CUTTER FOR A BORING HEAD

Abstract: The present invention relates to a cutter (10) for a boring head, preferably a boring head for shaft drilling, wherein the cutter (10) is rotatably mounted, via a shaft (12) of the cutter (10), in a saddle secured to the boring head. Bearings (18, 20) are provided between the shaft (12) and an outer roller body (16) of the cutter (10) to make it possible for the roller body (16) to rotate relative to the shaft (12). Seals (33) are disposed between the shaft (12) and the roller body (16) and channels/bores (38, 48, 50, 66) are provided to introduce lubrication internally into the cutter (10). The shaft (12) has a center axis (14). The invention is characterized in that a device (70) for positioning of spacer means (42, 44), a lubrication channel (66) and a diaphragm (60) are provided in the shaft (12), substantially concentrically with the center axis (14), said device, channel and reservoir being provided to accommodate lubrication. The invention further relates to a method for filling a lubrication system.

Description: Cutter for a boring head Prior art The present invention relates to a cutter for a boring head, preferably a boring head for shaft drilling, wherein the cutter is rotatably mounted, via a shaft of the cutter, in a saddle secured to the boring head and wherein bearings are provided between the shaft and an outer roller body of the cutter to make it possible for the roller body to rotate relative to the shaft, wherein seals are disposed between the shaft and the roller body and channels/holes are provided to introduce lubrication into the bearings. The invention further relates to a method for filling a lubrication system. When cutters of the type mentioned above are working it is necessary that the bearings are embedded in a lubricant, preferably grease, i.e. the space between the shaft and the cutter is filled with grease. This is done in order to minimize the friction when the roller body is rotated relative to the shaft. By having a low internal friction in the bearings, the life of the cutter is kept at an acceptable level. However, it has turned out that under very tough working conditions, i.e., when the cutter is subjected to a heavy load, much heat is generated by rotation of the roller body relative to the shaft and by friction as the cutter works the rock. Due to the heat generation the grease expands and the internal pressure of the cutter rises. Under such conditions it occasionally happens that the internal pressure of the cutter reaches a level where the seal means are not able to withstand said internal pressure, i.e., the seals collapse and the grease emerges from the bearings. It is readily understood that if the seals collapse then the cutter will rapidly breakdown. From DE-PS 27 42 01 9 a cutter for a tunnel boring machine is previously known, the cutter being equipped with pressure relief valves connected to certain ends of the internal grease passages. Other ends of the internal grease passages are equipped with nipples for introducing grease into the internal grease passages. The function of the pressure relief valves is to allow passage of excessive grease both when grease is primarily introduced into the interior of the cutter as well as when regreasing of the cutter is effected. However, if the cutter according to DE-PS 27 42 019 is subjected to heavy loads and consequently a thermal expansion of the grease takes place, the pressure will increase until the pressure relief valves open. Thus, it is absolutely necessary that the valves function properly to avoid damages primarily to the seals and subsequently to the bearings. It is well known that the working conditions of cutters are extremely tough and that a considerable amount of dirt/cuttings adhere to the cutter. Therefore, there is considerable risk that the pressure relief valves become clogged and consequently do not open at their nominal pressure. Other prior art devices of this kind are often subjected to disadvantages such as it not being possible to refill additional grease after a period of use of the cutter or it being impossible to avoid air pockets during refill, whereby the air content in the grease system can be up to 15%. Objects of the present invention An object of the present invention is to provide a cutter with pressure compensation that can be used under extreme tough working conditions, when the cutter is surrounded by fluid which pressurizes the seals in the cutter and when heat is generated inside the cutter and the grease expands. Another object of the present invention is to provide an effective method to fill a grease system with grease to obtain a maximum coefficient of fullness, i.e. a minimum of air bubbles will remain in the system after filling. These and other objects of the present invention are realized by a cutter, a holder and a method that have been given the characteristics of the appended claims. Short description of the drawings Below, an embodiment of the cutter according to the present invention is described, reference being made to the accompanying drawings, wherein: Fig. 1 shows a cross-section through a cutter when grease is introduced in and in the vicinity of the bearing races of the cutter; Fig. 2 shows a cross- section through a cutter according to the invention when grease is introduced centrally into the cutter; Fig. 3 shows a cross-section through a flexible diaphragm of the cutter and Fig. 4 shows a cross-section through a cutter according to the invention, in an active position. Detailed description of the invention The cutter 10 according to Fig. 1 includes a shaft 12 having a longitudinal center axis 14. The ends 12A and 12B of the shaft 1 2 is to be mounted in a saddle (not shown), which is secured to the boring head. A roller body 16 is rotatably mounted on the shaft 12 via two sets of bearings 18 and 20, respectively. The bearings 18 are received in a first circumferential groove 22 formed in an outer periphery of the shaft 12, while the bearings 20 are received in a second circumferential groove 24 formed in an inner periphery of the roller body 16. The roller body 16 is locked axially relative to the shaft 12 by locking means 26, preferably including an annular row of balls 26 disposed in cooperating with third and fourth circumferential channels or grooves 28 and 30, formed respectively in the shaft 12 and in the roller body 16. Between the axial ends of the roller body 16 and the shaft 12, the cutter 10 is provided with seal retainer means 32 supporting seals 33 that prevents grease from leaking out from the interior of the cutter 10. Both seal retainer means 32 are equipped with first relief holes 34 in which conical plugs 36 are mounted to prevent grease from leaking out through the holes 34. The function of the first relief holes 34 is explained more in detail below. The cutter 10 according to Fig. 1 is provided with an axial bore 38 that extends from one end 12B of the shaft 12, i.e., in the disclosed embodiment from the end of the shaft 12 where the roller body 16 has its smallest diameter. The axial bore 38 extends about halfway of the length of the shaft 12. In the vicinity of the inner end of the bore 38, a generally radial bore 40 extends from the axial bore 38 to the third groove 28. The bore 40 is used to install the balls of the locking means 26. When the balls have been installed, a ball plug 42 and a spacer plug 44 are mounted in the bore 40. The plugs 42 and 44 together extend between the balls of the locking means 26 and a filling plug 46, which is inserted into the axial bore 38 by a slide fit. For access reasons the filling plug 46 extends out of the bore 38 and is provided with a grease nipple 47 and an internal axial feeding hole 49 that extends from the nipple 47 to the opposite end portion of the filling plug 46. A radially extending discharge hole 51 emanates from the feeding hole 49 and perforates the envelope surface of the filling plug 46. The ball plug 42 is provided with two axially extending holes 48 which are offset from the longitudinal center axis of the ball plug 42, while the spacer plug 44 is provided with one axially extending central hole 50. The reason why the holes 48 of the ball plug 42 are offset from the axis of the plug 42 is to prevent the area of contact between the balls of the locking means 26 and the ball plug from blocking the entry of grease into the locking means 26 and further into the bearings 18, 20. In Fig. 1 the cutter 10 is shown in a first postion for being greased or regreased. It should be noted that greasing takes place in two separate steps. The filling plug 46 is inserted into the axial bore 38 of the shaft 12. A grease gun (not shown) is attached to the grease nipple 47 and grease is pumped into the cutter by the grease gun. Thereby grease is forced through the channels 49 and 51 in the filling plug such that grease is forced out through an orifice in the plug and into the races 28 and 30, between the shaft 12 and the hub 16 carrying the bearings 26. The filling plug has such geometry that it together with the bore prevents axial flow of grease and therefore the plug will not be subjected to axial reactional forces during filling. The first relief holes 34 are used to control the level of the grease inside the cutter 10. That is, excess grease is forced through the holes 34 when the first step of filling is completed. Then the filling plug is retracted from the bore and the bore is left substantially grease-free. The conical plugs 36 are mounted in the first relief holes 34 when the first step of greasing or regreasing is completed. A device or a retainer 70 for the plug 44, see for instance Fig. 4, which has a shorter length than the filling plug 46, is inserted into the bore 38. The retainer 70 for the spacer plug 44 is arranged in the bore 38 and is mounted with clearance fit in the bore. The retainer 70 includes a cylinder, which is substantially thin walled in order to contain much grease primarily internally but is preferably surrounded by grease due to the clearance fit. The retainer has an inwardly extending flange 71. The flange has two objects, to strengthen the retainer and to stop the flexible diaphragm 60, see below, such that the yield point of the diaphragm cannot be reached at high external pressures. A central hole 72 is provided in the flange to allow passage of grease. A number of holes 77 are arranged in the retainer in the vicinity of the bore 40 to allow communication between the bore 40 and an internal space 76 of the retainer. A bellows or flexible diaphragm 60 in Fig. 3, known per se, is provided after the retainer 70 in the bore 38. The diaphragm has a circular basic shape and its largest diameter corresponds substantially to the diameter of the bore 38. In the mounted position the diaphragm has the same diameter as the part of the bore which holds the retainer. One end 75A of the retainer is brought into contact with the bottom of the bore and the diaphragm is brought against the other end 75B of the retainer. Then these are secured against axial displacement by means of a centrally hollow washer 73 and a snap ring 74. The diaphragm preferably projects axially a distance into the retainer. The diaphragm is provided to level the pressure differences that develop during temperature increases in the grease or during shaft sinking of holes filled with deep water. The diaphragm separates the grease from the fluid in the bore hole, which enters into the outer orifice of the bore 38 and through the snap ring 74 and the washer 73. The retainer 70, the grease channel 66 and the diaphragm 60 are provided in the shaft 12, substantially concentrically with the center axis 14. The cutter 10 is shown in Fig. 2 during the second step of greasing or regreasing. A nozzle 67 of a grease gun is inserted in and through the channel 66 and through the central hole 72, whereafter the free end of the nozzle is positioned at or in the vicinity of the movable part 61 of the flexible diaphragm. A precondition for filling is that the grease channel 66, the retainer 70 and the diaphragm 60 are substantially concentrical with the center axis 14. Then grease is pumped inwardly such that it fills the part 61 whereafter as the space around the free end of the nozzle is filled, a counter- pressure is created on the nozzle 66 and the nozzle is pushed outwardly. The operator of the grease gun then realizes that the inner parts of the bore are filled and thus releases the feed pressure on the gun such to allow the gun to be pushed back by the grease during continous filling of grease, i.e. the reactional forces from the grease on the nozzle control the retraction speed of the nozzle. The nozzle 67 is removed when it has been fully pushed out of the grease channel 66, which is now filled. The channel is then sealed by a screw 69 or a similar seal means, see Fig. 4. The complete grease system contains less than 5 % air. The cutter 10 according to the present invention functions in the following way. When a cutter 10 is set under working conditions it rotates and is subjected to heavy loads. This means in a first case, that friction generates heat in the bearings 18,20 and the locking means 26 of the cutter 10 and consequently also the grease is heated and expands or in a second case, that the grease is compressed due to the high external pressure from the fluid in the bore hole. In the first case, when the grease is heated, it expands and since the seal retainers 32 prevent grease from leaking out between the roller body 16 and the shaft 12, the grease will push the movable part 61 of the diaphragm in the direction of the arrow IA in Fig. 3 to the position IIA. In the second case the cutter is surrounded by fluid under a relatively high pressure and therefore the volume of the grease system will diminish due to displacement of the part 61 in the direction of the arrow IB to the position IIB to achieve the same internal pressure as externally. These movements of the part 61 , the change of the internal volume in both cases, occur continously during the drilling or during sinking into fluid and the positions shown in Fig. 3 shall be seen as examples only. Essentially less or larger changes in volume are possible, such as for instance a volume change in the interval + 5 % relative to the original volume. It is often advantageous to fill at least the diaphragm with grease before mounting and then completely fill by means of the nozzle 67. It is possible to practice the invention in connection with raise boring, cutters/discs for tunnel boring heads or shaft sinking. Although present invention has been described in connection with a preferred embodiment thereof, it will be appreciated by those skilled in the art that additions, deletions, modifications, and substitutions not specifically described may be made without departing from the spirit and scope of the invention as defined in the appended claims.

Claims: Claims 1. Cutter for a boring head, preferably a boring head for shaft drilling, wherein the cutter (10) is rotatably mounted, via a shaft (12) of the cutter (10), in a saddle secured to the boring head and wherein bearings (18,20) are provided between the shaft (12) and an outer roller body (16) of the cutter (10) to make it possible for the roller body (16) to rotate relative to the shaft (12), wherein seals (33) are disposed between the shaft (12) and the roller body (16) and channels/bores (38,48,50,66) are provided to introduce lubrication internally into the cutter (10), said shaft (12) having a center axis (14), characterized in that a device (70) for positioning of spacer means (42,44), a lubrication channel (66) and a diaphragm (60) are provided in the shaft (12), substantially concentrically with the center axis (14), said device, channel and diaphragm being provided to accomodate lubrication and that a space (76) inside the device (70) communicates with the bearings (18,20) via the spacer means (42,44) that are located between the device (70) and axial locking means (26) for the roller body (16). 2. Cutter according to claim 1 , characterized in that the device (70) is substantially cylindrically tube shaped and provided with an intermediate portion (71) having a reduced diameter compared to the rest of the device (70). 3. Cutter according to claim 2, characterized in that the device (70) at one (75B) of its ends is provided with a pressure relief diaphragm (60), that is communicating with the space (76) via a hole (72). 4. Cutter according to claim 3, characterized in that the device (70), the diaphragm (60), a hollow washer (73) and a locking ring (74) are inserted into the bore (38) in successive order, said diaphragm abutting against one end (75B) of the device and preferably projecting axially a distance into the device. 5. Cutter according to any of the preceding claims, characterized in that the device (70) is mounted in the bore (38) by a clearance fit. 6. A method of filling lubrication into a cutter (10), which is rotatably mounted, via a shaft (12) of the cutter (10), in a saddle secured to a boring head, characterized in that the method comprises the steps of: - inserting a filling plug (46) into an axial bore (38) of said shaft (12), - forcing lubrication through channels (49,51) of the filling plug so that lubrication exits an outlet of the plug and enters into a bearing means (28,30) disposed between the shaft (12) and a roller body (16) and in which bearings (18,20) are disposed, - removing the filling plug (46) from the bore, leaving the bore generally lubrication-free, - installing in succession a substantially cylindrically tube shaped device (70) and a diaphragm (60) into the bore and locking these axially in the bore, - inserting a nozzle (67) in a channel (66), which communicates with the bore, in the shaft (12), - forcing lubrication into the bore (38), - removing the nozzle and sealing the channel. 7. Method according to claim 6, characterized i n that filling of lubrication first takes place in the area of the diaphragm (60) and then successively in direction towards the outer end of the channel (66) and that the nozzle is removed relatively slowly during substantially continously filling of lubrication.

Inventors: BROLUND STIG-AAKE, BROLUND, STIG-AAKE
Applicants: BROLUND STIG AAKE, SANDVIK AB, BROLUND, STIG-AAKE
Application year: 1996
Main classification: E21B10
IPC codes: E21B10, F16N37