CN1080084C - Earth digging tool assembly and its fluid pressure head assembly - Google Patents

Abstract

A soil penetrating tool assembly (10) having a tool shank (18) pivotally mounted for bypassing obstacles in the ground. Movement of the shank away from its normal position is opposed by a hydraulic ram (22). The force required to be exerted by the shank (18) to overcome the opposing force of the ram (22) is initially high but decreases when the tool (18) is scheduled to move and thus the ram (22) is scheduled to retract. This allows the tool (18) to more easily bypass large obstacles without damaging the tool (18). Two alternative valve arrangements are disclosed; one problem is in the interior of the ram (fig. 4, 10) where a plug extending within the ram cylinder cooperates with a sleeve in the ram, and an external valve (fig. 11) includes a cam that acts on a valve member in the fluid supply line. A hydraulic circuit having a pressure amplifier and a head charge bleed check valve is also disclosed.

Description

Earth digging tool assembly and its fluid pressure head assembly

technical field

The present invention relates to an improved earthmoving tool assembly, and more particularly to an assembly having the ability to avoid or jump over obstacles such as ground stumps.

Background technique

Earth-moving tool assemblies are commonly used in agriculture to break up soil for planting or other land preparation operations. Each tool assembly typically includes a shank that is sharpened at one end or is otherwise equipped with an earthmoving tool, and each shank is mounted on a cultivator frame or to a tool bar that is driven by a tractor through a The drawbar pulls and the tool bar is attached to the tractor with a three-point hitch.

It is common for the handle of each tool assembly to be loose mounted to prevent damage to the handle, frame, tool bar and/or implement handle when encountering obstacles in the soil.

Various means have been used to attach implement assemblies and handles to a cultivator frame. In one common construction, a clamping assembly is clamped or bolted to the frame with a mounting pin or bolt and a safety pin extending through each set of aligned holes, and the The handle is clamped or bolted to the clamp assembly. Where excessive obstructions or loads in the soil are encountered, the handle can pivot and cause the safety pin to break. In these and other arrangements using a safety pin system, a breakage of the safety pin necessitates stopping the prime mover and replacing the safety pin to allow tillage to resume.

Other arrangements provide a spring system in which a spring exerts a biasing force on the handle to keep the handle in the soil. However, it is generally desired that the spring be of such a size that it applies as high a force as possible to the shank to keep it in the soil. In hard compacted soils, the sufficient force required to keep the digging tines in the ground requires large and impractically sized springs.

Other systems use hydraulic rams as a means of resisting removal of the shank from the soil. These systems require large and impractical hydraulic heads to maintain penetration in hard compacted soil. The large rams and large springs also expose the digging tines and shanks to possible breaking action during the action of jumping over obstacles when the shanks and tines are in the raised, non-digging configuration. Furthermore, the spring and ram in the above arrangement are arranged to apply force to the handle in such a way that all movement of the handle is resisted by the same force. It is an object of the present invention to overcome or alleviate one or more of the many disadvantages described above, or to at least provide an alternative to an earthmoving tool assembly of the type described above. Other objects and advantages will become apparent from the following description.

Summary of the invention

One aspect of the present invention therefore provides an earthmoving tool assembly comprising:

an earth-moving tool assembly mounted to move between a lowered normal operating position and a raised position wherein said tool can clear an obstacle,

fluid head means associated with said tool, said head means comprising a hydraulic cylinder and piston means moving within said hydraulic cylinder,

hydraulic relief means associated with said ram means generally resisting movement of fluid from said ram means and thereby resisting movement of said piston means relative to the hydraulic cylinder and the tool from working positional movement, when the fluid pressure in said ram means exceeds a predetermined maximum pressure due to said tool encountering an obstacle, the hydraulic pressure relief means moves the piston means relative to the hydraulic cylinder and thereby causes the the tool moves, and

valve means inside said ram means for connecting said fluid ram means to A fluid supply source having a pressure lower than said predetermined maximum pressure.

The valve means suitably comprises a first valve member which is immovable relative to the hydraulic cylinder and a second valve member which moves with the piston means. To supply fluid from the fluid supply source, a fluid supply tube may extend longitudinally into the hydraulic cylinder, the valve means controlling communication between the tube and the hydraulic cylinder.

The cylinder of the ram unit may be connected to an end cap at the end of the cylinder opposite the piston unit. The end cap is connectable to a fluid supply and supports a fluid supply tube which suitably comprises an elongated tube which communicates with the hydraulic supply and preferably extends coaxially through the hydraulic cylinder and into the piston assembly Inside. The free end of the tube can receive the first valve part of the valve arrangement. A second valve part of the valve means is adapted to co-operate with the first valve part, which second valve part may be mounted on the piston means, and the two valve parts generally co-operate to prevent fluid from flowing into the hydraulic cylinder via the pipe. When the piston means is predetermined to move relative to the hydraulic cylinder, the first and second valve members are separated to connect the hydraulic cylinder via the tube to a supply of fluid under reduced pressure. This makes it easier to move the piston device into the hydraulic cylinder, thereby moving the tool out of its normal operating position. When the piston means returns the tool rearwardly to an operative position, the valve means defined by the first and second valve members close to close communication between the tube and the hydraulic cylinder.

The first valve member is preferably in the form of a ring or enlargement at the free end of the tube. The piston and piston rod of the piston unit are preferably hollow so that the tube extends into its interior. The second valve part carried by the piston means is preferably in the form of an annular insert within the piston and/or piston rod which is in sealing engagement with the first valve part at the end of the tube in the closed position of the valve means. The annular insert can be made of plastic. The annular insert, when subjected to fluid pressure within the hydraulic cylinder, is expandable to secure sealing engagement with the valve member at the end of the tube.

The initial resistance to movement of the piston means is preferably established by a hydraulic multiplier. The same effect can be achieved with a spring loaded valve. The hydraulic multiplier may consist of a stepped piston, the larger piston end of which is subjected to system fluid pressure and the smaller piston end generally in communication with the hydraulic cylinder so that when the piston assembly of the head unit begins to contract, it The movement at the smaller end of the piston is resisted by the multiplied fluid pressure.

The earthmoving tool of the tool assembly is preferably mounted for pivotal movement between its first and second positions. The implement assembly can most commonly be configured so that it can be mounted on a tool shaft of an agricultural implement, and for this purpose the implement assembly can include a clamping device for attaching the assembly to the implement shaft. The tool may be supported on the tool bar by a linkage which, in addition to pivoting the tool as described above, also allows the tool to be raised upwardly when the tool hits or encounters an obstacle. The linkage means may include a pivot linkage assembly pivotally mounted at one end thereof to the clamping means and pivotally supporting the handle of the tool at its opposite end. Fluid head means may be connected between the tool handle or an extension thereof and the clamping means to generally hold the tool in the ground in an operative position. The ram unit may be pivotally connected to the clamping unit and to the handle. The ram cylinder is suitably pivotally connected to the clamping device and the ram piston assembly is pivotally connected to the tool or an extension thereof. Alternatively, these connections can be reversed.

The ram means and associated hydraulic relief means enable the tool to undergo a first range of movement in its operative position. This occurs when the load on the tool is sufficient to move the piston unit within the hydraulic cylinder due to varying resistance in the ground and exceeds the safety pressure of the hydraulic pressure relief device. But when a large obstacle in the ground is encountered, a sufficient force will be applied to the tool, which will tend to cause the tool to pivot to go around the obstacle, this movement being resisted by the fluid pressure head arrangement up to the center of the tool. The fluid pressure exceeds the predetermined pressure as set by the hydraulic pressure relief device. Predetermined movement of the tool, and thus of the piston means relative to the hydraulic cylinder, causes valve means to connect the ram means to a low pressure fluid supply which enables the tool to pivot upwards more easily around obstacles. This may be done by gradual depressurization from a first predetermined pressure to lower pressures, or may be a stepped decompression.

The reduced fluid pressure in the hydraulic cylinder, as it is connected to the fluid supply, can also be used to push the tool back toward its normal operating position. During the movement of the piston means pushing the tool back towards its operating position, the valve means will close, again requiring the tool in its normal operating position to overcome the increased pressure set by the hydraulic relief means and The head assembly is moved a predetermined distance before being connected to the lower pressure fluid supply, so that it can move around large obstacles as previously described.

In order to return the piston means to its fully extended position when the tool is in an operating position, fluid is supplied to the hydraulic cylinder primarily through the tubes and open valve means. When the predetermined extension movement of the piston means brings the valve parts into alignment with each other again to close the valve means, the fluid supplied to the hydraulic cylinder can no longer be supplied through the tubes. In this case, the fluid supplied to the hydraulic cylinder is supplied through an auxiliary passage connected to the system fluid supply source. In order to reduce shock loads when the tool is returned towards the operating position, the auxiliary passage may have a reduced cross-section or include a portion of reduced cross-section so as to limit the flow to the hydraulic cylinder and thus reduce the time when the piston means returns the tool to the How fast it moves when manipulating the position.

Although it is possible to mount the tool to a tool bar via a linkage assembly as described, it is possible, if desired, to pivot the tool directly to the clamping device which clamps the tool assembly to the tool bar superior. Of course, the tool assembly may be mounted to the prime mover by any other suitable means such as by a three point linkage. The implement may be of any suitable type as required for plowing or other land work, or may include a fixed or removable tine.

In another aspect, the present invention provides an earthmoving tool assembly comprising: an earthmoving tool; support means for said tool; linkage means pivotally connected to said tool and support means, For supporting the tool to move between a lowered normal operating position and a raised position, wherein said tool can clear an obstacle; a fluid pressure head device pivotally connected between said tool and support means, the pressure a head assembly comprising a hydraulic cylinder and a piston assembly movable within the hydraulic cylinder; hydraulic pressure relief means associated with said head assembly which generally resists movement of fluid from said head assembly, and Thus resisting movement of the piston means relative to the hydraulic cylinder and movement of the tool from an operative position, when the fluid pressure in the ram means exceeds a predetermined maximum pressure due to the tool encountering an obstruction, the said hydraulic pressure relief means for moving the piston means relative to the hydraulic cylinder and thus the tool; and valve means inside said ram means for moving said tool towards a raised position to clear said obstacle, The valve means thereby connects said fluid head means to a fluid supply having a pressure below said predetermined maximum pressure when said piston means is moved beyond a predetermined distance.

In another aspect, the present invention provides a fluid ram assembly comprising: a hydraulic cylinder and a piston arrangement movable within the hydraulic cylinder; hydraulic relief means resisting movement of fluid from the fluid ram assembly , and thereby resist movement of the piston means within said hydraulic cylinder from the first position unless the fluid pressure within said ram assembly exceeds a predetermined maximum pressure; and valve means inside said ram means, when said The valve means connects the ram means to a fluid supply source having a pressure lower than said predetermined pressure for causing the piston means to move within said predetermined pressure when the piston means is predetermined to move from a first position in said hydraulic cylinder. Less restricted movement within the hydraulic cylinder from the first position.

Brief description of the drawings

In order that the present invention may be more easily understood and to produce practical effects, reference is now made to the accompanying drawings, which illustrate a preferred embodiment of the present invention, and wherein:

Figure 1 shows a tool assembly in a first operating position according to the invention;

Figure 2 shows the tool assembly of Figure 1 with the tool handle partially raised to clear an obstacle;

Figure 3 shows the tool assembly of Figure 1 with the handle assembly raised further to bypass an obstacle;

Figure 4 is a cross-sectional view of an indenter for use in the tool assembly of the present invention;

Figure 5 is a corresponding perspective cutaway view of the end block of the ram cylinder shown in Figure 4;

Fig. 6 is a schematic longitudinal sectional view of the hydraulic cylinder end block and components along the A-A direction of Fig. 5 omitting the multiplier;

Fig. 7 is a vertical sectional view along the line B-B of Fig. 6;

Fig. 8 is a sectional view along line C-C of Fig. 6;

Fig. 9 is a schematic sectional view of parts on the right side of line D-D omitted in the line B-B direction of Fig. 6;

FIG. 10 shows the ram shown in FIG. 4 in a depressurized position.

Detailed description of the embodiment

Referring to the drawings and initially to Figures 1-3, Figures 1-3 illustrate an earthmoving tool assembly 10 according to the present invention comprising a tool support 11 adapted to be mounted to a tool bar 12 And for this purpose it comprises a first fixed jaw 13 mounted to engage a pair of adjacent faces of the tool shaft 12 . A clamping plate 14 is adapted to cooperate with the tool shaft 12 and the support 11 to clamp the tool assembly 10 to the tool shaft 12 . The support 11 pivotally supports the link assembly 15 via a pivot connection 16 . Linkage assembly 15 supports at its opposite end via pivot connection 17 a tool shank 18 which may receive at its lower end an earth-moving tool 19 which may include a removable tip.

The handle 18 includes a pair of spaced apart ears 20 and on the support 11 is provided a likewise pair of spaced apart ears 21 . Extending between a respective pair of ears 20 and 21 is a hydraulic head 22 adapted to retain handle 18 in the ground. The ram 22 includes a piston assembly 23 pivotally mounted at 24 to a pair of ears 20 and a hydraulic cylinder 25 terminating in a valve block 26 pivoted at 27. It is axially mounted between the pair of ears 21 . Hydraulic fluid supplied to hydraulic cylinder 25 will therefore extend piston assembly 23 to hold handle 18 in the ground. If the handle 18 encounters an obstacle or increased load, a force will be applied to the handle 18 to pivot it upwards and rearwards as shown in FIG. 23 moves inwardly into hydraulic cylinder 25. If the force exerted by the handle 18 causes the piston assembly 23 to move a predetermined distance into the hydraulic cylinder 25, the fluid pressure in the hydraulic cylinder 25 will be partially released to allow the handle 18 to move further upwards more freely in the manner shown in FIG. Move around obstacles without the possibility of damaging handle 18 or tool 19.

In order to realize this effect, the hydraulic head 22 has the structure shown in FIG. 4 . The piston assembly 23 of the ram 22 comprises a hollow piston rod 28 fitted at one end with a piston 29 equipped with a suitable seal 30 mounted to slide inside the hydraulic cylinder 25 . On the inside of the "piston" end of the rod 28 is formed an annular shoulder 31 against which an annular insert 32 is held in place by a circlip 33. For purposes as will be described further below, the trailing end of insert 32 is circularly chamfered as at 34 .

Hydraulic cylinder 25 extends from end block 26 and is secured thereto by welding or by other connecting means, or hydraulic cylinder 25 may be integrally formed with end block 26 . A hollow tube 35 is rigidly connected to or integrally formed with the end block 26 and is mounted coaxially with the piston rod 28 and extends into the piston rod 28 and the piston 29 . The hollow tube 35 is fitted at its free end with an annular valve element 36 having an annularly chamfered end face 37 facing away from the end face 34 of the insert 32 . The valve member 36 is sealingly engaged with the insert 32 but is slidable relative to the insert 32 . The insert 32 is made of plastic and when subjected to fluid pressure in the hydraulic cylinder 25, it is pressed against the shoulder 31 so that it compresses axially and causes radial expansion to be pushed into firm engagement with the valve member 36, Thereby maintaining a seal between them.

Cooperative operation between the valve member 36 and the insert 32 provides a fluid separation between the interior 38 of the piston rod 28 and the interior 39 of the hydraulic cylinder 25 until the piston rod 23 and piston 29 move a predetermined distance into the hydraulic cylinder 25. So far, this distance is determined by the distance between the corresponding chamfered surfaces 34 and 37. When this predetermined degree of movement occurs, surface 37 moves to a position adjacent to and beyond surface 34 such that fluid communication between interior 38 of piston rod 28 and interior 39 of cylinder 25 is established as shown in FIG. 10 . This also enables communication between the interior 39 of the hydraulic cylinder 25 and the interior of the hollow tube 35 .

As mentioned above, the hollow tube 35 is connected to the end block 26 and, as shown in FIGS. Chamber 42 communicates with one side of end block 26 and is internally threaded at 43 to allow connection via hydraulic hoses to the hydraulic circuit of the prime mover or to a hydraulic accumulator. Chamber 42 communicates via a passage 44 with another chamber 45 having a first portion 46 and a second portion 47 of enlarged diameter relative to first portion 46 . A stepped piston assembly 48 (see FIG. 8 ) is disposed within chamber 45 having associated pistons 49 and 50 disposed in respective chamber portions 46 and 47 . The end 51 of the chamber portion 47 is closed with a screw-in plug, while a vent passage 52 vents the chamber portion 47 in front of the piston 50 to the atmosphere. This arrangement of piston assembly 48 within chamber 45 acts as a hydraulic multiplier as further described below.

The chamber portion 46 is additionally connected to the interior 39 of the hydraulic cylinder 25 via respective passages 53 , 54 and 55 , while the passage 55 communicates with the hydraulic cylinder 25 at 56 . Piston assembly 48 also acts as a valve, and fluid pressure in chamber portion 47 generally presses piston assembly 48 toward one end of chamber 45 (to the right as shown in FIG. 8 ), thereby blocking communication between passageway 44 and chamber portion 46. . In addition, the piston 49 is forced to the end of the chamber portion 46 to block the communication of the passage 53 with the chamber portion 46 and the passage 44 . Connected to passage 44 and passage 53 is another passage 57, which passage 57 includes a valve seat 58 on which a ball valve 59 can be mounted. Also intersecting passages 60 and 61 connect chamber portion 47 behind piston portion 50 to chamber 42 .

In use, with chamber 42 connected to a supply of hydraulic fluid, for example at 2000 pounds per square inch (psi), fluid flows to chamber portion 47 via passages 41, 61 and 60 to act on the piston assembly 48 comes up and pushes the piston assembly 48 to the right as shown in FIG. Consequently, due to the position of the piston 49 , fluid flowing into the chamber 42 is blocked from communicating with the chamber portion 46 via the passageway 44 . The graded nature of the fluid feed into chamber portion 47 through piston assembly 45 produces a multiplier pressure effect at the end of piston 49 proportional to the respective surface areas of pistons 50 and 49 . For example, if, as in this case, pistons 50 and 49 have a ratio of 3:1, the pressure seen at the end of chamber 46 is three times the pressure in chamber 47 . So in the present case, at maximum load, when the pressure in chamber portion 47 is 2000 psi, the pressure at the end of this chamber portion is 6000 psi. Since passages 53 , 54 and 55 are located inside 39 of hydraulic cylinder 25 , this pressure is also seen. When encountering an obstacle causing a force to be applied to the tool handle 18, when the applied force exceeds a predetermined value, the piston 29 will move in the direction of the end block 26 in the hydraulic cylinder 25, thus in the hydraulic pressure A pressure is developed in the cylinder 25 which in this embodiment can be up to three times the pressure of the accumulator or hydraulic system.

In operation and in the event of encountering a very high resistance, such as where the handle 18 or tool 19 encounters a large obstacle, the piston assembly 23 will resist inwardly against the fluid pressure in the hydraulic cylinder 25, as determined by the pressure. The pressure determined by the multiplier piston assembly 48. As piston 29 moves within cylinder 25 towards end block 26 against that pressure, fluid will flow through passages 55 , 54 and 53 to the end of chamber portion 46 to act on piston 49 . The piston assembly 48 will therefore be forced to move backwards. Piston assembly 48 moves when chamber portion 47 between pistons 49 and 50 is vented to atmosphere via passage 52 . Communication between chamber 46 and passage 44 opens when piston assembly 48 moves a predetermined amount such that fluid in interior 39 of hydraulic cylinder 25 flows rearwardly into the accumulator or hydraulic system. As piston 29 moves a predetermined distance, valve member 36 and insert 34 will move to a position in which surfaces 34 and 37 are spaced apart to allow fluid to flow from interior 39 of cylinder 25 into tube 35 into passage 40 . However, passage 40 is subject to depressurization through its connection via passage 41 to chamber 42, which is connected to a hydraulic accumulator or a normal fluid pressure supply, which in this case is 2000psi. This thus reduces the fluid pressure within the hydraulic cylinder 25, which enables the handle 18 to have less resistance to movement and resistance to pivoting upward in order to get around obstacles in the manner shown in FIGS. 2 and 3 .

Fluid at system pressure continues to supply the interior 39 of the hydraulic cylinder 25 through the tube 35 and through the insert 32 and the open valve member 36 to act on the face of the piston 29 . Some fluid will also be supplied from chamber 42 through valve 59 and through passages 53 , 54 and 55 to interior 39 of the hydraulic cylinder. But the fluid pressure supplied to the interior 39 of the hydraulic cylinder 25 is at reduced system pressure, in this case 2000 psi. This will thus cause the piston assembly 23 to extend from the hydraulic cylinder 25 and the ram 22 to expand to push the tool handle 18 rearwardly from the position of Figure 3 to the position of Figures 2 and 1, forcing the tool 19 into the ground. But when the piston 29 has moved a predetermined amount, the valve opening between the valve member 36 and the insert 32 will close, thereby blocking the fluid supply through the tube 35. But fluid will continue to flow from chamber 42 through passage 44 and through ball valve 59 into passages 53, 54 and 55 into interior 39 of hydraulic cylinder 25 to act on piston 29 to continue extending piston assembly 23 and thereby push tool handle 18 rearwardly. Push to the position in Figure 1.

As is evident in FIG. 5 , the ball valve chamber 57 has a valve seat 58 on which the ball 59 is seated under the bias of a spring 62 . A passage 63 connects between valve seat 58 and chamber 44 to communicate valve chamber 47 with chamber 44 . Passage 63 has a reduced diameter which limits the flow rate of fluid from chamber 44 to interior 39 of cylinder 25 through passages 53 , 54 and 55 . This will reduce the speed at which the handle 18 moves back into the ground, thus minimizing the impact loads on the handle and other components of the tool assembly 10. This overcomes a shortcoming of conventional systems where, in order to return a shank into the ground, the ram is subjected to full flow from a hydraulic circuit, which would cause the shank 18 to move quickly into the ground and create high pressure on the assembly. impact load.

Tool handle 18 is thus returned to the position of FIG. 1 and can act in the manner previously described.

In the embodiment described with reference to Figures 4-10, the fluid supply to the hydraulic cylinder is controlled by means of valve means provided in the hydraulic cylinder 25 between the valve member 36 and the insert 32. But it is also possible to control the pressure head 22 with an external valve as shown in the configuration of FIG. 11 . In this embodiment, ram 22 does not include inner tube 35 , insert 32 or valve member 36 . In order to reduce the pressure of the fluid in the hydraulic cylinder 25 when the piston assembly 23 moves a predetermined distance in the hydraulic cylinder 25, an external valve 65 is provided. In this embodiment, the valve 65 includes a valve member 66 which controls a connection Communication between a passage 67 to the hydraulic cylinder 25 and a passage 68 to a hydraulic circuit or accumulator. Valve 65 may be mounted on end block 46 containing the previously described components for creating high resistance to movement of piston assembly 23 into hydraulic press 25 through fluid pressure multiplication. An external drive member 69 is connected to piston assembly 23 at 70 and mounts a drive cam 71 for driving valve member 66 . The driver 69 is supported for sliding relative to the valve 65 by, for example, being guided in one of the bores.

When the piston assembly 23 is predetermined to move within the hydraulic cylinder, the cam 71 will contact the valve 66 and cause the valve 66 to actuate to open communication between the passage 67 and the passage 68 to connect the hydraulic cylinder 25 to the hydraulic circuit or accumulator Reduced fluid pressure. As the cam 71 is so moved, it gradually opens the valve 66 by cooperating with the valve 66 so that the hydraulic cylinder 25 is subjected to a gradually decreasing fluid pressure. The reduced pressure in the hydraulic cylinder 25 will cause the handle 18 to pivot further upward as in Figure 3, as previously described, to get around large obstacles. System hydraulic pressure supplied via passage 68 , open valve 66 and passage 67 will return handle 18 rearwardly to the position in FIG. 1 when the obstacle has been circumvented and the resistance on handle 18 is reduced. When the piston assembly 23 is moved as intended, the cam 71 will stop acting on the valve 66, so the valve 66 will close and the ram 22 will be fed rearwardly by the fluid supply through the ball valve 59 and the passages 53, 54 and 55 as previously described. Push back to its Figure 1 position. The handle 18 will then be in a position where it will be subjected to an increased counter fluid pressure in the manner previously described.

In the preferred embodiment, movement of the tool is resisted by a hydraulic ram using hydraulic fluid. However, it is also possible to counteract the movement of the tool with a pneumatic ram.

Various earthmoving tools as used in the above tool configurations can have many different designs and include single or multiple earthmoving points. Furthermore, the tool may comprise a plurality of tool handles, the movement of the handles from their operating positions being counteracted in the manner described.

All such changes and modifications are considered to be within the broad scope and scope of the invention as described herein.

Claims (31)

1. soil penetrating tool assembly, described tool assembly comprises:

A soil penetrating tool, it is mounted between normal operating position that descends and lifting position and moves, and wherein said instrument can be crossed a barrier,

With the fluid head device that described instrument links, the piston apparatus that this indenter device comprises a hydraulic cylinder and moves in this hydraulic cylinder,

The hydraulic pressure reducing device that links with described indenter device, this hydraulic pressure reducing device is generally resisted fluid moving from described indenter device, and thereby resist described piston apparatus moving and instrument moving with respect to hydraulic cylinder from an operating position, when the fluid pressure in the described indenter device surpasses predetermined maximum pressure owing to instrument runs into a barrier, this hydraulic pressure reducing device piston apparatus is moved with respect to hydraulic cylinder and therefore described instrument is moved and

Be positioned at the valve gear of described indenter device inside, when described instrument towards raised position move with cross described barrier, thus described piston apparatus be moved beyond predetermined apart from the time, this valve gear is connected to the fluid head device on the fluid supply source, and this fluid supply source has the pressure that is lower than described predetermined maximum pressure.

2. one kind according to the described soil penetrating tool assembly of claim 1, it is characterized in that, described valve gear comprises first valve member and second valve member that moves with described piston apparatus fixing with respect to hydraulic cylinder and do not move.

3. one kind according to the described soil penetrating tool assembly of claim 2, and it comprises a fluid supply line that is connected on the described fluid supply source, and this fluid supply line longitudinal extension enters hydraulic cylinder, and described valve gear is controlled the connection between this pipe and the hydraulic cylinder.

4. one kind according to the described soil penetrating tool assembly of claim 3, it is characterized in that described pipe has a free end in hydraulic cylinder, and the free end of this pipe is installed first valve member of described valve gear; And second valve member of this valve gear is fit to and the first valve member co-operating.

5. one kind according to the described soil penetrating tool assembly of claim 4, it is characterized in that, described piston apparatus moves with respect to hydraulic cylinder predetermined and makes described two valve members move to become mutually not line up, so as to make fluid from described fluid provider through this pipe inflow hydraulic cylinder.

6. one kind according to the described soil penetrating tool assembly of claim 5, it is characterized in that described first valve member comprises an annular element or amplifier section at the free end of this pipe.

7. one kind according to the described soil penetrating tool assembly of claim 6, it is characterized in that described piston apparatus is hollow, so that hold the free end of described pipe; And described second valve member comprises a ring plugin in this hollow piston device.

8. one kind according to the described soil penetrating tool assembly of claim 7, it is characterized in that described ring plugin is made of plastic, when valve gear cuts out, just expand into and the described first valve member sealed engagement when this plug-in unit is subjected to fluid pressure action in the hydraulic cylinder.

9. one kind according to the described soil penetrating tool assembly of claim 8, it is characterized in that, described hollow piston device comprises a hollow piston bar, and this bar is installed a piston that moves in described hydraulic cylinder, and described hollow piston bar holds the free end of described fluid supply line.

10. one kind according to the described soil penetrating tool assembly of claim 1, it is characterized in that described hydraulic pressure reducing device comprises a hydraulic multiplier, and this hydraulic multiplier is connected on the described fluid supply source.

11. one kind according to the described soil penetrating tool assembly of claim 10, it is characterized in that, described hydraulic multiplier comprises a stepped piston, it has a bigger piston end and a less piston end, this bigger piston end is subjected to the effect of described fluid supply pressure, and less piston end is communicated with described hydraulic cylinder.

12. one kind according to the described soil penetrating tool assembly of claim 11, it is characterized in that, described fluid supply source is connected to described hydraulic cylinder by additional access device in addition, this access device has an area that reduces in order to limit the flow that flows to described hydraulic cylinder after closing when valve gear, returns described operating position with the speed that reduces when crossing a described barrier with convenient instrument.

13. one kind according to the described soil penetrating tool assembly of claim 1, it is characterized in that, described instrument is mounted to that pivoting moves between its decline and lifting position.

14. one kind according to the described soil penetrating tool assembly of claim 13, it also comprises erecting device, is used for described tool assembly is installed to a tool bar.

15. one kind according to the described soil penetrating tool assembly of claim 14, it is characterized in that described instrument is bearing on the described erecting device by linkage.

16. one kind according to the described soil penetrating tool assembly of claim 15, it is characterized in that described linkage comprises a pivoting link assembly, it at one end pivoting be installed on the described erecting device, and support described instrument at its opposite end pivoting.

17. the soil penetrating tool assembly according to claim 16 is characterized in that, described fluid head device is connected between described instrument and the erecting device.

18. one kind according to the described soil penetrating tool assembly of claim 3, it comprises an end cap in the end of described hydraulic cylinder, and described end cap supports described fluid and supplies with source capsule and this fluid is supplied with source capsule and be connected on the fluid supply source.

19. a soil penetrating tool assembly, this tool assembly comprises: a soil penetrating tool; The supporting arrangement that is used for this instrument; Linkage, its pivoting are connected on the supporting arrangement of described instrument and this instrument of supporting, are used for moving between the normal operating position of a decline and a lifting position, and wherein said instrument can be crossed a barrier; Fluid head device, its pivoting are connected between described instrument and the supporting arrangement, and this indenter device comprises a hydraulic cylinder and a piston apparatus that moves in this hydraulic cylinder; The hydraulic pressure reducing device that links with described indenter device, this hydraulic pressure reducing device is resisted fluid moving from described indenter device usually, and thereby resist described piston apparatus moving and the described instrument of opposing moving with respect to hydraulic cylinder from operating position, when the fluid pressure in the described indenter device surpassed a predetermined maximum pressure owing to this instrument runs into a barrier, this hydraulic pressure reducing device made described piston apparatus move with respect to hydraulic cylinder and therefore this instrument is moved; With the valve gear that is positioned at described indenter device inside, when described instrument move towards the position of a rising with cross described barrier, thus this piston apparatus be moved beyond one predetermined apart from the time, described valve gear is connected to the fluid head device on the fluid supply source, and this fluid pressure source has the pressure that is lower than described predetermined maximum pressure.

20. a fluid head assembly, this pressure head component comprises: a hydraulic cylinder and a piston apparatus that moves in this hydraulic cylinder; Hydraulic pressure reducing device, its opposing fluid moves from described fluid head assembly, and thereby the opposing hydraulic cylinder in piston apparatus from the moving of primary importance, the fluid pressure in described indenter device surpasses a predetermined maximum pressure; With the valve gear that is positioned at described indenter device inside, when described piston apparatus predetermined when mobile from primary importance in hydraulic cylinder, this valve gear is connected to described fluid head device on the fluid supply source, this fluid supply source has the pressure that is lower than described predetermined pressure, so that piston apparatus moves more without restriction from this primary importance in hydraulic cylinder.

21. one kind according to the described fluid head assembly of claim 20, it is characterized in that, described valve gear comprises that first valve member of fixing with respect to described hydraulic cylinder and not moving and one are fixed into second valve member that moves with described piston apparatus.

22. one kind according to the described fluid head assembly of claim 21, it comprises a fluid supply line that is connected on the described fluid supply source, this fluid supply line extends longitudinally and enters described hydraulic cylinder, and described valve gear is controlled being communicated with between described pipe and the hydraulic cylinder.

23. one kind according to the described fluid head assembly of claim 22, it is characterized in that described pipe has a free end in hydraulic cylinder, this end is installed first valve member of described valve gear; And second valve member of described valve gear is installed on the described piston component, so that move and suitable and the described first valve member co-operating thereupon.

24. one kind according to the described fluid head assembly of claim 23, it is characterized in that, predetermined when mobile when described piston component, described two valve members are moved into mutually and do not line up, and make fluid flow into the described hydraulic cylinder by this valve member from described fluid supply source.

25. one kind according to the described fluid head assembly of claim 22, it is characterized in that described first valve member comprises an annular element or amplifier section at the free end of described pipe.

26. one kind according to the described fluid head assembly of claim 25, it is characterized in that described piston apparatus is hollow, so that hold the free end of described pipe; And described second valve member comprises a ring plugin in described hollow piston device.

27. one kind according to the described fluid head assembly of claim 26, it is characterized in that, described ring plugin is made of plastic, when described valve gear cuts out, just expand into and the first valve member sealed engagement during fluid pressure action of described plug-in unit in being subjected to hydraulic cylinder.

28. one kind according to the described fluid head assembly of claim 27, it is characterized in that, described hollow piston device comprises a hollow piston rod, and this piston rod is installed a piston that moves in described hydraulic cylinder, and described hollow piston rod holds the free end of fluid supply line.

29. one kind according to the described fluid head assembly of claim 21, it is characterized in that described hydraulic pressure reducing device comprises a fluid pressure multiplier, it is connected on the described fluid supply source.

30. one kind according to the described fluid head assembly of claim 29, it is characterized in that, described fluid pressure multiplier comprises a stepped piston, this stepped piston has a bigger piston end and a less piston end, this bigger piston end is subjected to the effect of described fluid supply pressure, and less piston end is communicated with described hydraulic cylinder.

31. one kind according to the described fluid head assembly of claim 30, it is characterized in that, described fluid supply source is connected on the described hydraulic cylinder by additional access device, this access device has an area that reduces, so that close the flow that the back restriction flows to described hydraulic cylinder at described valve gear, so that described piston apparatus is with the described primary importance of speed back of a reduction.

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