US3729014A - Flow divider - Google Patents

Flow divider Download PDF

Info

Publication number
US3729014A
US3729014A US3729014DA US3729014A US 3729014 A US3729014 A US 3729014A US 3729014D A US3729014D A US 3729014DA US 3729014 A US3729014 A US 3729014A
Authority
US
United States
Prior art keywords
chambers
sub
pressure
diaphragm
flow
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.)
Expired - Lifetime
Application number
Other languages
English (en)
Inventor
T Narumi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyoda Koki KK
Original Assignee
Toyoda Koki KK
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 Toyoda Koki KK filed Critical Toyoda Koki KK
Application granted granted Critical
Publication of US3729014A publication Critical patent/US3729014A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/101—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic equalising arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2514—Self-proportioning flow systems
    • Y10T137/2521—Flow comparison or differential response
    • Y10T137/2524—Flow dividers [e.g., reversely acting controls]
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/265—Plural outflows
    • Y10T137/2652—Single actuator operates plural outlets simultaneously

Definitions

  • a low divider has an inlet port, a pair of outlet ports, [58] Field of Search ..l37/98, I00, 101, and a control chamber therein.
  • the control chamber 1 108 is separated by a diaphragm into a pair of sub-chambers.
  • Restriction orifices are provided between the References Cited inlet port and the pair of sub-chambers and valve seat members are provided between the pair of sub-cham- UNITED STATES PATENTS bers and the outlet ports and have throttling effects 2,283,266 5/1942 Kinsella ..l37/ 101 between the valve seat members and the diaphragm.
  • a conventional flow divider has structure for controlling the amount of distributed flow by means of a spool which slides, in response to differential pressure, within a cylinder formed in the flow divider casing.
  • Such a structure is costly, because high precision is needed in making said spool in order to prevent leakage of the pressure fluid into a passage perforated in the cylinder or spool.
  • the spool responds at slow speed when a differential pressure develops within the cylinder. Therefore, it has been impossible to perform an accurate control function with conventional flow dividers.
  • This invention relates to flow dividers which are capable of eliminating such defects and providing an accurate and highly sensitive control for a long period of time through the employment of a diaphragm.
  • FIG. 1 is a cross-sectional view of an embodiment of this invention.
  • FIG. 2 is a cross-sectional view of another embodiment of this invention.
  • FIG. 1 there is shown a flow divider casing 1 having a cylindrical bore 1a therein.
  • Disc members 4 and 6 are retained within the bore la by a snap ring 2 and a circular closure member 3 which is threaded into the casing l.
  • Sealing rings and 16 are provided in peripheral grooves in the disc members 4 and 6.
  • Disc members 4 and 6 have complementary recesses 4a and 6a in their opposing surfaces.
  • a flexible diaphragm 5 is gripped at its peripheral edge between Moreover, in the flow divider casing 1, there is pro-- vided an axial passage 8 connected to the port 7 and 0 having branch passages 9 and 10 which communicate with the outer periphery of the disc members 4 and 6, respectively.
  • annular grooves 11 and 12 On the outer periphery of the disc members 4 and 6 are formed annular grooves 11 and 12 connected with the branch passages 9 and 10, respectively. Radial passages 13 and 14 extend between and communicate with the chambers 25 and 26 and the annular grooves 11 and 12, respectively. Restriction orifices l7 and 18 having a suitable throttling effect are fitted in the passages 13 and 14 at the locations where they open into the chambers 25 and 26.
  • Axially extending outlet ports 19 and 20 are provided in projections 4c and 60 formed at the approximately central parts of the disc members 4 and 6.
  • the pressure fluid which is supplied into the chambers 25 and '26 from the intake port 7 through the passages 8, 13, and 14 and orifices 17 and 18, flows out through the outlet ports 19 and 20.
  • These outlet ports 19 and 20 communicate with passages 21 and 22 formed in the projecting parts 4b and 6b at the center of the recesses 4a and 6a of the disc members 4 and 6, respectively.
  • Valve seat members 23 and 24 having suitable throttling effects are fitted between the passages 21 and 22 and the chambers 25 and 26.
  • the diaphragm 5 is formed of an elastic material such as rubber and thin steel sheets 5a and 5b are attached to both sides of its central portion for preventing deformation thereof.
  • the diaphragm 5 is located between the orifices 17 and 18 and valve seat members 23 and 24, respectively. Therefore, the diaphragm 5, being maintained in a stabilized state, may be moved in a substantially axial direction in response to a change of the relative load pressures developed at the outlet ports 19 and 20 to control the clearances between the diaphragm 5 and the valve seat members 23 and 24 in such a manner as to maintain equal the pressure in the chambers 25 and 26, thereby distributing equally the pressure fluid supplied from the intake port 7 to the outlet ports 19 and 20.
  • the members of the pair of orifices 17 and 18 and, also, the pair of valve seat members 23 and 24, are formed of the same construction, respectively, and are located symmetrically with respect to the diaphragm 5, and the members of each pair have throttling effects of equal ratio. Therefore, the pressure fluid supplied from the fluid pressure source is divided in the same fluid flow ratio.
  • the pressure fluid supplied from the fluid pressure source, not shown, into the flow divider assembly through the intake port 7 passes through the passage 8 to the branch passages 9 and 10.
  • the pressure fluid divided by the branch passages 9 and 10 flows into the passages 13 and 14 by way of the annular grooves 11 and 12.
  • the divided fluid whose pressure is decreased as it passes through-the orifices 17 and 18, flows into the chambers 25 and 26 and thence into the passages 21 and 22 through the clearances between the diaphragm 5 and the valve seat members 23 and 24, respectively, and then the pressure fluid is discharged from the flow divider assembly through the outlet ports 19 and 20.
  • These outlet ports 19 and may be connected with a power steering mechanism and a power brake mechanism, in the case of automobiles, for example.
  • the pressure within the chamber 26 is increased.
  • the pressure in the valve seat member 23 is higher than that in the valve seat member 24, as the diameter of the diaphragm 5 is sufficiently larger than those of the valve seat members 23 and 24, the diaphragm 5 is pressed back leftwardly so as to decrease the pressure in the chamber 26.
  • the diaphragm 5 is brought to a halt at an equilibrium position where the pressure in the chamber 26 is almost equal to that in the chamber 25. Therefore, the pressure drops across nozzles 17 and 18 are almost equal, and, accordingly, almost the same quantity of pressure fluid is discharged from the outlet ports 19 and 20 on the right and left hand of the flow divider assembly.
  • the fluid flow supplied from the fluid pressure source is divided into two branches having the same fluid flow.
  • the fluid flow may be divided in any desired ratio by changing the dimensions of the orifices 17 and 18.
  • H6. 2 illustrates another embodiment of a flow divider which, though based on the same principle, is so designed as to compensate for the distribution error of the main control chamber by means of a sub-control chamber provided in front of the main control chamber.
  • the cross-sectional areas of the orifices and valve seat members of this apparatus vary from right to left respectively, so that the amount of fluid flow may be proportioned at such a ratio as 4 to 1, for example.
  • a disc member 104 having a recess 104a, a flexible auxiliary diaphragm 105 held on both sides of its peripheral edge by spacers 127 and 128, a disc member 106 having recesses 106a and 106b on opposite sides, a flexible main diaphragm 107 held on both sides of its peripheral edge by spacers 129 and 130, and a disc member 108 having a recess 108a, these parts being arranged in the stated order from the side of the snap ring 102.
  • Sealing rings 115, 116 and 117 are provided in peripheral grooves in the disc members 104, 106 and 108, respectively.
  • the recesses 104a and 1060 define an auxiliary control chamber 143 which is separated by the auxiliary diaphragm 105 into sub-chambers 131 and 132.
  • the recesses 106b and 10811 define a main control chamber 142 which is separated by the main diaphragm 107 into sub-chambers 140 and 141.
  • the main and auxiliary diaphragms 107 and 105 are made of resilient materials, such as plastic or metal sheets.
  • the flow divider casing 101 is provided with an intake port 109 and an outlet port 110, which communicate with annular grooves 111 and l 12 formed on the outer periphery of the disc member 106. From these annular grooves 111 and 112 extend radial passages 113 and 114 which communicate with the chambers 132 and 140. A restriction orifice 118 and a valve seat member 119 having suitable throttling effects are fitted in the passages 113 and 114, respectively, at the positions where they open into the chambers 132 and 140. Furthermore, below the orifice 118 there is provided an axial passage 120 connecting the chambers 132 and 140.
  • an axial inlet port 121 and an axial outlet port 124 are provided at the approximate centers of the projections 104c and 108a formed on the outer sides of the disc members 104 and 108.
  • the ports 121 and 124 communicate through passages 122 and 125 with chambers 131 and 141.
  • a restriction orifice 123 and a valve seat member 126 are fitted in the passages 122 and 125 for cooperation with the auxiliary diaphragm 105 and main diaphragm 107 respectively.
  • annular grooves 133 and 135 which communicate with the chambers 131 and 141 through passages 134 and 136 respectively.
  • the flow divider casing 101 is perforated with branch passages 137 and 138 which communicate with the annular grooves 133 and 135, and with each other by means of a passage 139 also formed in the casing 101.
  • the crosssectional areas of the orifices 123 and 118 and valve seat members 119 and 126 are respectively so proportioned as to divide the amount of pressure fluid to be discharged out of the outlet ports 110 and 124 in a predetermined ratio, and therefore the pressure fluid discharged out of the flow divider assembly from the outlets 110 and 124 are divided in a ratio of, for example, 4 to 1.
  • the pressure fluid supplied from the fluid pressure source flows into the flow divider assembly through the intake ports 109 and 121.
  • the pressure fluid coming in from the intake port 109 flows into the passage 113 by way of the annular groove 111, and then into the chamber 132 through the orifice 118.
  • the fluid, whose pressure is decreased, flows through the clearance between the orifice 118 and the auxiliary diaphragm 105, and thence into the chamber 140, by way of the passage 120.
  • the fluid whose pressure is further decreased, flows through the clearance between the valve seat member 119 and the main diaphragm 107, thence to the outlet port 110, by way of the valve seat member 119, passage 114 and annular groove 112, from whence it is discharged out of the flow divider assembly into load means.
  • the pressure fluid flowing from the intake port 121 into the flow divider assembly passes through the passage 122, to decrease the pressure thereof, thence through the clearance between the orifice 123 and the auxiliary diaphragm 105 into the chamber 131.
  • the fluid flows into the branch passage 137 through the passage 134 and annular groove 133, and then it flows into the chamber 141 by way of the passage 139, branch passage 138, annular groove 135 and passage 136.
  • the fluid whose pressure is further decreased, flows through the clearance between the valve seat member 126 and the main diaphragm 107, and reaches the outlet port 124 by way of the passage 125, from which the fluid is discharged out of the flow divider assembly into load means.
  • the pressure fluid discharged out of the outlet ports 1 and 124 are proportioned in a predetermined ratio, such as 4 to 1, for example, in accordance with the ratio of the sectional areas of the orifices 123 and 118 and valve seat members 119 and 126, respectively.
  • the main diaphragm 107 controls the amount of fluid flow by means of such a displacement as to make up the difference of pressure between the chambers 140 and 141 in the above-mentioned function, but it cannot adjust the pressure difference accurately, because of the existence of the restitution force of the main diaphragm 107.
  • the auxiliary diaphragm 105 is made to bend in a bowed or circular form in a direction (i.e. to the right in FIG.
  • auxiliary diaphragm will act in the opposite way to make up the error due to the restitution force of the auxiliary diaphragm 105.
  • this invention makes it possible to obtain a prompt response characteristic which can perform accurate distribution control with a flow divider which distributes the pressure fluid discharged out of the fluid pressure source evenly or in a predetermined flow ratio by means of the passage, orifices and valve seat members, because of its structure which is so designed as to maintain the amount of flow distributed from each outlet port to each subsequent means at a predetermined ratio by means of the displacement of the diaphragm in accordance with the changes of the load pressure acting upon each outlet port. ln addition, as compared with the conventional spool-type flow dividers, this divider cannot only be manufactured easily but also ensures the performance of long and effective distribution functions, since it has eliminated various troubles through the elimination of the sliding parts.
  • a flow divider having at least one inlet zone and first and second outlet ports, comprising:
  • first, second and third disc members mounted in said casing, said first and second disc members defining a main control chamber, said second and third disc members defining an auxiliary control chamber; imperforate, flexible main diaphragm means provided in said main control chamber and separating the same into first and second sub-chambers; imperforate, flexible auxiliary diaphragm means provided in said auxiliary control chamber and separating the same into third and fourth subchambers, said first and second sub-chambers being respectively connected to said fourth and third sub-chambers;
  • said first and second disc members being respectively provided with first and second openings communicating with said first and second sub-chambers, said first and second openings being connected to said first and second outlet ports;
  • said second and third disc members being respectively provided with third and fourth openings communicating with said third and fourth sub-chambers, said third and fourth openings being connected to said inlet zone;
  • first and second variable restriction means provided between said main diaphragm means and said first and second openings, said main diaphragm means being responsive to pressure in said first and second sub-chambers to vary the flow restricting effects of said first and second variable restriction means;
  • third and fourth variable restriction means provided between said auxiliary diaphragm means and said third and fourth openings, said auxiliary diaphragm means being responsive to pressure in said third and fourth sub-chambers to vary the flow restricting effects of said third and fourth variable restriction means, so that rate of flow of fluid through said first and second outlet ports is maintained constant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)
US3729014D 1970-02-07 1971-02-03 Flow divider Expired - Lifetime US3729014A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1092070A JPS498974B1 (es) 1970-02-07 1970-02-07

Publications (1)

Publication Number Publication Date
US3729014A true US3729014A (en) 1973-04-24

Family

ID=11763671

Family Applications (1)

Application Number Title Priority Date Filing Date
US3729014D Expired - Lifetime US3729014A (en) 1970-02-07 1971-02-03 Flow divider

Country Status (3)

Country Link
US (1) US3729014A (es)
JP (1) JPS498974B1 (es)
DE (1) DE2105225B2 (es)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807426A (en) * 1973-06-25 1974-04-30 R Henes Pressure operated valve
US4204554A (en) * 1977-03-08 1980-05-27 The Bendix Corporation Fluid control means
US5085243A (en) * 1991-02-14 1992-02-04 Westinghouse Air Brake Company Hydraulic isolation valve for railway vehicle
US5732497A (en) * 1988-06-06 1998-03-31 Saf-T-Lok Corporation Gun lock assembly
US5749166A (en) * 1988-06-06 1998-05-12 Saf T Lok Corporation Gun lock assembly
US5974717A (en) * 1996-09-25 1999-11-02 Saf T Lok Corporation Firearm safety mechanism
CN109595373A (zh) * 2019-01-07 2019-04-09 山东大学 一种柔性铰链厚膜节流器及调节方法
US10578221B2 (en) 2016-10-11 2020-03-03 Precision Planting Llc Flow divider
RU2796719C1 (ru) * 2022-12-16 2023-05-29 федеральное государственное бюджетное образовательное учреждение высшего образования "Донской государственный технический университет" (ДГТУ) Дроссельный делитель потока

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2339765A1 (fr) * 1976-02-02 1977-08-26 Cloup Jean Dispositif diviseur de debit
JPS52132572U (es) * 1976-04-05 1977-10-07
US4033371A (en) * 1976-06-24 1977-07-05 Pall Corporation Proportioning valve for volumetric proportioning of flow
JPS601794U (ja) * 1983-06-15 1985-01-08 日本ハム株式会社 屠体解体処理装置における屠体回転装置
JPS6050076U (ja) * 1983-09-14 1985-04-08 日立造船株式会社 レ−ル方向変換装置
US4923092A (en) * 1988-07-20 1990-05-08 The Coca-Cola Company Binary syrup metering system for beverage dispensing
JPH0382382U (es) * 1989-12-13 1991-08-22
DE102017101970A1 (de) * 2017-02-01 2018-08-02 GETRAG B.V. & Co. KG Hydraulikanordnung und Kraftfahrzeugantriebsstrang

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US353704A (en) * 1886-12-07 Method of commingling flowing fluids in definite proportions
US1780589A (en) * 1927-03-21 1930-11-04 Howard A Hyde Water-regulating device
US1993790A (en) * 1931-02-06 1935-03-12 Celanese Corp Distribution of fluids
GB539895A (en) * 1940-03-23 1941-09-29 Ass Equipment Co Ltd Improvements in and relating to fluid-pressure-operated braking devices
US2283266A (en) * 1939-04-24 1942-05-19 Celanese Corp Distribution of fluids
US2992652A (en) * 1956-11-01 1961-07-18 Louis F Guenther Safety valve
US3010469A (en) * 1960-02-23 1961-11-28 Hydro Aire Company Leak sealing valve for fluid brake systems

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US353704A (en) * 1886-12-07 Method of commingling flowing fluids in definite proportions
US1780589A (en) * 1927-03-21 1930-11-04 Howard A Hyde Water-regulating device
US1993790A (en) * 1931-02-06 1935-03-12 Celanese Corp Distribution of fluids
US2283266A (en) * 1939-04-24 1942-05-19 Celanese Corp Distribution of fluids
GB539895A (en) * 1940-03-23 1941-09-29 Ass Equipment Co Ltd Improvements in and relating to fluid-pressure-operated braking devices
US2992652A (en) * 1956-11-01 1961-07-18 Louis F Guenther Safety valve
US3010469A (en) * 1960-02-23 1961-11-28 Hydro Aire Company Leak sealing valve for fluid brake systems

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807426A (en) * 1973-06-25 1974-04-30 R Henes Pressure operated valve
US4204554A (en) * 1977-03-08 1980-05-27 The Bendix Corporation Fluid control means
US5732497A (en) * 1988-06-06 1998-03-31 Saf-T-Lok Corporation Gun lock assembly
US5749166A (en) * 1988-06-06 1998-05-12 Saf T Lok Corporation Gun lock assembly
US5085243A (en) * 1991-02-14 1992-02-04 Westinghouse Air Brake Company Hydraulic isolation valve for railway vehicle
US5974717A (en) * 1996-09-25 1999-11-02 Saf T Lok Corporation Firearm safety mechanism
US10578221B2 (en) 2016-10-11 2020-03-03 Precision Planting Llc Flow divider
CN109595373A (zh) * 2019-01-07 2019-04-09 山东大学 一种柔性铰链厚膜节流器及调节方法
RU2796719C1 (ru) * 2022-12-16 2023-05-29 федеральное государственное бюджетное образовательное учреждение высшего образования "Донской государственный технический университет" (ДГТУ) Дроссельный делитель потока

Also Published As

Publication number Publication date
DE2105225B2 (de) 1974-02-14
DE2105225C3 (es) 1974-09-19
JPS498974B1 (es) 1974-03-01
DE2105225A1 (de) 1971-08-19

Similar Documents

Publication Publication Date Title
US3729014A (en) Flow divider
US3868972A (en) Hydraulic pressure compensator
US3455210A (en) Adjustable,metered,directional flow control arrangement
US3106934A (en) Integrating and proportional flow control apparatus
US5447093A (en) Flow force compensation
US4168721A (en) Pressure control valve
US4083375A (en) Pilot regulator
US3724494A (en) Flow regulating valve
US3561488A (en) Fluid flow control valve
US3554222A (en) Automatic flow control valve
CA1196544A (en) Flow control device
US4187877A (en) Compensated work port fluid valves
US3251633A (en) Controlled fluid-lubricated bearings
US3581772A (en) Frictionless spool valve
US2937656A (en) Flow rate compensator
US3011506A (en) Control valve
US2931343A (en) Electro-hydraulic servo valve with pressure repeating power amplification
US4858515A (en) Priority valve for hydraulic installations
US4094333A (en) Regulating valve system
US4509548A (en) Reactant pressure differential control for fuel cell gases
US3590844A (en) Device for dividing the flow of liquid into two parts
US6532989B1 (en) Hydraulic distributor
US2718877A (en) Hydraulic servo with integral equalization
US2904055A (en) Hydraulic amplifier valve with feedback
US3211063A (en) Pressure control switching valve