tractor front end loader hydraulic pump free sample

This monoblock valve functions as a hydraulic directional control valve. These valves start and stop fluid flow into hydraulic cylinders or hydraulic motors.

Is the flow through this valve less than 21 GPM? If installing on a tractor, please check tractor-data.com, it will say under the hydraulics – “Pump Flow” – of the data sheet. The GPM flow may be printed on the pump itself.

Do you have an open-center hydraulic system? If you’re installing this on a tractor, please check tractor-data.com. The website will say under the hydraulics of the data sheet if it is. These valves are setup for use on open-center hydraulic systems. If you do have a closed-center system, you’ll need to get the NOTE: None of our valves have load-sensing capabilities.

Do you have other valves downstream from this valve (Examples include: Other Control Valves, Rear Remote Valve, Backhoe Valve, 3-Point Valve)? If so, you’ll need the Note: This is only needed on open-center hydraulic systems. If you have a closed-center system, you will tee into a pressure line to connect other valves.

Are you operating a hydraulic cylinder or a hydraulic motor?If you’re operating a hydraulic cylinder, you’ll need to get “A” spools for double acting cylinders. For operations with a hydraulic motor, you’ll need “D” spools for motor control. Note: “D” spools cannot be used for operating hydraulic cylinders and “A” spools cannot be used to operate hydraulic motors.

This valve uses a pressure line (Inlet), tank line (outlet), work ports (A/B ports that go to hydraulic cylinder or motor), and optional power beyond port (N Port, used to connect valves downstream). Some common examples of connecting this valve are shown below, however, it is possible to connect it in different configurations than shown.

The present invention relates to utility vehicles, such as industrial or agricultural tractors. Particularly, the invention relates to tractors having one or more hydraulically powered attachments.

Utility vehicles typically include an internal combustion engine, which delivers power to a transmission and ultimately to a wheel for traction, and also delivers power to pressurize hydraulic fluid, via one or more pumps, to operate hydraulic tools or implements.

For example, a tractor may have three hydraulic pumps driven from the engine. A first pump may provide pressurized hydraulic fluid to charge a steering cylinder of the vehicle. A second or “main” pump is usually fixed directly to the crankshaft of the engine and may be used to charge pressurized hydraulic fluid to the loader and the backhoe hydraulic cylinders.

A third or “auxiliary” pump may generate pressurized hydraulic fluid to charge a power takeoff clutch pack and at least one hydraulic cylinder which operates a three point hitch or “rockshaft.” The power takeoff is a shaft that is rotated by the vehicle transmission and is used for supplying rotational power to tools, such as mower decks, where rotation is required.

In small utility tractors, the first or steering pump typically requires about 1.4 to about 8 horsepower, depending on steering demand, and about 22 L/min (about 6 gallons per minute) of hydraulic fluid. The second or “main” pump typically requires about 3.2 to about 21.3 horsepower, depending on demand from loader or backhoe hydraulic systems, and about 46 L/min (about 12 gallons per minute) of hydraulic fluid. The third or “auxiliary” pump typically requires about 1 to about 9.5 horsepower, depending on demand from the rockshaft circuit, and about 20 L/min (about 5 gallons per minute) of hydraulic fluid. The engine for a small utility tractor typically delivers about 25 to 50 horsepower.

When a hydraulically powered attachment such as a sweeper, snow thrower, breaker, auger or cold planer is attached to a utility vehicle, the rockshaft may not be needed, nor is it practically operable. The present inventors have recognized the desirability of diverting hydraulic fluid that would otherwise supply the rockshaft when an attachment such as a sweeper, snow thrower, breaker, auger or cold planer is used. Furthermore, the present inventors have recognized the desirability of using the circulating hydraulic fluid otherwise available to the rockshaft to improve the effectiveness and efficiency of the utility vehicle.

Hydraulically powered attachments such as a sweeper, snow thrower, breaker, auger or cold planer are typically attached to the utility vehicle loader in place of the loader bucket. These attachments may be raised and positioned using the boom and bucket hydraulic cylinders.

The present inventors have recognized that a proper balance of available engine horsepower directed to the various tractor functions at the proper time is required for best operation of the machine. For example, U.S. Pat. No. 6,672,399 assigned to Deere and Company of Moline, Ill. relates to a method and apparatus for diverting pressurized hydraulic fluid, otherwise available to a utility vehicle rockshaft system, to be used by a backhoe hydraulic system.

While the loader is in use, the transmission must necessarily also be in use simultaneously. As such, it is desirable to limit the available horsepower consumed in the operation of the loader while demands are placed on the transmission, to prevent the engine from stalling. Furthermore, it is desirable to limit the hydraulic flow to the boom and bucket circuits so that the boom and bucket do not move too fast, but move at an appropriate rate.

The inventors also have recognized that hydraulically powered attachments such as a sweeper, snow thrower, breaker, auger or cold planer are used without high demand on the transmission, backhoe, rockshaft, or steering circuits. Furthermore, the inventors have recognized that it would be desirable to utilize additional flow from tractor hydraulic systems which are sitting idle while such an attachment is in use.

The present invention provides an apparatus for diverting pressurized hydraulic fluid, otherwise available to a utility vehicle rockshaft, to be used by a hydraulically powered attachment such as a sweeper, snow thrower, breaker, auger or cold planer. Particularly, the invention provides a method and apparatus for diverting pressurized hydraulic fluid from the rockshaft system to be available to a hydraulically powered attachment. Additionally, the invention provides a method and apparatus to divert pressurized hydraulic fluid for an attachment without reducing tractive horsepower the loader needs when it is in use.

The apparatus of the invention may be advantageously accomplished by use of an auxiliary diverter valve connected to the auxiliary pump. The auxiliary diverter valve can direct pressurized hydraulic fluid from the auxiliary pump to either the backhoe system, the rockshaft system, or the auxiliary circuit of the loader hydraulic system.

The auxiliary diverter valve may be connected to a mid-inlet position of the loader hydraulic system. Pressurized hydraulic fluid from the auxiliary pump may be available to the auxiliary circuit of the loader hydraulic system, and not to the boom and bucket circuits. Additional hydraulic flow is made available to an attachment such as a sweeper, snow thrower, breaker, auger or cold planer, allowing for faster movement of the operating cylinders or other hydraulic devices of the attachment, and thus faster and/or more efficient operation of the attachment.

FIG. 1 illustrates utility vehicle 20 such as a tractor with an attachable rear-mounted implement, such as backhoe 24, and a front mounted loader assembly 48. Utility vehicle 20 may include cab or operator"s station 28 including seat 32, steering wheel 34, and loader controls 36. The loader controls may include a selective control valve which may serve a single function or several functions. The cab may be supported on chassis 42 which is supported on front wheels 44 and larger rear wheels 46. The invention may be used with any size and type utility tractor, but is particularly useful for small utility tractors of the general size and type shown in FIG. 1.

The loader assembly may include bucket 81 and boom 82. Hydraulic cylinder 83 may raise and lower the boom, and hydraulic cylinder 84 may actuate the bucket between load holding and dumping positions. Cylinders 83, 84 may be double-acting.

As shown in the schematic of FIG. 3, the boom or lift circuit may be served by first control valve 177, and the bucket or tilt circuit may be served by second control valve 178. The first or boom control valve 177 and the second or bucket control valve 178 may be spool or cartridge valves within a mono block or bolted together, and controlled by an operator with loader controls 36 such as a selective control valve.

Various hydraulically powered auxiliary attachments such as a sweeper, snow thrower, breaker, auger or cold planer may be attached to the vehicle loader. For example, as shown in FIG. 2, the loader bucket may be removed so that snow thrower 61 may be attached to the boom 81 at the front end of tractor 20 in place of the bucket. The hydraulically powered attachment may have a hydraulic motor connected by fluid lines to the auxiliary circuit of the loader hydraulic system.

The auxiliary circuit of the loader hydraulic system may be served by a third or auxiliary control valve 179 shown in FIG. 3. The third or auxiliary control valve also may be a spool or cartridge valve in a mono block or bolted together with the boom and bucket control valves 177 and 178, and also may be controlled using loader controls 36. Alternatively, the auxiliary attachment may be served by an auxiliary control valve that is a separate or “add-on” device, not in a mono body with the boom and bucket control valves.

FIG. 3 illustrates hydraulic system 120 in one embodiment of the invention. Hydraulic system 120 may be charged by three pumps. Steering pump 124 and auxiliary pump 126 may be driven by the auxiliary drive of engine 130. Main pump 134 may be driven by the crankshaft of engine 130.

In one embodiment, steering pump 124 may charge power steering system 142 and ultimately powers steering cylinder 144. Hydraulic fluid out of steering system 142 may charge hydrostatic transmission 148 which transfers power from the engine to the utility vehicle gear train.

In one embodiment, main pump 134 may charge loader hydraulic system 166 which may include a loader selective control valve, and backhoe hydraulic system 168 which may include a backhoe selective control valve. The loader selective control valve may include a lever which operates the first or boom control valve 177 and the second or bucket control valve 178. The first or boom control valve 177 is part of the boom circuit which may include one or more double acting hydraulic cylinders used to raise or lower the boom. The second or bucket control valve is part of the bucket circuit which may include hydraulic cylinders to control movements of the bucket. Similarly, the backhoe selective control valve may include a lever which operates control valves connected to hydraulic cylinders which control movements of the backhoe, including cylinders for the bucket, dipper, stabilizer, boom and swing.

In one embodiment, auxiliary pump 126 may charge power takeoff system clutch pack 156, and either rockshaft hydraulic system 162, backhoe hydraulic system 168, or the auxiliary circuit of loader hydraulic system 166.

In one embodiment, when the auxiliary pump is connected to rockshaft hydraulic system 162, the pump may direct hydraulic fluid through a rockshaft selective control valve which powers at least one rockshaft hydraulic cylinder. The hydraulic cylinder(s) may control vertical and/or attitude and/or pitch adjustment of the three point hitch. When the auxiliary pump is connected to backhoe hydraulic system 168, the pump may direct hydraulic fluid through a backhoe selective control valve which may include control valves that power several hydraulic cylinders.

When the auxiliary pump is connected to auxiliary control valve 179, the pump may direct hydraulic fluid through an auxiliary hydraulic circuit of the loader hydraulic system. The auxiliary circuit include auxiliary control vale 179 and one or more valves 202, 203 that may be coupled to hydraulically powered attachments such as a sweeper, snow thrower, breaker, auger or cold planer. The attachment may have a hydraulic motor. In one embodiment, the attachment may be operated by use of a loader selective control valve.

In one embodiment, an auxiliary diverter valve in the form of spool or cartridge valve 200 may be hydraulically connected to pressurized hydraulic fluid from auxiliary pump 126. The auxiliary diverter valve may have several positions including a first position to deliver pressurized hydraulic fluid to rockshaft hydraulic system 162, a second position to deliver pressurized hydraulic fluid to backhoe hydraulic system 168, and a third position to deliver pressurized hydraulic fluid to auxiliary control valve 179 of the loader hydraulic system.

By diverting hydraulic fluid to the auxiliary circuit of the loader hydraulic system, the auxiliary pump may be used to increase total pump capacity to a hydraulically powered attachment such as a sweeper, snow thrower, breaker, auger or cold planer. The auxiliary pump previously represented unused capacity during operation of those hydraulically powered attachments.

The size of pump 134 is typically selected to correspond to the total horsepower demand of the front loader, via loader hydraulic system 166. The engine is typically sized to provide reserve horsepower over the demand of the loader to power the hydrostatic transmission during loader work, when the backhoe or other attachments are not in use. Thus, according to one embodiment of the invention, sufficient engine horsepower is available to drive both pumps 126, 134 to supply an attachment such as a sweeper, snow thrower, breaker, auger or cold planer with increased hydraulic capacity. By diverting flow from the auxiliary pump to the auxiliary circuit, the overall horsepower required by the vehicle may be reduced. The invention may therefore be particularly advantageous to retrofit existing utility vehicles or existing designs for utility vehicles.

In one embodiment, the auxiliary diverter valve may have a mid-inlet connection position to the loader hydraulic system so that hydraulic flow from the auxiliary pump is available only to the third or auxiliary control valve, and not to the first or boom control valve or to the second or bucket control valve of the loader hydraulic system. Attachments such as a sweeper, snow thrower, breaker, auger or cold planer typically do not use high hydraulic pressures, and do not require high tractive horsepower from the vehicle hydrostatic transmission. In contrast, the loader boom and bucket circuits require high pressures and, during loader operation, high tractive horsepower is needed from the vehicle.

Thus, hydraulic flow from the auxiliary pump may be diverted to the auxiliary circuit of the loader hydraulic system when an attachment is used. With additional flow from the auxiliary pump, total hydraulic flow available to the attachment may be at least about 20% higher than the hydraulic flow from the main pump alone. For example, in one embodiment, with additional flow from the auxiliary pump, total hydraulic flow available to an attachment may be about 60 L/min (about 16 gallons per minute), compared to about 46 L/min (12 gallons per minute) from the main pump alone.

In accordance with one embodiment of the invention, hydraulic flow from the auxiliary pump is not diverted to the boom or bucket control valves of the loader hydraulic system. As a result, sufficiently high tractive horsepower remains available when the loader is used so that the vehicle"s engine will not stall out.

In one embodiment, auxiliary diverter valve 200 may be connected via fluid line 201 to a mid-inlet position of the loader hydraulic system. In this embodiment, fluid line 201 is connected downstream of boom and bucket control valves 177, 178. For example, fluid line 201 may be connected to a neutral core line between the bucket or boom control valves and auxiliary control valve 179. In this embodiment, hydraulic flow from the auxiliary pump through the auxiliary diverter valve may be available to the auxiliary control valve and auxiliary circuit only.

In an alternative embodiment, hydraulic flow from the auxiliary pump through the auxiliary diverter valve also may be available to the backhoe hydraulic system. For example, the auxiliary diverter valve may have only two positions, i.e., a first position directing hydraulic fluid to the rockshaft hydraulic system, and a second position directing hydraulic fluid to either the backhoe hydraulic system or the auxiliary circuit of the loader hydraulic system. In this alternative embodiment, the auxiliary control valve may be used to select either the backhoe and the auxiliary circuit of the loader hydraulic system. As a result, fluid line 204 may not be needed for this alternative embodiment.

In one embodiment, sufficient flow from the auxiliary pump may be diverted to the auxiliary control valve and auxiliary circuit so that most of the engine power is provided to the hydraulically powered attachment. For example, in one embodiment, about 75 percent of the available engine horsepower may be available for the main and auxiliary hydraulic pumps when a hydraulically powered attachment is used. In contrast, when the loader is being used, only about 50 percent of the available engine horsepower may be available to the main hydraulic pump, with the remainder may be available as tractive horsepower. When the rockshaft is in use, the auxiliary pump uses only about 25 percent of the available engine horsepower. These examples are representative for a small utility tractor that are capable of reducing tractive power if the engine slows excessively due to the loader hydraulic circuits.

"It gives me full-time hydraulics on an older tractor without having to spend thousands of dollars for a new tractor," says Wilson. "I bought the tractor used for $300 and paid another $200 for materials. A used tractor equipped with live hydraulics would have cost me at least $3,000."

The tractor was originally equipped with a loader but it wasn"t built strong enough so it kept bending. He used 2 by 8-in. channel iron to build a new one. The tractor did not have live hydraulics so that whenever he depressed the clutch, he had no hydraulic power. "That meant whenever I stopped to shift gears I couldn"t raise the loader bucket," says Wilson.

He got the pumps cheap from a salvage yard and had them rebuilt for about $25 each. One pump operates the tractor"s power steering system and the other one operates the loader. A pair of valves controls bucket tilt and also the up and down motion of the loader. He paid $10 for the valves which he bought at a farm auction. Many of the hoses were also bought at auctions.

The tractor has three hydraulic cylinders - two 3-in. dia. ones to raise and lower the bucket and a 4-in. dia. one (off a log splitter) to tilt the bucket. The two 3-in. dia. cylinders are off an old Horn front-end loader.

1949 Case Tractor Gets New Loader, Full-Time Hydraulics TRACTORS Loaders 28-5-27 Bill Wilson, Thompson Falls, Montana, built a hydraulic-operated front-end loader for his 1949 Case DC tractor. He also added the power steering system and a pair of hydraulic pumps off a couple of old Case combines."It gives me full-time hydraulics on an older tractor without having to spend thousands of dollars for a new tractor," says Wilson. "I bought the tractor used for $300 and paid another $200 for materials. A used tractor equipped with live hydraulics would have cost me at least $3,000."The tractor was originally equipped with a loader but it wasn"t built strong enough so it kept bending. He used 2 by 8-in. channel iron to build a new one. The tractor did not have live hydraulics so that whenever he depressed the clutch, he had no hydraulic power. "That meant whenever I stopped to shift gears I couldn"t raise the loader bucket," says Wilson. He got the pumps cheap from a salvage yard and had them rebuilt for about $25 each. One pump operates the tractor"s power steering system and the other one operates the loader. A pair of valves controls bucket tilt and also the up and down motion of the loader. He paid $10 for the valves which he bought at a farm auction. Many of the hoses were also bought at auctions.The tractor has three hydraulic cylinders - two 3-in. dia. ones to raise and lower the bucket and a 4-in. dia. one (off a log splitter) to tilt the bucket. The two 3-in. dia. cylinders are off an old Horn front-end loader. Contact: FARM SHOW Followup, Bill Wilson, 44 Gable Road, Thompson Falls, Montana 59873 (ph 406 827-3006).

The present invention relates to utility vehicles, such as industrial or agricultural tractors. Particularly, the invention relates to tractors having one or more hydraulically powered attachments.

Utility vehicles typically include an internal combustion engine, which delivers power to a transmission and ultimately to a wheel for traction, and also delivers power to pressurize hydraulic fluid, via one or more pumps, to operate hydraulic tools or implements.

For example, a tractor may have three hydraulic pumps driven from the engine. A first pump may provide pressurized hydraulic fluid to charge a steering cylinder of the vehicle. A second or “main” pump is usually fixed directly to the crankshaft of the engine and may be used to charge pressurized hydraulic fluid to the loader and the backhoe hydraulic cylinders.

A third or “auxiliary” pump may generate pressurized hydraulic fluid to charge a power takeoff clutch pack and at least one hydraulic cylinder which operates a three point hitch or “rockshaft.” The power takeoff is a shaft that is rotated by the vehicle transmission and is used for supplying rotational power to tools, such as mower decks, where rotation is required.

In small utility tractors, the first or steering pump typically requires about 1.4 to about 8 horsepower, depending on steering demand, and about 22 L/min (about 6 gallons per minute) of hydraulic fluid. The second or “main” pump typically requires about 3.2 to about 21.3 horsepower, depending on demand from loader or backhoe hydraulic systems, and about 46 L/min (about 12 gallons per minute) of hydraulic fluid. The third or “auxiliary” pump typically requires about 1 to about 9.5 horsepower, depending on demand from the rockshaft circuit, and about 20 L/min (about 5 gallons per minute) of hydraulic fluid. The engine for a small utility tractor typically delivers about 25 to 50 horsepower.

When a hydraulically powered attachment such as a sweeper, snow thrower, breaker, auger or cold planer is attached to a utility vehicle, the rockshaft may not be needed, nor is it practically operable. The present inventors have recognized the desirability of diverting hydraulic fluid that would otherwise supply the rockshaft when an attachment such as a sweeper, snow thrower, breaker, auger or cold planer is used. Furthermore, the present inventors have recognized the desirability of using the circulating hydraulic fluid otherwise available to the rockshaft to improve the effectiveness and efficiency of the utility vehicle.

Hydraulically powered attachments such as a sweeper, snow thrower, breaker, auger or cold planer are typically attached to the utility vehicle loader in place of the loader bucket. These attachments may be raised and positioned using the boom and bucket hydraulic cylinders.

The present inventors have recognized that a proper balance of available engine horsepower directed to the various tractor functions at the proper time is required for best operation of the machine. For example, U.S. Pat. No. 6,672,399 assigned to Deere and Company of Moline, Ill. relates to a method and apparatus for diverting pressurized hydraulic fluid, otherwise available to a utility vehicle rockshaft system, to be used by a backhoe hydraulic system.

While the loader is in use, the transmission must necessarily also be in use simultaneously. As such, it is desirable to limit the available horsepower consumed in the operation of the loader while demands are placed on the transmission, to prevent the engine from stalling. Furthermore, it is desirable to limit the hydraulic flow to the boom and bucket circuits so that the boom and bucket do not move too fast, but move at an appropriate rate.

The inventors also have recognized that hydraulically powered attachments such as a sweeper, snow thrower, breaker, auger or cold planer are used without high demand on the transmission, backhoe, rockshaft, or steering circuits. Furthermore, the inventors have recognized that it would be desirable to utilize additional flow from tractor hydraulic systems which are sitting idle while such an attachment is in use.

The present invention provides an apparatus for diverting pressurized hydraulic fluid, otherwise available to a utility vehicle rockshaft, to be used by a hydraulically powered attachment such as a sweeper, snow thrower, breaker, auger or cold planer. Particularly, the invention provides a method and apparatus for diverting pressurized hydraulic fluid from the rockshaft system to be available to a hydraulically powered attachment. Additionally, the invention provides a method and apparatus to divert pressurized hydraulic fluid for an attachment without reducing tractive horsepower the loader needs when it is in use.

The apparatus of the invention may be advantageously accomplished by use of an auxiliary diverter valve connected to the auxiliary pump. The auxiliary diverter valve can direct pressurized hydraulic fluid from the auxiliary pump to either the backhoe system, the rockshaft system, or the auxiliary circuit of the loader hydraulic system.

The auxiliary diverter valve may be connected to a mid-inlet position of the loader hydraulic system. Pressurized hydraulic fluid from the auxiliary pump may be available to the auxiliary circuit of the loader hydraulic system, and not to the boom and bucket circuits. Additional hydraulic flow is made available to an attachment such as a sweeper, snow thrower, breaker, auger or cold planer, allowing for faster movement of the operating cylinders or other hydraulic devices of the attachment, and thus faster and/or more efficient operation of the attachment.

FIG. 1 illustrates utility vehicle 20 such as a tractor with an attachable rear-mounted implement, such as backhoe 24, and a front mounted loader assembly 48. Utility vehicle 20 may include cab or operator"s station 28 including seat 32, steering wheel 34, and loader controls 36. The loader controls may include a selective control valve which may serve a single function or several functions. The cab may be supported on chassis 42 which is supported on front wheels 44 and larger rear wheels 46. The invention may be used with any size and type utility tractor, but is particularly useful for small utility tractors of the general size and type shown in FIG. 1.

The loader assembly may include bucket 81 and boom 82. Hydraulic cylinder 83 may raise and lower the boom, and hydraulic cylinder 84 may actuate the bucket between load holding and dumping positions. Cylinders 83, 84 may be double-acting.

As shown in the schematic of FIG. 3, the boom or lift circuit may be served by first control valve 177, and the bucket or tilt circuit may be served by second control valve 178. The first or boom control valve 177 and the second or bucket control valve 178 may be spool or cartridge valves within a mono block or bolted together, and controlled by an operator with loader controls 36 such as a selective control valve.

Various hydraulically powered auxiliary attachments such as a sweeper, snow thrower, breaker, auger or cold planer may be attached to the vehicle loader. For example, as shown in FIG. 2, the loader bucket may be removed so that snow thrower 61 may be attached to the boom 81 at the front end of tractor 20 in place of the bucket. The hydraulically powered attachment may have a hydraulic motor connected by fluid lines to the auxiliary circuit of the loader hydraulic system.

The auxiliary circuit of the loader hydraulic system may be served by a third or auxiliary control valve 179 shown in FIG. 3. The third or auxiliary control valve also may be a spool or cartridge valve in a mono block or bolted together with the boom and bucket control valves 177 and 178, and also may be controlled using loader controls 36. Alternatively, the auxiliary attachment may be served by an auxiliary control valve that is a separate or “add-on” device, not in a mono body with the boom and bucket control valves.

FIG. 3 illustrates hydraulic system 120 in one embodiment of the invention. Hydraulic system 120 may be charged by three pumps. Steering pump 124 and auxiliary pump 126 may be driven by the auxiliary drive of engine 130. Main pump 134 may be driven by the crankshaft of engine 130.

In one embodiment, steering pump 124 may charge power steering system 142 and ultimately powers steering cylinder 144. Hydraulic fluid out of steering system 142 may charge hydrostatic transmission 148 which transfers power from the engine to the utility vehicle gear train.

In one embodiment, main pump 134 may charge loader hydraulic system 166 which may include a loader selective control valve, and backhoe hydraulic system 168 which may include a backhoe selective control valve. The loader selective control valve may include a lever which operates the first or boom control valve 177 and the second or bucket control valve 178. The first or boom control valve 177 is part of the boom circuit which may include one or more double acting hydraulic cylinders used to raise or lower the boom. The second or bucket control valve is part of the bucket circuit which may include hydraulic cylinders to control movements of the bucket. Similarly, the backhoe selective control valve may include a lever which operates control valves connected to hydraulic cylinders which control movements of the backhoe, including cylinders for the bucket, dipper, stabilizer, boom and swing.

In one embodiment, auxiliary pump 126 may charge power takeoff system clutch pack 156, and either rockshaft hydraulic system 162, backhoe hydraulic system 168, or the auxiliary circuit of loader hydraulic system 166.

In one embodiment, when the auxiliary pump is connected to rockshaft hydraulic system 162, the pump may direct hydraulic fluid through a rockshaft selective control valve which powers at least one rockshaft hydraulic cylinder. The hydraulic cylinder(s) may control vertical and/or attitude and/or pitch adjustment of the three point hitch. When the auxiliary pump is connected to backhoe hydraulic system 168, the pump may direct hydraulic fluid through a backhoe selective control valve which may include control valves that power several hydraulic cylinders.

When the auxiliary pump is connected to auxiliary control valve 179, the pump may direct hydraulic fluid through an auxiliary hydraulic circuit of the loader hydraulic system. The auxiliary circuit include auxiliary control vale 179 and one or more valves 202, 203 that may be coupled to hydraulically powered attachments such as a sweeper, snow thrower, breaker, auger or cold planer. The attachment may have a hydraulic motor. In one embodiment, the attachment may be operated by use of a loader selective control valve.

In one embodiment, an auxiliary diverter valve in the form of spool or cartridge valve 200 may be hydraulically connected to pressurized hydraulic fluid from auxiliary pump 126. The auxiliary diverter valve may have several positions including a first position to deliver pressurized hydraulic fluid to rockshaft hydraulic system 162, a second position to deliver pressurized hydraulic fluid to backhoe hydraulic system 168, and a third position to deliver pressurized hydraulic fluid to auxiliary control valve 179 of the loader hydraulic system.

By diverting hydraulic fluid to the auxiliary circuit of the loader hydraulic system, the auxiliary pump may be used to increase total pump capacity to a hydraulically powered attachment such as a sweeper, snow thrower, breaker, auger or cold planer. The auxiliary pump previously represented unused capacity during operation of those hydraulically powered attachments.

The size of pump 134 is typically selected to correspond to the total horsepower demand of the front loader, via loader hydraulic system 166. The engine is typically sized to provide reserve horsepower over the demand of the loader to power the hydrostatic transmission during loader work, when the backhoe or other attachments are not in use. Thus, according to one embodiment of the invention, sufficient engine horsepower is available to drive both pumps 126, 134 to supply an attachment such as a sweeper, snow thrower, breaker, auger or cold planer with increased hydraulic capacity. By diverting flow from the auxiliary pump to the auxiliary circuit, the overall horsepower required by the vehicle may be reduced. The invention may therefore be particularly advantageous to retrofit existing utility vehicles or existing designs for utility vehicles.

In one embodiment, the auxiliary diverter valve may have a mid-inlet connection position to the loader hydraulic system so that hydraulic flow from the auxiliary pump is available only to the third or auxiliary control valve, and not to the first or boom control valve or to the second or bucket control valve of the loader hydraulic system. Attachments such as a sweeper, snow thrower, breaker, auger or cold planer typically do not use high hydraulic pressures, and do not require high tractive horsepower from the vehicle hydrostatic transmission. In contrast, the loader boom and bucket circuits require high pressures and, during loader operation, high tractive horsepower is needed from the vehicle.

Thus, hydraulic flow from the auxiliary pump may be diverted to the auxiliary circuit of the loader hydraulic system when an attachment is used. With additional flow from the auxiliary pump, total hydraulic flow available to the attachment may be at least about 20% higher than the hydraulic flow from the main pump alone. For example, in one embodiment, with additional flow from the auxiliary pump, total hydraulic flow available to an attachment may be about 60 L/min (about 16 gallons per minute), compared to about 46 L/min (12 gallons per minute) from the main pump alone.

In accordance with one embodiment of the invention, hydraulic flow from the auxiliary pump is not diverted to the boom or bucket control valves of the loader hydraulic system. As a result, sufficiently high tractive horsepower remains available when the loader is used so that the vehicle"s engine will not stall out.

In one embodiment, auxiliary diverter valve 200 may be connected via fluid line 201 to a mid-inlet position of the loader hydraulic system. In this embodiment, fluid line 201 is connected downstream of boom and bucket control valves 177, 178. For example, fluid line 201 may be connected to a neutral core line between the bucket or boom control valves and auxiliary control valve 179. In this embodiment, hydraulic flow from the auxiliary pump through the auxiliary diverter valve may be available to the auxiliary control valve and auxiliary circuit only.

In an alternative embodiment, hydraulic flow from the auxiliary pump through the auxiliary diverter valve also may be available to the backhoe hydraulic system. For example, the auxiliary diverter valve may have only two positions, i.e., a first position directing hydraulic fluid to the rockshaft hydraulic system, and a second position directing hydraulic fluid to either the backhoe hydraulic system or the auxiliary circuit of the loader hydraulic system. In this alternative embodiment, the auxiliary control valve may be used to select either the backhoe and the auxiliary circuit of the loader hydraulic system. As a result, fluid line 204 may not be needed for this alternative embodiment.

In one embodiment, sufficient flow from the auxiliary pump may be diverted to the auxiliary control valve and auxiliary circuit so that most of the engine power is provided to the hydraulically powered attachment. For example, in one embodiment, about 75 percent of the available engine horsepower may be available for the main and auxiliary hydraulic pumps when a hydraulically powered attachment is used. In contrast, when the loader is being used, only about 50 percent of the available engine horsepower may be available to the main hydraulic pump, with the remainder may be available as tractive horsepower. When the rockshaft is in use, the auxiliary pump uses only about 25 percent of the available engine horsepower. These examples are representative for a small utility tractor that are capable of reducing tractive power if the engine slows excessively due to the loader hydraulic circuits.

The present invention relates to front end loader assemblies that are commonly used to lift and move loose material such as dirt, gravel, snow and the like. More specifically, the present invention relates to front end loader assemblies that are selectively attachable to vehicles.

The prior art record is replete with many different types of front end loader assemblies. Front end loader assemblies typically include a lift bucket. The lift bucket is attached to a linkage arrangement that supports the lift bucket at various positions and orientations. Hydraulic cylinders engage the lift bucket and support linkages at various points. By selectively controlling the various hydraulic cylinders, the bucket can be moved throughout a large range of motions.

Front end loader assemblies are commonly used on construction equipment such a bulldozers and back hoes. On such vehicles, the front end loaders are used to move earth, gravel, stones and other loose or heavy materials. Since the front end loaders are used to move heavy materials, such front end loaders are typically constructed from large and heavy metal components that are capable of bearing the large stresses incurred. Heavily constructed front end loader assemblies present no problem to construction vehicles such as bulldozers and back hoes, because such vehicles have large engines, heavy frames and they are designed to hold the weight of a large heavy front end loader assembly. However, these same front end loader assemblies cannot be used on common road vehicles because they are too heavy and would damage most any truck or other road vehicle to which they were attached.

Construction vehicles such as bulldozers and back hoes are expensive and are not practical for an average person to own. However, many people have the occasional need to use a front end loader to move snow, spread mulch, move dirt, or the like. Traditional front end loader assemblies cannot be attached to passenger vehicle because traditional front end loaders are too heavy for the frames of the vehicle and require anchoring points not available on trucks and passenger vehicles. As a result, people must rent a construction vehicle with a front end loader or do without.

Municipalities, and other local authorities also commonly need front end loaders to remove snow and other debris from streets. Municipalities have many different types of vehicles at their disposal. However, most municipalities only have only one or just a few construction vehicles with front end loaders. These few vehicles are insufficient to clear snow from the numerous streets in a municipality after a major snow storm. It may therefore take a municipality several days to clear snow away from vital facilities after a significant snow fall.

A need therefore exists in the art for a light front end loader assembly that can be attached to large road vehicle such as a full sized pick-up truck, dump truck, garbage truck or the like. Such a front end loader assembly would enable individuals and municipalities to add front end loaders to vehicles they already own. Consequently, a vehicle with a front end loader can be readily produced at the fraction of the price of purchasing a construction vehicle with a typical prior art front end loader.

The present invention is a front end loader assembly that is attachable to a truck or other common road vehicle that is not designed to use a front end loader. The front end loader assembly includes a stationary mount with a base that attaches to the chassis of the vehicle. The stationary mount also includes a support frame that extends upwardly in front of the vehicle"s bumper. A frame structure is provided having a pair of generally vertical frame elements and at least one generally horizontal frame elements. The frame structure is pivotably coupled to the stationary mount at a first point of attachment. A single first hydraulic cylinder extending between the stationary mount and the frame structure, wherein the first hydraulic cylinder is capable of moving the frame structure relative the stationary mount about the first point of attachment. An arm structure is coupled to the frame structure by a hinged connection, wherein the hinged connection exists between the vertical frame elements of the frame structure. A single second hydraulic cylinder extends between the frame structure and the arm structure, wherein the second hydraulic cylinder is capable of moving the arm structure relative the frame assembly. A bucket is coupled to the arm structure. A third cylinder is coupled between the bucket and the arm structure for selectively moving the bucket relative to the arm structure.

Referring to FIG. 1, a first preferred embodiment of the present invention front end loader assembly 10 is shown. The front end loader assembly 10 is a light weight assembly that is specifically designed for use on common road vehicles, such as pick-up trucks and dump trucks, that are not designed to use front end loaders. As will be later explained, the front end loader assembly 10 does not require that the vehicle have any specialized mounts. Rather, the front end loader assembly 10 is capable of being mounted to most any truck or other large vehicle as that vehicle manufactured by the factory.

The purpose of the front end loader assembly 10 is to provide to individuals and municipalities, the ability to convert and existing vehicle, such as a pick-up truck, a dump truck, a garbage truck or other vehicle into a front end loader. The front end loader assembly 10 is light weight, yet has the power to lift loose material such as snow, sand, gravel, mulch, soil and the like. Consequently, individuals can own their own front end loader for a reasonable price and municipalities can convert existing vehicle into snow removal equipment.

Referring to FIG. 2, it can be seen that the first section of the present invention front end loader assembly that attaches to a vehicle is a stationary mount 12. The stationary mount 12 contains at least two frame elements 14 that bolt to the chassis frame of a vehicle under the front end of the vehicle. The length shape and distance between the frame elements 14 will vary from one vehicle model to another. Accordingly, the stationary mount 12 is ordered by a purchaser to match the type of vehicle onto which the front end loader assembly 10 (FIG. 1) is being attached. Different vehicles have different chassis frames and various under chassis elements. By custom ordering a stationary mount 12 for a particular type of vehicle, it can be ensured that the stationary mount 12 will fit properly and will not interfere with other under chassis elements of the vehicle.

A support frame 22 extends upwardly from the mounting bracket 16. The support frame 22 contains two vertical elements 24 and a horizontal cross element 26 that joins the tops of the vertical elements 24 together. The lower 28 portion of the vertical elements 24 may be angled away from the vertical. This allows the stationary mount 12 to attach to a vehicle without the vertical elements 24 touching the front bumper of the vehicle. In many vehicles with air bags, the trigger for the air bag is contained within the front bumper of that vehicle. By keeping the stationary mount 12 away from the front bumper, it is less likely that the front end loader assembly 10 (FIG. 1) will accidently trigger the vehicle"s air bag during the use of the front end loader assembly.

A cylinder mounting plate 30 extends downwardly from the horizontal cross element 26 that joins the two vertical elements 24 together. The cylinder mounting plate 30 is adapted to receive the primary lift cylinder (not shown) as will later be explained.

Referring to FIG. 3, an exemplary embodiment of a linkage assembly 40 is shown. The linkage assembly 40 is the section of the front end loader assembly 10 (FIG. 1) that is articulated and attaches a bucket 34 (FIG. 1) to the stationary mount 12 (FIG. 1) that is attached to a vehicle. The linkage assembly 40 contains two main frame elements. These frame elements include an L-shaped frame assembly 42 and an lift arm frame assembly 44.

The L-shaped frame assembly 42 is comprised of two L-shaped frame elements 46 that are spaced a predetermined distance D apart by a series of cross elements. Each of the L-shaped frame elements 46 has a horizontal segment 48 and a vertical segment 50. The vertical segment 50 joins to the horizontal segment 48 at an angle of between 75 degrees and 90 degrees. An optional angle bracket 52 can be placed between the horizontal segment 48 and the vertical segment 50 to reinforce the point of junction. The free end of each of the horizontal segments 48 contains a pin aperture 54. The width and spacing of the horizontal segments 48 are designed so that the free ends of the horizontal segments 48 can fit between each pair of mounting flanges 18 (FIG. 2) on the stationary mount 12 (FIG. 2). A pivot pin 56 passes through the apertures 20 (FIG. 2) in the mounting bracket 18 (FIG. 2) and the pin apertures 54 in the horizontal segments 48, thereby joining the L-shaped frame elements 46 to the stationary mount 12 (FIG. 2) with a hinged connection.

A cylinder mount 58 is disposed at a point between the L-shaped frame elements 46 at a point proximate the mid-length of each horizontal segment 48. The cylinder mount 58 attaches to one end of the primary lift cylinder 60 with a pivot pin 62. The opposite end of the primary lift cylinder 60 attaches to the cylinder mount 30 (FIG. 2) that extends from the top of the stationary mount 12 (FIG. 2). As a result, as the primary lift cylinder 60 expands and contracts, the entire L-shaped frame assembly 40 is rotated about pivot pins 56 at the free end of the horizontal segments 48 and the entire L-shaped frame assembly 40 moves relative the stationary mount 12 (FIG.2).

Pivot rod apertures 64 are formed through the free end of the vertical segments 50 of the L-shaped frame elements 46. The pivot rod apertures 64 are concentrically aligned and sized to receive a pivot rod 66. Short arms 68 extend from the vertical segments 50 of the L-shaped frame elements 46 at points near their free ends. The short arms 68 slope upwardly at an acute angle with respect to the horizontal. Pivot pin apertures 70 are disposed in the short arms 68 proximate their free ends. The apertures 70 are sized to receive pivot pins 72, the purpose of which will be later explained.

A base frame structure 74 extends forward of the L-shaped frame elements 46 from the point where the vertical segment 50 of the L-shaped frame elements 46 meets the horizontal segments 48. The base frame structure 74 is rigidly affixed to the L-shaped frame elements 46 and lays in the same general plane as does the horizontal segments 48 of the L-shaped frame elements 46. Guide arms 76 extend forward of the base frame structure 74. The guide arms 76 are slightly tapered so that the front ends of the guide arms 76 are closer together than is the base of the guide arms 76. The purpose of the guide arms 76 will later be explained.

A cylinder mount 78 is affixed to the base frame structure 74 at a point between the guide arms 76. The cylinder mount 78 attaches to one end of an arm lift cylinder 80 with a pivot pin 82. The arm lift cylinder 80 lifts the lift arm frame assembly 44 in a manner which will later become apparent.

The lift arm frame assembly 44 is comprised of two maim frame elements 84. Each of the main frame elements 84 is generally J-shaped, having a straight vertical element 86 and a foot segment 88 that extends away from the vertical element 86 at an obtuse angle. The free end of the foot segment 88 and the free end of the vertical element 86 are joined together by an optional reinforcement element 90, thereby forming a triangular truss. The two main frame elements 84 are joined together by three hollow tubes. The first hollow tube 92 is positioned between the ends of the foot segment 88 of the main frame elements 84. Apertures 94 are formed at this position in the foot segment 88 that communicate with the interior of the hollow tube 92. As a result, a continuous conduit is formed through the arm frame assembly 44 that is sized to accept the first pivot rod 66 therein.

The third hollow tube 106 is positioned at the base of the vertical element 86 of each main frame element 84. The third hollow tube 106 has two open ends, wherein the third hollow tube 106 is sized to receive a bucket axle 108 therein. The bucket axle 108 terminates at both ends with a pivot arm plate 110. As a result, the pivot arm plates 110 are free to rotate with the bucket axle 108 as the bucket axle turns within the third hollow tube 106. Each of the pivot arm plates 110 has a front end 112 and a back end 113. The bucket axle 108 is joined to the pivot arm plates 110 at a point between the midpoint and the front end 112 of the pivot arm plates 110.

A bucket support frame 115 extends upwardly from the pivot arm plates 110. The bucket support frame 115 has a generally inverted U-shape, wherein two vertical elements support a horizontal cross element 117. A cylinder mount 114 extends downwardly from the middle of the horizontal cross element 117. The cylinder mount 114 joins to a bucket cylinders 116 that is used to turn the bucket assembly 34 (shown in FIG. 4).

Apertures 116 are also formed in the pivot arm plates 110 at a point proximate the front end 112 of the pivot arm plates 110. The apertures 116 are sized to receive pivot pins 118 that join the front end 112 of the pivot arm plates 110 to the bucket 34 (FIG.4), as will later be explained.

A first linkage arm 120 is attached to the back end 113 of each pivot arm plate 110 with a hinged connection. The first linkage arm 120 extends upward and engages the front end 123 of a second linkage arm 122 with yet another hinged connection. The back end 124 of the second linkage arm 122 connects to suspension linkages 126 that support the back end 124 of the second arm linkage 122 from the short arms 68 that extend from the L-shaped frame elements 46. The interconnections between the support linkages 126 and the second arm linkage 122 are all achieved with pivot pins (not shown) that allow independent movement of each element.

The second linkage arm 122 contains three apertures. One aperture exists at each end of the second linkage arm 122 and one aperture 129 exists at a point between the middle of the second linkage arm 122 and its back end 124. As has previously been explained, the back end 124 of the second linkage arm 122 is attached to support linkages 126 and the front end 123 of the second linkage arm 122 is attached to the first linkage arm. The second linkage arm 122 rests in the hinge bracket 102 that extends from the main frame element 84 of the lift arm frame assembly 44. The second pivot rod 100 extends through the hinge bracket 102, the middle aperture 129 in the second linkage arm 122 and the second hollow tube 96 in the lift arm frame assembly 44. The second pivot rod 100 therefore becomes the fulcrum point around which the second linkage arm 122 pivots.

When assembled, the foot segment 88 of the main frame elements 84 on the lift arm frame assembly 44 pass between the free ends of the vertical segments 50 of the L-shaped frame elements 46. The interior of the first hollow tube 92 on the lift arm frame assembly 44 aligns with the apertures 64 at the free end of the vertical segments 50 of the L-shaped frame elements 46. The first pivot rod 66 passes through the apertures 64 in the vertical segments 50 of the L-shaped frame elements 46 and the first hollow tube 92. This creates a hinged connection between the L-shaped frame assembly 42 and the lift arm frame assembly 44.

When the arm lift cylinder 80 is fully contracted, the bottom of the lift arm frame assembly 44 abuts against the base frame structure 74 of the L-shaped frame assembly 42. The guide arms 76 extending from the base frame structure 74 help guide the lift arm frame assembly 42 into position so that the majority of the lift arm frame assembly 44 is positioned between the L-shaped frame elements 46 of the L-shaped frame assembly 42.

Referring to FIG. 4, an exemplary embodiment of a bucket assembly 130 is shown. The bucket assembly 130 includes a light weight bucket 34 formed in the shape of traditional front end loader buckets. On the rear surfaces of the bucket 34 are formed two mounting brackets 132 and a cylinder engagement bracket 135. Each of the mounting brackets 132 contains lower mount flanges 134. The lower mount flanges 134 are adapted to receive the front end 112 (FIG. 3) of the pivot arm plate 110 (FIG. 3) wherein the pivot arm plate 110 attached to the lower mount flanges 134 with a pivot pin 118 (FIG. 3). The cylinder engagement bracket 135 contains apertures 136. The apertures 136 receive a pivot pin 137. The space within the cylinder engagement bracket 135 and the pivot pin 137 are adapted to receive the bucket cylinder 116 (FIG. 3). As the bucket cylinder 116 expands and contracts, the bucket assembly 130 rotates about the lower mount flanges 134.

Referring to FIG. 6, a schematic of the hydraulic controls for the exemplary embodiment are shown. To attach the present invention front end loader assembly to a vehicle, a hydraulic pump 200 is first added to the vehicle. The hydraulic pump can be electric. However, in the preferred embodiment, the hydraulic pump 200 is mechanical pump that runs from the rotation of the vehicle engine 202 via a fan belt or similar connection.

The hydraulic pump 200 is connected to a control manifold 204, wherein the control manifold 204 is affixed to all of the hydraulic cylinders contained within the front end loader assembly. The direction of the flow of hydraulic fluid from the hydraulic pump 200 to the hydraulic cylinders is controlled by the valving of the control manifold 204. The control manifold 204 can be attached to any stationary part of the vehicle or to the front end loader itself. The valving contained within the control manifold 204 is controlled by at least one control handle 206. To facilitate the operation of the control manifold 204 from within the passenger compartment 208 of the vehicle, at least one control cable 210 is strung from the passenger compartment 208 to the control manifold 204. The cable 210 is affixed to control levers 212 within the passenger compartment 208, wherein the manipulation of the control levers 212 is transferred to the control manifold 204 via the cable 210.

Returning to FIG. 5, it can be sen that the present invention front end loader assembly 10 can be attached to most any existing vehicle. Once attached, the front end loader assembly 10 can be used to scoop material from the ground, as is shown in FIG. 1 or lift material off of the ground, as is shown in FIG. 5. The use of the linkage elements 110, 120, 122, 126 on the bucket 34,eliminate the need for complicated controls when lifting the bucket 34. Consequently, the entire front end loader can be operated by controlling the expansion of the main lift cylinder 60, the arm lift cylinder 80 and the bucket cylinders 116. The use of only a few cylinders helps to make the front end loader assembly 10 be low cost, light weight and easy to operate.

It will be understood that a person skilled in the art of front end loader design can make alternate embodiments of the present invention using functionally equivalent components that have not been specifically described. For example, the size, shape, and location of the various frame elements and linkages can be changed as desired. All such obvious modifications are intended to be included in the scope of this disclosure as defined by the appended claims.

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The loader technology package prep provides the installed harness to further install a hardware bundle that has four features to make material handling easier and more efficient. The package is only for mid-model year 2022 6R 110 to 6R 250 Tractors when equipped with the electric joystick and mid- valves.

This feature moves the loader boom and bucket automatically to predefined positions. The operator can save two sets of boom height and bucket angles (A and B). With one short push or pull of the joystick, the loader automatically returns the boom and bucket to the desired position.

When more positions are needed, such as loading bales in two layers on a trailer or including transport heights and angles in the positioning feature, the second set of positions (b) can be used. All values and settings are shown in the main screen of the tractor, including the current bucket angle.

This feature levels the attachment parallel to the ground, while conventional loader leveling systems maintain the same angle versus the tractor. This means that when riding in hilly conditions or over curbs on the farm, the pallet fork, bucket, or other attachment is actively moved into a horizontal position. If this behavior is not desired by the operator, it can be turned off in the tractor display. The attachment is then leveled to the tractor if equipped with a leveling feature such as mechanical self-leveling (MSL).

The DWS feature displays the current weight loaded in the attachment, such as a bucket. The tractor does not need to stop for weighing, allowing the operator to fill up a bucket to the required target weight without interrupting for a separate weighing cycle. It also allows the operator to enter target weights per component, such as silage, forage, or soy. This provides an instant overview of needed ingredients for feeding wagons and other loading tasks. If starting a new silage pit with changed nutrition value, the target value for this single component is easily adjustable.

The weighing system includes a counter for every loading cycle. The tractor counts with every loading cycle, confirmed by simply pushing a button integrated into the loader joystick. The weighing system even registers multiple units. For example, when handling two bales in one grapple, the tractor can count two bales with every loading cycle.

The loader camera provides visibility to the loader carrier and surroundings. The hooks of the carrier are visible to facilitate connecting attachments. When working with pallet forks, the fork tips are visible to assist picking up pallets with ease. The video image is shown in the built-in display of the 6R Tractor.

The camera is factory-installed in the loader factory; the wiring harness is protected inside the boom. The camera angle can be adjusted if needed. It is possible that a different position of the camera is desired, such as showing the contents of a bucket or the side of a snow blade. For such unique desires, spare cable length is available to enable customized camera positions.

When a hydraulic system fails, finding the source of the problem can be a challenge. Though hydraulic systems primarily consist of a sump, motor, pump, valves, actuators and hydraulic fluid, any of these parts could be the source of failure. That"s not to mention the additional potential for failure through human error and faulty maintenance practices. If your system fails, you need to know why it fails, how to find the failure and how to keep it running smoothly in the future, all while keeping personnel safe.

It"s often easy to tell when a hydraulic system fails — symptoms can include high temperatures, low pressure readings and slow or erratic operation are glaring problems. But what are the most common causes of hydraulic systems failures? We can trace most hydraulic issues back to a few common causes, listed below.

Air and water contamination are the leading causes of hydraulic failure, accounting for 80 to 90% of hydr