The invention relates to a hydraulic system used in an industrial vehicle, and in particular a materials handling vehicle or forklift truck. Examples of forklift trucks include reach trucks and turret trucks.
Forklift trucks are used in the transportation of goods and materials in a wide variety of applications. A fundamental characteristic of a forklift truck is the ability to lift and lower a load. Similarly, in order to improve efficiencies of transportation, additional load handling functions may be employed to adjust the position of the load after it has been raised. These functions, including lifting and lowering, are typically controlled by hydraulic systems that use hydraulic pressure that provides an operating force. The hydraulic system includes a pump and motor to generate the hydraulic pressure and corresponding hydraulic flow that operates mechanical devices performing the hydraulic functions.
An operator of the forklift truck is typically seated or standing in an operator cabin that includes any number of operator controls. Some of these operator controls control the hydraulic functions, including lifting and lowering the load. Other hydraulic functions may include side-shifting the load or tilting a mast, for example.
Hydraulic systems have a finite level of hydraulic fluid and hydraulic pressure that may be utilized in operating the hydraulic functions. For example, an available hydraulic fluid level may be limited by the size of a hydraulic reservoir. Similarly, the hydraulic pressure may be limited by the size of the hydraulic pump. Performance of the hydraulic functions can be reduced if the operator attempts to operate more than one hydraulic function at the same time, or the hydraulic system may instead restrict operation to one function at any given time. In either case, efficiencies of operation are negatively impacted.
The present invention addresses these and other problems associated with the prior art.
A hydraulic system may include a main hydraulic system having two or more pump motors and a second hydraulic system fluidly coupled to the main hydraulic system. A load sensing circuit detects a change in hydraulic pressure and diverts a hydraulic flow from one of the two or more pump motors to the second hydraulic system.
The foregoing and other objects, features and advantages of the invention will become more readily apparent from the following detailed description of a preferred embodiment of the invention which proceeds with reference to the accompanying drawings.
A description of a novel hydraulic system is herein provided, making reference to the aforementioned drawings and the several embodiments described further below.
It is therefore advantageous to increase functionality and performance of the forklift truck 50 by providing operator controls 60 that operate a hydraulic system more efficiently. For example, a hydraulic system may reduce cycle time by combining hydraulic functions or increasing the number of hydraulic functions that can be operated at the same time.
Accordingly, an improved hydraulic system includes a load sensing system that controls pump flow to one or more hydraulic functions in a forklift truck. Certain hydraulic functions that may be actuated concurrently are combined while maintaining desired performance levels of each function. Power regeneration is also provided when the hydraulic system returns to a state of reduced pressure.
This is described in more detail in
By way of example, some of the possible hydraulic functions that are compatible with the hydraulic system 100 of
It is noted that the simplified system diagram shown in
A different number of cylinders may be used in the main and auxiliary lift cylinder assemblies 104 and 106 due to a difference in weight between the operator cabin 55 and the attachment 65. Two cylinders may be required to lift a heavier operator cabin 55. However it is understood that fewer or less cylinders may be used for either the main or auxiliary lift cylinder assemblies 104 and 106, respectively, depending on the size of the lift cylinders and the weight of the component or load being lifted.
Hydraulic control systems 110, 120 and 130 may be fluidly connected by one or more hydraulic lines having hydraulic ports 23 and 29, however it is understood that more or fewer hydraulic lines may be used, and that
The main hydraulic control system 110 may be located in a motor compartment 85 of the forklift truck 50, as shown in
In addition, the main hydraulic control system 110 may include a maximum pressure relief valve 20 and a monometer port 21 for each hydraulic supply line, a pressure and tank port 22 for optional stabilizers 95, a pressure port 23 to supply hydraulic fluid to the second hydraulic control system 120, dual pressure ports 24 fluidly coupled to the main lift cylinder assembly 104, and pressure and tank ports 91 and 92 for the hydraulic pump and motor assemblies 46 and 47.
In addition, the second hydraulic control system 120 may include a load sensing manometer port 28, load sensing, pressure and return ports 29 to the third hydraulic control system 130, a pressure port 30 to the auxiliary lift cylinder assembly 106, and pressure ports 31 for the traverse motor 122 with preload and shock valves. Additionally, the second hydraulic control system 120 may include tapped ports 32 to manually release pressure from the traverse motor 122, a gigler valve 33, a flow compensation valve 34 for lowering the forks 75 and a pressure limiting valve 39 for the traverse motor 122.
The second hydraulic control system 120 may include additional load sensing components such as a flow compensation valve 36, a stabilizer valve 35, two flip flop valves 38 and 40, and a maximum pressure relief valve 37. The load sensing components may be collectively referred to as a load sensing circuit 93, although load sensing components may be concentrated or distributed between one or more of the hydraulic control systems 110-130 and the hydraulic and auxiliary functions.
When utilized for an additional auxiliary function 136, as shown in
The hydraulic system 100 (
If only the main lift cylinder assembly 104 is activated, then a combined hydraulic flow and pressure from both hydraulic pump and motor assemblies 46 and 47 may be utilized to lift the operator cabin 55. When a second hydraulic function is activated, then the main hydraulic control system 110 may divide the flow from the hydraulic pump and motor assemblies 46 and 47 between operating the main lift cylinder assembly 104 and the other hydraulic function. In this manner, a first pump and motor, such as hydraulic pump and motor assembly 46, may be utilized to lift the operator cabin 55. The second pump and motor, such as hydraulic pump and motor assembly 47, may be used to actuate the auxiliary hydraulic function.
The hydraulic system permits combined movements of the operator cabin 55 and the attachment 65 or forks 75 in a number of ways. The table shown in
An enabled, or open, valve in columns I-P is indicated by a box located in a respective selection square, whereas a disabled, or closed, valve is indicated by an empty selection square. For example, the selection square in column I for row 5 indicates an open valve 1, whereas the selection square in column I for row 6 indicates a closed valve 1. Similarly, the second pump “pump 2” in the pump columns identified as H is shown as being enabled in a “FWD” forward direction for row 1, and as being enabled in a “REV” reverse direction for row 2, thereby providing an example of the two bidirectional flow states that may be used. In row 3, the empty square indicates that the second pump “pump 2” is disabled. In one embodiment, “pump 1” is understood as being included in the hydraulic pump and motor assembly 46, whereas “pump 2” is understood as being included in the hydraulic pump and motor assembly 47.
Column A identifies a name of a system function to be performed, for example rows 23 and 24 indicate a fork synchronization system function. Columns B-G indicate the hydraulic functions or types of components or attachments that are involved with the system function. For example, fork synchronization system functions identified at rows 23 and 24 include hydraulic functions of Translate, identified at column D, and Rotate, identified at column E, wherein both Translate and Rotate may be in either a “LEFT” or “RIGHT” orientation.
Columns H-P indicate the pumps or valves that are utilized to perform the hydraulic functions. For example, the fork synchronization system functions at rows 23 and 24 include actuation of a second pump, “pump 2” at column 1, such as used in the pump and motor assembly 47. System functions at rows 23 and 24 further include actuation of the Translate valves 9 and 10, reference column M, and the Rotate valves 11 and 12, reference column N. Valves 9-12 are also shown with respect to the hydraulic schematic diagrams of
In general, independent movement of the operator cabin 55 through actuation of the main hoist cylinder assembly 104 may be combined with any front end attachment functions, such as lifting and lowering, translation, and rotation of the forks 75. When no front end attachment function is selected, for example in rows 1-4, then all hydraulic flow from the first and second pumps in hydraulic pump and motor assemblies 46 and 47, may be directed to the main hoist cylinder assembly 104, with selector valve 1, identified in the table as EV1 in column 1, in a closed position.
As soon as a front end attachment function is selected, for example at rows 5 and 10-68, then selector valve 1 is shifted to an open position which reroutes a pressure from the hydraulic pump and motor assembly 47 to port 23, shown in
In the system function identified at row 9 in
Similarly, in the system function identified at row 10, independent movement of the main hoist cylinder assembly 104 to lower the operator cabin 55, identified at column B, is combined with a lifting of the forks 75, identified at column C. In this case, on-off flow control valve 2, identified as “EV 2” in the Mains column J, and the infinitely positioning flow control valve 3, identified as “EV 3”, are opened to permit a lowering of the operator cabin 55, shown in
In addition, in the system function identified at row 8, independent movement of the main hoist cylinder assembly 104 to lower the operator cabin 55, identified at column B, is combined with a lowering of the forks 75, identified at column C. In this case, valves 2, 3, 4 and 7 are opened, and “Pump 1” and “Pump 2” of the hydraulic pump and motor assemblies 46 and 47 are operated in a reverse direction to permit a hydraulic return to the hydraulic reservoir 102. The variable positioning flow control valve 3, identified as “EV3” in
In one embodiment, the load sensing circuit 93 shown generally in
The load sensing circuit 93 starts with the flow compensation valve 36 positioned on the pressure line to the auxiliary lift cylinder assembly 106 and before the flow control valve 8, as shown in
The flip-flop type shuttle valves 38, 40, 41 (
The load sensing circuit 93 may be limited to a maximum operating pressure by the pressure relief valve 37 and, for example, may become active according to a minimum threshold pressure operating on a valve preload of the flow compensation valve 36. When a low hydraulic pressure is applied, the pressure relief valve 37 tends toward being open, whereas when an increasing hydraulic pressure is applied, the pressure relief valve 37 tends toward being closed in order to keep a maximum oil flow and pressure in the load sensing circuit 93. In addition, each hydraulic circuit for a given hydraulic function may include a pressure limiting valve, for example pressure limiting valves 20, 39, 42, 44 and 45. The pressure limiting valves limit the required working pressure per a given hydraulic function even if a higher pressure is called by another hydraulic function.
As mentioned, the pumps in the hydraulic pump and motor assemblies 46 and 47 may be bidirectional, and used along with an electrical circuit in the forklift truck 50 to reclaim energy from a return or sending hydraulic pressure of the operator cabin 55 when it is being lowered. Making use of the reclaimed energy may serve to reduce overall battery consumption and prolong a battery charge. Similarly, reducing the number of times a vehicle battery is charged may permit greater operating efficiencies, resulting in a reduced cycle time at no additional cost in overall energy consumption.
By utilizing bi-directional pumps in the hydraulic pump and motor assemblies 46 and 47, the hydraulic system 100 allows a return pressure from a lowering of the operator cabin 55, for example, to turn the bidirectional pumps and hence reclaim energy at the motors. The combination of movements allows for a recovery of energy whether using one or both of the hydraulic pump and motor assemblies 46 and 47, depending if combined hydraulic functions are requested. In this way, a performance of the forklift truck 50 may be improved either by using the recuperated energy to augment active hydraulic function performance levels or by sustaining moderate performance levels over a longer period of time in between battery charging operations.
Having described and illustrated the principles of the invention in a preferred embodiment thereof, it should be apparent that the invention may be modified in arrangement and detail without departing from such principles. I claim all modifications and variation coming within the spirit and scope of the following claims.
This application claims priority from U.S. Provisional Application 60/671,547, filed Apr. 14, 2005, and herein incorporated by reference.
Number | Date | Country | |
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60671547 | Apr 2005 | US |