WO2007092708A1 - Pompe utilisant l'énergie l'énergie de torsion d'un arbre rotatif ou non rotatif - Google Patents

Pompe utilisant l'énergie l'énergie de torsion d'un arbre rotatif ou non rotatif Download PDF

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Publication number
WO2007092708A1
WO2007092708A1 PCT/US2007/061332 US2007061332W WO2007092708A1 WO 2007092708 A1 WO2007092708 A1 WO 2007092708A1 US 2007061332 W US2007061332 W US 2007061332W WO 2007092708 A1 WO2007092708 A1 WO 2007092708A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
pump
chamber
shaft
vane
Prior art date
Application number
PCT/US2007/061332
Other languages
English (en)
Inventor
Roger T. Simpson
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
Application filed by Borgwarner Inc filed Critical Borgwarner Inc
Publication of WO2007092708A1 publication Critical patent/WO2007092708A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C9/00—Oscillating-piston machines or pumps
    • F04C9/002—Oscillating-piston machines or pumps the piston oscillating around a fixed axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/162—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material with forced fluid circulation

Definitions

  • the invention pertains to the field of pumps. More particularly, the invention pertains to a pump that uses torsional energy from a rotating shaft to operate.
  • Figure 1 shows a graph of the relationship of the torsional energy of the crankshaft of an 14 engine and second order resonance generated as oscillation of the crankshaft and speed increase.
  • the torsional energy of the crankshaft shown by the dashed line, is high when the crank oscillation is high and the average speed is low.
  • the torsional energy decreases as the average speed increases and the crank oscillation decreases.
  • the ends of the crankshaft twist and go into resonance, indicated by the unbroken line as shown in Figure 1. Since the firing frequency occurs twice per crank revolution, a second order resonance occurs as the engine speed increases.
  • dampers are added to the crankshaft.
  • One type of damper splits the crank resonance shown by the unbroken line of Figure 2 into two lower frequencies, indicated by the dash-dot line, that are opposite of the crank resonance.
  • a friction damper Another type of damper used to prevent resonance is a friction damper. By creating friction between a damper and the crankshaft, the twisting and resulting resonance of the crankshaft can be lowered or counteracted at higher speeds. Weights added to the crankshaft are one example of a friction damper.
  • the pump is comprised of a ring, a housing, a rotor, first and second return springs, inlet passages, and outlet passages.
  • the ring surrounds and is fixedly attached to a housing.
  • the rotor connects to a shaft coaxially located within the housing.
  • the housing and the rotor define at least one vane separating a chamber in the housing into an advance and a retard chamber.
  • a first return spring is received between the housing and the vane in the advance chamber and a second return spring is received between the housing and the vane in the retard chamber.
  • Inlet passages are present between a supply and the advance chamber and the supply and the retard chamber.
  • Each of the passages have at least one inlet check valve.
  • Outlet passages are present between the advance chamber and an output and the retard chamber and an output.
  • Each of the passages has at least one outlet check valve.
  • the shaft may be rotating or non-rotating.
  • the rotating shaft may be a crankshaft or a camshaft.
  • the non-rotating shaft may be variable displacement control shafts or other shafts that have reciprocating motion.
  • the torsional pump uses the torsional energy from the shaft to damper or eliminate torsional vibration of a crankshaft over the entire speed range of the engine, instead of just at the crankshaft resonance speed.
  • FIG. 1 shows a graph of the filing frequency order and the fourth order of resonance as related to crank oscillation and average speed.
  • Fig. 2 shows a graph of the tuned absorber signal and the crank resonance as related to crank oscillation and average speed.
  • Fig. 3 shows a graph of the torsional pump resonance of the present invention and the crank resonance as related to crank oscillation and average speed.
  • Fig. 4 shows a graph comparing the output pressure of the torsional pump of the present invention and the output pressure of a conventional pump as related to pressure, speed, and the amount of pressure need by the engine.
  • Fig. 5 shows a graph comparing the output pressure of the torsional pump of the present invention and the output pressure of a downsized conventional pump as related to pressure, speed, and the amount of pressure needed by the engine.
  • Fig. 6 shows a schematic of the torsional pump of the present invention showing a pumping loop with negative torque pulses.
  • Fig. 7 shows a schematic of the torsional pump of the present invention showing a pumping loop with positive torque pulses.
  • Fig. 8 shows an exploded view of the torsional pump of the present invention.
  • Fig. 9 shows a top view of the torsional pump of the present invention.
  • Fig. 10 shows an isometric view of the torsional pump of the present invention.
  • Fig. 11 shows a side view of the torsional pump of the present invention.
  • Fig. 12 shows a schematic of a torsional pump of an alternate embodiment showing a pumping loop with negative torque pulses.
  • Fig. 13 shows a schematic of a torsional pump of an alternate embodiment showing a pumping loop with positive torque pulses.
  • Figures 6 through 11 show a torsional pump of a first embodiment that uses torsional energy from a rotating shaft or a non-rotating shaft to function.
  • An inertia ring Ib and a mating housing Ia form a complete housing 1 that surrounds a rotor 3 attached to a rotating shaft or a non-rotating shaft 22.
  • the inertia ring Ib has the necessary mass to delay or lag the motion of the ring so that there is relative motion between the rotor 3 and the housing Ia.
  • the rotor 3 has one or more vanes 6 mounted to the end of the shaft 22, which are surrounded by the housing 1.
  • the housing 1 and the rotor 3 form chambers into which the vanes fit.
  • the vanes 6 separate each chamber into an advance chamber 2 and a retard chamber 4.
  • An advance return spring 18 is present in the advance chamber 2 with one end of the spring 18 received by a bore 25 a in the mating housing Ia and the other end received by a bore 6a in the vane 6.
  • a retard return spring 17 is present in the retard chamber 4 with one end of the spring 17 received by a bore 25b in the mating housing Ia and the other end received by a bore 6b in the vane 6.
  • the return springs 17, 18 keep the rotor 3 in between the ends stops, preventing the vane 6 from slamming into the mating housing Ia on either side of the vane 6 and allowing the position of the rotor 3 to be adjusted.
  • a front end plate 23 is placed relative to one side of the housing 1 and an end plate 21 is placed on the other side of the housing 1 and receives the shaft 22.
  • the front end plate 23 is secured to the rotor 3 and the end plate 21 using bolts
  • the pump supply 8 supplies fluid through line 16 to either the advance chamber 2 through inlet check valve 14 and inlet line 19 or to the retard chamber 4 through inlet check valve 15 and inlet line 20. Fluid exits the advance chamber 2 through outlet line 12, outlet check valve 5, and outlet line 10 to the output flow line 9. Fluid exits the retard chamber 4 through outlet line 13, outlet check valve 7, and outlet line 11 to the output flow line 9.
  • the output flow from line 9 and the pressure may be used for general engine lubrication and other hydraulic devices in the engine such as hydraulic tensioners, hydraulic lash adjusters, and piston squirters.
  • the housing 1 has a large inertia so that when the input shaft 22 has some torsional excitation the motion of the housing 1 will lag the rotor 3 so that there is some relative motion between the rotor 3 and the housing 1.
  • oil or hydraulic fluid is pushed out of the retard chamber 4 into line 13 and through outlet check valve 7 to line 11 and the output flow line 9.
  • pump supply 8 supplies fluid through line 16 and inlet check valve 14 to line 19 and the advance chamber 2.
  • pump supply 8 supplies fluid through line 16 and inlet check valve 15 to line 20 and the retard chamber 4 as shown in Figure 7.
  • the oil pressure from the pump supply 8 varies, depending on the torsional input.
  • Figures 12 and 13 show a torsional pump of another embodiment that uses torsional energy from a rotating or non-rotating shaft to function.
  • the inertia ring Ib has the necessary mass to delay or lag the motion of the ring so that there is relative motion between the rotor 3 and the housing Ia.
  • the rotor 3 has one or more vanes 6 mounted to the end of the shaft 22, which are surrounded by the housing 1.
  • the housing 1 and the rotor 3 form chambers into which the vanes fit.
  • the vanes 6 separate each chamber into an advance chamber 2 and a retard chamber 4.
  • An advance return spring 18 is present in the advance chamber 2 with one end of the spring 18 received by a bore 25a in the mating housing Ia and the other end received by a bore 6a in the vane 6.
  • a retard return spring 17 is present in the retard chamber 4 with one end of the spring 17 received by a bore 25b in the mating housing Ia and the other end received by a bore 6b in the vane 6.
  • the return springs 17, 18 keep the rotor 3 in between the ends stops, preventing the vane 6 from slamming into the mating housing Ia on either side of the vane 6 and allowing the position of the rotor 3 to be adjusted.
  • the pump supply 8 supplies fluid through line 16 to either the advance chamber 2 through inlet check valve 14 and inlet line 19 or to the retard chamber 4 through inlet check valve 15 and inlet line 20. Fluid exits the advance chamber 2 through outlet line 12, outlet check valve 5, outlet line 10, and the output flow line 9 to the accumulator (not shown) and the regulator valve 30. Fluid exits the retard chamber 4 through outlet line 13, outlet check valve 7, outlet line 10, and the output flow line 9 to the accumulator (not shown) and the regulator valve 30.
  • the regulator valve 30 sets the pressure to a fixed value, but may adjust the pressure of the torsional pump depending on the operation conditions of the engine.
  • the pressure regulator valve 30 is comprised of an exhaust passage 30b, a spool 31 with lands 31a, 31b received within a sleeve 30e for blocking passage to and from the exhaust line 30b, a spring 30a, and a piece 30c.
  • the pressure from outlet flow line 9 biases one end of the spool 31 against the spring 30a, depending on how high the output pressure is.
  • the housing 1 has a large inertia so that when the input shaft 22 has some torsional excitation the motion of the housing 1 will lag the rotor 3 so that there is some relative motion between the rotor 3 and the housing 1.
  • oil or hydraulic fluid is pushed out of the retard chamber 4 into line 13 and through outlet check valve 7 to line 10 and line 9 and an accumulator (not shown) prior to entering the regulator valve 30.
  • pump supply 8 supplies fluid through line 16 and inlet check valve 14 to line 19 and the advance chamber 2.
  • the rotating shaft with torsional energy in the above embodiments may be camshafts and crankshafts.
  • the non-rotating shaft of the above embodiments may be variable displacement control shafts and any shaft that has reciprocating motion.
  • the inertia ring Ib of the torsional pumps in the above embodiments may be used to drive the front end accessory drive (FEAD) belt or the vehicle's transmission.
  • FEAD front end accessory drive
  • the torsional pump of the above embodiments may also be used or applied to an engine or transmission of an automobile.
  • the torsional pumps of the above embodiments may be used as a friction type damper to prevent or help decrease crankshaft resonance.
  • the shaft torsional excitation can be reduced as shown in Figure 3.
  • the pump can take the energy from the shaft 22 by adjusting the output pressure or flow out of line 9 or adjusting the flow rate of fluid into the pump from the pump supply 8.
  • the torsional vibration damper on a conventional rotating or non-rotating shaft may be eliminated and torsional vibration can be controlled over the entire speed range rather then just at the crankshaft resonance speed.
  • FIG. 4 shows a graph of the output pressure of a conventional pump and the torsional pump of the present invention as speed increases in comparison to the output pressure needed by the engine.
  • the dashed line shows the output pressure needed from the pump as the engine speed increases.
  • the unbroken line shows the output pressure of a conventional pump.
  • the output pressure of a conventional pump is low when the speed of the engine is low, and does not meet the necessary pressure needed by the engine.
  • the output pressure of the conventional pump increases.
  • the output of the conventional pump is significantly greater than pressure actually needed by the engine.
  • the output pressure of the torsional pump of the present invention is shown by the dash dot line and is high at low speeds and below what the engine requires at high speeds.
  • Figure 5 shows another graph of the output of pressure of the torsional pump of the present invention and a downsized conventional pump as speed increases in the comparison to the output of pressure needed by the engine.
  • the dashed line shows the output pressure needed from the pump as the engine speed increases.
  • the unbroken line shows the output pressure of a downsized conventional pump.
  • the output pressure is mostly below the pressure required by the engine and reaches only slightly greater than the pressure required by the engine as speed increases.
  • the output pressure of the torsional pump of the present invention is shown by the dash dot line and is high at low speeds and below what the engine requires at high speeds.

Abstract

L'invention concerne une pompe dans laquelle l'énergie de torsion d'un arbre est convertie en haute pression de manière qu'elle actionne la pompe. Une bague (16) entoure et est fixée à demeure sur un logement (1). Le rotor (3) est relié à un arbre (22) coaxialement monté dans le logement. Le logement et le rotor définissent au moins une aube (6) séparant une chambre située dans le logement en une chambre d'avancement (2) et une chambre de retard (4). Un premier ressort de rappel (18) est logé entre le logement et l'aube dans la chambre d'avancement et un second ressort de rappel (17) est logé entre le logement et l'aube située dans la chambre de retard. Des passages d'arrivée (19; 20) sont présents entre une alimentation et la chambre d'avancementment et la chambre de retard. Chaque passage comprend au moins une soupape d'aspiration (14; 15). Des passages de sortie (12;13) sont présents entre la chambre d'avancementment et une sortie et la chambre de retard et une sortie. Chaque passage comprend au moins une soupape de refoulement (5; 7).
PCT/US2007/061332 2006-02-03 2007-01-31 Pompe utilisant l'énergie l'énergie de torsion d'un arbre rotatif ou non rotatif WO2007092708A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US76550406P 2006-02-03 2006-02-03
US60/765,504 2006-02-03
US77343106P 2006-02-15 2006-02-15
US60/773,431 2006-02-15

Publications (1)

Publication Number Publication Date
WO2007092708A1 true WO2007092708A1 (fr) 2007-08-16

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Application Number Title Priority Date Filing Date
PCT/US2007/061332 WO2007092708A1 (fr) 2006-02-03 2007-01-31 Pompe utilisant l'énergie l'énergie de torsion d'un arbre rotatif ou non rotatif

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Country Link
WO (1) WO2007092708A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017060002A1 (fr) * 2015-10-05 2017-04-13 Continental Automotive Gmbh Amortisseur de vibrations pour une pompe d'alimentation haute pression, pompe d'alimentation haute pression munie d'un amortisseur de vibrations et procédé de commande d'un tel amortisseur de vibrations
WO2019086258A1 (fr) * 2017-11-03 2019-05-09 Hasse & Wrede Gmbh Amortisseur ou dispositif d'atténuation de vibrations de torsion
DE102015116581B4 (de) 2015-05-11 2022-02-10 Hyundai Motor Company Fahrzeug-Dämpfungsvorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB305527A (fr) * 1928-02-06 1929-11-21 Hugo Junkers
US2359819A (en) * 1944-01-25 1944-10-10 Irving W Bachrach Oscillating pump
GB842304A (en) * 1957-10-15 1960-07-27 Clarence Lamar Norsworthy Jr Improvements in oscillating vane motors, pumps, or the like
US5761969A (en) * 1994-02-25 1998-06-09 Simpson Industries, Inc. Torsional vibration damper

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB305527A (fr) * 1928-02-06 1929-11-21 Hugo Junkers
US2359819A (en) * 1944-01-25 1944-10-10 Irving W Bachrach Oscillating pump
GB842304A (en) * 1957-10-15 1960-07-27 Clarence Lamar Norsworthy Jr Improvements in oscillating vane motors, pumps, or the like
US5761969A (en) * 1994-02-25 1998-06-09 Simpson Industries, Inc. Torsional vibration damper

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015116581B4 (de) 2015-05-11 2022-02-10 Hyundai Motor Company Fahrzeug-Dämpfungsvorrichtung
WO2017060002A1 (fr) * 2015-10-05 2017-04-13 Continental Automotive Gmbh Amortisseur de vibrations pour une pompe d'alimentation haute pression, pompe d'alimentation haute pression munie d'un amortisseur de vibrations et procédé de commande d'un tel amortisseur de vibrations
KR20180061356A (ko) * 2015-10-05 2018-06-07 콘티넨탈 오토모티브 게엠베하 고압 연료 펌프용 진동 댐퍼, 진동 댐퍼를 갖는 고압 연료 펌프, 및 이러한 진동 댐퍼를 제어하기 위한 방법
CN108138905A (zh) * 2015-10-05 2018-06-08 大陆汽车有限公司 用于高压燃料泵的振动阻尼器、带有振动阻尼器的高压燃料泵和用于控制这种振动阻尼器的方法
KR102166582B1 (ko) 2015-10-05 2020-10-16 콘티넨탈 오토모티브 게엠베하 고압 연료 펌프용 진동 댐퍼, 진동 댐퍼를 갖는 고압 연료 펌프, 및 이러한 진동 댐퍼를 제어하기 위한 방법
WO2019086258A1 (fr) * 2017-11-03 2019-05-09 Hasse & Wrede Gmbh Amortisseur ou dispositif d'atténuation de vibrations de torsion
CN111295534A (zh) * 2017-11-03 2020-06-16 哈瑟 & 弗雷德有限公司 扭振阻尼器或扭振减振器
KR20200077585A (ko) * 2017-11-03 2020-06-30 하쎄 앤드 브레데 게엠베하 비틀림 진동 댐퍼 또는 비틀림 진동 흡수기
CN111295534B (zh) * 2017-11-03 2022-03-22 哈瑟&弗雷德有限公司 扭振阻尼器或扭振减振器
US11371581B2 (en) 2017-11-03 2022-06-28 Hasse & Wrede Gmbh Torsional vibration damper or torsional tuned mass damper
KR102433482B1 (ko) * 2017-11-03 2022-08-18 하쎄 앤드 브레데 게엠베하 비틀림 진동 댐퍼 또는 비틀림 진동 흡수기

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