preferred embodiments of the present invention will now be described with reference to the drawings . [ 0023 ] fig1 is a side view showing a machine tool to which a linear guide apparatus according to the present invention is applied . in fig1 the reference numeral 10 designates a bed and 2 designates a column . a spindle head 4 is vertically movably mounted to the column 2 . the reference numeral 5 designates a spindle . a table 12 is provided on the bed 10 , and moves back and forth on the bed 2 . in the below - described embodiments , a linear guide apparatus according to the present invention is applied as a guide for the table 12 . [ 0026 ] fig2 shows , together with a table , a linear guide apparatus according to a first embodiment of the present invention as viewed from the front in the moving direction of the table . this embodiment relates to application to a roller - type rolling guide for guiding a table in a machine tool . in fig2 the reference numeral 10 designates a bed and 12 designates the table . a ball screw 13 , constituting a feed mechanism for the table 12 , is provided on the upper surface of the bed 10 . a pair of guide rails 14 , disposed on either side of the ball screw 13 , is laid in parallel with the axial direction of the ball screw 13 . guide units 15 , each constituting the linear guide apparatus of this embodiment , are mounted to the lower surface of the table 12 each in engagement with the guide rail 14 . [ 0028 ] fig3 is a side view of the linear guide apparatus of this embodiment . as shown in fig3 each guide unit 15 comprises a rolling guide section 16 and a brake section 17 , disposed on the guide rail 14 . a total of 4 guide units 15 are mounted to the front and back portions on either side of the table 12 shown in fig2 . according to this embodiment , the rolling guide section 16 and the brake section 17 are designed as separate components . it is , however , possible to provide the two sections as an integral structure . further , though in this embodiments the brake sections 17 are of the same number as the rolling guide sections 16 , the number of the brake sections 17 may not necessarily be the same as the rolling guide sections 16 , i . e ., more or fewer brake sections than rolling guide sections may be employed depending upon the machine to which the apparatus of the present invention is applied . as shown in fig4 the rolling guide section 16 is a known rolling unit having a plurality of rollers 18 within it . on either side of the guide rail 14 , generally v - shaped guide grooves 19 extend in the longitudinal direction . the upper and lower surfaces of the guide grooves 19 have roller - rolling surfaces 19 a , 19 b on which the rollers 18 roll . the roller - rolling surfaces 19 a , 19 b are symmetrical horizontally and vertically , forming an angle of 90 ° with each other . the guide unit 15 is so designed that the full weight load of the table 12 is received by the rolling guide section 16 , whereas no weight load is applied from the table 12 to the brake section 17 . [ 0031 ] fig5 shows a cross - sectional view of the brake section 17 . in fig5 the reference numeral 20 designates amounting block that constitutes the body of the brake section 17 , and 22 designates brake shoes . the mounting block 20 of the brake section 17 is a steel block having a u - shaped cross - section . each brake shoe 22 is a steel shoe which has a generally trapezoidal cross - section , corresponding to the shape of the guide groove 19 , so that the shoe as a whole can closely fit the guide groove 19 . the inclined surfaces of the brake shoe 22 are sliding surfaces which slide on the roller - rolling surfaces 19 a , 19 b of the guide rail 14 . according to this embodiment , plate - shaped sliding members 21 a , 21 b , mounted to the brake shoe 22 , slide on the roller - rolling surfaces 19 a , 19 b . the sliding members 21 a , 21 b may preferably be made of a fluororesin , in particular a polytetrafluoroethylene turcite ( trade name , available from busak + shamban k . k .). a metal shoe may also be used . in that case , a solid lubricant may be embedded in the surfaces of the sliding members 21 a , 21 b . alternatively , it is possible to use an oil - free sliding member , for example oiles ( trade name , available from oiles corporation ), which is impregnated with a lubricating agent . compression springs 26 are disposed in the space between the back surface of the brake shoe 22 and the inner side surface of the mounting block 20 , so that the brake shoe 22 is pressed against the roller - rolling surfaces 19 a , 19 b at an appropriate pressure by the elastic force of each compression spring 26 . the brake shoe 22 itself has thin portions 27 which are designed to be bent by the force applied from the compression spring 26 . the brake shoe 22 has in the peripheral portion flange portions 22 a , and a plurality of adjustment bolts 24 are screwed into the flange portions 22 a symmetrically with respect to the center . the brake shoe 22 is fastened , against the elastic force of the compression springs 26 , to the inner side surface of the mounting block 20 by means of the bolts 24 . the adjustment bolts 24 are inserted from bolt holes 25 that penetrate the side portion of the mounting block 20 . as shown in fig3 end plates 30 , 31 are mounted to the ends of the brake section 17 . the end plates 30 , 31 function to remove dust adhering to the roller - rolling surfaces 19 a , 19 b of the guide rail 14 . the same end plates 30 , 31 are provided also in the guide section 16 . a detailed description will now be given of the pressing force that presses the brake shoes 22 against the guide rail 14 in the brake section 17 . as a result of experiments carried out by using the linear guide apparatus of this embodiment , it has been found that when table 12 of an about one - meter square is supported by the rolling guide sections 16 consisting of four units , two and two on either side of the table , each unit specifically being # 55 linear roller way manufactured by nippon thomson co ., ltd ., the degree of damping increases about threefold by application of about 1000 n pressing force by each unit of the brake section 17 , as compared to the case of applying no pressing force , achieving an adequate enhancement of damping capacity . in this connection , referring to fig5 f ru , f rd , f lu and f ld designate the pressing forces that press the sliding members 21 a , 21 b of the brake shoes 22 against the roller - rolling surfaces 19 a , 19 b of the guide rail 14 . the total pressing force f is as follows : because of the horizontal and vertical symmetry , the pressing force applied to each of the roller - rolling surfaces 19 a , 19 b of the guide rail 14 is as follows : assuming that the sliding members 21 a , 21 b each have a width of 8 mm and a length of 120 mm , the specific pressure applied to each of the sliding members 21 a , 21 b will be determined as follows : the pressure value thus determined falls within a proper pressure range in a practical point of view in the case of utilizing the roller - rolling surfaces 19 a , 19 b as sliding surfaces for the brake shoes 22 . with respect to the compression springs 26 of the brake section 17 , on the other hand , the forces f r , f l nipping the guide rail 14 from either side can be calculated as follows : f r = f l = f ru /{ square root }{ square root over ( )} 2 + f rd /{ square root }{ square root over ( )} 2 = 354 ( n ) thus , the compression springs 26 , 26 on either side of the guide rail 14 must have such a spring force as to nip the guide rail 14 at 354 n . while the table 12 is moving , it is guided by the rolling guide sections 16 . taking the advantage of rolling guides , the table 12 can be transferred at a high speed . further , when the table 12 is moving , the brake shoes 22 are pressed against the roller - rolling surfaces 19 a , 19 b by the above - described pressing force f , whereby an appropriate frictional force is generated . accordingly , as described above , the degree of damping increases about threefold as compared to the case of not generating a frictional force , enabling effective damping of cutting vibrations during machining . further according to the present brake section , each brake shoe 22 is made to closely fit the guide groove 19 , defining the roller - rolling surfaces 19 a , 19 b , by utilizing the simple shape of the brake shoe , while the brake shoe 22 is spring - biased by the compression spring 26 . in addition , the thin portions 27 are provided in the brake shoe 22 , so that the brake shoe 22 has such a flexible structure that it can bend by the elastic force of the compression spring 26 . thus , the brake section 17 of this embodiment , unlike the conventional braking mechanisms , does not have a complicated mechanism or a hard structure which could form a gap between a brake shoe and a guide rail . the brake section 17 does not form even a slight gap between the brake shoe 22 and the guide rail 14 , and can securely provide a sufficient damping capacity to the linear guide apparatus . the sliding members 21 a , 21 b mounted to the brake shoe 22 wear gradually during a long period of operation of the apparatus . however , since a constant force from the compressing springs 26 keeps acting on the brake shoe 22 , a change in the frictional force due to the wear of the brake shoe can be made extremely small . further , the use of turcite , which has excellent sliding properties , for the sliding members 21 a , 21 b or the use of oiles sliding members makes it possible to maintain the damping capacity over a long period of time without maintenance and without causing damage to the roller - rolling surfaces 19 a , 19 b of the guide rail 14 . the second embodiment relates to application of the present invention to a ball - type rolling guide . instead of the known rolling guide using the rollers 18 employed in the first embodiment , a known rolling guide using balls is employed in this embodiment . [ 0049 ] fig6 shows a cross - sectional view of the brake section 32 of this embodiment . guide grooves 33 , each having a semicircular cross - section , are formed in the both side surfaces of the guide rail 14 . the curved surface of each guide groove 33 serves as a ball - rolling surface . a sliding member 34 , which slides on the ball - rolling surface of the guide groove 33 , is provided integrally in each of the brake shoes 22 . the sliding member 34 has a curved surface , whose curvature is made the same as that of the curved surface of the guide groove 33 so that the sliding member 34 closely fits the guide groove 33 , and extends in the long direction of the guide rail 14 . as with the first embodiment , a resin sliding member or an oil - free metal sliding member , such as the above - described turcite or oiles , may be used as the sliding member 34 . the components according to the second embodiment , other than the brake shoes 22 , are the same as the first embodiment . the same components are given the same reference numerals , and a description thereof is herein omitted . as described hereinabove , the present invention is applicable not only to a roller - type rolling guide but also to a ball - type rolling guide . the brake section according to the present invention , unlike the conventional braking devices , has a soft structure and does not have a complicated mechanism or a hard structure which could form a gap between a brake shoe and a guide rail , and can therefore securely provide a sufficient damping capacity to the linear guide apparatus . [ 0054 ] fig7 shows the brake section of the linear guide apparatus according to a third embodiment of the present invention . the third embodiment adds to the brake section 17 of the first embodiment , shown in fig5 pressing force adjustment bolts 42 for fine adjustment of the pressing force of the brake shoes 22 . the other components are the same as those of the brake section 17 of fig5 . screw holes 41 , penetrating the side portions of the mounting block 20 , are provided at locations corresponding to the compression springs 26 disposed in the long direction , and the pressing force adjustment bolts 42 are screwed into the screw holes 41 . the front end of each pressing force adjustment bolt 42 is in contact with the compression spring 26 , while the rear end protrudes from the mounting block 20 . the pressing force adjustment bolt 42 has a male screw portion formed over the full length of the bolt . the portion of bolt 42 protruding from the mounting block 20 is in screw engagement with a lock nut 43 , and the pressing force adjustment bolt 42 is secured by the lock nut 43 to the mounting block 20 . according to the third embodiment having the above construction , the pressing force can be adjusted in the following manner : as the pressing force adjustment bolt 42 is screwed and advanced in the screw hole 42 , the compression spring 26 is increasingly compressed , whereby the pressing force of the compression spring 26 , acting on the brake shoe 22 to press it against the roller - rolling surfaces 19 a , 19 b of the guide rail 14 , increases accordingly , whereas the pressing force decreases as the pressing force adjustment bolt 42 is moved back in the opposite direction . accordingly , by adjusting the screwing degree of each pressing force adjustment bolt 42 and fastening the lock nut 43 to fix the screwing degree , the pressing force of the brake shoe 22 as a whole can be distributed evenly over the roller - rolling surfaces 19 a , 19 b . the fourth embodiment , shown in fig8 relates to application of the preceding embodiment , i . e . the embodiment using the pressing force adjustment bolts 42 for evenly distributing the pressing force of the brake shoe 22 , to a ball - type rolling guide . the fourth embodiment is the same as the second embodiment shown in fig6 except for the provision of the pressing force adjustment bolts 42 shown in fig8 . the same components as the second embodiment are given the same reference numerals , and a description thereof is herein omitted . according to the fourth embodiment , the pressing force of the brake shoe 22 can be distributed evenly over the ball - rolling surface of the guide groove 33 . while the linear guide apparatus of the present invention has been described with reference to the preferred embodiments which relate to application as a guide for a table of a machine tool , the present invention can also be applied to various other movable bodies of a machine tool , such as a spindle head , a saddle , a cross rail , etc . as described hereinabove , the brake section of the linear guide apparatus according to the present invention , unlike the conventional braking devices , utilizes an elastic member as a biasing means , has a flexible structure , and does not have a complicated mechanism or a hard structure that could form a gap between a brake shoe and a guide rail . the addition of such a gap - free braking device to a conventional rolling guide can provide a sufficient damping capacity to the linear guide apparatus .