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Патент USA US3077199

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Feb. 12, 1963
H. HERRMANN
3,077,188
PISTON IMPACT MOTOR
Filed April '7. 1960
2 Sheets-Sheet l
/NVENTORÍ
[ffl/1107
Feb. 12, 1963
H. HERRMANN
3,077,188
PISTON IMPACT MOTOR
Filed April 7. 1960
2 Sheets-Sheet 2
lN VEN TOR .'
~`r Q; g E
HEavaT HERR/10AM#
BY
'
SPM/My
n n’o KM? V5
Unite States ¿Patent Office
Bßïllââ
Patented Feb. l2, 1.8%3
2
Helmut Herrmann, @ritiri-nen, Germany, assigner to
‘Gerwerlïschait
Westfalia, Westphalia, Gen
many, a German corporation
During the baci: and forth movement of the flange ex
tension within the annular extension chamber as the piston
is operated, a suction is created on one side of the ñange
extension whereby intake gas or air is drawn through
the checli valve into the corresponding portion of the an
Filed Apr. 7, i969, Ser. No. 2%,625
Claims priority, application Germany Apr. ld, 14.959
1S Claims. (Qi. 1235-46)
nular 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 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.
ber on the other side is forced through a unilateral con
Various piston impact motors have been heretofore
provided which have a double chamber cylinder contain
ing 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 Íor 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 oscil
lations 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 oper
able 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 accord
ance with the invention, and
FEGURE 2 is a schematic sectional View of a further
the corresponding portion of the annular extension charn
duit to a corresponding cylinder chamber. Hence, dur
ing operation of the piston Within the cylinder each cylin
der 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 ex
tension 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 dur
ing
second half of the cycle.
in accordance with the preferred embodiment, a uni
lateral 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 eiîected in order to start
the motor, since compressed gas may pass from the cor
responding rcservoirs alternately into the cylinder cham-y
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.
bers to effect a back and forth movement of the piston
until the motor is started.
cylinder beine provided with combustible gas intake means
to each chamber of the double cylinder. A pressure re
During baci; and forth movement or" the double piston,
tions, and generally comprises a motor cylinder having 40 the pressure exerting means is correspondingly actuated
to alternately force fuel through the fuel injection valve
a motor piston movable back and forth therewithin, the
and exhaust gas outlet means as well as iuel iniection
snonsive fuel injection valve is provided for each chamber
means.
of the cylinder so ‘as to alternately iniect fuel into the
The fuel iniection means includes a pressure re
sponsive fuel . ctio-n valve for regulating the passage
of fuel to the cyli
r and pressure exerting means re
sponsive 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. Fïhe
piston may be constructed es a free living double piston Cu O
slidable baci:
forth wit' n the cylinder. The cylin
der may be constructed as
double chamber cylinder,
each che ther hai/ins fuel injection ineens and exhaust
outlet means.
thus,
impact piston alternately
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 ar
ranged with a cone end for attaininzi the sealing abutment
and is preferably spring loaded. Upon reaching a pre
determined 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.
'
^oves from one end of tl‘e cylincer to the other, alter
nately into and out of the corresponding chamber of
trie
' cylinder in accordance with the Z-cycle diesel tech
A pressure exerting means responsive to back and’fort'h
movement of the piston is provided preferably for- each
of the flange extension with respect thereto.
piston is connected for delayed action opening of a fuel
i
fue?> injection valve. The pressure exerting means ger1-.`
erallv tal/.es the form of a pump means operating to force
The impact piston is preferably constructed with piston
fuel through the valve due to the pre-determined counter-y
ends of the seme di
vv ich move into and out of 60 pressure exertedV by the fuel against the valve in conse
the corresponding chamber of the cylinder cooperating
quence of bumping actuation. The pump is actuated in
therewith. On the intermediate portion of the piston an
forward direction during the comnressio'n stroke of the
extension ilange is provided which is received Within an
corresoonding end of the double piston with respect there
intermediate annular extension chamber located between
to and is actuated in a return direction bv suitable resilient
the end chambers of the cylinder.
urrinrz means such as a compression spring so as to attain
Unilateral air inlet
valves are provided on the
suilicient suction within the pump means to draw addis
annular extension chamber on each side of the flange ex
tional fuel for the next pumping actuation.
tension. Moreover, each end of the double piston is
rl`he pump may include a pump cylinder communicat
provided with a unilateral conduit for passage of intake
ing with the fuel conduit for the motor, in which a pump
air or combustion
into its corresponding cylinder
piston is slidably received and normally resiliently urged
chamber from the intake check valve on the opposite side
in return direction outward of the cylinder. The pump
nique.
8,077,188
3
intake' valve for the pump upon forward movement of
the pump piston into the cylinder a pre-determined dis
tance. 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
tion 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
the pump piston end remote from the cylinder slidably 10 these elements is spring loaded under pre-determined ten
extends into the annular extension chamber of the motor
sion, so as to effect operation in accordance with the fore
cylinder and into the path of the flange extension there
going.
within. The pump piston is mounted for forward move
ment by contact with the flan-ge extension in the same lon
18 having two end chambers 45 and an intermediate an
Referring to the drawings, FIGURE 1 shows a cylinder
nular extension chamber 11, Within cylinder 10 a double
gitudinal direction as the flange extension in accordance
piston 12 is movable back and forth, piston 12 being
with this embodiment. Thus, the movement back and
provided with an intermediate flange portion 13 radially
forth of the flange extension drives the pump piston in
outwardly projecting into annular chamber 11. A fuel
forward direction to operate the pumping action.
tank 14 flow communicates via a line 15 with a valve
The pump piston in accordance with this embodiment is
provided with a projection bar for urging an auxiliary 20 means located at either side of cylinder 10 with corre
sponding inlet lines 16 leading to the corresponding ends
piston correspondingly in the forward direction of move
of cylinder 1d. Each chamber 4S of cylinder 10 is pro
ment of the pump piston. The auxiliary piston is mounted
vided with a plurality of outlet openings 17 for exhaust
in an auxiliary cylinder having both ends in bilateral re
ing combustion gases from the diesel piston impact motor.
cycle flow communication with one another remote from
Each end of piston 12 is provided with a central bore 1S
the auxiliary piston. One path of ñow communication
communicating with a corresponding lateral bore 19 pass.
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
ing to the opposite side of iîange 13 with respect thereto.
The front surfaces of the corresponding ends of piston are
provided with a check valve 2t?, in each case, permitting
opposite side of the auxiliary cylinder. The other path of
flow communication includes a throttle for restricting the 30 unilateral iiow of gases or air to be combusted into the
corresponding chamber 45. The other end of the conduit
flow of the fluid to the opposite side of the auxiliary cylin
defined by bore 1S and bore 19 opens into annlar chamber
der. The end of the auxiliary piston remote from the pro
11 on the opposite side of ilange portion 13. Each side
jection bar contains a link bar pivotally mounted at one
of annular chamber 11 is provided with a check valve 21
end thereon and linkably seated at the other end within
a recess in the pump piston. The link bar is urged into 35 defining an air or combustion gas inlet.
Thus, as piston 12 moves back and forth within cylin
contact with the fuel intake valve to open the same in
der 1t), flange portion 13, in turn, moves back and forth
delayed sequence after the pump piston has moved for
within annular chamber 11. During this back and forth
ward a pre-determined distance. Since the link bar is
connected to the auxiliary piston which moves in con
movement, suction is created on one side of flange por
sequence of the forward urging of the projection bar, as 40 tion 13 within annular chamber 11 so as to open check
valve 21 on that side of annular chamber 11 whereby
well as to the pump piston itself, the link bar will make
the delayed sequence contact with the fuel intake valve
air from the atmosphere or combustion gas fed from a
in the desired manner. Due to the unilateral check valve
source on the other side of check valve 21 may be drawn
and throttle arrangement of the auxiliary cylinder, the
Within annular chamber 11. Since during this forward
auxiliary piston, and in turn the link bar will move in 45 movement check valve 26 remains closed, there is no
the return direction slowly so as to cause the fuel intake
equalization of pressure between chamber 4S on the op
valve to correspondingly close slowly. This permits ad
posite side and the portion of annular chamber 11 draw
ditional fuel to be drawn through the intake valve into
ing in the air or combustion gas. At the same time
the pump cylinder for the next pumping actuation. Since
with respect to the portion of annular chamber 11 on
the pump piston is normally resiliently urged in the return 50 the opposite side of flange portion 13, air or combus
direction, the same will pass out of the cylinder faster than
tion gas disposed within annular chamber 11 is forced
the return of the auxiliary piston, the link bar and the
by pump action through bore 19 and bore 18 to the
intake fuel valve.
chamber d5 on the other side of cylinder. Since check
ln accordance with another embodiment of the inven
valve 21 is a unilateral check valve, no air will flow
tion, the pump piston end remote from the pump cylin 55 out of annular chamber 11 through the check valve at
der is received within a further cylinder which is in flow
that side but will only pass through bore 19 and bore
communication with the corresponding cylinder chamber
18 into the oppositely disposed chamber 45. Since check
of the mo-tor cylinder. In this way upon compression of
valve Ztl is a unilateral check valve, this gas or air un
the corresponding motor piston end in the cylinder cham
der the pressure created in annular chamber 11 is forced
ber, gases within the cylinder chamber will be forced into 60 into the chamber ¿i5 in communication therewith.
the further cylinder causing movement of the pump piston
A pressure reservoir 22 having two separate pressure
in forward direction in conjunction therewith. In this
chambers is arranged with respect to cylinder 10 so that
instance,-the auxiliary cylinder is also mounted for move
each chamber of pressure reservoir 22 is in separate
ment in the direction of movement of the pump piston;
flow communication via a line 23 with a corresponding
however, `the auxiliary cylinder is not urged by a' projec 65 end of cylinder :tu by means of unilateral check valve
tion bar but instead is in unilateral flow communication
25. During the back and forth movement or” piston 12
with the corresponding cylinder chamber of the motor.
within chamber 10, enough pressure is generated to force
Similarly, therefore, upon compression of the moto-r pis
a portion of the gases within each chamber 45 through
ton combustion gas is forced therefrom into the auxiliary
unilateral check valve 25 and conduit 23 into a corre
cylinder flow communicating therewith causing movement 70 sponding chamber of pressure reservoir 22. After a
of the auxliary piston in the forward direction. The
lluid passing into the auxiliary cylinder is released there
certain period operation, each separate chamber of pres
sure reservoir 22 will contain combustion gases or air
from through a restricted outflow opening. Due to the
up to a pre-determined pressure.
unilateral flow communication and the restricted outflow
Advantageously, each line 23 is in further discontinu
opening, the auxiliary piston moves in the return direc 75 ous flow communication with a corresponding chamber
5
3,077,188
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 cyl
inder 1d. Since check valves 2S are unilateral check
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 move
ment 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 pro
valves, they will keep the gases within pressure reservoir
vided having a suction piston ¿t2 normally spring urged
22 under the pre-determined desired pressure, the re
in sealing abutment so as to close valve 4l.
lease 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 communicat
ing fuel lines 12S with each chamber ¿i5 of cylinder lll.
A cone pointed spring loaded needle piston 2’7 is urged
by spring 23 into closing engagement with needle valve
mote 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
At the re
portion i3 and proiection 32, respectively, link bar 33
will be correspondingly urged in the same direction
26 in rest position. Needle Z7 may be urged out of 15 against projection Il@ so as to unseat piston ¿l2 from seal
ing engagement. lt will be appreciated that piston 3i?
closing contact with needle valve 26 upon the reaching
moves Within cylinder 29 so as to force fuel disposed
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
within cylinder 29, conduit 33, and line lid through needle
valve 26 and into the corresponding cylinder chamber
motor of the invention includes a pump assembly ar 20 ¿i5 before link bar 38 urges against projection dll to open
valve 4l. As piston 3@ returns to its original position a
ranged at either side of the cylinder if?. Thus, a pump
suction is created within the cylinder 29 which causes fuel
piston 3d is slidably arranged at one end within a pump
from line l5 to be drawn through valve di and into cyl
cylinder 29 and at the other end within annular cham
inder 29, link bar 38 having reached projection dit! by this
ber 1l by means of an opening in the side wall of cham
ber il. Pump cylinder 29 is in flow communication 25 time to cause the movement of valve piston 42 to open
valve dll.
with fuel lines lle by means of conduit 33. Pump pis
While piston Sill returns to its original position with
ton 30 is normally urged outwardly of pump cylinder
reasonable speed, piston 36 and piston 37 are returned to
29 by means or" spring 3l. As double piston l2 moves
their original position more slowly due to the action of
back and forth within cylinder lll, flange portion 13 cor
respondngly moves back and forth within annular cham 30 throttle opening 44. This causes a lag in the closing of
ber lll so as to abuttingly engage pump piston 3d, forc
ing 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, dis
placed frorn sealing abutment with needle valve 26 open
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,
ing the same for flow of `fuel to the motor.
35, piston rod 3'7, cylinder 35, conduits 3d and fifi, check
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
valve d6, throttle opening rif-l, and link bar 38 will be pro
cation with the other end, remote from piston 36, by
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 lâ 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 corre
sponding ends of cylinder
Each end of cylinder l@ is
in the same way provided with outlet openinvs i7 for ex
vided in each instance. The same may ’oe said for pro
jection di), valve piston ¿i2 and valve lil as well as needle
valve 26 and needle 27.
35. Piston 36 is mounted on a piston rod 37 for move
in operation fuel from fuel tank i4 may pass through
ment therewith within cylinder 3S. A link bar 33 is piv
otally connected to piston rod 37 at one end and link 45 each conduit l5 to a fuel intake valve 4l for passage there
through to line i6 and accordingly into chamber during
abiy seated within a recess 39 delined in piston 3ft at
the back and forth movement of the double piston l2.
the other end. A pr jecticn bar 32 is mounted on the
Valve ¿il together with pump piston 3i? and pump cylinder
end of piston Sti remote from cylinder 29 for urging
29 regulate the amount of fuel to be injected through
against the opposite end of piston rod 37. ln this man
needle valve 2d. Puel passage through needle- valve 2d
ner, as piston E@ is moved further within cylinder Z9
takes place in a shock-like manner due to the sudden for
in consequence of the force exerted by flange portion
ward movement of pump piston Sil in consequence of the
i3, projection 3.?, will force piston rod 35' and in turn
forward movement of ilange portion i3. rThe piston
piston 36 in the same direction of movement as pis
impact motor of the invention operates with diesel fuel
ton 30.
under high compression within the chambers ¿l5 to force
Each end of auxiliary cylinder 3S is in dow communi
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 per
mits 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 con
duit 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 with
hausting spent gases.
ln accordance with the embodiment of FÍGURE 2,
fuel
line l5 iiow communicates through valve @il with lines
out lag.
70 dil and the corresponding end of cylinder l@ upon passage
However, upon the return movement of piston 3%' and
through the needle valve having a cone ended needle 62
projection 32, piston 36 will return only slowly in conse
normally spring urged in closed position. In this in
quence of spring urgence in the return direction of piston
stance, a pump piston di? is provided at one end within a
36 since check valve 46 will be closed to return ñow so
cylinder portion di and at the other end within a large-r
that the duid within cylinder 35 can only pass through
cylinder zi'ì’ ilow communicating with the corresponding
end of cylinder 1t?. Within cylinder d'7 piston @i6 is pro
vided with a correspondingiy larger piston head 5S, piston
46 being normally urged by spring 59 out of cylinder 6l
and into cylinder 47. Cylinder 14j is also in flow com
munication through line 54 with an auxiliary cylinder 48
by means of a unilateral check valve 53.
Piston 49, nor
mally 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 for
ward movement of piston 46 and piston 4,9, respectively,
the outlet openings will be sealed otf from the corre
sponding 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 move
ent 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 por
tion, 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 de
creases as the pressure in the annular chamber on the
opposite side of the frange portion increases.
During these operations, the pressure reservoir is ñlled
link bar Sil’ will be urged against valve piston fr?. to open 20 with air or gases in increments until the pressure reser
voir reaches the equilibrium pressure with that effected
The operation in this instance is the same as
within the cylinder chambers. The pressure reservoir
that described for the embodiment shown in FÍGURE l
thereafter is available to start the piston impact motor
whereby upon initial forward movement of piston 46 with
by merely opening the `by-pass valve alternately on each
in cylinder 6l fuel within line 6ft is forced against needle
side of the cylinder so as to force air against correspond
62 so as to unseat the same and allow the passage of the
ing sides of the double piston whereby the piston is
fuel into the corresponding end of cylinder lâ. Since
moved back and forth within the cylinder in shock-like
there is a 'lag of movement of piston rod 52 and link bar
the same.
manner so as to energize the pump means and force fuel
into the cylinder chambers for effecting diesel motor
as to allow the passage of fuel through valve Lill in re
sponse to the suction created by the return movement of 30 operation. The piston impact motor fuel supply may be
Sil, valve piston d2 will be opened by delayed action so
piston 45 out of cylinder 6i.
The operation of the pump device in this embodiment
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
is carried out by the back yand forth movement of the
of the motor will, therefore, easily be attained to pro
double piston within cylinder l@ in such a way that upon
the compression stroke, combustion gases or air will be 35 duce linear oscillations within »a wide range of frequencies
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 cylin
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 illustra
der l@ is in communication via line 54 with cylinder 4S,
through check valve 53, addition-al combustion gases or 40 tion, it will be obvious to those skilled in the art that
various modifications and changes may be made Without
air will force piston d@ in the same direction as that of
departing from the spirit and scope of the invention which
piston 46. The delayed action return of piston 49 is
is to be limited only by the scope of the appended claims.
carried out by reason of the restricted outlet 57 in cylin
What is claimed is:
der 48. Thus, while spring 55 will urge piston d@ in
l. Piston impact diesel motor for the production of
the return direction, the air or compressed gases within
direct mechanical linear oscillations which comprises a
cylinder 4S will only pass out of opening 57 at a com
motor cylinder means, a free dying impact motor piston
paratively slow rate. Accordingly, link bar 5h’ will
move in the return direction under deiayed action so that
means lmovable back and forth within said cylinder means,
said piston means being constructed and arranged for
suction of fuel from line lâ through valve di and into
line 6@ and cylinder 61 may take place upon the return 50 imparting direct mechanical linear oscillations to said
cylinder means and operatively dividing said cylinder
movement of piston 46 within cylinder 47.
means into two corresponding end portions, said cylinder
It will be appreciated with respect to FIGURES 1
means having combustible gas intake means and exhaust
and 2 that the amount of fuel injected on each side of
gas outlet means for each end portion, and fuel injection
cylinder l@ will be determined by the amount of lag be
tween the movement of the pump piston and that of the 55 means including pressure responsive fuel injection valve
means at each cylinder end portion for regulating the
auxiliary piston. Thus, the pump piston is urged in for
passage of fuel to each corresponding cylinder end por
ward direction a certain distance before the auxiliary
tion and alternate pressure and suction exerting means
piston begins to move (see FIGURE l) or the auxiliary
at each cylinder end portion responsive to back and forth
piston moves forward more slowly than the pump piston
due to the air outlet release (see outlet 57, FIGURE 2). 60 movement of said piston means for actuation in forward
direction by said piston means during the compression
In this way, fuel is forced by the pumping action past
stroke of the corresponding end of the piston means to
the needle valve aud into chamber 45 before the fuel
attain a predetermined counterpressure to force fuel
intake valve 4l is opened. The fuel intake valve 5l is
through the corresponding valve means noon attaining
opened actually toward the end of the forward stroke of
the pump piston in conjunction with the forward stroke 65 the predetermined counterpressure and into the corre
of the auxiliary piston whereupon fuel may be drawn
sponding cylinder end portion and thereafter actuation
in the return direction to attain sutiicient suction to draw
past valve 4i and into the pump cylinder in consequence
additional fuel within said alternate pressure and suc
of the suction created by the return movement of the
tion means for the next pressure actuation.
pump piston. Due to the lag occasioned by the slow
2. Piston impact diesel motor for the production of di
return movement of the auxiliary piston, the fuel intake 70
valve remains open during the return stroke of the pump
rect mechanical linear oscillations which comprises a
piston to allow additional fuel to be drawn into the pump
double chamber motor cylinder, a free dying impact mo
apparatus.
It will be noted that npon the start of a compression
tor double piston movable back and forth within said
cylinder and constructed and arranged for imparting di
stroke by the double piston within the double cylinder,
rect mechanical linear oscillations to said cylinder, said
n
3,077,185;
9
l@
piston being provided with an intermediate flange por
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
tion having an outside diameter larger than that of the
ends of the double piston and said double chamber cylin
der being provided with an intermediate annular exten
sion chamber, slidably receiving said flange portion, said
cylinder having combustible gas intake means and eX
haust gas outlet means, and fuel injection means including
wherein said valve means includes a valve opening and
a valve piston normally resilientlyv urged in sealing abut
ment with said valve opening, said valve piston being dis
placed from said sealing abutment to open said valve
pressure responsive fuel injection valve means provided
for each chamber of the cylinder for regulating the pw
means upon the attaining of a predetermined counter
means, each pressure exerting means including a pump
means for forcing fuel through said valve means and into
wherein said valve piston is spring loaded.
the corresponding cylinder chamber in conjunction with
wherein a pressure exerting means responsive to back and
forth movement of said piston means is provided for
pressure exerted thereagainst.
sage of fuel to the corresponding chamber and a corre 10
7. Piston impact diesel motor according to claim 6
spending pressure exerting means responsive to back and
wherein said valve piston has a cone edge for the sealing
forth movement of said piston provided for operatively
abutment with said valve opening.
v
controlling each pressure responsive fuel injection valve
8. Piston impact diesel motor according to claim 7
said back and forth movement upon the attaining of a
g
9. Piston impact diesel motor according to claim 5
predetermined counterpressure by said pump means, each
each of said pressure responsive fuel injection valve
said pump means being actuated by said double piston
means.
during said back and forth movement first in forward 20
10. Piston impact diesel motor according to claim 9
direction during the compression stroke of the corre
wherein said pressure exerting means is a pump means
sponding end of the double piston to attain said counter
for forcing fuel through said valve means upon the attain
pressure and force said fuel through the corresponding
ing of a predetermined counter-pressure by said pump
valve means, and thereafter in the return direction to at
means.
tain sufficient suction to draw additional fuel within said 25
l1. Piston impact diesel motor according to claim 2
pump> means for the next pumping actuation.
wherein said pump means includes a pump cylinder com
3. Piston impact diesel motor for the production of
direct mechanical linear oscillations which comprises a
double chamber motor cylinder, a free flying impact mo
tor double piston movable back and fort-h within said
cylinder and constructed and arranged for imparting di
rect mechanical linear oscillations to said cylinder, said
piston being provided with an intermediate iiange por
tion having an outside diameter larger than that of the
ends of the double piston and said double chamber cyl
inder being provided with an intermediate annular ex
municating 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 cyl
inder, 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
tension chamber, slidably receiving said flange portion,
which causes additional fuel to be drawn into the pump
and fuel injection means including pressure responsive
fuel injection valve means for regulating the passage of
cylinder for the next pump-ing actuation.
fuel to -said cylinder and pressure exerting means respon
sive to back and forth movement of said piston for al
ternately forcing fuel through said valve means and into
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
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
each said cylinder double chamber in conjunction with
has been opened by the pump piston of said pump means,
said back and forth movement, said annular extension
said valve is closed by delayed action permitting additional
chamber being provided with combustible gas intake 45 fuel to be drawn therethrough into the pump cylinder for
check valve means on each side of said flange portion
the next pumping actuation.
and each end of said double piston being provided with
13. Piston impact diesel motor according to claim 12
a unilateral conduit for passage of combustible intake
wherein the pump piston end remote from said pump
gas into the corresponding cylinder' chamber therefor
cylinder slidably extends into the annular extension cham
from the check valve means on the opposite side of said
ber of the motor cylinder means and into the path of
iiange portion with respect thereto, and said cylinder
said flange portion, said pump piston being mounted for
chambers being provided with outlet openings defined
forward movement by contact with said flange portion in
therein for exhaustinng the combustion products formed,
the same longitudinal direction as said flange portion.
whereby during back and forth movement of said flange
14. Piston impact diesel motor according to claim 13
portion within said annular extension chamber, a suction 55 wherein said pump piston is provided with a projection
is created on one side of said flange portion and intake
bar for urging an auxiliary piston correspondingly in the
gas is drawn through said check valve means into the
forward direction of movement of said pump piston, said
corresponding portion of said annular extension cham
auxiliary piston being mounted in an auxiliary cylinder
ber on said one side, and a compression is created on the
having both ends thereof in bilateral recycle flow com
other side of said flange portion and intake gas disposed 60 munication remote from said auxiliary piston, one path
in the corresponding portion of said annular extension
of flow communi-cation including a unilateral check valve
chamber on said other side is forced through a unilateral
for passing ñuid from one side of said auxiliary cylinder
conduit to a corresponding cylinder chamber.
into which said auxiliary piston moves upon actuation by
4. Piston impact diesel motor according to claim 3
said profection bar to the opposite side of said cylinder,
wherein a unilateral conduit is provided extending from 65 the other path of flow communication including a throttle
each end of said double chamber cylinder to a corre
for restricting the flow of said liuid to said opposite side,
sponding reservoir for forcing iiuid from each end of
the end of said auxiliary piston remote from said projec
said cylinder under compression during back and forth
tion bar having a link bar pivotally conected at one end
movement of said double piston to said reservoir, each
thereto and linkably seated at the other end within a
said reservoir being in by-pass valve communication with 70 recess in the pump piston, said link bar being urged in con
the corresponding end of said double chamber cylinder
tact with the fuel intake valve to open the same in delayed
for starting the back and forth movement of said piston
sequence after the forward movement of said pump piston
upon opening of the by-pass valve communication to per
and said auxiliary piston a predetermined distance, said
mit the return ñow of said fluid under compression.
auxiliary piston due to said unilateral check valve and
5. Piston impact diesel motor according to claim 3 75 said throttle and in turn said link bar moving in the re
enviarse
11
12
turn direction slowly so as to cause said fuel intake valve
to close slowly so that additional fuel may be drawn
same in delayed sequence after the forward movement of
said pump piston and said auxiliary piston a predeter~
mined distance, said auxiliary piston due to said uni
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
lateral 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
spring loaded.
16. Piston impact diesel motor according to claim 12
close slowly so that additional fuel may be drawn there
wherein the pump piston end remote from said pump
cylinder is received within a further cylinder in flow com
muncation wtih the corresponding cylinder chamber of
said motor cylinder means whereby upon compression of
actuation.
the corresponding motor piston means in said cylinder
chamber, ñuid is forced into said further cylinder
for movement of said pump piston in the forward direc 15
tion.
-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 correspond
ing movement in the direction 4of movement of said pump 20
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 cylin
der chamber, ñuid is forced into said auxiliary cylinder 25
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
through intr;~ the pump cylinder for the next pumping
18. Piston impact diesel motor according to claim 17
wherein said pump piston and said auxiliary piston are
spring loaded.
References Cited in the ñle of this patent
UNITED STATES PATENTS
1,254,097
Weiss ________________ __ Jan. 22, 1918
1,535,659
1,858,102
1,980,997
2,344,058
2,405,043
Fog _________________ __ Apr. 28,
McKeown ____________ _- May 10,
Jenkins ______________ __ Nov. 20,
Pescara ______________ .__ Apr. 14,
Meitzler _____________ __ July 30,
1925
2,463,051
1932
1934
1944
1946
Pescara ______________ __ Mar. l, 1949
2,944,535
Fikse _______________ __ July 12, 1960
692,863
Germany ____________ __ June 27, 1940
FOREIGN PATENTS
OTHER REFERENCES
Cockerell, German application 1,012,777, printed July
one end thereto and linkably seated at the other end 30 25, 1957.
within a recess in the pump piston, said link bar being
urged in contact with the fuel intake -valve to open the
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