US3077188A - Piston impact motor - Google Patents

Description

Feb. 12, 1963 Filed April '7. 1960 H. HERRMANN 3,077,188

PISTON IMPACT MOTOR 2 Sheets-Sheet l /NVENTOR [ffl/1107- Feb. 12, 1963 H. HERRMANN 3,077,188

PISTON IMPACT MOTOR Filed April 7. 1960 2 Sheets-Sheet 2 -`r Q; g E HEavaT HERR/10AM# SPM/My n no KM? V5 lN VEN TOR Unite States Patent Office Bll Patented Feb. l2, 1.8%3

The present invention relates to a piston impact motor and more particularly to a free flying double piston Biesel motor for the production of linear oscillations.

Various piston impact motors have been heretofore provided which have a double chamber cylinder containing a double acting piston therewithin, w iich are used for the production of linear oscillations for conveyor device and the like. ln such motors, however, the control oi the motor, i.e. the control of fuel supply to the motor, is carried out by the provision or auxil'a y devices which operate under the influence of the ru ning motor.

lt is an object or" the present invention to provide a piston impact motor for the production of linear oscillations in accordance with the diesel-Z-cycle techni-que.

-lt is a further object of the invention to provide such a piston impact motor having direct control means operable in conjunction with the piston of the motor to meter fuel to the cylinder in timed sequence during the back and forth movement of the piston.

Gther and further objects of the invention will become apparent from a study of the within specilication and accompanying drawings in which:

FlGURE l is a schematic longitudinal sectional View of one embodiment of a piston impact motor in accordance with the invention, and

FEGURE 2 is a schematic sectional View of a further embodiment of a piston impact motor in accordance with the invention.

The piston impact diesel motor in accordance with the invention is useful for the production of linear oscille.- tions, and generally comprises a motor cylinder having a motor piston movable back and forth therewithin, the cylinder beine provided with combustible gas intake means and exhaust gas outlet means as well as iuel iniection means. The fuel iniection means includes a pressure responsive fuel ctio-n valve for regulating the passage of fuel to the cyli r and pressure exerting means responsive to and rorth movement of the piston for forcing fuel through the valve and into tre cylinder in conjunction with the baci; and forth movement. Fhe piston may be constructed es a free living double piston slidable baci: forth wit' n the cylinder. The cylinder may be constructed as double chamber cylinder, each che ther hai/ins fuel injection ineens and exhaust outlet means. thus, impact piston alternately ^oves from one end of tle cylincer to the other, alternately into and out of corresponding chamber of cylinder in accordance with the Z-cycle diesel techthe trie nique.

The impact piston is preferably constructed with piston ends of the seme di vv ich move into and out of the corresponding chamber of the cylinder cooperating therewith. On the intermediate portion of the piston an extension ilange is provided which is received Within an intermediate annular extension chamber located between the end chambers of the cylinder.

Unilateral air inlet valves are provided on the annular extension chamber on each side of the flange extension. Moreover, each end of the double piston is provided with a unilateral conduit for passage of intake air or combustion into its corresponding cylinder chamber from the intake check valve on the opposite side of the flange extension with respect thereto.

During the baci: and forth movement of the flange extension within the annular extension chamber as the piston is operated, a suction is created on one side of the ange extension whereby intake gas or air is drawn through the checli valve into the corresponding portion of the annular extension chamber on said one side. ln contrast thereto a compression is created on the other side of the ilanve extension whereby intake air or gas disposed in the corresponding portion of the annular extension charnber on the other side is forced through a unilateral conduit to a corresponding cylinder chamber. Hence, during operation of the piston Within the cylinder each cylinder chamber is supplied with combustion gas or air by deans of the unilateral conduit within the piston leading from the opposite side of the Piange extension with respect thereto. In essence, the llange extension and annular extension chamber operate together during movement of the piston as a pumping device which draws in combustion gas through the check valve during one half of the cycle, and compresses the same forcing it through the piston conduit into the oppositely disposed cylinder chamber during second half of the cycle.

in accordance with the preferred embodiment, a unilateral conduit is provided which extends from each end of the double chamber cylinder to a corresponding reservoir therefor. During the movement of the piston into the corresponding cylinder chamber gases disposed therewithin are forced under compression.` through the conduit to the reservoir. Each reservoir is equipped with a by-pass valve placing the` same in communication with the corresponding end of the double chamber cylinder so that upon opening the lay-pass valve, the compressed gas is permitted to return to the corresponding cylinder" chamber. This action may be eiected in order to start the motor, since compressed gas may pass from the corresponding rcservoirs alternately into the cylinder cham-y bers to effect a back and forth movement of the piston until the motor is started.

During baci; and forth movement or" the double piston, the pressure exerting means is correspondingly actuated to alternately force fuel through the fuel injection valve to each chamber of the double cylinder. A pressure resnonsive fuel injection valve is provided for each chamber of the cylinder so as to alternately iniect fuel into the cylinder for operating the motor. The fuel injection valve includes a valve opening and a valve piston normal: 1y resiliently urged in sealing abutment Wi-th the valve opening, thus closing the valve. The valve piston is arranged with a cone end for attaininzi the sealing abutment and is preferably spring loaded. Upon reaching a predetermined counter-pressure exerted against the valve piston. the same will be displaced from sealing abutment and the valve will open to allow fuel to be injected into the respective cylinder chambers.

A pressure exerting means responsive to back andfort'h movement of the piston is provided preferably for each fue? injection valve. The pressure exerting means ger1.` erallv tal/.es the form of a pump means operating to force fuel through the valve due to the pre-determined counter-y pressure exertedV by the fuel against the valve in consequence of bumping actuation. The pump is actuated in forward direction during the comnressio'n stroke of the corresoonding end of the double piston with respect thereto and is actuated in a return direction bv suitable resilient urrinrz means such as a compression spring so as to attain suilicient suction within the pump means to draw addis tional fuel for the next pumping actuation.

rl`he pump may include a pump cylinder communicating with the fuel conduit for the motor, in which a pump piston is slidably received and normally resiliently urged in return direction outward of the cylinder. The pump piston is connected for delayed action opening of a fuel intake' valve for the pump upon forward movement of the pump piston into the cylinder a pre-determined distance. Upon return movement of the pump piston, an auxiliary delayed action return piston arrangement comes into play which governs the speed of closing of the fuel intake valve, so that the valve is closed by delayed action. This permits additional fuel to be drawn therethrough and into the pump cylinder for the next pumping actuation.

In accordance with one embodiment of the invention the pump piston end remote from the cylinder slidably extends into the annular extension chamber of the motor cylinder and into the path of the flange extension therewithin. The pump piston is mounted for forward movement by contact with the flan-ge extension in the same longitudinal direction as the flange extension in accordance with this embodiment. Thus, the movement back and forth of the flange extension drives the pump piston in forward direction to operate the pumping action.

The pump piston in accordance with this embodiment is provided with a projection bar for urging an auxiliary piston correspondingly in the forward direction of movement of the pump piston. The auxiliary piston is mounted in an auxiliary cylinder having both ends in bilateral recycle flow communication with one another remote from the auxiliary piston. One path of ow communication includes a unilateral check valve for passing iluid from the side of the auxiliary cylinder into which the auxiliary piston moves upon actuation by the projection bar to the opposite side of the auxiliary cylinder. The other path of flow communication includes a throttle for restricting the flow of the fluid to the opposite side of the auxiliary cylinder. The end of the auxiliary piston remote from the projection bar contains a link bar pivotally mounted at one end thereon and linkably seated at the other end within a recess in the pump piston. The link bar is urged into contact with the fuel intake valve to open the same in delayed sequence after the pump piston has moved forward a pre-determined distance. Since the link bar is connected to the auxiliary piston which moves in consequence of the forward urging of the projection bar, as well as to the pump piston itself, the link bar will make the delayed sequence contact with the fuel intake valve in the desired manner. Due to the unilateral check valve and throttle arrangement of the auxiliary cylinder, the auxiliary piston, and in turn the link bar will move in the return direction slowly so as to cause the fuel intake valve to correspondingly close slowly. This permits additional fuel to be drawn through the intake valve into the pump cylinder for the next pumping actuation. Since the pump piston is normally resiliently urged in the return direction, the same will pass out of the cylinder faster than the return of the auxiliary piston, the link bar and the intake fuel valve.

ln accordance with another embodiment of the invention, the pump piston end remote from the pump cylinder is received within a further cylinder which is in flow communication with the corresponding cylinder chamber of the mo-tor cylinder. In this way upon compression of the corresponding motor piston end in the cylinder chamber, gases within the cylinder chamber will be forced into the further cylinder causing movement of the pump piston in forward direction in conjunction therewith. In this instance,the auxiliary cylinder is also mounted for movement in the direction of movement of the pump piston; however, `the auxiliary cylinder is not urged by a' projection bar but instead is in unilateral flow communication with the corresponding cylinder chamber of the motor. Similarly, therefore, upon compression of the moto-r piston combustion gas is forced therefrom into the auxiliary cylinder flow communicating therewith causing movement of the auxliary piston in the forward direction. The lluid passing into the auxiliary cylinder is released therefrom through a restricted outflow opening. Due to the unilateral flow communication and the restricted outflow opening, the auxiliary piston moves in the return direction only slowly. In the same manner as aforesaid, the slow return movement of the auxiliary piston and the link bar pivotally connected thereto and linkably seated within a recess in the pump piston permits the fuel intake Valve to close slowly. Therefore, additional fuel may be drawn therethrough into the pump cylinder for the next pumping actuation.

In accordance with the preferred construction of the pump piston auxiliary piston and fuel intake valve, each of these elements is spring loaded under pre-determined tension, so as to effect operation in accordance with the foregoing.

Referring to the drawings, FIGURE 1 shows a cylinder 18 having two end chambers 45 and an intermediate annular extension chamber 11, Within cylinder 10 a double piston 12 is movable back and forth, piston 12 being provided with an intermediate flange portion 13 radially outwardly projecting into annular chamber 11. A fuel tank 14 flow communicates via a line 15 with a valve means located at either side of cylinder 10 with corresponding inlet lines 16 leading to the corresponding ends of cylinder 1d. Each chamber 4S of cylinder 10 is provided with a plurality of outlet openings 17 for exhausting combustion gases from the diesel piston impact motor. Each end of piston 12 is provided with a central bore 1S communicating with a corresponding lateral bore 19 pass. ing to the opposite side of iange 13 with respect thereto. The front surfaces of the corresponding ends of piston are provided with a check valve 2t?, in each case, permitting unilateral iiow of gases or air to be combusted into the corresponding chamber 45. The other end of the conduit defined by bore 1S and bore 19 opens into annlar chamber 11 on the opposite side of ilange portion 13. Each side of annular chamber 11 is provided with a check valve 21 defining an air or combustion gas inlet.

Thus, as piston 12 moves back and forth within cylinder 1t), flange portion 13, in turn, moves back and forth within annular chamber 11. During this back and forth movement, suction is created on one side of flange portion 13 within annular chamber 11 so as to open check valve 21 on that side of annular chamber 11 whereby air from the atmosphere or combustion gas fed from a source on the other side of check valve 21 may be drawn Within annular chamber 11. Since during this forward movement check valve 26 remains closed, there is no equalization of pressure between chamber 4S on the opposite side and the portion of annular chamber 11 drawing in the air or combustion gas. At the same time with respect to the portion of annular chamber 11 on the opposite side of flange portion 13, air or combustion gas disposed within annular chamber 11 is forced by pump action through bore 19 and bore 18 to the chamber d5 on the other side of cylinder. Since check valve 21 is a unilateral check valve, no air will flow out of annular chamber 11 through the check valve at that side but will only pass through bore 19 and bore 18 into the oppositely disposed chamber 45. Since check valve Ztl is a unilateral check valve, this gas or air under the pressure created in annular chamber 11 is forced into the chamber i5 in communication therewith.

A pressure reservoir 22 having two separate pressure chambers is arranged with respect to cylinder 10 so that each chamber of pressure reservoir 22 is in separate flow communication via a line 23 with a corresponding end of cylinder :tu by means of unilateral check valve 25. During the back and forth movement or piston 12 within chamber 10, enough pressure is generated to force a portion of the gases within each chamber 45 through unilateral check valve 25 and conduit 23 into a corresponding chamber of pressure reservoir 22. After a certain period operation, each separate chamber of pressure reservoir 22 will contain combustion gases or air up to a pre-determined pressure.

Advantageously, each line 23 is in further discontinuous flow communication with a corresponding chamber 4S by means of a valve 24 and an alternate conduit 50.

Therefore, in order to start the motor, the operator may merely open the valve 24 to alternately force gas or air from pressure reservoir 22 under pressure through conduit Sti to force piston l2 back and forth within cylinder 1d. Since check valves 2S are unilateral check valves, they will keep the gases within pressure reservoir 22 under the pre-determined desired pressure, the release of this pressure being carried out only through valves 24 and conduits Si?. At the ends of cylinder lll, a fuel injection needle valve 26 is provided communicating fuel lines 12S with each chamber i5 of cylinder lll. A cone pointed spring loaded needle piston 27 is urged by spring 23 into closing engagement with needle valve 26 in rest position. Needle Z7 may be urged out of closing contact with needle valve 26 upon the reaching of a counter-pressure within lines lr6 which is greater than the urging force of spring 23.

The fuel inlet regulating device for the piston impact motor of the invention includes a pump assembly arranged at either side of the cylinder if?. Thus, a pump piston 3d is slidably arranged at one end within a pump cylinder 29 and at the other end within annular chamber 1l by means of an opening in the side wall of chamber il. Pump cylinder 29 is in flow communication with fuel lines lle by means of conduit 33. Pump piston 30 is normally urged outwardly of pump cylinder 29 by means or" spring 3l. As double piston l2 moves back and forth within cylinder lll, flange portion 13 correspondngly moves back and forth within annular chamber lll so as to abuttingly engage pump piston 3d, forcing the same further within pump cylinder 29. ln this Way fuel present within pump cylinder 129 will be forced through conduit 33 and line 16 into the corresponding chamber 45 of cylinder lill, since the force exerted on the fuel by piston 3b is greater than that exerted by spring 2S on needle 27. Needle 27 is, therefore, displaced frorn sealing abutment with needle valve 26 opening the same for flow of `fuel to the motor.

Disposed above pump piston 3l? and pump cylinder 29 is an auxiliary piston 36 slidably disposed under spring action within a double-ended auxiliary cylinder 35. Piston 36 is mounted on a piston rod 37 for movement therewith within cylinder 3S. A link bar 33 is pivotally connected to piston rod 37 at one end and linkabiy seated within a recess 39 delined in piston 3ft at the other end. A pr jecticn bar 32 is mounted on the end of piston Sti remote from cylinder 29 for urging against the opposite end of piston rod 37. ln this manner, as piston E@ is moved further within cylinder Z9 in consequence of the force exerted by flange portion i3, projection 3.?, will force piston rod 35' and in turn piston 36 in the same direction of movement as piston 30.

Each end of auxiliary cylinder 3S is in dow communication with the other end, remote from piston 36, by means of conduit 34 on one side and conduit i3 on the other. One flow communicating path between conduit 3d and conduit 43 includes a check valve do which permits flow of lluid thcrewithin in a unilateral direction from conduit i3 to conduit 34. On the other hand, another flow path is provided from conduit 3d to conduit 43, which includes a throttle opening is restricting free flow in either direction. Piston 3o is spring loaded so that upon movement of the same in response to the force exerted by projection 32 of piston 39, fluid within cylinder 35 will pass through check valve le as well as throttle opening d4 from conduit i3 to conduit 34 without lag.

However, upon the return movement of piston 3%' and projection 32, piston 36 will return only slowly in consequence of spring urgence in the return direction of piston 36 since check valve 46 will be closed to return ow so that the duid within cylinder 35 can only pass through d throttle opening la to conduit 43. Accordingly, while piston 36 will move in the forward direction simultaneous- 1y with and approximately at the same speed of movement as piston Sill, piston 3d will return to its original position more slowly than will piston 3d.

Disposed above conduit 33 a fuel intake valve di is provided having a suction piston t2 normally spring urged in sealing abutment so as to close valve 4l. At the remote end of Valve piston d2, a projection fit) is provided which is situated within the path of movement of link bar 3*. Accordingly, as piston Sti and piston 36 move in the forward direction in response to the force of flange portion i3 and proiection 32, respectively, link bar 33 will be correspondingly urged in the same direction against projection Il@ so as to unseat piston l2 from sealing engagement. lt will be appreciated that piston 3i? moves Within cylinder 29 so as to force fuel disposed within cylinder 29, conduit 33, and line lid through needle valve 26 and into the corresponding cylinder chamber i5 before link bar 38 urges against projection dll to open valve 4l. As piston 3@ returns to its original position a suction is created within the cylinder 29 which causes fuel from line l5 to be drawn through valve di and into cylinder 29, link bar 38 having reached projection dit! by this time to cause the movement of valve piston 42 to open valve dll.

While piston Sill returns to its original position with reasonable speed, piston 36 and piston 37 are returned to their original position more slowly due to the action of throttle opening 44. This causes a lag in the closing of valve 41 so as to permit fuel in line l5 to pass through the valve and into cylinder 2g by reason of the suction created in cylinder 29 as piston 3i? returns to its original position.

It will be appreciated that a corresponding pump means, including a piston 3dr, cylinder 29, conduit 33, spring 3l, and projection 32 is present at either side. of cylinder lt?. In the same way, a similar arrangement, including piston, 35, piston rod 3'7, cylinder 35, conduits 3d and fifi, check valve d6, throttle opening rif-l, and link bar 38 will be provided in each instance. The same may oe said for projection di), valve piston i2 and valve lil as well as needle valve 26 and needle 27.

in operation fuel from fuel tank i4 may pass through each conduit l5 to a fuel intake valve 4l for passage therethrough to line i6 and accordingly into chamber during the back and forth movement of the double piston l2. Valve il together with pump piston 3i? and pump cylinder 29 regulate the amount of fuel to be injected through needle valve 2d. Puel passage through needlevalve 2d takes place in a shock-like manner due to the sudden forward movement of pump piston Sil in consequence of the forward movement of ilange portion i3. rThe piston impact motor of the invention operates with diesel fuel under high compression within the chambers l5 to force the double piston l2 back and forth within cylinder lil to effect the desired linear oscillations.

Referring to FlGURE 2, a similar double piston is shown within a cylinder lll which is provided with a [lange portion l moving back and forti within an annular extension portion il of cylinder ld. rl'he annular flange portion in this embodiment as well is equipped with check valves 2l for intake of combustible gases, such as air. Such gases may flow via bores It? and ld into the corresponding ends of cylinder Each end of cylinder l@ is in the same way provided with outlet openinvs i7 for exhausting spent gases.

ln accordance with the embodiment of FGURE 2, fuel line l5 iiow communicates through valve @il with lines dil and the corresponding end of cylinder l@ upon passage through the needle valve having a cone ended needle 62 normally spring urged in closed position. In this instance, a pump piston di? is provided at one end within a cylinder portion di and at the other end within a large-r cylinder zi' ilow communicating with the corresponding end of cylinder 1t?. Within cylinder d'7 piston @i6 is provided with a correspondingiy larger piston head S, piston 46 being normally urged by spring 59 out of cylinder 6l and into cylinder 47. Cylinder 14j is also in flow communication through line 54 with an auxiliary cylinder 48 by means of a unilateral check valve 53. Piston 49, normally urged by spring 55 within cylinder portion 56, is positioned within auxiliary cylinder 4S for back and forth movement therewithin. An outlet opening 57 is disposed in cylinder 43 for exhausting combustion gases or air forced into cylinder 4S and against piston 49 through check valve 53 in response to the compression stroke movement of the piston within cylinder lll. Auxiliary piston 49 is provided with a piston rod S2 to which a link bar Sii is pivotally connected at one end. The other end of link bar 5ft is linkably seated within a recess 5l defined in piston 46. Valve piston 42 is provided in a manner analogous with that of FlGURE l so that upon the forward movement of piston 46 and piston 4,9, respectively, link bar Sil will be urged against valve piston fr?. to open the same. The operation in this instance is the same as that described for the embodiment shown in FGURE l whereby upon initial forward movement of piston 46 within cylinder 6l fuel within line 6ft is forced against needle 62 so as to unseat the same and allow the passage of the fuel into the corresponding end of cylinder l. Since there is a 'lag of movement of piston rod 52 and link bar Sil, valve piston d2 will be opened by delayed action so as to allow the passage of fuel through valve Lill in response to the suction created by the return movement of piston 45 out of cylinder 6i.

The operation of the pump device in this embodiment is carried out by the back yand forth movement of the double piston within cylinder l@ in such a way that upon the compression stroke, combustion gases or air will be forced into Cylinder t7 and against piston head 5d so that piston 46 will be urged into cylinder itl to pump the fuel to the motor in the customary manner. Since cylinder l@ is in communication via line 54 with cylinder 4S, through check valve 53, addition-al combustion gases or air will force piston d@ in the same direction as that of piston 46. The delayed action return of piston 49 is carried out by reason of the restricted outlet 57 in cylinder 48. Thus, while spring 55 will urge piston d@ in the return direction, the air or compressed gases within cylinder 4S will only pass out of opening 57 at a comparatively slow rate. Accordingly, link bar 5h will move in the return direction under deiayed action so that suction of fuel from line l through valve di and into line 6@ and cylinder 61 may take place upon the return movement of piston 46 within cylinder 47.

It will be appreciated with respect to FIGURES 1 and 2 that the amount of fuel injected on each side of cylinder l@ will be determined by the amount of lag between the movement of the pump piston and that of the auxiliary piston. Thus, the pump piston is urged in forward direction a certain distance before the auxiliary piston begins to move (see FIGURE l) or the auxiliary piston moves forward more slowly than the pump piston due to the air outlet release (see outlet 57, FIGURE 2). In this way, fuel is forced by the pumping action past the needle valve aud into chamber 45 before the fuel intake valve 4l is opened. The fuel intake valve 5l is opened actually toward the end of the forward stroke of the pump piston in conjunction with the forward stroke of the auxiliary piston whereupon fuel may be drawn past valve 4i and into the pump cylinder in consequence of the suction created by the return movement of the pump piston. Due to the lag occasioned by the slow return movement of the auxiliary piston, the fuel intake valve remains open during the return stroke of the pump piston to allow additional fuel to be drawn into the pump apparatus.

It will be noted that npon the start of a compression stroke by the double piston within the double cylinder,

the outlet openings will be sealed otf from the corresponding chamber and air or gases to be burned will be compressed. When the maximum compression stroke has almost been reached fuel will be injected through the needle valve whereupon, under the extreme pressure combustion will take place and the double piston will be urged in the return direction. During this return moveent the exhaust gases present in the chamber will flow out of the outlet openings and when the pressure within the chamber corresponds with that generated within the annular chamber on the opposite side of the flange portion, combustion gases or air to be used for the next stroke pass through the bore and in turn the unilateral check valve into the chamber. The check valve at this point allows the passage of intake air or combustion gas since the chamber pressure exerted on the valve decreases as the pressure in the annular chamber on the opposite side of the frange portion increases.

During these operations, the pressure reservoir is lled with air or gases in increments until the pressure reservoir reaches the equilibrium pressure with that effected within the cylinder chambers. The pressure reservoir thereafter is available to start the piston impact motor by merely opening the `by-pass valve alternately on each side of the cylinder so as to force air against corresponding sides of the double piston whereby the piston is moved back and forth within the cylinder in shock-like manner so as to energize the pump means and force fuel into the cylinder chambers for effecting diesel motor operation. The piston impact motor fuel supply may be adjusted advantageously by adjusting the spring fo-rce of the various pistons and valves as well as the piston diameters with respect to one another. Smooth running of the motor will, therefore, easily be attained to produce linear oscillations within a wide range of frequencies due to the various adjustment possibilities for supplying the fuel to the motor.

While the foregoing specification and accompanying drawings have been set forth for the purpose of illustration, it will be obvious to those skilled in the art that various modifications and changes may be made Without departing from the spirit and scope of the invention which is to be limited only by the scope of the appended claims.

What is claimed is:

l. Piston impact diesel motor for the production of direct mechanical linear oscillations which comprises a motor cylinder means, a free dying impact motor piston means lmovable back and forth within said cylinder means, said piston means being constructed and arranged for imparting direct mechanical linear oscillations to said cylinder means and operatively dividing said cylinder means into two corresponding end portions, said cylinder means having combustible gas intake means and exhaust gas outlet means for each end portion, and fuel injection means including pressure responsive fuel injection valve means at each cylinder end portion for regulating the passage of fuel to each corresponding cylinder end portion and alternate pressure and suction exerting means at each cylinder end portion responsive to back and forth movement of said piston means for actuation in forward direction by said piston means during the compression stroke of the corresponding end of the piston means to attain a predetermined counterpressure to force fuel through the corresponding valve means noon attaining the predetermined counterpressure and into the corresponding cylinder end portion and thereafter actuation in the return direction to attain sutiicient suction to draw additional fuel within said alternate pressure and suction means for the next pressure actuation.

2. Piston impact diesel motor for the production of direct mechanical linear oscillations which comprises a double chamber motor cylinder, a free dying impact motor double piston movable back and forth within said cylinder and constructed and arranged for imparting direct mechanical linear oscillations to said cylinder, said piston being provided with an intermediate flange portion having an outside diameter larger than that of the ends of the double piston and said double chamber cylinder being provided with an intermediate annular extension chamber, slidably receiving said flange portion, said cylinder having combustible gas intake means and eX- haust gas outlet means, and fuel injection means including pressure responsive fuel injection valve means provided for each chamber of the cylinder for regulating the pwsage of fuel to the corresponding chamber and a correspending pressure exerting means responsive to back and forth movement of said piston provided for operatively controlling each pressure responsive fuel injection valve means, each pressure exerting means including a pump means for forcing fuel through said valve means and into the corresponding cylinder chamber in conjunction with said back and forth movement upon the attaining of a predetermined counterpressure by said pump means, each said pump means being actuated by said double piston during said back and forth movement first in forward direction during the compression stroke of the corresponding end of the double piston to attain said counterpressure and force said fuel through the corresponding valve means, and thereafter in the return direction to attain sufficient suction to draw additional fuel within said pump means for the next pumping actuation.

3. Piston impact diesel motor for the production of direct mechanical linear oscillations which comprises a double chamber motor cylinder, a free flying impact motor double piston movable back and fort-h within said cylinder and constructed and arranged for imparting direct mechanical linear oscillations to said cylinder, said piston being provided with an intermediate iiange portion having an outside diameter larger than that of the ends of the double piston and said double chamber cylinder being provided with an intermediate annular extension chamber, slidably receiving said flange portion, and fuel injection means including pressure responsive fuel injection valve means for regulating the passage of fuel to -said cylinder and pressure exerting means responsive to back and forth movement of said piston for alternately forcing fuel through said valve means and into each said cylinder double chamber in conjunction with said back and forth movement, said annular extension chamber being provided with combustible gas intake check valve means on each side of said flange portion and each end of said double piston being provided with a unilateral conduit for passage of combustible intake gas into the corresponding cylinder' chamber therefor from the check valve means on the opposite side of said iiange portion with respect thereto, and said cylinder chambers being provided with outlet openings defined therein for exhaustinng the combustion products formed, whereby during back and forth movement of said flange portion within said annular extension chamber, a suction is created on one side of said flange portion and intake gas is drawn through said check valve means into the corresponding portion of said annular extension chamber on said one side, and a compression is created on the other side of said flange portion and intake gas disposed in the corresponding portion of said annular extension chamber on said other side is forced through a unilateral conduit to a corresponding cylinder chamber.

4. Piston impact diesel motor according to claim 3 wherein a unilateral conduit is provided extending from each end of said double chamber cylinder to a corresponding reservoir for forcing iiuid from each end of said cylinder under compression during back and forth movement of said double piston to said reservoir, each said reservoir being in by-pass valve communication with the corresponding end of said double chamber cylinder for starting the back and forth movement of said piston upon opening of the by-pass valve communication to permit the return ow of said fluid under compression.

5. Piston impact diesel motor according to claim 3 l@ wherein a pressure responsive fuel injection valve means is provided for each chamber of the cylinder.

6. Piston impact diesel motor according to claim 5 wherein said valve means includes a valve opening and a valve piston normally resilientlyv urged in sealing abutment with said valve opening, said valve piston being displaced from said sealing abutment to open said valve means upon the attaining of a predetermined counterpressure exerted thereagainst.

7. Piston impact diesel motor according to claim 6 wherein said valve piston has a cone edge for the sealing abutment with said valve opening. v

8. Piston impact diesel motor according to claim 7 wherein said valve piston is spring loaded. g

9. Piston impact diesel motor according to claim 5 wherein a pressure exerting means responsive to back and forth movement of said piston means is provided for each of said pressure responsive fuel injection valve means.

10. Piston impact diesel motor according to claim 9 wherein said pressure exerting means is a pump means for forcing fuel through said valve means upon the attaining of a predetermined counter-pressure by said pump means.

l1. Piston impact diesel motor according to claim 2 wherein said pump means includes a pump cylinder communicating with the fuel conduit for the motor hav-ing a pump piston slidably received therein and normally resiliently urged in return direction outward of Isaid cylinder, said pump piston upon actuation forcing the fuel through said injection valve means and being connected for the delayed action opening of a fuel intake valve for the pump means upon forward movement of the pump piston into said pump cylinder a predetermined distance, whereupon on the return movement of the pump piston outwardly of the pump cylinder, a suction is created which causes additional fuel to be drawn into the pump cylinder for the next pump-ing actuation.

12. Piston impact diesel motor according to claim 11 wherein said fuel intake valve for the pumping means is connected for movement with a delayed action return piston arrangement whereby after said fuel intake valve has been opened by the pump piston of said pump means, said valve is closed by delayed action permitting additional fuel to be drawn therethrough into the pump cylinder for the next pumping actuation.

13. Piston impact diesel motor according to claim 12 wherein the pump piston end remote from said pump cylinder slidably extends into the annular extension chamber of the motor cylinder means and into the path of said flange portion, said pump piston being mounted for forward movement by contact with said flange portion in the same longitudinal direction as said flange portion.

14. Piston impact diesel motor according to claim 13 wherein said pump piston is provided with a projection bar for urging an auxiliary piston correspondingly in the forward direction of movement of said pump piston, said auxiliary piston being mounted in an auxiliary cylinder having both ends thereof in bilateral recycle flow communication remote from said auxiliary piston, one path of flow communi-cation including a unilateral check valve for passing uid from one side of said auxiliary cylinder into which said auxiliary piston moves upon actuation by said profection bar to the opposite side of said cylinder, the other path of flow communication including a throttle for restricting the flow of said liuid to said opposite side, the end of said auxiliary piston remote from said projection bar having a link bar pivotally conected at one end thereto and linkably seated at the other end within a recess in the pump piston, said link bar being urged in contact with the fuel intake valve to open the same in delayed sequence after the forward movement of said pump piston and said auxiliary piston a predetermined distance, said auxiliary piston due to said unilateral check valve and said throttle and in turn said link bar moving in the reenviarse 11 turn direction slowly so as to cause said fuel intake valve to close slowly so that additional fuel may be drawn therethrough into the pump cylinder for t-he next pumping actuation.

15. Piston impact diesel motor according to claim 14 wherein said pump piston and said auxiliary piston are spring loaded.

16. Piston impact diesel motor according to claim 12 wherein the pump piston end remote from said pump cylinder is received within a further cylinder in flow communcation wtih the corresponding cylinder chamber of said motor cylinder means whereby upon compression of the corresponding motor piston means in said cylinder chamber, uid is forced into said further cylinder for movement of said pump piston in the forward direction.

17. Piston impact diesel motor according to claim 16 wherein said pump means is provided with an auxiliary piston mounted in an auxiliary cylinder for corresponding movement in the direction 4of movement of said pump piston, said auxiliary cylinder being in unilateral flow communication with the corresponding cylinder chamber of said motor cylinder means whereby upon compression of the corresponding motor piston means in said cylinder chamber, uid is forced into said auxiliary cylinder for movement `of said auxiliary piston in the forward direction, said fluid being released from the auxiliary cylinder by means of a restricted outfiow opening, said vauxiliary pist-on having a link bar pivotally connected at one end thereto and linkably seated at the other end within a recess in the pump piston, said link bar being urged in contact with the fuel intake -valve to open the same in delayed sequence after the forward movement of said pump piston and said auxiliary piston a predetermined distance, said auxiliary piston due to said unilateral flow communciation and said restricted `outflow opening and in turn said link bar moving in the return direction slowly so as to cause said fuel intake valve to close slowly so that additional fuel may be drawn therethrough intr;- the pump cylinder for the next pumping actuation.

18. Piston impact diesel motor according to claim 17 wherein said pump piston and said auxiliary piston are spring loaded.

References Cited in the le of this patent UNITED STATES PATENTS 1,254,097 Weiss Jan. 22, 1918 1,535,659 Fog Apr. 28, 1925 1,858,102 McKeown May 10, 1932 1,980,997 Jenkins Nov. 20, 1934 2,344,058 Pescara Apr. 14, 1944 2,405,043 Meitzler July 30, 1946 2,463,051 Pescara Mar. l, 1949 2,944,535 Fikse July 12, 1960 FOREIGN PATENTS 692,863 Germany June 27, 1940 OTHER REFERENCES Cockerell, German application 1,012,777, printed July 25, 1957.

Claims (1)

1. PISTON IMPACT DIESEL MOTOR FOR THE PRODUCTION OF DIRECT MECHANICAL LINEAR OSCILLATIONS WHICH COMPRISES A MOTOR CYLINDER MEANS, A FREE FLYING IMPACT MOTOR PISTON MEANS MOVABLE BACK AND FORTH WITHIN SAID CYLINDER MEANS, SAID PISTON MEANS BEING CONSTRUCTED AND ARRANGED FOR IMPARTING DIRECT MECHANICAL LINEAR OSCILLATIONS TO SAID CYLINDER MEANS AND OPERATIVELY DIVIDING SAID CYLINDER MEANS INTO TWO CORRESPONDING END PORTIONS, SAID CYLINDER MEANS HAVING COMBUSTIBLE GAS INTAKE MEANS AND EXHAUST GAS OUTLET MEANS FOR EACH END PORTION, AND FUEL INJECTION MEANS INCLUDING PRESSURE RESPONSIVE FUEL INJECTION VALVE MEANS AT EACH CYLINDER END PORTION FOR REGULATING THE PASSAGE OF FUEL TO EACH CORRESPONDING CYLINDER END PORTION AND ALTERNATE PRESSURE AND SUCTION EXERTING MEANS AT EACH CYLINDER END PORTION RESPONSIVE TO BACK AND FORTH MOVEMENT OF SAID PISTON MEANS FOR ACTUATION IN FORWARD DIRECTION BY SAID PISTON MEANS DURING THE COMPRESSION STROKE OF THE CORRESPONDING END OF THE PISTON MEANS TO ATTAIN A PREDETERMINED COUNTERPRESSURE TO FORCE FUEL THROUGH THE CORRESPONDING VALVE MEANS UPON ATTAINING THE PREDETERMINED COUNTERPRESSURE AND INTO THE CORRESPONDING CYLINDER END PORTION AND THEREAFTER ACTUATION IN THE RETURN DIRECTION TO ATTAIN SUFFICIENT SUCTION TO DRAW ADDITIONAL FUEL WITHIN SAID ALTERNATE PRESSURE AND SUCTION MEANS FOR THE NEXT PRESSURE ACTUATION.

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