4771 4775.output

* GB785178 (A)

Description: GB785178 (A) ? 1957-10-23

Improvements relating to steam irons

Description of GB785178 (A)

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PATENT SPECIFICATION 782 Date of Application and filing Complete Specification Feb 16, 1956 No4918/56 A Pplication rn m 'ain United States of America on Feb 17, 1955. Complete Specification Published Oct 23,1957. Index at Acceptance:-Class 138 ( 2), t 2 F. International Classification:-Do 6 f. COMPLETE SPECIFICATION 6 Improvements relating to Steam Irons"' We, HOOVER LIMITED, a Company registered under the Laws of Great Britain, of Perivale, Greenford, Middlesex, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: This invention relates to steam irons and is concerned with a simple and effective arrangement of flash boiler and steam passage for such

an iron. According to the present invention a sole plate for a steam iron includes a generally U-shaped heating element having its bight in the forward part of the sole plate and a pair of limbs extending rearwardly from it, a flash boiler adjacent the rear end of one limb of the heating element, a number of steam ports extending through the sole plate to the ironing surface in its forward part, and a steam passage leading from the boiler alongside the heating element on one side (inside or outside) of the U, round the end of the limb remote from the boiler and alongside that limb on the other side of the U to the steam ports For example the steam ports may be located outside the U of the heating element while the distributing passage extends from the boiler inside the U The invention may be carried into practice in various ways, by one specific embodiment will be described by way of example with reference to the accompanying drawings, in which:Figure 1 is a side elevation, partly in section, of an iron embodying the invention, Figure 2 is a plan view of the sole plate with part of its cover plate broken away, and Figures 3 and 4 are sections respectively on the lines 3-3 and 4-4 of Figure 2. The iron shown in the drawings comprises a sole plate 10 formed of cast aluminium. Embedded within the sole plate is a horseshoe shaped heating element 11 of the li' sheathed resistance type, comprising a bight 12 adjacent the toe of the sole plate 10 and a pair of limbs 13 and 14 extending rearwardly along the sides of the sole plate and having turned up rear ends 15 and 16 to form 50 electrical connections as well as providing zones of concentrated heat. Formed in the upper surface of the sole plate 10 is a flash boiler recess 17 As'shown in Figure 2 this is situated within the U, that 55 is between the limbs, of the heating element, close to the upturned rear end 15 of the limb 13 The recess 17 communicates with a steam passage 18 having a portion 19 extending forwards from the flash boiler in heat 60 exchange relationship with the inside of the limb 13 of the heating element, a portion 20 extending thence across the inside of the bight 12 of the heating element, a portion 21 extending back along the inside of the 65 limb 14 of the heating element, a portion 22 extending round the rear end of the limb 14 of the'heating element at a point of concentrated heating caused by the upturned end 16, a portion 23 extending forward on the 70 outside of the limb 14 of the heating element, a portion 24 extending across outside, or forward of, the bight 12 of the heating element, and a portion 25 extending thence rearwards outside the forward part of the limb 13 of 75 the heating element. Formed in the floor of the portions 24 and and the forward part of the

portion 23 of the -steam passage are a number of steam ports 26 which extend through the sole plate 80 to the ironing surface to deliver steam to the fabric being ironed. The flash boiler 17 and the steam passage 18 are closed by -a cover plate 30 having an opening 31 immediately above the flash 85 boiler 17 The cover plate is secured to the sole plate by screws so that it may be removed to facilitate cleaning of the boiler and the steam passage. Water is supplied to the flash boiler 17 90 i,178 from a reservoir 34 through a valve 32 having an inlet 35 communicating with the reservoir and an outlet 33 projecting into the opening 31 The valve has a stem 36 arranged to open or close the inlet 35 and sealed by a flexible bellows 37. The, valve 32 may be operated in any convenient manner In the arrangement shown the sole plate 10 is surmounted by a cover shell 41 to the rear end of which is secured the single rear pillar of a handle 50, whilst a control dial 45 connected to an adjustable thermostat 46 by a driving connection 47 overlies the central part of the cover shell and serves to control the temperature of the sole plate The operation of the valve 32 is controlled by the control dial 45 through a generally Z-shaped actuating slide 39 This has a central limb lying horizontally and connected by a pin and slot connection 42 to the top of the cover shell 41, a vertical depending arm engaging the end of the valve stem 36, and a vertical upstanding arm 43 co-operating with a cam surface 44 on the temperature control dial 45 The actuating slide 39 is urged rearwards by a tension spring 38 connected between it and a bracket secured inside the rear end of the cover shell 41 The cam 44 is formed to close the valve 32 at all temperature settings except the one particular setting which is considered appropriate for steam ironing At this setting the cam is formed with a recess which permit' the spring 38 to draw the actuating slide 39 rearwards and so allow the flexible bellows to expand to open the valve. It will be seen that steam is generated in the flash boiler 17 which is in a zone of concentrated heat, being close to the upturned end 15 of the limb 13 of the heating element. The steam then passes forward across and back through the portions 19, 20, and 21 of the steam passage, all of which lie close alongside the heating element 11, between its limbs As it passes -round the end of the 45 limb 14 in the portion 22 of the passage the steam is again in a zone of concentrated heat due to the upturned end 16 of that limb. Thence it passes forward through the passage portion 23 in good heat exchange relation 50 ship with the outside of the limb 14 of the heating element, and finally through the passage portions 24 and 25 where it is still close to the bight portion and limb 13 of the heating element Accordingly the steam is 55 caused to pass through a

long passage in the whole of which it is subjected to the superheating effect of the element, so that when it passes down through the ports 26 it will be in super heated form and no water will 60 be ejected through the ports 26 to stain the fabric being ironed.

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* GB785179 (A)

Description: GB785179 (A) ? 1957-10-23

Improvements in or relating to a safety means for use in a system forcontrolling a fluid actuated device


PATENT SPECIFICATION 785,179 Date of Application and filing Complete Specification: Feb 28, 1956. No 6142/56. Application made in United States of America on March 18, 1955. (Patent of Addition to No 744,581 dated March 23, 1954) Complete Specification Published: Oct 23, 1957. Index at acceptance:-Class 80 ( 4), R 4. International Classification:-FO 6 p. COMPLETE SPECIFICATION Improvements in or relating to a Safety Means for use in a System for Controlling a Fluid Actuated Device We, ROSS OPERATING VALVE COMPANY, a corporation organized under the laws of the State of Michigan, United States of America, of 120 East Golden Gate Avenue, Detroit 3, Michigan, United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by

the following statement:- This invention relates to fluid control valves, and more particularly to safety valves and systems for controlling the application of pressure to fluid actuated devices such as presses, clamping fixtures, or the like This application is for a Patent of Addition to the patent applied for in application Serial No 8437/54, filed March 23, 1954, by the present applicant. In the aforementioned parent application, a device is disclosed which provides an economical and efficient means for automatically shutting off the supply to a fluid actuated device if for any reason a plurality of control valves are not synchronously moved to their various positions during the cycle. This may for example happen when an operator deliberately "ties down" one of a pair of simultaneously operable valves (pro vided for safety purposes) in order to speed up operation of a machine The device comprises a safety valve which is disposed in the parallel connections between the control valves and the fluid actuated device. The safety valve normally serves merely to conduct fluid to and from the fluid actuated device, but includes sensing meansresponsive to pressure differentials created by nonsychronous movement of the control valves to disenable said connections and prevent further operation of the fluid actuated device. Upon subsequent movement of the control valves in unison, the safety valve is again restored to its normal condition. The present application relates to the lPrice 38 6 d l further improvement residing in additional means for compensating for supply pressure fluctuations and also for preventing safety valve cut-off caused by minor discrepancies in control valve movement In industrial 50 installations it is not uncommon to have a fluid supply pressure which varies from time to time This variation in supply pressure could cause corresponding variations in the manner of operation of a safety valve of this 55 type In particular, the changes in frictional and in velocity characteristics in the more restricted passageways could cause the sensitivity of the safety valve to fluctuate through a wide range Moreover, it is ordi 60 narily desirable -that the system be kept in operation even though the operator may move one control valve at a slightly different time than the other Such a discrepancy could easily be created by human error, the 65 operator being devoid of any intent to tie down one of the valves. Several means for overcoming these difficulties are provided in the safety valve shown in the accompanying drawings In 70 particular,, a pair of one-way restrictions are disposed between the control valves and the safety valve for providing restricted flow of fluid toward the safety valve and relatively unrestricted flow toward the control

valves 75 Moreover, a by-pass conduit is provided between the fluid connections to the control valves, this conduit having an adjustable restriction, whereby cut-off of the safety valve caused by minor non-synchronism of 80 the control valves is avoided. According to the invention there is provided a safety device according to British patent application 8437/54 for use in a system for controlling a fluid actuated device includ 85 ing a pair of independently operable manual control valves for controlling the supply and exhaust to said device, parallel connections between said independently operable valves and said fluid actuated device, and safety 90 Price 25 p means separate from said fluid actuated different positions for purposes of clarity A device, said safety means being interposed threaded connection 58 is provided at the between said parallel connections and said outer end of each extension 54, line 17 being device and having a normal position per attached to this connection A compression mitting uninterrupted fluid flow between coil spring 59 is disposed within connection 70 said valves and said device in either direction, 58 and engages the outer end of slidable said safety means having sensing elements member 55, urging valve 56 against a valve responsive to a pressure differential caused seat 61 A central passageway 62 is provided by the non-uniform position of said valves in member 55, this passageway leading from to disenable said connections, said safety connection 58 to a T-shaped passageway 63 75 device comprising a pair of one-way restric When members 55 are in the position tions between said parallel connections and shown in Figure 1, valves 56 are closed and said safety means, said restrictions providing passageways 63 are connected with chambers restricted flow of fluid toward said safety 48 With this position, it will be seen that means and relatively unrestricted flow toward if either pilot valve 12 is turned to its supply 80 said control valves position, fluid will flow through connection In order that the invention may be under 58, passageway 62 and passageway 63 of the stood, it will now be described with reference corresponding slidable member 55 The to the accompanying drawings in which: restriction imposed by passageway 63 will Figure 1 is a side elevational view in cause the pressure build-up in corresponding 85 cross section of the improved safety valve chamber 48 to be slightly delayed, the time of this invention incorporating means for of this delay depending on the size of passagefor compensating for supply pressure fluctua way 63 Due to the T-shaped nature of tions and for decreasing the sensitivity of passageways 63 the fluid flowing from of the safety valve, and; passageways 62 will not impinge directly 90 Figure 2 is a cross sectional view taken on balls 39 and will therefore not interfere along the line 2-2 of Figure 1 and showing with their operation When

either pilot the adjustable restriction for the by-pass valve 12 is turned to exhaust, the fluid conduit pressure in corresponding chamber 48 will The safety valve is generally indicated at force member 55 outwardly, compressing 95 49 A pair of one-way restrictions generally spring 59 and opening valve 56 Fluid will indicated at 51 are disposed between lines then flow through valve 56, passages 57 and 17 and chambers 48, and a by-pass conduit 52 connections 58 to lines 17 The area available connects left and right hand chambers 48, for this flow from safety valve 49 to pilot this conduit having an adjustable restricting valves 12 is substantially greater than the 100 device These features are discussed in restricted flow area available from pilot valves detail below 12 to the safety valve It will be noted that The valve is connected between a pair of each slidable member 55 can move independparallel connections 17 which are controlled ently of the other slidable member, so that by pilot valves 12 movable between supply the position of each will be governed by the 105 and exhaust positions A conduit 22 connects position of its corresponding pilot valve 12 central chamber 33 of the safety valve to and the pressure in its corresponding chamber a fluid actuated device (not shown) Housing 48. 18 of the safety valve encloses slidable valve By-pass conduit 52 comprises a passagemembers 26 and spherical elements 39 within way which connects left and right hand 110 the central passages of these valve members chambers 48, by-passing ball valves 39 and Vent openings 32 in the valve housing are central chamber 33 The diameter of this connectible with central chamber 33 by passageway may be any appropriate size, inward movement of valve members 26 but is preferably small enough to ensure Central passages 41 in valve members 26 have appreciable frictional losses in fluid flow 115 flared outer portions 53 adjacent chambers passing from one chamber to the other A 48, passages 37 connecting passages 41 to restricting device comprising a screw 64 is central chamber 33 By virtue of flared mounted in housing 18, this screw having portions 53 of passages 41, the fluid velocity an end portion 65 capable of restricting a and therefore the pressure drop across a predetermined area of passageway 52 A 120 ball 39 will be lessened when it is disposed lock nut 66 may be provided for holding within the flared portion of the passageway screw 64 in position By means of this One way restrictions 51 are enclosed within passageway, it will be seen that the build-up extensions 54 of housing 18 and each restric of pressure in either chamber 48 will take tion comprises a slidable member 55 carrying place more slowly than if the passageway 125 a valve 56 at one end thereof Each member were not present. has flat sides so as to provide passages 57 In operation, it will be

assumed that between the inner surface of extension 54 left hand control valve 12 is turned to its and member 55 The left hand and right supply position and that a few moments hand members 55 in Figure 1 are shown in later right hand-control valve is turned to 130 785,179 _ rapid With the sources of fluid described above, this is achieved by providing a relatively unrestricted flow from chamber 48 to the pilot valve 12 which is connected to 60 exhaust. Tests have proved that the presence of restrictions 51 in the system will not interfere with its operation in terms of offering excessive resistance to flow One reason 65 for this is that the unitized nature of the safety valve makes possible a minimum of outside piping in the system, and the friction losses thus eliminated make it feasible to use controlled restrictions of the type 70 described.


* GB785180 (A)

Description: GB785180 (A) ? 1957-10-23

Improvements in or relating to servo units for hydraulic brakes


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DE1229866 (B) DE1229866 (B) less Translate this text into Tooltip

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The EPO does not accept any responsibility for the accuracy of data and information originating from other authorities than the EPO; in particular, the EPO does not guarantee that they are complete, up-to-date or fit for specific purposes.

PATENT SPECIFICATION -85,18 N Date of Applicatin and filing Complete Specification March 1, 1956. 443 t N No 6445/56. Ago pplication made in United States of America on March 25, 1955. Complete Specification Publshed Oct 23, 1957. Index at Acceptance:-Classes 79 ( 5), 119; and 103 ( 1), F 1 (A 2 A 2 81: A 2 C: Bl H 13). International Classification:-B 61 h. COMPLETE SPECIFICATION "Improvements in or Relating to Servo Units for Hydraulic Brakes " We, WAGNER ELECTRIC CORPORATION, a tion between said pump and said cylinder, corporation-organised under the laws of the throttling means establishing communicaState of Delaware, United States of America, tion between opposite faces of said piston, of 6400 Plymouth Avenue, City of St Louis, throttling control means for controlling said State of Missouri, United States of America, throttling means, said throttling control 50 do hereby declare the invention, for which means extending through said piston and we pray that a patent may be granted to us, said extension and terminating within an and the method by which it is to be per outlet chamber, said outlet chamber being formed, to be particularly described in and connected with said brake operating motor by the following statement: and having compensating fluid means 55 This invention relates to series power associated therewith. hydraulic braking systems and in particular One of the principal objects of the present to a servo motor employed therein to control invention is to provide a servo motor which said system is balanced to function regardless of -the The present invention provides a hydraulic existing ambient pressure in its particular 60 cylinder comprising a housing having a bore section of the system. therein, said bore having an inlet and an out Another object of this invention -is to let for pressure fluid, said housing having a provide a servo motor which operates the coaxial bore with a reservoir port and an vehicle brake assemblies even if there is a outlet port therein, a piston slidable in said power failure in the system 65 bore and defining chambers in said bore Still another object of the present invenadjacent to the opposite faces of said piston, tion is to provide a servo motor having a free said piston being normally urged toward said and slidably mounted power piston which inlet port, a passageway connecting said does not displace pressure fluid during a chambers,

throttling means operatively posi braking: operation after there has been a 70 tioned between said inlet and said piston for power failure and which thereby reduces the controlling the flow of pressure fluid through manually applied force normally reqpired said passageway, said throttling means being under such conditions. operated by an external force, said piston Still another object of the present invenhaving an extension thereon extending into tion is to provide a servo motor which pro 75 said coaxial bore, a seal slidably mounted in vides " feel " for the operator "Feel" is the said coaxial bore, said seal adapted to be proportional reactionary force in opposition moved in response to said piston extension to the applied force which affords the operand said external force for forcing pressure ator an appraisal as to the extent of the brak fluid from said coaxial bore to the outlet ing application 80 port Another object of the present invention is The present invention further provides a to provide a servo motor which appreciably power braking system comprising a hydraulic reduces the port hole cutting of the sealing servo cylinder having a bore therein, a cup used therein. reservoir having fluid therein associated with These and other objects and advantages 85 said cylinder, a brake operating motor, 'a will become apparent hereinafter The pump operatively associated with said present invention comprises a plurality of cylinder, a piston slidable in the bore of said ' servo motors serially arranged with a positive cylinder, said piston having an extension displacement pressure producing means in thereon, means for establishing communica a hydraulic system The servo motors are -90 lPrice 3 s 6 d l Price Ss 04, Pace 33 p-6 l 785,180 manually operated thereby restricting the pressure fluid flow therethrough to establish a pressure differential This pressure differential-supplements the operator applied force and acts as a booster force to actuate the vehicle brakes, power steering, and the like. The servo motor described hereinafter provides safe operation of the brake assemblies during and after a power failure; however, in the event of failure, the operator must supply all of the force required. The invention also consists in the parts and in the arrangements and combination of parts hereinafter described and claimed In the accompanying drawings which form part of this specification and herein like numerals and symbols refer to like parts wherever they occur: Fig 1 illustrates a braking system having a preferred embodiment of this invention therein: shown partially in cross-section, and Fig 2 shows a modification of the preferred embodiment partially in cross-section in a braking system Referring to Fig 1, the-power hydraulic system shown comprises a positive-4 isplacement pumping means 1 supplied by a fluid reservoir 2 through a conduit 3 The

pressure side of the pumping means 1 is connected by a conduit 4 to an inlet and an inlet chamber A in a servo motor 5 A conduit 6 connects the outlet side of the motor 5 with a power hydraulic steering valve 7 arranged in series with said motor The outlet of said steering valve 7 is connected with the reservoir 2 by a conduit 8 thus providing a return passage for the fluid displaced by the pumping means 1. In addition to the above circuit, a conduit 9 is provided connecting the conduits 6 and 8 and having a reverse flow valve 10 interposed therein, said reverse flow valve being employed to facilitate pressure fluid recirculation during a power steering failure application If desired, the valve 10 may be -integral with the power steering valve 7. A pressure relief valve 11 is interposed in a conduit 12 which connects the conduits 3 and 4 and provides a shunt around the pumping means 1 thereby protecting said means from pressure overloads Also a conduit 13 is connected between the reservoir 2 and a fluid port in the servo motor 5 for compensation purposes A conduit 14 is attached to the pressure side of the servo motor 5 and leads to a plurality of wheel cylinders 15 which actuate the brake assemblies. The servo motor 5 comprises a booster housing 16 having a brake housing 17 secured to the right end thereof The booster housing 16 has a -piston bore 18 and a counterbore 19 horizontally arranged therein. The counterbore 19 is provided with a vertically positioned inlet 20 at its left end and an outlet 21 near the right end thereof. A ball type pressure relief valve 22 is interposed between inlet 20 and outlet 21 being received in the connecting passage formed by a horizontal bore 23 and axially aligned 70 counterbore 24, said valve 22 being biased against a seat 25 by a valve spring 26 carried by a guide member 27 The right end of the spring 26 abuts against a sealing member 28 and has its compressive force predeter 75 mined by a spacer 29 against which the right side of said sealing member 28 abuts. A power piston 30 is freely and slidably mounted in the bore 18 and counterbore 19 and is provided with an enlarged portion 31 80 substantially at the mid-portion thereof carrying an "O" ring to provide a seal between the wall of said counterbore 19 and the outer periphery of said enlarged portion. Thus, the enlarged portion 31 forms an inlet 85 -chamber A in the counterbore leftwardly thereof and a main or central chamber B rightwardly thereof Another X)" ring, supported in a groove in the bore 11 o S=scals, the left end of the piston 30 Cross-drille 90 passageways 32 and 33 are positioned one opposite sides of the enlarged portion 31 and intersect a bore 34 within said piston 30. Slidably received in the bore 34 is a throttling rod 35 having a circumferential groove 36 95 in its mid-portion forming a throttling

passage D and a channel 37 between said rod 35 -and bore 34 An "O" ring, supported in the leet end of the rod 36, provides a seal between the bore 34 and said rod 35,-and 100 another "O" ring, supported in said rod 35 rightwardly of the groove 37, provides a seal between said bore 34 and the rod 35 The leftward end of the throttling rod 35 pivotally receives one end of a push rod 38 A 105 resilient boot 39 prevents the entry of foreign matter in the servo motor 5 and is positioned between the left end of said servo motor 5 and the push rod 38 The opposite end of said push rod 38 is attached to a brake 110 actuating pedal 40 through a mechanical linkage (not shown) The actuating pedal 40 is provided with a return spring (not shown) which imparts a positive return action to the push rod 38 and consequently, to the 115 throttling rod 35. The free and slidable power piston 30 projects coaxially into a bore 41 provided in the brake housing 17 through a sealing ring 42 retained in the right end of the counterbore 120 19 by suitable means The right end of the throttling rod 35 also projects into the bore 41 extending beyond the piston 30 and carries a snap ring 43 which is received in an inner recess 44 in the right end portion 125 of the power piston 30 The throttling ro 4 also carries a cup backup washer 45 and a double-lipped, resilient, sealing cup 46 which are positioned thereon by retaining means 47 fixedly attached to said rod Since 130 the rod 35 is urged leftwardly by the actuating pedal return spring (not shown), as aforementioned, the retainer 47, the cup 46, the washer 45, and the right end or edge of I, 785,180 the piston 30 are normally biased into an abutting relationship, and the snap ring 43 is seated in the recess 44. A reservoir port 48 is vertically positioned in the upper portion of the brake housing 17 for compensation purposes One end of the reservoir port 48 receives the conduit 13 and the other end intersects the bore 41 adjacent to the lip of the cup 46 as shown An outlet chamber C is formed in the'bore 41 rightwardly of the cup 46 and is provided with an outlet port or brake port 49 which connects the rightward end of the bore 41 with the conduit 14 A compensation valve 50 is positioned between the reservoir port 48 and the brake port 49 and is mounted in a connecting passageway formed by a horizontal bore 51 and an axially aligned counterbore 52 The valve 50 is biased against a seat 53 by a spring 54 positioned between said valve and an end plug 55 fixedly mounted in the counterborec 52 Another passageway 56 is angularly interposed between the reservoir port 48 and the bore 41 and functions as a fluid supply port and lubrication means. In this series system, the pressure relief valve 11 operates at a pressure equal to the sum of-the maximum pressure differentials allowed across the individual servo motors and protects the pumping

means 1 from pressure overloading which is caused when one or more of said servo motors exceed predetermined maximum pressure differential. Each servo motor is provided with a pressure relief valve which predetermines the maximum pressure differential allowed across said servo motors, and the pressure existing in a servo motor at any time is effective upon every servo motor of prior position in the system If the steering valve 7 is actuated, the pressure differential created therein causes a back pressure which is effective throughout the servo motor 5 against which the pumping means 1 must work Ordinarily a servo motor of prior position would be. actuated by this back pressure; however, the servo motor 5 is balanced to prevent such an occurrence Balancing is achieved by a symmetry of cross-sectional areas which are affected by the aforesaid back pressure In the free and slidable piston 30, the effective cross-sectional area of the leftward portion of the enlarged portion 31 in the inlet chamber A is equal to the cross-sectional area of the rightward portion which forms part of the main chamber C In the throttling rod 35, the affected cross-sectional area forming the leftward wall of the groove 36 is balanced by an equal affected area forming the rightward wall thereof In this manner, equal and opposite self-cancelling forces are created obviating the effect of any' back pressure imposed throughout the servo motor S in that particular section of the series system. Assuming the steering valve 7 to be unrestricted, pressure fluid is normally discharged from the pumping means through the conduit 4 and the inlet 20 into the inlet chamber A of the servo motor 5 where it 70 flows through passageway 32 unrestricted into the channel 37 and'through the passageway 33 and therefrom into the counterbore 19 or chamber B From the counterbore 19, the fluid flows through the outlet 21 and the 75 conduit 6 into the power steering valve 7 and is then'returned to the reservoir 2 through the conduit 8. When the vehicle operator applies a force to the actuating pedal 40, a proportional 80 force is transmitted' to the push rod 38 and the throttling rod 35 through the intermediate linkage (not shown) Therefore, the throttling rod 35 is moved rightwardly restricting pressure fluid flow through the throttling passage 85 D and the channel 37 thereby creating a pressure differential across the enlarged portion 31 of the free and slidable piston 30. Because of the existing pressure differential, the piston 30 moves rightwardly carrying the 90 washer 45 and cup 46 further into the bore 41, and the throttling rod 35 necessarily follows and maintains the restriction of the throttling passage D and the restriction of fluid through the channel 37 because of the 95 manually applied force This movement displaces pressure fluid from the bore 41 or outlet chamber C

to the brake port 49 and the conduit 14 into the wheel cylinders 15 thereby actuating the brake assemblies The 100 magnitude of the maximum pressure differential is predetermined by the operating or actuating pressure of the pressure relief valve 22 The fluid pressure developed in the outlet chamber C acts on the effective areas of 105 the washer 45 and the cup 46 and also the rod 35 creating a reactionary force in opposi tion to the motivating force of the piston 30 and said rod 35 When the reactionary force equals the motivating force, the rightward 110 movement of said piston 30 and rod 35 ceases Since the reactionary force thus created is effective upon the rod 35, the operator is afforded a direct "feel" as to the extent of the braking application 115 When the operator releases the applied force, the established fluid pressure in the bore 41 and the actuating pedal return spring returns the throttling rod 35, the free and slidable piston 30, and parts associated 120 therewith to their normal positions When this occurs, a partial vacuum is developed in the bore 41 The compressive force of the spring 54 in association with the compensation valve 50 is very light allowing said valve 125 to be actuated at a very small pressure differential, said differential existing between the bore 51 and the bore 41 Thus pressure fluid is allowed to flow to compensate past the valve 50 at a small pressure differential 130 Since fluid compensation into chamber C is not accomplished by collapsing the lip of sealing cup 46, said sealing cup may be provided with a shorter and stiffer lip portion so that it will be exposed to port hole cutting C displacing pressure fluid therefrom through for a shorter distance and be more resistant the brake port 49 and conduit 14 into the to port hole cutting during said shorter wheel cylinders 15 which actuate the brake 70 distance assemblies In this case, the reverse flow In the event of a power failure, the operator valve 59 is necessitated for the recirculations is required to supply all of the actuating of the pressure fluid displaced from the force to operate the servo motor 5 As pre counterbore 19 by the piston 30 Upon the viously described, the force applied by the release of the applied force, the fluid pressure 75 operator moves the throttling rod 35 right in the bore 41 and the actuating pedal spring wardly Due to the absence of pressure fluid returns the rod 35, the piston 30, and parts flow through thek throttling passage D and associated therewith, to their normal the channel 37, a pressure differential is not positions. created to motivate the free and slidable This invention is intended to cover all 8 () piston 30 The immobility of the piston 30 changes and modifications of the example of obviates a reverse flow valve in conjunction the invention herein chosen for purposes of with the servo motor 5 since displacement the disclosure, which do not constitute of pressure fluid therefrom does not occur departures from the scope of

the invention.


* GB785181 (A)

Description: GB785181 (A) ? 1957-10-23

Improvements in and relating to sound recorders


-I. PATENT SPECIFICATION 785,181 Date of application and filing Complete I Specification: March 2, 1956. No 6557/56. Complete Spec Ification Published: Oct 23, 1957. Index at acceptance:-Class 40 ( 2), D 2 BU, D 2 C( 1 A: 1 U: 7 G 2: 7 H 2: 7 L), D 2 E 2 E. l Iternational Clasuification:-Gl Oj. COMPLETE SPECIFICATION Improvements in and relating to Sound Recorders I, JOHN GAR Fi ELD Fo Nr AINT, a Citizen of Canada, of 5,789, College Highroad, in the City of Vancouver, in the Province of British Columbia, Canada, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement: - My invention relates to improvements in sound recorders. With the development of telephone message recording devices it is becoming increasingly -necessary to provide recorder disks, cylinders or tapes capable of carrying messages of one, two or more hours duration To accomplish this it is necessary that the sound track upon

the record shall be extremely narrow and that the convolutions or paths of such track shall be very close together The conventional screw feed for moving the tone arm radially across the record is therefore unsatisfactory since it is not practical to provide the feed screw and -the nut for moving the tone arm with a sufficiently fine thread. The object of the present device is to provide a mounting whereby the tone arm may be moved steadily across a six inch record to either record or play messages or music of a duration of two hours, or more. A further object is to provide means whereby when the device is set to record, the -stylus of the pickup will be subjected to greater downward pressure onto the record than when it is set to play According to the invention, a sound recorder comprises: a spindle for rotating a record disk, a horizontal track rail supported within the recorder, a carriage movable along the rail, a tone arm upon the carriage adapted to engage a record disk driven by the spindle, rack and pinion means for moving the carriage in one direction, a motor having a shaft for rotating the pinion and a clutch interposed between said shaft and said pinion lNee 4 J Referring to the accompanying drawings:Figure 1 is a fragmentary plan view of the invention so Figure 2 is a sectional view taken on the line 2-2 of Figure 1. Figure 3 is a sectional plan view taken on the line 3-3 of Figure 2. In the drawings like characters of refer SS ence indicate corresponding parts in each figure. The numeral 1 indicates a table from which a housing 2 is suspended to enclose the mechanism of the recorder In the device as 60 here shown, a record disk 4 is provided on the table upon which a disk record 5 is adapted to be rotated by a vertical spindle 6 Aslotted opening 7 is formed in the table 1 and suitably supported below said opening is a 65 square rail 8, see Figures 1, 2 and 3 A carriage 10 is mounted for endwise movement upon the rail 8, which carriage consists of upper and lower plates 11 and 12 between which two pairs of horizontal wheels 14 each 70 having peripheral V-grooves 15 are mounted The V-grooves 15 ride upon the horizontally opposing edges of the rail 8 and maintain said carriage against any rotational movement about said rail Extending in 75 wardly from the lower plate member 12 is a toothed rack 17, the purpose of which will hereinafter appear. Mounted upon the carriage is a platform which carries a substantially U-shaped 80 housing 21 having side walls 22 extending forwardly beyond the slotted opening 7 A -tone arm 24 is journalled intermediate its=. length on a pair of needle bearings 25 carried adjacent the free ends of the housing side 85 walls 22 The tone arm 24 is preferably formed of very thin spring sheet material on edge so as to provide a slight transverse flexi bility, the-forward end 26 is provided with a pickup

head 27 and stylus The rear end of 90 the tone arm 24 is provided with a horizontal member 28 and said tone arm and housing 21 are adapted to be partly enclosed in a re It will be apparent that by this method of movable cover 29 shown in dotted line in effecting the transverse movement of the 65 Figure 2 A spring pressed plunger 30 is carriage the number of convolutions capable fitted to the cover 29 and is adapted to be of being used on a record is limited only by depressed to engage the member 28 and lift the width of the sound track inscribed bn the tone arm out of engagement with the the record.


* GB785182 (A)

Description: GB785182 (A) ? 1957-10-23

Improvements in brakes for perambulators


PATENT SPECFICATION Date of filing Complete Specification: April 27, 1956. Application Date: March 8, 1956 No 7254/56. Complete Specifkation Published: Oct 23, 1957. Index at Acceptance:-Class 103 ( 1), E 2 H 9 A. International Classification: FO 6 d. COMPLETE SPECIFICATION. Improvements in Brakes for Perambulators. I, THOMAS RICHARDSON, of 9 Christopher Street, Hendon, Sunderland, in the County of Durham, a British Subject, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement:

This invention relates to perambulators and has for an object to provide improved four wheel braking mechanism, such that whenever the handlebar of the perambulator is released the brakes are automatically applied. The invention accordingly provides fourwheel braking mechanism for a perambulator, comprising a framework including two transverse bars at the ends of which are brake pads each to engage one of the wheels, a pair of brackets secured or securable to extend rearwardly from the permanent frame to which the wheel axles are secured, a transverse rod mounted in said brackets, a T-member having the lower end of its shank connected to said rod and its cross bar locatable adjacent and parallel to the handlebar of the perambulator resilient means serving' for connecting said framework and the permanent frame so as to apply the brake pads to the wheels, and link means serving to connect said framework and the shank of the T-member at such a level above said rod that drawing of the cross bar into proximity to the handlebar displaces said framework so as to withdraw the brake pads from the wheels. The T-member may be telescopic so as to be adjustable to the height of a handlebar of any perambulator. The foregoing and other features of the invention will be better understood from the following description by way of example of an embodiment illustrated in the accompanying drawings wherein: Fig 1 is a plan view of a mechanism applied to the permanent frame of a perambulator; and Fig 2 is a side elevation of same. The perambulator frame illustrated comprises a pair of tubular members 1 having upwardly curved ends 2 at the extremities of which are two pairs of studs 3 from which the perambulator body 25 is slung A handlebar 4 is supported from the rear of the body by a pair of rising tubular members 5 The frame is carried upon a front axle 6 upon which are mounted a pair of wheels 7, and a rear axle 8 and having at its ends a pair of wheels 9. The braking mechanism according to the invention comprises a pair of longitudinal members 10 interconnected by front and rear transverse bars 11 and 12 on the ends of which are mounted brake pads 13, one to engage each of the four wheels. Connecting the rear bar 12 to the rear axle 8 are a pair of tension springs 14, the ends of each of which are secured respectively to said bar and to a clip 15 bolted ta said rear axle. There are secured to the rear curved portions 2 of the frame a pair of brackets 16 extending rearwardly and upwardly and carrying at their lower ends a transverse tension bar 17 upon the middle of which is mounted the lower end of a shank 18 of a T-member which has a cross bar 19 mounted adjacent the handlebar 4.

At a suitable level above the tension bar 17 the shank 18 is embraced by a link member of strip metal as shown, bent to Y-form with a double leg the two sides 20 of which embraces the shank 18, while the forward ends 21 of the prongs are bent horizontal and secured by rivets or bolts to the rear transverse bar 12. The mechanism is such that when the 785 q 182 O.w i -60; XW v 9 785,182 cross bar 19 and the handlebar 4 are both grasped so that the cross bar is moved rearwardly to the position shown in chain dotted lines, the displacement of the shank 18 acting upon the Y-form link pulls the rectangular brake frame rearwardly against the force of the springs 14 so as to displace the brake pads 13 sufficiently from the wheels to release the latter, while when the handlebar is released the cross bar 19 is free to move forward by the pull of the springs 14 acting on its shaft 18 through the Y-form link and the brakes are automatically applied. The location of the link 20 above the tension bar 17 is such that the permitted movement of the rectangular brake is sufficient to allow full application and release of the brake pads while affording a leverage such that there is no strain upon the hands in holding the cross bar 19 in proximity to the handlebar 4 in opposition to pull of the springs 14. As shown, the front end of the brake frame is supported by the forward transverse bar riding upon the members 1, and is held down against the tendency to lift by a wire cross bar 22 having coiled ends 23 by which it is secured to the members 1. Evidently in an alternative arrangement which might better suit other types of perambulator frame, the front end of the brake framework might he adapted to be supported upon such a cross bar 22 and held down against the tendency to lift by the forward transverse bar being located below the side members 1. Further as shown the rear end of the brake framework is held down against the tendency to lift when the brakes are applied by the longitudinal members 10 being located below the rear axle This rear end is suitably supported by the springs 14 alone, but in an alternative arrangement when the springs do not support the rear end this may be supported by a pin 24 passing loosely through a hole in the shank 18 and the parts 20 of the link member. Evidently brake mechanism according -to the invention may be suitably modified to suit different types of perambulator frame. For example, series of holes may be provided in the longitudinal members 10 so that the transverse bars 11 and 12 may be suita ably placed in relation to other arrangements of wheels Further, the brackets 16 and the parts 20 of the link means may be provided with series of holes in which the tension bar 17 and pin 24 are engageable

so as to adjust the location of the T-member 18, 19, if desired with suitable telescopic adjustment of the shank 18, to enable convenient operation of the brakes while bringing the cross bar 19 into suitable relation to the ia 5 handlebar 4.
