 차량의 드라이브라인 조립 구조
KR101495086B1 (ko) * 2013-05-30 2015-02-25 주식회사평화발레오 더블 클러치와 트랙션 모터의 연결 구조

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FR1115708A (fr) * 1954-09-07 1956-04-27 Appareil régulateur de vitesses notamment utilisé sur les véhicules automobiles
DE1240345B (de) * 1961-09-05 1967-05-11 Uetersener Maschinenfabrik Hat Hydrostatische Regelkupplung
GB2211918A (en) * 1987-11-04 1989-07-12 Joseph Gardner Torque-controlled hydraulic coupling
WO1995035453A1 (fr) * 1994-06-22 1995-12-28 Entrepreneurial Technologies, Inc. Embrayage rotatif active par pression

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FR1115708A (fr) * 1954-09-07 1956-04-27 Appareil régulateur de vitesses notamment utilisé sur les véhicules automobiles
DE1240345B (de) * 1961-09-05 1967-05-11 Uetersener Maschinenfabrik Hat Hydrostatische Regelkupplung
GB2211918A (en) * 1987-11-04 1989-07-12 Joseph Gardner Torque-controlled hydraulic coupling
WO1995035453A1 (fr) * 1994-06-22 1995-12-28 Entrepreneurial Technologies, Inc. Embrayage rotatif active par pression

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112392931A (zh) * 2020-12-01 2021-02-23 广西星云电机械制造有限公司 一种液压离心力变速器

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