Improvements in hydraulic rotary cylinders

Abstract: The improvements are for application in hydraulic rotary cylinders used for the action of hydraulic machine tools which are comprised by a hollow cylinder (1) which houses in its interior a hollow shaft (49) with a piston (50), which moves axially by means of the alternating application of hydraulic pressure in nozzles (2) and (3). The improvements are designed to effect a continuous and simultaneous oiling of the bearings (8) and (9) on which the rotary shaft (7) turns, which is achieved by means of the rendering of a channel which conducts the drainage oil directly to the said bearings. In a variation for implementing these improvements and in order to optimise the oiling itself or for special hydraulic rotary cylinders, two independent channels are arranged for the drainage of the oil, making it possible to perform an individualised and more regular oiling of the bearings, also constant and simultaneous.

Description: OBJECT OF THE INVENTION The invention refers to improvements made in hydraulic rotary cylinders used in machine tools for acting on work tools. The object of the improvements is to provide simultaneous and constant lubrication to the bearings on which the rotary shaft turns, based on the fact that a nozzle is executed on the pressure distribution piece and between both annular chambers established in the cylinder, extending as ducts which simultaneously connect with the bearings, in order to achieve a simultaneous and constant supply of oil to both bearings for the purpose of improving their lubrication. Another object of the invention is to establish two nozzles for conducting the oil to the bearings by means of independent ducts, so that each bearing receives the oil through an independent duct, this solution being applicable for hydraulic rotary cylinders requiring optimum lubrication. BACKGROUND TO THE INVENTION In the Spanish utility model number 273099, an hydraulic rotary cylinder is described which uses a particular lubrication technique, as shown in figure 1 which is attached as the state of the technique. The component represented in this figure 1 consists of a hollow cylinder (1) which houses in its interior, with a capacity for axial movement, the hollow shaft (49) of the piston which externally forms the piston (50) itself The hollow shaft (1) has a thread (51) for coupling the tool which needs to be used, such as, for example, an hydraulic tie-down. The axial movement of the piston (50) and thus that of its hollow shaft (49) is effected by hydraulic pressure. The oil under pressure enters alternately through the nozzles (2) and (3), in order to pass on to the annular chambers (5) and (6), from which point it is distributed through ducts to the chambers defined by the piston (50) in the hollow cylinder (1). In the case of the annular chamber (5), the distribution of the oil is effected through the duct (52) made in the rotary shaft (7) up to one of the chambers, and the annular chamber (6) distributes it by means of a similar duct, which is not visible in the cross-section view of this figure, up to the opposite chamber defined by the piston (50). The supply of oil for these chambers is effected through the non-return pressure valves (52 - 53) respectively, which are pilot-operated and work in opposite directions. Oil is applied under pressure in an alternating manner, through the nozzles (2) or (3), releasing the pressure of the other nozzle in order to allow the outflow of oil through it. In this way, hydraulic pressure is applied to one of the chambers which the piston (50) defines, that is, to one side or the other of the piston, in order to thus achieve the axial movement of the hollow shaft (49). The oil in the chamber where pressure is not applied, leaves through the respective non-return valve, moving through the circuit in a reverse direction in order to return to the hydraulic base. The axial position of the hollow shaft (49) is determined by means of the electronic detectors (20) and (21), in order to synchronise the machine during its operation. The turning of the rotary shaft (7) is effected on the bearings (8) and (9) of the distribution piece (4) which remains in a fixed position. When the hydraulic pressure is applied to the annular chamber (5), there is a slight leak or drainage of oil through a small opening existing between the distribution piece (4) and the rotary shaft (7) in the direction indicated by the arrows (10) and (11), in order to allow a smooth rotation of the rotary shaft (7) lubricating its contact with the distribution piece (4). This drainage of oil continues its route towards the bearing (9) and the annular chamber (6). The drainage of oil does not lubricate both bearings (8) and (9), as the oil which drains in the direction of the arrow (10) only oils bearing (9), because the drainage in the direction of the arrow (11) goes to the annular chamber (6) which is free from pressure, as the hydraulic pressure is being applied in the annular chamber (5), for which reason the said drainage of oil flows through the annular chamber (6) in order to return to the oil deposit of the pressure pump or hydraulic base. On cutting off the drainage of oil in the annular chamber (6), the oil no longer flows in the direction of the arrow (11) towards bearing (8), for which reason, this bearing does not receive oil until the provision of pressure through the annular chamber (6) alternates and the pressure in the annular chamber (5) is released. When this change occurs in the injection of pressure into the other chamber, in order to move the hollow shaft (49) in the other direction, the same process is repeated, which this time affects bearing (9). In these devices, the simultaneous lubrication of both bearings (8) and (9) is very important, due to the high speeds to which cylinders of this type are subjected, and which, with current techniques, lubricate in an alternating manner in response to the change in the application of hydraulic pressure, and never both at the same time. The oil drained after lubricating bearing (8) or bearing (9) moves in the direction indicated by the arrows (12) and (13) up to the oil catch (14), in order to return it through duct (15) to the deposit of the hydraulic base. Oil-breaking catchers are located at the ends of the rotary shaft (7) and the hollow cylinder (1), which prevent any left-over oil from leaking to the outside of the cylinder and, by means of their circular grooves (16) and (17), they conduct the oil to the collection casing (14) through ducts (18) and (19). Over time and with technological progress, in the other designs, the collection casing (14) has been shortened, as shown in figure 2, without altering the essence of the mechanism, however, on shortening the collector (14), new problems arise. In this figure 2, all of the components are the same and operate in the same manner as those in figure 1; only the shape of some of these components varies and the new oil collector (23) is presented, which has oil-collecting lids (24) and (25) with the same functions as the earlier devices and which carry the oil-breaking grooves (26) and (27) which return the oil through ducts (28) and (29) to the collector (23). The reduction in the size of the collector (23) and the lids (24) and (25) with respect to the model shown in figure 1 has brought about the need for cutting back the outflow of the drainage oil, which cannot be conducted on account of the aforementioned reduction of space and thus it spills to the outside. In order to solve this problem, two new annular chambers (31) and (32) have been introduced to the pressure distribution piece (4) carrying the annular chambers (5) and (6), at the cylindrical ends of its internal periphery, and close to the bearings (8) and (9). These chambers (31) and (32) have been connected with the ducts (33) and (34) in order to return the oil directly to the collector (23), as the ducts (28) and (29) cannot do so completely on account of their reduced size. This solution heightens the problem of lubricating the bearings (8) and (9), which, if in the case of the model shown in figure 1, lubricated alternately, in this case, one bearing is not oiled and the other is oiled very deficiently. This incomplete oiling brings about problems of overheating, breakdowns and their ensuing risks. DESCRIPTION OF THE INVENTION The improvements introduced in hydraulic rotary cylinders which have been developed in this invention make it possible for the bearings to be constantly and simultaneously oiled, thus improving their operation considerably, by reducing their operating temperature, increasing their safety coefficient in relation to breakdowns and accidents, and as a result, extending the useful lifetime of the device. For the same reasons, it is possible to achieve a greater number of revolutions in the operation of the machine. The characteristics of these improvements make it possible to apply them to hydraulic rotary cylinders with large or shortened oil collection casings, or with no casing at all, by effecting the collection of the oil directly from the distribution piece with a special drainage catcher. In order to achieve these significant advantages, the invention consists of effecting an independent nozzle on the pressure distribution piece between the two annular chambers, which is extended by ducts through which it allows the oil to pass to both bearings, lubricating them simultaneously. In this way, with the hydraulic pressure being applied in one or the other annular chamber, this nozzle and ducts constitute an alternative channel for the passage of oil, which prevents it from flowing completely towards the chamber which is free from pressure, thus giving rise to the problems mentioned earlier, and which also serves to guide the oil to both bearings simultaneously and independently of whichever annular chamber is under pressure. This type of oiling can be optimised, and in fact should be in certain types of hydraulic rotary cylinders, such as, for example, cylinders driving borers and gripping chucks in production or numerical control lathes. Thus, for this case, a variation has been designed or, in other words, an additional improvement based on replacing the single nozzle referred to earlier for the intake of oil, with two independent nozzles, each of which is connected to ducts which are also independent and lead to the respective bearings. On the basis of the independent nozzles and ducts introduced, it is possible for each bearing to have its own channel of lubricating oil supply, which provides a greater supply of this fluid to each bearing and consequently a better lubrication. This increase in the quantity and the individualised supply of oil constitutes a more effective and appropriate lubrication for certain type of hydraulic rotary cylinders, such as those which drive borers and gripping chucks in production or numerical control lathes. DESCRIPTION OF THE DRAWINGS In order to complement the description provided herein and for the purpose of helping to convey a better understanding of the characteristics of the invention, in accordance with a preferred example of a practical rendering of same, a set of drawings is attached as a integral part of this description, in which, on an illustrative and non-restrictive basis, the following aspects are shown: Figure 1.- Shows a sectional side view of a known hydraulic rotary cylinder, which serves to illustrate the problems existing in these mechanisms. In the left part of the figure, and drawn with a finer line, the axial movement of the hollow shaft and its piston is shown. Figure 2.- Shows a similar view to that shown in figure one above for the purpose of illustrating the state of the technique and is centred on the problems presented by the models with a shortened oil collector. In this figure, the improvements of the invention are also incorporated. Figure 3.- Shows a sectional side view of an hydraulic rotary cylinder which incorporates the improvements which are the object of this invention. Figure 4.- Shows a sectional side view of an hydraulic rotary cylinder with the improvements of the invention for instances of a shortened oil collection casing. It also shows a sectional front view in which the said improvements are seen from this perspective. Figure 5.- Shows a sectional side view of a variation for implementing the invention. Figure 6.- Shows an elevational side and front sectional view such as those in figure 4, but with the implementation variation in which two nozzles are included. Figure 7.- Shows, finally, a side view of a complete rotary cylinder which serves to illustrate the implementation variation represented in the preceding figure. PREFERRED EMBODIMENT OF THE INVENTION By observing figure 3, it can be understood that the invention consists of rendering a nozzle (41) on the pressure distribution piece (4) and between annular chamber (5) and annular chamber (6), also visible in the front section of figure 4. This nozzle (41) is extended in duct (42) arranged in a radial direction with respect to the rotation axis of the cylinder, which in turn is connected to the duct (43) arranged in an axial direction, which connects directly to the sides of the bearings (8) and (9), thus constituting a direct channel for the drainage oil to pass on to the bearings (8) and (9). In this way, the passage made up by the nozzle (41) and the ducts (42) and (43), indistinctly of whichever annular chamber (5) or (6) is supplied with hydraulic pressure, allows the drainage of oil which, instead of passing completely through the pressure-free annular chamber, does so through the nozzle (41) and duct (42), being distributed through the duct (43) to the bearings (8) and (9) simultaneously, effectively lubricating both bearings throughout the operating time of the machine. A variation has been foreseen in the implementation of the invention, applicable to specific models of rotary cylinders, or in order to adapt to certain applications of the invention. In this variation, the channel for the passage of oil is effected in the body of the rotary shaft (7) instead of the pressure distribution piece (4), as is shown in figure 5. This channel is constituted in a similar manner by means of the nozzle (45) between the annular chambers (5) and (6), which, in a radial directions, connects with the duct (46) arranged in a linear direction, which in this variation is extended in nozzles (47) and (48), also radial, next to the bearings (8) and (9) to which the oil is supplied, also in a continuous and simultaneous manner. In a variation of the implementation shown in figures 6 and 7, it can be seen how between the annular chambers (5) and (6) there is a radial opening corresponding to the duct (54) which is extended in an axial direction in duct (55), which leads to bearing (8). This opening acts as a nozzle, allowing the oil originating from the annular chamber under pressure, regardless of whether this is annular chamber (5) or annular chamber (6), to flow through duct (54) and duct (55) in order to reach the bearing (8), as indicated by the arrow (56) in figure 6. In the same way, between the two chambers (5) and (6), there is an opening corresponding to duct (57), with a radial projection and extended axially into duct (58) which leads to bearing (9). These ducts (57) and (58) allow a part of the drainage of the oil from one of the annular chambers to flow towards bearing (9), as is indicated by the arrow (59) in figure 6 itself. Referring back to ducts (54) and (57), it can be seen how they are separated in a radial manner one from the other, constituting, together with the respective ducts (55) and (58), independent channels for the individualised drainage of the oil, one for bearing (8) and the other for bearing (9). The said independent channels achieve an individualised oiling of the bearings, and at the same time allow a regulated and independent drainage of the oil reaching the bearings, for which reason they are oiled more regularly. As can be observed in figure 7, in an implementation variation, the independent oiling ducts are rendered in the rotary shaft (7) instead of the distribution piece (4), thus achieving the same effect and advantages sought. Specifically, the ducts (60) and (61), with a radial separation between them, are arranged in the rotary shaft (7) and connect respectively with ducts (62) and (63), making independent drainage to the bearing (8) and (9) possible.

Claims: Hydraulic rotary cylinder for use in machine tools for acting on work tools which is comprised of a hollow cylinder (1) which houses a hollow shaft (49) which forms a piston (50), which can be moved in an axial direction by means of the alternating provision of pressure through nozzles (2, 3), and where the rotation of a rotary shaft (7) takes place on bearings (8, 9) of a pressure distribution piece (4) having annular chambers (5, 6), and with the intention of achieving a more satisfactory oiling of the bearings, characterised in that a nozzle (41) is incorporated in the pressure distribution piece (4) between the annular chambers (5, 6) and is extended as a duct (42) in a radial direction, which in turn connects with a duct (43) arranged in the axial direction of the device, which connects directly to the bearings (8, 9), thus constituting a direct channel for the passage of the drainage oil to the bearings (8, 9), originating indistinctly from any of the annular chambers (5, 6), which is supplied with hydraulic pressure at any given moment, with the intention of avoiding drainage of the entire amount of oil towards the annular chambers without pressure, by directing the oil to both bearings (8, 9) simultaneously and in a continuous manner throughout the duration of the operation of the device, whereby the operating temperature is reduced, the operation of the device and its safety coefficient are improved, and it is possible to achieve a higher number of revolutions. Hydraulic rotary cylinder according to claim 1 and , in order to adapt the invention to certain models of cylinders and their possible applications, the channel for the passage of oil is effected in the body of the rotary shaft (7) instead of the pressure distribution piece (4) characterised in that in the body of the rotary shaft (7) a nozzle (45) is opened between the annular chambers (5, 6), which in a radial direction is connected to a duct (46) arranged in an axial direction, which in turn is extended to radial nozzles (47, 48) which allow passage to the bearings (8, 9), in order to constitute a channel for direct passage of the drainage oil to the said bearings, lubricating them in a continuous and simultaneous manner. Hydraulic rotary cylinders, according to claims 1 and 2, characterised by either a large oil collecting casing, a shortened casing or no oil collecting casing. Hydraulic rotary cylinders, according to the preceding claims, characterised in that in the pressure distribution piece (4), between the annular chambers (5, 6), ducts (54, 57) are opened, both in a radial direction and with a radial separation, which are extended respectively to the axial ducts (55, 58) which reach the bearings (8, 9), in such a way that these ducts constitute independent oil drainage channels leading form the annular chambers (5, 6), respectively achieving an independent and more regular oiling of the bearings (8, 9). Hydraulic rotary cylinder, according to claim 4, characterised in that the independent channels for the individualised oiling of the bearings (8, 9) are effected in the rotary shaft (7) instead of the distribution piece (4) using in this case ducts (60, 61), both radial and separated, reaching the relevant bearings through ducts (63, 64).

Inventors: GALVEZ CAMPOS JOSE LUIS, GALVEZ CAMPOS, JOSE LUIS, Galvez Campos, José Luis
Applicants: GALVEZ CAMPOS JOSE LUIS, GALVEZ CAMPOS, JOSE LUIS
Application year: 1999
Main classification: B23B31
IPC codes: B23B31