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Publication numberUS3459131 A
Publication typeGrant
Publication dateAug 5, 1969
Filing dateJul 26, 1967
Priority dateJul 26, 1967
Publication numberUS 3459131 A, US 3459131A, US-A-3459131, US3459131 A, US3459131A
InventorsOaklan R Senf
Original AssigneeContinental Motors Corp
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Hydraulic throttle advance
US 3459131 A
Abstract  available in
Previous page
Next page
Claims  available in
Description  (OCR text may contain errors)

Aus. 5. 1969 o. R. SENF 3,459,131

HYDRAULIC THROITLE ADVANCE Filed July 26, 1967 figg INVENTOR OAKLAN R. SENF ATTORNEYS United States Patent Cftice Patented Aug. 5, 1969 3,459,131 HYDRAULIC THROTTLE ADVANCE Oaklan R. Senf, Muskegon, Mich., assignor to Continental Motors Corporation, Muskegon, Mich., a corporation of Virginia Filed July 26, 1967, Ser. No. 656,096 Int. Cl. F04b 49/04; F04d 15/00; F15b 13/02 U.S. Cl. 103-4-17 8 Claims ABSTRACT OF THE DISCLOSURE A hydraulic actuator using a ow-by principle wherein a plunger member floats in a non-fluid tight bore that communicates with a high pressure source and a separate rod member is spring biased toward the plunger and axially aligned therewith so that increases in pressure will produce regulated movement of the rod.

BACKGROUND OF THE INVENTION Field of the invention v This invention relates to hydraulic throttle advance devices and more particularly to mechanisms for the automatic throttle control for a motor operating a hydraulic pump for actuating various load devices for use on vehicles.

Description of the prior art In the employment of pumps operated by driving means such as a motor vehicle engine, a problem in many applications of such pumps is the maintenance of a pressure which is relatively constant regardless of the demand upon the pump. This problem is particularly acute in the case of trucks and other vehicles which use hydraulic pumps to do various types of work. The operator has loads, traffic, etc., to watch, and automatic throttle control devices are required to enable him to perform his work without having to monitor the engine revolutions per minute, to concern himself with prevention of vehicle stalling and, where torque converters or fluid couplings are used, to eliminate the problem of the vehicle creeping forward. One type of automatic throttle control device is shown in U.S. Patent No. 2,931,305, issued Apr. 5, 1960, which therein discloses a How-through or llow-by arrangement pressure responsive mechanism. Still another type of device is disclosed in U.S. Patent No. 3,232,182 issued Feb. 6 1966 wherein the flow-by concept is not employed and requires internal high pressure sealing means resulting in undesired operating characteristics. The use of high pressure internal sealing means, such as O-rings around the piston, will lead to erratic action of the piston and thus prevent quick response of the pressure compensating means to varying loads. Other disadvantages of the prior art structures such as an excessive number of parts and high manufacturing costs will become apparent in the description of the invention.

SUMMARY OF THE INVENTION According to the present invention, the prior art difficulties are eliminated by means of the improved hydraulic actuator for the throttle of vehicle engines that permits the engine to maintain its revolutions per minute at near idle while varying amounts of loads, up to maximum lifting loads, are imposed upon the engine, Applicant has used the ow-by principle in his device in connection with a unique independent primary plunger and secondary operating rod arrangement which allows the hydraulic fluid to by-pass the plunger so that it is free floating in operation. Another feature of applicants invention is the fact that the plunger will not permit free flow of the hydraulic lluid through the actuator and restricts flow to the passage created by the non-fluid tight fit between the floating plunger and its cooperating bore, and thus prevents a substantial loss of the hydraulic uid through the actuator. Further, the fact that a relatively small amount of fluid bypasses the plunger to the return conduit, means that a substantially constant pressure exists during the operation of the actuator with the result that the pressure acting on the plunger is not affected except by changes in the back pressure on the pump.

An object of the present invention is the provision of a hydraulic actuator which has improved response to varying loads.

Another object of the present invention is to provide a hydraulic actuator that is simple in construction and requires a minimum of parts.

A further object of the invention is the provision of a hydraulic throttle which is adaptable to the requirements of various installations and operations.

Further objects and advantages of the invention will become apparent from the following description of the preferred embodiment thereof, reference being made to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the drawings, there is shown in FIG. 1 a hydraulic circuit in which the actuator means is indicated generally by the numeral 10, located adjacent a carburetor 12, which it will be understood is attached to an internal combustion engine in any one of various types of vehicles such as a fork lift truck, for example. The speed of the engine is controlled by a conventional throttle or butterfly valve operated through a lever 14 which is automatically controlled by the actuator means or pressure responsive mechanism 10 of the present invention. Suitable valve means are provided at 16 for the purpose of operating a hydraulic load device, indicated by the numeral 18. The power for operating the hydraulic' load device is supplied by pump 20. Fluid returning from the load 18 is discharged into a sump or reservoir 22 which is connected to the intake side of the pump 20 to complete the hydraulic circuit. All of the separate elements may be of conventional construction.

The pressure responsive mechanism 10 will now be described in detail. Referring to FIG. 2 the housing 24, which in the instant embodiment is formed from hex bar stock as the housing material, is shown in partial cross section.

Within the housing 24 is a plunger 26 which is freeoating in a closely held bore 28. The bore 28- has aligned counterbores 36 and 32, shown at each end of the housing, which communicate with the bore 28. The smaller bore 30, located at the left end of the housing 24 in FIG. 2,

3 s shown threaded at 34 to receive a conventional hydraulic fitting indicated at 36 in FIG. 1.

The aligned counterbore 32, at the right hand end of the housing 24 in FIG. 2, is of larger diameter than the bore 30, and the bore 32 is in turn counterbored at 38 for the reception of gland member 40, within which a secondary piston rod 42 is positioned for slidable movement. The gland member 40 has O-ring seals 41 and 43 to seal head member 44, fixedly attached to rod 42, within bore 32. Biasing means, such as the helical spring 48, is provided to urge the head 44 and the rod 42 towards the left, as viewed in FIG. 2. The spring 48 is disposed concentrically of head 44 and the stem 50 of gland member 40. The spring 48 is compressed between the head flange 46 and gland member 40 so that under no load conditions the spring 48 retains the head 44 in abutment with base 52 of bore 32. It will be noted that the free end of stem 50 provides a stop portion to limit the free movement of head 44. The length of the gap between the head and stern, indicated by the letter G, can be changed to suit different engine applications.

The housing 24 is connected to the low pressure side, denoted by the reservoir 22 of the fluid system by means of a port 54 extending into the bore 32, provided with a fluid coupling 56 (FIG. 1) for connecting bore 32 to conduit 58 which communicates with the reservoir 22. As indicated above, the high pressure side of the fluid system is connected to the housing 24 through a threaded opening 34 for connecting the bore 30 to line 60 which is in turn, connected to line 62 by T-member 63 such that the discharging pressure of pump 20 is reflected within the chamber 30. While it is noted in FIGS. 1 and 2 that the coupling 56 is shown connected to the top portion of the housing 24 for purposes of description, the preferred arrangement of the actuator housing would be in a position rotated 90 such that the coupling S6 would extend in a horizontal plane. The casing is provided with grooves 64 to enable the devices to be mounted `by bracket members (not shown) to an internal combustion engine.

An inventive feature of applicants device that allows improved operating characteristics in the arrangement of the plunger 26 without sealing means, by means of a nonfluid tight fit in the bore 28, so as to be fioatably slidable therein. Other types of so-called floatable piston arrangements, while eliminating internal sealing means, still require high pressure seals. However, due to applicants novel two-part constructed wherein the plunger 26 is a separate member from the members 42 and 44, allows the plunger 26 to float free of any sealing members. The seal 41, because it is not in hydraulic communication with the high pressure side of bore 30, does not require a heavy seal which would cause sluggish and erratic action of rod 42.

In applicants invention the head 44 acts as an anvil to receive the plunger force created by the axial movement of the plunger 26 under influences of increase in pressure in the bore 30. Another feature of the invention is that of the applicants unique flow-by arrangement of the hydraulic fluid whereby the plunger 26 is able to move into the bore 32 an amount determined by gap distance G and the hydraulic fluid is never permitted to have an uninterrupted passage from bore 30 into bore 32 to communicate with the port 54. The fluid is always required to bypass the plunger 26 which provides, with bore 28, a small tolerance passage so that a controlled amount of fluid will float plunger 26 and enter bore 32 to eliminate pressure buildup in the spring cavity while at the same time preventing excessive loss of the hydraulic fluid.

"It will be appreciated that with a low back pressure o n the pump, the head 44 will be in contact with the abutment surface 52, as shown in FIG. 2. An increase in the fluid pressure in chamber 30 will force lplunger 26 to the right in contact with head 44 to allow the head to overcome the biasing action of spring 48. The hydraulic fiuid located between face 68 of plunger 26 and the face 45 of applications.

head 44 will be forced radially outwardly by the movement of the plunger. The radial flow of the hydraulic fluid between the surfaces 45 and 52 together with the pressure or blow of the plunger against the head 44 will combine to result in prompt opening of the throttle with a relatively low back pressure on the pump.

Applicants two-part construction, wherein the plunger 26 is separate from the rod and head assembly, eliminates alignment problems of a one-piece rod and plunger design. Also by means of replacing the gland member 40, the gap G can be changed to cover different engine applications.

It should be understood of course that the foregoing disclosure relates to only a preferred embodiment of the invention and that numerous modifications or alterations may be made.

What is claimed is:

1. In an automatic control device for controlling the throttle of an engine operating a pump having an inlet side and ana outlet side, said automatic control device comprising a housing having an inner wall defining a first bore at one end to which said pump outlet side is directly connected, a plunger member slidably mounted in said first bore, said housing having a second bore at the other end coaxial with and registering with said first bore, a head member in said second bore axially aligned with said plunger but separate therefrom and serving as anvil means to receive the force of said plunger when said plunger is moved in one direction due to an increase in uid pressure in said first bore, said plunger being movable within said first bore to a position out of engagement with head member, a rod coaxial with said plunger secured to said head member and extending to the exterior of said housing, resilient biasing means between said head member and said housing urging said head member into contact with said plunger, said second bore being connected to the inlet side of said pump, and said plunger member being spaced from the wall defining said first bore to provide a continuous passage connecting said first bore to said second bore wherein both said plunger and said rod are axially movable within said bores in response to pressure changes therebetween without requiring internal sealing means to seal against the high pressure fluid of said pump.

2. The automatic control device as defined in claim 1, wherein said rod is slidably received within a stem portion extending into said second bore such that said stem portions free end provides a stop to limit the axial movement of said head member in said one direction.

3. The automatic control device as defined in claim 1, wherein said second ybore has a diameter at least twice the diameter of said first bore and counter-bored for receiving a gland member for enclosing said second bore of said housing, said gland member slidably receiving said rod and provided with an integral stem portion for guiding the axial travel of said rod.

4. The automatic control device as defined in claim 3, wherein said gland stem and said head member have the same diameter and said biasing means is a coil spring surrounding said head member and stem and retained thereby for urging the head member in the opposite direction from said one direction.

5. The automatic control device as defined in claim 4, wherein said head member is provided with a flange at its plunger engaging end for seating said coil spring.

6. The automatic control device as defined in claim 1, wherein the axial length of said plunger exceeds the axial length of said first bore so that said plunger cannot escape into said second bore and thereby cause excessive loss of the hydraulic fiuid.

7. The automatic control device as defined in claim 4, wherein said head member and said stem are separated by a gap and said gap can be varied for different engine 8. The automatic control device as defined in claim 1,

5 6 wherein low pressure external sealing means are provided 3,116,728 1/ 1964 Evans A 92-129 between said rod and said housing. 3,133,553 5/ 1964 Frantz 91-47 3,232,182 2/ 1966 Gilbert 103-16 References Cited WILLIAM L. FREEH, Primary Examiner UNITED STATES PATENTS 5 Gale U'S. C1. X'R. 211261863 8/1938 BaIOIl 103-16 91 47, 392; 129

2,931,305 4/1960 Stratton 103-16 '22;330 UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,459, 131 Dated August 5L 1969 'Inventor(s) Oklan R. Senf It is certified that error appears in the above-identified patent and that said Letters Patentare hereby corrected as shown below:

IN THE SPECIFICATION Column 3, line 4l, "in" should be line 47, "constructed" should be Column 3,

IN THE CLAIMS -Claim l, line 19, "ana" should be Claim l, line 30, following "with" insert -said.

SIGNED AND SEALED MA1 191970 L' (SEAL) Attest:

Edwatd M. Fletch@ It. WILLIAM E. BGHUYIIER, JR.

Attesting Officer Comiuioner of hun

Patent Citations
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US570727 *Feb 1, 1894Nov 3, 1896 Valve mechanism
US2126863 *Aug 26, 1935Aug 16, 1938American Steam Pump CompanyGovernor for fire-pump apparatus
US2931305 *Apr 25, 1957Apr 5, 1960Stratton Equipment CompanyAutomatic throttle control
US3116728 *Jan 7, 1963Jan 7, 1964Cav LtdLiquid fuel pumps
US3133553 *Mar 26, 1962May 19, 1964Martin Marietta CorpHydromechanical remote indication and memory apparatus
US3232182 *Aug 15, 1963Feb 1, 1966Gilbert John FHydraulic pressure compensating means for internal combustion engine systems
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3797967 *May 10, 1972Mar 19, 1974D HowethHydraulic throttle actuator
US3889828 *May 8, 1974Jun 17, 1975Sargent IndustriesNoise reduction apparatus and method
US3898806 *May 17, 1974Aug 12, 1975Sargent IndustriesNoise reduction apparatus
US3987625 *Aug 15, 1975Oct 26, 1976Fluid Controls, Inc.Combined sensor and control
US4002027 *Jan 28, 1976Jan 11, 1977Tyrone Hydraulics, Inc.Multiple pump control system
US5746179 *Sep 27, 1996May 5, 1998The Nason CompanyThrottle control device
US7234922Mar 24, 2004Jun 26, 2007Clarke Fire Protection Products, Inc.Pump pressure limiting engine speed control and related engine and sprinkler system
US8545188 *Jan 25, 2009Oct 1, 2013Weber Hydraulik GmbhController and the use thereof
US8955607Jun 6, 2012Feb 17, 2015Clarke Fire Prevention Products, Inc.Cooling arrangements for fire suppression sprinkler system fire pumps
US20040247448 *Mar 24, 2004Dec 9, 2004Kunkler Kevin J.Pump pressure limiting engine speed control and related engine and sprinkler system
US20090129935 *Nov 18, 2008May 21, 2009Kunkler Kevin JPump suction pressure limiting speed control and related pump driver and sprinkler system
US20110008187 *Jan 25, 2009Jan 13, 2011Weber Hydraulik GmbhController and the Use Thereof
USRE28717 *Dec 9, 1974Feb 24, 1976Sargent Industries, Inc.Noise reduction apparatus and method
USRE28765 *Dec 9, 1974Apr 13, 1976Sargent Industries, Inc.Noise reduction apparatus and method
EP0445399A1 *Dec 17, 1990Sep 11, 1991Robert Bosch GmbhHydraulic control device for the throttle of the internal combustion engine of a vehicle
EP0482329A1 *Sep 6, 1991Apr 29, 1992Steag AgHydraulic actuator for controlling and regulating valves
U.S. Classification417/34, 91/392, 91/47, 60/431, 92/129
International ClassificationF02D11/06, F02D29/04, G05D13/00, F02D29/00, F15B11/10
Cooperative ClassificationF02D2700/07, F15B11/10, F02D29/00, F02D11/06, F02D29/04, G05D13/00
European ClassificationF02D29/00, F02D29/04, F02D11/06, G05D13/00, F15B11/10