US3861205A

US3861205A - Machine for testing toe and heel clamps on ski bindings

Info

Publication number: US3861205A
Application number: US387689A
Authority: US
Inventors: Max Frey; Max A Eberle
Original assignee: Hydron Corp
Current assignee: Hydron Corp
Priority date: 1973-08-13
Filing date: 1973-08-13
Publication date: 1975-01-21
Anticipated expiration: 1992-01-21

Abstract

A ski with a boot releasably secured thereon by toe and heel clamps is mounted on rests on the machine and secured by a pair of hydraulic clamps. Transverse toe check and heel check beams are slidably mounted for adjustment according to the position and size of the boot. The toe check beam is equipped with a pair of opposed hydraulically operated thrust arms for applying lateral forces to the sole of the boot alternately in opposite directions sufficient to effect release of the boot from its toe clamp on the ski. The heel check beam is equipped with a sling strap which may be raised under the heel of the boot by hydraulic actuators to effect release of the heel clamp on the ski. These hydraulic devices are actuated by a pump under pushbutton control. A maximum reading fluid pressure gauge registers the force necessary to release the boot from the toe clamp and heel clamp.

Description

[451 Jan. 21, 1975 United States Patent [191 Frey et al.

[ MACHINE FOR TESTING TOE AND HEEL Primary Examiner-Charles A. Ruehl CLAMPS 0N SKI BINDINGS Attorney, Agent, or FirmLee R. Schermerhorn [75] Inventors: Max Frey, Portland, Oreg.; Max A.

Eberle, Upper Saddle River, NJ.

Hydron Corporation, Portland, Oreg.

Assigneez A ski with a boot releasably secured thereon by toe and heel clamps is mounted on rests on the machine and secured by a pair of hydraulic clamps. Transverse toe check and heel check beams are slidably mounted [22] Filed: Aug. 13, 1973 [21] APPL No; 387,689 for adjustment according to the position and size of the boot. The toe check beam is equipped with a pair of opposed hydraulically operated thrust arms for ap- U'S. A lateral forces to the Sole of the boot uhcrnut ly Int. Cl. in pposite directions sufficient to effect release of [he [58] Field of 73/133 A boot f its toe Clamp on the 1 The heel Check beam is equipped with a sling strap which may be raised under the heel of the boot by hydraulic actua- References Cited UNITED STATES PATENTS tors to effect release of the heel clamp on the ski. These hydraulic devices are actuated by a pump under FOREIGN PATENTS OR APPLICATIONS 3,621,712 Beyl pushbutton control. A maximum reading fluid pressure gauge registers the force necessary to release the boot from the toe clamp and heel clamp.

12 Claims. 16 Drawing Figures 8/1971 Germany......................,... 11/1965 Switzerland.............

PATENTEDJANZI ms SHEET 1 BF 7 MACHINE FOR TESTING TOE AND HEEL CLAMPS ON SKI BINDINGS BACKGROUND OF THE INVENTION This invention relates to a machine for testing and calibrating toe and heel clamps on ski bindings.

Heretofore these tests have usually been made by separate manually operated portable devices which are subject to human error and are not very accurate. Such devices are not well suited for testing or calibrating a large number of ski bindings quickly and with a high degree of uniformity and accuracy.

Objects of the invention are, therefore, to provide a single machine for testing and calibrating toe and heel clamps on skis, to provide a machine of the type described which is power operated and largely eliminates human error, to provide a machine which will perform all the necessary tests with the ski clamped in a fixed position in the machine, to provide a machine having improved features that make it economical to manufacture, to provide an improved hydraulic control valve unit, to provide an attachment for applying a downward force against the toe of the boot during the toe check tests, and to provide a machine of the type described which is suitable for use by ski or binding manufacturers having large numbers of ski bindings to test and calibrate in an efficient manner.

SUMMARY OF THE INVENTION In the present machine, a ski carrying a ski boot is clamped in testing position by a pair of hydraulic clamps. Transverse toe check and heel check beams are adjustable to the position and size of the boot. The toe check beam carries a pair of opposed hydraulic thrust arms arranged to apply sufficient lateral force right and left to the sole of the boot to effect release of the toe clamp on the ski. The heel check beam carries a hydraulically actuated sling strap which is lifted under the heel of the boot to effect release of the heel clamp on the ski. All of these tests are performed with the ski clamped in fixed position.

An attachment is provided for applying a downward force on the toe of the boot during the toe check tests.

The hydraulic system is energized by a pump under pushbutton control. A maximum reading fluid pressure gauge registers the force required to release the boot from the toe and heel clamps on the ski. The various operations are performed mechanically to minimize operator error and insure consistently accurate readings in an efficient manner.

The foregoing and other objects and advantages will become apparent and the invention will be better understood from the following description of the preferred embodiment illustrated in the accompanying drawings. Various changes may be made, however, in

' the details of construction and arrangement of parts and certain features may be used without others. All such modifications within the scope of the appended claims are included in the invention.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a machine embodying the invention;

FIG. 2 is a view on the line 2-2 in FIG. 1;

FIG. 3 is a view on the line 33 in FIG. 1;

FIG. 4 is a view on the line 4-4 in FIG. 1;

FIG. 5 is a view on the line 5-5 in FIG. 4;

FIG. 6 is a view on the line 6-6 in FIG. 1, showing one of the toe checks in retracted position;

FIG. 7 is a view similar to FIG. 6, showing the toe check in operative position; 1

FIG. 8 is a view on the line 8-8 in FIG. 6;

FIG. 9 is a schematic diagram of the hydraulic system;

FIG. 10 is a view on the line 1010 in FIG. 1;

FIG. 11 is a view on the line 11-11 in FIG. 1;

FIG. 12 is a view on the line l2l2 in FIG. 1;

FIG. 13 is a view on the line 13-l3 in FIG. 1;

FIG. 14 is an elevation view with parts broken away, showing an attachment for applying a downward force on the toe of the boot;

FIG. 15 is a view on the line l5l5 in FIG. 14; and

FIG. 16 is an elevation view of the attachment at right angles to FIG. 14.

DESCRIPTION OF THE PREFERRED EMBODIMENT General Description The general features of the machine will first be described with reference to FIG. 1. A frame 10 has a pair of

horizontal end panels

11 and 12 equipped with ski rests 13 to support the bottom of a ski S. Each rest 13 comprises a V-shaped metal plate 14 carrying a pair of rubber pads 15. The V-shape of these rests provides lateral stability so that the ski is not dislodged under the lateral forces applied to the ski boot B during the testing or calibration of the bindings. The ski is firmly clamped on rests 13 by a pair of hydraulic clamps 20.

The ski bindings are omitted in the drawings for clarity of illustration. It is understood that the heel of boot B is secured to ski S by a conventional type of heel clamp on the ski which is releasable by a predetermined uplift force applied to the heel of the boot. The boot is also secured by a toe clamp on the ski which is releasable by the application of a predetermined horizontal or twisting force applied in either right or left directions to the toe of the boot. The purpose of the present machine is to test or calibrate the uplift force required to release the heel of the boot from its heel clamp and to test or calibrate the horizontal force required to release the toe of the boot from its toe clamp in either right or left directions. The heel and toe clamps on the ski must be accurately adjusted according to the strength and skill of the skier as is well understood in the art.

The present machine is designed to perform these tests or calibrations rapidly and efficiently for the manufacturers of skis and ski bindings and for the operators of skiing facilities where conventional equipment is too slow and uncertain for the purpose. The safety of the skier depends on having his bindings properly adjusted so that the heel and toe clamps will not release too easily or will not require too great a force for release.

A heel check beam 21 is mounted for sliding movement on a pair of longitudinal ways 22. A control knob 23 adjusts the position of beam 21 to place an uplift sling strap 25 under the heel of the boot, between the heel and the ski. Sling 25 is lifted by hydraulic actuators which apply gradually increasing force until the boot is released from its heel binding.

In a similar manner, a toe check beam 26 is also mounted for sliding movement on the longitudinal ways 22. The position of this beam is adjusted by control knob 27 to place a pair of opposed

lateral thrust arms

30 and 31 in predetermined position adjacent the toe of the boot. Arm 30 may be hydraulically actuated toward the right and arm 31 may be hydraulically actuated toward the left to release the boot laterally from its toe binding on the ski. Adjusting

knobs

23 and 27 thus permit accommodation to different sizes of ski boots and to the position of the boot on the machine so that the boot and ski do not have to be accurately positioned before the clamps are actuated.

Pushbuttons in a control panel 35 start a pump to pressure the hydraulic system, actuate hydraulic clamps 20, energize the hydraulic actuators for sling and thrust arms and 31, and release the fluid pressure from the hydraulic actuators and pressure gauge 36.

Ski Clamps The two clamps 20 are of identical construction as shown in FIG. 2. Each clamp 20 comprises an L-shaped clamp arm having an upright portion and a transverse portion 41, each formed of sheet metal in channel shape. Thus, upright portion 40 has two

parallel flanges

42 and 43 bent from opposite sides of an interconnecting web portion 44. The two

channel members

40 and 41 are connected together by a pair of roll pins 45 having a press fit in holes in the flanges. The outer end of channel member 41 is equipped with a plastic shoe 46 to bear against the top of the ski.

Clamp arm 20 is pivotally mounted on a roll pin 47, the opposite ends of which have a press fit in holes in a pair of spaced parallel vertical plates 48 depending from top panel 11. The clamp arm is biased toward its retracted position, shown in broken lines, by a tension spring 50, one end of which is connected to a roll pin 51 in the clamp arm and the other end of which is connected to a roll pin 52 spanning the two vertical plates 48. The clamp arm is moved to clamping position, shown in solid lines in FIG. 2, by a hydraulic actuator 55A.

Hydraulic actuator 55A comprises a diaphragm chamber 56, a guide cylinder 57 and a piston 58 which is slidable in cylinder 57 and extended hy hydraulic pressure beind a diaphragm in diaphragm chamber 56. The outer end of piston 58 is equipped with a Teflon wafer 59 which bears against a roll pin 60 mounted in the

flanges

42, 43 of channel arm portion 40.

Diaphragm chamber 56 is formed with two parallel shoulders 61 which seat on a pair of roll pins 62 spanning the two vertical plates 48. The end of the diaphragm chamber has an external connection 63 for a hydraulic line. The axis of piston 58 is tangential to the arcuate path of movement of pin 60 at the mid point of its normal travel. This makes it unnecessary to provide a pivotal mounting for diaphragm chamber 56. The slight shift of position of pin 60 on wafer 59 is accommodated by the resilience of the plastic.

Piston 58 is retained in its guide cylinder 57 by retracting spring and in the same manner the diaphragm chamber is held seated on pins 62 without any positive fastening or connection. If clamp arm 20 is held in its clamped position shown in solid lines, the hydraulic actuator A may be removed by merely forcing the piston 58 into cylinder 57 and then lifting the unit 55A bodily away from pins 62. Pins 62 provide an abutment type of support which is effective as long as pin bears against the end of the piston. This mounting of the hydraulic actuator is employed throughout the machine, greatly simplifying assembly in manufacture and disassembly for service or inspection.

Heel Check FIG. 3 shows the right side of the heel check device on transverse beam 21. A channel-shaped arm 65 is pivotally mounted on a roll pin 66 which is supported at its ends in holes in a pair of spaced apart vertical plates 67 which are attached to the top of beam 2] by screw 68. Arm 65 is biased downward by a tension spring 70 connected at its upper end to a roll pin 71 spanning the flanges of channel arm 65 and anchored at its lower end to a roll pin 72 mounted in the pair of plates 67. Arm 65 may be lifted by a hydraulic actuator 558 which is mounted as described in connection with hydraulic actuator 55A in FIG. 2. Shoulders 61 on diaphragm chamber 56 seat on a pair of roll pins 62 spanning the upstanding plate 67 and plastic wafer 59 on piston 58 bears against a roll pin 73 bridging the flanges of channel arm 65.

One end of sling strap 25 is anchored on a roll pin 75 in the end of arm 65 and the opposite end of the sling strap is similarly anchored to an opposed corresponding arm 65 on the left side of the machine as shown in FIG. 1. One end of the sling strap may be detachable from its lifting pin 75 for convenience in passing the strap under the boot heel. The uplift device on the left side is the same as that shown on the right side in FIG. 3.

When hydraulic pressure is introduced into diaphragm chambers 56 on the left and right sides of the machine, the two pistons 58 raise the arms 65 toward broken line position gradually lifting the heel of boot B until the boot is released from its heel clamp on the ski. The maximum hydraulic pressure developed in diaphragm chambers 56 at the instant of release measures the uplift force applied to the heel of the boot. This pressure is registered on gauge 36 in FIG. 1.

Upon release of the boot from its heel clamp, a pin 76 on arm 65 opens a normally closed switch 77 to stop the motor for the hydraulic pump which energizes diaphragm chamber 56. The upward movement of arm 65 is limited by the engagement of the ends of pin 73 with top flanges 78 on plates 67.

The geometry of the movement in FIG. 3 is arranged to provide a substantially constant mechanical advantage in applying an uplift force to the heel of the boot. The decrease in mechanical advantage as arm 65 changes its angular position in rising is approximately compensated by the increasing mechanical advantage of sling strap 25 as it moves closer to a vertical position. Thus, an essentially linear relationship exists between the uplift force applied to the heel and the hydraulic pressure to which pressure gauge 36 responds whereby the gauge scale may be marked in pounds of applied force.

The uplift force applied by sling strap 25 tends to lift the center of the ski and deflect its ends downward. This distortion is resisted by the additional rests 13 in FIG. 1 beyond the clamps 20.

As described in connection with FIG. 2, retracting spring 70 retains piston 58 in guide cylinder 57 and holds the entire actuator unit 55B seated on roll pins 62 without any positive fastening connection. In assembling the machine, hydraulic actuator 55B is installed by raising the arm 65 and merely placing the hydraulic actuator is installed by raising the arm 65 and merely placing the hydraulic actuator in position on its supporting pins 62. Removal of hydraulic actuator 55B for service or inspection is accomplished by merely raising arm 65 and lifting the hydraulic actuator off pins 62. The axis of piston 58 is tangential to the arcuate path of movement of pin 73 at the mid point in the movement as explained in connection with FIG. 2.

The mounting and adjustment of beam 21 are shown in FIGS. 4 and 5. Beam 21 is of channel shape having a top web 80 with depending side flanges 81. Grooved Teflon rings 82 are mounted in holes 83 in the side flanges 81 at opposite ends of the beam. Rings 82 serve as bearings to support the beam for sliding movement on the ways 22 which comprise a pair of stationary metal tubes supported at their opposite ends in the frame of the machine.

The left end of beam 21 is provided with a rack 85 which is engaged by a pinion 86 on a shaft 87. Shaft 87 is mounted in a bearing 88 on frame 10 and is equipped with the knob 23 for moving the beam to position sling strap 25 under the heel of the boot after the ski has been clamped by clamps 20.

Toe Check FIGS. 6, 7 and 8 illustrate one of the toe check mechanisms. These mechanisms are mounted on a beam 26 which is slidable on the ways 22 and adjustable longitudinally of the machine by knob 27 as described in connection with FIG. 4 with respect to the knob 23 and beam 21. Each

thrust arm

30 and 31 carries a plastic shoe 90 on its free end to bear against the side of the boot sole adjacent the toe clamp. Adjusting knob 27 accomplishes this relationship after the ski has been secured by clamps 20.

The inner end of arm 30 is pivotally mounted on a roll pin 91 in a rocker frame 92. The elevation of shoe 90 is adjustable by a screw 93 to accommodate different thicknesses of skis and boot soles, this range of adjustment being represented by the arrow 94 in FIG. 7. This adjustment is accomplished by a nut 95 on screw 93 which has a trunnion pin 96 journaled in holes in the arm 30. Screw 93 is journaled for rotation in a hole in a bottom plate 97 in rocker frame 92.

Rocker frame 92 is pivoted for rotative movement on pin 91 which is supported in a slide 101. Rocker frame 92 is biased clockwise on its supporting pin 91 by a pair of tension springs 102 connected at one end to a pin 103 in the rocker frame and anchored at its other end on a pin 104 in slide 101. The clockwise rotation of rocker frame 92 is limited by a stop screw 105 in slide 101 which engages a roll pin 106 in the rocker frame. Slide 101 is supported for a sliding movement by four horizontal rollers 110 and four vertical rollers 111 which travel in guide tracks 112, 113 on the beam 26.

Rocker frame 92 and slide 101 are shifted by an arm 130 which is pivotally mounted at its lower end on a roll pin 131 which is supported at its opposite ends in two spaced apart vertical plates 132 within the beam 26. A pin 100 in rocker frame 92 extends through a slot 133 in the upper end of arm 130. Arm 130 is biased clockwise by a pair of retracting springs 135 which are connected to a roll pin 136 in the arm 130 and to a roll pin 137 in the plates 132.

Arm 130 is actuated counterclockwise to operative position by a hydraulic actuator 55C which has shoulders 61 seated on a pair of roll pins 138 in the plates 132 similar to the mounting arrangement described in connection with FIG. 2. Piston 58 is faced with a Teflon disc 59 to bear against a roll pin 140 in the arm 130. Piston 58 moves in a straight line tangent to the arc of travel of pin 140 at the mid point of the arc, the resilience of the plastic accommodating the slight relative movement between the pin and the piston. Springs 135 retain piston 58 in its guide cylinder 57 and hold diaphragm chamber 56 seated against pins 138 without any positive connection, as described in connection with FIG. 2.

In FIG. 6 the toe check mechanism is in retracted position with springs 135 holding arm 130 to the right. The upper end of arm 130 bears against pin in rocker frame 92, causing the back side of the rocker frame to bear against pin 104 as a stop with thrust arm 30 depressed to its retracted position in solid lines. With the counterclockwise rotation of rocker frame 92 stopped by pin 104, the clockwise bias of springs 135 on the upper end of arm also holds slide 101 fully retracted to the right.

When piston 58 is extended, arm 130 starts to swing to the left, rotating rocker frame 92 clockwise on its pivot 91 until the top of the rocker frame engages stop 105, this movement placing thrust arm 30 in its broken line position in FIG. 6 on the level of the boot sole.

Further movement of arm 130 to the left starts to move slide 101 leftward, allowing spring 141 to lift latch member 142 on its pivot pin 143 in the slide as latch tongue 144 draws away from stop pin 145 in stationary plates 132. The lifting of latch member 142 raises a stop pin 146 in the latch member up behind the lower corner of rocker frame 92 to latch the rocker frame and thrust arm 30 in FIG. 7 position. Further extension of piston 58 continues to move arm 130 and slide 101 to the left until the movement is stopped by engagement of shoe 90 on thrust arm 30 with the sole of the boot. In testing a toe clamp, the hydraulic pressure continues to increase in diaphragm chamber 56 until the toe of the boot is dislodged laterally by thrust arm 30, the maximum pressure developed in diaphragm chamber 56 being utilized in pressure gauge 36 to measure the maximum thrust exerted by the thrust arm 30 in dislodging the boot.

As the boot is dislodged from its toe clamp, pin 136 on arm 130 opens a normally closed switch 147 to shut off the pump which supplies hydraulic pressure to diaphragm chamber 56. Leftward movement of arm 130 is limited by a stop pin 150 in plates 132.

When the valves in the multiple valve unit are shifted to retract positions, hydraulic pressure is relieved from diaphragm chamber 56 and springs retract piston 58, displacing hydraulic fluid from the diaphragm chamber. With rocker frame 92 locked against rotation by stop pin 46, themovement of arm 130 to the right retracts slide 101 to the right until latch tongue 144 engages stop pin 145, this engagement pulling stop pin 146 down and away from engagement with the back side of rocker frame 92. This brings the parts back to FIG. 6 position with pin serving as a stop for the retracting movement of slide 101. Then, as arm 130 continues to move to the right, it rotates rocker frame 92 counterclockwise until the back side of the rocker frame engages pin 104 placing thrust arm 30 in the depressed position shown in solid lines. With the thrust arm thus retracted and depressed, it does not interfere with the dislodgement of the boot by thrust arm 31 on the opposite side in the next test operation.

The toe check mechanism associated with thrust arm 31 corresponds to that shown in FIGS. 6 and 8.

Hydraulic System In the hydraulic integrated circuit shown in FIG. 9, a pump 200 supplies a pressure line 201. Excess flow beyond the demands of the system is bypassed around the pump by a bypass relief valve 202. A series of

manual valves

203, 204, 205 and 206 supply hydraulic fluid under pressure to the hydraulic actuators 55A, in the clamps 55C in the right and left toe checks, and 55B in the heel check, respectively. The pressure fluid is transmitted through check valves 210, and also through restricted orifices 211 in the case of the toe and heel checks, to

lines

212, 213, 214 and 215 connected with the respective hydraulic actuators.

A series of

manual valves

216, 217, 218 and 219 is connected to the

respective lines

212, 213, 214 and 215 to discharge fluid from the

hydraulic actuators

55A, 55C and 55A into a relief line 220. The clamps 20 are released by manual valve 216, the spring 50 in FIG. 2 causing fluid in the diaphragm chamber 56 of each hydraulic actuator 55A to discharge through line 212, valve 216 and relief line 220.

Heel check sling strap 25 is released by manual valve 219, the springs 70, one of which appears in FIG. 3, causing fluid in hydraulic actuators 55B to discharge through line 215, valve 219 and relief line 220.

Toe check thrust

arms

30 and 31 are retracted by

valves

218 and 217, the springs 135, one of which appears in FIG. 6, causing fluid in hydraulic actuators 55C to discharge through lines 214 and 213,

valves

218 and 217 and relief line 220.

A pressure gauge line 225 is connected through

check valves

226 and 227 to the toe check lines 213 and 214, respectively. Pressure gauge line 225 is also connected through a manual valve 228 and restricted orifice 229 to the heel check line 215. After the toe check and heel check operations,

valves

226, 227 and 228 hold the maximum pressure in gauge 36 until the pressure is relieved by manual valve 228.

Valves

219 and 228 have a common operator as indicated in FIG. 9.

Multiple Valve Unit The valves in the hydraulic integrated circuit in FIG. 9 are contained in a valve unit which comprises a single block of metal 240 having groups of intersecting vertical and horizontal bores as shown in FIGS. 10, 11 and 12. One group of such bores contains the valves for the heel check as shown in FIG. 10, another group of bores contains the valves for the right toe check as shown in FIG. 11, another identical group of bores (not shown) contains the valves for the left toe check, and another group of bores contains the valves for the clamps 20 as shown in FIG. 12.

The lower ends of the vertical bores are closed by slidable plugs 241 which provide spring seats for valve springs 242. These plugs are sealed in the bores by rubber O-rings 243. Some of the horizontal bores provide fluid passageways as shown and others receive special plugs such as the slidable plugs 244. The plugs 241 and 244 have protruding heads and are retained in their bores by a casing 245 which supports the unit on the underside of a cover plate 246. Cover plate 246 is suspended from panel 12 by a bracket 247. Cover plate 246 is bolted to casing 245 and bracket 247. This arrangement greatly facilitates manufacture and assembly by avoiding the threading of most of the numerous bores and plugs.

The upper ends of the vertical bores in metal block 240 receive slidable valve stems for opening the manual valves described in FIG. 9. Thus, in FIG. 10 ball valve 206 is opened and closed by a valve stem 250. This and other similar bores are sealed by a washer 251 and rubber O-ring 243 receive in counterbores in the top of the block 240. The valve stem is biased upward by a spring 252. In a similar manner, the ball valve 219 may be unseated downward by a valve stem 253 and the ball valve 228 may be unseated by a valve stem 254.

The valve stems 250, 253, 254 are depressed selectively by horizontal roll pins 255, 256 and 257 in a three-position pushbutton rocking lever 260. Lever 260 is of channel-shape having a pair of apertured vertical flanges 261 journaled on a horizontal shaft 262 mounted in the bracket 247. The web of the channel is cut away in its mid portion, leaving one end portion 263 which forms a pushbutton for actuating the heel check device and an opposite end portion 264 which forms a pushbutton for retracting the heel check device.

Pushbutton lever 260 is normally held in horizontal position by a pair of tension springs 265 connected to opposite ends thereof. In FIG. 10, pushbutton 263 is indicated as being held depressed by finger pressure represented by the arrow 266. This opens the valve 206 to actuate the heel check device. When finger pressure at 266 is released, the springs 265 return pushbutton arm 260 to horizontal position, closing valve 206.

When pushbutton 264 is depressed, valve 219 is first opened to permit spring retraction of the heel check device and then valve 228 is opened to relieve fluid pressure from gauge 36. Valve stem 254 forms a restricted orifice at 229 to prevent sudden return of the gauge needle to its zero position. Stem 254 is equipped with a stop 268.

Pushbuttons

263 and 264 protrude through openings 267 in panel 12.

In a similar manner, pressing pushbutton 270 in FIG. 11 depresses valve stem 271 to open valve 204 and actuate the right toe check. Releasing pushbutton 270 closes valve 204 and pressing pushbutton 272 depresses valve stem 273 to open valve 217. This relieves the pressure in hydraulic actuator 55C in the right toe check device, allowing its thrust arm to be spring retracted. The valve and pushbutton arrangement for the left toe check is the same. As previously mentioned, the gauge 36 is returned to zero pressure after a toe check by pressing heel check release pushbutton 264 in FIG. 10.

In FIG. 12, pushing pushbutton 275 depresses valve stem 276 to open valve 203 and actuate the clamps 20. Pushing pushbutton 277 depresses valve stem 278 to open valve 216 to relief line 220 and permit spring retraction of the clamps.

As shown in FIGS. 10, 11 and 12, each of the pushbutton arms 260 is mounted for relative rotation in shaft 262. The arms 260 are maintained in properly spaced relation to the shaft by spacer sleeves 279 between the arms. A radial pin 280 in shaft 262 between the side flanges 261 of each pushbutton arm 260 bears against pin 256 in the arm. Thus, any one of

pushbuttons

263, 270 and 275 in FIGS. 10, 11 and 12 produces clockwise rotation of shaft 262.

Shaft 262 extends out of the front end of casing 245 where it is equipped with another radial pin 281 as shown in FIG. 13. The left end of pin 281 is biased downward by a spring 282 to engage the actuating button 283 of a normally closed limit switch 285 and hold the switch open.

When any one of the

pushbuttons

263, 270 or 275 in FIGS. to 12 is depressed to actuate the heel check, toe check or clamps, the pin 256 associated with the depressed pushbutton rotates shaft 262 and pin 281 to the position shown in FIG. 13, allowing switch 285 to close and start the hydraulic pump 200. This occurs just prior to the opening of the

valve

206, 204 or 203 which is associated with the depressed pushbutton so that the pump motor is started before the valve is opened.

When the depressed pushbutton is released, the springs 265 return the pushbutton arm 260 to horizontal position, allowing shaft 262 to rotate counterclockwise under the bias of spring 282 and cause pin 281 to engage switch button 283 and open the pump motor switch 285 to stop the pump. Thus, the pump operates only as long as one of the

pushbuttons

263, 270 or 275 is depressed.

The limit switches 77 in FIG. 3, 147 in FIGS. 6 and 7 and 285 in FIG. 13 are all wired in series with the pump motor whereby all of these switches must be closed to start the pump 200 and whereby the opening of any one switch will stop the pump.

Toe Pressure Attachment FIGS. 14 to 16 illustrate an attachment for applying a downward force on the toe of the boot to simulate the weight of the wearer when he is using the skis. A factor to be considered in adjusting the ski toe clamps is the sliding friction between the sole of the boot and the top of the ski. This frictional restraint against the lateral movement of the toe of the boot affects the lateral force necessary to slide the boot on the ski and release the toe from the toe clamp in skiing. The use of the attachment on the present machine more closely approximates the condition existing in actual skiing.

A transverse beam 300 is supported at each end by two pairs of crossed

arms

301 and 302 which are pivotally connected at their upper ends to

pins

303 and 304 in the beam. The lower ends of each pair of arms are pivotally connected to pins 305 and 306 in the opposite ends of a rocker arm 307. Each rocker arm 307 is pivotally mounted at its center on a pin 308 in a support frame 310. The underside of each support frame 310 contains an angle iron 311 which rests on top of beam 26 between the slides 101. Support frame 310 are open through their centers to admit the toe check thrust

arms

30 and 31. Bars 312 and angle irons 311 underlie ski S and interconnect the right and left support frames 310. Tie plate 313 interconnects the two angle irons 3 1 1.

A square housing 314 in the center of beam 300 supports a vertical cylinder 315 on pins 316. An inner cylinder 317 has guide rings 318 slidable in cylinder 315. Mounted on the lower end of cylinder 317 is a recessed cylinder head 319 having a chamber 320 containing hydraulic fluid. A bore 321 communicating with chamber 320 has an external connection at one end for a'hydraulic tube 322 leading to a fluid pressure gauge 325 on the beam 300.

A flexible pressure shoe 326 is pivotally mounted on pins 327 in a bracket 328 connected with cylinder head 319. Pressure shoe 326 contains a chamber 326a filled with liquid so that the pressure shoe 326 can conform to the shape of the top of the toe of the boot B as well as pivot on pins 327 as shown in FIG. 16. Pressure shoe 326 and cylinder 317 are biased upward by springs 329.

An adjusting screw 330 has threaded engagement with an end member 331 in the cylinder 315. Screw 330 provides means for applying a downward force against a piston 332 in cylinder 317 which transmits this force to hydraulic fluid in chamber 320, cylinder head 319 and pressure shoe 326. The amount of the applied force is indicated in pounds on the pressure gauge 325. The upward reaction from this downward force is assumed by angle irons 311 and bars 312 under the ski. Thus, the attachment merely rests on beam 26 and does not have to have positive connection therewith.

Linkage arms

301, 302, 307 allow lengthwise movement of beam 300 when one of the

thrust arms

30 and 31 pushes the toe of the boot laterally out of the toe clamp on the ski. For example, if beam 300 moves to the right with a boot in FIG. 14, the

arms

301, 302 rock the arm 307 clockwise to follow this movement without significantly raising or lowering the pivot points 303 and 304. Within a limited range of movement right or left, the beam 300 shifts in a rectilinear path of travel at uniform elevation.

The downward force applied against the toe of the boot produces a frictional restraint against lateral movement of the boot sole on the top of the ski equivalent to that produced by the weight of the skier whereby the ski toe clamp may be adjusted so that the lateral force applied by

thrust arm

30 or 31 to release the toe clamp may be significantly related to the actual conditions in skiing.

Having now described our invention and in what manner the same may be used, what we claim as new and desire to protect by Letters Patent is:

1. machine for testing ski bindings comprising an elongated frame, means for clamping a ski with a ski boot in said frame, a heel clamp testing device, means for adjusting said heel clamp testing device longitudinally in said frame, a toe clamp testing device operable on the right side of said boot, a toe clamp testing device operable on the left side of said boot, means for adjusting said toe clamp testing devices longitudinally in said frame, said heel and toe clamp testing devices all being operable with the ski clamped in a single fixed position by said clamping means, and means for applying a downward force on the toe of the boot during operation of said toe clamp testing devices.

2. A machine for testing ski bindings comprising an elongated frame, means for clamping a ski with a ski boot in said frame, a heel clamp testing device, means for adjusting said heel clamp testing device longitudinally in said frame, a toe clamp testing device operable on the right side of said boot, a toe clamp testing device operable on the left side of said boot, and means for adjusting said toe clamp testing devices longitudinally in said frame, said heel and toe clamp testing devices all being operable with the ski clamped in a single fixed position by said clamping means, said means for adjusting said heel clamp testing device comprising a first transverse beam slidably supported on ways extending along opposite sides of said frame, and said means for.

adjusting said right and left toe clamp testing devices comprising a second transverse beam slidably supported on said ways.

3. A machine as defined in claim 2 including an attachment for mounting on said second beam to apply a downward force on the toe of the boot.

4. A machine as defined in claim 3, said attachment comprising an upper transverse beam, a linkage supporting said upper beam for lengthwise movement on said second beam at constant elevation, a vertical cylinder slidably mounted in said upper beam and having a cylinder head and pressure shoe on its lower end, bydraulic fluid in said cylinder head communicating with a fluid pressure gauge on said upper beam, and a screw in said upper beam bearing against the upper end of a piston in said cylinder to press said pressure shoe against the top of the toe of the boot.

5. A machine as defined in claim 2 including V- shaped rests for the ski on opposite ends of said frame, pivotal clamp arms movable into engagement with the top of the ski above said rests, and hydraulic actuators for said clamp arms.

6. A machine as defined in claim 2, said heel clamp testing device comprising a heel sling strap, a pair of pivotal arms on said first beam connected with opposite ends of said sling strap, and hydraulic actuators on said first beam for raising said arms.

7. A machine as defined in claim 2, said toe clamp testing device comprising a pair of slides on opposite ends of said second beam, a rocker frame in each of said slides, thrust arms on said rocker frames arranged to bear against opposite sides of the boot sole selectively, a pair of actuating arms pivotally mounted on opposite ends of said second beam and having swinging ends pivotally connected with said rocker frames, retracting springs connected with said actuating arms to depress said thrust arms and retract said slides toward the ends of said second beam, and hydraulic actuators operable on said actuating arms to raise said thrust arms and move said slides toward the center of said second beam causing said thrust arms to engage said boot sole.

8. A machine as defined in claim 7 including adjusting means to raise and lower said thrust arms relative to said rocker frames in accordance with the thickness of the ski and the thickness of the boot sole.

9. A machine for testing ski bindings comprising an elongated frame, means for clamping a ski with a ski boot in said frame, a heel clamp testing device, means for adjusting said heel clamp testing device longitudinally in said frame, a toe clamp testing device operable on the right side of the said boot, a toe clamp testing device operable on the left side of said boot, means for adjusting said toe clamp testing devices longitudinally in said frame, said heel and toe clamp testing devices all being operable with the ski clamped in a single fixed position by said clamping means, hydraulic actuators for said ski clamping means, said heel clamp testing device and said toe clamp testing devices, a hydraulic pressure system for operating said actuators, manual valves in said system for transmitting hydraulic pressure to said actuators, manual valves for relieving hydraulic pressure from said actuators, a hydraulic pressure gauge, hydraulic lines connecting said pressure gauge with said actuators for said heel and toe clamp testing devices, check valves in said lines to hold maximum pressures in said gauge occurring during operation of said heel and toe clamp testing devices, and a manual valve for relieving said pressures in said gauge.

10. A machine as defined in claim 9, said hydraulic pressure system including a hydraulic integrated circuit in which said manual valves comprise spring actuated ball valves seated in bores in a block of metal, slidable valve stems arranged to unseat said ball valves, and push buttons arranged to move said valve stems.

11. A machine for testing ski bindings comprising a frame, a pair of pivotal arms for clamping said ski on said frame at a point in front of said bindings and at a point behind said bindings, a heel clamp testing device comprising a heel sling strap, a pair of pivotal arms on said frame connected with opposite ends of said sling strap to lift said sling strap, a toe clamp testing device comprising right and left side lateral thrust arms, a pivotal arm for actuating each of said thrust arms; a hydraulic actuator for actuating each of said pivotal arms, each of said actuators comprising a shouldered pres sure chamber having a cylinder and a piston in said cyl inder, said pressure chamber in each actuator bearing against a pair of pins in said frame and the end of said piston in each actuator bearing against a pin in one of said pivotal arms, and retracting springs acting on said pivotal arms to hold said actuators in operative positions bearing against said pins.

12. A machine as defined in claim 11, said cylinders being in fixed positions with their axes tangent to the arcuate paths of travel of said pins in said pivotal arms at the mid points of said paths of travel.

Claims

2. A machine for testing ski bindings comprising an elongated frame, means for clamping a ski with a ski boot in said frame, a heel clamp testing device, means for adjusting said heel clamp testing device longitudinally in said frame, a toe clamp testing device operable on the right side of said boot, a toe clamp testing device operable on the left side of said boot, and means for adjusting said toe clamp testing devices longitudinally in said frame, said heel and toe clamp testing devices all being operable with the ski clamped in a single fixed position by said clamping means, said means for adjusting said heel clamp testing device comprising a first transverse beam slidably supported on ways extending along opposite sides of said frame, and said means for adjusting said right and left toe clamp testing devices comprising a second transverse beam slidably supported on said ways.

4. A machine as defined in claim 3, said attachment comprising an upper transverse beam, a linkage supporting said upper beam for lengthwise movement on said second beam at constant elevation, a vertical cylinder slidably mounted in said upper beam and having a cylinder head and pressure shoe on its lower end, hydraulic fluid in said cylinder head communicating with a fluid pressure gauge on said upper beam, and a screw in said upper beam bearing against the upper end of a piston in said cylinder to press said pressure shoe against the top of the toe of the boot.

5. A machine as defined in claim 2 including V-shaped rests for the ski on opposite ends of said frame, pivotal clamp arms movable into engagement with the top of the ski above sAid rests, and hydraulic actuators for said clamp arms.

11. A machine for testing ski bindings comprising a frame, a pair of pivotal arms for clamping said ski on said frame at a point in front of said bindings and at a point behind said bindings, a heel clamp testing device comprising a heel sling strap, a pair of pivotal arms on said frame connected with opposite ends of said sling strap to lift said sling strap, a toe clamp testing device comprising right and left side lateral thrust arms, a pivotal arm for actuating each of said thrust arms; a hydraulic actuator for actuating each of said pivotal arms, each of said actuators comprising a shouldered pressure chamber having a cylinder and a piston in said cylinder, said pressure chamber in each actuator bearing against a pair of pins in said frame and the end of said piston in each actuator bearing against a pin in one of said pivotal arms, and retracting springs acting on said pivotal arms to hold said actuators in operative positions bearing against said pins.