WO1998040260A1 - Sous-ensemble armature et manchon pour soupapes de commande du systeme de freinage d'un vehicule, et leur procede de fabrication - Google Patents

Sous-ensemble armature et manchon pour soupapes de commande du systeme de freinage d'un vehicule, et leur procede de fabrication Download PDF

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Publication number
WO1998040260A1
WO1998040260A1 PCT/US1998/004824 US9804824W WO9840260A1 WO 1998040260 A1 WO1998040260 A1 WO 1998040260A1 US 9804824 W US9804824 W US 9804824W WO 9840260 A1 WO9840260 A1 WO 9840260A1
Authority
WO
WIPO (PCT)
Prior art keywords
armature
valve
sleeve
valve body
subassembly
Prior art date
Application number
PCT/US1998/004824
Other languages
English (en)
Inventor
Herbert L. Linkner, Jr.
Original Assignee
Kelsey-Hayes Company
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kelsey-Hayes Company filed Critical Kelsey-Hayes Company
Priority to EP98910326A priority Critical patent/EP0966379A1/fr
Priority to AU64591/98A priority patent/AU6459198A/en
Publication of WO1998040260A1 publication Critical patent/WO1998040260A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • 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
    • 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
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • 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
    • B60T8/3655—Continuously controlled electromagnetic valves
    • B60T8/366—Valve details
    • B60T8/367—Seat valves, e.g. poppet valves
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/003—Housing formed from a plurality of the same valve elements
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/081—Magnetic constructions

Definitions

  • This invention relates in general to vehicular braking systems, and in particular is concerned with a low-fiiction sleeve and armature subassembly for a control valve in vehicular braking systems.
  • Hydraulic braking systems for vehicles are well known.
  • a typical hydraulic braking system includes a master cylinder, fluid conduit arranged into a desired circuit, and wheel brake cylinders.
  • the master cylinder generates hydraulic forces in the brake circuit by pressurizing brake fluid when the driver steps on the brake pedat.
  • the pressurized fluid travels through the fluid conduit in the circuit to actuate brake cylinders at the wheels and slow the vehicle.
  • Anti-lock braking systems for vehicles are also well known hydraulic systems.
  • a hydraulic control unit or housing containing control valves and other components such as a pump, is located between the master cylinder and the wheel brake assemblies. Through an electronic controller, the control valves and other components selectively control pressure to the wheel brake assemblies to provide a desired braking response of the vehicle.
  • a typical solenoid valve includes an armature which reacts to magnetic flux generated by a coil subassembly of the solenoid valve.
  • An armature can be formed as a cylindrical element slidably mounted in a tube or sleeve.
  • Many anti- lock braking systems include both normally open solenoid valves (isolation valves) and normally closed solenoid valves (dump/hold valves). 5 Solenoid control vaTves use lateral magnetic circuits and operate at high frequencies. While lateral magnetic circuits provide the axial output force versus displacement characteristics need for proportional hydraulic control, they usually suffer from significant detrimental lateral forces that can cause undesirable levels of hysteresis and slow performance.
  • a reduction in such hysteresis can improve l o armature performance, and thus provide improved performance of a braking system.
  • Various coatings oflow friction materials have been applied to the outer surface of armatures to reduce hysteresis. However such coatings can be expensive and may be limited in thickness. Furthermore, it is desirable to improve the construction of control valves to reduce costs ⁇ d the time required 5 for assembly.
  • This invention relates to vehicular braking systems and solenoid control valves for such systems.
  • the invention includes a sleeve and armature 20 subassembly for controf valves an ⁇ Ta method for forming the subassembly.
  • a sleeve is fitted on the armature to reduce hysteresis between the armature and a flux tube, also known as a sleeve, which slidably receives the armature.
  • the sleeve can be formed from a relatively thick film (e.g., 0.20 mm) with eccentricity controlled (e.g., +/- 0.0025 on the armature and +/- 0.0050 5 mm on the flux tube) to provide a very desirable armature film thickness/eccentricity ratio.
  • eccentricity controlled e.g., +/- 0.0025 on the armature and +/- 0.0050 5 mm on the flux tube
  • a control valve for a vehicular braking system includes a valve subassembly including an armature slidably received in a flux tube.
  • a solenoid subassembly is mounted on the valve subassembly for inducing a magnetic flux to slide the armature.
  • a sleeve is fitted onto the armature to reduce friction between the armature and the flux tube.
  • the sleeve is formed from a low-friction material.
  • a method is disclosed for forming the armature and sleeve subassembfy.
  • the present control valve has less hysteresis than previous control valves and can improve performance of a vehicular braking system.
  • the flux tube according to this invention can be formed as a three piece subassembfy including a non-ferromagnetic section disposed between two ferromagnetic sections.
  • the present valve subassembly includes a valve body having a cap. A fluid passageway is providedin the valve body and the cap. The cap acts as a valve seat for the armature and/or a valve element to control fluid flow through the control valve.
  • FIG. 1 is a sectional view of a control valve according to the present invention mounted on a hydraulic control unit of a vehicular anti-lock braking system.
  • FTG. 2 is a partly sectionat view illustrating an expanded tubing being slid onto an armature for forming a low-friction sleeve and armature subassembly for use in the control valve of FIG. 1.
  • FIG. 3 is a partly sectional view illustrating chamfered ends of the tubing after it has been slid onto the armature and heated as desired.
  • FIG: 4 is an enlarged, partial view of a sleeve and armature subassembly according to the present invention after jgrinding has reduced the thickness of a cylindrical portion of the sleeve as desired
  • FIG. 5 is a schematic view of one embodiment of a vehicular braking system in which the controf valve of FIG. 1 can be incorporated.
  • FIG. 6 is a sectional view of a second embodiment of the present control valve illustrated as both a normally open isolation valve and a normally closed hold dump valve in a schematically illustrated vehicular braking system.
  • a fluid controt valve according to the present invention is indicated generally at 10 in FIG. 1.
  • the valve 10 which can be a proportional valve, is particularly suited to regutate brake fluid pressure in vehicular braking systems such as an anti-lock braking system (ABS), a traction control braking system (TCS), or an electronic brake management system (EBM) .
  • the valve 10 includes a solenoid subassembly 12 connected or secured to a valve subassembly 14.
  • the solenoid subassembfy I2 ⁇ n cludes a cup-shaped housing or casing 16,
  • the casing 16 is a drawn member having a generally large area and a planar end surface IS.
  • a coil 20, preferably a bobbin-less coil, is placed inside the casing 16. At its outer diameter, the coil 20 can be wrapped with a suitable tape (not illustrated) for protection and retention of a coil lead tower washer (not illustrated).
  • a flux ring 22 is pressed into the casing 16 to secure the coil 20.
  • a pair of winding terminals 24a and 24b extend outwardly through respective openings in the end surface ⁇ S of the casing 16 and are adapted to be connected to an electronic control module (not illustrated) for inducing a magnetic field in a well known manner.
  • the solenoid subassembly 12 is pressed onto a flux tube or sleeve 25 of the valve subassembly 14.
  • the flux tube 25 can be formed as a three-piece subassembly having a first, cup-shaped ferromagnetic section 26, a second, cylindrical non-ferromagnetic section 28, and a third, cylindrical ferromagnetic section 30.
  • the sections 26 " , 28, and 30 can be friction welded together and then machined to a desired finish.
  • the sections 26, 28, and 30 can be oven brazed or laser weldedT together.
  • the sections 26, 28, and 30 may be made as a metal injection molding.
  • a radial flange 31 is formed about a lower portion of the third section 3TJ which extends downwardly beyond the flux ring 22 when the solenoid subassembly 12 is pressed onto the flux tube 25.
  • a cylindrical armature 32 is slidably received within the flux tube 25.
  • the armature 32 can be formed as an iron cylinder.
  • the armature 32 is formed with at least one chamfered end 32a.
  • a non-magnetic sleeve 33 is snugly fitted about at least the axial length of the armature 32.
  • the sleeve 3T is formed from a low-friction material and preferably has a substantially uniform wall thickness.
  • a preferred material for the sleeve 33 is polytetrafluoroethylene, commonly known by the trademark Teflon. Other preferred materials for the sleeve 33 include fluorocarbons.
  • a chamfered ends 33a of the sleeve 3 " may be rounded over an upper end of the armatur 32. In other embodiments, the sleeve 33 can be cut even with the ends of the armature 32 " .
  • the armature 32 and sleeve 33 are formed as a subassembly prior to positioning within the flux tube 25. The sleeve 33 reduces friction between the armature 32 and flux tube 25 and reduces hysteresis of the armature 32.
  • the sleeve 33 established the magnetic gap between the armature 32 and the flux tube 25. This magnetic gap is substantially uniform due to the substantially uniform thickness of the sleeve 33. Also, the sleeve 33 is relatively thick when compared to coatings and a desired sleeve thickness/eccentricity ratio.
  • a recess 34; formed in an outer end of the armature 32 receives a spring 36, illustrated as a coil spring. An opposite end of the spring 36 is received by the cup-shaped first section 26 of the flux tube 25. A hollow cylindrical spacer 3S is used to center the spring 36 within the first section 26. In this constructiorL. spring 36 ⁇ provides a force to bias the armature 32 away form the outer end 18 of the casing 16. When the magnetic field is induced, the armature 32 is urged toward the outer end 18 of the casing 16 and compresses spring 36.
  • the inner surfaces of the sections 26, 28, and 30 of the flux tube 25 are burnished and the outer surface of the armature 32 is ground so that these surfaces are highly concentric to minimize lateral (radial) forces, coulomb friction and hysteresis.
  • the sleeve 33 provides concentricity and resists friction to reduce hysteresis.
  • a drop-in assembly is desired for the spacer 38, spring 36, and armature 32. These elements can be easily slid into the interior volume of the flux tube 25 without any special assembly techniques.
  • valve body 41 is formed from a non-magnetic material so that the valve body 4T is not part of t rermagnetic circuit formed when the coil 20 is energized.
  • the valve body 41 may be formed from plastic, aluminum, or steel, as well as other desired materials.
  • the valve body 41 is a generally cylindrical member having an axial passageway 42.
  • An upper end of the valve body 41 is formed as an outwardly projecting cap 44.
  • an outer surface of the cap 44 terminates in an apex, illustrated in this embodiment as a conical portion.
  • a passageway 46 is formed in the cap 44 concentric with-passageway 42.
  • An outer surface of the cap 44 " acts as a valve seat for a lower end surface of the armature 3Z.
  • a valve element such as a disc or a hall (neither of which is illustrated) can be disposed between the end surface of the armature 32 and the cap 44 to assist in blocking fluidTfl w.
  • At least one ⁇ uid passageway 47 is formed in the valve body 4T radially outwardly from passageway 42.
  • A_radial flange 43T is formed about an outer surface of the valve body 41.
  • a reduced diameter portion 50 is formed in a lower portion of the valve body 41.
  • the valve body 41 is received in a stepped opening or. bore 104 forme in a hydraulic control unit (HCTJ) 102 of a vehicular braking system.
  • the bore 104 includes a first step or shoulder 106 which receives a lower surface of the flange 48:
  • An inner reduced diameter portion 108 of the bore 104 receives the reduced diameter portion 50 of the valve body 41.
  • a seal 52 received in an annular groove 54 " formedin an outer surface of the lower portion 50-of the valve body 41 provides a fluid seat between the valve body 41 and the HCU 102.
  • a seal 56 is trapped between the flange 3T of the flux tube 25 andThe radial flange 48 of the valve body 41 to provide a fluid seal.
  • valve 10 is significantly smaller than other known proportional solenoid valves.
  • valve 10 can be constructed with a 24 " mm diameter and a length of 52mm.
  • Valve W is easier to assembly, more resistant to contamination, and uses less current than other known proportional control valves.
  • valve Ifruses only Q.35 amp during periods of pressure change..
  • various components are stacked together andthen retained on the HC 102 by a single orbital swaging operation.
  • the spring 36; spacer 38, and armature 32 are inserted intoihe flux tube 25.
  • the valve body 41 with seal 52 " is pressed into place (preferabry- ⁇ vith a low force) into the bore 104.
  • Seal 56 is trapped between the flux tube-25 andlhe. valve body 41.
  • An annular tip 99 is formed from material surrounding the bore 104.
  • the Gp 9 can be formed by any desired metal-forming technique, including orbital swaging.
  • the lip 99 ⁇ f ⁇ r ⁇ ed by a single process retains the valve 10 on the HCU I02 ⁇ andholds the components of the valve 10 together, all in one operation.
  • valve 10 controls fluid flow with a poppet seat provided by cap 44 and disc 4TX Such a poppet seat is highly resistant to contamination and is highly resistant to leakage.
  • the sofenoid valve sensitivity (i.e, valve flow opening/[pressure demand- pressure output]) " of valve 10 is controlled by the spring rate oFspring J6 and not by the magnetic circuit spring rate since the preferred magnetic spring rate is zero (flat). If valve sensitivity needs to be changed for larger brake systems, then merely a spring 36 " different spring rate need be changed.
  • a pair of valves 10 can-be used to control braking at a wheel.
  • One valve 10 can be configured as a normally closed valve as fltustrated in FIG I, and one valve can be configured & a no ⁇ nally open valve as discusse Delow.
  • one valve 10 can be used to control pressure apply while a second valve 10 can be used to control pressure release. Only one valve.10 is energized . at a time and only during peak periods of pressure change. On long downhill grades with long periods of unchanged brake pressure holding, the valve 10 will draw no.
  • valve 10 triereby greatly reducing solenoid__yalve heat dissipation.
  • the magnetic forces of valve 10 tend to be close to a linear function of current, rather than a function of current squared, as is the case with many magnetic circuits.
  • This aspect of valve 10 which results from the configuration and sizing of the armature 32 andflux tube 25 and associated primary air gap, produces a valve whose output sensitivily-to input control currents is substantially uniform (at both high and low brake fluid pressures), thus making pressure control proportional to current.
  • FIGS. 2-4 A preferred method for forming the subassembly compri ing the sleeve 33 and the armature 32 is illustrated in FIGS. 2-4 as successive steps.
  • the method involves the use of a toot 200 having a downwardly projecting annular step 202 and a passageway 204 preferably aligned with an axis of the step 202.
  • the tool 200 can be positioned as desired with respect to an armature 32.
  • Shrink tubing 206 formed from a flexible, low-friction material is used with the tool 200.
  • the armature 32 is provided A predetermined length of tubing 206 is provided and mounted about the step 202 Pressurized air travels through the passageway 204 to expand the predeterminedlength of tubing 206.
  • the inner diameter of the tubing 206 is preferably less than the outer diameter of the armature 327
  • pressurized air increases column strength of the tubing 206 to prevent buckling or collapsing' as the armature 32 is slid into the tubing 206.
  • the tool 200 with the tubing 206 is moved downwardly toward the armature 32 SO that the tubing 206 slides Over thtTr.ter f p irefi end 7a nf the armature 32 as illustrated in FIG. 2.
  • the chamfered end 32a leads the tubing 206 onto the armature 32 and provides an initial pressure seal with the tubing 206.
  • the pressurized air expands the length anddiameter of thE> tubing 206 for easier installation onto the armature 32 " and results " in residual hoop stress to retain the
  • the tubing 206 is heated to form the subassembly of the armature 32 and sleeve 33. As illustrated in FIG. ., heat allows additional conforming of the tubing 206 to the armature 32 " and causes the ends 206a to round-over around the ends of the armature, resulting in the chamfered ends 33a of the sleeve 33. Ends 206a relieves and bending stress at the end corners which could otherwise cause the cylindrical portion of the sleeve 33 to separate from the armature 32.
  • the armature 32 and tubing 206 can undergo a grinding process to accurately set the subassembly diameter. For example, the grinding step can be accomplished by a centerless grinding operation using ⁇ grinding wheel and a follow wheel.
  • the centertess grinding operation accurately reduces the thickness of the cylindrical portion of the tubing 206as compared to the thickness of the ends 206a
  • a cutting process removes portion of the tubing 206 from an end of the armature 32 which engages the valve body 41, as illustrated in FIG. 4.- Once the proper diameter has been set and the endportion removed, the armature 32 and sleeve 33 subassembly can be used with control valve 10 as illustrated in FIG. 1.
  • Tubing 206 formed from polytetrafluoroethylene has been successfully used Centertess grinding has resultedin accurate armature core diameter (+/- 0.0025 mm), accurate armature-sleeve subassembly diameter-(+/- 0.0025 mm), and an accurate thickness, low-friction sleeve 33 that is well attached to the armature 32.
  • 0.20 mm low-friction tubing 206 in this method and +/- 0.0025mm eccentricity on the armature 32and+A- 0.0050 eccentricity on the flux tube 25, desirable results have been obtained.
  • a control valve 10 with the present armature 32 and sleeve 33 produces a low hysteresis versus proportional output by having a gh ratio of armature non-magnetic gap-thickness, versus armature positional eccentricity.
  • a vehicular braking system indicated generally at 300 in FIG. 5 represents one example of a braking system which can incorporate trie-control valve 10 with its armature 32 ⁇ and sleeve 33 presented above.
  • a brake pedal 310 is connectedto a master cylinder 312 to provide pressurized brake fluid to a wheel brake 314.
  • the wheel brake 314 is illustrated as a disc assembly; however, the wheel brake 314 may be any type found on vehicles.
  • a hydraulic control unit (HCU) 302 is a housing for valves and other components as described below. For purposes ofcrarity of illustration, only one set of components are illustrated in FIG. 5 Typically, however, the HCU 302 also houses corresponding components for other wheels of the vehicle.
  • the HCU 302 " inctudes a normally open isolation_vabte 316 disposed between the master cylinder 3T2 and the wheef brake 314, at least one low pressure accumulator 318, a normally closed hold/dump valve 320 disposed between the wheel brake 314 and the low pressure accumulator 318, and a hydraulic pump 322 connectedbeiween the low pressure accumulator 318 and an inlet to the isolation valve 316.
  • the HCU 302 may als include.an attenuator 324 between an output of the pump 322 and the inlet to the isolation valve 316 to limit and smooth fluid flow from the pump 322 ⁇ back to the master cylinder 312.
  • Various fluid passageways are provided in the HCU 302 to. connect the various components.
  • the isolation valve 3T6 and the hold/dump vatver320 are control valves preferably formed as electrically actuatedsolenoid valves-
  • the isolation valve 316 is preferably formed as a two position, solenoid valve having a normally open configuration.
  • the hold/dump valve 320 is preferably formed as a two position, solenoid valve having a normally closed configuration.
  • the valves 316 and 320 are switched by an electronic control module (not illustrated) to provide anti-lock braking in a. well known manner
  • control valve 10 is a solenoid valve having a normally closed configuration.
  • Control valve l ⁇ an he substituted for hoId dump valve 320to perform in system 300.
  • the low hysteresis provided by control valve 10 results in better performance of system 300.
  • the pressure output of control valve 10 is a function of current to the valve 10 times the input pressure to the valve 10. By varying the current and knowing the input pressure, the output pressure can be controlled
  • a control valve 10 ⁇ according_to this invention incorporating the above-described armature 32 and sleeve 33 can be configured as a normally open solenoid valve.
  • a second vehicular braking system is indicated generally at 400 and illustrated inFIG. 6.
  • system 400 includes a normally open isolation valve 422 incorporating an armature and sleeve as described above.
  • a brake pedal 412 is connectedtoa master cylinder 414.
  • a fluid conduit 416 is connected between the master cylinder 414 and an inlet port 418 " formed in a hydraulic control unit (HCU) 420.
  • HCU hydraulic control unit
  • the.HCU 420 is a housing formed from a suitable lightweight material which includes bores for receiving various components and internal conduits connecting such components.
  • a first solenoid valve 422 function as an isolation and proportional reapply valve as describedhelow.
  • Tsotation valve 422 includes a valve body 424 received in a first bore 426 of the HCU 420.
  • the valve body 424 has a radial flange 428, a first internal channel 430 and a second internal channel 432.
  • an annual lip 434 is formed by swaging material of the HCU 420 adjacent the bore 426 to retain the valve body 424 on the HCU 420.
  • the second channel 432 is aligned with an outlet port 436 formed in the HCU 420.
  • the outlet port 436 is in fluid communication with a fluid conduit 437.
  • a seaL43 is received in a groove formed in an outer surface of the valve body 424 to provide a seal between the inlet port 418 and the outlet port 436.
  • the isolation valve 422 also includes a coil assembly 440.
  • the coil assembly 440 is inserted onto the valve body 424 and can be retained by a cover assembly or an electronic control module assembly (neither of which is illustrated) or the like, which is pushed downwardly onto the coil assembly 440.
  • a cup-shaped housing or casing 442T provides a flux return path.
  • a coil 444 preferably an epoxy bound bobbin-tess coil, is placed around-a.fl.ux tube 446.
  • a flux ring 44% is pressed into the casing 442 to secure the coil 418 and complete the flux return path.
  • the flux ring 422 is machined to minimize air gaps between the casing 442 and the flux tube 446.
  • a pair of winding terminals 450A and 450B " extend outwardly through respective openings in the casing 442 and are adapted to be connected to an electronic control module (not illustrated) for inducing a magnetic field through the flux tube 446 in a well known manner.
  • the flux tube 446 is formed as a three-piece cylindrical member having a first, cup-shaped ferromagnetic section 452, a second ⁇ cylindrical non-ferromagnetic section 454, and a third, cylindrical ferromagnetic section 4515.
  • the magnetic field passes through the first and third sections 452 and 456, and not the second section 454.
  • a cylindrical armature 451T is slidably received within the flux tube 446.
  • a spring 460 is seated at one end on a spring seat 462 formed on the lower end of the armature 458.
  • the spring 460 is seated at its opposite end on a spring seat 464 formed on an upper end of the valve body 424.
  • the solenoid valve 422 is normally open as the spring 460 urges the armature 458 away from the valve body 424 with a tow spring force.
  • the coil 444 is energized, the armature 458 is urged downwardly against the spring 460 by magnetic forces until spring seat 462 contacts spring.seat 464 to close the isolation valve 422.
  • the magnetic force works against the pressure differential across a valve seat formed by the spring seats 462 and 464.
  • the flux tube 446 is roll burnished and the outer diameter of the armature 4584s ground to provide very precise positional concentricity of the armature 458, thereby minimizing lateral forces.
  • a low-friction sleeve 465 fitted on the armature 458 ⁇ (like sleeve 33 " on armature 32) will provide low friction between the armature 458 and the flux tube 446 and minimize hysteresis.
  • the magnetic configuration of the isolation valve 422 provides a lateral working air gap in which the magnetic permeance is a linear function of axial travel
  • the axial magnetic force is proportional to current and independent of the travel oTthe armature 458 in its operating range
  • proportional control oFthe isolation valve 422 is stable and controlled.
  • a second solenoid valve 466 functions as a prorwrtionaLdump valvcas described below.
  • Dump valve 466 is a normally closed valve having a valve body 468 and a coil assembly 470.
  • the valve body 46% is preferably retained in a bore 472 in the HCU 420 by an annular swaged lip 474.
  • a first channel 476 is in fluid communication with an inlet port 478 formed in the HCU 420.
  • a second channel 480 is in fluid communication with an outlet port 482 formed in the HCU 420.
  • Outlet port 482 is in fluid communication with an inlet line 484 of a hydraulic pump 486.
  • the coil assembly 470 includes a casing 488, a coiL490, a flux tube 492, and an armature 494 stidably received inside the flu tube 492.
  • the flux tube 492 is formed as a three-piece cylindrical member having a first, cup- shaped ferromagnetic section 496, a second, cylindrical non-ferromagnetic section 498, and a third, cylindrical ferromagnetic section 500.
  • the magnetic field passes through the first and third sections 496 and 500, and not the second section 498.
  • a low-friction sjeeve 501 is fitted on the armature 494 (like sleeve 33 on armature 32) to provide low friction between the armature 494 and the flux tube 492 and minimize hysteresis.
  • a spring 502 is received in a cavity 504 formed in an upper portion of the armature 494 and urges the armature downwardly so that a lower surface 506 of the armature 494 contacts a valve seat 50% formed on an upper surface of the valve body 468.
  • the pump 486 outlet is connected to conduit 416-and delivers fluid to inlet port 418:
  • a check valve 510 permits only one-way fluid flow from conduit 43Tto conduit 416.
  • a pressure transducer 512 reduces the effects of varied pressure from the master cylinder 414 during certain modes of the system 400 as described below.
  • both solenoid valves 422 and 466 are not energized and the pump 486 is not operated.
  • Increased fluid pressure travels- through inlet port 418 and channel 430, past spaced-apart spring seats 464 and 462 to channel 432 and outlet port 436 to conduit 437 Pressurized fluid reaches a wheel brake 514, illustrated as a cafiper, to cause braking of a wheel rotor 516.
  • the pump 486 is operated and the solenoid valves 422 and 466 are energized
  • the isolation solenoid valve 422 By energizing the isolation solenoid valve 422, the armature 458 ⁇ slides downwardly to engage the valve body 424 and block fluid flow from the master cylinder 414 to the wheel brake 5T4.
  • the dump solenoid valve 466 is opened as the a ⁇ nature 494 is putted upwardly away from the valve body 468 so that fluid pressure is relieved from the wheel brake 514 through inlet port 478, outlet port 482 and conduit 484.
  • the dump valve 466 is de-energized and the voltage to the isolation valve 422 is reduced to a predetermined stored vatue plus a second value which is a function of the master cylinder 414 pressure. This causes the isolation valve 422 to quickly reapply a pressure to the brakes that is a function of the stored voltage.
  • the stored voltages are retained in the electronic control module (not illustrated). Afterwards, current to the isolation valve 422 is decreased at a controlled rate which is also a function of master cylinder 414 pressure, ihereby causing brake pressure to increase at a relatively stow rate after a proportional quick reapply of the isolation valve 422.
  • the isolation valve 422 current is decreased at a faster rate, thereby providing a faster brake pressure reapply for this portion of the anti-lock braking cycle.
  • the voltage of the isolation valve 422 is first stored Next, the isolation valve 422is fully energized and the dump valve 466 is energized The stored voltage indicates the pressure needed to lockup a when under the conditions of the previous cycle and is used to control the next reapply cycle.
  • a proportion of the stored voltage is quickly applied to the isolation valve 422, fottowedby a slowly decreasing voltage.
  • a fast proportional reapply is followed by a slow reapply as described above.
  • Similar togic can be used for proportional dump control.
  • a quick increase in dump valve 466 current can be fottowe by a slower increase until the vehicle wheels start spinning up again. If ⁇ he wheels do not start spinning up after a desired interval (e.g., approximately 0.20 seconds), the dump current rate can be increased. The value of the current at which the wheels start to spin up is stored and used on the next dump cycle, thus providing proportional pressure dump.
  • the isolation valve 422 provides a reapply pressure that is an inverted function of current and is based on master cylinder pressure.
  • the pressure transducer 5T2 is beneficia ⁇ aLin providing input to adjust control current to diminish effects of varied master cylinder pressure on reapply pressures to the wheel brake 514.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Electromagnetism (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une soupape de commande (10), conçue pour le système de freinage d'un véhicule, comprenant un sous-ensemble soupape (14), pourvu d'une armature (32) logée coulissante dans un tube à écoulement de flux (25). Un sous-ensemble solénoïde (12) est monté sur ledit sous-ensemble soupape (14), afin d'amener un flux magnétique à glisser le long de ladite armature (32). Un manchon (33, 206, 465, 501) est ajusté sur cette armature (32), afin de diminuer le frottement entre ladite armature (32) et ledit tube à écoulement de flux (25). Ce manchon (33, 206, 465, 501) est fabriqué dans un matériau de faible frottement. L'invention concerne également un procédé de fabrication du sous-ensemble armature (32) et manchon (32, 206, 465, 501). La soupape de commande (10) de la présente invention présente une hystérèse inférieure à celle des soupapes de commande traditionnelles, et permet d'améliorer les performances du système de freinage d'un véhicule.
PCT/US1998/004824 1997-03-11 1998-03-11 Sous-ensemble armature et manchon pour soupapes de commande du systeme de freinage d'un vehicule, et leur procede de fabrication WO1998040260A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP98910326A EP0966379A1 (fr) 1997-03-11 1998-03-11 Sous-ensemble armature et manchon pour soupapes de commande du systeme de freinage d'un vehicule, et leur procede de fabrication
AU64591/98A AU6459198A (en) 1997-03-11 1998-03-11 Sleeve and armature subassembly for control valves of vehicular braking systems and method of forming

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US4016797P 1997-03-11 1997-03-11
US60/040,167 1997-03-11
US95414197A 1997-10-20 1997-10-20
US08/954,141 1997-10-20

Publications (1)

Publication Number Publication Date
WO1998040260A1 true WO1998040260A1 (fr) 1998-09-17

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Family Applications (1)

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PCT/US1998/004824 WO1998040260A1 (fr) 1997-03-11 1998-03-11 Sous-ensemble armature et manchon pour soupapes de commande du systeme de freinage d'un vehicule, et leur procede de fabrication

Country Status (3)

Country Link
EP (1) EP0966379A1 (fr)
AU (1) AU6459198A (fr)
WO (1) WO1998040260A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000070628A1 (fr) * 1999-05-14 2000-11-23 Continental Teves Ag & Co. Ohg Electro-aimant
EP1118518A2 (fr) * 1999-12-29 2001-07-25 Kelsey Hayes Company Soupape hydraulique à solénoide pour unité de commande hydraulique
EP1216904A1 (fr) * 2000-12-19 2002-06-26 CLAAS Industrietechnik GmbH Dispositif connecteur et solénoide
EP1065116A3 (fr) * 1999-06-30 2003-04-16 Kelsey Hayes Company Armature de valve d'isolement configurée pour réduire les forces de Bernoulli pendant des freinages normaux
WO2003072954A1 (fr) * 2002-02-22 2003-09-04 Robert Bosch Gmbh Procede de production d'un tube sous pression d'un electro-aimant de levage et tube sous pression d'un electro-aimant de levage
WO2004014592A1 (fr) * 2002-08-02 2004-02-19 Eto Magnetic Kg Dispositif de commande electromagnetique
WO2004044467A1 (fr) * 2002-11-12 2004-05-27 Ina Schaeffler Kg Electrovanne hydraulique, notamment distributeur 3/2, pour la commande d'une distribution variable d'un moteur a combustion interne
WO2007045375A1 (fr) * 2005-10-18 2007-04-26 Thomas Magnete Gmbh Electroaimant
WO2011018087A1 (fr) * 2009-08-13 2011-02-17 Danfoss A/S Procédé de fabrication d'une soupape
WO2013020749A1 (fr) * 2011-08-10 2013-02-14 Schaeffler Technologies AG & Co. KG Dispositif d'étanchéité pour une soupape relais d'une unité hydraulique
JP2017009004A (ja) * 2015-06-18 2017-01-12 株式会社デンソー 弁装置
CN109185256A (zh) * 2018-11-22 2019-01-11 李军 一种球阀

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CH309663A (de) * 1952-03-10 1955-09-15 Herion Erich Magnetventil.
DE2052307A1 (de) * 1970-10-24 1972-05-25 Teves Gmbh Alfred Elektromagnetisch betätigtes Sitzventil
DE2236586A1 (de) * 1972-07-26 1974-02-07 Dungs Karl Fa Konstruktion und verfahren zur herstellung einer einteiligen magnetschlusshuelse zur betaetigung von elektromagneten, insbesondere zur anwendung bei magnetventilen
US3817491A (en) * 1971-05-14 1974-06-18 Daimler Benz Ag Rapidly shifting, leak-proof electromagnetically actuated discharge valve
US3829060A (en) * 1972-02-22 1974-08-13 Bosch Gmbh Robert Magnet valve
US3989063A (en) * 1974-01-26 1976-11-02 Robert Bosch G.M.B.H. Electromagnetic 3-way valve
US4004343A (en) * 1974-04-18 1977-01-25 Expert Industrial Controls Limited Method of making core tubes for solenoids
US4553735A (en) * 1982-01-13 1985-11-19 Brundage Robert W Solenoid controlled valve
DE3502730A1 (de) * 1985-01-28 1986-07-31 Rausch & Pausch, 8672 Selb Magnetventil
US4714234A (en) * 1982-09-07 1987-12-22 Greatbatch Enterprises, Inc. Low power electromagnetic valve
US4785848A (en) * 1986-10-09 1988-11-22 Daimler-Benz Aktiengesellschaft Electromagnetic directional control valve assembly
US4828335A (en) * 1985-08-09 1989-05-09 Kelsey-Hayes Company Control valve for vehicle anti-lock brake system
US4896860A (en) * 1989-05-08 1990-01-30 Eaton Corporation Electrically operated refrigerant valve
EP0559067A1 (fr) * 1992-03-06 1993-09-08 Sumitomo Electric Industries, Limited Soupape à solénoide
DE4431457A1 (de) * 1994-09-03 1996-03-07 Bosch Gmbh Robert Elektromagnetisch betätigbares Druckregelventil

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH309663A (de) * 1952-03-10 1955-09-15 Herion Erich Magnetventil.
DE2052307A1 (de) * 1970-10-24 1972-05-25 Teves Gmbh Alfred Elektromagnetisch betätigtes Sitzventil
US3817491A (en) * 1971-05-14 1974-06-18 Daimler Benz Ag Rapidly shifting, leak-proof electromagnetically actuated discharge valve
US3829060A (en) * 1972-02-22 1974-08-13 Bosch Gmbh Robert Magnet valve
DE2236586A1 (de) * 1972-07-26 1974-02-07 Dungs Karl Fa Konstruktion und verfahren zur herstellung einer einteiligen magnetschlusshuelse zur betaetigung von elektromagneten, insbesondere zur anwendung bei magnetventilen
US3989063A (en) * 1974-01-26 1976-11-02 Robert Bosch G.M.B.H. Electromagnetic 3-way valve
US4004343A (en) * 1974-04-18 1977-01-25 Expert Industrial Controls Limited Method of making core tubes for solenoids
US4553735A (en) * 1982-01-13 1985-11-19 Brundage Robert W Solenoid controlled valve
US4714234A (en) * 1982-09-07 1987-12-22 Greatbatch Enterprises, Inc. Low power electromagnetic valve
DE3502730A1 (de) * 1985-01-28 1986-07-31 Rausch & Pausch, 8672 Selb Magnetventil
US4828335A (en) * 1985-08-09 1989-05-09 Kelsey-Hayes Company Control valve for vehicle anti-lock brake system
US4785848A (en) * 1986-10-09 1988-11-22 Daimler-Benz Aktiengesellschaft Electromagnetic directional control valve assembly
US4896860A (en) * 1989-05-08 1990-01-30 Eaton Corporation Electrically operated refrigerant valve
EP0559067A1 (fr) * 1992-03-06 1993-09-08 Sumitomo Electric Industries, Limited Soupape à solénoide
DE4431457A1 (de) * 1994-09-03 1996-03-07 Bosch Gmbh Robert Elektromagnetisch betätigbares Druckregelventil

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000070628A1 (fr) * 1999-05-14 2000-11-23 Continental Teves Ag & Co. Ohg Electro-aimant
EP1065116A3 (fr) * 1999-06-30 2003-04-16 Kelsey Hayes Company Armature de valve d'isolement configurée pour réduire les forces de Bernoulli pendant des freinages normaux
EP1118518A2 (fr) * 1999-12-29 2001-07-25 Kelsey Hayes Company Soupape hydraulique à solénoide pour unité de commande hydraulique
EP1118518A3 (fr) * 1999-12-29 2002-12-04 Kelsey Hayes Company Soupape hydraulique à solénoide pour unité de commande hydraulique
EP1216904A1 (fr) * 2000-12-19 2002-06-26 CLAAS Industrietechnik GmbH Dispositif connecteur et solénoide
WO2003072954A1 (fr) * 2002-02-22 2003-09-04 Robert Bosch Gmbh Procede de production d'un tube sous pression d'un electro-aimant de levage et tube sous pression d'un electro-aimant de levage
US7266883B2 (en) 2002-02-22 2007-09-11 Bosch Rexroth Ag Methods for the production of a pressure pipe of an electric hoisting magnet and pressure pipe of a hoisting magnet
WO2004014592A1 (fr) * 2002-08-02 2004-02-19 Eto Magnetic Kg Dispositif de commande electromagnetique
US7021256B2 (en) 2002-11-12 2006-04-04 Ina Schaeffler Kg Electromagnetic hydraulic valve, particularly 3/2-way pilot valve for controlling a variable valve drive of an internal combustion engine
WO2004044467A1 (fr) * 2002-11-12 2004-05-27 Ina Schaeffler Kg Electrovanne hydraulique, notamment distributeur 3/2, pour la commande d'une distribution variable d'un moteur a combustion interne
KR101009801B1 (ko) * 2002-11-12 2011-01-19 쉐플러 카게 내연기관의 가변형 밸브 구동 장치 제어를 위한 전자기 유압 밸브, 특히 3/2-방향 제어 밸브
WO2007045375A1 (fr) * 2005-10-18 2007-04-26 Thomas Magnete Gmbh Electroaimant
WO2011018087A1 (fr) * 2009-08-13 2011-02-17 Danfoss A/S Procédé de fabrication d'une soupape
CN102483175A (zh) * 2009-08-13 2012-05-30 丹佛斯公司 阀的制造方法
RU2499938C1 (ru) * 2009-08-13 2013-11-27 Данфосс А/С Способ изготовления клапана
WO2013020749A1 (fr) * 2011-08-10 2013-02-14 Schaeffler Technologies AG & Co. KG Dispositif d'étanchéité pour une soupape relais d'une unité hydraulique
JP2017009004A (ja) * 2015-06-18 2017-01-12 株式会社デンソー 弁装置
CN109185256A (zh) * 2018-11-22 2019-01-11 李军 一种球阀
CN109185256B (zh) * 2018-11-22 2020-04-28 亚太泵阀有限公司 一种球阀

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Publication number Publication date
EP0966379A1 (fr) 1999-12-29
AU6459198A (en) 1998-09-29

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