IE20100600A1 - Hydraulically-operated tipping-bodied vehicle - Google Patents
Hydraulically-operated tipping-bodied vehicle Download PDFInfo
- Publication number
- IE20100600A1 IE20100600A1 IE20100600A IE20100600A IE20100600A1 IE 20100600 A1 IE20100600 A1 IE 20100600A1 IE 20100600 A IE20100600 A IE 20100600A IE 20100600 A IE20100600 A IE 20100600A IE 20100600 A1 IE20100600 A1 IE 20100600A1
- Authority
- IE
- Ireland
- Prior art keywords
- tipping
- hydraulic cylinder
- hydraulic
- vehicle according
- bodied
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 16
- 230000005484 gravity Effects 0.000 claims abstract description 9
- 230000000694 effects Effects 0.000 claims abstract description 3
- 230000000452 restraining effect Effects 0.000 claims description 5
- 239000010720 hydraulic oil Substances 0.000 description 26
- 239000000463 material Substances 0.000 description 8
- 238000009958 sewing Methods 0.000 description 3
- 230000037396 body weight Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000002301 combined effect Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000000135 prohibitive effect Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
- B60P1/00—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading
- B60P1/04—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element
- B60P1/16—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element actuated by fluid-operated mechanisms
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
- B60P1/00—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading
- B60P1/04—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element
- B60P1/16—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element actuated by fluid-operated mechanisms
- B60P1/162—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element actuated by fluid-operated mechanisms the hydraulic system itself
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The present invention relates to a hydraulic tipping arrangement for raising and lowering the tipping body of a tipping-bodied vehicle, the vehicle including a first hydraulic cylinder for pushing the tipping body from a lowered position to a raised position and a second hydraulic cylinder to assist gravity in pulling the tipping body from the raised position to the lowered position, the first and second hydraulic cylinders being in fluid communication such that fluid emptied from one cylinder effects filling of fluid into the other and vice versa.
Description
Background of the invention The tipping body is the tippable container part of a tipping-bodied vehicle.
The container normally has its rear end pivoted at the rear end of the vehicle for rotation about an axis transverse to the front-to-rear direction of the vehicle. This allows the front end of the container to be raised (and subsequently lowered) by rotation of the container about the pivot axis, so that the container can be tilted rearwardly to allow discharge of a contained load by gravity through an opening at the rear of the container. This raising/tilting action is generally achieved by the use of hydraulic cylinder(s).
The invention applies to tipping bodies associated with, for example, trucks, semi-trailer trucks, agricultural and other trailers, all collectively referred to herein as "vehicles".
For example, Figures 1 and 2 are diagrammatic side views of a typical prior art agricultural trailer with a tipping body. The trailer comprises a main trailer chassis 10 with ground wheels 12 and a drawbar 14 at the front for hitching to a tractor. The tipping body comprises a container 16 mounted on an independent container chassis 18 and its rear end is pivoted by hinges 20 to the rear end of the trailer chassis 10 for rotation of the container about a horizontal transverse axis. In Figure 1 the container is shown in transport (lowered) position in which the container chassis 18 lies horizontally on the main trailer chassis 10, and in Figure 2 the container is shown in tipped (raised) position. The tipping operation is performed by a push-type single- acting multi—stage telescopic hydraulic cylinder 22 which is located under the container 16 and is connected at its top end to the container chassis 18 and at its bottom end to a cross member located directly behind the rear end of the drawbar 14.
In tipping-bodied vehicles such as the tractor trailer shown in Figures 1 and 2 the tipping operation is usually performed using one or two push-type single- acting multi-stage telescopic hydraulic cylinders that are located under the tipping body. One end of the, or each, hydraulic cylinder is connected. to the vehicle chassis, or to a member connected to the vehicle chassis, and the other end of the hydraulic cylinder is connected to the tipping body chassis or other part of the tipping body. The operation of such hydraulic tipping cylinders is achieved by connecting the cylinder by a hydraulic hose to a hydraulic valve that is located on the agricultural tractor that is deployed to tow the trailer, and operating the valve accordingly. Where two hydraulic cylinders are used, they are normally disposed parallel to one another on opposite sides of the vehicle and are operated in synchronism. In the rest of this specification, only one push-type hydraulic cylinder is shown, but in each case it is to be understood that two or more may be present and operated in synchronism with the first.
The speed of rotating the tipping body upwardly to the tipped position is dependent upon the net upward force resulting from the combination of the upward force derived from the lifting effort of the hydraulic tipping cylinder(s) on the body and the downward force exerted upon the tipping cylinder(s) due to the weight of the tipping body and any material contained within the body. Factors influencing the hydraulic lifting effort are the hydraulic oil pressure within the hydraulic cylinder that is derived from the performance of the vehicle's hydraulic pump, and the area of the piston within the hydraulic cylinder upon which pressurised hydraulic oil acts. It therefore follows that the deployment of larger sized hydraulic cylinders with associated larger pistons results in a greater speed of body raising for any particular hydraulic oil pressure and body weight.
The tipping body is returned to the transport mode by removing the hydraulic pressure applied by the hydraulic pump so that the weight of the body and any material remaining within it causes the piston within the hydraulic cylinder to pressurise the hydraulic oil in the cylinder which results in the return flow of the hydraulic oil to the vehicle hydraulic oil reservoir when the controlling valve is operated to accommodate this return flow.
The speed of lowering is determined by the rate of return flow of the hydraulic oil, which is directly related to the pressure of the hydraulic oil, which is dependent in turn upon the weight of the tipping body and any material contained within the body and the area of the piston within the hydraulic cylinder, together with the volume of hydraulic oil to be returned to the tractor hydraulic oil reservoir. It therefore follows that the deployment of larger sized hydraulic cylinders with associated larger pistons results in both a greater volume of hydraulic oil to be returned to the tractor hydraulic oil reservoir and a reduced hydraulic oil pressure which results in a reduced rate of hydraulic oil return flow for any particular body weight when in lowering mode. The combined effect is a greater volume of hydraulic oil returning at a reduced rate of flow that results in a ‘double negative’ disadvantage in terms of speed of body lowering. It is for this reason that the benefits of deploying larger hydraulic cylinders to achieve speedier body raising are somewhat negated by the aforementioned disadvantages in respect of the speed of body lowering.
The compressive force exerted on the hydraulic cylinder by the weight of the body reduces as the body is raised, eventually reaching zero when the centre of gravity of the tipping body and any material contained therein is vertically above the pivot axis. If the body could continue to rotate beyond this point lE10060i0 4 under the influence of gravity, the body would overbalance and a pull or tensile force would be exerted on the hydraulic cylinder and it would not be possible to lower the tipping body by means of a push-type single acting hydraulic cylinder. To avoid this the maximum extent of body raising is limited to a position before the overbalance point - this also avoids a very slow lowering speed at the commencement of lowering from the fully tipped position.
Tipping cycle times are influenced by the rate of body raising and body lowering but also by the maximum angle of tip. The friction between a tipping body and the material contained within that body is more easily overcome when a greater maximum angle of tip is achieved, and once this friction has been overcome the discharge rate of the material from the tipping body is greater when the maximum angle of tip is greater. However the benefits of a greater maximum angle of tip in providing speedier discharge of material from the tipped body is negated by the aforementioned slower body lowering speeds associated with a greater maximum angle of tip. It is therefore often necessary to shunt a tipped tipping body in a sudden forward motion followed by sudden application of the wheel brakes to achieve overcoming the friction between the tipping body and the material contained within the body. This sudden movement action can be unsafe due to the height of the centre of gravity of the tipped body and load and also results in dynamic stresses being imposed upon the extended hydraulic cylinders, the tipping body and vehicle.
It would therefore be desirable to use larger sized hydraulic cylinders to achieve speedier body raising together with having a greater maximum angle of tip if the disadvantages of both of these measures in respect of the body lowering could be overcome. One means of overcoming these disadvantages would be to deploy double-acting (i .e. pushl pull) hydraulic cylinders for performing the tipping actions. Traditionally it has been necessary to deploy multi—stage telescopic hydraulic cylinders for body tipping to avoid the use of very large single-stage hydraulic cylinders with very large pistons in order to lE1006oo avoid the pistons buckling under the compressive forces experienced during body raising. Whilst it is possible to manufacture double-acting telescopic hydraulic cylinders, the cost of manufacture and maintenance is prohibitive.
Such hydraulic cylinders are more suited to deployment within stationary machinery applications rather than mobile machinery where dynamic stresses result from the motion associated with mobile machinery.
It is an object of the invention to provide a hydraulically~operated tipping- bodied vehicle which avoids or mitigates the above disadvantages.
Summary of the invention According to the present invention there is provided a tipping-bodied vehicle including a first hydraulic cylinder for pushing the tipping body from a lowered position to a raised position and a second hydraulic cylinder to assist gravity in pulling the tipping body from the raised position to the lowered position.
Preferably, the second hydraulic cylinder is a single-acting single-stage pull- type hydraulic cylinder.
Preferably, the second hydraulic cylinder is a double-acting hydraulic cylinder operating in pull mode to assist in lowering the body.
Preferably, the first hydraulic cylinder is a single-acting multi-stage push-type hydraulic cylinder.
Preferably, one end of the second hydraulic cylinder is connected to the vehicle by a shearable connection.
Preferably, the tipping-bodied vehicle comprises restraining means for restraining the disconnected hydraulic cylinder from freely rotating about the remaining connected end as a result of failure of the shearable connection.
Preferably, the first and second hydraulic cylinders are in fluid communication such that fluid emptied from one cylinder effects filling of fluid into the other and vice versa.
Preferably, the tipping-bodied vehicle comprises a hydraulic double-acting spool valve connecting the first and second hydraulic cylinders in fluid communication with one another.
Preferably, the tipping-bodied vehicle comprises a pressure reducing valve in operative association with the second hydraulic cylinder and operable to limit the working pressure of fluid sewing the second hydraulic cylinder.
Preferably, the tipping-bodied vehicle comprises a hydraulic pressure relief valve in operative association with the second hydraulic cylinder, the pressure relief valve being operable to open upon a predetermined oil pressure being reached within the second hydraulic cylinder Preferably, the tipping-bodied vehicle comprises a hydraulic non-return valve in operative association with the pressure relief valve and operable to permit the unidirectional flow of hydraulic fluid from the second hydraulic cylinder, through the pressure relief valve, to the first hydraulic cylinder.
Preferably, the tipping-bodied vehicle comprises a floating connection via which one end of the second hydraulic cylinder is connected to the vehicle.
As used herein, the term “hydraulic cylinder” is intended to cover any fluid powered cylinder such as a liquid powered cylinder, for example using oil as iE1oosoo the drive medium, or a gas powered cylinder, for example using air as the drive medium.
Brief description of the drawings Embodiments of the invention will now be described, by way of example, with reference to the accompanying drawings, in which: Figures 1 and 2, previously described, are diagrammatic side views of a typical prior art agricultural trailer with a tippable container.
Figure 3 is a diagrammatic side view of an agricultural trailer embodying the invention with its tippable container in its lowered position.
Figures 4 and 5 are diagrammatic side views of the trailer of Figure 3 during raising and lowering of the container respectively, also showing the hydraulic circuit.
Figure 6 is a diagrammatic side view of a truck embodying the invention with its tippable container in its lowered position.
Figure 7 is a diagrammatic side view of the truck of Figure 6 with the container raised.
Detailed description of the drawings An agricultural trailer according to a first embodiment of the invention is shown in Figures 3 to 5. This trailer is largely the same as that shown in Figures 1 and 2, and the same reference numerals have been used for parts that are the same or equivalent to parts in Figures 1 and 2. However, isioosoo 3 significantly, the trailer differs from that of Figures 1 and 2 by the provision of a second hydraulic cylinder 24 extending between the main chassis 10 and the container chassis 18. in this embodiment the second cylinder 24 is a single-acting single-stage pull—type hydraulic cylinder and is located rearwardly of the first (push-type) cylinder 22. The first hydraulic cylinder 22 operates as before to push the container 16 from its lowered position to its raised position. However, the second hydraulic cylinder 24 is used to assist gravity to pull the container 16 downwardly from the raised position to the lowered position.
Figures 4’ and -5 shows‘t'he operation of the hydraulic circuit while the container 16 is being raised and lowered respectively. The hydraulic circuit comprises a hydraulic spool valve 26 (mounted on the tractor) having ports A and B. A hydraulic line 28 connects port A to the hydraulic cylinder 24, and a hydraulic line 30 connects port B to the hydraulic cylinder 22.
During the operation of raising the container 16, Figure 4, pressurised hydraulic oil exits from port B and extends the push-type telescopic hydraulic cylinder 22 in normal manner. This raises the container 16 and extends the pull-type hydraulic cylinder 24 which results in hydraulic oil returning from this hydraulic cylinder to port A. The direction of movement of the hydraulic cylinders is indicated by the arrows 32, while the direction of hydraulic oil flow is indicated by the arrows 34.
During the lowering of the container 16, Figure 5, pressurised hydraulic oil exits from port A to retract the pull-type cylinder 24. This exerts a pull force on the container 16, thus speeding up the lowering action compared to using gravity alone and causing a speedier return of hydraulic oil from push-type cylinder 22 to port B. Again, the direction of movement of the hydraulic cylinders is indicated by the arrows 32, while the direction of hydraulic oil flow is indicated by the arrows 34. lE100600 9 It should be understood that whilst only one second hydraulic cylinder 24 is shown that two or more may be present and operated in synchronism with the first hydraulic cylinder 22.
Figures 6 and 7 show a truck embodying the invention. In these figures the same reference numerals have been used for parts which are the same or equivalent to parts in Figures 3 to 5.
Figures 6 and 7 are largely self-explanatory based on the preceding description, the only significant difference being that the vehicle chassis 10' is now integral with the driver's cab..36. (which is mounted on it) rather than being a separate towable part. Figures 6 and 7 also show an alternative position for the push-type single—acting multi-stage telescopic hydraulic cylinder, which is shown at 22‘ at the front of the container 16 rather than being of underbody type 22. The hydraulic circuit is the same as for the preceding embodiment. in both embodiments it is advantageous to have one end of the single-acting single-stage pull-type hydraulic cylinder 24 connected to the relevant vehicle element by means of a shear bolted bracket type connection. Such a shearable connection will allow the relevant end of the hydraulic cylinder 24 to become disconnected by shearing the connection if any of the relevant hydraulic hoses are not connected to the spool valve, rather than risking damage to the cylinder. In such a case it is also advantageous to have a means of restraining the disconnected hydraulic cylinder from freely rotating about the remaining connected end as a result of failure of the shearable connection, to avoid the hydraulic cylinder coming into contact with any moving part of the vehicle or touching ground. A cross-member or chain/strap, etc. would be a suitable means of achieving this objective.
An alternative to the shear bolted bracket type connection (shearable connection) on one end of the single-acting single-stage pull-type hydraulic lE100600 cylinder 24 is the provision of a connection (not shown) between the hydraulic lines 28, 30 which serve each hydraulic cylinder, this connection to incorporate a hydraulic pressure relief valve (not shown) and a hydraulic non- return valve (directional valve). The hydraulic pressure relief valve can be utilised to open upon the occurrence of any excessively high hydraulic oil pressure within the second hydraulic cylinder 24 and associated hydraulic feed line 28 thus directing the hydraulic oil flow to the hydraulic line 30 sewing the first hydraulic cylinder 22. The non-return valve (directional valve) serves to inhibit any hydraulic oil flow in the opposite direction (i.e. from the hydraulic line 30 serving the first hydraulic cylinder 22 to the hydraulic line 28 serving the second cylinder 24.
The working hydraulic oil pressure within the hydraulic line 28 sewing the second hydraulic cylinder 24 may also be limited by use of a hydraulic pressure reducing valve (not shown). This facilitates control of the force exerted by the second hydraulic cylinder 24 and hence the rate of tipping body lowering and hydraulic oil return flow rates from the first hydraulic cylinder 22.
A slot profile opening rather than the normal circular profile opening can be provided on the brackets (not shown) connecting one end of the second hydraulic cylinder 24 to either the trailer/vehicle chassis 10 or container 16.
This provides for a completion of retraction of the second hydraulic cylinder 24 prior to the container 16 being fully lowered and the resulting floating connection arrangement allows the fully retracted second hydraulic cylinder 24 to move with a degree of freedom at the relevant connecting location until the container 16 reaches the fully lowered position, thus avoiding the container 16 impacting upon its resting location with any increased intensity.
Some of the advantages provided by the invention are as follows: iE1ooaoo - Less stress on the hydraulic cylinders and vehicle during the tipping operation thus reducing maintenance and repair costs and reducing associated downtime together with extending the vehicle life expectancy.
Greater efficiency and productivity due to reduced tipping cycle time hence facilitating reduced turn-around times.
Speeding up the tipping operation allows subsequent machine operations (e.g. further loading or filling being undertaken by another machine) to be undertaken more quickly thus increasing the efficiency of these subsequent machines by reducing the "idle time associated with waiting for the tipping operation to be completed. - _Safer tipping operations with the potential for reduced downtime and costs normally associated with incidentsl accidents.
The invention facilitates the use of ‘general purpose’ tipping trailers for roles previously only associated with other trailer types, e.g. dump trailers which have higher body maximum tipping angles.
Claims (12)
1. A tipping-bodied vehicle including a first hydraulic cylinder for pushing the tipping body from a lowered position to a raised position and a second hydraulic cylinder to assist gravity in pulling the tipping body from the raised position to the lowered position.
2. A tipping-bodied vehicle according to claim 1 in which the second hydraulic cylinder is a single-acting single-stage pull-type hydraulic cylinder.
3. A tipping-bodied vehicle according to claim 1 in which the second hydraulic cylinder is a double—acting hydraulic cylinder operating in pull mode to assist in lowering the body.
4. A tipping-bodied vehicle according to any preceding claim in which the first hydraulic cylinder is a single—acting multi~stage push-type hydraulic cylinder.
5. A tipping-bodied vehicle according to any preceding claim in which one end of the second hydraulic cylinder is connected to the vehicle by a shearable connection.
6. A tipping-bodied vehicle according to claim 5 comprising restraining means for restraining the disconnected hydraulic cylinder from freely rotating about the remaining connected end as a result of failure of the shearable connection.
7. A tipping-bodied vehicle according to any preceding claim in which the first and second hydraulic cylinders are in fluid communication such that fluid emptied from one cylinder effects filling of fluid into the other and vice versa.
8. A tipping-bodied vehicle according to any preceding claim comprising a hydraulic double-acting spool valve connecting the first and second hydraulic cylinders in fluid communication with one another.
9. A tipping-bodied vehicle according to any preceding claim comprising a pressure reducing valve in operative association with the second hydraulic cylinder and operable to limit the working pressure of fluid serving the second hydraulic cylinder.
10. A tipping-bodied vehicle according to any preceding claim comprising a hydraulic pressure relief valve in operative association with the second hydraulic cylinder, the pressure relief valve being operable to open upon a predetermined oil pressure being reached within the second hydraulic cyunder
11. A tipping-bodied vehicle according to claim 10 comprising a hydraulic non-return valve in operative association with the pressure relief valve and operable to permit the unidirectional flow of hydraulic fluid from the second hydraulic cylinder, through the pressure relief valve, to the first hydraulic cylinder.
12. A tipping-bodied vehicle according to any preceding claim comprising a floating connection via which one end of the second hydraulic cylinder is connected to the vehicle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| IE20100600A IE20100600A1 (en) | 2009-09-22 | 2010-09-20 | Hydraulically-operated tipping-bodied vehicle |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| IE20090731 | 2009-09-22 | ||
| IE20100600A IE20100600A1 (en) | 2009-09-22 | 2010-09-20 | Hydraulically-operated tipping-bodied vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| IE20100600A1 true IE20100600A1 (en) | 2011-04-13 |
Family
ID=43065448
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| IE20100600A IE20100600A1 (en) | 2009-09-22 | 2010-09-20 | Hydraulically-operated tipping-bodied vehicle |
Country Status (2)
| Country | Link |
|---|---|
| GB (1) | GB2473742A (en) |
| IE (1) | IE20100600A1 (en) |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB681997A (en) * | 1949-08-08 | 1952-11-05 | Anthony Co | Improvements in and relating to tipping vehicles and the like |
| JP4234893B2 (en) * | 2000-09-12 | 2009-03-04 | 株式会社小松製作所 | Cylinder operation control device |
| JP4917617B2 (en) * | 2007-02-16 | 2012-04-18 | 日立建機株式会社 | Transport vehicle |
-
2010
- 2010-09-20 GB GB1015646A patent/GB2473742A/en not_active Withdrawn
- 2010-09-20 IE IE20100600A patent/IE20100600A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| GB2473742A (en) | 2011-03-23 |
| GB201015646D0 (en) | 2010-10-27 |
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