WO2006115472A1 - Pompe/moteur efficace a perte d'energie reduite - Google Patents

Pompe/moteur efficace a perte d'energie reduite Download PDF

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Publication number
WO2006115472A1
WO2006115472A1 PCT/US2005/013532 US2005013532W WO2006115472A1 WO 2006115472 A1 WO2006115472 A1 WO 2006115472A1 US 2005013532 W US2005013532 W US 2005013532W WO 2006115472 A1 WO2006115472 A1 WO 2006115472A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
pump
motor
casing
back plate
Prior art date
Application number
PCT/US2005/013532
Other languages
English (en)
Inventor
Charles L. Gray, Jr.
Original Assignee
Government Of The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency
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 Government Of The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency filed Critical Government Of The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency
Priority to EP05737521A priority Critical patent/EP1875044A1/fr
Priority to PCT/US2005/013532 priority patent/WO2006115472A1/fr
Priority to CA002605407A priority patent/CA2605407A1/fr
Publication of WO2006115472A1 publication Critical patent/WO2006115472A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/328—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the axis of the cylinder barrel relative to the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels

Definitions

  • This disclosure relates generally to improvements of various components and systems commonly found in bent-axis pump/motors.
  • Bent-axis pump/motors provide a high degree of efficiency in converting energy supplied as a pressurized fluid, from a hydraulic accumulator, or some other pressurized fluid source, into kinetic energy. Additionally, bent-axis pump/motors provide a further advantage over many other hydraulic technologies, inasmuch as bent-axis pump/motors operate equally well as pumps or motors, providing the potential, in automotive applications, of reclaiming and storing kinetic energy during braking, for use during a subsequent acceleration.
  • FIG. 1 shows a simplified diagrammatical representation of a hydraulic pump/motor system 100.
  • the system 100 comprises a bent-axis pump/motor 102, which includes a casing 125, a yoke 118 and a cylinder barrel 104.
  • the cylinder barrel 104 has piston cylinders 106 radially spaced around a common center.
  • the barrel 104 is configured to rotate around an axis A.
  • Each of the cylinders 106 includes a piston 108 having a first end 110 positioned within the cylinder 106, and configured such that there is a pressure tight seal between the first end 110 of the piston 108 and the wall of the respective cylinder 106.
  • a second end 112 of each of the pistons 106 engages a drive plate 114, which is coupled to an input/output shaft 116 of the pump/motor 102.
  • the angle of the barrel 104 relative to the drive plate 114 dictates the displacement volume of the pump/motor 102 and hence the amount of energy converted by the pump/motor 102.
  • the angle of the barrel 104 is controlled by the yoke 118, which includes a back plate 119 to which the barrel 104 is rotatably coupled.
  • the yoke 118 further includes a pair of trunnions 120, 121 upon which the yoke 118 rotates, around an axis B.
  • the trunnions 120, 121 are received by apertures 122, 123 in the pump/motor casing 125, and their rotation is accommodated by bearings 126, 127 that are positioned within the apertures 122, 123 of the casing 125, and which encircle the trunnions 120, 122, respectively.
  • Fluid channels 128, 129 are coupled from the yoke 118, via a valve plate surface 130 of the back plate 119, to each of the cylinders 106 of the barrel 104, as the barrel 104 rotates over the valve plate 130.
  • the fluid channels 128, 129 run down respective arms 132, 133 of the yoke 118 to the trunnions 120, 121.
  • the channels 128, 129 within the yoke 118 terminate at the trunnions 120, 121 at respective ports 134, 135 that are positioned to couple with corresponding fluid ports 136, 137 within the pump/motor casing 125.
  • the fluid ports 136, 137 of the pump/motor casing 125 are each coupled to low- and high-pressure fluid sources 138, 140, via respective switching valves 142, 143 configured to selectively couple the low-pressure source 138 to one side of the pump/motor 102 via the arm 132 of the yoke 118 and the high- pressure source 140 to the other side of the pump/motor 102 via the other arm 133, or alternatively, to reverse this arrangement. In this way, the device can be selectively configured to apply rotational force to the output shaft 116 in a clockwise or counter-clockwise direction.
  • the coupling between the valves 142, 143 and the fluid ports 136, 137 of the pump/motor casing 125 is generally accomplished using respective pressure hoses 144, 145.
  • the casing 125 encloses the moving parts of the pump/motor 102.
  • the space 117 within the casing 125 is filled with hydraulic fluid and may be in fluid communication with the low-pressure fluid source 138 via a high volume, low loss fluid connection such as a large-bore pressure hose (not shown).
  • This connection maintains the fluid in the casing 125 at a pressure substantially equal to the pressure at the low-pressure fluid source 138.
  • the pump/motor casing 125 may be manufactured to withstand the pressure of the low-pressure fluid source 138. This pressure may be on the order of 100 to 300 psi.
  • fluid from the high-pressure source 140 is coupled to fluid port 137 of the pump/motor 102 by valve 143.
  • the other fluid port 136 is simultaneously coupled to the low-pressure fluid source 138 by the other valve 142.
  • High-pressure fluid enters the pump/motor 124 via the fluid port 137, passes from trunnion 121 , through the channel 129, to the valve plate 130 and into the cylinders 106, as the barrel 104 rotates over the valve plate 130.
  • the pistons 108 are sequentially driven against the drive plate 114, causing the drive plate 114 to rotate around a "bent" axis A to achieve displacement.
  • the fluid in the cylinders 106 is sequentially released through the valve plate 130 and into the channel 128, to be vented back through the valve 142 to the low-pressure fluid source 138.
  • energy from the high-pressure source 140 is converted to kinetic energy by the pump/motor 102 to be transmitted via the rotating shaft 116 to the drive train of the vehicle or other mechanical system.
  • the high- and low- pressure connections are reversed, such that the low-pressure source 138 is coupled by the valve 143 to the port 137, while the high-pressure source 140 is coupled by the valve 142 to the port 136.
  • the shaft 116 is driven, by the forward momentum of the vehicle, to rotate in the forward direction. Because the pressure connections have been reversed on the pump/motor 102, the pump/motor is now resisting the rotation of the shaft 116.
  • the vehicle is slowed and, at the same time, fluid is drawn from the low-pressure side of the circuit and forced into the high-pressure fluid source 138, the pump/motor 102 functioning as a pump to store energy to be used subsequently.
  • This is commonly referred to as regenerative braking.
  • a bent axis pump/motor including a casing configured to be substantially filled with fluid, a back plate positioned within the casing and configured to receive or include a valve plate, and a check valve positioned in the back-plate and configured to permit passage of fluid from within the casing and outside of the back plate through the check valve to an interior of the back plate.
  • the check valve is further configured to restrict flow of fluid from the interior of the back plate through the check valve.
  • the casing of the pump/motor comprises first and second apertures positioned coaxially on opposite sides of the casing and traversing from the interior of the casing to the exterior thereof.
  • the pump motor further comprises a yoke coupled to the back plate.
  • the yoke includes first and second trunnions positioned within the first and second apertures, respectively, and the yoke is configured to rotate on the trunnions around an axis.
  • First and second bearings are positioned between the first and second trunnions and an inner wall of each of the first and second apertures, respectively, the position of each of the first and second bearings further defined by respective inner and outer planes, parallel to each other and transverse to the axis, with the respective bearing positioned therebetween.
  • Each of the first and second bearings occupies less than the complete circumference of the respective trunnion.
  • Each of the trunnions includes a respective aperture for passage of fluid therethrough, positioned between the inner and outer planes in a portion of the circumference not occupied by the bearing.
  • the pump/motor includes first and second fluid supply channels formed integrally with the casing.
  • the supply channels are configured to transmit fluid from valves or other fluid switching means to the first and second trunnions via apertures provided within the first and second apertures and positioned and configured to couple with the apertures provided in the trunnions.
  • a further embodiment of the invention provides a valve positioned within the casing and configured to selectively couple high- and low-pressure fluid supplies to the first and second trunnions, via the first and second fluid supply channels.
  • a yoke configured to carry a rotatable barrel
  • a trunnion coupled to the yoke and configured to be received by an aperture of a pump casing, and further configured to receive a bearing between the trunnion and a wall of the aperture in a position defined by two parallel planes transverse to an axis of the trunnion, and a fluid channel passing within the yoke to the trunnion and exiting the trunnion via an aperture positioned between the two planes.
  • a pump/motor having a casing configured to receive components of the pump/motor, a valve configured to selectively control fluid flow, the valve including a valve body, integral to the casing; and a first fluid channel, integral to the frame, having a first terminus at the valve and a second terminus at a first fluid port configured to transmit fluid to a first trunnion of the pump/motor.
  • the pump/motor may also include a second fluid channel, integral to the frame, having a first terminus at the valve and a second terminus at a second fluid port configured to transmit fluid to a second trunnion of the pump/motor.
  • Figure 1 is a diagrammatical representation of a pump/motor according to known art.
  • Figure 2 is an elevation of a yoke of a pump motor according to an embodiment of the invention.
  • Figure 3A is a cross section of the yoke of Figure 2, taken along line 3-3.
  • Figure 3B is a detail of a check valve of the type illustrated in the sectional view of Figure 3A.
  • Figure 4 is a side elevation of a pump/motor according to an embodiment of the invention.
  • Figure 5A is a cross section of the pump/motor of Figure 4, taken along line 5-5.
  • Figures 5B - 5D are details of the pump/motor of Figure 5A, according to various embodiments of the invention.
  • Figure 6 is a cross section of the pump/motor of Figure 4, taken along line 6-6.
  • sources of high- and low-pressure fluid are not shown.
  • Such fluid sources are well known in the art.
  • a common type of pressurized fluid storage is ' an accumulator, which is referred to occasionally in the present descriptions, and is well understood in the art.
  • Other types of fluid supply and storage may be employed and are considered to fall within the scope of the invention.
  • a pump/motor is configured to operate as a pump, forcing fluid at high pressure into the high-pressure source, and drawing fluid from the low-pressure source.
  • the pump/motor 102 draws low-pressure fluid from port 137 during braking and pumps high-pressure fluid to port 136.
  • FIG 2 shows a yoke 150 of a pump/motor 190 (the pump/motor 190 is shown in Figures 4-6).
  • the yoke 150 of pump/motor 190 includes a back plate 152, arms 154, 155, and trunnions 156, 157.
  • the yoke 150 also includes check valves 160 in the back plate 152, which will be described in detail hereafter.
  • FIG. 3A a cross-section of the back plate 152 is shown, including details of the check valve 160.
  • An enlarged view of a check valve 160 is shown in Figure 3B. More particularly, the check valve 160 of this embodiment includes a threaded insert 162 configured to engage a threaded aperture 164 in the back plate 152. Seal 166 provides a fluid seal between the insert 162 and the back plate 152. Poppet valve 168 is biased in a closed position by spring 170.
  • the yoke 150 further includes fluid channels 172, 173 located within the arms 154, 155. It may be seen, in Figure 3A 1 that there are two fluid channels 172 within the arm 154, and two fluid channels 173 within the arm 155. The provision of two fluid channels 172, 173 in each of the arms 154, 155 enhances the stiffness of the arms 154, 155 as compared with arms having single, larger fluid channels in each of the arms.
  • pump/motor 190 is coupled to the drive train of a vehicle, high-pressure fluid is introduced to the yoke via port 175 (see Figure 2) and travels up the arm 155 to the back plate 152 via channels 173.
  • the high- pressure fluid is supplied to the valve plate 178 and to the barrel 158 via fluid cavities 177.
  • the yoke 150 is sealed within a casing 192 (see Figure 5A). Space within the casing 192 around the yoke 150 may be filled with hydraulic fluid, and coupled to a low-pressure fluid source, such as an accumulator, via a high volume, low loss fluid connection such as a large-bore pressure hose (not shown).
  • a low-pressure fluid source such as an accumulator
  • the fluid pressure connections at trunnion ports 175, 174 are reversed, as described in more detail hereafter, such that the high- pressure fluid source, a high-pressure accumulator, for example, is coupled to trunnion port 174, while the low-pressure fluid source is coupled to trunnion port 175.
  • the high-pressure fluid source a high-pressure accumulator
  • the low-pressure fluid source is coupled to trunnion port 175.
  • low-pressure fluid is drawn into the cylinders 180 of the barrel 158 via the fluid cavities 177, and pumped at high pressure from the cylinders 180 into the fluid cavities 176, and thence to the high-pressure accumulator via the trunnion port 174.
  • FIG. 3B shows a detail of a check valve 160 similar to that shown in Figure 3A.
  • the check valve 160 of Figure 3B is shown in an open position, as described above. It may be seen, with reference to Figure 3B, that when the poppet 168 is in the open position, fluid may pass freely around the poppet and into the fluid cavities 177.
  • the check valves may be configured to remain open under reverse pressures greater than the pressure found in the low-pressure side of the circuit, but to close under pressures much lower than the pressure present in the high-pressure side (spring biased open). In this way, low-pressure fluid may flow in either direction through the check valves, thus further reducing losses by generally bypassing most of the restrictive passages between the back plate of the pump/motor and the low-pressure fluid source, for example on the motor discharge side.
  • valves will close instantly when high pressure is present in the corresponding fluid cavity.
  • High pressure fluid must enter or exit the yoke.
  • fluid traversing the trunnions 120, 121 must execute several sharp turns in entering or leaving the pump/motor 102.
  • fluid entering via trunnion port 135 makes a sharp turn to pass axially through the trunnion 121 and through the bearing 127, and then another sharp turn to rise into the channel 129 of the arm 133.
  • the fluid returning from the pump/motor must pass through a similar series of turns as it exits the trunnion 120.
  • Figure 4 shows the pump/motor 190 according to an embodiment of the invention.
  • Figure 5A shows a cross-section of the pump/motor 190 of Figure 4, taken along line 5-5.
  • Trunnion ports 174, 175 are located in positions occupied, in pump/motors of known art, by the lower portion of the trunnion bearings.
  • trunnion port 174 is shown exiting trunnion 156 between vertical planes that also define the horizontal limits of trunnion bearing 196.
  • Fluid seals 200, 201 are positioned on either side of the trunnion bearings 196, 197 and trunnion ports 174, 175 of trunnions 156, 157, respectively.
  • FIG. 5A shows the yoke 150 and cylinder barrel 158 of Figure 2, and provides a cross-sectional view of the trunnions 156, 157.
  • Trunnion ports 174, 175 are shown coupled to fluid ports 182, 183 of the pump/motor casing 192. It may be seen that the fluid channels 172, 173 are much straighter as compared to those of a conventional pump/motor such as pump/motor 102 of Figure 1 , inasmuch as the trunnion ports 174, 175 can now be positioned in a location that, in the pump/motor of Figure 1 , is occupied by the lower half of bearings 126, 127.
  • the trunnions 156, 157 may be made shorter than previously known trunnions, such as trunnions 120, 121 of Figure 1, reducing the size and mass of the pump/motor 190 as compared to previously known pump/motors.
  • the arms 154, 155 and the trunnions 156, 157 undergo a distortion, with each of the arms 154, 155 tending to pivot upward and outward on the fulcrums formed by the bearings 196, 197.
  • the forces concentrated on the upper portions of the bearings 196, 197 not only are the forces concentrated on the upper portions of the bearings 196, 197, but the forces are concentrated in a small area of the top of each bearing along an inner rim closest to the respective arm 154, 155.
  • several bearing configurations are provided to improve efficiency and reduce wear on the trunnions 156, 157 and bearings 196, 197.
  • Figures 5B-5D illustrate three of the bearing configurations provided in accordance with various embodiments of the invention.
  • a sectional detail of the trunnion 157 is shown, together with a portion of the pump/motor casing 192 and trunnion end cap 205.
  • trunnion bearings configured to operate with trunnion 157 are shown, corresponding bearings are also provided to operate with trunnion 156, which are substantially identical, and so need not be illustrated separately.
  • Figure 5B shows trunnion bearing 197.
  • Bearing 197 is a roller bearing comprising a cage frame 203 and a plurality of needle rollers 215.
  • FIG. 5C shows a conical bushing 207.
  • Bushing 207 is in the form of a section of a hollow cone.
  • the bushing 207 tapers in thickness from an outboard edge 211 to an inboard edge 213, as may be seen by phantom lines T, which indicate the tapering thickness of the bushing 207.
  • the bushing 207 is positioned on the trunnion 157 such that the inboard edge 213 is closest to the arm 155. Because of the taper of the bushing 207, when the pump 190 is idle, the upper surface closest to the inboard edge 213 does not contact the corresponding inner surface of the pump casing 192.
  • the bushing 207 may be formed of bronze or some other suitable material, and may be impregnated with a lubricant.
  • Figure 5D illustrates a cylindrical bushing 209.
  • bushing 209 In addition to having a cylindrical cross-section in a first axis C, in order to accommodate the cylindrical shape of the trunnion 157, bushing 209 also has a cylindrical cross-section in a second axis D, as may be clearly seen in the sectional view of Figure 5D.
  • This shape permits the bushing 209 to adjust slightly within the space provided for it in the trunnion 157 of Figure 5D as the varying forces placed on the trunnion 157 cause it to rotate slightly on the second axis D within the pump/motor casing 192. In this way, the stresses can be evenly distributed across the upper and lower surfaces of the bushing 209, preventing localized wear and stress.
  • the bushing 209 may be formed of bronze or some other suitable material, and may be impregnated with an appropriate lubricant.
  • FIG. 6 is a cross-sectional view of the pump/motor 190 taken along line 6-6 of Figure 4. Referring to Figure 4, a fluid supply channel 198 may be seen as it curves up toward the trunnion cover plate 204.
  • the fluid supply channels 198, 199 are integrated into the structure of the pump/motor frame, eliminating the need for an external hose in this location. Referring to Figure 6, the fluid supply channels 198, 199 may be clearly seen, positioned to carry fluid to and from the yoke 150 via spool valve 210. It may be seen, with reference to Figures 4 and 6, that the fluid supply channels 198, 199 are configured to provide passage for hydraulic fluid, while avoiding sharp turns and tight restrictions, wherever possible. Additionally, a spool valve 210 is integrated into the pump/motor frame. Because high- and low-pressure switching is accomplished by the spool valve 210, couplings and transmission lines between exterior switching valves and the pump/motor 190 are eliminated.
  • valves may also be incorporated into the structure of the pump/motor 190, such as pilot valves, check valves, and actuator valves.
  • an actuator 218 controls the rotation of the yoke 150 on trunnions 156, 157.
  • the actuator 218 is controlled by actuator control valve 216, which may be incorporated into the structure of the pump/motor 190.
  • actuator control valve 216 may be incorporated into the structure of the pump/motor 190.
  • the pump/motor 190 of Figure 6 also includes pressure input ports 212, 214, configured to receive a high-pressure fluid supply and a low-pressure fluid supply, respectively.
  • pressure input ports 212, 214 configured to receive a high-pressure fluid supply and a low-pressure fluid supply, respectively.
  • Channels formed within the pump/motor casing are almost always shorter than equivalent channels formed using hoses, since a hose channel is required to follow a longer path around the pump/motor.
  • the pressure loss is reduced over known systems and, additionally, the number of components of the pump/motor is reduced. It is known that, in hydraulic systems in general, hoses and hose connections are among the most frequent sources of failure and down time. Thus, by eliminating such from the system, the overall durability and dependability of the system is improved.
  • a first valve 142 is used to couple the fluid supply line 144 alternately to the high- or low-pressure fluid source, while a second valve 143 is used to perform the same function for the fluid supply line 145.
  • a second valve 143 is used to perform the same function for the fluid supply line 145.
  • valves By incorporating the valves into a single valve with multiple ports configured to control a coupling of both fluid supply lines with both the high- and low-pressure fluid sources, such as through spool valve 210 of Figure 6, the coordination of the switching is improved, while the circuitry required to control the switching is simplified. If pressure losses in the high- or low-pressure sides of the hydraulic circuit of the pump/motor are reduced, the pressure differential at the valve plate of the pump/motor will be closer to that between the high- and low- pressure fluid sources. This will result in an increase in available power as well as improved fuel economy for an associated vehicle.
  • the maximum pressure required in the low-pressure side of the circuit to overcome those losses may also be reduced. This makes possible the reduction of the overall pressure in the low-pressure accumulator, resulting in a further increase in the pressure differential at the motor, with a concomitant increase in available power to the motor. Finally, if the maximum pressure in the low-pressure side of the circuit is reduced, the pressure within the pump/motor casing will also be reduced.
  • the casing With lower pressure in the pump/motor casing, the casing may be manufactured to lower pressure tolerances. Additionally, the low-pressure accumulator may also be manufactured to lower pressure tolerances. This allows a reduction in mass and weight of the casing and accumulator, which further increases the operational economy of the pump/motor while reducing its overall size, without reducing its power output.

Abstract

Pompe/moteur à axe courbe comprenant : plaque arrière dans un boîtier, et vanne de contrôle dans ladite plaque, cette vanne contrôlant le passage de fluide issu du boîtier et destiné à la plaque arrière. Un collier couplé à cette plaque, comprend des pivots dans des ouvertures correspondantes du boîtier, sur lesquels pivote le collier. Des paliers occupant moins que la circonférence complète des pivots correspondants, se trouvent entre chacun des différents pivots et les parois internes respectives des ouvertures. Les ouvertures qui laissent passer le fluide se trouvent sur une partie de la circonférence non occupée par les paliers correspondants. Une vanne placée dans le boîtier assure le couplage sélectif de fluide haute et basse pression avec les pivots. Des canaux d'alimentation de fluide, intégrés au boîtier, permettent le passage de fluide depuis la vanne vers les pivots via des ouvertures de fluide pratiquées dans les ouvertures du boîtier.
PCT/US2005/013532 2005-04-20 2005-04-20 Pompe/moteur efficace a perte d'energie reduite WO2006115472A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP05737521A EP1875044A1 (fr) 2005-04-20 2005-04-20 Pompe/moteur efficace a perte d'energie reduite
PCT/US2005/013532 WO2006115472A1 (fr) 2005-04-20 2005-04-20 Pompe/moteur efficace a perte d'energie reduite
CA002605407A CA2605407A1 (fr) 2005-04-20 2005-04-20 Pompe/moteur efficace a perte d'energie reduite

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2005/013532 WO2006115472A1 (fr) 2005-04-20 2005-04-20 Pompe/moteur efficace a perte d'energie reduite

Publications (1)

Publication Number Publication Date
WO2006115472A1 true WO2006115472A1 (fr) 2006-11-02

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PCT/US2005/013532 WO2006115472A1 (fr) 2005-04-20 2005-04-20 Pompe/moteur efficace a perte d'energie reduite

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CA (1) CA2605407A1 (fr)
WO (1) WO2006115472A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010091305A3 (fr) * 2009-02-06 2011-05-19 Government Of The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency Pompe/moteur à axe brisé de longueur variable

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1053602A (fr) 1959-01-24
FR2067811A5 (fr) 1969-11-18 1971-08-20 Lucas Industries Ltd

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1053602A (fr) 1959-01-24
FR2067811A5 (fr) 1969-11-18 1971-08-20 Lucas Industries Ltd

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010091305A3 (fr) * 2009-02-06 2011-05-19 Government Of The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency Pompe/moteur à axe brisé de longueur variable
US8356547B2 (en) 2009-02-06 2013-01-22 The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency Variable length bent-axis pump/motor

Also Published As

Publication number Publication date
CA2605407A1 (fr) 2006-11-02
EP1875044A1 (fr) 2008-01-09

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