US20010022469A1 - Hydraulic actuator for an anti-lock braking system - Google Patents
Hydraulic actuator for an anti-lock braking system Download PDFInfo
- Publication number
- US20010022469A1 US20010022469A1 US09/808,955 US80895501A US2001022469A1 US 20010022469 A1 US20010022469 A1 US 20010022469A1 US 80895501 A US80895501 A US 80895501A US 2001022469 A1 US2001022469 A1 US 2001022469A1
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- United States
- Prior art keywords
- cup
- bore
- shaped diaphragm
- braking system
- hydraulic actuator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
- B60T8/4068—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system the additional fluid circuit comprising means for attenuating pressure pulsations
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
- B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
- B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
- B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master cylinders
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S303/00—Fluid-pressure and analogous brake systems
- Y10S303/10—Valve block integrating pump, valves, solenoid, accumulator
Definitions
- the present invention relates to a hydraulic actuator preferably used for controlling braking fluid of an anti-lock braking system (hereinafter, abbreviated by ABS) installed in an automotive vehicle.
- ABS anti-lock braking system
- the hydraulic actuator is operated to precisely and promptly increase and decrease the hydraulic pressure of each wheel cylinder in accordance with rotational conditions of each wheel to prevent the wheel from locking during the braking operation.
- An object of the present invention is to secure a sufficient damper capacity for an ABS actuator to reduce the noise caused during an ABS operation.
- the present invention provides a first ABS actuator comprising a housing having a first predetermined surface where a bore is formed.
- a damper defined in the bore, has an axis extending in a depth direction of the bore.
- a cup-shaped diaphragm disposed in the bore, divides an inside space of the bore into a first chamber and a second chamber.
- the cup-shaped diaphragm has an opening at one axial end and a bottom at an opposed axial end. The opening of the cup-shaped diaphragm becomes a leading side when the cup-shaped diaphragm is inserted into the bore.
- a plug-like wall member closes an opening of the bore.
- a damper chamber is constituted by the first chamber and includes an inside space of the cup-shaped diaphragm.
- the housing has a second predetermined surface where a control valve is installed.
- the second predetermined surface is substantially perpendicular to the first predetermined surface.
- the housing has a third predetermined surface where a first port is formed.
- the third predetermined surface is substantially perpendicular to the first predetermined surface and is opposed to the second predetermined surface.
- a main conduit line connects the first port to the control valve.
- the plug-like wall member has a protruding portion for pushing the bottom of the cup-shaped diaphragm.
- the protruding portion is spaced from a cylindrical wall of the bore.
- An annular space is formed between the protruding portion and the cylindrical wall of the bore.
- the annular space constitutes the second chamber.
- a first conduit line has its inlet opened to the annular space provided around the protruding portion and extends from the annular space as part of the main conduit line.
- the damper diameter can be increased to a level equivalent to the diameter of the bore. This realizes a large damper capacity. Thus, it becomes possible to reduce the noise caused during the ABS operation.
- the present invention provides a second ABS actuator comprising a housing having a first predetermined surface where a bore is formed.
- a damper defined in the bore, has an axis extending in a depth direction of the bore.
- a cup-shaped diaphragm disposed in the bore, divides an inside space of the bore into a first chamber and a second chamber.
- the cup-shaped diaphragm has an opening at one axial end and a bottom at an opposed axial end. The opening of the cup-shaped diaphragm becomes a leading side when the cup-shaped diaphragm is inserted into the bore.
- a plug-like wall member closes an opening of the bore.
- a damper chamber is constituted by the first chamber and includes an inside space of the cup-shaped diaphragm.
- the housing has a second predetermined surface where a control valve is installed.
- the second predetermined surface is substantially perpendicular to the first predetermined surface.
- the housing has a third predetermined surface where a first port is formed.
- the third predetermined surface is substantially perpendicular to the first predetermined surface and is opposed to the second predetermined surface.
- a second port is formed on the first predetermined surface where the damper is installed.
- a main conduit line is formed in the housing so as to communicate with the second chamber. The main conduit line connects the first port to the second port via the control valve.
- the first port is offset from the control valve in an axial direction of the damper.
- the control valve is located far from the first predetermined surface compared with the first port.
- the main conduit line connects the second chamber to the control valve via a first conduit line extending obliquely with respect to the axis of the damper from a cylindrical wall of the bore.
- the plug-like wall member has a protruding portion for pushing the bottom of the cup-shaped diaphragm. And, the protruding portion is spaced from the cylindrical wall of the bore. An annular space is formed between the protruding portion and the cylindrical wall of the bore constitutes the second chamber.
- the first conduit line has its inlet opened to the annular space provided around the protruding portion.
- the protruding portion of the plug-like wall member is a circular protruding portion formed at an inner end of the plug-like wall member.
- a diameter of the circular protruding portion is smaller than that of a main body of the plug-like wall member.
- the circular protruding portion presses the bottom of the cup-shaped diaphragm when the plug-like wall member is inserted into the bore, so that an insertion amount of the circular protruding portion substantially determines an axial position of the cup-shaped diaphragm in the bore.
- the cylindrical protruding portion is spaced from the cylindrical wall of the bore when the plug-like wall member is inserted in the bore so as to close the opening of the bore, so that the second chamber surrounds the cylindrical protruding portion of the plug-like wall member.
- the main conduit line further comprises a second conduit line which extends from the control valve in a direction substantially perpendicular to the second predetermined surface and is connected to the first conduit line.
- the pressurizing control valve is offset from the annular space provided around the protruding portion of the plug-like wall member in a direction normal to the first predetermined surface.
- the first conduit line extends straight and obliquely from the annular space and is connected to the second conduit line.
- two control valves are installed adjacent to each other on the second predetermined surface.
- One of the two control valves is directly connected to the first conduit line via the second conduit line.
- the other of the two control valves is connected to the first conduit line via the second conduit line and a third conduit line connecting the two control valves.
- a through-hole is opened on the bottom of the cup-shaped diaphragm.
- the through-hole serves as an orifice connecting the first chamber to the second chamber.
- a region where the through-hole is opened is thin in thickness compared with the remaining portion of the bottom of the cup-shaped diaphragm.
- a recessed region is formed on the bottom so as to surround the through-hole. The recessed region has a sufficient depth so that a burr formed around the through-hole remains in a retracted position with respect to a surface of the bottom.
- the burr is inherently produced along an annular periphery of a through-hole during a formation of the through-hole, the above-described arrangement prevents the burr from protruding from the surface of the bottom. Thus, it becomes possible to prevent the burr from peeling off the cup-shaped diaphragm.
- the cup-shaped diaphragm has a press-fitting portion partly formed on a cylindrical wall thereof.
- the press-fitting portion has an enlarged diameter larger than the diameter of other portion of the cup-shaped diaphragm. And, the cup-shaped diaphragm is firmly fixed in the bore by the press-fitting portion.
- the press-fitting portion protrudes radially outward from a surface of the cylindrical wall of the cup-shaped diaphragm.
- the press-fitting portion extends in a circumferential direction of the cylindrical wall of the cup-shaped diaphragm.
- an opening periphery of the cup-shaped diaphragm is squeezed in diameter compared with other portion of the cup-shaped diaphragm.
- the opening periphery of the cup-shaped diaphragm is curled radially inward so as to have a smaller diameter compared with a cylindrical wall of the cup-shaped diaphragm, so that the cup-shaped diaphragm can be easily inserted into the cylindrical bore from the opening periphery of the cup-shaped diaphragm.
- the cup-shaped diaphragm has a diameter substantially identical with that of the bore.
- the cup-shaped diaphragm has an axis identical with that of the bore.
- FIG. 1 is a partly cross-sectional view showing an ABS actuator in accordance with a first embodiment of the present invention
- FIG. 2 is a plan view showing the ABS actuator shown in FIG. 1;
- FIG. 3 is an enlarged cross-sectional view showing a through-hole and its vicinity of the ABS actuator shown in FIG. 1;
- FIG. 4 is a partly cross-sectional view showing an ABS actuator previously proposed by the inventor of the present application.
- FIG. 4 shows the arrangement of the ABS actuator previously proposed by the inventor.
- An ABS actuator 1100 is disposed between a master cylinder and a wheel cylinder in a braking apparatus.
- the ABS actuator 1100 has a housing 101 with a surface where various control valves 102 and 103 are installed.
- the control valves 102 and 103 control braking fluid flowing in a brake pipe arrangement.
- the housing 101 has a surface where a motor 104 is installed, which is opposed to the surface where the various control valves 102 and 103 are installed.
- the motor 104 drives a pump 105 .
- the housing 101 has a surface where a reservoir 106 is installed, which is different from the surface where the various control valves 102 and 103 are installed and is also different from the surface where the motor 104 is disposed.
- the housing 101 has a surface where a damper 107 is installed, which is opposed to the surface where the reservoir 106 is installed. This arrangement is effective in downsizing the housing 101 compared with a comparative arrangement in which the reservoir 106 and the damper 107 are installed on the same surface.
- the damper 107 is defined by a cylindrical sleeve 111 and a plug-like wall member 112 .
- the cylindrical sleeve 111 has an axis extending in the H direction of FIG. 4.
- the sleeve 111 is inserted into a cylindrical bore 110 provided at the surface where a port 108 of the wheel cylinder is installed.
- the cylindrical bore 110 has an axis extending in the H direction of FIG. 4.
- the plug-like wall member 112 is capable of closing an inlet opening of the bore 110 . After the cylindrical sleeve 111 is inserted into the bore 110 , the inlet opening of the bore 110 is closed by the plug-like wall member 112 .
- An inside space of the sleeve 111 defines a damper chamber 113 .
- the sleeve 111 has a stepped portion 111 a at a predetermined axial position where the diameter of the sleeve 111 is reduced compared with that of the remaining portion.
- the diameter of the sleeve 111 at a portion closer to the bottom of the bore 110 is larger than the diameter of the sleeve 111 at a portion closer to an inlet opening of the bore 110 .
- a large-diameter portion 111 b of the sleeve 111 is brought into contact with a cylindrical wall of the bore 110 .
- a small-diameter portion 111 c is spaced from the cylindrical wall of the bore 110 .
- a clearance 114 is provided between the small-diameter portion 111 c and the cylindrical wall of the bore 110 .
- the sleeve 111 has a through-hole 111 d opened at the small-diameter portion 111 c.
- the clearance 114 communicates with the damper chamber 113 via the through-hole 111 d.
- the port 109 of the master cylinder is offset from a pressurizing control valve 102 in the H direction of FIG. 4.
- the pressurizing control valve 102 is located adjacent to the reservoir 106 than the port 109 of the master cylinder.
- a conduit line A is a fluid passage connecting the master cylinder to the wheel cylinder.
- the conduit line A consists of a conduit line A 1 and a conduit line A 2 .
- the conduit line A 1 positioned between the port 109 of the master cylinder and the damper 107 , extends straight in an L direction from the port 109 of the master cylinder to the damper 107 .
- the conduit line Al extends along an axis of the port 109 of the master cylinder perpendicularly to the surface where the port 109 of the master cylinder is installed.
- the conduit line A 2 positioned between the damper 107 to the pressurizing control valve 102 , extends straight from the damper 107 to the pressurizing control valve 102 .
- conduit line A 2 extends along an axis of the pressurizing control valve 102 perpendicularly to the surface where the pressurizing control valve 102 is installed.
- the conduit line A 1 is offset from the conduit line A 2 in the H direction of FIG. 4.
- the conduit line A 2 is located adjacent to the reservoir 106 than the conduit line A 1 .
- the sleeve 111 is brought into contact with a bottom surface of the plug-like wall member 112 at its contact face 111 e.
- the contact face 111 e of the plug-like wall member 112 is configured into a bell mouth or an annular flange.
- a distance from the contact face 111 e to the stepped portion 111 a is equivalent to an offset amount of the conduit line A 1 with respect to the conduit line A 2 .
- the conduit line A 1 is connected to the conduit line A 2 via the clearance 114 .
- the braking fluid in the clearance 114 flows around the cylindrical sleeve 111 from the conduit line A 1 to the conduit line A 2 .
- the port 108 of the wheel cylinder is located at a predetermined position from the pressurizing control valve 102 .
- the pressurizing control valve 102 is spaced from the port 108 by a predetermined distance in the H direction.
- the distance between the port 108 and the pressurizing control valve 102 is, for example, equivalent to a minimum space (length) for forming the port 108 of the wheel cylinder in the housing 101 .
- This arrangement makes it possible to locate the pressurizing control valve 102 adjacent to the reservoir 106 . A distance from the port 108 of the wheel cylinder to the reservoir 106 can be reduced correspondingly. Accordingly, the housing 101 can be downsized in the H-direction of FIG. 4.
- the loudness of the noise caused during an ABS operation is dependent on a damper capacity. It is thus desirable to enlarge the damper capacity as much as possible to reduce the ABS noise. Especially, the anti-lock braking system is frequently operated in a cold weather condition. Thus, the need for reducing the ABS noise is very high and serious in cold areas.
- the clearance 114 between the sleeve 111 and the cylindrical wall of the bore 111 is formed as an annular fluid passage. This leads to lack of the diameter of the damper chamber 113 . Therefore, the damper capacity is substantially restricted to an insufficient value.
- the present invention proposes an improved arrangement of the hydraulic actuator preferably used for controlling braking fluid of an anti-lock braking system.
- This embodiment is based on an ABS actuator comprising a total of eight control valves which is practically known as 8-solenoid type ABS actuator.
- FIG. 1 is a cross-sectional view showing an ABS actuator 100 in accordance with a preferred embodiment of the present invention. Furthermore, FIG. 2 is a plan view showing the ABS actuator seen from the top. The arrangement of the ABS actuator 100 is explained with reference to FIGS. 1 and 2.
- the ABS actuator 100 is disposed between a master cylinder (not shown) and a wheel cylinder (not shown).
- the ABS actuator 100 comprises a housing 1 which is substantially configured into a hexahedral (or a cubic) body with various conduit lines formed therein.
- the housing 1 has a surface (i.e., second predetermined surface) where various control valves 2 and 3 are installed.
- the control valves 2 and 3 are provided to control braking fluid flowing in a brake piping arrangement.
- Each four of the control valves 2 ( 3 ) are alined in a W direction, as shown in FIG. 2.
- the W direction is normal to each of H and L directions.
- Two lines of the control valves 2 and 3 are arrayed in the H direction as shown in FIG. 1.
- the housing 1 has a surface (i.e., third predetermined surface) opposed to the above-described surface (i.e., second predetermined surface) where the various control valves 2 and 3 are installed.
- a motor 4 is installed on this surface (i.e., on the third predetermined surface). The motor 4 is provided to drive a pump 5 .
- the housing 1 has a surface (i.e., fourth predetermined surface) where a reservoir 6 is installed, which is substantially perpendicular to the surface (i.e., second predetermined surface) where various control valves 2 and 3 are installed and also perpendicular to the surface (i.e., third predetermined surface) where the motor 4 is installed.
- the housing 1 has a surface (i.e., first predetermined surface) where dampers 7 are installed, which is opposed to the surface where (i.e., fourth predetermined surface) the reservoir 6 is installed.
- a total of four ports 8 to be connected to the wheel cylinder are formed on the surface (i.e., first predetermined surface) where the dampers 7 are installed. These ports 8 communicate with pressurizing control valves 2 in the housing 1 .
- Two ports 9 to be connected to the master cylinder are formed on the surface (the third predetermined surface) where the motor 4 is installed.
- One of two master cylinder ports 9 is connected to two pressurizing control valves 2 positioned at a right side of the housing 1 shown in the plan view of FIG. 2.
- the other of two master cylinder ports 9 is connected to two pressurizing control valves 2 positioned at a left side of the housing 1 shown in the plan view of FIG. 2.
- Each master cylinder port 9 communicates via a conduit line A with the corresponding wheel cylinder ports 8 .
- the pressurizing control valve 2 provided in the conduit line A, opens or closes the conduit line A.
- the conduit line A is connected to a conduit line B at a predetermined portion between the pressurizing control valve 2 and the wheel cylinder.
- the conduit line B is connected to the reservoir 6 .
- the depressurizing control valve 3 provided in the conduit line B, controls braking fluid supplied to the reservoir 6 .
- the conduit line A is connected to the reservoir 6 at a portion between the master cylinder and the pressurizing control valve 2 via a conduit line C.
- the braking fluid, discharged into the reservoir 6 is returned to the conduit line A via the conduit line C.
- the pump 5 and the dampers 7 are provided in the conduit C to introduce and discharge braking fluid into and from the reservoir 6 .
- each damper 7 is inserted into a bore 10 .
- the bore 10 has a cylindrical shape with an axis of the bore 10 extending in the H direction.
- the cylindrical bore 10 is, for example, formed by partly drilling or machining the housing 1 from the surface (i.e., first predetermined surface) where the wheel cylinder ports 8 are formed.
- Each damper 7 is installed in the following manner.
- a cup-shaped diaphragm 21 is inserted into the cylindrical bore 10 so that the cup-shaped diaphragm 21 is settled in an inner portion (i.e., a bottom side) of the cylindrical bore 10 with an axis of the cup-shaped diaphragm 21 extending in the H direction.
- a plug-like wall member 12 is inserted into the cylindrical bore 10 to close the inlet opening of the bore 10 .
- the cup-shaped diaphragm 21 divides an inside space of the cylindrical bore 10 into two chambers 13 a and 13 b. Of two chambers 13 a and 13 b thus defined, one chamber 13 a (i.e., a first chamber) serves as a damper chamber which is connected to the conduit line C.
- the other chamber 13 b i.e., a second chamber is connected to the conduit line A.
- the cup-shaped diaphragm 21 is configured into a cylindrical cup shape with a circular opening at one axial end thereof (i.e., at the bottom side of the cylindrical bore 10 ) and a circular bottom 21 a at the other axial end thereof.
- the cup-shaped diaphragm 21 has an axis identical with that of the cylindrical bore 10 .
- the circular opening of the cup-shaped diaphragm 21 becomes a leading side when the cup-shaped diaphragm 21 is inserted into the cylindrical bore 10 in the axial direction.
- An opening periphery 21 b i.e., an annular opening edge of the cup-shaped diaphragm 21 is slightly squeezed in diameter compared with the remaining portion (i.e., a cylindrical wall of the cup-shaped diaphragm 21 ).
- the opening periphery 21 b being thus curled radially inward, makes it possible to easily insert the cup-shaped diaphragm 21 into the cylindrical bore 10 from the opening side of the cup-shaped diaphragm 21 .
- the cup-shaped diaphragm 21 has a press-fitting portion 21 c partly formed on the cylindrical wall thereof.
- the press-fitting portion 21 c protrudes radially outward from the surface of the cylindrical wall of the cup-shaped diaphragm 21 .
- the press-fitting portion 21 c extends in a circumferential direction of the cylindrical wall of the cup-shaped diaphragm 21 at a height equivalent to a center of the cup-shaped diaphragm 21 (in the axial direction of the cup-shaped diaphragm 21 ).
- the press-fitting portion 21 c has an enlarged diameter larger than the diameter of the remaining portion of the cylindrical wall of the cup-shaped diaphragm 21 .
- the cup-shaped diaphragm 21 has a through-hole 21 d, serving as an orifice, opened across a plate of the bottom 21 a.
- Two chambers 13 a and 13 b, separated by the cup-shaped diaphragm 21 communicate with each other via the through-hole 21 d.
- the conduit line C is connected to the conduit line A via the through-hole 21 d.
- FIG. 3 is an enlarged view of the through-hole 21 d and its vicinity.
- a region where the through-hole 21 d is provided is thin in thickness compared with the remaining portion of the bottom 21 a.
- the thinned or recessed region surrounding the through-hole 21 d can be easily formed by partly pressing the bottom 21 a of the cup-shaped diaphragm 21 .
- Providing the thinned or recessed region for the through-hole 21 d on the bottom 21 a is advantageous to prevent a burr 21 e from protruding from the surface of the bottom 21 a.
- the burr 21 e is inherently produced along an annular periphery of the through-hole 21 d when a drilling or machining operation is applied on the bottom 21 a for formation of the through-hole 21 d. If any force is applied on the burr 21 e, the burr 21 e may peel off the cup-shaped diaphragm 21 . However, this arrangement surely prevents the burr 21 e from peeling off the cup-shaped diaphragm 21 since the burr 2 l e stays or remains in a retracted position with respect to the surface of the bottom 21 a.
- the plug-like wall member 12 has a cylindrical main body (refer to FIG. 2) which corresponds to the cylindrical bore 10 . Furthermore, as shown in FIG. 1, a circular protruding portion 12 a is formed at an inner end of the plug-like wall member 12 .
- the circular protruding portion 12 a has a diameter smaller than that of the main body of the plug-like wall member 12 .
- the protruding portion 12 a presses the bottom 21 a of the cup-shaped diaphragm 21 .
- an insertion amount of the protruding portion 12 a determines an axial position of the cup-shaped diaphragm 21 when inserted in the cylindrical bore 10 .
- the cylindrical protruding portion 12 a is spaced from the cylindrical wall of the bore 10 . So, the chamber 13 b surrounds the cylindrical protruding portion 12 a of the plug-like wall member 12 .
- the conduit line A consists of a conduit line A 1 connecting the master cylinder port 9 to the chamber 13 b in the cylindrical bore 10 , a conduit line A 2 connecting the chamber 13 b to the pressurizing control valve 2 , and a conduit line A 3 connecting the pressurizing control valve 2 to the wheel cylinder port 8 .
- the conduit line A 1 extends straight in the L direction from the master cylinder port 9 toward the chamber 13 b of the cylindrical bore 10 .
- the master cylinder port 9 is offset from the pressurizing control valve 2 in the H direction.
- the conduit line A 2 comprises a straight conduit line S and a straight conduit line T.
- the conduit line S extends straight from the cylindrical wall of the bore 10 in both of the H and W directions. In other words, the conduit line S extends obliquely with respect to the axis of the cylindrical bore 10 .
- the conduit line T extends straight from the pressurizing control valve 2 in the L direction and communicates with the conduit line S.
- the present embodiment forms the straight conduit line S extending in both the H and W directions (i.e., obliquely) from the cylindrical wall of the cylindrical bore 10 constituting the chamber 13 b. This makes it possible to connect the master cylinder port 9 and the pressurizing control valve 2 which are offset each other.
- a conduit line U is provided between two adjacent pressurizing control valves 2 so as to extend in the W direction.
- the conduit line U connects two inlet ports of the adjacent pressurizing control valves 2 positioned at each of the right and left sides of the housing 1 shown in FIG. 2.
- each of two pressurizing control valves 2 located outside of the housing 1 can communicate with the chamber 13 b via the conduit line U.
- the conduit line A 3 extends straight from the pressurizing control valve 2 toward the master cylinder port 8 which is connected to the wheel cylinder. In this manner.
- the conduit line A consists of three straight conduit lines A 1 , A 2 and A 3 .
- the wheel cylinder port 8 is located at a predetermined distance from the pressurizing control valve 2 .
- the wheel cylinder port 8 is spaced in the H direction from the pressurizing control valve 2 .
- the distance from the wheel cylinder port 8 to the pressurizing control valve 2 is, for example, equivalent to a minimum space for forming the wheel cylinder port 8 .
- This arrangement makes it possible to locate the pressurizing control valve 2 adjacently to the reservoir 6 . A distance from the wheel cylinder port 8 to the reservoir 6 can be reduced correspondingly.
- the ABS actuator of the above-described embodiment is characterized in that the cup-shaped diaphragm 21 divides the inside space of the cylindrical bore 10 into the chambers 13 a and 13 b.
- One chamber 13 a serves as the damper chamber.
- the other chamber 13 b constitutes part of the conduit line A.
- the ABS actuator of the above-described embodiment no longer requires the clearance 114 of the annular fluid passage (refer to FIG. 4) which is provided in the ABS actuator previously proposed by the inventor of this application.
- the diameter of the damper 7 can be increased to a level equivalent to the diameter of the cylindrical bore 10 . This realizes a large capacity of the damper 7 . Having a large damper capacity is advantageous in reducing the noise caused during the ABS operation.
- the ABS actuator of the above-described embodiment comprises the reservoir 6 and the damper 7 disposed on the opposed surfaces of the housing 1 .
- This is advantageous in downsizing the housing 1 in the L direction shown in FIG. 1, like the ABS actuator shown in FIG. 4.
- the master cylinder port 8 is offset from the pressurizing control valve 2 in the H direction. This offset arrangement produces or secures a space for arranging the port 8 of the wheel cylinder. This is advantageous in downsizing the housing 1 in the H direction shown in FIG. 1, like the ABS actuator shown in FIG. 4.
- the sleeve 111 has a cylindrical body. An edge of the sleeve 111 is pressed by the plug-like wall member 112 . So, the sleeve 111 provides the damper chamber 113 partitioned from the conduit line A. However, the braking fluid may leak through a clearance between the sleeve 111 and the plug-like wall member 112 . This gives adverse influence to the orifice effect should be brought by the through-hole 111 d.
- the above-described embodiment employs the cup-shaped diaphragm 21 to provide the chamber 13 a serving as the damper chamber which is partitioned from the chamber 13 b constituting part of the conduit line A. Employment of the cup-shaped diaphragm 21 ensures the orifice effect brought by the through-hole 21 d.
- the master cylinder port 9 is offset from the pressurizing control valve 2 .
- the conduit line T extends 5 obliquely from the cylindrical wall of the bore 10 .
- the housing 1 can be downsized in the H direction in FIG. 1.
- the present invention does not always require the above-described arrangement since it is possible to secure a sufficient damper capacity in a case where the annular fluid passage of the ABS actuator shown in FIG. 4 is not necessary. Even in this case, it is possible to downsize the housing 1 in the L direction of FIG. 1.
Abstract
Description
- The present invention relates to a hydraulic actuator preferably used for controlling braking fluid of an anti-lock braking system (hereinafter, abbreviated by ABS) installed in an automotive vehicle.
- In the anti-lock braking system, the hydraulic actuator is operated to precisely and promptly increase and decrease the hydraulic pressure of each wheel cylinder in accordance with rotational conditions of each wheel to prevent the wheel from locking during the braking operation.
- An object of the present invention is to secure a sufficient damper capacity for an ABS actuator to reduce the noise caused during an ABS operation.
- To accomplish the above and other related objects, the present invention provides a first ABS actuator comprising a housing having a first predetermined surface where a bore is formed. A damper, defined in the bore, has an axis extending in a depth direction of the bore. A cup-shaped diaphragm, disposed in the bore, divides an inside space of the bore into a first chamber and a second chamber. The cup-shaped diaphragm has an opening at one axial end and a bottom at an opposed axial end. The opening of the cup-shaped diaphragm becomes a leading side when the cup-shaped diaphragm is inserted into the bore. A plug-like wall member closes an opening of the bore. A damper chamber is constituted by the first chamber and includes an inside space of the cup-shaped diaphragm. The housing has a second predetermined surface where a control valve is installed. The second predetermined surface is substantially perpendicular to the first predetermined surface. The housing has a third predetermined surface where a first port is formed. The third predetermined surface is substantially perpendicular to the first predetermined surface and is opposed to the second predetermined surface. And, a main conduit line connects the first port to the control valve.
- In this first ABS actuator, the plug-like wall member has a protruding portion for pushing the bottom of the cup-shaped diaphragm. The protruding portion is spaced from a cylindrical wall of the bore. An annular space is formed between the protruding portion and the cylindrical wall of the bore. The annular space constitutes the second chamber. And, a first conduit line has its inlet opened to the annular space provided around the protruding portion and extends from the annular space as part of the main conduit line.
- With this arrangement, the damper diameter can be increased to a level equivalent to the diameter of the bore. This realizes a large damper capacity. Thus, it becomes possible to reduce the noise caused during the ABS operation.
- Furthermore, the present invention provides a second ABS actuator comprising a housing having a first predetermined surface where a bore is formed. A damper, defined in the bore, has an axis extending in a depth direction of the bore. A cup-shaped diaphragm, disposed in the bore, divides an inside space of the bore into a first chamber and a second chamber. The cup-shaped diaphragm has an opening at one axial end and a bottom at an opposed axial end. The opening of the cup-shaped diaphragm becomes a leading side when the cup-shaped diaphragm is inserted into the bore. A plug-like wall member closes an opening of the bore. A damper chamber is constituted by the first chamber and includes an inside space of the cup-shaped diaphragm. The housing has a second predetermined surface where a control valve is installed. The second predetermined surface is substantially perpendicular to the first predetermined surface. The housing has a third predetermined surface where a first port is formed. The third predetermined surface is substantially perpendicular to the first predetermined surface and is opposed to the second predetermined surface. A second port is formed on the first predetermined surface where the damper is installed. And, a main conduit line is formed in the housing so as to communicate with the second chamber. The main conduit line connects the first port to the second port via the control valve.
- In this second ABS actuator, the first port is offset from the control valve in an axial direction of the damper. The control valve is located far from the first predetermined surface compared with the first port. And, the main conduit line connects the second chamber to the control valve via a first conduit line extending obliquely with respect to the axis of the damper from a cylindrical wall of the bore.
- In this manner, providing the first conduit line extending obliquely with respect to the axis of the damper from the cylindrical wall of the bore makes it possible to connect the second chamber to the control valve under a condition where the first port is offset from the control valve in the axial direction of the damper and the control valve is located far from the first predetermined surface compared with the first port. Accordingly, in addition to the above-described effect of the first ABS actuator, it becomes possible to downsize the housing in the axial direction of the damper.
- In the above-described second ABS actuator, It is preferable that the plug-like wall member has a protruding portion for pushing the bottom of the cup-shaped diaphragm. And, the protruding portion is spaced from the cylindrical wall of the bore. An annular space is formed between the protruding portion and the cylindrical wall of the bore constitutes the second chamber. The first conduit line has its inlet opened to the annular space provided around the protruding portion. With this arrangement, it becomes possible to fix the position of the cup-shaped diaphragm by the protruding portion.
- According to a preferred embodiment of the present invention, the protruding portion of the plug-like wall member is a circular protruding portion formed at an inner end of the plug-like wall member. A diameter of the circular protruding portion is smaller than that of a main body of the plug-like wall member. The circular protruding portion presses the bottom of the cup-shaped diaphragm when the plug-like wall member is inserted into the bore, so that an insertion amount of the circular protruding portion substantially determines an axial position of the cup-shaped diaphragm in the bore.
- Preferably, the cylindrical protruding portion is spaced from the cylindrical wall of the bore when the plug-like wall member is inserted in the bore so as to close the opening of the bore, so that the second chamber surrounds the cylindrical protruding portion of the plug-like wall member.
- According to the preferred embodiment of the present invention, the main conduit line further comprises a second conduit line which extends from the control valve in a direction substantially perpendicular to the second predetermined surface and is connected to the first conduit line.
- The pressurizing control valve is offset from the annular space provided around the protruding portion of the plug-like wall member in a direction normal to the first predetermined surface. The first conduit line extends straight and obliquely from the annular space and is connected to the second conduit line.
- For example, two control valves are installed adjacent to each other on the second predetermined surface. One of the two control valves is directly connected to the first conduit line via the second conduit line. And, the other of the two control valves is connected to the first conduit line via the second conduit line and a third conduit line connecting the two control valves.
- In this manner, when two control valves are disposed adjacent to each other, it is desirable that one of two control valves is directly connected to the first conduit line via the second conduit line. The other control valve can be connected to the first conduit line via the second and third conduit lines.
- Furthermore, it is preferable that a through-hole is opened on the bottom of the cup-shaped diaphragm. The through-hole serves as an orifice connecting the first chamber to the second chamber.
- In this case, it is further preferable that a region where the through-hole is opened is thin in thickness compared with the remaining portion of the bottom of the cup-shaped diaphragm. For example, a recessed region is formed on the bottom so as to surround the through-hole. The recessed region has a sufficient depth so that a burr formed around the through-hole remains in a retracted position with respect to a surface of the bottom.
- Although the burr is inherently produced along an annular periphery of a through-hole during a formation of the through-hole, the above-described arrangement prevents the burr from protruding from the surface of the bottom. Thus, it becomes possible to prevent the burr from peeling off the cup-shaped diaphragm.
- Furthermore, it is preferable that the cup-shaped diaphragm has a press-fitting portion partly formed on a cylindrical wall thereof. The press-fitting portion has an enlarged diameter larger than the diameter of other portion of the cup-shaped diaphragm. And, the cup-shaped diaphragm is firmly fixed in the bore by the press-fitting portion.
- Preferably, the press-fitting portion protrudes radially outward from a surface of the cylindrical wall of the cup-shaped diaphragm. The press-fitting portion extends in a circumferential direction of the cylindrical wall of the cup-shaped diaphragm.
- In this manner, forming the press-fitting portion on the cylindrical wall of the cup-shaped diaphragm makes it possible to firmly fix the cup-shaped diaphragm in the bore.
- Moreover, it is preferable that an opening periphery of the cup-shaped diaphragm is squeezed in diameter compared with other portion of the cup-shaped diaphragm.
- Preferably, the opening periphery of the cup-shaped diaphragm is curled radially inward so as to have a smaller diameter compared with a cylindrical wall of the cup-shaped diaphragm, so that the cup-shaped diaphragm can be easily inserted into the cylindrical bore from the opening periphery of the cup-shaped diaphragm.
- In this manner, squeezing the diameter of the opening periphery of the cup-shaped diaphragm makes it possible to easily insert the cup-shaped diaphragm in the bore.
- Preferably, the cup-shaped diaphragm has a diameter substantially identical with that of the bore. The cup-shaped diaphragm has an axis identical with that of the bore.
- The above and other objects, features and advantages of the present invention will become more apparent from the following detailed description which is to be read in conjunction with the accompanying drawings, in which:
- FIG. 1 is a partly cross-sectional view showing an ABS actuator in accordance with a first embodiment of the present invention;
- FIG. 2 is a plan view showing the ABS actuator shown in FIG. 1;
- FIG. 3 is an enlarged cross-sectional view showing a through-hole and its vicinity of the ABS actuator shown in FIG. 1; and
- FIG. 4 is a partly cross-sectional view showing an ABS actuator previously proposed by the inventor of the present application.
-
- The inventor has previously proposed a compact ABS actuator in an earlier unpublished patent application (i.e., the Japanese patent application No. 11-8145).
- FIG. 4 shows the arrangement of the ABS actuator previously proposed by the inventor.
- An
ABS actuator 1100 is disposed between a master cylinder and a wheel cylinder in a braking apparatus. TheABS actuator 1100 has ahousing 101 with a surface wherevarious control valves control valves housing 101 has a surface where amotor 104 is installed, which is opposed to the surface where thevarious control valves motor 104 drives apump 105. - The
housing 101 has a surface where areservoir 106 is installed, which is different from the surface where thevarious control valves motor 104 is disposed. Thehousing 101 has a surface where adamper 107 is installed, which is opposed to the surface where thereservoir 106 is installed. This arrangement is effective in downsizing thehousing 101 compared with a comparative arrangement in which thereservoir 106 and thedamper 107 are installed on the same surface. - The
damper 107 is defined by acylindrical sleeve 111 and a plug-like wall member 112. Thecylindrical sleeve 111 has an axis extending in the H direction of FIG. 4. Thesleeve 111 is inserted into acylindrical bore 110 provided at the surface where aport 108 of the wheel cylinder is installed. Thecylindrical bore 110 has an axis extending in the H direction of FIG. 4. The plug-like wall member 112 is capable of closing an inlet opening of thebore 110. After thecylindrical sleeve 111 is inserted into thebore 110, the inlet opening of thebore 110 is closed by the plug-like wall member 112. An inside space of thesleeve 111 defines adamper chamber 113. - The
sleeve 111 has a steppedportion 111 a at a predetermined axial position where the diameter of thesleeve 111 is reduced compared with that of the remaining portion. The diameter of thesleeve 111 at a portion closer to the bottom of thebore 110 is larger than the diameter of thesleeve 111 at a portion closer to an inlet opening of thebore 110. A large-diameter portion 111 b of thesleeve 111 is brought into contact with a cylindrical wall of thebore 110. A small-diameter portion 111 c is spaced from the cylindrical wall of thebore 110. Thus, aclearance 114 is provided between the small-diameter portion 111 c and the cylindrical wall of thebore 110. - Furthermore, the
sleeve 111 has a through-hole 111 d opened at the small-diameter portion 111 c. Theclearance 114 communicates with thedamper chamber 113 via the through-hole 111 d. - The
port 109 of the master cylinder is offset from a pressurizingcontrol valve 102 in the H direction of FIG. 4. The pressurizingcontrol valve 102 is located adjacent to thereservoir 106 than theport 109 of the master cylinder. - A conduit line A is a fluid passage connecting the master cylinder to the wheel cylinder. The conduit line A consists of a conduit line A1 and a conduit line A2. The conduit line A1, positioned between the
port 109 of the master cylinder and thedamper 107, extends straight in an L direction from theport 109 of the master cylinder to thedamper 107. In other words, the conduit line Al extends along an axis of theport 109 of the master cylinder perpendicularly to the surface where theport 109 of the master cylinder is installed. The conduit line A2, positioned between thedamper 107 to the pressurizingcontrol valve 102, extends straight from thedamper 107 to the pressurizingcontrol valve 102. In other words, the conduit line A2 extends along an axis of the pressurizingcontrol valve 102 perpendicularly to the surface where the pressurizingcontrol valve 102 is installed. Thus, the conduit line A1 is offset from the conduit line A2 in the H direction of FIG. 4. The conduit line A2 is located adjacent to thereservoir 106 than the conduit line A1. - The
sleeve 111 is brought into contact with a bottom surface of the plug-like wall member 112 at itscontact face 111 e. Thecontact face 111 e of the plug-like wall member 112 is configured into a bell mouth or an annular flange. A distance from thecontact face 111 e to the steppedportion 111 a is equivalent to an offset amount of the conduit line A1 with respect to the conduit line A2. The conduit line A1 is connected to the conduit line A2 via theclearance 114. The braking fluid in theclearance 114 flows around thecylindrical sleeve 111 from the conduit line A1 to the conduit line A2. - On the other hand, the
port 108 of the wheel cylinder is located at a predetermined position from the pressurizingcontrol valve 102. Namely, the pressurizingcontrol valve 102 is spaced from theport 108 by a predetermined distance in the H direction. The distance between theport 108 and the pressurizingcontrol valve 102 is, for example, equivalent to a minimum space (length) for forming theport 108 of the wheel cylinder in thehousing 101. This arrangement makes it possible to locate the pressurizingcontrol valve 102 adjacent to thereservoir 106. A distance from theport 108 of the wheel cylinder to thereservoir 106 can be reduced correspondingly. Accordingly, thehousing 101 can be downsized in the H-direction of FIG. 4. - The above-described downsizing of the
housing 101 in the L and H directions leads to the overall downsizing of theABS actuator 1100. - The loudness of the noise caused during an ABS operation is dependent on a damper capacity. It is thus desirable to enlarge the damper capacity as much as possible to reduce the ABS noise. Especially, the anti-lock braking system is frequently operated in a cold weather condition. Thus, the need for reducing the ABS noise is very high and serious in cold areas.
- However, according to the above-described ABS actuator, the
clearance 114 between thesleeve 111 and the cylindrical wall of thebore 111 is formed as an annular fluid passage. This leads to lack of the diameter of thedamper chamber 113. Therefore, the damper capacity is substantially restricted to an insufficient value. -
- In view of the foregoing, the present invention proposes an improved arrangement of the hydraulic actuator preferably used for controlling braking fluid of an anti-lock braking system.
- Hereinafter, a preferred embodiment of the present invention will be explained with reference to FIGS.1 to 3. This embodiment is based on an ABS actuator comprising a total of eight control valves which is practically known as 8-solenoid type ABS actuator.
- FIG. 1 is a cross-sectional view showing an
ABS actuator 100 in accordance with a preferred embodiment of the present invention. Furthermore, FIG. 2 is a plan view showing the ABS actuator seen from the top. The arrangement of theABS actuator 100 is explained with reference to FIGS. 1 and 2. - The
ABS actuator 100 is disposed between a master cylinder (not shown) and a wheel cylinder (not shown). The ABS actuator 100 comprises ahousing 1 which is substantially configured into a hexahedral (or a cubic) body with various conduit lines formed therein. - The
housing 1 has a surface (i.e., second predetermined surface) wherevarious control valves control valves control valves control valves housing 1. - The
housing 1 has a surface (i.e., third predetermined surface) opposed to the above-described surface (i.e., second predetermined surface) where thevarious control valves motor 4 is installed on this surface (i.e., on the third predetermined surface). Themotor 4 is provided to drive apump 5. - The
housing 1 has a surface (i.e., fourth predetermined surface) where areservoir 6 is installed, which is substantially perpendicular to the surface (i.e., second predetermined surface) wherevarious control valves motor 4 is installed. Thehousing 1 has a surface (i.e., first predetermined surface) wheredampers 7 are installed, which is opposed to the surface where (i.e., fourth predetermined surface) thereservoir 6 is installed. - Furthermore, as shown in FIG. 2, a total of four
ports 8 to be connected to the wheel cylinder are formed on the surface (i.e., first predetermined surface) where thedampers 7 are installed. Theseports 8 communicate with pressurizingcontrol valves 2 in thehousing 1. Twoports 9 to be connected to the master cylinder are formed on the surface (the third predetermined surface) where themotor 4 is installed. One of twomaster cylinder ports 9 is connected to two pressurizingcontrol valves 2 positioned at a right side of thehousing 1 shown in the plan view of FIG. 2. The other of twomaster cylinder ports 9 is connected to two pressurizingcontrol valves 2 positioned at a left side of thehousing 1 shown in the plan view of FIG. 2. These twoports 9 are offset from the pressurizingcontrol valves 2 in the H direction as apparent from FIG. 1. Compared with the position of themaster cylinder ports 9, the pressurizingcontrol valves 2 are located far from the surface (i.e., the first predetermined surface) where thedampers 7 are installed. - Hereinafter, a detailed connecting arrangement of the above-described components will be explained.
- Each
master cylinder port 9 communicates via a conduit line A with the correspondingwheel cylinder ports 8. The pressurizingcontrol valve 2, provided in the conduit line A, opens or closes the conduit line A. The conduit line A is connected to a conduit line B at a predetermined portion between the pressurizingcontrol valve 2 and the wheel cylinder. The conduit line B is connected to thereservoir 6. The depressurizingcontrol valve 3, provided in the conduit line B, controls braking fluid supplied to thereservoir 6. - The conduit line A is connected to the
reservoir 6 at a portion between the master cylinder and the pressurizingcontrol valve 2 via a conduit line C. The braking fluid, discharged into thereservoir 6, is returned to the conduit line A via the conduit line C. Thepump 5 and thedampers 7 are provided in the conduit C to introduce and discharge braking fluid into and from thereservoir 6. - More specifically, each
damper 7 is inserted into abore 10. Thebore 10 has a cylindrical shape with an axis of thebore 10 extending in the H direction. The cylindrical bore 10 is, for example, formed by partly drilling or machining thehousing 1 from the surface (i.e., first predetermined surface) where thewheel cylinder ports 8 are formed. Eachdamper 7 is installed in the following manner. - First, a cup-shaped
diaphragm 21 is inserted into the cylindrical bore 10 so that the cup-shapeddiaphragm 21 is settled in an inner portion (i.e., a bottom side) of the cylindrical bore 10 with an axis of the cup-shapeddiaphragm 21 extending in the H direction. Next, a plug-like wall member 12 is inserted into the cylindrical bore 10 to close the inlet opening of thebore 10. The cup-shapeddiaphragm 21 divides an inside space of the cylindrical bore 10 into twochambers chambers chamber 13 a (i.e., a first chamber) serves as a damper chamber which is connected to the conduit line C. Theother chamber 13 b (i.e., a second chamber) is connected to the conduit line A. - The cup-shaped
diaphragm 21 is configured into a cylindrical cup shape with a circular opening at one axial end thereof (i.e., at the bottom side of the cylindrical bore 10) and a circular bottom 21 a at the other axial end thereof. The cup-shapeddiaphragm 21 has an axis identical with that of thecylindrical bore 10. The circular opening of the cup-shapeddiaphragm 21 becomes a leading side when the cup-shapeddiaphragm 21 is inserted into the cylindrical bore 10 in the axial direction. An openingperiphery 21 b (i.e., an annular opening edge) of the cup-shapeddiaphragm 21 is slightly squeezed in diameter compared with the remaining portion (i.e., a cylindrical wall of the cup-shaped diaphragm 21). Providing the openingperiphery 21 b, being thus curled radially inward, makes it possible to easily insert the cup-shapeddiaphragm 21 into the cylindrical bore 10 from the opening side of the cup-shapeddiaphragm 21. - Furthermore, the cup-shaped
diaphragm 21 has a press-fittingportion 21 c partly formed on the cylindrical wall thereof. The press-fittingportion 21 c protrudes radially outward from the surface of the cylindrical wall of the cup-shapeddiaphragm 21. The press-fittingportion 21 c extends in a circumferential direction of the cylindrical wall of the cup-shapeddiaphragm 21 at a height equivalent to a center of the cup-shaped diaphragm 21 (in the axial direction of the cup-shaped diaphragm 21). - The press-fitting
portion 21 c has an enlarged diameter larger than the diameter of the remaining portion of the cylindrical wall of the cup-shapeddiaphragm 21. When the cup-shapeddiaphragm 21 is inserted into thecylindrical bore 10, the press-fittingportion 21 c is pressed into thecylindrical bore 10. So, the cup-shapeddiaphragm 21 is firmly fixed in the cylindrical bore 10 of thehousing 1. - Furthermore, the cup-shaped
diaphragm 21 has a through-hole 21 d, serving as an orifice, opened across a plate of the bottom 21 a. Twochambers diaphragm 21, communicate with each other via the through-hole 21 d. In other words, the conduit line C is connected to the conduit line A via the through-hole 21 d. - FIG. 3 is an enlarged view of the through-
hole 21 d and its vicinity. A region where the through-hole 21 d is provided is thin in thickness compared with the remaining portion of the bottom 21 a. For example, the thinned or recessed region surrounding the through-hole 21 d can be easily formed by partly pressing the bottom 21 a of the cup-shapeddiaphragm 21. Providing the thinned or recessed region for the through-hole 21 d on the bottom 21 a is advantageous to prevent aburr 21 e from protruding from the surface of the bottom 21 a. Theburr 21 e is inherently produced along an annular periphery of the through-hole 21 d when a drilling or machining operation is applied on the bottom 21 a for formation of the through-hole 21 d. If any force is applied on theburr 21 e, theburr 21 e may peel off the cup-shapeddiaphragm 21. However, this arrangement surely prevents theburr 21 e from peeling off the cup-shapeddiaphragm 21 since the burr 2le stays or remains in a retracted position with respect to the surface of the bottom 21 a. - The plug-
like wall member 12 has a cylindrical main body (refer to FIG. 2) which corresponds to thecylindrical bore 10. Furthermore, as shown in FIG. 1, a circular protrudingportion 12 a is formed at an inner end of the plug-like wall member 12. The circular protrudingportion 12 a has a diameter smaller than that of the main body of the plug-like wall member 12. When the plug-like wall member 12 is inserted into thecylindrical bore 10, the protrudingportion 12 a presses the bottom 21 a of the cup-shapeddiaphragm 21. In other words, an insertion amount of the protrudingportion 12 a determines an axial position of the cup-shapeddiaphragm 21 when inserted in thecylindrical bore 10. When the plug-like wall member 12 is inserted in the cylindrical bore 10 so as to close the opening of thebore 10, the cylindrical protrudingportion 12 a is spaced from the cylindrical wall of thebore 10. So, the chamber 13 bsurrounds the cylindrical protrudingportion 12 a of the plug-like wall member 12. - Furthermore, as shown in FIGS. 1 and 2, the conduit line A consists of a conduit line A1 connecting the
master cylinder port 9 to thechamber 13 b in thecylindrical bore 10, a conduit line A2 connecting thechamber 13 b to the pressurizingcontrol valve 2, and a conduit line A3 connecting the pressurizingcontrol valve 2 to thewheel cylinder port 8. - The conduit line A1 extends straight in the L direction from the
master cylinder port 9 toward thechamber 13 b of thecylindrical bore 10. Themaster cylinder port 9 is offset from the pressurizingcontrol valve 2 in the H direction. The conduit line A2 comprises a straight conduit line S and a straight conduit line T. The conduit line S extends straight from the cylindrical wall of thebore 10 in both of the H and W directions. In other words, the conduit line S extends obliquely with respect to the axis of thecylindrical bore 10. The conduit line T extends straight from the pressurizingcontrol valve 2 in the L direction and communicates with the conduit line S. - In this manner, the present embodiment forms the straight conduit line S extending in both the H and W directions (i.e., obliquely) from the cylindrical wall of the cylindrical bore10 constituting the
chamber 13 b. This makes it possible to connect themaster cylinder port 9 and the pressurizingcontrol valve 2 which are offset each other. - As shown in FIG. 2, a conduit line U is provided between two adjacent
pressurizing control valves 2 so as to extend in the W direction. The conduit line U connects two inlet ports of the adjacentpressurizing control valves 2 positioned at each of the right and left sides of thehousing 1 shown in FIG. 2. Thus, each of two pressurizingcontrol valves 2 located outside of thehousing 1 can communicate with thechamber 13 b via the conduit line U. The conduit line A3 extends straight from the pressurizingcontrol valve 2 toward themaster cylinder port 8 which is connected to the wheel cylinder. In this manner. The conduit line A consists of three straight conduit lines A1, A2 and A3. - On the other hand, the
wheel cylinder port 8 is located at a predetermined distance from the pressurizingcontrol valve 2. In other words, thewheel cylinder port 8 is spaced in the H direction from the pressurizingcontrol valve 2. The distance from thewheel cylinder port 8 to the pressurizingcontrol valve 2 is, for example, equivalent to a minimum space for forming thewheel cylinder port 8. This arrangement makes it possible to locate the pressurizingcontrol valve 2 adjacently to thereservoir 6. A distance from thewheel cylinder port 8 to thereservoir 6 can be reduced correspondingly. - As explained above, the ABS actuator of the above-described embodiment is characterized in that the cup-shaped
diaphragm 21 divides the inside space of the cylindrical bore 10 into thechambers chamber 13 a serves as the damper chamber. Theother chamber 13 b constitutes part of the conduit line A. With this arrangement, the ABS actuator of the above-described embodiment no longer requires theclearance 114 of the annular fluid passage (refer to FIG. 4) which is provided in the ABS actuator previously proposed by the inventor of this application. Hence, the diameter of thedamper 7 can be increased to a level equivalent to the diameter of thecylindrical bore 10. This realizes a large capacity of thedamper 7. Having a large damper capacity is advantageous in reducing the noise caused during the ABS operation. - Furthermore, as shown in FIG. 1, the ABS actuator of the above-described embodiment comprises the
reservoir 6 and thedamper 7 disposed on the opposed surfaces of thehousing 1. This is advantageous in downsizing thehousing 1 in the L direction shown in FIG. 1, like the ABS actuator shown in FIG. 4. Furthermore, themaster cylinder port 8 is offset from the pressurizingcontrol valve 2 in the H direction. This offset arrangement produces or secures a space for arranging theport 8 of the wheel cylinder. This is advantageous in downsizing thehousing 1 in the H direction shown in FIG. 1, like the ABS actuator shown in FIG. 4. - According to the ABS actuator shown in FIG. 4, the
sleeve 111 has a cylindrical body. An edge of thesleeve 111 is pressed by the plug-like wall member 112. So, thesleeve 111 provides thedamper chamber 113 partitioned from the conduit line A. However, the braking fluid may leak through a clearance between thesleeve 111 and the plug-like wall member 112. This gives adverse influence to the orifice effect should be brought by the through-hole 111 d. - To the contrary, the above-described embodiment employs the cup-shaped
diaphragm 21 to provide thechamber 13 a serving as the damper chamber which is partitioned from thechamber 13 b constituting part of the conduit line A. Employment of the cup-shapeddiaphragm 21 ensures the orifice effect brought by the through-hole 21 d. -
- According to the above-described embodiment, the
master cylinder port 9 is offset from the pressurizingcontrol valve 2. The conduit line T extends 5 obliquely from the cylindrical wall of thebore 10. Thehousing 1 can be downsized in the H direction in FIG. 1. However, the present invention does not always require the above-described arrangement since it is possible to secure a sufficient damper capacity in a case where the annular fluid passage of the ABS actuator shown in FIG. 4 is not necessary. Even in this case, it is possible to downsize thehousing 1 in the L direction of FIG. 1. - The present embodiments as described are therefore intended to be only illustrative and not restrictive, since the scope of the invention is defined by the appended claims rather than by the description preceding them. All changes that fall within the metes and bounds of the claims, or equivalents of such metes and bounds, are therefore intended to be embraced by the claims.
Claims (39)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP2000-81826 | 2000-03-17 | ||
JP2000-081826 | 2000-03-17 | ||
JP2000081826A JP3690236B2 (en) | 2000-03-17 | 2000-03-17 | ABS actuator |
Publications (2)
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US20010022469A1 true US20010022469A1 (en) | 2001-09-20 |
US6443537B2 US6443537B2 (en) | 2002-09-03 |
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Application Number | Title | Priority Date | Filing Date |
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US09/808,955 Expired - Lifetime US6443537B2 (en) | 2000-03-17 | 2001-03-16 | Hydraulic actuator for an anti-lock braking system |
Country Status (5)
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US (1) | US6443537B2 (en) |
EP (1) | EP1134141B1 (en) |
JP (1) | JP3690236B2 (en) |
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US4349233A (en) * | 1980-05-07 | 1982-09-14 | Caterpillar Tractor Co. | Method and apparatus for controlling wheel slip on differentially mounted wheels |
US5022717A (en) * | 1988-12-12 | 1991-06-11 | Lucas Industries Public Limited Company | Pressure control unit, especially for motor vehicle brake systems |
DE8900706U1 (en) * | 1989-01-23 | 1990-05-23 | Lucas Industries P.L.C., Birmingham, West Midlands, Gb | |
DE4013160A1 (en) * | 1990-04-25 | 1991-10-31 | Bosch Gmbh Robert | HOUSING BLOCK FOR A HYDRAULIC BRAKE SYSTEM |
DE4111201A1 (en) | 1991-04-06 | 1992-10-08 | Bosch Gmbh Robert | Hydraulic regulator for vehicle antilocking braking system - has damping chamber provided by blind bore in housing block fitted to regulator valve |
JP3364990B2 (en) * | 1992-08-28 | 2003-01-08 | 株式会社デンソー | Anti-skid device |
DE4306222A1 (en) * | 1992-10-09 | 1994-09-01 | Teves Gmbh Alfred | Hydraulic unit for slip-controlled brake systems |
DE4311263A1 (en) * | 1993-04-06 | 1994-10-13 | Bosch Gmbh Robert | Damping device in particular for a hydraulic brake system |
JPH0747944A (en) | 1993-08-05 | 1995-02-21 | Nissin Kogyo Kk | Anti-lock brake control device |
DE19542582A1 (en) * | 1995-11-15 | 1997-05-22 | Teves Gmbh Alfred | Electrohydraulic unit for pressure control in motor vehicle brake systems |
DE19808626B4 (en) * | 1998-02-28 | 2009-06-18 | Continental Teves Ag & Co. Ohg | Electrohydraulic unit for pressure control in motor vehicle brake systems |
JP4304757B2 (en) * | 1998-04-24 | 2009-07-29 | 株式会社デンソー | ABS actuator |
JP3932710B2 (en) * | 1998-12-12 | 2007-06-20 | アイシン精機株式会社 | Hydraulic control unit |
JP2000203405A (en) * | 1999-01-14 | 2000-07-25 | Denso Corp | Abs actuator |
-
2000
- 2000-03-17 JP JP2000081826A patent/JP3690236B2/en not_active Expired - Fee Related
-
2001
- 2001-01-18 CA CA002331635A patent/CA2331635C/en not_active Expired - Fee Related
- 2001-03-15 EP EP01106570A patent/EP1134141B1/en not_active Expired - Lifetime
- 2001-03-15 DE DE60110959T patent/DE60110959T2/en not_active Expired - Lifetime
- 2001-03-16 US US09/808,955 patent/US6443537B2/en not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060125314A1 (en) * | 2004-12-13 | 2006-06-15 | Hitoshi Hashiba | Vehicle control device utilizing brake hydraulic pressure |
US7720589B2 (en) | 2004-12-13 | 2010-05-18 | Advics Co., Ltd. | Vehicle control device utilizing brake hydraulic pressure |
Also Published As
Publication number | Publication date |
---|---|
CA2331635A1 (en) | 2001-09-17 |
US6443537B2 (en) | 2002-09-03 |
DE60110959T2 (en) | 2006-04-27 |
JP3690236B2 (en) | 2005-08-31 |
EP1134141A2 (en) | 2001-09-19 |
JP2001260846A (en) | 2001-09-26 |
CA2331635C (en) | 2004-04-20 |
EP1134141B1 (en) | 2005-05-25 |
EP1134141A3 (en) | 2003-08-13 |
DE60110959D1 (en) | 2005-06-30 |
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