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Publication numberUS3596565 A
Publication typeGrant
Publication dateAug 3, 1971
Filing dateJul 25, 1969
Priority dateJul 25, 1969
Publication numberUS 3596565 A, US 3596565A, US-A-3596565, US3596565 A, US3596565A
InventorsDuane Edward Atkinson
Original AssigneeDuane Edward Atkinson
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Remotely controlled hydraulic system
US 3596565 A
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Description  (OCR text may contain errors)

United States Patent [72] Inventor Duane Edward Atkinson [56] References Cited 136 Newton Drive, Burlingame, Calif. UNTED STATES PATENTS 94010 2,343,912 3/1944 Lauck 60/97 E X 2Y5; fi'fi 2,361,460 10/1944 Daugherty 60/53 x [45] Pat ted 3 l97l 2,613,703 10/1952 Calvert 60/52 X 2,665,122 1/1954 Rowland 60/53 ux 3,173,381 3/1965 Charles et a1. 298/35 M X 3,427,075 2/1969 Kress et a1. 105/240 X [54] REMOTELY CONTROLLED HYDRAULIC SYSTEM 4 Claims 7 Drawing Figs. Primary Exammer- Edgar W. Geoghegan Au0meyFlehr, Hohbach, Test, Albritton & Herbert [52] US. Cl 91/411 R, 105/240, 105131] R, 298/35 M, 91/2 [51] Int. Cl FlSb 11/16 ABSTRACT: Heavy duty equipment such as construction [50] Field 01 Search 91/41 1, equipment with adjustably positioned, remotely controlled,

361, 2; 105/240, 311, 31 1 C; 298/35 M hydraulically actuated movable members.

TO OTHE R DOOR SYS.

( OPEN) 43 49 I2 1 52 34 I 7| CLOSE) 53M l OP EN 58 72 11x54 22 PARTIAL) 2 55 c CLOSE) I PATENIEU Am; 3191;

SHEET 1 OF 3 DUANE E. ATKINSON INVENTOR,

BY 4M; 222

ATTORNEYS PAIENIl-imuc 3m SHEET 3 BF 3 DUANE E. ATKINSON INVENTOR.

ATTORNEYS REMOTELY CONTROLLED HYDRAULIC SYSTEM BACKGROUND OF THE INVENTION This invention relates generally to heavy duty, remotely controlled, hydraulically operated equipment, and more particularly to equipment for the heavy construction industry.

In the construction industry, materials such as sand, dirt, rock, gravel and the like are often transported by earth moving equipment to be used as fill. One type of such equipment includes a tractor-trailer combination. The trailer comprises a large top-loading bin having sloping sides and ends which converge at discharge openings at the bottom. One or more pairs of doors or closures are adapted to selectively open and close the discharge opening.

Successful use of large size trailers in heavy construction service requires features in the door operating system that may or may not be required in other services. Unlike mining or other fixed haul operations, embankment dam construction involves hauling different kinds of materials from different locations on a balanced basis to allow the various zones of the dam to be raised in an integrated fashion. Furthermore, the hauling unit or trailer must provide the preliminary distribution of the material on the dam rather than simply dumping a full load at a fixed terminal point.

The optimum size of the dumped windrow is dependent upon the type and condition of the material being dumped, the width of the zone being raised, the lift height allowable at that point, and proper integration with the final spreading and compacting equipment in use. If the windrow is large, then it becomes difficult to handle with equipment of normal size. For these reasons, it is important that trailers have an adjustable door opening for dumping that is intermediate between full-closed and full-open, thus allowing control of the size of the dumped windrow. After the dumping is completed, the doors are preferably opened fully to completely clear the trailer, particularly when hauling wet or sticky materials.

Absent any drift, the intermediate door opening position can be left unchanged for the duration of agiven haul operation. At other times, however, changing dumping zones, changing pits, changes in material, moisture content, etc., may require frequent adjustment of the intermediate door opening setting or position.

One type of trailer includes two completely independent door systems which first allow dumping the rear half of the trailer, thereby maintaining weight on the tractor driving wheels, and then dumping the front half of the trailer to complete the operation. Each pair of doors operates independently of the other and has three control positions; full-closed, an adjustable intermediate position, and full-open. The three opening settings for each of the two door systems are controlled by the operator as he drives across the fill and the dumping zone.

One type of system for setting the intermediate opening includes a cam which moves with the door to operate a cam valve when the door reaches a predetermined intermediate opening position. The actuation of the cam valves causes interruption of the hydraulic flow to the associated door operating ram thereby holding the door at this position. This type of direct control subjects the sensing elements to the rugged environment prevailing at the doors. Changes in the door opening setting require access to the door region and sensing element which may not be easily accessible.

The setting or adjustment of the adjustable position of the controlled member should not require special tools and should be simple and convenient whereby adjustment can be expeditiously accomplished in the field. The control system components should preferably be rugged for use in the construction environment or located in a position in which they are protected from the environment.

Remote control of other hydraulically actuated heavy-duty equipment is also important for example, the positioning of cutting blades in scrapers and levelers; positioning of concrete mixing and handling equipment, loaders and the like used in the construction industry.

SUMMARY OF THE INVENTION AND OBJECTS There is provided hydraulically controlled equipment of the type which includes a hydraulically actuated movable means such as doors or blades. Control means are located at the operator location for permitting the operator to control the position of the movable member, for example, doors between two extreme positions and an adjustable intermediate position. Said hydraulic system includes a fluid metering device connected in the fluid line between the hydraulic supply means and the hydraulic motive means, such as motor or rams, which activiate the members to meter the fluid supplied to the motive means, and means responsive to said metering device for interrupting the flow of hydraulic fluid to said motive means to stop the member or doors at an adjustable intermediate position when a predetermined amount of hydraulic fluid has been supplied. The system also includes means for automatically compensating for drift.

It is a general object of the present invention to provide an improved hydraulic system for controlling a hydraulically operated member.

It is another object of the present invention to provide a door opening system for earth moving equipment in which the intermediate door opening position may be simply, quickly and readily adjustable by unskilled field personnel or by the operator without special tools and without taking the truck out of a haul system longer than is absolutely necessary.

It is a further object of the present invention to provide a hydraulic system for operating movable members which is extremely reliable and trouble free.

It is still a further object of the present invention to provide a hydraulic system in which the control sensing means are remotely located in a protected portion of the material carrier.

It is another object of the present invention to provide a system in which the controls for the operators are simple to operate.

The foregoing and other objects of the invention will become more clearly apparent when taken in conjunction with the following description and drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevational view of a tractor trailer incorporating the present invention.

FIG. 2 is an enlarged view of the doors associated with the trailer of FIG. 1.

FIG. 3 is a sectional view taken along the line 3-3 of FIG. 1 and showing the doors in the closed position.

FIG. 4 shows the doors in FIG. 3 in their fully open position.

FIG. 5 is a schematic diagram of an electrical control system for controlling the hydraulic door rams for operating the doors.

FIG. 6 is a schematic diagram of another electrical control system incorporating the present invention.

FIG. 7 is a schematic diagram of a hydraulic control system for controlling operation of hydraulically operated members.

DESCRIPTION OF THE PREFERRED EMBODIMENT The invention is described with reference to typical earth moving equipment. It will, however, be apparent that the invention is equally as useful in connection with the control of other hydraulically driven members. Referring to Figure l, the equipment comprises a tractor 11 adapted to tow a trailer 12 which is filled with construction material 13. The trailer is suitably attached to the tractor by means of a gooseneck attachment 14. The trailer illustrated includes discharge openings 16 each having a pair of discharge doors 17a, 17b. The discharge doors are mounted on spaced pins 18 disposed on opposite ends of the opening 16. The pins are engaged by door brackets 19. Hydraulic rams 21, 22 located on opposite sides of the trailer engage the corresponding door. The rams are adapted to pivot the doors around the pivot point pins 18 and open the doors upwardly as shown in Figure 4. It will be apparent that hydraulic motors or operators may be substituted for the rams.

In accordance with the preferred embodiment of the present invention, the hydraulic fluid supplied to the hydraulic rams is controlled by an electrical control system of the type shown in Figure 5. Referring to Figure 5, the hydraulic system includes a hydraulic pump 31 which, in the present example, is located on the tractor and provides hydraulic fluid under pressure from the reservoir 12 to the hydraulic rams 21, 22 disposed on opposite sides of the trailer. The hydraulic fluid from the pump passes through a pressure relief valve 32 which is adapted to continuously supply hydraulic fluid to the hydraulic line 33 at predetermined pressure. However, when the piston 34 associated with each ram reaches its limiting position and no further fluid can flow, the bypass valve 32 bypasses the fluid to the line 36 back to the reservoir 32. The pressure relief valve thereby controls and maintains constant pressure on the line 33. A return line 37 serves to return fluid from the hydraulic pistons to the reservoir 12.

A solenoid valve 38 is connected in the fluid supply and return lines 33 and 37 and serves to selectively connect these lines to the hydraulic lines 41, 42 which supply fluid to opposite sides of the pistons 34. The four-way valve includes actuating solenoids 43 and 44. When the solenoid 43 is actuated, it serves to connect the supply and return lines 33, 37 to the lines 42, 41, respectively, as shown by arrows, to move the pistons in the direction indicated by the arrows 47 which is the direction for opening the doors connected to the pistons. When the valve is not energized, lines 33, 37 and 41,42 are blocked as indicated at 48 whereby no fluid flows to or from the hydraulic pistons. The pistons are thereby maintained in a fixed position. When the solenoid 44 is energized, the lines 33, 37 are connected to lines 41, 42, respectively, and the pistons are moved in the direction shown by the arrows 49 which is the closing direction for the doors connected to pistons 34. As previously described, when the pistons achieve either of the two extreme positions, the pistons are maintained under the predetermined pressure supplied to line 33 thereby keeping the doors in the fully open or fully closed position with predetermined force.

Hydraulic motors 51 and 52 are connected in parallel in the line 42. The output shaft of each hydraulic motor will rotate in proportion to the amount of fluid being supplied to the respective piston and will, therefore, inferentially indicate the position of the piston. If the output shafts of the two motors are mechanically coupled, the motors form a flow divider that synchronizes the operation of the two rams. The two metering motors 51, 52 can be replaced by a single duplex pump motor that combines both these units in a single casing. Units of this type are readily available and widely used as flow dividers.

If the door or member associated with one ram tends to bind or otherwise operate slowly, the fluid divider will automatically increase the pressure on that ram and reduce the pressure on the other. In the extreme case, the slow ram will see twice the system pressure while the fast ram will see zero pressure. This provides a very effective synchronizing means between the two rams and allows use of a single feedback mechanism for the entire door system thereby reducing the control system complexity and cost.

The coupled shafts 53 of the metering motors 51 and 52 are connected to a gear reducer 54. A gear reducer is preferably used since a practical and economical size of motor 51, 52 will make a number of revolutions in delivering enough fluid to the ram to fully open and close the doors. The small gear box is inserted to thereby give an appropriate ratio whereby the output shaft 55 will undergo approximately one revolution between fully open and fully closed positions of the doors. As the metering motor turns, it will drive the movable electrical tap 56 along the resistor 57 to vary the electrical resistance 57a, 57b between the tap and the lines 58, 59, respectively. A slip clutch 60 is inserted in the output shaft 55 and stops 6!, 62 limit rotation of the shaft by abutting the member 63 mounted for rotation with the shaft. Preferably, the gear reducer is chosen to give slightly more than one full revolution of the output shaft as the door goes from fully closed to fully open.

The fixed stops 6!, 62 are positioned so as to allow the shaft 55a to make slightly less than one full revolution. in this way, any tendency for the system to drift because of fluidleakage is automatically corrected. For example, if the metering motor has lagged in rotation in the opening" direction, the output shaft will lag in its position correspondingly. However, when the door closes, the output shaft will attempt to turn back beyondits fixed stop, i.e., past zero, because of the lag. When the output shaft 55a reaches its fixed stop, the slip clutch will operate allowing the metering motor to continue to turn until the door finally reaches its fully closed position. The output shaft and door are thereby resynchronized and the drift error cancelled. Drift errors in the opposite direction are cancelled by the equivalent action when the door reaches its fully open position.

Correcting system drift errors by use of a slip clutch has the effect of reducing the range of possible intermediate door opening settings from 0- percent to about 5-95 percent. However, this is no practical disadvantage in the heavy equipment industry. Actually, system drift will be quite small in the usual case since the metering motors ordinarily will have essentially zero pressure drop across them with a corresponding reduction in slippage. Furthermore, since the system corrects itself in each full cycle of operation, very serious ram blowby, system leakage, etc., would have to occur before serious positioning errors would occur. Normal system repair and maintenance would preclude this degree of hydraulic system degradation.

Another advantage of employing a slip clutch is to provide a predetermined torque limit between the metering motor shaft and the sensing means employed, thus allowing use of relatively small and simple control devices such as the potentiometer described.

Referring again to the drawing, the resistor 57 forms two legs 57a, 57 b of a bridge circuit. A potentiometer 66 including tap 67 defining resistor portions 66a and 66b between the tap 67 and lines 58 and 59 respectively forms another two legs of a bridge. A coil 68 is connected between the bridge terminals defined by taps 56 and 67. One bridge terminal 59 is grounded and voltage +V is applied to the other bridge terminal. The coil 68 operates contactor 69 of a polarized relay. The contactor connects the voltage +V to one or the other of the contacts 71, 72, when the bridge is unbalanced. When the bridge is balanced, contactor 69 remains in a center or neutral position and neither contact 71 or 72 is energized.

With the control switch in the operators location set to connect the voltage +V to the line 58, the contactor 69 will contact either contactor 71 or 72 to energize the corresponding solenoid 43 or 44 to operate the solenoid valve to supply fluid to the hydraulic pistons until tap 56 is moved to bring the bridge into balance. The position is controlled by moving tap 67, and the door can be made to follow by moving the tap 67. Thus, by providing a setting potentiometer in the operator's cab, he can continuously adjust the intermediate door openmg.

ln order to close the doors, the operator connects the voltage supply +V to line '76 energizing solenoid 74, causing the pistons to move in the direction indicated by arrows 49. The doors are maintained closed by the hydraulic pressure supplied to the pistons via line 33. When the dumping area is reached, the operator connects the voltage supply to line 58 and the doors open to the position determined by setting of the tap 67. It is noted that the operator can at this time control or move the doors by moving the tap 67. When the load is discharged, the operator may switch back to the closed position connecting the voltage supply to line 76 or to the open position connecting the voltage to line 77 and energizing solenoid 43 and causing the pistons to move in the direction indicated by the arrows 47. This assures complete discharge of the material. Thereafter, the operator switches to the close position. The above sequence of operation from fully closed, to intermediate, to fully open and back to fully closed is the preferred operation since it will correct for drift errors in either direction.

It is to be observed that the electrical control system and metering motors can be located remote from the doors where they will not be subjected to the rugged environment. The controls may be as simple as a three-position switch and a potentiometer. Lamps may be incorporated in the lines to give the operator a visual indication of the cycle and the potentiometer can be calibrated to indicate the intermediate door opening.

A full servosystem has been described; that is, a system in which the operator can move the door in either direction when the switch is in the intermediate position. By eliminating the contact 72, the operator can only control the position to which the door opens.

Referring to Figure 6, there is shown a control system which employs a switch 84 for controlling the valve 38 to stop the doors at the intermediate point. ln Figure 6, the same reference numerals are applied to parts which correspond to those in Figure 5. The sensor assembly shown in the dotted block 81 differs from the sensor assembly previously described in that it includes a cam 82 mounted on the shaft 55a. The cam 82 is adapted to move the button or plunger 83 which opens the normally closed switch 84. When the operators switch is set to apply voltage to the line 58, fluid will be applied to the door rams 21, 22 to open the doors. When the cam 82 strikes the button 84, the switch is opened to thereby deenergize the valve solenoid. The valve returns to its neutral position wherein the rams are held in the intermediate position.

As before, operation of the switch by the operator to connect the voltage +V to line 59 will actuate the rams to close the doors. Adjustment of the intermediate position is affected by properly setting the cam 82 relative to the position at the stop 63 on the shaft 55a, or by moving the position of the stops 61, 62. The control system in Figure 6 requires a mechanical adjustment. However, the assembly is removed from the door position and can be located in an easily accessible portion of the equipment. Thus, adjustment can be easily accomplished. The system again includes means with stops 61, 62 for com pensating for leakage or drift.

A control system which is entirely hydraulic is shown in Figure 7. A hydraulic motor is shown in place of a ram. A hydraulic pump 31a supplies hydraulic fluid under pressure to the bypass valve 32a and thence to the lines 33a and 37a. A valve 86 is connected in the lines 33a and 37a. The valve is under the control of the operator to be positioned in one of three positions. Three output lines are associated with the valves. The line 87 provides fluid under pressure to the motor 88 to cause rotation of shaft 89 to fully close the associated door and maintain the same under pressure. The line 91 is adapted to provide hydraulic fluid under pressure to the motor to rotate the shaft 89 to fully open the associated door. The fluid line 92 is connected to a metering motor 93 and thence through a two-way valve 94 to join with line 91 and apply fluid under pressure to drive the motor and rotate the shaft in an opening direction to an intermediate position. A gear reduction box 96 is connected to the motor shaft and thence to a slip clutch 97. A cam 98 is mounted on the output shaft 99 of the slip clutch and is adapted to activate the two-way valve 94 by depressing the plunger 101. A stop assembly including stops 102, 103 and member 104 aflixed to the shaft serves to stop the rotation of the shaft 99.

In operation, to open the door from the closed position to the intermediate position, the valve 86 is adjusted whereby the connections between the lines 33a, 37a and 87, 91 and 92 are as indicated at 106 wherein the pressure line 33a is connected to the metering motor line 92 through the valve 94 to the motor 88. When the cam 98 has rotated to depress the plunger 101, the valve 94 closes and motor rotation is stopped at the intermediate position which is preset by adjustment of the cam 98.

To drive the motor to its extreme position, the valve 86 is adjusted to the position 108 wherein the line 33a is connected to the line 91 and the line 37a to the line 87.

Thereafter, to drive the motor to its other extreme position, the three-way valve 86 is moved to the position indicated at 109 whereby pressure is applied to the motor along line 87 to rotate it in the opposite direction. The lines 91, 92 are connected to the return line 37a.

The control valve in the embodiment shown can be located at the operator position. On the other hand, the complete hydraulic system may operate through pilot lines which control hydraulic actuators on the valve 86.

There has been provided a control system to remotely control hydraulically actuated movable members. The control can be located at a protected position. The system includes means whereby drift is automatically compensated by operation of the control member between two extreme positions. The control system is simple in design and relatively easy to adjust to provide selected intermediate positions for the movable, hydraulically operated controlled members. The connections between the operator location and the operating mechanism for the controlled member can be electrical or hydraulic.

lt is apparent that the invention is not to be limited to a tractor-trailer combination but rather that it is applicable to equipment which is remotely controlled to control hydraulically actuated movable members to be selectively positioned.

1 claim:

1. A control system for use in equipment of the type which includes hydraulic fluid supply means, a movable member, hydraulically driven motive means connected to drive said movable member and hydraulic lines connected between said supply means and said motive means comprising fluid metering means including a hydraulic motor having an output shaft which rotates responsive to the flow of fluid through said motor for metering the fluid supplied to said motive means, interrupting means including a control valve for controlling the flow of fluid to said motive means and means responsive to predetermined rotation of said shaft for controlling said valve means to interrupt the flow of fluid to said motive means to stop said movable member at a predetermined position.

2. A control system as in claim 1 in which said control valve comprises a solenoid valve and said means responsive to predetermined rotation of said shaft comprises electric circuit means.

3. A control system as in claim 2 in which said electrical means includes a switch, and said shaft carries a cam adapted to operate said switch.

4. A control system as in claim 3 wherein said electrical means comprises a potentiometer adapted to be driven from said shaft and a bridge circuit associated with said potentiometer.

5. A control system as in claim 1 wherein said means for interrupting the flow of fluid to said motive means comprises a hydraulically actuated valve means, and means are associated with said shaft for controlling the flow of hydraulic fluid to said valve means.

6. A control system for use in equipment of the type which includes hydraulic fluid supply means, a movable member adapted to be moved between first, second and adjustable and intermediate positions, a hydraulically driven motive means connected to drive said movable member between said first and second positions and hydraulic lines connected between said supply means and said motive means adapted to supply hydraulic fluid to said motive means to move the same from said first to said second position and back including a fluid metering means in the hydraulic lines for metering fluid supplied to said motive means and providing a measure thereof, a control valve disposed in said fluid hydrauliclines to control the flow of fluid to said motive means, means responsive to a predetermined measure of fluid for controlling said valve to interrupt the flow of fluid to said motive means to stop said movable member at said intermediate position, and means for thereafter controlling said valve to selectively apply fluid to said motive means to selectively move theImovable member to the first or second position i i Y 7. A control system as in claim 6 wherein said fluid metering means includes a movable member and wherein said means responsive, to a predetermined measure of fluid comprises means responsive to movement of said movable member.

8. A control system as in claim 7 wherein said fluid metering means comprises a hydraulic motor with a rotatable shaft and said means responsive to movement is responsive to rotation of said shaft.

9. A control system as in claim 8 in which said control valve comprises a solenoid valve and said means responsive to predetermined rotation of said shaft comprises electric circuit means.

10. A control system as in claim 9 in which said electrical means includes a switch, and said shaft carries a cam adapted to operate said switch.

- 11. A control system as in claim 10 wherein said electrical means comprises a potentiometer adapted to be driven from said shaft and a bridge circuit associated with said potentiometer.

12. A control system as in claim 8 wherein said means for interrupting the flow of fluid to said motive means comprises a hydraulically actuated valve means, and means are associated with said shaft for controlling the flow of hydraulic fluid to said valve means.

13. A control system as in claim 8 in which said shaft includes first and second portions with slip means disposed between said first and second portions whereby the second portion can stop while the first portion continues to rotate, and'stop means for interrupting rotation of said second portion prior to said movable member reaching its first and second positions.

14. A control system as in claim 13 including a gear reduction means associated in said first shaft portion whereby said second-portion rotates one revolution responsive to movement of said movable member between the first and second positions.

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Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3828948 *Jan 3, 1972Aug 13, 1974Pullman IncPneumatic hopper car door actuating system
US4153168 *Sep 29, 1977May 8, 1979Reustle Walter CAutomatic hopper door opener
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US5657700 *Dec 14, 1995Aug 19, 1997Herzog Contracting CorporationRailroad hopper car with ballast distributing blades and remote control system
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Classifications
U.S. Classification91/392, 91/459, 91/2, 91/512, 105/311.1, 298/35.00M, 105/240
International ClassificationF15B11/16, B60P1/56, F15B21/08
Cooperative ClassificationF15B11/16, B60P1/56, F15B2211/3111, F15B2211/327, F15B2211/7128, F15B2211/40515, F15B2211/3122, F15B2211/411, F15B2211/41527, F15B2211/45, F15B2211/423, F15B2211/6326, F15B2211/41509, F15B21/08
European ClassificationF15B21/08, B60P1/56, F15B11/16