US2707796A

US2707796A - Door check and closer

Info

Publication number: US2707796A
Application number: US113624A
Authority: US
Inventors: Otis J Hawks
Original assignee: Individual
Current assignee: Individual
Priority date: 1949-09-01
Filing date: 1949-09-01
Publication date: 1955-05-10
Anticipated expiration: 1972-05-10

Description

.o. J. HAWKS 2,707,796

DOOR CHECK AND CLOSER Filed Sept. 1, 1949 6 Sheets-Sheet 1 INVENTOR was, M

M %vz; M

ATTORNEY O. J. HAWKS 7 DOOR CHECK AND CLOS ER May 10, 1955 6 Sheets-Sheet 2 IIIIII'IIIII II Elli!!! 1! Lil.

IIIIIIIIII'IIIII I .411. l Ilfififfd i 1/ III Filed Sept. 1, 1.949

ATTORNEY May 10, 1955 o. J. HAWKS DOOR cmacx AND CLOSER 6 Sheets-Sheet Filed Sept, 1, 1949 w by ///A #1 A'iTORNEY y 0, 1955 o. J. HAWKS 2,707,796

DOOR CHECK AND CLOSER Filed Septr l, 19 49 I 6 Sheets-Sheet 5 A INVENTOR M y 1955 o. J. HAWKS 2,707,796

' DOOR CHECK AND CLOSER Filed Sept. 1, 1949 6 Sheets-Sheet 6 United States Patent i 1 2,707,796 DGQR CHECK AND CLOSER ()tis J. Hawks, Portsmouth, Va. Application September 1, 1949, Serial No. 113,624 37 Claims. (Cl. 16-52) This invention relates to a door check and closer which is designed and constructed in such manner that it may be interposed between a door and a door casing to hold the door in its closed position and to return the door to closed position at a regulated rate after it has been opened and released. The invention relates more particularly to a door check and closer which comprises a clock-type coiled spring which is loaded during the opening movement of the associated door and which acts to return the door to closed position at a rate regulated by the fluid resistance encountered by a radial type piston of an associated hydraulic checking mechanism. The door check and closer is of the universal type, being constructed in such manner that it may be employed to close a door which is hinged to either the right hand side or the left hand side of a door casing without requiring the door closer to be disassembled and certain of the component parts rearranged, for example, the spring elements of the closer arm.

Each of the several universal door closers heretofore known, has included a helical type spring arranged to be wound or loaded, by anchoring either end and moving the other relatively thereto. In one instance, in the case of a spring disposed with its axis vertical, the spring wound by means which acts upon its upper end, and, in the second instance, causing it to be loaded by means which acts upon its lower end. This arrangement provides a satisfactorily acting door closer of the universal type, but when the mass of spring metal which is necessary to provide the desired spring action is arranged in the tubular form of a helical member the resulting spring is too high to incorporate in a door closer which has commercially acceptable dimensions and appearance. The same amount of spring metal may, however, be employed in the more compactly arranged clock-type spring form of a much smaller overall size.

It is one of the principal objects of this invention to provide a compact and entirely effective door closer of the universal type in which the operating mechanism comprises a clock-type spring.

The universal door closer heretofore most commonly used comprises a crank member arranged to drive the piston of a hydraulic checking mechanism so that, irrespective of the direction of rotation imparted to the crank by the closer arm from normal starting position, the piston is caused to move in the same direction. Alternatively, such door closer comprises a half pinion and double rack arrangement for driving the piston of the hydraulic checking mechanism wherein the half pinion moved by the closer arm swings from engagement with teeth provided in one side of a rack actuated by the closer arm to engagement with teeth formed on the other side of the rack to impart the same reciprocatory movemovement to the piston irrespective of the direction in which the pinion is caused to move by the closer arm from normal starting position.

Each of such mechanisms as described immediately above necessarily has a dead center at the termination of the piston movement in one direction, and as a movement of this extent is accomplished when the associated door is opened to as little as 80 it will be apparent that effective checking action by the hydraulic checking mechanism is absent for a considerable movement of the associated 2,707,795 Patented May 1'0, 1955 2 results in undesirable back-lash, or lost motion, when the closer is operated, which back-lash or lost motion is greatly amplified by the leverage ratio which exists between the relatively short stroke of the piston and the distance traversed by the edge of the door in moving from its open to its closed position.

A further object of this invention is to provide a hydraulic checking mechanism for a universal door closer which employs a radial type piston which precludes the disadvantages inherent in devices which operate through a dead center, and which obviates the possibility of lost motion developing between the hydraulic checking mechanism and the door with which the closer is associated. The radial piston type hydraulic checking mechanism offers the further advantage that the entire body of fiuid in the mechanism is employed for checking action. In the reciprocatory piston type mechanism a large portion of the fluid present merely serves to fill up void space in the piston chambers and is not metered through control apertures during the door closing control action of the closer. Accordingly, the practical adaptation of the radial type piston mechanism to a universal acting clocktype spring effects a saving in the fluid required, and without increased cost makes it practical to use more expensive long lasting fiuids which have improved operating characteristics such as constant viscosity over a wide temperature range, high volitization temperature, and high surface tension. Accordingly, another object of the invention is to utilize a radial type piston in a hydraulic checking mechanism in conjunction with a universai clock-type spring mechanism to furnish an efiicient, compact and attractive universal door closer.

A further object of the invention is to provide a radial piston type checking mechanism embodying a general speed control and a latch bolt speed control, the latch bolt speed control being designed and constructed to effect a reversal of the direction in which hydraulic resistance is encountered by the radial piston of the hydraulic checking mechanism.

A further object of the invention is to provide a closer arm assembly for a door closer embodying a radial piston type hydraulic checking mechanism which readily permits the closer arm to be readjusted, and the piston repositioned when the hand of the closer is reversed.

A further feature of the invention locates the door closer speed controls and adjustments in a position in which they may readily be adjusted when the door closer is operatively assembled with a door and door casing in normal overhead position. Another feature of the invention is directed to obtaining a uniform rate of movement of the edge of the door with which the closer is associated from the moment the closing movement begins until the latch bolt speed control mechanism becomes operative. A further feature provides improved means for venting air which may be entrapped in the fiuid pressure chamber of the hydraulic checking mechanism in which the radial piston is supported to insure an immediate and smooth response from the hydraulic checking mechanism of the closer when the door is released for closing movement. A further object of the invention is to provide an improved type general speed control valve which may be used with particular advantage in conjunction with a radial piston type hydraulic checking mechanism. A further object of the invention is to provide a means of adjusting the initial resistance of a clock-type closer spring during assembly of the closer, which nevertheless permits a full range of adjustments to be made externally after the closer has been assembled. Another object is to provide an improved linkage for connecting the door closer to the door casing in which a spring-like section of the linkage serves as a frictionless pivot between the linkage and the fixed attachment to the door casing, and serves to absorb shocks transmitted to the closer assembly during certain phases of the closing movement of the door.

Other features and advantages of the invention will be apparent from the following detailed description there of which is made with reference to an embodiment illustrated in the accompanying drawings. It will be understood, however, that the detailed description made with reference to the illustrated embodiment is for the purpose of facilitating an understanding of the invention and that the invention is not to be construed as limited to the described and illustrated details, as various changes and modifications thereof will be apparent to those skilled in the art to which the invention relates.

In the drawings:

Figure l is a side elevational view of the door closer illustrating the manner in which the closer is operatively interposed between a door and a door casing, the lower portion of the door closer housing being cut away to reveal the lower portion of the closer body and the location of the manually operated speed controls and adjustment mechanism;

Figure 2 is a bottom plan View or" the door closer further illustrating the location of the speed controls and adjustments on the body portion of the door closer, and the closer arm linkage;

Figure 3 is a perspective illustration of the door closer supports;

Figure 4 is a vertical sectional. view along the vertical axis of the door closer illustrating in detail the spring mechanism, the hydraulic checking mechanism, the spring winding mechanism and the closer arm assembly;

Figure 5 is a transverse sectional view of the hydraulic checking mechanism along the line .5--5 of Figure 4 showing the relative position of the piston and piston stop member when the closer is in a door closed condition;

Figure 6 is a transverse sectional view of the hydraulic checking mechanism along the line 6-6 of Figure 4 which passes through the general speed control valve which is situated in a passage passing from one side to the other of the piston;

Figure 7 illustrates the relative position of the piston and the piston stop member of the hydraulic checking mechanism when the closer is in a fully opened position;

Figure 8 is a view along the line 55 of Figure 4 illustrating the piston transiting the area in which th latch bolt speed control mechanism becomes operative as the general speed control mechanism is cut out during the closing movement of the associated door;

Figure 9 illustrates the action of the by-pass port check valves during that phase of the closing movement;

Figure 10 illustrates the action of the by-pass ports during the initial stage of the closing movement of the associated door;

Figure 11 is a partial sectional view of a portion 01" the hydraulic checking mechanism illustrating the relative position between the piston stop member, the lid of the fluid pressure chamber, the rotary latch speed control valve and the venting channels formed in the under side of the lid;

Figure 12 is a vertical sectional view through the piston stop member showing the rotary alve therein positioned for operation of the closer on one hand;

Figure 13 is a horizontal section through the same piston stop member;

Figure 14 is a top plan view thereof:

Figure 15 is a sectional view similar to that of Figure 12 but illustrating the rotary valve positioned for operation of the closer on the reversed hand;

Figure 16 is a view similar to Figure 13 but showing the rotary valve positioned for operation of the closer on the reversed hand;

Figure 17 is a perspective view of the rotary valve which serves to reverse the hand of the closer, regulate the latch bolt speed of the closer, and control the access of the operating fluid to the expansion chamber;

Figure 18 is an exploded view of the spring mechanism of the closer;

Figure 19 is a perspective view of the piston stop member, the radial piston and the piston shaft of the hydraulic checking mechanism;

Figure 20 is a perspective view illustrating the position of the registerin slots formed in the piston and piston stop member, respectively;

Figure Zl is a partial sectional view through the upper margin of the lower body portion of the closer illustrating the manner in which the locking pin is received in the lower body portion and the adjusting ring;

Figure 22 is a plan View of an alternative form of the lever of the closer arm assembly;

Figure 23 is a detailed illustration of the closer arm hub assembly; and

Figure 24 illustrates an alternative construction for the byass ports illustrated in Figure 6.

Referring to Figures 1 and 2 wherein the general appearance of the door closer and the manner in which it may be operatively associated with a door 2% hinged to a door casing 21 is illustrated, it will be seen that the door closer comprises a generally cylindrical two piece housing, the lower portion 22 of which may be detached from the upper portion 23 to expose the lower portion 24 of the closer body or base member to provide ready access to the manually operated controls of the door closer which are located on the bottom of the body portion of the closer as hereafter explained in more detail.

Fixed to, or formed integrally with the body portion of the closer is a plate 25 provided with obliquely disposed lateral edges 26 and 27 which are adapted to be received in a bracket which may be fixed to the door with which the closer is to be associated to support the closer on the door. The obliquely disposed lateral edges 26 and 27 of the plate are adapted to be received in the respective channels between the l..-members 28 and 2) fixed to, or formed integrally with, the door bracket 30. The bracket 30 is also provided with a tab 31 disposed normally to the face of the bracket and adapted to underlie the bottom edge 32 of the plate 25 when the plate is positioned on the bracket. The plate is provided with a threaded opening 33 which is positioned to register with the aperture 34' in the tab 31. A locking screw may be inserted into the aligned openings and tightened to draw the plate 25 downwardly, the oblique lateral edges of the plate tightly engaging the channels of the bracket to hold the door closer in a rigid, fixed relationship with the bracket. This support construction considerably simplifies assembling the door closer on the door as it is unnecessary to support the weight of the entire closer while the bracket is being fastened to the door.

The spring and hydraulic checking mechanisms of the door closer are actuated by, and subsequently control the closer arm 33 which is supported on the end of a rotatable shaft extending through the top portion of the door closer. The distal end of the closer arm is connected with the casing arm 34 which at its other end is secured to the door casing 21 so that relative movement between the door and the door casing causes the closer arm to be rotated, and the spring and hydraulic checking mechanisms of the door closer to be actuated thercby as will be described hereinafter in detail.

Referring to Figure 4, it may be seen that the door closer comprises an upper annular body portion 35 which is enlarged in diameter toward its lower end at which l mechanism indicated generally at H. A radial type piston 39 is rotatably supported within the fluid pressure chamber 38 and rigidly aifixed to the piston shaft 40 which extends upwardly through the central aperture of the annular lid member 37 and the upper body portion 35, and which is journaled for rotative movement in the spring loaded leather packing 41 and the needle bearing 42. It is the normal practice to store assembled closers with their longitudinal axis horizontal and the packing 41 prevents fluid from leaking or creeping out along the shaft 40 when the closer thus stored is exposed to atmospheric changes which during reduced temperatures cause air to be drawn into the expansion chamber along the shaft which air later expands during temperature increases and forces the fluid outwardly along the shaft. The upper notched end 40' of the piston shaft engages the hub assembly of the closer arm, described in more detail hereinafter, whereby rotary movement imparted to the closer arm 33 caused by opening movement of the door with which the closer is associated is transmitted to the rotary shaft 40 and to the radial piston 39. The piston is thereupon moved into position in which the hydraulic checking mechanism will be effective to regulate the rate at which the energy stored in the spring mechanism, indicated generally at S, by the opening movement of the closer arm will be applied to the closer arm to return the door to its closed position.

The spring mechanism S of the door closer comprises a coil or clock-type spring 43 which is supported within the outer spring casing 44, illustrated most clearly in Figures 4 and 18. A clock-type or coil spring, as used herein, refers to the type of spring which is formed from a length of spring metal with each of the lateral edges thereof throughout its length disposed in the same plane and in spiral form. The outer end 45 of the spring is fixed to a spring abutment, and it may, for example, be

passed through apertures provided in the side wall of the spring casing 44 and crimped against the casing to securely anchor the end of the spring to the casing. A spring abutment which may be in the form of an inner spring casing 46 is positioned within the central opening of the coiled spring 43 and provided with an aperture in the tubular portion thereof through which the inner end 47 of the spring is passed, the inner end 47 of the spring being splayed, or flared, or otherwise arranged, to prevent the end from Withdrawing from the aperture. The casing 46 is provided with an upstanding circular flange 48 at the lower end of its tubular section and the spring thus assembled with the casing members is adapted to encircle the upper body portion 35 which is provided with a circular shoulder 50 which engages the underside of the circular flange 48 and supports the assembled spring and spring casings.

The spring mechanism is arranged so that the spring may be wound from either end and the closer adapted for universal action by providing the spring casing 44, to which the outer end of the spring is attached, with Winding catches 54 and 55 which are engaged by a winding member connected with the closer arm when the closer arm is moved in one direction, and by providing winding catches 56 and 57 on the spring casing 46, to which the inner end of the spring is fixed, which are engaged by a winding member when the closer arm is causedto be moved in the other direction by the opening movement of the door. As seen best in Figures 4 and 18, the winding catches 54, 55 are formed on the top surface of the spring casing 44, and may be tabs which are punched out of the casing into an upright position. 'The winding catches 56 and 57, also seen best in Figures 4 and 18, may be punched out of the cylindrical wall of the spring casing 46 so as to be facing inwardly towards one another from opposite points on the cylindrical walls.

A dog 58 is fixed to the closer arm 33 and extends downwardly to engage in the peripheral notches of the winding ratchet 59 which is freely supported on and guided by the piston shaft 40. To the underside of the ratchet 59 is fixed a pair of locking pins 60 which are arranged to extend downwardly into two diametrically opposite holes of the series of holes arranged circumferentially on the hub portion of the winding arm 61 which is also freely supported on and guided by the piston shaft 40. Thus arranged, rotary movement of the closer arm 33 will cause a corresponding rotation of the winding arm 61. The winding catches 54 and 55 are disposed at different radial distances from the central axis of the outer spring casing 44, and the

arms

62 and 63 of the winding arm 61 are of correspondingly different lengths, so that the depending

flanges

64 and 65 on the respective arms will engage one of the winding catches 54 or 55. The arm 61 is initially positioned so that the winding catches 54 and 55 are both offset in a clockwise direction from the depending

flanges

64 and 65 whereupon clockwise movement of the winding arm 61 will result immediately in engagement between the depending flanges and the winding catches and the casing 44 caused to rotate in a clockwise direction thereby winding the spring 43 from its outer end 45 which is fixed to the wall of the casing. It will be seen, however, that counter-clockwise movement of the closer arm causes counter-clockwise movement of the winding arm 61, which moves the

flanges

64 and 65 away from the winding catches 54 and 55, respectively, and causes the flange 64 to pass outwardly of the catch 55 and the flange 65 to pass inwardly of the catch 54 if the movement is continued throughout more than Counter-clockwise movement of the wind ing arm 61 would therefore be unimpeded until the arm had been rotated through approximately a complete revolution at which point the depending

flanges

64 and 65 would be adjacent to and about to engage the winding catches radially disposed at distances corresponding to the length oft he

respective arms

62 and 63.

A second winding member 69 is supported on and guided by the piston shaft 40 and arranged to engage the winding tabs 56 and 57 on the inner spring casing when the closer arm is caused to rotate in a counter-clockwise direction as a result of opening movement of the associated door. The locking pins 60 are of suflicient length to extend through the winding arm 61 and to be received in the diametrically spaced holes provided in the upper portion of the member 69. The winding member 69 is provided with tabs 70 and 71 which extend radially from the outer vertical wall of the member and are positioned at different distances along the longitudinal axis of the member to correspond with the longitudinal axial displacement of the winding tabs 56 and 57, respectively, on the inner spring casing. The winding member 69 is adapted to be positioned within the central aperture of the annular inner spring casing 46 with the winding catches 56 and 57 disposed in a counter-clockwise direction from the tabs 70 and 71, respectively. Thus positioned, counter-clockwise rotation of the closer arm 33 will be transmitted to the winding member 69, and the tabs thereof will immediately engage the winding catches of the inner spring casing 46 and cause the casing to move in a counter-clockwise direction drawing with it the inner end 47 of the spring 43 aflixed thereto. Clockwise movement of the closer arm 33, on the other hand, will move the tabs 70 and 71 away from the immediately adjacent winding catches, and continuation of the clockwise movement will cause the tab 70 to pass above the winding catch 57 and the tab 71 to pass beneath the winding catch 5 6, thus allowing the winding member '79 to move unobstructed throughout approximately a complete revolution which is considerably in excess of the arcuate movement of the closer arm required in normal operation of the door closer.

The circular flange portion 48 of the inner spring casing is provided with a depending retaining lug 72 which is initially positioned in a counter-clockwise direction from the stop member 73 fixed to the lower enlarged portion of the upper body portion 35 and positioned radially to engage the retaining lug 72 and prevent movement of the inner spring casing, and the inner end 47 of the spring, when the spring is being wound from its outer end by clockwise movement of the closer arm 33.

There is also provided an arrangement for retaining the outer spring casing 44, and the outer end 45 of the spring, immovable while the spring is being wound from its inner end as a result of counter-clockwise movement of the closer arm which also provides a means for selectively adjusting the initial resistance offered by the spring during assembly of the closer. The arrangement is such that a full range of spring tensioning adjustments can later be made externally by means of the winding ratchet 59 even though the retaining means is previously utilized during assembly of the closer to adjust the closer to a desired initial torque characteristic.

For this purpose the lower edge of the outer spring casing is provided with retaining

lugs

74 and 75 positioned at different radial distances from the central axis of the casing. An adjusting ring 76 is supported on a circular shoulder 77 formed on the upper section of the lower body portion 24 and provided with stops '78 and 79 which are positioned at a radial distance from the center of the ring which corresponds to the location of the retaining lugs 74 and 75, respectively. The ring 76 is initially positioned so that the

stops

78 and 79 are immediately adjacent and in a counter-clockwise direction from the retaining lugs on the spring casing 44. Accordingly, the outer spring casing 44 is free to move in a clockwise direction when clockwise rotation is imparted to the winding arm 61 which in turn rotates the casing in the same direction; and the casing will be prevented from moving by the

steps

78 and 79 bearing against the retaining lugs 74 and 75, respectively, when the spring is wound from its inner end by counter-clockwise rotation of the winding member 69 which in turn imparts the same rota tion to the inner spring casing 46 to which the inner end of the spring is affixed. The outer casing 44 is free to rotate in a clockwise direction through approximately a full revolution as the retaining lug 74 will pass inwardly of the stop 79 and the retaining lug 75 will pass outwardly of the stop 78 if the clockwise movement is continued through more than 180.

The ring 76 is provided with a series of circumferential notches adapted to receive a iocking plate 31 which at its lower end is arranged to engage a notch in the upper margin of the lower body portion 24, and to carry a pin 82 as illustrated in Figure 18, which is received in an opening in the upper part of the lower body portion 24 whereby the ring may be locked in a fixed relationship with the body portion of the closer.

In assembling the closer the initial tension of the spring 4-3 may require adjustment to obtain the desired initial torque characteristic due to variations between difi'erent springs in the spiraling of the spring. To accomplish the desired adjustment the locking plate may be removed and the ring rotated in a clockwise direction. This wit] cause the

steps

78 and 79 of the ring to bear against the retaining lugs 74 and 75, respectively, and impart clockwise movement to the outer spring casing 44 to accomplish the desired initial tensioning of the spring. The locking plate may then be reinserted in the closer body and in the notch in the adjusting ring then closest to alignment with the locking pin. The notches provided in the ring are angularly spaced to correspond with the spacing of the circumferentially disposed holes in the hub portion of the winding arm 61. As the clockwise adjustment of the casing 4-4 causes the winding catches 54 and 55 to move away from the normal position in which they are immediately adjacent the depending flanges 64- and 65, respectively, the arm 61 may be correctly repositioned to correspond to the adjusted setting draw the locking pins 60 from the hub portion of the winding arm and rotating the Winding arm clockwise sufficiently to move the hole beneath the locking pin 60 which corresponds with the notch in which the locking pin. 81 was previously set. The adjustment, which is made normally only by the manufacturer when assembling the closer, does not limit the range of adjustments of the spring tension which may be accomplished later by external adjustment of the winding ratchet 59.

When the spring has been wound by movement of the closer arm in the manner described as a result of. opening movement or" the door with which the closer is associated and the door thereafter released, the energy stored in the wound spring is exerted on the closer arm through the winding member which is responsive to the particular direction of movement of the closer arm, the Winding ratchet, and the closer arm dog. The rate of this closing movement is selectively regulated by the action of the hy raulic checking mechanism indicated generally at H in Figure 4.

The hydraulic mechanism comprises the radial piston 39 having a hub portion 85 which is substantially cylindrical in form and a wing portion 86 which extends radially therefrom. The wing portion is rounded at its outer edge to conform to the curvature of, and to closely engage, the inner wall of the circular fiuid pressure chamber 38 in which the piston is rotatably supported. The under surface of the hub portion of the piston is provided with a depending boss 83 in axial alignment with the piston shaft 50 which boss is received in a recess formed in the inner bottom of the fluid pressure chamber to aid in guiding the rotary movement of the piston within the fluid pressure chamber. The piston is rigidly fixed to the lower end of the piston shaft 40 which at its upper end is connected with the closer arm hub assembly to cause the piston to be rotated in one direction during opening movement of the closer arm, and to permit the piston to regulate the rate of movement of the closer arm during closing movement as will be more fully described hereafter.

The hydraulic checking mechanism also comprises a piston stop member fit which serves with the radial piston to regulate the rate at which fluid contained in the fluid pressure chamber is passed from one side of the piston to the other side thereof as the piston is caused to rotate within the chamber which determines, in turn, the rate of closing movement of the closer arm. As seen most clearly in Figure 12 the piston stop member is provided with two transverse

parallel passages

91 and 92, and a vertically disposed central aperture 93 which intersects the

passages

91 and 92. A rotatable valve 94 (Figure 17) provided with a unidirectional fluid fiow checking member 95 is positioned within the aperture 93 and serves to selectively determine the direction in which tluid impelled by movement of the radial piston will be passed through the piston stop member or blocked thereby. The direction may be reversed by rotating the valve 94 through to the position indicated in Figure 15 to reverse the direction in which the checking action of the member 95 will be effective. The piston stop member 99 is positioned within the fluid pressure chamber so that one of the lateral surfaces 96 or 83 of the member abuts the adjoining lateral surface of the wing portion of the piston when the closer arm is disposed in one of its normal closed positions. One of the normal closed positions of the closer arm is illustrated in Figures 1 and 2, wherein opening movement of the door with which the closer is associated will cause the closer arm and the radial piston to move in a clockwise direction. Except as indicated otherwise, the following description will be made with respect to the arrangement of the closer components which adapt the closer for operation on the hand on which opening movement of the associated door will cause clockwise movement of the closer arm.

The piston stop member may be provided with dowels 97 which are received in corresponding openings in the inside bottom of the pressure chamber 38 and in the pressure chamber lid 37 to provide a simple and reliable method of retaining the piston stop member in a fixed position within the pressure chamber. The outer surface of the piston stop member is contoured to closely engage the inner Wall of the circular pressure chamber 33, and the centrally facing surface of the stop member is cambered to engage the rounded hub portion 85 of the radial piston.

The hub portion of the piston is provided with a general speed control fluid passage 98 along a diameter of the hub portion perpendicular to the axis of the wing portion 86 of the piston extending therefrom. An upwardly extending aperture 99 formed coaxially with the piston rod 40 is provided in the bottom portion of the piston and opens into the central portion of the general speed control passage 98 (Figure 4). This aperture receives a plug or piston 100 which acts as a valve to regulate the flow of fluid through the passage 8 from one side of the piston to the other. The valve Hit) can be adjustably positioned to restrict the passage 98 by adjustments of the general speed control operating member 101 which comprises a stem which extends upwardly through the bottom of the lower body portion 24 into engagement with the undersurface of the plug or piston 100. The piston 100 is provided with a longitudinal passage 84 which equalizes the hydraulic pressure on either side of the piston and prevents a differential pressure from developing on either side thereof which would cause the piston to move from its selected setting.

The end of the stern engaging the undersurfaceof the plug is rounded or otherwise reduced in cross-section to minimize the friction between the two members and to obviate the possibility of the adjustable stem member being dragged around and misadjusted as a result of the plug being seized by and rotated with the piston during normal operation of the closer. The essential factor, however, is the provision of the regulating member in two pieces (1G0, 101) so that the manipulated part (101) may be made readily accessible by being brought out through the lower body portion, with respect to which the piston that receives the other part (1%) moves relatively during normal operation of the closer.

A spring 102 is inserted between the upper end of the plug and the end of the aperture to cause the plug to follow the adjusting movements of the operating member 101 at all times.

Thus arranged, when the piston is caused to move from its initial position indicated in solid lines in Figure in a clockwise direction as a result of opening movement of the door with which the closer is associated moving the closer arm in clockwise direction, the fluid in front of the piston will be forced through the piston stop member, entering the passage 92a, dislodging the checking member 95 of the valve 94-, and passing through the passage 91]) to the low pressure side of the piston (Figure 12). Transfer of the fluid through the stop member and the rotary valve 9 therein will continue until the piston has moved to its fully open position indicated in dotted lines in Figure 5 in which it is abutting the lateral face 83 of the piston stop member, or until the opening movement is terminated. As the spring unwinds to effect closing movement of the door, the piston will be rotated in counterclockwise direction, and as the rotary valve 94 will block flow of fluid through the piston stop member in the direction the piston is now moving, the fluid can be transferred from the high pressure side of the piston to the low pressure side thereof to permit further rotary movement only through the general speed control passage 98 which is adjustably restricted by the valve member 100. Accordingly, the rate at which the door returns to its closed position may be regulated throughout the first phase of its closing movement, designated herein as the general speed range by, appropriate adjustment of the valve 160.

it will be observed, however, that when the piston has rotated to its fully open position in which it abuts the lateral face 83 of the piston stop member (Figure 7) the one end of the passage 98 is blocked off by the cambered face of the stop member and communication between the high pressure and the low pressure sides of the piston through the piston is blocked off.

Piston release ports

104 and 105, provided in the piston to communicate between the general speed control fluid passage 98 on either side of the general speed control valve, respectively, and the respective lateral faces of the wing portion of the piston, serve to pass the fluid from the high pressure to the low pressure side of the piston during the interval when one end of the passage 98 is blocked in the manner described. These release ports are shown most clearly in Figures 6, 7, 9 and 10. During the initial movement of the piston from its wide open position, therefore, fluid will pass from the high pressure side of the piston into the open end of the passage 98, through the general speed control valve centrally disposed in the passage, and through the passage 104 to the low pressure side of the piston. The piston is thus permitted to move toward clo ed position at a rate which is here again regulated by the general speed control valve disposed in the passage 98. The fluid flow during this stage of the return movement is indicated by the arrows in Figure 10.

it will be seen, therefore, that the general speed control valve is effective to regulate the closing movement of the door at a uniform rate throughout the general speed range as the entire body of fluid passed from the high pressure side to the low pressure side of the piston during this period is metered by the single general speed control valve 100.

The piston release port 105 is symmetrically arranged with the port 164 and operates in a similar manner when the closer is set for operation from the reverse hand. Unidirectional fluid flow valves, such as the

check valves

106 and 107, may be arranged in the wing portion terminals of the ports 164 and 105, respectively, to block entry of fluid into the ports when the respective terminals of the passages are communicating with the high pressure side of the piston. The necessity for this action will be apparent from an inspection of Figures 8 and 9 which illustrate the status of the various fluid passages as the piston moves past the point at which the general speed control passage 98 is blocked off by the cambered face of the stop member and the latch bolt speed control mechanism (described hereinafter) assumes control of the rate of closing movement. .t this point a fluid passage to the low pressure side of the piston is opened through the latch bolt speed control mechanism as indicated by the arrows in Figure 8. However, if the ball check 167 in port 105 were absent, the fluid would continue to fiow through port 105', to passage 98, and through valve 1% to the low pressure side of the piston, and control of the rate of closing movement during the last stages thereof could not be obtained by the latch bolt speed control mechanism alone. The ball checks serve to block off the flow of fluid through the piston as indicated in Figure 9 when the latch bolt speed control mechanism becomes operative.

An alternative means of transferring fluid from the high pressure to the low pressure side of the piston at a rate regulated by the general speed control valve during the initial portion of the piston movement from its fully open position is illustrated in Figure 24. An

elongated slot 108 is provided in the cambered face of the piston stop member 90 in position to register with end of the passage 98 which is covered by the cambered face as the piston approaches its fully open position which is illustrated in solid lines in Figure 7. A port 109 is provided in the stop member communicating with the slot 108 and with a registering port 110 in the rotary valve 94. The port 110 communicates with the passage 91 in the piston stop member which, in turn,

communicates to the low pressure side of the piston. The ends of the passage 98 are enlarged to form a tapered aperture so that the passage 98 will remain in communication with the slot 108 until the covered end of the passage 98 has rotated clear of the solid portion 111 of the piston stop member. Both ends of the passage 98 are symmetrically arranged with tapered apertures and the rotary valve 94 is provided with symmetrically disposed passages llfi so that the arrangement described is operable irrespective of the hand on which the closer is operated.

As the piston approaches its closed or initial position indicated in solid lines in Figure during the closing movement thereof, the end of the passage 98 on the high pressure side of the piston is blocked off by the cambered face of the piston stop member 9t). This action also occurs in the operation of the modification illustrated in Figure 24 in which instance the solid portion 111 of the piston stop member blocks off the passage 98 as aforesaid. At this instant the latch bolt speed control mechanism becomes operative to regulate the rate of closing movement of the door during the latter stages thereof (Figures 8 and 9). The latch bolt speed control mechanism comprises a slot 112 formed in the face of the cylindrical hub portion which slot is positioned to register with a similarly shaped slot 113 provided in the cambered face of the piston stop member (Figure A port 114 communicates between the slot 113 and the central aperture 93 of the piston stop member. As seen most clearly in Figure 17 the rotary unidirectional fluid flow valve 9-1 is provided with a port 116 having terminals 116a and 116:; positioned so that they may be moved into registration with the inner terminus of the port 114, a port 117 communicates between the port 116 and an arcuate slot 118 which is positioned to register with the passage 91a in the piston stop member as illustrated most clearly in Figure 12. Accordingly, as the piston approaches its closed position and the general speed control passage 93 is blocked off, the slot 112 overlaps the slot 113 and the fluid on the high pressure side of the piston is passed through the port 114, the ports 116, 11.7, the slot 118 and the passage 91a to the low pressure side of the piston. The rate of fluid flow, and consequently the rate of movement of the piston and closer arm during this last stage of the closing movement, may be regulated by rotating the valve 94 and thereby varying the degree of registration between the mutually facing terminals of the port 116 in the valve and the port 114 in the piston stop member.

The terminals of the port 116 are feathered to avoid an abrupt cut-off during adjustment of the degree of registration with port 114, and to increase the accuracy with which adjustment may be made by decreasing the variation in registration obtained per degree of rotation of the valve 94 as the valve is moved toward the cut-oil point. The cut-out portions 51. and 52 of the valve 94 which communicate with the

passages

91 and 92. respectively, of the piston stop member have sufficient arcuate dimensions to maintain communication with the

passages

91 and 92 throughout the full range of adjustments of the terminals 116a, 1161: with respect to port 114.

When it is desired to change the direction in which fluid resistance is offered to rotation of the piston in order to change the hand of the closer, the valve 94 is rotated through 180 to the position indicated in Figure 15. The rotation of the valve 94 to change the hand of the closer, or to vary the latch bolt speed is accomplished by means of the latch bolt speed control member 119, which comprises a stem extending upwardly through an appropriately packed aperture in the bottom of the lower body portion 24 of the closer into a notched-out keyway formed in the bottom of the body portion of the valve.

The valve 94 is provided with the symmetrically disposed passage 116 so that the latch bolt speed control obtainable by varying the extent of registration of the

passages

116 and 114 can be obtained when the hand of the closer has been reversed by rotating the valve 94 throughout 180 as previously described. It will be noted, therefore, that this single convenient control located on the bottom side of the closer is arranged to perform the functions of controlling the latch bolt speed and of reversing the direction in which fluid resistance is encountered by the piston when it is desired to change the hand of operation of the closer. The remaining door closer control, the general speed control, is similarly conveniently arranged adjacent the latch bolt speed and reversal control on the bottom side of the closer body in a position from which all necessary adjustments can be accomplished easily when the closer is supported in normal overhead position on the door. The arrangement is such that suitable simplified instructions for adjustments may be fixed to the bottom side of the body closer as illustrated in Figure 2 so that they may be read without difliculty and the appropriate adjustments made with ease and convenience. The lower section of the closer housing 22 is readily detachable to expose the controls for adjustment and easily reassembled to prevent unauthorized tampering with the controls.

Smooth uniform movement of the piston through the fluid pressure chamber is assured by providing an expansion chamber 120 defined between the enlarged lower portion of the upper body portion 35 and the pressure chamber lid 3'! which chamber is in constant communication with the low pressure side of the piston during closing movement thereof. Air entrapped in the pressure chamber may escape to the expansion chamber and replacement fluid is supplied therefrom. Referring to Figure 11 it may be seen that the pressure chamber lid 37 is provided with a circular aperture 121 into which the notched portion 122 of the rotary unidirectional valve 94 extends. Two

slots

123 and 124 are cut into the under side of the pressure chamber lid to form channels between the mutually facing surfaces of the piston stop member and the lid 37. These channels communicate between the central aperture 121 and either side of the piston stop member, respectively. As the venting channels are provided in the top of the fluid pressure chamber and extend linearly to the expansion chamber complete venting of the fluid pressure chamber is assured. When the rotary valve 94 is positioned as indicated in Figures 11, 12 and 13, which is the setting corresponding to the hand of operation when the opening movement of the closer arm and the piston is in clockwise direction, the low pressure side of the piston during the closing movement thereof is in communication with the expansion chamber through the channel 124 and the portion of the central aperture 121 left open by the notched portion 122 of the valve 94. The solid portion of the valve 94 which extends into the aperture 121 of the lid is contoured to closely engage the walls of the aperture and to block flow of fluid from the channel 123 into the expansion chamber. It will be apparent from the construction illustrated in Figure 11 that reversal of the valve 94 to alter the hand of the closer will also reverse the valving action of the notched portion and again place the low pressure side of the piston during closing movement thereof in communication with the expansion chamber 120.

It should be noted that the construction of the valve 94 which enables the valve to perform this function does not alter or limit its efficacy as a means for reversing the direction of fluid resistance in changing the hand of the closer, or in controlling the latch bolt speed by varying the extent of registration of the ports 114 and 115.

It will be apparent that changing the hand of the closer to adapt it for use with a door hinged on the hand which would cause counter-clockwise rotation of the closer arm upon opening movement of the door requires shifting the initial, or door closed position, of the piston from that illustrated in solid lines in Figure to the dotted line position therein in which the piston abuts the lateral face 83 of the piston stop member. As the piston shaft 40 is limited to less than a full revolution by the piston and the piston stop member, it is necessary when changing the hand of the closer to change the initial position of the closer arm with respect to the face of the door to dispose the arm in a counterclockwise direction from the perpendicular to the face of the door, as contrasted with its clockwise disposition therefrom as, illustrated in Figure 2, as well as rotating the unidirection fluid flow valve 94 throughout 180 to reverse the direction of resistance to fluid flow through piston stop member 90 as previously described.

In keeping with the universal character of the closer re-positioning of the piston and the closer arm is accomplished without requiring the arm to be removed from the closer by external adjustments of the closer arm hub assembly illustrated in Figure 23. The hub assembly comprises a disc 125 provided with a central aperture configured to receive the notched end of the piston shaft 40 and to secure the disc against rotation relative to the shaft. The disc is provided with a lug 126 on its periphery which extends into the slotted portion 127 formed in the central aperture of the hub portion of the closer arm into which the disc is received, and which closely engages the disc along a portion of its circumference. The lug 126 normally abuts one or the other of the shoulders 128 or 129 provided by the ends of the slot 127, and when arranged in the solid line position illustrated in Figure 13 wherein the lug abuts the shoulder 128, closing movement of the closer in a counter-clockwise direction caused by the force applied to the closer arm through the pin 58 by the loaded spring mechanism is retarded according to the rate at which the piston with which the disc is rigidly connected, rotates in response to the particular force applied to the closer arm by the spring mechanism. The disc is provided with a radially disposed aperture 130 in which a locking member or detent 131 is positioned which is spring pressed outwardly by a light spring 132 into a recess 117 provided in the wall of the central aperture formed in the hub portion of the closer arm. When the pin 53 has been disengaged the locking member 131 is displaceable by hand pres sure and when it is desired to change the hand of the closer it may be easily dislodged by rotating the closer arm 33 in clockwise direction until the piston abuts the lateral face 83 of the piston stop member. Continuing the rotation of the closer arm after the disc which is rigidly connected with the piston is thus stopped, displaces the locking member 131 from the recess 132 and brings the lug 126 to bear against the shoulder 129 as indicated in dotted lines in Figure 23. When the closer arm has been re-positioned as described, the locking member 131 will engage in the recess 133 with sufiicient firmness to cause the disc 125 to rotate along with the closer arm during opening movement of the associated door as very little fluid resistance is encountered by the piston during the opening movement. It is apparent that the locking action between the disc and the arm which may be overcome by hand pressure can be obtained in various ways, for example, by supporting a friction disc, or other friction element, on the disc 125 which disc or element is arranged to bear against a suitable portion of the closer arm.

The casing arm 34 of the closer arm linkage is provided with a stiff helical type spring section 135 aflixed to the boss 136 of the mounting plate 137 which spring section provides a frictionless pivotal means about which the arm oscillates during the opening and closing movements of the door with which the door closer is associated. The spring is wound so that the adjacent coils are spaced apart a short distance relative to the diameter of the wire from which the spring is wound. Accordingly, the spring is subject to slight compression and acts to absorb shocks transmitted to the closer arm linkage when the door is moving toward its closed position. This arrangement is particularly effective and necessary where the speed settings on the closer cause a sharp change in the rate of closing movement of the associated door. The slight spacing between the turns of the spring also increases its flexibility and reduces the resistance to pivotal action which would exist in a conventional extension spring in which the adjacent turns are normally in contact with one another. A similarly constructed spring section 116' may be provided towards the other end of the arm as illustrated in Figure 22.

The casing arm may also comprise the section 136 which telescopes within the section 137 which is provided with a threaded opening which receives the correspondingly screw threaded extension 133 of the section 136; the overall length of the arm being adjustable by varying the extent to which the section 138 is screwed into the section 137. The section 137 is provided with a threaded boss 139 which is adapted to be screwed into the outer end of the spring section 135, the inner faces of the turns of the coil functioning in the same manner as the lands of a conventional threaded opening. A plate 146 is pivoted to the distal end of the section 136 and provided with a pin 141 (Figure 1) which extends downwardly into an aperture provided in the free end of the closer arm 33 as illustrated most clearly in Figure 1. It may be seen from Figure 1 that in order to juxtaposition the ends of the

arms

33 and 34, it is necessary to have the arm 34 inclined slightly downwardly. This downward disposition of the arm 34 is permitted by the coil spring 135, which, as previously mentioned, also acts as a pivot means and shock absorber. In order that the axis of the pin 141 be aligned with the axis of the aperture provided in the end of the arm 33, it is necessary that the plate 141) be turned slightly upwardly with respect to the longitudinal axis of the arm 34. This, of course, is permitted by the pivotal support of the plate 140 on the arm 34. A further means for obtaining the upward deflection of the end of the arm 34 so that the pin 141 will be properly aligned with the aperture in the end of the arm 33 is shown in Figure 22. In this latter construction, the spring 116' provided towards the distal end of the arm 34 permits the end of the arm carrying the pin 141 to be deflected upwardly sufficiently to permit alignment of the pin with the aperture provided in the end of the arm 33. Both of these arrangements permit pivotal action between the closer arm 33 and the casing arm 34 and permit the pivotal connection between the arms to be readily broken in the event it is desirable to readjust the length of the casing arm by screwing the section 136 further into or out of the section 137. The adjustment selected is positively retained by inserting the pin 141 into the aperture provided in the end of the closer arm which re-establishes the pivotal connection between the arms and locks the section 136 of the casing arm against further rotation.

Having thus described the invention, what is claimed as new and desired to be secured by Letter Patent is:

1. A door closer comprising in combination a coil spring, an abutment fixed to the inner end of said spring and an abutment fixed to the outer end of the spring, and mechanism for acting upon and moving either of said spring abutments along an arcuate path while maintaining the other such abutment stationary, to load the spring, said mechanism including an arm assembly and a base member assembled for relative rotation about a common axis one being adapted to be connected to a door and the other to a door frame, said arm assembly comprises a rotatably supported closer arm, two winding members rigidly fixed thereto, one said winding member arranged to act upon and move one of said spring abutments when the said arm is rotated in one direction, and the other said winding member arranged to act upon and move said 15 other such abutment when the said arm is rotated in the other direction.

2. A door closer as claimed in claim 1 in which the said one abutment is provided with winding catches spaced at different distances from said common axis, the one side winding member comprises arms of different lengths corresponding to the said different distance, respectively, to engage only one of the said catches, the other such abutment is provided with radially extending winding catches spaced at different distances along the said common axis, and the other said winding member is provided with protrusions at distances along said common axis, respectively, to engage only one of said radially extending winding catches.

3. A door closer embodying a spring member, a hychamber, a piston stop member fixedly positioned within the said chamber in operable association with said piston, said stop member having a cambered face engaging said piston, means inter-connecting the said piston with the said spring member to cause rotary movement of said piston as said spring is loaded by opening movement of the associated door or as the spring unloads to close the associated door, said stop member being provided with fluid passages from either side thereof to an intermediate aperture therein, a fluid passage extending from said cambered face of said stop member to said aperture, a fluid passage extending from one side to the other side of said piston, a fluid flow adjusting valve in said passage in said piston for governing the general speed of closing, a slot in the face of said piston which engages said cambered face positioned to register with a fluid passage extending from the face of said piston which engages said cambered face to govern the latch-bolt speed of closing, a rotary check valve positioned within the said aperture to govern the passage of all fluid passing through said stop memher, and means for rotating said valve within the aperture to selectively arrange said valve to pass fluid freely from the high pressure side to low pressure side of piston as the piston is caused to rotate by the spring loading movement of the associated door, and to block the flow of fluid from the high pressure side to low pressure side of piston as the piston is caused to rotate in the opposite direction by unloading of the spring, when said spring is loaded selectively from either one of two directions.

4. A door closer and check comprising a hydraulic mechanism, a spring member, and means operatively connecting said check mechanism and said spring member, said hydraulic check mechanism including a fluid pressure chamber, a wing piston rotatably supported therein, a piston stop member positioned in said chamber, a face of said stop member operatively engaging a face of said piston, fluid passages from either side of said piston stop member to an intermediate aperture therein, a rotary check valve positioned in said aperture, said piston being provided with a passage communicating from one side thereof to the other to pass fluid through said piston when said piston is caused to move by the unloading of said spring member, an adjustable valve positioned within said passage for regulating the rate of fluid transfer from one side of the piston to the other, the ends of said passage being arranged on said piston so as to be closed off, respectively, by the said stop member face as the piston approaches the limit of its movement in the respective direction, a latch bolt speed control slot provided in said piston face, a cooperating slot on said stop memher face arranged to register in part with said first named slot as the piston approaches the limits of its movement and said passage is closed off as aforesaid, a port in said stop member communicating between said piston stop member slot and the said aperture, and a further passageway in the said rotary valve located at one end for registration with said port and at its other end to communicate with the one of fluid passages in the stop member between the said aperture and the low pressure side of said piston, whereby the latch bolt speed of the door during closing movement may be regulated by adjustment of said rotary valve to vary the extent of registration between the said further passageway and the said port, and the hand of operation of the closer reversed by turning the said rotary valve to a greater degree than required to effect full range of adjustment of the latch bolt speed.

5. A door closer as claimed in claim 4 in which said adjustable valve for regulating the rate of fluid transfer from one side of the piston to the other comprises, a plug supported within an aperture in said piston formed concentrically with the axis of rotation of the said piston, said passage from one side of the piston to the other being formed in part by said aperture, and means extending through said pressure chamber adjustable axially with respect to the said plug, said means having a leading edge of reduced cross-section bearing against the lower portion of said plug, whereby the plug may be moved axially to restrict adjustably fluid flow through said piston passage, and the plug permitted to rotate with said piston without disturbing the setting of said adjustable means.

6. A door closer as claimed in claim 5 in which the walls of said pressure chamber comprise the lowermost section of said closer, said means for adjusting said rotary valve comprises a stem extending upwardly through the bottom of said chamber to engage said rotary valve, and said plug adjusting means comprises a second stem extending upwardly through the bottom of said pressure chamber to engage the said plug as aforesaid, whereby both the general speed and the latch bolt speed of the closer may be adjusted conveniently when the closer is supported in an overhead position.

7. A door closer as claimed in claim 4 wherein the said pressure chamber is cylindrical in form, the said piston comprises a rounded hub portion and a wing portion extending radially from one section thereofto closely engage the cylindrical wall of said chamber, the remaining section of the hub portion being the face of the piston which is operatively engaged by said stop member face, said latter face being formed complementary to said rounded hub portion for close engagement therewith.

8. A door closer comprising a fluid pressure chamber, an expansion chamber, a common wall forming the lid of the said pressure chamber and the bottom of the said expansion chamber, a piston stop member fixedly secured within the said pressure chamber, the upper surface of said stop member closely engaging the under surface of said common wall, a radial piston rotatably supported in said pressure chamber, said stop member being provided with passages from either side thereof to an intermediate aperture, a rotary unidirectional fluid flow valve positioned in said aperture to permit transit of fluid through said member from the high pressure side to the low pressure side of the piston during piston rotation in one direction and blocking fiuid flow through said stop member during piston rotation in the other direction, a second aperture provided in the said common wall to register with said intermediate aperture, slots provided in the undersurface of said common wall to form two channels between the mutually engaging faces of said common wall and said stop member, each of said channels communicating with said second aperture and, respectively,

with the pressure chamber on either side of said stop member, said rotary valve having an upper solid portion extending into said second aperture positioned to block off said second aperture from the channel communicating with the high pressure side of said piston during the piston rotation in said other direction, and an upper notched portion permitting communication through the other of said channels to said second aperture and expansion chamber from the low pressure side of said piston during said last named rotation of the said piston.

9. A door closer as claimed in claim 4 which com prises an expansion chamber, a common wall forming the lid of said pressure chamber and the bottom of said expansion chamber, the upper surface of said stop member closely engaging the under surface of said common wall, a second aperture provided in the said common wall to register with said intermediate aperture, slots provided in the under surface of said common wall to form two channels between the mutually engaging surface of said stop member and common wall, each of said channels communicating with said second aperture and, respectively, with the pressure chamber on either side of said stop member, said rotary valve having an upper solid portion extending into said second aperture positioned to block off said second aperture from the channel communicating with the high pressure side of said piston as said piston is caused to move in the said opposite direction by the unloading of said spring member, and an upper notched portion permitting communication through the other of said channels to said expansion chamber from the low pressure side of said piston during said last named movement of the said piston.

10. A door closer comprising a body, a shaft rotatably supported within the body, a radial piston affixed to one end of the said shaft, and a closer arm assembly aflixed to the other end thereof, a fluid pressure chamber formed in a portion of the said body, said piston being positioned within said chamber, a clock type spring, winding mechanism including the closer arm of said closer arm assembly for moving either end of said spring, means for holding the inner end of the spring against movement when the said spring is wound from its outer end by rotation of the arm in one direction, means for holding the outer end of spring against movement when the spring is wound from its inner end by rotation of the arm in the other direction, a piston stop member fixed within the chamber, a unidirectional fluid flow control valve within an aperture provided in said stop member that communicates with passages for conducting fluid from one side of said stop member to the other side thereof, said valve being rotatably positionable in one of two settings corresponding, respectively, with the direction from which said spring is to be wound to permit in either of said settings fluid in the said chamber to pass through said stop member freely as movement of the said arm causes the spring to be wound, and to block fluid flow through said stop member as the spring unwinds, said closer arm assembly comprising means for operably securing the said closer arm in one of two positions corresponding, respectively, with the setting of said valve, said means comprising a disc member secured to said rotatable shaft, a hub portion on said arm having a central aperture adapted to receive said disc in close engagement, said hub portion being provided with two spaced stop members, means on said disc arranged to engage said stop members to limit the relative rotary movement between said disc and said hub portion and to transmit rotary movement imparted to the hub portion to said disc member, a pressure displaceable spring pressed locking member positioned in a radially extending aperture in said disc member to normally protrude from the periphery of said disc into one of two depressions provided in the closely engaged face of said hub portion,.said depressions being positioned respectively to align with said locking member when said lug bears against one or the other of said stop members, whereby the hand of the closer may be reversed by changing the'said valve and closer arm, respectively, from one of their corresponding positions to the other.

11. A door closer of the type which includes a hydraulic mechanism for regulating the rate at which energy stored in a spring member associated with the closer is released, said closer comprising a closer arm'assembly, a fluid pressure chamber, a radial piston rotatably supported within said chamber, a rotatable shaft connecting said piston with said closer arm assembly, a piston stop member fixed within said chamber, valve means associated with said stop member for reversing the direction of hydraulic resistance to the said pistonduring its rotary movement between the limits defined by said stop member, said closer arm assembly comprising a disc member secured to said rotatabie shaft, a hub portion on said arm having a central aperture adapted to receive said disc in close engagement, said hub portion being provided with two spaced stop members, means on said disc ar ranged to engage said stop members to limit the relative rotary movement between said disc and said hub portion and to transmit rotary movement imparted to the hub portion to said disc member, a pressure displaceable spring pressed locking member positioned in a radially extending aperture provided in said disc member to normally protrude from the periphery of said disc into one of two depressions provided in the closely engaged face of said hub portion, said depressions being positioned, respectively, to align with said locking member when said lug bears against one or the other of said stop members, whereby the initial position of said piston with respect to the said piston stop member and the position of said arm with respect to the said piston may be changed to correspond with a reversed setting of said valve to reverse the hand of the closer by causing said closer arm lug to rotate from contact with one of said stop members into contact with the other of said stop members.

12. In a door closer of the type having a hydraulic mechanism for regulating the rate of return movement of a spring driven closer arm, said mechanism including a radial piston rotatably supported within a fluid pressure chamber and provided with a general speed control valve positioned within a passage in the piston for passing fluid from the high pressure side to the low pressure side of the piston, said passage being positioned therein to be restricted at one end by a piston stop member fixed within the said chamber as the piston approaches either of its extreme positions in which it bears, respectively, against either side of the stop member so as to permit an associated latch bolt speed control mechanism to regulate the latter portion of return movement of the piston; a means separate from said latch bolt speed control mechanism and operable, when the said fluid passage through the piston is blocked off as aforesaid during the initial portion of the return movement of the piston,- to pass fluid from the high pressure side of the piston to the low pressure side thereof through said general speed control valve, said means comprising a port communicating at one end with said fluid passage in the said piston between the restricted terminus thereof and the said general speed control valve, and communicating at the other end with the low pressure side of said piston, whereby the general speed control mechanism alone regulates the closing speed from the instant the closing movement starts until the latch-bolt speed control mechanism takes over.

13. In a door closer of the type having a hydraulic mechanism for regulating the rate of return movement of a spring driven closer arm, said mechanism including a radial piston rotatably supported within a fluid pressure chamber and provided with a general speed control valve positioned within a passage in the piston for passing fluid from the high pressure side to the low pressure side of the piston, said passage being positioned therein to be blocked off at one end by a piston stop member fixed within the said chamber as the piston approaches either of its extreme positions in which it bears, respectively, against either side of the stop member so as to permit an associated latch bolt speed control mechanism to regulate the latter portion of return movement of the piston; a means separate from said latch-bolt speed control mechanism and operable, when the said fluid passage through the piston is blocked off as aforesaid during the initial portion of the return movement of the piston, to pass fluid from the high pressure side of the piston to the low pressure side thereof through said general speed control valve, said means comprising two ports provided in said piston communicating at one end with said fluid passage on either side of said general speed control valve, respectively, and at their other ends with the spaces between either side of the piston and the stop member, respectively, whereby the general speed mechanism alone regulates the closing speed from the instant the closing movement starts until the latch-bolt speed control mechanism takes over.

14. In a door closer of the type having a hydraulic mechanism for regulating the rate of return movement of a spring driven closer arm, said mechanism including a radial piston rotatably supported within a fluid pressure chamber and provided with a general speed control valve positioned within a passage in the piston for passing fiuid from the high pressure side to the low pressure side of the piston, said passage being positioned therein to be blocked off at one end by a piston stop member fixed within the said chamber as the piston approaches either of its extreme positions in which it bears, respectively, against either side of the stop member so as to permit an associated latch bolt speed control mechanism to regulate the latter portion of return movement of the piston; a means separate from said latch-bolt speed control mechanism and operable when the said fluid passage through the piston is blocked off as aforesaid during the initial portion of the return movement of the piston to pass fluid from the high pressure side of the piston to the low pressure side thereof through said general speed control valve, said means comprising a slot provided in said piston stop member positioned to register with the end of said fluid passage blocked off by said piston stop member, and a passage provided in said stop member communicating between said slot and the low pressure side of the said stop member whereby the general speed control mechanism alone regulates the closing speed from the instant the closing movement starts until the latch-bolt speed control mechanism takes over.

15. A door closer as claimed in claim 14 in which said passage provided in the said piston stop member communicates with both sides of said piston stop member; and which comprises a rotatable valve selectively positionable in said passage to pass fluid to one side only of said stop member.

16. A door closer comprising a body portion, a clocktype spring supported thereon, a closer arm pivotally supported on said body portion, means associated with said spring and closer arms which permits the spring to be wound from its outer or inner end by rotation of said arm in one or in the other direction, respectively, said means comprising winding catches fixed, respectively, to each of the two ends of said spring, a first winding member rigidly connected with said closer arm and adapted to engage one side of one of said catches when said arm is rotated in a first direction, a second winding member rigidly connected to said closer arm and adapted to engage one side of the other of said catches when said arm is rotated in said other direction, retaining means fixed to each of the two ends of said spring, stop members fixed to the body portion of said closer and positioned to engage, respectively, oppositely facing sides of the respective retaining means, said winding catches being positioned adjacent one edge of said spring and said retaining means adjacent the opposite edge thereof whereby the free end of the said spring will be held against movement when the spring is wound from its other end by movement of said closer arm in either the one or the other direction.

17. A door closer as claimed in claim 16 which comprises means for adjusting the initial tension of said spring, said means comprising an adjusting ring encircling said body portion and rotatably supported thereon immediately adjacent one of said retaining means, one of said stop members being fixed to said ring and positioned to engage said retaining means when said ring is rotated,

removable locking means engaging said ring and said body portion to hold the stop member fixed to said ring and the retaining means engaged by said stop member in a selected initial position.

18. A door closer as claimed in claim 16 which cornprises means for adjusting the initial tension or" said spring, said means comprising an arcuate member movably supported on said body portion immediately adjacent one of said retaining means, one of said stop members being fixed to said arcuate member and positioned to engage said one retaining means, when said arcuate member is moved in one direction on said body portion, removable locking means engaging said arcuate member and said body portion to lock the said stop member and the retaiuing means engaged thereby in a selected initial position, whereby a selected initial tension may be applied to said spring.

19. A door closer comprising a closer body, a rotatable shaft journaled centrally in said body, a closer arm, a universal acting clock-type spring mechanism, means connecting the spring of said mechanism to said closer arm to transmit movement of said arm to said spring to load the spring, said mechanism comprising said spring disposed around said shaft, an inner annuiar spring casing disposed within the spring and around said shaft, the inner end of said spring being affixed thereto, an outer annuiar sp g casing disposed around the said spring, the outer end of said spring eing affixed thereto, two winding catches fixed to said outer casing at different distances from said shaft, a first winding member rigidly connected with said arm, said member having radially extending arms of different lengths adapted and positioned to engage one side of the respective said winding catcl es disposed at different distances from said shaft. two winding catches fixed to the inner surface of said annular inner casing at different distances along the axis thereof, an annular winding member having radially extending protrusions at different distances along its axis each positioned to engage one side of the respective winding catches disposed at different distances along the axis of said inner casing.

20. A door closer comprising a closer body, a rotata lc shaft journaled centrally in said body, a closer arm, a universal acting clock-type spring mechanism, means connecting the spring of said mechanism to said closer arm to transmit movement of said arm to said spring to wind the spring, said mechanism comprising said spring disposed around said shaft, an inner annular spring casing disposed within the spring and around said shaft, the inner end of said spring being afiixed thereto, an outer annular spring casing disposed around the said spring, the outer end of said spring being afiixed thereto, two diametrically disposed winding catches fixed to said outer casing at different distances from said shaft, a first winding member rigidly connected with said arm, said member having radially extending arms of different lengths adapted and positioned to engage one side of the rcspective said winding catches disposed at different distances from said shaft, two diametrically disposed winding catches fixed to the inner surface of said annular inner casing at different distances along the axis thereof, an annular winding member having radially extendin protrusions at difierent distances along its axis each positioned to engage one side of the respective winding catches disposed at dilierent distances along the axis of said inner casing, retaining means fixed to each of the two ends of said spring, stop members fixed to the body portion of said closer and positioned to engage, respectively, oppositely facing sides of the respective retaining means, whereby the free end of the said spring will be held against movement when the spring is wound from its other end by movement of said closer arm in either the one or the other direction.

21. A door closer as claimed in claim 2-) which comprises means for adjusting the initial tension of said spring, said means comprising an adjusting ring encircling said body portion and rotatably supported thereon immedi ately adjacent one of said retaining means, one of said stop members being fixed to said ring and positioned to engage said retaining means when said ring is rotated, removable locking means engaging said ring and said body portion to hold the stop member fixed to said ring and the retaining means engaged by said stop member in a selected initial position.

22. A door closer as claimed in claim 20 which comprises means for adjusting the initial tension of said spring, said means comprising an arcuate member movably supported on said body portion immediately adjacent one of said retaining means, one of said stop members being fixed to said arcuate member and positioned to engage said one retaining means when said arcuate member is moved in one direction on said body portion, removable locking means engaging said arcuate member and said body portion to lock the said stop member and the retaining means engaged thereby in a selected initial position, whereby a selected initial tension may be applied to said spring.

23. A door closer arm linkage comprising a lever pivotally supported on the closer, and a second lever connected at one end to the free end of said first lever and adapted to be fixed to a door or door casing at its other end, one section in the length of said second lever consisting of a coil spring fixed at each end to the adjacent section of said second lever, the adjacent coils thereof being normally spaced apart, whereby said coil spring permits the outer end of said second lever to pivot and be displaced relative to the fixed end thereof, and absorbs shocks transmitted to the linkage.

24. A door closer arm assembly adapted for a universal radial piston type door closer comprising a disc member supported on one end of a rotatable shaft to which said piston is affixed, a closer arm having a hub portion provided with a central aperture adapted to receive said disc in close engagement, said hub portion being provided with two spaced stop members, a lug onsaid disc arranged to engage said stop member to limit the relative rotary movement between said disc and hub portion, and to transmit rotary movement imparted to said hub portion to said disc member, a pressure displaceabie spring pressed locking member positioned in a radially extending aperture in said disc member to normally protrude from the periphery of said disc into one of two depressions provided in the closely engaged face of said hub portion, said depressions being positioned respectively to align with said locking member when said lug bears against one or the other of said stop members.

25. A door closer embodying a spring member, a by draulic mechanism for regulating the rate at which energy stored in the spring member is applied to close a door with which the closer is associated, a fluid pressure chamber, a radial piston rotatably supported within the said chamber, a piston stop member positioned within said chamber in operable association with said piston, said stop member having a cambered face engaging said piston, means interconnecting the said piston with the said spring member to cause rotary movement of said piston as said spring is loaded by opening movement of the associated door or as the spring unloads to close the associated door, said stop member being provided with fluid passages from either side thereof to an intermediate aperture therein, a fluid passage extending from said cambered face of 'said stop member to said aperture, a fluid passage extending from one side to the other side of said piston, a fluid flow adjusting valve in said passage in said piston and governing the general speed of closing, a slot in the face of said piston which engages said cambered face positioned to register with the fluid passage extending from the face of said piston which engages said cambered face to control the latch-bolt speed of c1osing,.a rotary check valve positioned within-the said aperture, and means for rotating said valve within the aperture to selectively arrange said valve to pass fluid freely from the high pressure side to low pressure side of piston as the piston is caused to rotate by the spring loading movement of the associated door, and to block the flow of fluid from the high pressure side to low pressure side of piston as the piston is caused to rotate in the opposite direction by unloading of the spring, when said spring is loaded selectively from either one of two directions.

26. A door closer of the type which includes a hydraulic mechanism for regulating the rate at which energy stored in a spring member associated with the closer is released, said closer comprising a closer arm assembly, a fluid pressure chamber, a radial piston rotatably supported within said chamber, a rotatable shaft connecting said piston with said closer arm assembly, a piston stop member within said chamber, valve means associated with said stop member for reversing the direction of hydraulic resistance to the said piston during its rotary movement between the limits defined by said stop member, said closer arm assembly comprising a disc member secured to said rotatable shaft, a hub portion on said arm having a central aperture adapted to receive said disc in close engagement, said hub portion being provided with two spaced stop members, a lug on said disc arranged to engage said stop members to limit the relative rotary movement between said disc and said hub portion and to transmit rotary movement imparted to the hub portion to said disc member, a pressure displaceable spring pressed locking member positioned in a radially extending aperture provided in said disc member to normally protrude from the periphery of said disc into one of two depressions provided in the closely engaged face of said hub portion, said depressions being positioned, respectively, to align with said locking member when said lug bears against one or the other of said stop members, whereby the initial position of said piston with respect to the said piston stop member and the position of said arm with respect to the said piston may be changed to correspond with a reversed setting of said valve to reverse the hand of the closer by causing said closer arm lug to rotate from contact with one of said stop members into contact with the other of said stop members.

27. A door closer arm assembly adapted for a universal radial piston type door closer comprising a friction member supported on one end of a rotatable shaft to which said piston is aflixed, a closer arm having a hub portion provided with a central aperture adapted to receive said shaft, said hub portion being provided with two spaced stop members, a lug on said shaft arranged to engage said stop members to limit the relative rotary movement be tween said shaft and hub portion, said friction member being arranged to displaceably engage said hub portion.

28. A door closer as claimed in claim 20 which comprises means for adjusting the initial tension of said spring, said means comprising an adjusting ring encircling said body portion and rotatably supported thereon immediately adjacent one of said retaining means, one of said stop members being fixed to said ring and positioned to engage said retaining means when said ring is rotated, removable locking means engaging said ring and said body portion to hold the stop member fixed to said ring and the retaining means engaged by said stop memher in a selected initial position, and means removably engaging one of said winding members and said closer arrn whereby the winding member may be repositioned with respect to the winding catch enga ed thereby without repositioning said closer arm.

29. A door closer as claimed in claim 28 in which said means removably engaging one of said winding members and said closer arm is freely supported on said rotatable shaft and exposed to permit further external adjustments of said spring whenthe said closer is fully assembled.

30. A door closer as claimed in claim 20 which comprises means for adjusting the initial tension of said spring, said means comprising an arcuate member movably supported on said body portion immediately adjacent one of said retaining means, one of said stop mem bers being fixed to said arcuate member and positioned to engage said one retaining means when said arcuate member is moved in one direction on said body portion, removable locking means engaging said arcuate member and said body portion to lock the said stop member and the retaining means engaged thereby in a selected initial position, whereby a selected initial tension may be applied to said spring, and means removably engaging one of said winding members and said closer arm whereby the winding member may be repositioned with respect to the winding catch engaged thereby without repositioning said closer arm.

31. A door closer as claimed in claim 30 in which said means removably engaging one of said winding members and said closer arm is freely supported on said rotatable shaft and exposed to permit further external adjustments of said spring when the said closer is fully assembled.

32. A door check and closer comprising a hydraulic check mechanism, a coil spring, means operatively eonnecting said hydraulic check mechanism and said coil spring, said means including a rotatable piston shaft extending from said check mechanism, said coil spring encircling said shaft and being substantially coaxial there with, and means located at the edge of said coil spring remote from said check mechanism for winding said coil spring, selectively, from its inner or outer end while retaining the other end stationary, said last named means comprising two winding members supported on said shaft and fixed to rotate therewith, an abutment at each end of said spring, one of said winding members being positioned to act upon and move one of said spring abutments when said shaft is rotated in one direction, and the other said winding members being positioned to act upon and move said other abutment when said shaft is rotated in the other direction.

33. A door check and closer comprising a hydraulic check mechanism, a coil spring, means operatively connecting said hydraulic check mechanism and said coil spring, said means including a rotatable piston shaft extending from said check mechanism, said coil spring encircling said shaft and being substantially coaxial therewith, and means located at the edge of said coil spring remote from said check mechanism for winding said coil spring, selectively, from its inner or outer end while retaining the other end stationary, said last named means comprising a winding member supported on said shaft and fixed to rotate therewith, a set of spring abutmcnts fixed to one end of said spring and offset from one another longitudinally of said shaft, a set of spring abutments fixed to the other end of said spring and otfset radially of said shaft, said winding member being arranged and positioned to act upon and move one set of abutments when said shaft is rotated in one direction and to act upon and move the other set of abutments when said shaft is rotated in the other direction.

34. A door closer embodying a spring member, a hydraulic check mechanism for regulating the rate at which energy stored in the spring member is applied to close a door with which the closer is associated, a fluid chamber, a radial piston rotatably supported within the said fluid chamber, a piston stop member positioned within the said chamber in operative association with said piston, means interconnecting the said piston with the said spring member to cause rotary movement of said piston as the spring is loaded by opening movement of the associated door or as the spring unloads to close the associated door, a passage provided in said piston from one side to the other thereof, a general speed control valve positioned in said passage to regulate the flow of fluids therethrough, a separate latch-bolt speed control mechanism comprising a slot provided in the face of said piston and a port in said stop member positioned to register with said slot when the piston approaches a limit of 24 its movement, said port communicating with the low pressure side of said piston.

35. A door closer arm linkage comprising a lever pivotally supported on the closer, and a second lever connected at one end to the free end of said first lever and adapted to be fitted to a door or door casing at its other end, one section in the length of said second lever consisting of a coil spring, a second section of said second lever being provided with threads at its one end and joined with said coil spring section by threaded engagement between the threaded portion thereof and the inner surface of said coil spring, the adjacent coils of said spring being normally spaced apart, whereby said coil spring permits the outer end of said second lever to pivot and be displaced relative to the fixed end thereof, and absorbs shocks transmitted to the linkage.

36. A door closer comprising a body portion, a clocl type spring supported thereon, a closer arm pivotally supported on said body portion, means associated with said spring and closer arms which permits the spring to be wound from its outer or inner end by rotation of said arm in one or in the other direction, respectively, said means comprising winding catches fixed, respectively, to each of the two ends of said spring, a first winding member rigidly connected with said closer arm and adapted to engage one side of one of said catches when said arm is rotated in a first direction, a second winding member rigidly connected to said closer arm and adapted to engage one side of the other of said catches when said arm is rotated in said other direction, retaining means fixed to each of the two ends of said spring, stop mem bers fixed to the body portion of said closer and positioned to engage, respectively, oppositely facing sides of the respective retaining means, said winding catches being positioned adjacent one edge of said spring and said retaining means adjacent the opposite edge thereof, whereby the free end of the said spring will be held against movement when the spring is wound from its other end by movement of said closer arm in either the one or the other direction, and a radial piston type hydraulic checking mechanism, the piston member of said last named mechanism being connected operatively with said closer arm.

37. A door closer arm linkage comprising a lever pivotally supported on the closer, and a second lever connected at one end to the free end of said first lever and adapted to be fixed to a door or door casing at its other end, one section in the length of said second lever consisting of a coil spring, the adjacent coils thereof being normally spaced apart. whereby said coil spring permits the outer end of said second lever to pivot and be displaced relative to the fixed end thereof and absorbs shocks transmitted to the linkage, a second section of said second lever consisting of a flexible element located towards the said one end thereof, and said coil spring section being located towards the said other end of said second lever.

References Cited in the file of this patent UNITED STATES PATENTS