DE2404655A1 - WORK AIR COMPRESSOR MACHINE - Google Patents

Description

Dr. F. Zumsteln sen. · Dr. E. Assmann Dr. R. Koenlgsberger - DIpI.-Phys. R. Holzbauer - Dr. F. Zumsteln Jun.

PATENT LAWYERS TELEPHONE: COLLECTIVE NO. 225341 TELEX 529979 8 MUNICH 2.

BRAUHAUSSTRASSE 4 TELEGRAMS: ZUMPAT

CHECK ACCOUNT: MUNICH 91139-809. Bank code 70010080 BANK ACCOUNT: BANKHAUS H. AUFHÄUSER ACCOUNT NO. 397997. BLZ 7OO3O6OO '

6 / Li
PG / 74/1051

Takahiro UENO, Wakayama, Japan

Working air compressor machine

SS SS SS SS SS SS SS SS SS SS SS SS SSS SS SI SS SS SS SS SS SSS SS SS SS SS SS ^ S SS SS SS SS

The invention relates to a machine which is equipped so that it can serve as an air compressor, in particular for an internal combustion engine,

Furthermore, the invention is applicable to machines Every type such as in gasoline engines or diesel engines and four-stroke engines or two-stroke engines or rotary engines, further in vehicles, ships, aircraft \ ma are installed. For the sake of simplicity, the description of the subject matter according to the invention relates exclusively to a machine installed in vehicles.

Such a machine compresses a mixture of gasoline and air in the compression chamber, or some fuel is injected into the compressed air, is ignited,

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to generate thermal energy that is converted into mechanical energy will. In every machine there is therefore a process of compression, and when the fuel supply is cut off, and while the machine is only being supplied with air, the air is compressed in compression chambers and then expands to be exhausted outward through the exhaust ports as long as the engine and vehicle are in that the machine is built in have kinetic energy.

Kinetic energy that acts on a machine is, on the one hand, the energy of the machine itself and, on the other hand, the Energy of the vehicle in which the machine is installed.

In order to control the kinetic energy, a mechanical braking device, for example, is conventionally used in order to kinetic Used to absorb energy

When stopping the machine or slowing down the machine has stopped the fuel supply and only air is supplied, which however contains engine oil, and the valve actuation of the exhaust ports is changed, the kinetic energy of the machine itself is directed so that the air sucked into the compression chambers is compressed and "consequently absorbed by the air as compression energy will. To achieve the above-described operation, the kinetic energy of both the vehicle and the machine is used consumed and the speed of the vehicle is controlled.

When no fuel is supplied in the operation described above, but air only takes up the space of some compression chambers, while the other chambers have a working machine function air compression is achieved in stages.

The control function in the inventive subject matter

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indicates a consistent way of working, which the vehicle and occupy the machine in when the machine is performing compression by working as an air compressor.

Known braking devices are friction brakes and engine brakes. In the case of friction brakes, the brake lining is worn down, which causes environmental pollution by asbestos. Engine brakes emit incompletely burned gas, which not only pollutes the environment, but also causes unwanted fire, unnecessary consumption of engine oil, afterburn and / or engine damage - all result Motor vehicle malfunctions. Furthermore, a lot of errors occur with engine brakes, especially with diesel engines, such as e.g. Kickback, all of which cause excessive and unnecessary noise.

The article of the invention can operate to perform an air compression process, and consequently compressed air and a resultant control force is generated therefrom, with all air chambers of the machine in operation are not supplied with fuel, but only with air in order to carry out the compression process.

Furthermore, such a machine works as an air compressor by increasing the number of valve actuations of a four-stroke engine can be doubled by exchanging the gas that supplies the compression chambers, and by changing the flow of the gas discharged from the compression chamber is changed.

Furthermore, the subject matter of the invention works as an air compressor by using the two-stroke engine with intake ports and Exhaust passages, with intake valves and exhaust valves therein and with means for operating the valves, as is the case with the four-stroke engine, so that the flow of the supply gas and the exhaust gas

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can be changed with the machine working as an air compressor.

The machine according to the invention also achieves a compression process by using a rotary motor with inlet and outlet ports is provided in such a way that the positions of these openings are point-symmetrical to the inlet and outlet openings are located, and that these inlet openings and outlet openings are provided with valves and actuating devices therefor are.

Furthermore, the machine according to the invention can generate compressed air in some of the compression chambers of the machine work as an air compressor, and at the same time the others work as a work machine.

In the case of the object according to the invention, wherein the working machine has only a single compression chamber, this becomes rapidly Compression chamber as an air compressor operated by the kinetic energy of the vehicle itself, and the work machine is operated to generate compressed air.

The subject matter of the invention can be used as an extremely effective and non-polluting engine brake that does not have the disadvantages the known engine brakes, work.

Furthermore, the object according to the invention should be designed in this way be that the valve lift can be changed by increasing the steps of the valve switching device and the The plunger can be held in a different position, which is in Engagement with the beveled nooke.

The machine according to the invention can also be designed in such a way that a power reduction device (usually known under the name of a load reducer) is provided, whereby the working machine constantly acts as an air compressor

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works while the other two valves are kept closed or open, or that one of the valves is constantly closed, while the other is constantly kept open a little.

Furthermore, in the machine according to the invention, the working machine be provided with automatic valves for the discharge, which also have automatic valves for the suction, so that the work machine easily performs a compression operation and an increase in pressure at the proper time the compressed air causes.

The object according to the invention can also be designed so that an outlet valve for the residual air, which is in the dead space discharges any compressed air that is present, is provided when the work machine is used as an air compressor, and thus the intake air by a considerable amount increased.

Furthermore, the machine according to the invention can be equipped with "an auxiliary valve actuation device be provided, which increases the elongation force of the valve springs, using them as a device for Application of the resistance against a strong counterforce is used, which causes a higher speed of the work machine or works during the compression process of the working machine so that the actuation of the opening and closing of the valves " can be made possible exactly.

According to the invention, this object is to both the mode of operation of a work machine and that of an air compressor at the same time, solved in the following way:

A four-stroke gasoline or diesel engine has one compression stroke for two strokes of the piston, the valve actuation cam the working machine is designed so that two strokes of the KoI-

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· "O ■ ·

bens the opening and closing of the inlet valve and the double the number of actuations of the exhaust valve to achieve four cycle steps, such as suction, discharge, suction and discharge strokes, to need in this regard.

On a two-stroke gasoline or diesel engine, an inlet port, an exhaust port, an intake valve, an exhaust valve are additionally provided, and furthermore an actuator is provided therefor available.

In a rotary engine, an intake port and an exhaust port are added, and exhaust valves at least for the additionally provided outlet channel and for the already existing outlet channel and valve actuation devices for it are also available.

The entire machine described above also has devices for actuating the valves for a compression process, a device for the supply only if necessary the compression chambers and a device for changing the flow path of the gas.

In a machine according to the invention, the oiling of the machine has not of great importance, but understandably it is necessary that when the fuel supply is stopped, a compression operation is required to cause motor oil to be mixed with the air.

Regarding the invention, a work machine means an internal combustion engine J and an operation as a work machine means an operation including four tacts of the work machine; these are: sucking in, compressing, Expanding and discharging, and functioning as a compressor means an operation that includes a suction process and a process for compressing the sucked air and

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then to expel the air includes.

Furthermore, there are two ways that the machine performs a compression process executes. One of them is to first separate the plurality of compression chambers into two groups so that one group works as an air compressor while the other works as a work machine. Lead in the other way all compression chambers or a part thereof from a compression process, so that the control of the engine of the motor vehicle by slowing down or stopping a moving motor vehicle can. However, if there is only one compression chamber, the compression process can only be achieved when the vehicle is moving slowed down.

Preferred embodiments of an inventive Subject are explained in more detail with reference to the accompanying drawing. Show it:

1 shows a plan view of an object according to the invention in a schematic representation; Fig. 2 a. Vertical sectional view of Fig. 1;

3 is a schematic view showing a compression chamber shows in a device according to the invention;

4 is a front view of the valve timing cam of FIG device according to the invention;

Fig. 5 is a sectional view taken along line V-V of Fig. 4;

6 is a sectional view taken along line VI-VI of FIG Fig. 4;

Fig. 7 is a plan view of a cam of the first embodiment example in which a power reduction device is provided on the valve actuation cam of the work machine is; .

Fig. 8 is a sectional view taken along the line VII-VIII

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of Fig. 8;

FIG. 9 is a sectional view taken along line IX-IX of FIG

Fig. 7;

Fig. 10 is a plan view of a cam of the second embodiment the valve actuation cam;

11, 12, 13 are partial sections of camshafts in FIG Working machine;

14 shows a schematic view of a cam switching device the working machine;

Fig. 15 is also a schematic view of a modified one Embodiment of the cam switching device;

Fig. 16 is a front view of a cam for. an outer valve of the third modified embodiment of FIG Valve actuation cam;

Fig. 17 is a sectional view taken along line XVII-XVII of Fig. 16;

Fig. 18 is a plan view of a cam for an intake valve of the third embodiment of the valve operating cam ;

Fig. 19 is a sectional view taken along line XIX-XIX of Fig. 18;

Fig. 20 is a plan view of a fourth embodiment the valve actuation cam;

Fig. 21 is a sectional view taken along line XXI-XXI of Fig. 20;

Figure 22 is a sectional view taken along lines XXII-XXII of Fig. 20;

23 shows a view of a flow profile of the gas Sir φι four-stroke engine in a schematic representation;

24 is a modified exemplary embodiment of the flow profile of the gas in the four-stroke engine, also in a schematic representation;

Figure 25 is a schematic view of an improved two-stroke gasoline engine;

26 is a schematic view of an improved modified embodiment of the two-stroke gasoline engine

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Depiction;

Fig. 27 is a top plan view of a valve operating cam in the two-stroke engine;

Fig. 28 is a sectional view taken along line XXVII-XXVII of Fig. 27;

Figure 29 is a perspective view of an alternate embodiment of a beveled cam;

Fig. 30 is a plan view of a modified embodiment of a valve operating cam in the two-stroke gasoline engine;

Fig. 31 is a sectional view taken along line XXXI-XXXI of Fig. 30;

32 is a view of a modified embodiment of a cam and a cam switching device as FIG Partial section in fragmentary. · And partly schematic Depiction;

33 is a schematic view of an improved two-stroke cross-scavenging diesel engine;

34 is a view of an improved two-stroke diesel engine with direct current purging in a schematic representation;

35 shows a view of a flow profile of the gas for a typical two-stroke engine, the three compression chambers has a schematic representation;

36 is a view of a modified embodiment of a flow path of the gas for the three compression cylinders in a schematic representation .;

37 is a side elevational view of an improved rotary motor having two rotors in cutaway;

Fig. 38 is a sectional view taken along the line XXXVIII-XXXVIII of Fig. 37;

39 is a schematic plan view of an embodiment of a valve device which opens and closes the side channels of the rotary motor;

40 ″ is a view in detail of a further exemplary embodiment the valve device, which the side channels

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of the rotary motor Opens and closes with a representation in an expanded arrangement;

Fig. 41 shows a table of the time and timing of the opening and closing the inlet ports and outlet ports a rotary or four-stroke engine, the one with an exhaust valve is provided for the air residue during a compression process;

42 shows a view of a flow profile of the gas fi the rotary motor with two rotors in a schematic representation;

43 shows a view of a modified exemplary embodiment of a flow profile of the gas for the rotary motor with two rotors in a schematic representation;

Fig. 44 is a sectional view of an automatic valve for the outlet; 45 is a view of part of a valve device;

the ^f GtMG ^c is provided with a Hilfsventiabetäti blast unit in the segment;

Fig. 46 is a sectional view taken along line XXXXVI-XXXXVI of Fig. 45;

Fig. 47 is a sectional view of a modified embodiment from an auxiliary valve actuator; which is provided on the valve device;

·. Fig. 48 is a side view of another embodiment of the auxiliary valve actuator;

Fig. 49 is a plan view of a compression cylinder provided with a discharge valve for the air residue; in a schematic representation;

Fig. 50 is a sectional view of a compression cylinder provided with a discharge valve for an air residue is;

Fig. 51 is a plan view of a cam for operation an exhaust valve for an air pressure valve for the four-stroke engine,

Fig. 52 is a valve timing chart showing the valve timing a compression chamber with a

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Outlet valve for the air residue is provided, shows;

Fig. 53 is a P.V. diagram showing an exhaust valve for the air residue is provided to achieve the compression process;

54 is a sectional view of an embodiment of a rotary motor equipped with an exhaust valve for the Air residue is provided, in a schematic representation.

1, 2 and 3 show a preferred embodiment of the device according to the invention. 1 denotes a four-stroke six-cylinder gasoline engine which has six compression chambers _: 2A,> 2B, 2C, 2D, 2E and 2F, which is installed in a known motor vehicle, the six compression chambers being arranged in series in the engine block 3 of the engine 1 . The pistons 4A, 4B, 4C, 4p, 4E and 4F in the compression chambers are connected to a crankshaft 7 through connecting rods and crank arms in this regard.

Numeral 8 denotes a. Inlet port which is opened and closed by an inlet valve 9, which is of a Camshaft 12 is actuated by a rocker arm 10 and a valve lift rod 11. 13 denotes a. Outlet opening, the is opened and closed by an exhaust valve 14 corresponding to the intake valve 9 and by a camshaft 12 by a rocker arm 15 and a valve lift rod (not shown) is operated.

A valve actuation device for actuating each individual valve of the engine 1 is shown in FIG. 1, which is shown in FIG is divided into two sub-areas - a valve actuation device on the left for the left four compression chambers and a valve operating device on the right for the right two compression chambers. It can be seen that the work machine has six compression chambers, the are divided into two sub-areas, which are independent of

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work each other.

The camshaft 12 is divided into two parts - the camshaft 12G for the left four compression chambers and the camshaft 12H for the right two compression chambers, each camshaft 12G, 12H from the crankshaft 7 through small chain wheels i6G, i6Hduxh attached to the crankshaft 7 large sprockets 17G, 17H attached to the camshaft and chains 18G, 18H that match the small sprockets with the large sprockets connect, is actuated. Each of the large sprockets 17 has twice as many teeth as the small wheels 16 on, so that the crankshaft 7 rotates once, to whom the Camshaft 12 executes only half a revolution. The camshaft 12G has four suction cams and four exhaust cams, by which the engine performs a compression operation, and the camshaft 12H also has two suction cams and two exhaust cams similar to those on camshaft 12G. The inlet cam 19 has a cam 19J to achieve the operation of a work machine, and also a cam 19K to perform a compression process achieve, and the exhaust cam 20 has a cam 20J for a work machine operation and a cam 20K in the same way for a compression process. These cams 19J and 19K and cams 2OJ and 2OK have a matching clearance attached in between and enclose a required angle with one another.

The cams for a work machine operation 19J, 2OJ, such as they are shown in Fig. 5 are tapered cams having the tapered outer peripheral surface of an oval cam, the is used in the known internal combustion engine, and the cams for a compression process 19K, 2OK, as shown in FIG 6 are tapered cams that have annular beads that are symmetrical about the center point on either side of the oval cam, and with one revolution of the

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Camshaft each of the cams 19K, 2OK actuates the tappet 21 ″ twice, while each of the cams for the work machine operation actuates the valve tappet 21 only once a cam for a work machine operation as well as a cam for a compression operation, which has tapered cams in the same shape as this for the work machine operation 19J, and the cam for the compression operation 19K, and the middle part thereof or the middle follower part, which the cam for connecting the working machine operation and the cam for the compression process is provided with an annular bead 22-, as shown in section in Figures 8 and 9. When the plunger 21 is brought into engagement with the annular bead, as shown in FIG the inlet valve is slightly open and remains as it is open with a small gap, and the outlet valve is fully closed in the event that that the plunger has fallen into the depressions on both sides of the annular bead. _L .S.pmi ± -J.st die

Power reduction device which serves to reduce the power without actuating the machine for a compression process to decrease, the inlet valve at the time when the machine is to work as an air compressor begins, or is opened at the time when the pressure in dan Storage space for the compressed air is kept constant. The cam as shown in Fig. 10 shows a modified one Embodiment both of the cams for a work machine operation and those for a compression process. The cam of this embodiment is in a row arranged by cams that are used both for a work machine operation and for a compression process (where a rotary ram is to be used). The camshafts 12G, 12H are at a suitable point with a cam for actuating a fuel pump (not shown) to drive the engine, and with a Linkage for actuating the ignition distributor (not shown)

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see, and the cams for a work machine operation, cams for a compression process, cams for actuating a fuel pump and linkages for actuating the ignition distributor form a unit with the camshaft and only the large sprockets 17G, 17H are axially and slidably mounted by a key. The camshafts 12G, 12H are also rotatably and slidably supported at both ends by the bearing such as a slide bearing, and each is simultaneously provided at one end thereof with a valve switching device 23, particularly a device for axially slidably moving the camshafts .

Cam arrangements with which the machine is operated as a work machine and / or as an air compressor are described with reference to FIGS. 11, 12 and 13. The drawings to the left of Figs. 11, 12 and 13 show cams for a work machine operation and cams for a compression operation, the suction and discharge of the left, respectively. ^: regulate four compression chambers, and the drawings on the right hand side show cams for work machine operation and cams for compression operation that regulate suction and discharge of the right two compression chambers.

Referring to Fig. 11, the picture shows on both the left as well as on the right side that the camshaft 12 is moved so that the cams for a compression process 19K, 2OK press against the tappet 21, which moves up and down twice with one revolution of the camshaft.

Referring to FIG. 12, the image on the left shows the cams for a work machine operation 19J, 20J, are pressed against the plunger 21, and the drawing on the right, the cams for a compression process 19K, 2OK are pressed against the plunger 21 so that the left four compression chambers are operated as an internal combustion engine and the right two compression chambers as one air

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compressors are operated.

Referring to Fig. 13, the images on both sides show the case where the camshaft is not moved and the cams for a work machine operation 19J, 20J are pressed against the ram, so that six compression chambers of the machine perform a work machine operation in total.

When the camshafts 12G, 12H move, the cams for a work machine operation become cams for a compression process converted when the engine is performing a work machine operation, it becomes a compression operation as an air compressor, where the intake valves and the exhaust valves twice as often in the four power strokes thereof be opened and closed.

Referring to Fig. 14, there is shown an embodiment of a cam switch device 23 for controlling the camshafts 12G, 12H, and Fig. 15 shows an embodiment thereof. The big one attached to the end of the camshaft 12 Sprocket 17 is slidable relative to the camshaft attached by a sliding key, and this sprocket becomes held securely by the stop component 25, which is firmly connected to the engine block 3 or is formed in this is, and a bearing metal is placed between the component 25 and the engine block 3. Numeral 26 represents a role with a recess which is fixedly attached to the camshaft or is formed like the cams with the camshaft are, and the * annular .. groove or recess 27 this role with recess 26 is t in engagement with the Fork ends 29 of a shift lever 28. This shift lever 28, which is rotatable with the support structure 30 by means of a bolt is connected, has a firmly connected to the engine block 3 Pivot point. The shift lever 28 is connected at the upper end to one end of a strong spring 31, the other end of the

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Spring is connected to the engine block 3, and the force to the fork ends ·. 29 of the shift lever 28 in the direction of arrow 32 in Moving Fig. 14 is applied by the spring. This force is applied by a stop (not shown) attached to the support structure 30 is attached, controlled. In the area where one end of the spring 31 with the upper end of the shift lever 28 is connected, an operating wire 33 is connected to the shift lever 28, this wire is directly on the other End connected to the braking device of the machine through an electrical control device which will be explained later and at the same time as the braking device is actuated, the actuating wire is pulled to keep the roller with To push wells 26 in the direction of arrow 34 and move thereby the camshaft 12 to change the cams. An actuating device can also be separate from this braking device a motor vehicle. A cam switch 23 is for each of the four left compression chambers and also provided for the two right compression chambers. Furthermore, it is desirable that a such means for the actuation of the control cable, such as by an oil pressure brake, a means so designed is that only the operating wire is provided to the operating wire through a solenoid controlled oil pressure changeover valve to connect with the braking device. Another way of operating the cam switch lever is, for example, a path-dependent oil pressure or water pressure or air pressure, as shown in Fig. 15, which shows the mounting of a multi-way oil pressure cylinder 35 along the axis of the cams and inserting the piston rod this Oil pressure cylinder 35 is rotatably connected to the upper end of the shift lever 28 to move the camshaft. or another way, not shown in the figures, is to attach a magnet instead of the roller with dimples 26 provides, which is firmly connected to the engine block 3, and there is later a spring between the end face and the

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Support part 25 is attached to the camshaft, and means is provided between the spring and the camshaft, which prevents the rotary movement of the camshaft to the spring, so that the camshaft is driven by a device for power transmission, consisting of a magnet and a spring.

Furthermore, the oil pressure of the multi-way oil pressure cylinder 35 can be adjusted from Fig. 15- are actuated by the master brake cylinder.

When the cams for a suction process (shown in Figs. 7, 8 and 9) for the cam switching device are installed carry out at least three steps for the cam switching. If a setting for a work machine operation is required during operation of the motor vehicle, the cams for work machine operation 19J are against the plunger 21 is pushed, and when a braking operation is performed, the cam for a compression operation 19K is opposed pressed the plunger, and when the machine is started or the pressure in the storage tank for the compressed air constant is held, the middle annular bead 22 'is pressed against the plunger. '

The cam switching can also be done in five steps, with any other position outside of the position of the plunger which is required to achieve the switching in three steps, so that the plunger is pressed against the beveled cam in two positions that · the valve opening-closing stroke ι is changeable. In this case, however, means should be provided to achieve an accurate valve-opening-closing action at a location v / o the tapered cam is pressed against the outside of the location of the plunger needed for a 3-step changeover.

As described above · ,, can be the valve actuation of the machine

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simple and easy into a valve actuation for an air compressor be converted and vice versa.

20 to 22 show a modified embodiment for the cam, the switching using the 3-step cam switching device with a cam 39 is achieved. The cam 39 is a barrel-shaped cam composed of a cam part 39J for working machine operation designed inversely to the beveled cam of FIG is composed of a cam part 39K for a compression operation and a part 39F therebetween.

When the plunger against which the cam part 39J for work machine operation pushes, is moved towards the intermediate part 39F, the valve is opened and the Air is not compressed, so the engine remains in a completely unloaded state, and then the fuel supply is stopped of course kept stopped. When the plunger moves from the intermediate part 39 to the cam part 39K moved for a compression operation, a steady air compression operation is carried out. The cam 39 can be for a valve be attached, either for the inlet valve or for the outlet valve; the cam as shown in FIG is used for the other valve.

16 to 19 show modified embodiments of the cam, in which the cam is formed so that a smooth Movement of the plunger from a work machine operation to an air compression process is achieved. In Figs. 16 and 17 cams for an exhaust process and in Figs. 18 and 19 cams for an intake process are shown: these Cams are intended to be used for the 5-step cam switching device Find.

The cam 36 for exhausting operation consists of a cam part 36J for a working machine operation, a cam part

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36a for a small stroke with a slightly smaller valve stroke, from a cam part 36b with an even smaller stroke a consequent smaller valve lift, a cam part 36c to keep the valve closed, and a cam part 36K for a compression process. For these parts of the cam 36, the cam 37 consists of an intake process a cam part 37J for working machine operation; and a cam part 37d of a small stroke that is associated with the cam part 37J, and a cam end portion 37e and a cam portion 37K for a compression operation.

A 5-step movement of a machine into which these cams 36 for exhausting and this cam 37 are installed for an intake process, is described below:

When the cams 36J, 37J are pressed against the lifters for work machine operation, it becomes ordinary Working machine operation carried out in the compression chamber. Otherwise the fuel supply is completely stopped, and the compression chamber is only supplied with air. When the cam parts 36a, 37 "d for a small stroke against the tappets are printed, air is sucked in and once for every four Cycle steps ejected in the compression chamber, with a compression process in the compression chamber of considerable low power is achieved. When the plunger engages the cam portion 36b for a smaller stroke and with is brought to the end part of the cam 37e, if a small amount of air is drawn in through the exhaust valve, it is Performance slightly higher than before when the ram was pressed against the cam part for a small stroke. if furthermore, the tappet is brought into engagement with the end part of the cams 36c, 37e, is both the intake valve and the exhaust valve is fully closed so that the engine works as an engine brake. When the plunger engages with the cam parts 36K, 37K for a compression process

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is brought, a compression process is carried out twice for every four clock steps as mentioned above.

A modified adapter that is between the cam for a work machine operation and the cam for a compression process is provided, can, as mentioned above, reduce the performance at the start of the machine, dampen the impact when switching from working machine operation to the compression process and thus achieves a machine braking process, the control power gradually and gradually gains.

When the machine is switched as an air compressor, both the suction mode and the for discharging can be changed accordingly, since sucked gas is different from discharged gas.

In Fig. 23 and 24 embodiments of the flow course for the sucked in and gas to be expelled are shown. X and Y in Figs. 23 and 24 illustrate the direction of flow caused by a device for opening and closing solenoid valves is changed.

When the six compression chambers 2A, 2B, 2C, 2D, 2E and 2F are all used as an air compressor, three-way solenoid / valves 41, 42 are opened to allow a flow to flow in the X direction, two-way solenoid valves 43, 44 are open and that -Three-way valve 45 "is ¹ open to allow flow in direction Y. Two-way solenoid valves 46, 47, 56 are closed so that the air drawn in through air inlet 48 is drawn through each into compression chambers 2A, 2B, 2C and 2D Tube 49 and each inlet port 8 flows therefrom, and when a certain pressure is reached, the air is expelled from each outlet port 13 to flow through each tube 50 into the

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Vacuum tank 51 to flow. The vacuum tank 51 is provided with an intercooler (not shown in the figures). The compressed air that has flowed into the negative pressure tank and that has been rapidly cooled by the intercooler flows through the tubes 52,53 into the compression chambers 2E, 2F, where the air is further compressed to flow through the tube 54 into the high pressure tank 55. The in the compression chambers 2A, 2B, 2C, 2D compressed air is stored in the high pressure tank 55 after being subjected to double compression pressure in the compression chambers 2E, 2F has been exposed. Because the most commonly used air pressure is between 8 and 10 kg / cm and the most effective pressure for the gasoline engine is between 4 "to 5 kg / cm, '-will · - with a double- ~'. compression, '3 A desired level of pressure' for the compressed air achieved when compressed air's levels Pressure is not required, the three-way solenoid valves' 41, opened to allow a current to flow in the X direction, and the three-way solenoid valve 45 in the Y direction, the two-way solenoid valves 46, $ 6 are opened, and the two-way solenoid valves ■ 43 »44, 47 are closed, so that those from the inlet port 48 sucked air flows through tubes 49,52 into the compression chambers 2A, 2B, 2C, 2D, 2E and 2F via an inlet port 8, and after compression, the air is expelled through the outlet opening 13, flowing through tubes 50,54 and in the Vacuum tank 51 is stored. In addition, the tanks 51,54 are provided with a device (not shown) for storing the compressed air always under the same pressure, and means (not shown) for ejecting the compressed Air. '

In the event that the six compression chambers 2A, 2B, 2C, 2D, 2E and 2F continuously and from the start as an internal combustion engine Each of the three-way solenoid valves 41, 42 and 45 open to allow flow in the Y direction, the two-way solenoid valves 46, 56 are open and the two-way solenoid valves 43,44 / 47 closed, so that a mixture of .Vergaser

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57 through the tubes 49,53 into all chambers, each inlet opening flows through these chambers, and after the processes of compression, ignition and expansion are ended the air is discharged from the outlet port 13 as exhaust gas, which is then expelled from the outlet port through the tubes 50,54 will.

When the left four compression chambers as an internal combustion engine and when the right two compression chambers are used as an air compressor the three-way solenoid valves 41, 42 are open to allow flow in the Y direction, and the three-way solenoid valve 45 is open, to pass a flow in the X direction, and the two-way solenoid valves 47, 56 are open and the two-way solenoid valves 43, 44 and 46 closed so that the mixture from the carburetor 57 into the left compression chambers 2A, 2B, 2C, 2D is sucked in through each inlet port 8 thereof _ and after Completing the compression, ignition, and expansion, the air is discharged from the outlet port 58 through the outlet port 13 and the tube 50, and at the same time the air sucked in from the other air intake ports 59 is passed through the Tube 53 and the inlet port 8 passed into the right compression chambers 2E, 2F, and after the air to a certain Pressure has been compressed, it is discharged from the outlet port to enter the vacuum tank 51 through the tube 54 to get. When the vacuum tank is filled with compressed air, an electrical signal will then be generated the two-way valves 47,56 closed and the two-way solenoid valves 42,44 opened, so that. the compressed air in that Vacuum tank is subjected to a doubling of the compression to be received in the overpressure tank 45.

Instead of taking in the air from the inlet port 48, a Solenoid valve for opening and closing a pipe may be provided on the fuel supply pipe coming from the carburetor 57, so that air can be drawn in through the carburetor 57.

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The above description relates to a case where the machine performs a compression process and is so designed that the compression is doubled in order to control the internal combustion engine, but in the modified cam for the compression process both the timing for discharging the compressed air and the duration of the discharging operation are changed can be so that the compression of the air to a pressure between 8 and 10 kg / cm can be achieved at once. In this case, one storage tank for the compressed air can be sufficient. With the diesel engine can compressed air from a pressure between 8 to 20 kg / cm can be achieved, and it is also possible to use high pressure air from a pressure with more

or less than 30 kg / cm can be achieved by doubling the compression is applied.

The arrangement of the tubes for suction and discharge for this above-mentioned case are shown in FIG. If all six Compression chambers working as an air compressor is the fuel supply pipe leading to the carburetor 57 through solenoid valves (not shown) closed and three-way solenoid valves 41,45 opened to allow flow in the Y direction, and the three-way solenoid valve 42 is opened to allow flow in the X direction. When the six compression chambers are used continuously and from the start as an internal combustion engine, the fuel supply pipe is open, and the Three-way solenoid valves 41, 42, 45 are opened to allow flow in the Y direction. If it is demanded that the left four compression chambers are used as an internal combustion engine, and that the right two compression chambers as one Air compressor used is the fuel supply pipe opened, and the three-way solenoid valves 41,45 are opened to allow a flow in the X direction, and that Three-way solenoid valve 42 is open to allow flow in the Y direction.

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Furthermore, all solenoid valves are controlled by an electrical control device (not shown) operated, and this is connected to the brake pedal or the handbrake lever and is through operated the same. It is of course possible to have another actuator specially designed for this electrical one Provide control device. The electrical control device is designed so that the time of actuation of the Plurality of solenoid valves is different from each other. If the solenoid valves are all operated at the same time, the residual gas, which contains fuel and exhaust gas and is located in the inlet pipe and the relevant outlet pipe, is fed into the storage tank for the compressed air, and after the fuel supply is cut off, therefore the solenoid valves are actuated with a time delay and gradually in the direction of flow of the gas.

When the machine built above has a compression process performs a compression operation during operation of the motor vehicle in which the engine is installed, compressed falls Breathing in, and at the same time the speed of the vehicle is controlled. When the speed of the machine is up a certain speed drops, a speedometer measures, such as a tachometer generator or a stroboscope, the speed and transmits a measurement signal to an electrical Control means to stop the compression process and cause the machine to operate to execute.

Referring to the embodiments of an article according to the invention, six compression chambers of a machine are divided into two groups, i.e. four compression chambers and two compression chambers, but the ratio can be 3: 3 or 5: 1, and if there are four compression chambers, the ratio can be 3: 1 or 1: 1, and with three compression ^chambers: the ratio 2: 1 and with eight compression chambers

4 0 9 8 3 2 / G 3 7 9

compression chambers can be the ratio 3: 1 or 5: 3 etc., and it is also possible to use the camshaft 12 without subdivision to train for the compression chambers. However, if some of the plurality of compression chambers are needed for work machine operation and the others are needed for one Compression process, it is necessary that the number of compression chambers for a work machine operation is greater than the number of compression chambers for a compression process. If in particular a compression process is carried out continuously, the energy generated by the internal combustion engine should always be sufficiently greater than that of an air compressor be consumed energy, and in an engine, the camshafts for the intake valve and the exhaust valve are provided separately on both sides of the engine block should - as mentioned above - be used.

With all forms of arrangement of the compression chambers for the Internal combustion engine in a car, such as in-line, star shape, V shape, X and Η shape, all have compression chambers divided will.

Another embodiment of the subject matter according to the invention is explained with reference to FIGS. 25 to 36.

In Fig. 25, a modified two-stroke engine is shown. A common two-stroke gasoline engine has neither intake nor Exhaust valves, whereas the modified two-stroke engine according to the invention has a scavenging port 61 and an exhaust port 62 is provided. In order for the compression chamber 63 of the machine to be able to perform a compression operation an outlet port 64 and an outlet valve 65 may be provided.

To achieve the oil process in a two-stroke gasoline engine, a lubricant system and a lubricant mixing system are provided separately for this purpose; with the previous system Motor oil mixed with air, and in the case of the

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An oil pump must be provided for the system. Furthermore is. required that the same oil history also with a Two-stroke diesel engine can be used. Therefore an outlet opening 64 and an outlet valve 65 are additionally provided, to be used for the compression process, and the piston is installed in the vicinity of the bottom dead center, a compression chamber is traversed only by air, through the flushing opening 61, the fuel supply already through the actuation of the solenoid of the valve has been blocked, and during the movement of the piston from bottom dead center to Top dead center air is compressed and when the piston reaches the vicinity of top dead center the exhaust valve becomes 65 opened to expel the compressed air, and there is little air in the compression chamber during the movement of the piston from top dead center to bottom dead center 63 »and accordingly the piston movement produces a good one Vacuum in the compression chamber. In this case the outlet opening 62 must be closed, for example by a solenoid valve will. When an inlet port 67, an inlet valve 68, an outlet port 64 and an outlet valve 65 are additionally provided are, and when the piston 66 is mounted in the vicinity of the top dead center, the exhaust valve 65 is opened, and as soon as the exhaust valve 65 is closed after the completion of the exhaust operation, the intake valve 68 is opened and air becomes only through the inlet port 67 during the movement of the piston 65 from the top dead center to the bottom dead center sucked in; and when the piston moves from bottom dead center to top dead center, the inlet valve 68 is closed, so that a compression process is achieved. In this case, the flushing opening 61 and the outlet opening 62 must be closed and the fuel supply must be stopped.

Referring to the two-stroke gasoline engine shown in FIG is an additional inlet port 67 and one

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additional outlet opening 64 with the known flushing opening 61 and the outlet opening 62 through a tube or a three-way solenoid valve connect, but if the openings 67,64 not with the openings 61,62 are connected, the inlet opening 67 and the outlet opening 64 with an air inlet opening and a compressed air storage tank as shown in Fig. 26, for example.

If this two-stroke gasoline engine and a two-stroke diesel engine to be explained later have an intake valve and a discharge valve are provided so that a compression process is achieved, an additional valve operating device must be provided be provided on one side of the compression cylinder. This valve actuation device should be designed in this way be that an operation remains prohibited while the machine is performing a work machine operation, and that actuation occurs while the machine is compressing. The valve actuator is with a camshaft of a cam switching device (see FIGS. 14 and 15) which is that of a modified four-stroke gasoline engine are similar, and furthermore, the camshaft is adapted to be driven from the crankshaft at the same speed is rotated so that the rocker arm and the valve lift rod are operated to open the valve and close. In this case, a work machine cam is not required as provided in the four-cycle engine, and therefore a beveled cam 71 is sufficient for the intake valve and a tapered cam 72 for the exhaust valve, a pair for each compression chamber for the Compression process is provided. In particular, each cam 71 has an intake valve and each cam 72 has an exhaust valve a cylindrical part O and a tapered part L, the camshafts 73 (not shown) thereof being so are designed to be axially displaceable by the cam switching device as shown in FIGS are, and when the plunger is in engagement with the cylindrical

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Part · O is the inlet valve 68 and the outlet valve closed, and the machine performs a work machine operation while when the ram is in engagement with the chamfered Part L is, the inlet valve 68 and the outlet valve 65 meet the same puncture as in the four-cylinder engine, and the machine performs a compression process.

In the embodiments of the four-stroke and the two-stroke engine listed above, the cams are for working machine operation and the cams for the compression process are formed on a camshaft, but a different arrangement of the Cams, such as a separate shape, are conceivable, with the Nockeian separately lying camshafts are formed, and the cams can also be formed on an overhead camshaft his etc.

Further, as with the four-stroke engine, it is possible that the switching the cam switching device is operated by a multi-step process, and the position of the plunger, which is against pushes the tapered part of the cam L can be doubled, so that both the number of intake movements as the number of outlet movements can also be changed. In this case, however, the shape of the tapered cams is formed so that, as shown in Fig. 26, one side of each tapered portion L has the same radius as that has cylindrical part which may be the same as that of the four-stroke engine.

FIGS. 30 and 31 show a power reduction device, which consists of a cam with an annular bead P on it. The annular bead P keeps the valve a little open, and this device causes a reduction in performance, just like the device provided in FIGS. 7, 8 and 9 for one Four-stroke engine.

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Furthermore, a cam switching device can be used in the two-stroke engine be replaced by a camshaft and a magnetic clutch: the design is that in the four-stroke engine, as shown in Fig. 32, used similarly, and the clutch is in a certain position with the Camshaft engaged to transmit the rotational movement of the crankshaft to this.

The different designs of the two-cylinder diesel engine, such as the valve outlet shapes, opposing piston shapes or U-shape of the direct current flushing design, or such as the cross-flow shape or circulating shape of the sea-current flushing design, all with corresponding valve devices, inlet ports and inlet valves, outlet ports and outlet valves or even are provided with outlet ports and outlet valves in order to carry out a compression process. The compression caramers of a diesel engine of the ventilated design with. DC flush type can work as an air compressor, by changing the time for opening and closing the exhaust valves so that the valves open when the piston is in the Is near top dead center, but preferably an exhaust port and an exhaust valve are as with that Two-stroke gasoline engine, provided because the air charge in the compression chamber is insufficient, and therefore the efficiency not very good in an air compressor when the piston is in the vicinity of the bottom dead center, and when the outlet port is closed and when the air is drawn in through the purge slot.

Referring to the transverse or recirculating sea-flow type, the machine is as shown in FIG is additionally provided with an inlet port 75, an inlet valve 76 and an outlet port 77 and an outlet valve 78; the additional inlet opening 75 is through a tube with connected to a flushing pipe (not shown) carrying a flow of

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a pre-compressor 79 to a flushing slot 80 passes. The outlet opening 81 for a working machine operation is closed, and the fuel supply is shut off by a corresponding solenoid valve. This way the effect can of the scavenging slot 80 can be improved for a work machine operation without an additional inlet opening 75 and an inlet valve 76 to be provided. The inlet port 75 and the inlet valve 76 are provided by an additional Valve actuator opened and closed similar to that of the two-stroke gasoline engine. With the counter-piston design with DC purging, the machine, as shown in FIG. 34, is additionally on the one in the middle Area of the counter-rotating pistons within the machine with an inlet port 84, with an inlet valve 85, with a Outlet opening 84 and an outlet valve 87, or only provided with an outlet opening 86 and an outlet valve 87 - with the valves also through a? Valve actuator opened and closed, which is additionally provided and similar to that mentioned above.

FIGS. 35 and 36 show, for example, the flow profile for the suction / discharge that occurs when all three Compression chambers of the two-stroke gasoline engine are arranged in parallel, which correspond to the arrangement in a two-stroke diesel engine, whose compression chambers are arranged in parallel in groups of three, corresponds. 35 shows the flow profile of a The improved machine of Fig. 25, Fig. 36 shows an improved machine of Fig. 26. Reference characters X, Y in Figs 35 and 36 show the direction of flow of air or a mixture passed by a solenoid valve or stopped.

35 will now be described in detail.

When three compression chambers 91Q, 91R and 91S all as one Air compressors used are the three-way solenoid valves

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92.93 opened to allow flow in direction Y, and the three-way solenoid valves 94, 95, 96, 79, 98, 99 and 100 are opened to allow flow in the X direction in this regard, and an arrangement for supplying fuel to the carburetor 57 or the course of the flow. from the carburetor 57 to the intake pipe is cut off by a solenoid valve. The air admitted through the carburetor 57 is drawn into the compression chambers through inlet openings 67 and after the compression is discharged through the additional outlet channel 64 into the vacuum tank 51, where the air is stored. Of the Pressure of the air to be compressed can be changed in the compression chambers by changing the time of actuation of the exhaust valve 65 is changed, an air pressure between 6 and 12 kg / cm is preferred and is extremely applicable on other machines.

When the three compression chambers are constantly used as an internal combustion engine are used, each of the three-way solenoid valves is 92 ^ 3 94,95,96,97,98,99 and 100 opened to allow flow in the Y direction and the carburetor 57 is fueled provided. A mixture generated in the carburetor 57 is fed into the compression chambers through the previous scavenging slots 61 passed, and exhaust gas is passed through the previous exhaust ports to be discharged through the exhaust port 58. In this case, the intake valves and the exhaust valves that have been additionally attached are kept closed.

When the left two compression chambers 91Q, 91R as one Internal combustion engine are used, and the right compression chamber 91S used as an air compressor are the Three-way solenoid valves 92, 93, 97 and 100 opened to allow flow in the X direction, and the three-way solenoid valves 94, 95 j 98 and 99 are opened to allow flow in the Y direction and the carburetor 57 is supplied with fuel. One mixture produced in the carburetor 57 is transferred to the compression

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chambers 91Q, 91R directed to be ignited and then as Exhaust gas to be expelled through the outlet port 58. on the other hand The compression chamber 91S only draws air through one Tube 101 on, the air not being passed through the carburetor 57 is, and after the compression of the air, the compressed air is through the additional outlet opening 64 in the Tank 51 ejected where the air is stored.

36 shows, as mentioned above, the flow course of the gas in the event that the additional inlet opening and outlet opening do not match the original flushing slot and connected to the dedicated discharge port, and if all compression chambers are used as an air compressor, the fuel supply is stopped and the three-way solenoid valves 92,93 are open to allow flow in direction X, to draw air through inlet port 102. When all compression chambers are used as an internal combustion engine it is sufficient that the opening and closing of the additionally attached Inlet-round exhaust valve by a device of Solenoid valves (not shown) are stopped and the two-way solenoid valve 103 is open and fuel is present. When the compression chambers 91Q and 9IR can be used as an internal combustion engine, and that. the compression chamber 91S is used as an air compressor, fuel is supplied, and the additionally provided Ven-; til of the compression chamber 91S is opened and closed, and the two-way solenoid valve 103 is closed and the three-way solenoid valves 92, 93 are connected to flow in the X direction to let through. Further, in Fig. 36, there is such an arrangement with which a doubling of the compression can be achieved, and the flow profile shown in FIG. 35 can be designed so that a doubling of the compression is achieved. In the course of the flow to achieve When the compression is doubled, all compression chambers are used for one compression process. It is sufficient

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however, to connect the three-way solenoid valves 92,93 to. a river in the Y direction, and the air once compressed in the compression chambers 91Q, 91R is fed into the tank 51 and then into the compression chamber 91S and then continues compressed to be stored in the positive pressure tank 55.

In the rotary piston engine shown in FIGS. 37 and 38, an additional inlet port 109 and an additional outlet port 110 on a known motor housing for one Rotary piston engine 108 is provided with an inlet port 106 and an outlet port 107. This additional inlet opening 109 and the additional outlet opening 110 are almost point-symmetrical to the original inlet opening 106 and to the original outlet opening 107 arranged on a circle around the eccentric shaft.

As a basic arrangement for the through-the-opening-inlet-outlet type There are three types: circumferential opening, side opening and a combination of these two. Furthermore it is foreseeable, the side opening design for the outlet opening too and with respect to each of the designs used, that of the additional openings provided should be considered to be pulled.

In view of the above, it is necessary to use the rotary piston engine perform a compression operation. The machine in this case is of the circumferential opening suction type, which are provided with an additional inlet port and an additional outlet port relative to the peripheral port inlet type. Each of the original and additional inlet and outlet ports should be valved. If the machine of the longitudinal port suction type having an inlet and an outlet port according to the longitudinal port suction type is provided - regardless of the type of design, the outlet opening is a circumferential opening -es. just have to

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the additional and original outlet openings must be provided with a valve. Should the machine be required by the circumferential opening suction type are provided with an additional inlet and outlet opening of the longitudinal opening suction type, however, if the outlet port is a circumferential port and vice versa, or if the machine is of a combination port suction type valves must be fitted as mentioned above. If the inlet and outlet ports Longitudinal openings are and an additional inlet opening and outlet opening are also longitudinal openings, need not each of the openings to be provided with a valve. In other words, when the openings are longitudinal openings Valves are not required for this, but if the openings are circumferential openings, valves are required. With longitudinal openings there may be overlap, and if the residual air discharge valve, which will be described later, is provided valves are also provided.

The rotary piston engine as shown in Figs. 37 and 38 is of the circumferential type with two pairs of inlet and outlet ports provided - an additional inlet opening 109, .an original Inlet opening 106, an additional outlet opening 110 and an original outlet opening 107 are marked with In-r outlet valves 111 and 113 and outlet valves 112 and 114 are provided.

Referring to . these valves open and close when the machine performs a compression process, as with the piston engine. When the machine is performing a work machine operation, the valves of the additional The inlet and outlet ports are closed and the valves of the original inlet and outlet ports are opened. In a rotary piston engine, the eccentric shaft rotates three times for one revolution of the rotor, and ignition takes place three times - so to speak with the eccentric shaft, so that with

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one rotation of the eccentric shaft is followed by an ignition cycle. The valves for this are coupled with the eccentric shaft, eo that each valve is opened and closed once at a given point in time during one revolution of the eccentric shaft will.

A valve actuation device for actuating the on the Rotary piston valves are shown in FIGS. 37 and 38. Referring to a new inlet and a new outlet opening, so a camshaft 115 is driven by an eccentric shaft 116 actuated via a sprocket and a chain and is arranged to be axially rotatable. The camshaft 115, a cam 117 and a cam switching device 118 are similar in construction to the corresponding parts of the valve operating device, as shown in Figs. 27,28,29,30 and 31 and further in Figures 14 and 15 are shown for a four stroke engine. Regarding the original inlet and outlet opening, the Camshaft 120 has a cam 119 which, similar to the original four-stroke gasoline engine, has an eccentric shaft is operated via a chain wheel and a chain, and a valve relief device, such as an electromagnet or a magnet (not shown) is built into it accordingly. These Device keeps the valves open in an electrical manner while the machine is performing a work operation. Further can the original inlet and outlet opening 'with a Valve actuation means may be provided which is similar to that for the additional inlet and outlet openings.

When the rotary piston engine requires a compression sions process executes, the tappets of the valves are at the additional inlet and outlet openings in engagement with the beveled Part L of the cam 117, and the valves 113 and 114 of the original inlet and outlet ports also stand in engagement with the cams 119. These valves. 'reach the same process as the valves on the four-stroke gasoline engine.

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Of course, the time of opening and closing of the valves is specially selected. When a work machine operation is to be achieved, the tappets of the valves 111, 112 in Engaged with the cylindrical part O of the cams 117, with the inlet and outlet ports closed, whereas the valves 113 »114 through this valve relief device are open. These . Inlet and outlet valves 111, 112, 113f1i4 are designed so that they are an annular part, such as an epitrochoid having two nodes that form a profile within the housing of the rotary piston engine 108 so that the construction does not have a gap between the valve surface and the tip of the seal of the rotor having.

As a device that characterizes a rotary piston engine, which has longitudinal openings and is provided with valves for opening and closing the openings, is such a device, as shown in Figs. 39 and 40 are applicable.

In Fig. 39, each port is provided with a valve, but each port operates in a different manner.

The original inlet port 106 does not need a valve since the timing and duration are the same when a compression process is being performed, or when a work machine operation is being performed.

The original outlet port 107 is open when the engine carries out a work machine operation, and when a compression operation is carried out, it is open only as long as until the rotor reaches top dead center. A rotary valve 201 for the original outlet port is a segment valve, which is rotatably attached to the shaft 202 which is cantilevered from a support member 203 that is slidable in a Channel 204 is installed, in which there is a spring 205 and a

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Magnet 206 are located, the spring against the support part 203 the wall of the channel presses, and-whereby the magnet uses the force of this Overcomes the spring and causes the J3tü.Wteil. 2.03 sliding is movable. A spring (not shown) is attached between the rotary valve 201 and the support member 203; this feather causes the rotary valve 201 to move together with the support member 203 rotates to open the outlet port 107. That Reference numeral 207 represents an intermediate piece that forms a whole with the rotary valve 201. This intermediate piece 207 is rollingly brought into engagement with a cam 201 which , is fixedly attached to a shaft 208. The reference symbol represents a stop for the rotary valve 201.

When the cam 209 is rollingly engaged with the intermediate piece 207, the rotary valve 201 overcomes the spring force and closes the outlet port 107, and when the intermediate piece 207 has fallen into the concave area of the cam 209, will the rotary valve 201 is rotated by the spring force and opens the outlet port 107. The shaft 208 is driven by the eccentric shaft 116 through wheels 213,214, 'and the wheel 214 is driven by a magnetic coupling that engages in a certain position.

When the machine is the working mode of the working machine operation changes to a compression process, the magnetic clutch, which engages in a certain position, is switched on, and the wheels 213, 214 are rotated, and the rotation of the cam 209 actuates the rotary valve 201 so that that the outlet port 107 is always opened at a certain point in time for the discharge. When the working of the machine is changed from a compression process to a working machine mode, the magnetic clutch is switched off, and at the same time the magnet 206 moves the shaft 202 so that the intermediate part 207. is no longer in rolling engagement with the Cam 209 stands, and then the outlet port 107 is opened.

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In other words, every time the magnetic clutch is switched off and the rotation of the cam 209 is stopped during rolling engagement of the intermediate part 207 with the Cam 209 to keep the rotary valve in the closed state, the outlet port 107 is opened quickly as the rotary valve 201 must be kept open for the outlet port 107 during the time for a work machine operation.

At the time of work machine operation, the additional intake port is 109 and an additional outlet opening 110 closed and are opened at a certain point in time for a certain period of time when a compression operation is carried out will. A segment-like rotary valve 216 that associated shaft, a channel, a support part, a spring and a magnet for the additional inlet opening 109 are mostly similar to that of the rotary valve 201, but the spring inserted between the rotary valve and the support member acts on the rotary valve to open the additional inlet port. The intermediate part 217 forms with the rotary valve 216 a unit and is connected to the cam 219 »the one on the shaft 218 is firmly attached, brought into rolling engagement.

A cam 221 is fixedly attached to the shaft 218, and the. Cam 221 connects to intermediate part 223 of the rotary valve 222 brought into rolling engagement for the additional exhaust port. The rotary valve 222 operates similarly to the rotary valve 216 so that the opening can be closed Iain.

Fig. 40 will be explained in more detail by an operation of the rotary valve.

A rotary valve 225 is attached to a side part of the housing for the rotary motor, the shaft 226 of which is from the Eccentric shaft 116 is driven via wheels 227,228 and a magnetic coupling, the magnetic coupling in a certain

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Position intervenes. The rotary valve 225 has an opening 230 that is similar in shape to the opening. Numeral 231 represents a seal to make the housing airtight complete when the rotary valve rotates at a high speed. Furthermore, a device for stopping the Rotary valve in a certain position when working machine operation is carried out - on one side of the rotary valve intended. This device works to open the valve with the original outlet opening is observed, and which is closed, the additional inlet opening and the additional outlet opening is also observed. To design such a facility, the rotary valve 225 is provided with a permanent magnet consisting of two semicircles, each Semicircle has the opposite polarity, and another permanent magnet is attached to the surface of the side housing with which the The rotary valve is held in sliding engagement so that the rotary valve 225 is stopped by the magnetic interaction forces of the two permanent magnets; and as in ' Fig. 40 is shown in the side of the rotary valve 225 formed a shallow recess 232, and a hemispherical Body 233 is sunk into the side housing in such a way that the spring force thereof always presses against the rotary valve, so that the rotating speed of the rotary valve can be decreased, and the rotary valve is stopped at the time at which the hemispherical body is brought into engagement with the recess 232.

Fig. 41 shows the timing of the opening and closing of the openings and the length of time during which the opening is opened is in the event that - as previously mentioned - circumferential openings or longitudinal openings on the machine with an additional Inlet and an additional outlet port are provided, each having a valve, so that the machine performs a compression process executes. Fig. 41 also shows a "state in which a residual air ^ exhaust valve, which will be described later,

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Residual gas has been forcibly expelled, and at the same time it shows comparatively the time of opening and closing of the openings and the time segment in the event that the four-stroke piston engine achieved a compression process. The broken lines represent the time of opening and closing of openings and the length of time when a work machine operation is performed.

Fig. 42 shows the flow profile for suction and discharge of the two-rotor rotary piston engine.

When the two compression chambers M and N are for a compression operation, the three-way solenoid valves 121 and 122 are opened to allow flow in the Y direction, and the three-way solenoid valve 123 is opened to allow flow in the X direction, and the fuel delivery pipe for the carburetor is closed by a device of a solenoid valve and stops the fuel supply. The air drawn in by the carburetor 57 flows through each of the tubes 124,125 and passes through the inlet ports 106,109 into the compression chambers where the air is compressed and expelled from each of the outlet valves 110,107 and released into the tank through outlet tubes 126,127.

When the compression chamber N is only a compression operation and the compression chamber M is a work machine operation is performed, the three-way solenoid valves 121 and 122 are opened to allow flow in the X direction and the three-way solenoid valve 125 is open to allow flow in the Y direction and the carburetor 57 is supplied with fuel. One Mixture generated in the carburetor 57 flows through the tube 124 and is drawn into the compression chamber M through the inlet port 106. The compression chamber N performs a work machine operation and discharges exhaust gas from the outlet 58 through the outlet port 107. For the compression chamber N only air flows through the tubes 128, 125, and it becomes only air

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into the compression chamber N through the inlet port 106,109 sucked in, in which the air is compressed, and through the outlet openings 107, 110, the tube 127 and the solenoid valve 121 is passed into the vacuum tank 51, where the air is stored.

When the compression chambers M, N for work machine operation are provided, all three-way solenoid valves 121, 122, 123 are open to allow flow in direction Y, and the carburetor 57 is supplied with fuel. Mixture passes through tubes 124, 125. and inlet port 106 into the compression terms M, N. Exhaust gas passes through the exhaust port 107 of the compression chambers M, N to be expelled through the tubes 126, 127 through the outlet opening 58.

When the two-rotor rotary piston engine is used as an air compressor for a. Two-stage compression is provided, as in 43, the fuel supply is shut off and the three-way solenoid valves 121, 123, 129, 130 are open to flow in the direction X, and the air compressed in the compression chamber M and in the half compression chamber N becomes one in-the vacuum tank 51 ", from which the" air into the. other Half of the compression chamber N, i.e., low pressure air is drawn into the inlet port 106 of the compression chamber N Low-pressure tank 51 is sucked in, and after the air has been compressed again in half of the compression chamber N, the air passes through the outlet opening 110 into the high pressure tank 55 to be saved *. Except for the double compression, the three-way solenoid valves 129, 130 are open, to let a river through in the Y direction.

Referring to the above embodiment of the rotary piston engine two compression chambers are split in a 1: 1 ratio, but with three compression chambers they can be divided in a ratio of 2: 1.

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With what has been described above it is achieved that a. Internal combustion engine without valves, such as a two-stroke gasoline engine, a two-stroke diesel engine and a rotary piston engine, performs a compression process by being provided with additional valves and actuating cams. If a machine is additionally provided with such automatic valves instead of the valves for opening and closing, the machine can be easily used as an air compressor, even though the lifetime and the switching performance of automatic valves are lower than for valves for closing and opening. An example of an automatic valve is described below with reference to Fig. 45:

Numeral 136 refers to an automatic valve for exhaust, which is at the exhaust port 138 of the cylinder head 137 (or on the housing of the rotary piston engine) of the machine is provided. The automatic valve 136 has a valve seat 139, a valve plate 140, a valve spring 141, which is a specially manufactured, annular coil spring, a valve seat 142, a bolt 143 and a Valve holder 144, the upper end of this holder 144 is built into a hook-shaped bore 145 which is in the Cylinder head 137 is formed, this bore being connected to a tube 146 to allow a high pressure flow to pass through.

The hook-shaped bore 145 has a slidable stop 147 and a spring built therein. The attack 147 is moved by the pressure of the high pressure stream to apply pressure to the upper surface of the upper end of the holder 144 and to relieve the holder 144. With no high pressure flow, the elastic force of the spring moves the stop 147 back in its original position in order to reduce the compressive force against the holder 144.

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When an internal combustion engine performs a compression operation, the compressed air in the compression chamber overcomes the restoring force of the valve spring 141, lifts the valve plate 140, and then the air enters the exhaust port through the opening between the valve plate 140 and the valve seat 139 ejected. When the machine is performing a work machine operation, a flow of high pressure is generated from one High pressure tank (not shown) passed through tube 146 into bore 145 to move stop 147 so that the Spring 148 is pressed. The stop 147 then presses on the holder 144, which quickly the valve plate 140 against the Valve seat 139 pushes so that the exhaust gas is shut off.

If inlet openings are also provided with an automatic valve, automatic valves are used for suction, which are similar in shape to automatic exhaust valves and used as a load reducing device v / ground, which opens the intake valves to relieve the load (commonly known as an intake reducer). However, when the machine is performing a work machine operation, the automatic valves may be used for priming be provided with a device just as is the case with the automatic exhaust valves, since the automatic valves should be completely closed.

The following is a description of a device that addresses the difficulties which occur in the event that the machine performs a compression process, solves. Usually press Cams against the valve lift rod, and rocker arms that act on the Valve stems act to open the intake valves and exhaust valves, relieving these valves from the repulsion of the valve stems be closed using the stretching force of the valve spring. When the outlet port of such a machine connected to a storage tank for compressed air

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is, · is a back pressure of the compressed air that is in the Exhaust tube is directed towards the exhaust valve, and the stretching force of the valve spring is reduced, and consequently Full closure of the exhaust valve cannot be expected when this machine is compressing. Thus, it is necessary to provide means which overcome the back pressure of the compressed air and which is a complete one Achieve closure of the outlet opening.

Referring to Figs. 45 to 48, an example becomes one such auxiliary valve actuator shown that the Increasing the stretching force of the valve spring allows to achieve a complete closure of the exhaust valve.

Numeral 151 denotes a cylinder head of an engine, and reference numeral 152 represents an inlet valve or an outlet valve to the inlet or outlet port 153 to open or close, which is provided in the cylinder head. The inlet or outlet valve 152 has a valve head 154 facing the compression chamber of the machine, as well as a valve stem 155 and a valve plate 156. The valve head 154 and the valve stem .155 form a whole component together, the plate 56 is removable attached to the valve stem 155. In other words, the Valve plate 156 is a transducer with a larger bezel than a common transducer. The reference number refers to a valve spring mounted between cylinder head 51 and plate 156. The valve spring is mounted around valve stem 155, the spring force of which is unidirectional, around the plate of the cylinder head move away. The reference numerals 158, 158 represent a device for increasing the valve spring force, for example a permanent magnet or an electromagnet. These magnets 158 are attached to the shaft 159, which is rotatably supported is by a support member (not shown) attached to the

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upper end of the cylinder head 151 or the cylinder head cover (Valve cover) is provided, and one end of the shaft 159 is provided with an operating lever 16O through which the shaft 159 is set in rotary motion. This lever can be operated manually, but it is much more advantageous To use electromagnets to operate the lever simultaneously with the valve spring force amplifying device. Further For example, the shaft 159 may be provided with drive means, such as a chain and a sprocket, to facilitate the rotational movement to transmit the crankshaft, so this device as a valve force-boosting device only can then be operated when the valves are closed. Reference numeral 161 denotes a rocker arm, the one Restoring force exerts in the opposite direction of the stretching force of the valve spring 157 in order to open the valve 152. Of the Rocker arm 161 is supported by a valve rocker shaft and operated by a nooke through a lift rod, shown in the drawing are not shown.

A 'support 162 of the cylinder head 151, the valve stem 155 guides axially slidable, is with a support part 163 made of cylindrical, self-lubricating material and two O-rings 164, which are installed in the annular channel of this support member 163, and seal the two O-rings completely removes the engine oil and the compressed air discharged from the valve rocker shaft.

47 and 48 show modified exemplary embodiments of a valve spring reinforcement device 158, the Reinforcement for the valve spring is arranged so that it can be achieved in an electrical manner. Referring to 47, the valve spring reinforcement device has a magnet I65, a shaft 166 built into the magnet 165 is, a fastening member 168 having a flange 16 ?, which is fixedly attached to the shaft 166 on. the

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Valve spring reinforcement device as shown in FIG. 48 has a horseshoe-shaped electromagnet 169. which is outside the engagement range of the rocker arm 161 is arranged. When electromagnets are used in the above embodiments, the devices must be so designed be that signals from a breaker are fed through an electronic circuit only when the valve is closed.

When the machine performs a compression operation with the aid of the auxiliary valve actuator and - as mentioned above is built, neither the compressed air left in the engine will cause the exhaust valves to be fully closed the valves are opened at the time of closing. This auxiliary valve actuator can operated at a time when the number of revolutions of the machine is high improves the tracking ability of the movement of the valves and prevents the valves from jamming, that they sway in their vertical position and that they pop out.

When the machine is compressing, the compression chambers are connected to the tank. That is why it is located There is air of high temperature and high pressure in the dead space, because there remains a very small opening between the upper one End of a compression chamber and a piston even when the pistons reach their top dead center. Even with. ' Intake stroke, where the pistons come down from top dead center, the intake is not stopped: - leads as long as the air of high temperature and high pressure remains in the dead space and expands, and so long the air pressure in the compression chambers becomes lower than the pressure in the inlet pipe. In other words, the air will not be drawn steadily through the inlet tubes as long as the pistons are a distance from top dead center move, and a suction stroke becomes steadily shorter and reduced

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the performance is remarkable to such an extent that the larger the dead space of a machine, as in the case of, for example a gasoline engine - the greater the extent.

In order to remedy such inconveniences, the high temperature and high pressure air that remains in the dead volume must expelled outward in an instant to make a steady intake stroke longer, so that the force of the intake inertia, which has an influence on the air in the intake pipe can be enlarged.

Referring to Figs. 49 to 54, an explanation follows in conjunction with a residual gas discharge valve that is used to achieve this mode of operation.

Fig. 49 shows a residual gas discharge valve installed in a cylinder of the engine as shown in Fig. 1, and FIG. 50 is a sectional view of FIG. 49.

The residual gas discharge valve 171 is at one between the inlet valve 9 and the exhaust valve 14 is provided, and the residual gas discharge valve 171 is provided by the camshaft operated by a rocker arm 172 and a lifting rod 173, as is the case with the intake and exhaust valves mentioned above.

The nooke has a camshaft 174 for the residual gas exhaust valve zv / ischen the inlet cam 19 and the outlet cam 20 are provided. The cam 174 for the residual gas exhaust valve is like shown in Fig. 51 is a tapered cam (the sectional view thereof is similar to that in Fig. 6). Just like it with the cam 2OK of an exhaust valve for an air compressor is the case. This cam. actuates a plunger 175 at one Rotation of the camshaft twice. A cylindrical part 0 is provided around the residual gas discharge valve 175

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closed and brings the plunger 175 into engagement the cylindrical part 0 when the machine is in a working machine operation executes.

Each of the cams 19, 20 and 174 is designed so that the Timing for opening and closing the residual gas discharge valve 171 to discharge the gas is as it is in one Valve timing diagram is shown in Fig. 52 so that the exhaust valve 14 is opened at time T when the air in the compression chamber 2 reaches a certain pressure, and is closed when the piston 4 is near the top Dead center is located. The residual gas discharge valve 171 is then opened at point U at the same time as the discharge valve 14 is closed is opened and at a point in time W or later than when the air pressure in the compression chamber 2 with becomes equal to the air pressure in the intake pipe, and the intake valve 9 opens at time W when the air pressure in the compression chamber 2 is the same as that in the inlet pipe

becomes at ¥, where a small overlap is allowed ....

and is closed at the point in time or after the point in time at which the pistons reach their bottom dead center Z.

Thus, the air of high temperature and high pressure, which is left in the dead volume have been _na ch externally discharged through the residual gas discharge valve 171 when the machine to perform a compression process, and hence, as shown in Fig. 53 shown -is, the inlet valve a machine with a residual _{gas discharge valve is opened when the volume is V 2} and the piston moves slowly downwards, whereas in a compression process of a machine without a residual gas discharge valve, the inlet valve is open when the residual air in the dead space is at a pressure P. and a volume V _fi adiabatically expands, until the air pressure P is _Q, and the volume ^V 2 ^{t) e 'Trä} S ^i: · ^{as the} volume ER in an actual intake stroke of an engine with a Restgasausstoßvsntil

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is aimed to be (ν ,, - Vp) greater than that of an engine without an exhaust valve, the inertia possessed by the air in the intake pipe increases, and consequently the air pressure Pp of a compression chamber becomes the volume V ^ am The end of an intake stroke of an engine with a residual gas discharge valve is achieved so that at the time when the piston closes the inlet valve 9 at its bottom dead center Z, the air pressure is greater than the air pressure Pp _a , ^ ^{er with an} engine without a residual gas discharge valve has been achieved.

As the volume V- ^ at the time when the air is compressed, and reaches a certain pressure, is greater than the volume V- of a machine without a residual gas exhaust valve, the exhaust

Impact volume (V ^ -V _n ) per stroke is consequently greater than the outlet volume (V ^ -Vq) of a machine without a residual gas discharge valve.

Although what has been described above is shown in connection with a four-stroke engine only, a two-stroke engine can also be used as well as a rotary engine can be provided with a residual gas discharge valve if they are equipped with an improved valve are equipped for a compression process. A rotary piston engine as shown in Fig. 54 is a rotary piston engine, which is so improved that it can perform a compression process as in Fig. 21, and is furthermore provided with residual gas discharge valves 177,178. These residual gas discharge valves 177,178 are at one revolution of the The eccentric shaft is actuated once by cams, as is the case with both Inlet and outlet valves 111, 112, 113 and 114 is the case, the cams additionally for the residual gas discharge valves the camshaft 115 for actuating the inlet and outlet valves 111,112,113,114 are attached. The inlet valve 113 and the ■ As already mentioned, exhaust valves 114 are held open during work machine operation, but while the residual gas exhaust valve is in operation 177 should be kept closed. The time of opening of the residual gas discharge valves 177,178, where

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the valves 177,178 are only actuated when a compression process is carried out, usually coincides with the time of the ignition process in the machine during operation of the working machine together, however, it is better if the point in time with a time shortly after the rotor has reached its top dead center reached, coincides.

If a machine is provided with the residual gas exhaust valve, an exhaust volume per stroke becomes larger and the air of high pressure and high temperature remaining in the dead volume is expelled to the outside, and hence becomes a Temperature rise in the compression chamber kept within limits, so that it is possible to achieve the required cooling capacity of a Reduce cooler. Furthermore, a supercharging operation can be achieved by adding air to be discharged into the intake pipes the other group of compression chambers.

When the machine performs a compression operation, no trouble arises to all the compression chambers as one Air compressor for use, but when a part of the plurality of compression chambers is used for a compression process v / ground, the timing for the ignition of the machine may be wrong and a torque change occurs, causing vibrations caused. When a part of a machine is expected to be compressing, it can become a state of equilibrium e.g. achieved by using a damper such as a Servo motor, is used to keep the torque fluctuations as small as possible, or that a larger flywheel is used, which has less torque fluctuation, or at equilibrium, parallel to the crankshaft, to lock them by a gear only when a compression process takes place.

The machine built into a motor vehicle, which - as above mentioned-built, can be both an air compressor as well

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a .control device_, with part or all of its compression chambers be for a compression process ..

The following is a control process of a machine whose Compression chambers all used for a compression process are described.

When a vehicle operator depresses the brake pedal (or the handbrake lever) to slow the motor vehicle or To stop, an electrical device (not shown) is operated a little later than a game, and some compression chambers of the machine work as an air compressor. Different In other words, the actuation of an electrical control device acts on the cam switching device in order to control the cams to switch some compression chambers into cams for a compression process, and solenoid valves work at the same time the carburetor and the inlet and outlet pipes gradually so that some of the compression chambers are only supplied with air. If the brake pedal is pressed again, the cam switching device for all compression chambers responds, and solenoid valves for separating inlet and outlet pipes open so that the inlet-outlet flow path that to leads to all compression chambers, can be transformed into a flow path for a compression process Braking the motor vehicle quickly. When the speed of the motor vehicle is reduced to a certain speed is, a speed monitoring device (not shown) transmits signals to the electrical control device, by keeping the machine idling and then resuming work machine operation. Different in terms of having absorbed a significant amount of the kinetic energy of a machine through a compression process is, a compression operation is changed to a work machine operation. If you press again the brake pedal is applied a friction brake while the

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240-655

Speed monitoring device continues to operate so that the motor vehicle can be stopped by its machine in a work machine operation.

If a machine has a single compression chamber and a single cam switch, it changes Simultaneously with the actuation of the electrical control device, the machine is turned into an air compressor by using a exerts strong steering force on the vehicle at one time. Furthermore, it is possible to stop the work machine operation and the Restart the machine using compressed air as shown later.

The process of controlling that the machine as a whole turns into an air compressor is transformed with the actuation of the electrical control device, can also be used in the case in which a machine has a plurality of compression chambers.

In the following description, of the compressed air that is obtained during a compression process of the machine, as described above, made use of.

When an air motor is used as a self-starter in vehicles, compressed air can be used to operate the air motor are generated while, when a hydraulic motor is used, the compressed air for operating the hydraulic motor can be used by an auxiliary hydraulic motor or the like.

Compressed air may further, by being injected through a residual gas ejection force valve in the engine, rather than as mentioned above, is used for starting an engine of operating a self-starter, which has been stopped, or may be the machine to operate continuously, thereby

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the consumption of fuel and exhaust gas is reduced.

When high pressure air used when operating a machine as a Air compressor to double the compression is achieved, acting on an air outlet as back pressure, is on the machine exerted an extremely large braking force.

If the air tank is completely filled with compressed air that is in a large Amount has been generated, is filled, the excess air should immediately be expelled or into the machine be ejected through the nozzle onto the same in order to use it to cool the machine. If the machine is connected to a Air starter and a pump, the excess air can enter the inlet port of the air starter and the pump ' are ejected, and it is compressed again, as with the · · double compression, ... .'i, to a desired to achieve compressed air. Furthermore, the excess air becomes in a spare tire or a chassis of the vehicle or otherwise saved if the © were previously converted into an auxiliary stench.

Furthermore, the vehicle can be provided with an additional discharge unit through which compressed air flows to achieve negative pressure, the auxiliary control device of the vehicle tending to apply negative pressure to the surface of the streets.

If the machine is used as an air compressor, it can they are operated as a vacuum pump and used for a fire engine, a vacuum vehicle or the like will.

If the compressed air is still after it for a such vacuum operation · or as a tool 'with compressed air operation · was used

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has low pressure, it can be used again for precompaction of the machine according to the subject matter of the invention will.

As a modified embodiment of a residual air discharge force valve or for their use, a sub-inlet valve of a flame machine is used as a power valve, and such a cam as shown in Fig. 20 is used, to change the lift of the sub-intake valve, and is adapted to accommodate the passage between the sub-combustion chamber and to open and close the main combustion chamber, reducing the cylinder opening and reducing the residual gas is expelled. Further, the engine can be opened into the engine by expelling compressed air through the sub-intake valve to be started.

If an engine with double, overhead camshaft is equipped with an additional residual gas exhaust valve, you can the intake and exhaust valves are operated together as an intake valve, and the power valve as a discharge power valve to work, or the intake valve and the exhaust valve are operated together as exhaust valves, and compressed

Air is expelled into the machine through the power valve at a given moment in order to use the valves as valves Start button that will cause the machine to start. ' In the case described above, the pipes and the like can be changed to choose a clever arrangement.

The following are the main advantages of the invention Object summarized.

At the same time as the steering of a motor vehicle, air can be compressed in the compression chambers of the engine, and consequently a control force on the machine can like

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can also be applied to the motor vehicle so that kinetic energy of the machine and the vehicle itself are effectively diverted can be.

The machine configured as an air compressor can have the function of a motor, an air compressor and an engine brake carry out.

The machine - as a machine brake - works more effectively than a conventional engine brake and does not have an environmentally polluting one Influence.

A machine with a plurality of compression chambers can use some of the compression chambers as an air compressor and the other than a work machine so that compressed air is gradually obtained from the air compressor. Consequently it is not necessary, as usual, to install an air compressor together with a working machine.

The machine according to the invention has a great utility value, since compressed air is used in a machine which is used as an air compressor works, accrues, for facilities for generating Syren for a supercharger, for a vacuum component, for an air blower device, etc. can be used.

A load reducing device attached to a camshaft is, simply and easily degrades the performance of a machine at the time of starting the machine when it is converted into an air compressor and at the time when compressed air is not required.

The auxiliary valve actuators provided can achieve precise opening and closing of the valves themselves if the machine is turned into an air compressor, and the stopping ability of the valve operation at a time when the machine is reaching a high speed can be reduced.

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- 5ο -

and can prevent the valves from locking, bouncing and jumping.

Since the position of a tappet engaged with the tapered cam can be moved to change a valve lift, suction and discharge can be achieved with great efficiency when the engine is at a high
Speed works.

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Claims (14)

Claims Working air compressor machine designed so that it can be used in a means of transport, characterized by an air supply device which controls the fuel supply to at least a compression chamber and the compression chamber is only supplied with air, an air release device, which at a certain point in time releases the compressed air in the compression chamber, and an actuating device, the air supply device and the air discharge device operated at a desired time. 2. A working air compressor machine according to claim 1, characterized by a machine bed having a plurality of cylindrical bores, the bores being provided with a first set and a second set of compression chambers, each of the sets having a plurality of compression chambers, and the first set having a greater number of compression chambers than the second set, each of the compression chambers being provided with an inlet and an outlet port, through an inlet and outlet valve installed for each compression chamber for closing and opening the inlet and outlet ports is, by a piston built in each compression chamber to be movable back and forth *, by crankshafts that are rotatably built into the machine bed and connected to the pistons for reciprocating the pistons, by a first camshaft that is rotatable and axially Slidably mounted in the machine bed and came with the first set of compression connected. den is, and by a second camshaft that is rotatable. and axially displaceably attached to the machine bed 409832/0379 and connected to the second set of compression chambers each of the camshafts being connected to the camshaft during operation to rotate therefrom held to ground by a pair of cams for each inlet and outlet valve of each compression chamber of the first Set attached to the first camshaft and a pair of cams for each intake and exhaust valve one each compression karamer of the second set attached to the second camshaft, each pair of Cam is divided into work machine and air compressor cams, each work machine and air compressor cam of each pair has a tapered cam surface opposite the other cam of the pair and is adapted to be engaged with a follower means by means of a follower means, those on the machine for each inlet and outlet valve to open and close the valves back and forth is movably installed, each camshaft being axially displaceable independently of one another between a first position, in which the work machine cams of each pair of cams on the camshaft are engaged with the follower means and a second position in which the air compressor cams of each pair of cams are attached to the Camshaft is in engagement with the tappet means, is mounted, the cam surface of each Work machine cam is designed so that the tappet device during each revolution of the communicating Camshaft is reciprocated once, and the cam surface of each air compressor cam is so formed is that the tappet means twice during each revolution of the associated camshaft is reciprocated, by a cam switching device, each of the camshafts of the first and second sets moved axially, by an air supply device, which shut off the fuel supply to the compression chambers 409832/0379 can and can only supply the compression chambers with air, vrobei this device for this process executes the first set and the second set separately, through an air dispenser, into the compressed Air is discharged from the compression chambers supplied with air only, and by an actuator which actuates the air supply device and the air discharge device. 3. Working air compressor machine according to claim 1, characterized characterized in that a two-stroke engine having a plurality of compression chambers is provided with exhaust ports is provided anywhere on the cylinder head of the engine, and wherein the valve operating device Exhaust valves for opening and closing the exhaust ports, that each cam of the valve operating device has a cylindrical part that closes the valves . Sen holds, so that the machine performs a work machine operation and has a chamfered part that has a The tappet is actuated once for one revolution of the camshaft, so that the machine carries out the compression process, and that some or all of the plurality of compression chambers can be operated as an air compressor. 4. Working air compressor machine according to claim 1, characterized in that each compression chamber of a rotary motor, having a plurality of compression chambers with. an additional inlet port and one Outlet opening is provided, which is usually point-symmetrical to an original inlet opening and an original Outlet opening on the machine are placed on a circle around the pivot point of the rotor that two pairs of Intake valves and exhaust valves to open and close the two pairs of intake and exhaust valves that a plurality of valve actuators to control the 409832/0379 to operate two pairs of inlet and outlet valves in pairs, that means that the inlet and outlet valves for the original inlet and outlet ports Holds open when a work machine operation is in progress and that a device is provided which only keeps the additional inlet and outlet valves open, when performing a work machine operation, the valve actuating means being adapted to each of the valves is opened once at a certain point in time during one rotation of the rotor, with some or all of the plurality of compression chambers operate as an air compressor. 5. Working air compressor machine according to claim 1, characterized by a machine with an additional compression chamber with an air supply device is provided, which shuts off the fuel supply and only supplies it with air, through an air discharge device which releases compressed air into the compression chamber at a specified time, and by an actuator, which the air supply device actuates the air discharge device at a certain point in time, being the machine like that. is designed to operate rapidly as an air compressor. 6. Working air compressor machine including cams, characterized in that each of the cams has an annular bead on v / eist which is in the middle between the cam for a work machine operation and the cam for a compression operation lies, with the cams alternately facing the camshaft. 7. Working air compressor machine according to claim 2 or 5, characterized in that on the between the cam for one work machine operation and the cam for one 409832/0 379 Compression process lying part, whereby these nooks are alternately opposite on the same camshaft, the suction cam is attached, with a half-open area to shorten the valve lift and with a final part to completely close the openings is provided that the outlet cam is a half-open Area, with a slightly open area to make the valve lift as small as possible, and with a final one Area is provided, and that these cams for a work machine operation and a compression process in passes over the area lying in the middle, and that the camshaft is designed so that it is through a device can be changed so that at least one five-step camshaft switching process occurs. 8. Working air compressor machine according to claim 2 or 5, characterized in that a beveled nooke for a compression process and a beveled cam _ are mounted for a work machine operation that they are offset from the camshaft and with its beveled. Surface outward showing that the beveled cams are connected to one another by a '^ cylindrical part are to keep the valves open, and that the camshaft is designed so that they are at least with a three-step camshaft switching process can be changed. 9. Working air compressor machine, characterized in that each of the cams for a compression process having a cylindrical part and a beveled part; is provided with an annular bead which extends around the cylindrical part of the cam. 10. Working air compressor machine according to claim 2, 3, 4 and 5, characterized in that there is a valve actuating device which is equipped with an auxiliary valve actuating device 409832/0379 Means is provided to change the stretching force of the valve springs at a certain point in time 11. Working air compressor machine, characterized in that that an opening is provided between the outlet and the inlet opening which leads to a compression chamber, and in that the opening is provided with a valve operated by a cam to form the valve is that it is opened for a period of time required for exhausting the residual air located in the dead space is, usually at the same time when the exhaust valve is closed. 12. Working air compressor machine, characterized in that that an engine having a cam operated valve with an additional inlet and outlet port is provided, both openings leading to a compression chamber, and that each inlet and outlet opening with an automatic valve is provided. 13. Working air compressor machine according to claim 12 with a automatic valve, characterized by a valve seat with a plurality of bores, a valve plate to close the bores by the compressive force of a spring, a valve seat for the exact attachment of the spring and the valve plate, a fastening device for fastening the valve receptacle to the valve plate Holder that passes through the receptacle to press the spring, and a compressive force device to put on the holder exert a force to push the spring. 14. Working air compressor machine, characterized by at least a single compression chamber for starting the working air compressor machine. 15 »Working air compressor machine according to claim 1, characterized 409832/0379 characterized in that each compression chamber of a rotary motor, which has a plurality of compression chambers, with an additional inlet port and one Outlet opening is provided, which is usually point-symmetrical to an original inlet opening and an original Outlet opening on the machine are placed on a circle around the fulcrum of the rotor to the two pairs of Inlet and outlet ports open and close that a plurality of valve actuators to the two pairs of inlet and outlet valves to operate in pairs, that one device operating the inlet and outlet valves keeps open for the original intake and exhaust ports when a work machine operation is in progress and that a device is provided which only keeps the additional inlet and outlet valves open, when a work machine operation is carried out, wherein the valve actuation devices are designed so that each of the valves is opened once at a certain point in time during one revolution of the rotor, \ robei some or all of the plurality of compression chambers function as an air compressor. 409832/0379 Blank page