Abstract:
A brake master cylinder which prevents a contact between a projection of a spring retainer and a stopper of a sleeve when a piston is suddenly retracted by an operation of a pressure applying device of a brake system or by an air relieving operation to offer a high reliability without deformation and damages of the spring retainer and the sleeve. A groove extended in axial direction is provided on the sleeve. A distance between a rear end surface of the groove and a radial projection of a first spring retainer when the brake is not applied corresponds to the total of a distance of a retracting distance of a second piston from the position defined by the non-braking operation to a position where a piston port and an opening of a reservoir communication conduit are overlapped and a predetermined additional distance.

Description:
This application is based on and claims priority under 35 U.S.C. §119 with respect to Japanese Application No. 2000-006821 filed on Jan. 14, 2000, the entire content of which is incorporated herein by reference. 
     FIELD OF THE INVENTION 
     This invention generally relates to vehicle braking. More particularly, the present invention pertains to a brake master cylinder for a braking device of a vehicle. 
     BACKGROUND OF THE INVENTION 
     A known brake master cylinder device is described in Japanese Patent Publication 04-27060. The disclosed brake master cylinder includes a cylinder housing including a cap engaged with the opening of a body. A first piston and a second piston penetrate through the cap are slidably disposed via a piston guide in the cylinder housing. A resin made sleeve for determining the position of the first piston is slidably attached to the first piston and is disposed in the cylinder housing. 
     A first pressure chamber is formed with the first piston, the second piston, and the sleeve. A second pressure chamber is formed with the second piston and the inner wall of the body. The first pressure chamber and the second pressure chamber are provided with a spring mechanism for biasing the first piston and the second piston rearwardly. 
     In this known brake master cylinder, when the first piston and the second piston are slidably moved into the first pressure chamber and the second pressure chamber respectively by brake pedal depression, the fluid pressure in the respective pressure chambers is increased to convey the pressurized brake fluid from an output port to respective brake systems. 
     The spring mechanism comprises a return spring, a guide screw, and a spring retainer. The guide screw having a forwardly projecting head portion is engaged with the first piston. The spring retainer slidably moves on the guide screw and contacts the rear side of the head portion of the guide screw. The return spring is provided in a compressed state between the spring retainer and the first piston. 
     The spring retainer includes a projection protruding in the radially outward direction. The sleeve is provided with an axially extending guide groove for slidable engagement by the projection and a stopper blocking the axial movement of the projection of the spring retainer and restricting the retraction of the projection. This structure makes it possible to reduce the size of the brake master cylinder and to restrict the limitation for the retracted position of the first piston and the second piston. 
     The air relieving operation for relieving air remaining in the brake fluid is conducted when the brake device is assembled. The air relieving operation includes a so-called pumping operation for releasing bubbled air remaining in the brake fluid from a master cylinder reservoir to the atmosphere by strongly stepping on the brake pedal several times while injecting the brake fluid into the master cylinder reservoir. When air is still remaining in the brake fluid in the master cylinder, the first and the second pistons are rearwardly returned by an unnecessary strong force because the bubbled air compressed by the stepping operation of the brake pedal is expanded simultaneously with releasing of the brake pedal. 
     However, in this known brake master cylinder in which the position of the second piston is determined by the projection of the spring retainer contacting the stopper of the sleeve, the projection of the spring retainer and the stopper of the sleeve may be deformed or damaged by the severe contact between the projection of the spring retainer and the stopper of the sleeve when the aforementioned air relieving operation is conducted. In addition, because the final retracted position of the second piston when the brake pedal is released is determined based on the position that an opening of the piston port provided on the second piston overlaps with the back side of the cup seal, which is the position when the brake is not applied, bubbled air in the brake fluid may not be completely relieved to the atmosphere through the master cylinder reservoir. 
     In an electronic control brake system, the flow of brake fluid may be sometimes reversed into each pressure chamber of the master cylinder by a pump connected to a brake piping system. Particularly when the flow of the brake fluid is reversed into the second pressure chamber, the second piston is forced to be further moved in the rearward direction from the retracted position, which may deform and damage the projection of the spring retainer and the stopper of the sleeve. 
     In light of the foregoing, a need exists for a brake master cylinder which is not as susceptible to the same disadvantages and drawbacks as those discussed above. 
     A need also exists for a brake master cylinder having a relatively high degree of reliability in which deformation and damage will not occur by contact between a projection of a spring retainer and a stopper of a sleeve when a second piston is suddenly retracted by the operation of a pressure applying device of the brake system or by the air relieving operation. 
     SUMMARY OF THE INVENTION 
     The brake master cylinder of the present invention includes a cylinder housing formed by a body having an internal bore open at one end and a cylinder cap assembled to the internal bore at the opening end, a first piston positioned in the cylinder housing and slidably movable in the axial direction, and a second piston positioned forward of the first piston and slidably movable in the axial direction in the cylinder housing, and a sleeve located in the cylinder housing and slidably supporting the first piston and the second piston. The second piston is retractable by a predetermined distance from the non-braking operation position of the second piston. 
     Because the second piston is retractable by the predetermined distance from the non-braking operation position, any member which moves forward and rearward in one unit with the second piston does not contact the other fixed members under the air relieving operation. This thus prevents the movable and fixed members from deforming and becoming damaged. 
     A pressure chamber is formed between the second piston and the cylinder housing, a reservoir connecting port is formed in the body for connection to a reservoir, and a generally radially extending reservoir communication conduit is formed in the sleeve, opens to the outer diameter surface of the second piston, and establishes communication between the reservoir connecting port and the pressure chamber. A first cup seal is provided between the second piston and the body at a position forward of the sleeve, a second cup seal is provided between the sleeve and the second piston at a position rearward of the reservoir communication conduit, and a piston port is provided on the second piston at a position rearward of the first cup seal to establish communication between the reservoir communication conduit and the pressure chamber during non-braking operation. The predetermined distance corresponds to the total of the retracting distance of the second piston from the non-braking operation position to the position at which an opening of the piston port and an opening of the reservoir communication conduit overlap and a predetermined additional distance. 
     Thus, in accordance with the present invention, the second piston is retracted from the non-braking operation position to the position at which the opening of the piston port and the opening of the reservoir communication conduit overlap and is further retractable by the predetermined additional distance. Accordingly, fluid communication between the pressure chamber and the reservoir communication conduit is always ensured to completely relieve the bubbled air in the brake fluid to the atmosphere through the master cylinder reservoir. 
     The predetermined distance can also be defined by the retracting distance of the second piston from the non-braking operation position to the position at which the opening of the piston port and a lip of the second cylinder cup overlap. The second piston can thus be retracted from the non-braking operation position to the position at which the opening of the piston port and the lip of the second cup seal positioned rearward of the first cup seal overlap. Accordingly, this enables the retracting amount of the second piston to be predetermined to be considerably large to avoid the contact of any member moving forward and rearward as a unit with the second piston with other fixed members, thus preventing deformation and damage of the movable and fixed members. 
     Further, the predetermined distance can correspond to the total of the retracting distance of the second piston from the non-braking operation position to the position at which the front end surface of the second piston and the opening of the reservoir communication conduit overlap and another predetermined additional distance. 
     The brake master cylinder also includes a spring retainer having a flange portion at a front end portion thereof that contacts the rear end portion of the second piston, a rod having one end engageable with the spring retainer, a rod engaging member fixed to a bottom of an internal bore opening to the forward of the first piston with the other end of the rod being engaged with the rod engaging member, and a compressed spring provided between the spring retainer and the rod engaging member. The predetermined distance is equal to the moving distance of the radial projection provided on the flange portion from the rear end portion of the second piston to the rear end portion of an axial groove provided on the sleeve in axial direction, with the second piston being retractable by the predetermined distance. Because the predetermined distance is defined in this way, and because the axial groove extending in the axial direction can be easily formed when the sleeve is made by resin molding, a mechanism defining the retracting distance of the second piston can be provided without increasing the manufacturing cost. The mechanism defining the retracting distance of the second piston prevents the first piston and the second piston from dropping off from the cylinder housing during delivery and handling of the brake master cylinder. 
     The predetermined distance can be equal to the moving distance of the radial projection provided on the flange portion from the rear end of the second piston to a rear stepped portion of a large diameter portion provided on a stepped internal bore of the cylinder housing. Because the rear stepped portion of the large diameter portion can be easily formed when the cylinder housing is made by casting, a mechanism defining the retracting distance of the second piston can be provided without substantially increasing the cost. Also, the mechanism defining the retracting distance of the second piston prevents the first piston and the second piston from dropping off from the cylinder housing during delivery and handling of the brake master cylinder. 
     In accordance with another aspect of the invention, a brake master cylinder includes a cylinder housing having an internal bore open at one end, a cylinder cap assembled to the internal bore at the open end of the body, a first piston positioned in the cylinder housing and slidably movable in the axial direction, a second piston positioned in the cylinder housing forward of the first piston and slidably movable in the axial direction, a radially extending projection engaging a rear end portion of the second piston to move rearwardly with the second piston upon rearward movement of the second piston, and a sleeve positioned in the cylinder housing and slidably supporting the first piston and the second piston. 
     The radially extending projection extends into a groove formed in the sleeve, with the radially extending projection being spaced from a rear end wall of the groove by a predetermined distance to permit the radially extending projection to move rearwardly by the predetermined distance during non-braking operation without contacting the end wall of the groove. 
     In accordance with another aspect of the invention, a brake master cylinder includes a cylinder housing having an internal stepped bore open at one end, a larger diameter portion and a smaller diameter portion with a stepped portion located between the larger and smaller diameter portions, a cylinder cap assembled to the internal bore at the open end of the body, a first piston positioned in the cylinder housing and slidably movable in the axial direction, a second piston positioned in the cylinder housing forward of the first piston and slidably movable in the axial direction, and a sleeve positioned in the cylinder housing and slidably supporting the first piston and the second piston. The sleeve possess a groove. A radial projection engages a rear end portion of the second piston to move rearwardly with the second piston upon rearward movement of the second piston. The radial projection extends through the groove of the sleeve and into the larger diameter portion of the stepped bore of the cylinder housing. The radial projection is spaced from the rear end wall of the groove and from the stepped portion by at least a predetermined distance to permit the radial projection to move rearwardly by the predetermined distance during non-braking operation without contacting the end wall of the groove and without contacting the stepped portion. 
    
    
     BRIEF DESCRIPTION OF THE DRAWING FIGURES 
     The foregoing and additional features and characteristics of the present invention will become more apparent from the following detailed description considered with reference to the accompanying drawing figures in which like reference numerals designate like elements and wherein: 
     FIG. 1 is a cross-sectional view of a brake master cylinder according to a first embodiment of the present invention; and 
     FIG. 2 is a cross-sectional view of a brake master cylinder according to a second embodiment of the present invention. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Several embodiments of a brake master cylinder according to the present invention are described below with reference to FIGS. 1 and 2. Referring initially to FIG. 1, the brake master cylinder according to a first embodiment is comprised of a cylinder housing  10  including a body  11  and a cylinder cap  12 . The brake master cylinder also includes a first cup seal  21 , a first spacer  22 , a sleeve  23 , a second cup seal  24 , a second spacer  25 , and a guide  26  which are disposed in the cylinder housing  10 . The brake master cylinder further includes a first piston  31 , and a second piston  32 . 
     The body  11  is made of metal and includes a stepped internal bore  11   a  opening to the rear end (i.e., the right end of FIG.  1 ), reservoir connecting ports  11   b ,  11   c  connected to a reservoir (not shown) via a connector  19 , and output ports  11   d ,  11   e  each connected to a wheel cylinder (not shown) via a respective hydraulic brake circuit. An internally screw threaded portion  11   f  is formed adjacent the opening end portion of the internal bore  11   a . The first cup seal  21  and the first spacer  22  are disposed in the internal bore  11   a  of the body  11 . The first cup seal  21  is positioned between the body  11  and the second piston  32  and seals in a liquid-tight manner a second pressure chamber R 2  which communicates with the output port  11   e . The annular first spacer  22  is positioned between the first cup seal  21  and the sleeve  23 , and allows fluid flow in the axial direction at the inner and outer periphery. The first spacer  22  also prevents a part of the first cup seal  21  from cutting into or cutting off a reservoir communication conduit  23   a  of the sleeve  23  when pressure is generated at the second pressure chamber R 2 . 
     The cylinder cap  12  includes an external screw threaded portion  12   a  that threadably engages the internally screw threaded portion  11   f  of the body  11  at the middle portion of the outer periphery of the cylinder cap  12 . The cylinder cap  12  also includes a cylindrical portion  12   b  that engages the internal bore  11   a  of the body  11  and accommodates a smaller diameter cylindrical portion of the sleeve  23 . The cylinder cap  12  is assembled in a liquid-tight manner to the cylinder body  11  via a first O-ring  13  and a second O-ring  14 . The cylinder cap  12  fastens the first cup seal  21 , the first spacer  22  and the sleeve  23  at the end surface of the cylindrical portion  12   b , and fastens the second cup seal  24 , the second spacer  25  and the guide  26  at a right end stepped portion  12   c   1  of a stepped internal bore  12   c  of the cylinder cap  12 . 
     The second annular spacer  25  is provided between the second cup seal  24  and the guide  26 , and allows fluid flow in the axial direction at both the inner and outer peripheries while also preventing a part of the second cup seal  24  from cutting into or cutting off a second communication groove  26   a  of the guide  26  when pressure is generated in a first pressure chamber R 1 . 
     A third cup seal  15  is positioned at the inner periphery of the right end portion of the cylinder cap  12 . A third O-ring  16  is positioned at the outer periphery of the right end portion of the cylinder cap  12 . The first O-ring  13  assembled at the outer periphery of the left end portion of the cylinder cap  12  provides a liquid-tight seal between the body  11  and the cylinder cap  12 . The second O-ring  14  is assembled to the inner periphery of the body  11  at a position rearward of or rightward of the O-ring  13 , and provides a liquid-tight seal between the body  11  and the cylinder cap  12 . The third cup seal  15  provides a liquid-tight seal between the inner periphery of the cylinder cap  12  and the outer periphery of the first piston  31 , while the third O-ring  16  provides a liquid-tight seal between a brake booster (not shown) and the cylinder cap  12 . The outer periphery of the rear end or right end of the cylinder cap  12  possesses a hexagonal shape. By rotating the hexagonal portion with an appropriately shaped tool, the cylinder cap  12  is capable of being assembled to and disassembled from the body  11 . 
     The cylindrical sleeve  23  can be made of resin and has a stepped portion on its outer periphery. A fourth cup seal  27  is positioned on the inner periphery of the left end portion of the cylindrical sleeve  23  and a fourth O-ring  28  is positioned on the outer periphery of the left end portion of the cylindrical sleeve  23 . 
     The sleeve  23  is disposed between and supported by the internal bore stepped portion of the body  11  and the end surface of the cylindrical portion  12   b  of the cylinder cap  12 . The fourth cup seal  27  provides a liquid-tight seal between the sleeve  23  and the second piston  32 , and the fourth O-ring  28  provides a liquid-tight seal between the sleeve  23  and the body  11 . 
     The sleeve  23  is provided with the reservoir communication conduit  23   a , a first communication groove  23   b , a groove  23   c , and a projection  23   d . A plurality of reservoir communication conduits  23   a  formed in an inclined manner towards the large diameter left end portion of the sleeve  23  and provided at a predetermined interval in the peripheral direction are always in communication with a reservoir connecting port  11   c  via an annular conduit P 1  formed between the body  11  and the sleeve  23 . The reservoir communication conduits  23   a  are also in communication with a piston port  32   a  provided on the second piston  32  via a gap between the first spacer  22  and the second piston  32 . 
     A plurality of communication grooves  23   b  positioned at a predetermined interval in the peripheral direction and extending straight along the axial direction on the inner periphery of the sleeve  23  are provided for effecting communication between the first pressure chamber R 1  formed between the first piston  31  and the second piston  32  and a recess portions of the second cup seal  24  and the fourth cup seal  27 . 
     The groove  23   c  is formed along or includes a small diameter cylindrical portion and a large diameter cylindrical portion. The groove  23   c  extends in the axial direction and opens towards the radial direction to always connect the first pressure chamber R 1  with the output port  11   d . The rear end portion  23   c   1  of the groove  23   c  functions as a stopper that restricts the retracting distance of the first piston  31  and the second piston  32  when a radial projection  35   a  provided on a flange portion of a spring retainer  35  contacts the rear end portion  23   c   1  of the groove  23   c.    
     The projection  23   d  is formed on the small diameter right end portion of the sleeve  23  and projects in the axial direction. The projection  23   d  is inserted into the cup-shaped recess portion of the second cup seal  24 . 
     The cylindrical guide  26  can be made of resin and is assembled in the internal bore  12   c  of the cylinder cap  12 . The cylindrical guide  26  is provided with the second communication groove  26   a  extending along the outer periphery of the cylindrical guide  26  to both ends of the cylindrical guide  26 . A plurality of communication grooves  26   a  formed along the outer periphery of the guide  26  in axial direction and possessing a U-shape along the both ends of the guide in the radial direction are provided at a predetermined interval and forms a first communication conduit adjacent the back surface of the second cup seal with the second spacer  25 . 
     The second communication groove  26   a  is always in communication with the reservoir connecting port  11   b  via a second communication conduit that includes an annular groove  12   d  provided on the front end portion of the cylinder cap  12  and a communication bore  12   e  (a plurality of such bores are provided at a predetermined interval in the peripheral direction) and via an annular conduit P 3  formed between the body  11  and the cylinder cap  12 . The second communication groove  26   a  is always in communication with a piston port  31   a  provided on the first piston  31  through a gap between the second spacer  25  and the first piston  31  and is always in communication with the cup-shaped recess portion of the cup seal through a gap between the cylinder cap  12  and the first piston  31  at the rear end portion of the guide  26 . 
     The annular groove  12   d  provided on the cylinder cap  12  possesses a diameter larger than that of the second cup seal  24  and is formed rearwardly adjacent the second cup seal  24 . The annular groove  12   d  is tapered in such a manner that the diameter of the outer peripheral wall gradually increases from the rear to the front and opens towards the inner periphery of the cylinder cap  12  to communicate with the communication groove  26   a  of the guide  26 . The communication bore  12   e  extending from the outer periphery of the cylinder cap  12  through the front outer peripheral portion of the annular groove  12   d  communicates the annular groove  12   d  with the annular conduit P 3  and is inclined upwardly towards the annular conduit P 3 . The structure of the communication bore  12   e  is effective for positioning the reservoir connecting port  11   b  at the forward position of the guide  26 , thus improving the assembly of the brake master cylinder to the vehicle body. 
     The first piston  31  can be made of metal is inserted into the cylinder housing  10  through the cylinder cap  12  and is slidably supported in the axial direction by the sleeve  23  and the guide  26 . 
     The first rod  33  can be made of metal and is assembled in one unit to the first piston  31  via the first retainer  34  and moves the in axial direction as one unit with the first piston  31 . The first retainer  34  can be made of metal and also serves as a spring retainer of the first spring S 1  to be fixedly engaged with the right end portion of the first rod  33 . The first retainer  34  is fitted into the internal bore stepped portion  31   b  of the piston  31  by press fit. 
     The first spring retainer  35  can be made of metal and is positioned between the first spring S 1  and the second piston  32 . The right end of the first spring retainer  35  is detachably connected in the left direction to a head portion  33   a  at the left end of the first rod  33 . The left end of the retainer  35  includes a radial projection  35   a  extending radially outwardly. The radial projection  35   a  extends to the large diameter portion  12   c   2  of the stepped internal bore  12   c  of the cylinder cap  12  through the groove  23   c  provided on the sleeve  23 . 
     The first spring S 1  is disposed in compression to have a predetermined attaching height or length by virtue of the first retainer  34  fixedly engaged with the first piston  31 , the first rod  33  fixedly engaged with the first retainer  34 , and the first spring retainer  35  connected to the first rod  33 . 
     The second piston  32  can be made of metal and is positioned coaxially with respect to the first piston  31 . The second piston  32  is slidably supported in the axial direction by the sleeve  23  in the cylinder housing  10 . 
     The second rod  36  can be made of metal and is assembled to the second piston  32  via the second retainer  37  to form one unit. The second retainer  37  is positioned at the right end portion of the second rod  36 , and the second rod  36  moves in the axial direction as a unit with the second piston  32 . The second retainer  37  can be made of metal and also serves as a spring retainer of the second spring S 2 . The second retainer  37  is fixedly engaged with the right end portion of the second rod  36  and is fitted into the internal stepped portion  32   b  of the second piston  32  by press fit. 
     A second spring retainer  38  which can be made of metal is provided between the second spring S 2  and the body  11 , and is detachably connected in the left direction to a head portion  36   a  of the second rod  36  at right end portion of the second spring retainer  38 . 
     In the embodiment of the present invention described above, when the brake master cylinder is assembled to the vehicle and brake fluid is filled in the cylinder housing  10  to move the first piston  31  in the axial direction (i.e., to the left in FIG.  1 ), the piston port  31 a of the first piston  31  passes through the second cup seal  24 , and communication between the first pressure chamber R 1  and the reservoir connecting port  11   b  is blocked to generate pressure in the first pressure chamber R 1 . 
     The second piston  32  thus moves in the axial direction to the left in FIG.  1  and the piston port  32   a  of the second piston  32  passes through the first cup seal  21  to block communication between the second pressure chamber R 2  and the reservoir connecting port  11   c , and pressure is generated in the second pressure chamber R 2 . Accordingly, pressurized fluid moves from the first pressure chamber R 1  to the output port  11   d  (the port connected to the wheel cylinder) and from the second pressure chamber R 2  to the output port  11   e  (the port connected to the wheel cylinder) to provide the braking effect on each wheel cylinder. 
     The air relieving operation relieving remaining air in the brake fluid is conducted after assembling the brake master cylinder to the vehicle and before filling the brake fluid in the cylinder housing. The air relieving operation includes so-called pumping operation for relieving bubbled air remaining in the brake fluid from a master cylinder reservoir to the atmosphere by repeatedly stepping on and releasing the brake pedal while injecting brake fluid into the master cylinder reservoir. When the air is not relieved completely, the first and second pistons are rearwardly returned by an unnecessarily strong force since the bubbled air compressed by stepping on the brake pedal is expanded simultaneously with the release of the brake pedal. 
     According to this version of the present invention shown in FIG. 1, by constructing the brake master cylinder so that a predetermined distance or interval exists between the radial projection  35   a  of the first spring retainer  35  and the rear end surface  23   c   1  of the groove  23   c  of the sleeve  23  (i.e., the dimension A in FIG.  1 ), even when the second piston is returned in the rearward direction with a strong force by the expansion of the bubbled air, the radial projection  35   a  of the first spring retainer  35  does not contact the rear end surface  23   c   1  of the groove  23   c  of the sleeve  23  (i.e., the portion of the sleeve  23  forming the rearward wall of the groove  23   c ). This advantageously prevents deformation and damage of the first spring retainer  35  and the sleeve  23 . 
     The predetermined distance A can be defined by the total of the retracting distance of the second piston  32  from the non-braking operation position to the position where then piston port  32   a  and the opening  23   a   1  of the reservoir communication conduit  23   a  overlap one another and a predetermined additional distance, thus facilitating prevention of contact between the radial projection  35   a  of the first spring retainer  35  and the rear end surface  23   c   1  of the groove  23   c  of the sleeve  23  (i.e., the portion of the sleeve  23  forming the rearward wall of the groove  23   c ). Further, because the piston port  32   a  can overlap with the opening  23   a   1  when the second piston  32  is retracted, sufficient passage space for relieving bubbled air to the reservoir is ensured. 
     The predetermined distance A can also be defined by the retracting distance of the second piston  32  from the non-braking operation position to the position where the piston port  32   a  and the lip of the fourth cup seal  27  overlap one another so that contact between the radial projection  35   a  of the first spring retainer  35  and the rear end surface  23   c   1  of the groove  23  of the sleeve  23  can be prevented. Further because the piston port  32   a  can overlap with the opening  23   a   1  when the second piston  32  is retracted, sufficient passage space for relieving bubbled air to the reservoir is ensured. 
     The predetermined distance A can also be defined by the total of the retracting distance of the second piston  32  from the non-braking operation position to the position where the front end surface  32   b  of the second piston  32  and the opening  23   a   1  of the reservoir communication conduit  23   a  overlap one another and a predetermined additional distance so that contact between the radial projection  35   a  of the first spring retainer  35  and the rear end surface  23   c   1  of the groove  23   c  of the sleeve  23  (i.e., the portion of the sleeve  23  forming the rearward wall of the groove  23   c ) can be prevented. In addition, because the piston port  32   a  can overlap with the opening  23   a   1  when the second piston  32  is retracted, sufficient passage space for relieving bubbled air to the reservoir is ensured. 
     In accordance with a second embodiment of the brake master cylinder of the present invention shown in FIG. 2, advantages and results similar to those associated with the first embodiment can be realized by providing a predetermined interval or distance between the radial projection  35   a  of the first spring retainer  35  and a stepped portion  12   c   3  of the large diameter portion  12   c   2  provided on the stepped internal bore  12   c  of the cylinder cap  12  (i.e., the interval or distance B shown in FIG.  2 ). Accordingly, the distance or interval B can be determined between the radial projection  35   a  of the first spring retainer  35  and the rear end surface  23   c   1  of the groove  23   c  of the sleeve  23  (i.e., the portion of the sleeve  23  forming the rearward wall of the groove  23   c ) as well as between the radial projection  35   a  of the first spring retainer  35  and the stepped portion  12   c   3  of the large diameter portion  12   c   2  provided on the stepped internal bore  12   c  of the cylinder cap  12 . This further improves the flexibility in design construction of the brake master cylinder. 
     The principles, preferred embodiments and modes of operation of the present invention have been described in the foregoing specification. However, the invention which is intended to be protected is not to be construed as limited to the particular embodiments disclosed. Further, the embodiments described herein are to be regarded as illustrative rather than restrictive. Variations and changes may be made by others, and equivalents employed, without departing from the spirit of the present invention. Accordingly, it is expressly intended that all such variations, changes and equivalents which fall within the spirit and scope of the present invention as defined in the claims, be embraced thereby.