JP5541146B2 - Reservoir - Google Patents

Description

  The present invention relates to a reservoir that has a valve body that can open and close a fluid inflow path to a reservoir chamber, and that opens and closes the inflow path by moving the valve body with a shaft. It is preferable to apply to a pressure regulating reservoir in which the brake fluid in the wheel cylinder flows in brake fluid pressure control such as control (anti-skid control).

  Conventionally, Patent Documents 1 and 2 disclose a vehicle brake device that performs ABS control using a pressure-regulating reservoir (switch reservoir). FIG. 6 is a cross-sectional view of a conventional pressure regulating reservoir disclosed in Patent Document 1. As shown in FIG.

  In the pressure regulating reservoir shown in FIG. 6, the large diameter portion 101 a of the shaft 101 press-fitted into the piston 100 contacts the lower surface 102 a of the seat valve 102, and the upper surface 100 b of the piston 100 constitutes the reservoir chamber 104 in the housing 103. The configuration is such that it does not come into contact with the upper end surface 105 of the wall surface. Thus, the lift amount of the ball valve 106 is set only by the portion of the shaft 101 that is in contact with the lower surface 102a of the seat valve 102 above the large diameter portion 101a, that is, the axial size of the small diameter portion 101b of the shaft 101. I have to. Therefore, even if a variation occurs when the shaft 101 is integrated with the piston 100, or a variation occurs when the unit including the ball valve 106, the seat valve 102, and the filter component 107 is caulked and fixed in the reservoir hole 108, The variation can be canceled, and a pressure regulating reservoir that can easily manage the lift amount of the ball valve 106 can be obtained.

  In the pressure regulating reservoir configured in this manner, the shaft 101 press-fitted into the piston 100 is pushed up by the elastic force of the spring 109 during normal braking (when brake fluid pressure control such as ABS control is not activated). The valve 106 is separated from the seat valve 102 and is opened. When the brake fluid pressure control is executed and a predetermined amount of brake fluid flows into the reservoir chamber 104, the ball valve 106 comes into contact with the seat valve 102 as the shaft 101 moves down together with the piston 100. For this reason, it is possible to prevent the brake fluid from flowing into the reservoir chamber 104 so that the piston 100 does not reach the bottom dead center. At this time, since the shaft 101 is coaxially disposed and integrated with the piston 100, the check valve and the shaft configured by the seat valve 102, the ball valve 106, and the like fixed coaxially with the piston 100 are provided. The position of the check valve coincides with that of the valve 101, and the check valve can be opened without being displaced.

  Also, the pressure regulating reservoir disclosed in Patent Document 2 has a structure in which a shaft is coaxially disposed and integrated with a piston, as in Patent Document 1. For this reason, the positions of the check valve and the shaft fixed coaxially with the piston in the opening of the housing coincide with each other, and the check valve can be opened without being displaced.

JP 2006-151362 A JP 2008-7080 A

  However, in order to increase the amount of brake fluid that can be stored in the reservoir chamber, that is, the reservoir capacity, it is necessary to enlarge the piston diameter or lengthen the stroke of the piston, and the housing must be increased accordingly. In particular, when the piston diameter must be increased, in the pressure regulating reservoirs disclosed in Patent Documents 1 and 2, the piston and the shaft have a coaxial structure. The problem arises that the thickness of the housing must be increased to ensure the thickness. This will be described with reference to FIGS.

  FIG. 7 shows a top layout and a front layout when the pressure regulating reservoir 110 is disposed in the vicinity of the pump 111. FIG. 8 shows a top layout and a front layout when the pressure regulating reservoir 110 is arranged in the vicinity of the solenoid valve 112. As shown in FIGS. 7 and 8, in the pressure regulating reservoir 110, a check valve 110a and a piston portion 110b are formed in a cylindrical shape, and these are arranged on a concentric shaft. As shown in FIG. 7, when the pressure regulating reservoir 110 is disposed in the vicinity of the pump 111, the check valve 110 a of the pressure regulating reservoir 110 and the pump 111 are made the same height, so that the housing 113 The pressure regulating reservoir 110 can be disposed in an empty space where the pump 111 is disposed. Further, as shown in FIG. 8, even when the pressure regulating reservoir 110 is disposed in the vicinity of the electromagnetic valve 112, the check valve 110 a and the electromagnetic valve 112 of the pressure regulating reservoir 110 are made to have the same height so that the housing 113. Among them, the pressure regulating reservoir 110 can be arranged in an empty space where the electromagnetic valve 112 is arranged.

  Here, in the state before increasing the reservoir capacity of the pressure adjusting reservoir 110, the layout shown by the broken line in FIG. 7 and FIG. 8 is obtained, and if the housing 113 is set to the dimension A, a necessary thickness corresponding to this layout is secured. Is done. In contrast, when the piston diameter of the pressure regulating reservoir 110 is increased to increase the reservoir capacity, the required thickness cannot be obtained if the size of the housing 113 is left as it is. For this reason, it is necessary to increase the thickness of the housing 113 from the dimension A in the state before increasing the reservoir capacity to the dimension A ′ indicated by a one-dotted line.

  In order to avoid this, as shown in FIGS. 9 and 10, the central axis of the check valve 110 a is offset with respect to the central axis of the pressure regulating reservoir 110, and the piston portion 110 b of the pressure regulating reservoir 110 is more It can be considered that the pump 111 and the solenoid valve 112 are structured to enter. In this way, the thickness of the housing 113 can be reduced to a dimension B smaller than the dimension A ′ that can ensure the necessary thickness when the offset is not indicated by the broken line in the drawing.

  However, when the central axis of the check valve 110a is offset with respect to the central axis of the piston part 110b, for example, when the piston and the shaft are lowered by the operation of the brake fluid pressure control and the piston is lowered below the check valve 110a. Is rotated in the circumferential direction, a circumferential displacement occurs between the shaft and the check valve. Accordingly, the check valve cannot be opened and closed by the shaft, and thus such a structure cannot be adopted.

  Here, the pressure regulating reservoir used for the ABS control has been described as an example. However, the pressure regulating reservoir is used as an example. However, the pressure regulating reservoir has a valve body that can open and close the fluid inflow path to the reservoir chamber, and the valve body is moved by the shaft. As a result, the above-described problem occurs with respect to all reservoirs that open and close the inflow path.

  In view of the above points, an object of the present invention is to provide a reservoir that can be further downsized and that can reliably perform opening and closing operations of a valve body.

  In order to achieve the above object, according to the first aspect of the present invention, the shaft (231) and the piston portion (22) are configured separately, and the shaft (231) reciprocates within the shaft support hole (216a). The shaft (231) insertion portion of the shaft support hole (216a) is movably supported and is characterized in that its axis is offset from the central axis of the piston portion (22).

  Thus, the shaft line of the shaft (231) in the shaft support hole (216a) and the central axis of the piston part (22) are offset from each other. For this reason, when the reservoir is disposed adjacent to the pump, various control valves, etc., the reservoir can be made closer to these while avoiding interference with the pump, various control valves, etc. Thereby, even if it does not increase the thickness of a housing (40), the thickness of the part which comprises the outer peripheral wall of a reservoir among housings (40) can be ensured.

The shaft (231) is separated from the piston portion (22) and is supported in a reciprocating manner in the shaft support hole (216a). Therefore, even if the fluid flows into the reservoir chamber (20C) and the piston portion (22) is moved away from the valve body (211 to 213), the shaft (231) remains in the shaft support hole (216a). The shaft (231) is not separated from the shaft support hole (216a). Thereby, even if it rotates in the circumferential direction when the piston part (22) is moved in the direction away from the valve body (211 to 213), the piston part (22) is again moved to the valve body (211 to 213) side. When returned, it is possible to prevent the positional deviation in the circumferential direction between the shaft (231) and the shaft support hole (216a) from occurring. Accordingly, the valve body (211 to 213) can be moved by the shaft (231) after that, and the valve body (211 to 213) can be reliably moved. The reservoir can be configured.
Further, in the first aspect of the invention, the piston portion (22) contacts the end portion (231e) of the shaft (231) on the piston portion (22) side and guides the shaft (231). ).
As described above, the piston portion (22) can be provided with the guide surface (225b) that abuts the end portion (231e) of the shaft (231) on the piston portion (22) side and guides the shaft (231). Thereby, it is possible to prevent the shaft (231) from being tilted by the gap between the shaft (231) and the shaft support hole (216a).

  In the second aspect of the present invention, between the piston portion (22) and the shaft (231), inside the reservoir chamber (20C) and on the opposite side of the reservoir chamber (20C) across the piston portion (22). It has a movable part (232, 233) which changes the distance to the valve body (211 to 213) by displacing based on the pressure difference between the inside of the back chamber (40b) located, and the movable part is a diaphragm. (233), and the diaphragm (233) is deformed by receiving a differential pressure between the reservoir chamber (20C) and the back chamber (40b), thereby moving the shaft (231). It is said.

  Thus, if it is set as the structure which moves a shaft (231) via a diaphragm (233), the eccentric load transmission from a shaft (231) to a piston part (22) is relieve | moderated by the elasticity of a diaphragm (233). That is, the load transmission area to the piston part (22) is expanded, and the influence of the uneven load is reduced. Further, the radial force acting on the shaft (231) is relieved by elasticity, and the shaft (231) is less likely to be twisted.

  In the invention according to claim 3, the movable part has a plate (232) that moves the shaft (231) in accordance with the deformation of the diaphragm (233), and the piston part (22) includes the plate (232) and the diaphragm. A stopper (225) for restricting the amount of movement of the shaft (233) in the shaft direction is provided. The stopper (225) is a ring-shaped member that fixes the outer edge of the diaphragm (233), and the inner peripheral surface of the ring-shaped member The amount of movement of the plate in the shaft direction is restricted by the flange portion (225a) projected from the center toward the center, and the tip of the flange portion (225a) is located on the piston portion (22) side of the shaft (231). A guide surface (225b) for guiding the shaft (231) in contact with the end (231e) of the shaft is configured.

  Thus, the guide surface (225b) that guides the shaft (231) by the tip of the flange (225a) of the stopper (225) contacting the end (231e) of the shaft (231) on the piston (22) side. ), It is possible to prevent the shaft (231) from being tilted by the gap between the shaft (231) and the shaft support hole (216a).

The invention according to claim 4 is characterized in that the guide surface (225b) has a tapered surface (225c) facing the valve body (211 to 213).

  As described above, by providing the guide surface (225b) with the tapered surface (225c), the shaft (231) is guided to the tip position of the guide surface (225b), and the shaft (231) can be prevented from being caught. For this reason, when a piston part (22), a stopper (225), etc. return to a normal position, it becomes possible to return more smoothly.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

It is piping schematic of the brake device to which the pressure regulation reservoir 20 concerning 1st Embodiment of this invention is applied. 3 is a cross-sectional view of a pressure regulating reservoir 20. FIG. (A) is a top view of the shaft 231, and (b) is a perspective view of the shaft 231. It is sectional drawing showing the action | operation of the pressure regulation reservoir | reserver 20 at the time of a service brake. It is sectional drawing showing the action | operation of the pressure regulation reservoir 20 at the time of pressure regulation. It is sectional drawing showing the action | operation of the pressure regulation reservoir 20 at the time of self-priming. It is sectional drawing showing the action | operation of the pressure regulation reservoir | reserver 20 at the time of ABS control. It is sectional drawing of the pressure regulation reservoir | reserver 20 concerning 2nd Embodiment of this invention. It is sectional drawing of the conventional pressure regulation reservoir. FIG. 6 is a schematic diagram showing a top layout and a front layout when the pressure regulating reservoir 110 is arranged in the vicinity of the pump 111. FIG. 6 is a schematic diagram showing a top layout and a front layout when the pressure regulating reservoir 110 is disposed in the vicinity of the electromagnetic valve 112. It is a schematic diagram which shows the upper surface layout and front layout in the case of offsetting the check valve 110a of the pressure regulation reservoir 110 with respect to the piston part 110b. It is a schematic diagram which shows the upper surface layout and front layout in the case of offsetting the check valve 110a of the pressure regulation reservoir 110 with respect to the piston part 110b.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
FIG. 1 shows a schematic piping diagram of a brake device to which a pressure regulating reservoir according to an embodiment of the present invention is applied. With reference to this figure, the basic structure of the brake device of this embodiment is demonstrated. However, since the pressure regulating reservoir is simplified in FIG. 1 and the characteristic part of the present invention is not illustrated, the characteristic part will be described with reference to FIG. 2 described later. Here, a case will be described in which the brake device according to the present embodiment is applied to a vehicle that constitutes a hydraulic circuit of an X pipe including the right front wheel-left rear wheel and the left front wheel-right rear wheel piping system. .

  As shown in FIG. 1, a brake pedal 1 as a brake operation member that is depressed by an occupant when a braking force is applied to a vehicle is connected to a booster 2, and a pedaling force applied to the brake pedal 1 by the booster 2. Is boosted.

  The booster 2 has a push rod or the like that transmits the boosted pedaling force to a master cylinder (hereinafter referred to as M / C) 3, and this push rod is a master disposed in the M / C 3. M / C pressure is generated by pressing the piston.

  Note that a master reservoir 3a for supplying brake fluid into M / C3 and storing excess brake fluid in M / C3 is connected to M / C3.

  The M / C pressure is transmitted to wheel cylinders (hereinafter referred to as W / C) 4 and 5 of each wheel via an ABS actuator. In FIG. 1, only the first piping system connected to W / C4 for the right front wheel FR and W / C5 for the left rear wheel RL is shown, but it is connected to the left front wheel FL and the right rear wheel RR side. The second piping system has the same structure as the first piping system. The following description will be made on the right front wheel FR and the left rear wheel RL side, but the same applies to the left front wheel FL and the right rear wheel RR side which are the second piping system.

  The brake device also includes a pipe line (main pipe line) A connected to the M / C 3. A differential pressure control valve 7 is provided in the pipeline A, and the pipeline A is divided into two parts at the position of the differential pressure control valve 7. Specifically, the pipe A includes a pipe A1 that receives the M / C pressure between M / C3 and the differential pressure control valve 7, and a line between the differential pressure control valve 7 and each of the W / Cs 4 and 5. It is divided into a pipeline A2.

  The differential pressure control valve 7 controls the communication state and the differential pressure state. The differential pressure control valve 7 is normally in a communication state, but by setting the differential pressure control valve 7 to a differential pressure state, the W / C 4 and 5 sides are made higher by a predetermined differential pressure than the M / C 3 side. Can be held.

  Further, in the pipeline A2, the pipeline A is branched into two, one of which is provided with a pressure increase control valve 30 for controlling the increase of the brake fluid pressure to the W / C 4, and the other is the W / C. A pressure increase control valve 31 for controlling the increase of the brake fluid pressure to C5 is provided.

  These pressure-increasing control valves 30 and 31 are configured as two-position valves that can control the communication / blocking state by an electronic control device (hereinafter referred to as ECU) for controlling brake fluid pressure (not shown). When the two-position valve is controlled to be in communication, a brake fluid pressure based on the M / C pressure or the discharge of the pump 10 described later can be applied to each of the W / Cs 4 and 5. These pressure-increasing control valves 30 and 31 are always in a communicating state at the time of normal braking in which brake fluid pressure control such as ABS control is not executed.

  Further, a pipeline B is connected between the pressure increase control valves 30, 31 in the pipeline A and the respective W / Cs 4, 5, and this pipeline B is connected to the reservoir hole 20 B of the pressure regulating reservoir 20. Has been. And it is comprised so that it can control that the brake fluid pressure in W / C4 and 5 is controlled by flowing brake fluid to the pressure regulation reservoir 20 through the pipe line B, and each wheel reaches a lock tendency. The details of the pressure regulating reservoir 20 will be described later.

  Further, pressure reduction control valves 32 and 33 that can control the communication / blocking state by the ECU are disposed in the pipe B. These pressure reduction control valves 32 and 33 are always cut off during normal braking, and are appropriately connected when the brake fluid flows to the pressure regulating reservoir 20 described above.

  A conduit C is connected between the differential pressure control valve 7 and the pressure increase control valves 30, 31 in the conduit A, and the conduit A and the reservoir hole 20 </ b> B of the pressure regulating reservoir 20 through the conduit C. Is tied. In the pipe C, the pump 10 is disposed together with the check valves 10a and 10b, and an accumulator is provided on the downstream side of the pump 10 in the pipe C in order to reduce the pulsation of the brake fluid discharged by the pump 10. 12 is disposed. A pipe D is provided so as to connect the reservoir hole 20A and M / C3, and the pump 10 draws the brake fluid in the pipe A1 through the pipe D and the pressure regulating reservoir 20, A part of B and the pipe C are discharged to the pipe A2 to increase the W / C pressure.

  Next, the configuration of the pressure regulating reservoir 20 described above will be described with reference to FIG.

  The pressure regulating reservoir 20 is built in a housing 40 that forms the outer shape of the ABS actuator, and reservoir holes 20A and 20B and a reservoir chamber 20C are configured by the inner wall surface of the recess 40a formed in the housing 40.

  The reservoir hole 20A is constituted by a hollow portion formed in the housing 40, is connected to the M / C3, and receives the flow of brake fluid from the conduit D serving as an inflow conduit having a pressure equivalent to the M / C pressure. . The reservoir hole 20B is configured by a hollow portion having a diameter larger than that of the reservoir hole 20A formed in the housing 40, and connects the pipelines B and C as the outflow pipeline and the reservoir chamber 20C. The reservoir chamber 20C is defined by a wall surface constituting the reservoir hole 20B of the housing 40, a piston main body 221 and the like described later, and stores the brake fluid flowing through the reservoir hole 20A or the reservoir hole 20B and sends it out through the reservoir hole 20B. is there. Here, the pipes B, C, and D constitute a “liquid flow path” that communicates with the reservoir chamber 20C.

  Specifically, the reservoir hole 20B is formed from one surface of the housing 40, and the reservoir hole 20A is formed from the upper end surface 20D of the wall surface constituting the reservoir chamber 20C of the housing 40. The reservoir hole 20A and the reservoir hole 20B are configured by forming a cylindrical concave portion with respect to the housing 40. In this embodiment, the center line of the reservoir hole 20A and the center line of the reservoir hole 20B are offset. It is formed to be.

  A check valve 21 is provided in the reservoir hole 20A. The check valve 21 includes a valve 211, a ball valve 212, a pin 213, a filter component 214, a spring 215, and a seat valve 216.

  The valve 211 is made of iron-based metal or the like, and together with the ball valve 212 and the pin 213, constitutes a valve body that opens and closes a large-diameter oil passage 216a formed in the seat valve 216 as will be described later. Further, the valve 211 forms a brake fluid flow path having a smaller diameter than the large diameter oil path 216a of the seat valve 216 when the large diameter oil path 216a of the seat valve 216 is closed. Specifically, the valve 211 has a cylindrical shape, and a hollow portion 211a serving as a brake fluid flow path is formed on the axis thereof.

  The hollow portion 211a has a stepped shape in which the brake fluid flow path gradually decreases toward the seat valve 216 side. Of the hollow portion 211a, the seat valve 216 side is the small-diameter oil passage 211b constituting the first oil passage having a smaller diameter (smaller passage area) than the large-diameter oil passage 216a. Further, in the hollow portion 211a, the ball valve 212 is disposed in the first accommodating portion 211c having a diameter larger than that of the small diameter oil passage 211b on the side opposite to the seat valve 216 relative to the small diameter oil passage 211b, and further larger than that. A pin 213 is arranged in the second accommodating portion 211d having a diameter. A boundary portion between the small-diameter oil passage 211b and the first housing portion 211c is a tapered seat surface to which the ball valve 212 is attached and detached.

  The ball valve 212 is made of an iron diameter metal or the like, and has a smaller diameter than the first housing portion 211c and a larger diameter than the small diameter oil passage 211b. When the ball valve 212 is detached from the seat surface of the valve 211, the small-diameter oil passage 211b is opened and closed.

  The pin 213 is made of an iron-based metal or the like, and is for holding the ball valve 212 in the valve 211. The pin 213 holds the ball valve 212 in the valve 211, and the small-diameter oil passage 211b is closed by the ball valve 212 during normal braking.

  In the present embodiment, the pin 213 is press-fitted into the inner peripheral surface of the valve 211 so as to be integrated with the valve 211. The pin 213 is fixed in a state where the pin 213 is positioned on the valve 211 by the tip of the pin 213 contacting the stepped portion of the valve 211. The pin 213 has a cylindrical shape with a flange formed at one end, and has a shape in which a communication path 213a extending in the axial direction is formed at one place or a plurality of places. The brake fluid path is secured by allowing the brake fluid to flow through the communication path 213a.

  Further, a concave portion 213b in which the ball valve 212 is accommodated is formed at the tip of the pin 213 in the insertion direction into the valve 211. The depth of the recess 213b is set so that the ball valve 212 is separated from the bottom surface of the recess 213b when the ball valve 212 is seated on the seat surface of the valve 211. The depth of the recess 213b is such that the lift amount when the ball valve 212 is pushed by the shaft 231 and moves away from the seat surface is between the cross-shaped portion 231c (described later) of the shaft 231 and the valve 211. It is set to be smaller than the distance.

  For this reason, the ball valve 212 is normally seated on the seat surface of the valve 211 to block the small-diameter oil passage 211b and close the brake fluid flow passage, but the piston portion 22 is on the side of reducing the capacity in the reservoir chamber 20C. When moved, the ball valve 212 is pushed by the shaft 231 and leaves the seat surface. Since the lift amount of the ball valve 212 is smaller than between the cross-shaped portion 231c and the valve 211, the ball valve 212 does not come into contact with the bottom surface of the recess 213b without contacting the cross-shaped portion 231c and the valve 211. Touch. Therefore, the pin 213 is moved upward against the elastic force of the spring 215 based on the force on the upper side of the paper applied from the shaft 231 to the ball valve 212. Thereby, the valve 211 integrated with the pin 213 is also moved, and the large diameter oil passage 216a can be opened.

  The filter component 214 is made of metal, resin, or the like, and six columnar members 214b are arranged at equal intervals with respect to the circular bottom surface portion 214a, and a mesh-shaped filter around the columnar member 214b ( (Not shown), and is generally cup-shaped when viewed as a whole.

  The spring 215 is disposed between the pin 213 and the filter component 214 and urges the pin 213 and the valve 211 toward the seat valve 216 by elastic force.

  The seat valve 216 is constituted by a hollow member made of iron-based metal or the like, and has a structure including a large-diameter oil passage 216a constituted by the hollow portion. The large-diameter oil passage 216a constitutes an inflow passage (fluid passage) for allowing the brake fluid to flow into the reservoir chamber 20C as a fluid, and the shaft 231 is inserted into the inside, and the shaft 231 is formed by the inner peripheral surface thereof. Is guided so as to be able to reciprocate. That is, the large-diameter oil passage 216a constituting the inflow passage (liquid passage) also functions as a shaft support hole for supporting the shaft 231.

  The outer diameter of the tip of the seat valve 216 on the filter component 214 side is equal to or slightly larger than the inner diameter of the opening of the filter component 214. And after accommodating the valve 211, the ball valve 212, the pin 213, and the spring 215 in the filter component 214, these parts are integrated by press-fitting the seat valve 216 into the opening part of the filter component 214, A unitized check valve 21 is configured. Further, the outer peripheral surface of the seat valve 216 has a stepped shape, and the outer diameter is the largest at the tip position opposite to the filter component 214. This outer diameter is made larger than the inner diameter on the inlet side of the hollow portion constituting the reservoir hole 20A. For this reason, by inserting the seat valve 216 together with the filter component 214 and the like into the hollow portion constituting the reservoir hole 20A, a part of the housing 40 is caulked by the portion having the largest outer diameter among the seat valves 216. A check valve 21 is held in the housing 40.

  An annular groove 216b that goes around the outer circumferential surface is formed on the outer circumferential surface of the seat valve 216, and a part of the housing 40 enters the annular groove 216b, so that the check valve 21 is inserted into the housing 40. It can be held firmly.

  On the other hand, the reservoir hole 20B is provided with a piston portion 22 and a valve opening / closing mechanism portion 23.

  The piston part 22 is configured to include a piston body 221, an O-ring 222, a spring 223, a cover 224, and a stopper 225.

  The piston body 221 is made of resin or the like. The piston body 221 is configured to slide in the vertical direction on the paper surface on the inner wall surface of the reservoir hole 20B. A valve opening / closing mechanism 23 is disposed at the center position of the piston body 221. Specifically, the piston main body 221 is formed in a cylindrical shape provided with a partition wall portion 221a, and the valve opening / closing mechanism portion 23 is accommodated with the check valve 21 side as the accommodating portion with respect to the partition wall portion 221a. Further, a communication hole 221b is provided at the center position of the partition wall portion 221a, and the pressure (atmospheric pressure) in the back chamber 40b is transmitted to the valve opening / closing mechanism portion 23.

  The O-ring 222 is provided on the outer peripheral surface of the piston main body 221. An annular groove 221c is provided at a portion of the piston main body 221 where the O-ring 222 is disposed, and the O-ring 222 is fitted into the annular groove 221c.

  The spring 223 is disposed between the piston main body 221 and the cover 224, and comes in contact with the partition wall portion 221a of the piston main body 221, thereby reducing the capacity of the piston main body 221 toward the check valve 21, that is, the reservoir chamber 20C. Energized.

  The cover 224 serves to receive the spring 223. The cover 224 is caulked and fixed to the inlet of the hollow portion of the housing 40. Although not shown in FIG. 2, an air introduction hole is provided at a desired position of the cover 224 so that the interior of the back chamber 40b formed between the piston body 221 and the cover 224 is maintained at atmospheric pressure. ing.

  The stopper 225 is a ring-shaped member made of resin, iron-based metal, or the like, and is supported using the piston body 221 as a support member. The stopper 225 plays a role of fixing the outer edge portion of the diaphragm 233 by pressing it toward the piston main body 221 and a role of restricting the movement of the plate 232 to the upper side (shaft direction). The stopper 225 is hooked at the tip position on the check valve 21 side on the inner peripheral surface of the piston main body 221, and the stopper 225 is press-fitted into the piston main body 221 with the diaphragm 233 and the plate 232 disposed. In the piston body 221, a stopper 225 is fixed together with a diaphragm 233 and a plate 232 by a snap foot. The stopper 225 includes a flange portion 225 a that protrudes from the inner peripheral surface of the stopper 225 toward the center. The hole diameter of the flange portion 225 a is smaller than the outer diameter of the plate 232. Therefore, the movement of the plate 232 is restricted by the flange 225a.

  Further, the valve opening / closing mechanism 23 is configured by a shaft 231, a plate 232, and a diaphragm 233.

  The shaft 231 is disposed in the large-diameter oil passage 216a of the seat valve 216, and has a structure in which a protrusion 231a having a smaller diameter than the small-diameter oil passage 211b is provided at the distal end portion on the valve 211 side. The shaft 231 is slid in the large-diameter oil passage 216 a, and the protrusion 231 a moves in the small-diameter oil passage 211 b accordingly, so that the ball valve 212 can be pushed or separated from the ball valve 212. It has become.

  FIGS. 3A and 3B are a top view and a perspective view of the shaft 231. As shown in FIGS. 3A and 3B, the shaft 231 is provided with a plurality of slits 231b parallel to the axial direction at equal intervals in the circumferential direction, so that the cross-sectional shape perpendicular to the axial direction is a cross shape. A cross-shaped portion 231c is formed. For this reason, it is comprised so that a brake fluid can flow through the slit 231b of the cross-shaped part 231c.

  The protrusion 231a is provided at the tip of the cross-shaped portion 231c. The protruding amount of the protrusion 231a from the cross-shaped portion 231c is designed to be a length that allows the ball valve 212 to be pushed up when the cross-shaped portion 231c contacts the valve 211. The distance between the cross-shaped portion 231c and the valve 211 is designed to be smaller than the maximum displacement amount of a diaphragm 233, which will be described later, and the valve 211 is pushed up by the cross-shaped portion 231c.

  Further, the cross-shaped portion 231c is provided with a stepped portion 231d whose outer diameter is reduced from the valve 211 side to the piston portion 22 side. Corresponding to the stepped portion 231d, a stepped portion 216c is provided on the inner wall surface of the large diameter oil passage 216a of the seat valve 216, and the shaft 231 is held in the large diameter oil passage 216a of the seat valve 216. It is made to do. For this reason, the shaft 231 is held in the housing 40 together with the check valve 21 while being accommodated in the check valve 21. Since the distance from the stepped portion 216c of the seat valve 216 to the upper end surface of the seat valve 216 is constant, and the distance from the stepped portion 231d of the shaft 231 to the protruding portion 231a is also constant, the protruding portion 231a and The positional relationship with the ball valve 212 is also uniquely determined, and the lift amount of the ball valve 212 can be easily managed.

  The plate 232 plays a role of moving the shaft 231 toward the ball valve 212 and a role of regulating the movement amount of the shaft 231. The plate 232 is composed of a disk-shaped member made of, for example, an iron-based metal. The plate 232 is moved in the vertical direction on the paper surface as the diaphragm 233 is deformed. The outer edge of the plate 232 is in contact with the stopper 225 so that the amount of movement upward on the paper surface is regulated. For this reason, even if the shaft 231 is moved in accordance with the movement of the plate 232, the movement amount is equivalent to the distance until the plate 232 comes into contact with the stopper 225.

  The diaphragm 233 is made of an elastic material, for example, rubber, and is disposed between the plate 232 and the partition wall portion 221a. The diaphragm 233 has a flat shape as shown in FIG. 2 when the brake fluid pressure control is not activated, but the difference between the pressure in the reservoir chamber 20C (reservoir internal pressure) and the pressure in the back chamber 40b (atmospheric pressure). When pressure is generated, it is deformed based on it. That is, when the pressure in the reservoir chamber 20C becomes negative due to the suction of the brake fluid by the pump 10, it becomes lower than the atmospheric pressure in the back chamber 40b, so that the diaphragm 233 is deformed. Due to this deformation, the diaphragm 233 pushes the plate 232 upward in the drawing, and the shaft 231 is moved.

  As described above, when the shaft 231 is moved via the diaphragm 233, the transmission of the offset load from the shaft 231 to the piston portion 22 is relieved by the elasticity of the diaphragm 233. That is, the load transmission area to the piston portion 22 is expanded, and the influence of the uneven load is reduced. Further, the force acting on the shaft 231 in the radial direction is relaxed by elasticity, and the shaft 231 can be prevented from being twisted.

  In this way, the valve opening / closing mechanism 23 is configured. In the present embodiment, the plate 232 and the diaphragm 233 of the valve opening / closing mechanism 23 configured as described above function as a movable portion.

  The pressure regulating reservoir 20 according to the present embodiment is configured as described above. In the pressure regulating reservoir 20 configured in this manner, as described above, the center line of the reservoir hole 20A and the center line of the reservoir hole 20B are offset. For this reason, the central axis of the check valve 21 arranged in the reservoir hole 20A and the central axis of the piston part 22 arranged in the reservoir hole 20B are offset. In other words, the axis of the insertion portion of the shaft 231 in the large-diameter oil passage 216a constituting the inflow passage and the central axis of the piston portion 22 can be arranged offset.

  In this way, if the axis of the insertion portion of the shaft 231 in the large-diameter oil passage 216a constituting the inflow passage and the central axis of the piston portion 22 are offset, the pressure regulating reservoir 20 is replaced with the pump 10 or the various control valves 7, 30. When the pressure adjusting reservoir 20 is disposed adjacent to the control valve 33 or the like, the pressure regulating reservoir 20 can be brought closer to the pump 10 or various control valves 7 and 30 to 33 while avoiding interference. Thereby, the thickness of the part which comprises the outer peripheral wall of the pressure regulation reservoir 20 among the housings 40 can be ensured, and it is not necessary to increase the thickness of the housing 40.

  Next, FIGS. 4A to 4D are sectional views showing the operation of the pressure regulating reservoir 20, and the operation of the pressure regulating reservoir 20 will be described with reference to FIG.

  First, at the time of regular braking, the pump 10 is not driven and the reservoir internal pressure and the brake fluid pressure are balanced, so the diaphragm 233 is not deformed. Therefore, as shown in FIG. 4A, since the shaft 231 cannot be moved upward in the drawing, the projection 231a is separated from the ball valve 212, and the tip position of the cross-shaped portion 231c of the shaft 231 is also the valve 211. It will be in the state away from. Thereby, the ball valve 212 is seated on the seat surface of the valve 211, the small diameter oil passage 211b is closed, and the large diameter oil passage 216a is also closed. Therefore, even if the check valve 21 of the pressure regulating reservoir 20 is closed and the M / C pressure is applied to the reservoir hole 20A by depressing the brake pedal 1, the brake fluid is prevented from flowing into the reservoir chamber 20C. can do. As a result, the check valve 21 can be closed during normal braking, and unnecessary brake fluid can be prevented from being consumed.

  Next, when the pressure is adjusted, for example, when the brake pedal 1 is depressed and the M / C pressure is applied to the reservoir hole 20A as in the case where the pressure assist (brake assist control) is executed, the pump 10 is driven. As a result, the pressure in the reservoir chamber 20C becomes negative. For this reason, as shown in FIG. 4B, the diaphragm 233 is deformed, and the plate 232 is moved upward along the paper surface. As a result, the shaft 231 is also pushed up above the paper surface, and the projection 231a becomes the small diameter oil passage 211b. It is made to pass through. At this time, since the M / C pressure is applied to the reservoir hole 20A, the ball valve 212 and the seat surface of the valve 211 are balanced so that the differential pressure between the M / C pressure and the reservoir internal pressure is balanced. The space between the gaps is maintained, and the reservoir internal pressure is regulated. For this reason, the deformation of the diaphragm 233 is not maximized, and the ball valve 212 is merely pushed up by the protrusion 231a, and the valve 211 is not pushed up by the shaft 231.

  And when sucking the brake fluid and generating the braking force by driving the pump 10 in the state where the M / C pressure is not generated at the time of self-priming, for example, at the time of traction control or side slip prevention control, By driving the pump 10, the inside of the reservoir chamber 20C becomes negative pressure. At this time, since the M / C pressure is not applied to the reservoir hole 20A, the diaphragm 233 is deformed as shown in FIG. 4C, and the amount of deformation is maximized. When the plate 232 moves upward in the drawing with the deformation of the diaphragm 233 and the shaft 231 is also pushed up in the drawing, the deformation amount of the diaphragm 233 is maximized, so that the ball valve 212 is pushed up by the protrusion 231a. In addition, the ball valve 212 contacts the bottom surface of the recess 213b, and the valve 211 is pushed up together with the pin 213. As a result, the large-diameter oil passage 216a is also opened, and the suction diameter can be increased compared with the case where only the small-diameter oil passage 211b is open. Therefore, it becomes possible to improve the responsiveness at the time of brake fluid pressure control.

  Further, when the brake fluid is discharged into the reservoir chamber 20C through the conduit B as in the ABS control, the spring is caused by the pressure of the brake fluid flowing into the reservoir chamber 20C as shown in FIG. The piston portion 22 is moved downward in the drawing against the elastic force of 223. As a result, the W / C pressure is reduced by the amount of the brake fluid discharged, and it is possible to prevent the wheel from being locked.

  At this time, the valve opening / closing mechanism 23 together with the piston 22 is moved downward in the drawing. However, since the shaft 231 is caught by the stepped portion 216 c of the seat valve 216, the shaft 231 is not moved downward with respect to the drawing surface together with the piston portion 22, and remains in the check valve 21. For this reason, even if the piston portion 22 rotates in the circumferential direction when the piston portion 22 returns to the initial position above the paper surface due to the pressure increase timing of the ABS control or the end of the ABS control, the shaft 231 and the check valve No misalignment with 21 occurs. Therefore, after that, the check valve 21 can be opened and closed again by the shaft 231.

  As described above, in the pressure regulating reservoir 20 of the present embodiment, both the small diameter oil passage 211b and the large diameter oil passage 216a are closed during normal braking. For this reason, the check valve 21 can be closed at the time of regular braking, and it is possible to prevent unnecessary consumption of the brake fluid. Further, only the small-diameter oil passage 211b is in an open state at the time of pressure regulation, so that the pressure regulation action can be exhibited accurately. During self-priming, the large-diameter oil passage 216a is in an open state, so that the suction diameter can be increased and the responsiveness at the time of brake fluid pressure control can be improved.

  In such a structure, the axis of the insertion portion of the shaft 231 in the large-diameter oil passage 216a constituting the inflow passage and the central axis of the piston portion 22 are offset. Therefore, when the pressure regulating reservoir 20 is disposed adjacent to the pump 10 and the various control valves 7, 30 to 33, etc., the pressure regulating reservoir 20 is interfered with the pump 10, the various control valves 7, 30 to 33, and the like. It is possible to get closer to these while avoiding them. Thereby, the thickness of the part which comprises the outer peripheral wall of the pressure regulation reservoir 20 among the housings 40 can be ensured, and it is not necessary to increase the thickness of the housing 40.

  The shaft 231 for opening and closing the check valve 21 is separated from the piston portion 22 and has a structure that guides the shaft 231 in a reciprocating manner while holding the shaft 231 on the inner peripheral surface of the large diameter oil passage 216a. Yes. Therefore, even if the brake fluid flows into the reservoir chamber 20C and the piston portion 22 is moved away from the check valve 21, the shaft 231 is held on the inner peripheral surface of the large-diameter oil passage 216a, and the shaft 231 is There is no separation from the large diameter oil passage 216a. Thereby, even if the piston portion 22 is moved in the direction away from the check valve 21 and rotated in the circumferential direction, when the piston portion 22 is returned to the check valve 21 side again, the shaft 231 and the large diameter oil passage It is possible to prevent positional deviation from 216a. Accordingly, the check valve 21 can be opened and closed again by the shaft 231 thereafter, the pressure regulating reservoir 20 can be downsized, and the check valve can be opened and closed reliably. can do.

(Second Embodiment)
A second embodiment of the present invention will be described. In the present embodiment, the structure of the pressure regulating reservoir 20 is changed with respect to the first embodiment, and the others are the same as those in the first embodiment, and therefore only the pressure regulating reservoir 20 will be described.

  FIG. 5 is a cross-sectional view of the pressure regulating reservoir 20 according to the present embodiment. As shown in this figure, in this embodiment, the structure of the stopper 225 is changed with respect to the pressure regulating reservoir 20 of the first embodiment. Specifically, in this embodiment, the inner diameter of the stopper 225 is reduced as compared with the first embodiment, and the tip of the flange portion 225a constituting the inner peripheral wall of the stopper 225 is the end portion on the piston portion 22 side of the shaft 231. The structure functions as a guide surface 225b that contacts the shaft 231e and guides the shaft 231. Further, on the check valve 21 side of the stopper 225, the tip of the flange 225a is chamfered to be a tapered surface 225c. According to the pressure regulating reservoir 20 having such a structure, the following effects can be obtained.

  Specifically, it is ideal that there is no gap between the shaft 231 and the inner peripheral wall surface constituting the large-diameter oil passage 216a of the seat valve 216. However, in consideration of manufacturing variations and the like, the gap is actually a gap. Will exist. For this reason, the shaft 231 is tilted by this gap. On the other hand, if the guide surface 225b of the flange 225a of the stopper 225 is in contact with the shaft 231 as in this embodiment, the tilt of the shaft 231 can be further suppressed.

  In addition, after the piston portion 22 is moved downward in the drawing by discharging the brake fluid into the reservoir chamber 20C, the stopper 225 comes into contact with the shaft 231 when the piston portion 22 returns to the upper drawing. At this time, since the flange portion 225a of the stopper 225 is provided with the tapered surface 225c, the shaft 231 is guided to the tip end position of the flange portion 225a of the stopper 225, and the hook portion 225a and the shaft 231 can be prevented from being caught. For this reason, when parts other than the shaft 231 of the piston part 22 and the valve opening / closing mechanism part 23 try to return to the normal position, it becomes possible to return more smoothly. The guide surface 225b may have a tapered surface 225c on both the check valve 21 side (upper side in the figure) and the opposite side (lower side in the figure) as shown in FIG. The taper surface 225c may be provided only on the side, but it is not essential to have the taper surface 225c. Further, when the guide surface 225b that suppresses the tilt of the shaft 231 is provided, the guide surface 225b is not limited to the above and may be directly provided on the piston main body 221 itself that is a member that is in sliding contact with the reservoir hole 20B.

(Other embodiments)
In each of the above-described embodiments, an example of the structure of the check valve 21 has been described. Any structure may be used as long as the valve 211 also constitutes the valve body of the large-diameter oil passage 216a.

  In each of the above embodiments, the pressure regulating reservoir 20 used for ABS control has been described as an example. However, the valve body has a valve body that can open and close the fluid flow path to the reservoir chamber. The present invention can be applied to all reservoirs that open and close the liquid flow path by moving the shaft with the shaft.

  DESCRIPTION OF SYMBOLS 1 ... Brake pedal, 3 ... M / C, 4, 5 ... W / C, 10 ... Pump, 20 ... Pressure regulation reservoir, 20A ... Reservoir hole, 20B ... Reservoir hole, 20C ... Reservoir chamber, 21 ... Check valve, 22 DESCRIPTION OF SYMBOLS ... Piston part, 23 ... Valve opening / closing mechanism part, 40 ... Housing, 40b ... Back chamber, 211 ... Valve, 211b ... Small diameter oil passage, 212 ... Ball valve, 213 ... Pin, 216 ... Seat valve, 216a ... Large diameter oil passage 221 ... piston body, 221a ... partition wall, 223 ... spring, 225 ... stopper, 225a ... collar, 225b ... guide surface, 225c ... tapered surface, 231 ... shaft, 231a ... projection, 232 ... plate, 233 ... Diaphragm

Claims (4)

A reservoir chamber (20C) configured by forming a recess (40a) with respect to the housing (40);
A valve body (211 to 213) that can open and close a liquid flow path (D) communicating with the reservoir chamber (20C);
A shaft (231) that is inserted into a shaft support hole (216a) provided in the housing (40) and moves the valve body;
In the reservoir comprising the piston chamber (22) that divides the reservoir chamber (20C) and reciprocates the shaft (231),
The shaft (231) and the piston part (22) are configured separately, and the shaft (231) is supported so as to be reciprocable in the shaft support hole (216a), and the shaft support hole (216a). ), The insertion portion of the shaft (231) is arranged with its axis offset from the central axis of the piston portion (22) ,
The piston part (22) includes a guide surface (225b) that abuts on an end part (231e) of the shaft (231) on the piston part (22) side and guides the shaft (231). Reservoir. A back chamber located between the piston portion (22) and the shaft (231) is located in the reservoir chamber (20C) and on the opposite side of the reservoir chamber (20C) with the piston portion (22) interposed therebetween. (40b) having a movable part (232, 233) for changing the distance to the valve body (211 to 213) by displacing based on the pressure difference between the inside and (40b),
The movable portion includes a diaphragm (233), and the diaphragm (233) is deformed by receiving a differential pressure between the reservoir chamber (20C) and the back chamber (40b), so that the shaft ( 231) is moved, the reservoir according to claim 1. The movable part has a plate (232) for moving the shaft (231) in accordance with the deformation of the diaphragm (233),
The piston portion (22) includes a stopper (225) that regulates the amount of movement of the plate (232) and the diaphragm (233) in the shaft direction,
The stopper (225) is a ring-shaped member that fixes an outer edge portion of the diaphragm (233), and the flange (225a) protrudes toward the center from the inner peripheral surface of the ring-shaped member. The amount of movement of the plate in the shaft direction is regulated, and the tip of the flange portion (225a) abuts on the end portion (231e) of the shaft (231) on the piston portion (22) side to contact the shaft (231). The reservoir according to claim 2, comprising a guide surface (225 b) for guiding the guide. The reservoir according to any one of claims 1 to 3, wherein the guide surface (225b) has a tapered surface (225c) facing the valve body (211 to 213).

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