POROUS STATIC PRESSURE GUIDE

Abstract: A static pressure lead screw includes a porous ceramic body (11) having fluid flow paths as part of a flank (9). The porous ceramic body (11) is fixed by a tubular base member (20) through which the fluid does not flow. Fluid guide holes (12) for supplying the fluid to the porous body (11) extend through the tubular base member (20) and are connected to the porous body (11). In a preferred embodiment, an electroless-plated layer is formed in a surface layer of the flank or an inner portion continuous with the surface layer, thereby obtaining various high-accuracy static pressure guides with high statical stiffness.

Description: Background of the Invention A static pressure lead screw is known as a means for achieving high-speed, high-accuracy feeding for converting rotational movement into linear movement. In the static pressure lead screw, a pressurized fluid is supplied between male and female screws or external and internal threads to support them through the pressurized fluid. A fluid bearing is also proposed to supply a pressurized fluid to a gap between a rotating shaft and a bearing for supporting it. These mechanical elements are so-called static pressure guides. The present invention particularly relates to a porous static pressure guide comprising a porous body for a bearing surface, a static pressure lead screw, and a feed mechanism using the same. Conventional static pressure lead screws as one type of static pressure guides will be briefly described below. A static pressure lead screw serves as a static pressure guide wherein a pressurized fluid is supplied to a gap between male and female screws (this gap is referred to as a screw gap hereinafter) to support the male and female screws through the pressurized fluid in a noncontact manner. The static pressure lead screws are classified into a hydrostatic lead screw and a pneumostatic lead screw according to the types of working fluid. These static pressure lead screws are not subjected to solid friction and are free from stick-slip and backlash. Feed accuracy can be greatly improved by a fluid film averaging effect. In addition, since no solid friction occurs in the static pressure lead screw, accuracy is not permanently degraded. For these and other reasons, in recent years, the static pressure lead screws have received a great deal of attention for a variety of applications in high-accuracy, high-speed apparatuses such as apparatuses for manufacturing semiconductor elements and optical components and electronic equipment. However, since the fluid is supplied, the structure of the female screw is complicated. In addition, design is difficult and more accurate machining is required, thus posing many problems to be solved. Therefore, practical static pressure lead screws have not yet been proposed. In particular, it is difficult to increase stiffness of an air lubrication film between the male and female screws in a pneumostatic lead screw using a gas of a very low viscosity. No practical pneumostatic lead screws are proposed. The structures of conventional hydrostatic lead screws are shown in Fig. 13(a) and 13(b) (Journal of the Japan Society of Precision Engineering (JSPE) 48, October (1982), p. 1341 and Journal of the Japan Society of Precision Engineering 48, October (1982), P. 1291). The Figures include sectional views and flanks of a female screw when viewed from the feed direction of the screw. A male screw 1 is a normal feed screw, whereas a female screw has a complex structure to supply oil in a screw gap 8 and to recover oil therefrom. More specifically, the female screw consists of a nut case 2 and a nut 3. Oil supply and recovery grooves 4 and 5 are helically formed in the inner surface of the cylinder of the nut case 2 or the outer surface of the cylinder of the nut 3 to correspond to the pitch of the male screw. The supply and recovery grooves 4 and 5 are connected to supply and recovery holes 6 and 7, respectively. As a result, a fluid is supplied to the screw gap 8 or is recovered therefrom. The oil supply holes 6 directly influence the amount and uniformity of the flow of fluid supplied to the screw gap 8 and determine the performance of the hydrostatic lead screw. High machining accuracy of the oil supply holes is required. Especially, when the hydrostatic lead screw is to be made compact, it is difficult to precisely form helical oil supply and recovery holes 6 and 7 in small mechanical parts. Therefore, compactness of the hydrostatic lead screws cannot be easily achieved. Furthermore, in a static pressure bearing, an oil pocket is formed to increase the pressure-receiving surface area. However, machining of the pocket is very complicated in a static pressure lead screw. In the prior art shown in Fig. 13(a), four pockets 11 dividing a circle into four portions are formed in the flank. This machining is done by groove machining in the inner surface of the nut 3, in practice, and is very difficult when access of a machine tool with respect to the machining portion is considered. Therefore, in the prior art shown in Fig. 13(b), elliptic supply ports 6 open in the flank are used as the pockets. A static pressure lead screw is based on the same principle as that of the static pressure bearing. In order to efficiently increase the stiffness of the bearing, flow path resistance such as a self-forming restrictor, a surface restrictor, and an orifice restrictor are usually added. In Fig. 13(a), orifice restrictors 12 are added midway along the oil supply holes 6. A static pressure lead screw requires a large number of oil supply holes. If complex machining such as formation of orifices is performed at a large number of portions, the entire static pressure lead screw becomes expensive. In Fig. 13(b), a portion for connecting the supply groove 4 and the supply hole 6 with a shallow groove serves as a surface restrictor 12'. The shallow groove is helically machined in the outer surface of the nut along the thread ridge. In the pneumostatic lead screw using a gas (e.g., air) as a working fluid, statical stiffness between the male and female screws is more important than in the hydrostatic lead screw. This is because the viscosity coefficient of the gas is extremely smaller than that of oil, i.e. it is as small as in the order of 1/1,000, and the used gas is a compressible fluid. For these reasons, the screw gap in the pneumostatic bearing must be smaller than that in the hydrostatic bearing and must fall within the range of several microns to a value between 10 and 20 microns. The pneumostatic lead screw uses a flank as an air bearing surface. In order to obtain the gap described above, surface flatness, geometrical accuracy, and pitch accuracy must be very high in machining of the female and male screws. In addition, orifice restrictors or other kinds of restrictors must be formed as well as a large number of air supply holes to give statical stiffness to the lead screw. Difficulties in complicated and more accurate machining result in a bulky pneumostatic lead screw at high cost. A practical pneumostatic lead screw cannot be realized. Figs. 14(a), 14(b), 14(c), 14(d) and 14(e) are respectively sectional views of conventional pneumostatic lead screws (Japanese Patent Laid-Open (Kokai) Nos. 58-166162, 59-113360 and 60-241566, and European Patent Document Nos. DE-A-2 030 260 and DE-A-2 032 160). The structure of Fig. 14(a) is very conventional like a hydrostatic lead screw as shown in Figs. 13(a) and 13(b). A triangular-shaped air supply groove 4 is helically formed on the outer surface of the nut 3. Then guide holes 6 are drilled from the supply groove to the flank of the nut 3. A very small hole diameter near the flank acts as a self-forming restrictor. In this case, a large number of air supply holes should be machined with high accuracy. In addition, because a self-forming restrictor requires a very small and uniform screw gap, extremely accurate machining in the flank shape and the pitch of both male and female screws is inevitable for obtaining practical stiffness. It is almost impossible, in practice, to achieve these requirements in machining. This complex and difficult machining makes this kind of pneumostatic screws large and very expensive. The nuts of the pneumostatic lead screws in Fig. 14(b), 14(c), 14(d) and 14(e) are made of porous bodies and serve as porous restrictors. In these porous lead screws, the flanks are formed by simple thread cutting. Since, the porous restrictors have high air supply efficiency and the statical stiffness of the pneumostatic lead screw can be improved as compared with lead screws employing other types of restrictor. In addition, with the structures in Fig. 14(b) and (d), air supply holes need not be formed because compressed air is supplied from a chamber 4.6. Otherwise, the air supply holes in Fig. 14(c) and (e) are formed by simply boring the porous body. However, because the nuts in Figure 14(a), (b), (c) and (d) are entirely porous, an unnecessary pressure drop is to be avoided. The porous portion having a high flow resistance, the pressure gradually drops at a position remote the air supply port. Referring to the porous nut shown in Fig 14(b) and (d), the pressure at the flank is largely reduced and not uniform because of a long and different porous path to the flank from the air supply chamber. In the case of the porous nuts in Fig. (c), the shape of the supply hole is a similar to the flank and the supply hole extends to the flank. In the case of the porous nut in Fig. 14(e), whole supply holes in the porous body have a sealing and a covering to prevent unnecessary pressure drop. In addition, ridge surfaces 12, 12' and 12" (indicated by thick lines) excluding the flanks in Figs. 14(c) and (d) are sealed. This is because the gap at the inner and outer circumferential portions of the screw is large which causes a large pressure drop. The inner and outer circumferential portions of the nut, i.e. positions where the gap is large, are not sealed in Fig. 14(b) and (d), and the compressed air spirally leaks through the large gap and the pressure of the flank portion is almost not increased. Although sealing is useful for preventing unnecessary pressure drop, it is very difficult or very complex to seal the inner surface of the nut. A seal portion must be an entire portion except for the engaging flank portion with the screw shaft (incomplete sealing causes leakage of pressurized air), and the gap at the engaging portions must be set to be very small. Therefore, the sealing agent must not project from the flank surface. More especially, sealing in Fig. 14(e) is much more complicated then the sealing of various kinds of air supply holes. These requirements of difficult sealing are a serious disadvantage in the structure of the conventional porous lead screws. In addition, the externally pressurized air bearing causes the problem of "pneumatic hammer". "Pneumatic hammer" is a self-excited vibration caused by the compressibility of the gas. The pneumatic hammer tends to occur in a gas bearing having a large flow path volume, such as a pocketed surface restrictor and a porous restrictor. The nuts in Figs. 14(b), (c), (d) and (e) are entirely made of porous bodies and have large flow path volumes. Therefore, the pneumatic hammer tends to occur in these lead screws. Almost all disadvantages described above, such as unnecessary pressure drop due to air leakage, requirement of very complicated sealing, and pneumatic hammer, are due to the fact that the entire nut consists of a porous body in conventional porous pneumostatic lead screws. The ridge shape of the lead screws in Figs. 14(a), (b), (c), (d), and (e) is defined as a tapered (trapezoidal) shape, which, primarily, has two disadvantages. The first one concerns the machining accuracy of the screw. The work piece tends to be bent due to radial machining forces during the machining of the trapezoidal screw. Bending deformation of the work piece during machining causes errors in pitch or shape of the screw. It is very important to assure a narrow uniform gap in air bearing so as to obtain high stiffness. Therefore, highly accurate machining is inevitable to achieve a practical pneumostatic lead screw. Another, i.e. the second disadvantage of the trapezoidal screw appears when applied to a feed mechanism. When a centripetal force acts between the nut and the screw shaft in the trapezoidal screw, the nut behavior is matched by the screw shaft. However, an elongated and complicated screw shaft is difficult to be machined straightly. Thus the centripetal force causes motion errors such as pitching and yawing. When the porous body is a metal porous body, clogging during drilling or cutting may pose a problem due to plastic deformation of the material. When the flanks 9 or the wall surfaces defining air supply holes 6 in Figs. 14(b) to (e) clog, the air flow paths are blocked, and the lead screws do not serve as pneumostatic lead screws. Proper clogging of the bearing surface in a porous air bearing is useful to improve the bearing performance. If a free margin is given in machining of the bearing surface in a planar bearing such as a linear slide bearing, such a clogging effect can be effectively utilized. However, when the floating screw gap is determined by the machining amount due to the dimensional limitations of opposite bearing surfaces as in a radial bearing, a pneumostatic lead screw, or the like, it is difficult to control proper collapsing during machining. Therefore, both the clogging amount and machining accuracy cannot be simultaneously satisfied. Pore collapsing in the porous metal body is performed by utilizing plastic deformation. More specifically, cutting or grinding is performed by selecting cutting conditions such as sharpness of a cutting edge of a cutting tool, a cutting depth, a machining speed, or a machining temperature. The sectional area of the fluid path present on the porous body surface can be decreased by plastic deformation. Therefore, an amount of plastic deformation corresponds to an increase in flow resistance. Since numerous large and small holes are present on the the porous body surface, the smaller pores tend to collapse when an amount of plastic deformation is increased. Therefore, pore collapsing by plastic deformation is limited to a material subjected to plastic deformation, and the machining conditions must be properly selected. Variations in sintering strength and hardness adversely affect machining conditions. Friction and wear of the machining tools fail to guarantee good machining conditions. Reproducibility and productivity are poor since plastic deformation itself is based on machining with skills or machining according to a given probability. In this sense, a uniform pore-collapsed surface cannot be formed. In other words, plastic deformation is a factor opposite to improvement of machining accuracy. As described before, machining accuracy improves performance of the static pressure guide itself directly. Pore collapsing by plastic deformation is a surface layer restrictor formation technique controversial to high performance of the static pressure guide. This fact explicitly indicates that problems for controlling the flow resistance to achieve porous restrictors and for forming surface layer restrictors are left unsolved. Summary of the Invention It is a primary object of the present invention to provide a porous static pressure guide having statical stiffness higher than that of a conventional static pressure guide. It is another object of the present invention to provide a porous static pressure guide wherein machining can be easier than conventional machining and machining accuracy can be improved as compared with conventional machining. It is still another object of the present invention to provide a static pressure lead screw free from a pneumatic hammer. It is still another object of the present invention to provide a porous static pressure guide wherein clogging tends not to occur regardless of use of a porous material. It is still another object of the present invention to provide a porous static pressure guide wherein restrictor characteristics of a porous material can be easily optimized. According to the present invention, these objects are achieved in a porous static pressure guide for guiding a first member defining a first surface in relation to an opposite object defining a second surface, wherein said first member comprises a solid base member and a porous body of ceramic material formed on the solid base member, and wherein said first and second surfaces are designed to allow relative guidance therebetween, in that the porous body defines only a part of the first surface, the remainder thereof being defined by the solid material of the base member, and that at least one guide hole is formed in the first member to extend through the solid base member into the porous body and is arranged to supply a fluid to the interior of the porous body for floating the same relative to the opposite object. According to another aspect of the present invention, there is suggested a method of manufacturing a static pressure guide, which method is characterized by the step of forming the porous body of a ceramic material on the solid base member, together constituting said first member so as to define at least a predetermined gap relative to the opposite object, wherein a guide hole is formed to extend through said solid base member and inside said porous body to supply fluid to the interior of said porous body, thereby floating said porous body relative to the opposite object. The porous body is used for a bearing restrictor, as well as for fluid supply paths, and fluid is supplied through holes bored in the porous body. Therefore, the structure of the static pressure guide is very simple, thus being appropriate for easy and accurate machining. The minimum necessary part of the bearing pad or the flank of the nut is the porous body. Therefore, the undesired pressure drop due to unnecessary air flow is small, no sealing to avoid fluid leakage is required, and the effect of pneumatic hammer does not tend to occur. The porous body is made of ceramic material, and thus no pore collapsing occurs in machining. Furthermore, the porous ceramic body surface may be plated by electroless plating, and the flow path resistance of the porous ceramic body can be adjusted by electroless nickel plating, thereby obtaining a maximum restrictor effect as well as avoiding pneumatic hammer. Therefore, a compact static pressure lead screw or bearing having high stiffness can be manufactured by a simple process. When a square screw thread is employed wherein a thread ridge angle is perpendicular to the screw axis, only an axial machining force acts thereon. A bending force does not act on the screw, whereby machining accuracy is improved. Brief Description of the Drawings Fig. 1(a) is a sectional view of a static pressure lead screw using a porous restrictor according to a first embodiment of the present invention; Fig. 1(b) is a view showing a flank of the first embodiment; Fig. 2 is a sectional view of a static pressure lead screw using a porous restrictor according to a second embodiment of the present invention; Figs. 3(a), 3(b), and 3(c) are sectional views for explaining the steps in manufacturing a static pressure lead screw using a porous restrictor according to a third embodiment of the present invention; Figs. 4(a) and 4(b) are views showing a static pressure lead screw using a porous restrictor with surface plating according to a fourth embodiment of the present invention; Fig. 5 is a view showing nickel electroless plating used for adjusting a flow resistance of a porous body according to a fifth embodiment of the present invention; Fig. 6 is a sectional view showing a nickel-plated porous restrictor; Figs. 7(A) and 7(B) are sectional views showing a sintered porous body; Fig. 8 is a graph showing the relationship between a floating screw gap h and statical stiffness k according to a static pressure floating test. Fig. 9 is a static pressure uniaxial feed mechanism according to a sixth embodiment of the present invention; Figs. 10(a) and 10(b) are views showing an a feed resolution of the static pressure uniaxial feed mechanism; Fig. 11 is a graph showing the relationship between the axial statical stiffness and a load capacity in the static pressure uniaxial feed mechanism; Fig. 12 is a graph showing feed accuracy of the static pressure uniaxial feed mechanism; Figs. 13(a) and 13(b) are sectional views showing conventional hydrostatic lead screws, respectively; and Fig. 14 (a) to (e) are sectional views showing conventional pneumostatic lead screws, respectively. Description of the Preferred Embodiments Embodiments of static pressure lead screws will be described below. (First Embodiment) Fig. 1(a) shows a first embodiment of the present invention. Reference numeral 10 denotes a porous body; and 6, a guide hole between each supply groove 4 and the porous body 10. The same reference numerals as in Figs. 13(a) and 13(b) and Fig. 14 (a) to (e) denote the same parts in Figs. 1(a) and 1 (b). Reference numeral 3' denotes crests made of a material of an inner cylinder 15 (to be described later) shown in Fig. 3(a); and 3, a screw body or a solid base member made of a material of an outer cylinder 16 (to be described later) shown in Fig. 3(a). A fluid passes through the guide holes 6 and reaches the porous body 10 and is then supplied to right and left screw gaps 8 of each thread ridge. Fig. 1(b) illustrates a portion near a flank of the static pressure lead screw shown in Fig. 1(a) when viewed in a direction perpendicular to the flank surface. The flank is helically continuous in a direction perpendicular to the surface of the drawing, but a sectional view thereof is omitted. The guide holes 6 are located at positions corresponding to the ridges, respectively. In general, the porous body 10 is constituted by numerous continuous microspaces and serves as a restrictor using the flow resistance upon flowing of the fluid through the porous body 10. For this reason, with this structure, the porous body 10 serves as a fluid supply path and as a means for applying a flow resistance (i.e., a restrictor). Although the porous material has surface waving and roughness since it is sintered, the flanks of the lead screw are tooled to obtain predetermined accuracy according to the present invention. Therefore, the surface of the porous body directly serves as a bearing surface. With the structure according to the present invention, a self-forming restrictor, an orifice restrictor, or a surface restrictor need not be formed. In addition, high machining accuracy of the supply holes reaching the flanks in the conventional lead screw is required, however, in this invention the supply hole is formed with accuracy for allowing the hole to communicate with the interior of the porous body. Only one supply hole is required to supply a fluid to the right and left flanks. As is apparent from the above description, the static pressure lead screw can be easily machined to achieve compactness and low cost. The porous restrictor allows supply of the pressurized fluid from the entire surface of the porous body, and then the range of the pressure in the gap can be widened. This indicates that a load acting on the static pressure lead screw or bearing can be increased, and their statical stiffness can also be improved. A gas such as air or a liquid such as an oil can be used in the static pressure lead screw according to the present invention. In this case, although the viscosity of the gas is greatly different from that of the liquid, the porous body 10 having an optimal flow resistance for the gas or liquid can be selected. An optimal flow rate of the fluid is determined by a ratio of the screw gap to the porosity of the porous body. When the screw gap is increased, the porosity must be increased accordingly. However, when the screw gap is decreased, the porosity can be decreased, thereby obtaining an optimal design value. The porosity of the porous body can be adjusted by a particle size of a material prior to sintering. In a conventional pneumostatic lead screw using a porous nut, the entire nut corresponding to the components 3 (solid base member), 3', and 10 in Fig. 1(a) is made of a porous material. With such structure, the pressure drop in the chamber is increased, since the flow path in the porous component is long. As a result, in order to avoid such dropping in pressure, the crest and the root of the nut are sealed. As previously mentioned, the pneumatic hammer in the air bearing tends to occur when the flow path volume is large. Therefore, in the pocketed surface restrictor and the porous restrictor, design of the flow path and setting of the flow rate must be taken into consideration to prevent the pneumatic hammer. However, in the static pressure lead screw of this embodiment, the volume of the porous body (a portion through which a gas flows) is minimized. As compared with the conventional case wherein the entire nut is made of the porous material, the flow path volume is small. In addition to the effect wherein the flow rate is optimized by the plated layer to be described later, the pneumatic hammer tends not to occur. (Second Embodiment) Fig. 2 shows a second embodiment of the present invention. In a conventional static pressure lead screw, the flanks 9 constitute a trapezoidal or triangular screw thread because a static pressure acts on the lead screw in a radial direction thereof to cause the nut to receive a load in a direction perpendicular to the feed direction or have a self-centering ability, and to allow easy connection of supply holes easily to the flanks. However, in such a thread profile, it is difficult for a machine tool to produce threads with good reproducibility and high accuracy. More specifically, since machining is performed using a die having a shape corresponding to the thread profile, it is not easy to machine flanks with high accuracy. In particular, a machining force in the radial direction of the lead screw is large. Under this condition, during machining of the male screw in which a feed speed is predetermined, bending moment components cause deformation of the male screw and which causes pitch error of the thread. As a result, accurate machining is not allowed. Judging from the above fact, in a square screw thread in which a ridge angle is formed to define a line perpendicular to the screw feed direction, bending deformation rarely occurs during machining. Therefore, the square screw having a ridge angle defining a line perpendicular to the screw feed direction is used in high-accuracy feed screw used in a lead screw for a machine tool. The static pressure lead screw according to the present invention can easily achieve high-accuracy screw feeding as the primary purpose of the static pressure lead screw since the ridge angle can be formed to define a line perpendicular to the screw feed direction, as compared with the conventional case. A separate linear guide parallel to the static pressure lead screw may be provided for a load in a direction perpendicular to the feed direction. Since the linear guide does not have a complicated shape unlike in the feed screw, it is possible to obtain a truely linear guide with high stiffness. It should be noted that the ridge angle in the static pressure lead screw according to the present invention is not limited to be set in a direction perpendicular to the feed direction but can be arbitrarily set to form a triangular screw thread, a trapezoidal screw thread, or the like. (Third Embodiment) Figs. 3(a), 3(b), and 3(c) show a third embodiment for explaining a method of manufacturing a static pressure lead screw according to the present invention. More specifically, Fig. 3(a) shows the step of preparing a substratum 13 constituting a nut of the static pressure lead screw according to the present invention, in which reference numeral 14 denotes a porous hollow cylinder; 15, an inner cylinder; and 16, an outer cylinder. The substratum 13 is prepared such that the inner and outer cylinders 15 and 16 are fitted in and on the inner and outer surfaces of the porous hollow cylinder 14. After the inner, outer, and porous hollow cylinders 15, 16, and 14 are integrally prepared, they are bonded by thermal diffusion. Alternatively, a porous material may be inserted in a gap between the inner and outer cylinders 15 and 16, and the resultant structure may be sintered. According to still another method, a porous portion is formed by plasma flame spraying on the outer surface of the inner cylinder 15 and a porous portion is also formed by plasma flame spraying on the inner surface of the outer cylinder 16, the inner cylinder 15 is then fitted in the outer cylinder 16, and the resultant structure is bonded to each other. Various other methods may also be utilized. Fig. 3(b) shows a nut 18 of the static pressure lead screw. A female screw portion 17 is formed in the base member 13 by known cutting and grinding. Spiral fluid supply and exhaust grooves 4 and 5 are also formed by cutting or grinding, and guide and exhaust holes 6 and 7 are formed by drilling. Fig. 3(c) shows a state wherein the nut 18 is built into a case 2 by press fitting or shrink fitting. As is apparent from Fig. 3(c), the guide and exhaust grooves 4 and 5 may be formed in the case 2. Unlike in the conventional static pressure lead screw, a large number of high-accuracy supply holes and flow grooves need not be formed. Only parts to be machined are flanks which are indispensable elements in the static pressure lead screw, thereby reducing an influence acting on machining accuracy and hence simplifying machining. Therefore, a high-performance static pressure lead screw at low cost can be provided. In the conventional static pressure lead screw wherein the supply holes and flow path grooves must be precisely formed, then the material of the nut 18 is limited to a metal. However, according to the present invention, the base member 13 may be replaced with a ceramic base material. The static pressure lead screw is formed in preliminary sintering, and the preliminarily sintered body is finally sintered. Only flanks of the screw are then ground or lapped with high accuracy. Therefore, a ceramic static pressure lead screw can be obtained. A ceramic material has better high-accuracy machining characteristics such as high stiffness and small machining distortion as compared with a metal. In addition, the ceramic material is free from plastic deformation, and clogging of the porous body during machining need not be taken into consideration. In this sense, the ceramic material is very advantageous in realizing the static pressure lead screw of the present invention. In addition, the ceramic material has a low thermal expansion coefficient and is lightweight. Therefore, the ceramic material is a material suitable for high-accuracy machining as the primary purpose of the static pressure lead screw. As described above, the high-accuracy supply holes and flow path grooves need not be formed in the static pressure lead screws having the porous restrictors and represented in the first and second embodiments unlike in the conventional self-forming restrictor or surface restrictor type static pressure lead screws. Therefore, machining can be simplified. In addition, the thread ridge angle can be arbitrarily selected, and the static pressure lead screws of the first and second embodiments can have a variety of applications. Realization of a screw having the ridge angle formed in a direction perpendicular to the axial direction thereof, which is almost impossible in the conventional lead screws, leads to high-accuracy feeding as the primary purpose of the static pressure lead screw. The method of manufacturing the static pressure lead screw according to the third embodiment of the present invention has advantages in that the base member for the porous restrictor type static pressure lead screw can be easily obtained by utilizing various methods and that a ceramic static pressure lead screw can be achieved, thereby performing high-speed, high-performance screw feeding utilizing the advantages of the ceramic material. The features of the static pressure lead screw of the present invention can be effectively utilized in high-accuracy feeding of a workpiece and a machining/measuring tool in an apparatus for performing high-accuracy machining or high-accuracy measurement, high-speed, high-accuracy driving in an x-y stage used in micropattern lithography or testing during the semiconductor element manufacturing process, and write access of an optical or magnetic disk drive and high-speed, high-accuracy positioning of a read head. (Fourth Embodiment) Figs. 4(a) and 4(b) show a fourth embodiment of the present invention. The same reference numerals as in Figs. 1(a) and 1(b) denote the same parts in Figs. 4 (a) and 4(b), and a detailed description thereof will be omitted. In general, a porous metal material is subjected to clogging of a machined surface during machining and an air permeability of the material is greatly decreased. Bearing performance is therefore extremely degraded. Clogging occurs when the material is plastically deformed during machining. One of the reasons why a ceramic material is used to form a porous body is based on clogging. More specifically, since the ceramic material is a material having no tenacity, it is not subjected to plastic deformation during machining such as cutting. Therefore, the porous body does not clog. Clogging of the porous body during machining can have an advantage in that bearing performance can be improved by properly controlling a clogging amount. It can be understood that an orifice is formed at an outlet of each of a large number of flow paths in the porous body. However, in a phenomenon of probability in which a large number of machining conditions such as plastic deformation during machining involve, it is difficult to cause desired clogging unless otherwise elaborated machining is performed. In addition, when dimensional accuracy as in the static pressure lead screw is required, it is impossible to satisfy both dimensional accuracy and the clogging amount. According to the present invention, nickel is plated on the ceramic porous body by electroless plating to optimize the flow rate (to be described in detail later). As shown in Fig. 4(a), after each flank 9 is formed to obtain desired geometrical accuracy by machining, portions indicated by hatched lines 9' are plated, so that the flow rate is adjusted to obtain maximum statical stiffness in accordance with the amount of a screw gap 8. According to such plating (to be described in detail later), the thickness of the plated layer can be accurately controlled by a plating time. As compared with the conventional clogging effect, a desired flow resistance can be easily obtained. Electroless plating will be briefly described below. As is well known, electroless plating is performed such that metal cations are attracted to a cathode by an external current effect. Electroless plating in a broad sense includes a plating technique for reducing and precipitating metal cations in an electrolytic solution without using an external current and is often called chemical plating. According to the feature of electroless plating, metal cations in an electrolytic solution are reduced and precipitated without using an external current. This method is classified into a technique in which cations of a metal (noble) having a higher potential than a metal (base) having a low potential are brought into contact with the base member to reduce and precipitate the noble metal as in substituted zinc plating or immersed gold plating, and a technique in which an object subjected to plating serves as a catalyst to reduce metal cations in an electrolytic solution and to precipitate a metal thereon as in chemical copper plating or electroless nickel (Ni) plating. It should be noted that a plating technique playing an important role on the industrial basis is a reduction method. Electroless plating is based on a chemical reaction on the surface of an object to be plated. Unlike in electric plating, plating is not concentrated on a portion having a high electric field intensity. The thickness of the plated layer is uniform, and plating can be performed on a portion where no electric field is present, e.g., within the porous body. In this manner, electroless plating has features different from those of electric plating. Of these methods, electroless nickel plating of a reduction method is most suitable as a means for controlling a flow resistance of a porous body and will be described in more detail below. Fig. 5 is a view for explaining electroless nickel plating as a method of controlling a flow resistance of a porous body according to the present invention. Reference numeral 113 denotes a porous body to be plated with nickel; 114, a holder; 115, a plating solution; 116, a water bath; and 118, a negative pressure tank connected to the holder 114 through a pipe 117 and to a vacuum pump 119. Reference numeral 120 denotes a negative pressure meter; and 121, a heater. Electroless nickel plating has the features described above, and the thickness of the plated layer can be controlled to be constant by a dipping time if the temperature is kept constant. Referring to Fig. 5, the holder 114 exposes only a surface 109 of the porous body 113 to a plating solution. A supply groove of the porous body 113 is connected to the pipe 117. Therefore, the diffusion depth of the plating solution in the porous body can be controlled by a negative pressure of the negative pressure tank 118. When the negative pressure is set to zero by a flow control valve 130 arranged midway along the pipe 117, the plating solution reaches only the surface layer portion of the porous body. Numerous pores present on the surface of the porous body 113 can be sealed. However, when plating is performed while the flow control valve 130 is open, an additional plating solution containing Ni cations is always replenished into the interior of the porous body 113. Therefore, the deep portion in the porous body 113 can be plated. In this manner, electroless nickel plating allows arbitrary control of the diffusion depth of the plating solution into the porous body by means of negative pressure suction as well as the thickness of the plated layer by the plating time. As compared with conventional mechanical clogging, the flow resistance of the porous body can be greatly, accurately, and easily controlled. For example, the flow resistance of the surface layer portion is set to be higher than that of the deep portion, thus increasing the control range of the flow resistance. In addition, the surface of the porous body can be sealed. Therefore, the unnecessary surface portion can be masked, thereby selectively obtaining a sealed surface portion of the porous body. As compared with the conventional technique utilizing plastic deformation, controllability of the flow resistance can be improved, and the control range can be widened. In addition, new effects are also obtained. Furthermore, if the flow rate of the plating solution is controlled, the thicknesses of the plated layers can be decreased from the surface layer of the porous body to the deep layer. The surface of the porous body 113 is turned with respect to the holding tool 114, a plated layer deep layer of the porous body 113 may be formed in addition to the plated surface layer. In addition to the effects of the above-mentioned embodiments, this embodiment provides the following effects. a) Since air (oil) supply efficiency of the porous restrictor can be improved as compared with the conventional restrictor and electroless nickel plating allows optimization of the flow resistance, the static pressure lead screw has high statical stiffness. b) Since the volume of the porous body having flow paths therein can be minimized, the pneumatic hammer tends not to occur even in a pneumostatic lead screw. c) Since the porous body is made of a ceramic material, no clogging during machining occurs. In addition, the ceramic material allows improvement of machining accuracy, is lightweight, and can have a small dimensional change although a temperature change occurs. Therefore, the static pressure lead screw is suitable for high-speed, high-accuracy operation. d) Since the thread ridge angle can be freely selected, the static pressure lead screw has a variety of applications. In particular, the ridge angle is formed to define a line perpendicular to the screw axis, high-accuracy as the primary purpose of the static pressure lead screw can be achieved. In addition, the static pressure lead screw having a nickel-plated layer has the same features as in the third embodiment described above. The state in which Ni is plated in the porous body will be described below to make the effect of nickel plating fully comprehensible. Figs. 7(a) and 7(b) show sectional structure models of a sintered porous body. Referring to Figs. 7(a) and 7(b), reference numerals 234 denote sintered particles; 235, bonding portions between the sintered particles 234; 236, pores, i.e., fluid paths of the porous body. Fig. 7(a) shows a cross section in which the sintered particles 234 are dominant, and Fig; 7(b) shows a cross section in which the pores are dominant. The sectional area of the flow paths 236 varies according to different sections, and the porous body is constituted as if gourd-like members are three-dimensionally stacked. For illustrative convenience in Figs. 7(a) and 7(b), spherical sintered particles 234 having identical diameters are regularly aligned. However, in practice, sintered particles 234 having different sizes are randomly stacked. Uniform flow paths are not necessarily formed in the porous body, and therefore, flow paths of different sizes are mixed therein. Since the porous body itself is formed by unique manufacturing techniques, it is not easy to obtain a desired flow resistance. Any means must be used to obtain a desired flow resistance in the existing porous material. In addition, a flow resistance control means is also required to increase a restrictor resistance in the surface layer portion, as described above. A sectional model having the porous restrictor plated with nickel is illustrated in Fig. 6. More specifically, reference numerals 22 denote originally large flow paths formed due to nonuniformity of the porous body; 23, small flow paths formed due to the same reason; 24, a flow-in side of the plating solution; 25, a flow-out side of the plating solution; 26, deep-layer plated films formed inside the porous body by increasing a supply amount of plating solution; and 27, surface-layer plated films formed by decreasing the supply amount of plating solution. The flow rate of the plating solution passing through the porous body can be controlled by a pressure difference between the flow-in side 24 and the flow out side 25. In this case, since the plating solution tends to flow through a low flow resistance path. Thus, more nickel is plated in the large flow path, regardless of the negative back pressure amount. For this reason, the plating solution is concentrated in the large flow paths 22 having a small flow resistance. Therefore, the plating solution entered into a deeper portion through the large flow paths 22. The plating solution is limited to the surface layer through the small flow paths 23. As a result, the total flow resistance of the porous body becomes uniform. However, since the plating solution is uniformly supplied to the flat portion on the surface of the porous body, the uniform thickness of the plated layer can be obtained, thereby maintaining flatness prior to plating. As is known, the plated Ni-film itself is a hard film having high resistance to corrosion, high wear resistance. The plated Ni-film is thus a film free from plastic deformation. For this reason, even after Ni is plated in and on the porous body, more accurate machining of the surface of the porous body can be performed by grinding or lapping. In particular, when alumina (Al₂O₃), silicon nitride (SiN), silicon carbide (SiC) or the like is used as a ceramic material for a porous body, the porous body itself is free from plastic deformation. Therefore, ultra accurate machining can be made up to the layer underlying the plated layer by using a diamond tool. Performance of the static pressure guide which is directly associated with improvement of machining accuracy can be greatly improved as compared with the conventional case. Fig. 8 is a graph showing test data representing characteristics of an Ni-plated porous restrictor bearing. As is apparent from Fig. 8, a load, acted on a sample obtained by sintering an annular porous portion in a ceramic disk, and compressed air was supplied to the porous portion. The bearing stiffness sample was measured. The dimensionless stiffness values are used to evaluate performance associated with bearing stiffness. In this case, stiffness of the bearing can be evaluated regardless of the shape and dimensions of the bearing and a supply pressure. As is apparent from Fig. 8, the Hi-plated porous restrictor bearing can have a dimensionless stiffness value of 0.5. In the conventional self-forming restrictor and the orifice restrictor, a maximum dimensionless stiffness value is as large as 0.2 to 0.3. Therefore, the porous bearing according to the present invention has a high stiffness value per unit area. According to the embodiment described above, the following effects are obtained: a) The flow resistance of the porous body can be accurately controlled. b) Both the surface and deep layers of the porous body can be plated, and the control range of the flow resistance can be increased by the degree of formation of the deep-layer plated film. c) The porous body can have the uniform flow resistance. d) Since the thickness of the plated film on the surface of the porous body is uniform, machining accuracy prior to plating can be easily maintained, and more accurate machining after plating can also be performed. e) The porous metal body can be replaced with a porous ceramic body free from plastic deformation. f) Use of the porous ceramic body allows ultra accurate machining of the surface of the porous body. The controllability of the flow resistance of the porous body can be greatly improved and the control range thereof can also be greatly widened. Unlike in the conventional flow resistance control means utilizing plastic deformation in which the porous body has poor reproducibility and productivity and more accurate machining cannot be performed, all conventional drawbacks can be solved by the present invention. Furthermore, additional new advantages are also obtained by the present invention, thereby obtaining a static pressure guide utilizing advantages of the porous restrictor and having a small flow rate and high bearing stiffness. The features of the porous restrictor static pressure guide having the flow resistance control means according to the present invention can be effectively utilized as a rotary bearing, a linear guide, a feed screw, or the like in a high-accuracy machine tool or measuring equipment requiring high speed, high stiffness, or high-accuracy positioning, and an apparatus for manufacturing electronic and optical components, or a semiconductor manufacturing apparatus. The fluid supplied to the static pressure guide is not specified. However, a gas or a liquid may be supplied to the static pressure guide. (Fifth Embodiment) Figs. 9 to 12 shows a fifth embodiment showing a static pressure uniaxial feed mechanism constituted by static pressure screws of the present invention. Referring to Fig. 9, reference numeral 301 denotes a male screw shaft, a flange of one end (left end) of which is supported by a thrust bearing 331 and a shaft for a radial bearing 330 and the other end (right end) of which is supported by a radial bearing 332 through a bushing 333. Reference numerals 302 and 302' denote nut cases into which the static pressure nuts consisting static pressure screws together with the male screw 301 according to the present invention are built. In this embodiment, two nuts are prepared as follows. One flank 9 of each thread ridge in Fig. 4(a) is sealed to prevent the fluid from flowing out from the porous body. The two nuts are joined together through a spacer 336 such that the right and left sealed surfaces are opposite to each other. A double-nut system is a conventional system used to adjust the preliminary load in the ball screw. The distance between the two nuts can be adjusted by changing the thickness of the spacer 336. A slider 328 connected to the male screw 301 is guided by the fluid bearing constituting a static pressure guide by means of a guide 329 along the longitudinal direction thereof. The guide 329, a stationary-side support plate 334, and a support-side support plate 335 are fixed on a base 337. The radial bearing 332 is constituted by the static pressure guide shown in Fig. 4(a). When the static pressure lead screw is combined with the rotatable or linearly movable static pressure bearing to constitute a feed mechanism, the feed mechanism free from solid friction in the movable parts of the mechanism can be easily assembled. Figs. 10(a) and 10(b) show test data representing ultra fine movement in the mechanism. A small rotation is given to the male screw by a fine movement actuator such as a piezoelectric element, and a linear displacement of the female screw is measured. More specifically, Fig. 10(a) shows a linear displacement of the female screw upon small rotation of the male screw, and Fig. 10(b) shows a linear stepwise displacement of the female screw when angular stepwise displacements are continuously applied to the male screw. As is apparent from Figs. 10(a) and 10(b), the static pressure lead screw according to the present invention has a movement resolution in units of nanometers. This resolution cannot be achieved by a mechanism subjected to solid friction since it receives an influence of stick-slip, thus exhibiting a great effect of the present invention. Fig. 11 shows measurement results wherein the displacement of the female screw with respect to the male screw, that is, a change in floating gap, is measured when an axial load acts on the female screw while the male screw is kept stationary. When the outer diameter of the male screw is given as 25 mm as a practical value, and the number of mating ridges per nut is 4, the statical stiffness (load/displacement) of the pneumostatic lead screw is higher than as 3 kgf/µm when compressed air Ps having a pressure of 5 kgf/cm² is supplied. This is achieved by a combination of the following effects. Since the shape of the static pressure lead screw of the present invention is simplified, machining accuracy can be improved. Since the porous ceramic body has a flow resistance controlled by an Ni-plated layer, high stiffness per unit area can be achieved. In addition, the screw gap can be controlled in a double-nut system. It is apparent from the results in Fig. 8 that the stiffness value can be further increased by more accurate machining. Fig. 12 shows test data obtained such that a rotary encoder is mounted on the male screw and a linear displacement of the female screw is measured by a laser interferometer while the angular displacement of the screw shaft is measured, and errors (lead errors complying with JIS B1192 - 1980, 1980) from ideal linear displacements with respect to the angular displacements. Referring to Fig. 12, a maximum variation e of the lead error is defined as a maximum value of variations from a recursive line of the cumulative lead errors within the overall screw length. A drunkenness e2π is defined as a maximum width of a lead error within any one lead. The most troublesome factor in error correction is the drunkenness in order to improve feed accuracy. The drunkenness in the static pressure screw according to the present invention is as low as 0.2 µm or less. The lead accuracy after machining of the male screw was 2 to 3 µm in the test. Therefore, when the static pressure lead screw is employed, lead accuracy can be increased by 10 times or more. This is because errors in shape, surface and pitch of the components are averaged by the fluid film and motion accuracy can be improved. This effect is called an averaging effect. In the above embodiment, the female screw is interlocked with the male screw through eight ridges, thus obtaining the above-mentioned averaging effect. The fluctuation is an error smaller by about 1/10 than that of the conventional high-accuracy ball screw. In addition, as shown in Fig. 9, when the static pressure lead screw is combined with a linear guide, the linear guide can be constituted by flat components. Therefore, machining can be performed with true linearity. Since the thread profile of the static pressure lead screw is a square, no bouyancy acts in the radial direction, thereby obtaining a feed mechanism with true linearity. When the thread profile is changed to a trapezoidal shape, the self-centering ability can be obtained. However, it is difficult to obtain a screw shaft with true linearity for machining the male screw. Even if such a lead screw is combined with a linear guide, the radial bouyancy acting on the female screw adversely affects true linearity of the feed mechanism. This drawback can be eliminated when the thread profile is changed to a square shape. When the feed mechanism is constituted by using the static pressure lead screw, the following effects can be additionally obtained. a) Since the feed mechanism free from solid friction can be achieved, a very high feed resolution can be obtained. b) Since the double-nut system can be employed to further adjust the screw gap, statical stiffness of the lead screw can be improved. c) Feed accuracy can be improved 10 times that machining accuracy of the component itself due to the averaging effect of the fluid film. d) The square screw thread is combined with the linear guide to achieve a feed mechanism with true linearity.

Claims: A porous static pressure guide for guiding a first member (2, 3, 10) defining a first surface in relation to an opposite object (1) defining a second surface, wherein said first member comprises a solid base member (3, 3') and a porous body (10) of ceramic material formed on the solid base member, and wherein said first and second surfaces are designed to allow relative guidance therebetween, characterized in that the porous body defines only a part (9) of the first surface, the remainder thereof being defined by the solid material of the base member (3 3'), and that at least one guide hole (6) is formed in the first member (2, 3, 10) to extend through the solid base member (3) into the porous body (10) and is arranged to supply a fluid to the interior of the porous body (10) for floating the same relative to the opposite object (1). A guide according to claim 1, wherein said opposite object (1) is movable along an axial direction of said solid base member (3, 3'). A guide according to claim 1, wherein said porous body (10) and said solid base member (3, 3') are movable along an axial direction of said opposite object (1). A guide according to claim 1, wherein said solid base member (3, 3'), said porous body (10), and said opposite object (1) are rotatable about one of said solid base member, said porous body, and said opposite object. A guide according to claim 1, wherein said solid base member (3, 3') is made of a metal material. A guide according to claim 1, wherein said solid base member (3, 3') is made of a ceramic material. A guide according to claim 1, wherein a plated layer (9') is formed on at least a surface portion of said porous body (10). A guide according to claim 7, wherein said plated layer (9') comprises an electroless nickel plating layer. A method of manufacturing a static pressure guide according to any one of claims 1 to 6, characterized by the step of forming the porous body (10) of a ceramic material on the solid base member (3), together constituting said first member (2, 3, 10), so as to define at least a predetermined gap (8) relative to the opposite object (1), wherein a guide hole (6) is formed to extend through said solid base member (3) and inside said porous body (10) to supply fluid to the interior of said porous body, thereby floating said porous body (10) relative to the opposite object (1). A method according to claim 9, further including the step of forming a plated layer (9') on at least a surface portion of said porous body (10). A method according to claim 10, wherein the step of forming said plated layer (9') comprises electroless nickel plating.

Inventors: ISHIHARA, SUNAO, KANAI, MUNENORI, KINOSHITA, HIROO
Applicants: NIPPON TELEGRAPH AND TELEPHONE CORPORATION
Application year: 1987
Main classification: F16H25
IPC codes: F16H25