US3842714A - Combine hydraulic valve - Google Patents
Combine hydraulic valve Download PDFInfo
- Publication number
- US3842714A US3842714A US00325957A US32595773A US3842714A US 3842714 A US3842714 A US 3842714A US 00325957 A US00325957 A US 00325957A US 32595773 A US32595773 A US 32595773A US 3842714 A US3842714 A US 3842714A
- Authority
- US
- United States
- Prior art keywords
- valve
- sump
- main passage
- fluid
- passage
- 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 - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
-
- Y—GENERAL 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S60/00—Power plants
- Y10S60/911—Fluid motor system incorporating electrical system
Definitions
- ABSTRACT A control valve consisting of two-way normally closed solenoid poppet valves and two stage normally open solenoid poppet valves.
- the normally closed solenoid valves are arranged to direct flow to and from a cylinder in the desired manner.
- one normally closed solenoid valve is required, whereas, for a double acting cylinder, four normally closed solenoid valves are needed.
- These sets of solenoid valves are incorporated in a single body or manifold to control the different functions on a combine such as reel height, reel speed, auger swing and traction drive.
- the control valve also includes a low flow circuit relief valve set at 2,000 psi and a 600 psi solenoid valve functioning as a relief valve to satisfy maximum pressure conditions for reel speed operation.
- the valve is located near to a supply pump and the pump flow passes through the normally open twoway solenoid valve and back to sump to minimize pressure drop in neutral.
- the electric over hydraulic control system of this invention includes a hydraulic manifold having two pairs of normally closed solenoid valves controlling flow to a double acting hydraulic cylinder without the need of separate check valves.
- Another feature of this invention is a combine control in which a single acting hydraulic cylinder is controlled by a pair of normally closed solenoid valves one of which serves (1) as a relief valve when not energized and (2) as a dumping valve (to achieve a control function) when energized.
- An object of this invention is to provide an improved electrohydraulic control valve for controlling functions performed by single and double acting cylinders in an open center hydraulic system in a combine harvester.
- Another object of this invention is to provide an inexpensive electrohydraulic control valve that will perform the functions of three-way and four-way spool valves with lockout check valves on mobile equipment.
- Another object of this invention is to provide twoway solenoid valves in an open center hydraulic circuit to perform functions previously performed by three and four-way spool valves with lockout check valves.
- Another object of this invention is to provide a hydraulic system wherein solenoid valves provide one or more functions at lower pressure than system pressure.
- a further object of this invention is to provide a hydraulic circuit having a hydraulic cylinder and utilizing solenoid valves and in which each solenoid valve works as a directional control valve to control direction of flow and as a check valve to a) isolate each function from the others in the circuit; and b) hold the hydraulic cylinder in activated position.
- FIG. 1 is a side elevation of a combine harvester embodying the invention
- FIG. 2 is a schematic view of the invention
- FIG. 3 is a section view through the valve body partially shown schematically.
- FIG. 4 is a summary of functions provided by various combinations of the solenoid valves.
- the invention is embodied in a self-propelled combine harvester 10 having a main frame 11 providing an operator station 12, a grain tank 13 provided with a swingable grain unloading auger 14, an internal combustion engine 15, an operators control console 16 and a harvesting and threshing and cleaning mechanism 17 including a reel 18 mounted on the forward end of combine 10.
- the foregoing are supported at the forward end of frame 11 on traction wheels 19 which are operatively connected to engine 15 by conventional means (not shown).
- the rearward end of the combine 10 is supported on dirigible wheels 20 operatively connected to steering wheel 21.
- FIG. 2 Mounted in the operators console 16 is a group of electrical switches 22, 23, 24 and 26 (FIG. 2) which are positioned for easy manipulation by the operator when positioned at station 12 (FIG. 1).
- a valve body or hydraulic manifold 27 is positioned centrally on frame 11 in reasonably close relation to pump 28, sump 29 and the functions of the combine to be hydraulically controlled.
- Pump 28 is operatively connected to engine 15 by conventional means (not shown).
- Valve body 27 (FIG. 3) is provided with a main passage 31 connected at one end to conduit 32 to provide a passage between pump 28 and main passage 31.
- a conventional relief valve 33 is interposed between conduit 32 and conduit 34 leading from sump 29 to pump 28.
- Solenoid valves 36, 37, 38, 39, 41 and 42 are mounted in valve body 27 in communication with main passage 31.
- Solenoid valves 43, 44 and 46 are also mounted in valve body 27 in communication with main passage 31.
- solenoid valve 36 which is a normally closed direct acting'solenoid valve and normally open two stage solenoid valve 39 are arranged as shown in FIG. 3. For the present discussion, consider that only these two valves are installed in the valve body 27 and the other valves are not present in FIG. 3.
- Pump 28 is connected to the valve inlet port 47 of main passage 31.
- the pump flow with none of the switches 22-26 (FIG. 2) actuated is as follows: the flow (FIG. 3) goes through passages 31, 48, 49, 51 and line 52 to the sump 29.
- Plunger 53 in solenoid valve 41 seats tight on the seat 54 and blocks the passage of flow from a motor or cylinder 56 to a motor passage or cavity 57.
- Valve 41 serves as a lock or check valve to hold cylinder pressure constant and also serves as a directional control valve to direct flow from cylinder 56 to cavity 57.
- solenoid valves 39 and I 41 are energized by pushing switch 22 upwardly.
- coil 58 (FIG. 3) of solenoid valve 39 is energized, plunger 59 thereof moves and seats on poppet 61 which in turn moves together with plunger 59 and seats on valve seat 62 blocking flow between passages 48 and 49.
- the flow from pump 28 is now blocked from sump 29 and is available for any of the functions comprehended by the valves in valve body 27.
- the energization of coil 63 of valve 41 causes plunger 53 to move away from seat 54 allowing hydraulic fluid to flow from passage 47 to cavity 57.
- De-energizing coil 63 will remove holding force from plunger 53 and spring 71 will force plunger 53 to position itself on seat 54 blocking passage 67 to passage 57.
- coil 58 of solenoid valve 39 is de-energized, plunger 59 will move away from poppet 61 which moves away from seat 62 allowing the flow from pump 28 to go to sump 29. This puts valve 39 back into neutral position. In this neutral position, reel lift cylinder 56 goes into hold position and the spring 71 holds the plunger 53 on seat 54 of solenoid valve 41 which acts as a lock valve.
- solenoid valve coil 63 of solenoid valve 41 is energized by depressing switch 22 (FIG. 2) resulting in plunger 53 (FIG. 3) being pulled away from seat 54 against spring 71. Plunger 53 moves away from seat 54 allowing hydraulic fluid from cylinder 56 to go to cavity 57. Oil flows from cavity 57 through passages 31, 48, 49 and S1 and line 52 back to sump 29. As soon as coil 63 of solenoid valve 41 is deenergized, spring 71 forces plunger 53 on seat 54 blocking flow from cylinder 56 to cavity 57.
- the steps described above illustrate complete operation of the reel lift section of the valve.
- the valve also has a traction drive section and a reel speed section which are identical to the reel lift operation and a repeat of describing such operation is not deemed necessary excepting that the reel speed function is carried on at 600 psi maximum pressure whereas the other functions, including the reel lift and traction drive, are at 2,000 psi.
- solenoid valves 38 and 46 are arranged as shown in FIG. 3. Operation of this valve section is identical to the operation of the reel lift cylinder section in that when solenoids 38 and 39 are energized to extend the reel speed cylinder 72, hydraulic fluid flows from pump 28 through valve 38, cavity 73 and line 74 to cylinder 72.
- solenoid valve 46 functioning as a relief valve and which regulates the pressure in cavity 73 at 600 psi. However, this does not affect the system pressure which is regulated by a relief valve 33 at 2,000 psi.
- solenoid valve 38 isolates cavity 73 from passage 31. If the pressure in cavity 73 exceeds 600 psi, plunger 75 retracts against spring 76 permitting flow of fluid to sump 29 maintaining pressure of 600 psi in cavity 73.
- the auger swing section has a double acting cylinder 77 and operation of the auger swing is accomplished by solenoid valves 36, 37, 42 and 43.
- solenoid valves 39, 36 and 43 will cause hydraulic fluid to flow through valve 36 to the auger swing cylinder piston end 78. Fluid from rod end 79 of the cylinder 77 will flow through valve 43 back to sump 29 and the cylinder 77 will extend. As soon as solenoid valves 39, 36 and 43 are de-energized, cylinder 77 will go into hold position and be held by solenoid valves, 36, 37, 42, and 43.
- Hydraulic fluid from the base end 78 goes to the sump 29 through solenoid valve 42 and cylinder 77 retracts. Cylinder 77 goes into the previously described hold position as soon as the solenoid valves are de-energized.
- valve body 27 Similar sections as described above, could be added to valve body 27 by inserting'additional sets of valves arranged in the same way as the auger swing section.
- FIG. 3 shows the valve body 27 connected in an open center system.
- Pump 28 supplies hydraulic fluid into valve body 27 at inlet port 47 and such hydraulic fluid flows through passages 31, 48, 49, 51 and line 52 back to sump 29.
- Solenoid valves 41, 36, 37, 42 and 44 act as check valves and they isolate each section from the other. Any of the functions available in the valve housing 27 can be operated as previously described without affecting the rest of the functions.
- solenoid valves 41, 42, 37 and 38 act as lock valves and hold the pressures in the respective cylinders.
- these solenoid valves When these solenoid valves are energized, they act'as directional control valves and direct flow from the pump to the cylinder or vice-versa.
- Solenoid valve 44 forms the traction drive section and this section functions exactly as the reel lift section was described as functioning; namely: to extend traction drive cylinder 81, solenoid valve 44 is energized by raising switch 24 (FIG. 2); When coil 58 (FIG.
- solenoid valve 39 When coil 82 of the solenoid valve 44 is energized, plunger 83 moves away from seat 84 allowing hydraulic fluid to flow from passage 31 through passage 86 to cavity 87. When pressure in cavity 87 exceeds cylinder pressure, such pressure fluid passes through passages 86, 87 and orifice 88 to cylinder 81. Orifice 88 controls the rate at which cylinder 81 extends or retracts. Excess flow, when orifice 88 is controlling the rate at which cylinder 81 extends, goes over relief valve 33.
- De-energizing coil 82 will remove the holding force from plunger 83 against the bias of spring 85 and spring 85 will force the plunger 83 to position on seat 84 blocking the passage from 86 to 87.
- coil 58 of solenoid valve 39 is de-energized, plunger 59 will move away from poppet 61 which moves away from seat 62 allowing pump flow to go to sump 29. This puts the valve back into neutral position.
- traction drive cylinder 81 goes into hold position and is held on poppet seat 84 of solenoid valve 44 which acts as a lock valve.
- solenoid coil 82 is energized which pulls plunger 83 away from seat 84 against spring 85. Plunger 83 moves away from seat 84 allowing hydraulic fluid from cylinder 81 to go to cavity 87. I-Iydraulic fluid flows from cavity 87 through passages 86,
- each of the switches 22, 23, 24 and 26 are shown to be of a double throw type. Each switch is provided with an upper connection 91 and a lower connection 92 leading to electrical power source 93 on combine 10.
- Switch 22 is provided with a lower lead 94 connected to the coil 63 of solenoid 41 so that by depressing switch 22 coil 63 is energized.
- Switches 22, 23, 24 and 26 are also provided with an upper contact 96 which is connected to the coil 58 of solenoid 39.
- Switch 22 is also provided with an upper lead 97 connected to the coil 63 of solenoid 41 so that by moving switch 22 upwardly power is supplied to lines 96 and 97 for energizing solenoids 39 and 41.
- Switch 23 is provided with a lower contact 98 connected to the coil of solenoid 42 and the coil of solenoid 37 and switch 23 is also provided a lower contact 99 connected to contact 96 so that when switch 23 is depressed solenoids 37, 39 and 42 are actuated for connecting the rod end 79 of cylinder 77 with line 31 and a source of hydraulic fluid and the piston end 78 of cylinder 77 is connected up with sump 29, respectively.
- Switch 23 is also provided with an upper contact 101 connected to the coils of solenoid valves 36 and 43 so that when switch 23 is raised valves 36, 39 and 42 are actuated, the rod end 79 of cylinder 77 is connected to sump 29 and the piston end 78 is connected to line 31 for receiving hydraulic fluid from pump 28.
- Switch 24 is provided with lower contact 102 connected to the coil of solenoid valve 44 so that when switch 24 is depressed solenoid 44 is energized connecting cylinder 81 with line 31 for return to sump 29.
- Switch 24 is also provided with an upper contact 103 so that when switch 24 is raised solenoids 39 and 44 are energized and hydraulic fluid flows from pump 28 to cylinder 81 extending same.
- Switch 26 is provided with lower contact 104 connected to the coil of solenoid valve 46 so that when switch 26 is depressed solenoid 46 is actuated to connect cylinder 72 with sump 29.
- Switch 26 is also provided with an upper contact 106 so that when switch 26 is raised solenoids 39 and 38 are energized and hydraulic fluid flows from pump 28 to cylinder 72 extending same.
- the engine on a combine must so run as to maintain constant speed on the threshing and separating mechanisms.
- the ground speed must be variable in minute increments as crop conditions vary. This speed variation is accomplished by a three-speed transmission driven through a variable diameter sheave arrangement.
- the effective diameter of the driven sheave is increased by a single acting hydraulic cylinder 81 and decreased by a spring in a conventional manner (not shown).
- an electrical signal is sent from operators station 12 to solenoid members 39 and 44 by raising switch 24.
- solenoid member 39 closes it causes the normally open poppet 61 to close blocking the flow through valve 39. When this happens pressure builds up in the valve to approximately 2000 psi when relief valve 33 upstream relieves.
- solenoid 44 Because solenoid 44 is also energized, it opens allowing hydraulic fluid to flow through orifice 88 to the traction drive cylinder 81. When the electrical signal from switch 24 is taken away, solenoid 44 closes trapping the hydraulic fluid in the traction drive cylinder 81 and maintaining that position of the variable diameter sheave arrangement and consequently, the speed of the vehicle. With no electrical signal, solenoid member 39 reopens and the hydraulic fluid is again free to circulate past solenoid 39 and deposit in sump 29.
- solenoid 44 To slow down the traction speed, an electrical signal is sent to solenoid 44 by depressing switch 24 at the operators station 12, this causes an opening of solenoid valve 44 and allowing the spring load to force the hydraulic fluid out of cylinder 81 through valve 44 and through valve 39 where it moves to sump 29.
- the reel height on the combine is maintained by a master-slave arrangement with only the master cylinder 56 being shown (FIG. 2).
- solenoid members 39 and 41 are energized by pressing up on switch 22. This allows hydraulic fluid exerting a 2000 psi pressure to move past solenoid 41 to the reel lift cylinder 56.
- the reel 18 (P10. 1) is held in its desired position by solenoid 41 reclosing when the electrical signal is removed.
- solenoid 41 When it is desired to lower reel 18 an electrical signal is transmitted to solenoid 41 by depressing switch 22 at the operators station. This results in the opening of solenoid 41 and permitting hydraulic fluid in ram 56 to exit through solenoid 41 into line 31 and through solenoid 39 to sump 29.
- the unloading auger 14 is moved into operative bin unloading position by a double acting cylinder 77.
- switch 23 is actuated upwardly at the operators station 12. This energizes solenoids 36, 39 and 43.
- the closing of solenoid 39 causes a pressure build-up in line 31 which causes hydraulic fluid to move through now open solenoid 36 to extend hydraulic cylinder 77. Hydraulic fluid from rod end 79 of cylinder 77 passes through now open solenoid valve 43 to be deposited in sump 29.
- solenoid 39 moves to an open position connecting line 31 with sump 29 and causes solenoids 36 and 43 to move to closed positions trapping the hydraulic fluid in both ends of cylinder 77.
- switch 23 is depressed actuating solenoids 37, 39 and 42.
- the closing of solenoid 39 causes a pressure build-up in line 31 which causes hydraulic fluid to move through now open solenoid 37 to retract hydraulic cylinder 77. Hydraulic fluid from piston end 78 of cylinder 77 passes through now open solenoid valve 42 to be deposited in sump 29.
- auger 14 has been swung to its transport position, it can be maintained in this position by interrupting the electrical signal from switch 23.
- Such interruption causes solenoid 39 to move to an open position connecting line 31 with sump 29 and causes solenoids 37 and 42 to move to closed positions trapping the hydraulic fluid in both ends of cylinder 77.
- the speed of reel 18 is controlled by a conventional variable diameter sheave drive (not shown) which by its design is limited to 600 psi. This drive provides very little return force.
- a solenoid 46 which acts as a relief valve and unloading device.
- the poppet load orifice size relationship is such that the poppet will unseat and act as a direct acting relief valve at 600 psi.
- solenoids 38 and 39 are energized by pressing up on switch 26.
- the closing of solenoid 39 results in a build-up of pressure in line 31 which pressurefluid pressurizes reel speed cylinder 72. This pressure is relieved to 600 psi by solenoid 46.
- solenoids 39 and 46 are energized. Solenoid 39 closes stopping the flow of hydraulic fluid to sump 29.
- the magnetic load at solenoid 46 unseats the 600 psi relief and allows the reel speed return hydraulic fluid to flow through an empty line 107 to sump 29. This allows the system to operate at 600 psi with very low return pressures.
- the closing of solenoid valve 39 prevents dumping of fluid from the main passage 31 to sump by way of the common sump return passage, shown schematically in FIG. 2, thus allowing a low fluid return pressure for reel speed motor 72; however, it is of course possible to exhaust fluid from motor 72 by opening solenoid valve 46 without closing valve 39.
- a hydraulic manifold having a main passage connected in fluid receiving relation to said pump and in fluiddelivery relation to said sump and having a pair of supply passages operatively connecting opposite ends of said cylinder to said main passage, said manifold being positioned in remote relation to said console and proximate to said pump and sump to provide a minimum'passage of hydraulic fluid between said pump and sump when said hydraulic cylinder is not being operated,
- a normally open solenoid valve mounted on said manifold and connected to said main passage, said normally open solenoid valve having an open position permitting hydraulic fluid to pass from said main passage to said sump and a closed position blocking fluid from flowing from said main passage to said sump,
- a second pair of normally closed solenoid valves connected respectively to said supply passages and operable to control flow of fluid therefrom to said sump, said second pair of normally closed solenoid valves when opened being operative to pass fluid from said cylinder to said sump without it passing through said main passage, and
- a hydraulic manifold having a main passage connected in fluid receiving relation to said pump and in fluid delivery relation to said sump and a motor passage connected at one endto said main passage and having its other end connected to said motor,
- a normally open solenoid valve mounted on said manifold connected in controlling relation to said main passage, said normally open solenoid valve having an open position permitting hydraulic fluid to pass from said pump to said sump by way of said main passage and a closed position blocking fluid from flowing from said pump to said sump by way of said main passage,
- a first normally closed solenoid valve mounted on said manifold and connected in controlling relation to said motor passage, said first normally closed solenoid valve functioning when not energized as a check valve preventing return flow from said motor through said motor passage and opening when energized to permit fluid flow in said motor passage between said main passage and said motor,
- first relief valve operatively connected to the output side of said pump to establish a relatively high operating pressure for said main passage of said manifold when said normally open solenoid valve is closed
- second normally closed solenoid valve interconnected between said motor passage and said sump and including a spring biased valve plunger operating as a second relief valve when said second valve is not energized, said second valve establishing a lower operating pressure for said motor passage than that established for said main passage by said first relief valve
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims (2)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US00325957A US3842714A (en) | 1973-01-22 | 1973-01-22 | Combine hydraulic valve |
CA182,465A CA994207A (en) | 1973-01-22 | 1973-10-02 | Combine hydraulic valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US00325957A US3842714A (en) | 1973-01-22 | 1973-01-22 | Combine hydraulic valve |
Publications (1)
Publication Number | Publication Date |
---|---|
US3842714A true US3842714A (en) | 1974-10-22 |
Family
ID=23270169
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US00325957A Expired - Lifetime US3842714A (en) | 1973-01-22 | 1973-01-22 | Combine hydraulic valve |
Country Status (2)
Country | Link |
---|---|
US (1) | US3842714A (en) |
CA (1) | CA994207A (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4149565A (en) * | 1977-02-02 | 1979-04-17 | International Harvester Company | Pilot controlled poppet valve assembly |
FR2409432A1 (en) * | 1977-11-16 | 1979-06-15 | Sanyo Kiki Kk | Hydraulic control system for hydraulic actuators - has solenoid-controlled valve groups joined to multiple control systems |
US4166506A (en) * | 1975-06-30 | 1979-09-04 | Kabushiki Kaisha Komatsu Seisakusho | Controlling apparatus for bulldozer blade |
US20030143085A1 (en) * | 1999-07-30 | 2003-07-31 | Fletcher Peter C. | Hydraulic pump manifold |
US7191889B1 (en) | 2004-12-14 | 2007-03-20 | Heley Kenneth J | Remote controlled swing auger system |
US20100293914A1 (en) * | 2009-05-20 | 2010-11-25 | Dale H Killen | A harvesting head reel support arrangemnt including hydraulic cylinders and control circuitry |
US10781864B2 (en) | 2018-11-16 | 2020-09-22 | Glg Farms Llc | Drive wheel clutch system |
-
1973
- 1973-01-22 US US00325957A patent/US3842714A/en not_active Expired - Lifetime
- 1973-10-02 CA CA182,465A patent/CA994207A/en not_active Expired
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4166506A (en) * | 1975-06-30 | 1979-09-04 | Kabushiki Kaisha Komatsu Seisakusho | Controlling apparatus for bulldozer blade |
US4149565A (en) * | 1977-02-02 | 1979-04-17 | International Harvester Company | Pilot controlled poppet valve assembly |
FR2409432A1 (en) * | 1977-11-16 | 1979-06-15 | Sanyo Kiki Kk | Hydraulic control system for hydraulic actuators - has solenoid-controlled valve groups joined to multiple control systems |
US20030143085A1 (en) * | 1999-07-30 | 2003-07-31 | Fletcher Peter C. | Hydraulic pump manifold |
US6729854B2 (en) * | 1999-07-30 | 2004-05-04 | Crs Services, Inc. | Hydraulic pump manifold |
US7191889B1 (en) | 2004-12-14 | 2007-03-20 | Heley Kenneth J | Remote controlled swing auger system |
US20100293914A1 (en) * | 2009-05-20 | 2010-11-25 | Dale H Killen | A harvesting head reel support arrangemnt including hydraulic cylinders and control circuitry |
US7866132B2 (en) * | 2009-05-20 | 2011-01-11 | Deere & Company | Harvesting head reel support arrangement including hydraulic cylinders and control circuitry |
US10781864B2 (en) | 2018-11-16 | 2020-09-22 | Glg Farms Llc | Drive wheel clutch system |
Also Published As
Publication number | Publication date |
---|---|
CA994207A (en) | 1976-08-03 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: CONNECTICUT NATIONAL BANK THE, A NATIONAL BANKING Free format text: SECURITY INTEREST;ASSIGNOR:ALLIS-CHALMERS CORPORATION A DE CORP.;REEL/FRAME:004149/0001 Effective date: 19830329 Owner name: WOODS KATHLEEN D., AS TRUSTEE Free format text: SECURITY INTEREST;ASSIGNOR:ALLIS-CHALMERS CORPORATION A DE CORP.;REEL/FRAME:004149/0001 Effective date: 19830329 |
|
AS | Assignment |
Owner name: DEUTZ-ALLIS CORPORATION BOX 933, MILWAUKEE, WI 53 Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:ALLIS-CHALMER CORPORATION A DE CORP;REEL/FRAME:004434/0722 Effective date: 19850627 |
|
AS | Assignment |
Owner name: WHIRLPOOL FINANCIAL CORPORATION, A DE CORP., MICHI Free format text: SECURITY INTEREST;ASSIGNOR:DEUTZ-ALLIS CORPORATION;REEL/FRAME:005356/0744 Effective date: 19900621 |