US2160978A - Fuel pump - Google Patents

Fuel pump Download PDF

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Publication number
US2160978A
US2160978A US5489435A US2160978A US 2160978 A US2160978 A US 2160978A US 5489435 A US5489435 A US 5489435A US 2160978 A US2160978 A US 2160978A
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Patent type
Prior art keywords
distributor
pump
cylinder
cylinders
fuel
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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 - Lifetime
Application number
Inventor
Frank C Mock
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Eclipse Aviation Corp
Original Assignee
Eclipse Aviation Corp
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL, WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangements of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangements of cylinders having cylinder axes coaxial with, or parallel or inclined to main shaft axis
    • F04B1/14Multi-cylinder machines or pumps characterised by number or arrangements of cylinders having cylinder axes coaxial with, or parallel or inclined to main shaft axis having stationary cylinders
    • F04B1/141Component parts
    • F04B1/146Swash plates or actuating elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL, WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2700/00Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/13Special devices for making an explosive mixture; Fuel pumps
    • F02M2700/1317Fuel pumpo for internal combustion engines
    • F02M2700/1329Controlled rotary fuel pump with parallel pistons or with a single piston in the extension of the driving shaft
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/7722Line condition change responsive valves
    • Y10T137/7837Direct response valves [i.e., check valve type]
    • Y10T137/7838Plural
    • Y10T137/7845With common biasing means
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/8593Systems
    • Y10T137/86493Multi-way valve unit
    • Y10T137/86501Sequential distributor or collector type

Description

June 6, 1939. F. c. MOCK FUEL PUMP Filed Dec. 17, 1955 'INVENTOR. Frank C. Mock BY ZJMM ATTORNEY.

Patented June 6, 1939 FUEL PUMP Frank 0. Mock, Montclain, N. J., 'assignor to Eclipse Aviation. Corporation, East Orange, N. J., a corporation of New Jersey Application December 17, 1935, Serial No. 54,894

2 Claims.

This invention relates to pumps, and more particularly to a multi-cylinder pump of the reciprocating piston type.

It has heretofore been proposed to provide v5 a multi-cylinder pump wherein the cylinders have the longitudinal axes thereof disposed parallel and spaced about a common central axis which coincides with the axis of rotation of a distributor adapted to control the discharge from each pump 10 cylinder. Such a pump has been used to supply fuel to the cylinders of internal combustion engines and is frequently referred to as a solid fuel injection pump. In the prior construction referred to, it has been considered necessary to provide means for bypassing a portion of the fuel discharged from each pump cylinder in order to control. the quantity of fuel delivered to the engine cylinders.

An object of the present invention is to pro- 20 vide a novel pump of the above type of simplified construction and one which does not require the use of a variable or adjustable by-pass discharge opening in order to regulate the rate of discharge from the pump.

Another object of the invention is to provide a multi-cylinder pump embodying novel means for regulating the discharge from each pump cylinder, said means constituting a distributor adapted to close the intake to each cylinder and 30 to open said intakes at selected times.

A further object is to provide novel pumping apparatus of the above type for supplying fuel to an internal combustion engine, said apparatus being so constructed that each pump cylinder will 35 have a constant angular time of intake port opening for any given control setting, the time in seconds of intake opening varying inversely as the engine speed.

Another object is to provide a novel method 4 for controlling the output of a pump.

'A further object is to provide a novel pump of the typewherein'the piston (or pistons) is of fixed stroke and is adapted to control the inlet to the pump cylinder, thevtime of inlet opening 45 being variable relative to the position of said piston with-respect to the inlet, whereby the output of the pump is controlled. 7

A still further object is to provide a novel pump 50 for supplying fuel to the cylinders of an internal combustion engine, said pump being so constructed. that the throttle lever or accelerator of the v .engine may be employed to simultaneously control' the engine air supply valve and to regulate the 55 fuel discharge from saidpump to secure the desired mixture of fuel and air supplied to the engine cylinders.

The above and other objects and advantages of the invention will appear more fully hereinafter in the detailed description which is to be read with the accompanying drawing illustrating the preferred embodiment. It is to be expressly understood, however, that the drawing is for the purpose of illustration only and is not designed as a definition of the limits of the invention, reference being primarily had for this purpose to the appended claims.

In the drawing wherein like reference characters refer to like parts throughout the several views, Fig. 1 is a longitudinal sectional view illustrating a multi-cylinder pump constructed in accordance with the invention;

Fig. 2 is a detail, partly in section and with parts broken away, illustrating suitable means for moving a pump piston to fuel discharge position in accordance with the present invention;

Fig. 3 is a detail, similar to Fig. 2, showing the piston and actuating means therefor in discharge position; and

Fig. 4 is a diagrammatic view illustrating operating connections between the pump shown in Fig. 1 and a multi-cylinder engine.

In the form shown in Fig. 1, the pump com prises a cup-shaped housing or casing 5' provided in the inner wall thereof, adjacent the top, with an annular shoulder 6 which constitutes a support for a mounting ring I for a plurality of pump cylinders 8. Thimbles 9 threaded into ring 1 secure said cylinders in operative position, the inner end of each thimble having engagement with a shoulder formed on theouter wall of the cylinder. A. piston ll) of fixed stroke, for each cylinder, is provided at its lower end with an adjustable tappet ll siidably guided in a plate i2 rigidly mounted in any suitable manner, as by an annular shoulder, in the lower portion of casing 5. Preferably, windows l3 are provided in the casing to facilitate adjustment of-tappets I l, and said'windows may be provided with a suitable closure or closures M. A coilcompressionspring i5 is interposed between thimble 9 and a follower l6 rigidly attached in any suitable manner to the lower end'of the piston, said spring surrounding an extension or sleeve 8a, formed integrally with the wall of cylinder 8, which p rojects through thimble 9 to provide the desired bearing surface 1 for the piston and to nreventengag'ement between the piston and'spring. The lattertendsto main- "tain' thepiston atthe end of its suction-stroke,

with follower I6 in engagement with the upper surface of plate I2.

Novel means are provided for moving pistons I8 to discharge position. As shown, said means is constituted by a power or drive shaft I1 adapted to be operatively connected in any suitable manner to a power shaft of the engine. Shaft I1 is rotatably mounted in casing by means of a hearing I8 carried in the lower wall of the casing and a bearing I9 mounted in the central cupshaped portion I2a of member I2. The upper splined end I1a of the power shaft projects above the plane of the upper surface of member I2. A radial arm 28 is rigidly attached to, or formed integrally with, shaft I1, intermediate the ends thereof, so that said arm projects laterally between bearings I8 and I9. Mounted on the outer end of arm 28 is a ball bearing cam roller 2I adapted to engage in succession the various piston tappets II whereby the pistons are moved to discharge position, said pistons being returned on the suction stroke by means of springs I5. It will be noted that the longitudinal axis of shaft I1 coincides with the longitudinal axis of casing 5 and that the axes of the cylinders 8 are parallel thereto, the radial distance of each cylinder axis from the shaft axis being the same.

Novel means are provided for distributing or supplying fuel to the various cylinders 8 through suitable cylinder intake passages 22, said distributor means being so constructed that the rate of fuel flow from each cylinder may be regulated by controlling said means. To this end casing 5 is provided with a cover 23 having a centrally disposed passage in which is mounted a spacing sleeve 24. A threaded boss 23a. surrounds the upper end of said passage to receive a nipple 25 for a fuel supply pipe 26 (Fig. 4). Cover 23 is provided on its lower face with a central and inwardly extending sleeve 23b constituting a housing for a rotatable distributor 21 adapted to be rotated by shaft I1 but angularly adjustable relative to said shaft.

In the form illustrated, the lower end of distributor 21 is provided with spiral splines 21a. which are engaged by a longitudinally movable sleeve 28, the lower end of said sleeve being slidably and drivably secured to the upper end Hit of the power or drive shaft by means of straight splines. Preferably, the lower portion of distributor 21 is of reduced diameter to provide a shoulder adapted to be engaged by suitable packing and a gland 29 for retaining said distributor in operative position within sleeve 23b. The upper portion or head of the distributor, which has a working clearance with the inner surface of the sleeve of approximately .002, is recessed to a diameter substantially equal to the inside diameter ofspacing sleeve 24, the fuel supplied to the pump flowing through nipple 25, sleeve 24, and into said recess 2117. A radial passage 38 is provided in the wall of the recessed portion or head of the distributor, said passage having a periphery substantially identical to that of a cross-section of each of the passages 22 and being located longitudinally of distributor 21 so that there will be full registry between opening 38 and the adjacent ends of each of the passages 22 during rotation of the distributor.

It is desirable to provide for angular adjustment of distributor 21 relative to intake passages 22 or cylinders 8, and for this purpose sleeve 28 is provided with suitable collars 28a to receive a shifting fork 3| adapted to be actuated by a rock shaft 32 which extends through the wall of easing 5. Movement of fork 3I in a counter-clockwise direction, for example, moves sleeve 28 upwardly. whereby the angular position of distributor 21 may be adjusted relative to the intake passages 22 of the cylinders, and this adjustment is niade without disturbing the driving relation'between said distributor and said shaft, and without longitudinal movement of the distributor.

Cover 23 is provided with discharge openings or passages 33 adapted to be closed by one or more valves 34, 35. As illustrated, valve 34 is a spring pressed ball valve of less diameter than the spring pressed ball valve 35. Seating spring 38 for ball valve 35 is positioned by the walls of a recess formed in a nipple 31, threaded into a boss 38 on the cover, each of the nipples 31 receiving pipes, one of which is shown at 39 in Fig. 4, for connecting each pump cylinder to the respective engine cylinder.

In operation, shaft I1 is rotated, whereby cam roller 2| engages follower levers II in succession .to actuate pistons I8 of fixed stroke to discharge fuel from cylinders 8 past valves 34, 35, pipes 39, to the corresponding cylinders of the engine. After each piston or plunger I8 is moved by roller 2I to discharge its fuel load, said piston is forced downwardly or inwardly by spring I5, whereupon a partial vacuum is created in the cylinder above the piston. If the piston be moved by spring I5 to a position such that the upper end of the piston is below intake passage'or side port 22, fuel will flow from the distributor into the cylinder when distributor passage 38 registers with intake passage 22. The amount of fuel drawn into the cylinder by the partial vacuum and hence the amount of fuel discharged from each cylinder may be regulated by controlling the angular time said port 38 opens relative to the upward movement of piston I8, it being noted that in its upward movement the piston is effective to seal the inner end of passage 22. The angular adjustment of distributor 21, and hence passage 38, is controlled by longitudinal movement of sleeve 28.

It will be noted that the construction illustrated and described gives a constant angular time of intake port opening, which results in an increasing time in seconds of port opening as the engine speed decreases. Consequently, an angular adjustment of distributor 21 is required which is similar to the angular adjustment required for the usual air intake or throttle valve of an internal combustion engine, and accordingly the desired mixture ratio for the engine may be obtained by mechanically connecting the adjusting mechanism for the distributor to the control lever for the engine air throttle.

As' shown more clearly in Fig. 4, the above connection may be effected by means of a link 48 pivotally connected at one-end to an arm 4| secured to the rock shaft 32 for fork 3I. The opposite end of link 48 is pivotally connected to a bell crank lever 42 which is operatively mount- .ed on a fixed pivot that may be carried by the A throttle or air valve 44 in said I pump which is simple in construction and which is adapted for a wide variety of uses. The pistons l coact with the angularly adjustable distributor 21 to control the output of the pump. For example, if the distributor is adjusted to such an angular position that port 30 does not begin to register with an inlet passage 22 until the piston for said passage reaches a position, in its upward movement, such that the inner end of passage 22 is almost closed, it will be seen that only a small amount of fuel will be drawn into the cylinder, and hence a small amount will be delivered to the engine cylinder. The time, in seconds, of intake opening varies inversely as the engine speed and accordingly the adjusting means for the distributor may be mechanically connected to the means for controlling the engine air intake valve.

Various changes may be made in details of construction and the arrangement of the parts, and, as will be understood by those skilled in the art, the apparatus and the novel method disclosed are not limited to use in connection with fuel injection, nor tomulti-cylinder pumps. It will be understood that the term distributor as used here is sufliciently broad to include means for controlling one or more inlets. Reference will accordingly be had, primarily, to the appended claims for a definition of the limits of the invention.

What is claimed is:

1. In a fluid pump, a body, a plurality of parallel cylinders therein arranged about a central drive shaft, a piston in each of said cylinders, a cam on said drive shaft arranged to actuate said pistons in sequence, said cylinders having discharge ports and inwardly extending inlet ports,

said pistons being movable to close said intake a portion forming a shaft, said valve shaft and said driving shaft being aligned, one of said shafts having helical threads on its outer surface and the other shaft having straight splines, a slidable sleeve encircling the adjacent ends of both shafts and cooperating with the threads and splines for changing the angular relation between the shafts, means for preventing axial movement of each of said shafts, said sleeve valve having'a port in its side wall adapted to align with each intake port in sequence, and means for introducing fiuid to the interior of said valve whereby the fluid is distributed to the cylinders.

2. In an apparatus of the class described, a casing, a fluid receiving distributor rotatably mounted in said casing, means for preventing axial movement of said distributor, a plurality of pump cylinders positioned in said casing at substantially equal radial distances from said distributor, said cylinders having intake-passages adapted to receive fluid from said distributor, said distributor being in the form of a shaft having an axial recess closed at its driven end and open at the other end for receiving a supply of fluid, and said distributor having a radial port extending through its side wall into said recess to periodically align with the cylinder intake passages and to permit fluid to flow from the recess into the cylinders, pistons in said cylinders arranged to close the cylinder intake passages during reciprocation of the pistons, means including a shaft for actuating said pistons, said shaft being axially aligned with said distributor shaft, means including an axially movable sleeve encircling the adjacent ends of both shafts for angularly adjusting said distributor relative to said piston actuating shaft and for driving the distributor.

FRANK C. MOCK.

US2160978A 1935-12-17 1935-12-17 Fuel pump Expired - Lifetime US2160978A (en)

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Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2436797A (en) * 1943-12-27 1948-03-02 Deschamps Fuel Injection Corp Fuel injection pump
US2647683A (en) * 1950-09-06 1953-08-04 Gen Motors Corp Compressor
US2982215A (en) * 1958-09-02 1961-05-02 William E Baker Atomizing pump
US3043224A (en) * 1960-08-04 1962-07-10 Brown Grease Gun Company Inc Self-contained service pump assembly
US3107623A (en) * 1961-08-10 1963-10-22 Budzich Tadeusz Variable discharge pump
US3129702A (en) * 1962-06-26 1964-04-21 Marion Arbanas Variable delivery pump
US3954353A (en) * 1973-09-17 1976-05-04 Ludwig Anton Mokesch Axial piston pump
US4286931A (en) * 1978-02-16 1981-09-01 Robert Bosch Gmbh Fuel injection pump for internal combustion engines, particularly for diesel engines
US4411602A (en) * 1979-02-12 1983-10-25 Ray Earl L Fuel injection apparatus for internal combustion engines
FR2660021A1 (en) * 1990-03-26 1991-09-27 Craf Modular pump with several outputs each fed by a pumping element.
US5207078A (en) * 1991-09-02 1993-05-04 Kabushiki Kaisha Toyoda Jidoshokki Reciprocatory piston type compressor for a refrigeration system
US5342178A (en) * 1992-01-29 1994-08-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Coolant gas guiding mechanism in compressor
US5362208A (en) * 1992-03-04 1994-11-08 Nippondenso Co., Ltd. Swash plate type compressor
US5366350A (en) * 1993-04-13 1994-11-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Gas guiding mechanism in a piston type compressor
US5378115A (en) * 1992-08-07 1995-01-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor
US5380163A (en) * 1993-02-23 1995-01-10 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Gas guiding mechanism in a piston type compressor
US5401144A (en) * 1992-05-13 1995-03-28 Kabushiki Kaisha Toyoda Jisoshokki Seisakusho Swash plate type refrigerant compressor
US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
US5478212A (en) * 1992-03-04 1995-12-26 Nippondenso Co., Ltd. Swash plate type compressor
US5674054A (en) * 1993-05-21 1997-10-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocating type compressor
US20110150675A1 (en) * 2009-12-22 2011-06-23 Ampro Manufacturing, Inc. Viscous Fluid Pump And Related Methods
WO2014135883A2 (en) * 2013-03-07 2014-09-12 Marshalsea Hydraulics Limited A pump

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2436797A (en) * 1943-12-27 1948-03-02 Deschamps Fuel Injection Corp Fuel injection pump
US2647683A (en) * 1950-09-06 1953-08-04 Gen Motors Corp Compressor
US2982215A (en) * 1958-09-02 1961-05-02 William E Baker Atomizing pump
US3043224A (en) * 1960-08-04 1962-07-10 Brown Grease Gun Company Inc Self-contained service pump assembly
US3107623A (en) * 1961-08-10 1963-10-22 Budzich Tadeusz Variable discharge pump
US3129702A (en) * 1962-06-26 1964-04-21 Marion Arbanas Variable delivery pump
US3954353A (en) * 1973-09-17 1976-05-04 Ludwig Anton Mokesch Axial piston pump
US4286931A (en) * 1978-02-16 1981-09-01 Robert Bosch Gmbh Fuel injection pump for internal combustion engines, particularly for diesel engines
US4411602A (en) * 1979-02-12 1983-10-25 Ray Earl L Fuel injection apparatus for internal combustion engines
FR2660021A1 (en) * 1990-03-26 1991-09-27 Craf Modular pump with several outputs each fed by a pumping element.
EP0449692A1 (en) * 1990-03-26 1991-10-02 Consortium De Recherches Pour L'application Des Fluides, Craf Modular pump with plural outlets, each supplied by a pump unit
US5207078A (en) * 1991-09-02 1993-05-04 Kabushiki Kaisha Toyoda Jidoshokki Reciprocatory piston type compressor for a refrigeration system
US5342178A (en) * 1992-01-29 1994-08-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Coolant gas guiding mechanism in compressor
US5362208A (en) * 1992-03-04 1994-11-08 Nippondenso Co., Ltd. Swash plate type compressor
US5478212A (en) * 1992-03-04 1995-12-26 Nippondenso Co., Ltd. Swash plate type compressor
US5401144A (en) * 1992-05-13 1995-03-28 Kabushiki Kaisha Toyoda Jisoshokki Seisakusho Swash plate type refrigerant compressor
US5378115A (en) * 1992-08-07 1995-01-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor
US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
US5380163A (en) * 1993-02-23 1995-01-10 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Gas guiding mechanism in a piston type compressor
US5366350A (en) * 1993-04-13 1994-11-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Gas guiding mechanism in a piston type compressor
US5674054A (en) * 1993-05-21 1997-10-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocating type compressor
US20110150675A1 (en) * 2009-12-22 2011-06-23 Ampro Manufacturing, Inc. Viscous Fluid Pump And Related Methods
US8333567B2 (en) * 2009-12-22 2012-12-18 Ampro Manufacturing, Inc. Viscous fluid pump and related methods
WO2014135883A2 (en) * 2013-03-07 2014-09-12 Marshalsea Hydraulics Limited A pump
WO2014135883A3 (en) * 2013-03-07 2014-11-06 Marshalsea Hydraulics Limited Axial piston pump

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