CA1196823A - Combined fluid pressure actuated fuel and oil pump - Google Patents
Combined fluid pressure actuated fuel and oil pumpInfo
- Publication number
- CA1196823A CA1196823A CA000413422A CA413422A CA1196823A CA 1196823 A CA1196823 A CA 1196823A CA 000413422 A CA000413422 A CA 000413422A CA 413422 A CA413422 A CA 413422A CA 1196823 A CA1196823 A CA 1196823A
- Authority
- CA
- Canada
- Prior art keywords
- pressure chamber
- volume
- low pressure
- chamber
- pumping
- 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.)
- Expired
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 96
- 239000012530 fluid Substances 0.000 title claims abstract description 26
- 238000005086 pumping Methods 0.000 claims abstract description 132
- 238000004891 communication Methods 0.000 claims description 14
- 238000006073 displacement reaction Methods 0.000 claims description 12
- 230000000694 effects Effects 0.000 claims description 7
- 238000010276 construction Methods 0.000 description 16
- 238000013459 approach Methods 0.000 description 7
- 238000002485 combustion reaction Methods 0.000 description 6
- 230000002093 peripheral effect Effects 0.000 description 5
- 239000000203 mixture Substances 0.000 description 4
- CUZMQPZYCDIHQL-VCTVXEGHSA-L calcium;(2s)-1-[(2s)-3-[(2r)-2-(cyclohexanecarbonylamino)propanoyl]sulfanyl-2-methylpropanoyl]pyrrolidine-2-carboxylate Chemical compound [Ca+2].N([C@H](C)C(=O)SC[C@@H](C)C(=O)N1[C@@H](CCC1)C([O-])=O)C(=O)C1CCCCC1.N([C@H](C)C(=O)SC[C@@H](C)C(=O)N1[C@@H](CCC1)C([O-])=O)C(=O)C1CCCCC1 CUZMQPZYCDIHQL-VCTVXEGHSA-L 0.000 description 2
- 150000002500 ions Chemical class 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 239000012528 membrane Substances 0.000 description 2
- 238000005192 partition Methods 0.000 description 2
- 101100310856 Drosophila melanogaster spri gene Proteins 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000003467 diminishing effect Effects 0.000 description 1
- 235000013531 gin Nutrition 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
- F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
- F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
- F04B9/1315—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members the movement of the pumping pistons in only one direction being obtained by a single-acting piston fluid motor, e.g. actuation in the other direction by spring means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
- F01B29/08—Reciprocating-piston machines or engines not otherwise provided for
- F01B29/10—Engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M3/00—Lubrication specially adapted for engines with crankcase compression of fuel-air mixture or for other engines in which lubricant is contained in fuel, combustion air, or fuel-air mixture
- F01M3/02—Lubrication specially adapted for engines with crankcase compression of fuel-air mixture or for other engines in which lubricant is contained in fuel, combustion air, or fuel-air mixture with variable proportion of lubricant to fuel, lubricant to air, or lubricant to fuel-air-mixture
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/12—Feeding by means of driven pumps fluid-driven, e.g. by compressed combustion-air
-
- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
-
- 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
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
-
- 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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
- F04B9/123—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber
- F04B9/125—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting elastic-fluid motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/04—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers
- F02B61/045—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers for marine engines
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Reciprocating Pumps (AREA)
- Hydraulic Motors (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
ABSTRACT OF THE INVENTION
Disclosed herein is a combined fuel and oil pump comprising a reciprocally movable member for pumping fuel in response to member reciprocation, a reciprocally movable element for pumping oil in response to element reciprocation, and a fluid pressure actuated motor connected to the member and to the element and responsive to a source of alternating relatively high and low pressures for effecting reciprocation of the member and the element at a frequency less than the frequency of the alternation of the relatively high and low pressures.
Disclosed herein is a combined fuel and oil pump comprising a reciprocally movable member for pumping fuel in response to member reciprocation, a reciprocally movable element for pumping oil in response to element reciprocation, and a fluid pressure actuated motor connected to the member and to the element and responsive to a source of alternating relatively high and low pressures for effecting reciprocation of the member and the element at a frequency less than the frequency of the alternation of the relatively high and low pressures.
Description
TITLE: COMBIN~D FLUID PRESSURE
ACTUA~ED FU~L AND OIL PUMP
I~VENTOR: FRANK J. WALSWORTH
BAC~GROUND OF THE INVENTION
The invention rela~es generally to fuel pumping arrangements.
The invention also generally relates to oil pumping arrangement~.
The invention al~o relate~ generally to 1uid pressure actua~ed motors.
The invention also relates to internal combustion engines and, more particularly, to two-stroke internal combustion engines and to means for supplying 6uch e~gines with a fuel/oil mixture.
~ ttention ifi directed to the U.S. Perlewitz Patent 2,935,057 issued May 30, 1960, to the U.S.
Sparrow Patent 3,481,318 issued December 2~ 1969, to the U.S. ~eitermann Patent 3,653,6B4 issued April 4.
1972, to the U.S. Shaver Patent 3~913.551 issued October 21, 1975 to the U.S. Schreier Patent 4,142,486 i~sued March 6, 1979, and to the U.S.
Beaton patent 1,5L9,478 issued December 16, 1924.
ACTUA~ED FU~L AND OIL PUMP
I~VENTOR: FRANK J. WALSWORTH
BAC~GROUND OF THE INVENTION
The invention rela~es generally to fuel pumping arrangements.
The invention also generally relates to oil pumping arrangement~.
The invention al~o relate~ generally to 1uid pressure actua~ed motors.
The invention also relates to internal combustion engines and, more particularly, to two-stroke internal combustion engines and to means for supplying 6uch e~gines with a fuel/oil mixture.
~ ttention ifi directed to the U.S. Perlewitz Patent 2,935,057 issued May 30, 1960, to the U.S.
Sparrow Patent 3,481,318 issued December 2~ 1969, to the U.S. ~eitermann Patent 3,653,6B4 issued April 4.
1972, to the U.S. Shaver Patent 3~913.551 issued October 21, 1975 to the U.S. Schreier Patent 4,142,486 i~sued March 6, 1979, and to the U.S.
Beaton patent 1,5L9,478 issued December 16, 1924.
-2-SUMMARY OF THE INVENTIOW
The invention provides a pump compcising means including a reciprocally movable member ~or pumping a fluid in response ~o reciprocation of the member, and motor means connected to the member and responsive to a source of alternating relatively hiyh and low pre~sures for effecting reciprocation of the member at a frequency less than the frequency of the alternation of the relatively high and low pressures.
The invention also provides a combined fuel and oil pump comprising means including a reciprocally movable member foc pumping fuel in response to reciprocation of the member, means including a reciprocally movable element for pumping oil in response to recipeocation of the element, and mo~or means connected to the member and to the element and responsive to a source of alternativing relatively high and low pressures t`or effecting reciprocation o~ the member and the element at a frequency less than the frequency of the alternation of the relatively high and low pressures.
The invention also prov;des a combined fuel and oil pump comprising means including a reciprocally movable member for ~umping fuel in ; . ;, .
6~3 response to reciprocation of the member, mean~
including a reciprocally movable element for pumping oil in response to reciproca~ion of the element. and motor mean~ connected to the member and ~o ~he element and responsive to a source of alternating relatively high and low pressures for ef~ecting reciprocation of the member and the element at a ~requency less than the frequency of the alternation of the relatively high and low pre~sures, which motor means includes relatively low and high pressure chambers which inversely vary in volume, and means for creating a pressuee differential between the high and low pressuLe chambers comp~i~ing means adapted to be connected to a soucce of alternating ralatively high and low pressures and including means permitting flow from the low pressure chamber and preventing flow to the low pressure chamber, and means permitti.ng flow to the high pressure chamber and preventing ~low from the high pressure chamber.
In one embodiment in accordance with the inventLon, the motor pLston, the fuel pumping member and the oil pump;ng element con6titute an integral component.
In one embodiment of the invention, the oil pumping means includes oil discharge means including a valved bore extendinq in the component between the oil pumping chamber and the fuel pumping chamber.
In one embodiment of ~he inventionO the oil pumping means, the ~uel pumping means, and the motor means form parts of a single housing.
In one embodiment of the inven~ion, the movable oil pumping element reciprocates through a given distance, and the oil pumping means includes meanR varying ~he output the~eof notwithstanding the reciprocation of the oil pumping element through the given distance.
In one embodiment in accordance with the invention, the means for creating a pressure d i f f erential between the high and low pressure chambers comprises means adapted to be connected to a source of alternativing telatively high and low pres~ures and including means permitting flow from the low pressure chamber, and means permitting flow to the high pre6sure chamber and preventing flow from the high pressure chamber.
In one embodiment in accordance with the invention, the motor also includes pressure rQlief mean~ connected between the high and low pres ure chambers to limit the pressure differential thare between.
: . . ~ . 1, ~IL~823 In one embodiment i~ accordance with the invention. the mean~ for establishing and disconnecting communication between the high and low pressure chambers includes a port in ~he motor piston, a valve member movable relative to the port between open and closed positions, means biasing the valve member away from the port. and means on ~he housing engageable with the valve member to close the port in response to piston movement minimizing the volume of the high pressure chamber.
Other features and advantages of the embodiments of the invention will become known by reference to the followinq general desceiption.
claims and appended drawings.
IN THE DRAWINGS
Fig. 1 is a schematic view of one embodimen~
of a combined fuel and oil pump including a fluid pressure actuated motor.
Fig. 2 is a schematic view of another embodiment of a combined fuel and oil pump including a fluid preSsure actuated motor.
Fig. 3 is a schematic view of still another embodiment of a combined fuel and oil pump including a fluid pressure actuated motor.
Before explaining one embodiment of the invention in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein is for the purpose of description and should not be regarded as limiting.
GENERAL DESCRIPTION
Shown in the drawings is a marine propulsion device in the form of an outboard motor 3 which includes a propulsion unit 5 including a power head 7 incorporating a two-stroke internal combustion engine 8, together with a lower unit 9 which is secured to the power head 7 and which rotatably supports a propeller 10 driven by the internal combustion engine 8.
Connected to the internal combustion engine 8 is a combined fuel and oil pump 11 including a fluid pressure motor 13 actuated by a source of alternating relatively high and low pressures.
More particularly, the combined fuel and oil pump 11 comprises a housing 15 and, in addition to the fluid pressure motor 13, includes an oil pumping means 17 and a fuel pumping means 19.
~ ~68~;~
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, . ~ ~
Still more particularly, the housing ].5 includes a peripheral wall 21, together with a top ~all 23, an intermediate wall or partition 25, a bottom wall 27, and a lower extension 29. The intermediate wall 25 includes a central bore or port 31 and divides the housing 15 into an upper compartment 33 and a lower compartment 35.
The fuel pumping means 19 includes a movable wall or member 39 which is located in the lower compartment 35 and which divides the lower compartment 35 into a variable volume fuel pumping chamber 45 located between the intermediate wall 25 and the fuel pumping piston or movable wall or member 39 and a lower or vent chamber 47 which communicates with the atmosphere through a port 49 in the bottom wall 27.
The movable wall or member 39 includes a piston 41 which, at its periphery, has attached thereto a flexible membrane or diaphragm 43 which, in turn, is attached -to the peripheral wall 21 of the housing 15.
The fuel pumping means 19 also includes, in the peripheral wall 21, a valved fuel inlet 51 which is adapted to communicate through a conduit 53 with a suitable source 55 of fuel and which includes one-way check valve means 57 affording inflow of Euel in response to an increase in the volume of the fuel pumping chamber 45 and which prevents outflow of fuel from the fuel pumping chamber ~5.
The fuel pumping means 19 also includes, in the peripheral wall 21, a valved Euel outlet 61 which is adapted to communicate through a conduit 63 with a device, such as a carburetor 65, for feeding a fuel/o.il mixture to the crankcase 67 of the two-stroke engine 8.
the valved outlet 61 includes one~way check valve means 71 which affords outflow of fuel in response to a decrease in the volume of the fuel pumping chamber 45 and which prevents inflow of fuel.
Preferably, the conduit 63 includes an accumulator 75 in the form of a cylinder 77 which, at one end, communicates with the conduit 63 and which, at the other or outer end, is vented to the atmosphere by a port 79. Located in the cylinder 77 is a piston 81 which is suitably biased by a spring 83 in the direction toward the conduit 63 so as to provide a variable volume accumulating chamber 85 which serves to reduce or eliminate pulsing of fuel at the discharge end of the conduit 63.
The oil pumping means 17 is located in the lower extension 29 and comprises a cylindrical space 87 which extends from the vent chamber 47 in generally aligned relation to the central port 31 in the intermediate wall 25. Located in the cylindrical space 87 is an oil pumping plunger or element 91 which preEerably extends integrally from the fuel pumping piston 41, which is reciprocal in the cylindrical space 87, and which, in part, defines a variable volume oil pumping chamber 93. Seal means 95 is provided between the oil pumping plunger or element 91 and the wall of the cylindrical space 87.
The oil pumping means 17 also includes a valved inlet 101 which is adapted to communicate through a conduit 103 with a source 105 of oil and which includes one-way check valve means 107 which a.EEords inflow of oil in response to an increase in the volume o~ the oil pumping chamber 93 and which prevents outflow of oil.
61~323 The oil pumping means 17 also includes a valve outlet 111. While various other arrangements can be employed, in the illustrated construction, the outlet 111 is designed to deliver oil to the fuel pumping chamber 45. More particularly, the oi.l outlet 111 comprises a bore 113 which extends axially in the oil pumping plunger or element 91, which, at one end, communicates with the oil pumping chamber 93, which, at the other end, includes one or more radial branch ports 115 which communicates with the fuel pumping chamber 45, and which includes, intermediate the inlet 101 and the outlet 111, an enlarged central portion 117 having a one way check valve means 119 which affords outflow of oil to the fuel pumping chamber 45 in response to a decrease in the volume of the oil pumping chamber 93 and which prevents inflow into the oil p-lmping chamber 93.
The fluid pressure actuated motor 13 is located generally in the upper compartment 33 and is connected to the oil pumping plunger 91 and to the fuel pumping piston 41 so as to effect common reciprocation thereof through a given stroke or distance. More particularly, the fluid pressure actuated motor 1.3 is responsive to a source of alternating relatively high and low pressures for effecting reciprocation of the fuel pumping piston ~1 and the oil pumping plunger or element 91 at a frequency less than the frequency of the alternation o~ the relatively high and low pressures. Still more particularly, the fluid pressure actuated motor 13 includes a movable wall 121 which divides the upper compartment 33 into an upper, relatively low pressure variable volume chamber 123 and a lower, relatively high pressure variable volume chamber 125. The movable wall 121 includes a central or motor piston 127 which, at its outer periphery, is connected to a flexible membrane or diaphragm 129 which, at its outer periphery, is secured to the peripheral housing wall 21 so as to divide the upper compartment 33 into the before-mentioned relatively low and high pressure chambers.
The central motor piston 127 is also preferably integrally connected with the fuel pumping piston 41 and with the oil pumping plunger or element 91 for common movement. In this last regard, the combined motor piston 127, fuel pumping piston 41, and oil pumping plunger 91 includes a central portion 131 which extends from the fuel pumping piston 41 toward the motor piston 127 and through the central bore or port 31 in the intermediate wall 25, and a connecting portion which forms an open valve cage 135 and which connects the central 131 to the motor piston 127. A suitable seal 139 is provided between the intermediate wall 25 and the central portion 131.
The fluid pressure actuated motor 13 furthur includes means biasing the movable wall 121 so as to displace the movable wall 121 in the direction minimizing the volume of the high pressure chamber 125 and maximizing the volume of the low pressure chamber 123. In the illustrated construction, such means comprises a helical spring 141 which, at one end, bears against the upper or top housing wall 23 and which, at the other end, bears against the motor piston 127.
The fluid pressure actuated motor 13 also includes means 151 for creating a pressure differential . ~
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. J ~ .
between the low and high pressure chambers 123 and 125, respectively, so as to displace the movable wall 121 in the dire~tion minimizing the volume of the low pressure chamber 123 and maximizing the volume of the high pressure chamber 125. While various arrangements can be employed, in the illustrated construction, such means includes means adapted for connection to a source oE alternating relatively high and low pressures and including means permitting flow from the low pressure chamber 123 and preventing flow to the low pressure chamber 123, and means permitting flow to the high pressure chamber 125 and preventing flow from the high pressure chamber 125.
Preferably, the source of alternating relatively high and low pressures is the crankcase 67 of the two-stroke engine 8. However, other sources of relatively high and low pressures can be employed. In addition, relatively high and low pressure can refer to two positive pressures above atmospheric pressure, to two negative pressures below atmospheric pressure, or to one positive pressure above atmospheric pressure and one negative pressure below atmospheric pressure.
Still more specifically, the means 151 for creating the pressure differential between the relati.vely low and high pressure cylinders 123 and 125, respectively, also includes a conduit system 161 including a main conduit 163 adapted to be connected to the source of alternating high and low pressures, such as the crankcase 67 of the two-stroke engine 8, together with a Eirst or low pressure branch conduit 165 which communicates between the low pressure chamber ~q~ 3 : !, 123 and the main conduit 163 and a second or high pressure branch conduit 167 which communicates between the high pressure chamber 125 and main conduit 163.
Included in the low pressure branch conduit 165 is a one-way check valve 169 which permits flow from the low pressure chamber 123 and prevents Elow to the low pressure chamber 123. Located in the high pressure branch conduit 167 is a one way check valve 171 which permits flow to the high pressure chamber 1~5 and which prevents flow from the high pressure chamber 125.
Accordingly, alternating pressure pulses of relatively high and low pressures present in the main conduit 163 will cause the existence of a relatively high pressure in the high pressure chamber 125 and a relatively low pressure in the low pressure chamber 123, which pressure differential is of sufficient magnitude, as compared to the biasing action of the movable wall biasing spring 141, so that the pressure differential is effective to cause movement of the movable wall 121 from a position in which the high pressure chamber 125 is at a minimum volume to a position in which the low pressure chamber 123 is at a minimum volume.
Preferably, the conduit system 161 also includes means for relieving an excessive pressure differential. In this regard, the conduit system 161 includes a bypass conduit 175 which communicates with the low and high pressure branch conduits 165 and 167, respectively, so as to be i~ direct communication with the low and high pressure chambers 123 and 125, respectively. The bypass conduit 175 includes a one-way ~ 3 ;~ /3 pressure regulating valve 177 including a ball member 179 which is engaged with a seat 181 and held in such engagement by spring 183 designed to release the ball member 179 from engagement with the seat 181 in the event of an excessive differential pressure.
The fluid pressure actuated motor 13 also includes means responsive to piston movement minimi~ing the volume of the low pressure chamber 123 for establishing communication between the low and high pressure chambers 123 and 125, respectively, so as thereby to reduce or minimize the pressure differential between the low an high pressure chambers 123 and 125, respectively, and thereby permit displacement of the movable wall 121 by the biasing spring 141 in the direction minimizing the volume of the high pressure chamber 125 and maximizing the volume of the low pressure chamber 123. ~hile such means can be provided, at least in part, by a conduit (not shown) bypassing the motor piston 127, in the illustrated construction, such means comprises a central port 191 in the motor piston 127, together with a valve member 193 which is located in the open cage 135 of the combined motor piston 127, fuel pumping piston 41 and oil pumping plunger 91, and which is movable between a closed and an open position. Preferably, the valve member 193 includes a downwardly extending stem 195 which is received in a mating recess or axial bore 197 in the central portion 131 of the combined piston so as to guide movement of the valve member 193 between its open and closed positions.
In addition, the means for effecting communication between the low and high pressure chambers 123 and 125l respectively, includes a helical valve member biasing spring 201 which urges the valve member 193 ~o the open position and which, at one end, bears against the upper or top wall 23 of the housing 15 and which, at the other end, extends through the port 191 in the motor piston 127 and bears against the upper surface of the valve member 193. The valve member biasing spring 201 is designed so as to be operable to overcome the pressure differential between the low and high pressure chambers 123 and 125, respectively, and thereby to displace the valve member 193 toward the open position as the motor piston 127 approaches the position minimizing the volume of the low pressure chamber 123.
Means are also provided for insuring full opening movement of the val.ve member 193 in response to approach of the motor piston 127 to the position minimizing the volume of the low pressure chamber 123.
Such means is provided in the low pressure chamber 123 and comprises means defining an intermediate chamber 211 communicating with the motor piston port 191 and providing resistance to flow from the intermediate chamber 211 to the low pressure chamber 123 upon initial opening of the valve member 193 so as thereby to effect reduction in the pressure differential between the high pressure chamber 125 and the intermediate chamber 211 and thereby to cause movement of the valve member 193 to the full opened position.
Such movement substantially reduces the pressure differential between the low pressure chamber 123 and the high pressure chamber 125, and thereby permits movement of the movable wall 121 to minimize the volume I S
. , ~,, ~
of the high pressure chamber 125 in response to the action of the motor piston biasing spring 141. While various arrangements can be employed, in the illustrated construction, such means comprises an annular flange or ring 213 extending inwardly of the low pressure chamber 123 from the top wall 23 o the housing lS and in radially outward relation from the valve member biasing spring 201 and in radially inward relation from the motor piston biasing spring 141. In addition, such means comprises a cooperating annular 1ange or ring 215 extending from the motor piston 127 toward the housing top wall 23 and movable into telescopic relation to the flange or ring 213 as the motor piston 127 approaches the end of the stroke minimi%ing the volume of the low pressure chamber 123 so as to telescopically form the intermediate chamber 211 and to provide resistance to flow from the intermediate chamber 211 to the low pressure chamber 123.
Such resistance to flow between the intermediate chamber 211 and the low pressure chamber 123 causes deminishment in the resistance to flow or pressure drop between the high pressure chamber 125 and the intermediate chamber 211, thereby assuring action of the valve member biasing spring 201 to effect di.splacement of the valve member 193 to its fully open position.
The fluid pressure actuated motor 13 also includes means responsive to piston movement minimizing the volume of the high pressure chamber 125 for disconti~uing communication between the low and high pressure chambers 123 and 125, respectively, so as to 6~3~3 ,...', 1~-thereby permit the creation of Eluid pressure differential between the low and high pressure chambers 123 and 125 by the fluid pressure differential creating means and thereby also to effect displacement of the motor piston 127 in the direction minimizing the volume of the low pressure chamber 123 and maximizing the volume of the high pressure chamber 125. While other arrangements can be employed, in the illustrated construction, such means comprises a plurality of studs or posts 221 which extend upwardly from the intermediate partition or wall 25 toward the valve member 193 and through the open valve cage 135 for engagement with the valve member 193 to seat the valve member 193 in the closed position as the motor piston 127 approaches the position minimizing the volume of the high pressure chamber 125.
Thus, in operation, the presence of alternating high and low pressures in the conduit system 161 causes (assuming the valve member 193 to be in the closed position) buildup and maintenance of higher pressure in the relatively high pressure chamber 125 and reduction and maintenance of low pressure in the low pressure chamber 123. The pressure differential thus created causes displacement of the movable wall 121, including the motor piston 127, against the action of the motor piston biasing spring 141, to the position minimizing the volume of the low pressure chamber 123. ~s the motor piston 127 approaches the position minimizing the volume of the low pressure chamber 123, the valve member biasing spri.ng 201 serves to open the motor piston port 191 by displacing the valve member 193 to the open position ~6~3 , ,., .~ i~.
and thereby to reduce or minimize the pressure diEferential and permit displacement of the movable wall 121 by action of the biasing spring 141 to the position minimizing the volume of the high pressure chamber 125. Duriny such movement, and in the absence of a pressure differential, the valve member 193 remains in the open position under the action of the valve member biasing spring 201.
~ pon approach of the movable wall 121, including the motor piston 127, to the position minimiæing the volume of the high pressure chamber 125, the studs 221 engage the valve member 193 to cause movement thereof to the closed position. With the motor piston port 191 thus closed, the pressure differential is again created and the movable wall 121 is again displaced in the opposite direction to commence another cylce of operation. As the fuel pumpiny ql and the oil pumping plunger 91 have common movement with the motor piston 127, the fluid actuated motor 13 causes reciprocation of these components at a Erequency less than the frequency exciting the motor 13, i.e., less than the rate of alternation of the high and low pressures in the source.
Preferably, means are provided for selectively adjusting the discharge rate of the oil pumping means 17, notwithstanding displacement of the oil pumping plunger 91 through a generally constant stroke. While various other arrangements can be employed, in the illustrated construction, such means comprises a subchamber 231 which extends from the oil pumping chamber 93 and which includes therein a floating piston 233. A suitable seal 235 is provided between the ii8~3 floating piston 233 and the wall of the subchamber 231. The floating piston 233 includas, at the outer end th~reof, a portion 237 which extends vu~wardly of the subchamber 231 and which is engaged by a cam 239 which is connected by a suitable linkage 241 ~hown in dotted outline to the engine throttle 243 and which is, accordingly, selectively positionable in accordance with selective positioning of the engine throttle 243. The cam 2~9 thus variably restricts outward movement of the floating pifiton 233 so as to thereby control the e~fective pumping stroke of the oil pumping plunger 9L. A more detailed description of the arrangement for varying the di~charge rate of the oil pumping means 17 can be found in my co-pending Canadian Application Serial No. 406,927 eiled July a. 1982.
The combined fuel and oil pumping device 11 can be mounted to the block of the two-stroke engine 8 so as to afford immediate connection to the engine crankcase 67 and can be connected to remote soueces of oil and fuel. ~lternately~ if desired, the combined fuel pump and oil pump 11 can be locatsd at a remote location more or less adjacent to or with the sources of fuel and oil and a conduit (not shown~
can extend between the crankcase 67, or other source of alternating high and low pressures, and the combined fuel and oil pumping device 11.
Shown in Fig. 2 is another embodiment of a combined euel and oil pump 301 in accordance with the invention. The construction shown in Fig. 2 is generally identical to that shown in Fig. 1, and the same referece numeral have applied for like components, except for the arrangement for insuring 61~3 full opening of the valve member 193 and the arrangement for varying the amount of oil flow and the oil discharge arrangement.
With respect to the arrangement or means for insuring full opening movement of the valve member 193 in response to approach of the motor piston 127 to the position minimizing the volume of the low pressure chamber 123, in the construction illustrated in Fig. 2, the rings 213 and 215 have been omitted, thereby also omitting provision of the intermediate chamber ~11.
Instead, there is pro~ided a member or post 302 which fixedly depends downwardly from the top housing wall 23 in position for engaging the valve member 193 as the movable wall 121 minimizes the volume of the low pressure chamber 123. Such engagement causes "cracking" or slight opening of the port 191, thereby somewhat diminishing the pressure diEferential across the rnovable wall 121. Such diminishment of the pressure differential facilitates immediately subsequent operation of the poppet valve member biasing spring 201 to displace the valve member 193 so as to fully open the port 191 and thereby to substantially eliminate the pressure differential and obtain wall movement in the direction minimizing the volume of the high pressure chamber 125 under the action of the movable wall biasing spring 141. It is also noted that the post 302 serves to stabilize or locate the upper end of the poppet valve member biasing spring 201.
In the embodiment shown in Fig. 2, the oil pumping arrangement inc].udes an oil pumping piston 303 which defines, in part, a variable volume oil pumping chamber 393~ The oil pumping piston 303 is slidably engaged by the movable element 91 by means of an upper end 305 of the piston 303 being located in an enclosed central chamber 307 in the movable element 91. A mid portion 309 of the piston 303 extends outwardly of the chamber 307 through an opening 311 and connects the upper end 305 of the piston 303 to a lower portion 313 in the cylindrical space 87. The upper end 305 of the piston 303 is larger than the opening 311 so when the movable element 91 moves upwardly, the piston 303 moves with the movable element 91. Seal means 315 are provided above a lower end 317 of the piston 303 and between the lower portion 313 of the piston and the wall of the cylindrical space 87. The location of the seal means 315 permits the lower end 317 of the piston to extend below the valve inlet 101 and outlet 319.
In the embodiment, the oil pumping means 17 includes a valved outlet 319 which extends coaxially with the valved inlet 101 but on the opposite side of the cylindrical space 87. The outlet 319 includes a one way check valve 321 and affords outflow of oil to the conduit 63 for feeding the oil to the carburetor 65.
In the embodiment shown in Fig. 2, the means for selectively adjusting the discharge rate of the oil pumping means includes an adjustable stop 323 which defines, in part, the oil pumping chamber 393. The adjustable stop 323 is located in the cylindrical space 87 below the inlet 101 and outlet 319. A suitable seal 325 is provided between the adjustable stop 323 and the wall of the cylindrical space 87, and a portion 327 of the adjustable stop above the seal 325 has a diameter less than the diameter of the cylindrical space 87 to permit the upper portion 327 of the adjustable stop to . .t '~1 extend above the inlet 101 and outlet 319. The lower end of the adjustable stop 323 includes a portion 329 which extends outwardly of the cylindrical space 87 and which is engaged by the cam 239. The cam 239 operates as previously described.
The oil pumping means also includes biasing means for biasing the oil piston 303 toward the adjustable stop 323. The biasing means comprises spring 331 between the upper end 305 of the piston and the movable element 91 in the central chamber 30~.
In operation, as the movable element 91 moves downward, the oil piston 303 moves downwardly an equal distance. The biasing means or spring 331 is preloaded so that it will not deflect due to either oil pump pressure or seal friction. As the piston 303 moves downwardly, the oil pumping chamber 393 will be reduced in volume and will force oil out through the valved outlet 319. However, when the oil piston 303 contacts the adjustable stop 323, it will move no Eurther and the remaining stroke of the movable element 91 will be taken up or lost by deflecting the biasing means or spring 331. The location of the adjustable stop 323 will, therefore, vary the volume of the oil pumping chamber 393 and the amount oE oil pumped by the pumping means.
Shown in Fig. 3 is still another embodiment of a combined fuel and oil pump 401 which is associa-ted with the internal combustion engine 8 and which embodies various of the features of the invention. The construction shown in Figure 3 is generally identical to the construction shown in Figure 2 and the same reference numerals have been applied Eor like components, except that the fuel pumping arrangement has been slightly modified, except that the oil pumping arrangement has been modified to provide for variation in the output of the oil pump in accordance with engine speed without use of a movable part 239 or element 323 and associated linkage, and except that the one-way pressure-regulating valve 177 has been omitted and the stroke of the motor piston 1~7 varies in accordance with engine speed. In this last regard, the poppet valve biasing spring 201 has a spring rate which serves to open the port 191 prior to the full stroke of the motor piston 127 when the engine 8 is operating at low speed and which serves to open the port 191 upon completion of the full stroke of the motor piston 127 when the engine 8 is operating at high speed.
More particularly, as is well known, in a two~stroke engine, such as ~he engine 8, movement of the piston relative to the cylinder and crankcase 67 serves to produce in the crankcase, cyclical conditions of relativel~ high and low pressures definlng a crankcase pressure amplitude which varies in accordance with engine speed, i.e., which increases with engine speed. As, for example, when engine operation is at idle or low speed, the pressures in the crankcase can vary from about ~3 psi to about -3 psi, thus providing a crankcase pressure amplitude of 6 psi. Also, for example, when operating at high engine speed, the pressure in the crankcase can vary from about ~5 psi to -6 psi, or Erom about +10 psi to about -1 psi, thus providing a crankcase pressure amplitude of 11 psi.
Under operating conditions, because of the connection of the crankcase 67 to the low and high ~3.~ 3 '`:~
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pressure chambers 123 and 125~ respectively, and the one-way check valves 169 and 171, the pressure conditions in the low and high pressure chambers 123 and 125, respectively, rapidly reflect the pressures in the crankcase ~7 an provide a pressure differential across the movable motor piston 127, i.e., between the low and high pressure chambers 123 and 125, respectively, which pressure differential has an amplitude approximating the crankcase pressure amplitude.
The poppet valve biasing spring 201, as already indicated, has a spring rate such that partial movement of the motor piston 127 between the positions causing minimum volume of the low and high pressure chambers 123 and 125, respectively, will cause such contractlon of the poppet valve biasing spring 201 as to overcome the force on the valve member 193 occurring in response to the pressure differential when the engine 8 is operating at low speed. However, the spring rate is such that, whenever the engine 8 operates at high speed, the force created by the pressure differential is sufficiently great to provide greater travel or full travel of the movable wall 121 or motor piston 127 prior to opening of the port 191.
As a consequence, the motor piston 127 is provided with a stroke which varies with engine speed, i.e., i5 provided with a stroke which increases in length with engine speed.
The fuel pumping arrangement employed in the construction shown in Fig. 3 varies from that shown in Figs. 1 and 2 by placing the valved fuel inlet 51 in communication with the lower chamber 47 tWhich is, of course, not vented). In addition, the Euel pumping piston 39 is provided with one or more apertures 411, each having associated therewith a one-way check valve member 413 affording flow rom the lower chamber 47 to the upper chamber 45 and preventing flow ~rom the upper chamber 45 to the lower chamber 47. The stroke of fuel pumping member or piston 39 is identical to the stroke of the motor piston 127 and hence the amount of fuel pumped will vary in accordance with engine speed, i.e., will increase with increasing engine speed.
If desired, a fuel pump construction identical to that shown in Figs. 1 and 2 could also be employed.
The oil pumping arrangement diEfers from the construction shown in Figs. 1 and 2. in that the amount of oil pumped is automatically varied in accordance with engine speed and in that, due to a lost-motion connection between the motor piston 127 and the oil pumping piston 303, oil pumping does not occur until after a Eirst engine speed level~ which can be intermediate the low and high engine speeds, and which, above the first engine speed level, increases with increasing engine speed.
In this last regard, the oil pumping piston 303 is connected to the motor piston 127 to provide for common movement therewith during a portion of the motor piston stroke and to provide for lost-motion during another portion of the motor piston 127 strokeO In this regard, the upper end of the oil pumping piston 303 i3 provided with an axial recess or bore 415 which is defined, at the upper end thereof, by an internal annular flange 417 defining an opening 419, and the motor piston 127 is provided with an extension 421 which projects through the opening 419 provided by the annualar flange 417 and includes~ at the lower end, an enlarged head 423 which cannot pass through the opening 419 defined by the annualar flange 417. Thus, initial upstroke movement of the motor piston 127 from the position minimizing the volume of the high pressure chamber l~S does not cause accompanying movement of the oil pumping piston 313. However, before the motor piston 127 reaches the position minimizing the volume o~ low pressure chamber 123, the head 423 engages the flange 417 to cause common movement of the oil pumping piston 303 with the motor piston 127. Initial downstroke motion of the motor piston 127 does not cause the oil pumping piston movement until the head 423 engages the blind end of the recess or bore 415.
Thus, oil pumping operation occurs only at the top of the upstroke o~ the motor piston movement and at the bottom of the downstroke of the motor piston movement.
Accordingly, the oil pumping arrangement disclosed in Fig. 3, provides ~or little or no pumping at low engine speeds and for increasing oil pumping with increasing speeds above low engine speed.
As in the construction shown in Fig. 2, the oil discharge from the output 319 is conveyed to the fuel discharge conduit 63 for mixture therewith.
~Iowever, i~ desired, the discharged oil could be conveyed Eor mixture with the fuel in either the upper chamber ~5 or in the lower chamber 47.
Various of the features of the invention are set forth in the following claims.
The invention provides a pump compcising means including a reciprocally movable member ~or pumping a fluid in response ~o reciprocation of the member, and motor means connected to the member and responsive to a source of alternating relatively hiyh and low pre~sures for effecting reciprocation of the member at a frequency less than the frequency of the alternation of the relatively high and low pressures.
The invention also provides a combined fuel and oil pump comprising means including a reciprocally movable member foc pumping fuel in response to reciprocation of the member, means including a reciprocally movable element for pumping oil in response to recipeocation of the element, and mo~or means connected to the member and to the element and responsive to a source of alternativing relatively high and low pressures t`or effecting reciprocation o~ the member and the element at a frequency less than the frequency of the alternation of the relatively high and low pressures.
The invention also prov;des a combined fuel and oil pump comprising means including a reciprocally movable member for ~umping fuel in ; . ;, .
6~3 response to reciprocation of the member, mean~
including a reciprocally movable element for pumping oil in response to reciproca~ion of the element. and motor mean~ connected to the member and ~o ~he element and responsive to a source of alternating relatively high and low pressures for ef~ecting reciprocation of the member and the element at a ~requency less than the frequency of the alternation of the relatively high and low pre~sures, which motor means includes relatively low and high pressure chambers which inversely vary in volume, and means for creating a pressuee differential between the high and low pressuLe chambers comp~i~ing means adapted to be connected to a soucce of alternating ralatively high and low pressures and including means permitting flow from the low pressure chamber and preventing flow to the low pressure chamber, and means permitti.ng flow to the high pressure chamber and preventing ~low from the high pressure chamber.
In one embodiment in accordance with the inventLon, the motor pLston, the fuel pumping member and the oil pump;ng element con6titute an integral component.
In one embodiment of the invention, the oil pumping means includes oil discharge means including a valved bore extendinq in the component between the oil pumping chamber and the fuel pumping chamber.
In one embodiment of ~he inventionO the oil pumping means, the ~uel pumping means, and the motor means form parts of a single housing.
In one embodiment of the inven~ion, the movable oil pumping element reciprocates through a given distance, and the oil pumping means includes meanR varying ~he output the~eof notwithstanding the reciprocation of the oil pumping element through the given distance.
In one embodiment in accordance with the invention, the means for creating a pressure d i f f erential between the high and low pressure chambers comprises means adapted to be connected to a source of alternativing telatively high and low pres~ures and including means permitting flow from the low pressure chamber, and means permitting flow to the high pre6sure chamber and preventing flow from the high pressure chamber.
In one embodiment in accordance with the invention, the motor also includes pressure rQlief mean~ connected between the high and low pres ure chambers to limit the pressure differential thare between.
: . . ~ . 1, ~IL~823 In one embodiment i~ accordance with the invention. the mean~ for establishing and disconnecting communication between the high and low pressure chambers includes a port in ~he motor piston, a valve member movable relative to the port between open and closed positions, means biasing the valve member away from the port. and means on ~he housing engageable with the valve member to close the port in response to piston movement minimizing the volume of the high pressure chamber.
Other features and advantages of the embodiments of the invention will become known by reference to the followinq general desceiption.
claims and appended drawings.
IN THE DRAWINGS
Fig. 1 is a schematic view of one embodimen~
of a combined fuel and oil pump including a fluid pressure actuated motor.
Fig. 2 is a schematic view of another embodiment of a combined fuel and oil pump including a fluid preSsure actuated motor.
Fig. 3 is a schematic view of still another embodiment of a combined fuel and oil pump including a fluid pressure actuated motor.
Before explaining one embodiment of the invention in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein is for the purpose of description and should not be regarded as limiting.
GENERAL DESCRIPTION
Shown in the drawings is a marine propulsion device in the form of an outboard motor 3 which includes a propulsion unit 5 including a power head 7 incorporating a two-stroke internal combustion engine 8, together with a lower unit 9 which is secured to the power head 7 and which rotatably supports a propeller 10 driven by the internal combustion engine 8.
Connected to the internal combustion engine 8 is a combined fuel and oil pump 11 including a fluid pressure motor 13 actuated by a source of alternating relatively high and low pressures.
More particularly, the combined fuel and oil pump 11 comprises a housing 15 and, in addition to the fluid pressure motor 13, includes an oil pumping means 17 and a fuel pumping means 19.
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Still more particularly, the housing ].5 includes a peripheral wall 21, together with a top ~all 23, an intermediate wall or partition 25, a bottom wall 27, and a lower extension 29. The intermediate wall 25 includes a central bore or port 31 and divides the housing 15 into an upper compartment 33 and a lower compartment 35.
The fuel pumping means 19 includes a movable wall or member 39 which is located in the lower compartment 35 and which divides the lower compartment 35 into a variable volume fuel pumping chamber 45 located between the intermediate wall 25 and the fuel pumping piston or movable wall or member 39 and a lower or vent chamber 47 which communicates with the atmosphere through a port 49 in the bottom wall 27.
The movable wall or member 39 includes a piston 41 which, at its periphery, has attached thereto a flexible membrane or diaphragm 43 which, in turn, is attached -to the peripheral wall 21 of the housing 15.
The fuel pumping means 19 also includes, in the peripheral wall 21, a valved fuel inlet 51 which is adapted to communicate through a conduit 53 with a suitable source 55 of fuel and which includes one-way check valve means 57 affording inflow of Euel in response to an increase in the volume of the fuel pumping chamber 45 and which prevents outflow of fuel from the fuel pumping chamber ~5.
The fuel pumping means 19 also includes, in the peripheral wall 21, a valved Euel outlet 61 which is adapted to communicate through a conduit 63 with a device, such as a carburetor 65, for feeding a fuel/o.il mixture to the crankcase 67 of the two-stroke engine 8.
the valved outlet 61 includes one~way check valve means 71 which affords outflow of fuel in response to a decrease in the volume of the fuel pumping chamber 45 and which prevents inflow of fuel.
Preferably, the conduit 63 includes an accumulator 75 in the form of a cylinder 77 which, at one end, communicates with the conduit 63 and which, at the other or outer end, is vented to the atmosphere by a port 79. Located in the cylinder 77 is a piston 81 which is suitably biased by a spring 83 in the direction toward the conduit 63 so as to provide a variable volume accumulating chamber 85 which serves to reduce or eliminate pulsing of fuel at the discharge end of the conduit 63.
The oil pumping means 17 is located in the lower extension 29 and comprises a cylindrical space 87 which extends from the vent chamber 47 in generally aligned relation to the central port 31 in the intermediate wall 25. Located in the cylindrical space 87 is an oil pumping plunger or element 91 which preEerably extends integrally from the fuel pumping piston 41, which is reciprocal in the cylindrical space 87, and which, in part, defines a variable volume oil pumping chamber 93. Seal means 95 is provided between the oil pumping plunger or element 91 and the wall of the cylindrical space 87.
The oil pumping means 17 also includes a valved inlet 101 which is adapted to communicate through a conduit 103 with a source 105 of oil and which includes one-way check valve means 107 which a.EEords inflow of oil in response to an increase in the volume o~ the oil pumping chamber 93 and which prevents outflow of oil.
61~323 The oil pumping means 17 also includes a valve outlet 111. While various other arrangements can be employed, in the illustrated construction, the outlet 111 is designed to deliver oil to the fuel pumping chamber 45. More particularly, the oi.l outlet 111 comprises a bore 113 which extends axially in the oil pumping plunger or element 91, which, at one end, communicates with the oil pumping chamber 93, which, at the other end, includes one or more radial branch ports 115 which communicates with the fuel pumping chamber 45, and which includes, intermediate the inlet 101 and the outlet 111, an enlarged central portion 117 having a one way check valve means 119 which affords outflow of oil to the fuel pumping chamber 45 in response to a decrease in the volume of the oil pumping chamber 93 and which prevents inflow into the oil p-lmping chamber 93.
The fluid pressure actuated motor 13 is located generally in the upper compartment 33 and is connected to the oil pumping plunger 91 and to the fuel pumping piston 41 so as to effect common reciprocation thereof through a given stroke or distance. More particularly, the fluid pressure actuated motor 1.3 is responsive to a source of alternating relatively high and low pressures for effecting reciprocation of the fuel pumping piston ~1 and the oil pumping plunger or element 91 at a frequency less than the frequency of the alternation o~ the relatively high and low pressures. Still more particularly, the fluid pressure actuated motor 13 includes a movable wall 121 which divides the upper compartment 33 into an upper, relatively low pressure variable volume chamber 123 and a lower, relatively high pressure variable volume chamber 125. The movable wall 121 includes a central or motor piston 127 which, at its outer periphery, is connected to a flexible membrane or diaphragm 129 which, at its outer periphery, is secured to the peripheral housing wall 21 so as to divide the upper compartment 33 into the before-mentioned relatively low and high pressure chambers.
The central motor piston 127 is also preferably integrally connected with the fuel pumping piston 41 and with the oil pumping plunger or element 91 for common movement. In this last regard, the combined motor piston 127, fuel pumping piston 41, and oil pumping plunger 91 includes a central portion 131 which extends from the fuel pumping piston 41 toward the motor piston 127 and through the central bore or port 31 in the intermediate wall 25, and a connecting portion which forms an open valve cage 135 and which connects the central 131 to the motor piston 127. A suitable seal 139 is provided between the intermediate wall 25 and the central portion 131.
The fluid pressure actuated motor 13 furthur includes means biasing the movable wall 121 so as to displace the movable wall 121 in the direction minimizing the volume of the high pressure chamber 125 and maximizing the volume of the low pressure chamber 123. In the illustrated construction, such means comprises a helical spring 141 which, at one end, bears against the upper or top housing wall 23 and which, at the other end, bears against the motor piston 127.
The fluid pressure actuated motor 13 also includes means 151 for creating a pressure differential . ~
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between the low and high pressure chambers 123 and 125, respectively, so as to displace the movable wall 121 in the dire~tion minimizing the volume of the low pressure chamber 123 and maximizing the volume of the high pressure chamber 125. While various arrangements can be employed, in the illustrated construction, such means includes means adapted for connection to a source oE alternating relatively high and low pressures and including means permitting flow from the low pressure chamber 123 and preventing flow to the low pressure chamber 123, and means permitting flow to the high pressure chamber 125 and preventing flow from the high pressure chamber 125.
Preferably, the source of alternating relatively high and low pressures is the crankcase 67 of the two-stroke engine 8. However, other sources of relatively high and low pressures can be employed. In addition, relatively high and low pressure can refer to two positive pressures above atmospheric pressure, to two negative pressures below atmospheric pressure, or to one positive pressure above atmospheric pressure and one negative pressure below atmospheric pressure.
Still more specifically, the means 151 for creating the pressure differential between the relati.vely low and high pressure cylinders 123 and 125, respectively, also includes a conduit system 161 including a main conduit 163 adapted to be connected to the source of alternating high and low pressures, such as the crankcase 67 of the two-stroke engine 8, together with a Eirst or low pressure branch conduit 165 which communicates between the low pressure chamber ~q~ 3 : !, 123 and the main conduit 163 and a second or high pressure branch conduit 167 which communicates between the high pressure chamber 125 and main conduit 163.
Included in the low pressure branch conduit 165 is a one-way check valve 169 which permits flow from the low pressure chamber 123 and prevents Elow to the low pressure chamber 123. Located in the high pressure branch conduit 167 is a one way check valve 171 which permits flow to the high pressure chamber 1~5 and which prevents flow from the high pressure chamber 125.
Accordingly, alternating pressure pulses of relatively high and low pressures present in the main conduit 163 will cause the existence of a relatively high pressure in the high pressure chamber 125 and a relatively low pressure in the low pressure chamber 123, which pressure differential is of sufficient magnitude, as compared to the biasing action of the movable wall biasing spring 141, so that the pressure differential is effective to cause movement of the movable wall 121 from a position in which the high pressure chamber 125 is at a minimum volume to a position in which the low pressure chamber 123 is at a minimum volume.
Preferably, the conduit system 161 also includes means for relieving an excessive pressure differential. In this regard, the conduit system 161 includes a bypass conduit 175 which communicates with the low and high pressure branch conduits 165 and 167, respectively, so as to be i~ direct communication with the low and high pressure chambers 123 and 125, respectively. The bypass conduit 175 includes a one-way ~ 3 ;~ /3 pressure regulating valve 177 including a ball member 179 which is engaged with a seat 181 and held in such engagement by spring 183 designed to release the ball member 179 from engagement with the seat 181 in the event of an excessive differential pressure.
The fluid pressure actuated motor 13 also includes means responsive to piston movement minimi~ing the volume of the low pressure chamber 123 for establishing communication between the low and high pressure chambers 123 and 125, respectively, so as thereby to reduce or minimize the pressure differential between the low an high pressure chambers 123 and 125, respectively, and thereby permit displacement of the movable wall 121 by the biasing spring 141 in the direction minimizing the volume of the high pressure chamber 125 and maximizing the volume of the low pressure chamber 123. ~hile such means can be provided, at least in part, by a conduit (not shown) bypassing the motor piston 127, in the illustrated construction, such means comprises a central port 191 in the motor piston 127, together with a valve member 193 which is located in the open cage 135 of the combined motor piston 127, fuel pumping piston 41 and oil pumping plunger 91, and which is movable between a closed and an open position. Preferably, the valve member 193 includes a downwardly extending stem 195 which is received in a mating recess or axial bore 197 in the central portion 131 of the combined piston so as to guide movement of the valve member 193 between its open and closed positions.
In addition, the means for effecting communication between the low and high pressure chambers 123 and 125l respectively, includes a helical valve member biasing spring 201 which urges the valve member 193 ~o the open position and which, at one end, bears against the upper or top wall 23 of the housing 15 and which, at the other end, extends through the port 191 in the motor piston 127 and bears against the upper surface of the valve member 193. The valve member biasing spring 201 is designed so as to be operable to overcome the pressure differential between the low and high pressure chambers 123 and 125, respectively, and thereby to displace the valve member 193 toward the open position as the motor piston 127 approaches the position minimizing the volume of the low pressure chamber 123.
Means are also provided for insuring full opening movement of the val.ve member 193 in response to approach of the motor piston 127 to the position minimizing the volume of the low pressure chamber 123.
Such means is provided in the low pressure chamber 123 and comprises means defining an intermediate chamber 211 communicating with the motor piston port 191 and providing resistance to flow from the intermediate chamber 211 to the low pressure chamber 123 upon initial opening of the valve member 193 so as thereby to effect reduction in the pressure differential between the high pressure chamber 125 and the intermediate chamber 211 and thereby to cause movement of the valve member 193 to the full opened position.
Such movement substantially reduces the pressure differential between the low pressure chamber 123 and the high pressure chamber 125, and thereby permits movement of the movable wall 121 to minimize the volume I S
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of the high pressure chamber 125 in response to the action of the motor piston biasing spring 141. While various arrangements can be employed, in the illustrated construction, such means comprises an annular flange or ring 213 extending inwardly of the low pressure chamber 123 from the top wall 23 o the housing lS and in radially outward relation from the valve member biasing spring 201 and in radially inward relation from the motor piston biasing spring 141. In addition, such means comprises a cooperating annular 1ange or ring 215 extending from the motor piston 127 toward the housing top wall 23 and movable into telescopic relation to the flange or ring 213 as the motor piston 127 approaches the end of the stroke minimi%ing the volume of the low pressure chamber 123 so as to telescopically form the intermediate chamber 211 and to provide resistance to flow from the intermediate chamber 211 to the low pressure chamber 123.
Such resistance to flow between the intermediate chamber 211 and the low pressure chamber 123 causes deminishment in the resistance to flow or pressure drop between the high pressure chamber 125 and the intermediate chamber 211, thereby assuring action of the valve member biasing spring 201 to effect di.splacement of the valve member 193 to its fully open position.
The fluid pressure actuated motor 13 also includes means responsive to piston movement minimizing the volume of the high pressure chamber 125 for disconti~uing communication between the low and high pressure chambers 123 and 125, respectively, so as to 6~3~3 ,...', 1~-thereby permit the creation of Eluid pressure differential between the low and high pressure chambers 123 and 125 by the fluid pressure differential creating means and thereby also to effect displacement of the motor piston 127 in the direction minimizing the volume of the low pressure chamber 123 and maximizing the volume of the high pressure chamber 125. While other arrangements can be employed, in the illustrated construction, such means comprises a plurality of studs or posts 221 which extend upwardly from the intermediate partition or wall 25 toward the valve member 193 and through the open valve cage 135 for engagement with the valve member 193 to seat the valve member 193 in the closed position as the motor piston 127 approaches the position minimizing the volume of the high pressure chamber 125.
Thus, in operation, the presence of alternating high and low pressures in the conduit system 161 causes (assuming the valve member 193 to be in the closed position) buildup and maintenance of higher pressure in the relatively high pressure chamber 125 and reduction and maintenance of low pressure in the low pressure chamber 123. The pressure differential thus created causes displacement of the movable wall 121, including the motor piston 127, against the action of the motor piston biasing spring 141, to the position minimizing the volume of the low pressure chamber 123. ~s the motor piston 127 approaches the position minimizing the volume of the low pressure chamber 123, the valve member biasing spri.ng 201 serves to open the motor piston port 191 by displacing the valve member 193 to the open position ~6~3 , ,., .~ i~.
and thereby to reduce or minimize the pressure diEferential and permit displacement of the movable wall 121 by action of the biasing spring 141 to the position minimizing the volume of the high pressure chamber 125. Duriny such movement, and in the absence of a pressure differential, the valve member 193 remains in the open position under the action of the valve member biasing spring 201.
~ pon approach of the movable wall 121, including the motor piston 127, to the position minimiæing the volume of the high pressure chamber 125, the studs 221 engage the valve member 193 to cause movement thereof to the closed position. With the motor piston port 191 thus closed, the pressure differential is again created and the movable wall 121 is again displaced in the opposite direction to commence another cylce of operation. As the fuel pumpiny ql and the oil pumping plunger 91 have common movement with the motor piston 127, the fluid actuated motor 13 causes reciprocation of these components at a Erequency less than the frequency exciting the motor 13, i.e., less than the rate of alternation of the high and low pressures in the source.
Preferably, means are provided for selectively adjusting the discharge rate of the oil pumping means 17, notwithstanding displacement of the oil pumping plunger 91 through a generally constant stroke. While various other arrangements can be employed, in the illustrated construction, such means comprises a subchamber 231 which extends from the oil pumping chamber 93 and which includes therein a floating piston 233. A suitable seal 235 is provided between the ii8~3 floating piston 233 and the wall of the subchamber 231. The floating piston 233 includas, at the outer end th~reof, a portion 237 which extends vu~wardly of the subchamber 231 and which is engaged by a cam 239 which is connected by a suitable linkage 241 ~hown in dotted outline to the engine throttle 243 and which is, accordingly, selectively positionable in accordance with selective positioning of the engine throttle 243. The cam 2~9 thus variably restricts outward movement of the floating pifiton 233 so as to thereby control the e~fective pumping stroke of the oil pumping plunger 9L. A more detailed description of the arrangement for varying the di~charge rate of the oil pumping means 17 can be found in my co-pending Canadian Application Serial No. 406,927 eiled July a. 1982.
The combined fuel and oil pumping device 11 can be mounted to the block of the two-stroke engine 8 so as to afford immediate connection to the engine crankcase 67 and can be connected to remote soueces of oil and fuel. ~lternately~ if desired, the combined fuel pump and oil pump 11 can be locatsd at a remote location more or less adjacent to or with the sources of fuel and oil and a conduit (not shown~
can extend between the crankcase 67, or other source of alternating high and low pressures, and the combined fuel and oil pumping device 11.
Shown in Fig. 2 is another embodiment of a combined euel and oil pump 301 in accordance with the invention. The construction shown in Fig. 2 is generally identical to that shown in Fig. 1, and the same referece numeral have applied for like components, except for the arrangement for insuring 61~3 full opening of the valve member 193 and the arrangement for varying the amount of oil flow and the oil discharge arrangement.
With respect to the arrangement or means for insuring full opening movement of the valve member 193 in response to approach of the motor piston 127 to the position minimizing the volume of the low pressure chamber 123, in the construction illustrated in Fig. 2, the rings 213 and 215 have been omitted, thereby also omitting provision of the intermediate chamber ~11.
Instead, there is pro~ided a member or post 302 which fixedly depends downwardly from the top housing wall 23 in position for engaging the valve member 193 as the movable wall 121 minimizes the volume of the low pressure chamber 123. Such engagement causes "cracking" or slight opening of the port 191, thereby somewhat diminishing the pressure diEferential across the rnovable wall 121. Such diminishment of the pressure differential facilitates immediately subsequent operation of the poppet valve member biasing spring 201 to displace the valve member 193 so as to fully open the port 191 and thereby to substantially eliminate the pressure differential and obtain wall movement in the direction minimizing the volume of the high pressure chamber 125 under the action of the movable wall biasing spring 141. It is also noted that the post 302 serves to stabilize or locate the upper end of the poppet valve member biasing spring 201.
In the embodiment shown in Fig. 2, the oil pumping arrangement inc].udes an oil pumping piston 303 which defines, in part, a variable volume oil pumping chamber 393~ The oil pumping piston 303 is slidably engaged by the movable element 91 by means of an upper end 305 of the piston 303 being located in an enclosed central chamber 307 in the movable element 91. A mid portion 309 of the piston 303 extends outwardly of the chamber 307 through an opening 311 and connects the upper end 305 of the piston 303 to a lower portion 313 in the cylindrical space 87. The upper end 305 of the piston 303 is larger than the opening 311 so when the movable element 91 moves upwardly, the piston 303 moves with the movable element 91. Seal means 315 are provided above a lower end 317 of the piston 303 and between the lower portion 313 of the piston and the wall of the cylindrical space 87. The location of the seal means 315 permits the lower end 317 of the piston to extend below the valve inlet 101 and outlet 319.
In the embodiment, the oil pumping means 17 includes a valved outlet 319 which extends coaxially with the valved inlet 101 but on the opposite side of the cylindrical space 87. The outlet 319 includes a one way check valve 321 and affords outflow of oil to the conduit 63 for feeding the oil to the carburetor 65.
In the embodiment shown in Fig. 2, the means for selectively adjusting the discharge rate of the oil pumping means includes an adjustable stop 323 which defines, in part, the oil pumping chamber 393. The adjustable stop 323 is located in the cylindrical space 87 below the inlet 101 and outlet 319. A suitable seal 325 is provided between the adjustable stop 323 and the wall of the cylindrical space 87, and a portion 327 of the adjustable stop above the seal 325 has a diameter less than the diameter of the cylindrical space 87 to permit the upper portion 327 of the adjustable stop to . .t '~1 extend above the inlet 101 and outlet 319. The lower end of the adjustable stop 323 includes a portion 329 which extends outwardly of the cylindrical space 87 and which is engaged by the cam 239. The cam 239 operates as previously described.
The oil pumping means also includes biasing means for biasing the oil piston 303 toward the adjustable stop 323. The biasing means comprises spring 331 between the upper end 305 of the piston and the movable element 91 in the central chamber 30~.
In operation, as the movable element 91 moves downward, the oil piston 303 moves downwardly an equal distance. The biasing means or spring 331 is preloaded so that it will not deflect due to either oil pump pressure or seal friction. As the piston 303 moves downwardly, the oil pumping chamber 393 will be reduced in volume and will force oil out through the valved outlet 319. However, when the oil piston 303 contacts the adjustable stop 323, it will move no Eurther and the remaining stroke of the movable element 91 will be taken up or lost by deflecting the biasing means or spring 331. The location of the adjustable stop 323 will, therefore, vary the volume of the oil pumping chamber 393 and the amount oE oil pumped by the pumping means.
Shown in Fig. 3 is still another embodiment of a combined fuel and oil pump 401 which is associa-ted with the internal combustion engine 8 and which embodies various of the features of the invention. The construction shown in Figure 3 is generally identical to the construction shown in Figure 2 and the same reference numerals have been applied Eor like components, except that the fuel pumping arrangement has been slightly modified, except that the oil pumping arrangement has been modified to provide for variation in the output of the oil pump in accordance with engine speed without use of a movable part 239 or element 323 and associated linkage, and except that the one-way pressure-regulating valve 177 has been omitted and the stroke of the motor piston 1~7 varies in accordance with engine speed. In this last regard, the poppet valve biasing spring 201 has a spring rate which serves to open the port 191 prior to the full stroke of the motor piston 127 when the engine 8 is operating at low speed and which serves to open the port 191 upon completion of the full stroke of the motor piston 127 when the engine 8 is operating at high speed.
More particularly, as is well known, in a two~stroke engine, such as ~he engine 8, movement of the piston relative to the cylinder and crankcase 67 serves to produce in the crankcase, cyclical conditions of relativel~ high and low pressures definlng a crankcase pressure amplitude which varies in accordance with engine speed, i.e., which increases with engine speed. As, for example, when engine operation is at idle or low speed, the pressures in the crankcase can vary from about ~3 psi to about -3 psi, thus providing a crankcase pressure amplitude of 6 psi. Also, for example, when operating at high engine speed, the pressure in the crankcase can vary from about ~5 psi to -6 psi, or Erom about +10 psi to about -1 psi, thus providing a crankcase pressure amplitude of 11 psi.
Under operating conditions, because of the connection of the crankcase 67 to the low and high ~3.~ 3 '`:~
'b~...
pressure chambers 123 and 125~ respectively, and the one-way check valves 169 and 171, the pressure conditions in the low and high pressure chambers 123 and 125, respectively, rapidly reflect the pressures in the crankcase ~7 an provide a pressure differential across the movable motor piston 127, i.e., between the low and high pressure chambers 123 and 125, respectively, which pressure differential has an amplitude approximating the crankcase pressure amplitude.
The poppet valve biasing spring 201, as already indicated, has a spring rate such that partial movement of the motor piston 127 between the positions causing minimum volume of the low and high pressure chambers 123 and 125, respectively, will cause such contractlon of the poppet valve biasing spring 201 as to overcome the force on the valve member 193 occurring in response to the pressure differential when the engine 8 is operating at low speed. However, the spring rate is such that, whenever the engine 8 operates at high speed, the force created by the pressure differential is sufficiently great to provide greater travel or full travel of the movable wall 121 or motor piston 127 prior to opening of the port 191.
As a consequence, the motor piston 127 is provided with a stroke which varies with engine speed, i.e., i5 provided with a stroke which increases in length with engine speed.
The fuel pumping arrangement employed in the construction shown in Fig. 3 varies from that shown in Figs. 1 and 2 by placing the valved fuel inlet 51 in communication with the lower chamber 47 tWhich is, of course, not vented). In addition, the Euel pumping piston 39 is provided with one or more apertures 411, each having associated therewith a one-way check valve member 413 affording flow rom the lower chamber 47 to the upper chamber 45 and preventing flow ~rom the upper chamber 45 to the lower chamber 47. The stroke of fuel pumping member or piston 39 is identical to the stroke of the motor piston 127 and hence the amount of fuel pumped will vary in accordance with engine speed, i.e., will increase with increasing engine speed.
If desired, a fuel pump construction identical to that shown in Figs. 1 and 2 could also be employed.
The oil pumping arrangement diEfers from the construction shown in Figs. 1 and 2. in that the amount of oil pumped is automatically varied in accordance with engine speed and in that, due to a lost-motion connection between the motor piston 127 and the oil pumping piston 303, oil pumping does not occur until after a Eirst engine speed level~ which can be intermediate the low and high engine speeds, and which, above the first engine speed level, increases with increasing engine speed.
In this last regard, the oil pumping piston 303 is connected to the motor piston 127 to provide for common movement therewith during a portion of the motor piston stroke and to provide for lost-motion during another portion of the motor piston 127 strokeO In this regard, the upper end of the oil pumping piston 303 i3 provided with an axial recess or bore 415 which is defined, at the upper end thereof, by an internal annular flange 417 defining an opening 419, and the motor piston 127 is provided with an extension 421 which projects through the opening 419 provided by the annualar flange 417 and includes~ at the lower end, an enlarged head 423 which cannot pass through the opening 419 defined by the annualar flange 417. Thus, initial upstroke movement of the motor piston 127 from the position minimizing the volume of the high pressure chamber l~S does not cause accompanying movement of the oil pumping piston 313. However, before the motor piston 127 reaches the position minimizing the volume o~ low pressure chamber 123, the head 423 engages the flange 417 to cause common movement of the oil pumping piston 303 with the motor piston 127. Initial downstroke motion of the motor piston 127 does not cause the oil pumping piston movement until the head 423 engages the blind end of the recess or bore 415.
Thus, oil pumping operation occurs only at the top of the upstroke o~ the motor piston movement and at the bottom of the downstroke of the motor piston movement.
Accordingly, the oil pumping arrangement disclosed in Fig. 3, provides ~or little or no pumping at low engine speeds and for increasing oil pumping with increasing speeds above low engine speed.
As in the construction shown in Fig. 2, the oil discharge from the output 319 is conveyed to the fuel discharge conduit 63 for mixture therewith.
~Iowever, i~ desired, the discharged oil could be conveyed Eor mixture with the fuel in either the upper chamber ~5 or in the lower chamber 47.
Various of the features of the invention are set forth in the following claims.
Claims (25)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
Claims
1. A pump comprising means including a reciprocally movable member for pumping a fluid in response to reciprocation of said member, and motor means connected to said member and responsive to a source of alternating relatively high and low pressures for effecting reciprocation of said member at a frequency less than the frequency of the alternation of the relatively high and low pressures.
2. A combined fuel and oil pump comprising means including a reciprocally movable member for pumping fuel in response to reciprocation of said member. means including a reciprocally movable element for pumping oil in response to reciprocation of said element. and motor means connected to said member and to said element and responsive to a source of alternating relatively high and low pressures for effecting reciprocation of said member and said element at a frequency less than the frequency of the alternation of the relatively high and low pressures.
3. A combined fuel and oil pump in accordance with claim 1 wherein said motor means includes a movable piston, wherein said fuel pumping means includes a variable volume fuel pumping chamber defined in part by said movable member, wherein said oil pumping means includes a variable volume oil pumping chamber defined in part by said movable element and wherein said motor piston, said member and said element constitute an integral component.
4. A combined fuel and oil pump in accordance with Claim 3 wherein said oil pumping means includes oil discharge means including a valved bore extending in said component between said oil pumping chamber and said fuel pumping chamber.
5. A combined fuel and oil pump in accordance with Claim 1 wherein said oil pumping means, said fuel pumping means, and said motor means form parts of a single housing.
6. A combined fuel and oil pump in accordance with Claim 3 wherein said fuel pumping means includes a variable volume pumping chamber defined in part by said movable member and wherein said oil pumping means includes discharge means communicating with said variable volume fuel pumping chamber.
7. A combined fuel and oil pump in accordance with Claim 1 wherein said movable element reciprocates through a given distance, and wherein said oil pumping means includes means for varying the output thereof notwithstanding the reciprocation of said element through said given distance.
8. A combined fuel and oil pump in accordance with Claim 1 wherein said motor means comprises a housing, a motor piston movable reciprocally in said housing and dividing said housing into a relatively low pressure chamber and a relatively high pressure chamber, means biasing said motor piston so as to displace said motor piston in the direction minimizing the volume of said high pressure chamber and maximizing the volume of said low pressure chamber, means for creating a fluid pressure differential between said high and low pressure chambers so as to displace said motor piston in the direction minimizing the volume of said low pressure chamber and maximizing the volume of said high pressure chamber, means responsive to motor piston movement minimizing the volume of said low pressure chamber for establishing communication between said low and high pressure chambers so as thereby to reduce the pressure differential between said high and low pressure chambers and thereby permit displacement of said motor piston by said biasing means in the direction minimizing the volume of said high pressure chamber and maximizing the volume of said low pressure chamber, and means responsive to motor piston movement minimizing the volume of said high pressure chamber for discontinuing communication between said high and low pressure chambers so as to thereby permit the creation of fluid pressure differential between said high and low pressure chambers by said fluid pressure differential creating means and thereby effect displacement of said motor piston in the direction minimizing the volume of said low pressure chamber and maximizing the volume of said high pressure chamber.
9. A combined fuel and oil pump in accordance with Claim 8 wherein said means for creating a pressure differential between said high and low pressure chambers comprises means adapted to be connected to a source of alternating relatively high and low pressures and including means permitting flow from said low pressure chamber and preventing flow to said low pressure chamber, and means permitting flow to said high pressure chamber and preventing flow from said high pressure chamber.
10. A combined fuel and oil pump in accordance with Claim 8 wherein said motor also includes pressure relief means connected between said high and low pressure chambers to limit the pressure differential therebetween.
11. A combined fuel and oil pump in accordance with Claim 8 wherein said means for establishing and disconnecting communication between said high and low pressure chambers includes a port in said motor piston, a valve member movable relative to said port between open and closed positions, means biasing said valve member away from said port, and means on said housing engageable with said valve member to close said port in response to piston movement minimizing the volume of said high pressure chamber.
12. A combined fuel and oil pump in accordance with Claim 11 wherein said means responsive to motor piston movement minimizng the volume of said low pressure chamber for establishing communication between said low and high pressure chambers so as thereby to reduce the pressure differential between said high and low pressure chambers and thereby permit displacement of said motor piston by said biasing means in the direction maximizing the volume of said low pressure chamber and minimizing the volume of said high pressure chamber comprises said port in said motor piston communicating between said low and high pressure chambers, said valve member which is movable between open and closed position whereby, when said valve member is in said closed position, and a pressure differential is created between said low and high pressure chambers, said motor piston is operable against the action of said motor piston biasing means so as to minimize the volume of said low pressure chamber, said means biasing valve member away from said port, which biasing means is operable, in response to motor piston movement minimizing the volume of said low pressure chamber, to displace said valve member toward said open position so as to permit limited flow from said high pressure chamber to said low pressure chamber when said valve member biasing means exerts a force which is equal to, or slightly greater than, the force resulting from the pressure differential between said low and high pressure chambers, and means in said low pressure chamber operable, in response to motor piston movement minimizing the volume of said low pressure chamber, to define an intermediate chamber communicating with said port and providing resistance
12. A combined fuel and oil pump in accordance with Claim 11 wherein said means responsive to motor piston movement minimizng the volume of said low pressure chamber for establishing communication between said low and high pressure chambers so as thereby to reduce the pressure differential between said high and low pressure chambers and thereby permit displacement of said motor piston by said biasing means in the direction maximizing the volume of said low pressure chamber and minimizing the volume of said high pressure chamber comprises said port in said motor piston communicating between said low and high pressure chambers, said valve member which is movable between open and closed position whereby, when said valve member is in said closed position, and a pressure differential is created between said low and high pressure chambers, said motor piston is operable against the action of said motor piston biasing means so as to minimize the volume of said low pressure chamber, said means biasing valve member away from said port, which biasing means is operable, in response to motor piston movement minimizing the volume of said low pressure chamber, to displace said valve member toward said open position so as to permit limited flow from said high pressure chamber to said low pressure chamber when said valve member biasing means exerts a force which is equal to, or slightly greater than, the force resulting from the pressure differential between said low and high pressure chambers, and means in said low pressure chamber operable, in response to motor piston movement minimizing the volume of said low pressure chamber, to define an intermediate chamber communicating with said port and providing resistance
Claim 12 (continued) to flow from said intermediate chamber to said low pressure chamber so as thereby to effect reduction in the pressure differential between said high pressure chamber and said intermediate chamber and thereby to cause movement of said valve member to said open position, whereby to substantially reduce the pressure differential between said low and high pressure chambers, and thereby to cause motor piston movement minimizing the volume of said high pressure chamber in response to the action of said motor piston biasing means.
13. A combined fuel and oil pump in accordance with Claim 8 wherein said motor piston reciprocates through a given distance, and further including means including an element reciprocally movable through said given distance for pumping oil in response to reciprocation of said element, said oil pumping means also including means for varying the output thereof notwithstanding the reciprocation of said element through said given distance.
14. A combined fuel and oil pump in accordance with Claim 8 wherein said fuel pumping means includes a variable volume fuel pumping chamber defined in part by said movable member, and further including means including an element reciprocally movable through said given distance for pumping oil in response to reciprocation of said element, said oil pumping means including a variable volume oil pumping chamber defined in part by said element, and wherein said motor piston, said member and said element constitute an integral component.
15. A combined fuel and oil pump in accordance with Claim 14 wherein said oil pumping means includes oil discharge means including a valved bore extending in said component between said oil pumping chamber and said fuel pumping chamber.
16. A combined fuel and oil pump in accordance with Claim 1 wherein said motor means comprises a housing. a motor piston movable reciprocally in said housing and dividing said housing into a relatively low pressure chamber and a relatively high pressure chamber, means biasing said motor piston so as to displace said motor piston in the direction minimizing the volume of said high pressure chamber and maximizing the volume of said low pressure chamber, means for creating a fluid pressure differential between said high and low pressure chambers so as to displace said motor piston in the direction minimizing the volume of said low pressure chamber and maximizing the volume of said high pressure chamber, and means responsive to motor piston movement minimizing the volume of said low pressure chamber for establishing communication between said low and high pressure chambers so as thereby to reduce the pressure differential between said high and low pressure chambers and thereby permit displacement of said motor piston by said biasing means in the direction minimizing the volume of said high pressure chamber and maximizing the volume of said low pressure chamber.
17. A combined fuel and oil pump in accordance with Claim 16 wherein said means for establishing communication between said high and low pressure chambers includes a port in said motor piston, a valve member movable relative to said port between open and closed positions, mean on said housing engageable with said valve member for initially displacing said valve member from said closed position in response to piston movement minimizing the volume of said low pressure chamber, and biasing means operable subsequent to initial, displacement of said valve member from said closed position, for displacing said valve member to said open position.
18. A combined fuel and oil pump in accordance with Claim 17 wherein said means for initially displacing said valve member from said closed position comprises a stationarily extending member.
19. A combined fuel and oil pump in accordance with Claims 2, 5 or 7 and wherein said means for pumping oil further includes a variable volume oil pumping chamber, an oil piston defining, in part, said oil pumping chamber, an adjustable stop defining, in part. said oil pumping chamber, and means connecting said movable element and said piston for displacing said piston in response to movement of said element and permitting lost motion between said element and said piston in response to engagement of said piston with said stop.
20. A combined fuel and oil pump comprising means including a reciprocally movable member for pumping fuel in response to reciprocation of said member, means including a reciprocally movable element for pumping oil in response to reciprocation of said element, and motor means connected to said member and to said element and responsive to a source of alternating relatively high and low pressures for effecting reciprocation of said member and said element at a frequency less than the frequency of the alternation of the relatively high and low pressures, said motor means including relatively low and high pressure chambers which inversely vary in volume, and means for creating a pressure differential between said high and low pressure chambers comprising means adapted to be connected to a source of alternating relatively high and low pressures and including means permitting flow from said low pressure chamber and preventing flow to said low pressure chamber, and means permitting flow to said high pressure chamber and preventing flow from said high pressure chamber.
21. A combined fuel and oil pump in accordance with Claim 20 wherein said oil pumping means includes oil discharge means including a valved bore extending in said component between said oil pumping chamber and said fuel pumping chamber.
-3?-
-3?-
22. A combined fuel and oil pump in accordance with Claim 20 wherein said oil pumping means, said fuel pumping means, and said motor means form parts of a single housing.
23. A combined fuel and oil pump in accordance with Claim 20 wherein said fuel pumping means includes a variable volume pumping chamber defined in part by said movable member, and wherein said oil pumping means includes discharge means communicating with said variable volume fuel pumping chamber.
24. A combined fuel and oil pump in aocordance with Claim 20 wherein said movable element reciprocates through a given distance, and wherein said oil pumping means includes means for varying the output thereof notwithstanding the reciprocation of said element through said given distance.
25. A combined fuel and oil pump in accordance with Claim 20 wherein said motor means comprises a housing closed to the atmosphere. a motor piston movable reciprocally in said housing and dividing said housing into a relatively low pressure chamber and a relatively high pressure chamber means biasing said motor piston so as to displace said motor piston in the direction minimizing the volume of said high pressure chamber and maximizing the volume of said low pressure chamber. means for creating a fluid pressure differential between said high and low pressure chambers so as to displace said motor piston in the direction minimizing the volume of said low pressure chamber and maximizing the volume of said high pressure chamber means responsive to motor piston movement minimizing the volume of said low pressure chamber for establishing communication between said low and high pressure chambers so as thereby to reduce the pressure differential between said high and low pressure chambers and thereby permit displacement of said motor piston by said biasing means in the direction minimizing the volume of said high pressure chamber and maximizing the volume of said low pressure chamber, and means responsive to motor piston movement minimizing the volume of said high pressure chamber for discontinuing communication between said high and low pressure chambers so as to thereby permit the creation of fluid pressure differential between said high and low pressure chambers by said Clam 25 (continued) fluid pressure differential creating means and thereby effect displacement of said motor piston in the direction minimizing the volume of said low pressure chamber and maximizing the volume of said high pressure chamber.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000474594A CA1204354A (en) | 1981-10-23 | 1985-02-19 | Combined fluid pressure actuated fuel and oil pump |
| CA000474597A CA1204355A (en) | 1981-10-23 | 1985-02-19 | Combined fluid pressure actuated fuel and oil pump |
| CA000474595A CA1205707A (en) | 1981-10-23 | 1985-02-19 | Combined fluid pressure actuated fuel and oil pump |
| CA000474596A CA1204358A (en) | 1981-10-23 | 1985-02-19 | Combined fluid pressure actuated fuel and oil pump |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US314,224 | 1981-10-23 | ||
| US06/314,224 US4473340A (en) | 1981-10-08 | 1981-10-23 | Combined fluid pressure actuated fuel and oil pump |
| US410,497 | 1982-08-23 | ||
| US06/410,497 US4539949A (en) | 1981-10-08 | 1982-08-23 | Combined fluid pressure actuated fuel and oil pump |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000474594A Division CA1204354A (en) | 1981-10-23 | 1985-02-19 | Combined fluid pressure actuated fuel and oil pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1196823A true CA1196823A (en) | 1985-11-19 |
Family
ID=26979264
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000413422A Expired CA1196823A (en) | 1981-10-23 | 1982-10-14 | Combined fluid pressure actuated fuel and oil pump |
Country Status (8)
| Country | Link |
|---|---|
| JP (3) | JPH0625530B2 (en) |
| AU (4) | AU563525B2 (en) |
| CA (1) | CA1196823A (en) |
| FR (1) | FR2515256B1 (en) |
| GB (1) | GB2108212B (en) |
| HK (4) | HK102090A (en) |
| IT (1) | IT1226867B (en) |
| SE (1) | SE8703997D0 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4552101A (en) * | 1983-02-07 | 1985-11-12 | Outboard Marine Corporation | Fluid pressure actuated motor with pneumatically-coupled pistons |
| US4551076A (en) * | 1983-10-07 | 1985-11-05 | Outboard Marine Corporation | Fluid driven pump with one-way valve in fluid inlet |
| US4594970A (en) * | 1985-02-11 | 1986-06-17 | Outboard Marine Corporation | Marine installation including fuel/oil mixing device |
| US6174136B1 (en) * | 1998-10-13 | 2001-01-16 | Liquid Metronics Incorporated | Pump control and method of operating same |
| US6280147B1 (en) | 1998-10-13 | 2001-08-28 | Liquid Metronics Incorporated | Apparatus for adjusting the stroke length of a pump element |
| CN106948861A (en) * | 2017-04-14 | 2017-07-14 | 覃勇 | Pressure kinetic energy engine and its implementation |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4323606Y1 (en) * | 1966-03-15 | 1968-10-05 | ||
| DE1804411A1 (en) * | 1968-10-22 | 1970-05-14 | Teves Gmbh Alfred | Device working with pneumatic assistants |
| DE1930811A1 (en) * | 1969-06-18 | 1971-01-07 | Nsu Auto Union Ag | Conveyor and metering pump |
| DE2034816A1 (en) * | 1970-07-14 | 1972-01-20 | Audi NSU Auto Union AG, 7107 Neckars ulm | Feeder and metering pump |
| JPS4938643A (en) * | 1972-08-11 | 1974-04-10 | ||
| US3913551A (en) * | 1974-01-04 | 1975-10-21 | Raymond Lee Organization Inc | Protection device for engine operating on gas-oil mixture |
| US3938425A (en) * | 1974-04-15 | 1976-02-17 | Houdaille Industries, Inc. | Pump stroke adjustment device |
| US4142486A (en) * | 1977-09-06 | 1979-03-06 | Schreier Joseph S | Fuel-oil mixing apparatus for internal-combustion engines |
-
1982
- 1982-09-24 GB GB08227383A patent/GB2108212B/en not_active Expired
- 1982-09-28 AU AU88803/82A patent/AU563525B2/en not_active Ceased
- 1982-10-14 CA CA000413422A patent/CA1196823A/en not_active Expired
- 1982-10-15 FR FR8217263A patent/FR2515256B1/en not_active Expired
- 1982-10-19 IT IT8249298A patent/IT1226867B/en active
-
1986
- 1986-07-31 AU AU60772/86A patent/AU581096B2/en not_active Ceased
- 1986-07-31 AU AU60773/86A patent/AU579746B2/en not_active Ceased
- 1986-07-31 AU AU60771/86A patent/AU579745B2/en not_active Ceased
-
1987
- 1987-10-14 SE SE8703997A patent/SE8703997D0/en not_active Application Discontinuation
-
1989
- 1989-07-24 JP JP1191237A patent/JPH0625530B2/en not_active Expired - Lifetime
- 1989-07-24 JP JP1191238A patent/JPH0625531B2/en not_active Expired - Lifetime
-
1990
- 1990-06-11 JP JP2152505A patent/JPH03115781A/en active Granted
- 1990-12-06 HK HK1020/90A patent/HK102090A/en unknown
- 1990-12-13 HK HK1049/90A patent/HK104990A/en unknown
- 1990-12-13 HK HK1048/90A patent/HK104890A/en unknown
- 1990-12-13 HK HK1047/90A patent/HK104790A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03115781A (en) | 1991-05-16 |
| JPH0454068B2 (en) | 1992-08-28 |
| GB2108212B (en) | 1986-04-16 |
| JPH0625530B2 (en) | 1994-04-06 |
| AU6077286A (en) | 1986-12-04 |
| JPH0625531B2 (en) | 1994-04-06 |
| HK102090A (en) | 1990-12-14 |
| FR2515256B1 (en) | 1986-04-18 |
| AU8880382A (en) | 1983-04-28 |
| FR2515256A1 (en) | 1983-04-29 |
| AU6077186A (en) | 1986-12-04 |
| JPH02161115A (en) | 1990-06-21 |
| HK104790A (en) | 1990-12-21 |
| GB2108212A (en) | 1983-05-11 |
| SE8703997L (en) | 1987-10-14 |
| IT8249298A0 (en) | 1982-10-19 |
| HK104990A (en) | 1990-12-21 |
| AU581096B2 (en) | 1989-02-09 |
| IT1226867B (en) | 1991-02-21 |
| SE8703997D0 (en) | 1987-10-14 |
| AU579746B2 (en) | 1988-12-08 |
| AU6077386A (en) | 1986-12-04 |
| AU579745B2 (en) | 1988-12-08 |
| HK104890A (en) | 1990-12-21 |
| JPH02161116A (en) | 1990-06-21 |
| AU563525B2 (en) | 1987-07-16 |
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| Publication | Publication Date | Title |
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